CN109028543B - Heat exchange device and air conditioning unit provided with same - Google Patents
Heat exchange device and air conditioning unit provided with same Download PDFInfo
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- CN109028543B CN109028543B CN201811063087.1A CN201811063087A CN109028543B CN 109028543 B CN109028543 B CN 109028543B CN 201811063087 A CN201811063087 A CN 201811063087A CN 109028543 B CN109028543 B CN 109028543B
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- heat exchange
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- exchange device
- air conditioning
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 33
- 239000003507 refrigerant Substances 0.000 claims abstract description 142
- 238000001816 cooling Methods 0.000 claims abstract description 60
- 238000004781 supercooling Methods 0.000 claims abstract description 23
- 230000009471 action Effects 0.000 claims abstract description 4
- 238000013461 design Methods 0.000 abstract description 10
- 230000009467 reduction Effects 0.000 abstract description 9
- 238000012546 transfer Methods 0.000 abstract description 6
- 239000007788 liquid Substances 0.000 description 9
- 230000001502 supplementing effect Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009413 insulation Methods 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 238000010977 unit operation Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention relates to a heat exchange device and an air conditioning unit provided with the same, wherein the heat exchange device comprises: a housing; a refrigerant input pipe; a main refrigerant circuit accommodated in the casing and communicated with the refrigerant input pipeline; the refrigerant auxiliary loop is accommodated in the shell and communicated with the refrigerant input pipeline, and comprises a depressurization and cooling unit, and the refrigerant in the refrigerant auxiliary loop is depressurized and cooled under the action of the depressurization and cooling unit; the refrigerant after the pressure reduction and the temperature reduction in the refrigerant auxiliary loop can exchange heat with the refrigerant in the refrigerant main loop. Above-mentioned heat transfer device, refrigerant realize step down and cooling through step down cooling unit in heat transfer device inside, and need not devices such as extra choke valve that set up outside heat transfer device to when guaranteeing to improve air conditioning unit's heat exchange capacity, improve refrigerant supercooling degree, simplified air conditioning unit's pipeline design and air conditioning unit accessory selection type scheme, reduced air conditioning unit's global design degree of difficulty.
Description
Technical Field
The invention relates to the field of heat exchange devices, in particular to a heat exchange device and an air conditioning unit with the same.
Background
The heat pump air conditioning system often works in a low temperature environment, the evaporation pressure is lower, the water supply temperature and the condensation temperature are maintained at certain values, the corresponding compression ratio is increased, the throttling loss of circulation is increased, the internal leakage loss of the machine is also increased, and the heat exchange efficiency is drastically reduced. On the other hand, the motor of the compressor is cooled by sucking refrigerant, and the refrigerant circulation amount of the air conditioning system is reduced at a high pressure ratio, so that the motor cannot be cooled well. Therefore, in order to improve the operation efficiency and the performance of the air conditioning system, the characteristics that the air suction, compression and exhaust processes of the compressor are positioned at different space positions are generally utilized at present, an air supplementing port is additionally arranged at the critical point of the air suction end and the compression start of the compressor, an economizer is arranged between the condenser and the evaporator, part of refrigerant conveyed to the economizer by the condenser is converted into overheated refrigerant gas, and the overheated refrigerant gas enters the compression cavity through the air supplementing port, so that the heat exchange capacity of the machine set is effectively improved, the exhaust temperature of the compressor is reduced, and the system has higher energy efficiency ratio. The other part of refrigerant is cooled in the economizer to form supercooled refrigerant liquid, and the supercooled refrigerant liquid enters the evaporator, so that the purposes of improving the refrigerating capacity and the refrigerating efficiency of the system are achieved.
However, the economizer is used as an additional accessory of the heat pump air conditioning system and needs to be matched with structures such as a throttle valve, so that the cost of the unit is increased, the problem of occupying excessive space is solved, and the vibration risk of the unit operation is correspondingly increased due to the higher requirements on the pipeline design.
Disclosure of Invention
Based on the above, it is necessary to provide a heat exchange device capable of simplifying the pipeline design and connection difficulty of an air conditioning unit and an air conditioning unit provided with the heat exchange device, aiming at the problem that the pipeline design and connection difficulty of the air conditioning unit are improved due to the arrangement of an economizer.
A heat exchange device, the heat exchange device comprising:
A housing;
a refrigerant input pipe;
A main refrigerant circuit housed in the casing and communicating with the refrigerant input pipe; and
The refrigerant auxiliary loop is accommodated in the shell and communicated with the refrigerant input pipeline, the refrigerant auxiliary loop comprises a depressurization and cooling unit, and the refrigerant in the refrigerant auxiliary loop is depressurized and cooled under the action of the depressurization and cooling unit;
The refrigerant in the auxiliary refrigerant loop after the pressure reduction and the temperature reduction can exchange heat with the refrigerant in the main refrigerant loop.
Above-mentioned heat transfer device, refrigerant realize step down and cooling through step down cooling unit in heat transfer device inside, and need not devices such as extra choke valve that set up outside heat transfer device to when guaranteeing to improve air conditioning unit's heat exchange capacity, improve refrigerant supercooling degree, simplified air conditioning unit's pipeline design and air conditioning unit accessory selection type scheme, reduced air conditioning unit's global design degree of difficulty.
In one embodiment, the depressurization and cooling unit comprises a throttle valve port and an adiabatic cooling cavity communicated with the throttle valve port, the adiabatic cooling cavity is communicated with the refrigerant input pipeline through the throttle valve port, and the caliber of the throttle valve port is smaller than the caliber of the refrigerant input pipeline.
In one embodiment, the orifice is adjustable in size.
In one embodiment, the caliber of the throttling valve port is adjusted according to the superheat degree of the outlet end of the auxiliary loop;
When the superheat degree of the outlet end of the auxiliary loop of the refrigerant is larger than the target superheat degree, the caliber of the throttling valve port is increased;
And when the superheat degree of the outlet end of the auxiliary loop of the refrigerant is smaller than the target superheat degree, the caliber of the throttling valve port is reduced.
In one embodiment, the volume of the adiabatic cooling chamber is adjustable.
In one embodiment, the volume of the adiabatic cooling chamber is adjusted according to the supercooling degree of the outlet end of the adiabatic cooling chamber;
When the supercooling degree of the outlet end of the heat-insulating cooling cavity is smaller than the target supercooling degree, the volume of the heat-insulating cooling cavity is increased;
And when the supercooling degree of the outlet end of the heat-insulating cooling cavity is larger than the target supercooling degree, the volume of the heat-insulating cooling cavity is reduced.
In one embodiment, the depressurization and cooling unit includes a fixed side wall, a movable side wall and a driving assembly, wherein the driving assembly is connected to the movable side wall, and the movable side wall can move relative to the fixed side wall under the driving of the driving assembly to form the heat-insulation cooling cavity with adjustable volume.
In one embodiment, the main circuit of the refrigerant comprises a first heat exchange channel and a main circuit output pipe, and the main circuit output pipe is communicated with the refrigerant input pipe through the first heat exchange channel.
In one embodiment, the auxiliary refrigerant circuit comprises an auxiliary input pipe, a second heat exchange channel and an auxiliary output pipe, wherein the second heat exchange channel is communicated with the adiabatic cooling cavity through the auxiliary input pipe, and the auxiliary output pipe is communicated with the auxiliary input pipe through the second heat exchange channel.
An air conditioning unit comprises the heat exchange device.
Drawings
Fig. 1 is a schematic structural view of an air conditioning unit according to an embodiment;
FIG. 2 is a schematic view of a front side of a heat exchange device of the air conditioning unit shown in FIG. 1;
FIG. 3 is a schematic view of the right side of the heat exchange device of FIG. 2;
fig. 4 is a schematic view of the left side of the heat exchange device shown in fig. 2.
Detailed Description
In order that the invention may be readily understood, a more complete description of the invention will be rendered by reference to the appended drawings. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.
It will be understood that when an element is referred to as being "fixed to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like are used herein for illustrative purposes only.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and/or" as used herein includes any and all combinations of one or more of the associated listed items.
As shown in fig. 1, an air conditioning unit 100 according to an embodiment of the present invention includes a compressor 10, an evaporator 30, a four-way valve 20, a heat exchange device 40, a condenser 50, a throttle valve 60, and the like, which are connected by pipes to form a cooling and heating circuit, so as to perform a cooling and heating operation.
Specifically, the compressor 10 includes a suction end, a discharge end, and a supply port. The four-way valve 20 includes a first valve port, a second valve port, a third valve port and a fourth valve port, which are selectively communicated with each other, wherein the first valve port is communicated with an exhaust end of the compressor 10 through a pipe, the second valve port is communicated with the evaporator 30 through a pipe, the third valve port is communicated with an intake end of the compressor 10 through a pipe, and the fourth valve port is communicated with the condenser 50 through a pipe. The evaporator 30 is also optionally in communication with the heat exchange device 40 or the condenser 50 via a conduit, the condenser 50 is optionally in communication with the heat exchange device 40 or the evaporator 30 via a conduit, and the air supply port of the compressor 10 is in communication with the heat exchange device 40 via a conduit.
When the air conditioning unit 100 performs a refrigeration cycle, the discharge port of the compressor 10, the first port of the four-way valve 20, the fourth port of the four-way valve 20, the condenser 50, the heat exchange device 40, the evaporator 30, the second port of the four-way valve 20, the third port of the four-way valve 20, and the suction port of the compressor 10 are sequentially connected. The compressor 10 compresses a refrigerant into a high-temperature and high-pressure gas state, and the high-temperature and high-pressure gas state refrigerant enters the condenser 50 through the four-way valve 20, and is discharged into the condenser 50 to form a medium-temperature and high-pressure gas state refrigerant. The medium-temperature high-pressure gaseous refrigerant enters the heat exchange device 40, one part of the refrigerant is depressurized and cooled in the heat exchange device 40 to form the gaseous refrigerant, then the gaseous refrigerant returns to the air supplementing port of the compressor 10, the other part of the refrigerant is discharged in the heat exchange device 40 to form liquid refrigerant, the liquid refrigerant enters the evaporator 30 through the throttling depressurization of the throttle valve 60, the liquid refrigerant absorbs heat in the evaporator 30 to evaporate into a gaseous state, and finally the liquid refrigerant returns to the air suction end of the compressor 10 through the four-way valve 20, so that one refrigeration cycle is completed. It will be appreciated that the above cycle is repeated so that the air conditioning unit 100 is continuously in the cooling process.
As shown in fig. 2 to 4, the heat exchange device 40 is an economizer, and includes a housing 41, a refrigerant input pipe 43, a main refrigerant circuit 45, and an auxiliary refrigerant circuit, wherein the refrigerant input pipe 43, the main refrigerant circuit 45, and the auxiliary refrigerant circuit are all accommodated in the housing 41 to form a compact whole.
The auxiliary refrigerant circuit includes a pressure-reducing and temperature-reducing unit 472, and the refrigerant entering the auxiliary refrigerant circuit is reduced in pressure and temperature under the action of the pressure-reducing and temperature-reducing unit 472, and the refrigerant subjected to pressure reduction and temperature reduction can exchange heat with the refrigerant in the main refrigerant circuit 45. The refrigerant in the auxiliary refrigerant circuit absorbs heat of the refrigerant in the main refrigerant circuit 45 to become gaseous refrigerant having a degree of superheat, and then enters the charge port of the compressor 10, and the refrigerant in the main refrigerant circuit 45 releases heat to become liquid refrigerant having a degree of supercooling, and enters the evaporator 30.
In this way, the refrigerant is reduced in pressure and cooled through the pressure reducing and cooling unit 472 in the heat exchange device 40, and the outside of the heat exchange device 40 is not required to be additionally connected with throttling and cooling devices such as the throttle valve 60 through pipelines, so that the heat exchange capacity of the air conditioning unit 100 is guaranteed to be improved, the supercooling degree of the refrigerant is improved, the pipeline design of the air conditioning unit 100 and the accessory type selection scheme of the air conditioning unit 100 are simplified, and the overall design difficulty of the air conditioning unit 100 is reduced.
With continued reference to fig. 2-4, in an embodiment, the refrigerant input pipe 43 includes a main inlet 432, a first outlet and a second outlet 434, the main inlet 432 and the second outlet 434 are disposed opposite to each other at two axial ends of the refrigerant input pipe 43, and the first outlet is disposed between the main inlet and the second outlet and is disposed on a sidewall of the refrigerant input pipe 43. The primary inlet 432 communicates with the housing 41 and with the condenser 50 via tubing, the first outlet communicates with the primary refrigerant circuit 45, and the second outlet 434 communicates with the auxiliary refrigerant circuit. As such, the medium temperature, high pressure gaseous refrigerant output from the condenser 50 enters the heat exchange device 40 through the primary inlet 432 of the refrigerant input line 43, with one portion entering the primary refrigerant circuit 45 through the first outlet and another portion entering the auxiliary refrigerant circuit through the second outlet 434.
The refrigeration main circuit comprises a first heat exchange channel 452 and a main circuit output pipeline 454, wherein the inlet end of the first heat exchange channel 452 is communicated with the first outlet of the refrigerant input pipeline 43, the outlet end of the first heat exchange channel 452 is communicated with the main circuit output pipeline 454, and the outlet end of the main circuit output pipeline 454 is communicated with the shell 41, so that the evaporator 30 is communicated through the pipeline. In this way, a part of the medium-temperature high-pressure gaseous refrigerant in the refrigerant input pipeline 43 firstly enters the first heat exchange channel 452, and undergoes heat exchange with the auxiliary circuit of the refrigerant in the first heat exchange channel 452, and after the heat of the refrigerant is released, the refrigerant forms a supercooled liquid refrigerant, and then is output from the heat exchange device 40 through the main circuit output pipeline 454, and finally enters the evaporator 30 (as shown in fig. 1).
The auxiliary refrigerant circuit includes a desuperheating unit 472, an auxiliary input conduit 474, a second heat exchange channel 476, and an auxiliary output conduit 478. The inlet end of the depressurization and temperature reduction unit 472 is communicated with the second outlet 434 of the refrigerant input pipeline 43, the outlet end of the depressurization and temperature reduction unit 472 is communicated with the inlet end of the auxiliary input pipeline 474, the outlet end of the auxiliary input pipeline 474 is communicated with the inlet end of the second heat exchange channel 476, the outlet end of the second heat exchange channel 476 is communicated with the inlet end of the auxiliary output pipeline 478, and the outlet end of the auxiliary output pipeline 478 is communicated with the shell 41 so as to be communicated with the air supplementing port of the compressor 10 through a pipeline (as shown in fig. 1).
In this way, a part of the refrigerant output from the refrigerant input pipe 43 flows through the depressurization and cooling unit 472, the auxiliary input pipe 474, the second heat exchange channel 476 and the auxiliary output pipe 478 in sequence, the gaseous refrigerant with medium temperature and high pressure is first cooled by the depressurization and cooling effect of the depressurization and cooling unit 472 into a supercooled gas-liquid two-phase mixed state, then enters the second heat exchange channel 476 to exchange heat with the refrigerant in the first heat exchange channel 452, the supercooled gas-liquid two-phase mixed state absorbs the heat of the refrigerant in the first heat exchange channel 452 to form the gaseous refrigerant with superheat degree, and the gaseous refrigerant then enters the auxiliary output pipe 478 to be output from the heat exchange device 40, and finally enters the air supplementing port of the compressor 10 (as shown in fig. 1).
Specifically, in some embodiments, the depressurization and depressurization unit 472 includes a throttle valve port 4721 that serves as a throttle and depressurization function and an adiabatic cooling chamber 4722 that serves as a cooling function, where the adiabatic cooling chamber 4722 communicates with the throttle valve port 4721. The orifice 4721 has a smaller diameter than the refrigerant inlet line 43, so that the potential energy decreases due to an increase in the flow rate of the refrigerant through the orifice of the throttle valve 60, resulting in a pressure drop of the refrigerant without a drop in enthalpy. The depressurized gaseous refrigerant enters the adiabatic cooling chamber 4722, the volume of the gaseous refrigerant increases, and the pressure is reduced, and the temperature of the refrigerant in the adiabatic cooling chamber 4722 is greatly reduced because the adiabatic cooling chamber 4722 does not exchange heat with the outside.
In some embodiments, the orifice size of the orifice 4721 may be adjusted based on the superheat at the outlet end of the auxiliary output conduit 478. When the superheat degree of the outlet end of the auxiliary loop of the refrigerant is greater than the target superheat degree, the caliber of the throttle valve port 4721 is increased; when the degree of superheat at the outlet end of the auxiliary refrigerant circuit is less than the target degree of superheat, the orifice of the throttle valve port 4721 is reduced, thereby ensuring that the gaseous refrigerant output from the auxiliary output pipe 478 has a degree of superheat of a certain magnitude, and reducing the power consumption of the compressor 10.
Specifically, in some embodiments, the air conditioning system detects the temperature T1 and the pressure P1 of the outlet end of the auxiliary output pipe 478 in real time, calculates the saturation temperature Tx of the outlet end of the corresponding auxiliary output pipe 478, and further obtains the superheat Δt1 of the outlet end of the auxiliary output pipe 478, Δt1=t1-Tx. Thereafter, the temperature change rate Δt3 of the outlet end of the auxiliary output pipe 478 is calculated, Δt3=t1-t1 t-60. When the heat exchange device 40 starts to operate, the throttle valve port 4721 is operated for T 2 seconds according to the initial opening R, and then the opening of the throttle valve port 4721 is adjusted according to the superheat degree Δt1 of the outlet end of the auxiliary output pipe 478 and the temperature change rate Δt3 of the outlet end of the auxiliary output pipe 478 at intervals of T 2 seconds, and the magnitude of each opening adjustment is Δr= (Δt2—Δt1) ·α+Δt3·β, (where Δt2 is the target superheat degree of the outlet end of the auxiliary output pipe 478, and α and β are constants) and are set according to the actual working conditions. Specifically, in one embodiment, orifice 4721 has a diameter that is 10% -40% of the diameter of refrigerant inlet line 43, thereby ensuring that the flow rate of refrigerant in main loop 45 is greater than the flow rate in the auxiliary loop.
In some embodiments, the volume size of the adiabatic cooling chamber 4722 may be adjusted based on the subcooling size of the outlet end of the adiabatic cooling chamber 4722 (i.e., the inlet end of the auxiliary input conduit 474). When the supercooling degree of the outlet end of the adiabatic cooling chamber 4722 is less than the target supercooling degree, the volume of the adiabatic cooling chamber 4722 is increased, and when the supercooling degree of the outlet end of the adiabatic cooling chamber 4722 is greater than the target supercooling degree, the volume of the adiabatic cooling chamber 4722 is reduced, thereby allowing the refrigerant flowing into the inlet end of the auxiliary input pipe 474 to have a certain supercooling degree, ensuring that the temperature of the refrigerant in the second heat exchange passage 476 is lower than the temperature of the refrigerant in the first heat exchange passage 452 and can absorb the heat of the refrigerant in the first heat exchange passage 452.
In particular, in one embodiment, the depressurization and cooling unit 472 includes a fixed side wall 4723, a movable side wall 4724, and a driving assembly 4725, wherein the driving assembly 4725 is connected to the movable side wall 4724, and the movable side wall 4724 can move relative to the fixed side wall 4723 under the driving of the driving assembly 4725 to form a heat-insulation cooling chamber 4722 with adjustable volume. More specifically, the driving assembly 4725 includes a driving motor and a transmission assembly, the driving motor can output power to the transmission assembly, and the transmission assembly drives the movable side wall 4724 to reciprocate in a linear motion under the driving of the driving motor, so as to adjust the volume of the adiabatic cooling cavity 4722. It is understood that the specific configuration of the depressurization and temperature reduction unit 472 is not limited thereto, and may be set according to actual needs.
Specifically, in one embodiment, the temperature T2 at the inlet end of the auxiliary input pipe 474 and the pressure P1 at the outlet end of the auxiliary output pipe 478 are detected in real time, and the saturation temperature Ty at the inlet end of the corresponding auxiliary input pipe 474 is calculated, so as to obtain the supercooling degree Δt4 at the inlet end of the auxiliary input pipe 474, where Δt4=ty-T2. When the heat exchange device 40 starts to operate, after the movable side wall 4724 is installed for an initial distance L to operate for T 4 seconds, the operation distance of the movable side wall 4724 is adjusted according to the supercooling degree every interval T 3 seconds, and the movement distance is adjusted each time by Δl= (Δt5- Δt4) ·γ, (where Δt5 is the target supercooling degree, γ is a constant, and is set according to the actual working condition).
In this way, the heat exchange device 40 can flexibly control the real-time flow of the refrigerant in the main refrigerant loop 45 and the auxiliary refrigerant loop according to the parameters such as the superheat degree DeltaT 1 of the outlet end of the auxiliary output pipeline 478 and the supercooling degree DeltaT 4 of the inlet end of the auxiliary input pipeline 474, so as to avoid the problem of uneven heat exchange caused by smaller flow of the refrigerant on one side and larger flow of the refrigerant on the other side in the prior art, and ensure the heat exchange device 40 to have higher heat exchange performance.
The heat exchange device 40 and the air conditioning unit 100 provided with the heat exchange device 40 have the functions of reducing pressure, reducing temperature and exchanging heat, so that other throttling devices are not required to be arranged outside the heat exchange device 40, and the heat exchange device 40 is communicated with an external device only through the refrigerant input pipeline 43, the main loop output pipeline 454 and the auxiliary output pipeline 478, and is different from the structure that the heat exchange device 40 is connected with the external device through four interfaces in the prior art, thereby simplifying the structure of the air conditioning unit 100 provided with the heat exchange device 40 and reducing the difficulty of pipeline design. In addition, the refrigerant after depressurization rapidly enters the adiabatic cooling cavity 4722 to cool, so that the real-time heat exchange efficiency of the heat exchange device 40 is enhanced, and the work of the heat exchange device 40 can be flexibly controlled according to real-time parameters, so that the optimal refrigeration performance is achieved.
The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.
The above examples illustrate only a few embodiments of the invention, which are described in detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.
Claims (7)
1. A heat exchange device (40), characterized in that the heat exchange device (40) comprises:
A housing (41);
a refrigerant input pipe (43);
a main refrigerant circuit (45) accommodated in the housing (41), wherein the main refrigerant circuit (45) comprises a first heat exchange channel (452) and a main circuit output pipeline (454), and the main circuit output pipeline (454) is communicated with the refrigerant input pipeline (43) through the first heat exchange channel (452); and
A refrigerant auxiliary circuit which is accommodated in the shell (41) and is communicated with the refrigerant input pipeline (43), wherein the refrigerant auxiliary circuit comprises a depressurization and cooling unit (472), and the refrigerant in the refrigerant auxiliary circuit is depressurized and cooled under the action of the depressurization and cooling unit (472);
The pressure reducing and cooling unit (472) comprises a throttle valve port (4721) and an adiabatic cooling cavity (4722) communicated with the throttle valve port (4721), the adiabatic cooling cavity (4722) is communicated with the refrigerant input pipeline (43) through the throttle valve port (4721), the caliber of the throttle valve port (4721) is smaller than the caliber of the refrigerant input pipeline (43), and the refrigerant subjected to pressure reducing and cooling in the auxiliary refrigerant loop can exchange heat with the refrigerant in the main refrigerant loop (45);
The depressurization and cooling unit (472) comprises a fixed side wall (4723), a movable side wall (4724) and a driving assembly (4725), wherein the driving assembly (4725) is connected to the movable side wall (4724), and the movable side wall (4724) can move relative to the fixed side wall (4723) under the driving of the driving assembly (4725) so as to form an adiabatic cooling cavity (4722) with adjustable volume.
2. The heat exchange device (40) of claim 1 wherein the orifice valve port (4721) is adjustable in caliber.
3. The heat exchange device (40) of claim 2 wherein the orifice size of the orifice valve (4721) is adjusted according to the superheat size of the outlet end of the auxiliary refrigerant circuit.
4. A heat exchange device (40) according to claim 3, wherein the orifice (4721) increases in caliber when the superheat at the outlet end of the auxiliary refrigerant circuit is greater than a target superheat;
When the superheat degree of the outlet end of the auxiliary refrigerant circuit is smaller than the target superheat degree, the aperture of the throttle valve port (4721) is reduced.
5. The heat exchange device (40) of claim 1 wherein the volume size of the adiabatic cooling chamber (4722) is adjusted according to the supercooling degree of the outlet end of the adiabatic cooling chamber (4722);
When the supercooling degree of the outlet end of the adiabatic cooling chamber (4722) is less than the target supercooling degree, the volume of the adiabatic cooling chamber (4722) is increased;
when the supercooling degree of the outlet end of the adiabatic cooling chamber (4722) is greater than the target supercooling degree, the volume of the adiabatic cooling chamber (4722) is reduced.
6. The heat exchange device (40) of claim 1, wherein the auxiliary refrigerant circuit includes an auxiliary input conduit (474), a second heat exchange channel (476), and an auxiliary output conduit (478), the second heat exchange channel (476) communicating with the adiabatic cooling chamber (4722) through the auxiliary input conduit (474), the auxiliary output conduit (478) communicating with the auxiliary input conduit (474) through the second heat exchange channel (476).
7. An air conditioning unit (100) comprising a heat exchange device (40) according to any one of claims 1 to 6.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811063087.1A CN109028543B (en) | 2018-09-12 | 2018-09-12 | Heat exchange device and air conditioning unit provided with same |
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| CN201811063087.1A CN109028543B (en) | 2018-09-12 | 2018-09-12 | Heat exchange device and air conditioning unit provided with same |
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| CN109028543A CN109028543A (en) | 2018-12-18 |
| CN109028543B true CN109028543B (en) | 2024-04-26 |
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