CN210512229U - Cascade high-temperature heat pump unit - Google Patents
Cascade high-temperature heat pump unit Download PDFInfo
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- CN210512229U CN210512229U CN201921102052.4U CN201921102052U CN210512229U CN 210512229 U CN210512229 U CN 210512229U CN 201921102052 U CN201921102052 U CN 201921102052U CN 210512229 U CN210512229 U CN 210512229U
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 50
- 230000008878 coupling Effects 0.000 claims abstract description 9
- 238000010168 coupling process Methods 0.000 claims abstract description 9
- 238000005859 coupling reaction Methods 0.000 claims abstract description 9
- 239000012530 fluid Substances 0.000 claims description 6
- 238000004378 air conditioning Methods 0.000 claims description 5
- 230000005855 radiation Effects 0.000 claims description 5
- 238000010438 heat treatment Methods 0.000 abstract description 30
- 230000009286 beneficial effect Effects 0.000 abstract description 3
- 239000003507 refrigerant Substances 0.000 description 15
- 239000007788 liquid Substances 0.000 description 8
- 239000000725 suspension Substances 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 7
- 239000003245 coal Substances 0.000 description 6
- 238000010521 absorption reaction Methods 0.000 description 5
- 238000005057 refrigeration Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000008400 supply water Substances 0.000 description 1
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Abstract
The cascade high-temperature heat pump unit is characterized in that the low-temperature stage thermodynamic cycle comprises a low-temperature stage subcooler, the high-temperature stage thermodynamic cycle comprises a high-temperature stage evaporator, and the subcooler and the evaporator are in a shared coupling structure. The beneficial effects are as follows: the air source heat pump can be started within the range from-40 ℃ to 10 ℃, the water supply temperature can be automatically adjusted from 30 ℃ to 90 ℃ according to the building load requirement and the tail end condition, the air source heat pump is suitable for various tail end equipment forms, and the continuous and stable heating output, the high energy efficiency ratio and the high water supply temperature of the air source heat pump under the low-temperature working condition can be realized.
Description
Technical Field
The utility model relates to a heat pump set field, especially a cascade high temperature heat pump set.
Background
Heating in winter is the basic living demand of residents in northern China. At present, the main energy source for northern heating is coal, and the coal-fired heating area accounts for about 83% of the total heating area. According to statistics, the coal for heating in China consumes about 4.4 hundred million tons of standard coal each year, which accounts for over 32 percent of the national building energy consumption of 13.9 hundred million tons of standard coal and accounts for 10 percent of the national total social energy consumption of 43.6 hundred million tons of standard coal. The coal combustion heating has low energy utilization rate and serious environmental pollution. In order to reduce atmospheric pollution, promote the energy consumption revolution and supply side structural reform, the implementation of electric energy substitution becomes the current energy development strategy in China. The low-temperature air source heat pump is used as an important alternative mode for coal-fired heating in winter in northern areas, and has the advantages of cleanness, environmental protection, economy, high efficiency and the like. According to the energy efficiency limit value and the energy efficiency grade (GB 37480-.
For the end equipment of the radiator which is widely applied in China, the supply and return water temperature is preferably 75/50 ℃, the temperature can not be basically realized by the conventional low-temperature air source heat pump system, or the performance and the energy efficiency of the air source heat pump system for realizing the temperature are poor. In addition, in a low-temperature heating mode, the compression ratio of a conventional heat pump compressor is remarkably increased, and the energy efficiency of the compressor and a unit is sharply reduced when the exhaust temperature is rapidly increased; meanwhile, due to the low ring temperature and frosting on the evaporator side, the heat absorption capacity of the air source heat pump from the air is reduced, the heating quantity is greatly reduced, and the heating effect of the building is influenced.
Disclosure of Invention
The utility model aims at solving the problem, a cascade high-temperature heat pump unit is designed. The specific design scheme is as follows:
the cascade high-temperature heat pump unit is characterized in that the low-temperature stage thermodynamic cycle comprises a low-temperature stage subcooler, the high-temperature stage thermodynamic cycle comprises a high-temperature stage evaporator, and the subcooler and the evaporator are in a shared coupling structure.
The shared coupling structure refers to a shared heat exchanger, namely the heat exchanger is not only a low-temperature-level subcooler, but also a high-temperature-level evaporator. The heating capacity of the heat pump unit mainly depends on the heat release capacity of the condenser, and the heat release capacity of the condenser is derived from the heat absorption capacity obtained by heat exchange of the thermodynamic cycle working medium from the evaporator. That is, the heating capacity of the high-temperature stage of the cascade system mainly comes from the heat absorption capacity of the high-temperature stage evaporator, that is, the heat release capacity of the low-temperature stage subcooler. Meanwhile, the heat release of the low-temperature stage subcooler also affects the low-temperature stage heating capacity. Namely, the total heating capacity of the cascade system is determined by the coupling of the shared heat exchangers.
The execution tail end circulation comprises an air conditioning unit tail end, a fan coil pipe tail end, a floor radiation tail end and a radiator tail end.
The low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle are connected in series, specifically, a water outlet of the high-temperature-stage condenser and a water inlet of the low-temperature-stage condenser are respectively connected with a water inlet and a water outlet for executing tail-end circulation, and a water inlet of the high-temperature-stage condenser is connected with a water outlet of the low-temperature-stage condenser.
The low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle are connected in parallel, specifically, a water outlet of the high-temperature-stage condenser and a water outlet of the low-temperature-stage condenser are both connected with an input end for executing the tail-end cycle, and a water inlet of the high-temperature-stage condenser and a water inlet of the low-temperature-stage condenser are both connected with an output end for executing the tail-end cycle.
In the series connection, the temperature difference between the low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle is larger than that of the parallel connection.
High-temperature stage thermodynamic cycle includes high-temperature stage compressor, high-temperature stage condenser, high-temperature stage choke valve, high-temperature stage compressor, high-temperature stage condenser, high-temperature stage choke valve connect gradually, the high-temperature stage evaporimeter is connected with compressor, high-temperature stage choke valve respectively, high-temperature stage compressor, high-temperature stage condenser, high-temperature stage choke valve, high-temperature stage evaporimeter whole form the high-temperature stage thermodynamic cycle of annular fluid circuit, high-temperature stage condenser with carry out terminal circulation heat transfer and connect, high-temperature stage compressor, high-temperature stage condenser, high-temperature stage choke valve, high-temperature stage evaporimeter are used for respectively showing throttle valve, evaporimeter, compressor, the condenser of installing in high-temperature stage thermodynamic cycle.
The low-temperature-stage thermodynamic cycle comprises a low-temperature-stage condenser, a low-temperature-stage compressor, a low-temperature-stage evaporator and a low-temperature-stage throttling valve, the low-temperature-stage condenser, the low-temperature-stage compressor, the low-temperature-stage evaporator and the low-temperature-stage throttling valve are sequentially connected, the low-temperature-stage subcooler is respectively connected with the low-temperature-stage throttling valve and the low-temperature-stage condenser, the low-temperature-stage compressor, the low-temperature-stage evaporator, the low-temperature-stage throttling valve and the low-temperature-stage subcooler integrally form the low-temperature-stage thermodynamic cycle of an annular fluid loop, the low-temperature-stage condenser is connected with the execution tail end in a cycle heat exchange mode, and the low-temperature-stage condenser, the low-temperature-stage.
Preferably, the low-temperature stage compressor can be a conventional air-supply enthalpy-increasing type compressor, such as a scroll compressor, a piston compressor or a screw compressor with air-supply enthalpy-increasing function; by adopting the transcritical working medium, under the supercritical condition, considerable temperature slippage exists in the heat release process, the temperature rise of hot water is facilitated, and higher water supply temperature can be obtained. The high-temperature stage compressor adopts a magnetic suspension centrifugal compressor and adopts a high-temperature single environment-friendly working medium, and can realize medium and high temperature heat pump circulation with high heat supply temperature, small circulating temperature rise and condensing pressure lower than critical pressure.
The magnetic suspension centrifugal compressor depends on the magnetic suspension bearing to suspend the rotor at a set position by utilizing electromagnetic force, has the advantages of no mechanical contact, no abrasion, high efficiency and the like, prolongs the service life, and has low noise and no surge. Meanwhile, the rotating speed can be adjusted according to the actual load and pressure ratio, and the compressor has higher performance than the traditional compressor under partial load, so that a good energy-saving effect is achieved.
By adopting the optimal cascade proportion, higher system energy efficiency can be obtained under the determined supply and return water temperature and the compressor displacement of the basic thermodynamic cycle; the optimal overlapping proportion mainly refers to the optimal proportion of the heat exchange area of the low-temperature stage subcooler and the heat exchange area of the low-temperature stage condenser, so that the thermodynamic cycle can realize the maximum heating capacity or the maximum energy efficiency ratio under the condition.
The valve arranged on the thermodynamic cycle pipeline can independently start and stop the low-temperature thermodynamic cycle and the high-temperature thermodynamic cycle, and can realize the functions of single-stage heating and single-stage refrigeration;
the magnetic suspension high-temperature heat pump and the related conventional heat pump or transcritical heat pump are adopted to form a cascade heat pump for supplying heat, and the high energy efficiency and the high water supply temperature of the system are considered at the same time, so that the temperature requirement of 75/50 ℃ or even higher requirement of the water supply/return temperature required by the tail end of the heating radiator is met.
Through the utility model discloses an above-mentioned technical scheme cascade high temperature heat pump set who obtains, its beneficial effect is:
the air source heat pump can be started within the range from-40 ℃ to 10 ℃, the water supply temperature can be automatically adjusted from 30 ℃ to 90 ℃ according to the building load requirement and the tail end condition, the air source heat pump is suitable for various tail end equipment forms, and the continuous and stable heating output, the high energy efficiency ratio and the high water supply temperature of the air source heat pump under the low-temperature working condition can be realized.
Drawings
Fig. 1 is a schematic structural view of the cascade high-temperature heat pump unit of the present invention connected in series and connected to the end of the radiator;
FIG. 2 is a schematic diagram of the cascade high temperature heat pump unit of the present invention connected in series and to the radiant floor end;
FIG. 3 is a schematic structural view of the cascade high temperature heat pump unit of the present invention connected in parallel to the air conditioning unit terminal and the fan coil terminal;
FIG. 4 is a schematic structural view of the cascade high temperature heat pump units of the present invention connected in parallel and connected to the radiation end of the floor;
in the figure, 1, a high-temperature stage compressor; 2. a high temperature stage condenser; 3. a high temperature stage throttle valve; 4a, a low-temperature stage subcooler; 4b, a high-temperature-stage evaporator; 5. a low temperature stage throttle valve; 6. a low temperature stage evaporator; 7. a low temperature stage compressor; 8. a low temperature stage condenser; 9. the tail end of the air conditioning unit; 10. the end of a fan coil; 11. a floor radiation tip; 12. the tail end of the radiator.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings.
The cascade high-temperature heat pump unit comprises a low-temperature stage thermodynamic cycle and a high-temperature stage thermodynamic cycle, wherein the low-temperature stage thermodynamic cycle and the high-temperature stage thermodynamic cycle are both circularly connected with an execution tail end, and the cascade high-temperature heat pump unit is characterized in that the low-temperature stage thermodynamic cycle comprises a low-temperature stage subcooler 4a, the high-temperature stage thermodynamic cycle comprises a high-temperature stage evaporator 4b, and the subcooler and the evaporator are of a shared coupling structure.
The shared coupling structure refers to a shared heat exchanger, namely the heat exchanger is not only a low-temperature-level subcooler, but also a high-temperature-level evaporator. The heating capacity of the heat pump unit mainly depends on the heat release capacity of the condenser, and the heat release capacity of the condenser is derived from the heat absorption capacity obtained by heat exchange of the thermodynamic cycle working medium from the evaporator. That is, the heating capacity of the high-temperature stage of the cascade system mainly comes from the heat absorption capacity of the high-temperature stage evaporator, that is, the heat release capacity of the subcooler. Meanwhile, the heat release of the subcooler also affects the low-temperature-level heating capacity. Namely, the total heating capacity of the cascade system is determined by the coupling of the shared heat exchangers.
The execution tail end circulation comprises an air conditioning unit tail end 9, a fan coil pipe tail end 10, a floor radiation tail end 11 and a radiator tail end 12.
The low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle are connected in series, specifically, a water outlet of the high-temperature-stage condenser 2 and a water inlet of the low-temperature-stage condenser 8 are respectively connected with a water inlet and a water outlet for executing end circulation, and a water inlet of the high-temperature-stage condenser 2 is connected with a water outlet of the low-temperature-stage condenser 8.
The low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle are connected in parallel, specifically, a water outlet of the high-temperature-stage condenser 2 and a water outlet of the low-temperature-stage condenser 8 are both connected with an input end executing the tail-end cycle, and a water inlet of the high-temperature-stage condenser 2 and a water inlet of the low-temperature-stage condenser 8 are both connected with an output end executing the tail-end cycle.
In the series connection, the temperature difference between the low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle is larger than that of the parallel connection.
High-temperature stage thermodynamic cycle includes high-temperature stage compressor 1, high-temperature stage condenser 2, high-temperature stage choke valve 3, high-temperature stage compressor 1, high-temperature stage condenser 2, high-temperature stage choke valve 3 connect gradually, high-temperature stage evaporimeter 4b is connected with compressor 1, high-temperature stage choke valve 3 respectively, high-temperature stage compressor 1, high-temperature stage condenser 2, high-temperature stage choke valve 3, high-temperature stage evaporimeter 4b whole form the high-temperature stage thermodynamic cycle of cyclic annular fluid circuit, high-temperature stage condenser 2 with it connects to carry out end circulation heat transfer, high-temperature stage compressor 1, high-temperature stage condenser 2, high-temperature stage choke valve 3, high-temperature stage evaporimeter 4b are used for respectively showing throttle valve, evaporimeter, compressor, condenser installed in high-temperature stage thermodynamic cycle.
The low-temperature-stage thermodynamic cycle comprises a low-temperature-stage condenser 8, a low-temperature-stage compressor 7, a low-temperature-stage evaporator 6 and a low-temperature-stage throttling valve 5, wherein the low-temperature-stage condenser 8, the low-temperature-stage compressor 7, the low-temperature-stage evaporator 6 and the low-temperature-stage throttling valve 5 are sequentially connected, a low-temperature-stage subcooler 4a is respectively connected with the low-temperature-stage throttling valve 5 and the low-temperature-stage condenser 8, the low-temperature-stage compressor 7, the low-temperature-stage evaporator 6, the low-temperature-stage throttling valve 5 and the low-temperature-stage subcooler 4a are integrally formed into the low-temperature-stage thermodynamic cycle of an annular fluid loop, the low-temperature-stage condenser 8 is in heat exchange connection with the execution tail end cycle, and the low-temperature-stage condenser, Compressor, evaporator, throttle valve, subcooler.
Preferably, the low-temperature stage compressor can be a conventional air-supply enthalpy-increasing type compressor, such as a scroll compressor, a piston compressor or a screw compressor with air-supply enthalpy-increasing function; by adopting the transcritical working medium, under the supercritical condition, the heat release process has considerable temperature slippage, thereby being beneficial to the temperature rise of hot water and being capable of obtaining higher temperature of supplied water. The high-temperature stage compressor adopts a magnetic suspension centrifugal compressor and adopts a high-temperature single environment-friendly working medium, and can realize medium and high temperature heat pump circulation with high heat supply temperature, small circulating temperature rise and condensing pressure lower than critical pressure.
The magnetic suspension centrifugal compressor depends on the magnetic suspension bearing to suspend the rotor at a set position by utilizing electromagnetic force, has the advantages of no mechanical contact, no abrasion, high efficiency and the like, prolongs the service life, and has low noise and no surge. Meanwhile, the rotating speed can be adjusted according to the actual load and pressure ratio, and the compressor has higher performance than the traditional compressor under partial load, so that a good energy-saving effect is achieved;
by adopting the optimal cascade proportion, higher system energy efficiency can be obtained under the determined supply and return water temperature and the compressor displacement of the basic thermodynamic cycle;
the optimal overlapping proportion mainly refers to the optimal proportion of the heat exchange area of the low-temperature stage subcooler and the heat exchange area of the low-temperature stage condenser, so that the thermodynamic cycle can realize the maximum heating capacity or the highest energy efficiency ratio under the condition. Reference may be made specifically to the explanation of "common coupling structure".
The transcritical working medium is a refrigerant which operates under the transcritical condition. The transcritical heat pump cycle is a heat pump cycle with the condensing side pressure running above the critical pressure and is performed in a supercritical stateUnder the condition, the transcritical refrigerant has considerable temperature slippage in the heat release process, and the temperature rise of hot water is facilitated. Thereby achieving a higher supply water temperature. With CO2For example, CO2The flow of transcritical refrigeration circulation is slightly different from that of the common vapor compression refrigeration circulation, in the transcritical refrigeration circulation, the suction pressure of a compressor is lower than the critical pressure, the evaporation temperature is also lower than the critical temperature, the circulating suction process is still carried out under the subcritical condition, and the heat exchange process is mainly completed by latent heat. However, the exhaust pressure of the compressor is higher than the critical pressure, the condensing process of the working medium is completely different from that in the subcritical state, and the heat exchange process is completed by sensible heat.
The functions of single-stage heating and single-stage refrigeration can be realized by independently starting and stopping the low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle;
the magnetic suspension high-temperature heat pump and the related conventional heat pump or transcritical heat pump are adopted to form a cascade heat pump for supplying heat, and the high energy efficiency and the high water supply temperature of the system are considered at the same time, so that the temperature requirement of 75/50 ℃ or even higher requirement of the water supply/return temperature required by the tail end of the heating radiator is met.
Under the working condition of low-temperature heating (-40 ℃ to-5 ℃), the high-temperature stage compressor 1 and the low-temperature stage compressor 7 are started simultaneously, and high-temperature and high-pressure gaseous refrigerant from the compressors passes through the high-temperature stage condenser 2 and the low-temperature stage condenser 8 respectively and is condensed into high-pressure and low-temperature liquid refrigerant. The low-temperature stage high-pressure low-temperature liquid refrigerant is further condensed by a low-temperature stage subcooler 4, is decompressed by a low-temperature stage throttling valve 5, is changed into a low-temperature low-pressure liquid refrigerant, is evaporated into a low-temperature low-pressure gaseous refrigerant by a low-temperature stage evaporator 6, and then enters a compressor to be compressed to complete a thermodynamic cycle. Meanwhile, the high-temperature stage high-pressure low-temperature liquid refrigerant is directly decompressed by the high-temperature stage throttling valve 3 to become a low-temperature low-pressure liquid refrigerant, and the low-temperature low-pressure liquid refrigerant is evaporated into a low-temperature low-pressure gas refrigerant by the high-temperature stage evaporator 4 and then enters the compressor to be compressed to complete a thermodynamic cycle. Under the simultaneous action of two thermodynamic cycles, cold water is promoted to be high-temperature hot water of 30-90 ℃ through the heat exchange of the high-temperature-stage condenser 2 and the low-temperature-stage condenser 8, and is used for building heating.
Under the normal-temperature heating working condition (not less than-5 ℃), only the compressor 7 can be started, high-temperature and high-pressure gaseous refrigerant from the compressor passes through the low-temperature stage condenser 8 to be condensed into high-pressure and low-temperature liquid refrigerant, further passes through the low-temperature stage subcooler 4 to be condensed, is decompressed through the low-temperature stage throttling valve 5 to become low-temperature and low-pressure liquid refrigerant, passes through the low-temperature stage evaporator 6 to be evaporated into low-temperature and low-pressure gaseous refrigerant, and then enters the compressor to be compressed, so that a thermodynamic cycle is completed. Meanwhile, cold water is heated to be high-temperature hot water at 30-90 ℃ through heat exchange of the condenser 8 side, and is used for building heating.
Above-mentioned technical scheme has only embodied the utility model discloses technical scheme's preferred technical scheme, some changes that this technical field's technical personnel probably made to some parts wherein have all embodied the utility model discloses a principle belongs to within the protection scope of the utility model.
Claims (4)
1. A cascade high-temperature heat pump unit comprises a low-temperature stage thermodynamic cycle and a high-temperature stage thermodynamic cycle, wherein the low-temperature stage thermodynamic cycle and the high-temperature stage thermodynamic cycle are both connected with an execution tail end in a circulating manner, and is characterized in that the low-temperature stage thermodynamic cycle comprises a low-temperature stage subcooler (4a), the high-temperature stage thermodynamic cycle comprises a high-temperature stage evaporator (4b), the subcooler and the evaporator are of a common coupling structure,
the low-temperature stage thermodynamic cycle comprises a low-temperature stage condenser (8), a low-temperature stage compressor (7), a low-temperature stage evaporator (6) and a low-temperature stage throttle valve (5), wherein the low-temperature stage condenser (8), the low-temperature stage compressor (7), the low-temperature stage evaporator (6), the low-temperature stage throttle valve (5) and the low-temperature stage subcooler (4a) are integrally formed into a low-temperature stage thermodynamic cycle of an annular fluid loop,
the high-temperature-stage thermodynamic cycle comprises a high-temperature-stage compressor (1), a high-temperature-stage condenser (2) and a high-temperature-stage throttle valve (3), wherein the high-temperature-stage compressor (1), the high-temperature-stage condenser (2), the high-temperature-stage throttle valve (3) and a high-temperature-stage evaporator (4b) are integrally formed into the high-temperature-stage thermodynamic cycle of the annular fluid loop.
2. The cascaded high temperature heat pump unit of claim 1, wherein the execution end loop comprises an air conditioning unit end (9), a fan coil end (10), a floor radiation end (11), and a radiator end (12).
3. The cascade high-temperature heat pump unit according to claim 1, wherein the low-temperature-stage thermodynamic cycle and the high-temperature-stage thermodynamic cycle are connected in series, and specifically, the water outlet of the high-temperature-stage condenser (2) and the water inlet of the low-temperature-stage condenser (8) are respectively connected with the water inlet and the water outlet of the end cycle, and the water inlet of the high-temperature-stage condenser (2) is connected with the water outlet of the low-temperature-stage condenser (8).
4. The cascade high-temperature heat pump unit according to claim 1, wherein the low-temperature stage thermodynamic cycle and the high-temperature stage thermodynamic cycle are connected in parallel, specifically, the water outlet of the high-temperature stage condenser (2) and the water outlet of the low-temperature stage condenser (8) are both connected to an input end of an end cycle, and the water inlet of the high-temperature stage condenser (2) and the water inlet of the low-temperature stage condenser (8) are both connected to an output end of the end cycle.
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| CN201921102052.4U CN210512229U (en) | 2019-07-15 | 2019-07-15 | Cascade high-temperature heat pump unit |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110260550A (en) * | 2019-07-15 | 2019-09-20 | 中国建筑科学研究院有限公司 | Cascade high-temperature heat pump unit |
| CN115013997A (en) * | 2022-06-21 | 2022-09-06 | 同济大学 | Supercooling and overheating double-effect type multistage semi-overlapping heat pump cycle |
| WO2023233937A1 (en) * | 2022-06-02 | 2023-12-07 | コベルコ・コンプレッサ株式会社 | Two-stage refrigeration apparatus |
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2019
- 2019-07-15 CN CN201921102052.4U patent/CN210512229U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110260550A (en) * | 2019-07-15 | 2019-09-20 | 中国建筑科学研究院有限公司 | Cascade high-temperature heat pump unit |
| WO2023233937A1 (en) * | 2022-06-02 | 2023-12-07 | コベルコ・コンプレッサ株式会社 | Two-stage refrigeration apparatus |
| CN115013997A (en) * | 2022-06-21 | 2022-09-06 | 同济大学 | Supercooling and overheating double-effect type multistage semi-overlapping heat pump cycle |
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