Method and apparatus for monitoring a refrigeration-cycle system

Description

BACKGROUND

1. Field of the Invention

The invention relates to a monitoring system for measuring the operating and efficiency of a refrigerant-cycle system, such as, for example, an air conditioning system or refrigeration system.

2. Description of the Related Art

One of the major recurring expenses in operating a home or commercial building is the cost of providing electricity to the Heating Ventilation Air Conditioning (HVAC) system. If the HVAC system is not operating at peak efficiency, then the cost of operating the system increases unnecessarily. Each pound of refrigerant circulating in the system must do its share of the work. It must absorb an amount of heat in the evaporator or cooling coil, and it must dissipate this heat—plus some that is added in the compressor—through the condenser, whether air cooled, water cooled, or evaporative cooled. The work done by each pound of the refrigerant as it goes through the evaporator is reflected by the amount of heat it picks up from the refrigeration load, chiefly when the refrigerant undergoes a change of state from a liquid to a vapor.

For a liquid to be able to change to a vapor, heat must be added to or absorbed in it. This is what happens in the cooling coil. The refrigerant enters the metering device as a liquid and passes through the device into the evaporator, where it absorbs heat as it evaporates into a vapor. As a vapor, it makes its way through the suction tube or pipe to the compressor. Here it is compressed from a low temperature, low pressure vapor to a high temperature, high pressure vapor; then it passes through the high pressure or discharge pipe to the condenser, where it undergoes another change of state—from a vapor to a liquid—in which state it flows out into the liquid pipe and again makes its way to the metering device for another trip through the evaporator.

When the refrigerant, as a liquid, leaves the condenser it may go to a receiver until it is needed in the evaporator; or it may go directly into the liquid line to the metering device and then into the evaporator coil. The liquid entering the metering device just ahead of the evaporator coil will have a certain heat content (enthalpy), which is dependent on its temperature when it enters the coil, as shown in Table 2 below and FIGS. 2-8. The vapor leaving the evaporator will also have a given heat content (enthalpy) according to its temperature, as shown in the refrigerant tables.

The difference between these two amounts of heat content is the amount of work being done by each pound of refrigerant as it passes through the evaporator and picks up heat. The amount of heat absorbed by each pound of refrigerant is known as the refrigerating effect of the system, or of the refrigerant within the system.

Situations that can reduce the overall efficiency of the system include, refrigerant overcharge, refrigerant undercharge, restrictions in refrigerant lines, faulty compressor, excessive load, insufficient load, undersized or dirty duct work, clogged air filters, etc.

Unfortunately, modern HVAC systems do not include monitoring systems to monitor the operating of the system. A modern HVAC system is typically installed, charged with refrigerant by a service technician, and then operated for months or years without further maintenance. As long as the system is putting out cold air, the building owner or home owner assumes the system is working properly. This assumption can be expensive, as the owner has no knowledge of how well the system is functioning. If the efficiency of the system deteriorates, the system may still be able to produce the desired amount of cold air, but it will have to work harder, and consume more energy, to do so. In many cases, the system owner does not have the HVAC system inspected or serviced until the efficiency has dropped so low that it can no longer cool the building. This is in part because servicing of an HVAC system requires specialized tools and knowledge that the typical building owner or home owner does not possess. Thus, the building owner or home owner must pay for an expensive service call in order to have the system evaluated. Even if the owner does pay for a service call, many HVAC service technicians do not measure system efficiency. Typically, the HVAC service technicians are trained only to make rudimentary checks of the system (e.g., refrigerant charge, output temperature), but such rudimentary checks may not uncover other factors that can cause poor system efficiency. Thus, the typical building owner, or home owner, operates the HVAC system year after year not knowing that the system may be wasting money by operating at less than peak efficiency. Moreover, inefficient use of electrical power can lead to brownouts and blackouts during heat waves or other periods of high air conditioning usage due to overloading of the electric power system (commonly referred to as the electric power grid).

SUMMARY OF THE INVENTION

These and other problems are solved by a real-time monitoring system that monitors various aspects of the operation of a refrigerant system, such as, for example, an HVAC system, a refrigerator, a cooler, a freezer, a water chiller, etc. In one embodiment, the monitoring system is configured as a retrofit system that can be installed in an existing refrigerant system.

In one embodiment, the system includes a processor that measures power provided to the HVAC system and that gathers data from one or more sensors and uses the sensor data to calculate a figure of merit related to the efficiency of the system. In one embodiment, the sensors include one or more of the following sensors: a suction line temperature sensor, a suction line pressure sensor, a suction line flow sensor, a hot gas line temperature sensor, a hot gas line pressure sensor, a hot gas line flow sensor, a liquid line temperature sensor, a liquid line pressure sensor, and a liquid line flow sensor. In one embodiment, the sensors include one or more of an evaporator air temperature input sensor, an evaporator air temperature output sensor, an evaporator air flow sensor, an evaporator air humidity sensor, and a differential pressure sensor. In one embodiment, the sensors include one or more of a condenser air temperature input sensor, a condenser air temperature output sensor, a condenser air flow sensor, and an evaporator air humidity sensor. In one embodiment, the sensors include one or more of an ambient air sensor and an ambient humidity sensor.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram of a typical refrigerant-cycle system used in HVAC systems, refrigerators, freezers, and the like.

FIG. 2 is a detailed pressure-heat diagram of a typical refrigerant (R-22).

FIG. 3 is a pressure-heat diagram showing pressure-enthalpy changes through a refrigeration cycle.

FIG. 4 is a pressure-heat diagram showing pressure, heat, and temperature values for a refrigeration cycle operating with a 40° F. evaporator.

FIG. 5 is a pressure-heat diagram showing pressure, heat, and temperature values for a refrigeration cycle operating with a 20° F. evaporator.

FIG. 6 is a pressure-heat diagram showing the cycle of FIG. 4 with a 40° F. evaporating temperature, where the condensing temperature has been increased to 120° F.

FIG. 7 is a pressure-heat diagram showing how subcooling by the condenser improves the refrigeration effect and the COP.

FIG. 8 is a pressure-heat diagram showing the cooling process in the evaporator.

FIG. 9A is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system.

FIG. 9B is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system, where operating data for the system is provided to a monitoring service, such as, for example, a power company or monitoring center, by using data transmission over power lines.

FIG. 9C is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system, where operating data for the system is provided to a monitoring service, such as, for example, a power company or monitoring center, by using data transmission over a computer network.

FIG. 9D is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system, where data regarding operation of the system is provided to a thermostat and/or to a computer system such as, for example, a site monitoring computer, a maintenance computer, a personal digital assistant, a personal computer, etc.

FIG. 9E is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system wherein an electronically-controlled metering device is provided to allow control of the system in an energy-efficient matter.

FIG. 9F is a block diagram of a thermostat control and monitoring system having a data interface device provided to the thermostat.

FIG. 9G is a block diagram of a thermostat control and monitoring system having a data interface device provided to the evaporator unit.

FIG. 9H is a block diagram of a thermostat control and monitoring system having a data interface device provided to the condenser unit.

FIG. 10 (consisting of FIGS. 10A and 10B) shows various sensors that can be used in connection with the system of FIGS. 9A-H for monitoring the operation of the refrigerant-cycle system.

FIG. 11 shows the temperature drop in the air through the evaporator as a function of humidity.

FIG. 12 shows heat capacity of a typical refrigerant-cycle system as a function of refrigerant charge.

FIG. 13 shows power consumed in a typical refrigerant-cycle system as a function of refrigerant charge.

FIG. 14 shows efficiency of a typical refrigerant-cycle system as a function of refrigerant charge.

FIG. 15 shows a differential-pressure sensor used to monitor an air filter in an air-handler system.

FIG. 16 shows a differential-pressure sensor used to monitor an air filter in an air-handler system using a wireless system to provide filter differential pressure data back to other aspects of the monitoring system.

FIG. 17 shows the system of FIG. 16 implemented using a filter frame to facilitate retrofitting of existing air handler systems.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 is a diagram of a typical refrigerant-cycle system 100 used in HVAC systems, refrigerators, freezers, and the like. In the system 100, a compressor 105 provides hot compressed refrigerant gas to a hot gas line 106. The hot gas line 106 provides the hot gas to a condenser 107. The condenser 107 cools the gas and condenses the gas into a liquid that is provided to a liquid line 108. The liquid refrigerant in the liquid line 108 is provided through a metering device 109 to an evaporator 110. The refrigerant expands back into a gas in the evaporator 110 and is provided back to the compressor 105 through a suction line 111. A suction service valve 120 provides access to the suction line 111. A liquid line service valve 121 provides access to the liquid line 108. A fan 123 provides input air 124 to the evaporator 110. The evaporator 110 cools the air and provides cooled evaporator output air 125. An optional drier/accumulator 130 can be provided in the liquid line 108. A fan 122 provides cooling air to the condenser 107.

The metering device 109 can be any refrigerant metering device as used in the art, such as, for example, a capillary tube, a fixed orifice, a Thermostatic eXpansion Valve (TXV), an electronically controlled valve, a pulsating solenoid valve, a stepper-motor valve, a low side float, a high-side float, an automatic expansion valve, etc. A fixed metering device such as a capillary tube or fixed orifice will allow some adjustment in system capacity as the load changes. As the outdoor condensing temperature increases, more refrigerant is fed through the metering device into the evaporator 110, increasing its capacity slightly. Conversely, as the heat load goes down, the outdoor condensing temperature goes down and less refrigerant is fed into the evaporator 110. For a location where the load does not vary widely, fixed metering devices may float with the load well enough. However, for climates where there is a relatively greater range in temperature variation, an adjustable metering device is typically used.

The system 100 cools the air through the evaporator 110 by using the refrigerating effect of an expanding gas. This refrigerating effect is rated in Btu per pound of refrigerant (Btu/lb). If the total heat load is known (given in Btu/hr), one can find the total number of pounds of refrigerant that must be circulated each hour of operation of the system. This figure can be broken down further to the amount that must be circulated each minute, by dividing the amount circulated per hour by 60.

Because of a small orifice in the metering device 109, when the compressed refrigerant passes from the smaller opening in the metering device 109 to the larger tubing in the evaporator 110, a change in pressure occurs together with a change in temperature. This change in temperature occurs because of the vaporization of a small portion of the refrigerant (about 20%) and, in the process of this vaporization, the heat that is involved is taken from the remainder of the refrigerant.

For example, from the table of saturated R-22 in FIG. 2, it can be seen that the heat content of 100° F. liquid is 39.27 Btu/lb and that of 40° F. liquid is 21.42 Btu/lb; this indicates that 17.85 Btu/lb has to be removed from each pound of refrigerant entering the evaporator 110. The latent heat of vaporization of 40° F. (17.85 Btu/lb) is 68.87 Btu/lb. This is another method of calculating the refrigerating effect, or work being done, by each pound of refrigerant under the conditions given.

The capacity of the compressor 105 should be such that it will remove from the evaporator 110 that amount of refrigerant which has vaporized in the evaporator 110 and in the metering device 109 in order to get the necessary work done. The compressor 105 must be able to remove and send on to the condenser 107 the same weight of refrigerant vapor, so that it can be condensed back into a liquid and so continue in the system 100 to perform additional work.

If the compressor 105 is unable to move this weight, some of the vapor will remain in the evaporator 110. This, in turn, will cause an increase in pressure inside the evaporator 110, accompanied by an increase in temperature and a decrease in the work being done by the refrigerant, and design conditions within the refrigerated space cannot be maintained.

A compressor 105 that is too large will withdraw the refrigerant from the evaporator 110 too rapidly, causing a lowering of the temperature inside the evaporator 110, so that design conditions will not be maintained.

In order for design conditions to be maintained within a refrigeration circuit, a balance between the requirements of the evaporator 110 and the capacity of the compressor 105 is maintained. This capacity is dependent on its displacement and on its volumetric efficiency. Volumetric efficiency depends on the absolute suction and discharge pressures under which the compressor 105 is operating.

In one embodiment, the system 100 controls the speed of the compressor 105 to increase efficiency. In one embodiment, the system 100 controls the metering device 109 to increase efficiency. In one embodiment, the system 100 controls the speed of the fan 123 to increase efficiency. In one embodiment, the system 100 controls the speed of the fan 122 to increase efficiency.

In the system 100, the refrigerant passes from the liquid stage into the vapor stage as it absorbs heat in the evaporator 110 coil. In the compressor 105 stage, the refrigerant vapor is increased in temperature and pressure, then the refrigerant gives off its heat in the condenser 107 to the ambient cooling medium, and the refrigerant vapor condenses back to its liquid state where it is ready for use again in the cycle.

FIG. 2 shows the pressure, heat, and temperature characteristics of this refrigerant. Enthalpy is another word for heat content. Diagrams such as FIG. 2 are referred to as pressure-enthalpy diagrams. Detailed pressure-enthalpy diagrams can be used for the plotting of the cycle shown in FIG. 2, but a basic or skeleton chart as shown in FIG. 3 is useful as a preliminary illustration of the various phases of the refrigerant circuit. There are three basic areas on the chart denoting changes in state between the saturated liquid line 301 and the saturated vapor line 302 in the center of the chart. The area to the left of the saturated liquid line 301 is the subcooled area, where the refrigerant liquid has been cooled below the boiling temperature corresponding to its pressure; whereas the area to the right of the saturated vapor line 302 is the area of superheat, where the refrigerant vapor has been heated beyond the vaporization temperature corresponding to its pressure.

The construction of the diagram 300 illustrates what happens to the refrigerant at the various stages within the refrigeration cycle. If the liquid vapor state and any two properties of a refrigerant are known and this point can be located on the chart, the other properties can be determined from the chart.

If the point is situated anywhere between the saturated liquid line 301 and vapor line 302, the refrigerant will be in the form of a mixture of liquid and vapor. If the location is closer to the saturated liquid line 301, the mixture will be more liquid than vapor, and a point located in the center of the area at a particular pressure would indicate a 50% liquid 50% vapor situation.

The change in state from a vapor to a liquid, the condensing process, occurs as the path of the cycle develops from right to left; whereas the change in state from a liquid to a vapor, the evaporating process, travels from left to right. Absolute pressure is indicated on the vertical axis at the left, and the horizontal axis indicates heat content, or enthalpy, in Btu/lb.

The distance between the two saturated lines 301 and 302 at a given pressure, as indicated on the heat content line, amounts to the latent heat of vaporization of the refrigerant at the given absolute pressure. The distance between the two lines of saturation 301 and 302 is not the same at all pressures, for they do not follow parallel curves. Therefore, there are variations in the latent heat of vaporization of the refrigerant, depending on the absolute pressure. There are also variations in pressure-enthalpy charts of different refrigerants and the variations depend on the various properties of the individual refrigerants.

There is relatively little temperature change of the condensed refrigeration liquid after it leaves the condenser 107 and travels through the liquid line 108 on its way to the expansion or metering device 109, or in the temperature of the refrigerant vapor after it leaves the evaporator 110 and passes through the suction line 111 to the compressor 105.

FIG. 4 shows the phases of the simple saturated cycle with appropriate labeling of pressures, temperatures, and heat content or enthalpy. Starting at point A on the saturated liquid where all of the refrigerant vapor at 100° F. has condensed into liquid at 100° F. and is at the inlet to the metering device, between points A and B is the expansion process as the refrigerant passes through the metering device 109; and the refrigerant temperature is lowered from the condensation temperature of 100° F. to the evaporating temperature of 40° F.

When the vertical line A-B (the expansion process) is extended downward to the bottom axis, a reading of 39.27 Btu/lb is indicated, which is the heat content of 100° F. liquid. To the left of point B at the saturated liquid line 301 is point Z, which is also at the 40° F. temperature line. Taking a vertical path downward from point Z to the heat content line, a reading of 21.42 Btu/lb is indicated, which is the heat content of 40° F. liquid.

The horizontal line between points B and C indicates the vaporization process in the evaporator 110, where the 40° F. liquid absorbs enough heat to completely vaporize the refrigerant. Point C is at the saturated vapor line, indicating that the refrigerant has completely vaporized and is ready for the compression process. A line drawn vertically downward to where it joins the enthalpy line indicates that the heat content, shown at h_cis 108.14 Btu/lb, and the difference between h_aand h_cis 68.87 Btu/lb, which is the refrigerating effect, as shown in an earlier example.

The difference between points h_zand h_c, on the enthalpy line amounts to 86.72 Btu/lb, which is the latent heat of vaporization of 1b of R-22 at 40° F. This amount would also exhibit the refrigerating effect, but some of the refrigerant at 100° F. must evaporate or vaporize in order that the remaining portion of each pound of R-22 can be lowered in temperature from 100° F. to 40° F.

All refrigerants exhibit properties of volume, temperature, pressure, enthalpy or heat content, and entropy when in a gaseous state. Entropy is defined as the degree of disorder of the molecules that make up the refrigerant. In refrigeration, entropy is the ratio of the heat content of the gas to its absolute temperature in degrees Rankin.

The pressure-enthalpy chart plots the line of constant entropy, which stays the same provided that the gas is compressed and no outside heat is added or taken away. When the entropy is constant, the compression process is called adiabatic, which means that the gas changes its condition without the absorption or rejection of heat either from or to an external body or source. It is common practice, in the study of cycles of refrigeration, to plot the compression line either along or parallel to a line of constant entropy.

In FIG. 5, line C-D denotes the compression process, in which the pressure and temperature of the vapor are increased from that in the evaporator 110 to that in the condenser 107, with the assumption that there has been no pickup of heat in the suction line 111 between the evaporator 110 and the compressor 105. For a condensing temperature of 100° F., a pressure gauge would read approximately 196 psig; but the chart is rated in absolute pressure and the atmospheric pressure of 14.7 is added to the psig, making it actually 210.61 psia.

Point Don the absolute pressure line is equivalent to the 100° F. condensing temperature; it is not on the saturated vapor line, it is to the right in the superheat area, at a junction of the 210.61 psia line, the line of constant entropy of 40° F., and the temperature line of approximately 128° F. A line drawn vertically downward from point D intersects the heat content line at 118.68 Btu/lb, which is h_d, and the difference between h_cand h_dis 10.54 Btu/lb—the heat of compression that has been added to the vapor. This amount of heat is the heat energy equivalent of the work done during the refrigeration compression cycle. This is the theoretical discharge temperature, assuming that saturated vapor enters the cycle; in actual operation, the discharge temperature may be 20° to 35° higher than that predicted theoretically. This can be checked in the system 100 by attaching a temperature sensor 1016 to the hot gas line 106.

During the compression process, the vapor is heated by the action of its molecules being pushed or compressed closer together, commonly called heat of compression.

Line D-E denotes the amount of superheat that must be removed from the vapor before it can commence the condensation process. A line drawn vertically downward from point E to point h_eon the heat content line indicates the distance h_d−h_e, or heat amounting to 6.57 Btu/lb, since the heat content of 100° F. vapor is 112.11 Btu/lb. This superheat is usually removed in the hot gas discharge line or in the upper portion of the condenser 107. During this process the temperature of the vapor is lowered to the condensing temperature.

Line E-A represents the condensation process that takes place in the condenser 107. At point E the refrigerant is a saturated vapor at the condensing temperature of 100° F. and an absolute pressure of 210.61 psia; the same temperature and pressure prevail at point A, but the refrigerant is now in a liquid state. At any other point on line E-A the refrigerant is in the phase of a liquid vapor combination; the closer the point is to A, the greater the amount of the refrigerant that has condensed into its liquid stage. At point A, each pound of refrigerant is ready to go through the refrigerant cycle again as it is needed for heat removal from the load in the evaporator 110.

Two factors that determine the coefficient of performance (COP) of a refrigerant are refrigerating effect and heat of compression. The equation (equation 1) may be written as:

$COP = \frac{refrigerating_effect}{heat_of_compression}$

Substituting values, from the pressure-enthalpy diagram of the simple saturated cycle previously presented, the equation would be:

$COP = \frac{h_{c} - h_{a}}{h_{d} - h_{c}} = \frac{68.87}{10.54} = 6.53$

The COP is, therefore, a rate or a measure of the theoretical efficiency of a refrigeration cycle and is the energy that is absorbed in the evaporation process divided by the energy supplied to the gas during the compression process. As can be seen from Equation 1, the less energy expended in the compression process, the larger will be the COP of the refrigeration system.

The pressure-enthalpy diagrams in FIGS. 4 and 5 show a comparison of two simple saturated cycles having different evaporating temperatures, to bring out various differences in other aspects of the cycle. In order that an approximate mathematical calculation comparison may be made, the cycles shown in FIGS. 4 and 5 will have the same condensing temperature, but the evaporating temperature will be lowered 20° F. The values of A, B, C, D, and E from FIG. 4 are compared to that in FIG. 5 (with a 20° F. evaporator 110). The refrigerating effect, heat of compression, and the heat dissipated at the condenser 107 in each of the refrigeration cycles will be compared. The comparison will be based on data about the heat content or enthalpy line, rated in Btu/lb.

For the 20° F. evaporating temperature cycle shown in FIG. 5:

Net refrigerating effect (h_c′−h_a)=67.11 Btu/lb
Heat of compression (h_d−h_c′)=12.30 Btu/lb

Comparing the data above with those of the cycle with the 40° F. evaporating temperature FIG. 4, shows that there is a decrease in the net refrigeration effect (NRE) of 2.6% and an increase in the heat of compression of 16.7%. There will be some increase in superheat, which should be removed either in the hot gas line 106 or the upper portion of the condenser 107. This is the result of a lowering in the suction temperature, the condensing temperature remaining the same.

It follows that the weight of refrigerant to be circulated per ton of cooling, in a cycle with a 20° F. evaporating temperature and a 100° F. condensing temperature, is 2.98 lb/min/ton:

$\begin{matrix} W = \frac{200 (Btu / \min)}{NRE (Btu / lb)} \\ = \frac{200 Btu / \min}{67.11 Btu / lb} \\ = 2.98 lb / \min \end{matrix}$

Circulating more refrigerant typically involves either a larger compressor 105, or the same size of compressor 105 operating at a higher rpm.

FIG. 6 shows the original cycle with a 40° F. evaporating temperature, but the condensing temperature has been increased to 120° F.

Again taking the specific data from the heat content or enthalpy line, one now finds for the 120° F. condensing temperature cycle that h_a′=45.71, h_c=108.14, h_d′=122.01, and h_e′=112.78. Thus, the net refrigerating effect (h_c−h_a′)=62.43 Btu/lb, the heat of compression (h_d′−h_c)=13.87 Btu/lb, and the condenser 107 superheat (h_d′−h_e′)=9.23 Btu/lb.

In comparison with the cycle having the 100° F. condensing temperature (FIG. 4), the cycle can also be calculated by allowing the temperature of the condensing process to increase to 120° F. (as shown in FIG. 6). FIG. 6 shows a decrease in the NRE of 9.4%, an increase in heat of compression of 31.6%, and an increase of superheat to be removed either in the discharge line or in the upper portion of the condenser 107 of 40.5%.

With a 40° F. evaporating temperature and a 120° F. condensing temperature, the weight of refrigerant to be circulated will be 3.2 lb/min/ton. This indicates that approximately 10% more refrigerant must be circulated to do the same amount of work as when the condensing temperature was 100° F.

Both of these examples show that for the best efficiency of a system, the suction temperature should be as high as feasible, and the condensing temperature should be as low as feasible. Of course, there are limitations as to the extremes under which the system 100 may operate satisfactorily, and other means of increasing efficiency must then be considered. Economics of equipment (cost+operating performance) ultimately determine the feasibility range.

Referring to FIG. 7, after the condensing process has been completed and all of the refrigerant vapor at 120° F. is in the liquid state, if the liquid can be subcooled to point A on the 100° F. line (a difference of 20° F.), the NRE (h_c−h_a) will be increased by 6.44 Btu/lb. This increase in the amount of heat absorbed in the evaporator 110 without an increase in the heat of compression will increase the COP of the cycle, since there is no increase in the energy input to the compressor 105.

This subcooling can take place while the liquid is temporarily in storage in the condenser 107 or receiver, or some of the liquid's heat may be dissipated to the ambient temperature as it passes through the liquid pipe on its way to the metering device 109. Subcooling can also take place in a commercial type water cooled system through the use of a liquid subcooler.

Normally, the suction vapor does not arrive at the compressor 105 in a saturated condition. As shown in FIG. 8, superheat is added to the vapor after the evaporating process has been completed, in the evaporator 110 and/or in the suction line 111, as well as in the compressor 105. If this superheat is added only in the evaporator 110, it is doing some useful cooling; for it too is removing heat from the load or product, in addition to the heat that was removed during the evaporating process. But if the vapor is superheated in the suction line 111 located outside of the conditioned space, no useful cooling is accomplished; yet this is what takes place in many systems.

In the system 100, the refrigerant pressure is relatively high in the condenser 107 and relatively low in the evaporator 110. A pressure rise occurs across the compressor 105 and a pressure drop occurs across the metering device 109. Thus, the compressor 105 and the metering device 109 maintain the pressure difference between the condenser 107 and the evaporator 110.

Thus, a refrigeration system can be divided into the high side and low side portions. The high side contains the high pressure vapor and liquid refrigerant and is the part of the system that rejects heat. The low side contains the low pressure liquid vapor and refrigerant and is the side that absorbs heat.

Heat is always trying to reach a state of balance by flowing from a warmer object to a cooler object. Heat only flows in one direction, from warmer to cooler. Temperature difference (TD) is what allows heat to flow from one object to another. The greater the temperature difference the more rapid the heat flow. For the high side of a refrigeration unit to reject heat, its temperature must be above the ambient or surrounding temperature. For the evaporator 110 to absorb heat, its temperature must be below the surrounding ambient temperature.

Two factors that affect the quantity of heat transferred between two objects are the temperature difference and the mass of the two objects. The greater the temperature difference between the refrigerant coil (e.g., the condenser 107 or the evaporator 110) and the surrounding air, the more rapid will be the heat transfer. The larger the size of the refrigerant coil, the greater the mass of refrigerant, which also increases the rate of heat transfer. Engineers can either design coils to have high temperature differences or larger areas to increase the heat transfer rate.

To increase energy efficiency, systems are designed with larger coils because it is more efficient to have a lower temperature difference and a larger area to transfer heat. It takes less energy to produce a smaller pressure/temperature difference within a refrigeration system. Manufacturers of new high efficiency air conditioning systems use this principle.

The same principle can be applied to the evaporator 110 coils. The temperature differences between the evaporator input air 124 and the evaporator output air 125 are lower than they were on earlier systems. Older, lower efficiency air conditioning systems may have evaporative coils that operate at 35° F. output temperature, while newer higher efficiency evaporator 110 may operate in the 45° F. output range. Both evaporators 110 can pick up the same amount of heat provided that the higher temperature, higher efficiency coil has greater area and, therefore, more mass of refrigerant being exposed to the air stream to absorb heat. The higher evaporative coil temperature may produce less dehumidification. In humid climates, dehumidification can be an important part of the total air conditioning.

Correct equipment selection is important to ensure system operation and to obtain desired energy efficiencies. Previously, it was a common practice in many locations for installers to select an evaporator 110 of a different tonnage than the condenser unit 101 capacity. While this practice in the past may provide higher efficiencies, for most of today's more technically designed systems proper matching is usually achieved by using the manufacturer's specifications in order to provide proper operation. Mismatching systems can result in poor humidity control and higher operating costs. In addition to poor energy efficiency and lack of proper humidity control, the compressor 105 in a mismatched system may not receive adequate cooling from returning refrigerant vapor. As a result the compressor 105 temperature will be higher, and this can reduce the life of the compressor 105.

As refrigerant vapor leaves the discharge side of the compressor 105, it enters the condenser 107. As this vapor travels through the condenser 107, heat from the refrigerant dissipates to the surrounding air through the piping and fans. As heat is removed, the refrigerant begins to change state from vapor to liquid. As the mixture of liquid and vapor continues to flow through the condenser 107, more heat is removed and eventually all, or virtually all, of the vapor has transformed into liquid. The liquid flows from the outlet of the condenser 107 through the liquid line 108 to the metering device 109.

The high pressure, high temperature liquid refrigerant passes through the metering device 109 where its temperature and pressure change. As the pressure and temperature change, some of the liquid refrigerant boils off forming flash gas. As this mixture of refrigerant, liquid, and vapor flow through the evaporator 110, heat is absorbed, and the remaining liquid refrigerant changes into a vapor. At the outlet of the evaporator 110 the vapor flows back through the suction line 111 to the compressor 105.

The compressor 105 draws in this low pressure, low temperature vapor and converts it to a high temperature, high pressure vapor where the cycle begins again.

An ideally sized and functioning system 100 is one where the last bit of refrigerant vapor changes into a liquid at the end of the condenser 107 and where the last bit of liquid refrigerant changes into a vapor at the end of the evaporator 110. However, because it is impossible to have a system operate at this ideal state, units are designed to have some additional cooling, called subcooling, of the liquid refrigerant to ensure that no vapor leaves the condenser 107. Even a small amount of vapor leaving the condenser 107 can significantly reduce efficiency of the system 100.

On the evaporator 110 side a small amount of additional temperature is added to the refrigerant vapor, called superheat, to ensure that no liquid refrigerant returns to the compressor 105. Returning liquid refrigerant to the compressor 105 can damage the compressor 105.

Systems that must operate under a broad range of temperature conditions will have difficulty maintaining the desired level of subcooling and superheat. There are two components that can be used in these systems to enhance the level of efficiency and safety in operation. They are the receiver and the accumulator. The receiver is placed in the liquid line 108 and holds a little extra refrigerant so the system has enough for high loads on hot days. The accumulator is placed in the suction line 111 and traps any the liquid refrigerant that would flow back to the compressor 105 on cool days with light loads.

A liquid receiver can be located at the end of the condenser 107 outlet to collect liquid refrigerant. The liquid receiver allows the liquid to flow into the receiver and any vapor collected in the receiver to flow back into the condenser 107 to be converted back into a liquid. The line connecting the receiver to the condenser 107 is called the condensate line and must be large enough in diameter to allow liquid to flow into the receiver and vapor to flow back into the condenser 107. The condensate line must also have a slope toward the receiver to allow liquid refrigerant to freely flow from the condenser 107 into the receiver. The outlet side of the receiver is located at the bottom where the trapped liquid can flow out of the receiver into the liquid line.

Receivers should be sized so that all of the refrigerant charge can be stored in the receiver. Some refrigeration condensing units come with receivers built into the base of the condensing unit.

The accumulator is located at the end of the evaporator 110 and allows liquid refrigerant to be collected in the bottom of the accumulator and remain there as the vapor refrigerant is returned to the compressor 105. The inlet side of the accumulator is connected to the evaporator 110 where any liquid refrigerant and vapor flow in. The outlet of the accumulator draws vapor through a U shaped tube or chamber. There is usually a small port at the bottom of the U shaped tube or chamber that allows liquid refrigerant and oil to be drawn into the suction line. Without this small port, refrigerant oil would collect in the accumulator and not return to the compressor 105. The small port does allow some liquid refrigerant to enter the suction line. However, it is such a small amount of liquid refrigerant that it boils off rapidly, so there is little danger of liquid refrigerant flowing into the compressor 105.

Accumulators are often found on heat pumps. During the changeover cycle, liquid refrigerant can flow back out of the outdoor coil. This liquid refrigerant could cause compressor 105 damage if it were not for the accumulator, which blocks its return.

The pressure-heat diagram of FIG. 8 shows the cooling process in the evaporator 110. Initially the high pressure liquid is usually subcooled 8-10° F. or more. When subcooled liquid from point A flows through the metering device 109, its pressure drops to the pressure of the evaporator 110. Approximately 20% of the liquid boils off to gas, cooling the remaining liquid-gas mixture. Its total heat (enthalpy) at point B is relatively unchanged from A. No external heat energy has been exchanged. From points B to C, the remainder of the liquid boils off, absorbing the heat flowing in from the evaporator 110 load (air, water, etc.). At point C, all of the liquid has evaporated and the refrigerant is vapor at the saturation temperature corresponding to the evaporator 110 pressure.

The subcooling increases cycle efficiency and can prevent flash gas due to pressure loss from components, pipe friction, or increase in height.

Many smaller refrigeration systems are designed to have the metering device 109 control the refrigerant flow so the evaporator 110 will heat the vapor beyond saturated conditions and ensure no liquid droplets will enter and possibly damage the compressor 105. It is assumed here for the sake of simplicity there is no pressure drop through the evaporator 110. In reality there are pressure drops which would slightly shift the evaporating and condensing processes from the constant pressure lines shown.

If the evaporator 110 does not have to superheat refrigerant vapor, it can produce more cooling capacity. On smaller systems the difference is relatively small and it is more important to protect the compressor 105. On larger systems, an increase in evaporator performance can be important. A flooded evaporator 110 absorbs heat from points B to C. It can circulate more pounds of refrigerant (more cooling capacity) per square foot of heat transfer surface.

An undersized evaporator with less heat transfer surface will not handle the same heat load at the same temperature difference as a correctly sized evaporator. The new balance point will be reached with a lower suction pressure and temperature. The load will be reduced and the discharge pressure and temperature will also be reduced. An undersized evaporator and a reduced heat load both have similar effects on the refrigerant cycle because they both are removing less heat from the refrigerant.

As the ambient temperature increases, the load on the evaporator 110 increases. When the load on the evaporator 110 increases, the pressures increase. The operating points shift up and to the right on the pressure-heat curve. As the load on the evaporator 110 decreases, the pressures decrease. The operating points on the pressure-heat curve shift down. Thus, knowledge of the ambient temperature is useful in determining whether the system 100 is operating efficiency.

FIG. 9A is a block diagram of a monitoring system 900 for monitoring the operation of the refrigerant-cycle system. In FIG. 9A, one or more condenser unit sensors 901 measure operating characteristics of the elements of the condenser unit 101, one or more evaporator unit sensors 902 measure operating characteristics of the evaporator unit 102, and one or more ambient sensors 903 measure ambient conditions. Sensor data from the condenser unit sensors 901, evaporator unit sensors 902, and ambient sensors 903 are provided to a processing system 904. The processing system 904 uses the sensor data to calculate system efficiency, identify potential performance problems, calculate energy usage, etc. In one embodiment, the processing system 904 calculates energy usage and energy costs due to inefficient operation. In one embodiment, the processing system 904 schedules filter maintenance according to elapsed time and/or filter usage. In one embodiment, the processing system 904 identifies potential performance problems (e.g., low airflow, insufficient or unbalanced load, excessive load, low ambient temperature, high ambient temperature, refrigerant undercharge, refrigerant overcharge, liquid line restriction, suction line restriction, hot gas line restriction, inefficient compressor, etc.). In one embodiment, the processing system 904 provides plots or charts of energy usage and costs. In one embodiment, the processing system 904 of the system 900 provides plots or charts of the additional energy costs due to inefficient operation of the refrigerant-cycle system. In one embodiment, a thermostat 952 is provided to the processing system 904. In one embodiment, the processing system 904 and thermostat 952 are combined.

FIG. 9B is a block diagram of the system 900 wherein operating data from the refrigerant-cycle system is provided to a remote monitoring system 950, such as, for example, a power company or monitoring center. In one embodiment, the system 900 provides operating data related to the operating efficiency of the refrigerant-cycle system to the remote monitoring system 950. In one embodiment, the remote monitoring system 950 provides operating efficiency data to an electric power company or governmental agency.

Data can be transmitted from the system 900 to a remote monitoring system 950 by using data transmission over power lines as shown in FIG. 9B and/or by using data transmission over a data network (e.g., the Internet, a wireless network, a cable modem network, a telephone network, etc.) as shown in FIG. 9C and also as shown in discussed in connection with FIGS. 9F-9H.

FIG. 9D is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system, where data regarding operation of the system is provided to a thermostat 952 and/or to a computer system 948 such as, for example, a site monitoring computer, a maintenance computer, a personal digital assistant, a personal computer, etc.

FIG. 9E is a block diagram of a monitoring system for monitoring the operation of the refrigerant-cycle system wherein an electronically-controlled metering device 960 is provided to allow control of the system in an energy-efficient matter.

FIG. 9F is a block diagram of a thermostat control and monitoring system having a data interface device 955 provided to the thermostat 952. The thermostat 952 typically communicates with an evaporator unit controller 953 using relatively low-voltage control wiring. The evaporator unit controller 953 typically provides relays and other control circuits for the air handler fan, and other systems in the evaporator unit 102. The control wiring is also provided to a condenser unit controller 954 in the condenser unit 101. The condenser unit controller 954 provides relays and other control circuits for the compressor 105, the condenser fan, etc. The data interface device 955 is provided to the low-voltage control wiring to allow the thermostat 952 to receive control signals from the remote monitoring system 950.

FIG. 9G is a block diagram of a thermostat control and monitoring system wherein a data interface device 956 is provided to the condenser unit controller 954. The data interface device 956 allows the remote monitoring system 950 to communicate with the condenser unit 101. In one embodiment, the data interface device 956 allows the remote monitoring system 950 to read sensor data from the condenser unit 101. In one embodiment, the data interface device 956 allows the remote monitoring system 950 to turn off the condenser unit 101. In one embodiment, the data interface device 956 allows the remote monitoring system 950 to switch the compressor 105 to a lower-speed mode. In one embodiment, the data interface device 956 allows the remote monitoring system 950 to switch the condenser unit 101 to a power conservation mode.

FIG. 9H is a block diagram of a thermostat control and monitoring system wherein a data interface device 957 is provided to the evaporator unit controller 953.

In one embodiment, the data interface devices 955-957 are configured as power line modems (e.g., using Broadband over Power Line (BPL), or other power line networking technology). In one embodiment, the data interface devices 955-957 are configured as wireless modems for communication using wireless transmission. In one embodiment, the data interface devices 955-957 are configured as telephone modems, cable modems, Ethernet modems, or the like, to communicate using a wired network.

In one embodiment, the system 900 provides sensor data from the condenser unit sensors 901 and/or the evaporator unit sensors 902 to the remote monitoring system 950. In one embodiment, the system 900 uses data from the condenser unit sensors 901 and/or the evaporator unit sensors 902 to compute an efficiency factor for the refrigerant-cycle system and the system 900 provides the efficiency factor to the remote monitoring system 950. In one embodiment, the system 900 provides power usage data (e.g., amount of power used) by the refrigerant-cycle system and the system 900 provides the efficiency factor to the remote monitoring system 950. In one embodiment, the system 900 provides an identification code (ID) with the data transmitted to the remote monitoring system 950 to identify the system 900.

In one embodiment, the remote monitoring system 950 is provided with data regarding a maximum expected efficiency for the refrigerant-cycle system (e.g., based on the manufacture and design characteristics of the refrigerant-cycle system) such that the remote monitoring system 950 can ascertain the relative efficiency (that is, how the refrigerant-cycle system is operating with respect to its expected operating efficiency). In one embodiment, the remote monitoring system 950 provides efficiency data to the power company or to a government agency so electric rates can be charged according to the system efficiency. In one embodiment, the homeowner (or building owner) is charged a higher electrical rate for electrical power provided to a refrigerant-cycle system that is operating at a relatively low absolute efficiency. In one embodiment, the homeowner (or building owner) is charged a higher electrical rate for electrical power provided to a refrigerant-cycle system that is operating at a relatively low relative efficiency. In one embodiment, the homeowner (or building owner) is charged an electrical rate according to a combination of the relative and absolute efficiency of the refrigerant-cycle system. In one embodiment, the data provided to the remote monitoring system 950 is used to provide notice to the homeowner (or building owner) that the refrigerant-cycle system is operating at a poor efficiency. In one embodiment, the data provided to the remote monitoring system 950 is used to provide notice to the homeowner (or building owner) that the refrigerant-cycle system is operating at a poor efficiency, and that the system must be serviced. In one embodiment, the owner is given a warning that service is needed. If the unit is not serviced (or if efficiency does not improve) after a period of time, the remote monitoring system 950 can remotely shut off the refrigerant-cycle system by sending commands to one or more of the data interface devices 955-957.

In one embodiment, the homeowner (or building owner) is charged a higher electrical rate for electrical power provided to a refrigerant-cycle system that is operating at a relatively low efficiency during a specified period of time, such as, for example, when the power system is highly loaded, during peak afternoon cooling periods, during heat waves, during rolling blackouts, etc. In one embodiment, the homeowner (or building owner) is charged a higher electrical rate (a premium rate) for electrical power provided to a refrigerant-cycle system during a specified period of time, such as, for example, when the power system is highly loaded, during peak afternoon cooling periods, during heat waves, during rolling blackouts, etc. In one embodiment, the homeowner (or building owner) can program the system 900 to receive messages from the power company indicating that premium rates are being charged. In one embodiment, the homeowner (or building owner) can program the system 900 to shut down during premium rate periods. In one embodiment, the homeowner (or building owner) can avoid paying premium rates by allowing the power company to remotely control operation of the refrigerant-cycle system during premium rate times. In one embodiment, the homeowner (or building owner) is only allowed to run the refrigerant-cycle system during premium rate periods if the system is operating above a prescribed efficiency.

In one embodiment, the system 900 monitors the amount of time that the refrigerant-cycle system has been running (e.g., the amount of runtime during the last day, week, etc.). In one embodiment, the remote monitoring system 950 can query the system 900 to obtain data regarding the operating of the refrigerant-cycle system and one or more of the data interface devices 955-957 will receive the query and send the requested data to the remote monitoring system 950. The query data may be, for example, the efficiency rating of the refrigerant-cycle system (e.g., the SEER, EER, etc.), the current operating efficiency of the refrigerant-cycle system, the runtime of the system during a specified time period, etc. The remote monitoring system 950 operator (e.g., the power company or power transmission company) can use the query data to make load balancing decisions. Thus, for example the decision regarding whether to instruct the refrigerant-cycle system to shut down or go into a low power mode can be based on the system efficiency (specified efficiency, absolute efficiency, and/or relative efficiency), the amount of time the system has been running, the home or building owner's willingness to pay premium rates during load shedding periods, etc. Thus, for example a homeowner who has a low-efficiency system that is heavily used, or who has indicated an unwillingness to pay premium rates, would have his/her refrigerant-cycle system shut off by the remote monitoring system 950 before that of a homeowner who has installed a high-efficiency system that is used relatively little, and who had indicated a willingness to pay premium rates. In one embodiment, in making the decision to shut off the system 900, the remote monitoring system 950 would take into account the efficiency of the system 900, the amount the system 900 is being used, and the owner's willingness to pay premium rates. In one embodiment, higher-efficiency systems are preferred over lower-efficiency systems (that is, higher-efficiency systems are less likely to be shut off during a power emergency), and lightly-used systems are preferred over heavily-used systems.

In one embodiment, the system 900 sends data regarding the set temperature of the thermostat 952 to the remote monitoring system 950. In one embodiment, the electricity rate charged to the homeowner (or building owner) is calculated according to a set point of the thermostat 952 such that a lower set point results in a higher rate charge per kilowatt-hour. In one embodiment, the electricity rate charged to the homeowner (or building owner) is calculated according to the set point of the thermostat 952 and the relative efficiency of the refrigerant-cycle system such that a lower set point and/or lower efficiency results in a higher rate charge per kilowatt-hour. In one embodiment, the electricity rate charged to the homeowner (or building owner) is calculated according to the set point of the thermostat 952 and the absolute efficiency of the refrigerant-cycle system such that a lower set point and/or lower efficiency results in a higher rate charge per kilowatt-hour. In one embodiment, the electricity rate charged to the homeowner (or building owner) is calculated according to the set point of the thermostat 952, the relative efficiency of the refrigerant-cycle system, and the absolute efficiency of the refrigerant-cycle system according to a formula whereby a lower set point and/or lower efficiency results in a higher rate charge per kilowatt-hour.

In one embodiment, the remote monitoring system 950 can send instructions to the system 900 to shut down if the refrigerant-cycle system is operating at a low efficiency. In one embodiment, the remote monitoring system 950 can send instructions to the system 900 to change the setting of the thermostat 952 (e.g., raise the set temperature of the thermostat 952) in response to low efficiency of the refrigerant-cycle system and/or to avoid a blackout. In one embodiment the remote monitoring system 950 can send instructions to the condenser unit 101 to switch the compressor 105 to a low-speed mode to conserve power.

In one embodiment, the remote monitoring system 950 knows the identification codes or addresses of the data interface devices 955-957 and correlates the identification codes with a database to determine whether the refrigerant-cycle system is serving a relatively high priority client such as, for example, a hospital, the home of an elderly or invalid person, etc. In such circumstances, the remote monitoring system 950 can provide relatively less cutback in cooling provided by the refrigerant-cycle system.

In one embodiment, the system 900 communicates with the remote monitoring system 950 to provide load shedding. Thus, for example, the remote monitoring system 950 (e.g., a power company) can communicate with the data interface device 956 and/or the data interface device 957 to turn off the refrigerant-cycle system. The remote monitoring system 950 can thus rotate the on and off times of air conditioners across a region to reduce the power load without implementing rolling blackouts. In one embodiment, the data interface device 956 is configured as a retrofit device that can be installed in a condenser unit to provide remote shutdown. In one embodiment, the data interface device 956 is configured as a retrofit device that can be installed in a condenser unit to remotely switch the condenser-unit to a low power (e.g., energy conservation) mode. In one embodiment, the data interface device 957 is configured as a retrofit device that can be installed in an evaporator unit to provide remote shutdown or to remotely switch the system to a lower power mode. In one embodiment, the remote monitoring system 950 sends separate shutdown and restart commands to one or more of the data interface devices 955-957. In one embodiment, the remote monitoring system 950 sends commands to the data interface devices 955-957 to shutdown for a specified period of time (e.g., 10 min, 30 min, 1 hour, etc.) after which the system automatically restarts.

In one embodiment, the system 900 communicates with the remote monitoring system 950 to control the temperature set point of the thermostat 952 to prevent blackouts or brownouts without regard to efficiency of the refrigerant-cycle system. When brownout or potential blackout conditions occur, the remote monitoring system 950 can override the homeowner's thermostat setting to cause the temperature set point on the thermostat 952 to change (e.g., increase) in order to reduce power usage. In most residential installations, low-voltage control wiring is provided between the thermostat 952 and the evaporator unit 102 and condenser unit 101. In most residential (and many industrial) applications the thermostat 952 receives electrical power via the low-voltage control wiring from a step-down transformer provided with the evaporator unit 102.

In one embodiment, the data interface device 955 is provided in connection with the power meter 949, and the data interface device 955 communicates with the thermostat 952 using wireless communications.

In a typical refrigeration or air conditioning system, the condenser unit 101 is placed outside the area being cooled and the evaporator unit 102 is placed inside the area being cooled. The nature of outside and inside depend on the particular installation. For example, in an air conditioning or HVAC system, the condenser unit 101 is typically placed outside the building, and the evaporator unit 102 is typically placed inside the building. In a refrigerator or freezer, the condenser unit 101 is placed outside the refrigerator and the evaporator unit 102 is placed inside the refrigerator. In any case, the waste heat from the condenser should be dumped outside (e.g., away from) the area being cooled.

When the system 900 is installed, the system 900 is programmed by specifying the type of refrigerant used and the characteristics of the condenser 107, the compressor 105, and the evaporator unit 102. In one embodiment, the system 900 is also programmed by specifying the size of the air handler system. In one embodiment, the system 900 is also programmed by specifying the expected (e.g., design) efficiency of the system 100.

The remote monitoring system 950 can do a better job of monitoring efficiency than published performance ratings such as the Energy Efficiency Ratio (EER) and SEER. The EER is determined by dividing the published steady state capacity by the published steady state power input at 80° F. DB/67° F. WB indoor and 95° F. DB outdoor. This is objective yet unrealistic with respect to system “real world” operating conditions. The published SEER rating of a system is determined by multiplying the steady state EER measured at conditions of 82° F. outdoor temperature, 80° F. DB/67° F. WB indoor entering air temperature by the (run time) Part Load Factor (PLF) of the system. A major factor not considered in SEER calculations is the actual part loading factor of the indoor evaporator cooling coil, which reduces the unit's listed BTUH capacity and SEER efficiency level. Many older air handlers and duct systems do not deliver the published BTUH and SEER Ratings. This is primarily due to inadequate air flow through the evaporator 110, a dirty evaporator 110, and/or dirty blower wheels. Also, improper location of supply diffusers and return air registers can result in inefficient floor level recirculation of the cold conditioned air, resulting in lack of heat loading of the evaporator 110.

By monitoring the system 100 under actual load conditions, and by measuring the relevant ambient temperature and humidity, the system 900 can calculate the actual efficiency of the system 100 in operation.

FIG. 10 shows a monitoring system 1000 for monitoring the operation of the system 100. The system 1000 shown in FIG. 10 is one example of an embodiment of the system 900 shown in FIGS. 9A-E. In the system 1000, a condenser unit sender 1002 monitors operation of the condenser unit 101 through one or more sensors, an evaporator sender unit 1003 monitors operation of the evaporator unit 102 through one or more sensors. The condenser unit sender 1002 and the evaporator sender unit 1003 communicate with the thermostat 1001 to provide data to the building owner. For purposes of explanation, and not by way of limitation, in FIG. 10 the processing system 904 and thermostat 952 from FIGS. 9A-E are shown as a single thermostat-processor. One of ordinary skill in the art will recognize that the processor functions can be separated from the thermostat.

In one embodiment, a building interior temperature sensor 1009 is provided to the thermostat 1001. In one embodiment, a building interior humidity sensor 1010 is provided to the thermostat 1001. In one embodiment, the thermostat 1001 includes a display 1008 for displaying system status and efficiency. In one embodiment, the thermostat 1001 includes a keypad 1050 and/or indicator lights (e.g., LEDs) 1051. A power sensor 1011 to sense electrical power consumed by the compressor 105 is provided to the condenser unit sender 1002. In one embodiment, a power sensor 1017 to sense electrical power consumed by the condenser fan 122 is provided to the condenser unit sender 1002. The air 125 from the evaporator 110 flows in the ductwork 1080.

In one embodiment, a temperature sensor 1012, configured to measure the temperature of the refrigerant in the suction line 111 near the compressor 105, is provided to the condenser unit sender 1002. In one embodiment, a temperature sensor 1016, configured to measure the temperature of the refrigerant in the hot gas line 106, is provided to the condenser unit sender 1002. In one embodiment, a temperature sensor 1014, configured to measure the temperature of the refrigerant in the liquid line 108 near the condenser 107, is provided to the condenser unit sender 1002.

Contaminants in the refrigerant lines 111, 106, 108, etc. can reduce the efficiency of the refrigerant-cycle system and can reduce the life of the compressor 105 or other system components. In one embodiment, one or more contaminant sensors 1034, configured to sense contaminants in the refrigerant (e.g., water, oxygen, nitrogen, air, improper oil, etc.) are provided in at least one of the refrigerant lines and provided to the condenser unit sender 1002 (or, optionally, to the evaporator unit sender 1003). In one embodiment, a contaminant sensor 1034 senses refrigerant fluid or droplets at the input to the compressor 105, which can cause damage to the compressor 105. In one embodiment, a contaminant sensor 1060 is provided in the liquid line 108 to sense bubbles in the refrigerant. Bubbles in the liquid line 108 may indicate low refrigerant levels, an undersized condenser 107, insufficient cooling of the condenser 107, etc. In one embodiment, the sensor 1034 senses water or water vapor in the refrigerant lines. In one embodiment, the sensor 1034 senses acid in the refrigerant lines. In one embodiment, the sensor 1034 senses air or other gasses (e.g., oxygen, nitrogen, carbon dioxide, chlorine, etc.).

In one embodiment, a pressure sensor 1013, configured to measure pressure in the suction line 111, is provided to the condenser unit sender 1002. In one embodiment, a pressure sensor 1015, configured to measure pressure in the liquid line 108, is provided to the condenser unit sender 1002. In one embodiment, a pressure sensor (not shown), configured to measure pressure in the hot gas line 106, is provided to the condenser unit sender 1002. In one embodiment, the pressure sensor 1013 and the pressure sensor 1015 are connected to the system 100, by attaching the pressure sensors 1013 and 1015 to the service valves 120 and 121, respectively. Attaching the pressure sensors to the service valves 120 and 121 is a convenient way to access refrigerant pressure in a retrofit installation without having to open the pressurized refrigerant system.

In one embodiment, a flow sensor 1031, configured to measure flow in the suction line 111, is provided to the condenser unit sender 1002. In one embodiment, a flow sensor 1030, configured to measure flow in the liquid line 108, is provided to the condenser unit sender 1002. In one embodiment, a flow sensor (not shown), configured to measure flow in the hot gas line 106, is provided to the condenser unit sender 1002. In one embodiment, the flow sensors are ultrasonic sensors that can be attached to the refrigerant lines without opening the pressurized refrigerant system.

In one embodiment, a temperature sensor 1028 configured to measure ambient temperature is provided to the condenser unit sender 1002. In one embodiment, a humidity sensor 1029 configured to measure ambient humidity is provided to the condenser unit sender 1002.

In one embodiment, a temperature sensor 1020, configured to measure the temperature of the refrigerant in the liquid line 108 near the evaporator 110 is provided to the evaporator sender unit 1003. In one embodiment, a temperature sensor 1021, configured to measure the temperature of the refrigerant in the suction line 111 near the evaporator 110 is provided to the evaporator sender unit 1003.

In one embodiment, a temperature sensor 1026, configured to measure the temperature of air 124 flowing into the evaporator 110 is provided to the evaporator sender unit 1003.

In one embodiment, a temperature sensor 1026, configured to measure the temperature of air 125 flowing out of the evaporator 110 is provided to the evaporator sender unit 1003. In one embodiment, an airflow sensor 1023, configured to measure the airflow of air 125 flowing out of the evaporator 110 is provided to the evaporator sender unit 1003. In one embodiment, a humidity sensor 1024, configured to measure the humidity of air 125 flowing out of the evaporator 110 is provided to the evaporator sender unit 1003. In one embodiment, a differential pressure sensor 1025, configured to measure a pressure drop across the evaporator 110, is provided to the evaporator sender unit 1003.

In one embodiment, the temperature sensors are attached to the refrigerant lines (e.g., the lines 106, 108, 111, in order to measure the temperature of the refrigerant circulating inside the lines. In one embodiment, the temperature sensors 1012 and/or 1016 are provided inside the compressor 105. In one embodiment, the temperature sensors are provided inside one or more of the refrigerant lines.

A tachometer 1033 senses rotational speed of the fan blades in the fan 123. The tachometer 1033 is provided to the evaporator unit sender 1003. A tachometer 1032 senses rotational speed of the fan blades in the condenser fan 122. The tachometer 1032 is provided to the condenser unit sender 1002.

In one embodiment, a power sensor 1027, configured to measure electrical power consumed by the fan 123 is provided to the evaporator sender unit 1003.

In one embodiment, the evaporator sender unit 1003 communicates sensor data to the condenser unit sender 1002 through wireless transmission. In one embodiment, the evaporator sender unit 1003 communicates sensor data to the condenser unit sender 1002 through existing HVAC wiring. In one embodiment, the evaporator sender unit 1003 communicates sensor data to the condenser unit sender 1002 through existing HVAC wiring by modulating sensor data onto a carrier that is transmitted using the existing HVAC wiring.

Each of the sensors shown in FIG. 10 (e.g., the sensors 1010-1034 etc.) are optional. The system 1000 can be configured with a subset of the illustrated sensors in order to reduce cost at the expense of monitoring system capability. Thus, for example, the contaminant sensors 1034 can be eliminated, but ability of the system 1000 to detect the contaminants sensed by the sensor 1034 will be compromised or lost.

The pressure sensors 1013 and 1015 measure suction and discharge pressures, respectively, at the compressor 105. The temperature sensors 1026 and 1022 measure evaporator 110 return air temperature and supply air temperature, respectively. The temperature sensors 1018 and 1019 measure input air and discharge air, respectively, at the condenser 107.

The power sensors 1011, 1017, and 1027 are configured to measure electric power. In one embodiment, one or more of the power sensors measure voltage provided to a load and power is computed by using a specified impedance for the load. In one embodiment, one or more of the power sensors measure current provided to a load and power is computed by using a specified impedance for the load. In one embodiment, one or more of the power sensors measure voltage and current provided to a load and power is computed by using a specified power factor for the load. In one embodiment, the power sensors measure voltage, current, and the phase relationship between the voltage and the current.

The temperature sensors 1012 and/or 1021 measure the temperature of the refrigerant at the suction line 111. By measuring the suction line 111 temperature, the superheat can be determined. The suction pressure has been measured by the pressure sensor 1013, so the evaporating temperature can be read from a pressure-temperature chart. The superheat is the difference between the suction line 111 temperature and the evaporating temperature.

The temperature sensors 1014 and/or 1020 measure the temperature of the refrigerant in the liquid line 108. By measuring the liquid line 108 temperature, the subcooling can be determined. The discharge pressure is measured by the pressure sensor 1015, and thus the condensing temperature can be read from the pressure-temperature chart. The subcooling is the difference between the liquid line 108 temperature and the condensing temperature.

In one embodiment, the system 1000 calculates efficiency by measuring the work (cooling) done by the refrigerant-cycle system and dividing by the power consumed by the system. In one embodiment, the system 1000 monitors the system 100 for abnormal operation. Thus, for example, in one embodiment, the system 1000 measures the refrigerant temperature drop across the condenser 107 using the temperature sensors 1016 and 1014 to be used in calculating the heat removed by the condenser 107. The system 1000 measures the refrigerant temperature drop across the evaporator 110 to be used in calculating the heat absorbed by the evaporator 110.

The monitoring system 1000 is typically used to monitor the operation of the system 100 that was originally checked out and put into proper operation condition. Mechanical problems in an air conditioning system are generally classified in two categories: air side problems and refrigeration side problems.

The primary problem that can occur in the air category is a reduction in airflow. Air handling systems do not suddenly increase in capacity, that is, increase the amount of air across the coil. On the other hand, the refrigeration system does not suddenly increase in heat transfer ability. The system 1000 uses the temperature sensors 1026 and 1022 to measure the temperature drop of the air through the evaporator 110. After measuring the return air and supply air temperatures and subtracting to get the temperature drop, the system 1000 checks to see whether the temperature difference is higher or lower than it should be.

FIG. 11 shows the temperature drop in the air through the evaporator 110 as a function of humidity. In one embodiment, the humidity sensors 1024 and/or 1010 are used to measure building humidity, and/or the humidity sensor 1029 is used to measure ambient humidity. The humidity readings are used to correct temperature readings for wet bulb temperature according to relative humidity.

In one embodiment, a comparison of the desired (or expected) temperature drop across the evaporator 110 with the measured actual temperature drop is used to help classify potential air problems from refrigerant cycle problems. If the actual temperature drop is less than the required temperature drop, then the airflow has likely been reduced. Reduced airflow can be caused by dirty air filters or evaporator 110, problems with the fan 123, and/or unusual restrictions in the duct system.

Air filters of the throwaway type are typically replaced at least twice each year, at the beginning of both the cooling and heating seasons. In one embodiment, the thermostat 1001 allows the owner to indicate when a new air filter is installed. The thermostat 1001 keeps track of the time the filter has been in use, and provides a reminder to the owner when the filter should be replaced. In one embodiment, the thermostat 1001 uses actual elapsed clock time to determine filter usage.

In one embodiment, the thermostat 1001 calculates filter usage according to the amount of time the air handler has been blowing air through the filter. Thus, for example, in moderate climates or seasons where the air handler system is not used continuously, the thermostat 1001 will wait a longer period of actual time before indicating that filter replacement is warranted. In some areas of higher use or where dust is high, the filter will generally have to be replaced relatively more often. In one embodiment, the thermostat 1001 uses a weighting factor to combine running time with idle time to determine filter usage. Thus, for example, in determining filter usage, hours when the air handler is blowing air thorough the filter are weighted relatively more heavily than hours where the air handler system is idle. In one embodiment, the owner can program the thermostat 1001 to indicate that filter replacement is needed after a specified number of hours or days (e.g., as actual days, as running days, or as a combination thereof).

In one embodiment, the thermostat 1001 is configured to receive information from an information source regarding daily atmospheric dust conditions and to use such information in calculating filter usage. Thus, in one embodiment, when calculating filter use, the thermostat 1001 weighs days of relatively high atmospheric dust relatively more heavily than days of relatively low atmospheric dust. In one embodiment, the information source for atmospheric dust information includes a data network, such as, for example, the Internet, a pager network, a local area network, etc.

In one embodiment, the thermostat 1001 collects data for calculating filter usage and passes such data to a computer monitoring system.

In commercial and industrial applications, a regular schedule of maintenance is generally used. In one embodiment, sensors are provided in connection with the air filter, as described below in connection with FIG. 15.

In one embodiment, power measured by the power sensor 1027 is used to help diagnose and detect problems with the fan 123 and/or the air handler system. If the fan 123 is drawing too much or too little current, or if the fan 123 is showing a low power factor, then possible problems with the blower and/or air handler system are indicated.

Placing furniture or carpeting over return air grilles reduces the air available for the blower to handle. Shutting off the air to unused areas will reduce the air over the evaporator 110. Covering a return air grille to reduce the noise from the centrally located furnace or air handler may reduce the objectionable noise, but it also drastically affects the operation of the system by reducing the air quantity. The collapse of the return air duct system will affect the entire duct system performance. Air leaks in the return duct will raise the return air temperature and reduce the temperature drop across the coil.

The airflow sensor 1023 can be used to measure air flow through the ducts. In one embodiment, the airflow sensor 1023 is a hot wire (or hot film) mass flow sensor. In one embodiment, the differential pressure sensor 1025 is used to measure airflow through the evaporator 110. In one embodiment, the differential pressure sensor 1025 is used to measure drop across the evaporator 110. In one embodiment, the pressure drop across the evaporator 110 is used to estimate when the evaporator 110 is restricting airflow (e.g., due to damage, dirt, hair, dust, etc.). In one embodiment, the differential pressure sensor 1025 is used to measure drop across an air filter to estimate when the filter is restricting airflow (e.g., due to age, damage, dirt, hair, dust, etc.). In one embodiment, the indicator lights 1051 are used to indicate that the filter needs to be changed. In one embodiment, the indicator lights 1051 are used to indicate that the evaporator 110 needs to be cleaned.

In one embodiment, the airflow sensor 1023 is used to measure airflow into the ductwork 1080. In one embodiment, the indicator lights 1051 are used to indicate that the airflow into the ductwork 1080 is restricted (e.g., due to dirt, furniture or carpets placed in front of vents, closed vents, dirty evaporator, dirty fan blades, etc.).

In one embodiment, a dust sensor is provided in the air stream of the evaporator 110. In one embodiment, the dust sensor includes a light source (optical and/or infrared) and a light sensor. The dust sensor measures light transmission between the source and the light sensor. The buildup of dust will cause the light to be attenuated. The sensor detects the presence of dust buildup at the evaporator 110 by measuring light attenuation between the light source and the light sensor. When the attenuation exceeds a desired value, the system 1000 indicates that cleaning of the air flow system is needed (e.g., the fan 123, the ductwork 1080, and/or the evaporator 110, etc.).

In one embodiment, the power sensor 1027 is used to measure power provided to the blower motor in the fan 123. If the fan 123 is drawing too much power or too little power, then potential airflow problems are indicated (e.g., blocked or closed vents, dirty fan blades, dirty evaporator, dirty filter, broken fan belt, slipping fan belt, etc.).

If the temperature drop across the evaporator 110 is less than desired, then the heat removal capacity of the system has been reduced. Such problems can generally be divided into two categories: refrigerant quantity, and refrigerant flow rate. If the system 100 has the correct amount of refrigerant charge and refrigerant is flowing at the desired rate (e.g., as measured by the flow sensors 1031 and/or 1030), the system 100 should work efficiently and deliver rated capacity. Problems with refrigerant quantity or flow rate typically affect the temperatures and pressures that occur in the refrigerant-cycle system when the correct amount of air is supplied through the evaporator 110. If the system is empty of refrigerant, a leak has occurred, and it must be found and repaired. If the system will not operate at all, it is probably an electrical problem that must be found and corrected.

If the system 100 will start and run but does not produce satisfactory cooling, then the amount of heat picked up in the evaporator 110 plus the amount of motor heat added and the total rejected from the condenser 107 is not the total heat quantity the unit is designed to handle. To diagnose the problem, the information listed in Table 1 is used. These results compared to normal operating results will generally identify the problem: (1) Evaporator 110 operating temperature; (2) Condensing unit condensing temperature; and/or (3) Refrigerant subcooling.

These items can be modified according to the expected energy efficiency ratio (EER) of the unit. The amount of evaporation and condensing surface designed into the unit are the main factors in the efficiency rating. A larger condensing surface results in a lower condensing temperature and a higher EER. A larger evaporating surface results in a higher suction pressure and a higher EER. The energy efficiency ratio for the conditions is calculated by dividing the net capacity of the unit in Btu/hr by the watts input.

TABLE 1

Condenser

Suction
Evaporator
Hot Gas
Liquid
Compressor

Pressure
Superheat
Pressure
Subcooling
Current

Probable Cause
(psig)
(° F.)
(psig)
(° F.)
(A)

1.
Insufficient or
Low
Low
Low
Normal
Low

unbalanced load

2.
Excessive load
High
High
High
Normal
High

3.
Low ambient
Low
High
Low
Normal
Low

temperature

4.
High ambient
High
High
High
Normal
High

temperature

5.
Refrigerant
Low
High
Low
Low
Low

undercharge

6.
Refrigerant
High
Low
High
High
High

overcharge

7.
Liquid line
Low
High
Low
High
Low

restriction

8.
Plugged capillary
Low
High
High
High
Low

tube

9.
Suction line
Low
High
Low
Normal
Low

restriction

10.
Hot gas line
High
High
High
Normal
High

restriction

11.
Inefficient
High
High
Low
Low
Low

compressor

Normal evaporator 110 operating temperatures can be found by subtracting the design coil split from the average air temperature going through the evaporator 110. The coil split will vary with the system design. Systems in the EER range of 7.0 to 8.0 typically have design splits in the range 25 to 30° F. Systems in the EER range of 8.0 to 9.0 typically have design splits in the range 20 to 25° F. Systems with 9.0+ EER ratings will have design splits in the range 15 to 20° F. The formula used for determining coil operating temperatures is:

$COT = (\frac{EAT + LAT}{2}) - split$

where COT is the coil operating temperature, EAT is the entering air temperature of the coil (e.g., as measured by the temperature sensor 1026), LAT is the leaving air temperature of the coil (e.g., as measured by the temperature sensor 1022), and split is the design split temperature.

The value (EAT+LAT)/2 is the average air temperature, which is also referred to as the mean temperature difference (MTD). It is also sometimes referred to as the coil TED or ΔT.

“Split” is the design split according to the EER rating. For example, a unit having an entering air condition of 80° F. DB and a 20° F. temperature drop across the evaporator 110 coil will have an operating coil temperature determined as follows: For an EER rating of 7.0 of 8.0:

$COT = (\frac{80 + 60}{2}) - 25 to 30 ° = 40 to 45 ° F .$

For an EER rating of 8.0 to 9.0:

$COT = (\frac{80 + 60}{2}) - 20 to 25 ° = 45 to 50 ° F .$

For an EER rating of 9.0+:

$COT = (\frac{80 + 60}{2}) - 15 to 20 ° = 50 to 55 ° F .$

Thus, the operating coil temperature changes with the EER rating of the unit.

The surface area of the condenser 107 affects the condensing temperature the system 100 must develop to operate at rated capacity. The variation in the size of the condenser 107 also affects the production cost and price of the unit. The smaller the condenser 107, the lower the efficiency (EER) rating. In the same EER ratings used for the evaporator 110, at 95° outside ambient, the 7.0 to 8.0 EER category will operate in the 25 to 30° condenser 107 split range, the 8.0 to 9.0 EER category in the 20 to 25° condenser 107 split range, and the 9.0+EER category in the to 20° condenser 107 split range.

This means that when the air entering the condenser 107 is at 95° F., the formula for finding the condensing temperature is:

RCT=EAT+split

where RCT is the refrigerant condensing temperature, EAT is the entering air temperature of the condenser 107, and split is the design temperature difference between the entering air temperature and the condensing temperatures of the hot high pressure vapor from the compressor 105.

For example, using the formula with 95° F. EAT, the split for the various EER systems would be:

For an EER rating of 7.0 to 8.0:

RCT=95°+25 to 30°=120 to 125° F.

For an EER rating of 8.0 to 9.0:

RCT=95°±20 to 25°=115 to 120° F.

For an EER rating of 9.0+:

RCT=95°±15 to 20°=110 to 115° F.

The operating head pressures vary not only with changes in outdoor temperatures but also with the different EER ratings.

The amount of subcooling produced in the condenser 107 is determined primarily by the quantity of refrigerant in the system 100. The temperature of the air entering the condenser 107 and the load in the evaporator 110 will have only a relatively small effect on the amount of subcooling produced. The amount of refrigerant in the system 100 has the predominant effect. Therefore, regardless of EER ratings, the unit should have, if properly charged, a liquid subcooled to 15 to 20° F. High ambient temperatures will produce the lower subcooled liquid because of the reduced quantity of refrigerant in the liquid state in the system. More refrigerant will stay in the vapor state to produce the higher pressure and condensing temperatures needed to eject the required amount of heat.

Table 1 shows 11 probable causes of trouble in an air conditioning system. After each probable cause is the reaction that the cause would have on the refrigeration system low side or suction pressure, the evaporator 110 superheat, the high side or discharge pressure, the amount of subcooling of the liquid leaving the condenser 107, and the amperage draw of the condensing unit. In one embodiment, an airflow sensor (not shown) is included to measure the air over the condenser 107.

Insufficient air over the evaporator 110 (as measured, for example, by using the airflow sensor 1023 and/or the differential pressure sensor 1025) is indicated by a greater than desired temperature drop in the air through the evaporator 110. An unbalanced load on the evaporator 110 will also give the opposite indication, indicating that some of the circuits of the evaporator 110 are overloaded while others are lightly loaded. In one embodiment, the temperature sensor 1022 includes multiple sensors to measure the temperature across the evaporator 110. The lightly loaded sections of the evaporator 110 allow liquid refrigerant to leave the coil and enter the suction manifold and suction line.

In TXV systems, the liquid refrigerant passing the sensing bulb of the TXV can cause the valve to close down. This reduces the operating temperature and capacity of the evaporator 110 as well as lowering the suction pressure. The evaporator 110 operating superheat can become very low because of the liquid leaving some of the sections of the evaporator 110.

With inadequate airflow, high side or discharge pressure will be low due to the reduced load on the compressor 105, reduced amount of refrigerant vapor pumped, and reduced heat load on the condenser 107. Condenser 107 liquid subcooling would be on the high side of the normal range because of the reduction in refrigerant demand by the TXV. Condensing unit amperage draw would be down due to the reduced load.

In systems using fixed metering devices, the unbalanced load would produce a lower temperature drop of the air through the evaporator 110 because the amount of refrigerant supplied by the fixed metering device would not be reduced; therefore, the system pressure (boiling point) would be approximately the same.

The evaporator 110 superheat would drop to zero with liquid refrigerant flooding into the suction line 111. Under extreme case of imbalance, liquid returning to the compressor 105 could cause damage to the compressor 105. The reduction in heat gathered in the evaporator 110 and the lowering of the refrigerant vapor to the compressor 105 will lower the load on the compressor 105. The compressor 105 discharge pressure (hot gas pressure) will be reduced.

The flow rate of the refrigerant will be only slightly reduced because of the lower head pressure. The subcooling of the refrigerant will be in the normal range. The amperage draw of the condensing unit will be slightly lower because of the reduced load on the compressor 105 and reduction in head pressure.

In the case of excessive load, the opposite effect exists. The temperature drop of the air through the coil will be less, because the unit cannot cool the air as much as it should. Air is moving through the coil at too high a velocity. There is also the possibility that the temperature of the air entering the coil is higher than the return air from the conditioned area. This could be from air leaks in the return duct system drawing hot air from unconditioned areas.

The excessive load raises the suction pressure. The refrigerant is evaporating at a rate faster than the pumping rate of the compressor 105. If the system uses a TXV, the superheat will be normal to slightly high. The valve will operate at a higher flow rate to attempt to maintain superheat settings. If the system 100 uses fixed metering devices, the superheat will be high. The fixed metering devices cannot feed enough increase in refrigerant quantity to keep the evaporator 110 fully active.

The high side or discharge pressure will be high. The compressor 105 will pump more vapor because of the increase in suction pressure. The condenser 107 must handle more heat and will develop a higher condensing temperature to eject the additional heat. A higher condensing temperature means a greater high side pressure. The quantity of liquid in the system has not changed, nor is the refrigerant flow restricted. The liquid subcooling will be in the normal range. The amperage draw of the unit will be high because of the additional load on the compressor 105.

When the temperature of the ambient air entering the condenser 107 is low, then the condenser 107 heat transfer rate is excessive, producing an excessively low discharge pressure. As a result, the suction pressure will be low because the amount of refrigerant through the metering device 109 will be reduced. This reduction will reduce the amount of liquid refrigerant supplied to the evaporator 110. The coil will produce less vapor and the suction pressure drops.

The decrease in the refrigerant flow rate into the coil reduces the amount of active coil, and a higher superheat results. In addition, the reduced system capacity will decrease the amount of heat removed from the air. There will be higher temperature and relative humidity in the conditioned area and the high side pressure will be low. This starts a reduction in system capacity. The amount of subcooling of the liquid will be in the normal range. The quantity of liquid in the condenser 107 will be higher, but the heat transfer rate of the evaporator 110 is less. The amperage draw of the condensing unit will be less because the compressor 105 is doing less work.

The amount of drop in the condenser 107 ambient air temperature that the air conditioning system will tolerate depends on the type of pressure reducing device in the system. Systems using fixed metering devices will have a gradual reduction in capacity as the outside ambient drops from 95° F. This gradual reduction occurs down to 65° F. Below this temperature the capacity loss is drastic, and some means of maintaining head pressure must be employed to prevent the evaporator 110 temperature from dropping below freezing. Some systems control air through the condenser 107 via dampers in the airstream or a variable speed condenser 107 fan.

Systems that use TXV will maintain higher capacity down to an ambient temperature of 47° F. Below this temperature, controls must be used. The control of airflow through the condenser 107 using dampers or the condenser 107 fan speed control can also be used. In larger TXV systems, liquid quantity in the condenser 107 is used to control head pressure.

The higher the temperature of the air entering the condenser 107, the higher the condensing temperature of the refrigerant vapor to eject the heat in the vapor. The higher the condensing temperature, the higher the head pressure. The suction pressure will be high for two reasons: (1) the pumping efficiency of the compressor 105 will be less; and (2) the higher temperature of the liquid will increase the amount of flash gas in the metering device 109, further reducing the system efficiency.

The amount of superheat produced in the coil will be different in a TXV system and a fixed metering device system. In the TXV system the valve will maintain superheat close to the limits of its adjustment range even though the actual temperatures involved will be higher. In a fixed metering device system, the amount of superheat produced in the coil is the reverse of the temperature of the air through the condenser 107. The flow rate through the fixed metering devices are directly affected by the head pressure. The higher the air temperature, the higher the head pressure and the higher the flow rate. As a result of the higher flow rate, the subcooling is lower.

Table 2 shows the superheat that will be developed in a properly charged air conditioning system using fixed metering devices. The head pressure will be high at the higher ambient temperatures because of the higher condensing temperatures required. The condenser 107 liquid subcooling will be in the lower portion of the normal range. The amount of liquid refrigerant in the condenser 107 will be reduced slightly because more will stay in the vapor state to produce the higher pressure and condensing temperature. The amperage draw of the condensing unit will be high.

TABLE 2

Air Temperature Entering

Condenser 107 (° F.)
Superheat (° F.)

65
30

75
25

80
20

85
18

90
15

95
10

105 & above
5

A shortage of refrigerant in the system means less liquid refrigerant in the evaporator 110 to pick up heat, and lower suction pressure. The smaller quantity of liquid supplied to the evaporator 110 means less active surface in the coil for vaporizing the liquid refrigerant, and more surface to raise vapor temperature. The superheat will be high. There will be less vapor for the compressor 105 to handle and less heat for the condenser 107 to reject, lower high side pressure, and lower condensing temperature. The compressor 105 in an air conditioning system is cooled primarily by the cool returning suction gas. Compressors 105 that are low on charge can have a much higher operating temperature.

The amount of subcooling will be below normal to none, depending on the amount of undercharge. The system operation is usually not affected very seriously until the subcooling is zero and hot gas starts to leave the condenser 107, together with the liquid refrigerant. The amperage draw of the condensing unit will be slightly less than normal.

An overcharge of refrigerant will affect the system 100 in different ways, depending on the pressure reducing device used in the system 100 and the amount of overcharge.

In systems using a TXV, the valve will attempt to control the refrigerant flow in the coil to maintain the superheat setting of the valve. However, the extra refrigerant will back up into the condenser 107, occupying some of the heat transfer area that would otherwise be available for condensing. As a result, the discharge pressure will be slightly higher than normal, the liquid subcooling will be high, and the unit amperage draw will be high. The suction pressure and evaporator 110 superheat will be normal. Excessive overcharging will cause even higher head pressure, and hunting of the TXV.

For TXV systems with excessive overcharge the suction pressure will typically be high. Not only does the reduction in compressor 105 capacity (due to higher head pressure) raise the suction pressure, but the higher pressure will cause the TXV valve to overfeed on its opening stroke. This will cause a wider range of hunting of the valve. The evaporator 110 superheat will be very erratic from the low normal range to liquid out of the coil. The high side or discharge pressure will be extremely high. Subcooling of the liquid will also be high because of the excessive liquid in the condenser 107. The condensing unit amperage draw will be higher because of the extreme load on the compressor 105 motor.

The amount of refrigerant in the fixed metering system has a direct effect on system performance. An overcharge has a greater effect than an undercharge, but both affect system performance, efficiency (EER), and operating cost.

FIGS. 12 through 14 show how the performance of a typical capillary tube air conditioning system is affected by an incorrect amount of refrigerant charge. In FIG. 12, at 100% of correct charge (55 oz), the unit develops a net capacity of 26,200 Btu/hr. When the amount of charge is varied 5% in either direction, the capacity drops as the charge is varied. Removing 5% (3 oz) of refrigerant reduces the net capacity to 25,000 Btu/hr. Another 5% (2.5 oz) reduces the capacity to 22,000 Btu/hr. From there on the reduction in capacity became very drastic: 85% (8 oz), 18,000 Btu/hr; 80% (11 oz), 13,000 Btu/hr; and 75% (14 oz), 8000 Btu/hr.

Overcharge has a similar effect but at a greater reduction rate. The addition of 3 oz of refrigerant (5%) reduces the net capacity to 24,600 Btu/hr; 6 oz added (10%) reduces the capacity to 19,000 Btu/hr; and 8 oz added (15%) drops the capacity to 11,000 Btu/hr. This shows that overcharging of a unit has a greater effect per ounce of refrigerant than does undercharging.

FIG. 13 is a chart showing the amount of electrical energy the unit demands because of pressure created by the amount of refrigerant in the system as the refrigerant charge is varied. At 100% of charge (55 oz) the unit uses 32 kW. As the charge is reduced, the wattage demand also drops, to 29.6 kW at 95% (3 oz), to 27.6 kW at 90% (6.5 oz), to 25.7 kW at 85% (8 oz), to 25 kW at 80% (11 oz), and to 22.4 kW at 75% (14 oz short of correct charge). When the unit is overcharged, the power consumed also increases. At 3 oz (5% overcharge) the power consumed is 34.2 kW, at 6 oz (10% overcharge) 39.5 kW, and at 8 oz (15% overcharge), 48 kW.

FIG. 14 shows the efficiency of the unit (EER rating) based on the Btu/hr capacity of the system 100 versus the power consumed by the condensing unit. At correct charge (55 oz) the efficiency (EER rating) of the unit is 8.49. As the refrigerant is reduced, the EER rating drops to 8.22 at 9% of charge, to 7.97 at 90%, to 7.03 at 85%, to 5.2 at 80%, and to 3.57 at 75% of full refrigerant charge. When refrigerant is added, at 5% (3 oz) the EER rating drops to 7.19. At 10% (6 oz) the EER is 4.8, and at 15% overcharge (8 oz) the EER is 2.29.

The effect of overcharge produces a high suction pressure because the refrigerant flow to the evaporator 110 increases. Suction superheat decreases because of the additional quantity to the evaporator 110. At approximately 8 to 10% of overcharge, the suction superheat becomes zero and liquid refrigerant will leave the evaporator 110. This causes flooding of the compressor 105 and greatly increases the chance of compressor 105 failure. The high side or discharge pressure is high because of the extra refrigerant in the condenser 107. Liquid subcooling is also high for the same reason. The power draw increases due to the greater amount of vapor pumped as well as the higher compressor 105 discharge pressure.

Restrictions in the liquid line 108 reduce the amount of refrigerant to the metering device 109. Both TXV valve systems and fixed metering device systems will then operate with reduced refrigerant flow rate to the evaporator 110. The following observations can be made of liquid line 108 restrictions. First, the suction pressure will be low because of the reduced amount of refrigerant to the evaporator 110. The suction superheat will be high because of the reduced active portion of the coil, allowing more coil surface for increasing the vapor temperature as well as reducing the refrigerant boiling point. The high side or discharge pressure will be low because of the reduced load on the compressor 105. Liquid subcooling will be high. The liquid refrigerant will accumulate in the condenser 107. It cannot flow out at the proper rate because of the restriction. As a result, the liquid will cool more than desired. Finally, the amperage draw of the condensing unit will be low.

Either a plugged fixed metering device or plugged feeder tube between the TXV valve distributor and the coil will cause part of the coil to be inactive. The system 100 will then be operating with an undersized coil, resulting in low suction pressure because the coil capacity has been reduced. The suction superheat will be high in the fixed metering device systems. The reduced amount of vapor produced in the coil and resultant reduction in suction pressure will reduce compressor 105 capacity, head pressure, and the flow rate of the remaining active capillary tubes. The high side or discharge pressure will be low.

Liquid subcooling will be high; the liquid refrigerant will accumulate in the condenser 107. The unit amperage draw will be low.

In TXV systems, a plugged feeder tube reduces the capacity of the coil. The coil cannot provide enough vapor to satisfy the pumping capacity of the compressor 105 and the suction pressure balances out at a low pressure. The superheat, however, will be in the normal range because the valve will adjust to the lower operating conditions and maintain the setting superheat range. The high side or discharge pressure will be low because of the reduced load on the compressor 105 and the condenser 107.

Low suction and discharge pressures indicate a refrigerant shortage. The liquid subcooling is normal to slightly above normal. This indicates a surplus of refrigerant in the condenser 107. Most of the refrigerant is in the coil, where the evaporation rate is low due to the higher operating pressure in the coil. The amperage draw of the condensing unit would be low because of the light load on the compressor 105.

If the hot gas line 106 is restricted, then the high side or compressor 105 discharge pressure will be high if measured at the compressor 105 outlet or low if measured at the condenser 107 outlet or liquid line 108. In either case, the compressor 105 current draw will be high. The suction pressure is high due to reduced pumping capacity of the compressor 105. The evaporator 110 superheat is high because the suction pressure is high. The high side pressure is high when measured at the compressor 105 discharge or low when measured at the liquid line 108. Liquid subcooling is in the high end of the normal range. Even with all of this, the compressor 105 amperage draw is above normal. All symptoms point to an extreme restriction in the hot gas line 106. This problem is easily found when the discharge pressure is measured at the compressor 105 discharge.

When the measuring point is the liquid line 108 at the condenser 107 outlet, the facts are easily misinterpreted. High suction pressure and low discharge pressure will usually be interpreted as an inefficient compressor 105. The amperage draw of the compressor 105 must be measured. The high amperage draw indicates that the compressor 105 is operating against a high discharge pressure. A restriction apparently exists between the outlet of the compressor 105 and the pressure measuring point.

When the compressor 105 will not pump the required amount of refrigerant vapor (e.g., because it is undersized, or is not working at rated capacity), the suction pressure will balance out higher than normal. The evaporator 110 superheat will be high. The high side or discharge pressure will be extremely low. Liquid subcooling will be low because not much heat will be in the condenser 107. The condensing temperature will therefore be close to the entering air temperature. The amperage draw of the condensing unit will be extremely low, indicating that the compressor 105 is doing very little work.

The following formulas can be used by the systems 900, 1000 to calculate various operating parameters of the system 100 using data from one or more of the sensors shown in FIG. 10.

Power is:

Watts=volts×amps×PF

where PF is the power factor.

Heat is:

Btu=W×ΔT

Specific heat is:

Btu=W×c×ΔT

Sensible heat added or removed from a substance is:

Q=W×SH×ΔT

Latent heat added or removed from a substance is:

Q=W×LH

The refrigeration effect is:

$W = \frac{200}{NRE}$

where W is weight of refrigerant circulated per minute (e.g., lb/min), 200 Btu/min is the equivalent of 1 ton of refrigeration, and NRE is the net refrigerating effect (Btu/lb of refrigerant).

The coefficient of performance (COP) is:

$COP = \frac{refrigerating_effect}{heat_of_compression}$

System capacity is:

Q_t=4.45×CFM×Δh

where Q_tis the total (sensible and latent) cooling being done, CFM is the airflow across the evaporator 110, and Δh is the change of enthalpy of the air across the coil.

Condensing temperature is:

RCT=EAT+split

where RCT is the refrigerant condensing temperature, EAT is the temperature of the air entering the condenser 107, and split is the design temperature difference between the entering air temperature and the condensing temperatures of the hot high-pressure vapor from the compressor 105.

Net cooling capacity is:

HC=HT−HM

where HT is the heat transfer (gross capacity), HM is the motor heat, and HC is the net cooling capacity.

Airflow rate of a system can be expressed as:

Q=Q_s(108×TD)

where Q is the flow rate in CFM, Q_sis the sensible-heat load in Btu/hr, and TD is the dry bulb temperature difference in ° F.

In a fan, airflow (CFM) is approximately related to rotation (rpm) as follows:

$\frac{{CFM}_{2}}{{CFM}_{1}} = \frac{{rpm}_{2}}{{rpm}_{1}}$

In a fan, pressure is approximately related to rotation as follows:

$\frac{{SP}_{2}}{{SP}_{1}} = {(\frac{{rpm}_{2}}{{rpm}_{1}})}^{2}$

In a fan, work is approximately related to rotation as follows:

$\frac{{Bhp}_{2}}{{Bhp}_{1}} = {(\frac{{rpm}_{2}}{{rpm}_{1}})}^{3}$

In one embodiment, the tachometer 1033 is provided to measure the rotational velocity of the fan 123. In one embodiment, the tachometer 1032 is provided to measure the rotational velocity of the fan 122. In one embodiment, the system 1000 uses one or more of the above fan equations to calculate desired fan rotation rates. In one embodiment, the system 1000 controls the speed of the fan 123 and/or the fan 122 to increase system efficiency.

The quantity of air used for cooling based on the sensible cooling is approximately:

CFM=H_s(TD×1.08)

The sensible heat removed is:

Q
_s=1.08×CFM×DBT difference

The latent heat removed is:

Q_L=0.68×CFM×gr moisture difference

The total heat removed is:

Q_t=Q_s+Q_L
or
Q_t=4.5×CFM×total heat difference

The rate of heat transfer is:

Q=U×A×TD

where Q is the heat transfer (Btuh), U is the overall heat transfer coefficient (Btuh/ft²/° F.), A is the area (ft²), TD is the temperature difference between inside and outside design temperature and the refrigerated space design temperature.

The keypad 1050 is used to provide control inputs to the efficiency monitoring system. The display 1008 provides feedback to the user, temperature set point display. In one embodiment, the power use and/or power cost can be displayed on the display 1008. In one embodiment, the system 1000 receives rate information from the power company to use in calculating power costs. In one embodiment, the absolute efficiency of the refrigerant-cycle system can be shown on the display 1008. In one embodiment, the relative efficiency of the refrigerant-cycle system can be shown on the display 1008. In one embodiment, the data from various sensors in the system 1000 can be shown on the display 1008. In one embodiment, diagnostic messages (e.g., change the filter, add refrigerant, etc.) are shown on the display 1008. In one embodiment, messages from the power company are shown on the display 1008. In one embodiment, warning messages from the power company are shown on the display 1008. In one embodiment, the thermostat 1001 communicates with the power company (or other remote device) using power line communication methods such as, for example, BPL.

When the system 1000 is configured, the installer programs in the fixed system parameters needed for calculation of efficiency and/or other quantities derived from the sensor data. Typical fixed programmed parameters include the type of refrigerant, the compressor specifications, the condenser specifications, the evaporator specifications, the duct specifications, the fan specifications, the system SEER, and/or other system parameters. Typical fixed programmed parameters can also include equipment model and/or serial numbers, manufacturer data, engineering data, etc.

In one embodiment, the system 1000 is configured by bringing the refrigerant-cycle system up to design specifications, and then running the system 1000 in a calibration mode wherein the system 1000 takes sensor readings to measure normal baseline parameters for the refrigerant-cycle system. Using the measured baseline data, the system 1000 can calculate various system parameters (e.g., split temperatures, etc.).

In one embodiment, the system 1000 is first run in a calibration mode to measure baseline data, and then run in a normal monitoring mode wherein it compares operation of the refrigerant-cycle system with the baseline data. The system 1000 then gives alerts to potential problems when the operating parameters vary too much from the baseline data.

In one embodiment, the system 1000 is configured by using a combination of programmed parameters (e.g., refrigerant type, temperature splits, etc.) and baseline data obtained by operating the refrigerant-cycle system.

FIG. 15 shows a differential-pressure sensor 1502 used to monitor an air filter 1501 in an air-handler system. As the air filter 1501 becomes clogged, the differential pressure across the air filter 1501 will rise. This increase in differential pressure is measured by the differential pressure sensor 1502. The differential pressure measured by the differential pressure sensor 1502 is used to assess the state of the air filter 1501. When the differential pressure is too high, then replacement of the air filter 1501 is indicated.

FIG. 16 shows the differential-pressure sensor 1502 from FIG. 15 provided to a wireless communication unit to allow the data from the differential pressure sensor 1502 to be provided to other aspects of the monitoring system, such as, for example, the condenser unit sender 1002 or the thermostat 1001.

FIG. 17 shows the system of FIG. 16 implemented using a filter frame 1701 to facilitate retrofitting of existing air handler systems. The frame 1701 includes the sensor 1502 and a sender 1601. The frame 1701 is configured to fit into a standard filter frame. The frame 1701 is configured to hold a standard filter 1501. In one embodiment, the frame 1701 evaluates the cleanliness of the filter 1501 by measuring a differential pressure between the filter input and output air. In one embodiment, the frame 1701 evaluates the cleanliness of the filter 1501 by providing a source of light on one side of the filter, a light sensor on the other side of the filter, and by measuring the light transmission through the filter. In one embodiment, the frame 1701 is calibrated to a baseline light transmission level. In one embodiment, the frame 1701 signals that the filter is dirty when the light transmission falls below a fixed threshold level. In one embodiment, the frame 1701 calibrates a baseline light transmission level each time a clean, filter is installed. In one embodiment, the frame 1701 signals that the filter is dirty when the light transmission falls below a percentage of the baseline level.

Although various embodiments have been described above, other embodiments will be within the skill of one of ordinary skill in the art. Thus, for example, although described primarily in terms of an air-conditioning system, one of ordinary skill in the art will recognize that all or part of the system 1000 can be applied to other refrigerant-cycle systems, such as commercial HVAC systems, refrigerator systems, freezers, water chillers, etc. Thus, the invention is limited only by the claims that follow.

Claims

1. A method of monitoring operation of a refrigerant-cycle system, the method comprising: measuring operating characteristics of the refrigerant-cycle system using a plurality of sensors, the refrigerant-cycle system including a condenser unit and an evaporator unit, the condenser unit including a condenser and a compressor, and the evaporator unit including an evaporator and a fan;using a processing system, receiving the measurements from the plurality of sensors and outputting data regarding operation of the refrigerant-cycle system to a remote monitoring system;calculating an efficiency of the refrigerant-cycle system based on the data;determining an expected efficiency of the refrigerant-cycle system; andbased on a comparison of the calculated efficiency of the refrigerant-cycle system with the expected efficiency of the refrigerant-cycle system, selectively performing at least one of: notifying an owner of the refrigerant-cycle system that the calculated efficiency of the refrigerant-cycle system is low,notifying the owner of the refrigerant-cycle system to seek service for the refrigerant-cycle system, andadjusting operation of the refrigerant-cycle system.
2. The method of claim 1 wherein measuring the operating characteristics of the refrigerant-cycle system includes measuring an electrical quantity indicative of power consumption of the refrigerant-cycle system using an electrical sensor.
3. The method of claim 2 further comprising calculating an amount of work done by the refrigerant-cycle system, wherein the calculated efficiency of the refrigerant-cycle system is calculated based on the amount of work done by the refrigerant-cycle system and the power consumption of the refrigerant-cycle system.
4. The method of claim 1 wherein the expected efficiency of the refrigerant-cycle system is determined based on an identification code of the refrigerant-cycle system.
5. The method of claim 1 wherein: the expected efficiency of the refrigerant-cycle system is determined based on an identification code of the refrigerant-cycle system; andthe method further includes determining a relative efficiency of the refrigerant-cycle system based on the expected efficiency of the refrigerant-cycle system and the calculated efficiency of the refrigerant-cycle system.
6. The method of claim 5 further comprising notifying an owner of the refrigerant-cycle system that the calculated efficiency of the refrigerant-cycle system is low in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value.
7. The method of claim 5 further comprising notifying an owner of the refrigerant-cycle system to seek service for the refrigerant-cycle system in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value.
8. The method of claim 5 further comprising selectively adjusting operation of the refrigerant-cycle system in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value for at least a predetermined period.
9. The method of claim 5 further comprising transmitting an instruction to a thermostat to adjust a setpoint temperature in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value for a predetermined period, wherein the thermostat controls operation of the condenser unit and the evaporator unit based on the setpoint temperature.
10. The method of claim 1 further comprising displaying the calculated efficiency of the refrigerant-cycle system on a display.
11. The method of claim 1 further comprising providing at least one of charts and plots of data related to the calculated efficiency of the refrigerant-cycle system.
12. A monitoring system for monitoring operation of a refrigerant-cycle system, the monitoring system comprising: a plurality of sensors measuring operating characteristics of the refrigerant-cycle system, the refrigerant-cycle system including a condenser unit and an evaporator unit, the condenser unit including a condenser and a compressor, and the evaporator unit including an evaporator and a fan;a processing system that (i) receives the measurements from the plurality of sensors, (ii) outputs data regarding operation of the refrigerant-cycle system, and (iii) calculates an efficiency of the refrigerant-cycle system based on the data; anda remote monitoring system that: determines an expected efficiency of the refrigerant-cycle system based on the data output by the processing system; andbased on a comparison of the calculated efficiency of the refrigerant-cycle system with the expected efficiency of the refrigerant-cycle system, selectively performs at least one of: notifying an owner of the refrigerant-cycle that the calculated efficiency of the refrigerant-cycle is low,notifying the owner of the refrigerant-cycle system to seek service for the refrigerant-cycle system, andadjusting operation of the refrigerant-cycle system.
13. The monitoring system of claim 12 wherein the plurality of sensors include an electrical sensor measuring an electrical quantity indicative of power consumption of the refrigerant-cycle system.
14. The monitoring system of claim 13 wherein the processing system: calculates an amount of work done by the refrigerant-cycle system; andcalculates the calculated efficiency of the refrigerant-cycle system based on the amount of work done by the refrigerant-cycle system and the power consumption of the refrigerant-cycle system.
15. The monitoring system of claim 12 wherein the remote monitoring system determines the expected efficiency of the refrigerant-cycle system based on an identification code of the refrigerant-cycle system.
16. The monitoring system of claim 12, wherein the remote monitoring system: determines the expected efficiency of the refrigerant-cycle system based on an identification code of the refrigerant-cycle system; anddetermines a relative efficiency of the refrigerant-cycle system based on the expected efficiency of the refrigerant-cycle system and the calculated efficiency of the refrigerant-cycle system.
17. The monitoring system of claim 16 wherein the remote monitoring system notifies an owner of the refrigerant-cycle system that the calculated efficiency of the refrigerant-cycle system is low in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value.
18. The monitoring system of claim 16 wherein the remote monitoring system notifies an owner of the refrigerant-cycle system to seek service for the refrigerant-cycle system in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value.
19. The monitoring system of claim 16 wherein the remote monitoring system selectively adjusts operation of the refrigerant-cycle system in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value for at least a predetermined period.
20. The monitoring system of claim 16 wherein: the remote monitoring system transmits an instruction to a thermostat to adjust a setpoint temperature in response to the relative efficiency of the refrigerant-cycle system being less than a predetermined value for a predetermined period, andthe thermostat controls operation of the condenser unit and the evaporator unit based on the setpoint temperature.
21. The monitoring system of claim 12 wherein the processing system displays the calculated efficiency of the refrigerant-cycle system on a display.
22. The monitoring system of claim 12 wherein the processing system provides at least one of charts and plots of data related to the calculated efficiency of the refrigerant-cycle system.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. Ser. No. 13/269,188, filed Oct. 7, 2011, which is a continuation of U.S. Ser. No. 11/779,203 filed Jul. 17, 2007, now U.S. Pat. No. 8,034,170, which is a continuation of U.S. Ser. No. 11/130,569, filed May 17, 2005, now U.S. Pat. No. 7,244,294, which is a continuation of U.S. Ser. No. 10/916,222, filed Aug. 11, 2004, now U.S. Pat. No. 7,275,377, the entire contents of which are hereby incorporated by reference.

US Referenced Citations (1324)

Number	Name	Date	Kind
2054542	Hoelle	Sep 1936	A
2296822	Wolfert	Sep 1942	A
2631050	Haeberlein	Mar 1953	A
2804839	Hallinan	Sep 1957	A
2962702	Derr et al.	Nov 1960	A
2978879	Heidorn	Apr 1961	A
3027865	Kautz et al.	Apr 1962	A
3047696	Heidorn	Jul 1962	A
3082951	Kayan	Mar 1963	A
3107843	Finn	Oct 1963	A
3170304	Hale	Feb 1965	A
3232519	Long	Feb 1966	A
3278111	Parker	Oct 1966	A
3327197	Marquis	Jun 1967	A
3339164	Landis et al.	Aug 1967	A
3400374	Schumann	Sep 1968	A
3513662	Golber	May 1970	A
3581281	Martin et al.	May 1971	A
3585451	Day, III	Jun 1971	A
3653783	Sauder	Apr 1972	A
3660718	Pinckaers	May 1972	A
3665339	Liu	May 1972	A
3665399	Zehr et al.	May 1972	A
3697953	Schoenwitz	Oct 1972	A
3707851	McAshan, Jr.	Jan 1973	A
3729949	Talbot	May 1973	A
3735377	Kaufman	May 1973	A
3742302	Neill	Jun 1973	A
3742303	Dageford	Jun 1973	A
3767328	Ladusaw	Oct 1973	A
3777240	Neill	Dec 1973	A
3783681	Hirt et al.	Jan 1974	A
3820074	Toman	Jun 1974	A
3882305	Johnstone	May 1975	A
3924972	Szymaszek	Dec 1975	A
3927712	Nakayama	Dec 1975	A
3935519	Pfarrer et al.	Jan 1976	A
3950962	Odashima	Apr 1976	A
3960011	Renz et al.	Jun 1976	A
3978382	Pfarrer et al.	Aug 1976	A
3998068	Chirnside	Dec 1976	A
4006460	Hewitt et al.	Feb 1977	A
4014182	Granryd	Mar 1977	A
4018584	Mullen	Apr 1977	A
4019172	Srodes	Apr 1977	A
4024725	Uchida et al.	May 1977	A
4027289	Toman	May 1977	A
4034570	Anderson et al.	Jul 1977	A
4038061	Anderson et al.	Jul 1977	A
4045973	Anderson et al.	Sep 1977	A
4046532	Nelson	Sep 1977	A
RE29450	Goldsby et al.	Oct 1977	E
4060716	Pekrul et al.	Nov 1977	A
4066869	Apaloo et al.	Jan 1978	A
4090248	Swanson et al.	May 1978	A
4102150	Kountz	Jul 1978	A
4102394	Botts	Jul 1978	A
4104888	Reedy et al.	Aug 1978	A
4105063	Bergt	Aug 1978	A
4112703	Kountz	Sep 1978	A
4132086	Kountz	Jan 1979	A
4136730	Kinsey	Jan 1979	A
4137057	Piet et al.	Jan 1979	A
4137725	Martin	Feb 1979	A
4142375	Abe et al.	Mar 1979	A
4143707	Lewis et al.	Mar 1979	A
4146085	Wills	Mar 1979	A
RE29966	Nussbaum	Apr 1979	E
4151725	Kountz et al.	May 1979	A
4153003	Willis	May 1979	A
4156350	Elliott et al.	May 1979	A
4161106	Savage et al.	Jul 1979	A
4165619	Girard	Aug 1979	A
4171622	Yamaguchi et al.	Oct 1979	A
4173871	Brooks	Nov 1979	A
RE30242	del Toro et al.	Apr 1980	E
4197717	Schumacher	Apr 1980	A
4205381	Games et al.	May 1980	A
4209994	Mueller et al.	Jul 1980	A
4211089	Mueller et al.	Jul 1980	A
4217761	Cornaire et al.	Aug 1980	A
4220010	Mueller et al.	Sep 1980	A
4227862	Andrew et al.	Oct 1980	A
4232530	Mueller	Nov 1980	A
4233818	Lastinger	Nov 1980	A
4236379	Mueller	Dec 1980	A
4244182	Behr	Jan 1981	A
4246763	Mueller et al.	Jan 1981	A
4248051	Darcy et al.	Feb 1981	A
4251988	Allard et al.	Feb 1981	A
4257795	Shaw	Mar 1981	A
4259847	Pearse, Jr.	Apr 1981	A
4267702	Houk	May 1981	A
4270174	Karlin et al.	May 1981	A
4271898	Freeman	Jun 1981	A
4281358	Plouffe et al.	Jul 1981	A
4284849	Anderson et al.	Aug 1981	A
4286438	Clarke	Sep 1981	A
4290480	Sulkowski	Sep 1981	A
4296727	Bryan	Oct 1981	A
4301660	Mueller et al.	Nov 1981	A
4306293	Marathe	Dec 1981	A
4307775	Saunders et al.	Dec 1981	A
4308725	Chiyoda	Jan 1982	A
4311188	Kojima et al.	Jan 1982	A
4319461	Shaw	Mar 1982	A
4325223	Cantley	Apr 1982	A
4328678	Kono et al.	May 1982	A
4328680	Stamp, Jr. et al.	May 1982	A
4333316	Stamp, Jr. et al.	Jun 1982	A
4333317	Sawyer	Jun 1982	A
4336001	Andrew et al.	Jun 1982	A
4338790	Saunders et al.	Jul 1982	A
4338791	Stamp, Jr. et al.	Jul 1982	A
4345162	Hammer et al.	Aug 1982	A
4346755	Alley et al.	Aug 1982	A
4350021	Lundstrom	Sep 1982	A
4350023	Kuwabara et al.	Sep 1982	A
4351163	Johannsen	Sep 1982	A
4356703	Vogel	Nov 1982	A
4361273	Levine et al.	Nov 1982	A
4365983	Abraham et al.	Dec 1982	A
4370098	McClain et al.	Jan 1983	A
4372119	Gillbrand et al.	Feb 1983	A
4376926	Senor	Mar 1983	A
4381549	Stamp, Jr. et al.	Apr 1983	A
4382367	Roberts	May 1983	A
4384462	Overman et al.	May 1983	A
4387368	Day, III et al.	Jun 1983	A
4387578	Paddock	Jun 1983	A
4390058	Otake et al.	Jun 1983	A
4390321	Langlois et al.	Jun 1983	A
4390922	Pelliccia	Jun 1983	A
4395886	Mayer	Aug 1983	A
4395887	Sweetman	Aug 1983	A
4399548	Castleberry	Aug 1983	A
4402054	Osborne et al.	Aug 1983	A
4406133	Saunders et al.	Sep 1983	A
4407138	Mueller	Oct 1983	A
4408660	Sutoh et al.	Oct 1983	A
4412788	Shaw et al.	Nov 1983	A
4415896	Allgood	Nov 1983	A
4418388	Allgor et al.	Nov 1983	A
4420947	Yoshino	Dec 1983	A
4425010	Bryant et al.	Jan 1984	A
4429578	Darrel et al.	Feb 1984	A
4432232	Brantley et al.	Feb 1984	A
4434390	Elms	Feb 1984	A
4441329	Dawley	Apr 1984	A
4448038	Barbier	May 1984	A
4449375	Briccetti	May 1984	A
4451929	Yoshida	May 1984	A
4460123	Beverly	Jul 1984	A
4463571	Wiggs	Aug 1984	A
4463574	Spethmann et al.	Aug 1984	A
4463576	Burnett et al.	Aug 1984	A
4465229	Kompelien	Aug 1984	A
4467230	Rovinsky	Aug 1984	A
4467385	Bandoli et al.	Aug 1984	A
4467613	Behr et al.	Aug 1984	A
4470092	Lombardi	Sep 1984	A
4470266	Briccetti et al.	Sep 1984	A
4474024	Eplett et al.	Oct 1984	A
4479389	Anderson, III et al.	Oct 1984	A
4489551	Watanabe et al.	Dec 1984	A
4490986	Paddock	Jan 1985	A
4494383	Nagatomo et al.	Jan 1985	A
4495779	Tanaka et al.	Jan 1985	A
4496296	Arai et al.	Jan 1985	A
4497031	Froehling et al.	Jan 1985	A
4498310	Imanishi et al.	Feb 1985	A
4499739	Matsuoka et al.	Feb 1985	A
4502084	Hannett	Feb 1985	A
4502833	Hibino et al.	Mar 1985	A
4502842	Currier et al.	Mar 1985	A
4502843	Martin	Mar 1985	A
4505125	Baglione	Mar 1985	A
4506518	Yoshikawa et al.	Mar 1985	A
4507934	Tanaka et al.	Apr 1985	A
4510547	Rudich, Jr.	Apr 1985	A
4510576	MacArthur et al.	Apr 1985	A
4512161	Logan et al.	Apr 1985	A
4516407	Watabe	May 1985	A
4517468	Kemper et al.	May 1985	A
4520674	Canada et al.	Jun 1985	A
4523435	Lord	Jun 1985	A
4523436	Schedel et al.	Jun 1985	A
4527247	Kaiser et al.	Jul 1985	A
4527399	Lord	Jul 1985	A
4535607	Mount	Aug 1985	A
4538420	Nelson	Sep 1985	A
4538422	Mount et al.	Sep 1985	A
4539820	Zinsmeyer	Sep 1985	A
4540040	Fukumoto et al.	Sep 1985	A
4545210	Lord	Oct 1985	A
4545214	Kinoshita	Oct 1985	A
4548549	Murphy et al.	Oct 1985	A
4549403	Lord et al.	Oct 1985	A
4549404	Lord	Oct 1985	A
4553400	Branz	Nov 1985	A
4555057	Foster	Nov 1985	A
4555910	Sturges	Dec 1985	A
4557317	Harmon, Jr.	Dec 1985	A
4558181	Blanchard et al.	Dec 1985	A
4561260	Nishi et al.	Dec 1985	A
4563624	Yu	Jan 1986	A
4563877	Harnish	Jan 1986	A
4563878	Baglione	Jan 1986	A
4567733	Mecozzi	Feb 1986	A
4568909	Whynacht	Feb 1986	A
4574871	Parkinson et al.	Mar 1986	A
4575318	Blain	Mar 1986	A
4577977	Pejsa	Mar 1986	A
4580947	Shibata et al.	Apr 1986	A
4583373	Shaw	Apr 1986	A
4589060	Zinsmeyer	May 1986	A
4593367	Slack et al.	Jun 1986	A
4598764	Beckey	Jul 1986	A
4602484	Bendikson	Jul 1986	A
4604036	Sutou et al.	Aug 1986	A
4611470	Enstrom	Sep 1986	A
4612775	Branz et al.	Sep 1986	A
4614089	Dorsey	Sep 1986	A
4617804	Fukushima et al.	Oct 1986	A
4620286	Smith et al.	Oct 1986	A
4620424	Tanaka et al.	Nov 1986	A
4621502	Ibrahim et al.	Nov 1986	A
4627245	Levine	Dec 1986	A
4627483	Harshbarger, III et al.	Dec 1986	A
4627484	Harshbarger, Jr. et al.	Dec 1986	A
4630572	Evans	Dec 1986	A
4630670	Wellman et al.	Dec 1986	A
4642034	Terauchi	Feb 1987	A
4642782	Kemper et al.	Feb 1987	A
4644479	Kemper et al.	Feb 1987	A
4646532	Nose	Mar 1987	A
4648044	Hardy et al.	Mar 1987	A
4649515	Thompson et al.	Mar 1987	A
4649710	Inoue et al.	Mar 1987	A
4653280	Hansen et al.	Mar 1987	A
4653285	Pohl	Mar 1987	A
4655688	Bohn et al.	Apr 1987	A
4660386	Hansen et al.	Apr 1987	A
4662184	Pohl et al.	May 1987	A
4674292	Ohya et al.	Jun 1987	A
4677830	Sumikawa et al.	Jul 1987	A
4680940	Vaughn	Jul 1987	A
4682473	Rogers, III	Jul 1987	A
4684060	Adams et al.	Aug 1987	A
4685615	Hart	Aug 1987	A
4686835	Alsenz	Aug 1987	A
4689967	Han et al.	Sep 1987	A
4697431	Alsenz	Oct 1987	A
4698978	Jones	Oct 1987	A
4698981	Kaneko et al.	Oct 1987	A
4701824	Beggs et al.	Oct 1987	A
4703325	Chamberlin et al.	Oct 1987	A
4706152	DeFilippis et al.	Nov 1987	A
4706469	Oguni et al.	Nov 1987	A
4712648	Mattes et al.	Dec 1987	A
4713717	Pejouhy et al.	Dec 1987	A
4715190	Han et al.	Dec 1987	A
4715792	Nishizawa et al.	Dec 1987	A
4716582	Blanchard et al.	Dec 1987	A
4716957	Thompson et al.	Jan 1988	A
4720980	Howland	Jan 1988	A
4722018	Pohl	Jan 1988	A
4722019	Pohl	Jan 1988	A
4724678	Pohl	Feb 1988	A
4735054	Beckey	Apr 1988	A
4735060	Alsenz	Apr 1988	A
4744223	Umezu	May 1988	A
4745765	Pettitt	May 1988	A
4745766	Bahr	May 1988	A
4745767	Ohya et al.	May 1988	A
4750332	Jenski et al.	Jun 1988	A
4750672	Beckey et al.	Jun 1988	A
4751501	Gut	Jun 1988	A
4751825	Voorhis et al.	Jun 1988	A
4754410	Leech et al.	Jun 1988	A
4755957	White et al.	Jul 1988	A
4765150	Persem	Aug 1988	A
4768346	Mathur	Sep 1988	A
4768348	Noguchi	Sep 1988	A
4783752	Kaplan et al.	Nov 1988	A
4787213	Gras et al.	Nov 1988	A
4790142	Beckey	Dec 1988	A
4796466	Farmer	Jan 1989	A
4798055	Murray et al.	Jan 1989	A
4805118	Rishel	Feb 1989	A
4807445	Matsuoka et al.	Feb 1989	A
4820130	Eber et al.	Apr 1989	A
4829779	Munson et al.	May 1989	A
4831560	Zaleski	May 1989	A
4831832	Alsenz	May 1989	A
4831833	Duenes et al.	May 1989	A
4835706	Asahi	May 1989	A
4835980	Oyanagi et al.	Jun 1989	A
4838037	Wood	Jun 1989	A
4841734	Torrence	Jun 1989	A
4843575	Crane	Jun 1989	A
4845956	Berntsen et al.	Jul 1989	A
4848099	Beckey et al.	Jul 1989	A
4848100	Barthel et al.	Jul 1989	A
4850198	Helt et al.	Jul 1989	A
4850204	Bos et al.	Jul 1989	A
4852363	Kampf et al.	Aug 1989	A
4853693	Eaton-Williams	Aug 1989	A
4856286	Sulfstede et al.	Aug 1989	A
4858676	Bolfik et al.	Aug 1989	A
4866635	Kahn et al.	Sep 1989	A
4866944	Yamazaki	Sep 1989	A
4869073	Kawai et al.	Sep 1989	A
4873836	Thompson	Oct 1989	A
4875589	Lacey et al.	Oct 1989	A
4877382	Caillat et al.	Oct 1989	A
4878355	Beckey et al.	Nov 1989	A
4881184	Abegg, III et al.	Nov 1989	A
4882747	Williams	Nov 1989	A
4882908	White	Nov 1989	A
4884412	Sellers et al.	Dec 1989	A
4885707	Nichol et al.	Dec 1989	A
4885914	Pearman	Dec 1989	A
4887436	Enomoto et al.	Dec 1989	A
4887857	VanOmmeren	Dec 1989	A
4889280	Grald et al.	Dec 1989	A
4893480	Matsui et al.	Jan 1990	A
4899551	Weintraub	Feb 1990	A
4903500	Hanson	Feb 1990	A
4903759	Lapeyrouse	Feb 1990	A
4904993	Sato	Feb 1990	A
4909041	Jones	Mar 1990	A
4909076	Busch et al.	Mar 1990	A
4910966	Levine et al.	Mar 1990	A
4913625	Gerlowski	Apr 1990	A
4916633	Tychonievich et al.	Apr 1990	A
4916909	Mathur et al.	Apr 1990	A
4916912	Levine et al.	Apr 1990	A
4918690	Markkula, Jr. et al.	Apr 1990	A
4918932	Gustafson et al.	Apr 1990	A
4924404	Reinke, Jr.	May 1990	A
4924418	Bachman et al.	May 1990	A
4928750	Nurczyk	May 1990	A
4932588	Fedter et al.	Jun 1990	A
4939909	Tsuchiyama et al.	Jul 1990	A
4943003	Shimizu et al.	Jul 1990	A
4944160	Malone et al.	Jul 1990	A
4945491	Rishel	Jul 1990	A
4948040	Kobayashi et al.	Aug 1990	A
4949550	Hanson	Aug 1990	A
4953784	Yasufuku et al.	Sep 1990	A
4959970	Meckler	Oct 1990	A
4964060	Hartsog	Oct 1990	A
4964125	Kim	Oct 1990	A
4966006	Thuesen et al.	Oct 1990	A
4967567	Proctor et al.	Nov 1990	A
4970496	Kirkpatrick	Nov 1990	A
4974427	Diab	Dec 1990	A
4974665	Zillner, Jr.	Dec 1990	A
4975024	Heckel	Dec 1990	A
4977751	Hanson	Dec 1990	A
4985857	Bajpai et al.	Jan 1991	A
4987748	Meckler	Jan 1991	A
4990057	Rollins	Feb 1991	A
4990893	Kiluk	Feb 1991	A
4991770	Bird et al.	Feb 1991	A
5000009	Clanin	Mar 1991	A
5005365	Lynch	Apr 1991	A
5009074	Goubeaux et al.	Apr 1991	A
5009075	Okoren	Apr 1991	A
5009076	Winslow	Apr 1991	A
5012629	Rehman et al.	May 1991	A
5018357	Livingstone et al.	May 1991	A
5018665	Sulmone	May 1991	A
RE33620	Persem	Jun 1991	E
5022234	Goubeaux et al.	Jun 1991	A
5039009	Baldwin et al.	Aug 1991	A
5042264	Dudley	Aug 1991	A
5051720	Kittirutsunetorn	Sep 1991	A
5056036	Van Bork	Oct 1991	A
5056329	Wilkinson	Oct 1991	A
5058388	Shaw et al.	Oct 1991	A
5062278	Sugiyama	Nov 1991	A
5065593	Dudley et al.	Nov 1991	A
5067099	McCown et al.	Nov 1991	A
RE33775	Behr et al.	Dec 1991	E
5070468	Niinomi et al.	Dec 1991	A
5071065	Aalto et al.	Dec 1991	A
5073091	Burgess et al.	Dec 1991	A
5073862	Carlson	Dec 1991	A
5076067	Prenger et al.	Dec 1991	A
5076494	Ripka	Dec 1991	A
5077983	Dudley	Jan 1992	A
5083438	McMullin	Jan 1992	A
5086385	Launey et al.	Feb 1992	A
5088297	Maruyama et al.	Feb 1992	A
5094086	Shyu	Mar 1992	A
5095712	Narreau	Mar 1992	A
5095715	Dudley	Mar 1992	A
5099654	Baruschke et al.	Mar 1992	A
5102316	Caillat et al.	Apr 1992	A
5103391	Barrett	Apr 1992	A
5107500	Wakamoto et al.	Apr 1992	A
5109222	Welty	Apr 1992	A
5109676	Waters et al.	May 1992	A
5109700	Hicho	May 1992	A
5109916	Thompson	May 1992	A
5115406	Zatezalo et al.	May 1992	A
5115643	Hayata et al.	May 1992	A
5115644	Alsenz	May 1992	A
5115967	Wedekind	May 1992	A
5118260	Fraser, Jr.	Jun 1992	A
5119466	Suzuki	Jun 1992	A
5119637	Bard et al.	Jun 1992	A
5121610	Atkinson et al.	Jun 1992	A
5123017	Simpkins et al.	Jun 1992	A
5123252	Hanson	Jun 1992	A
5123253	Hanson et al.	Jun 1992	A
5123255	Ohizumi	Jun 1992	A
5125067	Erdman	Jun 1992	A
RE34001	Wrobel	Jul 1992	E
5127232	Paige et al.	Jul 1992	A
5131237	Valbjorn	Jul 1992	A
5141407	Ramsey et al.	Aug 1992	A
5142877	Shimizu	Sep 1992	A
5150584	Tomasov et al.	Sep 1992	A
5156539	Anderson et al.	Oct 1992	A
5167494	Inagaki et al.	Dec 1992	A
5170935	Federspiel et al.	Dec 1992	A
5170936	Kubo et al.	Dec 1992	A
5181389	Hanson et al.	Jan 1993	A
5186014	Runk	Feb 1993	A
5197666	Wedekind	Mar 1993	A
5199855	Nakajima et al.	Apr 1993	A
5200872	D'Entremont et al.	Apr 1993	A
5200987	Gray	Apr 1993	A
5201862	Pettitt	Apr 1993	A
5203178	Shyu	Apr 1993	A
5203179	Powell	Apr 1993	A
5209076	Kauffman et al.	May 1993	A
5209400	Winslow et al.	May 1993	A
5219041	Greve	Jun 1993	A
5224354	Ito et al.	Jul 1993	A
5224835	Oltman	Jul 1993	A
5226472	Benevelli et al.	Jul 1993	A
5228300	Shim	Jul 1993	A
5228304	Ryan	Jul 1993	A
5228307	Koce	Jul 1993	A
5230223	Hullar et al.	Jul 1993	A
5231844	Park	Aug 1993	A
5233841	Jyrek	Aug 1993	A
5235526	Saffell	Aug 1993	A
5237830	Grant	Aug 1993	A
5241664	Ohba et al.	Aug 1993	A
5241833	Ohkoshi	Sep 1993	A
5243827	Hagita et al.	Sep 1993	A
5243829	Bessler	Sep 1993	A
5245833	Mei et al.	Sep 1993	A
5248244	Ho et al.	Sep 1993	A
5251453	Stanke et al.	Oct 1993	A
5251454	Yoon	Oct 1993	A
5255977	Eimer et al.	Oct 1993	A
5257506	DeWolf et al.	Nov 1993	A
5262704	Farr	Nov 1993	A
5265434	Alsenz	Nov 1993	A
5269458	Sol	Dec 1993	A
5271556	Helt et al.	Dec 1993	A
5274571	Hesse et al.	Dec 1993	A
5276630	Baldwin et al.	Jan 1994	A
5279458	DeWolf et al.	Jan 1994	A
5282728	Swain	Feb 1994	A
5284026	Powell	Feb 1994	A
5289362	Liebl et al.	Feb 1994	A
5290154	Kotlarek et al.	Mar 1994	A
5291752	Alvarez et al.	Mar 1994	A
5299504	Abele	Apr 1994	A
5303112	Zulaski et al.	Apr 1994	A
5303560	Hanson et al.	Apr 1994	A
5311451	Barrett	May 1994	A
5311562	Palusamy et al.	May 1994	A
5316448	Ziegler et al.	May 1994	A
5320506	Fogt	Jun 1994	A
5333460	Lewis et al.	Aug 1994	A
5335507	Powell	Aug 1994	A
5336058	Yokoyama	Aug 1994	A
5347476	McBean, Sr.	Sep 1994	A
5351037	Martell et al.	Sep 1994	A
5362206	Westerman et al.	Nov 1994	A
5362211	Iizuka et al.	Nov 1994	A
5368446	Rode	Nov 1994	A
5369958	Kasai et al.	Dec 1994	A
5381669	Bahel et al.	Jan 1995	A
5381692	Winslow et al.	Jan 1995	A
5388176	Dykstra et al.	Feb 1995	A
5395042	Riley et al.	Mar 1995	A
5410230	Bessler et al.	Apr 1995	A
5414792	Shorey	May 1995	A
5415008	Bessler	May 1995	A
5416781	Ruiz	May 1995	A
5423190	Friedland	Jun 1995	A
5423192	Young et al.	Jun 1995	A
5426952	Bessler	Jun 1995	A
5431026	Jaster	Jul 1995	A
5432500	Scripps	Jul 1995	A
5435145	Jaster	Jul 1995	A
5435148	Sandofsky et al.	Jul 1995	A
5440890	Bahel et al.	Aug 1995	A
5440891	Hindmon, Jr. et al.	Aug 1995	A
5440895	Bahel et al.	Aug 1995	A
5446677	Jensen et al.	Aug 1995	A
5450359	Sharma et al.	Sep 1995	A
5452291	Eisenhandler et al.	Sep 1995	A
5454229	Hanson et al.	Oct 1995	A
5457965	Blair et al.	Oct 1995	A
5460006	Torimitsu	Oct 1995	A
5467011	Hunt	Nov 1995	A
5467264	Rauch et al.	Nov 1995	A
5475986	Bahel et al.	Dec 1995	A
5478212	Sakai et al.	Dec 1995	A
5481481	Frey et al.	Jan 1996	A
5481884	Scoccia	Jan 1996	A
5483141	Uesugi	Jan 1996	A
5491978	Young et al.	Feb 1996	A
5495722	Manson et al.	Mar 1996	A
5499512	Jurewicz et al.	Mar 1996	A
5509786	Mizutani et al.	Apr 1996	A
5511387	Tinsler	Apr 1996	A
5512883	Lane, Jr.	Apr 1996	A
5515267	Alsenz	May 1996	A
5515692	Sterber et al.	May 1996	A
5519301	Yoshida et al.	May 1996	A
5528908	Bahel et al.	Jun 1996	A
5532534	Baker et al.	Jul 1996	A
5533347	Ott et al.	Jul 1996	A
5535136	Standifer	Jul 1996	A
5535597	An	Jul 1996	A
5546015	Okabe	Aug 1996	A
5546073	Duff et al.	Aug 1996	A
5546756	Ali	Aug 1996	A
5546757	Whipple, III	Aug 1996	A
5548966	Tinsler	Aug 1996	A
5555195	Jensen et al.	Sep 1996	A
5562426	Watanabe et al.	Oct 1996	A
5563490	Kawaguchi et al.	Oct 1996	A
5564280	Schilling et al.	Oct 1996	A
5566084	Cmar	Oct 1996	A
5570085	Bertsch	Oct 1996	A
5570258	Manning	Oct 1996	A
5572643	Judson	Nov 1996	A
5577905	Momber et al.	Nov 1996	A
5579648	Hanson et al.	Dec 1996	A
5581229	Hunt	Dec 1996	A
5586445	Bessler	Dec 1996	A
5586446	Torimitsu	Dec 1996	A
5590830	Kettler et al.	Jan 1997	A
5592058	Archer et al.	Jan 1997	A
5592824	Sogabe et al.	Jan 1997	A
5596507	Jones et al.	Jan 1997	A
5600960	Schwedler et al.	Feb 1997	A
5602749	Vosburgh	Feb 1997	A
5602757	Haseley et al.	Feb 1997	A
5602761	Spoerre et al.	Feb 1997	A
5610339	Haseley et al.	Mar 1997	A
5611674	Bass et al.	Mar 1997	A
5613841	Bass et al.	Mar 1997	A
5615071	Higashikata et al.	Mar 1997	A
5616829	Balaschak et al.	Apr 1997	A
5623834	Bahel et al.	Apr 1997	A
5628201	Bahel et al.	May 1997	A
5630325	Bahel et al.	May 1997	A
5635896	Tinsley et al.	Jun 1997	A
5641270	Sgourakes et al.	Jun 1997	A
5643482	Sandelman et al.	Jul 1997	A
5650936	Loucks et al.	Jul 1997	A
5655379	Jaster et al.	Aug 1997	A
5655380	Calton	Aug 1997	A
5656767	Garvey, III et al.	Aug 1997	A
5682949	Ratcliffe et al.	Nov 1997	A
5684463	Diercks et al.	Nov 1997	A
5689963	Bahel et al.	Nov 1997	A
5691692	Herbstritt	Nov 1997	A
5694010	Oomura et al.	Dec 1997	A
5696501	Ouellette et al.	Dec 1997	A
5699670	Jurewicz et al.	Dec 1997	A
5706007	Fragnito et al.	Jan 1998	A
5707210	Ramsey et al.	Jan 1998	A
5711785	Maxwell	Jan 1998	A
5713724	Centers et al.	Feb 1998	A
5714931	Petite et al.	Feb 1998	A
5715704	Cholkeri et al.	Feb 1998	A
5718822	Richter	Feb 1998	A
5724571	Woods	Mar 1998	A
5729474	Hildebrand et al.	Mar 1998	A
5737931	Ueno et al.	Apr 1998	A
5741120	Bass et al.	Apr 1998	A
5743109	Schulak	Apr 1998	A
5745114	King et al.	Apr 1998	A
5749238	Schmidt	May 1998	A
5751916	Kon et al.	May 1998	A
5752385	Nelson	May 1998	A
5754450	Solomon et al.	May 1998	A
5754732	Vlahu	May 1998	A
5757664	Rogers et al.	May 1998	A
5757892	Blanchard et al.	May 1998	A
5761083	Brown, Jr. et al.	Jun 1998	A
5764509	Gross et al.	Jun 1998	A
5772214	Stark	Jun 1998	A
5772403	Allison et al.	Jun 1998	A
5784232	Farr	Jul 1998	A
5790898	Kishima et al.	Aug 1998	A
5795381	Holder	Aug 1998	A
5798941	McLeister	Aug 1998	A
5802860	Barrows	Sep 1998	A
5805856	Hanson	Sep 1998	A
5807336	Russo et al.	Sep 1998	A
5808441	Nehring	Sep 1998	A
5810908	Gray et al.	Sep 1998	A
5812061	Simons	Sep 1998	A
5825597	Young	Oct 1998	A
5827963	Selegatto et al.	Oct 1998	A
5839094	French	Nov 1998	A
5839291	Chang	Nov 1998	A
5841654	Verissimo et al.	Nov 1998	A
5857348	Conry	Jan 1999	A
5860286	Tulpule	Jan 1999	A
5861807	Leyden et al.	Jan 1999	A
5867998	Guertin	Feb 1999	A
5869960	Brand	Feb 1999	A
5873257	Peterson	Feb 1999	A
5875430	Koether	Feb 1999	A
5875638	Tinsler	Mar 1999	A
5884494	Okoren et al.	Mar 1999	A
5887786	Sandelman	Mar 1999	A
5900801	Heagle et al.	May 1999	A
5904049	Jaster et al.	May 1999	A
5918200	Tsutsui et al.	Jun 1999	A
5924295	Park	Jul 1999	A
5924486	Ehlers et al.	Jul 1999	A
5926103	Petite	Jul 1999	A
5926531	Petite	Jul 1999	A
5930773	Crooks et al.	Jul 1999	A
5934087	Watanabe et al.	Aug 1999	A
5939974	Heagle et al.	Aug 1999	A
5946922	Viard et al.	Sep 1999	A
5947693	Yang	Sep 1999	A
5947701	Hugenroth	Sep 1999	A
5949677	Ho	Sep 1999	A
5950443	Meyer et al.	Sep 1999	A
5953490	Wiklund et al.	Sep 1999	A
5956658	McMahon	Sep 1999	A
5971712	Kann	Oct 1999	A
5975854	Culp, III et al.	Nov 1999	A
5984645	Cummings	Nov 1999	A
5986571	Flick	Nov 1999	A
5987903	Bathla	Nov 1999	A
5988986	Brinken et al.	Nov 1999	A
5995347	Rudd et al.	Nov 1999	A
5995351	Katsumata et al.	Nov 1999	A
6006142	Seem et al.	Dec 1999	A
6006171	Vines et al.	Dec 1999	A
6011368	Kalpathi et al.	Jan 2000	A
6013108	Karolys et al.	Jan 2000	A
6017192	Clack et al.	Jan 2000	A
6020702	Farr	Feb 2000	A
6023420	McCormick et al.	Feb 2000	A
6026651	Sandelman	Feb 2000	A
6028522	Petite	Feb 2000	A
6035653	Itoh et al.	Mar 2000	A
6035661	Sunaga et al.	Mar 2000	A
6038871	Gutierrez et al.	Mar 2000	A
6041605	Heinrichs	Mar 2000	A
6041609	Hornsleth et al.	Mar 2000	A
6041856	Thrasher et al.	Mar 2000	A
6042344	Lifson	Mar 2000	A
6044062	Brownrigg et al.	Mar 2000	A
6047557	Pham et al.	Apr 2000	A
6050098	Meyer et al.	Apr 2000	A
6050780	Hasegawa et al.	Apr 2000	A
6052731	Holdsworth et al.	Apr 2000	A
6057771	Lakra	May 2000	A
6065946	Lathrop	May 2000	A
6068447	Foege	May 2000	A
6070110	Shah et al.	May 2000	A
6075530	Lucas et al.	Jun 2000	A
6077051	Centers et al.	Jun 2000	A
6081750	Hoffberg et al.	Jun 2000	A
6082495	Steinbarger et al.	Jul 2000	A
6082971	Gunn et al.	Jul 2000	A
6085530	Barito	Jul 2000	A
6088659	Kelley et al.	Jul 2000	A
6088688	Crooks et al.	Jul 2000	A
6092370	Tremoulet, Jr. et al.	Jul 2000	A
6092378	Das et al.	Jul 2000	A
6092992	Imblum et al.	Jul 2000	A
6095674	Verissimo et al.	Aug 2000	A
6098893	Berglund et al.	Aug 2000	A
6102665	Centers et al.	Aug 2000	A
6110260	Kubokawa	Aug 2000	A
6119949	Lindstrom	Sep 2000	A
6122603	Budike, Jr.	Sep 2000	A
6125642	Seener et al.	Oct 2000	A
6128583	Dowling	Oct 2000	A
6128953	Mizukoshi	Oct 2000	A
6129527	Donahoe et al.	Oct 2000	A
6138461	Park et al.	Oct 2000	A
6144888	Lucas et al.	Nov 2000	A
6145328	Choi	Nov 2000	A
6147601	Sandelman et al.	Nov 2000	A
6152375	Robison	Nov 2000	A
6152376	Sandelman et al.	Nov 2000	A
6153942	Roseman et al.	Nov 2000	A
6153993	Oomura et al.	Nov 2000	A
6154488	Hunt	Nov 2000	A
6157310	Milne et al.	Dec 2000	A
6158230	Katsuki	Dec 2000	A
6160477	Sandelman et al.	Dec 2000	A
6169979	Johnson	Jan 2001	B1
6172476	Tolbert, Jr. et al.	Jan 2001	B1
6174136	Kilayko et al.	Jan 2001	B1
6176686	Wallis et al.	Jan 2001	B1
6177884	Hunt et al.	Jan 2001	B1
6178362	Woolard et al.	Jan 2001	B1
6179214	Key et al.	Jan 2001	B1
6181033	Wright	Jan 2001	B1
6190442	Redner	Feb 2001	B1
6191545	Kawabata et al.	Feb 2001	B1
6192282	Smith et al.	Feb 2001	B1
6199018	Quist et al.	Mar 2001	B1
6211782	Sandelman et al.	Apr 2001	B1
6213731	Doepker et al.	Apr 2001	B1
6215405	Handley et al.	Apr 2001	B1
6216956	Ehlers et al.	Apr 2001	B1
6218953	Petite	Apr 2001	B1
6223543	Sandelman	May 2001	B1
6223544	Seem	May 2001	B1
6228155	Tai	May 2001	B1
6230501	Bailey, Sr. et al.	May 2001	B1
6233327	Petite	May 2001	B1
6234019	Caldeira	May 2001	B1
6240733	Brandon et al.	Jun 2001	B1
6240736	Fujita et al.	Jun 2001	B1
6244061	Takagi et al.	Jun 2001	B1
6249516	Brownrigg et al.	Jun 2001	B1
6260004	Hays et al.	Jul 2001	B1
6266968	Redlich	Jul 2001	B1
6268664	Rolls et al.	Jul 2001	B1
6272868	Grabon et al.	Aug 2001	B1
6276901	Farr et al.	Aug 2001	B1
6279332	Yeo et al.	Aug 2001	B1
6290043	Ginder et al.	Sep 2001	B1
6293114	Kamemoto	Sep 2001	B1
6293767	Bass	Sep 2001	B1
6302654	Millet et al.	Oct 2001	B1
6304934	Pimenta et al.	Oct 2001	B1
6324854	Jayanth	Dec 2001	B1
6327541	Pitchford et al.	Dec 2001	B1
6332327	Street et al.	Dec 2001	B1
6334093	More	Dec 2001	B1
6349883	Simmons et al.	Feb 2002	B1
6359410	Randolph	Mar 2002	B1
6360551	Renders	Mar 2002	B1
6366889	Zaloom	Apr 2002	B1
6375439	Missio	Apr 2002	B1
6378315	Gelber et al.	Apr 2002	B1
6381971	Honda	May 2002	B2
6385510	Hoog et al.	May 2002	B1
6389823	Loprete et al.	May 2002	B1
6390779	Cunkelman	May 2002	B1
6391102	Bodden et al.	May 2002	B1
6393848	Roh et al.	May 2002	B2
6397606	Roh et al.	Jun 2002	B1
6397612	Kernkamp et al.	Jun 2002	B1
6406265	Hahn et al.	Jun 2002	B1
6406266	Hugenroth et al.	Jun 2002	B1
6408228	Seem et al.	Jun 2002	B1
6408258	Richer	Jun 2002	B1
6412293	Pham et al.	Jul 2002	B1
6414594	Guerlain	Jul 2002	B1
6430268	Petite	Aug 2002	B1
6433791	Selli et al.	Aug 2002	B2
6437691	Sandelman et al.	Aug 2002	B1
6437692	Petite et al.	Aug 2002	B1
6438981	Whiteside	Aug 2002	B1
6442953	Trigiani et al.	Sep 2002	B1
6449972	Pham et al.	Sep 2002	B2
6450771	Centers et al.	Sep 2002	B1
6451210	Sivavec et al.	Sep 2002	B1
6453687	Sharood et al.	Sep 2002	B2
6454177	Sasao et al.	Sep 2002	B1
6454538	Witham et al.	Sep 2002	B1
6456928	Johnson	Sep 2002	B1
6457319	Ota et al.	Oct 2002	B1
6457948	Pham	Oct 2002	B1
6460731	Estelle et al.	Oct 2002	B2
6462654	Sandelman et al.	Oct 2002	B1
6463747	Temple	Oct 2002	B1
6466971	Humpleman et al.	Oct 2002	B1
6467280	Pham et al.	Oct 2002	B2
6471486	Centers et al.	Oct 2002	B1
6474084	Gauthier et al.	Nov 2002	B2
6484520	Kawaguchi et al.	Nov 2002	B2
6487457	Hull et al.	Nov 2002	B1
6490506	March	Dec 2002	B1
6492923	Inoue et al.	Dec 2002	B1
6497554	Yang et al.	Dec 2002	B2
6501240	Ueda et al.	Dec 2002	B2
6501629	Marriott	Dec 2002	B1
6502409	Gatling et al.	Jan 2003	B1
6505087	Lucas et al.	Jan 2003	B1
6505475	Zugibe et al.	Jan 2003	B1
6510350	Steen, III et al.	Jan 2003	B1
6522974	Sitton	Feb 2003	B2
6523130	Hickman et al.	Feb 2003	B1
6526766	Hiraoka et al.	Mar 2003	B1
6529590	Centers	Mar 2003	B1
6529839	Uggerud et al.	Mar 2003	B1
6533552	Centers et al.	Mar 2003	B2
6535123	Sandelman et al.	Mar 2003	B2
6535859	Yablonowski et al.	Mar 2003	B1
6537034	Park et al.	Mar 2003	B2
6542062	Herrick	Apr 2003	B1
6549135	Singh et al.	Apr 2003	B2
6551069	Narney, II et al.	Apr 2003	B2
6553774	Ishio et al.	Apr 2003	B1
6558126	Hahn et al.	May 2003	B1
6560976	Jayanth	May 2003	B2
6571280	Hubacher	May 2003	B1
6571566	Temple et al.	Jun 2003	B1
6571586	Ritson et al.	Jun 2003	B1
6574561	Alexander et al.	Jun 2003	B2
6577959	Chajec et al.	Jun 2003	B1
6577962	Afshari	Jun 2003	B1
6578373	Barbier	Jun 2003	B1
6583720	Quigley	Jun 2003	B1
6589029	Heller	Jul 2003	B1
6591620	Kikuchi et al.	Jul 2003	B2
6595475	Svabek et al.	Jul 2003	B2
6595757	Shen	Jul 2003	B2
6598056	Hull et al.	Jul 2003	B1
6601397	Pham et al.	Aug 2003	B2
6604093	Etzion et al.	Aug 2003	B1
6609070	Lueck	Aug 2003	B1
6609078	Starling et al.	Aug 2003	B2
6615594	Jayanth et al.	Sep 2003	B2
6616415	Renken et al.	Sep 2003	B1
6618578	Petite	Sep 2003	B1
6618709	Sneeringer	Sep 2003	B1
6621443	Selli et al.	Sep 2003	B1
6622925	Carner et al.	Sep 2003	B2
6622926	Sartain et al.	Sep 2003	B1
6628764	Petite	Sep 2003	B1
6629420	Renders	Oct 2003	B2
6631298	Pagnano et al.	Oct 2003	B1
6636893	Fong	Oct 2003	B1
6643567	Kolk et al.	Nov 2003	B2
6644848	Clayton et al.	Nov 2003	B1
6647735	Street et al.	Nov 2003	B2
6658373	Rossi et al.	Dec 2003	B2
6662584	Whiteside	Dec 2003	B1
6662653	Scaliante et al.	Dec 2003	B1
6671586	Davis et al.	Dec 2003	B2
6672846	Rajendran et al.	Jan 2004	B2
6675591	Singh et al.	Jan 2004	B2
6679072	Pham et al.	Jan 2004	B2
6684349	Gullo et al.	Jan 2004	B2
6685438	Yoo et al.	Feb 2004	B2
6698218	Goth et al.	Mar 2004	B2
6701725	Rossi et al.	Mar 2004	B2
6708083	Orthlieb et al.	Mar 2004	B2
6708508	Demuth et al.	Mar 2004	B2
6709244	Pham	Mar 2004	B2
6711470	Hartenstein et al.	Mar 2004	B1
6711911	Grabon et al.	Mar 2004	B1
6717513	Sandelman et al.	Apr 2004	B1
6721770	Morton et al.	Apr 2004	B1
6725182	Pagnano et al.	Apr 2004	B2
6732538	Trigiani et al.	May 2004	B2
6745107	Miller	Jun 2004	B1
6747557	Petite et al.	Jun 2004	B1
6758050	Jayanth et al.	Jul 2004	B2
6758051	Jayanth et al.	Jul 2004	B2
6760207	Wyatt et al.	Jul 2004	B2
6772096	Murakami et al.	Aug 2004	B2
6772598	Rinehart	Aug 2004	B1
6775995	Bahel et al.	Aug 2004	B1
6784807	Petite et al.	Aug 2004	B2
6785592	Smith et al.	Aug 2004	B1
6786473	Alles	Sep 2004	B1
6799951	Lifson et al.	Oct 2004	B2
6804993	Selli	Oct 2004	B2
6811380	Kim	Nov 2004	B2
6816811	Seem	Nov 2004	B2
6823680	Jayanth	Nov 2004	B2
6829542	Reynolds et al.	Dec 2004	B1
6832120	Frank et al.	Dec 2004	B1
6832898	Yoshida et al.	Dec 2004	B2
6836737	Petite et al.	Dec 2004	B2
6837922	Gorin	Jan 2005	B2
6839790	Barros De Almeida et al.	Jan 2005	B2
6854345	Alves et al.	Feb 2005	B2
6862498	Davis et al.	Mar 2005	B2
6868678	Mei et al.	Mar 2005	B2
6868686	Ueda et al.	Mar 2005	B2
6869272	Odachi et al.	Mar 2005	B2
6870486	Souza et al.	Mar 2005	B2
6885949	Selli	Apr 2005	B2
6889173	Singh	May 2005	B2
6891838	Petite et al.	May 2005	B1
6892546	Singh et al.	May 2005	B2
6897772	Scheffler et al.	May 2005	B1
6900738	Crichlow	May 2005	B2
6901066	Helgeson	May 2005	B1
6904385	Budike, Jr.	Jun 2005	B1
6914533	Petite	Jul 2005	B2
6914893	Petite	Jul 2005	B2
6922155	Evans et al.	Jul 2005	B1
6931445	Davis	Aug 2005	B2
6934862	Sharood et al.	Aug 2005	B2
6952658	Greulich et al.	Oct 2005	B2
6956344	Robertson et al.	Oct 2005	B2
6964558	Hahn et al.	Nov 2005	B2
6966759	Hahn et al.	Nov 2005	B2
6968295	Carr	Nov 2005	B1
6973410	Seigel	Dec 2005	B2
6973793	Douglas et al.	Dec 2005	B2
6973794	Street et al.	Dec 2005	B2
6976366	Starling et al.	Dec 2005	B2
6978225	Retlich et al.	Dec 2005	B2
6981384	Dobmeier et al.	Jan 2006	B2
6983321	Trinon et al.	Jan 2006	B2
6983889	Alles	Jan 2006	B2
6986469	Gauthier et al.	Jan 2006	B2
6987450	Marino et al.	Jan 2006	B2
6990821	Singh et al.	Jan 2006	B2
6996441	Tobias	Feb 2006	B1
6997390	Alles	Feb 2006	B2
6998963	Flen et al.	Feb 2006	B2
6999996	Sunderland	Feb 2006	B2
7000422	Street et al.	Feb 2006	B2
7003378	Poth	Feb 2006	B2
7009510	Douglass et al.	Mar 2006	B1
7010925	Sienel et al.	Mar 2006	B2
7019667	Petite et al.	Mar 2006	B2
7024665	Ferraz et al.	Apr 2006	B2
7024870	Singh et al.	Apr 2006	B2
7030752	Tyroler	Apr 2006	B2
7031880	Seem et al.	Apr 2006	B1
7035693	Cassiolato et al.	Apr 2006	B2
7039532	Hunter	May 2006	B2
7042180	Terry et al.	May 2006	B2
7042350	Patrick et al.	May 2006	B2
7043339	Maeda et al.	May 2006	B2
7043459	Peevey	May 2006	B2
7047753	Street et al.	May 2006	B2
7053766	Fisler et al.	May 2006	B2
7053767	Petite et al.	May 2006	B2
7054271	Brownrigg et al.	May 2006	B2
7062580	Donaires	Jun 2006	B2
7062830	Alles	Jun 2006	B2
7063537	Selli et al.	Jun 2006	B2
7072797	Gorinevsky	Jul 2006	B2
7075327	Dimino et al.	Jul 2006	B2
7079810	Petite et al.	Jul 2006	B2
7079967	Rossi et al.	Jul 2006	B2
7082380	Wiebe et al.	Jul 2006	B2
7089125	Sonderegger	Aug 2006	B2
7091847	Capowski et al.	Aug 2006	B2
7092767	Pagnano et al.	Aug 2006	B2
7092794	Hill et al.	Aug 2006	B1
7096153	Guralnik et al.	Aug 2006	B2
7102490	Flen et al.	Sep 2006	B2
7103511	Petite	Sep 2006	B2
7110843	Pagnano et al.	Sep 2006	B2
7110898	Montijo et al.	Sep 2006	B2
7113376	Nomura et al.	Sep 2006	B2
7114343	Kates	Oct 2006	B2
7123020	Hill et al.	Oct 2006	B2
7123458	Mohr et al.	Oct 2006	B2
7124728	Carey et al.	Oct 2006	B2
7126465	Faltesek	Oct 2006	B2
7130170	Wakefield et al.	Oct 2006	B2
7130832	Bannai et al.	Oct 2006	B2
7134295	Maekawa	Nov 2006	B2
7137550	Petite	Nov 2006	B1
7145438	Flen et al.	Dec 2006	B2
7145462	Dewing et al.	Dec 2006	B2
7159408	Sadegh et al.	Jan 2007	B2
7162884	Alles	Jan 2007	B2
7171372	Daniel et al.	Jan 2007	B2
7174728	Jayanth	Feb 2007	B2
7180412	Bonicatto et al.	Feb 2007	B2
7184861	Petite	Feb 2007	B2
7188482	Sadegh et al.	Mar 2007	B2
7188779	Alles	Mar 2007	B2
7201006	Kates	Apr 2007	B2
7207496	Alles	Apr 2007	B2
7209840	Petite et al.	Apr 2007	B2
7212887	Shah et al	May 2007	B2
7222493	Jayanth et al.	May 2007	B2
7224740	Hunt	May 2007	B2
7225193	Mets et al.	May 2007	B2
7227450	Garvy et al.	Jun 2007	B2
7228691	Street et al.	Jun 2007	B2
7236765	Bonicatto et al.	Jun 2007	B2
7244294	Kates	Jul 2007	B2
7246014	Forth et al.	Jul 2007	B2
7255285	Troost et al.	Aug 2007	B2
7260505	Felke et al.	Aug 2007	B2
7261762	Kang et al.	Aug 2007	B2
7263073	Petite et al.	Aug 2007	B2
7266812	Pagnano	Sep 2007	B2
7270278	Street et al.	Sep 2007	B2
7274995	Zhan et al.	Sep 2007	B2
7275377	Kates	Oct 2007	B2
7286945	Zhan et al.	Oct 2007	B2
7290398	Wallace et al.	Nov 2007	B2
7290989	Jayanth	Nov 2007	B2
7295128	Petite	Nov 2007	B2
7328192	Stengard et al.	Feb 2008	B1
7330886	Childers et al.	Feb 2008	B2
7331187	Kates	Feb 2008	B2
7337191	Haeberle et al.	Feb 2008	B2
7343750	Lifson et al.	Mar 2008	B2
7343751	Kates	Mar 2008	B2
7346463	Petite et al.	Mar 2008	B2
7346472	Moskowitz et al.	Mar 2008	B1
7349824	Seigel	Mar 2008	B2
7350112	Fox et al.	Mar 2008	B2
7351274	Helt et al.	Apr 2008	B2
7352545	Wyatt et al.	Apr 2008	B2
7363200	Lu	Apr 2008	B2
7376712	Granatelli et al.	May 2008	B1
7383030	Brown et al.	Jun 2008	B2
7383158	Krocker et al.	Jun 2008	B2
7392661	Alles	Jul 2008	B2
7397907	Petite	Jul 2008	B2
7412842	Pham	Aug 2008	B2
7421850	Street et al.	Sep 2008	B2
7424343	Kates	Sep 2008	B2
7424527	Petite	Sep 2008	B2
7432824	Flen et al.	Oct 2008	B2
7437150	Morelli et al.	Oct 2008	B1
7440560	Barry	Oct 2008	B1
7440767	Ballay et al.	Oct 2008	B2
7445665	Hsieh et al.	Nov 2008	B2
7447609	Guralnik et al.	Nov 2008	B2
7454439	Gansner et al.	Nov 2008	B1
7458223	Pham	Dec 2008	B2
7468661	Petite et al.	Dec 2008	B2
7469546	Kates	Dec 2008	B2
7474992	Ariyur	Jan 2009	B2
7480501	Petite	Jan 2009	B2
7483810	Jackson et al.	Jan 2009	B2
7484376	Pham	Feb 2009	B2
7490477	Singh et al.	Feb 2009	B2
7491034	Jayanth	Feb 2009	B2
7503182	Bahel et al.	Mar 2009	B2
7523619	Kojima et al.	Apr 2009	B2
7552030	Guralnik et al.	Jun 2009	B2
7555364	Poth et al.	Jun 2009	B2
7574333	Lu	Aug 2009	B2
7580812	Ariyur et al.	Aug 2009	B2
7606683	Bahel et al.	Oct 2009	B2
7636901	Munson et al.	Dec 2009	B2
7644591	Singh et al.	Jan 2010	B2
7648342	Jayanth	Jan 2010	B2
7650425	Davis et al.	Jan 2010	B2
7660700	Moskowitz et al.	Feb 2010	B2
7686872	Kang	Mar 2010	B2
7697492	Petite	Apr 2010	B2
7704052	Iimura et al.	Apr 2010	B2
7738999	Petite	Jun 2010	B2
7739378	Petite	Jun 2010	B2
7742393	Bonicatto et al.	Jun 2010	B2
7756086	Petite et al.	Jul 2010	B2
7791468	Bonicatto et al.	Sep 2010	B2
7844366	Singh	Nov 2010	B2
7845179	Singh et al.	Dec 2010	B2
7905098	Pham	Mar 2011	B2
7922914	Verdegan et al.	Apr 2011	B1
7941294	Shahi et al.	May 2011	B2
7949494	Moskowitz et al.	May 2011	B2
7949615	Ehlers et al.	May 2011	B2
7978059	Petite et al.	Jul 2011	B2
7987679	Tanaka et al.	Aug 2011	B2
8000314	Brownrigg et al.	Aug 2011	B2
8013732	Petite et al.	Sep 2011	B2
8029608	Breslin	Oct 2011	B1
8031650	Petite et al.	Oct 2011	B2
8034170	Kates	Oct 2011	B2
8041539	Guralnik et al.	Oct 2011	B2
8046107	Zugibe et al.	Oct 2011	B2
8064412	Petite	Nov 2011	B2
8065886	Singh et al.	Nov 2011	B2
8171136	Petite	May 2012	B2
8182579	Woo et al.	May 2012	B2
8214175	Moskowitz et al.	Jul 2012	B2
8328524	Iimura et al.	Dec 2012	B2
20010005320	Ueda et al.	Jun 2001	A1
20010025349	Sharood et al.	Sep 2001	A1
20010054291	Roh et al.	Dec 2001	A1
20010054293	Gustafson et al.	Dec 2001	A1
20010054294	Tsuboi	Dec 2001	A1
20020000092	Sharood et al.	Jan 2002	A1
20020013679	Petite	Jan 2002	A1
20020016639	Smith et al.	Feb 2002	A1
20020017057	Weder	Feb 2002	A1
20020018724	Millet et al.	Feb 2002	A1
20020020175	Street et al.	Feb 2002	A1
20020029575	Okamoto	Mar 2002	A1
20020031101	Petite et al.	Mar 2002	A1
20020035495	Spira et al.	Mar 2002	A1
20020040280	Morgan	Apr 2002	A1
20020064463	Park et al.	May 2002	A1
20020067999	Suitou et al.	Jun 2002	A1
20020082747	Kramer	Jun 2002	A1
20020082924	Koether	Jun 2002	A1
20020093259	Sunaga et al.	Jul 2002	A1
20020095269	Natalini et al.	Jul 2002	A1
20020103655	Boies et al.	Aug 2002	A1
20020113877	Welch	Aug 2002	A1
20020117992	Hirono et al.	Aug 2002	A1
20020118106	Brenn	Aug 2002	A1
20020127120	Hahn et al.	Sep 2002	A1
20020139128	Suzuki et al.	Oct 2002	A1
20020143482	Karanam et al.	Oct 2002	A1
20020152298	Kikta et al.	Oct 2002	A1
20020157408	Egawa et al.	Oct 2002	A1
20020159890	Kajiwara et al.	Oct 2002	A1
20020161545	Starling et al.	Oct 2002	A1
20020163436	Singh et al.	Nov 2002	A1
20020170299	Jayanth et al.	Nov 2002	A1
20020173929	Seigel	Nov 2002	A1
20020187057	Loprete et al.	Dec 2002	A1
20020189267	Singh et al.	Dec 2002	A1
20020193890	Pouchak	Dec 2002	A1
20020198629	Ellis	Dec 2002	A1
20030004660	Hunter	Jan 2003	A1
20030004765	Wiegand	Jan 2003	A1
20030005710	Singh et al.	Jan 2003	A1
20030006884	Hunt	Jan 2003	A1
20030014218	Trigiani et al.	Jan 2003	A1
20030019221	Rossi et al.	Jan 2003	A1
20030036810	Petite	Feb 2003	A1
20030037555	Street et al.	Feb 2003	A1
20030050737	Osann	Mar 2003	A1
20030050824	Suermondt et al.	Mar 2003	A1
20030051490	Jayanth	Mar 2003	A1
20030055603	Rossi et al.	Mar 2003	A1
20030063983	Ancel et al.	Apr 2003	A1
20030070438	Kikuchi et al.	Apr 2003	A1
20030070544	Mulvaney et al.	Apr 2003	A1
20030074285	Hoffman et al.	Apr 2003	A1
20030077179	Collins et al.	Apr 2003	A1
20030078677	Hull et al.	Apr 2003	A1
20030078742	VanderZee et al.	Apr 2003	A1
20030089493	Takano et al.	May 2003	A1
20030094004	Pham et al.	May 2003	A1
20030108430	Yoshida et al.	Jun 2003	A1
20030115890	Jayanth et al.	Jun 2003	A1
20030135786	Vollmar et al.	Jul 2003	A1
20030137396	Durej et al.	Jul 2003	A1
20030150924	Peter	Aug 2003	A1
20030150926	Rosen	Aug 2003	A1
20030150927	Rosen	Aug 2003	A1
20030171851	Brickfield et al.	Sep 2003	A1
20030183085	Alexander	Oct 2003	A1
20030191606	Fujiyama et al.	Oct 2003	A1
20030199247	Striemer	Oct 2003	A1
20030205143	Cheng	Nov 2003	A1
20030213256	Ueda et al.	Nov 2003	A1
20030213851	Burd et al.	Nov 2003	A1
20030216837	Reich et al.	Nov 2003	A1
20030216888	Ridolfo	Nov 2003	A1
20030233172	Granqvist et al.	Dec 2003	A1
20040016241	Street et al.	Jan 2004	A1
20040016244	Street et al.	Jan 2004	A1
20040016251	Street et al.	Jan 2004	A1
20040016253	Street et al.	Jan 2004	A1
20040019584	Greening et al.	Jan 2004	A1
20040024495	Sunderland	Feb 2004	A1
20040037706	Hahn et al.	Feb 2004	A1
20040042904	Kim	Mar 2004	A1
20040047406	Hunt	Mar 2004	A1
20040049715	Jaw	Mar 2004	A1
20040059691	Higgins	Mar 2004	A1
20040068390	Saunders	Apr 2004	A1
20040078695	Bowers et al.	Apr 2004	A1
20040079093	Gauthier et al.	Apr 2004	A1
20040093879	Street et al.	May 2004	A1
20040095237	Chen et al.	May 2004	A1
20040111186	Rossi et al.	Jun 2004	A1
20040117166	Cassiolato	Jun 2004	A1
20040133314	Ehlers et al.	Jul 2004	A1
20040133367	Hart	Jul 2004	A1
20040140772	Gullo et al.	Jul 2004	A1
20040140812	Scallante et al.	Jul 2004	A1
20040144106	Douglas et al.	Jul 2004	A1
20040153437	Buchan	Aug 2004	A1
20040159113	Singh et al.	Aug 2004	A1
20040183687	Petite et al.	Sep 2004	A1
20040184627	Kost et al.	Sep 2004	A1
20040184928	Millet et al.	Sep 2004	A1
20040184929	Millet et al.	Sep 2004	A1
20040184930	Millet et al.	Sep 2004	A1
20040184931	Millet et al.	Sep 2004	A1
20040187502	Jayanth et al.	Sep 2004	A1
20040191073	Iimura et al.	Sep 2004	A1
20040210419	Wiebe et al.	Oct 2004	A1
20040213384	Alles et al.	Oct 2004	A1
20040230582	Pagnano et al.	Nov 2004	A1
20040230899	Pagnano et al.	Nov 2004	A1
20040239266	Lee et al.	Dec 2004	A1
20040258542	Wiertz et al.	Dec 2004	A1
20040261431	Singh et al.	Dec 2004	A1
20050040249	Wacker et al.	Feb 2005	A1
20050043923	Forster et al.	Feb 2005	A1
20050053471	Hong et al.	Mar 2005	A1
20050056031	Jeong	Mar 2005	A1
20050073532	Scott et al.	Apr 2005	A1
20050086341	Enga et al.	Apr 2005	A1
20050100449	Hahn et al.	May 2005	A1
20050103036	Maekawa	May 2005	A1
20050125439	Nourbakhsh et al.	Jun 2005	A1
20050126190	Lifson et al.	Jun 2005	A1
20050131624	Gaessler et al.	Jun 2005	A1
20050149570	Sasaki et al.	Jul 2005	A1
20050166610	Jayanth	Aug 2005	A1
20050169636	Aronson et al.	Aug 2005	A1
20050172647	Thybo et al.	Aug 2005	A1
20050188842	Hsieh et al.	Sep 2005	A1
20050195775	Petite et al.	Sep 2005	A1
20050198063	Thomas et al.	Sep 2005	A1
20050201397	Petite	Sep 2005	A1
20050204756	Dobmeier et al.	Sep 2005	A1
20050207741	Shah et al.	Sep 2005	A1
20050214148	Ogawa et al.	Sep 2005	A1
20050222715	Ruhnke et al.	Oct 2005	A1
20050228607	Simons	Oct 2005	A1
20050229612	Hrejsa et al.	Oct 2005	A1
20050229777	Brown et al.	Oct 2005	A1
20050232781	Herbert et al.	Oct 2005	A1
20050235660	Pham	Oct 2005	A1
20050235661	Pham	Oct 2005	A1
20050235662	Pham	Oct 2005	A1
20050235663	Pham	Oct 2005	A1
20050235664	Pham	Oct 2005	A1
20050247194	Kang et al.	Nov 2005	A1
20050251293	Seigel	Nov 2005	A1
20050252220	Street et al.	Nov 2005	A1
20050262856	Street et al.	Dec 2005	A1
20050262923	Kates	Dec 2005	A1
20060010898	Suharno et al.	Jan 2006	A1
20060015777	Loda	Jan 2006	A1
20060020426	Singh	Jan 2006	A1
20060021362	Sadegh et al.	Feb 2006	A1
20060032245	Kates	Feb 2006	A1
20060032246	Kates	Feb 2006	A1
20060032247	Kates	Feb 2006	A1
20060032248	Kates	Feb 2006	A1
20060032379	Kates	Feb 2006	A1
20060036349	Kates	Feb 2006	A1
20060041335	Rossi et al.	Feb 2006	A9
20060097063	Zeevi	May 2006	A1
20060098576	Brownrigg et al.	May 2006	A1
20060117773	Street et al.	Jun 2006	A1
20060130500	Gauthier et al.	Jun 2006	A1
20060138866	Bergmann et al.	Jun 2006	A1
20060196196	Kates	Sep 2006	A1
20060196197	Kates	Sep 2006	A1
20060201168	Kates	Sep 2006	A1
20060222507	Jayanth	Oct 2006	A1
20060259276	Rossi et al.	Nov 2006	A1
20070006124	Ahmed et al.	Jan 2007	A1
20070186569	Street et al.	Aug 2007	A1
20070229305	Bonicatto et al.	Oct 2007	A1
20070239894	Thind et al.	Oct 2007	A1
20080015797	Kates	Jan 2008	A1
20080016888	Kates	Jan 2008	A1
20080051945	Kates	Feb 2008	A1
20080078289	Sergi et al.	Apr 2008	A1
20080114569	Seigel	May 2008	A1
20080216495	Kates	Sep 2008	A1
20080223051	Kates	Sep 2008	A1
20080319688	Kim	Dec 2008	A1
20090068947	Petite	Mar 2009	A1
20090093916	Parsonnet et al.	Apr 2009	A1
20090096605	Petite et al.	Apr 2009	A1
20090140880	Flen et al.	Jun 2009	A1
20090187281	Kates	Jul 2009	A1
20090215424	Petite	Aug 2009	A1
20090296832	Hunt	Dec 2009	A1
20100017465	Brownrigg et al.	Jan 2010	A1
20100039984	Brownrigg	Feb 2010	A1
20100168924	Tessier et al.	Jul 2010	A1
20100179703	Singh et al.	Jul 2010	A1
20100194582	Petite	Aug 2010	A1
20100250054	Petite	Sep 2010	A1
20100265909	Petite et al.	Oct 2010	A1
20100312881	Davis et al.	Dec 2010	A1
20110054842	Kates	Mar 2011	A1
20110071960	Singh	Mar 2011	A1
20110121952	Bonicatto et al.	May 2011	A1
20110185895	Freen	Aug 2011	A1
20110212700	Petite	Sep 2011	A1
20110264324	Petite et al.	Oct 2011	A1
20110309953	Petite et al.	Dec 2011	A1
20110310929	Petite et al.	Dec 2011	A1
20110315019	Lyon et al.	Dec 2011	A1
20110320050	Petite et al.	Dec 2011	A1
20120075092	Petite et al.	Mar 2012	A1
20120092154	Petite	Apr 2012	A1
20120125592	Fadell et al.	May 2012	A1
20120260804	Kates	Oct 2012	A1
20120291629	Tylutki et al.	Nov 2012	A1
20120318135	Hoglund et al.	Dec 2012	A1
20120318137	Ragland et al.	Dec 2012	A1
20130287063	Kates	Oct 2013	A1
20140000290	Kates	Jan 2014	A1
20140000291	Kates	Jan 2014	A1
20140000292	Kates	Jan 2014	A1
20140000293	Kates	Jan 2014	A1
20140000294	Kates	Jan 2014	A1
20140012422	Kates	Jan 2014	A1

Foreign Referenced Citations (112)

Number	Date	Country
1147440	May 1983	CA
173493	Nov 1934	CH
1133425	Oct 1996	CN
1297522	May 2001	CN
1356472	Jul 2002	CN
842351	Jun 1952	DE
764179	Apr 1953	DE
1144461	Feb 1963	DE
1403516	Oct 1968	DE
1403467	Oct 1969	DE
3118638	May 1982	DE
3133502	Jun 1982	DE
3422398	Dec 1985	DE
29723145	Apr 1998	DE
0060172	Sep 1982	EP
0085246	Aug 1983	EP
0124603	Nov 1984	EP
0254253	Jan 1988	EP
0346152	Dec 1989	EP
0351272	Jan 1990	EP
0351833	Jan 1990	EP
0355255	Feb 1990	EP
0361394	Apr 1990	EP
0398436	Nov 1990	EP
0410330	Jan 1991	EP
0419857	Apr 1991	EP
0432085	Jun 1991	EP
0453302	Oct 1991	EP
0479421	Apr 1992	EP
0557023	Aug 1993	EP
0579374	Jan 1994	EP
0660213	Jun 1995	EP
0747598	Dec 1996	EP
0877462	Nov 1998	EP
0982497	Mar 2000	EP
1008816	Jun 2000	EP
1087142	Mar 2001	EP
1087184	Mar 2001	EP
1138949	Oct 2001	EP
1139037	Oct 2001	EP
1187021	Mar 2002	EP
1209427	May 2002	EP
1241417	Sep 2002	EP
1245912	Oct 2002	EP
1245913	Oct 2002	EP
1393034	Mar 2004	EP
2472862	Jul 1981	FR
2582430	Nov 1986	FR
2589561	May 1987	FR
2628558	Sep 1989	FR
2660739	Oct 1991	FR
2062919	May 1981	GB
2064818	Jun 1981	GB
2075774	Nov 1981	GB
2116635	Sep 1983	GB
2229295A	Sep 1990	GB
56010639	Feb 1981	JP
59145392	Aug 1984	JP
61046485	Mar 1986	JP
62116844	May 1987	JP
63061783	Mar 1988	JP
63302238	Dec 1988	JP
01014554	Jan 1989	JP
02110242	Apr 1990	JP
02294580	Dec 1990	JP
04080578	Mar 1992	JP
06058273	Mar 1994	JP
08021675	Jan 1996	JP
08087229	Apr 1996	JP
08284842	Oct 1996	JP
2000350490	Dec 2000	JP
2002155868	May 2002	JP
2003018883	Jan 2003	JP
2003176788	Jun 2003	JP
2004316504	Nov 2004	JP
2005188790	Jul 2005	JP
2005241089	Sep 2005	JP
2005345096	Dec 2005	JP
2006046219	Feb 2006	JP
2006046519	Feb 2006	JP
2009002651	Jan 2009	JP
10-1998-0036844	Aug 1998	KR
1020000000261	Jan 2000	KR
1020000025265	May 2000	KR
1020020041977	Jun 2002	KR
20040021281	Mar 2004	KR
8601262	Feb 1986	WO
8703988	Jul 1987	WO
8705097	Aug 1987	WO
8802527	Apr 1988	WO
8806703	Sep 1988	WO
9718636	May 1997	WO
9748161	Dec 1997	WO
9917066	Apr 1999	WO
9961847	Dec 1999	WO
9965681	Dec 1999	WO
0021047	Apr 2000	WO
0051223	Aug 2000	WO
0169147	Sep 2001	WO
0214968	Feb 2002	WO
0249178	Jun 2002	WO
0275227	Sep 2002	WO
02090840	Nov 2002	WO
02090913	Nov 2002	WO
02090914	Nov 2002	WO
03090000	Oct 2003	WO
2004049088	Jun 2004	WO
2005022049	Mar 2005	WO
2005065355	Jul 2005	WO
2005073686	Aug 2005	WO
2005108882	Nov 2005	WO
2006023075	Mar 2006	WO

Non-Patent Literature Citations (363)

Entry
Trane EarthWise™ CenTra Vac™ Water-Cooled Liquid Chillers 165-3950 Tons 50 and 60 Hz; CTV PRC007-EN; Oct. 2002; 56 pages.
K. A. Manske et al.; Evaporative Condenser Control in Industrial Refrigeration Systems; University of Wisconsin—Madison, Mechanical Engineering Department; International Journal of Refrigeration, vol. 24, No. 7; pp. 676-691; 2001, 21 pages.
European Search Report for EP 82306809.3; Apr. 28, 1983; 1 Page.
European Search Report for EP 91 30 3518; Jul. 22, 1991; 1 Page.
Palani, M. et al, Monitoring the Performance of a Residential Central Air Conditioner under Degraded Conditions on a Test Bench, ESL-TR-92105-05, May 1992.
Palani, M. et al, The Effect of Reducted Evaporator Air Flow on the Performance of a Residential Central Air Conditioner, ESL-HH-92-05-04, Energy Systems Laboratory, Mechanical Engineering Department, Texas A&M University, Eighth Symposium on Improving Building System in Hot and Humid Climates, May 13-14, 1992.
Tamarkin, Tom D., “Automatic Meter Reading,” Public Power magazine, vol. 50, No. 5, Sep.-Oct. 1992, http://www.energycite.com/news/amr.html, 6 pages.
European Search Report for EP 93 30 4470; Oct. 26, 1993; 1 Page.
Honeywell, Excel 5000® System, Excel Building Supervisor—Integrated, 74-2034, Copyright © 1994, Rev. 11-94, 12 pages.
UltraSite User's Guide, Computer Process Controls, Apr. 1, 1996.
Honeywell, Excel 50000® System, Excel Building Supervisor, 74-2033-1, Copyright @ 1996, Rev. 6-96, 12 pages.
Texas Instruments, Inc. Mechanical Data for “PT (S-PQFP-G48) Plastic Quad Flatpack,” Revised Dec. 1996, 2 pages.
European Search Report for EP 94 30 3484; Apr. 3, 1997; 1 Page.
International Search Report; International Application No. PCT/IB96/01435; May 23, 1997; 1 Page.
Ultrasite User's Guide RMCC Supplement, Computer Process Controls, Jun. 9, 1997.
Ultrasite User's Guide BCU Supplement, Computer Process Controls, Sep. 4, 1997.
Ultrasite User's Guide BEC Supplement, Computer Process Controls, Oct. 6, 1997.
Watt, James; Development of Empirical Temperature and Humidity-Based Degraded-Condition Indicators for Low-Tonnage Air Conditioners; ESL-TH-97112-03; Dec. 1997.
Low-Cost Multi-Service Home Gateway Creates New Business Opportunities, Coactive Networks, Copyright 1998-1999, 7 pages.
Pin, C. et al., “Predictive Models as Means to Quantify the Interactions of Spoilage Organisms,” International Journal of Food Microbiology, vol. 41, No. 1, 1998, pp. 59-72, XP-002285119.
Building Environmental Control (BEC) Installation and Operation Manual, Computer Process Controls, Jan. 5, 1998, 153 pages.
Building Control Unit (BCU) Installation and Operation Manual, Computer Process Controls, Jan. 28, 1998, 141 pages.
Einstein RX-300 Refrigeration Controller Installation and Operation Manual, Computer Process Controls, Apr. 1, 1998, 329 pages.
European Search Report for EP 96 30 4219; Dec. 1, 1998; 2 Pages.
International Search Report; International Application No. PCT/US98/18710; Jan. 26, 1999; 1 Page.
European Search Report for EP 98 30 3525; May 28, 1999; 2 Pages.
Liao et al., A Correlation of Optimal Heat Rejection Pressures in Transcritical Carbon Dioxide Cycles, Applied Thermal Engineering 20 (2000), Jul. 25, 1999, 831-841.
Refrigeration Monitor and Case Control Installation and Operation Manual, Computer Process Controls, Aug. 12, 1999.
Ultrasite 32 User's Guide, Computer Process Controls, Sep. 28, 1999.
BChydro, “Power Factor” Guides to Energy Management: The GEM Series, Oct. 1999.
European Search Report for EP 99 30 6052; Dec. 28, 1999; 3 Pages.
Translation of claims and Abstract of KR Patent Laying-Open No. 2000-0000261.
Flow & Level Measurement: Mass Flowmeters, http://www.omega.com/literature/transactions/volume4/T9904-10-MASS.html, 2001, 19 pages.
Frequently Asked Questions, http://www.lipaedge.com/faq.asp, Copyright © 2001, 5 pages.
LIPA Launches Free, First-in-Nation Internet-Based Air Conditioner Control Program to Help LIPA and Its Customers Conserve Electricity & Save Money, Apr. 19, 2001, http://www.lipower.org/newscmter/pr/2001/aprill9—01.html, 3 pages.
European Search Report for EP 01 30 7547; Feb. 20, 2002; 1 Page.
European Search Report for Application No. EP 01 30 1752, dated Mar. 26, 2002.
European Search Report for EP 02 25 0266; May 17, 2002; 3 Pages.
Udelhoven, Darrell, “Optimizing Air Conditioning Efficiency TuneUp Optimizing the Condensor Output, Seer, Air, HVAC Industry,” http://www.udarrell.com/air-conditioning-efficiency.html, Jul. 19, 2002, 13 pages.
International Search Report, International Application No. PCT/US02/13456, dated Aug. 22, 2002, 2 Pages.
International Search Report for PCT/US02/13459; ISA/US; date mailed Sep. 19, 2002.
European Search Report for Application No. EP 02 25 1531, dated Sep. 30, 2002.
Office Action regarding U.S. Appl. No. 09/977,552, dated Jan. 14, 2003.
Udelhoven, Darrell, “Air Conditioner EER, SEER Ratings, BTUH Capacity Ratings, & Evaporator Heat Load,” http://www.udarrell.comfair-conditioner-capacity-seer.html, Apr. 3, 2003, 15 pages.
Vandenbrink et al., “Design of a Refrigeration Cycle Evaporator Unit,” Apr. 18, 2003.
Written Opinion regarding PCT/US02/13459, dated Apr. 23, 2003.
Final Office Action regarding U.S. Appl. No. 09/977,552, dated Jun. 18, 2003.
Advanced Utility Metering: Period of Performance, Subcontractor Report, National Renewable Energy Laboratory, Sep. 2003, 59 pages.
International Preliminary Examination Report regarding PCT/US02/13456, dated Sep. 15, 2003.
Texas Instruments, Inc., Product catalog for “TRF690 1 Single-Chip RF Transceiver,” Copyright 2001-2003, Revised Oct. 2003, 27 pages.
Office Action regarding U.S. Appl. No. 10/061,964, dated Oct. 3, 2003.
Udelhoven, Darrell, “Air Conditioning System Sizing for Optimal Efficiency,” http://www.udarrell.com/airconditioning-sizing.html, Oct. 6, 2003, 7 pages.
Response to Rule 312 Communication regarding U.S. Appl. No. 09/977,552, dated Oct. 31, 2003.
Office Action regarding U.S. Appl. No. 09/977,552, dated Dec. 3, 2003.
Reh, F. John, “Cost Benefit Analysis”, http://managementabout.com/cs/money/a/CostBenefit.htm, Dec. 8, 2003.
Jeffus, Larry, “Refrigeration and Air Conditioning: An Introduction to HVAC/R,” Appendix C, pp. 1060-1063, Copyright 2004.
Jeffus, Larry, “Refrigeration and Air Conditioning: An Introduction to HVAC/R,” Section II, Chapter 4, pp. 176-201, Copyright 2004.
Jeffus, Larry, “Refrigeration and Air Conditioning: An Introduction to HVAC/R,” Section II, Chapter 5, pp. 239-245, Copyright 2004.
Jeffus, Larry, “Refrigeration and Air Conditioning: An Introduction to HVAC/R,” Section II, Chapter 6, p. 322, Copyright 2004.
Jeffus, Larry, “Refrigeration and Air Conditioning: An Introduction to HVAC/R,” Section IV, Chapter 9, pp. 494-504, Copyright 2004.
Final Office Action regarding U.S. Appl. No. 10/061,964, dated Mar. 8, 2004.
Final Office Action regarding U.S. Appl. No. 09/977,552, dated Apr. 26, 2004.
Nickles, Donald, “Broadband Communications Over Power Transmission Lines,” A Guest Lecture From the Dr. Shreekanth Mandaynam Engineering Frontiers Lecture Series, May 5, 2004, 21 pages.
Office Action regarding U.S. Appl. No. 10/286,419, dated Jun. 10, 2004.
European Search Report for EP 02 72 9050, Jun. 17, 2004, 2 pages.
Supplementary European Search Report for EP 02 73 1544, Jun. 18, 2004, 2 Pages.
Notice of Allowance regarding U.S. Appl. No. 10/061,964, dated Jul. 19, 2004.
International Search Report, International Application No. PCT/US04/13384; Dated Aug. 1, 2004; 1 Page.
International Search Report for International Application No. PCT/US2008/009618, dated Dec. 8, 2008.
Office Action regarding U.S. Appl. No. 10/940,877, dated Dec. 8, 2008.
Written Opinion of International Searching Authority for International Application No. PCT/US2008/009618, dated Dec. 8, 2008.
Non-Final Office Action regarding U.S. Appl. No. 11/214,179, dated Nov. 5, 2008.
Notice of Allowance dated Nov. 3, 2008 from Related U.S. Appl. No. 11/417,701.
Office Action regarding U.S. Appl. No. 11/337,918, dated Oct. 28, 2008.
Final Office Action regarding U.S. Appl. No. 09/977,552, dated Oct. 22, 2008.
Examiner Interview regarding U.S. Appl. No. 11/256,641, dated Sep. 16, 2008.
Office Action regarding U.S. Appl. No. 111098,575, dated Sep. 9, 2008.
First Office Action issued by the Chinese Patent Office for Application No. 200480015875.3, dated Sep. 5, 2008.
International Search Report from PCT/U52008/060900, Aug. 4, 2008, 6 pages.
Office Action dated Jul. 24, 2008 from Related U.S. Appl. No. 11/417,557.
Office Action dated Jul. 16, 2008 from Related U.S. Appl. No. 11/417,701.
Office Action regarding U.S. Appl. No. 11/098,582, dated Jul. 7, 2008.
Office Action dated Jul. 1, 2008 from Related U.S. Appl. No. 11/927,425.
Office Action regarding U.S. Appl. No. 11/120,166, dated Jun. 5, 2008.
Office Action regarding U.S. Appl. No. 10/940,877, dated Jun. 5, 2008.
First Office Action issued by the Chinese Patent Office on May 30, 2008 regarding Application No. 200580013451.8.
Office Action regarding U.S. Appl. No. 11/256,641, dated Apr. 29, 2008.
Office Action regarding U.S. Appl. No. 11/098,575, dated Mar. 26, 2008.
Examiner Interview Summary regarding U.S. Appl. No. 10/940,877, dated Mar. 25, 2008.
Office Action regarding U.S. Appl. No. 11/337,918, dated Mar. 25, 2008.
Office Action dated Feb. 15, 2008 from Related U.S. Appl. No. 11/417,557.
International Search Report for International Application No. PCT/US07/019563, dated Jan. 15, 2008, 3 Pages.
Written Opinion of the International Searching Authority regarding International Application No. PCT/US2007/019563, dated Jan. 15, 2008.
Office Action regarding U.S. Appl. No. 09/977,552, dated Jan. 11, 2008.
Notice of Allowance dated Dec. 21, 2007 from Related U.S. Appl. No. 11/417,609.
Notice of Allowance dated Dec. 3, 2007 from Related U.S. Appl. No. 11/130,562.
Final Office Action regarding U.S. Appl. No. 10/940,877, dated Nov. 13, 2007.
Notice of Allowance dated Oct. 26, 2007 from Related U.S. Appl. No. 10/916,223.
International Search Report for International Application No. PCT/US2007/016135 dated Oct. 22, 2007.
Office Action regarding U.S. Appl. No. 11/120,166, dated Oct. 2, 2007.
International Search Report and Written Opinion of the International Searching Authority regarding International Application No. PCT/US06/33702, dated Sep. 26, 2007.
International Search Report, Int'l. App. No. PCT/US 06/05917, dated Sep. 26, 2007.
Written Opinion of the International Searching Authority, Int'l. App. No. PCT/US 06/05917, dated Sep. 26, 2007.
Office Action regarding U.S. Appl. No. 11/098,582, dated Sep. 21, 2007.
Office Action dated Sep. 18, 2007 from Related U.S. Appl. No. 11/130,562.
Office Action dated Aug. 21, 2007 from Related U.S. Appl. No. 11/417,557.
Office Action dated Aug. 17, 2007 from Related U.S. Appl. No. 11/417,609.
Office Action dated Aug. 17, 2007 from Related U.S. Appl. No. 11/417,701.
Non Final Office Action from related U.S. Appl. No. 13/269,188 dated Aug. 14, 2012; 9 pages.
Non Final Office Action from related U.S. Appl. No. 13/269,188 dated Oct. 4, 2013; 11 pages.
Restriction from related U.S. Appl. No. 13/269,188 dated Apr. 9, 2013; 5 pages.
Non Final Office Action from related U.S. Appl. No. 13/269,188 dated Jul. 17, 2014; 10 pages.
Non Final Office Action from related U.S. Appl. No. 13/269,188 dated Feb. 20, 2014; 9 pages.
Final Office Action from related U.S. Appl. No. 13/269,188 dated May 23, 2013; 11 pages.
Non Final Office Action from related U.S. Appl. No. 13/767,479 Oct. 24, 2013; 8 pages.
Final Office Action from related U.S. Appl. No. 13/767,479 dated Mar. 14, 2014; 6 pages.
Non Final Office Action from related U.S. Appl. No. 13/835,742 dated Oct. 7, 2013; 9 pages.
Notice of Allowance from related U.S. Appl. No. 13/835,742 dated Jan. 31, 2014; 7 pages.
Notice of Allowance from related U.S. Appl. No. 13/835,742 dated Jun. 2, 2014; 8 pages.
Non Final Office Action from related U.S. Appl. No. 13/835,621 dated Oct. 30, 2013; 8 pages.
Non Final Office Action from related U.S. Appl. No. 13/835,621 dated Apr. 2, 2014; 11 pages.
Non Final Office Action from related U.S. Appl. No. 13/836,043 dated Oct. 23, 2013; 8 pages.
Final Office Action from related U.S. Appl. No. 13/836,043 dated Mar. 12, 2014; 5 pages.
Non Final Office Action from related U.S. Appl. No. 13/836,043 dated Jul. 11, 2014; 5 pages.
Non Final Office Action from related U.S. Appl. No. 13/836,244 dated Oct. 15, 2013; 11 pages.
Non Final Office Action from related U.S. Appl. No. 13/836,244 dated Feb. 20, 2014; 10 pages.
Notice of Allowance from related U.S. Appl. No. 13/836,244 dated Jul. 2, 2014; 8 pages.
Non Final Office Action from related U.S. Appl. No. 13/836,453 dated Aug. 20, 2013; 8 pages.
Notice of Allowance from related U.S. Appl. No. 13/836,453 dated Jan. 14, 2014; 8 pages.
Notice of Allowance from related U.S. Appl. No. 13/836,453 dated Apr. 21, 2014; 8 pages.
Non Final Office Action from related U.S. Appl. No. 13/767,479 dated Jul. 23, 2014; 9 pages.
Notice of Allowance from related U.S. Appl. No. 13/836,453 Aug. 4, 2014.
Non Final Office Action for related U.S. Appl. No. 13/835,621 dated Aug. 8, 2014.
HVAC Service Assistant, ACRx Efficiency and Capacity Estimating Technology, Field Diagnostics, 2004.
Honeywell, Advanced Portable A/C Diagnostics, The HVAC Service Assistant, 2003.
The Honeywell HVAC Service Assistant, A Tool for Reducing Electrical Power Demand and Energy Consumption, Field Diagnostics, 2003.
Honeywell, HVAC Service Assistant, TRGpro PalmTM OS Interface and HVAC Service Assistant A7075A1000, 2002.
“Air Conditioning Equipment and Diagnostic Primer,” Field Diagnostic Services, Inc., Sep. 9, 2002.
Honeywell, A7075A1000 HVAC Service Assistant, 2001.
International Search Report, International Application No. PCT/US2004/027654, dated Aug. 25, 2004, 4 Pages.
Office Action regarding U.S. Appl. No. 10/675,137, dated Sep. 7, 2004.
Office Action regarding U.S. Appl. No. 09/977,552, dated Oct. 18, 2004.
Notice of Allowance and Notice of Allowability regarding U.S. Appl. No. 10/286,419, dated Dec. 2, 2004.
Office Action regarding U.S. Appl. No. 10/675,137, dated Feb. 4, 2005.
European Search Report regarding Application No. EP02729051, dated Feb. 17, 2005.
Office Action regarding U.S. Appl. No. 10/698,048, dated Mar. 21, 2005.
Office Action dated May 4, 2005 from Related U.S. Appl. No. 10/916,223.
Final Office Action regarding U.S. Appl. No. 09/977,552, dated May 13, 2005.
Office Action regarding U.S. Appl. No. 10/675,137, dated Jun. 29, 2005.
Restriction Requirement regarding U.S. Appl. No. 10/940,877, dated Jul. 25, 2005.
Notice of Allowance for U.S. Appl. No. 10/698,048, dated Sep. 1, 2005.
International Search Report for International Application No. PCT/US2005/11154, dated Oct. 19, 2005.
Office Action dated Oct. 27, 2005 from Related U.S. Appl. No. 10/916,223.
Office Action dated Nov. 9, 2005 from Related U.S. Appl. No. 11/130,562.
Office Action dated Nov. 9, 2005 from Related U.S. Appl. No. 11/130,601.
Office Action dated Nov. 9, 2005 from Related U.S. Appl. No. 11/130,871.
Advisory Action Before the Filing of an Appeal Brief regarding U.S. Appl. No. 09/977,552, dated Nov. 10, 2005.
Office Action regarding U.S. Appl. No. 10/940,877, dated Nov. 14, 2005.
Notice of Allowance and Notice of Allowability regarding U.S. Appl. No. 10/675,137, dated Dec. 16, 2005.
First Examination Communication regarding European Application No. EP02729051.9, dated Dec. 23, 2005.
Office Action dated Jan. 6, 2006 from Related U.S. Appl. No. 11/130,562.
Office Action dated Jan. 6, 2006 from Related U.S. Appl. No. 10/916,222.
Office Action dated Jan. 18, 2006 from Related U.S. Appl. No. 11/130,601.
Examiner's First Report on Australian Patent Application No. 2002259066, dated Mar. 1, 2006.
International Search Report for International Application No. PCT/US04/43859, dated Mar. 2, 2006.
Office Action dated Mar. 30, 2006 from Related U.S. Appl. No. 11/130,569.
Office Action dated Apr. 19, 2006 from Related U.S. Appl. No. 10/916,223.
Second Examination Communication regarding European Application No. EP02729051.9, dated Jul. 3, 2006.
Final Office action regarding U.S. Appl. No. 11/337,918, dated Feb. 4, 2010.
Restriction Requirement regarding U.S. Appl. No. 11/214,179, dated Feb. 2, 2010.
Office Action regarding U.S. Appl. No. 11/497,644, dated Jan. 29, 2010.
Non-Final Office Action for U.S. Appl. No. 11/098,575 dated Jan. 27, 2010.
First Office Action issued by the Chinese Patent Office regarding Application No. 200780030810.X dated Dec. 25, 2009.
Examiner's Answer regarding U.S. Appl. No. 09/977,552, dated Dec. 17, 2009.
Examiner-Initiated Interview Summary regarding U.S. Appl. No. 11/214,179, dated Dec. 11, 2009.
Supplementary European Search Report regarding Application No. PCT/US2006/005917, dated Nov. 23, 2009.
Advisory Action Before the Filing of an Appeal Brief regarding U.S. Appl. No. 11/098,575, dated Nov. 16, 2009.
Second Official Report regarding Australian Patent Application No. 2007214381, dated Oct. 30, 2009.
Examination Report received from Australian Government IP Australia dated Oct. 29, 2009 regarding patent application No. 2008202088.
Office Action for U.S. Appl. No. 11/497,579, dated Oct. 27, 2009.
Advisory Action Before the Filing of an Appeal Brief regarding U.S. Appl. No. 11/098,575, dated Sep. 28, 2009.
Office Action regarding U.S. Appl. No. 11/394,380, dated Sep. 25, 2009.
Notice of Allowance regarding U.S. Appl. No. 10/940,877, dated Sep. 4, 2009.
Advisory Action regarding U.S. Appl. No. 11/214,179, dated Aug. 28, 2009.
Office Action regarding U.S. Appl. No. 11/337,918, dated Aug. 17, 2009.
Notice of Panel Decision from Pre-Appeal Brief Review regarding U.S. Appl. No. 09/977,552, dated Aug. 4, 2009.
Office Action regarding U.S. Appl. No. 11/098,582, dated Aug. 4, 2009.
Office Action regarding U.S. Appl. No. 11/120,166, dated Jul. 20, 2009.
Office Action regarding U.S. Appl. No. 11/098,575, dated Jul. 13, 2009.
Office Action for U.S. Appl. No. 11/497,644, dated Jul. 10, 2009.
Second Office Action received from the Chinese Patent Office dated Jun. 26, 2009 regarding Application No. 2004800114631, translated by CCPIT Patent and Trademark Law Office.
Office Action dated Jun. 22, 2009 from Related U.S. Appl. No. 12/050,821.
Office Action dated Jun. 19, 2009 from Related U.S. Appl. No. 11/866,295.
Second Office action issued by the Chinese Patent Office dated Jun. 19, 2009 regarding Application No. 200510005907.8, translation provided by CCPIT Patent and Trademark Law Office.
Third Office Action issued by the Chinese Patent Office on Jun. 19, 2009 regarding Application No. 200580013451.8, translated by CCPIT Patent and Trademark Law Office.
Office Action dated Jun. 17, 2009 from Related U.S. Appl. No. 12/033,765.
Final Office Action regarding U.S. Appl. No. 11/214,179, dated May 29, 2009.
Notice of Allowance and Fees Due and Notice of Allowability regarding U.S. Appl. No. 11/256,641, dated May 19, 2009.
Office Action dated May 6, 2009 from Related U.S. Appl. No. 11/830,729.
Final Office Action regarding U.S. Appl. No. 10/940,877, dated Apr. 27, 2009.
International Search Report for International Application No. PCT/US2008/012364 dated Mar. 13, 2009.
Written Opinion of the International Searching Authority for International Application No. PCT/US2008/012364 dated Mar. 12, 2009.
International Preliminary Report on Patentability regarding International Application No. PCT/US2007/019563 dated Mar. 10, 2009.
Second Office Action issued by the Chinese Patent Office on Mar. 6, 2009 regarding Application No. 200580013451.8.
Second Office Action issued by the Chinese Patent Office for Application No. 200480015875.3, dated Feb. 27, 2009.
Notice of Allowance and Fees Due and Notice of Allowability regarding U.S. Appl. No. 11/098,582, dated Feb. 24, 2009.
Office Action dated Feb. 13, 2009 from Related U.S. Appl. No. 12/033,765.
Office Action dated Feb. 13, 2009 from Related U.S. Appl. No. 12/050,821.
International Search Report for International Application No. PCT/US2008/012362, dated Feb. 12, 2009.
Office Action dated Feb. 3, 2009 from Related U.S. Appl. No. 11/866,295.
Final Office Action regarding U.S. Appl. No. 11/256,641, dated Feb. 2, 2009.
Interview Summary regarding U.S. Appl. No. 11/214,179, dated Jan. 30, 2009.
Office Action regarding U.S. Appl. No. 11/098,575, dated Jan. 29, 2009.
Office Action for U.S. Appl. No. 11/394,380, dated Jan. 6, 2009.
Office Action for U.S. Appl. No. 11/497,644, dated Dec. 19, 2008.
Office Action regarding U.S. Appl. No. 11/120,166, dated Dec. 15, 2008.
First Official Report regarding Australian Patent Application No. 2007214381, dated Dec. 12, 2008.
Examiner Interview Summary regarding U.S. Appl. No. 10/940,877, dated Dec. 8, 2008.
Office Action regarding U.S. Appl. No. 12/261,643, dated Feb. 15, 2012.
Non-Final Office Action in U.S. Appl. No. 12/685,375, mailed Jan. 19, 2012.
Examiner's First Report on Australian Patent Application No. 2007292917 dated Jan. 10, 2012.
Notice of Allowance regarding U.S. Appl. No. 12/261,677, dated Dec. 15, 2011.
Fourth Office Action from the State Intellectual Property Office of People's Republic of China regarding Chinese Patent Application No. 200510005907.8, dated Dec. 8, 2011. Translation provided by Unitalen Attorneys at Law.
Notice of Allowance and Fees Due, Interview Summary and Notice of Allowability regarding U.S. Appl. No. 11/214,179, dated Nov. 23, 2011.
Office Action regarding U.S. Appl. No. 12/261,643, dated Nov. 2, 2011.
Non-Final Office Action for U.S. Appl. No. 12/054,011, dated Oct. 20, 2011.
Third Office Action regarding Chinese Application No. 2005100059078 from the State Intellectual Property Office of People's Republic of China, dated Aug. 24, 2011. Translation provided by Unitalen Attorneys at Law.
Office Action regarding 12/261,677, dated Aug. 4, 2011.
Final Office Action regarding U.S. Appl. No. 11/214,179, dated Jul. 21, 2011.
Final Office Action regarding U.S. Appl. No. 12/261,643, dated Jul. 7, 2011.
Final Office Action for U.S. Appl. No. 12/054,011, dated Jun. 30, 2011.
International Search Report regarding Application No. PCT/US2010/056315, mailed Jun. 28, 2011.
Communication from European Patent Office concerning Substantive Examination regarding European Patent Application No. 06790063.9, dated Jun. 6, 2011.
First Office Action regarding Chinese Application No. 200880106319.5, dated May 25, 2011. English translation provided by Unitalen Attorneys at Law.
Notice of Allowance regarding U.S. Appl. No. 12/685,424, dated Apr. 25, 2011.
Non-Final Office Action mailed Mar. 3, 2011 for U.S. Appl. No. 12/054,011.
Final Office Action regarding U.S. Appl. No. 11/337,918, dated Feb. 17, 2011.
Examiner's First Report on Australian Patent Application No. 2008319275, dated Jan. 31, 2011.
Non-Final Office Action regarding U.S. Appl. No. 12/261,643, dated Jan. 27, 2011.
Second Office Action regarding Chinese Patent Application No. 200890100287.3, dated Jan. 27, 2011. English translation provided by Unitalen Attorneys at Law.
Non-Final Office Action regarding U.S. Appl. No. 11/214,179, dated Jan. 24, 2011.
Official Action regarding Australian Patent Application No. 2008325240, dated Jan. 19, 2011.
First Office Action regarding Chinese Patent Application No. 201010117657.8, dated Dec. 29, 2010. English translation provided by Unitalen Attorneys at Law.
International Search Report regarding Application No. PCT/US2010/036601, mailed Dec. 29, 2010.
Written Opinion of the International Searching Authority regarding Application No. PCT/US2010/036601, mailed Dec. 29, 2010.
Final Office Action regarding U.S. Appl. No. 11/497,644, dated Dec. 22, 2010.
Final Office Action mailed Dec. 7, 2010 for U.S. Appl. No. 12/054,011.
First Office Action regarding Chinese Patent Application No. 200780032977.X, dated Sep. 27, 2010. English translation provided by Unitalen Attorneys at Law.
Notice of Allowance and Fees Due and Notice of Allowability regarding U.S. Appl. No. 11/098,582, dated Sep. 24, 2010.
Office Action regarding U.S. Appl. No. 11/776,879, dated Sep. 17, 2010.
Non-Final Office Action mailed Aug. 13, 2010 for U.S. Appl. No. 12/054,011.
Office Action regarding U.S. Appl. No. 11/850,846, dated Aug. 13, 2010.
Second Office Action regarding Chinese Patent Application No. 200780030810X, dated Aug. 4, 2010. English translation provided by Unitalen Attorneys at Law.
Examiner Interview Summary regarding U.S. Appl. No. 11/394,380, dated Jul. 29, 2010.
Interview Summary regarding U.S. Appl. No. 11/497,579, dated Jul. 15, 2010.
First Office Action from the State Intellectual Property Office of the People's Republic of China regarding Chinese Patent Application No. 200890100287.3, issued Oct. 25, 2010. Translation provided by Unitalen Attorneys at Law.
Final Office Action regarding U.S. Appl. No. 11/098,575, dated Jun. 17, 2010.
Supplementary European Search Report regarding European Application No. EP06790063, dated Jun. 15, 2010.
Office Action regarding U.S. Appl. No. 11/497,644, dated Jun. 14, 2010.
Non-Final Office Action regarding U.S. Appl. No. 11/214,179, dated Jun. 8, 2010.
Final Office Action regarding U.S. Appl. No. 11/497,579, dated May 14, 2010.
International Preliminary Report on Patentability for International Application No. PCT/US2008/012362, dated May 4, 2010.
International Preliminary Report on Patentability for International Application No. PCT/US2008/012364, dated May 4, 2010.
Interview Summary regarding U.S. Appl. No. 11/497,644, dated May 4, 2010.
Interview Summary regarding U.S. Appl. No. 11/098,582, dated Apr. 27, 2010.
International Preliminary Report on Patentability for International Application No. PCT/US2008/009618, dated Mar. 24, 2010.
Office Action regarding U.S. Appl. No. 11/098,582 dated Mar. 3, 2010.
Office Action regarding U.S. Appl. No. 11/120,166, dated Feb. 17, 2010.
International Search Report for PCT/US2013/061389, Jan. 22, 2014, 7 pages.
Final Office Action regarding U.S. Appl. No. 11/850,846, mailed Jan. 17, 2014.
Non-Final Office Action regarding U.S. Appl. No. 13/770,479, dated Jan. 16, 2014.
European Search Report regarding Application No. 07811712.4-1608/2069638 PCT/US2007019563, dated Jan. 7, 2014.
Fourth Office Action regarding Chinese Patent Application No. 200910211779.0, dated Jan. 6, 2014. English translation provided by Unitalen Attorneys at Law.
Final Office Action regarding U.S. Appl. No. 13/784,890, mailed Dec. 30, 2013.
Office Action regarding U.S. Appl. No. 13/737,566, dated Dec. 20, 2013.
Non-Final Office Action regarding U.S. Appl. No. 13/932,611, mailed Nov. 25, 2013.
Advisory Action regarding U.S. Appl. No. 12/261,643, dated Nov. 22, 2013.
First Office Action regarding Chinese Patent Application No. 201110349785.X, dated Nov. 21, 2013, and Search Report. English translation provided by Unitalen Attorneys at Law.
Final Office Action regarding U.S. Appl. No. 13/770,123, dated Nov. 15, 2013.
Notice of Grounds for Refusal regarding Korean Patent Application No. 10-2009-7000850, mailed Oct. 4, 2013. English translation provided by Y.S. Chang & Associates.
First Examination Report regarding Australian Patent Application No. 2012241185, dated Sep. 27, 2013.
Final Office Action regarding U.S. Appl. No. 12/261,643, dated Sep. 16, 2013.
Third Office Action regarding Chinese Patent Application No. 200910211779.0, dated Sep. 4, 2013. English translation provided by Unitalen Attorneys at Law.
First Office Action regarding Canadian Patent Application No. 2,777,349, dated Jul. 19, 2013.
Non-Final Office Action regarding U.S. Appl. No. 13/770,123, dated Jul. 3, 2013.
Non-Final Office Action in U.S. Appl. No. 13/784,890, mailed Jun. 11, 2013.
Non-Final Office Action in U.S. Appl. No. 11/850,846, mailed May 24, 2013.
International Search Report regarding Application No. PCT/US2013/021161, mailed May 8, 2013.
Written Opinion of the International Searching Authority regarding Application No. PCT/US2013/021161, mailed May 8, 2013.
Non-Final Office Action regarding U.S. Appl. No. 12/261,643, dated Mar. 12, 2013.
Second Office Action regarding Chinese Patent Application No. 200910211779.0, dated Feb. 4, 2013. English translation provided by Unitalen Attorneys at Law.
First Examination Report regarding Australian Patent Application No. 2010319488, dated Jan. 10, 2013.
Non-Final Office Action regarding U.S. Appl. No. 12/943,626, dated Dec. 20, 2012.
Record of Oral Hearing regarding U.S. Appl. No. 09/977,552, dated Nov. 29, 2012.
Non-Final Office Action for U.S. Appl. No. 13/030,549, dated Nov. 5, 2012.
Notification of First Office Action from the State Intellectual Property Office of People's Republic of China regarding Chinese Patent Application No. 200880122964.6, dated Nov. 5, 2012. Translation provided by Unitalen Attorneys at Law.
European Search Report for Application No. EP 12 182 243.1, dated Oct. 29, 2012.
Extended European Search Report regarding Application No. 12182243.1-2311, dated Oct. 29, 2012.
Notice of Allowance and Fee(s) Due regarding U.S. Appl. No. 12/789,562, dated Oct. 26, 2012.
Non-Final Office Action regarding U.S. Appl. No. 12/955,355, dated Sep. 11, 2012.
International Search Report for PCT/US2012/026973, Sep. 3, 2012, 5 pages.
European Search Report regarding Application No. 04022784.5-2315/1500821, dated Aug. 14, 2012,.
Final Office Action for U.S. Appl. No. 11/850,846, mailed Aug. 13, 2012.
Non-Final Office Action for U.S. Appl. No. 12/685,375, mailed Aug. 6, 2012.
Notice of Allowance regarding U.S. Appl. No. 13/303,286, dated Jul. 19, 2012.
Patent Examination Report No. 3 regarding Australian Patent Application No. 2008325240, dated Jul. 19, 2012.
Notice of Allowance regarding U.S. Appl. No. 11/776,879, dated Jul. 9, 2012.
Final Office Action regarding U.S. Appl. No. 12/261,643, dated Jun. 27, 2012.
Non-Final Office Action regarding U.S. Appl. No. 13/435,543, dated Jun. 21, 2012.
International Preliminary Report on Patentability regarding Application No. PCT/US2010/056315, mailed May 24, 2012.
Non-Final Office Action regarding U.S. Appl. No. 13/176,021, dated May 8, 2012.
First Office Action regarding Chinese Patent Application No. 200910211779.0, dated May 3, 2012. English translation provided by Unitalen Attorneys at Law.
Non-Final office Action regarding U.S. Appl. No. 11/850,846, dated Apr. 24, 2012.
Non-Final Office Action for U.S. Appl. No. 12/054,011, dated Apr. 10, 2012.
Office Action regarding U.S. Appl. No. 13/303,286, dated Mar. 26, 2012.
Non-Final Office Action for U.S. Appl. No. 11/776,879, dated Mar. 16, 2012.
Issue Notification regarding U.S. Appl. No. 11/214,179, dated Mar. 14, 2012.
Examiner's Report No. 2 regarding Australian Patent Application No. 2008325240, dated Mar. 5, 2012.
Office Action dated Jul. 11, 2006 from Related U.S. Appl. No. 11/130,562.
Office Action dated Jul. 11, 2006 from Related U.S. Appl. No. 10/916,222.
Office Action regarding U.S. Appl. No. 091977,552, dated Jul. 12, 2006.
Notice of Allowance dated Jul. 13, 2006 from Related U.S. Appl. No. 11/130,601.
Office Action dated Jul. 27, 2006 from Related U.S. Appl. No. 11/130,871.
Office Action regarding U.S. Appl. No. 11/120,166, dated Oct. 2, 2006.
Office Action dated Nov. 14, 2006 from Related U.S. Appl. No. 11/130,569.
Office Action dated Nov. 16, 2006 from Related U.S. Appl. No. 10/916,223.
Office Action dated Jan. 23, 2007 from Related U.S. Appl. No. 10/916,222.
Election/Restriction Requirement regarding U.S. Appl. No. 09/977,552, dated Jan. 25, 2007.
Office Action dated Feb. 1, 2007 from Related Application No. 11/130,562.
First Office Action received from the Chinese Patent Office dated Feb. 2, 2007 regarding Application No. 200480011463.2, translated by CCPIT Patent and Trademark Law Office.
Notice of Allowance dated Feb. 12, 2007 from Related U.S. Appl. No. 11/130,871.
International Search Report, International Application No. PCT/US2006/040964, dated Feb. 15, 2007, 2 Pages.
Examiner Interview Summary regarding U.S. Appl. No. 10/940,877, dated Mar. 2, 2007.
Office Action regarding U.S. Appl. No. 11/120,166, dated Apr. 12, 2007.
Office Action Communication regarding U.S. Appl. No. 09/977,552, dated Apr. 18, 2007.
Notice of Allowance dated May 2, 2007 from Related Application No. 11/130,569.
Office Action regarding U.S. Appl. No. 10/940,877, dated May 21, 2007.
Notice of Allowance dated May 29, 2007 from Related U.S. Appl. No. 11/130,569.
First Office Action from the Patent Office of the People's Republic of China dated Jun. 8, 2007, Application No. 200480027753.6 and Translation provided by CCPIT.
Notice of Allowance dated Jun. 11, 2007 from Related U.S. Appl. No. 10/916,222.
Office Action dated Jun. 27, 2007 from Related U.S. Appl. No. 11/417,557.
First Office Action from the Patent Office of the People's Republic of China regarding Application No. 200510005907.8, dated Jun. 29, 2007.
Office Action dated Jul. 11, 2007 from Related U.S. Appl. No. 11/417,609.
Office Action dated Jul. 11, 2007 from Related U.S. Appl. No. 11/417,701.
European Search Report for Application No. EP 04 81 5853, dated Jul. 17, 2007.
European Search Report for Application No. EP 06 02 6263, dated Jul. 17, 2007.
Final Office Action regarding U.S. Appl. No. 09/977,552, dated Jul. 23, 2007.
Notice of Allowance dated Jul. 25, 2007 from Related U.S. Appl. No. 10/916,223.
Office Action dated Jan. 18, 2006 from Related U.S. Appl. No. 11/130,871.
Non Final Office Action from related U.S. Appl. No. 13/369,067 dated Jan. 16, 2014; 16 pages.
Final Office Action from related U.S. Appl. No. 13/369,067 dated May 1, 2014; 19 pages.
Final Office Action regarding U.S. Appl. No. 13/932,611, mailed May 28, 2014.
Supplementary European Search Report regarding Application No. EP 07 81 1712, dated Jan. 7, 2014.
Non-Final Office Action regarding U.S. Appl. No. 13/770,123, dated Jun. 11, 2014.
Notice of Allowance and Fees Due regarding U.S. Appl. No. 13/737,566, dated Jun. 18, 2014.
Notice of Allowance and Fees Due regarding U.S. Appl. No. 12/943,626, dated Jun. 19, 2014.
Notice of Allowance and Fees Due regarding U.S. Appl. No. 12/261,643, dated Jun. 23, 2014.
Extended European Search Report regarding Application No. 07796879.0-1602/2041501 PCT/US2007016135, dated Jul. 14, 2014.
Interview Summary from related U.S. Appl. No. 12/054,011 dated Jan. 30, 2012.
Written Opinion from related PCT Application No. PCT/US2014/028074 mailed Jun. 19, 2014.
Advisory Action from related U.S. Appl. No. 13/784,890 dated Mar. 14, 2014.
International Search Report from related PCT Application No. PCT/US2014/028074 mailed Jun. 19, 2014.
Examiner's Answer from related U.S. Appl. No. 13/784,890 dated Jul. 3, 2014.

Related Publications (1)

	Number	Date	Country
	20140000292 A1	Jan 2014	US

Continuations (4)

	Number	Date	Country
Parent	13269188	Oct 2011	US
Child	13835810		US
Parent	11779203	Jul 2007	US
Child	13269188		US
Parent	11130569	May 2005	US
Child	11779203		US
Parent	10916222	Aug 2004	US
Child	11130569		US

Method and apparatus for monitoring a refrigeration-cycle system

Information

Patent Number

Date Filed

Date Issued

Inventors

Original Assignees

Examiners

Agents

CPC

US Classifications

Field of Search

US

International Classifications

Disclaimer

Abstract