CN201672739U - Cascade high-temperature heat pump with gaseous medium-temperature heat source and double low-temperature heat sources - Google Patents
Cascade high-temperature heat pump with gaseous medium-temperature heat source and double low-temperature heat sources Download PDFInfo
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- CN201672739U CN201672739U CN2010201878190U CN201020187819U CN201672739U CN 201672739 U CN201672739 U CN 201672739U CN 2010201878190 U CN2010201878190 U CN 2010201878190U CN 201020187819 U CN201020187819 U CN 201020187819U CN 201672739 U CN201672739 U CN 201672739U
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Abstract
A cascade high-temperature heat pump with a gaseous medium-temperature heat source and double low-temperature heat sources consists of a high-temperature heat pump circulation system and a low-temperature heat pump circulation system in cascade, wherein the low-temperature heat pump circulation system includes a low-temperature compressor, a double-heat-source evaporator, a heat sourced condensation evaporator, a low-temperature throttle valve and a connecting pipeline, heat pump working media are low-temperature heat pump working media, the high-temperature heat pump circulation system comprises a high-temperature compressor, a heat sourced condensation evaporator, a high-temperature condenser, a high-temperature throttle valve and a connecting pipeline, heat pump working media are high-temperature heat pump working media, the double-heat-source evaporator is provided with a low-temperature heat pump working medium passage and two heat source passages, and the heat sourced condensation evaporator is provided with a low-temperature heat pump working medium passage, a high-temperature heat pump working medium passage and a gaseous heat source passage. The cascade high-temperature heat pump can effectively provide hot water above 75 DEG C, can be widely applied to heating systems of civil buildings, public buildings and villa constructions, and can meet high-temperature hot water requirement for industrial production.
Description
Technical field
The utility model relates to the heat pump air conditioner technical field, especially relates to a kind of cascade high-temperature heat pump with warm source and two low-temperature heat sources in the gaseous state that hot water more than 75 ℃ is provided.
Background technology
Along with the continuous propelling of national energy-saving and emission-reduction work, the medium small boiler in the city is eliminated gradually, presses for new high-efficient energy-saving environment friendly device at present and replaces the medium small boiler that is eliminated for heating with the high-temperature-hot-water that provides more than 75 ℃ is provided.Traditional heat pump can only provide water temperature not to be higher than 55 ℃ hot water, can not satisfy heating and production demand, and the single-stage of studying at present circulation and superposition type cyclic high-temperature heat pump all can only adopt single low temperature or single in warm source, can't realize compound utilization to two or more thermals source, and the worst hot case running efficiency is very low, is difficult to apply.
Summary of the invention
The purpose of this utility model provide at existing weak point in the above-mentioned prior art just a kind of can to air, solar energy, regenerative resource such as energy and various waste heat, used heat carry out comprehensive with rationally utilize, can produce the cascade high-temperature heat pump with warm source and two low-temperature heat sources in the gaseous state of hot water more than 75 ℃.
The purpose of this utility model can realize by following technique measures:
Cascade high-temperature heat pump with warm source in the gaseous state and two low-temperature heat sources of the present utility model is to be formed by two heat pump circulating system overlappings of high and low temperature:
A, the circulation of described low temperature comprise cryogenic compressor, two thermal source evaporimeter, heat source type condenser/evaporator, cryogenic throttle valve and connecting line; Described pair of thermal source evaporimeter has a hot pump in low temp working medium passage and two thermal source passages, and the heat source type condenser/evaporator has a hot pump in low temp working medium passage, a high temperature heat pump working medium passage and a gaseous state thermal source passage; Wherein the import of cryogenic compressor connects the outlet of the hot pump in low temp working medium passage of two thermal source evaporimeters, and the outlet of cryogenic compressor connects the import of the hot pump in low temp working medium passage of heat source type condenser/evaporator; The outlet of the hot pump in low temp working medium passage of heat source type condenser/evaporator is connected by the import of cryogenic throttle valve with the hot pump in low temp working medium passage of two thermal source evaporimeters, and its heat pump fluid is hot pump in low temp working medium (for the used working medium of conventional heat pump air conditioner); Being connected with the import and export pipeline of gaseous state thermal source respectively of the gaseous state thermal source passage of described heat source type condenser/evaporator, constitute independently loop into and out of interface; Two thermal source passages of described pair of thermal source evaporimeter connecting with the import and export pipeline of two kinds of different low-temperature heat sources respectively separately, constitute two independently loops into and out of interface;
B, described high temperature circulation comprise high temperature compressed machine, heat source type condenser/evaporator, high temperature condenser, high temperature choke valve and connecting line; Wherein the import of high temperature compressed machine connects the outlet of the high temperature heat pump working medium passage of heat source type condenser/evaporator, the outlet of high temperature compressed machine connects the import of the heat pump fluid passage of high temperature condenser, the import of the high temperature heat pump working medium passage of heat source type condenser/evaporator is connected by the outlet of high temperature choke valve with the heat pump fluid passage of high temperature condenser, and its heat pump fluid is high temperature heat pump working medium (for condensation temperature 〉=75 in the higher high temperature heat pump working medium of condensation temperature, its nominal situation scope ℃).
The described pair of employed thermal source of thermal source evaporimeter can be temperature≤30 ℃ air, solar energy, regenerative resource and various waste heat and used heat such as energy.
The employed thermal source of described heat source type condenser/evaporator can be the air of temperature 〉=30 ℃ and various gaseous state waste heat, used heat.
Cascade high-temperature heat pump with warm source in the gaseous state and two low-temperature heat sources of the present utility model both can absorb warm source heat in gaseous state low-temperature heat source, liquid low-temperature heat source and the gaseous state separately, can absorb the heat of any two or three thermal source in the warm source in gaseous state low-temperature heat source, liquid low-temperature heat source, the gaseous state again simultaneously.
Two thermal source evaporimeters are Chinese patent 200720091299.1 disclosed fin-sleeve type three mediums composite heat exchangers described in the utility model, also can adopt Chinese patent 200820069364.5 disclosed shell-sleeve type three mediums composite heat-exchangers with three kinds of medium channels.
The condenser/evaporator of heat source type described in the utility model is Chinese patent 200720091299.1 disclosed fin-sleeve type three mediums composite heat exchangers.
The beneficial effects of the utility model are as follows:
Device of the present utility model can provide the hot water more than 75 ℃ efficiently, can be widely used in the heating system of civil buildings, public building, villa buildings, and can satisfy industrial high-temperature-hot-water demand.
Description of drawings
Fig. 1 is the structure principle chart of the cascade high-temperature heat pump of the warm source in the gaseous state of the utlity model has and two low-temperature heat sources.
Fig. 2 is gaseous state and liquid structure principle chart with the cascade high-temperature heat pump in warm source and two low-temperature heat sources in the gaseous state for low-temperature heat source.
Fig. 3 is the structure principle chart of the cascade high-temperature heat pump with warm source in the gaseous state and two low-temperature heat sources of two kinds of liquid heat sources for low-temperature heat source.
Sequence number among the figure: 1 cryogenic compressor, 1 ' the high temperature compressed machine, 2 pairs of thermal source evaporimeters, 3 high temperature condensers, 4 cryogenic throttle valves, 4 ' high temperature choke valve, 5 heat source type condenser/evaporators.
The specific embodiment
The utility model is further described below with reference to embodiment (accompanying drawing), but does not limit the utility model.
As shown in Figure 1, the cascade high-temperature heat pump with warm source in the gaseous state and two low-temperature heat sources of the present utility model is to be formed by two heat pump circulating system overlappings of high and low temperature: described low temperature circulation comprises cryogenic compressor 1, two thermal source evaporimeter 2, heat source type condenser/evaporator 5, cryogenic throttle valve 4 and connecting line; Described pair of thermal source evaporimeter 2 has a hot pump in low temp working medium passage and two thermal source passages, and heat source type condenser/evaporator 5 has a hot pump in low temp working medium passage, a high temperature heat pump working medium passage and a gaseous state thermal source passage; Wherein the import of cryogenic compressor 1 connects the outlet of the hot pump in low temp working medium passage of two thermal source evaporimeters 2, and the outlet of cryogenic compressor 1 connects the import of the hot pump in low temp working medium passage of heat source type condenser/evaporator 5; The outlet of the hot pump in low temp working medium passage of heat source type condenser/evaporator 5 is connected by the import of cryogenic throttle valve 4 with the hot pump in low temp working medium passage of two thermal source evaporimeters 2, and its heat pump fluid is hot pump in low temp working medium (for the used working medium of conventional heat pump air conditioner); Being connected with the import and export pipeline of gaseous state thermal source respectively of the gaseous state thermal source passage of described heat source type condenser/evaporator 5, constitute independently loop into and out of interface; Two thermal source passages of described pair of thermal source evaporimeter 2 connecting with the import and export pipeline of two kinds of different low-temperature heat sources respectively separately, constitute two independently loops into and out of interface; Described high temperature circulation comprises high temperature compressed machine 1 ', heat source type condenser/evaporator 5, high temperature condenser 3, high temperature choke valve 4 ' and connecting line; Wherein the import of high temperature compressed machine 1 ' connects the outlet of the high temperature heat pump working medium passage of heat source type condenser/evaporator 5, the outlet of high temperature compressed machine 1 ' connects the import of the heat pump fluid passage of high temperature condenser 3, the import of the high temperature heat pump working medium passage of heat source type condenser/evaporator 5 is connected by the outlet of high temperature choke valve 4 ' with the heat pump fluid passage of high temperature condenser 3, and its heat pump fluid is high temperature heat pump working medium (for condensation temperature 〉=75 in the higher high temperature heat pump working medium of condensation temperature, its nominal situation scope ℃).
As shown in Figure 2, the present embodiment structure is identical with embodiment 1, and the low-temperature heat source described in this embodiment is gaseous state and liquid heat source.
As shown in Figure 3, the present embodiment structure is identical with embodiment 1, and the low-temperature heat source described in this embodiment is two kinds of liquid heat sources.
Two thermal source evaporimeters are Chinese patent 200720091299.1 disclosed fin-sleeve type three mediums composite heat exchangers described in the utility model, also can adopt Chinese patent 200820069364.5 disclosed shell-sleeve type three mediums composite heat-exchangers with three kinds of medium channels.
The condenser/evaporator of heat source type described in the utility model is Chinese patent 200720091299.1 disclosed fin-sleeve type three mediums composite heat exchangers.
Workflow of the present utility model is as follows:
(1) independent low-temperature heat source pattern
A, single gaseous state low-temperature heat source pattern.
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters two thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, enters cryogenic compressor behind the absorption gaseous state thermal source heat and enters next circulation; High temperature heat pump working medium is by the 1 ' compression of high temperature compressed machine, through to high temperature condenser 3 release heat, and through high temperature choke valve 4 ', heat source type condenser/evaporator 5, absorption hot pump in low temp working medium heat is laggard goes into high temperature compressed machine and enters next circulation.
B, single liquid low-temperature heat source pattern.
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters two thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, enters cryogenic compressor behind the absorption liquid heat source heat and enters next circulation; High temperature heat pump working medium is by the 1 ' compression of high temperature compressed machine, through to high temperature condenser 3 release heat, and through high temperature choke valve 4 ', heat source type condenser/evaporator 5, absorption hot pump in low temp working medium heat is laggard goes into high temperature compressed machine and enters next circulation.
C, the two low-temperature heat source composite modes of gaseous state-liquid state.
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters pair thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, absorbs simultaneously to enter cryogenic compressor behind gaseous state thermal source and the liquid heat source heat and enter next circulation; High temperature heat pump working medium is by the 1 ' compression of high temperature compressed machine, through to high temperature condenser 3 release heat, and through high temperature choke valve 4 ', heat source type condenser/evaporator 5, absorption hot pump in low temp working medium heat is laggard goes into high temperature compressed machine and enters next circulation.
D, biliquid attitude low-temperature heat source composite mode.
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters pair thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, absorbs simultaneously to enter cryogenic compressor behind the heat of two kinds of liquid heat sources and enter next circulation; High temperature heat pump working medium is by the 1 ' compression of high temperature compressed machine, through to high temperature condenser 3 release heat, and through high temperature choke valve 4 ', heat source type condenser/evaporator 5, absorption hot pump in low temp working medium heat is laggard goes into high temperature compressed machine and enters next circulation.
(2) warm source module in the independent gaseous state
Close cryogenic compressor 1, high temperature heat pump working medium is by high temperature compressed machine 1 ' compression, and through to high temperature condenser 3 release heat, through high temperature choke valve 4 ', heat source type condenser/evaporator 5 enters high temperature compressed machine behind the heat of warm source in the absorption gaseous state and enters next circulation.
(3) warm source and single low-temperature heat source composite mode in the gaseous state
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters two thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, enters cryogenic compressor behind absorption gaseous state or the liquid heat source heat and enters next circulation; High temperature heat pump working medium is by high temperature compressed machine 1 ' compression, and through to high temperature condenser 3 release heat, through high temperature choke valve 4 ', heat source type condenser/evaporator 5 enters high temperature compressed machine behind the heat of warm source in absorption hot pump in low temp working medium and the gaseous state and enters next circulation.
(4) warm source and two low-temperature heat source composite modes in the gaseous state
Hot pump in low temp working medium through to heat source type condenser/evaporator 5 release heat, enters pair thermal source evaporimeters 2 through cryogenic throttle valve 4 by cryogenic compressor 1 compression, absorbs simultaneously to enter cryogenic compressor behind gaseous state and the liquid heat source heat and enter next circulation; High temperature heat pump working medium is by high temperature compressed machine 1 ' compression, and through to high temperature condenser 3 release heat, through high temperature choke valve 4 ', heat source type condenser/evaporator 5 enters high temperature compressed machine behind the heat of warm source in absorption hot pump in low temp working medium and the gaseous state and enters next circulation.
Claims (1)
1. cascade high-temperature heat pump with warm source in the gaseous state and two low-temperature heat sources, it is characterized in that: this device is formed by two heat pump circulating system overlappings of high and low temperature:
A, the circulation of described low temperature comprise cryogenic compressor (1), two thermal source evaporimeter (2), heat source type condenser/evaporator (5), cryogenic throttle valve (4) and connecting line; Described pair of thermal source evaporimeter (2) has a hot pump in low temp working medium passage and two thermal source passages, and heat source type condenser/evaporator (5) has a hot pump in low temp working medium passage, a high temperature heat pump working medium passage and a gaseous state thermal source passage; Wherein the import of cryogenic compressor (1) connects the outlet of the hot pump in low temp working medium passage of two thermal source evaporimeters (2), and the outlet of cryogenic compressor (1) connects the import of the hot pump in low temp working medium passage of heat source type condenser/evaporator (5); The outlet of the hot pump in low temp working medium passage of heat source type condenser/evaporator (5) is connected by the import of cryogenic throttle valve (4) with the hot pump in low temp working medium passage of two thermal source evaporimeters (2), and its heat pump fluid is a hot pump in low temp working medium; Being connected with the import and export pipeline of gaseous state thermal source respectively of the gaseous state thermal source passage of described heat source type condenser/evaporator (5), constitute independently loop into and out of interface; Two thermal source passages of described pair of thermal source evaporimeter (2) connecting with the import and export pipeline of two kinds of different low-temperature heat sources respectively separately, constitute two independently loops into and out of interface;
B, described high temperature circulation comprise high temperature compressed machine (1 '), heat source type condenser/evaporator (5), high temperature condenser (3), high temperature choke valve (4 ') and connecting line; The import of wherein high temperature compressed machine (1 ') connects the outlet of the high temperature heat pump working medium passage of heat source type condenser/evaporator (5), the outlet of high temperature compressed machine (1 ') connects the import of the heat pump fluid passage of high temperature condenser (3), the import of the high temperature heat pump working medium passage of heat source type condenser/evaporator (5) is connected by the outlet of high temperature choke valve (4 ') with the heat pump fluid passage of high temperature condenser (3), and its heat pump fluid is a high temperature heat pump working medium.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201878190U CN201672739U (en) | 2010-05-13 | 2010-05-13 | Cascade high-temperature heat pump with gaseous medium-temperature heat source and double low-temperature heat sources |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010201878190U CN201672739U (en) | 2010-05-13 | 2010-05-13 | Cascade high-temperature heat pump with gaseous medium-temperature heat source and double low-temperature heat sources |
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| Publication Number | Publication Date |
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| CN201672739U true CN201672739U (en) | 2010-12-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010201878190U Expired - Fee Related CN201672739U (en) | 2010-05-13 | 2010-05-13 | Cascade high-temperature heat pump with gaseous medium-temperature heat source and double low-temperature heat sources |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2489568A (en) * | 2011-03-25 | 2012-10-03 | Bruker Biospin Ag | Cascade Cooling Arrangement with Controllable Evaporation Temperature |
-
2010
- 2010-05-13 CN CN2010201878190U patent/CN201672739U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2489568A (en) * | 2011-03-25 | 2012-10-03 | Bruker Biospin Ag | Cascade Cooling Arrangement with Controllable Evaporation Temperature |
| GB2489568B (en) * | 2011-03-25 | 2017-11-15 | Bruker Biospin Ag | Cooling device with controllable evaporation temperature |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20101215 Termination date: 20150513 |
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| EXPY | Termination of patent right or utility model |