CN211222955U - Double-chamber external heat exchanger heat pump system - Google Patents

Abstract

A dual outdoor heat exchanger heat pump system comprising: compressor, indoor condenser, main outdoor heat exchanger, supplementary outdoor heat exchanger and indoor evaporimeter with accumulator, the utility model discloses can realize that the defrosting goes on with heating simultaneously, can realize heating in succession, reach the effect of the less or even no decay of heating amount attenuation range, the maximize utilize outdoor heat exchanger's ability, during the system refrigeration, outdoor heat exchanger heat-sinking capability is best, the pressure loss is less, when the system heats, outdoor heat exchanger imports and exports the switching-over, realize that the refrigerant overflow formula flows to reach best evaporation effect, the pressure loss is also less relatively.

Description

Double-chamber external heat exchanger heat pump system

Technical Field

The utility model relates to a technique in the field of automobile air conditioners, in particular to a heat pump system of a double-chamber outer heat exchanger.

Background

The refrigeration of new energy automobile in current market adopts traditional air conditioning system, the heating adopts the electric heating PTC mode, the requirement of passenger cabin travelling comfort has been realized to a certain extent, however electric heating PTC's efficiency is less than 1 all the time, along with ambient temperature's reduction, efficiency can reduce, consume battery energy grow moreover, cause whole car continuation of the journey mileage greatly reduced, along with when more and more the requirement that national policy and user put forward car key parameter-continuation of the journey mileage, various heat pump system come into force, whole car thermal management concept along with carrying heat pump system also becomes more and more hot.

The heat pump system adopts the reverse Carnot cycle principle, can continuously absorb heat from outdoor environment media (air, water or other heat sources) and then release the heat into an indoor space needing to be heated, after heating for a period of time, the heat exchanger absorbing heat from the outdoor environment media generates condensed water on the surface of the heat exchanger along with the existence of water in the environment due to too low surface temperature, when the temperature of the outdoor environment media is too low, frost or ice is condensed on the surface of the heat exchanger so as to block heat exchange fins of the heat exchanger, the heating effect of the heat pump system is poor, the efficiency is reduced, a defrosting mode needs to be operated at the moment, high-temperature and high-pressure gaseous refrigerants discharged by a compressor directly enter the outdoor heat exchanger, the defrosting purpose of the heat exchanger is realized through a hot gas defrosting mode, however, the heating effect of a passenger compartment is sacrificed to a certain extent, because outdoor heat exchanger can not follow the heat absorption in the outdoor environment air, the heat that passenger cabin emitted all relies on the compressor to do work to only a small part is used for the heating, and defrosting time will prolong to some extent otherwise, and user side experience is felt worsen, and is the infringement mutually with the original purpose of installing heat pump system additional in order to reach energy-conserving effect.

SUMMERY OF THE UTILITY MODEL

The utility model discloses it is not high to current new energy automobile passenger cabin travelling comfort, need intermittent type nature to change frost not enough when heating winter, provide a two outer heat exchanger heat pump system of room, can realize defrosting and heat and go on simultaneously, can realize heating in succession, reach the effect of the less zero decay even of heating quantity attenuation range, the maximize utilizes outdoor heat exchanger's ability, during the system refrigeration, outdoor heat exchanger heat-sinking capability is best, the pressure loss is less, when the system heats, outdoor heat exchanger imports and exports the switching-over, realize that the refrigerant overflow formula flows, thereby reach best evaporation effect, the pressure loss is also less relatively.

The utility model discloses a realize through following technical scheme:

the utility model discloses a: compressor, condensing equipment, main outdoor heat exchanger, supplementary outdoor heat exchanger and indoor evaporimeter with accumulator, wherein: the output end of the compressor is connected with the condensing equipment, the auxiliary outdoor heat exchanger, the main outdoor heat exchanger and the indoor evaporator in sequence, and the output end of the indoor evaporator is connected with the input end of the liquid storage separator to form a refrigerating loop; the input end of the main outdoor heat exchanger is provided with a second three-way electromagnetic valve connected with the input end of the liquid storage separator, a first bypass is arranged between a first port of the second three-way electromagnetic valve and the main outdoor heat exchanger, and a fourth bypass is arranged between a second port of the second three-way electromagnetic valve and the input end of the liquid storage separator; a second bypass is arranged between the output end of the main outdoor heat exchanger and the output end of the condensing equipment, and a second main throttle valve is arranged on the second bypass; a first three-way electromagnetic valve is arranged between the input end of the auxiliary outdoor heat exchanger and a third port of the second three-way electromagnetic valve, and a third bypass is arranged between the first three-way electromagnetic valve and the auxiliary outdoor heat exchanger; and the third port of the first three-way electromagnetic valve is connected with the output end of the main outdoor heat exchanger.

The main outdoor heat exchanger and the auxiliary outdoor heat exchanger form a double-chamber outdoor heat exchanger module, and a bidirectional main throttle valve is arranged between the double-chamber outdoor heat exchanger module and the auxiliary outdoor heat exchanger module.

The first bypass is provided with a sixth stop valve, the third bypass is provided with a second stop valve, and the second main throttle valve is connected with a fifth stop valve in parallel.

And the condensing equipment is further provided with an auxiliary plate type heat exchanger, and the input end and the output end of the plate type heat exchanger are respectively connected with the input end of the compressor and the input end of the auxiliary outdoor heat exchanger.

Technical effects

Compared with the prior art, the utility model discloses technical effect includes:

1. when the heat pump system is used for refrigerating and heating, the flow directions of refrigerants at the inlet and the outlet of the outdoor heat exchanger are reversed, so that the heat exchange effect and the pressure loss of the outdoor heat exchanger when the outdoor heat exchanger is used as a condenser and an evaporator can be optimally balanced, the energy consumption of the system is reduced, the heat exchange effect is improved, and the heat exchange efficiency of the system is improved;

2. the heat pump system can independently realize continuous and uninterrupted heating without depending on other power consumption equipment, and simultaneously considers the operation of the defrosting mode, so that the comfort of the passenger compartment is greatly improved;

3. the heat pump system can realize dehumidification effects of high temperature, high humidity and low temperature, thereby meeting the requirement of comfort in the passenger compartment at multiple environmental temperatures.

Drawings

FIG. 1 is a schematic structural view of the present invention;

fig. 2 is a schematic diagram of a refrigerant flow path in the cooling mode of the embodiment 1, in which a solid line part represents a medium refrigerant flow path, and a dashed line part represents a refrigerant non-circulation state;

fig. 3 is a schematic diagram of a refrigerant flow path in the first heating mode of operation in embodiment 1, in which a solid line portion represents a medium refrigerant flow path, and a dashed line portion represents a refrigerant non-flow state;

fig. 4 is a schematic diagram of a refrigerant flow path in the second heating mode of operation in embodiment 1, in which a solid line portion represents a medium refrigerant flow path, and a dashed line portion represents a refrigerant non-flow state;

fig. 5 is a schematic diagram of a refrigerant flow path in the third heating mode of the embodiment 1, in which a solid line portion represents a medium refrigerant flow path, and a dashed line portion represents a refrigerant non-flowing state;

fig. 6 is a schematic view of a refrigerant flow path in the low temperature dehumidification mode of the embodiment 1, in which a solid line part indicates a medium refrigerant flow path, and a dotted line part indicates a refrigerant non-flowing state;

fig. 7 is a schematic diagram of a refrigerant flow path in the high temperature mode of operation in embodiment 1, in which a solid line portion represents a medium refrigerant flow path, and a dashed line portion represents a refrigerant non-flowing state;

FIG. 8 is a view showing a variation of embodiment 2 of the dual chamber external heat exchanger heat pump system;

FIG. 9 is a view showing a variation of the dual chamber external heat exchanger heat pump system of embodiment 3;

in the figure: the system comprises a compressor 1, an indoor condenser 2, a first stop valve 3, an auxiliary outdoor heat exchanger 4, a first main throttle valve 5, an outdoor heat exchanger 6, a second main throttle valve 7, a first three-way electromagnetic valve 8, a second three-way electromagnetic valve 9, a first auxiliary throttle valve 10, an indoor evaporator 11, a liquid storage 12, a second stop valve 13, a third stop valve 14, a second auxiliary throttle valve 15, a fifth stop valve 16, a sixth stop valve 17, a seventh stop valve 18, a kettle 19, a pump 20, a plate heat exchanger 21, a warm air core 22, a first bypass a, a second bypass b, a third bypass c and a fourth bypass d.

Detailed Description

Example 1

As shown in fig. 1, the present embodiment includes: compressor 1 with liquid storage separator 12, indoor condenser 2, main outdoor heat exchanger 6, auxiliary outdoor heat exchanger 4 and indoor evaporator 11, wherein:

the output end of the compressor 1 is sequentially connected with an indoor condenser 2, an auxiliary outdoor heat exchanger 4, a main outdoor heat exchanger 6 and an indoor evaporator 11, and the output end of the indoor evaporator 11 is connected with the input end of a liquid storage separator 12 to form a refrigerating loop;

a second three-way electromagnetic valve 9 connected with the input end of the liquid storage separator 12 is arranged at the input end of the main outdoor heat exchanger 6, a first bypass is arranged between a first port of the second three-way electromagnetic valve 9 and the main outdoor heat exchanger 6, and a fourth bypass is arranged between a second port of the second three-way electromagnetic valve 9 and the input end of the liquid storage separator 12;

a second bypass is arranged between the output end of the main outdoor heat exchanger 6 and the output end of the indoor condenser 2, and a second main throttle valve 7 is arranged on the second bypass;

a first three-way electromagnetic valve 8 is arranged between the input end of the auxiliary outdoor heat exchanger 4 and a third port of the second three-way electromagnetic valve 9, and a third bypass is arranged between the first three-way electromagnetic valve 8 and the auxiliary outdoor heat exchanger 4; the third port of the first three-way solenoid valve 8 is connected to the output of the main outdoor heat exchanger 6.

And a first stop valve 3 is arranged between the output end of the indoor condenser 2 and the auxiliary outdoor heat exchanger 4.

And a first main throttle valve 5 is arranged at the output end of the auxiliary outdoor heat exchanger 4.

The input end of the indoor evaporator 11 is provided with a first auxiliary throttle valve 10 with a cut-off function.

The system performs specific temperature control in the following way:

cooling mode

As shown in fig. 2, a high-temperature and high-pressure gaseous refrigerant discharged from a compressor 1 flows through an indoor condenser 2, passes through a first stop valve 3, enters an auxiliary outdoor heat exchanger 4, releases heat to the environment to achieve a precooling effect, then flows through a first main throttle valve 5, enters an outdoor heat exchanger 6, continues to release heat to the outdoor environment to achieve a supercooled state, flows through a first three-way electromagnetic valve 8, enters a first auxiliary throttle valve 10 for throttling, becomes a low-temperature and low-pressure two-phase refrigerant, enters an indoor evaporator 11, absorbs the heat of air blown into a passenger compartment by a blower to become a low-pressure and low-temperature gaseous refrigerant, achieves a refrigerating effect of the passenger compartment, and finally flows through a gas-liquid separator to enter the compressor to complete a cycle;

under this mode, the temperature air door is closed in the air-conditioning box, and first stop valve 3 and first main choke valve 5 open, and first three solenoid valve 8 right part UNICOM, second three solenoid valve 9 close completely, and first auxiliary choke valve 10 has the throttle function.

② first heating mode

As shown in fig. 3, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows into the indoor condenser 2, the air blown into the blower releases heat and then becomes high-pressure medium-temperature supercooled refrigerant, the air is throttled in the second main throttle valve 7 on the second bypass b and becomes low-temperature and low-pressure two-phase refrigerant, the low-temperature and low-pressure two-phase refrigerant flows into the outdoor heat exchanger 6, the heat in the environment is absorbed and becomes low-temperature and low-pressure gaseous/two-phase refrigerant, the low-temperature and low-pressure gaseous/two-phase refrigerant then flows into the first bypass a, passes through the second three-way electromagnetic valve 9 and flows into the liquid storage separator 12 to complete the separation of;

under this mode, the temperature air door is opened in the air-conditioning box, first shut-off valve 3, first main throttle valve 5, first three way solenoid valve 8 to and first auxiliary throttle valve 10 are closed completely, and the side part UNICOM on the second three way solenoid valve 9.

Third heating mode

As shown in fig. 4, when it is detected that the surface of the main outdoor heat exchanger 6 is frosted and the heat exchange effect is affected, the heat pump system starts the second heating mode. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 1 flows into the indoor condenser 2, the air blown into the blower releases heat to change into high-pressure medium-temperature supercooled refrigerant, enters the second bypass b, flows through the second main throttle valve 7, flows into the main outdoor heat exchanger 6, releases heat, melts frost on the surface layer of the main outdoor heat exchanger 6 to change into high-pressure low-temperature supercooled refrigerant, then is throttled by the first main throttle valve 5 to change into low-temperature low-pressure two-phase refrigerant, flows into the auxiliary outdoor heat exchanger 4, absorbs heat in the environment to change into low-temperature low-pressure gaseous/two-phase refrigerant, enters the third bypass c, then flows through the first three-way electromagnetic valve 8 and the second three-way electromagnetic valve 9, enters the liquid storage separator 12 through the fourth bypass d to complete gas-liquid separation, and saturated gaseous refrigerant enters the compressor 1 to complete a cycle;

under this mode, the temperature air door is opened in the air-conditioning box, and first stop valve 3 and first auxiliary throttle valve 10 close completely, and second main throttle valve 7 is opened, and 8 partial UNICOMs on the part under the first three way solenoid valve, 9 right side parts UNICOMs on the second three way solenoid valve, first main throttle valve 6 has the throttling function.

Fourthly third heating mode

As shown in fig. 5, when the system determines that the heating effect is deteriorated due to frosting on the surface layer of the auxiliary outdoor heat exchanger 4 through the sensor, the third heating mode is started. High-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows through the indoor condenser 2, is changed into high-pressure and medium-temperature supercooled refrigerant after releasing heat to wind blown by a blower, enters the auxiliary outdoor heat exchanger 4 through the first stop valve 3, is changed into high-pressure and low-temperature supercooled refrigerant after melting frost on the surface layer of the auxiliary outdoor heat exchanger 4, flows into the first main throttle valve 5 for throttling, then enters the main outdoor heat exchanger 6, absorbs heat in the environment to be changed into low-temperature and low-pressure gaseous/two-phase refrigerant, sequentially flows through the first three-way electromagnetic valve 8 and the second three-way electromagnetic valve 9, enters the liquid storage separator 12 through the fourth bypass d to complete gas-liquid separation, and saturated gaseous refrigerant enters the compressor 1 to complete a cycle;

in the mode, a temperature air door in the air conditioning box is opened, the first stop valve 3 is opened, the second main throttle valve 7 and the first auxiliary throttle valve 10 are completely closed, the right parts of the first three-way electromagnetic valve 8 and the second three-way electromagnetic valve 9 are communicated, and the first main throttle valve 6 has a throttling function.

Low temperature dehumidification mode

As shown in fig. 6, when the automobile is in a low-temperature and high-humidity environment, the dehumidification mode needs to be activated for the comfort of the passenger compartment. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 1 flows into the indoor condenser 2, releases heat to dry and cold air flowing through the indoor evaporator 11, then becomes high-pressure medium-temperature supercooled refrigerant, enters the second bypass b, flows into the second main throttle valve 7 for throttling, then enters the main outdoor heat exchanger 6, absorbs heat in the environment to become low-temperature low-pressure gaseous/two-phase refrigerant, then passes through the first main throttle valve 5, enters the auxiliary outdoor heat exchanger 4, absorbs heat in the environment to become low-temperature low-pressure gaseous/two-phase refrigerant, enters the third bypass c, then flows through the first three-way electromagnetic valve 8, enters the first auxiliary throttle valve 10 for secondary throttling, becomes low-temperature low-pressure two-phase refrigerant, absorbs heat blown by the blower to become low-pressure low-temperature gaseous refrigerant, separates moisture in the air, and realizes the effect of dehumidifying the passenger compartment, the mixture enters the compressor 1 through the liquid storage separator 12 to complete a cycle;

under this mode, the temperature air door is opened in the air-conditioning box, and first shut-off valve 3 and second three way solenoid valve 9 close completely, and first main choke valve 5 is opened, and first three way solenoid valve 8 part UNICOM down, second main choke valve 7 and first auxiliary throttle valve 10 have the throttle function.

High temperature dehumidification mode

As shown in fig. 7, when the automobile is in a high temperature and high humidity environment, the dehumidification mode needs to be activated for the comfort of the passenger compartment. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 1 flows through the indoor condenser 2, passes through the first stop valve 3, enters the auxiliary outdoor heat exchanger 4, releases heat to the air in the outdoor environment to achieve a precooling effect, becomes high-pressure high-temperature gaseous refrigerant, then passes through the first main throttle valve 5, enters the main outdoor heat exchanger 6, releases heat to the air in the environment to achieve a supercooling effect, becomes high-pressure medium-temperature supercooled refrigerant, then flows through the first three-way electromagnetic valve 8, enters the first auxiliary throttle valve 10 to be throttled, becomes low-temperature low-pressure two-phase refrigerant, absorbs the heat of the air blown by the blower to become low-pressure low-temperature gaseous refrigerant, separates out the moisture in the air, achieves the dehumidification effect of the passenger compartment, and enters the compressor 1 through the liquid storage separator 12 to complete a cycle;

in the mode, a temperature air door in the air conditioning box is closed, the first stop valve 3 and the first main throttle valve 5 are opened, the right part of the first three-way electromagnetic valve 8 is communicated, the second three-way electromagnetic valve 9 and the second main throttle valve 7 are completely closed, and the first auxiliary throttle valve 10 has a throttling function.

Example 2

As shown in fig. 8, compared with embodiment 1, in this embodiment, a sixth stop valve 17 is arranged on the first bypass a, a second stop valve 13 is arranged on the third bypass c, and a fifth stop valve 16 is connected in parallel to the second main throttle 7, so that the mode is switched to avoid the frosting condition in advance or to heat and defrost while the frosting is avoided on the premise that the basic cooling, heating and dehumidifying functions of the heat pump system can be ensured to provide continuous heat for the passenger compartment, thereby really solving the problem that the heating effect is sacrificed when the frosting of the heat pump is lost.

Example 3

As shown in fig. 9, compared with embodiment 1, in this embodiment, the indoor condenser 2 is replaced by a warm air core 22, and an auxiliary plate heat exchanger 21 is further provided between the warm air core 2, the first stop valve 3 and the compressor 1, a first input end and a first output end of the plate heat exchanger 21 are respectively connected to the compressor 1 and the first stop valve 3, and a second input end and a second output end are respectively connected to an auxiliary pump body 20 with a water source 19 and the warm air core 22.

The present embodiment can also realize the above modes, but due to the addition of the heat exchange devices, compared with the heat pump system of embodiment 1, under the same conditions, the heat loss is increased, but the defect of air volume attenuation under refrigeration and high temperature dehumidification of embodiment 1 is also made up to a certain extent, the air conditioning box can cancel the temperature air door, the control difficulty is reduced, and the air volume of the air conditioning box under refrigeration and high temperature dehumidification is improved.

In the embodiment, the front cabin is provided with the main outdoor heat exchanger and the auxiliary outdoor heat exchanger, the bypass path a and the bidirectional throttling device 5 are sequentially connected between the main outdoor heat exchanger 6 and the auxiliary outdoor heat exchanger 4, and the existence of the key combination enables the double-outdoor heat exchanger to work uninterruptedly, so that continuous heat is provided for a heat pump system.

This embodiment is all to current vehicle air conditioning system adopt single outdoor heat exchanger, does not possess the ability of subregion control, moreover under the system operation special mode, often can only realize a function: absorbing or dissipating heat. In an environment temperature range of-7-10 ℃, the heat pump system runs a heating mode for a long time, the surface layer of the outdoor heat exchanger is easy to frost or even block a channel, so that the heat exchange capacity of the outdoor heat exchanger is greatly reduced, at the moment, the outdoor heat exchanger is expected to dissipate heat and defrost, the heat exchange capacity of the outdoor heat exchanger is improved, and the outdoor heat exchanger is expected not to generate large attenuation when absorbing heat in the environment air.

The main and auxiliary outdoor heat exchanger modules are adopted, the state of the refrigerant entering the two outdoor heat exchangers can be controlled through the bidirectional throttle valve, so that refrigerant partition control is realized, the two outdoor heat exchangers are coordinately controlled, different functions under different modes are realized, and the system can continuously run.

Compared with the prior art, the device improves the heat dissipation capacity of the outdoor heat exchanger in the refrigeration mode. The double-chamber outer heat exchanger can be partially overlapped, which is equivalent to fully utilizing the space of the front cabin, and the sum of the areas of the unfolded fins of the double-chamber outer heat exchanger is larger than that of the single-chamber outer heat exchanger, so that the heat dissipation performance is enhanced; the double-stage throttling can be started no matter in a refrigerating or heating mode, under the condition that the suction superheat degree of the compressor is unchanged, the supercooling degree of the high-pressure section is increased, the enthalpy difference of an evaporation inlet and an evaporation outlet of the low-pressure section is increased, and the refrigerating and heating effects are enhanced; due to the existence of the main outdoor heat exchanger module and the auxiliary outdoor heat exchanger module, in a heating mode, any outdoor heat exchanger frosts, and the other outdoor heat exchanger can work normally. The medium-temperature refrigerant flows through the frosted outdoor heat exchanger to melt the frost layer on the surface layer of the fin, the supercooling degree of the high-pressure section is increased due to the temperature reduction of the refrigerant, and then the refrigerant passes through the bidirectional throttle valve; the heat in the ambient air is absorbed by another outdoor heat exchanger after throttling, and the heat is continuously supplied to the heat pump system.

The foregoing embodiments may be modified in various ways by those skilled in the art without departing from the spirit and scope of the present invention, which is not limited by the above embodiments but is to be accorded the full scope defined by the appended claims, and all such modifications and variations are within the scope of the invention.

Claims (5)

1. A dual outdoor heat exchanger heat pump system, comprising: compressor, condensing equipment, main outdoor heat exchanger, supplementary outdoor heat exchanger and indoor evaporimeter with accumulator, wherein: the output end of the compressor is connected with the condensing equipment, the auxiliary outdoor heat exchanger, the main outdoor heat exchanger and the indoor evaporator in sequence, and the output end of the indoor evaporator is connected with the input end of the liquid storage separator to form a refrigerating loop; the input end of the main outdoor heat exchanger is provided with a second three-way electromagnetic valve connected with the input end of the liquid storage separator, a first bypass is arranged between a first port of the second three-way electromagnetic valve and the main outdoor heat exchanger, and a fourth bypass is arranged between a second port of the second three-way electromagnetic valve and the input end of the liquid storage separator; a second bypass is arranged between the output end of the main outdoor heat exchanger and the output end of the condensing equipment, and a second main throttle valve is arranged on the second bypass; a first three-way electromagnetic valve is arranged between the input end of the auxiliary outdoor heat exchanger and a third port of the second three-way electromagnetic valve, and a third bypass is arranged between the first three-way electromagnetic valve and the auxiliary outdoor heat exchanger; and the third port of the first three-way electromagnetic valve is connected with the output end of the main outdoor heat exchanger.

2. The system of claim 1 wherein the main outdoor heat exchanger and the auxiliary outdoor heat exchanger comprise a dual outdoor heat exchanger module with a bi-directional main throttle valve therebetween.

3. The system as claimed in claim 1, wherein a sixth stop valve is provided on the first bypass, a second stop valve is provided on the third bypass, and a fifth stop valve is connected in parallel to the second main throttle.

4. The system as set forth in claim 1, wherein said condensing means is further provided with an auxiliary plate heat exchanger having an input and an output connected to the compressor and the input of the auxiliary outdoor heat exchanger, respectively.

5. The system of claim 1 or 4, wherein the condensing device is an indoor condenser or a warm air core.

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