WO2017193860A1

WO2017193860A1 - Heat pump air-conditioning system and electric vehicle

Info

Publication number: WO2017193860A1
Application number: PCT/CN2017/082951
Authority: WO
Inventors: 叶梅娇; 陈雪峰
Original assignee: 比亚迪股份有限公司
Priority date: 2016-05-10
Filing date: 2017-05-03
Publication date: 2017-11-16

Abstract

A heat pump air-conditioning system and an electric vehicle. The heat pump air-conditioning system comprises: an indoor condenser (601), an indoor evaporator (602), a compressor (604), and an outdoor heat exchanger (605). An outlet of the compressor (604) is in communication with an inlet of the indoor condenser (601); an outlet of the indoor condenser (601) is in communication with an inlet of the outdoor heat exchanger (605) via a first throttling branch or a first through-flow branch selectively; an outlet of the outdoor heat exchanger (605) is selectively in communication with an inlet of the compressor (604) via a second through-flow branch or in communication with an inlet of the indoor evaporator (602) via a second throttling branch; an outlet of the indoor evaporator (602) is in communication with the inlet of the compressor (604). The heat pump air-conditioning system improves heating energy efficiency and facilitates installation.

Description

Heat pump air conditioning system and electric vehicle

Technical field

The present disclosure relates to an automotive air conditioning system, and in particular to a heat pump air conditioning system, and to an electric vehicle provided with the heat pump air conditioning system.

Background technique

Electric vehicles do not have the engine waste heat that traditional cars use to heat, and cannot provide heating sources. Therefore, the air conditioning system of an electric vehicle must have its own heating function, that is, a heat pump type air conditioning system and/or electric heating.

The utility model patent published as CN102788397A discloses an electric vehicle heat pump air conditioning system. Although the heat pump air conditioning system can be used in various types of electric vehicles, the system uses two outdoor heat exchangers (an outdoor condenser and an outdoor evaporator), resulting in a large wind resistance of the front end module of the automobile, and the system structure is complicated and affects. Heating effect.

Summary of the invention

The purpose of the present disclosure is to provide a heat pump air conditioning system and an electric vehicle to solve the problem that the pure electric vehicle or the hybrid vehicle without the engine waste heat circulation system uses the pure electric mode of the automobile heat pump air conditioning system, has low heating efficiency and cannot meet the requirements of defrost and defogging. Requirements, installation complexity and other issues.

In order to achieve the above object, according to a first aspect of the present disclosure, 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 and the indoor condenser The inlet is in communication, and the outlet of the indoor condenser is selectively in communication with the inlet of the outdoor heat exchanger via a first throttle branch or a first flow branch, the outlet of the outdoor heat exchanger being selectively via A second flow branch is in communication with an inlet of the compressor or with an inlet of the indoor evaporator via a second throttle branch, the outlet of the indoor evaporator being in communication with an inlet of the compressor.

According to an embodiment of the present disclosure, the first through-flow branch is provided with a first on-off valve, and the first throttle branch is provided with a first expansion valve.

According to an embodiment of the present disclosure, the heat pump air conditioning system further includes an expansion switch valve, an inlet of the expansion switch valve is in communication with an outlet of the indoor condenser, an outlet of the expansion switch valve and an inlet of the outdoor heat exchanger In communication, the first throttle branch is a throttle passage of the expansion switch valve, and the first through branch is a through flow passage of the expansion switch valve.

According to an embodiment of the present disclosure, the second through-flow branch is provided with a second on-off valve, the second throttle branch A second expansion valve is provided on the road.

According to an embodiment of the present disclosure, the outlet of the indoor evaporator is in communication with the inlet of the compressor via a one-way valve.

According to an embodiment of the present disclosure, the heat pump air conditioning system is applied to an electric vehicle, and the second through-flow branch is provided with a plate heat exchanger, which is simultaneously disposed in a motor cooling system of the electric vehicle .

According to an embodiment of the present disclosure, the second through-flow branch is provided with a second switching valve, and a refrigerant inlet of the plate heat exchanger is in communication with an outlet of the outdoor heat exchanger, the plate heat exchanger The refrigerant outlet is in communication with the inlet of the second switching valve.

According to an embodiment of the present disclosure, the motor cooling system includes a motor, a motor radiator, and a water pump that are connected in series with the plate heat exchanger to form a circuit.

According to an embodiment of the present disclosure, the heat pump air conditioning system further includes a gas-liquid separator, an outlet of the indoor evaporator is in communication with an inlet of the gas-liquid separator, and an outlet of the outdoor heat exchanger is via the first A two-flow branch is in communication with an inlet of the gas-liquid separator, and an outlet of the gas-liquid separator is in communication with an inlet of the compressor.

According to an embodiment of the present disclosure, the heat pump air conditioning system further includes a PTC heater for heating the wind flowing through the indoor condenser.

According to an embodiment of the present disclosure, 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 disclosure, an electric vehicle is provided, comprising the heat pump air conditioning system provided in accordance with the first aspect of the present disclosure.

The heat pump air conditioning system provided by the present disclosure can realize the refrigeration and heating functions of the automobile air conditioning system and the defrosting function of the outdoor side heat exchanger without changing the direction of the refrigerant circulation, and can meet the requirements of simultaneous cooling and heating. In the process of bypassing the outdoor heat exchanger, the heating demand in the car can still be met. In addition, since the heat pump air conditioning system of the present disclosure uses only one outdoor heat exchanger, the wind resistance of the front end module of the automobile can be reduced, and the pure electric vehicle or the hybrid vehicle without the engine waste heat circulation system can be used to use the pure electric mode automobile heat pump air conditioner. The system has low energy efficiency, can not meet the requirements of defrost and defogging regulations, and complicated installation, so as to reduce energy consumption, simplify system structure, and facilitate pipeline layout. The heat pump air conditioning system provided by the present disclosure has the characteristics of simple structure, and thus is easy to mass-produce.

Other features and advantages of the present disclosure will be described in detail in the detailed description which follows.

DRAWINGS

The drawings are intended to provide a further understanding of the disclosure, and are in the In the drawing:

1 is a schematic structural view of a heat pump air conditioning system according to an embodiment of the present disclosure;

2 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure;

3 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure;

4 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure;

5 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure;

6 is a schematic top plan view of an expansion switch valve according to a preferred embodiment of the present disclosure;

Figure 7 is a cross-sectional structural view taken along line AB-AB of Figure 6, wherein the first valve port and the second valve port are both in an open state;

8 is a schematic front elevational view of the expansion switch valve according to a preferred embodiment of the present disclosure along a viewing angle;

Figure 9 is a cross-sectional structural view taken along line AB-AB of Figure 6, wherein the first valve port is in an open state and the second valve port is in a closed state;

Figure 10 is a cross-sectional structural view taken along line AB-AB of Figure 6, wherein the first valve port is in a closed state, and the second valve port is in an open state;

11 is a front elevational view of the expansion switch valve according to a preferred embodiment of the present disclosure along another perspective;

Figure 12 is a cross-sectional structural view taken along line AC-AC of Figure 11, wherein the first valve port is in an open state and the second valve port is in a closed state;

13 is a first internal structural diagram of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port and the second valve port are both in an open state;

Figure 14 is a partial enlarged view of a portion A in Figure 13;

15 is a second internal structural diagram of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port is in an open state and the second valve port is in a closed state;

16 is a third internal structural diagram of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port is in a closed state and the second valve port is in an open state.

detailed description

The specific embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. It is to be understood that the specific embodiments described herein are not to be construed

In the present disclosure, the orientation words used, such as "up, down, left, and right", are generally relative to the drawing direction of the drawing, and the "upstream, downstream" is relative to The medium, for example, in the flow direction of the refrigerant, specifically, the flow direction toward the refrigerant is downstream, and the flow direction away from the refrigerant is upstream, and "inside and outside" means the inside and outside of the contour of the corresponding member.

In the present disclosure, an electric vehicle may include a pure electric vehicle, a hybrid vehicle, and a fuel cell vehicle.

1 is a schematic structural view of a heat pump air conditioning system according to an embodiment of the present disclosure. As shown in Figure 1, the system can include: HVAC (Heating Ventilation and Air Conditioning) A 600 and damper mechanism (not shown) may be utilized, wherein the damper mechanism may be used to conduct air passages to the indoor evaporator 602 and the indoor condenser 601. In addition, the system also includes a compressor 604 and an outdoor heat exchanger 605. Wherein, the HVAC assembly 600 can include an indoor condenser 601 and an indoor evaporator 602. The outlet of the compressor 604 is in communication with the inlet of the indoor condenser 601, and the outlet of the indoor condenser 601 is selectively in communication with the inlet of the outdoor heat exchanger 605 via the first throttle branch or the first through branch, outdoor heat exchange The outlet of the 605 is selectively in communication with the inlet of the indoor evaporator 602 via the second throttle branch or with the inlet of the compressor 604 via the second flow branch, the outlet of the indoor evaporator 602 and the inlet of the compressor 604 Connected.

In the present disclosure, the outlet of the indoor condenser 601 is either in communication with the inlet of the outdoor heat exchanger 605 via the first throttle branch or with the inlet of the outdoor heat exchanger 605 via the first flow branch. This connection can be implemented in a variety 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 whose inlet is in communication with an outlet of the indoor condenser 601, and the outlet of the expansion switch valve 603 is The inlet of the outdoor heat exchanger 605 is in communication, wherein the first throttle branch is a throttle passage of the expansion switch valve 603, and the first flow branch is a through flow passage of the expansion switch valve 603.

In the present disclosure, the expansion switch valve is a valve having both an expansion valve function (also referred to as an electronic expansion valve function) and an on-off valve function (also referred to as a solenoid valve function), which can be regarded as an on-off valve and expansion. Valve integration. A through flow passage and a throttle passage are formed inside the expansion switch valve. When the expansion switch valve is used as an on-off valve, the internal flow passage is electrically connected, and a through-flow branch is formed at this time; When used as an expansion valve, the internal throttling flow path is turned on, and a throttling branch is formed at this time.

As another alternative embodiment, as shown in FIG. 2, the heat pump air conditioning system may further include a first switching valve 608 and a first expansion valve 607, wherein the first switching branch is provided with a first switching valve 608, A first expansion valve 607 is disposed on the first throttle branch. Specifically, as shown in FIG. 2, the outlet of the indoor condenser 601 communicates with the inlet of the outdoor heat exchanger 605 via the first switching valve 608 to form a first through-flow branch, and the outlet of the indoor condenser 601 passes through the first expansion valve. 607 is in communication with the inlet of the outdoor heat exchanger 605 to form a first throttle branch. When the system is in the high temperature cooling mode, the first switching valve 608 is turned on, the first expansion valve 607 is closed, and the outlet of the indoor condenser 601 is in communication with the inlet of the outdoor heat exchanger 605 via the first through branch. When the system is in the low temperature heating mode, the first expansion valve 607 is turned on, the first switching valve 608 is closed, and the outlet of the indoor condenser 601 is in communication with the inlet of the outdoor heat exchanger 605 via the first throttle branch.

In order to facilitate pipe laying and space saving, it is preferred to employ an expansion switch valve 603, that is, the embodiment shown in FIG. 1, in the heat pump air conditioning system provided by the present disclosure.

Similar to the implementation of the first through-flow branch and the first throttle branch in the above alternative embodiment, as shown in FIG. 1, the second through-flow branch is provided with a second on-off valve 610, the second section A second expansion valve 609 is provided on the flow branch. Specifically, as shown in FIG. 3, the outlet of the outdoor heat exchanger 605 is in communication with the inlet of the compressor 604 via the second switching valve 610 to form a second through branch, and the outlet of the outdoor heat exchanger 605 is via the second expansion valve. 609 and the inlet of the indoor evaporator 602 The ports are connected to form a second throttle branch. When the system is in the high temperature cooling mode, the second expansion valve 609 is open, the second switching valve 610 is closed, and the outlet of the outdoor heat exchanger 605 is in communication with the inlet of the indoor evaporator 602 via the second throttle branch. When the system is in the low temperature heating mode, the second switching valve 610 is turned on, the second expansion valve 609 is closed, and the outlet of the outdoor heat exchanger 605 is in communication with the inlet of the compressor 604 via the second through branch.

FIG. 3 shows a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure. As shown in FIG. 3, the heat pump air conditioning system may further include a gas-liquid separator 611 and a check valve 615, wherein an outlet of the indoor evaporator 602 is in communication with an inlet of the gas-liquid separator 611, and an outlet of the gas-liquid separator 611 is The inlet of the compressor 604 is in communication. Thus, the refrigerant flowing out through the indoor evaporator 602 can be first subjected to gas-liquid separation through the gas-liquid separator 611, and the separated gas is returned to the compressor 604, thereby preventing the liquid refrigerant from entering the compressor 604 and damaging the compressor. 604, thereby extending the life of the compressor 604 and increasing the efficiency of the entire heat pump air conditioning system. The outlet of the indoor evaporator 602 is in communication with the inlet of the gas-liquid separator 611 through a one-way valve 615. Here, the check valve 615 is provided to prevent the refrigerant from flowing back to the indoor evaporator 602 in the low temperature heating mode (described in detail below), thereby affecting the heating effect.

The cycle process and principle of the heat pump air conditioning system provided by the present disclosure in different working modes will be described in detail below by taking FIG. 3 as an example. It should be understood that the system cycle process and principle of other embodiments (for example, the embodiments shown in FIG. 1 to FIG. 3) are similar to those of FIG. 3, and will not be further described herein.

Mode 1: High temperature cooling mode. When the system is in this mode, the entire system forms a high temperature refrigeration cycle. As shown in FIG. 3, first, the compressor 604 is compressed to discharge high temperature and high pressure gas, and the compressor 604 is connected to the indoor condenser 601. At this time, the wind is controlled by the damper mechanism without passing through the indoor condenser 601. Since no wind passes, heat exchange is not performed in the indoor condenser 601, and the indoor condenser 601 is only used as a flow path. The 601 exit is still a high temperature and high pressure gas. The outlet of the indoor condenser 601 is connected to the inlet of the expansion switch valve 603. At this time, the expansion switch valve 603 functions as a switching valve and flows only as a flow path. At this time, the outlet of the expansion switch valve 603 is still a high temperature and high pressure gas. The outlet of the expansion switch valve 603 is connected to the inlet of the outdoor heat exchanger 605. The outdoor heat exchanger 605 exchanges heat with the outdoor air to dissipate heat into the air, and the outlet of the outdoor heat exchanger 605 is a medium-temperature high-pressure liquid. At this time, the second switching valve 610 is closed, the outlet of the outdoor heat exchanger 605 is connected to the inlet of the second expansion valve 609, the second expansion valve 609 acts as a throttling element to throttle, and the outlet is a low temperature and low pressure liquid. The second expansion valve 609 opening degree can be set according to actual demand, and the opening degree can be calculated according to the pressure and temperature data collected by the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The evaporator outlet refrigerant superheat is adjusted. The outlet of the second expansion valve 609 is connected to the inlet of the indoor evaporator 602, and the low temperature and low pressure liquid is evaporated in the indoor evaporator 602 such that the outlet of the indoor evaporator 602 is a low temperature and low pressure gas. The outlet of the indoor evaporator 602 is connected to the inlet of the one-way valve 615, the outlet of the one-way valve 615 is connected to the inlet of the gas-liquid separator 611, and the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas Returning to compressor 604, a cycle is formed thereby. At this time, the HVAC assembly 600 stroke only flows through the indoor evaporator 602, and the indoor condenser 601 passes through the refrigerant flow path.

Mode 2: Low temperature heating mode. When the system is in this mode, the entire system forms a low temperature heating cycle. As shown in FIG. 3, first, the compressor 604 is compressed to discharge high temperature and high pressure gas, and the compressor 604 is connected to the indoor condenser 601. At this time, the indoor condenser 601 has a wind passing through, and the high temperature and high pressure gas is in the indoor condenser 601. Condensation is carried out so that the outlet of the indoor condenser 601 is a medium-temperature high-pressure liquid. The outlet of the indoor condenser 601 is connected to the inlet of the expansion switch valve 603. At this time, the expansion switch valve 603 functions as an expansion valve, functions as a throttling element for throttling, and its outlet is a low temperature and low pressure liquid. Wherein, the opening degree of the expansion switch valve 603 can be set according to actual demand, and the opening degree can be based on the temperature data collected by the pressure-temperature sensor installed at the outlet of the compressor 604 (ie, the compressor exhaust temperature). Adjustment. The outlet of the expansion switch valve 603 is connected to the inlet of the 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 a low temperature and low pressure gas. At this time, the second on-off valve 610 is opened, the second expansion valve 609 is closed, the refrigerant does not directly enter the gas-liquid separator 611 through the indoor evaporator 602, and the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure The gas is returned to the compressor 604, thereby forming a cycle.

Mode 3: Simultaneous cooling and heating mode. When the system is in this mode, the entire system forms a cooling and heating simultaneous opening and closing system. As shown in FIG. 3, first, the compressor 604 is compressed to discharge high-temperature and high-pressure gas, and the compressor 604 is connected to the indoor condenser 601. 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 the inlet of the expansion switch valve 603. At this time, the expansion switch valve 603 functions as an expansion valve, functions as a throttling element for throttling, and its outlet is a low temperature and low pressure liquid. Wherein, the opening degree of the expansion switch valve 603 can be set according to actual demand, and the opening degree can be based on the temperature data collected by the pressure-temperature sensor installed at the outlet of the compressor 604 (ie, the compressor exhaust temperature). Adjustment. The outlet of the expansion switch valve 603 is connected to the inlet of the outdoor heat exchanger 605, and the outlet of the outdoor heat exchanger 605 is a low temperature and low pressure liquid, and the outlet is kept in a low temperature and low pressure liquid state by incomplete evaporation. At this time, the second opening and closing valve 610 is closed, the second expansion valve 609 is opened, and the second expansion valve 609 is throttled once as a throttle element. The outlet of the second expansion valve 609 is connected to the 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 a low temperature and low pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, and the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas is returned to 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.

Mode 4: Defrost mode of outdoor heat exchanger. As shown in FIG. 3, first, the compressor 604 is compressed to discharge high temperature and high pressure gas, and the compressor 604 is connected to the indoor condenser 601. At this time, the indoor condenser 601 flows only as a flow path, and the outlet of the indoor condenser 601 is still a high-temperature high-pressure gas. The outlet of the indoor condenser 601 is connected to the inlet of the expansion switch valve 603. At this time, the expansion switch valve 603 functions as a switching valve and flows only as a flow path. At this time, the outlet of the expansion switch valve 603 is still a high temperature and high pressure gas. The outlet of the expansion switch valve 603 is connected to the inlet of the outdoor heat exchanger 605. The outdoor heat exchanger 605 exchanges heat with the outdoor air to dissipate heat into the air, and the outlet of the outdoor heat exchanger 605 is a medium-temperature high-pressure liquid. At this time, the second The on-off valve 610 is closed, the second expansion valve 609 is open, the second expansion valve 609 acts as a throttling element for throttling, and its outlet is a low temperature, low pressure liquid. The second expansion valve 609 opening degree can be set according to actual demand, and the opening degree can be calculated according to the pressure and temperature data collected by the pressure-temperature sensor installed between the outlet of the indoor evaporator 602 and the inlet of the gas-liquid separator 611. The evaporator outlet refrigerant superheat is adjusted. The outlet of the second expansion valve 609 is connected to the inlet of the indoor evaporator 602, and the outlet of the indoor evaporator 602 is a low temperature and low pressure gas. The indoor evaporator 602 is connected to the gas-liquid separator 611, and the unvaporized liquid is separated by the gas-liquid separator 611, and finally the low-temperature low-pressure gas is returned to the compressor 604, thereby forming a cycle. At this point, the HVAC assembly 600 may not open.

In summary, the heat pump air conditioning system provided by the present disclosure can realize the refrigeration and heating of the automobile air conditioning system and the defrosting function of the outdoor side heat exchanger without changing the direction of the refrigerant circulation, and can satisfy the simultaneous cooling and heating. demand. In the process of bypassing the outdoor heat exchanger, the heating demand in the car can still be met. In addition, since the heat pump air conditioning system of the present disclosure uses only one outdoor heat exchanger, the wind resistance of the front end module of the automobile can be reduced, and the pure electric vehicle or the hybrid vehicle without the engine waste heat circulation system can be used to use the pure electric mode automobile heat pump air conditioner. The system has low energy efficiency, can not meet the requirements of defrost and defogging regulations, and complicated installation, so as to reduce energy consumption, simplify system structure, and facilitate pipeline layout. The heat pump air conditioning system provided by the present disclosure has the characteristics of simple structure, and thus is easy to mass-produce.

In the low temperature heating mode and the simultaneous cooling and heating mode, in order to improve the heating capacity, preferably, as shown in FIG. 4, a plate heat exchanger 612 is provided in the entire heat pump air conditioning system, and the plate heat exchanger 612 is also set. In the motor cooling system of electric vehicles. In this way, the residual heat of the motor cooling system can be utilized to heat the refrigerant of the air conditioning system, thereby increasing the intake temperature and the intake amount of the compressor 604. The plate heat exchanger 612 can be arbitrarily disposed upstream or downstream of the second switching valve 610. In the embodiment shown in FIG. 4, the plate heat exchanger 612 is disposed upstream of the second switching valve 610, that is, the refrigerant inlet 612a of the plate heat exchanger 612 is in communication with the outlet of the outdoor heat exchanger 605, plate heat exchange The refrigerant outlet 612b of the 612 is in communication with the inlet of the second switching valve 610. In another embodiment (not shown), the plate heat exchanger 612 is disposed downstream of the second switching valve 610, ie, the refrigerant inlet 612a of the plate heat exchanger 612 is in communication with the outlet of the second switching valve 610, The refrigerant outlet 612b of the plate heat exchanger 612 is in communication with the inlet of the gas-liquid separator 611.

At the same time, the plate heat exchanger 612 is simultaneously disposed in the motor cooling system. As shown in FIG. 4, the motor cooling system can include a motor in series with the plate heat exchanger 612 to form a circuit, a motor radiator 613, and a water pump 614. In this way, the refrigerant can be heat exchanged with the coolant in the motor cooling system through the plate heat exchanger 612.

In the heat pump air conditioning system provided by the present disclosure, various refrigerants such as R134a, R410a, R32, and R290 can be used, and a medium-high temperature refrigerant is preferred.

FIG. 5 is a schematic structural view of a heat pump air conditioning system according to another embodiment of the present disclosure. As shown in FIG. 5, the HVAC assembly 600 can also include a PTC heater 619 for heating the wind flowing through the indoor condenser 601.

In the present disclosure, the PTC heater 619 can be a high voltage PTC (driven by a vehicle high voltage battery) with a voltage range of 200V-900V. Alternatively, the PTC heater 619 can also be a low voltage PTC (12V or 24V battery drive) with a voltage range of 9V-32V. In addition, the PTC heater 619 may be a complete core composed of several or several PTC ceramic chip modules and heat dissipating fins, or may be a strip or block PTC ceramic chip module with heat dissipating fins.

In the present disclosure, the PTC heater 619 may be disposed on the windward side or the leeward side of the indoor condenser 601. Further, in order to improve the heating effect on the wind flowing through the indoor condenser 601, the PTC heater 619 may be disposed in parallel with the indoor condenser 601. In other embodiments, the PTC heater 619 may also be disposed at the blower tuyere and the defroster tuyere of the cabinet of the HVAC assembly 600, and may also be disposed at the tuyere of the defroster duct.

If the PTC heater 619 is disposed on the windward side or the leeward side of the indoor condenser 601 in the tank, and arranged in parallel with the indoor condenser 601, the tank can be grooved in the casing, and the PTC heater 619 is vertically inserted into the casing. It is also possible to weld the bracket on the side plate of the indoor condenser 601, and the PTC heater 619 is fixed to the bracket of the indoor condenser 601 by screws. If the PTC heater 619 is disposed at the blower vent and the defrosting vent of the cabinet, or at the tuyere of the defrosting duct, it can be directly fixed to the air outlet of the cabinet and the tuyere of the air duct by screws.

Through this embodiment, when the outside temperature of the vehicle is too low, and the heating capacity of the low temperature heating of the heat pump does not meet the demand in the vehicle, the PTC heater 619 can be operated to assist the heating, thereby eliminating the heat generation of the heat pump air conditioning system during low temperature heating. The vehicle is defrost and defogged, and the heating effect is not good.

As described above, in the present disclosure, the expansion switching valve is a valve having both an expansion valve function and an on-off valve function, which can be regarded as an integration of an on-off valve and an expansion valve. An example embodiment of an expansion switch valve will be provided below.

As shown in FIGS. 6 and 7, the above-mentioned expansion switch valve may include a valve body 500 in which an inlet 501, an outlet 502, and an internal flow communicating between the inlet 501 and the outlet 502 are formed. The first spool 503 and the second spool 504 are mounted on the inner flow passage. The first spool 503 directly connects or disconnects the inlet 501 and the outlet 502, and the second spool 504 allows the inlet 501 and the outlet 502 to pass through the section. The flow port 505 is connected or disconnected.

Wherein, the "direct communication" achieved by the first spool means that the refrigerant entering from the inlet 501 of the valve body 500 can flow directly to the outlet 502 of the valve body 500 through the internal flow passage without passing through the first spool. The "disconnected communication" achieved by the first spool means that the refrigerant entering from the inlet 501 of the valve body 500 cannot pass over the first spool and cannot flow through the internal passage to the outlet 502 of the valve body 500. The "connected through the orifice" realized by the second spool means that the refrigerant entering from the inlet 501 of the valve body 500 can flow over the second spool through the throttling of the orifice 505 to the outlet of the valve body 500. 502, and the "disconnected communication" achieved by the second spool means that the refrigerant entering from the inlet 501 of the valve body 500 cannot pass over the second spool and cannot flow through the orifice 505 to the outlet 502 of the valve body 500.

Thus, by controlling the first spool and the second spool, the expansion switch valve of the present disclosure can cause the refrigerant entering from the inlet 501 to achieve at least three states. That is, 1) an off state; 2) a direct communication state over the first valve body 503; and 3) a throttle communication mode over the second valve body 504.

Wherein, the high-temperature high-pressure liquid refrigerant can be a low-temperature low-pressure mist-like liquid refrigerant after being throttled through the orifice 505, which can create conditions for the evaporation of the refrigerant, that is, the cross-sectional area of the orifice 505 is smaller than the outlet. The cross-sectional area of 502, and by controlling the second spool, the opening degree of the orifice 505 can be adjusted to control the flow rate through the orifice 505, to prevent insufficient refrigeration due to too little refrigerant, and to prevent Excessive refrigerant causes the compressor to produce a liquid hammer phenomenon. That is, the cooperation of the second spool 504 and the valve body 500 can cause the expansion switch valve to function as an expansion valve.

Thus, by installing the first spool 503 and the second spool 504 on the inner flow passage of the same valve body 500, the on-off control and/or the throttle control function of the inlet 501 and the outlet 502 are realized, and the structure is simple and easy to produce and When installed, the expansion switch valve provided by the present disclosure can reduce the refrigerant charge of the entire heat pump system, reduce the cost, simplify the pipeline connection, and facilitate the oil return of the heat pump system.

As an exemplary internal mounting structure of the valve body 500, as shown in FIGS. 6 to 11, the valve body 500 includes a valve seat 510 forming an internal flow passage and a first valve housing 511 mounted on the valve seat 510 and a second valve housing 512, a first electromagnetic driving portion 521 for driving the first valve body 503 is mounted in the first valve housing 511, and a second electromagnetic driving portion for driving the second valve core 504 is mounted in the second valve housing 512. 522, the first spool 503 extends from the first valve housing 511 to the internal flow passage in the valve seat 510, and the second spool 504 extends from one end adjacent to 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 power of the first electromagnetic driving portion 521 (eg, the electromagnetic coil), thereby controlling the direct connection or disconnection of the inlet 501 and the outlet 502; The control of the on/off of the second electromagnetic driving portion 522 (e.g., the electromagnetic coil) can conveniently control the position of the second spool 504, thereby controlling whether the inlet 501 and the outlet 502 are in communication with the orifice 505. In other words, the electronic expansion valve and the solenoid valve sharing the inlet 501 and the outlet 502 are installed in parallel in the valve body 500, thereby enabling automatic control of the on/off and/or throttling of the expansion switch valve, and simplifying the course of the pipe.

In order to make full use of the spatial position of the expansion switch valve in various directions, to avoid interference between the expansion switch valve and different pipeline connections, the valve seat 510 is formed into a polyhedral structure, the first valve housing 511, the second valve housing 512, the inlet 501 and the outlet 502 They are respectively disposed on different surfaces of the polyhedral structure, wherein the mounting directions of the first valve housing 511 and the second valve housing 512 are perpendicular to each other, and the opening directions of the inlet 501 and the outlet 502 are perpendicular to each other. In this way, the inlet and outlet pipes can be connected to different surfaces of the polyhedral structure, which can avoid the problem of messy and entangled pipe arrangement.

As a typical internal structure of the expansion switch valve, as shown in FIGS. 6 to 9, the internal flow path includes a first flow path 506 and a second flow path 507 respectively communicating with the inlet 501, and the first flow path 506 is formed with The first valve port 503 is engaged with the first valve port 516, and the throttle port 505 is formed on the second flow path 507 to form a second valve port 517 that cooperates with the second valve body 504, the first flow path 506 and the second flow Lane 507 meets downstream of second valve port 517 and is in communication with outlet 502.

That is, the closing or opening of the first valve port 516 is achieved by changing the position of the first valve body 503, thereby controlling the cutting or conduction of the first flow path 506 connecting the inlet 501 and the outlet 502, so that the above described The function of connecting or disconnecting the solenoid valve. Similarly, the second valve port 517 is realized by changing the position of the second valve body 504. It is cut off or turned on, so that the throttling function of the electronic expansion valve can be realized.

The first flow path 506 and the second flow path 507 can communicate with the inlet 501 and the outlet 502 respectively in any suitable arrangement. To reduce the overall occupied space of the valve body 500, as shown in FIG. 10, the second flow path 507 is the same as the outlet 502. To the opening, the first flow path 506 is formed as a first through hole 526 perpendicular to the second flow path 507, and the inlet 501 is connected to the second flow path 507 through the second through hole 527 opened in the sidewall of the second flow path 507. The first through hole 526 and the second through hole 527 are respectively in communication with the inlet 501. The first through hole 526 can be disposed in a vertical direction or in parallel with the second through hole 527, which is not limited by the disclosure, and is all within the protection scope of the present disclosure.

To further simplify the overall footprint of the valve body 500, as shown in FIGS. 13-16, the inlet 501 and the outlet 502 are perpendicular to each other on the valve body 500. Thus, as shown in FIGS. 13 to 15, the axis of the inlet 501, the axis of the outlet 502 (i.e., the axis of the second flow path 507), and the axis of the first flow path 506 are vertically arranged in space, thereby preventing the first The movement of the spool 503 and the second spool 504 causes interference and the internal space of the valve body 500 can be utilized to the maximum.

As shown in FIGS. 9 and 10, in order to facilitate the closing and opening of the first valve port 516, the first valve core 503 is coaxially disposed with the first valve port 516 in the moving direction to selectively block or disengage the first valve. Port 516.

To facilitate closing and opening of the second valve port 517, the second spool 504 is disposed coaxially with the second valve port 517 in the direction of movement to selectively block or disengage the second valve port 517.

Wherein, as shown in FIG. 12, in order to ensure the reliability of the first valve core 503 blocking the first flow passage 506, the first valve core 503 may include a first valve stem 513 and a first end connected to the first valve stem 513. A plug 523 for sealing against the end face of the first valve port 516 to block the first flow passage 506.

To facilitate adjustment of the opening of the orifice 505 of the expansion switch valve, as shown in FIGS. 9 and 10, the second spool 504 includes a second valve stem 514 whose end is tapered. The head structure, the second valve port 517 is formed as a tapered hole structure that cooperates with the tapered head structure.

The opening 505 opening of the expansion switch valve can be adjusted by the up and down movement of the second valve core 504, and the up and down movement of the second valve core 504 can be adjusted by the second electromagnetic driving portion 522. If the opening of the orifice 505 of the expansion switch valve is zero, as shown in FIG. 9, the second spool 504 is at the lowest position, and the second spool 504 blocks the second valve port 517, and the refrigerant is completely unable to pass the throttle. Port 505, that is, the second valve port 517; if the expansion switch valve throttle port 505 has an opening degree, as shown in FIG. 10, there is a gap between the tapered head structure of the end portion of the second valve body 504 and the orifice 505 After the refrigerant is throttled, it flows to the outlet 502. If it is required to increase the throttle opening degree of the expansion switch valve, the second solenoid 504 can be moved upward by controlling the second electromagnetic driving portion 522 to make the tapered head structure away from the throttle opening 505, thereby realizing the throttle opening 505. The opening degree becomes larger; on the contrary, when it is required to reduce the opening degree of the orifice 505 of the expansion switching valve, the second valve body 504 can be driven to move downward.

When in use, when only the solenoid valve function of the expansion switch valve is required, as shown in FIG. 9, FIG. 12 and FIG. 15, the first The spool 503 is disengaged from the first valve port 516, the first valve port 516 is in an open state, the second valve core 504 is at a lowest position, and the second valve core 504 blocks the throttle hole 505 and flows from the inlet 501 to the internal flow path. The refrigerant can not pass through the orifice 505 at all, and can only flow into the outlet 502 through the first valve port 516 and the first through hole 526 in sequence. When the solenoid valve is de-energized, the first spool 503 moves to the left, the first plug 523 and the first valve port 516 are separated, the refrigerant can pass through the first through hole 526; when the solenoid valve is energized, the first spool 503 Moving to the right, the first plug 523 and the first valve port 516 are fitted together, and the refrigerant cannot pass through the first through hole 526.

It should be noted that the dotted line with arrows in FIGS. 9 and 15 represents the circulation route and the tendency of the refrigerant when the solenoid valve function is used.

When only the electronic expansion valve function of the expansion switch valve is required, as shown in FIGS. 10 and 16, the second valve port 517, that is, the throttle port 505 is in an open state, and the first valve body 503 blocks the first valve port 516. The refrigerant flowing from the inlet 501 to the internal flow passage cannot pass through the first through hole 526, and can only flow into the outlet 502 through the second through hole 527 and the throttle port 505 in sequence, and can move the second valve core 504 up and down. The size of the opening of the orifice 505 is adjusted.

It should be noted that the dashed arrows with arrows in FIGS. 10 and 16 represent the 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 of the expansion switch valve and the electronic expansion valve function, as shown in FIGS. 7, 13, and 14, wherein the dotted line with an arrow represents the flow path and the direction of the refrigerant, the first spool 503 Deviating from the first valve port 516, the first valve port 516 is in an open state, the throttle port 505 is in an open state, and the refrigerant flowing into the inner flow channel can flow along the first flow channel 506 and the second flow channel 507 to the outlet 502, respectively, thereby It also has a solenoid valve function and an electronic expansion valve function.

It should be understood that the above-described embodiments are merely one example of an expansion switch valve, and are not intended to limit the present disclosure, and other expansion switch valves having both an expansion valve function and an on-off valve function are equally applicable to the present disclosure.

The present disclosure also provides an electric vehicle including the above described heat pump air conditioning system provided in accordance with the present disclosure. Among them, the electric vehicle may include a pure electric vehicle, a hybrid vehicle, and a fuel cell vehicle.

The preferred embodiments of the present disclosure have been described in detail above with reference to the accompanying drawings. However, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications can be made to the technical solutions of the present disclosure within the scope of the technical idea of the present disclosure. These simple variations are all within the scope of the disclosure.

It should be further noted that the specific technical features described in the above specific embodiments may be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, the present disclosure will not be further described in various possible combinations.

In addition, any combination of various embodiments of the present disclosure may be made as long as it does not deviate from the idea of the present disclosure, and should also be regarded as the disclosure of the present disclosure.

Claims

A heat pump air conditioning system, comprising: a compressor (604), an indoor condenser (601), an indoor evaporator (602), and an outdoor heat exchanger (605), an outlet of the compressor (604) An inlet of the indoor condenser (601) is in communication, and an outlet of the indoor condenser (601) is selectively connected to the outdoor heat exchanger (605) via a first throttle branch or a first through branch In communication, the outlet of the outdoor heat exchanger (605) is selectively in communication with the inlet of the compressor (604) via a second flow branch or via the second throttle branch with the indoor evaporator (602) The inlet of the chamber is in communication, and the outlet of the indoor evaporator (602) is in communication with the inlet of the compressor (604).
The heat pump air conditioning system according to claim 1, wherein the first through-flow branch is provided with a first switching valve (608), and the first throttle branch is provided with a first expansion valve (607) .
The heat pump air conditioning system according to claim 1, wherein said heat pump air conditioning system further comprises an expansion switch valve (603), an inlet of said expansion switch valve (603) and an outlet of said indoor condenser (601) Connected, an outlet of the expansion switch valve (603) is in communication with an inlet of the outdoor heat exchanger (605), and the first throttle branch is a throttle passage of the expansion switch valve (603). The first flow branch is a through flow passage of the expansion switch valve (603).
The heat pump air conditioning system according to claim 1, wherein the second through-flow branch is provided with a second switching valve (610), and the second throttle branch is provided with a second expansion valve (609) .
The heat pump air conditioning system of claim 1 wherein the outlet of the indoor evaporator (602) is in communication with the inlet of the compressor (604) via a one-way valve (615).
The heat pump air conditioning system according to claim 1, wherein said heat pump air conditioning system is applied to an electric vehicle, and said second throughflow branch is provided with a plate heat exchanger (612), said plate heat exchanger ( 612) is simultaneously disposed in the motor cooling system of the electric vehicle.
The heat pump air conditioning system according to claim 6, wherein the second through-flow branch is provided with a second switching valve (610), and a refrigerant inlet (612a) of the plate heat exchanger (612) is The outlet of the outdoor heat exchanger (605) is in communication, and the refrigerant outlet (612b) of the plate heat exchanger (612) is in communication with the inlet of the second switching valve (610).
A heat pump air conditioning system according to claim 6 wherein said motor cooling system includes a motor in series with said plate heat exchanger (612) to form a circuit, a motor radiator (613) and a water pump (614).
The heat pump air conditioning system according to claim 1, wherein said heat pump air conditioning system further comprises a gas-liquid separator (611), an outlet of said indoor evaporator (602) and said gas-liquid separator (611) The inlet of the outdoor heat exchanger (605) is in communication with the inlet of the gas-liquid separator (611) via the second through-flow branch, An outlet of the gas-liquid separator (611) is in communication with an inlet of the compressor (604).
The heat pump air conditioning system according to claim 1, wherein said heat pump air conditioning system further comprises a PTC heater (619) for heating to flow through said indoor condenser (601) wind of.
The heat pump air conditioning system according to claim 10, wherein the PTC heater (619) is disposed on a windward side or a leeward side of the indoor condenser (601).
An electric vehicle characterized by comprising the heat pump air conditioning system according to any one of claims 1-11.