Patent Application
20140182329
The present invention relates to air-conditioning apparatuses applied to, for example, multi-air-conditioning apparatuses for buildings.
As an air-conditioning apparatus, such as a multi-air-conditioning apparatus for a building, an air-conditioning apparatus has existed which implements a cooling and heating mixed operation by causing a refrigerant to circulate from an outdoor unit to a relay unit and causing a heat medium, such as water, to circulate from the relay unit to an indoor unit so that the conveyance power of the heat medium is reduced while the heat medium, such as water, is circulating in the indoor unit (see, for example, Patent Literature 1).
Furthermore, a circuit which injects liquid into the middle of a compressor from a high-pressure liquid pipe in a refrigeration cycle in order to reduce the discharge temperature of the compressor and an air-conditioning apparatus which is capable of controlling the discharge temperature to a set temperature, regardless of the operating state, have existed (see, for example, Patent Literature 2).
Furthermore, an air-conditioning apparatus exists which is capable of injecting a liquid refrigerant in a high-pressure state in a refrigeration cycle into a suction side of a compressor either in a cooling operation or a heating operation (see, for example Patent Literature 3).
In the air-conditioning apparatus, such as a multi-air-conditioning apparatus for a building, described in Patent Literature 1, there is no problem if R410A or the like is used as a refrigerant. However, in the case where R32 or the like is used as a refrigerant, at the time of a heating operation or the like when the outdoor air temperature is low, the discharge temperature from a compressor becomes excessively high, which may deteriorate the refrigerant and refrigerating machine oil. Furthermore, although the description of a cooling and heating concurrent operation is provided in Patent Literature 1, there is no description about a method of reducing the discharge temperature. Moreover, in the multi-air-conditioning apparatus for a building, an expansion device, such as an electronic expansion valve, for reducing the pressure of a refrigerant, is installed in the relay unit or the indoor unit, which is remote from the outdoor unit.
In the air-conditioning apparatus disclosed in Patent Literature 2, only the method of injection to the middle of the compressor from the high-pressure liquid pipe is described, and the air-conditioning apparatus cannot handle, for example, a case in which the circulation passage in the refrigeration cycle is reversed (switching between cooling and heating). Furthermore, the air-conditioning apparatus does not support a cooling and heating mixed operation.
The air-conditioning apparatus described in Patent Literature 3 has a configuration in which check valves are arranged in parallel with expansion devices on the indoor side and the outdoor side so that suction-injection of the liquid refrigerant can be performed at the time of heating and cooling. However, a special indoor unit is required for this configuration, and therefore there is a problem in that a normal indoor unit in which a check valve is not connected in parallel with an expansion device cannot be used and the required configuration is not a general-purpose configuration.
The present invention has been made in order to solve the above-described problems. Accordingly, a safe-operation and long-service-life air-conditioning apparatus is provided which is capable of injecting a refrigerant into a suction side of a compressor either at the time of a cooling operation or a heating operation and capable of reducing the discharge temperature of the compressor regardless of the operation mode.
An air-conditioning apparatus according to the present invention has a refrigeration cycle including a compressor, a first heat exchanger, a first expansion device, and second heat exchangers that are connected by pipes and includes a suction-injection pipe configured to introduce, into a suction side of the compressor, a refrigerant in a liquid or two-phase state that is branched from a refrigerant flow passage through which the refrigerant that transfers heat in the first heat exchanger or the second heat exchangers circulates; a second expansion device arranged at the suction-injection pipe; and a controller configured to regulate, by controlling an opening degree of the second expansion device, a suction-injection flow rate of the refrigerant introduced into the suction side of the compressor through the suction-injection pipe.
In an air-conditioning apparatus according to the present invention, the discharge temperature from the compressor is restrained from rising excessively high even in the case where a refrigerant whose discharge temperature goes high is used by performing suction-injection of the refrigerant into or out of a suction side of the compressor, regardless of the operation mode. Therefore, the air-conditioning apparatus according to the present invention is capable of operating safely without the refrigerant and refrigerating machine oil being deteriorated, thus a longer service life is ensured.
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
In
Generally, the outdoor unit 1 is arranged in an outdoor space 6 (for example, a rooftop, etc.), which is a space outside a structure 9, such as a building, and supplies cooling energy or heating energy to the indoor units 2 via the heat medium relay unit 3. The indoor units 2 are arranged in positions from which cooling air or heating air can be supplied to an indoor space 7 (for example, a living room, etc.), which is a space inside the structure 9, and supply cooling air or heating air to the indoor space 7, which is to be an air-conditioned space. The heat medium relay unit 3 is configured as a unit separated from the outdoor unit 1 and the indoor unit 2 so as to be installed at a position different from the outdoor space 6 and the indoor space 7, and is connected to the outdoor unit 1 and the indoor units 2 by the refrigerant pipes 4 and the pipes 5, respectively, and transmits cooling energy or heating energy supplied from the outdoor unit 1 to the indoor units 2.
As illustrated in
In
The heat medium relay unit 3 may also be installed in close proximity to the outdoor unit 1. However, in the case where the distance from the heat medium relay unit 3 to each of the indoor units 2 is excessively long, the conveyance power of a heat medium is increased considerably. Therefore, attention needs to be paid to the fact that the energy saving effect is degraded. Moreover, the number of the connected outdoor units 1, indoor units 2, and heat medium relay units 3 is not necessarily equal to the number illustrated in
In the case where a plurality of heat medium relay units 3 are connected to a single outdoor unit 1, the plurality of heat medium relay units 3 may be installed in a scattered manner in shared spaces, spaces above the ceiling, or the like of a structure, such as a building. With this arrangement, an air-conditioning load can be handled by an intermediate heat exchanger of each of the heat medium relay units 3. Furthermore, each of the indoor units 2 can be installed at a distance or a height within a conveyance allowable range of a heat medium conveyance device of a corresponding one of the heat medium relay units 3, and the heat medium relay units 3 can thus be arranged over the entire structure such as a building.
The outdoor unit 1 includes a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat-source-side heat exchanger 12, and an accumulator 19 that are connected in series with one another by the refrigerant pipes 4. Furthermore, the outdoor unit 1 includes a first connecting pipe 4a, a second connecting pipe 4b, a check valve 13a, a check valve 13b, a check valve 13c, and a check valve 13d. By providing the first connecting pipe 4a, the second connecting pipe 4b, the check valve 13a, the check valve 13b, the check valve 13c, and the check valve 13d, the flow of a heat-source-side refrigerant flowing into the heat medium relay unit 3 can be maintained in a constant direction, regardless of an operation requested from each of the indoor units 2.
The compressor 10 may be, for example, a capacity-controllable inverter compressor or the like that sucks a heat-source-side refrigerant and compresses the heat-source-side refrigerant into the high-temperature and high-pressure state. The first refrigerant flow switching device 11 performs switching between the flow of a heat-source-side refrigerant at the time of a heating operation (at the time in a heating only operation mode and the time in a heating main operation mode) and the flow of a heat-source-side refrigerant at the time of a cooling operation (at the time in a cooling only operation mode and the time in a cooling main operation mode). The heat-source-side heat exchanger 12 functions as an evaporator at the time of a heating operation and a condenser (or a radiator) at the time of a cooling operation, exchanges heat between air supplied from a fan, which is not illustrated, and a heat-source-side refrigerant, and evaporates and gasifies or condenses and liquefies the heat-source-side refrigerant. The accumulator 19 is provided on the suction side of the compressor 10, and stores an excess refrigerant generated due to a difference between the time of a heating operation and the time of a cooling operation or an excess refrigerant generated due to a change in a transitional operation.
The check valve 13d is arranged at a portion of the refrigerant pipe 4 positioned between the heat medium relay unit 3 and the first refrigerant flow switching device 11, and allows a heat-source-side refrigerant to flow only in a specific direction (the direction from the heat medium relay unit 3 to the outdoor unit 1). The check valve 13a is arranged at a portion of the refrigerant pipe 4 positioned between the heat-source-side heat exchanger 12 and the heat medium relay unit 3, and allows a heat-source-side refrigerant to flow only in a specific direction (the direction from the outdoor unit 1 to the heat medium relay unit 3). The check valve 13b is arranged at the first connecting pipe 4a, and causes a heat-source-side refrigerant discharged from the compressor 10 to circulate in the heat medium relay unit 3 at the time of a heating operation. The check valve 13c is arranged at the second connecting pipe 4b, and causes a heat-source-side refrigerant that has returned from the heat medium relay unit 3 to circulate into the suction side of the compressor 10 at the time of a heating operation.
In the outdoor unit 1, the first connecting pipe 4a connects the refrigerant pipe 4 positioned between the first refrigerant flow switching device 11 and the check valve 13d with the refrigerant pipe 4 positioned between the check valve 13a and the heat medium relay unit 3. In the outdoor unit 1, the second connecting pipe 4b connects the refrigerant pipe 4 positioned between the check valve 13d and the heat medium relay unit 3 with the refrigerant pipe 4 positioned between the heat-source-side heat exchanger 12 and the check valve 13a.
In a refrigeration cycle, a rise in the temperature of a refrigerant causes deterioration of the refrigerant and refrigerating machine oil which circulate within the circuit, and thus, the upper limit of the temperature is set. This upper limit temperature is normally set, for example, at 120 degrees Centigrade. The highest temperature in the refrigeration cycle is a refrigerant temperature on the discharge side (discharge temperature) of the compressor 10. Therefore, control may be performed such that the discharge temperature does not reach 120 degrees Centigrade or higher. If, for example, R410A or the like is used as a refrigerant, the discharge temperature does not usually reach 120 degrees Centigrade under a normal operation. However, if R32 is used as a refrigerant, the discharge temperature becomes high due to its physical properties, and thus, it is necessary to provide means for reducing the discharge temperature in the refrigeration cycle.
Accordingly, the outdoor unit 1 is configured to include a gas-liquid separator 27a, a gas-liquid separator 27b, an opening/closing device 24, a backflow prevention device 20, an expansion device 14a, an expansion device 14b, a medium pressure detection device 32, a discharged refrigerant temperature detection device 37, a high-pressure detection device 39, a suction-injection pipe 4c, a branch pipe 4d, and a controller 50. Furthermore, the compressor 10 has a low-pressure shell structure. With this structure, the compressor 10 includes a compression chamber within an air-tight container which is under a refrigerant pressure atmosphere of low pressure, and a low-pressure refrigerant within the air-tight container is sucked into the compression chamber and is compressed. However, the structure of the compressor 10 is not limited thereto.
In addition, a refrigerant introduction port is provided at the flow passage between the compressor 10 and the accumulator 19, and the suction-injection pipe 4c for introducing the refrigerant into the suction side of the compressor from the outside of the compressor is provided, so that the refrigerant can be introduced (injected) from the suction-injection pipe 4c into the suction side of the compressor. Accordingly, the temperature of the refrigerant discharged from the compressor 10 or the degree of superheat (discharge superheat) of the refrigerant discharged from the compressor 10 can be reduced.
By controlling the opening/closing device 24, the expansion device 14a, the expansion device 14b, and so on with the controller 50, the discharge temperature of the compressor 10 can be reduced, thus a safe operation being achieved. A more specific control operation will be explained later in the explanation of an operation in each operation mode. The controller 50 includes a microcomputer or the like. On the basis of detection information obtained by various detection devices and instructions from a remote controller, the controller 50 controls, not only the above-described actuators, but also the driving frequency of the compressor 10, the rotation speed (including ON/OFF) of the fan, the switching operation of the first refrigerant flow switching device 11, and so on, and executes various operation modes, which will be described below.
The branch pipe 4d connects the gas-liquid separator 27a, which is provided on the downstream side of the check valve 13a and the check valve 13b, with the gas-liquid separator 27b, which is provided on the upstream side of the check valve 13d and the check valve 13c. In the branch pipe 4d, the backflow prevention device 20 and the opening/closing device 24 are arranged in this order from the side of the gas-liquid separator 27b. The suction-injection pipe 4c connects the branch pipe 4d positioned between the backflow prevention device 20 and the expansion device 14b to the refrigerant introduction port, which is arranged on the suction side of the compressor 10. The suction-injection pipe 4c is connected to the branch pipe 4d via a connection port formed at the branch pipe 4d.
The gas-liquid separator 27a separates the refrigerant that has flowed via the check valve 13a or the check valve 13b into a flow into the refrigerant pipe 4 and a flow into the branch pipe 4d. The gas-liquid separator 27b separates the refrigerant that has returned from the heat medium relay unit 3 into a flow into the branch pipe 4d and a flow into the check valve 13b or the check valve 13c. The gas-liquid separator 27a and the gas-liquid separator 27b each have, in an operation mode in which a liquid refrigerant flows into the gas-liquid separators, a function of separating part of the liquid refrigerant from the liquid refrigerant which has flowed into the gas-liquid separator, and in an operation mode in which a two-phase refrigerant flows into the gas-liquid separator, a function of separating part of a liquid refrigerant from the two-phase refrigerant which has flowed into the gas-liquid separator. The backflow prevention device 20 allows the refrigerant to flow only in a specific direction (the direction from the gas-liquid separator 27b to the gas-liquid separator 27a). The opening/closing device 24 includes a two-way valve or the like and opens and closes the branch pipe 4d. The expansion device 14a is provided on the upstream side of the check valve 13c in the second connecting pipe 4b, and decompresses and expands the refrigerant flowing through the second connecting pipe 4b. The expansion device 14b is provided at the suction-injection pipe 4c, and decompresses and expands the refrigerant flowing through the suction-injection pipe 4c.
The medium pressure detection device 32 is provided on the upstream side of the check valve 13d and the expansion device 14a and on the downstream side of the gas-liquid separator 27b, and detects the pressure of the refrigerant flowing through the refrigerant pipe 4 at a position at which the medium pressure detection device 32 is installed. The discharged refrigerant temperature detection device 37 is provided on the discharge side of the compressor 10, and detects the temperature of the refrigerant discharged from the compressor 10. The high-pressure detection device 39 is provided on the discharge side of the compressor 10, and detects the pressure of the refrigerant discharged from the compressor 10.
The difference in the discharge temperature between when R410A is used as a refrigerant and when R32 is used as a refrigerant will be briefly explained. The case in which the evaporating temperature in a refrigeration cycle is zero degrees Centigrade, the condensing temperature is 49 degrees Centigrade, and the superheat (degree of superheat) of the refrigerant sucked into the compressor is zero degrees Centigrade will be considered. If R410A is used as a refrigerant and adiabatic compression (isentropic compression) is performed, the discharge temperature of the compressor 10 is about 70 degrees Centigrade, due to the physical properties of the refrigerant. In contrast, if R32 is used as a refrigerant and adiabatic compression (isentropic compression) is performed, the discharge temperature of the compressor 10 is about 86 degrees Centigrade, due to the physical properties of the refrigerant. Specifically, when R32 is used as a refrigerant, the discharge temperature rises by about 16 degrees Centigrade than when R410A is used as a refrigerant.
In an actual operation, polytropic compression, which is an operation less efficient than the adiabatic compression, is performed in the compressor 10, and thus, the discharge temperature becomes higher than the above-described value. When R410A is used as a refrigerant, it is not unusual that an operation is performed in the state in which the discharge temperature exceeds 100 degrees Centigrade. Under the condition that an operation is performed using R410A in the state in which the discharge temperature exceeds 104 degrees Centigrade, in the case of the use of R32, the discharge temperature exceeds the upper limit temperature, that is, 120 degrees Centigrade. Therefore, it is necessary to reduce the discharge temperature.
Here, the case where the compressor 10 has a low-pressure shell structure in which a compression chamber and a motor are accommodated in an air-tight container (compressor shell) and the air-tight container in the compressor 10 has a low pressure refrigerant atmosphere and where, for example, the compression chamber is arranged in an upper portion of the air-tight container and the motor is arranged in a lower portion of the air-tight container, will be considered. In the compressor 10 having such a structure, a low-pressure refrigerant sucked into the lower portion of the air-tight container passes around the motor and is sucked into the compression chamber, and after being compressed, the refrigerant is flowed out to the upper portion of the air-tight container which is partitioned off so that the refrigerant is prevented from circulating in the lower portion of the air-tight container, and then the refrigerant is discharged from the compressor 10. The air-tight container is made of metal and is in contact with a low-temperature and low-pressure refrigerant in the lower portion and a high-temperature and high-pressure refrigerant in the upper portion. Furthermore, the motor also generates heat.
Therefore, the refrigerant sucked into the compressor 10 is heated by the air-tight container and the motor, and reaches the compression chamber after the degree of superheat increases. Thus, when the liquid or the two-phase, low-temperature and low-pressure refrigerant is suction-injected into the suction side of the compressor 10, the degree of superheat of the refrigerant sucked into the compression chamber can be decreased, and the discharge temperature can be decreased. Furthermore, in the case where the compressor 10 has a high-pressure shell structure, in which the air-tight container has high pressure, the refrigerant sucked into the compressor 10 directly enters the compression chamber and is compressed. Therefore, when a liquid or two-phase, low-temperature and low-pressure refrigerant is suction-injected into the refrigerant sucked into the compressor 10, the refrigerant starting to be compressed enters the two-phase state, and the discharge temperature decreases by the latent heat.
Regarding a way how to control the suction-injection flow rate into the suction side of the compressor 10, preferably, the discharge temperature is controlled to a target value, for example, 100 degrees Centigrade, and the control target value is changed in accordance with outdoor air temperature. Furthermore, control may be performed such that suction-injection is performed if the discharge temperature is likely to exceed a target value, for example, 110 degrees Centigrade and such that suction-injection is not performed if the discharge temperature is likely to be equal to or lower than the target value. Furthermore, control may be performed such that the discharge temperature falls within a target range, for example, from 80 to 100 degrees Centigrade and such that the suction-injection flow rate is increased if the discharge temperature is likely to exceed the upper limit of the target range and the suction-injection flow rate is decreased if the discharge temperature is likely to be lower than the lower limit of the target range.
Preferably, the discharge superheat (discharge heat degree) is calculated using a high pressure detected by the high-pressure detection device 39 and a discharge temperature detected by the discharged refrigerant temperature detection device 37, the suction-injection flow rate is controlled such that the discharge superheat becomes a target value, for example, 30 degrees Centigrade, and the control target value is changed in accordance with outdoor air temperature. Alternatively, control may be performed such that suction-injection is performed if the discharge superheat is likely to exceed a target value, for example, 40 degrees Centigrade, and such that injection is not performed if the discharge superheat is likely to be equal to or lower than the target value. Furthermore, control may be performed such that the discharge superheat falls within a target range, for example, from 10 to 40 degrees Centigrade and such that the suction-injection flow rate is increased if the discharge superheat is likely to exceed the upper limit of the target range and the suction-injection flow rate is decreased if the discharge superheat is likely to be lower than the lower limit of the target range.
Furthermore, as a method of causing a refrigerant in a two-phase state to be sucked into the compressor 10, a method of causing a refrigerant in a two-phase state to be flowed out of an evaporator. Since the accumulator 19 is arranged on the upstream side of the compressor 10, the refrigerant which has flowed out of the evaporator first flows into the accumulator 19. The accumulator 19 has a structure that can store a certain amount of refrigerant. Unless a certain amount or more of refrigerant is accumulated, two-phase refrigerant including a large amount of liquid refrigerant does not flow out of the accumulator 19 and into the compressor 10.
However, the amount of refrigerant enclosed within the refrigeration cycle has a limit, and only excess refrigerant is stored within the accumulator 19. Thus, it is not possible to control the two-phase refrigerant including the amount of liquid refrigerant required to reduce the discharge temperature to be supplied to the compressor 10 in accordance with the discharge temperature. Therefore, it is necessary to perform suction-injection of the liquid refrigerant between the accumulator 19 and the compressor 10 to supply the required liquid refrigerant to the compressor 10.
The case in which R32 circulates within the refrigerant pipes 4 has been explained above. However, the refrigerant is not limited to R32. Any refrigerant can decrease the discharge temperature and can obtain effects similar to those described above if the configuration of the present invention is employed, as long as the refrigerant causes the discharge temperature to become higher than that in the case of using conventional R410A when the condensing temperature, the evaporating temperature, the superheat (degree of superheat), the subcool (degree of subcooling), and the efficiency of the compressor are the same as those of R410A. In particular, if a refrigerant that causes the discharge temperature to become higher than R410A by three degrees Centigrade or higher is used, more positive effects can be obtained.
Furthermore, as is clear from the calculation of the discharge temperature using a method similar to that described above for a mixed refrigerant of R32 and HFO1234ze, which is a tetrafluoropropene refrigerant having a small global warming potential and having a chemical formula represented by CF3 CH═CHF, the discharge temperature is about 70 degrees Centigrade, which is substantially the same as the discharge temperature of R410A, when the mass ratio of R32 is 34% and the discharge temperature is about 73 degrees Centigrade, which is higher than that of R410A by three degrees Centigrade, when the mass ratio of R32 is 43%. Accordingly, when the mass ratio of R32 is 43% or higher, more positive effects can be obtained by reducing the discharge temperature by performing suction-injection.
These trial calculations were made using REFPROP Version 8.0 released by NIST (National Institute of Standards and Technology). Additionally, the type of mixed refrigerant is not limited to the above-described type. The use of a mixed refrigerant containing a small amount of another refrigerant component does not greatly affect the discharge temperature, and effects similar to those described above can be obtained. For example, a mixed refrigerant containing R32, HFO1234yf, and a small amount of another refrigerant may be used. As stated above, the above-described calculations are made, assuming that adiabatic compression is performed. However, the actual compression is performed by polytropic compression, and thus, the temperature is higher than the above-described temperature by several tens of degrees Centigrade, for example, by 20 degrees Centigrade or higher.
A use-side heat exchanger 26 is provided in each of the indoor units 2. The use-side heat exchangers 26 are connected to heat medium flow control devices 25 and second heat medium flow switching devices 23 in the heat medium relay unit 3 through the pipes 5. The use-side heat exchangers 26 perform heat exchange between air supplied from a fan, which is not illustrated, and a heat medium, and generate heating air or cooling air to be supplied to the indoor space 7.
The two intermediate heat exchangers 15, two expansion devices 16, two opening/closing devices 17, two second refrigerant flow switching devices 18, two pumps 21, four first heat medium flow switching devices 22, the four second heat medium flow switching devices 23, and the four heat medium flow control devices 25 are provided in the heat medium relay unit 3.
The two intermediate heat exchangers 15 (the intermediate heat exchanger 15a and the intermediate heat exchanger 15b) function as condensers (radiators) or evaporators, perform heat exchange between a heat-source-side refrigerant and a heat medium, and transmit cooling energy or heating energy generated in the outdoor unit 1 and stored in the heat-source-side refrigerant to the heat medium. The intermediate heat exchanger 15a is arranged between an expansion device 16a and a second refrigerant flow switching device 18a in the refrigerant circuit A, and is used for cooling the heat medium in the cooling and heating mixed operation mode. The intermediate heat exchanger 15b is arranged between an expansion device 16b and a second refrigerant flow switching device 18b in the refrigerant circuit A, and is used for heating the heat medium in the cooling and heating mixed operation mode.
The two expansion devices 16 (the expansion device 16a and the expansion device 16b) each have a function as a pressure reducing valve or an expansion valve, and each decompress and expand a heat-source-side refrigerant. The expansion device 16a is arranged on the upstream side of the intermediate heat exchanger 15a in the flow of a heat-source-side refrigerant at the time of a cooling operation. The expansion device 16b is arranged on the upstream side of the intermediate heat exchanger 15b in the flow of a heat-source-side refrigerant at the time of a cooling operation. The two expansion devices 16 each preferably include a device whose opening degree (opening area) can be variably controlled, for example, an electronic expansion valve or the like.
The two opening/closing devices 17 (an opening/closing device 17a and an opening/closing device 17b) each include a two-way valve or the like and open and close the refrigerant pipes 4. The opening/closing device 17a is arranged at the refrigerant pipe 4 on the entry side of a heat-source-side refrigerant. The opening/closing device 17b is arranged at a pipe (a bypass pipe 4e) which connects the entry side and exit side for a heat-source-side refrigerant of the refrigerant pipe 4 together. The opening/closing devices 17 may be of any type as long as they can open and close the refrigerant pipes 4. The opening/closing devices 17 may be, for example, electronic expansion valves whose opening degree can be variably controlled.
The two second refrigerant flow switching devices 18 (the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b) each include a four-way valve or the like and perform switching of the flow of a heat-source-side refrigerant so that the corresponding intermediate heat exchanger 15 operates as a condenser or an evaporator in accordance with an operation mode. The second refrigerant flow switching device 18a is arranged on the downstream side of the intermediate heat exchanger 15a in the flow of a heat-source-side refrigerant at the time of a cooling operation. The second refrigerant flow switching device 18b is arranged on the downstream side of the intermediate heat exchanger 15b in the flow of a heat-source-side refrigerant at the time of a cooling only operation.
The two pumps 21 (a pump 21a and a pump 21b) cause the heat medium flowing through the pipes 5 to circulate in the heat medium circuit B. The pump 21a is arranged at the pipe 5 positioned between the intermediate heat exchanger 15a and the second heat medium flow switching devices 23. The pump 21b is arranged at the pipe 5 positioned between the intermediate heat exchanger 15b and the second heat medium flow switching devices 23. The two pumps 21 each preferably include, for example, a capacity-controllable pump or the like, and the flow rate of the pumps 21 is adjustable in accordance with the size of load in the indoor units 2.
The four first heat medium flow switching devices 22 (first heat medium flow switching devices 22a to 22d) each include a three-way valve or the like and perform switching of the flow passage of the heat medium. The first heat medium flow switching devices 22 are arranged in such a manner that the number of the first heat medium flow switching devices 22 corresponds to the number of the indoor units 2 installed (here, four). One of the three ways of each of the first heat medium flow switching devices 22 is connected to the intermediate heat exchanger 15a, another one of the three ways is connected to the intermediate heat exchanger 15b, and the other one of the three ways is connected to the corresponding one of the heat medium flow control devices 25. The first heat medium flow switching devices 22 are arranged on the exit side of the heat medium flow passages of the use-side heat exchangers 26. The first heat medium flow switching devices 22 are illustrated as the first heat medium flow switching device 22a, the first heat medium flow switching device 22b, the first heat medium flow switching device 22c, and the first heat medium flow switching device 22d in this order from the bottom side of the drawing, in association with the indoor units 2. Furthermore, the switching of the heat medium flow passages includes partial switching from one to another way as well as complete switching from one to another way.
The four second heat medium flow switching devices 23 (second heat medium flow switching devices 23a to 23d) each include a three-way valve or the like and perform switching of the flow of the heat medium. The second heat medium flow switching devices 23 are arranged in such a manner that the number of the second heat medium flow switching devices 23 corresponds to the number of the indoor units 2 installed (here, four). One of the three ways of each of the second heat medium flow switching devices 23 is connected to the intermediate heat exchanger 15a, another one of the three ways is connected to the intermediate heat exchanger 15b, and the other one of the three ways is connected to the corresponding one of the use-side heat exchangers 26. The second heat medium flow switching devices 23 are arranged on the entry side of the heat medium flow passages of the use-side heat exchangers 26. The second heat medium flow switching devices 23 are illustrated as the second heat medium flow switching device 23a, the second heat medium flow switching device 23b, the second heat medium flow switching device 23c, and the second heat medium flow switching device 23d in this order from the bottom side of the drawing, in association with the indoor units 2. Furthermore, the switching of the heat medium flow passages includes partial switching from one to another way as well as complete switching from one to another way.
The four heat medium flow control devices 25 (heat medium flow control devices 25a to 25d) each include a two-way valve or the like whose opening area can be controlled and control the flow rate of the heat medium flowing through the corresponding pipes 5. The heat medium flow control devices 25 are arranged in such a manner that the number of the heat medium flow control devices 25 corresponds to the number of the indoor units 2 installed (here, four). One of the two ways of each of the heat medium flow control devices 25 is connected to the corresponding one of the use-side heat exchangers 26 and the other one of the two ways is connected to the corresponding one of the first heat medium flow switching devices 22. The heat medium flow control devices 25 are arranged on the exit side of the heat medium flow passages of the use-side heat exchangers 26. That is, the heat medium flow control devices 25 regulate the amount of heat medium flowing into the indoor units 2 on the basis of the temperature of the heat medium flowing into the indoor units 2 and the temperature of the heat medium flowing out of the indoor units 2, and are capable of supplying an optimal amount of heat medium corresponding to the indoor load to the indoor units 2.
The heat medium flow control devices 25 are illustrated as the heat medium flow control device 25a, the heat medium flow control device 25b, the heat medium flow control device 25c, and the heat medium flow control device 25d in this order from the bottom side of the drawing, in association with the indoor units 2. The heat medium flow control devices 25 may be arranged on the entry side of the heat medium flow passages of the use-side heat exchangers 26. Furthermore, the heat medium flow control devices 25 may be arranged at positions on the entry side of the heat medium flow passages of the use-side heat exchangers 26 and between the second heat medium flow switching devices 23 and the use-side heat exchangers 26. Furthermore, in the case of stopping, thermo-off, or the like, which requires no load, in the indoor units 2, by fully-closing the heat medium flow control devices 25, heat medium supply to the indoor units 2 can be stopped.
The heat medium relay unit 3 includes various detection devices (two first temperature sensors 31, four second temperature sensors 34, four third temperature sensors 35, and two pressure sensors 36). Information (temperature information and pressure information) detected by these detection devices are transmitted to a controller (for example, the controller 50) that performs integrated control of the operation of the air-conditioning apparatus 100, and is used for controlling the driving frequency of the compressor 10, the rotation speed of a fan, which is not illustrated, switching of the first refrigerant flow switching device 11, the driving frequency of the pumps 21, switching of the second refrigerant flow switching devices 18, switching of the flow passage of the heat medium, and the like. Although the state in which the controller 50 is provided inside the outdoor unit 1 has been described above, the arrangement is not limited thereto and may be provided so as to be capable of communicating with the heat medium relay unit 3, the indoor units 2, or individual units.
The two first temperature sensors 31 (a first temperature sensor 31a and a first temperature sensor 31b) each detect the temperature of the heat medium that has flowed out of the corresponding intermediate heat exchanger 15, that is, the temperature of the heat medium at the exit of the corresponding intermediate heat exchanger 15, and each include, for example, a thermistor or the like. The first temperature sensor 31a is arranged at the pipe 5 on the entry side of the pump 21a. The first temperature sensor 31b is arranged at the pipe 5 on the entry side of the pump 21b.
The four second temperature sensors 34 (second temperature sensors 34a to 34d) are arranged between the first heat medium flow switching devices 22 and the flow control devices 25, each detect the temperature of the heat media that have flowed out of the use-side heat exchangers 26, and each may include a thermistor or the like. The second temperature sensors 34 are arranged in such a manner that the number of the second temperature sensors 34 corresponds to the number of the indoor units 2 installed (here, four). The second temperature sensors 34 are illustrated as the second temperature sensor 34a, the second temperature sensor 34b, the second temperature sensor 34c, and the second temperature sensor 34d in this order from the bottom side of the drawing, in association with the indoor units 2.
The four third temperature sensors 35 (third temperature sensors 35a to 35d) are arranged on the entry side or exit side of heat-source-side refrigerants of the intermediate heat exchangers 15, each detect the temperature of the heat-source-side refrigerants flowing into the intermediate heat exchangers 15 or the temperature of the heat-source-side refrigerants flowing out of the intermediate heat exchanges 15, and each may include a thermistor or the like. The third temperature sensor 35a is arranged between the intermediate heat exchanger 15a and the second refrigerant flow switching device 18a. The third temperature sensor 35b is arranged between the intermediate heat exchanger 15a and the expansion device 16a. The third temperature sensor 35c is arranged between the intermediate heat exchanger 15b and the second refrigerant flow switching device 18b. The third temperature sensor 35d is arranged between the intermediate heat exchanger 15b and the expansion device 16b.
A pressure sensor 36b is arranged at a position similar to the position at which the third temperature sensor 35d is arranged, between the intermediate heat exchanger 15b and the expansion device 16a, and detects the pressure of a heat-source-side refrigerant flowing between the intermediate heat exchanger 15b and the expansion device 16b. A pressure sensor 36a is arranged at a position similar to the position at which the third temperature sensor 35a is arranged, between the intermediate heat exchanger 15a and the second refrigerant flow switching device 18a, and detects the pressure of a heat-source-side refrigerant flowing between the intermediate heat exchanger 15a and the second refrigerant flow switching device 18a.
The heat medium relay unit 3 includes a controller, which is not illustrated, including a microcomputer. The controller controls driving of the pumps 21, the opening degree of the expansion devices 16, opening and closing of the opening/closing devices 17, switching of the second refrigerant flow switching devices 18, switching of the first heat medium flow switching devices 22, switching of the second heat medium flow switching devices 23, the opening degree of the heat medium flow control devices 25, and so on, on the basis of detection information obtained by various detection devices and instructions from a remote controller, and executes various operation modes, which will be described below. The controller may be arranged in only one of the outdoor unit 1 and the heat medium relay unit 3. That is, the controller 50 arranged in the outdoor unit 1 may control various devices provided in the heat medium relay unit 3.
The pipes 5 through which flows of the heat medium flow include pipes connected to the intermediate heat exchanger 15a and pipes connected to the intermediate heat exchanger 15b. The pipes 5 are branched in accordance with the number of the indoor units 2 connected to the heat medium relay unit 3 (here, four branches for each pipe). The pipes 5 are connected through the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23. By controlling the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23, a determination as to whether the heat medium from the intermediate heat exchanger 15a is to be flowed into the use-side heat exchangers 26 or the heat medium from the intermediate heat exchanger 15b is to be flowed into the use-side heat exchangers 26, is made.
In the air-conditioning apparatus 100, the compressor 10, the first refrigerant flow switching device 11, the heat-source-side heat exchanger 12, the opening/closing devices 17, the second refrigerant flow switching devices 18, a refrigerant flow passage for the intermediate heat exchanger 15a, the expansion devices 16, and the accumulator 19 are connected through the refrigerant pipes 4 to configure the refrigerant circuit A. Furthermore, a heat medium flow passage for the intermediate heat exchanger 15a, the pumps 21, the first heat medium flow switching devices 22, the heat medium flow control devices 25, the use-side heat exchangers 26, and the second heat medium flow switching devices 23 are connected through the pipes 5 to configure the heat medium circuit B. That is, the plurality of use-side heat exchangers 26 are connected in parallel to each of the intermediate heat exchangers 15, so that the heat medium circuit B is formed as a plural system.
Accordingly, in the air-conditioning apparatus 100, the outdoor unit 1 and the heat medium relay unit 3 are connected through the intermediate heat exchanger 15a and the intermediate heat exchanger 15b provided in the heat medium relay unit 3, and the heat medium relay unit 3 and the indoor units 2 are connected through the intermediate heat exchanger 15a and the intermediate heat exchanger 15b. That is, in the air-conditioning apparatus 100, heat exchange is performed, in the intermediate heat exchanger 15a and the intermediate heat exchanger 15b, between a heat-source side refrigerant circulating in the refrigerant circuit A and a heat medium circulating in the heat medium circuit B.
Various operation modes executed by the air-conditioning apparatus 100 will be explained. The air-conditioning apparatus 100 is capable of performing, with each of the indoor units 2, a cooling operation or a heating operation on the basis of an instruction from the respective indoor units 2. That is, the air-conditioning apparatus 100 is capable of allowing all the indoor units 2 to perform the same operation and also allowing the individual indoor units 2 to perform different operations.
The operation modes executed by the air-conditioning apparatus 100 include a cooling only operation mode in which all of the operating indoor units 2 perform cooling operations, a heating only operation mode in which all of the operating indoor units 2 perform heating operations, a cooling main operation mode, which is a mode in which cooling load is larger than heating load of a cooling and heating mixed operation mode in which a cooling operation and a heating operation coexist, and a heating main operation mode, which is a mode in which the heating load is larger than the cooling load of the cooling and heating mixed operation mode. Hereinafter, the various operation modes will be explained, together with the flow of the heat-source side refrigerant and the heat medium.
In the case of the cooling only operation mode illustrated in
First, the flow of a heat-source-side refrigerant in the refrigerant circuit A will be explained.
A low-temperature and low-pressure refrigerant is compressed by the compressor 10 and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11 and flows into the heat-source-side heat exchanger 12. Then, the gas refrigerant is condensed and liquefied by the heat-source-side heat exchanger 12 into the high-pressure liquid refrigerant while transferring heat to outdoor air. The high-pressure liquid refrigerant that has flowed out of the heat-source-side heat exchanger 12 passes through the check valve 13a, partially flows out of the outdoor unit 1 via the gas-liquid separator 27a, passes through the refrigerant pipe 4, and flows into the heat medium relay unit 3. The high-pressure liquid refrigerant that has flowed into the heat medium relay unit 3 passes through the opening/closing device 17a, is split out, and is expanded by the expansion device 16a and the expansion device 16b into the low-temperature and low-pressure two-phase refrigerant.
The two-phase refrigerant flows into the intermediate heat exchanger 15a and the intermediate heat exchanger 15b operating as evaporators, and turns into the low-temperature and low-pressure gas refrigerant while cooling the heat medium by receiving heat from the heat medium circulating in the heat medium circuit B. The gas refrigerant discharged from the intermediate heat exchanger 15a and the intermediate heat exchanger 15b passes through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b, flows out of the heat medium relay unit 3, passes through the refrigerant pipe 4, and flows into the outdoor unit 1 again. The refrigerant that has flowed into the outdoor unit 1 passes through the gas-liquid separator 27b and the check valve 13d, passes through the first refrigerant flow switching device 11 and the accumulator 19, and is sucked into the compressor 10 again.
At this time, the opening degree (opening area) of the expansion device 16a is controlled such that the superheat (degree of superheat) obtained as the difference between the temperature detected by the third temperature sensor 35a and the temperature detected by the third temperature sensor 35b is maintained constant. Similarly, the opening degree of the expansion device 16b is controlled such that the superheat obtained as the difference between the temperature detected by the third temperature sensor 35c and the temperature detected by the third temperature sensor 35d is maintained constant. Furthermore, the opening/closing device 17a is opened, and the opening/closing device 17b is closed.
In the case of a refrigerant such as R32, since the discharge temperature of the compressor 10 is high, the discharge temperature is reduced by using a suction-injection circuit. An operation performed at this time will be explained with reference to
In the cooling only operation mode, the refrigerant that has been sucked into the compressor 10 and compressed by the compressor 10 (point I in
In the case where the compressor 10 is of a low-pressure shell type, within the compressor 10, sucked refrigerant and oil flow into a lower portion thereof, a motor is arranged in an intermediate portion thereof, and a high-temperature and high-pressure refrigerant compressed by a compassion chamber is discharged into a discharge chamber inside an air-tight container from an upper portion thereof and then discharged from the compressor 10. Therefore, since the air-tight container, which is made of metal, in the compressor 10 includes a portion exposed to a high-temperature and high-pressure refrigerant and a portion exposed to a low-temperature and low-pressure refrigerant, the air-tight container has a medium temperature between the temperatures of these portions. Furthermore, since current flows in the motor, the motor generates heat. Therefore, the low-temperature and low-pressure refrigerant that has been sucked into the compressor 10 is heated by the air-tight container and the motor in the compressor 10, and is sucked into the compression chamber after the temperature increases (point F in
In the case where suction-injection is performed, the low-temperature and low-pressure gas refrigerant that has passed through an evaporator and the two-phase and low-temperature, suction-injected refrigerant are merged together, and the refrigerant in the two-phase state is sucked into the compressor 10. The two-phase refrigerant is heated and evaporated by the air-tight container and the motor in the compressor 10, turns into the low-temperature and low-pressure gas refrigerant (point H in
With the operation described above, in the case where a refrigerant, such as R32, the use of which increases the discharge temperature of the compressor 10, is used, the discharge temperature of the compressor 10 can be reduced, thereby a safety use is ensured.
At this time, the refrigerant in the flow passage in the branch pipe 4d from the opening/closing device 24 to the backflow prevention device 20 is a high-pressure refrigerant, and the refrigerant flowing out of the heat medium relay unit 3 via the refrigerant pipe 4, returning to the outdoor unit 1, and reaching the gas-liquid separator 27b is a low-pressure refrigerant. The backflow prevention device 20 prevents a refrigerant from flowing from the branch pipe 4d to the gas-liquid separator 27b. With the operation of the backflow prevention device 20, the high-pressure refrigerant in the branch pipe 4d and the low-pressure refrigerant in the gas-liquid separator 27b are prevented from mixing together.
Instead of a solenoid valve or the like for which switching between opening and closing can be performed, the opening/closing device 24 may be an electronic expansion valve or the like whose opening area can be changed. The opening/closing device 24 may be of any type as long as it can perform switching between opening and closing of a flow passage. The backflow prevention device 20 may be a check valve or a device that can perform switching between opening and closing of a flow passage, such as a solenoid valve or the like for which switching between opening and closing can be performed or an electronic expansion valve or the like whose opening area can be changed. Since the refrigerant does not flow in the expansion device 14a, the opening degree of the expansion device 14a may be set to a desired value. Furthermore, an electronic expansion valve or the like whose opening area can be changed is used as the expansion device 14b, and the opening area is controlled such that the discharge temperature of the compressor 10 detected by the discharged refrigerant temperature detection device 37 does not become excessively high.
Regarding a way how to perform control, control may be performed such that the opening degree increases by a specific opening degree, for example, by 10 pulses, when the discharge temperature exceeds a specific value, for example, 110 degrees Centigrade. Furthermore, the opening degree of the expansion device 14b may be controlled such that the discharge temperature is maintained at a target value, for example, 100 degrees Centigrade. Furthermore, the expansion device 14b may be a capillary tube, and injection of the amount of refrigerant corresponding to a pressure difference may be performed.
Next, the flow of the heat medium in the heat medium circuit B will be explained.
In the cooling only operation mode, both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b transmit the cooling energy of the heat-source-side refrigerant to the heat medium, and the pump 21a and the pump 21b allow the cooled heat medium to flow through the pipes 5. The heat medium that have been pressurized by and flowed out of the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and flows into the use-side heat exchanger 26a and the use-side heat exchanger 26b. When the heat medium receives heat from indoor air by the use-side heat exchanger 26a and the use-side heat exchanger 26b, cooling of the indoor space 7 is performed.
Then, the heat medium flows out of the use-side heat exchanger 26a and the use-side heat exchanger 26b, and flows into the heat medium flow control device 25a and the heat medium flow control device 25b. At this time, the heat medium is flowed into the use-side heat exchanger 26a and the use-side heat exchanger 26b in such a manner that the flow rate of the heat medium is controlled, with the operation of the heat medium flow control device 25a and the heat medium flow control device 25b, to a flow rate required for the air conditioning load necessary for inside the room. The heat medium that has flowed out of the heat medium flow control device 25a and the heat medium flow control device 25b passes through the first heat medium flow switching device 22a and the first heat medium flow switching device 22b, flows into the intermediate heat exchanger 15a and the intermediate heat exchanger 15b, and is sucked into the pump 21a and the pump 21b again.
In the pipes 5 for the use-side heat exchangers 26, the heat medium flows in the direction in which the heat medium from the second heat medium flow switching devices 23 passes through the heat medium flow control devices 25 and flows into the first heat medium flow switching devices 22. Furthermore, the air-conditioning load necessary for the indoor space 7 can be achieved by controlling the difference between the temperature detected by the first temperature sensor 31a or the temperature detected by the first temperature sensor 31b and the temperature detected by the second temperature sensors 34 to be maintained at a target value. As the exit temperature of the intermediate heat exchangers 15, either the temperature obtained by the first temperature sensor 31a or the first temperature sensor 31b may be used. Alternatively, the average of these temperatures may be used. At this time, the opening degree of the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23 is set to an intermediate degree so that flow passages to both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b can be secured.
For execution of the cooling only operation mode, since it is not necessary to flow the heat medium into a use-side heat exchanger 26 in which heat load is not generated (including thermo-off), the flow passage is closed by the corresponding heat medium flow control device 25 so that the heat medium is not flowed into the use-side heat exchanger 26. In
In the case of the heating only operation mode illustrated in
First, the flow of a heat-source-side refrigerant in the refrigerant circuit A will be explained.
A low-temperature and low-pressure refrigerant is compressed by the compressor 10, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, flows through the first connecting pipe 4a, passes through the check valve 13b and the gas-liquid separator 27a, and is flowed out of the outdoor unit 1. The high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4 and flows into the heat medium relay unit 3. The high-temperature and high-pressure gas refrigerant that has flowed into the heat medium relay unit 3 is split out, and the split flows of gas refrigerant pass through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b and flow into the intermediate heat exchanger 15a and the intermediate heat exchanger 15b.
The high-temperature and high-pressure gas refrigerant that has flowed into the intermediate heat exchanger 15a and the intermediate heat exchanger 15b is condensed and liquefied into high-pressure liquid refrigerant while transferring heat to the heat medium circulating in the heat medium circuit B. The liquid refrigerant that has flowed out of the heat intermediate heat exchanger 15a and the intermediate heat exchanger 15b is expanded by the expansion device 16a and the expansion device 16b and turns into two-phase, intermediate-temperature and medium pressure refrigerant. The two-phase refrigerant passes through the opening/closing device 17b, flows out of the heat medium relay unit 3, passes through the refrigerant pipe 4, and flows into the outdoor unit 1 again. The refrigerant that has flowed into the outdoor unit 1 partially flows into the second connecting pipe 4b via the gas-liquid separator 27b and passes through the expansion device 14a, is expanded by the expansion device 14a into the two-phase, low-temperature and low-pressure refrigerant, passes through the check valve 13c, and flows into the heat-source-side heat exchanger 12 operating as an evaporator.
Then, the refrigerant that has flowed into the heat-source-side heat exchanger 12 receives heat from outdoor air by the heat-source-side heat exchanger 12 and turns into the low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant that has flowed out of the heat-source-side heat exchanger 12 passes through the first refrigerant flow switching device 11 and the accumulator 19, and is sucked into the compressor 10 again.
At this time, the opening degree of the expansion device 16a is controlled such that the subcool (degree of subcooling) obtained as the difference between the value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and the temperature detected by the third temperature sensor 35b is maintained constant. Similarly, the opening degree of the expansion device 16b is controlled such that the subcool obtained as the difference between the value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and the temperature detected by the third temperature sensor 35d is maintained constant. The opening/closing device 17a is closed, and the opening/closing device 17b is opened. In the case where the temperature of the intermediate position of the intermediate heat exchangers 15 can be measured, the temperature at the intermediate position may be used instead of the pressure sensor 36. In this case, an inexpensive system configuration can be achieved.
In the case of a refrigerant such as R32, since the discharge temperature of the compressor 10 is high, the discharge temperature is reduced by using a suction-injection circuit. An operation performed at this time will be explained with reference to
In the heating only operation mode, the refrigerant that has been sucked into the compressor 10 and compressed by the compressor 10 (point I in
In the case where the compressor 10 is of a low-pressure shell type, the temperature of the air-tight container is a medium temperature, as described above. Therefore, a low-temperature and low-pressure refrigerant that has been sucked into the compressor 10 is heated by the air-tight container and the motor in the compressor 10, and is sucked into the compression chamber after the temperature increases (point F in
In the case where suction-injection is performed, the low-temperature and low-pressure gas refrigerant that has passed through the evaporator and the two-phase and low-temperature, suction-injected refrigerant are merged together, and the refrigerant in the two-phase state is sucked into the compressor 10. The two-phase refrigerant is heated and evaporated by the air-tight container and the motor in the compressor 10, turns into the low-temperature and low-pressure gas refrigerant (point H in
With the operation described above, in the case where a refrigerant, such as R32, the use of which increases the discharge temperature of the compressor 10, is used, the discharge temperature of the compressor 10 can be reduced, thereby a safety use is ensured, similar to the time of the cooling only operation mode.
At this time, the opening/closing device 24 is closed, which prevents the refrigerant in the high-pressure state from the gas-liquid separator 27a from being mixed with the refrigerant in the medium pressure state that has passed through the backflow prevention device 20. The configuration of the opening/closing device 24 and the backflow prevention device 20 are similar to that explained for the cooling only operation mode. Furthermore, the configuration and control method of the expansion device 14b are also similar to those explained for the cooling only operation mode.
Furthermore, preferably, an electronic expansion valve or the like whose opening area can be changed is used as the expansion device 14a. With the use of an electronic expansion valve, the medium pressure on the upstream side of the expansion device 14a can be controlled to a desired pressure. For example, by controlling the opening degree of the expansion device 14a such that the medium pressure detected by the medium pressure detection device 32 is maintained constant, a stable control of the discharge temperature by the expansion device 14b is ensured. However, the expansion device 14a is not limited thereto. It may be possible, with a combination of opening/closing valves such as compact solenoid valves, to perform selection between a plurality of opening areas. Alternatively, medium pressure may be formed in accordance with pressure loss of the refrigerant by using a capillary tube as the expansion device 14a. In this case, although controllability is slightly degraded, the discharge temperature can be controlled to a target value. Furthermore, the medium pressure detection device 32 may be a pressure sensor. Alternatively, medium pressure may be obtained by calculation using a temperature sensor.
In the heating only operation mode, since both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b heat the heat medium, the pressure (medium pressure) of the refrigerant on the upstream side of the expansion device 14a may be controlled to be slightly high as long as the pressure falls within a range in which the expansion device 16a and the expansion device 16b can control subcool. By controlling the medium pressure to be slightly high, its pressure difference from the pressure inside the compression chamber becomes larger, thereby a large suction-injection flow rate can be ensured. Thus, even in the case where the outdoor air temperature is low, a suction-injection flow rate sufficient for reducing the discharge temperature can be ensured.
Furthermore, the expansion device 14a and the expansion device 14b are not necessarily controlled in the way described above. The expansion device 14a and the expansion device 14b may be controlled in such a way that the expansion device 14b is fully opened and the discharge temperature of the compressor 10 is controlled by the expansion device 14a. With this way, control can be simplified, and an inexpensive device can be advantageously used as the expansion device 14b.
Next, the flow of the heat medium in the heat medium circuit B will be explained.
In the heating only operation mode, both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b transmit the heating energy of heat-source-side refrigerant to heat medium, and the pump 21a and the pump 21b allow the heated heat medium to flow through the pipes 5. The heat medium that have been pressurized by and flowed out of the pump 21a and the 21b pass through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and flow into the use-side heat exchanger 26a and the use-side heat exchanger 26b. Then, when the flows of the heat medium transfer heat to indoor air by the use-side heat exchanger 26a and the use-side heat exchanger 26b, heating of the indoor space 7 is performed.
Then, the flows of the heat medium flow out of the use-side heat exchanger 26a and the use-side heat exchanger 26b, and flow into the heat medium flow control device 25a and the heat medium flow control device 25b. At this time, the flows of the heat medium are flowed into the use-side heat exchanger 26a and the use-side heat exchanger 26b in such a manner that the flow rate of the heat medium is controlled, with the operation of the heat medium flow control devices 25a and 25b, to a flow rate required for the air-conditioning load necessary for inside the room. The heat medium that has flowed out of the heat medium flow control device 25a and the heat medium flow control device 25b passes through the first heat medium flow switching device 22a and the first heat medium flow switching device 22b, flows into the intermediate heat exchanger 15a and the intermediate heat exchanger 15b, and is sucked into the pump 21a and the pump 21b again.
In the pipes 5 for the use-side heat exchangers 26, the heat medium flows in the direction in which the heat medium from the second heat medium flow switching devices 23 passes through the heat medium flow control devices 25 and flows into the first heat medium flow switching devices 22. Furthermore, the air-conditioning load necessary for the indoor space 7 can be achieved by controlling the difference between the temperature detected by the first temperature sensor 31a or the temperature detected by the first temperature sensor 31b and the temperature detected by the second temperature sensors 34 to be maintained at a target value. As the exit temperature of the intermediate heat exchangers 15, either the temperature obtained by the first temperature sensor 31a or the first temperature sensor 31b may be used. Alternatively, the average of these temperatures may be used.
At this time, the opening degree of the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23 is set to an intermediate degree so that flows to both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b can be secured. Originally, the use-side heat exchanger 26a should be controlled on the basis of the difference between the temperature of the entry and exit thereof. However, since the heat medium temperature on the entry side of the use-side heat exchanger 26 is almost the same as the temperature detected by the first temperature sensor 31b, using the first temperature sensor 31b reduces the number of temperature sensors. Accordingly, an inexpensive system configuration can be achieved. Similar to the cooling only operation mode, the opening degree of the heat medium flow control devices 25 may be controlled in accordance with the presence or absence of the heat load in the use-side heat exchangers 26.
In the case of the cooling main operation mode illustrated in
First, the flow of a heat-source-side refrigerant in the refrigerant circuit A will be explained.
A low-temperature and low-pressure refrigerant is compressed by the compressor 10, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, and flows into the heat-source-side heat exchanger 12. Then, the gas refrigerant is condensed into the two-phase refrigerant while transferring heat to outdoor air by the heat-source-side heat exchanger 12. The two-phase refrigerant that has flowed out of the heat-source-side heat exchanger 12 passes through the check valve 13a, partially flows out of the outdoor unit 1 via the gas-liquid separator 27a, passes through the refrigerant pipe 4, and flows into the heat medium relay unit 3. The two-phase refrigerant that has flowed into the heat medium relay unit 3 passes through the second refrigerant flow switching device 18b, and flows into the intermediate heat exchanger 15b operating as a condenser.
The two-phase refrigerant that has flowed into the intermediate heat exchanger 15b is condensed and liquefied into the liquid refrigerant while transferring heat to the heat medium circulating in the heat medium circuit B. The liquid refrigerant that has flowed out of the intermediate heat exchanger 15b is expanded by the expansion device 16b into the two-phase, low-pressure refrigerant. The two-phase, low-pressure refrigerant passes through the expansion device 16a, and flows into the intermediate heat exchanger 15a operating as an evaporator. The two-phase, low-pressure refrigerant that has flowed into the intermediate heat exchanger 15a turns into the low-pressure gas refrigerant while cooling the heat medium by receiving heat from the heat medium circulating in the heat medium circuit B. The gas refrigerant flows out of the intermediate heat exchanger 15a, passes through the second refrigerant flow switching device 18a, flows out of the heat medium relay unit 3, passes through the refrigerant pipe 4, and flows into the outdoor unit 1 again. The refrigerant that has flowed into the outdoor unit 1 passes through the gas-liquid separator 27a, the check valve 13d, the first refrigerant flow switching device 11, and the accumulator 19, and is sucked into the compressor 10 again.
At this time, the opening degree of the expansion device 16b is controlled such that the superheat obtained as the difference between the temperature detected by the third temperature sensor 35a and the temperature detected by the third temperature sensor 35b is maintained constant. Furthermore, the expansion device 16a is fully opened, the opening/closing device 17a is closed, and the opening/closing device 17b is closed. Here, the opening degree of the expansion device 16b may be controlled such that the subcool obtained as the difference between the value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and the temperature detected by the third temperature sensor 35d is maintained constant. Furthermore, the expansion device 16b may be fully opened, and the superheat or the subcool may be controlled using the expansion device 16a.
In the case of a refrigerant such as R32, since the discharge temperature of the compressor 10 is high, the discharge temperature is reduced by using a suction-injection circuit. An operation performed at this time will be explained with reference to
In the cooling main operation mode, the refrigerant that has been compressed by the compressor 10 is condensed by the heat-source-side heat exchanger 12 into the two-phase, high-pressure refrigerant (point J in
In the case where the compressor 10 is of a low-pressure shell type, the temperature of the air-tight container is a medium temperature, as described above. Therefore, a low-temperature and low-pressure refrigerant that has been sucked into the compressor 10 is heated by the air-tight container and the motor in the compressor 10, and is sucked into the compression chamber after the temperature increases (point F in
In the case where suction-injection is performed, the low-temperature and low-pressure gas refrigerant that has passed through the evaporator and the two-phase and low-temperature, suction-injected refrigerant are merged together, and the refrigerant in the two-phase state is sucked into the compressor 10. The two-phase refrigerant is heated and evaporated by the air-tight container and the motor in the compressor 10, turns into the low-temperature and low-pressure gas refrigerant (point H in
With the operation described above, in the case where a refrigerant, such as R32, the use of which increases the discharge temperature of the compressor 10, is used, the discharge temperature of the compressor 10 can be reduced, thereby a safety use is ensured, similar to the cooling only operation mode.
The configuration and operation of the opening/closing device 24, the backflow prevention device 20, the expansion device 14a, and the expansion device 14b are similar to those explained for the cooling only operation mode.
Next, the flow of the heat medium in the heat medium circuit B will be explained. In the cooling main operation mode, the intermediate heat exchanger 15b transmits the heating energy of a heat-source-side refrigerant to the heat medium, and the pump 21b allows the heated heat medium to flow through the pipes 5. Furthermore, in the cooling main operation mode, the intermediate heat exchanger 15a transmits the cooling energy of the heat-source-side refrigerant to the heat medium, and the pump 21a allows the cooled heat medium to flow through the pipes 5. The heat medium that has been pressurized by and flowed out of the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and flows into the use-side heat exchanger 26a and the use-side heat exchanger 26b.
In the use-side heat exchanger 26b, when the heat medium transfers heat to indoor air, heating of the indoor space 7 is performed. Furthermore, in the use-side heat exchanger 26a, when the heat medium receives heat from indoor air, cooling of the indoor space 7 is performed. At this time, the heat medium is flowed into the use-side heat exchanger 26a and the use-side heat exchanger 26b in such a manner that the flow rate of the heat medium is controlled, with the operation of the heat medium flow control device 25a and the heat medium flow control device 25b, to be a flow rate required for the air-conditioning load necessary for inside the room. The heat medium that has passed through the use-side heat exchanger 26b and whose temperature has been slightly reduced passes through the heat medium flow control device 25b and the first heat medium flow switching device 22b, flows into the intermediate heat exchanger 15b, and is sucked into the pump 21b again. The heat medium that has passed through the use-side heat exchanger 26a and whose temperature has been slightly increased passes through the heat medium flow control device 25a and the first heat medium flow switching device 22a, flows into the intermediate heat exchanger 15a, and is sucked into the pump 21a again.
During this processing, with the operation of the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23, the warm heat medium and the cold heat medium do not mix together and are individually introduced into the corresponding use-side heat exchangers 26 in which the heating load and the cooling load are generated. Here, in the pipes 5 for the use-side heat exchangers 26, the heat medium flows in the direction, for both the heating side and the cooling side, in which the heat medium from the second heat medium flow switching devices 23 passes through the heat medium flow control devices 25 and reaches the first heat medium flow switching devices 22. Furthermore, the air-conditioning load necessary for the indoor space 7 can be achieved by, for the heating side, controlling the difference between the temperature detected by the first temperature sensor 31b and the temperature detected by the corresponding second temperature sensor 34 to be maintained at a target value and, for the cooling side, controlling the difference between the temperature detected by the corresponding second temperature sensor 34 and the temperature detected by the first temperature sensor 31a to be maintained at a target value.
As in the cooling only operation mode and the heating only operation mode, the opening degree of the heat medium flow control devices 25 is controlled in accordance with the presence or absence of heat load in the use-side heat exchangers 26.
In the case of the heating main operation mode illustrated in
First, the flow of a refrigerant in the refrigerant circuit A will be explained.
A low-temperature and low-pressure refrigerant is compressed by the compressor 10, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, the first connecting pipe 4a, and the check valve 13b, and flows out of the outdoor unit 1 via the gas-liquid separator 27a. The high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 passes through the refrigerant pipe 4, and flows into the heat medium relay unit 3. The high-temperature and high-pressured gas refrigerant that has flowed into the heat medium relay unit 3 passes through the second refrigerant flow switching device 18b, and flows into the intermediate heat exchanger 15b operating as a condenser.
The gas refrigerant that has flowed into the intermediate heat exchanger 15b is condensed and liquefied into the liquid refrigerant while transferring heat to the heat medium circulating in the heat medium circuit B. The liquid refrigerant that has flowed out of the intermediate heat exchanger 15b is expanded by the expansion device 16b and turns into the two-phase, medium pressure refrigerant. The two-phase, medium pressure refrigerant passes through the expansion device 16a, and flows into the intermediate heat exchanger 15a operating as an evaporator. The two-phase, medium pressure refrigerant that has flowed into the intermediate heat exchanger 15a evaporates by receiving heat from the heat medium circulating in the heat medium circuit B, and thus cools the heat medium. The two-phase, medium pressure refrigerant flows out of the intermediate heat exchanger 15a, passes through the second refrigerant flow switching device 18a, flows out of the heat medium relay unit 3, and flows through the refrigerant pipe 4 into the outdoor unit 1 again.
The refrigerant that has flowed into the outdoor unit 1 partially flows into the second connecting pipe 4b via the gas-liquid separator 27b, passes through the expansion device 14a, is expanded by the expansion device 14a into the two-phase, low-temperature and low-pressure refrigerant, passes through the check valve 13c, and flows into the heat-source-side heat exchanger 12 operating as an evaporator. Then, the refrigerant that has flowed into the heat-source-side heat exchanger 12 receives heat from outdoor air by the heat-source-side heat exchanger 12, and thus turns into the low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant that has flowed out of the heat-source-side heat exchanger 12 passes through the first refrigerant flow switching device 11 and the accumulator 19, and is sucked into the compressor 10 again.
At this time, the opening degree of the expansion device 16b is controlled such that the subcool obtained as the difference between the value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and the temperature detected by the third temperature sensor 35b is maintained constant. Furthermore, the expansion device 16a is fully opened, the opening/closing device 17a is closed, and the opening/closing device 17b is closed. Here, the expansion device 16b may be fully opened, and the subcool may be controlled using the expansion device 16a.
In the case of a refrigerant such as R32, since the discharge temperature of the compressor 10 is high, the discharge temperature is reduced by using a suction-injection circuit. An operation performed at this time will be explained with reference to
In the heating main operation mode, the refrigerant returns from the heat medium relay unit 3 via the refrigerant pipe 4 to the outdoor unit 1. The refrigerant that has returned to the outdoor unit 1 reaches the gas-liquid separator 27b. With the operation of the expansion device 14a, the pressure of the refrigerant on the upstream side of the expansion device 14a is controlled to a medium pressure state (point J in
In the case where the compressor 10 is of a low-pressure shell type, the temperature of the air-tight container is a medium temperature, as described above. Therefore, a low-temperature and low-pressure refrigerant that has been sucked into the compressor 10 is heated by the air-tight container and the motor in the compressor 10, and is sucked into the compression chamber after the temperature increases (point F in
In the case where suction-injection is performed, the low-temperature and low-pressure gas refrigerant that has passed through the evaporator and the two-phase and low-temperature, suction-injected refrigerant are merged together, and the refrigerant in the two-phase state is sucked into the compressor 10. The two-phase refrigerant is heated and evaporated by the air-tight container and the motor in the compressor 10, turns into the low-temperature and low-pressure gas refrigerant (point H in
With the operation described above, in the case where a refrigerant, such as R32, the use of which increases the discharge temperature of the compressor 10, is used, the discharge temperature of the compressor 10 can be reduced, thereby a safety use is ensured, similar to the cooling only operation mode.
The configuration and operation of the opening/closing device 24, the backflow prevention device 20, the expansion device 14a, and the expansion device 14b are similar to those explained for the heating only operation mode. Furthermore, the expansion device 14a and the expansion device 14b are controlled in a way similar to that explained for the heating only operation mode.
In the heating main operation mode, the heat medium needs to be cooled in the intermediate heat exchanger 15a. Therefore, the pressure (medium pressure) of the refrigerant on the upstream side of the expansion device 14a cannot be controlled to be very high. Since the medium pressure cannot be controlled to become high, the suction-injection flow rate is small, thus reducing a decrease in the discharge temperature. However, since it is necessary to prevent the heat medium from freezing, when the outdoor air temperature is low, for example, −5 degrees Centigrade or lower, the heating only operation mode is not entered. When the outdoor air temperature is high, since the discharge temperature is not very high and a large injection flow rate is not required, no problem occurs. With the expansion device 14a, the heat medium in the intermediate heat exchanger 15b can be cooled, and setting to a medium pressure at which an injection flow rate sufficient for reducing the discharge temperature can be supplied to the compression chamber is performed. Therefore, a safety operation can be ensured.
Next, the flow of the heat medium in the heat medium circuit B will be explained.
In the heating main operation mode, the intermediate heat exchanger 15b transmits the heating energy of the heat-source-side refrigerant to the heat medium, and the pump 21b allows the heated heat medium to flow through the pipes 5. Furthermore, in the heating main operation mode, the intermediate heat exchanger 15a transmits the cooling energy of the heat-source-side refrigerant to the heat medium, and the pump 21a allows the cooled heat medium to flow through the pipes 5. The heat medium that has been pressurized by and flowed out of the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and flows into the use-side heat exchanger 26a and the use-side heat exchanger 26b.
In the use-side heat exchanger 26b, when the heat medium receives heat from indoor air, cooling of the indoor space 7 is performed. Furthermore, in the use-side heat exchanger 26a, when the heat medium transfers heat to indoor space, heating of the indoor space 7 is performed. At this time, the heat medium is flowed into the use-side heat exchanger 26a and the use-side heat exchanger 26b in such a manner that the flow rate of the heat medium is controlled, with the operation of the heat medium flow control device 25a and the heat medium flow control device 25b, to be a flow rate required for the air-conditioning load necessary for inside the room. The heat medium that has passed through the use-side heat exchanger 26b and whose temperature has been slightly increased passes through the heat medium flow control device 25b and the first heat medium flow switching device 22b, flows into the intermediate heat exchanger 15a, and is sucked into the pump 21a again. The heat medium that has passed through the use-side heat exchanger 26a and whose temperature has been slightly reduced passes through the heat medium flow control device 25a and the first heat medium flow switching device 22a, flows into the intermediate heat exchanger 15b, and is sucked into the pump 21b again.
During this processing, with the operation of the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23, the warm heat medium and the cold heat medium do not mix together and are individually introduced into the corresponding use-side heat exchangers 26 in which the heating load and the cooling load are generated. Here, in the pipes 5 for the use-side heat exchangers 26, for both the heating side and the cooling side, the heat medium flows in the direction in which the heat medium from the second heat medium flows switching devices 23 passes through the heat medium flow control devices 25 and flows into the first heat medium flow switching devices 22. Furthermore, the air-conditioning load necessary for the indoor space 7 can be achieved by, for the heating side, controlling the difference between the temperature detected by the first temperature sensor 31b and the temperature detected by the corresponding second temperature sensor 34 to be maintained at a target value and, for the cooling side, controlling the difference between the temperature detected by the corresponding second temperature sensor 34 and the temperature detected by the first temperature sensor 31a to be maintained at a target value.
As in the cooling only operation mode, the heating only operation mode, and the cooling main operation mode, the opening degree of the heat medium flow control devices 25 may be controlled in accordance with the presence or absence of heat load in the use-side heat exchangers 26.
[Expansion Device 14a and/or Expansion Device 14b]
Suction-injection to the suction side of the compressor 10 in each operation mode is performed as described above. Accordingly, the flows of liquid refrigerant separated by the gas-liquid separator 27a and the gas-liquid separator 27b flow into the expansion device 14a and the expansion device 14b. However, in any mode except for the cooling only operation mode, the liquid refrigerant separated by the gas-liquid separator 27a and the gas-liquid separator 27b is not sub-cooled, and the liquid refrigerant is in the saturated liquid state. In actuality, saturated liquid represents a state in which a small amount of minute refrigerant gas exists. In addition, due to minute pressure loss in the opening/closing device 24, a refrigerant pipe, or the like, the liquid refrigerant may turn into the two-phase refrigerant.
In the case where an electronic expansion valve is used as an expansion device, when the refrigerant in a two-phase state flows into the expansion device, if a gas refrigerant and a liquid refrigerant flow separately, the state in which gas flows into the expansion part and the state in which liquid flows into the expansion part may occur individually. In this case, the pressure on the exit side of the expansion device may be unstable. In particular, when the quality is low, refrigerant separation occurs, and this tendency is highly likely to occur. Under such a situation, by using the expansion device 14a and/or the expansion device 14b having the configuration illustrated in
Referring to
The mixing device 46 may be of any type as long as it is capable of generating a state in which the gas refrigerant and the liquid refrigerant mix together substantially uniformly. For example, this state can be achieved by using foam metal. Foam metal is a metal porous body having the same three-dimensional net-like structure as a resin foam body, such as a sponge, and has the maximum (between 80% and 97%) porosity (void) of all the types of metal porous body. Circulation of a two-phase refrigerant through such foam metal achieves an advantage of finely cutting gas in the refrigerant, agitating the gas, and mixing the gas with the liquid uniformly, due to the three-dimensional net-like structure.
In the field of fluid mechanics, it is clear that when a refrigerant inside a pipe travels from a portion having a structure disturbing the flow to a portion in which L/D reaches between 8 and 10, where D represents the inner diameter of the pipe and L represents the length of the pipe, the influence of the disturbance disappears and the original flow is recovered. In the case where the mixing device 46 is arranged at a position where L/D is 6 or less, where D represents the inner diameter of the inflow pipe 41 of the expansion device 14 and L represents the length from the mixing device 46 to the expansion part 43, the mixed two-phase refrigerant maintained in the mixed state can reach the expansion part 43, thus a stable control is ensured.
Furthermore, the state of a high discharge temperature occurs in the case where the frequency of the compressor 10 increases and the condensing temperature increases in order to maintain the evaporating temperature at a target temperature, for example, zero degrees Centigrade during a cooling operation when the outdoor air temperature is high. Alternatively, the state of a high discharge temperature occurs in the case where the frequency of the compressor 10 increases and the evaporating temperature decreases in order to maintain the condensing temperature at a target temperature, for example, 49 degrees Centigrade during a heating operation when the outdoor air temperature is low. At the time of a cooling main operation, the condensing temperature and the evaporating temperature need to be maintained at corresponding target temperatures, for example, 49 degrees Centigrade and zero degrees Centigrade, respectively. In the case of a cooling main operation when the outdoor air temperature is high, since the condensing temperature and the evaporating temperature are higher than the corresponding target temperatures, the state in which the frequency of the compressor 10 becomes very high is not likely to occur, unlike a cooling operation when the outdoor air temperature is high, and increasing the frequency of the compressor 10 is limited in order not to cause the condensing temperature to become excessively high.
Thus, in the cooling main operation mode, the discharge temperature is less likely to become high. Because of this, as illustrated in
As described above, the air-conditioning apparatus 100 according to this embodiment have some operation modes. In these operation modes, the heat-source-side refrigerant flows in refrigerant pipes 4, which connect the outdoor unit 1 with the heat medium relay unit 3.
In some operation modes executed by the air-conditioning apparatus 100 according to this embodiment, the heat medium, such as water, antifreeze, or the like, flow in the pipes 5, which connect the heat medium relay unit 3 with the indoor units 2.
The case in which the pressure sensor 36a is arranged at the flow passage between the intermediate heat exchanger 15a and the second refrigerant flow switching device 18a that operate as a cooling side in a cooling and heating mixed operation and the pressure sensor 36b is arranged at the flow passage between the intermediate heat exchanger 15b and the expansion device 16b that operate as a heating side in a cooling and heating mixed operation has been described above. With this arrangement, even if pressure loss occurs in the intermediate heat exchanger 15a and the intermediate heat exchanger 15b, the saturation temperature can be accurately calculated.
However, since pressure loss on the condensing side is small, the pressure sensor 36b may be arranged at the flow passage between the intermediate heat exchanger 15b and the expansion device 16b. Even in this case, the accuracy in calculation is not very degraded. Furthermore, although pressure loss in an evaporator is relatively large, in the case where an intermediate heat exchanger whose pressure loss can be estimated or whose pressure loss is small is used, the pressure sensor 36a may be arranged at the flow passage between the intermediate heat exchanger 15a and the second refrigerant flow switching device 18a.
In the case where only heating load or cooling load is generated in a use-side heat exchanger 26, the air-conditioning apparatus 100 sets the opening degree of a corresponding first heat medium flow switching device 22 and a corresponding second heat medium flow switching device 23 to an intermediate degree so that the heat medium flows to both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b. Accordingly, since both the intermediate heat exchanger 15a and the intermediate heat exchanger 15b can be used for a heating operation or a cooling operation, a large heat transmission area can be achieved, thus an efficient heating operation or cooling operation is ensured.
Furthermore, in the case where heating load and cooling load are generated in a mixed manner in the use-side heat exchangers 26, a heating operation and a cooling operation can be freely performed in each of the indoor units 2 by switching a first heat medium flow switching device 22 and a second heat medium flow switching device 23 corresponding to a use-side heat exchanger 26 that is performing a heating operation to the flow connected to the intermediate heat exchanger 15b for heating and switching a first heat medium flow switching device 22 and a second heat medium flow switching device 23 corresponding to a use-side heat exchanger 26 that is performing a cooling operation to the flow connected to the intermediate heat exchanger 15a for cooling.
Furthermore, the medium pressure detection device 32 may calculate medium pressure, for example, by a calculation by the controller 50 on the basis of temperature detected by a temperature sensor, as well as by a pressure sensor. Furthermore, in the case where an electronic expansion valve or the like whose opening area can be changed is used as the expansion device 14b, the controller 50 controls the opening area of the expansion device 14b such that the discharge temperature of the compressor 10 detected by the discharged refrigerant temperature detection device 37 does not become excessively high. Regarding a way how to perform control, when it is determined that the discharge temperature exceeds a specific value (for example, 110 degrees Centigrade or the like), the opening degree of the expansion device 14b may be controlled to be opened by a specific opening degree, for example, by 10 pulses.
Furthermore, the opening degree of the expansion device 14b may be controlled such that the discharge temperature is maintained at a target value (for example, 100 degrees Centigrade). Alternatively, the opening degree of the expansion device 14b may be controlled such that the discharge temperature falls within a target range (for example, between 90 degrees Centigrade and 100 degrees Centigrade). Furthermore, by calculating the discharge degree of superheat of the compressor 10 on the basis of the temperature detected by the discharged refrigerant temperature detection device 37 and the pressure detected by the high-pressure detection device 39, the opening degree of the expansion device 14b may be controlled such that the discharge degree of superheat is maintained at a target value (for example, 40 degrees Centigrade) or such that the discharge degree of superheat falls within a target range (for example, between 20 degrees Centigrade and 40 degrees Centigrade).
Although the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23 explained in Embodiment 1 may be devices that can perform switching of a flow passage, such as a combination of two devices, that is, a three-way valve or the like that can perform switching between three-way passages and an opening/closing valve or the like that opens and closes two-way passages. Furthermore, two devices, that is, a combination of a mixing valve of a stepping motor driven type or the like that can change the flow rate of three-way passages and an electronic expansion valve or the like that can change the flow rate of two-way passages, may be used as the first heat medium flow switching devices 22 and the second heat medium flow switching devices 23. In this case, occurrence of water hammering, which is caused by sudden opening/closing of a flow passage, can be prevented. Furthermore, although the case in which the heat medium flow control devices 25 are two-way valves has been described as an example in Embodiment 1, control valves having three-way passages may be provided as the heat medium flow control devices 25, together with bypass pipes for bypassing the use-side heat exchangers 26.
Furthermore, devices of a stepping motor driven type that can control the flow rate in a flow passage preferably be used as the heat medium flow control devices 25. Two-way valves, three-way vales whose one end is closed, or the like may be used as the heat medium flow control devices 25. Furthermore, opening/closing valves or the like that open and close two-way passages may be used as the heat medium flow control devices 25, so that the average flow rate can be controlled by repeating ON and OFF.
Furthermore, although the second refrigerant flow switching devices 18 have been explained as if they were four-way valves, the second refrigerant flow switching devices 18 are not necessarily four-way valves. The second refrigerant flow switching devices 18 may be configured to include a plurality of two-way flow switching valves or three-way flow switching valves so that the refrigerant flows in a way similar to that described above.
Furthermore, needless to mention, a similar operation can be achieved even in the case where only one use-side heat exchanger 26 and one heat medium flow control device 25 are connected. In addition, naturally, there is no problem if a plurality of devices that perform the same operations are provided as the intermediate heat exchangers 15 and the expansion devices 16. Moreover, although the case in which the heat medium flow control devices 25 are built in the heat medium relay unit 3 has been described above as an example, the heat medium flow control devices 25 are not necessarily built in the heat medium relay unit 3 and may be built in the indoor units 2. Alternatively, the heat medium flow control devices 25 may be configured independent of the heat medium relay unit 3 and the indoor units 2.
As a heat medium, for example, brine (antifreeze), water, a liquid mixture of brine and water, a liquid mixture of water and an additive having a high anticorrosive effect, or the like may be used. Thus, in the air-conditioning apparatus 100, even if the heat medium leaks through the indoor units 2 to the indoor space 7, since a material used for the heat medium is highly safe, the use of the highly safe material contributes to improvement in the safety.
Furthermore, in general, a fan is mounted in each of the heat-source-side heat exchanger 12 and the use-side heat exchangers 26a to 26d in many cases, so that condensation or evaporation is urged by air sending. However, a fan is not necessarily mounted in each of the heat-source-side heat exchanger 12 and the use-side heat exchangers 26a to 26d. For example, panel heaters or the like that use radiation may be used as the use-side heat exchangers 26a to 26d, and a device of a water cooled type that transports heat by water or antifreeze may be used as the heat-source-side heat exchanger 12. That is, devices of any type may be used as the heat-source-side heat exchanger 12 and the use-side heat exchangers 26a to 26d as long as they have a configuration capable of transferring or receiving heat.
In Embodiment 1, the case where four use-side heat exchangers, the use-side heat exchangers 26a to 26d, are provided has been explained as an example. However, any number of use-side heat exchangers may be connected. Furthermore, the case where two intermediate heat exchangers, the intermediate heat exchanger 15a and the intermediate heat exchanger 15b, are provided has been explained as an example. However, obviously, the configuration is not limited thereto and any number of intermediate heat exchangers can be provided as long as they are configured to be capable of cooling and/or heating the heat medium. Furthermore, the number of each of the pump 21a and the pump 21b is not necessarily one. A plurality of small-capacity pumps may be arranged in parallel to one another. Furthermore, although the case in which the air-conditioning apparatus 100 includes the accumulator 19 has been explained as an example in Embodiment 1, the accumulator 19 is not necessarily provided.
Normal gas-liquid separators separate a gas refrigerant and a liquid refrigerant in a two-phase refrigerant from each other. In contrast, as explained above, in the case of the gas-liquid separators 27 (the gas-liquid separator 27a and the gas-liquid separator 27b) used in the air-conditioning apparatus 100, when the refrigerant in the two-phase state flows into the inlet of the gas-liquid separators 27, the gas-liquid separators 27 separate part of a liquid refrigerant from the two-phase refrigerant, run the separated part of liquid refrigerant through the branch pipe 4d, and cause the residual two-phase refrigerant (having a slightly increased quality) to flow out of the gas-liquid separators 27. Thus, as shown in
A horizontal gas-liquid separator represents a gas-liquid separator having a structure in which when the gas-liquid separator is arranged, the length in the horizontal direction, which is a direction in which the refrigerant flows in and flows out is greater than the length in the vertical direction, which is perpendicular to the direction in which the refrigerant flows in (the horizontal direction in which the refrigerant flows in). However, as the gas-liquid separators 27, any structure may be adoptable as long as part of a liquid refrigerant can be separated from the refrigerant that has flowed in the gas-liquid separators 27 in the two-phase state and the residual two-phase refrigerant can be flowed out of the gas-liquid separators 27.
Furthermore, the system has been explained as an example in which the compressor 10, the first refrigerant flow switching device 11, the heat-source-side heat exchanger 12, the expansion device 14a, the expansion device 14b, the opening/closing device 24, and the backflow prevention device 20 are accommodated within the outdoor unit 1, the use-side heat exchangers 26 are accommodated within the indoor units 2, and the intermediate heat exchangers 15 and the expansion devices 16 are accommodated within the heat medium relay unit 3. The system has been further explained as an example in which a pair of pipes connects the outdoor unit 1 with the heat medium relay unit 3, so that the heat medium circulates between the outdoor unit 1 and the heat medium relay unit 3, a pair of pipes connects each of the indoor units 2 with the heat medium relay unit 3, so that the heat medium circulates between the indoor unit 2 and the heat medium relay unit 3, and the intermediate heat exchangers 15 perform heat exchange between the refrigerant and the heat medium. However, the system does not necessarily have the above-mentioned configuration.
For example, application to a direct expansion system is also possible in which the compressor 10, the first refrigerant flow switching device 11, the heat-source-side heat exchanger 12, the expansion device 14a, the expansion device 14b, the opening/closing device 24, and the backflow prevention device 20 are accommodated within the outdoor unit 1, load-side heat exchangers that perform heat exchange between air in an air-conditioned space and the refrigerant and the expansion devices 16 are accommodated within the indoor units 2, a relay unit formed independent of the outdoor unit 1 and the indoor units 2 is provided, a pair of pipes connects the outdoor unit 1 with the relay unit, a pair of pipes connects each of the indoor units 2 with the relay unit, the refrigerant is caused to circulate between the outdoor unit 1 and each of the indoor units 2 via the relay unit, and a cooling only operation, a heating only operation, a cooling main operation, and a heating main operation can be performed. With this system, similar effects can be achieved.
Furthermore, application to an air-conditioning apparatus of a direct expansion type is also possible in which the compressor 10, the first refrigerant flow switching device 11, the heat-source-side heat exchanger 12, the expansion device 14a, and the expansion device 14b are accommodated within the outdoor unit 1, load-side heat exchangers that perform heat exchange between air in an air-conditioned space and the refrigerant and the expansion devices 16 are accommodated within the indoor units 2, a pair of pipes connects each of a plurality of indoor units to the outdoor unit 1, so that the refrigerant circulates between the outdoor unit 1 and the indoor units 2, and only switching between a cooling only operation and a heating only operation is performed. With this system, similar effects can also be achieved.
Furthermore, application to an air-conditioning apparatus is also possible in which a heat exchanger that exchanges heat between water and the refrigerant is provided in the heat medium relay unit 3 and only switching between a cooling only operation and a heating only operation is performed. With this system, similar effects can also be achieved.
As described above, the air-conditioning apparatus 100 according to Embodiment 1 can perform suction-injection of the refrigerant to the suction side of the compressor 10 so that the discharge temperature is controlled not to become excessively high, regardless of an operation mode, even in the case where a refrigerant, such as R32, the use of which increases the discharge temperature of the compressor 10, is used. Therefore, with the air-conditioning apparatus 100, the refrigerant and refrigerating machine oil can be efficiently suppressed from being deteriorated, and a safe operation can be achieved, thus a longer service life is ensured.
As illustrated in
In actuality, saturated liquid is in a state in which a small amount of minute refrigerant gas exists, and may turn into the two-phase refrigerant due to minute pressure loss in the opening/closing device 24, a refrigerant pipe, or the like. With the use of an electronic expansion valve as an expansion device, when the refrigerant in the two-phase state flows into the expansion device, in the case where a gas refrigerant and a liquid refrigerant flow separately, a state in which gas flows in the expansion part and a state in which liquid flows in the expansion part occur independently. Therefore, the pressure at the exit side of the expansion device may be unstable. In particular, in the case where the quality is low, refrigerant separation occurs, and this tendency is highly likely to occur.
Under such circumstances, in the air-conditioning apparatus 100A according to Embodiment 2, the refrigerant-refrigerant heat exchanger 28 is mounted at the suction-injection pipe 4c. The refrigerant-refrigerant heat exchanger 28 exchanges heat between a high-pressure liquid refrigerant separated by the gas-liquid separator 27a or the gas-liquid separator 27b and a two-phase, low-pressure refrigerant decompressed by the expansion device 14b. By this processing, a high-pressure liquid refrigerant flowing into the refrigerant-refrigerant heat exchanger 28 is decompressed and cooled by a two-phase, low-pressure refrigerant whose pressure and temperature have been reduced, and thus the liquid refrigerant is sub-cooled and flows into the expansion device 14b. Therefore, the refrigerant containing bubbles is prevented from flowing into the expansion device 14b, and a stable control can be ensured in all the cooling only operation, heating only operation, cooling main operation, and heating main operation.
As described above, the air-conditioning apparatus 100A according to Embodiment 2 achieves effects similar to those of the air-conditioning apparatus 100 according to Embodiment 1, and is capable of controlling individual executed operation modes more stably.
This application is a U.S. national stage application of PCT/JP2011/006194 filed on Nov. 7, 2011, the contents of which are incorporated herein by reference.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2011/006194 | 11/7/2011 | WO | 00 | 2/12/2014 |
