CN210512235U - Heat pump system - Google Patents
Heat pump system Download PDFInfo
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- CN210512235U CN210512235U CN201921521527.3U CN201921521527U CN210512235U CN 210512235 U CN210512235 U CN 210512235U CN 201921521527 U CN201921521527 U CN 201921521527U CN 210512235 U CN210512235 U CN 210512235U
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- 238000010438 heat treatment Methods 0.000 claims abstract description 28
- 239000003507 refrigerant Substances 0.000 claims abstract description 22
- 238000001704 evaporation Methods 0.000 claims description 12
- 230000008020 evaporation Effects 0.000 claims description 9
- 238000005057 refrigeration Methods 0.000 abstract description 16
- 238000001816 cooling Methods 0.000 description 6
- 239000013589 supplement Substances 0.000 description 6
- 230000009977 dual effect Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000006698 induction Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Abstract
The utility model provides a heat pump system. The heat pump system comprises a compressor, a four-way valve, an indoor heat exchanger, a first throttling element and a first heat source heat exchanger which are sequentially connected to form a main circulation of a refrigerating and heating refrigerant, and further comprises a second heat source heat exchanger and a second throttling element which are sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element is connected to a pipeline between the indoor heat exchanger and the first heat source heat exchanger, the other end of the second throttling element is connected with one end of the second heat source heat exchanger, and the other end of the second heat source heat exchanger is connected to an air suction port of the compressor. The utility model discloses a heat pump system makes heat pump system no matter be in heating mode or refrigeration mode, all has two evaporators, makes and guarantees that heat pump system can utilize two heat sources simultaneously, promotes heat pump system's operation efficiency by a wide margin, reduces heat pump system's running cost.
Description
Technical Field
The utility model belongs to the technical field of air conditioning, concretely relates to heat pump system.
Background
In recent years, with the increase of environmental pollution and the exhaustion of energy, air conditioning technologies are increasingly being promoted, and the goal of efficient operation of air conditioners is achieved by adopting efficient energy-saving technical means such as (temperature and humidity independent control technology and heat pump technology). At present, based on the reasons, a plurality of heat pump systems with double evaporators have been developed in the market, but most of the heat pump systems are strictly limited in a cooling mode or a heating mode due to the purpose of evaporation, heat absorption and temperature reduction of the double evaporators, that is, the existing heat pump systems mostly have the problem of single function, and a few parts of refrigerant circulation in the heat pump systems have switching working conditions of heating and cooling, but the double evaporators only have the function under the heating mode or the cooling mode, so that the load distribution of the two evaporators cannot be flexibly adjusted, and the energy efficiency of the heat pump systems is low. For example, patent publication No. CN205505465U discloses a single-unit two-stage compression double-evaporator large temperature difference water chilling unit, which can only realize double-evaporation temperature refrigeration, has a single function, cannot flexibly control the loads of two evaporation sides, and does not have a heating mode, so that the whole equipment is idle in winter, and resources are wasted.
SUMMERY OF THE UTILITY MODEL
Therefore, the to-be-solved technical problem of the utility model is to provide a heat pump system, no matter make heat pump system be in heating mode or refrigeration mode, all have two evaporators, make and guarantee that heat pump system can utilize two heat sources simultaneously, promote heat pump system's operation efficiency by a wide margin, reduce heat pump system's running cost.
In order to solve the problem, the utility model provides a heat pump system, including connecting formation refrigeration and heating refrigerant main cycle's compressor, cross valve, indoor heat exchanger, first throttling element, first heat source heat exchanger in order, still including connecting second heat source heat exchanger, the second throttling element who forms supplementary heat transfer branch road in order, the one end of second throttling element connect in indoor heat exchanger with on the pipeline between the first heat source heat exchanger, the other end of second throttling element with the one end of second heat source heat exchanger is connected, the other end of second heat source heat exchanger connect in the induction port of compressor.
Preferably, the evaporation temperature of the second heat source heat exchanger is higher than that of the first heat source heat exchanger or the indoor heat exchanger as an evaporator.
Preferably, the compressor comprises a first two-stage compressor and a second two-stage compressor which are connected in parallel, the exhaust port of the first two-stage compressor and the exhaust port of the second two-stage compressor are combined to form a first pipeline and are connected with the port a of the four-way valve, and the suction port of the first two-stage compressor and the suction port of the second two-stage compressor are combined to form a second pipeline and are connected with the port C of the four-way valve.
Preferably, the first two-stage compressor and the second two-stage compressor are both air-supply enthalpy-increasing compressors, and further include a flash tank and a third throttling element, the flash tank and the third throttling element are sequentially connected between the first throttling element and the first heat source heat exchanger, the flash tank is located between the first throttling element and the third throttling element, the first two-stage compressor is provided with a first air-supply port, the second two-stage compressor is provided with a second air-supply port, an air-supply branch of the flash tank is connected with the first air-supply port through a first electromagnetic valve, and an air-supply branch of the flash tank is connected with the second air-supply port through a second electromagnetic valve.
Preferably, the auxiliary heat exchange branch comprises a first switching pipeline and a second switching pipeline, a first trunk section is arranged between the indoor heat exchanger and the first throttling element, a second trunk section is arranged between the third throttling element and the first heat source heat exchanger, the first switching pipeline is provided with a third electromagnetic valve and is located between the second throttling element and the first trunk section, and the second switching pipeline is provided with a fourth electromagnetic valve and is located between the second throttling element and the second trunk section.
Preferably, the auxiliary heat exchange branch further comprises a fifth solenoid valve, and the fifth solenoid valve is connected between the second heat source heat exchanger and the suction port of the compressor.
Preferably, the second pipeline has a first branch section connected to the first two-stage compressor and a second branch section connected to the second two-stage compressor, and a sixth solenoid valve is further disposed on the second branch section.
The utility model provides a pair of heat pump system, because supplementary heat transfer branch road connect in indoor heat exchanger with between the induction port of pipeline and compressor between the first heat source heat exchanger, this makes heat pump system no matter is in the mode of refrigeration or heats the mode, second heat source heat exchanger all will exert the effect of endothermic evaporation, so realizes double evaporation temperature mode under heat pump system's the operating mode is satisfied simultaneously and is refrigerate and heat the demand, is favorable to improving heat pump system's operation efficiency, reduces running cost, and makes the system can be applicable to warm and humid independent control's occasion.
Drawings
Fig. 1 is a schematic diagram of a heat pump system according to an embodiment of the present invention;
fig. 2 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a dual-heat-source air-replenishing heating mode;
fig. 3 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a dual-heat-source non-air-supply heating mode;
fig. 4 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a single heat source air-supplementing heating mode;
fig. 5 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a single heat source non-air-make heating mode;
fig. 6 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a defrosting mode;
FIG. 7 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in FIG. 1 is a dual-heat-source air-replenishing refrigeration mode;
FIG. 8 is a schematic view illustrating a flow direction of a refrigerant in the heat pump system shown in FIG. 1 when the operation mode is the dual-heat-source non-air-supply refrigeration mode;
fig. 9 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a single heat source air-replenishing refrigeration mode;
fig. 10 is a schematic view illustrating a flow direction of a refrigerant when the operation mode of the heat pump system shown in fig. 1 is a single-heat-source non-air-make heating mode.
The reference numerals are represented as:
111. a first two-stage compressor; 112. a second two-stage compressor; 12. a four-way valve; 13. an indoor heat exchanger; 14. a first throttling element; 15. a first heat source heat exchanger; 16. a flash tank; 17. a third throttling element; 21. a second heat source heat exchanger; 22. a second throttling element; 101. a first solenoid valve; 102. a second solenoid valve; 103. a third electromagnetic valve; 104. a fourth solenoid valve; 105. a fifth solenoid valve; 106. a sixth electromagnetic valve; 201. a first switching line; 202. a second switching line; 203. a first trunk section; 204. a second trunk section; 205. a first leg section; 206. a second leg segment.
Detailed Description
With reference to fig. 1 to 10, according to an embodiment of the present invention, a heat pump system is provided, including a compressor, a four-way valve 12, an indoor heat exchanger 13, a first throttling element 14, a first heat source heat exchanger 15, which are connected in sequence to form a main circulation of a cooling and heating refrigerant, and further including a second heat source heat exchanger 21 and a second throttling element 22, which are connected in sequence to form an auxiliary heat exchange branch, wherein one end of the second throttling element 22 is connected to a pipeline between the indoor heat exchanger 13 and the first heat source heat exchanger 15, the other end of the second throttling element 22 is connected to one end of the second heat source heat exchanger 21, and the other end of the second heat source heat exchanger 21 is connected to an air suction port of the compressor. In the technical scheme, the auxiliary heat exchange branch is connected between the pipeline between the indoor heat exchanger 13 and the first heat source heat exchanger 15 and the air suction port of the compressor, so that the second heat source heat exchanger 21 can play a role in absorbing heat and evaporating no matter the heat pump system is in a refrigeration mode or a heating mode, and thus a double-evaporation temperature mode of the heat pump system under the full working condition is realized, the refrigeration and heating requirements are met simultaneously, the operation energy efficiency of the heat pump system is improved, the operation cost is reduced, and the system can be suitable for the occasions with independent temperature and humidity control.
Preferably, the evaporation temperature of the second heat source heat exchanger 21 is higher than that when the first heat source heat exchanger 15 or the indoor heat exchanger 13 is used as an evaporator. Specifically, the first heat source heat exchanger 15 may adopt a conventional forced convection heat exchanger (i.e., an air source), and the second heat source heat exchanger 21 may adopt a heat exchanger of solar energy and a water source (including river and lake water), for example, in winter (when the outside air temperature is low), the second heat source heat exchanger 21 adopts a solar heat exchanger to perform heat exchange between the heat of the high-temperature heat source recovered on the one hand (through a corresponding working medium) and the refrigerant in the main cycle of the cooling and heating refrigerant, so as to raise the evaporation temperature flowing through the second heat source heat exchanger 21, which will certainly improve the energy efficiency of the compressor, that is, the energy efficiency of the heat pump system.
To further improve the energy efficiency of the heat pump system, it is preferable that the compressor includes a first two-stage compressor 111 and a second two-stage compressor 112 connected in parallel, the four-way valve 12 has an a port, a B port, a C port, and a D port (as shown in fig. 1, as known in the art, the four-way valve has 4 ports, which is specifically defined herein for convenience of description only and is not a limitation of the present invention), the exhaust port of the first two-stage compressor 111 and the exhaust port of the second two-stage compressor 112 are combined to form a first pipeline and connected to the a port of the four-way valve 12, and the suction port of the first two-stage compressor 111 and the suction port of the second two-stage compressor 112 are combined to form a second pipeline and connected to the C port of the four-way valve 12.
Further, the first two-stage compressor 111 and the second two-stage compressor 112 are both air-supply enthalpy-increasing compressors, and further include an flash tank 16 and a third throttling element 17, the flash tank 16 and the third throttling element 17 are sequentially connected between the first throttling element 14 and the first heat source heat exchanger 15, the flash tank 16 is located between the first throttling element 14 and the third throttling element 17, the first two-stage compressor 111 has a first air supplement port, the second two-stage compressor 112 has a second air supplement port, an air supplement branch of the flash tank 16 is connected with the first air supplement port through a first electromagnetic valve 101, an air supplement branch of the flash tank 16 is connected with the second air supplement port through a second electromagnetic valve 102, and the heat pump system is designed to be a corresponding system with air-supply enthalpy-increase, which can further improve the energy efficiency of the system, wherein the first electromagnetic valve 101, The design of the second electromagnetic valve 102 is beneficial to meeting the flow path switching requirement of the heat pump system in different working modes.
The auxiliary heat exchange branch comprises a first switching pipeline 201 and a second switching pipeline 202, a first trunk section 203 is arranged between the indoor heat exchanger 13 and the first throttling element 14, a second trunk section 204 is arranged between the third throttling element 17 and the first heat source heat exchanger 15, a third electromagnetic valve 103 is arranged in the first switching pipeline 201 and is positioned between the second throttling element 22 and the first trunk section 203, and a fourth electromagnetic valve 104 is arranged in the second switching pipeline 202 and is positioned between the second throttling element 22 and the second trunk section 204, so that the flow path of refrigerant in the heat pump system can be further enriched through the design of the third electromagnetic valve 103 and the fourth electromagnetic valve 104, and the type of the working mode of the heat pump system can be further enriched. In the same way, further, the auxiliary heat exchange branch further includes a fifth electromagnetic valve 105, and the fifth electromagnetic valve 105 is connected between the second heat source heat exchanger 21 and the suction port of the compressor; the second pipeline has a first branch segment 205 connected to the first two-stage compressor 111 and a second branch segment 206 connected to the second two-stage compressor 112, and the second branch segment 206 is further provided with a sixth solenoid valve 106.
According to the utility model discloses an embodiment still provides a heat pump system's control method, includes following step:
acquiring the working mode of a heat pump system;
and controlling the on-off of the electromagnetic valve and the throttling element so as to enable the heat pump system to operate in the acquired working mode.
The operation modes can be nine modes, such as a double-heat-source air-supplementing heating mode, a double-heat-source non-air-supplementing heating mode, a single-heat-source non-air-supplementing heating mode, a defrosting mode, a double-heat-source air-supplementing refrigerating mode, a double-heat-source non-air-supplementing refrigerating mode, a single-heat-source air-supplementing refrigerating mode and a single-heat-source non-air-supplementing refrigerating mode.
For example, as shown in fig. 2 to 5, when the obtained operation mode is the dual-heat-source air-replenishing heating mode, the ports a and D, and the ports B and C of the four-way valve 12 are controlled to be communicated, the first throttle element 14, the second throttle element 22, the third throttle element 17, the first solenoid valve 101, the third solenoid valve 103, and the fifth solenoid valve 105 are controlled to be opened, and the second solenoid valve 102, the fourth solenoid valve 104, and the sixth solenoid valve 106 are controlled to be closed; or, when the obtained working mode is the dual-heat-source non-air-supply heating mode, the port a and the port D, and the port B and the port C of the four-way valve 12 are controlled to be communicated respectively, the first throttling element 14, the second throttling element 22, the third throttling element 17, the third electromagnetic valve 103, and the fifth electromagnetic valve 105 are controlled to be opened, and the first electromagnetic valve 101, the second electromagnetic valve 102, the fourth electromagnetic valve 104, and the sixth electromagnetic valve 106 are controlled to be closed; or when the acquired working mode is the single heat source air-supplementing heating mode, the port a and the port D, and the port B and the port C of the four-way valve 12 are controlled to be communicated respectively, the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102, and the sixth electromagnetic valve 106 are controlled to be opened, and the third electromagnetic valve 103, the fourth electromagnetic valve 104, the fifth electromagnetic valve 105, and the second throttling element 22 are controlled to be closed; or, when the acquired working mode is the single heat source non-gas-supply heating mode, the port a and the port D, and the port B and the port C of the four-way valve 12 are controlled to be respectively communicated, the first throttling element 14, the third throttling element 17, the third electromagnetic valve 103 and the sixth electromagnetic valve 106 are controlled to be opened, and the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103, the fourth electromagnetic valve 104, the fifth electromagnetic valve 105 and the second throttling element 22 are controlled to be closed. In the technical scheme, it is worth emphasizing that when the working mode adopts a dual heat source (no matter refrigeration or heating), the sixth electromagnetic valve 106 should be ensured to be switched off, so that the refrigerant of the refrigeration and heating refrigerant main cycle and the refrigerant of the auxiliary heat exchange branch enter the first two-stage compressor 111 and the second two-stage compressor 112 respectively and independently from each other, and the energy efficiency of the heat pump system is prevented from being reduced after the refrigerants with different temperatures are mixed; in the case of a single heat source, the sixth solenoid valve 106 is opened and the fifth solenoid valve 105 is closed, so that the suction ports of the low-pressure stage compression chambers of the first and second dual- stage compressors 111 and 112 share a single refrigerant pressure. It will be further appreciated that in the dual heat source heating mode (air make-up or non-air make-up), both the second heat source heat exchanger 21 and the first heat source heat exchanger 15 function as evaporators, while the indoor heat exchanger 13 functions as a condenser.
For another example, as shown in fig. 7 to 10, when the obtained operation mode is the dual-heat-source air-replenishing refrigeration mode, the port a and the port B, and the port C and the port D of the four-way valve 12 are controlled to be communicated, the first throttling element 14, the second throttling element 22, the third throttling element 17, the first electromagnetic valve 101, the fourth electromagnetic valve 104, and the fifth electromagnetic valve 105 are controlled to be opened, and the second electromagnetic valve 102, the third electromagnetic valve 103, and the sixth electromagnetic valve 106 are controlled to be closed; or, when the obtained working mode is the dual-heat-source non-air-supply refrigeration mode, the port a and the port B, and the port C and the port D of the four-way valve 12 are controlled to be communicated respectively, the first throttling element 14, the second throttling element 22, the third throttling element 17, the fourth electromagnetic valve 104 and the fifth electromagnetic valve 105 are controlled to be opened, and the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103 and the sixth electromagnetic valve 106 are controlled to be closed; or, when the obtained working mode is the single heat source air supply refrigeration mode, the port a and the port B, and the port C and the port D of the four-way valve 12 are controlled to be respectively communicated, the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102, and the sixth electromagnetic valve 106 are controlled to be opened, and the second throttling element 22, the third electromagnetic valve 103, the fourth electromagnetic valve 104, and the fifth electromagnetic valve 105 are controlled to be closed; or, when the acquired working mode is the single heat source non-gas-supply refrigeration mode, the port a and the port B, and the port C and the port D of the four-way valve 12 are controlled to be respectively communicated, the first throttling element 14, the third throttling element 17, and the sixth electromagnetic valve 106 are controlled to be opened, and the second throttling element 22, the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103, the fourth electromagnetic valve 104, and the fifth electromagnetic valve 105 are controlled to be closed. It will be further appreciated that in the dual heat source cooling mode (air make-up or non-air make-up), both the second heat source heat exchanger 21 and the indoor heat exchanger 13 function as evaporators, while the first heat source heat exchanger 15 functions as a condenser.
Specifically, as shown in fig. 6, when the acquired operating mode is the defrosting mode, the port a of the four-way valve 12 is controlled to be communicated with the port B, the second throttling element 22 and the fifth electromagnetic valve 105 are controlled to be opened, and the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103, the fourth electromagnetic valve 104 and the sixth electromagnetic valve 106 are controlled to be closed, so that the second heat source heat exchanger 21 utilizes heat of an external high-temperature heat source to defrost the first heat source heat exchanger 15, and the indoor temperature does not fluctuate greatly.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The above description is only exemplary of the present invention and should not be construed as limiting the present invention, and any modifications, equivalents and improvements made within the spirit and principles of the present invention are intended to be included within the scope of the present invention. The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (7)
1. The heat pump system is characterized by comprising a compressor, a four-way valve (12), an indoor heat exchanger (13), a first throttling element (14) and a first heat source heat exchanger (15) which are sequentially connected to form a main circulation of a refrigerating and heating refrigerant, and further comprising a second heat source heat exchanger (21) and a second throttling element (22) which are sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element (22) is connected to a pipeline between the indoor heat exchanger (13) and the first heat source heat exchanger (15), the other end of the second throttling element (22) is connected with one end of the second heat source heat exchanger (21), and the other end of the second heat source heat exchanger (21) is connected to an air suction port of the compressor.
2. A heat pump system according to claim 1, characterized in that the evaporation temperature of the second heat source heat exchanger (21) is higher than the evaporation temperature when acting as an evaporator in the first heat source heat exchanger (15) or the indoor heat exchanger (13).
3. The heat pump system of claim 1, wherein the compressor comprises a first two-stage compressor (111) and a second two-stage compressor (112) connected in parallel, an exhaust port of the first two-stage compressor (111) and an exhaust port of the second two-stage compressor (112) are combined to form a first pipeline and are connected with an A port of the four-way valve (12), and an intake port of the first two-stage compressor (111) and an intake port of the second two-stage compressor (112) are combined to form a second pipeline and are connected with a C port of the four-way valve (12).
4. The heat pump system according to claim 3, wherein the first (111) and second (112) two-stage compressors are each a vapor-make-up enthalpy-increasing compressor, further comprising a flash tank (16), a third throttling element (17), the flash generator (16) and the third throttling element (17) are connected in series between the first throttling element (14) and the first heat source heat exchanger (15), the flash evaporator (16) being located between the first (14) and third (17) throttling element, the first two-stage compressor (111) having a first make-up port, the second two-stage compressor (112) having a second make-up port, the air supply branch of the flash tank (16) is connected with the first air supply port through a first electromagnetic valve (101), and the air supply branch of the flash tank (16) is connected with the second air supply port through a second electromagnetic valve (102).
5. The heat pump system according to claim 4, characterized in that said auxiliary heat exchange branch comprises a first switching line (201), a second switching line (202), a first trunk section (203) between said indoor heat exchanger (13) and said first throttling element (14), a second trunk section (204) between said third throttling element (17) and said first heat source heat exchanger (15), a third solenoid valve (103) in said first switching line (201) and between said second throttling element (22) and said first trunk section (203), a fourth solenoid valve (104) in said second switching line (202) and between said second throttling element (22) and said second trunk section (204).
6. The heat pump system according to claim 5, wherein said auxiliary heat exchange branch further comprises a fifth solenoid valve (105), said fifth solenoid valve (105) being connected between said second heat source heat exchanger (21) and the suction of said compressor.
7. The heat pump system according to claim 6, wherein said second circuit has a first branch (205) connected to said first two-stage compressor (111) and a second branch (206) connected to said second two-stage compressor (112), said second branch (206) being further provided with a sixth solenoid valve (106).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921521527.3U CN210512235U (en) | 2019-09-12 | 2019-09-12 | Heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921521527.3U CN210512235U (en) | 2019-09-12 | 2019-09-12 | Heat pump system |
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| Publication Number | Publication Date |
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| CN210512235U true CN210512235U (en) | 2020-05-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201921521527.3U Withdrawn - After Issue CN210512235U (en) | 2019-09-12 | 2019-09-12 | Heat pump system |
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| CN (1) | CN210512235U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500804A (en) * | 2019-09-12 | 2019-11-26 | 珠海格力电器股份有限公司 | Heat pump system and control method |
| CN112361648A (en) * | 2020-11-11 | 2021-02-12 | 珠海格力电器股份有限公司 | Compressor, heat pump system, and method for controlling heat pump system |
-
2019
- 2019-09-12 CN CN201921521527.3U patent/CN210512235U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500804A (en) * | 2019-09-12 | 2019-11-26 | 珠海格力电器股份有限公司 | Heat pump system and control method |
| CN110500804B (en) * | 2019-09-12 | 2023-09-22 | 珠海格力电器股份有限公司 | Heat pump system and control method |
| CN112361648A (en) * | 2020-11-11 | 2021-02-12 | 珠海格力电器股份有限公司 | Compressor, heat pump system, and method for controlling heat pump system |
| CN112361648B (en) * | 2020-11-11 | 2022-01-11 | 珠海格力电器股份有限公司 | Compressor, heat pump system, and method for controlling heat pump system |
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