CN201811498U - A dual heat source type multistage compression high temperature heat pump - Google Patents
A dual heat source type multistage compression high temperature heat pump Download PDFInfo
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- CN201811498U CN201811498U CN2010205477758U CN201020547775U CN201811498U CN 201811498 U CN201811498 U CN 201811498U CN 2010205477758 U CN2010205477758 U CN 2010205477758U CN 201020547775 U CN201020547775 U CN 201020547775U CN 201811498 U CN201811498 U CN 201811498U
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- 230000006835 compression Effects 0.000 title claims description 18
- 230000009977 dual effect Effects 0.000 title 1
- 239000007788 liquid Substances 0.000 claims abstract description 27
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 239000002131 composite material Substances 0.000 claims description 21
- 230000005855 radiation Effects 0.000 claims description 9
- 239000011248 coating agent Substances 0.000 claims description 8
- 238000000576 coating method Methods 0.000 claims description 8
- 230000008676 import Effects 0.000 claims description 3
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 238000010438 heat treatment Methods 0.000 abstract description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 8
- 238000005516 engineering process Methods 0.000 abstract description 3
- 238000009776 industrial production Methods 0.000 abstract 1
- 238000001704 evaporation Methods 0.000 description 7
- 230000008020 evaporation Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 229920006395 saturated elastomer Polymers 0.000 description 6
- 238000001816 cooling Methods 0.000 description 5
- 239000000203 mixture Substances 0.000 description 5
- 239000011555 saturated liquid Substances 0.000 description 5
- 230000009102 absorption Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000009408 flooring Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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Abstract
The utility model relates to a double heat source type multi-compression high temperature heat pump, wherein an outlet of a low pressure compressor is connected with one port of an intercooler, another port of the intercooler is connected with an air suction port of a high pressure compressor, an outlet of the high pressure compressor is connected with a user-side heat exchanger, a liquid pipeline coming out of the user-side heat exchanger is divided into two paths, one path is connected with a third port of the intercooler through a throttling valve, the other path is connected with a port of a heat source side double heat source heat exchanger through an inner disc pipe of the intercooler and the throttling valve, and a refrigerating fluid port coming out of the heat source side double heat source heat exchanger is connected with an air suction port of the low pressure compressor. The double heat source type multi-compression high temperature heat pump can provide hot water above 75 DEG C for a heating system and the productive technology, and can be widely applied in the heating systems of civil architecture, public building and villa building, and the requirements on high-temperature hot water of industrial production.
Description
Technical field
The utility model relates to the heat pump air conditioner technical field, relate in particular to a kind of utilize simultaneously air, low grade heat energies such as energy be transformed into the double heat source type multi-stage compression formula high temperature heat pump device of the high-grade heat energy that can directly utilize.
Background technology
At present, in most of area, the north of China, the winter heating load is big and the time is long, and the proportion that heating energy consumption accounts for annual energy consumption is bigger, and accounted for leading position in the central heating mode of coal-burning boiler, do not meet the needs of current social energy-saving and environmental protection and sustainable development situation.And conventional single-stage heat pump can only provide and not be higher than 55 ℃ hot water, if adopt air-conditioning draught fan coiled radiator or flooring radiation system can use reluctantly, when adopting radiator to be end-equipment, water temperature will be on the low side.Therefore, in the old heating system of aging blocks is transformed, do not changing the sheet number of original radiator, providing simultaneously under the situation of the domestic water more than 75 ℃, adopting double heat source type multi-stage compression formula high temperature heat pump system will be the selection an of the best.
The utility model content
The purpose of this utility model just providing a kind of can to air, solar energy, regenerative resource such as energy and various waste heat, used heat fully utilize, produce the double heat source type multi-stage compression formula high temperature heat pump of hot water more than 75 ℃.
The purpose of this utility model can realize by following technique measures, but not limit the utility model.
A kind of double heat source type multi-stage compression formula high temperature heat pump device, comprise low pressure compressor, high pressure compressor, the two thermal source heat exchangers of heat source side, the user side heat exchanger, intercooler, choke valve and connecting line, the low pressure compressor outlet is connected with an interface of intercooler, another interface of intercooler is connected with the air entry of high pressure compressor, the outlet of high pressure compressor and user side heat exchanger join, the liquid line that comes out from the user side heat exchanger is divided into two-way, and one the tunnel is connected with the 3rd interface of intercooler through choke valve, and another road is through intercooler inner coil pipe, choke valve is connected with an interface of the two thermal source heat exchangers of heat source side, the cold-producing medium interface that comes out from the two thermal source heat exchangers of heat source side is connected with the air entry of low pressure compressor, and above-mentioned connection all connects by connecting line.
Described low pressure compressor and high pressure compressor are single machine with variable speed type compressor.
Described low pressure compressor and high pressure compressor are the multiple compressors composition.
The two thermal source heat exchangers of described heat source side are the fin-sleeve type three mediums composite heat exchanger, the fin that this heat exchanger comprises outer tube, is installed on the inner sleeve in the outer tube tube chamber and combines with the outer tube outer wall; Described inner sleeve external diameter is less than the aperture of outer tube, and constitutes the heat pump fluid passage by the ring-like space between inner sleeve outer wall and the outer sleeve inner wall, and the tube chamber of inner sleeve constitutes the liquid heat source passage; Constitute the air heat source passage between outer tube outer wall and the fin.
The two thermal source heat exchangers of described heat source side are shell-sleeve type three mediums composite heat-exchanger, and this heat exchanger comprises the closed shell that is provided with medium import and outlet, are encapsulated in the outer heat exchange coil of housing that housing is interior and its two ends extend to respectively; Described heat exchange coil is made up of outer tube and the inner sleeve that is installed in the outer tube tube chamber, and the external diameter of inner sleeve is less than the aperture of outer tube, and constitute the heat pump fluid passage by the annular space between the inwall of the outer wall of inner sleeve and outer tube, the tube chamber of inner sleeve constitutes a liquid heat source passage, and the inwall of housing and the outer wall of outer tube constitute another liquid heat source passage.
The two thermal source heat exchangers of described heat source side are the two thermal source composite heat-exchangers of band solar radiation absorbing coating fin tube type, and this heat exchanger comprises the solar radiation absorbing coating of heat exchanger tube, the fin that combines with the heat exchanger tube outer wall and heat exchange pipe external surface and fin outer surface; Be the heat pump fluid passage in the heat exchanger tube wherein, constitute the air heat source passage between heat exchange pipe external surface and the fin.
Double heat source type multi-stage compression formula high temperature heat pump device of the present utility model can be heating system and production technology hot water more than 75 ℃ is provided, and can be widely used in the heating system and the industrial high-temperature-hot-water demand of civil buildings, public building, villa buildings.
Description of drawings
Fig. 1 is the structure principle chart of the utility model embodiment 1.
Fig. 2 is the structure principle chart of the utility model embodiment 2.
Fig. 3 is the structure principle chart of the utility model embodiment 3.
Fig. 4 is the structure principle chart of the utility model embodiment 4.
Fig. 5 is the utility model fin-sleeve type three mediums composite heat exchanger structural representation.
Fig. 6 is the utility model shell-sleeve type three-medium composite heat exchanger structural representation.
Fig. 7 is the utility model fin-sleeve type three mediums composite heat exchanger structural representation.
The specific embodiment
The utility model is further described below with reference to accompanying drawing, but does not limit the utility model:
As shown in Figure 5, fin-sleeve type three mediums composite heat exchanger, the fin 7 that comprises outer tube 6, is installed on the inner sleeve 10 in the outer tube tube chamber and combines with the outer tube outer wall; Described inner sleeve 10 external diameters are less than the aperture of outer tube 6, and constitute heat pump fluid passage 8 by the ring-like space between inner sleeve 10 outer walls and outer tube 6 inwalls, and the tube chamber of inner sleeve constitutes liquid heat source passage 11; Constitute air heat source passage 9 between outer tube outer wall and the fin.
As shown in Figure 6, shell-sleeve type three-medium composite heat exchanger comprises the closed shell 15 that is provided with medium import and outlet, outside the housing that heat exchange coil is encapsulated in the housing and its two ends extend to respectively; Described heat exchange coil is made up of outer tube 16 and the inner sleeve 17 that is installed in the outer tube tube chamber, and the external diameter of inner sleeve 17 is less than the aperture of outer tube 16, and constitute the heat pump fluid passage by the annular space between the inwall of the outer wall of inner sleeve 17 and outer tube 16, the tube chamber of inner sleeve constitutes a liquid heat source passage 14, and the outer wall of the inwall of housing 15 and outer tube 16 constitutes another liquid heat source passage 12.
As shown in Figure 7, be with the two thermal source composite heat-exchangers of solar radiation absorbing coating fin tube type, comprise the solar radiation absorbing coating of heat exchanger tube 18, the fin 19 that combines with the heat exchanger tube outer wall and heat exchange pipe external surface and fin outer surface; Be heat pump fluid passage 20 in the heat exchanger tube 18 wherein, constitute air heat source passage 21 between heat exchanger tube 18 outer surfaces and the fin 19.
Workflow is as follows: (1) single gaseous state heat source models.Under this mode of operation, the two thermal source heat exchangers 2 of heat source side are the fin-sleeve type three mediums composite heat exchanger.
Low-pressure steam is sucked and is compressed to intermediate pressure by low pressure compressor 1, enter intercooler 4, arrived and the corresponding saturation temperature of intermediate pressure by the evaporative cooling of liquid refrigerant therein, enter high pressure compressor 1 ' further compression again, be divided into two-way after entering user side heat exchanger 3 release heat then, one the tunnel enters intercooler 4 heat absorptions after choke valve 5 ' throttling, the exhaust of cooling low pressure compressor 1 and the highly pressurised liquid in intercooler 4 coil pipes, another road enters the two thermal source heat exchangers 2 of heat source side through the inner coil pipe and the choke valve 5 of intercooler 4, evaporation enters after absorbing gaseous state thermal source heat, enters low pressure compressor 1 and enters next circulation.
(2) single liquid heat source pattern.Under this mode of operation, the two thermal source heat exchangers 2 of heat source side are fin-sleeve type three mediums composite heat exchanger or shell-sleeve type three mediums composite heat-exchanger.
This mode of operation is compared with single gaseous state heat source models, and its difference is: the process choke valve enters the cold-producing medium of the two thermal source heat exchangers 2 of heat source side, and what evaporation absorbed is the heat of single liquid heat source.
(3) the two heat source models of gaseous state-liquid state.Under this mode of operation, the two thermal source heat exchangers 2 of heat source side are fin-sleeve type three mediums composite heat exchanger.
This mode of operation is compared with single gaseous state heat source models, and its difference is: the process choke valve enters the cold-producing medium of the two thermal source heat exchangers 2 of heat source side, and what evaporation absorbed is the heat of gaseous state and the two thermals source of liquid state.
(4) biliquid attitude heat source models.Under this mode of operation, the two thermal source heat exchangers 2 of heat source side are shell-sleeve type three-medium composite heat exchanger.
This mode of operation is compared with single gaseous state heat source models, and its difference is: the process choke valve enters the cold-producing medium of heat source side heat exchanger 2, and what evaporation absorbed is the heat of biliquid attitude thermal source.
(5) the two heat source models of solar energy-air.Under this mode of operation, the two thermal source heat exchangers 2 of heat source side are the two thermal source composite heat-exchangers of band solar radiation absorbing coating fin tube type.
This mode of operation is compared its difference with single gaseous state heat source models and is: the process choke valve enters the cold-producing medium of heat source side heat exchanger 2, and what evaporation absorbed is the heat of solar energy and two kinds of thermals source of air.
Other are with embodiment 1.
Other are with embodiment 1.
Other are with embodiment 1.
Claims (6)
1. double heat source type multi-stage compression formula high temperature heat pump device, comprise low pressure compressor (1), high pressure compressor (1 '), the two thermal source heat exchangers (2) of heat source side, user side heat exchanger (3), intercooler (4), choke valve and connecting line, it is characterized in that: low pressure compressor (1) outlet is connected with an interface of intercooler (4), another interface of intercooler (4) is connected with the air entry of high pressure compressor (1 '), the outlet of high pressure compressor (1 ') and user side heat exchanger (3) join, the liquid line that comes out from user side heat exchanger (3) is divided into two-way, one the tunnel is connected with the 3rd interface of intercooler (4) through choke valve (5 '), another road is through intercooler (4) inner coil pipe, choke valve (5) is connected with an interface of the two thermal source heat exchangers (2) of heat source side, the cold-producing medium interface that comes out from the two thermal source heat exchangers (2) of heat source side is connected with the air entry of low pressure compressor (1), and above-mentioned connection all connects by connecting line.
2. double heat source type multi-stage compression formula high temperature heat pump according to claim 1 is characterized in that: described low pressure compressor (1) and high pressure compressor (1 ') are single machine with variable speed type compressor.
3. double heat source type multi-stage compression formula high temperature heat pump according to claim 1 is characterized in that: described low pressure compressor (1) and high pressure compressor (1 ') are that multiple compressors forms.
4. double heat source type multi-stage compression formula high temperature heat pump according to claim 1, it is characterized in that: the two thermal source heat exchangers (2) of described heat source side are the fin-sleeve type three mediums composite heat exchanger, the fin (7) that this heat exchanger comprises outer tube (6), is installed on the inner sleeve (10) in the outer tube tube chamber and combines with the outer tube outer wall; Described inner sleeve (10) external diameter is less than the aperture of outer tube (6), and by the ring-like space formation heat pump fluid passage (8) between inner sleeve (10) outer wall and outer tube (6) inwall, the tube chamber of inner sleeve constitutes liquid heat source passage (11); Constitute air heat source passage (9) between outer tube outer wall and the fin.
5. double heat source type multi-stage compression formula high temperature heat pump according to claim 1, it is characterized in that: the two thermal source heat exchangers (2) of described heat source side are shell-sleeve type three mediums composite heat-exchanger, this heat exchanger comprises the closed shell (15) that is provided with medium import and outlet, is encapsulated in the outer heat exchange coil of housing that housing is interior and its two ends extend to respectively; Described heat exchange coil is made up of outer tube (16) and the inner sleeve (17) that is installed in the outer tube tube chamber, and the external diameter of inner sleeve (17) is less than the aperture of outer tube (16), and constitute the heat pump fluid passage by the annular space between the inwall of the outer wall of inner sleeve (17) and outer tube (16), the tube chamber of inner sleeve constitutes a liquid heat source passage (14), and the outer wall of the inwall of housing (15) and outer tube (16) constitutes another liquid heat source passage (12).
6. double heat source type single stage compress formula high temperature heat pump according to claim 1, it is characterized in that: the two thermal source heat exchangers (2) of described heat source side are for the two thermal source composite heat-exchangers of band solar radiation absorbing coating fin tube type, this heat exchanger comprises heat exchanger tube (18), the fin (19) that combines with the heat exchanger tube outer wall and the solar radiation absorbing coating of heat exchange pipe external surface and fin outer surface; Be heat pump fluid passage (20) in the heat exchanger tube (18) wherein, constitute air heat source passage (21) between heat exchanger tube (18) outer surface and the fin (19).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205477758U CN201811498U (en) | 2010-09-29 | 2010-09-29 | A dual heat source type multistage compression high temperature heat pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205477758U CN201811498U (en) | 2010-09-29 | 2010-09-29 | A dual heat source type multistage compression high temperature heat pump |
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| CN201811498U true CN201811498U (en) | 2011-04-27 |
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| CN2010205477758U Expired - Fee Related CN201811498U (en) | 2010-09-29 | 2010-09-29 | A dual heat source type multistage compression high temperature heat pump |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103075807A (en) * | 2013-01-15 | 2013-05-01 | 顺德职业技术学院 | Coupling intercooler for two-stage compression heat pump water heater |
| CN103322714A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Single-throttling two-stage compression refrigerating system |
| CN103322715A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Single-throttling complete-inter-cooling dual-working-condition refrigerating system |
| CN103322713A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Four-cycle double-stage compression refrigeration system |
| CN104114959A (en) * | 2011-12-23 | 2014-10-22 | Gea博客有限公司 | Compressor |
| CN104329821A (en) * | 2013-07-22 | 2015-02-04 | 刘雄 | Air conditioning refrigeration equipment and control method thereof |
| CN106766306A (en) * | 2016-11-29 | 2017-05-31 | 天津商业大学 | A kind of double stage compresses hot pump in low temp system |
| CN107036319A (en) * | 2016-02-04 | 2017-08-11 | 松下知识产权经营株式会社 | Refrigerating circulatory device |
| CN111306840A (en) * | 2019-02-15 | 2020-06-19 | 李华玉 | Multidirectional thermodynamic cycle |
| CN112752934A (en) * | 2018-09-28 | 2021-05-04 | 大金工业株式会社 | Multi-stage compression system |
| CN114131371A (en) * | 2021-12-02 | 2022-03-04 | 大连理工大学 | Ice clamping system based on split type compression refrigeration |
-
2010
- 2010-09-29 CN CN2010205477758U patent/CN201811498U/en not_active Expired - Fee Related
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104114959A (en) * | 2011-12-23 | 2014-10-22 | Gea博客有限公司 | Compressor |
| CN103075807A (en) * | 2013-01-15 | 2013-05-01 | 顺德职业技术学院 | Coupling intercooler for two-stage compression heat pump water heater |
| CN103075807B (en) * | 2013-01-15 | 2015-04-29 | 顺德职业技术学院 | Coupling intercooler for two-stage compression heat pump water heater |
| CN103322714A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Single-throttling two-stage compression refrigerating system |
| CN103322715A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Single-throttling complete-inter-cooling dual-working-condition refrigerating system |
| CN103322713A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Four-cycle double-stage compression refrigeration system |
| CN103322715B (en) * | 2013-07-04 | 2015-04-08 | 天津商业大学 | Single-throttling complete-inter-cooling dual-working-condition refrigerating system |
| CN104329821A (en) * | 2013-07-22 | 2015-02-04 | 刘雄 | Air conditioning refrigeration equipment and control method thereof |
| EP3203164B1 (en) | 2016-02-04 | 2021-04-14 | Panasonic Intellectual Property Management Co., Ltd. | Refrigeration cycle apparatus |
| CN107036319A (en) * | 2016-02-04 | 2017-08-11 | 松下知识产权经营株式会社 | Refrigerating circulatory device |
| CN107036319B (en) * | 2016-02-04 | 2020-10-02 | 松下知识产权经营株式会社 | Refrigeration cycle device |
| CN106766306A (en) * | 2016-11-29 | 2017-05-31 | 天津商业大学 | A kind of double stage compresses hot pump in low temp system |
| CN112752934A (en) * | 2018-09-28 | 2021-05-04 | 大金工业株式会社 | Multi-stage compression system |
| CN112752934B (en) * | 2018-09-28 | 2022-03-01 | 大金工业株式会社 | Multistage compression system |
| CN111306840A (en) * | 2019-02-15 | 2020-06-19 | 李华玉 | Multidirectional thermodynamic cycle |
| CN114131371A (en) * | 2021-12-02 | 2022-03-04 | 大连理工大学 | Ice clamping system based on split type compression refrigeration |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110427 Termination date: 20120929 |