CN214928824U - Air conditioner heat pump system and electric automobile - Google Patents
Air conditioner heat pump system and electric automobile Download PDFInfo
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- CN214928824U CN214928824U CN202121135902.8U CN202121135902U CN214928824U CN 214928824 U CN214928824 U CN 214928824U CN 202121135902 U CN202121135902 U CN 202121135902U CN 214928824 U CN214928824 U CN 214928824U
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Abstract
The application provides an air conditioner heat pump system and electric automobile relates to the air conditioner field, includes: a compressor; an indoor heat exchanger; the heat recovery mechanism comprises a first heat exchange section and a second heat exchange section which exchange heat with each other; the air-conditioning heat pump system further comprises a first expansion valve, a second expansion valve, a fourth expansion valve, a first stop valve, a second stop valve, a third stop valve and an evaporator. The application provides an air conditioner heat pump system, under the condition that satisfies refrigeration and heating demand, for prior art greatly reduced the quantity of valve, reduced the leakage risk and the equipment degree of difficulty.
Description
Technical Field
The application relates to the technical field of air conditioners, in particular to an air conditioner heat pump system and an electric automobile.
Background
The existing air-conditioning heat pump systems applied to electric vehicles (such as pure electric vehicles and electric hybrid vehicles) generally adopt a plurality of valves. In some specific examples, the existing air-conditioning heat pump system has 4 one-way valves, 2 electronic expansion valves, 3 three-way valves, and 1 four-way reversing valve, i.e., 10 valves in total. Due to the high system pressure, there are correspondingly many possible leakage points for each more valve, thereby increasing the risk of leakage throughout the system. In addition, in the case of many valves, it is difficult to connect the valves when assembling the heat pump system. Therefore, the 10 valves adopted in the prior art actually have relatively high leakage risk and assembly difficulty, and increase the maintenance cost of the air-conditioning heat pump system.
Furthermore, the prior art air conditioning heat pump systems provide cooling and heating only to the passenger compartment, while there is usually little attention to the rest of the vehicle, which results in the prior art solutions not being fully functional in practice. In addition, the prior art air conditioning heat pump system has limited modes, namely, a cooling mode and a heating mode, and is not flexible.
SUMMERY OF THE UTILITY MODEL
The application provides an air-conditioning heat pump system and an electric automobile, which at least solve one of the technical problems.
In a first aspect, the present application provides an air conditioning heat pump system, comprising:
a compressor;
an indoor heat exchanger;
the heat recovery mechanism comprises a first heat exchange section and a second heat exchange section which exchange heat with each other;
the air-conditioning heat pump system also comprises a first expansion valve, a second expansion valve, a fourth expansion valve, a first stop valve, a second stop valve, a third stop valve and an evaporator;
the output end of the compressor is communicated with the first end of the indoor heat exchanger, the second end of the indoor heat exchanger is communicated with the first end of the second heat exchange section through the first stop valve, and the second end of the second heat exchange section is communicated with the input end of the first expansion valve;
the output end of the first expansion valve is communicated with the first end of the evaporator, and the second end of the evaporator is communicated with the first end of the third stop valve;
the second end of the third stop valve is communicated with the second end of the first heat exchange section, and the first end of the first heat exchange section is communicated with the input end of the compressor;
the output end of the second expansion valve is communicated with the second end of the second heat exchange section, and the input end of the second expansion valve is communicated with the first end of the evaporator;
the input end of the fourth expansion valve is communicated with the second end of the indoor heat exchanger, and the output end of the fourth expansion valve is communicated with the first end of the third stop valve;
and the first end of the second stop valve is communicated with the first end of the second heat exchange section, and the second end of the second stop valve is communicated with the second end of the first heat exchange section.
Preferably, the air-conditioning heat pump system comprises an outdoor heat exchanger, the second end of the indoor heat exchanger is communicated with the first end of the outdoor heat exchanger through the first stop valve, and the second end of the outdoor heat exchanger is communicated with the first end of the second heat exchange section.
Preferably, the air-conditioning heat pump system includes a third expansion valve and a heat generating component cooler;
the input end of the third expansion valve is communicated with the second end of the second heat exchange section, the output end of the third expansion valve is communicated with the first end of the heat generating component cooler, and the second end of the heat generating component cooler is communicated with the second end of the first heat exchange section.
Preferably, the working medium of the air-conditioning heat pump system is carbon dioxide.
Preferably, the first expansion valve, the second expansion valve, the third expansion valve and the fourth expansion valve are all electronic expansion valves.
Preferably, the air-conditioning heat pump system comprises a damper mechanism for blowing indoor air to the evaporator and the indoor heat exchanger respectively, and one or both of two air flows passing through the evaporator and the indoor heat exchanger are conveyed to the indoor by a temperature damper.
Preferably, the heat generating component cooler is a battery cooler.
Preferably, the heat recovery mechanism is configured to enable gas-liquid separation of the working medium before entering the second end of the first heat exchange section.
Preferably, the battery cooler is used for cooling a battery, the battery is used for an electric automobile, and the room is the interior of a passenger compartment of the electric automobile.
In a second aspect, the present application provides an electric vehicle comprising an air conditioning heat pump system as described above.
In a third aspect, the present application provides a method of controlling an air conditioning heat pump system, the method for controlling the system described above, the method comprising:
adjusting the system to: the second expansion valve is closed, the fourth expansion valve is closed, the first stop valve is opened, and the second stop valve is closed;
and adjusting the system to: at least one of the first expansion valve and the third expansion valve is opened; the third shut-off valve is closed only when only the third expansion valve of both the first expansion valve and the third expansion valve is open.
Preferably, the method further comprises:
further adjusting the system to: the air outlet of the temperature air door is only the air outlet of the evaporator; or the temperature air door does not output air or the output air of the temperature air door is mixed air of the evaporator and the indoor heat exchanger.
In a fourth aspect, the present application provides a method of controlling an air conditioning heat pump system, the method for controlling the system described above, the method comprising:
adjusting the system to: the first expansion valve is closed, the fourth expansion valve is opened, the first stop valve is closed, the second stop valve is opened, the third stop valve is closed, and the temperature air door is adjusted to be air outlet which is mixed air outlet of the evaporator and the indoor heat exchanger;
and adjusting the system to: both the second expansion valve and the third expansion valve are opened or only the second expansion valve of the second expansion valve and the third expansion valve is opened;
and adjusting the system to: the opening degree of the fourth expansion valve is maximum, and the second expansion valve is in a throttling state; or the fourth expansion valve is in a throttle state and the opening degree of the second expansion valve is maximum.
The application provides an air conditioner heat pump system, under the condition that satisfies refrigeration and heating demand, for prior art greatly reduced the quantity of valve, reduced the leakage risk and the equipment degree of difficulty.
In order to make the aforementioned objects, features and advantages of the present application more comprehensible, preferred embodiments accompanied with figures are described in detail below.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained from the drawings without inventive effort.
Fig. 1 is a schematic diagram illustrating a first embodiment of a circuit structure of an air-conditioning heat pump system according to the present application;
FIG. 2 is a schematic diagram illustrating a second embodiment of a circuit configuration of the air conditioning heat pump system of the present application;
FIG. 3 shows a schematic of the passenger compartment cooling mode of the present application;
FIG. 4 shows a schematic diagram of the battery cooling mode of the present application;
FIG. 5 is a schematic diagram illustrating a passenger compartment and battery common cooling mode of the subject application;
FIG. 6 shows a schematic of the heating mode of the present application;
fig. 7 shows a schematic diagram of the waste heat recovery heating mode of the present application.
Reference numerals:
1-an electric compressor; 2-indoor heat exchanger; 3-an evaporator; 4-outdoor heat exchanger; 5-a battery cooler; 6-a heat regeneration mechanism; 61-a heat regenerator; 62-a gas-liquid separator; 7-a first expansion valve; 8-a second expansion valve; 9-a third expansion valve; 10-a fourth expansion valve; 11-a first stop valve; 12-a second stop valve; 13-third stop valve.
Detailed Description
The technical solutions of the present application will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.
In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present application.
Referring to fig. 1, fig. 1 shows a first embodiment of an air-conditioning heat pump system provided in this embodiment, which includes an electric compressor, an indoor heat exchanger, an evaporator, an outdoor heat exchanger, a battery cooler, a heat recovery mechanism, a first expansion valve, a second expansion valve, a third expansion valve, a fourth expansion valve, a first stop valve, a second stop valve, and a third stop valve. The communication and the operation principle of the above components will be described in detail below.
It should be noted that, as an example, the air conditioning heat pump system in the present embodiment uses carbon dioxide (i.e., CO)2) As the working fluid, because carbon dioxide is a natural working fluid, ODP is 0 and GWP is 1. Here, ODP means ozone depletion Potential, GWP means Global Warming Potential, Global variationA warm potential. Due to the properties of carbon dioxide in both these respects, there are no environmental problems and potential uncertainty factors. This makes the air conditioning heat pump system that this embodiment provided safe nontoxic and environmental friendly.
In addition, the carbon dioxide can also run in a vapor compression cycle at the temperature lower than 0 ℃, and has the advantages of easy acquisition, no need of recovery, good heat transfer performance, small flow resistance, large dehumidification capacity and the like, and the characteristic of large refrigerating capacity per unit volume. The air-conditioning heat pump system still has good heating performance at low temperature, and can meet the heating requirement even in a severe environment of 20 ℃ below zero, so that the air-conditioning heat pump system can adapt to a relatively severe working environment and has high system energy efficiency. Therefore, in view of the fact that carbon dioxide is used as the working medium in the present embodiment, the electric compressor 1 in the present embodiment is correspondingly configured as a carbon dioxide electric compressor.
Further, in the embodiment, the above-mentioned four expansion valves may adopt electronic expansion valves, and the electronic expansion valves are ones that control the voltage or current applied to the expansion valves by using the electric signals generated by the adjusted parameters, so as to achieve the purpose of adjusting the liquid supply amount, and are suitable for the air-conditioning heat pump system with multiple working modes in this embodiment.
Specifically, the expansion valves used in the present embodiment have a one-way flow direction, and the direction in which the respective expansion valves allow the working medium to flow therethrough after being installed in the air-conditioning heat pump system will be described below with reference to the "through-flow direction". Namely, for any expansion valve, the through-flow direction of the working medium is as follows: the working medium can only flow from the input end to the output end of the expansion valve.
Further, in the first embodiment, the reflux mechanism employs a regenerator having a gas-liquid separation effect. In addition, the "indoor" and "outdoor" referred to herein may refer to the inside and outside of the passenger compartment, respectively, in the present embodiment.
On the basis of the above-described features, the communication relationship of the components in the air conditioning heat pump system in the first embodiment will be further described below.
As shown in fig. 1, in the following description, the communication relationship of the respective components will be described in detail, and is adaptively explained based on the orientation given in fig. 1. Wherein, the output end (lower end) of the electric compressor 1 is communicated with the lower end of the indoor heat exchanger 2. The upper end of the indoor heat exchanger 2 is communicated with the upper end of the outdoor heat exchanger 4 through a first stop valve 11, and the lower end of the outdoor heat exchanger 4 is communicated with the c end of the heat recovery mechanism 6.
Further, the end d of the heat recovery mechanism 6 is communicated with the end c, the end d of the heat recovery mechanism 6 is communicated with the input end (upper end) of the first expansion valve 7, and the output end (lower end) of the first expansion valve 7 is communicated with the end b of the evaporator. The end a of the evaporator is communicated with the upper end of a third stop valve 13, the lower end of the third stop valve 13 is communicated with the end b of the heat recovery mechanism 6, the end a of the heat recovery mechanism 6 is communicated with the end b, and the end a of the heat recovery mechanism 6 is communicated with the input end (upper end) of the electric compressor 1. It should be noted here that the ab section and the cd section of the heat recovery mechanism 6 exchange heat when flowing through working media with different temperatures.
On this basis, the input end (lower end) of the fourth expansion valve 10 of the air-conditioning heat pump system communicates with the second end (upper end) of the indoor heat exchanger 2, and the output end (upper end) of the fourth expansion valve 10 communicates with the upper end of the third cut-off valve 13.
Further, an input end (lower end) of a second expansion valve 8 of the air-conditioning heat pump system is communicated with the b end of the evaporator, and an output end (upper end) of the second expansion valve 8 is communicated with the d end of the heat recovery mechanism 6.
Further, an input end (upper end) of a third expansion valve 9 of the air-conditioning heat pump system is communicated with the d end of the heat regenerative mechanism 6, an output end (lower end) of the third expansion valve 9 is communicated with the lower end of the battery cooler 5, and the upper end of the battery cooler 5 is communicated with the b end of the heat regenerative mechanism 6.
Further, the upper end of the second stop valve 12 communicates with the upper end of the outdoor heat exchanger 4, and the lower end of the second stop valve 12 communicates with the b end of the regenerative mechanism 6.
Further, although not shown in the drawings, the evaporator and the indoor heat exchanger 2 are associated with two damper mechanisms in the passenger compartment, respectively. Taking the evaporator as an example, the air door mechanism corresponding to the evaporator blows the air in the passenger compartment through the evaporator, and then blows the air into the passenger compartment through the air door of the air door mechanism; similarly, the indoor heat exchanger 2 is also the same, and the description thereof is omitted.
The above is the first embodiment of the air-conditioning heat pump system. Referring to fig. 2, as a second embodiment of the air-conditioning heat pump system, the air-conditioning heat pump system provided in fig. 2 has some differences from the air-conditioning heat pump system provided in fig. 1, which are embodied in the heat recovery mechanism 6. Specifically, in the example given in fig. 2, the regenerative mechanism 6 in the example given in fig. 1 is replaced with a regenerator 61 and a gas-liquid separator 62. In the second embodiment, the regenerator 61 does not have a gas-liquid separation function, and is therefore incorporated in the gas-liquid separator 62. The regenerator 61 includes four end portions of a, b, c, and d at the same positions as those of the regenerative mechanism 6 in fig. 1, in which the communication relationship of the d end with the first expansion valve 7, the second expansion valve 8, and the third expansion valve 9 is the same as the example in fig. 1, except that the b end is connected in series with the aforementioned gas-liquid separator 62 with the lower end of the second stop valve 12.
On the basis of the air-conditioning heat pump system described above, the following will specifically describe the operating principle of the air-conditioning heat pump system by taking the first embodiment given in fig. 1 as an example, and the operating principle mainly relates to the description of 7 operating modes of the air-conditioning heat pump system, and the operating mode of the air-conditioning system is controlled by adjusting the opening degree of the electronic expansion valve, adjusting the on-off state of the stop valve, and adjusting the position of the temperature damper (i.e., the damper of the damper mechanism), so as to meet the cold and heat requirements of the whole vehicle.
The above operation modes will be described in detail in the following, but it should be noted that, although the following operation modes are described in the following order, this does not mean that the following operation modes must be performed in the following order, in other words, the operator can directly start one of the 7 operation modes and switch between different operation modes according to the actual operation mode of the operation modes.
As shown in fig. 3, in mode 1, the adjustment: the first expansion valve 7 throttles, the second expansion valve 8 closes, the third expansion valve 9 closes, the fourth expansion valve 10 closes, the first stop valve 11 opens, the second stop valve 12 closes, the third stop valve 13 opens, and the air outlet of the temperature air door is only the air outlet of the evaporator.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, then flows into the outdoor heat exchanger 4 through the first stop valve 11, and in this case, the indoor heat exchanger 2 and the outdoor heat exchanger 4 are used as air coolers together.
The refrigerant releases heat to the air in the indoor heat exchanger 2 and the outdoor heat exchanger 4, is converted into a transcritical state with lower temperature, flows into the heat regenerative mechanism 6 through the c end, releases heat to the low-temperature refrigerant entering the ab section from the b end of the heat regenerative mechanism 6, and is further cooled.
The cooled refrigerant flows into the first expansion valve 7 for throttling and is expanded into low-temperature and low-pressure two-phase fluid. The two-phase fluid flows into the evaporator to be evaporated and absorb heat, and then is changed into low-temperature and low-pressure superheated gas, and then flows into the b end of the heat recovery mechanism 6 through the third stop valve 13, so that the heat of the refrigerant entering from the c end of the heat recovery mechanism 6 is absorbed, the superheat degree is further improved, and the superheated refrigerant flows out through the a end of the heat recovery mechanism 6 and then enters the electric compressor 1 to be compressed, and then the next cycle is started.
Because the air outlet of the temperature air door is only the air outlet of the evaporator, and the two-phase fluid flows into the evaporator to evaporate and absorb heat, the air outlet of the temperature air door is low-temperature air, and the refrigerating requirement of the passenger compartment is met.
The 2 nd mode of operation is a battery cooling mode, which is suitable for situations where the battery needs to be cooled and the passenger compartment does not have a cooling or heating requirement.
As shown in fig. 4, in the 2 nd operating mode, the adjustment: the first expansion valve 7 is closed, the second expansion valve 8 is closed, the third expansion valve 9 throttles, the fourth expansion valve 10 is closed, the first stop valve 11 is opened, the second stop valve 12 is closed, the third stop valve 13 is closed, and the outlet air of the temperature regulating air door is only the outlet air of the evaporator 3, namely the outlet air at the ambient temperature.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, then flows into the outdoor heat exchanger 4 through the first stop valve 11, and in this case, the indoor heat exchangerThe heat exchanger 2 and the outdoor heat exchanger 4 together function as an air cooler.
The refrigerant releases heat to the air in the indoor heat exchanger 2 and the outdoor heat exchanger 4, is converted into a transcritical state with lower temperature, flows into the heat regenerative mechanism 6 through the c end, releases heat to the low-temperature refrigerant entering the ab section from the b end of the heat regenerative mechanism 6, and is further cooled.
The cooled refrigerant flows into the third expansion valve 9 for throttling and is expanded into a low-temperature low-pressure two-phase fluid. The two-phase fluid flows into the battery cooler 5 to be evaporated and absorb heat, is changed into low-temperature and low-pressure superheated gas, flows into the end b of the heat recovery mechanism 6, absorbs the heat of the refrigerant entering from the end c of the heat recovery mechanism 6 to further improve the superheat degree, flows out from the end a of the heat recovery mechanism 6, enters the electric compressor 1 to be compressed, and starts the next cycle.
In the above cycle process, the working medium in the battery cooler 5 is CO2And a coolant, CO, circulating in the battery cooler 5 and the battery circuit2And the heat exchange is carried out with the coolant, so that the temperature of the battery is reduced to realize the refrigeration of the battery.
The 3 rd working mode is a passenger compartment and battery cooling mode, which is suitable for the situation that the passenger compartment has the cooling requirement and the battery also needs to be cooled.
As shown in fig. 5, in the 3 rd mode of operation, the: the first expansion valve 7 is throttled, the second expansion valve 8 is closed, the third expansion valve 9 is throttled, the fourth expansion valve 10 is closed, the first stop valve 11 is opened, the second stop valve 12 is closed, the third stop valve 13 is opened, and the outlet air of the temperature regulating air door is only the outlet air of the evaporator.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, then flows into the outdoor heat exchanger 4 through the first stop valve 11, and the indoor heat exchanger 2 and the outdoor heat exchanger 4 are jointly used as air coolers.
The refrigerant releases heat to the air in the indoor heat exchanger 2 and the outdoor heat exchanger 4, is converted into a transcritical state with lower temperature, flows into the heat regenerative mechanism 6 through the c end, releases heat to the low-temperature refrigerant entering the ab section from the b end of the heat regenerative mechanism 6, and is further cooled.
The cooled refrigerant flows into the branch of the first expansion valve 7 and the branch of the third expansion valve 9 which are connected in parallel. The refrigerant is throttled by the third expansion valve 9 and expanded into a low-temperature low-pressure two-phase fluid, flows into the battery cooler 5 to be evaporated and absorbed heat, is changed into low-temperature low-pressure superheated gas, flows into the end b of the heat returning mechanism 6, and absorbs the heat of the refrigerant entering from the end c of the heat returning mechanism 6 to further improve the superheat degree. The other branch of refrigerant is throttled by the first expansion valve 7, expanded into a low-temperature low-pressure two-phase fluid, enters the evaporator to be evaporated and absorb heat, is changed into low-temperature low-pressure superheated gas, flows into the b end of the heat regenerative mechanism 6 through the third stop valve 13, and absorbs the heat of the refrigerant entering from the c end of the heat regenerative mechanism 6 to further improve the superheat degree.
After the refrigerants of the two branches are reheated, the refrigerants flow out of the end a of the reheating mechanism 6 and enter the electric compressor 1 to be compressed, and then the next cycle is started.
Wherein the working medium in the battery cooler 5 is CO2And a coolant, CO, circulating in the battery cooler 5 and the battery circuit2And the heat exchange is carried out with the coolant, so that the temperature of the battery is reduced to realize the refrigeration of the battery. Because the air outlet of the temperature air door is only the air outlet of the evaporator, and the two-phase fluid flows into the evaporator to evaporate and absorb heat, the air outlet of the temperature air door is low-temperature air, and the refrigerating requirement of the passenger compartment is met.
The 4 th working mode is a heating mode, and the working mode is suitable for the situation that the passenger compartment has the heating requirement.
As shown in fig. 6, the adjustment: the first expansion valve 7 is closed, the second expansion valve 8 is opened, the third expansion valve 9 is closed, the fourth expansion valve 10 is opened, the first stop valve 11 is closed, the second stop valve 12 is opened, the third stop valve 13 is closed, and the temperature regulating damper is mixed outlet air of the evaporator and the indoor heat exchanger 2.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, passes through the fourth expansion valve 10, and then enters the evaporator. The evaporator plays a different role in the system by adjusting the opening degree of the fourth expansion valve 10, as will be described in detail below.
In the first case, the opening degree of the fourth expansion valve 10 is adjusted to the maximum, that is, the fourth expansion valve 10 is in the full-flow state and the second expansion valve 8 is in the throttle state. In this case, the evaporator and the indoor heat exchanger 2 are used together as the air cooler. The refrigerant which is cooled after exchanging heat with air flows out from the end b of the evaporator and throttles by the second expansion valve 8 to become a low-temperature and low-pressure two-phase fluid, then enters the outdoor heat exchanger 4 after passing through the cd section of the heat regenerative mechanism 6, absorbs the heat of the outdoor air to become low-temperature and low-pressure superheated gas, and then returns to the inlet of the electric compressor 1 through the second stop valve 12 and the ab section of the heat regenerative mechanism 6 to start the next cycle.
In the first case, the air cooler has a large heat exchange area and high heat exchange efficiency, and compared with the operation mode that the indoor heat exchanger 2 is independently used as the air cooler, the air cooler can reduce the exhaust pressure and temperature under the condition that the heating capacity is not changed, reduce the energy consumption of the compressor and save more energy.
In the second case, the fourth expansion valve 10 is in the throttle state, and the opening degree of the second expansion valve 8 is adjusted to the maximum, that is, the second expansion valve 8 is in the full flow state. In this case, the evaporator and the outdoor heat exchanger 4 are used together as an evaporator. The refrigerant is throttled by the fourth expansion valve 10, expanded into a low-temperature low-pressure two-phase fluid, flows into the evaporator to absorb heat in the air, flows out, enters the outdoor heat exchanger 4 after passing through the second expansion valve 8 and the cd section of the heat regenerative mechanism 6 to continuously absorb heat, is evaporated into low-temperature low-pressure superheated gas, then returns to the input end of the electric compressor 1 through the second stop valve 12 and the ab section of the heat regenerative mechanism 6, and starts the next cycle.
Under the second condition, the evaporator has large heat exchange area and high heat exchange efficiency, and can reduce the evaporation temperature and pressure under the condition of unchanging heating quantity, thereby reducing the exhaust pressure and temperature, reducing the energy consumption of the compressor and saving more energy.
The 5 th working mode is a waste heat recovery heating mode, and the mode is suitable for the condition that the passenger compartment has a heating requirement and the battery loop has waste heat.
As shown in fig. 7, the adjustment: the first expansion valve 7 is closed, the second expansion valve 8 is throttled, the third expansion valve 9 is throttled, the fourth expansion valve 10 is throttled, the first stop valve 11 is closed, the second stop valve 12 is opened, the third stop valve 13 is closed, and the air outlet of the temperature air door is adjusted to be mixed air outlet of the evaporator and the indoor heat exchanger 2.
The 5 th operation mode is an operation mode in which the third expansion valve 9 is opened and the opening degree is adjusted to the throttle state in addition to the heating mode which is the 4 th operation mode. After the refrigerant flows through the second expansion valve 8, part of the refrigerant flows to the third expansion valve 9, exchanges heat with the battery coolant through the battery cooler 5, evaporates into superheated gas, merges with the superheated gas flowing out of the outdoor heat exchanger 4, flows into the heat recovery mechanism 6 from the b end of the heat recovery mechanism 6, flows back to the input end of the electric compressor 1 after passing through the ab end of the heat recovery mechanism 6, and starts the next cycle.
The 5 th working mode fully utilizes the waste heat of the battery, achieves two purposes at one stroke, and achieves the effects of energy conservation and emission reduction.
The 6 th mode is a dehumidification mode, which is suitable for situations where there is a need for dehumidification of the passenger compartment.
The adjustment of this operating mode is the same as in fig. 3, i.e. adjustment: the first expansion valve 7 throttles, the second expansion valve 8 closes, the third expansion valve 9 closes, the fourth expansion valve 10 closes, the first stop valve 11 opens, the second stop valve 12 closes, the third stop valve 13 opens, and the outlet air of the temperature regulating air door is only the outlet air of the evaporator.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, then flows into the outdoor heat exchanger 4 through the first stop valve 11, and the indoor heat exchanger 2 and the outdoor heat exchanger 4 are jointly used as air coolers.
The refrigerant releases heat to the air in the indoor heat exchanger 2 and the outdoor heat exchanger 4, is converted into a transcritical state with lower temperature, flows into the heat regenerative mechanism 6 through the c end, releases heat to the low-temperature refrigerant entering the ab section from the b end of the heat regenerative mechanism 6, and is further cooled.
The cooled refrigerant flows into the first expansion valve 7 for throttling and is expanded into low-temperature and low-pressure two-phase fluid. The two-phase fluid flows into the evaporator again to be evaporated and absorbed heat, and is changed into low-temperature and low-pressure superheated gas, and then flows into the b end of the heat recovery mechanism 6 through the third stop valve 13, so that the heat of the refrigerant entering from the c end of the heat recovery mechanism 6 is absorbed, the superheat degree is further improved, and the refrigerant flows out from the a end of the heat recovery mechanism 6 and enters the electric compressor 1 to be compressed, and then the next cycle is started.
In the 6 th working mode, the wind blowing through the evaporator is condensed on the surface of the evaporator, the humidity is reduced, and then the wind enters the passenger compartment to achieve the aim of dehumidification.
The 7 th working mode is a defrosting mode, and the working mode is suitable for the frosting condition of the outdoor heat exchanger 4.
The valve opening and closing conditions in this mode of operation are the same as in fig. 3, i.e. adjustment: the first expansion valve 7 throttles, the second expansion valve 8 closes, the third expansion valve 9 closes, the fourth expansion valve 10 closes, the first stop valve 11 opens, the second stop valve 12 closes, and the third stop valve 13 opens. The difference lies in that the temperature adjusting air door does not output air or the output air is mixed air of the evaporator and the indoor heat exchanger 2.
Low temperature low pressure gaseous refrigerant (CO)2) The refrigerant is compressed by the electric compressor 1 and converted into a supercritical state, flows into the indoor heat exchanger 2, then flows into the outdoor heat exchanger 4 through the first stop valve 11, and the indoor heat exchanger 2 and the outdoor heat exchanger 4 are jointly used as air coolers.
The refrigerant releases heat to the air in the indoor heat exchanger 2 and the outdoor heat exchanger 4, is converted into a transcritical state with a lower temperature, flows into the heat regenerative mechanism 6 through the c end of the heat regenerative mechanism 6, releases heat to the low-temperature refrigerant entering the b end of the heat regenerative mechanism 6, and is further cooled.
The cooled refrigerant flows into the first expansion valve 7 for throttling and is expanded into low-temperature and low-pressure two-phase fluid. The two-phase fluid flows into the evaporator again to be evaporated and absorbed heat, and is changed into low-temperature and low-pressure superheated gas, and then flows into the b end of the heat recovery mechanism 6 through the third stop valve 13, so that the heat of the refrigerant entering from the c end of the heat recovery mechanism 6 is absorbed, the superheat degree is further improved, and the refrigerant flows out from the a end of the heat recovery mechanism 6 and enters the electric compressor 1 to be compressed, and then the next cycle is started.
In the 7 th operation mode, the refrigerant inside the outdoor heat exchanger 4 flows to release heat to melt frost on the outer surface thereof.
Compared with the prior art, the air-conditioning heat pump system greatly reduces the number of valves, the leakage risk and the assembly difficulty. Seven modes are flexibly adjusted, and different cold and hot requirements of passengers under different external environments are met. The air-conditioning heat pump system not only meets the cold and hot demands of the passenger compartment, but also can cool the battery, so that the battery is kept at a relatively proper temperature, is fully charged and discharged, and effectively maintains the efficiency and the service life of the battery. The air-conditioning heat pump system can also utilize the waste heat of the battery, recover the waste heat and supply the waste heat to the passenger compartment (waste heat recovery heating), and is environment-friendly and efficient.
The embodiment further provides an electric vehicle, which includes the air conditioning heat pump system as described above, and also includes the above beneficial effects, which are not described herein again.
The embodiment also provides a control method of more than one air-conditioning heat pump system, and specifically comprises the following steps:
adjusting the system to: the second expansion valve 8 is closed, the fourth expansion valve 10 is closed, the first stop valve 11 is opened, and the second stop valve 12 is closed;
and adjusting the system to: at least one of the first expansion valve 7 and the third expansion valve 9 is opened; the third shut-off valve 13 is closed only when only the third expansion valve 9 of both the first expansion valve 7 and the third expansion valve 9 is open.
Further adjusting the system to: the air outlet of the temperature air door is only the air outlet of the evaporator; or the temperature air door does not output air or the output air of the temperature air door is mixed air of the evaporator and the indoor heat exchanger 2.
In this control method, the operation modes 1 to 3 and 6 and 7 are included, and the above operation modes are described in detail and are not described herein again.
In addition, the present embodiment further provides another control method for the air conditioning heat pump system, specifically:
adjusting the system to: the first expansion valve 7 is closed, the fourth expansion valve 10 is opened, the first stop valve 11 is closed, the second stop valve 12 is opened, the third stop valve 13 is closed, and the temperature air door is adjusted to be mixed air outlet of the evaporator and the indoor heat exchanger 2;
and adjusting the system to: both the second expansion valve 8 and the third expansion valve 9 are opened or only the second expansion valve 8 of the two is opened;
and adjusting the system to: the opening degree of the fourth expansion valve 10 is the largest, and the second expansion valve 8 is in a throttling state; alternatively, the fourth expansion valve 10 is in the throttle state, and the opening degree of the second expansion valve 8 is the maximum.
In this control method, the 4 th and 5 th operation modes are included, and since the above operation modes have been described in detail, they are not repeated here.
The above description is only a preferred embodiment of the present application, and not intended to limit the scope of the present application, and all changes that can be made in the details of the description and drawings, or directly/indirectly implemented in other related technical fields, are intended to be embraced therein without departing from the spirit of the present application.
Claims (10)
1. An air conditioning heat pump system, the air conditioning heat pump system comprising:
a compressor;
an indoor heat exchanger;
the heat recovery mechanism comprises a first heat exchange section and a second heat exchange section which exchange heat with each other;
the air-conditioning heat pump system is characterized by also comprising a first expansion valve, a second expansion valve, a fourth expansion valve, a first stop valve, a second stop valve, a third stop valve and an evaporator;
the output end of the compressor is communicated with the first end of the indoor heat exchanger, the second end of the indoor heat exchanger is communicated with the first end of the second heat exchange section through the first stop valve, and the second end of the second heat exchange section is communicated with the input end of the first expansion valve;
the output end of the first expansion valve is communicated with the first end of the evaporator, and the second end of the evaporator is communicated with the first end of the third stop valve;
the second end of the third stop valve is communicated with the second end of the first heat exchange section, and the first end of the first heat exchange section is communicated with the input end of the compressor;
the output end of the second expansion valve is communicated with the second end of the second heat exchange section, and the input end of the second expansion valve is communicated with the first end of the evaporator;
the input end of the fourth expansion valve is communicated with the second end of the indoor heat exchanger, and the output end of the fourth expansion valve is communicated with the first end of the third stop valve;
and the first end of the second stop valve is communicated with the first end of the second heat exchange section, and the second end of the second stop valve is communicated with the second end of the first heat exchange section.
2. The system of claim 1,
the air-conditioning heat pump system comprises an outdoor heat exchanger, a second end of the indoor heat exchanger is communicated with a first end of the outdoor heat exchanger through the first stop valve, and a second end of the outdoor heat exchanger is communicated with a first end of the second heat exchange section.
3. The system of claim 2,
the air-conditioning heat pump system comprises a third expansion valve and a heat generating component cooler;
the input end of the third expansion valve is communicated with the second end of the second heat exchange section, the output end of the third expansion valve is communicated with the first end of the heat generating component cooler, and the second end of the heat generating component cooler is communicated with the second end of the first heat exchange section.
4. The system of claim 3, wherein the working fluid of the air conditioning heat pump system is carbon dioxide.
5. The system of claim 3,
the first expansion valve, the second expansion valve, the third expansion valve and the fourth expansion valve are all electronic expansion valves.
6. The system of claim 3, wherein the air conditioning heat pump system includes a damper mechanism for directing air from the room toward the evaporator and the indoor heat exchanger, respectively, one or both of the two air streams passing through the evaporator and the indoor heat exchanger being delivered to the room by a temperature damper.
7. The system of claim 6, wherein the heat-generating component cooler is a battery cooler.
8. The system of claim 3, wherein the recuperative mechanism is configured to enable gas-liquid separation of the working fluid prior to entering the second end of the first heat exchange section.
9. The system of claim 7, wherein the battery cooler is configured to cool a battery used in an electric vehicle, and the compartment is an interior of a passenger compartment of the electric vehicle.
10. An electric vehicle characterized by comprising the air-conditioning heat pump system according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121135902.8U CN214928824U (en) | 2021-05-25 | 2021-05-25 | Air conditioner heat pump system and electric automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121135902.8U CN214928824U (en) | 2021-05-25 | 2021-05-25 | Air conditioner heat pump system and electric automobile |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214928824U true CN214928824U (en) | 2021-11-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202121135902.8U Active CN214928824U (en) | 2021-05-25 | 2021-05-25 | Air conditioner heat pump system and electric automobile |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN214928824U (en) |
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2021
- 2021-05-25 CN CN202121135902.8U patent/CN214928824U/en active Active
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| TR01 | Transfer of patent right |
Effective date of registration: 20221010 Address after: 200241 Floor 3, Building B, No. 940, Jianchuan Road, Minhang District, Shanghai Patentee after: Fuao Zhiyan (Shanghai) Automobile Technology Co.,Ltd. Address before: No. 777, Dongfeng South Street, automobile economic and Technological Development Zone, Changchun City, Jilin Province Patentee before: Fuao Automotive Parts Co.,Ltd. Patentee before: Thermal system technology branch of Fuao Auto Parts Co.,Ltd. |
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