CN204494786U - For the production of the multi-staged air source heat pump of high-temperature-hot-water - Google Patents
For the production of the multi-staged air source heat pump of high-temperature-hot-water Download PDFInfo
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- CN204494786U CN204494786U CN201420859030.3U CN201420859030U CN204494786U CN 204494786 U CN204494786 U CN 204494786U CN 201420859030 U CN201420859030 U CN 201420859030U CN 204494786 U CN204494786 U CN 204494786U
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- heat exchanger
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- expansion valve
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Abstract
The utility model discloses a kind of multi-staged air source heat pump for the production of high-temperature-hot-water, comprise the first refrigerant loop and second refrigerant loop.First refrigerant loop is connected with heat exchanger, and the first refrigerant loop and second refrigerant loop are interconnected by intermediate heat exchanger and finned type heat exchanger, the first refrigerating circuit and second refrigerating circuit of finned type heat exchanger inside are interleaved each other in the fin of heat exchanger.The utility model devises the multi-staged air source heat pump of the production high-temperature-hot-water that a kind of coefficient of performance is optimized, the utility model can keep the coefficient of performance of optimization at the operation interval of a wide range, make the utility model realize high-adaptability to border change condition simultaneously.Finally, the utility model is compact to design, simply, easily controls, and efficiently can perform required defrost circulation.
Description
Technical field
The utility model relates to air source heat pump, more particularly, relates to the multi-staged air source heat pump for the production of high-temperature-hot-water.
Background technology
Net for air-source heat pump units is the machine being provided freezing of high-temperature-hot-water and can heat from draw heat around low temperature environment to user by inverse compression cycle (inverse Carnot cycle).The use of air source heat pump is produced a certain amount of hot water at a certain temperature or provide certain heating capacity QT at the temperature of user's setting.Performance coefficient of heat pump (COP) is defined as the ratio of available heat (being supplied to the heat of user) and total power consumption (absorbed power PA).
There is now various types of air-source hot water heat pump for the production of high-temperature-hot-water.The shortcoming that traditional single-stage air source hot water heat pump exists is that the temperature difference of the highest hot water temperature of ambient air temperature and production needs in certain limited field.Particularly, there is corresponding decay in the COP value of unit under high compression ratio.And when air themperature declines, the thermal capacity QT that source pump is supplied to user also reduces.
Use the cold-producing medium thermal characteristics imperfection of traditional two-stage air-source heat pump of unitary system cryogen, and range of operation is little.Heat pump, to the change bad adaptability of boundary condition, can influence each other between high pressure and low pressure, and keeps the minimum compression ratio in two stages to there is certain difficulty.Also have the two-stage air source heat pump with two cascade refrigeration loops, but structure is extremely complicated, adapts to boundary condition poor, be difficult to the single refrigerant loop of independent control.
There is defrosting cycle inefficiency in these heat pumps, and be difficult to the difficulty of the minimum compression ratio in two stages of maintenance when air themperature height.These heat pumps are finally only applicable to produce high-temperature-hot-water specially.
Utility model content
The temperature difference for the highest hot water temperature of the ambient air temperature existed in prior art and production needs in certain limited field, cold-producing medium thermal characteristics imperfection, and range of operation is little, to the change bad adaptability of boundary condition, structure is extremely complicated, the shortcomings such as defrosting cycle inefficiency, the purpose of this utility model is to provide a kind of multi-staged air source heat pump for the production of high-temperature-hot-water.
For achieving the above object, the utility model adopts following technical scheme:
According to the utility model, a kind of multi-staged air source heat pump for the production of high-temperature-hot-water is provided, it is characterized in that, comprise the first refrigerant loop and second refrigerant loop.First refrigerant loop is connected with heat exchanger, and the first refrigerant loop and second refrigerant loop are interconnected by intermediate heat exchanger and finned type heat exchanger, the first refrigerating circuit and second refrigerating circuit of finned type heat exchanger inside are interleaved each other in the fin of heat exchanger
According to an embodiment of the present utility model, the first refrigerant loop comprises the first compressor, cross valve, the first expansion valve, the second expansion valve, the 3rd expansion valve, the first check valve.The entrance of cross valve connects the first compressor, and its outlet connects heat exchanger, the first check valve and finned type heat exchanger respectively.First expansion valve is arranged at the upstream of intermediate heat exchanger, and the second expansion valve is arranged at the upstream of finned type heat exchanger, and the 3rd expansion valve is connected with heat exchanger, and is connected with the second expansion valve with the first expansion valve.
According to an embodiment of the present utility model, the first refrigerant loop also comprises the first check-valves, the second check-valves, the 3rd check-valves, gas-liquid separator, reservoir, the second check valve.First check valve and the first compressor are connected by gas-liquid separator and form loop.Set gradually the first check-valves and the 3rd check-valves between first expansion valve and the second expansion valve, one end of the second check-valves connects the 3rd expansion valve, and the other end connects the first check-valves, the 3rd check-valves and reservoir.Reservoir is connected with finned type heat exchanger by the second check valve.
According to an embodiment of the present utility model, second refrigerant loop comprises the second compressor, the 4th expansion valve.Second compressor one end connecting fin plate heat exchanger, the other end connects intermediate heat exchanger, and intermediate heat exchanger is connected with finned type heat exchanger by the 4th expansion valve.
According to an embodiment of the present utility model, second refrigerant loop also comprises the 3rd check valve, and one end of the 3rd check valve connects the second check valve and reservoir, and its other end connects the 3rd expansion valve and heat exchanger.
According to an embodiment of the present utility model, cross valve comprises an entrance and three outlets, and entrance can switch any one outlet of connection, and can interconnect between each outlet.
According to an embodiment of the present utility model, the first refrigerant loop determines its inner the first cold-producing medium used by the temperature difference of air themperature and production hot water.
According to an embodiment of the present utility model, second refrigerant loop uses the second refrigerant different from the first cold-producing medium.
In technique scheme, the utility model devises the multi-staged air source heat pump of the production high-temperature-hot-water that a kind of coefficient of performance is optimized, the coefficient of performance of optimization can be kept at the operation interval of a wide range, make the utility model realize high-adaptability to border change condition simultaneously.Finally, the utility model is compact to design, simply, easily controls, and efficiently can perform required defrost circulation.
Accompanying drawing explanation
System circuit figure when Fig. 1 is the first loop production high-temperature water;
System circuit figure when Fig. 2 is second servo loop production high-temperature water;
Fig. 3 be finned heat exchanger defrosting or work for the production of cold water time system circuit figure;
Fig. 4 is the enlarged drawing of cross valve.
Detailed description of the invention
The technical solution of the utility model is further illustrated below in conjunction with drawings and Examples.
The utility model discloses a kind of multi-staged air source heat pump for the production of high-temperature-hot-water, it comprises the first refrigerant loop 1 and second refrigerant loop 2, describes structure and the annexation of above-mentioned all parts below in detail.
As Fig. 1, the first refrigerant loop 1 comprises the first compressor 7, cross valve 8, first expansion valve 9, second expansion valve 10, the 3rd expansion valve 11, first check valve 13.First refrigerant loop 1 is connected with the heat exchanger 5 for user 6 by waterway circulating, and user 6 is connected into heat exchanger 5 from right side, and heat exchanger 5 wherein one end connects the first compressor 7 by cross valve 8.Cross valve 8 is divided into entrance 81, outlet 82, outlet 83, outlet 84, and entrance can switch any one outlet of connection, and can interconnect between each outlet.The entrance 81 of cross valve 8 connects the first compressor 7, and its outlet 82 connects heat exchanger 5, outlet 83 connects the first check valve 13, exports 84 connecting fin plate heat exchangers 4.Heat exchanger 5 other end is connected with the 3rd expansion valve 11, and is connected with the second expansion valve 10 with the first expansion valve 9.First expansion valve 9 is arranged at the upstream of intermediate heat exchanger 3, and the second expansion valve 10 is arranged at the upstream of finned type heat exchanger 4.
Continue to see Fig. 1, the first refrigerant loop 1 also comprises the first check-valves 121, second check-valves 122, the 3rd check-valves 123, gas-liquid separator 14, reservoir 15, second check valve 18.First check valve 13 and the first compressor 7 are connected by gas-liquid separator 14 and form loop.First check-valves 121 and the 3rd check-valves 123 are arranged between the first expansion valve 9 and the second expansion valve 10, second check-valves 122 is arranged between the 3rd expansion valve 11 and reservoir 15, first check-valves 121, second check-valves 122 and the 3rd check-valves 123 are in angular distribution.One end of second check-valves 122 connects the 3rd expansion valve 11, and the other end connects the first check-valves 121, the 3rd check-valves 123 and reservoir 15.Reservoir 15 is connected with finned type heat exchanger 4 by the second check valve 18.
As Fig. 2, second refrigerant loop 2 comprises the second compressor 16, the 4th expansion valve 17.Second compressor 16 left end connects intermediate heat exchanger 3, right-hand member connecting fin plate heat exchanger 4.Intermediate heat exchanger 3 is connected by the 4th expansion valve 17 with finned type heat exchanger 4.Second refrigerant loop 2 is connected with the heat exchanger 5 for user 6 by waterway circulating, and user 6 is connected into heat exchanger 5 from right side, and heat exchanger 5 wherein one end connects the first compressor 7 by cross valve 8.Cross valve 8 is divided into entrance 81, outlet 82, outlet 83, outlet 84, and entrance can switch any one outlet of connection, and can interconnect between each outlet.The entrance 81 of cross valve 8 connects the first compressor 7, and its outlet 82 connects heat exchanger 5, outlet 83 connects the first check valve 13, exports 84 connecting fin plate heat exchangers 4.Heat exchanger 5 other end is connected with the 3rd expansion valve 11, and is connected with the second expansion valve 10 with the first expansion valve 9.First expansion valve 9 is arranged at the upstream of intermediate heat exchanger 3, and the second expansion valve 10 is arranged at the upstream of finned type heat exchanger 4.
Continue to see Fig. 2, one end that second refrigerant loop also comprises the 3rd check valve the 19, three check valve 19 connects the second check valve 18 and reservoir 15, and its other end connects the 3rd expansion valve 11 and heat exchanger 5.First check valve 13 and the first compressor 7 are connected by gas-liquid separator 14 and form loop.First check-valves 121 and the 3rd check-valves 123 are arranged between the first expansion valve 9 and the second expansion valve 10, second check-valves 122 is arranged between the 3rd expansion valve 11 and reservoir 15, first check-valves 121, second check-valves 122 and the 3rd check-valves 123 are in angular distribution.One end of second check-valves 122 connects the 3rd expansion valve 11, and the other end connects the first check-valves 121, the 3rd check-valves 123 and reservoir 15.Reservoir 15 is connected with finned type heat exchanger 4 by the second check valve 18.
As Fig. 3, first refrigerant loop 1 is connected with heat exchanger 5, and the first refrigerant loop 1 and second refrigerant loop 2 are interconnected by intermediate heat exchanger 3 and finned type heat exchanger 4, the first refrigerating circuit 1 of finned type heat exchanger 4 inside and the second refrigerating circuit 2 are interleaved each other in the fin of heat exchanger 5.
First refrigerant loop 1 determines its inner the first cold-producing medium used by the temperature difference of air themperature and production hot water.Second refrigerant loop 2 uses the second refrigerant different from the first cold-producing medium.First compressor 7 and the first cold-producing medium are by its operation characteristic in high pressure phase optimization by choice for use, and the second compressor 16 and second refrigerant are because its operation characteristic in periods of low pressure optimization is by choice for use.
The utility model is for the production of high-temperature water, the difference of controller record air themperature and water temperature, if this difference is in operation interval, such as when outside air temperature is higher, close the first check-valves 121 and the second check-valves 122, open the 3rd check-valves 123, the entrance 81 switching cross valve 8 is connected to outlet 82 and is connected with outlet 83, outlet 84, and connects the compressor 7 of the first refrigerant loop 1.In described first refrigerant loop 1, finned heat exchanger 4 uses as this evaporimeter, and heat exchanger 5 uses as condenser.
The utility model has high thermal capacity and high COP.If the air themperature read and the difference of water temperature drop in the second refrigerating circuit, (such as, when external air temperature is low) time, controller cuts out the second check-valves 122 and the 3rd check-valves 123, open the first check-valves 121, switch check valve 8 entrance 81 to outlet 82, and make the compressor 7 of the first refrigerant loop 1 and the compressor 16 in second refrigerant loop 2 access circulation.In the first refrigerant loop 1, heat exchanger 4 is the evaporimeter in second refrigerant loop 2, the condenser of intermediate heat exchanger 3 as second refrigerant loop 2 and the evaporimeter of the first refrigerant loop 1, simultaneously heat exchanger 5 as the condenser of the first refrigerant loop 1.Therefore two compressor 7 and 16 total workings are in suitable temperature range, and in suitable compression ratio.
The integrating control that the utility model is provided convenience, according to boundary condition, determines optimum switching time from single to two stage.
The utility model also can be used in reverse mode, provides cold water (in summer) or provide defrost cycle for fin heat exchanger 4 for user.In this case, this electric controller controls as follows: close the first check-valves 121 and the 3rd check-valves 123, open two check-valves 122, switch reversal valve 8, entrance 81 is connected to outlet 84, and outlet 82 is connected with outlet 83, and make the first compressor 7 of the first refrigerant loop 1 be connected in closed circuit, in this circulation, heat exchanger 4 is as condenser, and heat exchanger 5 is as evaporimeter.But it should be noted that, if this heat exchanger 4 is " overlappings ", heat pump not only can be made very compact, and second servo loop 2 also extremely simplify, do not need reverse kind of refrigeration cycle to ensure the defrosting of finned type heat exchanger, only need the first loop to carry out work.When controller determination finned type heat exchanger 4 freezes, switch the second compressor 16, and make the first refrigerant loop 1 reverse circulation, condensation heat is provided on finned type heat exchanger 4, carrys out the ice that melting heat interchanger has been formed.
The utility model provides the possibility of producing high-temperature-hot-water, (such as even higher than 80 DEG C), in the temperature range of environment temperature and water widely, have higher COP, the flexibility of height, hot water temperature and the outside atmosphere temperature of production are expanded greatly.Especially, in the thermal capacity of heat pump, can substantially not change with the reduction of external air temperature.Described refrigerant loop and the compressor of cold-producing medium can be optimized for each operation circuit, to make compressor with suitable compression ratio work, to guarantee the highest efficiency, and enough lubrications and suitable running temperature.Certainly, compressor and the cold-producing medium of any type and quantity also can be used in each circulation level section.Can multiple change and modification be carried out for the multi-staged air source heat pump producing high-temperature water, all belong to concept and range of the present utility model.In addition, all details all can carry out technical equivalent replacement.
Those of ordinary skill in the art will be appreciated that, above embodiment is only used to the utility model is described, and be not used as restriction of the present utility model, as long as in spirit of the present utility model, all will drop in Claims scope of the present utility model the change of the above embodiment, modification.
Claims (8)
1., for the production of a multi-staged air source heat pump for high-temperature-hot-water, it is characterized in that, comprising:
First refrigerant loop and second refrigerant loop;
Described first refrigerant loop is connected with heat exchanger, and described first refrigerant loop and second refrigerant loop are interconnected by intermediate heat exchanger and finned type heat exchanger, the first refrigerating circuit and second refrigerating circuit of described finned type heat exchanger inside are interleaved each other in the fin of heat exchanger.
2., as claimed in claim 1 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described first refrigerant loop comprises:
First compressor, cross valve, the first expansion valve, the second expansion valve, the 3rd expansion valve, the first check valve;
The entrance of described cross valve connects described first compressor, and its outlet connects described heat exchanger, the first check valve and finned type heat exchanger respectively;
Described first expansion valve is arranged at the upstream of described intermediate heat exchanger, described second expansion valve is arranged at the upstream of described finned type heat exchanger, described 3rd expansion valve is connected with described heat exchanger, and is connected with the second expansion valve with described first expansion valve.
3., as claimed in claim 2 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described first refrigerant loop also comprises: the first check-valves, the second check-valves, the 3rd check-valves, gas-liquid separator, reservoir, the second check valve;
Described first check valve and described first compressor are connected by described gas-liquid separator and form loop;
Set gradually the first check-valves and the 3rd check-valves between described first expansion valve and the second expansion valve, one end of described second check-valves connects described 3rd expansion valve, and the other end connects described first check-valves, the 3rd check-valves and described reservoir;
Described reservoir is connected with described finned type heat exchanger by described second check valve.
4., as claimed in claim 3 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described second refrigerant loop comprises: the second compressor, the 4th expansion valve;
Described second compressor one end connects described finned type heat exchanger, and the other end connects described intermediate heat exchanger, and described intermediate heat exchanger is connected with described finned type heat exchanger by described 4th expansion valve.
5. as claimed in claim 4 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described second refrigerant loop also comprises the 3rd check valve, one end of described 3rd check valve connects described second check valve and described reservoir, and its other end connects described 3rd expansion valve and described heat exchanger.
6. as claimed in claim 5 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described cross valve comprises an entrance and three outlets, and described entrance can switch any one outlet of connection, and can interconnect between each outlet.
7. as claimed in claim 6 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described first refrigerant loop determines its inner the first cold-producing medium used by the temperature difference of air themperature and production hot water.
8. as claimed in claim 7 for the production of the multi-staged air source heat pump of high-temperature-hot-water, it is characterized in that, described second refrigerant loop uses the second refrigerant different from described first cold-producing medium.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420859030.3U CN204494786U (en) | 2014-12-29 | 2014-12-29 | For the production of the multi-staged air source heat pump of high-temperature-hot-water |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420859030.3U CN204494786U (en) | 2014-12-29 | 2014-12-29 | For the production of the multi-staged air source heat pump of high-temperature-hot-water |
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| Publication Number | Publication Date |
|---|---|
| CN204494786U true CN204494786U (en) | 2015-07-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420859030.3U Withdrawn - After Issue CN204494786U (en) | 2014-12-29 | 2014-12-29 | For the production of the multi-staged air source heat pump of high-temperature-hot-water |
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| Country | Link |
|---|---|
| CN (1) | CN204494786U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104501406A (en) * | 2014-12-29 | 2015-04-08 | 克莱门特捷联制冷设备(上海)有限公司 | Multistage air source heat pump for producing high temperature hot water |
| CN110662932A (en) * | 2017-01-19 | 2020-01-07 | 株式会社新进能量技术 | 3-stage cooling and defrost system using quick freezing chamber, freezing chamber and refrigerating chamber |
-
2014
- 2014-12-29 CN CN201420859030.3U patent/CN204494786U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104501406A (en) * | 2014-12-29 | 2015-04-08 | 克莱门特捷联制冷设备(上海)有限公司 | Multistage air source heat pump for producing high temperature hot water |
| CN104501406B (en) * | 2014-12-29 | 2017-03-29 | 克莱门特捷联制冷设备(上海)有限公司 | For producing the multi-staged air source heat pump of high-temperature-hot-water |
| CN110662932A (en) * | 2017-01-19 | 2020-01-07 | 株式会社新进能量技术 | 3-stage cooling and defrost system using quick freezing chamber, freezing chamber and refrigerating chamber |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150722 Effective date of abandoning: 20170329 |
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| AV01 | Patent right actively abandoned |