CN107356023B - Heat pump air conditioning system and electric automobile - Google Patents
Heat pump air conditioning system and electric automobile Download PDFInfo
- Publication number
- CN107356023B CN107356023B CN201610310423.2A CN201610310423A CN107356023B CN 107356023 B CN107356023 B CN 107356023B CN 201610310423 A CN201610310423 A CN 201610310423A CN 107356023 B CN107356023 B CN 107356023B
- Authority
- CN
- China
- Prior art keywords
- valve
- outlet
- heat exchanger
- inlet
- branch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00007—Combined heating, ventilating, or cooling devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
the invention discloses a heat pump air conditioning system and an electric automobile, the system comprises a compressor and an indoor condenser, the indoor condenser is communicated with the indoor evaporator through a first throttling branch or a first through-flow branch, the outdoor heat exchanger is communicated with a low-pressure air inlet of the compressor through a second through-flow branch or communicated with the indoor evaporator through a second throttling branch, the indoor evaporator is communicated with a low-pressure air inlet of the compressor, the indoor condenser is communicated with the outdoor heat exchanger through a first enthalpy-increasing branch which is connected or disconnected, the outdoor heat exchanger is communicated with a medium-pressure air inlet of the compressor through a second enthalpy-increasing branch, the first enthalpy-increasing branch and the second enthalpy-increasing branch exchange heat through a first plate heat exchanger, a first expansion valve is arranged on the second enthalpy-increasing branch, and the outdoor heat exchanger is communicated with the first plate heat exchanger through the first expansion valve. Therefore, the effects of improving heating energy efficiency, meeting the requirements of defrosting and demisting regulations and the like can be achieved.
Description
Technical Field
The invention relates to the field of air conditioners of electric automobiles, in particular to a heat pump air conditioning system and an electric automobile.
Background
the electric automobile does not have the engine waste heat that traditional car was used for the heating, can't provide the heating heat source. Therefore, the air conditioning system of the electric vehicle must have a heating function itself, that is, a heat pump type air conditioning system and/or electric heating is used.
The invention patent application with the publication number of CN102788397A discloses a heat pump air-conditioning system of an electric automobile. Although the heat pump air-conditioning system can be used in various electric automobiles, the system uses two outdoor heat exchangers (an outdoor condenser and an outdoor evaporator), so that the wind resistance of an automobile front-end module is large, the system structure is complex, and the heating effect is influenced.
Disclosure of Invention
The invention aims to provide a heat pump air-conditioning system and an electric automobile, which are used for solving the problems that a pure electric vehicle or a hybrid vehicle without an engine waste heat circulating system uses an automobile heat pump air-conditioning system in a pure electric mode, the heating energy efficiency is low, the requirements of defrosting and demisting regulations cannot be met, the installation is complex and the like, and the heating performance of the electric automobile can be obviously improved.
In order to achieve the above object, according to a first aspect of the present invention, there is provided 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 an inlet of the outdoor heat exchanger selectively via a first throttling branch or a first through-flow branch, an outlet of the outdoor heat exchanger being in communication with a low pressure air inlet of the compressor selectively via a second through-flow branch or with an inlet of the indoor evaporator via a second throttling branch, an outlet of the indoor evaporator being in communication with a low pressure air inlet of the compressor, an outlet of the indoor condenser being in communication with an inlet of the outdoor heat exchanger further via a first enthalpy increasing branch which is selectively turned on or off, an outlet of the outdoor heat exchanger being in communication with a medium pressure air inlet of the compressor further via a second enthalpy increasing branch, the first enthalpy-increasing branch and the second enthalpy-increasing branch exchange heat through the first plate heat exchanger, a first expansion valve is arranged on the second enthalpy-increasing branch, and an outlet of the outdoor heat exchanger is communicated with the first plate heat exchanger through the first expansion valve.
Optionally, a first switching valve is disposed on the first enthalpy-increasing branch, and an outlet of the indoor condenser is communicated with the first plate heat exchanger through the first switching valve.
Optionally, a second switch valve is disposed on the first through-flow branch, and a second expansion valve is disposed on the first throttle branch.
Optionally, the system further includes an expansion switch valve, an inlet of the expansion switch valve is communicated with an outlet of the indoor condenser, an outlet of the expansion switch valve is communicated with an inlet of the outdoor heat exchanger, the first throttling branch is a throttling flow passage of the expansion switch valve, and the first through-flow branch is a through-flow passage of the expansion switch valve.
Optionally, a third on-off valve is disposed in the second bypass branch, and a third expansion valve is disposed in the second throttle branch.
Optionally, the outlet of the indoor evaporator is in communication with the low pressure inlet of the compressor via a one-way valve.
Optionally, the heat pump air conditioning system is applied to an electric vehicle, and a second plate heat exchanger is further arranged on the second bypass and is arranged in a motor cooling system of the electric vehicle.
Optionally, a third on-off valve is disposed in the second bypass, a refrigerant inlet of the second plate heat exchanger is communicated with an outlet of the outdoor heat exchanger, and a refrigerant outlet of the second plate heat exchanger is communicated with an inlet of the third on-off valve.
optionally, the motor cooling system comprises a motor, a motor radiator and a water pump connected in series with the second plate heat exchanger to form a loop.
Optionally, the system further comprises a gas-liquid separator, an outlet of the indoor evaporator is communicated with an inlet of the gas-liquid separator, an outlet of the outdoor heat exchanger is communicated with an inlet of the gas-liquid separator via the second flow bypass, and an outlet of the gas-liquid separator is communicated with a low-pressure gas inlet of the compressor.
Optionally, the system further comprises a PTC heater for heating the wind flowing through the indoor condenser.
Optionally, the PTC heater is disposed on a windward side or a leeward side of the indoor condenser.
According to a second aspect of the present invention, there is provided an electric vehicle comprising the heat pump air conditioning system of the first aspect of the present invention.
The heat pump air-conditioning system provided by the invention can realize the refrigeration and heating functions of the automobile air-conditioning system and the defrosting function of the outdoor heat exchanger under the condition of not changing the circulation direction of the refrigerant, and can meet the requirements of simultaneous refrigeration and heating. In the bypass defrosting process of the outdoor heat exchanger, the requirement of heating in the vehicle can be still met. In addition, because the heat pump air-conditioning system only adopts one outdoor heat exchanger, the wind resistance of the front-end module of the automobile can be reduced, the problems that a pure electric vehicle or a hybrid vehicle without an engine waste heat circulating system uses an automobile heat pump air-conditioning system in a pure electric mode, the heating energy efficiency is low, the requirements of defrosting and demisting regulations cannot be met, the installation is complex and the like are solved, and the effects of reducing energy consumption, simplifying the system structure and facilitating pipeline arrangement are achieved. In addition, the enthalpy-increasing branch is arranged in the system, so that the low-temperature heating performance of the system can be obviously improved. The heat pump air conditioning system provided by the invention has the characteristic of simple structure, so that the mass production is easy.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
drawings
The accompanying drawings, which 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 principles of the invention and not to limit the invention. In the drawings:
Fig. 1 is a schematic structural view of a heat pump air conditioning system according to an embodiment of the present invention;
Fig. 2 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 3 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 4 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 5 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 6 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 7 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
Fig. 8 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention;
FIG. 9 is a schematic diagram of a top view of an expansion switch valve provided in accordance with a preferred embodiment of the present invention;
FIG. 10 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, wherein both the first and second ports are in an open state;
Fig. 11 is a front structural view in one perspective of an expansion switching valve provided in a preferred embodiment of the present invention;
FIG. 12 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, with the first port in an open state and the second port in a closed state;
FIG. 13 is a schematic cross-sectional view taken along line AB-AB of FIG. 9, with the first port in a closed position and the second port in an open position;
Fig. 14 is a front view schematically illustrating the construction of the expansion switching valve according to another view in accordance with the preferred embodiment of the present invention;
FIG. 15 is a schematic cross-sectional view taken along line AC-AC of FIG. 14, wherein the first port is in an open state and the second port is in a closed state;
Fig. 16 is a first internal structural view of the expansion switching valve according to the preferred embodiment of the present invention, in which the first port and the second port are both in an open state;
fig. 17 is a partially enlarged view of a portion a in fig. 16;
fig. 18 is a second internal structural view of the expansion switching valve according to the preferred embodiment of the present invention, wherein the first port is in an open state and the second port is in a closed state;
fig. 19 is a third internal structural view of the expansion switch valve according to the preferred embodiment of the present invention, wherein the first valve port is in a closed state and the second valve port is in an open state.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present invention, are given by way of illustration and explanation only, not limitation.
In the present invention, unless otherwise specified, terms of orientation such as "upper, lower, left, and right" are generally used with respect to the direction of the drawing of the drawings, "upstream, and downstream" are used with respect to the medium, e.g., the flow direction of the refrigerant, specifically, the downstream direction is toward the flow direction of the refrigerant, and the upstream direction is away from the flow direction of the refrigerant, "inner and outer" refer to the inner and outer of the contour of the corresponding component.
In addition, in the present invention, the electric vehicle may include a pure electric vehicle, a hybrid vehicle, and a fuel cell vehicle.
Fig. 1 is a schematic configuration diagram of a heat pump air conditioning system according to an embodiment of the present invention. As shown in fig. 1, the system may include: an HVAC (Heating Ventilation and Air Conditioning) assembly 600 and a damper mechanism (not shown), wherein the HVAC assembly 600 may include an indoor condenser 601 and an indoor evaporator 602. The damper mechanism may be used to open a duct leading to the indoor evaporator 602 and the indoor condenser 601. As shown in fig. 1, an outlet of the compressor 604 communicates with an inlet of the indoor condenser 601, an outlet of the indoor condenser 601 selectively communicates with an inlet of the outdoor heat exchanger 605 via a first throttling branch or a first flow-through branch, an outlet of the outdoor heat exchanger 605 selectively communicates with an inlet of the indoor evaporator 602 via a second throttling branch or a second flow-through branch, and an outlet of the indoor evaporator 602 communicates with a low pressure air inlet 604a of the compressor 604. The outlet of the indoor condenser 601 is further communicated with the inlet of the outdoor heat exchanger 605 through a first enthalpy-increasing branch 621 which is selectively opened or closed, the outlet of the outdoor heat exchanger 605 is further communicated with the medium-pressure air inlet 604b of the compressor 604 through a second enthalpy-increasing branch 622, the first enthalpy-increasing branch 621 exchanges heat with the second enthalpy-increasing branch 622 through the first plate heat exchanger 620, the second enthalpy-increasing branch 622 is provided with a first expansion valve 623, and the outlet of the outdoor heat exchanger 605 is communicated with the first plate heat exchanger 620 through the first expansion valve 623. The first enthalpy-increasing branch 621 and the second enthalpy-increasing branch 622 are used for conducting in an ultra-low temperature heating mode, which is described below, and the performance of the system in an ultra-low temperature environment can be remarkably improved. Specifically, the first enthalpy increasing branch 621 may be provided with a first switching valve 624, and an outlet of the indoor condenser 601 is communicated with the first plate heat exchanger 620 through the first switching valve 624, that is, the first enthalpy increasing branch 621 is turned on or off under the control of the first switching valve 624. It should be further noted that the second enthalpy-increasing branch 622 is provided with a first expansion valve 623, and the first expansion valve 623 can realize the connection or the disconnection of the second enthalpy-increasing branch 622 by adjusting the opening degree.
In the present invention, the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via either the first throttling branch or the first circulating branch. This communication may be accomplished in a number of ways. For example, in one embodiment, as shown in fig. 1, the heat pump air conditioning system may further include an expansion switch valve 603, an inlet of the expansion switch valve 603 is communicated with an outlet of the indoor condenser 601, an outlet of the expansion switch valve 603 is communicated with an inlet of the outdoor heat exchanger 605, wherein the first throttling branch is a throttling flow passage of the expansion switch valve 603, and the first through-flow branch is a through-flow passage of the expansion switch valve 603.
In the present invention, the expansion switch valve is a valve having both an expansion valve function, which may be referred to as an electronic expansion valve function, and a switch valve function, which may be referred to as a solenoid valve function, and may be considered as an integration of the switch valve and the expansion valve. A through flow channel and a throttling flow channel are formed in the expansion switch valve, when the expansion switch valve is used as the switch valve, the through flow channel in the expansion switch valve is conducted, and a through flow branch is formed at the moment; when the expansion switch valve is used as an expansion valve, the throttling flow passage in the expansion switch valve is communicated, and a throttling branch is formed at the moment.
As another alternative embodiment, as shown in fig. 2, the heat pump air conditioning system may further include a second on-off valve 608 and a second expansion valve 607, wherein the second on-off valve 608 is disposed on the first through-flow branch, and the second expansion valve 607 is disposed on the first throttle branch. Specifically, as shown in fig. 2, an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a second switching valve 608 to form a first through-flow branch, and an outlet of the indoor condenser 601 communicates with an inlet of the outdoor heat exchanger 605 via a second expansion valve 607 to form a first throttle branch. When the system is in the high-temperature cooling mode, the second switching valve 608 is turned on, the second expansion valve 607 is closed, and the outlet of the indoor condenser 601 is communicated with the inlet of the outdoor heat exchanger 605 via the first through-flow branch. When the system is in the low temperature heating mode, the second expansion valve 607 is turned on, the second switching valve 608 is closed, and the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via the first throttling branch.
In order to facilitate piping and save space, it is preferable to use an expansion switch valve 603 in the heat pump air conditioning system provided by the present invention, i.e., the embodiment shown in fig. 1.
Similar to the first flow branch and the first throttle branch in the above alternative embodiment, as shown in fig. 1, a third on/off valve 610 is disposed on the second flow branch, and a third expansion valve 609 is disposed on the second throttle branch. As shown in fig. 1, the heat pump air conditioning system may further include a third on/off valve 610 and a third expansion valve 609, wherein the second bypass path is provided with the third on/off valve 610, and the second throttle path is provided with the third expansion valve 609. Specifically, as shown in fig. 1, the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the third on/off valve 610 to form a second pass branch, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the third expansion valve 609 to form a second throttle branch. When the system is in the high-temperature cooling mode, the third expansion valve 609 is turned on, the third switching valve 610 is closed, and the outlet of the outdoor heat exchanger 605 communicates with the inlet of the indoor evaporator 602 via the second throttling branch. When the system is in the low temperature heating mode, the third switching valve 610 is turned on, the third expansion valve 609 is closed, and the outlet of the outdoor heat exchanger 605 communicates with the low pressure air inlet 604a of the compressor 604 via the second pass branch.
fig. 3 to 6 are schematic structural views illustrating a heat pump air conditioning system according to another embodiment of the present invention. As shown in fig. 3 to 6, the heat pump air conditioning system may further include a gas-liquid separator 611 and a check valve 625, wherein an outlet of the indoor evaporator 602 communicates with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 communicates with the low pressure inlet 604a of the compressor 604. In this way, the refrigerant may first pass through the gas-liquid separator 611 to undergo gas-liquid separation, and the separated gas may then flow back into the compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 and damaging the compressor 604, so that the service life of the compressor 604 may be extended, and the efficiency of the entire heat pump air conditioning system may be improved. An outlet of the indoor evaporator 602 communicates with an inlet of the gas-liquid separator 611 through a check valve 625. Here, the check valve 625 is provided to prevent refrigerant from flowing back to the indoor evaporator 602 in a low temperature heating mode (described in detail below), affecting a heating effect.
The following will describe in detail the cycle process and principle of the heat pump air conditioning system provided by the present invention in different operation modes by taking fig. 3 to fig. 6 as an example. It should be understood that the system cycle process and principle under other embodiments (for example, the embodiments shown in fig. 1 to 3) are similar to those in fig. 3 to 6, and are not repeated here.
The first mode is as follows: a high temperature refrigeration mode. When the system is in this mode, the entire system forms a high temperature refrigeration cycle. As shown in fig. 3, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the air is controlled by the damper mechanism not to pass through the indoor condenser 601, and since no air passes through, heat exchange is not performed in the indoor condenser 601, the indoor condenser 601 is used only as a flow passage, and at this time, the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor condenser 601 is connected to an expansion switch valve 603, and at this time, the expansion switch valve 603 functions as a switch valve and only serves as a flow channel to flow through, and at this time, the outlet of the expansion switch valve 603 is still high-temperature and high-pressure gas. The outlet of the expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the third switching valve 610 is closed, the outlet of the outdoor heat exchanger 605 is connected to the third expansion valve 609, the third expansion valve 609 functions as a throttling element to perform throttling, and the outlet thereof is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the evaporator outlet refrigerant from the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. An outlet of the third expansion valve 609 is connected to an inlet of the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The outlet of the indoor evaporator 602 is connected to the inlet of the check valve 625, the outlet of the check valve 625 is connected to the inlet of the gas-liquid separator 611, the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604 through the low-pressure inlet 604a of the compressor 604, thereby forming a cycle. In this case, the flow of air in the HVAC unit 600 flows only through the indoor evaporator 602, and the indoor condenser 601 flows only as a refrigerant flow path without air. In addition, the first switching valve 624 and the first expansion valve 623 are both in a closed state, so that the first enthalpy increasing branch 621 and the second enthalpy increasing branch 622 are both blocked.
And a second mode: and (4) a low-temperature heating mode. When the system is in this mode, the entire system forms a low temperature heating cycle system. As shown in fig. 4, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the indoor condenser 601 is connected to an expansion switch valve 603, and the expansion switch valve 603 functions as an expansion valve and functions as a throttling element to throttle, and the outlet is low-temperature and low-pressure liquid. The opening degree of the expansion switch valve 603 may be a certain opening degree according to actual requirements, and the opening degree may be adjusted according to the temperature acquisition data (i.e., the compressor discharge temperature) of the pressure-temperature sensor installed at the outlet of the compressor 604. The outlet of the expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 absorbs the heat of the outdoor air, and the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure gas. At this time, the third switching valve 610 is opened, the third expansion valve 609 is closed, the refrigerant directly enters the gas-liquid separator 611 without passing through the indoor evaporator 602, the liquid that has not been evaporated is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604 through the low-pressure inlet 604a of the compressor 604, thereby forming one cycle. In addition, the first switching valve 624 and the first expansion valve 623 are both in a closed state, so that the first enthalpy increasing branch 621 and the second enthalpy increasing branch 622 are both blocked.
And a third mode: and an ultra-low temperature heating mode. When the system is in this mode, the entire system forms an ultra-low temperature heating cycle system. As shown in fig. 5, on the basis of the low temperature heating mode, the first switching valve 624 and the first expansion valve 623 are opened, so that the first enthalpy increasing branch 621 and the second enthalpy increasing branch 622 are both turned on. Thus, the medium-temperature high-pressure liquid flowing out of the outlet of the indoor condenser 601 is divided into two paths, one path of the medium-temperature high-pressure liquid is throttled by the expansion switch valve 603 to be changed into low-temperature low-pressure liquid to enter the outdoor heat exchanger 605, and the other path of the medium-temperature high-pressure liquid is changed into low-temperature high-pressure liquid to enter the outdoor heat exchanger 5 by the first switch valve 624 and the first plate heat exchanger 620. The refrigerant coming out of the outdoor heat exchanger 605 is a mixture of low-temperature low-pressure gas and low-temperature high-pressure liquid, wherein the low-temperature low-pressure gas enters the low-pressure inlet 604a of the compressor 604 via the third on-off valve 610, thereby forming a cycle; the low-temperature high-pressure liquid is throttled by the first expansion valve 623 to become a low-temperature medium-pressure liquid, which is converted into a medium-temperature medium-pressure gas by the first plate heat exchanger 620, and enters the medium-pressure gas inlet 604b of the compressor 604, thereby forming a cycle. It can be seen that the refrigerant in the second enthalpy increasing branch 622 absorbs heat from the refrigerant in the first enthalpy increasing branch 621 in the process of passing through the first plate heat exchanger 620, so that the suction temperature and the suction amount of the compressor 604 can be increased, and the heating performance of the system can be improved.
And a fourth mode: and simultaneously, a cooling and heating mode is adopted. When the system is in the mode, the whole system forms a refrigerating and heating simultaneous open circulation system. As shown in fig. 6, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601, and the high-temperature and high-pressure gas is condensed in the indoor condenser 601, so that the outlet of the indoor condenser 601 is medium-temperature and high-pressure liquid. The outlet of the indoor condenser 601 is connected to an expansion switch valve 603, and at this time, the expansion switch valve 603 functions as an expansion valve and functions as a throttling element to perform throttling, and the outlet of the expansion switch valve is low-temperature and low-pressure liquid. The opening degree of the expansion switch valve 603 may be a certain opening degree according to actual requirements, and the opening degree may be adjusted according to temperature acquisition data of a pressure-temperature sensor installed at an outlet of the compressor 604, that is, a discharge temperature of the compressor. The outlet of the expansion switch valve 603 is connected to the outdoor heat exchanger 605, the outlet of the outdoor heat exchanger 605 is low-temperature and low-pressure liquid, at this time, the third switch valve 610 is closed, the third expansion valve 609 is opened, and the third expansion valve 609 is used as a throttling element to throttle again. An outlet of the third expansion valve 609 is connected to the indoor evaporator 602, and the low-temperature and low-pressure liquid is evaporated in the indoor evaporator 602, so that the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 605, and separates unevaporated liquid by the gas-liquid separator 611, and finally, the low-temperature and low-pressure gas is returned to the compressor 604 through a low-pressure inlet 604a of the compressor 604, thereby forming a cycle. At this time, the wind in the HVAC assembly 600 flows through the indoor condenser 601 and the indoor evaporator 602 at the same time.
And a fifth mode: and an outdoor heat exchanger defrosting mode. As shown in fig. 4, the compressor 604 compresses and discharges high-temperature and high-pressure gas, and is connected to the indoor condenser 601. At this time, the indoor condenser 601 flows only as a flow channel, and the outlet of the indoor condenser 601 is still high-temperature and high-pressure gas. The outlet of the indoor condenser 601 is connected to an expansion switch valve 603, and at this time, the expansion switch valve 603 functions as a switch valve and only serves as a flow channel to flow through, and at this time, the outlet of the expansion switch valve 603 is still high-temperature and high-pressure gas. The outlet of the expansion switch valve 603 is connected with an outdoor heat exchanger 605, the outdoor heat exchanger 605 exchanges heat with outdoor air to radiate heat into the air, and the outlet of the outdoor heat exchanger 605 is medium-temperature high-pressure liquid. At this time, the third switching valve 610 is closed, the third expansion valve 609 is opened, the third expansion valve 609 functions as a throttling element to perform throttling, and the outlet thereof is low-temperature and low-pressure liquid. The opening degree of the third expansion valve 609 may be given an opening degree according to actual demand, and the opening degree may be adjusted by calculating the degree of superheat of the evaporator outlet refrigerant from the pressure and temperature acquisition data of the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The outlet of the third expansion valve 609 is connected to the indoor evaporator 602, and the outlet of the indoor evaporator 602 is low-temperature and low-pressure gas. The indoor evaporator 602 is connected to a gas-liquid separator 611, and the unevaporated liquid is separated by the gas-liquid separator 611, and finally the low-temperature and low-pressure gas is returned to the compressor 604, thereby forming a cycle. The HVAC assembly 600 may not be turned on at this time.
in conclusion, the heat pump air-conditioning system provided by the invention can realize the refrigeration and heating functions of the automobile air-conditioning system and the defrosting function of the outdoor heat exchanger under the condition of not changing the circulation direction of the refrigerant, and can meet the requirements of simultaneous refrigeration and heating. In the bypass defrosting process of the outdoor heat exchanger, the requirement of heating in the vehicle can be still met. In addition, because the heat pump air-conditioning system only adopts one outdoor heat exchanger, the wind resistance of the front-end module of the automobile can be reduced, the problems that a pure electric vehicle or a hybrid vehicle without an engine waste heat circulating system uses an automobile heat pump air-conditioning system in a pure electric mode, the heating energy efficiency is low, the requirements of defrosting and demisting regulations cannot be met, the installation is complex and the like are solved, and the effects of reducing energy consumption, simplifying the system structure and facilitating pipeline arrangement are achieved. In addition, the enthalpy-increasing branch is arranged in the system, so that the low-temperature heating performance of the system can be obviously improved. The heat pump air conditioning system provided by the invention has the characteristic of simple structure, so that the mass production is easy.
In the low-temperature heating mode, the ultra-low-temperature heating mode, and the simultaneous cooling heating mode, in order to improve heating capacity, it is preferable that, as shown in fig. 7, a second plate heat exchanger 612 is provided in the entire heat pump air conditioning system, and the second plate heat exchanger 612 is also provided in the motor cooling system of the electric vehicle at the same time. In this way, the residual heat of the motor cooling system can be used to heat the air conditioning system refrigerant, thereby increasing the suction temperature and suction capacity of the compressor 604.
the plate heat exchanger 612 may be disposed upstream or downstream of the third on/off valve 610. In the embodiment shown in fig. 7, the plate heat exchanger 612 is disposed upstream of the third switching valve 610, i.e., the refrigerant inlet 612a of the plate heat exchanger 612 communicates with the outlet of the outdoor heat exchanger 605, and the refrigerant outlet 612b of the plate heat exchanger 612 communicates with the inlet of the third switching valve 610. In another embodiment (not shown), the plate heat exchanger 612 is disposed downstream of the third on/off valve 610, i.e., the refrigerant inlet 612a of the plate heat exchanger 612 communicates with the outlet of the third on/off valve 610, and the refrigerant outlet 612b of the plate heat exchanger 612 communicates with the inlet of the gas-liquid separator 611.
At the same time, the plate heat exchanger 612 is simultaneously provided in the motor cooling system. As shown in fig. 7, the motor cooling system may include a motor in series with a plate heat exchanger 612 to form a loop, a motor radiator 613, and a water pump 614. In this way, the refrigerant is able to exchange heat with the coolant in the motor cooling system through the plate heat exchanger 612. The refrigerant passes through the third switching valve 610 and then returns to the compressor 604.
In the heat pump air conditioning system provided by the present invention, various refrigerants such as R134a, R410a, R32, R290 and the like can be used, and a medium-high temperature refrigerant is preferably used.
Fig. 8 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present invention. As shown in fig. 8, the HVAC assembly 600 may further include a PTC heater 619, the PTC heater 619 being used to heat the wind flowing through the indoor condenser 601.
in the present invention, the PTC heater 619 may be a high voltage PTC (driven by the vehicle high voltage battery), with a voltage range: 200V-900V. Alternatively, the PTC heater 619 may be a low voltage PTC (12V or 24V battery operated), voltage range: 9V-32V. In addition, the PTC heater 619 may be a complete core composed of several PTC ceramic wafer modules and heat dissipation fins, or a strip-shaped or block-shaped PTC ceramic wafer module with heat dissipation fins.
In the present invention, the PTC heater 619 may be disposed on the windward side or the leeward side of the indoor condenser 601. Also, in order to improve the heating effect of the wind flowing through the indoor condenser 601, the PTC heater 619 may be provided in parallel with the indoor condenser 601. In other embodiments, the PTC heater 619 may also be disposed at the foot blowing air port and the defrost air port of the box of the HVAC assembly 600, or at the air ports of the defrost air duct.
If the PTC heater 619 is arranged on the windward side or the leeward side of the indoor condenser 601 in the box body and is arranged in parallel with the indoor condenser 601, a groove can be dug in the shell of the box body, the PTC heater 619 is vertically inserted into the box body, a bracket can be welded on the side plate of the indoor condenser 601, and the PTC heater 619 is fixed on the bracket of the indoor condenser 601 through a screw. If the PTC heater 619 is arranged at the foot blowing air port and the defrosting air port of the box body or at the air port of the defrosting air channel, the PTC heater can be directly fixed at the air ports of the air outlet and the air channel port of the box body through screws.
Through the embodiment, when the temperature outside the vehicle is too low, and the heating capacity of the low-temperature heating of the heat pump does not meet the requirement in the vehicle, the PTC heater 619 can be operated to assist in heating, so that the defects that the heating capacity is small when the low-temperature heating of the heat pump air conditioning system is carried out, the defrosting and demisting of the whole vehicle are slow, the heating effect is poor and the like can be eliminated.
As described above, in the present invention, the expansion switching valve is a valve having both the expansion valve function and the switching valve function, and may be regarded as an integration of the switching valve and the expansion valve. Hereinafter, an example embodiment of an expansion switching valve will be provided.
As shown in fig. 9, the above-mentioned expansion switching valve may include a valve body 500, wherein the valve body 500 is formed with an inlet 501, an outlet 502, and an internal flow passage communicating between the inlet 501 and the outlet 502, the internal flow passage is mounted with a first valve spool 503 and a second valve spool 504, the first valve spool 503 makes the inlet 501 and the outlet 502 directly communicate or disconnect from each other, and the second valve spool 504 makes the inlet 501 and the outlet 502 communicate or disconnect from each other through a choke 505.
The "direct communication" realized by the first valve core means that the coolant entering from the inlet 501 of the valve body 500 can pass through the first valve core and directly flow to the outlet 502 of the valve body 500 through the internal flow passage without being affected, and the "disconnection communication" realized by the first valve core means that the coolant entering from the inlet 501 of the valve body 500 cannot pass through the first valve core and cannot flow to the outlet 502 of the valve body 500 through the internal flow passage. The "communication through the orifice" realized by the second valve spool means that the coolant entering from the inlet 501 of the valve body 500 can flow to the outlet 502 of the valve body 500 through the orifice after passing through the second valve spool and throttling, and the "disconnection" realized by the second valve spool means that the coolant entering from the inlet 501 of the valve body 500 cannot flow to the outlet 502 of the valve body 500 through the orifice 505 without passing through the second valve spool.
Thus, the expansion switching valve of the present invention can allow the coolant entering from the inlet 501 to achieve at least three states by controlling the first and second spools. I.e., 1) an off state; 2) a direct communication state across the first spool 503; and 3) throttle communication across the second spool 504.
The high-temperature and high-pressure liquid refrigerant can be turned into low-temperature and low-pressure fog-shaped hydraulic refrigerant after being throttled by the throttle 505, conditions can be created for evaporation of the refrigerant, namely the cross-sectional area of the throttle 505 is smaller than that of the outlet 504, and the opening degree of the throttle 505 can be adjusted by controlling the second valve core, so that the flow rate of the refrigerant flowing through the throttle 505 is controlled, insufficient refrigeration caused by too little refrigerant is prevented, and liquid impact of the compressor caused by too much refrigerant is prevented. That is, the cooperation of the second valve spool 504 and the valve body 500 may make the expansion switching valve function as an expansion valve.
Thus, the first valve core 503 and the second valve core 504 are arranged on the internal flow passage of the same valve body 500 to realize the on-off control and/or throttling control functions of the inlet 501 and the outlet 502, the structure is simple, the production and the installation are easy, and when the expansion switch valve provided by the invention is applied to a heat pump system, the refrigerant charge of the whole heat pump system can be reduced, the cost is reduced, the pipeline connection is simplified, and the oil return of the heat pump system is facilitated.
As an exemplary internal mounting structure of the valve body 500, as shown in fig. 9 to 14, the valve body 500 includes a valve seat 510 forming an internal flow passage, and a first valve housing 511 and a second valve housing 512 mounted on the valve seat 510, a first electromagnetic driving part 521 for driving a first valve core 503 is mounted in the first valve housing 511, a second electromagnetic driving part 522 for driving a second valve core 504 is mounted in the second valve housing 512, the first valve core 503 extends from the first valve housing 511 to the internal flow passage in the valve seat 510, and the second valve core 504 extends from the second valve housing 512 to the internal flow passage in the valve seat 510.
Wherein, the position of the first valve core 503 can be conveniently controlled by controlling the on/off of the first electromagnetic driving part 521, such as an electromagnetic coil, so as to control the direct connection or disconnection of the inlet 501 and the outlet 502; the position of the second spool 504 can be conveniently controlled by controlling the energization and de-energization of the second electromagnetic drive 522, e.g., a solenoid, to control whether the inlet 501 and outlet 502 are in communication with the orifice 505. In other words, the electronic expansion valve and the electromagnetic valve, which share the inlet 501 and the outlet 502, are installed in parallel in the valve body 500, so that the automatic control of the on-off and/or throttling of the expansion switch valve can be realized, and the pipeline trend is simplified.
in order to fully utilize the spatial positions of the expansion switch valve in all directions and prevent the expansion switch valve from interfering with the connection of different pipelines, the valve seat 510 is formed in a polyhedral structure, and the first and second valve casings 511 and 512, the inlet 501 and the outlet 502 are respectively disposed on different surfaces of the polyhedral structure, wherein the installation directions of the first and second valve casings 511 and 512 are perpendicular to each other, and the opening directions of the inlet 501 and the outlet 502 are perpendicular to each other. Like this, can be with import, outlet pipe way connection on polyhedral structure's different surfaces, can avoid the problem that the pipeline arrangement is in disorder, tangled.
As a typical internal structure of the expansion switching valve, as shown in fig. 9 to 12, the internal flow passage includes a first flow passage 506 and a second flow passage 507 respectively communicating with the inlet 501, the first flow passage 506 is formed with a first valve port 516 cooperating with the first spool 503, the orifice 505 is formed in the second flow passage 507 to form a second valve port 517 cooperating with the second spool 504, and the first flow passage 506 and the second flow passage 507 meet downstream of the second valve port 517 and communicate with the outlet 502.
that is, the position of the first valve core 503 is changed to close or open the first valve port 516, and thus the blocking or communication of the first flow passage 506 communicating the inlet 501 and the outlet 502 is controlled, so that the above-described function of communicating or blocking the communication of the solenoid valve can be realized. Similarly, the position of the second valve element 504 is changed to open or close the second valve port 517, thereby achieving the throttle function of the electronic expansion valve.
The first flow channel 506 and the second flow channel 507 can respectively communicate with the inlet 501 and the outlet 502 in any suitable arrangement, in order to reduce the overall occupied space of the valve body 500, as shown in fig. 13, the second flow channel 507 and the outlet 502 are opened in the same direction, the first flow channel 506 is formed as a first through hole 526 perpendicular to the second flow channel 507, the inlet 501 communicates with the second flow channel 507 through a second through hole 527 opened on the side wall of the second flow channel 507, and the first through hole 526 and the second through hole 527 respectively communicate with the inlet 501. The first through hole 526 may be spatially perpendicular to or parallel to the second through hole 527, which is not limited in the present invention and falls within the protection scope of the present invention.
to further simplify the overall footprint of the valve body 500, as shown in fig. 16-19, an inlet 501 and an outlet 502 are provided on the valve body 500 perpendicular to each other. In this way, as shown in fig. 16 to 18, the axis of the inlet 501, the axis of the outlet 502 (i.e., the axis of the second flow passage 507), and the axis of the first flow passage 506 are arranged vertically two by two in space, thereby preventing interference of the movements of the first and second spools 503 and 504 and enabling maximum use of the internal space of the valve body 500.
As shown in fig. 12 and 13, to facilitate the closing and opening of the first port 516, the first valve element 503 is disposed coaxially with the first port 516 in the moving direction to selectively block or separate from the first port 516.
To facilitate the closing and opening of the second valve port 517, the second spool 504 is disposed coaxially with the second valve port 517 in the moving direction to selectively block or disengage the second valve port 517.
As shown in fig. 15, in order to ensure the reliability of the first valve core 503 for blocking the first flow passage 506, the first valve core 503 may include a first valve rod 513 and a first plug 523 connected to an end of the first valve rod 513, wherein the first plug 523 is used for sealing and pressing against an end surface of the first valve port 516 to block the first flow passage 506.
To facilitate adjustment of the opening degree of the orifice 505 of the expansion switch valve, as shown in fig. 12 and 13, the second valve spool 504 includes a second valve stem 514, an end portion of the second valve stem 514 is formed into a conical head structure, and the second valve port 517 is formed into a conical hole structure matched with the conical head structure.
the opening degree of the orifice 505 of the expansion switch valve can be adjusted by the vertical movement of the second valve element 504, and the vertical movement of the second valve element 504 can be adjusted by the second electromagnetic driving unit 522. If the opening degree of the orifice 505 of the expansion switch valve is zero, as shown in fig. 12, the second valve body 504 is at the lowest position, the second valve body 504 blocks the second valve port 517, and the refrigerant cannot pass through the orifice 505 at all, that is, the second valve port 517; if the expansion switch valve orifice 505 has an opening degree, as shown in fig. 13, a gap is formed between the orifice 505 and the tapered head structure at the end of the second valve body 504, and the refrigerant is throttled and then flows to the outlet 502. If the throttle opening of the expansion switch valve needs to be increased, the second electromagnetic driving part 522 is controlled to enable the second valve core 504 to move upwards, so that the conical head structure is far away from the throttle opening 505, and the opening of the throttle opening 505 is increased; on the contrary, when the opening degree of the orifice 505 of the expansion switch valve needs to be decreased, the second spool 504 may be driven to move downward.
In use, when only the solenoid function of the expansion switch valve is required, as shown in fig. 12, 15, and 18, the first valve body 503 is separated from the first port 516, the first port 516 is in an open state, the second valve body 504 is at the lowest position, the second valve body 504 closes the orifice 505, and the refrigerant flowing into the internal flow path from the inlet 501 cannot pass through the orifice 505 at all but flows into the outlet 502 through the first port 516 and the first through hole 526 in this order. When the electromagnetic valve is powered off, the first valve core 503 moves to the left, the first plug 523 is separated from the first valve port 516, and the refrigerant can pass through the first through hole 526; when the electromagnetic valve is energized, the first valve core 503 moves rightwards, the first plug 523 is attached to the first valve port 516, and the refrigerant cannot pass through the first through hole 526.
Note that the dashed lines with arrows in fig. 12 and 18 represent the flow paths and the direction of the refrigerant when the solenoid valve function is used.
When only the electronic expansion valve function using the expansion switch valve is required, as shown in fig. 13 and 19, the second port 517, i.e., the choke 505, is in an open state, the first valve body 503 closes the first port 516, the refrigerant flowing from the inlet 501 into the internal flow passage cannot flow through the first through hole 526 but flows only through the second through hole 527 and the choke 505 into the outlet 502, and the second valve body 504 can be moved up and down to adjust the opening degree of the choke 505.
In fig. 13 and 19, dotted lines with arrows represent flow paths and directions of the refrigerant when the electronic expansion valve function is used.
When it is required to simultaneously use the solenoid valve function and the electronic expansion valve function of the expansion switch valve, as shown in fig. 10, 16 and 17, wherein the dotted lines with arrows represent the flow path and the direction of the refrigerant, the first valve spool 503 is separated from the first valve port 516, the first valve port 516 is in an open state, and the orifice 505 is in an open state, the refrigerant flowing into the internal flow passage can flow to the outlet 502 along the first flow passage 506 and the second flow passage 507, respectively, thereby simultaneously having the solenoid valve function and the electronic expansion valve function.
It should be understood that the above-described embodiment is merely an example of one of the expansion on-off valves, and is not intended to limit the present invention, and other expansion on-off valves having both the expansion valve function and the on-off valve function are also applicable to the present invention.
The invention also provides an electric automobile which comprises the heat pump air-conditioning system provided by the invention. The electric automobile can comprise a pure electric automobile, a hybrid electric automobile and a fuel cell automobile.
The preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, however, the present invention is not limited to the specific details of the above embodiments, and various simple modifications can be made to the technical solution of the present invention within the technical idea of the present invention, and these simple modifications are within the protective scope of the present invention.
It should be noted that the various features described in the above embodiments may be combined in any suitable manner without departing from the scope of the invention. The invention is not described in detail in order to avoid unnecessary repetition.
In addition, any combination of the various embodiments of the present invention is also possible, and the same should be considered as the disclosure of the present invention as long as it does not depart from the spirit of the present invention.
Claims (11)
1. A heat pump air conditioning system, characterized by comprising a compressor (604), an indoor condenser (601), an indoor evaporator (602) and an outdoor heat exchanger (605), the outlet of the compressor (604) being in communication with the inlet of the indoor condenser (601), the outlet of the indoor condenser (601) being in communication with the inlet of the outdoor heat exchanger (605) selectively via a first throttling branch or a first flow-through branch, the outlet of the outdoor heat exchanger (605) being in communication with the low pressure air inlet (604a) of the compressor (604) selectively via a second flow-through branch or with the inlet of the indoor evaporator (602) selectively via a second throttling branch, the outlet of the indoor evaporator (602) being in communication with the low pressure air inlet (604a) of the compressor (604), the outlet of the indoor condenser (601) being also in communication with the inlet of the outdoor heat exchanger (605) via a first enthalpy increasing branch (621) selectively conducting or blocking, the outlet of the outdoor heat exchanger (605) is also communicated with the medium-pressure air inlet (604b) of the compressor (604) through a second enthalpy-increasing branch (622), the first enthalpy-increasing branch (621) and the second enthalpy-increasing branch (622) exchange heat through the first plate heat exchanger (620), a first expansion valve (623) is arranged on the second enthalpy-increasing branch (622), the outlet of the outdoor heat exchanger (605) is communicated with the first plate heat exchanger (620) through the first expansion valve (623), the system further comprises an expansion switch valve (603), the inlet of the expansion switch valve (603) is communicated with the outlet of the indoor condenser (601), the outlet of the expansion switch valve (603) is communicated with the inlet of the outdoor heat exchanger (605), the first throttling branch is a throttling flow passage of the expansion switch valve (603), and the first through flow branch is a through flow passage of the expansion switch valve (603), when the expansion switch valve (603) is used as a switch valve, the through flow channel inside the expansion switch valve is communicated, and when the expansion switch valve (603) is used as an expansion valve, the throttling channel inside the expansion switch valve is communicated.
2. the heat pump air conditioning system according to claim 1, wherein a first switching valve (624) is provided on the first enthalpy increasing branch (621), and an outlet of the indoor condenser (601) communicates with the first plate heat exchanger (620) via the first switching valve (624).
3. The heat pump air conditioning system according to claim 1, wherein a third on/off valve (610) is provided in the second flow path, and a third expansion valve (609) is provided in the second throttle path.
4. The heat pump air conditioning system of claim 1, wherein an outlet of the indoor evaporator (602) communicates with a low pressure intake (604a) of the compressor (604) via a check valve (625).
5. The heat pump air-conditioning system according to claim 1, wherein the heat pump air-conditioning system is applied to an electric vehicle, and a second plate heat exchanger (612) is further arranged on the second flow branch, and the second plate heat exchanger (612) is simultaneously arranged in a motor cooling system of the electric vehicle.
6. The heat pump air conditioning system according to claim 5, wherein a third on/off valve (610) is provided in the second bypass path, a refrigerant inlet of the second plate heat exchanger (612) communicates with an outlet of the outdoor heat exchanger (605), and a refrigerant outlet of the second plate heat exchanger (612) communicates with an inlet of the third on/off valve (610).
7. The heat pump air conditioning system of claim 5, wherein the motor cooling system comprises a motor, a motor radiator (613) and a water pump (614) in series with the second plate heat exchanger (612) to form a circuit.
8. The heat pump air conditioning system according to claim 1, further comprising a gas-liquid separator (611), an outlet of the indoor evaporator (602) communicating with an inlet of the gas-liquid separator (611), an outlet of the outdoor heat exchanger (605) communicating with an inlet of the gas-liquid separator (611) via the second bypass, an outlet of the gas-liquid separator (611) communicating with a low pressure air inlet (604a) of the compressor (604).
9. The heat pump air conditioning system of claim 1, wherein the system further comprises a PTC heater (619), the PTC heater (619) being adapted to heat the air flowing through the indoor condenser (601).
10. The heat pump air conditioning system according to claim 9, wherein the PTC heater (619) is disposed on a windward side or a leeward side of the indoor condenser (601).
11. An electric vehicle characterized by comprising the heat pump air conditioning system according to any one of claims 1 to 10.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610310423.2A CN107356023B (en) | 2016-05-10 | 2016-05-10 | Heat pump air conditioning system and electric automobile |
| PCT/CN2017/082948 WO2017193857A1 (en) | 2016-05-10 | 2017-05-03 | Heat pump air-conditioning system and electric vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610310423.2A CN107356023B (en) | 2016-05-10 | 2016-05-10 | Heat pump air conditioning system and electric automobile |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107356023A CN107356023A (en) | 2017-11-17 |
| CN107356023B true CN107356023B (en) | 2019-12-10 |
Family
ID=60266217
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610310423.2A Active CN107356023B (en) | 2016-05-10 | 2016-05-10 | Heat pump air conditioning system and electric automobile |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107356023B (en) |
| WO (1) | WO2017193857A1 (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108155439B (en) * | 2018-02-01 | 2024-04-26 | 湖南华强电气股份有限公司 | Air conditioner battery cooling single cooling system and control method |
| CN108931021B (en) * | 2018-09-19 | 2023-12-08 | 珠海格力电器股份有限公司 | Heat pump system and air conditioner with same |
| CN109130784A (en) * | 2018-10-12 | 2019-01-04 | 泰铂（上海）环保科技股份有限公司 | A kind of dual system electric truck Air conditioner on car system of changes in temperature one |
| CN109489294B (en) * | 2018-11-19 | 2023-05-26 | 佛山市德天电器有限公司 | Multifunctional oil content device with system enthalpy increasing function and heat pump system thereof |
| CN109442794A (en) * | 2018-11-28 | 2019-03-08 | 宁波奥克斯电气股份有限公司 | A kind of air-conditioning refrigeration system, Defrost method and air conditioner |
| CN109520170B (en) * | 2018-11-28 | 2023-04-07 | 中原工学院 | Air source heat pump unit with double-stage supercooling and liquid pulse defrosting functions |
| CN111251812B (en) * | 2018-11-30 | 2022-07-15 | 比亚迪股份有限公司 | Thermal management system of vehicle and vehicle |
| CN109677236B (en) * | 2018-12-26 | 2021-10-15 | 四川赛特制冷设备有限公司 | Air conditioning system of electric vehicle |
| CN109808449B (en) * | 2019-02-26 | 2024-04-26 | 鞍山新北精工有限公司 | Ultralow-temperature heat pump air conditioning system of electric automobile |
| CN112440656A (en) * | 2019-08-29 | 2021-03-05 | 浙江三花汽车零部件有限公司 | Air conditioning system |
| CN110726196B (en) * | 2019-10-10 | 2024-06-04 | 合肥天鹅制冷科技有限公司 | Cold liquid integrated system of air conditioner |
| CN113776223B (en) * | 2021-10-13 | 2023-01-24 | 广东积微科技有限公司 | Double-enhanced vapor injection refrigeration system |
| CN115200268A (en) * | 2022-06-10 | 2022-10-18 | 智己汽车科技有限公司 | Heat exchange circulation system, air conditioner and vehicle |
| CN115284818B (en) * | 2022-07-15 | 2024-05-14 | 智己汽车科技有限公司 | Heat pump system, air conditioner and vehicle |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000203249A (en) * | 1999-01-13 | 2000-07-25 | Denso Corp | Air conditioner |
| JP2003042604A (en) * | 2001-07-25 | 2003-02-13 | Denso Corp | Vapor compression type heat pump cycle and air conditioner |
| JP3985384B2 (en) * | 1998-09-24 | 2007-10-03 | 株式会社デンソー | Refrigeration cycle equipment |
| JP2008025862A (en) * | 2006-07-18 | 2008-02-07 | Denso Corp | Ejector type refrigerating cycle |
| JP4048654B2 (en) * | 1999-07-26 | 2008-02-20 | 株式会社デンソー | Refrigeration cycle equipment |
| JP4061820B2 (en) * | 1999-10-20 | 2008-03-19 | 株式会社デンソー | Refrigeration cycle equipment |
| JP4134433B2 (en) * | 1999-03-30 | 2008-08-20 | 株式会社デンソー | Heat pump air conditioner |
| CN202747508U (en) * | 2012-07-06 | 2013-02-20 | 浙江盾安人工环境股份有限公司 | Heat pump air conditioning system of electric automobile |
| JP2013154805A (en) * | 2012-01-31 | 2013-08-15 | Denso Corp | Vehicle air conditioning system |
| CN104121720A (en) * | 2013-04-26 | 2014-10-29 | 中国科学院理化技术研究所 | Electric car air conditioning system with air source heat pump |
| CN104169112A (en) * | 2012-03-14 | 2014-11-26 | 株式会社电装 | Refrigeration cycle device |
| CN104290561A (en) * | 2014-09-11 | 2015-01-21 | 中国科学院理化技术研究所 | Method for recycling exhaust air heat of electric automobile and heat pump air-conditioning system adopting same |
| CN105473356A (en) * | 2013-08-23 | 2016-04-06 | 三电控股株式会社 | Vehicle air conditioner |
| KR20160048237A (en) * | 2014-10-23 | 2016-05-04 | 한온시스템 주식회사 | Heat pump system for vehicle |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3841039B2 (en) * | 2002-10-25 | 2006-11-01 | 株式会社デンソー | Air conditioner for vehicles |
| JP5533816B2 (en) * | 2011-08-08 | 2014-06-25 | 株式会社デンソー | Air conditioner for vehicles |
| CN103121393B (en) * | 2011-11-17 | 2015-07-08 | 株式会社电装 | Configuration of vehicle heat exchanger |
| JP5949648B2 (en) * | 2013-04-18 | 2016-07-13 | 株式会社デンソー | Refrigeration cycle equipment |
-
2016
- 2016-05-10 CN CN201610310423.2A patent/CN107356023B/en active Active
-
2017
- 2017-05-03 WO PCT/CN2017/082948 patent/WO2017193857A1/en active Application Filing
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3985384B2 (en) * | 1998-09-24 | 2007-10-03 | 株式会社デンソー | Refrigeration cycle equipment |
| JP2000203249A (en) * | 1999-01-13 | 2000-07-25 | Denso Corp | Air conditioner |
| JP4134433B2 (en) * | 1999-03-30 | 2008-08-20 | 株式会社デンソー | Heat pump air conditioner |
| JP4048654B2 (en) * | 1999-07-26 | 2008-02-20 | 株式会社デンソー | Refrigeration cycle equipment |
| JP4061820B2 (en) * | 1999-10-20 | 2008-03-19 | 株式会社デンソー | Refrigeration cycle equipment |
| JP2003042604A (en) * | 2001-07-25 | 2003-02-13 | Denso Corp | Vapor compression type heat pump cycle and air conditioner |
| JP2008025862A (en) * | 2006-07-18 | 2008-02-07 | Denso Corp | Ejector type refrigerating cycle |
| JP2013154805A (en) * | 2012-01-31 | 2013-08-15 | Denso Corp | Vehicle air conditioning system |
| CN104169112A (en) * | 2012-03-14 | 2014-11-26 | 株式会社电装 | Refrigeration cycle device |
| CN202747508U (en) * | 2012-07-06 | 2013-02-20 | 浙江盾安人工环境股份有限公司 | Heat pump air conditioning system of electric automobile |
| CN104121720A (en) * | 2013-04-26 | 2014-10-29 | 中国科学院理化技术研究所 | Electric car air conditioning system with air source heat pump |
| CN105473356A (en) * | 2013-08-23 | 2016-04-06 | 三电控股株式会社 | Vehicle air conditioner |
| CN104290561A (en) * | 2014-09-11 | 2015-01-21 | 中国科学院理化技术研究所 | Method for recycling exhaust air heat of electric automobile and heat pump air-conditioning system adopting same |
| KR20160048237A (en) * | 2014-10-23 | 2016-05-04 | 한온시스템 주식회사 | Heat pump system for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107356023A (en) | 2017-11-17 |
| WO2017193857A1 (en) | 2017-11-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107356023B (en) | Heat pump air conditioning system and electric automobile | |
| CN107356005B (en) | Heat pump air conditioning system and electric automobile | |
| CN107356003B (en) | Heat pump air conditioning system and electric automobile | |
| CN107351628B (en) | Heat pump air conditioning system and electric automobile | |
| CN107351624B (en) | Heat pump air conditioning system and electric automobile | |
| WO2017193859A1 (en) | Heat pump air conditioning system and electric automobile | |
| CN107351627B (en) | Automobile thermal management system and electric automobile | |
| CN107351695B (en) | Automobile thermal management system and electric automobile | |
| WO2017193851A1 (en) | Heat pump air-conditioning system and electric vehicle | |
| CN205980092U (en) | Heat pump air conditioning system and electric automobile | |
| CN205980465U (en) | Heat pump air conditioning system and electric automobile | |
| CN205980466U (en) | Heat pump air conditioning system and electric automobile | |
| CN107359382B (en) | automobile heat management system and electric automobile | |
| WO2017193860A1 (en) | Heat pump air-conditioning system and electric vehicle | |
| CN107351620B (en) | Automobile thermal management system and electric automobile | |
| CN108248331B (en) | Heat pump air conditioning system and electric automobile | |
| CN108116186B (en) | Automobile heat management system and electric automobile | |
| WO2017193854A1 (en) | Heat pump air-conditioning system and electric vehicle | |
| CN107356002B (en) | Heat pump air conditioning system and electric car | |
| CN108116189B (en) | Automobile heat management system and electric automobile | |
| CN108116185B (en) | Automobile heat management system and electric automobile | |
| CN108116188B (en) | Automobile heat management system and electric automobile | |
| CN107356020B (en) | Heat pump air conditioning system and electric automobile | |
| CN107356022B (en) | Heat pump air conditioning system and electric automobile | |
| CN108116187B (en) | Automobile heat management system and electric automobile |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |