CN210892242U - Heat exchange system - Google Patents
Heat exchange system Download PDFInfo
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- CN210892242U CN210892242U CN201921398930.1U CN201921398930U CN210892242U CN 210892242 U CN210892242 U CN 210892242U CN 201921398930 U CN201921398930 U CN 201921398930U CN 210892242 U CN210892242 U CN 210892242U
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- reversing valve
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- 238000010438 heat treatment Methods 0.000 claims abstract description 47
- 238000001816 cooling Methods 0.000 claims abstract description 32
- 238000005057 refrigeration Methods 0.000 claims abstract description 17
- 238000004891 communication Methods 0.000 claims description 27
- 238000001704 evaporation Methods 0.000 claims description 20
- 238000006073 displacement reaction Methods 0.000 claims description 10
- 238000007664 blowing Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 abstract description 19
- 230000008020 evaporation Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 7
- 238000007791 dehumidification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
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Abstract
The utility model provides a heat transfer system, heat transfer system includes first four-way reversing valve, second four-way reversing valve, first indoor heat exchanger, the indoor heat exchanger of second, outdoor heat exchanger and have the compressor of first cylinder and second cylinder, this scheme has carried out the association with the interface of first four-way reversing valve and second four-way reversing valve, get into first four-way reversing valve earlier from compressor exhaust refrigerant, then get into second four-way reversing valve through pipeline or other parts, when switching heat transfer system's refrigeration heating operation mode like this, can realize first four-way reversing valve and switch interface connected state earlier, then switch interface connected state behind the second four-way reversing valve, thereby can be smooth, realize heat transfer system's operation mode's switching reliably, the problem of switching failure has been avoided. And moreover, the indoor return air is subjected to gradient cooling and dehumidifying treatment, so that the system operation energy efficiency is improved under the condition of ensuring the system refrigerating capacity and dehumidifying capacity.
Description
Technical Field
The utility model relates to an air conditioner technical field particularly, relates to a heat transfer system.
Background
When air temperature and humidity are adjusted using an air conditioner, it is generally necessary to reduce the evaporator temperature to a level lower than the return air dew point temperature in order to satisfy dehumidification demand. From the perspective of energy efficiency of the refrigeration system, the lower the evaporation temperature, that is, the higher the suction-discharge pressure ratio of the compressor, the lower the energy efficiency of the system under the condition that the condensation temperature of the system is constant.
In order to solve the problem of low system energy efficiency caused by large temperature difference between return air temperature and evaporating temperature during the operation of an air conditioning system, a heat exchange system is provided in the prior art, namely two evaporators are respectively arranged in a single or same heat exchange channel, and indoor return air exchanges heat through the two evaporators successively so as to ensure that the evaporating temperature of one evaporator is higher than the evaporating temperature of a conventional system, thereby improving the system energy efficiency. However, the system uses two mutually independent four-way reversing valves, and when the refrigeration mode and the heating mode are switched, the two four-way reversing valves are required to synchronously act, so that the switching is successful. However, when the four-way reversing valve is used, synchronous operation of the two four-way reversing valves is not easy to guarantee, if the four-way reversing valves are not operated synchronously, one of the four-way reversing valves is normally reversed, and the other four-way reversing valve is not normally reversed, so that the switching of the operation mode is finally failed.
SUMMERY OF THE UTILITY MODEL
The utility model provides a heat transfer system to the problem of switching failure can appear when switching the mode of operation in the heat transfer system who solves among the prior art.
In order to solve the problems, the utility model provides a heat exchange system, including first four-way reversing valve, second four-way reversing valve, first indoor heat exchanger, second indoor heat exchanger, outdoor heat exchanger and have the compressor of first cylinder and second cylinder, wherein, the first D pipe of first four-way reversing valve communicates with the gas vent of compressor, the first E pipe of first four-way reversing valve communicates with one end of first indoor heat exchanger, the first S pipe of first four-way reversing valve communicates with the induction port of first cylinder, the first C pipe of first four-way reversing valve communicates with one end of outdoor heat exchanger; a second D pipe of a second four-way reversing valve is communicated with a first E pipe, a second C pipe of the second four-way reversing valve is communicated with one end of a second indoor heat exchanger, a second S pipe of the second four-way reversing valve is communicated with an air suction port of a second air cylinder, and the second E pipe of the second four-way reversing valve is communicated with the first C pipe in an on-off manner; the other end of the first indoor heat exchanger and the other end of the second indoor heat exchanger are communicated with the other end of the outdoor heat exchanger.
Further, the heat exchange system has a refrigeration mode, and under the condition that the heat exchange system is in the refrigeration mode, the first D pipe is communicated with the first C pipe, the first E pipe is communicated with the first S pipe, the second D pipe is communicated with the second E pipe, the second C pipe is communicated with the second S pipe, and the first C pipe is disconnected from the second E pipe.
Furthermore, the heat exchange system is also provided with a heating mode and a refrigerating-heating mode, and under the condition that the heat exchange system is in the refrigerating-heating mode, the first D pipe is communicated with the first E pipe, the first C pipe is communicated with the first S pipe, the second D pipe is communicated with the second E pipe, and the second C pipe is communicated with the second S pipe.
Further, the heat exchange system has a heating mode, and under the condition that the heat exchange system is in the heating mode, the first D pipe is communicated with the first E pipe, the first C pipe is communicated with the first S pipe, the second D pipe is communicated with the second C pipe, the second E pipe is communicated with the second S pipe, and the first C pipe is communicated with the second E pipe.
Furthermore, the heat exchange system is also provided with a refrigeration mode and a heating-to-refrigeration mode, and under the condition that the heat exchange system is in the heating-to-refrigeration mode, the first D pipe is communicated with the first C pipe, the first E pipe is communicated with the first S pipe, the second D pipe is communicated with the second C pipe, and the second E pipe is communicated with the second S pipe.
Further, under the condition that the heat exchange system is in the cooling mode, the evaporation temperature of the first indoor heat exchanger is higher than that of the second indoor heat exchanger.
Furthermore, the displacement of the first cylinder is V1, the displacement of the second cylinder is V2, the ratio of V1 to V2 is A, and A is more than or equal to 0.5 and less than or equal to 2.
Further, the heat exchange system still includes: the fan is used for blowing air towards the first indoor heat exchanger and the second indoor heat exchanger, and the first indoor heat exchanger is located between the fan and the second indoor heat exchanger.
Further, the heat exchange system still includes: and the electromagnetic valve is arranged on a pipeline connecting the first C pipe and the second E pipe to control the connection or disconnection of the first C pipe and the second E pipe.
Further, the heat exchange system still includes: the first expansion valve is arranged on a pipeline connecting the first indoor heat exchanger and the outdoor heat exchanger; and the second expansion valve is arranged on a pipeline connecting the second indoor heat exchanger and the outdoor heat exchanger.
Further, the heat exchange system still includes: one end of the third expansion valve is communicated with the other end of the outdoor heat exchanger, and the other end of the first indoor heat exchanger and the other end of the second indoor heat exchanger are communicated with the other end of the third expansion valve; and the throttling structure is arranged on a pipeline connecting the second indoor heat exchanger and the third expansion valve.
Further, the heat exchange area of the first indoor heat exchanger is A1, the heat exchange area of the second indoor heat exchanger is A2, the ratio of A1 to A2 is B, and B is more than or equal to 0.3 and less than or equal to 3.
Furthermore, the heat exchange system has a refrigeration mode and a heating mode, and under the condition that the heat exchange system is in the refrigeration mode, the first four-way reversing valve is in a power-off state, and the second four-way reversing valve is in a power-on state; under the condition that the heat exchange system is in a heating mode, the first four-way reversing valve is in an electrified state, and the second four-way reversing valve is in a power-off state.
By applying the technical scheme of the utility model, in a heat exchange system, a first D pipe of a first four-way reversing valve is communicated with an exhaust port of a compressor, a first E pipe of the first four-way reversing valve is communicated with one end of a first indoor heat exchanger, a first S pipe of the first four-way reversing valve is communicated with an air suction port of a first cylinder, and a first C pipe of the first four-way reversing valve is communicated with one end of an outdoor heat exchanger; the second D pipe of the second four-way reversing valve is communicated with the first E pipe, the second C pipe of the second four-way reversing valve is communicated with one end of the second indoor heat exchanger, the second S pipe of the second four-way reversing valve is communicated with the air suction port of the second air cylinder, and the second E pipe of the second four-way reversing valve is communicated with the first C pipe in a break-and-make mode. According to the scheme, the interfaces of the first four-way reversing valve and the second four-way reversing valve are associated, the refrigerant discharged from the compressor enters the first four-way reversing valve firstly, and then enters the second four-way reversing valve through a pipeline or other parts, so that when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve can be switched to be in the interface communication state, and then the second four-way reversing valve is switched to be in the interface communication state, so that the operation modes of the heat exchange system can be switched smoothly and reliably, and the problem of switching failure is avoided.
Through the technical scheme of the utility model, can realize following technological effect: two evaporators are arranged on the evaporator side, and the running energy efficiency of the system is improved by performing gradient cooling and dehumidifying treatment on indoor return air under the condition of ensuring the refrigerating capacity and dehumidifying capacity of the system; two four-way reversing valves are arranged between the compressor and the two indoor heat exchangers and are connected in a certain connection mode, and when the operation modes of the system are switched, the reliable switching of the operation modes is realized by switching the two four-way valves in sequence, so that the operation reliability of the system is improved; the requirement for stable switching of the operation modes of the heat exchange system is met through a reasonable control method.
Drawings
The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic diagram illustrating a heat exchange system in a cooling mode according to a first embodiment of the present invention;
FIG. 2 shows a schematic diagram of the heat exchange system of FIG. 1 in a cooling to heating mode;
FIG. 3 shows a schematic diagram of the heat exchange system of FIG. 1 in a heating mode;
FIG. 4 is a schematic diagram illustrating the heat exchange system of FIG. 1 in a heating to cooling mode;
fig. 5 shows a schematic diagram of the heat exchange system provided in the second embodiment of the present invention in a cooling mode;
fig. 6 shows a schematic diagram of the heat exchange system of fig. 5 in a heating mode.
Wherein the figures include the following reference numerals:
10. a first four-way reversing valve; 20. a second four-way reversing valve; 30. a first indoor heat exchanger; 40. a second indoor heat exchanger; 50. an outdoor heat exchanger; 60. a compressor; 61. a first cylinder; 62. a second cylinder; 74. an electromagnetic valve; 81. a first expansion valve; 82. a second expansion valve; 83. a third expansion valve; 84. and (4) a throttling structure.
Detailed Description
The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the embodiments described are only some embodiments of the invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
As shown in fig. 1 to 4, the first embodiment of the present invention provides a heat exchange system, which includes a first four-way reversing valve 10, a second four-way reversing valve 20, a first indoor heat exchanger 30, a second indoor heat exchanger 40, an outdoor heat exchanger 50, and a compressor 60 having a first cylinder 61 and a second cylinder 62, wherein a first D pipe of the first four-way reversing valve 10 is communicated with an exhaust port of the compressor 60, a first E pipe of the first four-way reversing valve 10 is communicated with one end of the first indoor heat exchanger 30, a first S pipe of the first four-way reversing valve 10 is communicated with an intake port of the first cylinder 61, and a first C pipe of the first four-way reversing valve 10 is communicated with one end of the outdoor heat exchanger 50; a second D pipe of the second four-way reversing valve 20 is communicated with a first E pipe, a second C pipe of the second four-way reversing valve 20 is communicated with one end of the second indoor heat exchanger 40, a second S pipe of the second four-way reversing valve 20 is communicated with an air suction port of the second air cylinder 62, and the second E pipe of the second four-way reversing valve 20 is communicated with the first C pipe in a switching mode; the other end of the first indoor heat exchanger 30 and the other end of the second indoor heat exchanger 40 are both communicated with the other end of the outdoor heat exchanger 50.
By applying the technical scheme of the embodiment, in the heat exchange system, the first D tube of the first four-way reversing valve 10 is communicated with the exhaust port of the compressor 60, the first E tube of the first four-way reversing valve 10 is communicated with one end of the first indoor heat exchanger 30, the first S tube of the first four-way reversing valve 10 is communicated with the suction port of the first cylinder 61, and the first C tube of the first four-way reversing valve 10 is communicated with one end of the outdoor heat exchanger 50; the second D pipe of the second four-way reversing valve 20 is communicated with the first E pipe, the second C pipe of the second four-way reversing valve 20 is communicated with one end of the second indoor heat exchanger 40, the second S pipe of the second four-way reversing valve 20 is communicated with the air suction port of the second cylinder 62, and the second E pipe of the second four-way reversing valve 20 is communicated with the first C pipe in a break-and-make manner. According to the scheme, the interfaces of the first four-way reversing valve 10 and the second four-way reversing valve 20 are associated, the refrigerant discharged from the compressor 60 enters the first four-way reversing valve 10 firstly, and then enters the second four-way reversing valve 20 through a pipeline or other parts, so that when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve 10 can be switched to the interface communication state firstly, and then the second four-way reversing valve 20 is switched to the interface communication state later, so that the switching of the operation modes of the heat exchange system can be smoothly and reliably realized, and the problem of switching failure is avoided.
As shown in fig. 1, in the drawing, a position marked with D of the first four-way reversing valve 10 is a first D pipe, a position marked with C is a first C pipe, a position marked with E is a first E pipe, and a position marked with S is a first S pipe, and the first D pipe, the first C pipe, the first E pipe, and the first S pipe can be understood as four ports of the first four-way reversing valve 10. In the figure, the position marked with D of the second four-way reversing valve 20 is the second D pipe, the position marked with E is the second E pipe, the position marked with C is the second C pipe, and the position marked with S is the second S pipe, and the second D pipe, the second E pipe, the second C pipe, and the second S pipe can be understood as four ports of the second four-way reversing valve 20.
In this embodiment, the heat exchange system has a cooling mode and a heating mode, and when the heat exchange system is in the cooling mode, the first four-way reversing valve 10 is in a power-off state, and the second four-way reversing valve 20 is in a power-on state; under the condition that the heat exchange system is in a heating mode, the first four-way reversing valve 10 is in an electrified state, and the second four-way reversing valve 20 is in a power-off state. Through the arrangement, the first four-way reversing valve 10 and the second four-way reversing valve 20 are in different electrifying states under the condition that the heat exchange system is in a cooling mode or a heating mode. Therefore, when the heat exchange system operates stably and switches the operation mode, the difference between the first four-way reversing valve 10 and the second four-way reversing valve 20 is increased, and the reliable switching of the operation mode and the normal operation of the heat exchange system can be further ensured.
In this embodiment, the evaporating temperature of the first indoor heat exchanger 30 and the evaporating temperature of the second indoor heat exchanger 40 may be set to different temperatures, that is, the evaporating temperature of one of the evaporators is higher than the evaporating temperature of the conventional system, so that the energy efficiency of the system may be improved.
As shown in fig. 1, the heat exchange system has a cooling mode, and when the heat exchange system is in the cooling mode, the first D tube is communicated with the first C tube, the first E tube is communicated with the first S tube, the second D tube is communicated with the second E tube, the second C tube is communicated with the second S tube, and the first C tube is disconnected from the second E tube.
At this time, high-pressure gas compressed by the compressor 60 passes through the first D tube of the first four-way reversing valve 10, then passes through the first C tube of the first four-way reversing valve 10 and enters the inlet of the outdoor heat exchanger 50, heat is released in the outdoor heat exchanger 50 and is condensed into high-pressure refrigerant liquid, the high-pressure refrigerant liquid enters the first indoor heat exchanger 30 and the second indoor heat exchanger 40 respectively, the high-pressure refrigerant liquid absorbs heat and is gasified in the two evaporators respectively, the gasified refrigerant gas is communicated with the first E tube of the first four-way reversing valve 10 and the second C tube of the second four-way reversing valve 20 respectively, and then the refrigerant gas is respectively conveyed to the first cylinder 61 and the second cylinder 62 of the compressor 60 through the first S tube and the second S tube to be compressed, so that the whole refrigeration cycle is completed.
As shown in fig. 2, in this embodiment, the heat exchange system further has a heating mode and a cooling-to-heating mode, and when the heat exchange system is in the cooling-to-heating mode, the first D tube is communicated with the first E tube, the first C tube is communicated with the first S tube, the second D tube is communicated with the second E tube, and the second C tube is communicated with the second S tube.
That is, when the cooling mode is switched to the heating mode, the first four-way reversing valve 10 completes the reversing first, the pressure difference between the first D tube and the first S tube of the first four-way reversing valve 10 is used to push the inner slide block to complete the reversing, and the schematic diagram of the system in which the first four-way reversing valve 10 completes the reversing and the second four-way reversing valve 20 does not reverse is shown in fig. 2. At this time, the second D tube of the second four-way selector valve 20 is in communication with the first E tube of the first four-way selector valve 10, at the discharge pressure high side, while the second S tube of the second four-way selector valve 20 is in communication with the second C tube, at the suction low side of the compressor 60. Therefore, the second four-way reversing valve 20 can utilize the pressure difference between the second D pipe and the second S pipe to push the sliding block to reverse, i.e., convert to the heating operation mode. And when the cold mode is switched to the heating mode, the first C pipe and the second E pipe are switched from off to on.
Through the arrangement, when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve 10 can be switched to be in the interface communication state, and then the second four-way reversing valve 20 is switched to be in the interface communication state, so that the switching of the operation modes of the heat exchange system can be smoothly and reliably realized, and the problem of switching failure is avoided.
As shown in fig. 3, in this embodiment, the heat exchange system has a heating mode, and when the heat exchange system is in the heating mode, the first D tube communicates with the first E tube, the first C tube communicates with the first S tube, the second D tube communicates with the second C tube, the second E tube communicates with the second S tube, and the first C tube communicates with the second E tube.
In this mode, the exhaust gas of the compressor 60 is connected to the second D-tubes of the first indoor heat exchanger 30 and the second four-way reversing valve 20 through the first D-tube and the first E-tube of the first four-way reversing valve 10, the second D-tube of the second four-way reversing valve 20 sends the exhaust gas of the compressor 60 to the second indoor heat exchanger 40 through the second C-tube of the second four-way reversing valve 20, so that the high-pressure refrigerant gas releases heat inside the first indoor heat exchanger 30 and the second indoor heat exchanger 40 and is condensed into high-pressure liquid, and then is sent to the outdoor heat exchanger 50, after absorbing heat and vaporizing in the outdoor heat exchanger 50, is sent to the first cylinder 61 and the second cylinder 62 of the compressor 60 through the first C-tube and the first S-tube of the first four-way reversing valve 10 and the second E-tube and the second S-tube of the second four-way reversing valve 20 to be compressed, thereby completing the entire heating cycle.
As shown in fig. 4, the heat exchange system further has a cooling mode and a heating-to-cooling mode, and when the heat exchange system is in the heating-to-cooling mode, the first D tube is communicated with the first C tube, the first E tube is communicated with the first S tube, the second D tube is communicated with the second C tube, and the second E tube is communicated with the second S tube.
That is, when the heating mode is switched to the cooling mode, the first four-way reversing valve 10 completes reversing by using a pressure difference between the first D tube and the second S tube thereof, at this time, the first C tube and the second E tube are switched from being communicated to being disconnected, the second D tube of the second four-way reversing valve 20 is connected to the first E tube of the first four-way reversing valve 10, the pressure is a suction pressure of the first indoor heat exchanger 30, at this time, the second S tube of the second four-way reversing valve 20 is in a vacuum state by suction of the compressor 60, and the second four-way reversing valve 20 can complete reversing by using a pressure difference between the second D tube and the second S tube at this time, and is switched to the cooling mode to operate. In this heat exchange system, various refrigerants such as R32, R410a, R134a, and R1234yf can be used as the refrigerant.
Through the arrangement, when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve 10 can be switched to be in the interface communication state, and then the second four-way reversing valve 20 is switched to be in the interface communication state, so that the switching of the operation modes of the heat exchange system can be smoothly and reliably realized, and the problem of switching failure is avoided.
In the present embodiment, in the case where the heat exchange system is in the cooling mode, the evaporation temperature of the first indoor heat exchanger 30 is higher than the evaporation temperature of the second indoor heat exchanger 40. Thus, the first indoor heat exchanger 30 has a high evaporation temperature and high energy efficiency, and the second indoor heat exchanger 40 has a low evaporation temperature and a good dehumidification effect, so that the energy efficiency of the heat exchange system can be improved under the condition of ensuring the refrigeration and dehumidification effects.
In the present embodiment, the exhaust port of the first cylinder 61 and the exhaust port of the second cylinder 62 are both communicated with the exhaust port of the compressor 60. Thus, the refrigerant compressed independently in the first cylinder 61 and the refrigerant compressed independently in the second cylinder 62 are mixed and discharged to be circulated.
In the embodiment, the displacement of the first cylinder 61 is V1, the displacement of the second cylinder 62 is V2, the ratio of V1 to V2 is A, and A is more than or equal to 0.5 and less than or equal to 2. With this arrangement, cooling, heating, and dehumidifying effects of the first and second indoor heat exchangers 30 and 40 can be ensured, and energy efficiency can be improved.
In the embodiment, the heat exchange area of the first indoor heat exchanger 30 is a1, the heat exchange area of the second indoor heat exchanger 40 is a2, the ratio of a1 to a2 is B, and B is greater than or equal to 0.3 and less than or equal to 3. With the above arrangement, the cooling, heating, and dehumidifying effects of the first and second indoor heat exchangers 30 and 40 can be further ensured, and energy efficiency can be improved.
For a heat exchange system having two heat exchangers (a high temperature evaporator and a low temperature evaporator, i.e., the first indoor heat exchanger 30 and the second indoor heat exchanger 40), the displacement ratio of the compressor is related to the load distribution of the high and low temperature evaporators. That is, under the refrigeration condition, in order to ensure the same heat exchange amount as that of the single-evaporator system, the evaporation temperature of the high-temperature evaporator is higher than that of the low-temperature evaporator, and the high-temperature evaporator and the low-temperature evaporator have an optimal temperature combination, so that the energy efficiency value of the heat exchange system with the two heat exchangers is optimal, and at the moment, the temperature difference value of the two evaporation temperatures is about 0.5 times of the air inlet and outlet temperature difference of the whole evaporator. If the load borne by the high-temperature evaporator is too high, the evaporation temperature of the high-temperature evaporator is reduced, and if the load borne by the high-temperature evaporator is too low, the evaporation temperature of the low-temperature evaporator is too low, and a preferable combination between the high-temperature evaporator and the low-temperature evaporator enables the energy efficiency of the heat exchange system to be better than that of a system with one evaporator.
Therefore, in order to ensure the cooling, heating and dehumidifying effects and improve energy efficiency, in the present application, the range of the ratio of the displacement of the first cylinder 61 to the displacement of the second cylinder 62 is set to be 0.5 ≤ a ≤ 2, and the range of the ratio of the heat exchange area of the first indoor heat exchanger 30 to the heat exchange area of the second indoor heat exchanger 40 is set to be 0.3 ≤ B ≤ 3. Preferably, a may be set to 1.25 and B may be set to 2. The energy efficiency improvement of the heat exchange system is a comprehensive effect of the effects of the first indoor heat exchanger 30 and the second indoor heat exchanger 40, so that the displacement ratio of two cylinders of the heat exchange system and the heat exchange area ratio of the two indoor heat exchangers are key factors for improving the energy efficiency of the system. The scheme carries out parameter limitation in a targeted manner, so that the system energy efficiency can be improved.
In the present embodiment, the first indoor heat exchanger 30 or the second indoor heat exchanger 40 may be a fin-and-tube heat exchanger, a microchannel heat exchanger, or another type of heat exchanger. The first indoor heat exchanger 30 and the second indoor heat exchanger 40 may be disposed in the same air duct, or may be disposed in different air ducts, respectively. The first indoor heat exchanger 30 may take the form of a radiant plate heat exchange. In the dehumidifying operation, the first indoor heat exchanger 30 mainly bears sensible heat load, and the second indoor heat exchanger 40 mainly bears indoor latent heat load.
In this embodiment, the heat exchange system further includes: and a blower for blowing air toward the first indoor heat exchanger 30 and the second indoor heat exchanger 40, the first indoor heat exchanger 30 being located between the blower and the second indoor heat exchanger 40. Through the arrangement, the gas to be subjected to heat exchange can firstly pass through the first indoor heat exchanger 30 for heat exchange and then passes through the second indoor heat exchanger 40 for heat exchange, so that the evaporating temperature of the first indoor heat exchanger 30 is higher than that of the second indoor heat exchanger 40.
In this embodiment, the heat exchange system further includes: and a solenoid valve 74, wherein the solenoid valve 74 is arranged on a pipeline connecting the first C pipe and the second E pipe to control the connection or disconnection of the first C pipe and the second E pipe. By arranging the solenoid valve 74, the connection or disconnection of the first pipe C and the second pipe E is conveniently controlled, and the working mode of the heat exchange system is conveniently controlled.
As shown in fig. 1 to 4, the heat exchange system further includes: a first expansion valve 81 provided on a pipe connecting the first indoor heat exchanger 30 and the outdoor heat exchanger 50; and a second expansion valve 82 provided on a pipe connecting the second indoor heat exchanger 40 and the outdoor heat exchanger 50. The first expansion valve 81 and the second expansion valve 82 can play a role in throttling and pressure reduction, so that the heat exchange system can stably and reliably operate.
As shown in fig. 5 and 6, in the second embodiment of the present invention, different from the above embodiment, the heat exchange system further includes: one end of the third expansion valve 83 is communicated with the other end of the outdoor heat exchanger 50, and the other ends of the first indoor heat exchanger 30 and the second indoor heat exchanger 40 are communicated with the other end of the third expansion valve 83; and a throttle structure 84 provided in a pipe connecting the second indoor heat exchanger 40 and the third expansion valve 83. The third expansion valve 83 and the throttle structure 84 perform throttling and pressure reduction in place of the first expansion valve 81 and the second expansion valve 82 in the above-described embodiment. Namely, the original two electronic expansion valves connected in parallel are replaced by an electronic expansion valve with a caliber larger than that of the original electronic expansion valve arranged in the loop of the first indoor heat exchanger 30, and a throttling structure 84 is arranged in the loop of the second indoor heat exchanger 40. Specifically, the throttling structure 84 may employ a throttling capillary tube.
In this embodiment, in the cooling mode, after the liquid high-pressure refrigerant at the outlet of the outdoor heat exchanger 50 is throttled by the third expansion valve 83, a part of the liquid high-pressure refrigerant directly enters the first indoor heat exchanger 30 (i.e., an indoor windward side high-temperature evaporator), and meanwhile, another part of the liquid high-pressure refrigerant is throttled again by the throttling structure 84 and enters the second indoor heat exchanger 40 (i.e., a leeward side low-temperature evaporator); in the heating mode, after the high-pressure refrigerant gas is condensed into high-pressure supercooled liquid in the indoor two heat exchangers, the refrigerant in the first indoor heat exchanger 30 (i.e., the indoor windward side condenser) directly enters the outdoor heat exchanger 50 after being throttled by the third expansion valve 83, and the refrigerant in the second indoor heat exchanger 40 (i.e., the leeward side condenser) enters the outdoor heat exchanger 50 after being throttled by the throttling structure 84 and then being throttled by the third expansion valve 83, thereby completing the system cycle.
The utility model discloses a control method for controlling above-mentioned heat transfer system includes: the heat exchange system is switched from a refrigeration mode to a heating mode, and in the switching process, the first four-way reversing valve 10 of the heat exchange system is controlled to reverse, and then the second four-way reversing valve 20 of the heat exchange system is controlled to reverse. By the mode, when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve 10 can be switched to the interface communication state firstly, and then the second four-way reversing valve 20 is switched to the interface communication state, so that the switching of the operation modes of the heat exchange system can be smoothly and reliably realized, and the problem of switching failure is avoided.
Specifically, in the process of switching from the cooling mode to the heating mode, the first four-way reversing valve 10 of the heat exchange system is controlled to reverse the direction, including: pushing a sliding block in the first four-way reversing valve 10 to move by using the pressure difference between a first D pipe and a first S pipe of the first four-way reversing valve 10, so that the first S pipe is communicated with a first E pipe of the first four-way reversing valve 10 and is switched to be communicated with the first S pipe and a first C pipe of the first four-way reversing valve 10, and the first D pipe is communicated with the first C pipe and is switched to be communicated with the first D pipe and the first E pipe; then controlling the second four-way reversing valve 20 of the heat exchange system to reverse comprises: pushing a sliding block in the second four-way reversing valve 20 to move by using the pressure difference between the second D tube and the second S tube of the second four-way reversing valve 20, so that the second S tube is communicated with the second C tube of the second four-way reversing valve 20 and is switched to be communicated with the second S tube and the second E tube of the second four-way reversing valve 20, and the second D tube is communicated with the second E tube and is switched to be communicated with the second D tube and the second C tube; and switching off the first C pipe and the second E pipe to be communicated.
Further, the control method further comprises: the heat exchange system is switched from a heating mode to a cooling mode, and in the switching process, the first four-way reversing valve 10 of the heat exchange system is controlled to reverse, and then the second four-way reversing valve 20 of the heat exchange system is controlled to reverse. By the mode, when the refrigerating and heating operation modes of the heat exchange system are switched, the first four-way reversing valve 10 can be switched to the interface communication state firstly, and then the second four-way reversing valve 20 is switched to the interface communication state, so that the switching of the operation modes of the heat exchange system can be smoothly and reliably realized, and the problem of switching failure is avoided.
Specifically, in the process of switching from the heating mode to the cooling mode, the first four-way reversing valve 10 of the heat exchange system is controlled to reverse the direction, including: pushing a sliding block in the first four-way reversing valve 10 to move by using the pressure difference between a first D pipe and a first S pipe of the first four-way reversing valve 10, so that the first S pipe is communicated with a first C pipe of the first four-way reversing valve 10 and is switched to be communicated with the first S pipe and a first E pipe of the first four-way reversing valve 10, and the first D pipe is communicated with the first E pipe and is switched to be communicated with the first D pipe and the first C pipe; then controlling the second four-way reversing valve 20 of the heat exchange system to reverse comprises: pushing a sliding block in the second four-way reversing valve 20 to move by using the pressure difference between the second D tube and the second S tube of the second four-way reversing valve 20, so that the second S tube is communicated with the second E tube of the second four-way reversing valve 20 and is switched to be communicated with the second S tube and the second C tube of the second four-way reversing valve 20, and the second D tube is communicated with the second C tube and is switched to be communicated with the second D tube and the second E tube; and switching the first C pipe and the second E pipe to be communicated and switching the first C pipe and the second E pipe to be disconnected.
Through the technical scheme of the utility model, can realize following technological effect: two evaporators are arranged on the evaporator side, and the running energy efficiency of the system is improved by performing gradient cooling and dehumidifying treatment on indoor return air under the condition of ensuring the refrigerating capacity and dehumidifying capacity of the system; two four-way reversing valves are arranged between the compressor and the two indoor heat exchangers and are connected in a certain connection mode, and when the operation modes of the system are switched, the reliable switching of the operation modes is realized by switching the two four-way valves in sequence, so that the operation reliability of the system is improved; the requirement for stable switching of the operation modes of the heat exchange system is met through a reasonable control method.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (13)
1. A heat exchange system, characterized by comprising a first four-way reversing valve (10), a second four-way reversing valve (20), a first indoor heat exchanger (30), a second indoor heat exchanger (40), an outdoor heat exchanger (50) and a compressor (60) having a first cylinder (61) and a second cylinder (62),
a first D pipe of the first four-way reversing valve (10) is communicated with an exhaust port of the compressor (60), a first E pipe of the first four-way reversing valve (10) is communicated with one end of the first indoor heat exchanger (30), a first S pipe of the first four-way reversing valve (10) is communicated with an air suction port of the first air cylinder (61), and a first C pipe of the first four-way reversing valve (10) is communicated with one end of the outdoor heat exchanger (50);
a second D pipe of the second four-way reversing valve (20) is communicated with the first E pipe, a second C pipe of the second four-way reversing valve (20) is communicated with one end of the second indoor heat exchanger (40), a second S pipe of the second four-way reversing valve (20) is communicated with a suction port of the second cylinder (62), and a second E pipe of the second four-way reversing valve (20) is communicated with the first C pipe in a switching mode;
the other end of the first indoor heat exchanger (30) and the other end of the second indoor heat exchanger (40) are both communicated with the other end of the outdoor heat exchanger (50).
2. The heat exchange system of claim 1, wherein the heat exchange system has a refrigeration mode, and when the heat exchange system is in the refrigeration mode, the first D-tube is in communication with the first C-tube, the first E-tube is in communication with the first S-tube, the second D-tube is in communication with the second E-tube, the second C-tube is in communication with the second S-tube, and the first C-tube is disconnected from the second E-tube.
3. The heat exchange system of claim 2, wherein the heat exchange system further has a heating mode and a cooling-to-heating mode, and when the heat exchange system is in the cooling-to-heating mode, the first D pipe is in communication with the first E pipe, the first C pipe is in communication with the first S pipe, the second D pipe is in communication with the second E pipe, and the second C pipe is in communication with the second S pipe.
4. The heat exchange system of claim 1, wherein the heat exchange system has a heating mode, and when the heat exchange system is in the heating mode, the first D tube is in communication with the first E tube, the first C tube is in communication with the first S tube, the second D tube is in communication with the second C tube, the second E tube is in communication with the second S tube, and the first C tube is in communication with the second E tube.
5. The heat exchange system according to claim 4, further comprising a cooling mode and a heating-to-cooling mode, wherein when the heat exchange system is in the heating-to-cooling mode, the first D pipe is communicated with the first C pipe, the first E pipe is communicated with the first S pipe, the second D pipe is communicated with the second C pipe, and the second E pipe is communicated with the second S pipe.
6. A heat exchange system according to claim 2, wherein the evaporating temperature of the first indoor heat exchanger (30) is higher than the evaporating temperature of the second indoor heat exchanger (40) with the heat exchange system in the cooling mode.
7. The heat exchange system of claim 1, wherein the first cylinder (61) has a displacement of V1, the second cylinder (62) has a displacement of V2, the ratio of V1 to V2 is A, and 0.5 ≦ A ≦ 2.
8. The heat exchange system of claim 1, further comprising:
a fan for blowing air toward the first indoor heat exchanger (30) and the second indoor heat exchanger (40), the first indoor heat exchanger (30) being located between the fan and the second indoor heat exchanger (40).
9. The heat exchange system of claim 1, further comprising:
a solenoid valve (74), wherein the solenoid valve (74) is arranged on a pipeline connecting the first C pipe and the second E pipe to control the connection or disconnection of the first C pipe and the second E pipe.
10. The heat exchange system of claim 1, further comprising:
a first expansion valve (81) provided on a pipe connecting the first indoor heat exchanger (30) and the outdoor heat exchanger (50);
and a second expansion valve (82) disposed on a pipe connecting the second indoor heat exchanger (40) and the outdoor heat exchanger (50).
11. The heat exchange system of claim 1, further comprising:
one end of the third expansion valve (83) is communicated with the other end of the outdoor heat exchanger (50), and the other end of the first indoor heat exchanger (30) and the other end of the second indoor heat exchanger (40) are both communicated with the other end of the third expansion valve (83);
and a throttle structure (84) provided on a pipe connecting the second indoor heat exchanger (40) and the third expansion valve (83).
12. The heat exchange system according to claim 1, wherein the heat exchange area of the first indoor heat exchanger (30) is A1, the heat exchange area of the second indoor heat exchanger (40) is A2, the ratio of A1 to A2 is B, and 0.3. ltoreq. B.ltoreq.3.
13. The heat exchange system of any one of claims 1 to 12, wherein the heat exchange system has a cooling mode and a heating mode,
under the condition that the heat exchange system is in the refrigeration mode, the first four-way reversing valve (10) is in a power-off state, and the second four-way reversing valve (20) is in a power-on state;
and under the condition that the heat exchange system is in the heating mode, the first four-way reversing valve (10) is in an electrified state, and the second four-way reversing valve (20) is in a power-off state.
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| CN201921398930.1U CN210892242U (en) | 2019-08-26 | 2019-08-26 | Heat exchange system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110425765A (en) * | 2019-08-26 | 2019-11-08 | 珠海格力电器股份有限公司 | heat exchange system and control method |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110425765A (en) * | 2019-08-26 | 2019-11-08 | 珠海格力电器股份有限公司 | heat exchange system and control method |
| CN110425765B (en) * | 2019-08-26 | 2023-10-10 | 珠海格力电器股份有限公司 | Heat exchange system and control method |
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