CN219550878U - Improved low-temperature air source cooling and heating heat pump - Google Patents
Improved low-temperature air source cooling and heating heat pump Download PDFInfo
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- CN219550878U CN219550878U CN202223606966.9U CN202223606966U CN219550878U CN 219550878 U CN219550878 U CN 219550878U CN 202223606966 U CN202223606966 U CN 202223606966U CN 219550878 U CN219550878 U CN 219550878U
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 19
- 238000001816 cooling Methods 0.000 title claims abstract description 18
- 239000003507 refrigerant Substances 0.000 claims abstract description 63
- 239000007788 liquid Substances 0.000 claims abstract description 49
- 238000004781 supercooling Methods 0.000 claims abstract description 28
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 25
- 230000001012 protector Effects 0.000 claims description 10
- 238000001035 drying Methods 0.000 claims 1
- 238000012423 maintenance Methods 0.000 abstract description 2
- 238000001704 evaporation Methods 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000004891 communication Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000000047 product Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The utility model discloses an improved low-temperature air source cooling and heating heat pump, wherein a heat exchanger of the heat pump is connected with a four-way valve, a gas-liquid separator is connected with a compressor, and a liquid storage tank is communicated with a check valve group through a main expansion valve; the coaxial double-pipe heat exchanger is provided with a refrigerant channel and a water flow channel which can perform heat exchange, the heat pump also comprises a group of supercooling enthalpy-increasing channels, one end of each supercooling enthalpy-increasing channel is connected between the economizer and the main expansion valve, and the other end of each supercooling enthalpy-increasing channel is communicated with the compressor through the economizer; the supercooling enthalpy-increasing passage is formed by connecting a first branch and a second branch in parallel, wherein the first branch comprises a first auxiliary expansion valve; the second branch includes a second auxiliary expansion valve. The utility model ensures that the heat pump can operate in different low-temperature environments through the supercooling enthalpy-increasing passage formed by the two branches, and ensures the air inflow and the working efficiency of the compressor. Meanwhile, the utility model has simple structure, stable operation and convenient maintenance and replacement.
Description
Technical Field
The utility model relates to the technical field of heat pump products, in particular to an improved low-temperature air source cooling and heating heat pump applicable to cold areas.
Background
The reduction of outdoor air temperature in winter can reduce the heat absorption quantity of the refrigerant in the evaporator in the heat pump system to the outdoor air, and simultaneously the evaporation pressure is reduced to reduce the air absorption quantity, the heating capacity and the running power attenuation. Particularly, when the outdoor air temperature in winter is reduced, the efficiency of the compressor in the heat pump system is reduced, the evaporation temperature T0 and the evaporation pressure P0 are also reduced, the condensation pressure PK is not greatly changed due to the restriction of the medium (indoor air and water), thus the compression ratio PK/P0 is inevitably increased, the irreversibility of the compressor is increased in the working process (the exhaust temperature is also increased, the compressor is damaged due to long-term high exhaust temperature operation), and the efficiency is reduced, so that the reduction of the working efficiency of the compressor at the outdoor low temperature is one of the reasons for insufficient air-cooled heat pump output.
Aiming at the problem of insufficient winter output of the heat pump, the current solution is mainly to add an economizer. The economizer is a heat exchanger, the working principle is that the high-pressure liquid refrigerant output from the condenser is divided into two parts after entering the economizer, one part is throttled by the expansion valve and is further cooled in a heat expansion mode, the temperature of the other part is reduced, the other part is supercooled, and the stabilized supercooled liquid enters the evaporator for refrigeration. And the other part of uncooled gaseous refrigerant passes through a communicating pipeline between the economizer and the compressor, and reenters the compressor to continue compression and enter the circulation. The liquid refrigeration medium is stabilized by the expansion refrigeration mode, so that the capacity and the efficiency of the system are improved. The supercooling degree of the refrigerant is further improved through heat exchange of the economizer, the air inflow of the compressor is increased, air supplementing and enthalpy increasing are achieved, and therefore the problem that the low-temperature operation efficiency of the compressor is reduced is solved. However, the current economizer cannot adapt to the requirements of different low-temperature environments on air supplementing and enthalpy increasing, so the inventor proposes the following technical scheme through improvement.
Disclosure of Invention
The utility model aims to overcome the defects of the prior art and provide an improved low-temperature air source cooling and heating heat pump.
In order to solve the technical problems, the utility model adopts the following technical scheme: an improved cryogenic air source cooling and heating heat pump, the heat pump comprising: the heat exchanger is connected with the four-way valve, the gas-liquid separator is connected with the compressor, and the liquid storage tank is communicated with the one-way valve group through a main expansion valve; the heat pump also comprises a group of supercooling enthalpy-increasing passages, one end of each supercooling enthalpy-increasing passage is connected between the economizer and the main expansion valve, and the other end of each supercooling enthalpy-increasing passage is communicated with the compressor through the economizer; namely, one channel of the economizer is communicated with the liquid storage tank and the main expansion valve, and the other channel is communicated with the supercooling enthalpy-increasing channel and the compressor; the supercooling enthalpy-increasing passage is formed by connecting a first branch and a second branch in parallel, wherein the first branch comprises a first auxiliary expansion valve; the second branch includes a second auxiliary expansion valve.
Furthermore, in the above technical scheme, the check valve set is disposed between the refrigerant channel of the coaxial double-pipe heat exchanger and the heat exchanger, and the check valve set is composed of two groups of check valve sets connected in parallel, wherein one group of check valve sets includes: first check valve and second check valve, another group check valve group includes: a third check valve and a fourth check valve; the economizer is connected between the first one-way valve and the second one-way valve; the main expansion valve is connected between a third check valve and a fourth check valve in the check valve group.
In the above technical solution, the conducting directions of the first check valve and the second check valve are opposite; the conduction directions of the third one-way valve and the fourth one-way valve are opposite.
In the technical scheme, a dry filter is further connected between the economizer and the main expansion valve.
In the technical scheme, a low-pressure gauge and a low-pressure protector are arranged on a channel between the compressor and the gas-liquid separator; and a separator needle valve is arranged at the inlet of the gas storage liquid separator.
In the above technical scheme, a high-pressure gauge and a high-pressure protector are arranged on the channel between the compressor and the four-way valve.
Furthermore, in the above technical solution, a needle valve of the liquid storage tank is disposed at an inlet of the liquid storage tank.
In the above technical scheme, the main expansion valve, the first auxiliary expansion valve and the second auxiliary expansion valve are all electronic expansion valves.
In the above technical solution, a first auxiliary check valve is further disposed in the first branch; and a second auxiliary one-way valve is also arranged in the second branch.
By adopting the technical scheme, compared with the prior art, the utility model has the following beneficial effects: the utility model ensures that the heat pump can operate in different low-temperature environments through the supercooling enthalpy-increasing passage formed by the two branches, and ensures the air inflow and the working efficiency of the compressor. Meanwhile, the utility model has simple structure, stable operation and convenient maintenance and replacement.
Drawings
Fig. 1 is a schematic structural view of the present utility model.
Detailed Description
The utility model will be further described with reference to specific examples and figures.
The utility model, as shown in fig. 1, is an improved low-temperature air source cooling and heating heat pump, comprising: the compressor 1, the four-way valve 2, the coaxial double-pipe heat exchanger 3, the check valve group 4, the liquid storage tank 5, the economizer 6, the heat exchanger 7, the gas-liquid separator 8, the main expansion valve 91 and the supercooling enthalpy-increasing passage 90. The inlet of the compressor 1 is communicated with the gas-liquid separator 8, a low-pressure gauge 81 and a low-pressure protector 82 are arranged on a channel between the inlet of the compressor 1 and the gas-liquid separator 8, and a separator needle valve 83 is arranged at the inlet of the gas-liquid separator 8. The outlet of the compressor 1 is connected to the four-way valve 2, and a high-pressure gauge 11 and a high-pressure protector 12 are provided on a passage between the compressor 1 and the four-way valve 2. The four-way valve 2 is controlled to switch different channel communication.
The coaxial double-pipe heat exchanger 3 is used as a condenser and is provided with a refrigerant channel and a water flow channel which can perform heat exchange, cold water or hot water is output from the water flow channel in the coaxial double-pipe heat exchanger 3 through the operation of the refrigerant in the heat pump, the coaxial double-pipe heat exchanger 3 is provided with the refrigerant channel and the water flow channel, one end of the refrigerant channel is communicated with the four-way valve 2, and the other end of the refrigerant channel is communicated with the one-way valve group 4.
The one-way valve group 4 is arranged between a refrigerant channel of the coaxial double-pipe heat exchanger 3 and the heat exchanger 7, the one-way valve group 4 is composed of two groups of one-way valve groups which are connected in parallel, and one group of one-way valve groups comprises: a first check valve 41 and a second check valve 42, the other set of check valve sets comprising: a third check valve 43 and a fourth check valve 44; the economizer 6 is connected between the first check valve 41 and the second check valve 42; the main expansion valve 91 is connected between the third check valve 43 and the fourth check valve 44 in the check valve set 4. Specifically, the first check valve 41 may be turned on from top to bottom; the second check valve 42 can be turned on from bottom to top; the third check valve 43 can be turned on from bottom to top; the fourth check valve 44 may be turned on from top to bottom.
The liquid storage tank 5 is arranged at the front end of the economizer 6, so that the liquid storage tank has the functions of storing liquid refrigerant and liquid sealing, meanwhile, the liquid storage tank 5 is arranged between the coaxial sleeve heat exchanger 3 and the economizer 6, effective heat exchange of the coaxial sleeve heat exchanger 3 is improved, liquid refrigerant is prevented from remaining in the coaxial sleeve heat exchanger 3, heat exchange of the coaxial sleeve heat exchanger 3 is not only influenced, but also a heat pump system is blocked.
The inlet end of the liquid storage tank 5 is connected between the first check valve 41 and the second check valve 42 in the check valve group 4, and a liquid storage tank needle valve 51 is arranged at the inlet of the liquid storage tank 5. The outlet end of the liquid storage tank 5 is communicated with one channel of the economizer 6.
The economizer 6 adopts a plate heat exchanger, one channel of the economizer 6 is respectively connected with the outlet of the liquid storage tank 5 and the main expansion valve 91, and a drier-filter 61 is also arranged between the economizer 6 and the main expansion valve 91. One end of the other channel of the economizer 6 is communicated with the supercooling enthalpy increasing passage 90, the other end of the other channel is communicated with the compressor 1, namely, the supercooling enthalpy increasing passage 90 is communicated with the compressor 1 through the economizer 6, and a pressure sensor 13 is arranged on a channel between the economizer 6 and the compressor 1.
The main expansion valve 91 is connected between the third check valve 43 and the fourth check valve 44 in the check valve set 4.
The supercooling enthalpy increasing passage 90 has one end connected between the dry filter 61 and the main expansion valve 91, and the other end connected to the compressor 1 through the economizer 6. The supercooling enthalpy increasing passage 90 is formed by connecting a first branch 92 and a second branch 93 in parallel, wherein the first branch 92 includes: a first auxiliary expansion valve 921 and a first auxiliary check valve 922 connected in series; the second branch 93 includes: a second auxiliary expansion valve 931 and a second auxiliary check valve 932 connected in series.
The heat exchanger 7 adopts an axial flow fan heat exchanger, one end of the heat exchanger is connected to the one-way valve group 4, and the other end is connected to the four-way valve 2.
The gas-liquid separator 8 is connected between the four-way valve 2 and the compressor 1, and a separator needle valve 83 is arranged at the inlet of the gas-liquid separator 8.
The main expansion valve 91, the first auxiliary expansion valve 921, and the second auxiliary expansion valve 931 are electronic expansion valves.
The present utility model will be described in detail with reference to the following working procedures. The utility model has two working modes: the heating mode and the cooling mode are specifically described below.
Heating mode:
the compressor 1 compresses the refrigerant to form a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant enters the four-way valve 2 after passing through the high-pressure gauge 11 and the high-pressure protector 12. At this time, the four-way valve 2 is controlled to communicate the compressor 1 with the refrigerant passage of the coaxial double pipe heat exchanger 3. The high-temperature and high-pressure refrigerant flows through the refrigerant channels of the coaxial double-pipe heat exchanger 3 from top to bottom. And cold water to be heated passes through the water flow channel of the coaxial double-pipe heat exchanger from bottom to top. The refrigerant and the water flow realize heat exchange in the coaxial double-pipe heat exchanger, the refrigerant with reduced temperature enters the one-way valve group 4, and the water flow with increased temperature is discharged for common use.
After the low-temperature high-pressure refrigerant flowing out of the coaxial double pipe heat exchanger 3 enters the check valve group 4, the third check valve 43 cannot be conducted, so that the refrigerant can only enter from the first check valve 41. At this time, the second check valve 42 is not turned on, so that the refrigerant 5 is introduced into the liquid storage tank 5. Through the liquid storage tank 5 and into the economizer 6. After passing through the dry filter 61, the air flows to the main expansion valve 91, and the pressure is reduced after being throttled by the main expansion valve 91. The low-pressure refrigerant again enters between the third check valve 43 and the fourth check valve 44 in the single-phase valve group 4. Since the refrigerant with high pressure is resisted and cannot be conducted outside the third check valve 43, the low pressure refrigerant can only push the fourth check valve 44 to flow to the heat exchanger 7.
The low-pressure refrigerant evaporates by absorbing heat from the air in the heat exchanger 7. The evaporated refrigerant gas will flow to the four-way valve 2 again. The four-way valve 2 is used for realizing the communication between the heat exchanger 7 and the gas-liquid separator 8, and the refrigerant enters the gas-liquid separator 8.
Finally, the refrigerant sequentially passes through the low-pressure gauge 81 and the low-pressure protector 82 from the gas-liquid separator 8 and then reenters the compressor 1, and the gas-state refrigerator is compressed into a high-temperature high-pressure liquid refrigerant through the compressor 1, so that one cycle is completed. In the above process, cold water continuously flows into the coaxial double pipe heat exchanger 3, and the high-temperature and high-pressure refrigerant flowing through the coaxial double pipe heat exchanger 3 exchanges heat with the cold water, so that the coaxial double pipe heat exchanger 3 can supply high-temperature hot water.
When the ambient temperature is slightly low, the refrigerant is reduced in evaporation capacity, so that the suction capacity of the compressor is reduced, and the working efficiency of the compressor is also reduced. The low temperature environment is lowered to increase the suction amount of the compressor through the supercooling enthalpy increasing passage 90 and to increase the supercooling degree of the refrigerant in order to increase the suction amount of the compressor. The user can select to open two branches of the supercooling enthalpy-increasing passage 90 at the same time or select one of the branches to open according to the specific ambient temperature. For example, after the refrigerant passes through the filter drier 61, one path of the refrigerant passes through the main path expansion valve 91 and enters the heat exchanger 7, and the other path of the refrigerant passes through the first branch path 92 and enters the economizer 6, and the liquid refrigerant further absorbs latent heat in the refrigerant at the high pressure end in the economizer 6 in a throttling and expansion manner through the first auxiliary expansion valve 921 and the first auxiliary one-way valve 922, so that the supercooling degree of the refrigerant is further improved. Meanwhile, the refrigerant after absorbing heat directly enters the compressor 1 to improve the air suction amount of the compressor 1, thereby ensuring the power of the compressor. Similarly, after the environmental temperature is further reduced, the supercooling enthalpy-increasing passage 90 can be opened simultaneously by the first branch 92 and the second branch 93, so as to further increase the supercooling degree of the refrigerant and further supplement air to the compressor 1.
Cooling mode:
the compressor 1 compresses the refrigerant to form a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant enters the four-way valve 2 after passing through the high-pressure gauge 11 and the high-pressure protector 12. At this time, the four-way valve 2 is controlled to communicate the compressor 1 with the heat exchanger 7. The high-temperature and high-pressure refrigerant enters the heat exchanger 7 after passing through the four-way valve 2, releases heat into the air through the heat exchanger 7, and enters the one-way valve group 4.
After the low-temperature high-pressure refrigerant flowing out of the heat exchanger 7 enters the check valve group 4, the fourth check valve 44 cannot be conducted, so that the refrigerant can only enter from the second check valve 42. At this time, the first check valve 41 is not turned on, so that the refrigerant 5 introduced into the accumulator 5 flows into the economizer 6. After passing through the dry filter 61, the air flows to the main expansion valve 91, and is throttled by the main expansion valve 91, whereby the expansion is reduced. The low-pressure refrigerant again enters between the third check valve 43 and the fourth check valve 44 in the single-phase valve group 4. Since the high-pressure refrigerant is resisted and cannot be conducted outside the fourth check valve 44, the low-pressure refrigerant can only push the third check valve 43 to flow to the coaxial double pipe heat exchanger 3.
The refrigerant enters the coaxial double-pipe heat exchanger 3 from bottom to top after entering the throttle through the main expansion valve 91 to start absorbing heat and evaporating, meanwhile, the heat of the water flowing through the water flow channel in the coaxial double-pipe heat exchanger 3 is continuously absorbed, the temperature is reduced, and finally the water flows out after being changed into cold water.
The refrigerant with the temperature increased flows out of the coaxial sleeve heat exchanger 3 and then enters the four-way valve 2, the communication between the coaxial sleeve heat exchanger 3 and the gas-liquid separator 8 is realized through the four-way valve 2, and the refrigerant enters the gas-liquid separator 8.
Finally, the refrigerant sequentially passes through the low-pressure gauge 81 and the low-pressure protector 82 from the gas-liquid separator 8 and then reenters the compressor 1, and the gas-state refrigerator is compressed into a high-temperature high-pressure liquid refrigerant through the compressor 1, so that one cycle is completed. In the above process, hot water continuously flows into the coaxial double pipe heat exchanger 3, and the low-temperature low-pressure refrigerant flowing through the coaxial double pipe heat exchanger 3 exchanges heat with the hot water, so that the coaxial double pipe heat exchanger 3 can supply low-temperature cold water.
It is understood that the foregoing description is only illustrative of the present utility model and is not intended to limit the scope of the utility model, but rather is to be accorded the full scope of all such modifications and equivalent structures, features and principles as set forth herein.
Claims (9)
1. An improved cryogenic air source cooling and heating heat pump, the heat pump comprising: the device is characterized by sequentially connecting a compressor (1), a four-way valve (2), a coaxial sleeve heat exchanger (3), a one-way valve group (4), a liquid storage tank (5), an economizer (6), a heat exchanger (7) and a gas-liquid separator (8), wherein the heat exchanger (7) is connected with the four-way valve (2), the gas-liquid separator (8) is connected with the compressor (1), and the liquid storage tank (5) is communicated with the one-way valve group (4) through a main expansion valve (91); the coaxial double-pipe heat exchanger (3) is provided with a refrigerant channel and a water flow channel which can perform heat exchange, and the water flow channel in the coaxial double-pipe heat exchanger (3) outputs cold water or hot water through the operation of the refrigerant in the heat pump, and is characterized in that:
the heat pump also comprises a group of supercooling enthalpy-increasing channels (90), one end of each supercooling enthalpy-increasing channel (90) is connected between the economizer (6) and the main channel expansion valve (91), and the other end of each supercooling enthalpy-increasing channel is communicated with the compressor (1) through the economizer (6); namely, one channel of the economizer (6) is communicated with the liquid storage tank (5) and the main expansion valve (91), and the other channel is communicated with the supercooling enthalpy-increasing channel and the compressor (1);
the supercooling enthalpy-increasing passage (90) is formed by connecting a first branch (92) and a second branch (93) in parallel, wherein the first branch (92) comprises a first auxiliary expansion valve (921); the second branch (93) comprises a second auxiliary expansion valve (931).
2. The improved cryogenic air source cooling and heating heat pump of claim 1, wherein: the one-way valve group (4) is arranged between a refrigerant channel of the coaxial double-pipe heat exchanger (3) and the heat exchanger (7), the one-way valve group (4) is composed of two groups of one-way valve groups which are connected in parallel, and one group of one-way valve groups comprises: a first check valve (41) and a second check valve (42), the other set of check valve sets comprising: a third check valve (43) and a fourth check valve (44); the economizer (6) is connected between the first check valve (41) and the second check valve (42); the main expansion valve (91) is connected between the third check valve (43) and the fourth check valve (44) in the check valve group (4).
3. The improved cryogenic air source cooling and heating heat pump of claim 2, wherein: the conduction directions of the first check valve (41) and the second check valve (42) are opposite; the conduction directions of the third check valve (43) and the fourth check valve (44) are opposite.
4. The improved cryogenic air source cooling and heating heat pump of claim 2, wherein: and a drying filter (61) is also connected between the economizer (6) and the main expansion valve (91).
5. The improved cryogenic air source cooling and heating heat pump of claim 1, wherein: a low-pressure gauge (81) and a low-pressure protector (82) are arranged on a channel between the compressor (1) and the gas-liquid separator (8); a separator needle valve (83) is arranged at the inlet of the gas-liquid separator (8).
6. The improved cryogenic air source cooling and heating heat pump of claim 1, wherein: a high-pressure gauge (11) and a high-pressure protector (12) are arranged on a channel between the compressor (1) and the four-way valve (2).
7. The improved cryogenic air source cooling and heating heat pump of claim 1, wherein: the inlet of the liquid storage tank (5) is provided with a liquid storage tank needle valve (51).
8. The improved cryogenic air source cooling and heating heat pump of claim 1, wherein: the main expansion valve (91), the first auxiliary expansion valve (921) and the second auxiliary expansion valve (931) are all electronic expansion valves.
9. The improved cryogenic air source cooling and heating heat pump of any one of claims 1-8, wherein: a first auxiliary one-way valve (922) is further arranged in the first branch (92); a second auxiliary one-way valve (932) is also arranged in the second branch (93).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223606966.9U CN219550878U (en) | 2022-12-30 | 2022-12-30 | Improved low-temperature air source cooling and heating heat pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223606966.9U CN219550878U (en) | 2022-12-30 | 2022-12-30 | Improved low-temperature air source cooling and heating heat pump |
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| Publication Number | Publication Date |
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| CN219550878U true CN219550878U (en) | 2023-08-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202223606966.9U Active CN219550878U (en) | 2022-12-30 | 2022-12-30 | Improved low-temperature air source cooling and heating heat pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118310193A (en) * | 2024-04-28 | 2024-07-09 | 中山市爱美泰电器有限公司 | A refrigeration and ultra-low temperature heating heat pump system |
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2022
- 2022-12-30 CN CN202223606966.9U patent/CN219550878U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118310193A (en) * | 2024-04-28 | 2024-07-09 | 中山市爱美泰电器有限公司 | A refrigeration and ultra-low temperature heating heat pump system |
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