Patent Application
20070061996
The present invention relates to heat exchanger devices in general, and in particular to control mechanisms for heat exchanger devices operated in combination with a carpet cleaning apparatus having exhaust gases of an internal combustion engine and a vacuum pump as inputs to the heat exchanger.
Currently, in situ cleaning of carpets and upholstery utilizes equipment for heating cleaning liquid that is conveyed under pressure to and sprayed onto the surface to be cleaned and then vacuum removed from the surface with the soil. This equipment is usually mounted in a panel truck, or van, for ease of transport and often includes the transport's internal combustion engine for driving the cleaning liquid and vacuum pumps.
As disclosed in co-pending U.S. patent application Ser. No. 10/329,227 filed Dec. 23, 2002 in the names of Wayne E. Boone, et al. for “D
Of the many industrial substrate cleaning systems available, a major segment are self-contained having an own power plant, heat source, vacuum source, chemical delivery system, and water dispersion and extraction capabilities. These are commonly referred to as “slide-in” systems and install permanently in cargo vans, trailers and other commercial vehicles, but can also be mounted on portable, wheeled carts. Slide-in systems comprise a series of components designed and integrated into a package with an overall goal of performance, economy, reliability, safety, useful life, serviceability, and sized to fit inside various commercial vehicles.
Typically, the components of a conventional slide-in carpet cleaner system 1 are structured around a frame or structural platform 2 onto which the majority of the components are mounted. The slide-in 1 typically includes a drive system 3 mounted on the platform 2 and having a power plant 4 coupled to receive fuel from an appropriate supply, a vacuum pump 5 that is the source of vacuum for removing gray water or soiled cleaning solution from the cleaned substrate, either carpet or other flooring, and an interface assembly 6 for transmitting power from the power plant 4 to the vacuum pump 5. The power plant 4 may be, for example, any steam or electric motor, but is usually an internal combustion motor, such as a gasoline, diesel, alcohol, propane, or otherwise powered internal combustion engine. A standard truck battery 7 is provided as a source of electric energy for starting the engine. An intake hose 8 is coupled to a source of fresh water, and a water pump or air compressor 9 driven by the power plant via V-belt (shown), direct drive, or otherwise for pressurizing the fresh water. One or more heat exchangers and associated plumbing 10 are coupled for receiving the pressurized fresh water and heating it. A recovery tank 11 is provided wherein gray water or soiled cleaning solution is stored after removal from the cleaned surface. A high pressure solution hose 12 is provided for delivering pressurized, hot water/chemical cleaning solution from the machine via a wand or cleaning tool 14 to the substrate to be cleaned, usually a carpet or hard flooring, and a chemical container 13 or other chemical system is coupled for delivering a stream of cleaning chemical additives into the hot water, typically as it enters the high-pressure solution hose 12. The wand or cleaning tool 14 is coupled to the high pressure solution hose 12 for receiving and dispersing the pressurized hot water/chemical cleaning solution to the carpet. The wand or cleaning tool 14 is the only “portable” part of truck-mount slide-in professional carpet cleaning systems 1 in that it is removed from the vehicle and carried to the carpet or other substrate to be cleaned, and it is the only equipment that makes physical contact with the carpet to be cleaned. A vacuum hose 15 is coupled to the wand or cleaning tool 14 for recovering the soiled water-based chemical cleaning solution from the cleaned surface via the wand or cleaning tool and delivering it to the recovery tank. Valves 16 and 17 control coupling of the hot water/chemical cleaning solution and recovery vacuum, respectively, to the wand or cleaning tool 14. The control valves 16, 17 may be either separate control valves (shown) or combined in a single control valve.
The slide-in or portable system 1 operates by delivering fresh water to an inlet to the system, utilizing either a standard garden hose or a fresh-water container. The system 1 adds energy to the fresh water, i.e., pressurizes it, by means of the pump or air compressor 9. The fresh water is pushed throughout the heat exchanger apparatus and associated plumbing 10 using pressure provided by either the pump or air compressor 9. The heat exchangers 10 gain their heat by thermal energy rejected from the power plant 4, e.g., from hot exhaust gases, coolant water used on certain engines, or another known means. On demand from the wand or cleaning tool 14, the heated fresh water is mixed with chemicals from the container 13 as the hot water is exiting the machine and entering the high-pressure hose 12. The hot water travels typically, but not limited to, between 50 feet to 300 feet to the wand or cleaning tool 14. The operator delivers the hot solution via the wand or cleaning tool 14 to the carpet or other surface to be cleaned and almost immediately extracts it along with soil that has been emulsified by thermal energy or dissolved and divided by chemical energy. The extracted, soiled water or cleaning solution is drawn via the vacuum hose 15 into the recovery tank 11 for eventual disposal as gray water.
It has been suggested that instead of using a separate heater for heating the cleaning liquid that waste heat from the internal combustion engine be used for that purpose. U.S. Pat. No. 4,593,753, granted Jun. 10, 1986 to P. J. McConnell for “E
In all of the aforementioned systems in which the cleaning liquid is directed in heat exchange relationship with the exhaust gases of the internal combustion engine there is a danger that the cleaning liquid could become overheated. To avoid damage to surfaces to be cleaned the temperature of the cleaning liquid, as a general rule, should not exceed 250 degrees F. Internal combustion engine exhaust gases can reach temperatures as high as 1650 degrees F. With the engine running and a low flow rate for the cleaning liquid the latter can rapidly be heated to an undesirably high temperature in the exhaust gas heat exchange.
One attempt at a solution for controlling the cleaning liquid temperature is disclosed by U.S. Pat. No. 3,594,849 granted Jul. 27, 1971 to C. L. Coshow for “C
More typically, a thermostatically controlled dump valve is incorporated for dumping the overheated cleaning liquid before it can reach the surface to be cleaned. One such dumping arrangement is described hereinafter and in the aforementioned U.S. Pat. No. 4,940,082 granted Jul. 10, 1990 to James R. Roden for “C
U.S. Pat. No. 4,991,254 granted Feb. 12, 1991 to Roden, et al. for “C
However, in some applications it would be desirable to avoid wasting the unused cleaning liquid by dumping it when it gets too hot.
The present invention is a heat exchanger for use with a carpet cleaning system having combined relatively hotter exhaust gases of an internal combustion engine and other hot exhaust gases expelled from a vacuum pump at a temperature relatively cooler than the engine exhaust gases as a single input to the heat exchanger. The present invention overcomes limitations of prior art devices by providing a heat exchanger control system that permits constant control of a stream of cleaning fluid both while the cleaning fluid is flowing through the heat exchanger and while the cleaning fluid is stagnant within the heat exchanger. Prior art devices required a constant flow of the cleaning fluid to avoid a potential overheat condition of the portion of cleaning fluid stagnant in the heat exchanger. Rather than permit interruptions in the constant flow of cleaning fluid through the heat exchanger, prior art devices re-circulated or simply dumped the fluid which permitted the flow through the heat exchanger to remain constant. In contrast, heat exchanger of the present invention permits interruptions in the flow of cleaning fluid without overheating the stagnant portion held in the heat exchanger.
According to one aspect of the invention, the invention is a liquid heating system having a first pipe that is structured to convey hot gases from an internal combustion engine as a first source of relatively higher temperature gases and a second pipe that is structured to convey hot gases from a vacuum pump as a second source of relatively lower temperature gases, with both the first and second pipes communicating with a gas mixing chamber that is structured for mixing relatively higher and lower temperature hot gases received therein. A heat exchange chamber is provided having an inlet that is coupled to the gas mixing chamber for receiving hot gases thereinto and having a heat exchange mechanism that is structured for passing pressurized liquid therethrough in thermal transfer communication with the hot gases, the heat exchange chamber is structured for exhausting the hot gases downstream of the heat exchange mechanism. A diverter is coupled between the first pipe and the gas mixing chamber, the diverter being structured for communicating between the first pipe and the gas mixing chamber as a function of a temperature of the mixed hot gases measured downstream of the inlet of the heat exchange chamber.
According to another aspect of the invention, the diverter includes a diverter valve that is operable between a first outlet that communicates with the gas mixing chamber and a second outlet that is inhibited from communication with the gas mixing chamber.
According to another aspect of the invention, the diverter valve is further responsive to a control signal generated by a control circuit as a function of the temperature of the mixed hot gases measured downstream of the inlet of the heat exchange chamber.
According to another aspect of the invention, the liquid heating system of the invention also includes a temperature sensor that is positioned downstream of the inlet of the heat exchange chamber. Optionally, the temperature sensor is positioned adjacent to an exhaust outlet of the heat exchange chamber.
According to another aspect of the invention, the liquid heating system of the invention is included in an industrial carpet cleaner system having a power plant of a type that produces hot exhaust gases and having an exhaust outlet that is coupled to the first pipe; a vacuum generator of a type that produces hot exhaust gases and having an exhaust outlet that is coupled to the second pipe; and a pump or other liquid pressurizing device that is coupled to an inlet of the heat exchange mechanism for forcing liquid to be heated through the heat exchange mechanism. According to another aspect of the invention, the industrial carpet cleaner system also includes a fluid dispersal and retrieval device, commonly referred to as a spray wand or cleaning head, that is coupled by a high pressure hose to an outlet of the heat exchange mechanism for receiving the heated liquid, and by a vacuum hose to the vacuum pump for retrieval of the spent cleaning fluid. Optionally, a waste recovery vessel is coupled to one end of the vacuum hose between the fluid dispersal device and the vacuum pump for storing gray water or soiled cleaning solution is after removal from the cleaned surface.
According to another aspect of the invention, a method is provided for heating a liquid, the method including conveying liquid to be heated to a heat exchange mechanism positioned within a heat exchange chamber; conveying hot gases from an internal combustion engine as a first source of relatively higher temperature hot gases to a gas mixing chamber; conveying hot gases from vacuum pump as a second source of relatively lower temperature gases to a gas mixing chamber; conveying mixed hot gases from a the gas mixing chamber into the heat exchange chamber and into thermal transfer communication with the heat exchange mechanism for transferring heat from the gases to the liquid to be heated; and intermittently temporarily diverting substantially all or at least a portion of the relatively higher temperature hot gases away from the gas mixing chamber as a function of measuring a temperature of the gases after transferring heat from the gases to the liquid to be heated.
According to another aspect of the method of the invention, diverting at least a portion of the relatively higher temperature hot gases away from the gas mixing chamber includes alternately diverting substantially all or at least a portion of the relatively higher temperature hot gases from the internal combustion engine away from the gas mixing chamber, and directing substantially all or at least a portion of the relatively higher temperature hot gases into the gas mixing chamber both as a function of measuring a temperature of the gases after transferring heat from the gases to the liquid to be heated.
According to another aspect of the method of the invention, the method also includes controlling the alternately diverting and directing of the relatively higher temperature hot gases away from or into the gas mixing chamber for maintaining the temperature of the gases after transferring heat from the gases to the liquid to be heated within a selected range of temperatures.
According to another aspect of the method of the invention, alternately diverting and directing the relatively higher temperature hot gases away from or into the gas mixing chamber optionally includes conveying hot gases from a first source of relatively higher temperature hot gases into a diverter and operating the diverter for alternately diverting and directing at least a portion of the relatively higher temperature hot gases away from or into the gas mixing chamber.
These and other aspects of the invention are detailed herein.
The foregoing aspects and many of the attendant advantages of this invention will become more readily appreciated as the same becomes better understood by reference to the following detailed description, when taken in conjunction with the accompanying drawings, wherein:
In the Figures, like numerals indicate like elements.
The carpet cleaning apparatus 100 includes mechanical structure that is configured for accomplishing tasks of pressurizing and pressurizing the cleaning fluid, and retrieving spent cleaning fluid discharged by the wand 102. For example, the carpet cleaning apparatus 100 includes an internal combustion engine or other conventional power plant 106 of a type that produces hot exhaust gases. The engine or other power plant 106 is coupled by a shaft or belt drive mechanism 108 to drive a water pump or other liquid pressurizing device 110 for pressurizing the cleaning fluid, whereby the pressurizing device 110 operates as source of pressurized cleaning fluid for delivery to the fluid dispersal device or cleaning wand 102. The power plant 106 is also coupled by a shaft or belt drive mechanism 112 to drive a vacuum generator or pump 114 for retrieving the spent cleaning fluid. Such a carpet cleaning apparatuses are generally well known, as disclosed, by example and without limitation, by Studebaker in U.S. Pat. No. 6,243,914, S
The cleaning fluid pressurizing device 110 is coupled by appropriate high-pressure input plumbing 116 for delivering pressurized cleaning fluid, i.e., pressurized water with or without cleaning chemical additives, to the heat exchanger 104 of the carpet cleaning apparatus 100. The heat exchanger 104 receives the pressurized cleaning fluid into an inlet 117 of an internal heat exchange mechanism 118, such as a coil of thermally conductive metal or other thermally conductive material, that is in thermal transfer communication with hot gases within the heat exchanger. The heat exchanger 104 subsequently outputs heated pressurized cleaning fluid through a high-pressure hose 120 coupled to an outlet 119 of the internal heat exchange mechanism 118 and an operator-manipulated delivery control valve 122 to the spray wand or other cleaning fluid dispersal and retrieval device 102 for receiving and dispersing the pressurized hot water/chemical cleaning solution to the carpet, as is generally well-known in the art. The pressurizing device 110 and associated high-pressure input plumbing 116 thus constitute means for conveying cleaning fluid through the heat exchanger 104 to the spray wand 102.
A chemical container 124 or other chemical system is coupled for delivering a stream of cleaning chemical additives into the hot water, typically as it enters the high-pressure solution hose 120. However, the chemical container 124 may be coupled to the high-pressure plumbing 116 for delivering the cleaning chemical additives into the pressurized fresh water before entering the heat exchanger 104.
A waste recovery vessel or tank 126 is provided wherein gray water or soiled cleaning solution is stored after removal from the cleaned surface. Vacuum generator or pump 114 is in communication with an interior 128 of the waste recovery tank 126 through a vacuum line 130 for drawing a vacuum in the recovery tank 126. A fluid inlet 131 receives recovered gray water or soiled cleaning solution into the recovery tank 126, and a drain valve 132 permits later draining of the stored liquid via a drain 133 to a drain pipe 134. A vacuum hose 136 is coupled to the wand or cleaning tool 102 via a vacuum control valve 138 for recovering the soiled water-based chemical cleaning solution from the cleaned surface and delivering it to the inlet 131 of the recovery tank 126. The vacuum control valve 138 is optionally combined with the delivery control valve 122 in a single combination control valve.
The operator delivers the hot solution via the wand or cleaning tool 102 to the carpet or other surface to be cleaned and almost immediately extracts it along with soil that has been emulsified by thermal energy or dissolved and divided by chemical energy. The extracted, soiled water or cleaning solution is drawn via the vacuum hose 136 into the recovery tank 126 for eventual disposal as gray water.
Heat exchanger 104 has as heat source inputs both hot exhaust gases generated by the engine or power plant 106 and other hot exhaust gases generated by the vacuum pump 114. As discussed above, output exhaust gases generated by internal combustion engines can reach temperatures as high as 1000-1200 degrees F. The air expelled from vacuum pump 114 also contains a considerable amount of heat, particularly heat generated by its own compressive action. For example, it is well-known that air may enter vacuum pump at around 120-130 degrees F and exit it at the temperature of around 200 degrees F. The engine or power plant 106 includes an exhaust outlet 139 coupled to an exhaust pipe 140. The vacuum pump 114 includes an exhaust outlet 141 coupled to its own exhaust pipe 142. The hot engine exhaust gases and expelled vacuum pump gases are output through the respective exhaust pipes 140, 142 which both communicate with a gas mixing chamber or mixer 144. The mixer 144 combines and mixes the hot exhaust gases from the engine 106 and vacuum pump 114 and outputs the hot gas mixture via a transfer pipe 146 which is coupled to an inlet duct 147 of the heat exchanger 104. Pressurized cleaning fluid enters the heat exchanger 104 via the high pressure input plumbing 116 and in a known manner absorbs heat from the hot exhaust gases entering from the mixer 144. The heated pressurized cleaning fluid exits the heat exchanger 104 taking a portion of the heat from the exhaust gases with it to the spray wand or other cleaning fluid dispersal device and retrieval 102. The exhaust gases in the heat exchanger are cooled by giving up heat to the cleaning fluid. Thereafter, the cooled exhaust gases exit the heat exchanger 104 via an exhaust outlet 148 coupled to an exhaust pipe 149.
As is known in the art, there is a danger that the cleaning fluid could become overheated in the heat exchange relationship with the exhaust gases of the internal combustion engine. As is also known, the temperature of the cleaning liquid, as a general rule, should not exceed 220 degrees F to avoid damage to surfaces to be cleaned. A direct heat exchange relationship with the exhaust gases of the internal combustion engine can heat the cleaning fluid to an undesirably high temperature. Similarly, it is known in the art that heating the cleaning fluid using engine exhaust gases mixed with hot gases from the vacuum pump still requires the cleaning fluid to run almost continuously to avoid overheating, whereby a thermostatically controlled dump valve is necessary for dumping over heated cleaning fluid into waste tank to maintain its temperature within the desired range when the demand for the cleaning fluid is temporarily suspended.
The present invention overcomes the necessity for dumping over heated cleaning fluid and thereby eliminates the thermostatically controlled dump valve required in prior art systems. An exhaust gas temperature sensor 150 is positioned to measure a temperature of the mixed hot exhaust gases measured downstream of the heat exchanger inlet duct 147 and the heat exchange mechanism 118. For example, the exhaust gas temperature sensor 150 is positioned adjacent to the exhaust outlet 148, either outside or inside the heat exchanger 104. According to one embodiment illustrated in
The exhaust gas temperature sensor 150 is part of a control circuit 152 that is structured to generate and output a control signal 153 as a function of the exhaust gas temperature sensor output signal 151. For example, the control circuit 152 includes a microprocessor that generates the control signal 153 as a function of a changing voltage of the temperature sensor output signal 151. The control circuit 152 is structured to control a diverter 156 in the exhaust pipe 140 leading from the engine 106 to the mixer 144. The diverter 156 is equipped with a diverter valve 158 operable between a HEAT MODE and a DIVERT MODE as a function of the control signal 153 output by the control circuit 152. In the HEAT MODE, the valve 158 of the diverter 156 is operated to open a first path through a first transfer outlet 159 that is coupled to a transfer pipe 160 leading to the gas mixer 144. Accordingly, in the HEAT MODE the operation of the diverter valve 158 causes the relatively higher temperature hot exhaust gases from the engine 106 to be delivered to the gas mixer 144 where they are mixed with the relatively lower temperature hot gases from the vacuum pump 114. The mixed hot gases are then delivered to the heat exchanger 104 via the transfer pipe 146, as discussed above. In the HEAT MODE, operation of the valve 158 of the diverter 156 also closes a second path through a second exhaust outlet 161 that is coupled to a diverter exhaust pipe 162 leading away from the gas mixer 144. Accordingly, in the HEAT MODE the operation of the diverter valve 158 inhibits the hot exhaust gases from being diverted away from the mixer 144 through the diverter exhaust pipe 162.
In the DIVERT MODE, the valve 158 of the diverter 156 is operated to close the first transfer outlet 159 leading to the gas mixer 144, and to simultaneously open the second exhaust outlet 161 which opens the second path through the diverter pipe 162 leading away from the mixer 144 for being exhausted into the surrounding environment instead. Accordingly, in the DIVERT MODE the operation of the diverter valve 158 inhibits the hot exhaust gases from communicating with the mixer 144, and instead diverts the hot exhaust gases away from the mixer 144 and into the diverter exhaust pipe 162. By example and without limitation, the diverter pipe 162 optionally connects with the heat exchanger exhaust pipe 149 sufficiently far downstream of the sensor 150 as to have no effect on its sensing temperature of gases in the heat exchanger exhaust pipe 149. For example, the diverter pipe 162 connects with the heat exchanger exhaust pipe 149 at a “T” coupler 164 before the heat exchanger exhaust pipe 149 continues to the atmosphere.
In operation, the valve of the diverter 156 is controlled by the control circuit 152 as a function of the sensor 150 sensing the exit temperature of the heat exchanger gases, which is a direct measure of the heat lost to from the hot gases in the heat exchanger 104, and is an indirect measure of the heat absorbed by the cleaning fluid passing through the heat exchanger 104. The diverter 156 is operated as a function of the sensor 150 output to controllably reduce or increase the amount of engine exhaust gases channeled to the mixer 144. When the heat exchanger exhaust temperature falls below a minimum as sensed by the sensor, the control circuit 152 causes the valve 158 to divert more hot exhaust gases from the engine 106 to the mixer 144 for raising the temperature of in the heat exchanger 104. When the heat exchanger exhaust temperature rises above a maximum as sensed by the sensor 150, the control circuit 152 causes the valve 158 to divert more hot exhaust gases from the engine 106 into the diverter pipe 162 and away from the mixer 144 for lowering the temperature in the heat exchanger 104. Accordingly, the temperature in the heat exchanger 104 is held substantially steady and the cleaning fluid can lie stagnant in the heat exchanger 104 and remain hot but without overheating because the diverter 156 is controlled so that the heat exchanger is not permitted either to fall below the minimum exhaust temperature, nor to rise above the maximum exhaust temperature, as measured by the sensor 150.
Optionally, the diverter 156 is an “on-off” device wherein the valve 158 is caused to operate at extremes between a first HEAT MODE position 158a that completely opens the input path to the mixer 144 through the transfer pipe 160, and simultaneously substantially closes off the exhaust path through the diverter exhaust pipe 162 to the atmosphere, and a second DIVERT MODE position 158b that substantially closes off the input path to the mixer 144 through the transfer pipe 160, and simultaneously completely opens the path through the diverter exhaust pipe 162 to the atmosphere. Alternatively, the diverter 156 is a continuous or graduated device wherein the valve 158 is operable continuously or incrementally between the extreme first HEAT MODE position 158a and the second DIVERT MODE position 158b. Rather, the valve 158 is of a type that is structured to operate at one or more positions wherein each of the paths to the mixer 144 through the transfer pipe 160 and the exhaust path through diverter exhaust pipe 162 are simultaneously open to the same or different degrees for passing a portion of the engine exhaust gases through to the mixer 144, and simultaneously exhausting a larger or smaller portion of the engine exhaust gases to the atmosphere. The diverter valve 158 is thus maintained in a substantially constant position while the cleaning fluid is moving through the heat exchanger 104 during operation of the cleaning wand 102, rather than fluctuating between the extreme first HEAT MODE 158a and second DIVERT MODE positions 158b.
Of course, the diverter valve 158 optionally includes first and second valves with one of the valves (indicated by the designator 158a) opening and closing the second exhaust outlet 161 that is coupled to a diverter exhaust pipe 162 leading away from the gas mixer 144, and another one of the valves (indicated by the designator 158b) opening and closing the first transfer outlet 159 that is coupled to a mixer input pipe 160 leading to the gas mixer 144. The first and second valves operate in concert both to control the amount of hot engine exhaust gases let into the mixer, and to avoid simultaneously sealing both the first transfer outlet 159 and second exhaust outlet 161 and choking the engine 106.
Optionally, an input gas temperature sensor 166 is positioned on the mixer transfer pipe 146 sufficiently close to the inlet duct 147 of the heat exchanger 104 for effectively measuring an input temperature of the exhaust gases to the heat exchanger 104, which is substantially the same as the exhaust gas temperature of the mixer 144.
The optional input gas temperature sensor 166 outputs a signal 167 representative of the measured input gas temperature to the heat exchanger 104. The heat exchanger input gas temperature signal 167 is provided as a second input to the control circuit 152, whereby the control signal 153 is generated as a function of both the heat exchanger exhaust gas temperature sensor output signal 151 and the heat exchanger input gas temperature sensor output signal 167. The diverter valve 158 is thus operable between the HEAT MODE and a DIVERT MODE as a function of input from both the heat exchanger exhaust gas temperature sensor 150 and the heat exchanger input gas temperature sensor 166. For example, the control signal 153 is generated as a function of the differential between the gas entrance and exit temperatures as measured respectively at the inlet duct 147 and the exhaust outlet 148 of the heat exchange chamber 104. Accordingly, the measure of heat absorbed by the cleaning fluid from the hot gases in the heat exchanger 104 may be more precise, which may be useful in controlling the cleaning fluid temperature.
In the DIVERT MODE, the valve 158 of the second diverter 156 is operated to close the first transfer outlet 159 leading to the gas mixer 144, and to simultaneously open the second exhaust outlet 161 which opens the second path through the diverter exhaust pipe 170 leading away from the mixer 144 for being exhausted into the surrounding environment instead. Accordingly, in the DIVERT MODE the operation of the diverter valve 158 of the second diverter 156 inhibits the hot exhaust gases from communicating with the mixer 144, and instead diverts the hot exhaust gases away from the mixer 144 and into the second diverter exhaust pipe 170.
As discussed above, the second diverter 156 also is either a continuous or graduated device, or alternatively an “on-off” device wherein the valve 158 of the second diverter 156 operates at extremes between the first HEAT MODE position 158a that completely opens the input path to the mixer 144 through the transfer pipe 160, and simultaneously substantially closes off the exhaust path through the diverter exhaust pipe 170 to the atmosphere, and the second DIVERT MODE position 158b that substantially closes off the input path to the mixer 144 through the transfer pipe 160, and simultaneously completely opens the exhaust path through the diverter exhaust pipe 170 to the atmosphere.
According to one embodiment of the invention, the control signal 153 output by the control circuit 152 is a single signal transmitted to both the first and second diverters 156. Optionally, the control circuit 152 outputs two different control signals 153. A first control signal 153 is output to the first diverter 156 that is coupled between the engine 106 and the mixer 144, and a different second control signal 153 is output to the second diverter 156 that is coupled between the vacuum pump 114 and the mixer 144. Accordingly, the two diverters 156 may be operated independently of one another for delivering the exhaust gases from the engine 106 and vacuum pump 114 to the mixer 144 either individually or in any desired combination for maintaining the cleaning fluid in the heat exchanger 104 at a desired temperature without overheating.
As discussed above, the valve 158 of the diverter 156 is operable between HEAT MODE and DIVERT MODE as a function of the control signal 153 output by the control circuit 152 which is responsive to the output signal 151 of the first exhaust gas temperature sensor 150, and the output signal 167 of the second exhaust gas temperature sensor 166 if present. In the HEAT MODE, the diverter valve 158 is operated to open the first path through its first transfer outlet 159 that is coupled to the inlet duct 147 of the heat exchanger 104 through the transfer pipe 146. Accordingly, in the HEAT MODE the operation of the diverter valve 158 causes the mixed hot gases from the engine 106 and vacuum pump 114 to be delivered to the heat exchanger 104 via the transfer pipe 146. As discussed above, in the HEAT MODE, operation of the valve 158 of the diverter 156 closes the exhaust path through the second exhaust outlet 161 and the diverter exhaust pipe 162 leading away from the gas mixer 144. Accordingly, in HEAT MODE the operation of the diverter valve 158 inhibits the mixture of hot exhaust gases from the mixer 144 from being diverted away from the heat exchanger 104 through the diverter exhaust pipe 162.
In DIVERT MODE, the diverter valve 158 is operated to close the first transfer outlet 159 leading to the heat exchanger 104, and to simultaneously open the second exhaust outlet 161 which opens the second path through the diverter exhaust pipe 162 leading away from the heat exchanger 104 for being exhausted into the surrounding environment instead. Accordingly, in DIVERT MODE the operation of the valve 158 of the diverter 156 inhibits the mixture of hot exhaust gases from communicating with the heat exchanger 104, and instead diverts the hot exhaust gases away from the heat exchanger 104 and into the diverter exhaust pipe 162.
As discussed above, the diverter 156 is either a continuous or graduated device, or alternatively an “on-off” device wherein the valve 158 of the diverter 156 operates at extremes between the first HEAT MODE position 158a that completely opens the input path through the transfer pipe 160 into the mixer 144, and simultaneously substantially closes off the exhaust path through the diverter exhaust pipe 170 to the atmosphere; and the second DIVERT MODE position 158b that substantially closes off the input path through the transfer pipe 160 into the mixer 144, and simultaneously completely opens the exhaust path through the diverter exhaust pipe 170 to the atmosphere.
While the preferred embodiment of the invention has been illustrated and described, it will be appreciated that various changes can be made therein without departing from the spirit and scope of the invention. For example, materials may be substituted for the different components of the heat exchanger apparatus of the invention without departing from the spirit and scope of the invention. Therefore, the inventor makes the following claims.
This application claims the benefit of U.S. Provisional Application Ser. No. 60/717,604, filed Sep. 17, 2005, the complete disclosure of which is incorporated herein by reference.
| Number | Date | Country | |
|---|---|---|---|
| 60717604 | Sep 2005 | US |
