CN210792732U - Heat pump air conditioning system and vehicle - Google Patents
Heat pump air conditioning system and vehicle Download PDFInfo
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- CN210792732U CN210792732U CN201921425140.8U CN201921425140U CN210792732U CN 210792732 U CN210792732 U CN 210792732U CN 201921425140 U CN201921425140 U CN 201921425140U CN 210792732 U CN210792732 U CN 210792732U
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Abstract
The present disclosure relates to a heat pump air conditioning system and a vehicle, the system including a compressor, an indoor condenser, an indoor evaporator, and an outdoor heat exchanger, an outlet of the compressor being communicated with an inlet of the indoor condenser, an outlet of the indoor condenser being selectively communicated with a first port of the outdoor heat exchanger via a through-flow branch or with a second port of the outdoor heat exchanger via a first throttle branch, the first port of the outdoor heat exchanger being further communicated with an inlet of the compressor via a first return branch selectively opened or closed, the second port of the outdoor heat exchanger being further communicated with an inlet of the indoor evaporator via a second throttle branch, an outlet of the indoor evaporator being communicated with an inlet of the compressor via a second return branch, the outdoor heat exchanger having a plurality of heat exchanging regions sequentially arranged in a direction from the first port of the outdoor heat exchanger to the second port thereof, flow resistances of the plurality of heat exchanging regions being gradually increased in a direction from the first port of the outdoor heat exchanger to the second port thereof, so that the heat exchange capacity of the refrigerant is more uniform and the heat exchange effect is better.
Description
Technical Field
The present disclosure relates to the field of air conditioning systems, and more particularly, to a heat pump air conditioning system and a vehicle using the same.
Background
The heat pump air conditioning system mainly comprises a compressor, an indoor condenser, an indoor evaporator and an outdoor heat exchanger, wherein in a refrigeration mode, a high-temperature and high-pressure refrigerant discharged by the compressor is radiated to the outside in the outdoor heat exchanger, so that a low-temperature and low-pressure refrigerant can be evaporated in the indoor evaporator, indoor heat is absorbed, and indoor refrigeration is realized; in the heating mode, a high-temperature and high-pressure refrigerant discharged by the compressor is condensed in the indoor condenser, so that heat is released indoors, indoor heating is realized, and the refrigerant flowing out of the indoor condenser absorbs external heat in the outdoor heat exchanger and finally returns to the compressor.
In the prior art, in either the cooling mode or the heating mode, the refrigerant flows through the outdoor heat exchanger, and the refrigerant enters the outdoor heat exchanger from the same inlet of the outdoor heat exchanger and flows out of the outdoor heat exchanger from the same outlet. That is, regardless of the cooling mode or the heating mode, the refrigerant takes the same path when absorbing (condensing) or dissipating (evaporating) heat in the outdoor heat exchanger, and since the condensing and the evaporating are two opposite physical processes, the same flow path may limit the heat exchange performance of the refrigerant when condensing or evaporating in the outdoor heat exchanger.
SUMMERY OF THE UTILITY MODEL
An object of the present disclosure is to provide a heat pump air conditioning system capable of effectively improving heat exchange performance of an outdoor heat exchanger and overall energy efficiency of the entire heat pump air conditioning system, and a vehicle using the same.
In order to achieve the above object, the present disclosure provides a heat pump air conditioning system including a compressor, an indoor condenser, an indoor evaporator, and an outdoor heat exchanger, an outlet of the compressor being in communication with an inlet of the indoor condenser, an outlet of the indoor condenser being in communication with a first port of the outdoor heat exchanger selectively via a through-flow branch or with a second port of the outdoor heat exchanger via a first throttling branch, the first port of the outdoor heat exchanger being in communication with an inlet of the compressor further via a first return branch selectively turned on or off, the second port of the outdoor heat exchanger being in communication with an inlet of the indoor evaporator further via a second throttling branch, an outlet of the indoor evaporator being in communication with an inlet of the compressor via a second return branch, the outdoor heat exchanger having a plurality of heat exchanging regions sequentially arranged in a direction from the first port of the outdoor heat exchanger to the second port thereof, the flow area of the plurality of heat transfer areas gradually decreases from the first port of the outdoor heat exchanger to the second port thereof.
Optionally, a plurality of flow channels with the same cross-sectional area are formed in each heat exchange region, the flow channels in two adjacent heat exchange regions are communicated with each other, the first port of the outdoor heat exchanger is communicated with the flow channel in the closest heat exchange region, the second port of the outdoor heat exchanger is communicated with the flow channel in the closest heat exchange region, and the number of the flow channels in the plurality of heat exchange regions decreases in sequence in a direction from the first port of the outdoor heat exchanger to the second port of the outdoor heat exchanger.
Optionally, the outdoor heat exchanger is a microchannel heat exchanger, at least one flat tube is arranged in each heat exchange region, and a plurality of flow channels are formed in the flat tubes.
Optionally, the outdoor heat exchanger includes a first header and a second header disposed opposite to each other, the flow channel extends between the first header and the second header, a first dividing partition is disposed in the first header, the first dividing partition divides an inside of the first header into a first confluence portion and a second transition portion, a second dividing partition is disposed in the second header, the second dividing partition divides an inside of the second header into a second confluence portion and a first transition portion, the first port of the outdoor heat exchanger is disposed on the first confluence portion, and the second port of the outdoor heat exchanger is disposed on the second confluence portion;
the heat exchange areas comprise a first heat exchange area, a second heat exchange area and a third heat exchange area which are sequentially arranged along the direction from a first port of the outdoor heat exchanger to a second port of the outdoor heat exchanger, an inlet of a flow channel in the first heat exchange area is communicated with the first confluence part, an outlet of the flow channel in the first heat exchange area is communicated with the first transition part, an inlet of the flow channel in the second heat exchange area is communicated with the first transition part, an outlet of the flow channel in the second heat exchange area is communicated with the second transition part, an inlet of the flow channel in the third heat exchange area is communicated with the second transition part, and an outlet of the flow channel in the third heat exchange area is communicated with the second confluence part.
Optionally, a first switch valve is disposed on the through-flow branch, and a second switch valve is disposed on the first return branch.
Optionally, a first switch valve is arranged on the through-flow branch, the heat pump air conditioning system further includes a three-way valve, the three-way valve is located on the first return branch and the second return branch at the same time, an opening a of the three-way valve is communicated with the first opening of the outdoor heat exchanger, an opening B of the three-way valve is communicated with the outlet of the indoor evaporator, and an opening C of the three-way valve is communicated with the inlet of the compressor.
Optionally, a first expansion valve is disposed on the first throttle branch, and a second expansion valve is disposed on the second throttle branch.
Optionally, the heat pump air conditioning system further comprises a gas-liquid separator disposed at an inlet of the compressor, an inlet of the gas-liquid separator selectively communicating with the first port of the outdoor heat exchanger via the first return branch or with the indoor evaporator via the second return branch, and an outlet of the gas-liquid separator communicating with the indoor condenser.
Optionally, a check valve is arranged at an outlet of the indoor evaporator.
Through the technical scheme, because the refrigerant is subjected to heat release condensation in the outdoor heat exchanger in the refrigeration mode and is changed into the liquid state from the gas state, the pressure when the refrigerant enters the outdoor heat exchanger is high, the specific volume is large, the flow speed is high, the large flow area of the heat exchange area close to the first opening of the outdoor heat exchanger is beneficial to heat exchange of more refrigerants through the heat exchange area close to the first opening of the outdoor heat exchanger, the heat exchange efficiency is improved, along with the gradual change of the refrigerant from the gas state to the liquid state, the pressure, the specific volume and the flow speed are gradually reduced, the flow area of the heat exchange area is adaptive to the state change of the refrigerant and is gradually reduced, namely, the heat exchange capacity when the refrigerant enters the outdoor heat exchanger from the first opening of the outdoor heat exchanger and flows out from the second opening in the refrigeration mode is more uniform, and the heat exchange effect is better. Similarly, because the refrigerant absorbs heat and evaporates in the outdoor heat exchanger in the heating mode and changes from liquid state to gas state, the pressure when the refrigerant enters the outdoor heat exchanger is small, the specific volume is small, the flow rate is small, along with the evaporation, the dryness of the refrigerant is continuously increased, the pressure and the specific volume of the refrigerant are continuously increased, and the flow rate becomes fast, therefore, the refrigerant enters the outdoor heat exchanger from the second port of the outdoor heat exchanger and flows out from the first port to enable the refrigerant to be in the outdoor heat exchanger in the heating mode, the flow area of the refrigerant is favorably increased along with the process that the refrigerant is changed from liquid state to gas state, the amount of the refrigerant entering the heat exchange region is gradually increased from the second port to the first port of the outdoor heat exchanger, and the heat exchange capability of the refrigerant absorbing heat and evaporating in the outdoor heat exchanger is more uniform, and the heat exchange effect is.
According to another aspect of the present disclosure, a vehicle is provided that includes the heat pump air conditioning system described above.
Additional features and advantages of the disclosure will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description serve to explain the disclosure without limiting the disclosure. In the drawings:
fig. 1 is a schematic structural diagram of a heat pump air conditioning system according to an embodiment of the present disclosure;
fig. 2 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, in which the heat pump air-conditioning system is in a cooling mode, and a thick solid line indicates a flow path of a refrigerant in the cooling mode;
fig. 3 is a schematic structural diagram of a heat pump air-conditioning system according to an embodiment of the present disclosure, wherein the heat pump air-conditioning system is in a heating mode, and a thick solid line indicates a flow path of a refrigerant in the heating mode;
fig. 4 is a schematic structural diagram of a heat pump air conditioning system according to another embodiment of the present disclosure;
fig. 5 is a schematic structural view of an outdoor heat exchanger according to an embodiment of the present disclosure;
fig. 6 is a schematic structural view of an outdoor heat exchanger according to another embodiment of the present disclosure;
description of the reference numerals
1 compressor 2 indoor condenser
3 indoor evaporator 4 outdoor heat exchanger
4a first port 4b second port
41 first header 411 first dividing wall
412 first bus 413 second transition
42 second header 421 second dividing wall
422 second confluence 423 first transition
43 first heat transfer zone 44 second heat transfer zone
45 through-flow branch of third heat exchange zone 5
6 first throttle branch 7 first return branch
8 second throttle branch 9 second return branch
10 flat tube 11 first switch valve
12 second on-off valve 13 three-way valve
14 first expansion valve 15 second expansion valve
16 gas-liquid separator 17 one-way valve
Detailed Description
The following detailed description of specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.
As shown in fig. 1 to 6, the present disclosure provides a heat pump air conditioning system including a compressor 1, an indoor condenser 2, an indoor evaporator 3, and an outdoor heat exchanger 4, an outlet of the compressor 1 communicates with an inlet of the indoor condenser 2, an outlet of the indoor condenser 2 selectively communicates with a first port 4a of the outdoor heat exchanger 4 via a through-flow branch 5 or communicates with a second port 4b of the outdoor heat exchanger 4 via a first throttling branch 6, the first port 4a of the outdoor heat exchanger 4 further communicates with an inlet of the compressor 1 via a first return branch 7 that is selectively turned on or off, the second port 4b of the outdoor heat exchanger 4 further communicates with an inlet of the indoor evaporator 3 via a second throttling branch 8, and an outlet of the indoor evaporator 3 communicates with an inlet of the compressor 1 via a second return branch 9. Wherein, the outdoor heat exchanger 4 is provided with a plurality of heat exchange areas which are sequentially arranged along the direction from the first port 4a to the second port 4b of the outdoor heat exchanger 4, and the flow areas of the plurality of heat exchange areas are gradually reduced from the direction from the first port 4a to the second port 4b of the outdoor heat exchanger 4.
It should be noted that, in the above and the following, the "through branch" refers to a branch that can selectively achieve conduction or cutoff of the refrigerant, "the throttling branch" refers to a branch that can selectively achieve throttling or cutoff of the refrigerant and can adjust the flow rate and pressure of the refrigerant when throttling, "communication" may be direct communication or indirect communication between two devices.
By controlling the communication relationship among the devices, the heat pump air conditioning system disclosed by the invention at least has a cooling mode and a heating mode. In the cooling mode, as shown in fig. 2, the compressor 1, the indoor condenser 2, the through-flow branch 5, the outdoor heat exchanger 4, the second throttling branch 8, the indoor evaporator 3, and the second return branch 9 are sequentially connected in series to form a loop, and at this time, no air passes through the indoor condenser 2 and no air passes through the indoor evaporator 3, that is, although the refrigerant passes through the indoor condenser 2 in the cooling mode, no condensation occurs at the indoor condenser 2. Whether the air passes through the indoor condenser 2 and the indoor evaporator 3 can be controlled by controlling the air door mechanism, and since the air door mechanism is a well-known technology in the field of heat pump air conditioners, the working principle of the air door mechanism is not described in detail in the present disclosure. In a refrigeration mode, a high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the outdoor heat exchanger 4 from the first port 4a of the outdoor heat exchanger 4 through the through-flow branch 5, exchanges heat with outdoor air in the outdoor heat exchanger 4, releases heat and condenses, and radiates heat to the air, a medium-temperature and high-pressure liquid refrigerant flows out of the second port 4b of the outdoor heat exchanger 4, the medium-temperature and high-pressure liquid refrigerant is throttled and depressurized by the second throttling branch 8 to become a low-temperature and low-pressure liquid refrigerant, the low-temperature and low-pressure liquid refrigerant is evaporated in the indoor evaporator 3 to absorb indoor heat (such as a passenger compartment of a vehicle) to realize a refrigeration function, and finally the refrigerant flows back to the compressor 1 through the second return branch 9.
In the heating mode, as shown in fig. 3, the compressor 1, the indoor condenser 2, the first throttle branch 6, the outdoor heat exchanger 4, and the first return branch 7 are sequentially connected in series to form one circuit. In this mode, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 is subjected to heat release condensation in the indoor condenser 2, and releases heat to the indoor space, so as to realize indoor heating, the outlet of the indoor condenser 2 is a medium-temperature and high-pressure liquid refrigerant, the medium-temperature and high-pressure liquid refrigerant is subjected to throttling and pressure reduction by the first throttling branch 6 and then is changed into a low-temperature and low-pressure liquid refrigerant, the low-temperature and low-pressure liquid refrigerant enters the outdoor heat exchanger 4 through the second port 4b of the outdoor heat exchanger 4, and is subjected to heat absorption and evaporation in the outdoor heat exchanger 4, so that the low-temperature and low-pressure gaseous refrigerant flows out of the first port 4a of the outdoor heat exchanger 4.
As shown in fig. 5 and 6, in the cooling mode, the refrigerant flows into the outdoor heat exchanger 4 from the first port 4a of the outdoor heat exchanger 4 and flows out from the second port 4b of the outdoor heat exchanger 4, and in the warming mode, the refrigerant flows into the outdoor heat exchanger 4 from the second port 4b of the outdoor heat exchanger 4 and flows out from the first port 4a of the outdoor heat exchanger 4, and since the flow areas of the plurality of heat transfer areas in the outdoor heat exchanger 4 are gradually decreased in the direction from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof, the flow area of the refrigerant entering the outdoor heat exchanger 4 in the cooling mode is gradually decreased in the outdoor heat exchanger 4, and the flow area of the refrigerant entering the outdoor heat exchanger 4 in the warming mode is gradually increased in the outdoor heat exchanger 4.
Thus, according to the above technical solution, since the refrigerant is subjected to heat release condensation in the outdoor heat exchanger 4 in the refrigeration mode and changes from a gaseous state to a liquid state, the pressure of the refrigerant entering the outdoor heat exchanger 4 is high, the specific volume is large, and the flow rate is high, and the flow area of the heat exchange region near the first port 4a of the outdoor heat exchanger 4 is large, so that more refrigerants are subjected to heat exchange through the heat exchange region near the first port 4a of the outdoor heat exchanger 4, the heat exchange efficiency is improved, the heat release of the refrigerant is facilitated, and the refrigerant changes from a gaseous state to a liquid state, in the two-phase region, as the refrigerant gradually changes from a gaseous state to a liquid state, the pressure and the specific volume are gradually reduced, the flow rate is reduced, and the flow area of the heat exchange region is gradually reduced in accordance with the state change of the refrigerant, that is, in other words, the heat exchange capability of the refrigerant entering the outdoor heat exchanger 4 from the first port 4a of the outdoor heat exchanger 4 and flowing, The heat exchange effect is better. In the same way, since the refrigerant absorbs heat and evaporates in the outdoor heat exchanger 4 in the heating mode, changes from a liquid state to a gas state, therefore, the pressure, specific volume and flow rate of the refrigerant entering the outdoor heat exchanger 4 are small, the dryness of the refrigerant is continuously increased along with the evaporation, the pressure and specific volume of the refrigerant are continuously increased, the flow rate is increased rapidly, thus, the refrigerant can be made to flow into the outdoor heat exchanger 4 from the second port 4b of the outdoor heat exchanger 4 and flow out of the first port 4a in the exterior heat exchanger 4 in the warming mode, is favorable for increasing the flow area of the refrigerant along with the process of changing the refrigerant from liquid state to gas state, so that the amount of the refrigerant introduced into the heat exchange zone is gradually increased from the second port 4b to the first port 4a of the outdoor heat exchanger 4, and further, the heat exchange capability of the refrigerant for absorbing heat and evaporating in the outdoor heat exchanger 4 is more uniform, and the heat exchange effect is better.
Further, in order to achieve a gradual decrease in the flow area of the plurality of heat transfer zones from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof, in one embodiment provided by the present disclosure, as shown in fig. 5 and 6, a plurality of flow channels with the same cross-sectional area are formed in each heat exchange region, and the flow channels in two adjacent heat exchange regions are communicated with each other, so that the refrigerant can flow through the plurality of heat exchange areas in sequence for heat exchange, the first port 4a of the outdoor heat exchanger 4 is communicated with the flow channel in the closest heat exchange area, the second port 4b of the outdoor heat exchanger 4 is communicated with the flow channel in the closest heat exchange area, so that the refrigerant can enter the outdoor heat exchanger 4 through the first port 4a or the second port 4b and sequentially flow through the plurality of heat exchange regions in a direction from the first port 4a to the second port 4b, or sequentially flow through the plurality of heat exchange regions in a direction from the second port 4b to the first port 4 a. Wherein the number of flow passages in the plurality of heat transfer zones decreases in order in a direction from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof. Since the cross-sectional areas of the plurality of flow passages are the same, the flow area of the heat exchange region with the larger number of flow passages is larger than the flow area of the heat exchange region with the smaller number of flow passages, that is, the flow areas of the plurality of heat exchange regions gradually decrease from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof. Here, the microchannel heat exchanger may be a horizontal header microchannel heat exchanger as shown in fig. 5, or may be a vertical header microchannel heat exchanger as shown in fig. 6, to which the present disclosure is not limited.
In other embodiments, the number of the flow passages in the plurality of heat transfer zones may be the same, and the cross-sectional areas of the flow passages may be different, and the cross-sectional areas of the flow passages of the plurality of heat transfer zones decrease in sequence from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof, so that the flow areas of the plurality of heat transfer zones gradually decrease from the first port 4a of the outdoor heat exchanger 4 to the second port 4b thereof.
Further, the flow channels may be directly integrated into the casing of the outdoor heat exchanger 4, or the outdoor heat exchanger 4 may be a micro-channel heat exchanger, at least one flat tube 10 is provided in each heat exchange area, and a plurality of flow channels are formed in the flat tubes 10. The flow channel formed in the flat tube 10 is usually a fine flow channel formed by an extrusion process, which is beneficial to making the outdoor heat exchanger 4 compact and light in structure and efficient in heat exchange.
In order to enable the refrigerant to sequentially flow through the plurality of heat exchange areas, in one embodiment provided by the present disclosure, as shown in fig. 5 and 6, the outdoor heat exchanger 4 includes a first header 41 and a second header 42 which are oppositely disposed, a flow passage extends between the first header 41 and the second header 42, a first dividing partition 411 is disposed in the first header 41, the first dividing partition 411 divides the inside of the first header 41 into a first merging portion 412 and a second transition portion 413, a second dividing partition 421 is disposed in the second header 42, the second dividing partition 421 divides the inside of the second header 42 into a second merging portion 422 and a first transition portion 423, a first port 4a of the outdoor heat exchanger 4 is disposed on the first merging portion 412, and a second port 4b of the outdoor heat exchanger 4 is disposed on the second merging portion 422; the plurality of heat exchange regions include a first heat exchange region 43, a second heat exchange region 44, and a third heat exchange region 45 sequentially arranged in a direction from the first port 4a to the second port 4b of the outdoor heat exchanger 4, an inlet of a flow passage in the first heat exchange region 43 is communicated with the first confluence portion 412, an outlet of the flow passage in the first heat exchange region 43 is communicated with the first transition portion 423, an inlet of the flow passage in the second heat exchange region 44 is communicated with the first transition portion 423, an outlet of the flow passage in the second heat exchange region 44 is communicated with the second transition portion 413, an inlet of the flow passage in the third heat exchange region 45 is communicated with the second transition portion 413, and an outlet of the flow passage in the third heat exchange region 45 is communicated with the second confluence portion 422.
In this way, taking the example where the refrigerant flows in from the first port 4a of the exterior heat exchanger 4 and flows out from the second port 4b of the exterior heat exchanger 4, the refrigerant may pass through the first port 4a of the exterior heat exchanger 4, sequentially flow through the first merging portion 412, the first heat transfer region 43, the first transition portion 423, the second heat transfer region 44, the second transition portion 413, and the second merging portion 422, and finally flow out from the second port 4 b. The refrigerant may sequentially flow through the plurality of heat exchange areas by providing the first dividing partition 411 and the second dividing partition 421.
In order to selectively connect or disconnect the flow branch 5 and the first return branch 7 in the first embodiment of the present disclosure, as shown in fig. 1, a first switch valve 11 may be disposed on the flow branch 5, and a second switch valve 12 may be disposed on the first return branch 7. Alternatively, in order to facilitate the control of the first and second switching valves 11 and 12, the first and second switching valves 11 and 12 may be both electromagnetic switching valves.
In a second embodiment provided by the present disclosure, as shown in fig. 4, the through-flow branch 5 may be provided with a first on-off valve 11, the heat pump air conditioning system further includes a three-way valve 13, the three-way valve 13 is located on both the first return branch 7 and the second return branch 9, a port a of the three-way valve 13 is communicated with the first port 4a of the outdoor heat exchanger 4, a port B of the three-way valve 13 is communicated with the outlet of the indoor evaporator 3, and a port C of the three-way valve 13 is communicated with the inlet of the compressor 1. When it is necessary to conduct the communication between the first port 4a of the outdoor heat exchanger 4 and the inlet of the compressor 1 in the heating mode, the port a of the three-way valve 13 may be controlled to conduct with the port C, and when it is necessary to conduct the communication between the evaporator and the compressor 1 in the cooling mode, the port B of the three-way valve 13 may be controlled to conduct with the port C.
In order to realize throttling and pressure reduction of the first throttling branch 6 and the second throttling branch 8, in an embodiment provided by the present disclosure, as shown in fig. 1 and 4, a first expansion valve 14 may be disposed on the first throttling branch 6, and a second expansion valve 15 may be disposed on the second throttling branch 8. In other embodiments, further throttle elements, for example throttle valves, can also be provided on the first throttle branch 6 and the second throttle branch 8.
Furthermore, as shown in fig. 1 and 4, the heat pump air conditioning system may further include a gas-liquid separator 16 provided at an inlet of the compressor 1, the inlet of the gas-liquid separator 16 being selectively communicated with the first port 4a of the outdoor heat exchanger 4 via the first return branch 7 or with the indoor evaporator 3 via the second return branch 9, and the outlet of the gas-liquid separator 16 being communicated with the indoor condenser 2. The gas-liquid separator 16 is disposed at an inlet of the compressor 1 to further perform gas-liquid separation on the refrigerant entering the compressor 1, so as to ensure that the refrigerant entering the compressor 1 is a gaseous refrigerant.
In addition, a check valve 17 may be provided at an outlet of the interior evaporator 3 in order to prevent the refrigerant from flowing back to the interior evaporator 3.
The cycle process and principle of the heat pump air conditioning system provided by the present disclosure in different modes will be described in detail below by taking the embodiment in fig. 1 as an example and combining fig. 2 and 3.
A refrigeration mode: as shown in fig. 2, in this mode, the first switch valve 11 is opened, the second switch valve 12 is closed, the first expansion valve 14 is closed, the second expansion valve 15 is opened, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 enters the indoor condenser 2, no air passes through the indoor condenser 2, the outlet of the indoor condenser 2 is still the high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 4 from the first port 4a of the outdoor heat exchanger 4, and is subjected to heat release condensation with outdoor air in the outdoor heat exchanger 4 to dissipate heat into air, the medium-temperature and high-pressure liquid refrigerant flows out from the second port 4b of the outdoor heat exchanger 4, the high-temperature and high-pressure liquid refrigerant is throttled and depressurized by the second expansion valve 15 to be a low-temperature and low-pressure liquid refrigerant, and the low-temperature and low-pressure liquid refrigerant, the gaseous refrigerant is further separated by the gas-liquid separator 16 and finally returned to the compressor 1.
A heating mode: as shown in fig. 3, in this mode, the first switch valve 11 is closed, the second switch valve 12 is opened, the first expansion valve 14 is opened, and the second expansion valve 15 is closed, so that the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 enters the indoor condenser 2, is subjected to heat radiation and condensation in the indoor condenser 2, the outlet of the indoor condenser 2 is a medium-temperature and high-pressure liquid refrigerant, the medium-temperature and high-pressure liquid refrigerant is throttled and depressurized by the first expansion valve 14 to become a low-temperature and low-pressure liquid refrigerant, the low-temperature and low-pressure liquid refrigerant enters the outdoor heat exchanger 4 through the second port 4b of the outdoor heat exchanger 4, is subjected to heat absorption and evaporation in the outdoor heat exchanger 4, so that a low-temperature and low-pressure gaseous refrigerant flows out of the first port 4a of the outdoor heat exchanger 4, and the low-temperature and low.
According to another aspect of the present disclosure, a vehicle is provided that includes the heat pump air conditioning system described above.
The preferred embodiments of the present disclosure are described in detail with reference to the accompanying drawings, however, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solution of the present disclosure within the technical idea of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.
It should be noted that, in the foregoing embodiments, various features described in the above embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, various combinations that are possible in the present disclosure are not described again.
In addition, any combination of various embodiments of the present disclosure may be made, and the same should be considered as the disclosure of the present disclosure, as long as it does not depart from the spirit of the present disclosure.
Claims (10)
1. A heat pump air conditioning system, characterized by comprising a compressor (1), an indoor condenser (2), an indoor evaporator (3) and an outdoor heat exchanger (4), the outlet of the compressor (1) being in communication with the inlet of the indoor condenser (2), the outlet of the indoor condenser (2) being in communication selectively with a first port (4a) of the outdoor heat exchanger (4) via a through-flow branch (5) or with a second port (4b) of the outdoor heat exchanger (4) via a first throttling branch (6), the first port (4a) of the outdoor heat exchanger (4) being also in communication with the inlet of the compressor (1) via a first return branch (7) which is selectively switched on or off, the second port (4b) of the outdoor heat exchanger (4) being also in communication with the inlet of the indoor evaporator (3) via a second throttling branch (8), the outlet of the indoor evaporator (3) is communicated with the inlet of the compressor (1) through a second return branch (9), the outdoor heat exchanger (4) is provided with a plurality of heat exchange areas which are sequentially arranged along the direction from the first port (4a) to the second port (4b) of the outdoor heat exchanger (4), and the flow areas of the plurality of heat exchange areas are gradually reduced from the direction from the first port (4a) to the second port (4b) of the outdoor heat exchanger (4).
2. The heat pump air conditioning system according to claim 1, wherein a plurality of flow passages having the same cross-sectional area are formed in each of the heat transfer zones, and the flow passages in adjacent two heat transfer zones communicate with each other, the first port (4a) of the outdoor heat exchanger (4) communicates with the flow passage in its closest one of the heat transfer zones, the second port (4b) of the outdoor heat exchanger (4) communicates with the flow passage in its closest one of the heat transfer zones, and the number of flow passages in the plurality of heat transfer zones decreases in the order from the first port (4a) of the outdoor heat exchanger (4) to the second port (4b) thereof.
3. The heat pump air conditioning system according to claim 2, wherein the outdoor heat exchanger (4) is a microchannel heat exchanger, at least one flat tube (10) is disposed in each heat exchange zone, and a plurality of flow channels are formed in the flat tube (10).
4. Heat pump air conditioning system according to claim 2, characterized in that the outdoor heat exchanger (4) comprises a first header (41) and a second header (42) arranged opposite each other, the flow channel extending between the first header (41) and the second header (42), a first dividing partition (411) is provided in the first header (41), the first dividing partition (411) dividing the interior of the first header (41) into a first merging portion (412) and a second transition portion (413), a second dividing partition plate (421) is arranged in the second collecting pipe (42), the second dividing partition plate (421) divides the interior of the second collecting pipe (42) into a second confluence part (422) and a first transition part (423), the first port (4a) of the outdoor heat exchanger (4) is provided on the first merging portion (412), a second port (4b) of the outdoor heat exchanger (4) is provided on the second merging portion (422);
the plurality of heat exchange zones comprises a first heat exchange zone (43), a second heat exchange zone (44) and a third heat exchange zone (45) arranged in sequence in a direction from the first port (4a) of the outdoor heat exchanger (4) to the second port (4b) thereof, an inlet of a flow passage in the first heat transfer area (43) communicates with the first merging portion (412), an outlet of the flow passage in the first heat transfer zone (43) communicates with the first transition portion (423), an inlet of a flow passage in the second heat transfer zone (44) communicates with the first transition portion (423), the outlet of the flow channel in the second heat transfer zone (44) is communicated with the second transition part (413), the inlet of the flow channel in the third heat transfer zone (45) is communicated with the second transition part (413), an outlet of the flow passage in the third heat transfer area (45) communicates with the second merging portion (422).
5. The heat pump air conditioning system according to claim 1, characterized in that a first on-off valve (11) is provided on the through-flow branch (5) and a second on-off valve (12) is provided on the first return branch (7).
6. The heat pump air-conditioning system according to claim 1, wherein a first on-off valve (11) is disposed on the through-flow branch (5), the heat pump air-conditioning system further comprises a three-way valve (13), the three-way valve (13) is disposed on the first return branch (7) and the second return branch (9), a port a of the three-way valve (13) is communicated with the first port (4a) of the outdoor heat exchanger (4), a port B of the three-way valve (13) is communicated with the outlet of the indoor evaporator (3), and a port C of the three-way valve (13) is communicated with the inlet of the compressor (1).
7. Heat pump air conditioning system according to claim 1, characterized in that a first expansion valve (14) is provided in the first throttle branch (6) and a second expansion valve (15) is provided in the second throttle branch (8).
8. The heat pump air conditioning system according to claim 1, characterized in that it further comprises a gas-liquid separator (16) arranged at the inlet of said compressor (1), the inlet of said gas-liquid separator (16) being in communication selectively with said first port (4a) of said outdoor heat exchanger (4) via said first return branch (7) or with said indoor evaporator (3) via said second return branch (9), the outlet of said gas-liquid separator (16) being in communication with said indoor condenser (2).
9. Heat pump air conditioning system according to claim 1, characterized in that a non-return valve (17) is provided at the outlet of the indoor evaporator (3).
10. A vehicle comprising a heat pump air conditioning system according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921425140.8U CN210792732U (en) | 2019-08-29 | 2019-08-29 | Heat pump air conditioning system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921425140.8U CN210792732U (en) | 2019-08-29 | 2019-08-29 | Heat pump air conditioning system and vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210792732U true CN210792732U (en) | 2020-06-19 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921425140.8U Active CN210792732U (en) | 2019-08-29 | 2019-08-29 | Heat pump air conditioning system and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210792732U (en) |
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2019
- 2019-08-29 CN CN201921425140.8U patent/CN210792732U/en active Active
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