CN101256042A - Large temperature rise compression heat pump units - Google Patents
Large temperature rise compression heat pump units Download PDFInfo
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- CN101256042A CN101256042A CNA2008101042006A CN200810104200A CN101256042A CN 101256042 A CN101256042 A CN 101256042A CN A2008101042006 A CNA2008101042006 A CN A2008101042006A CN 200810104200 A CN200810104200 A CN 200810104200A CN 101256042 A CN101256042 A CN 101256042A
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Abstract
The invention pertains to heating and hot water supply field, relating to a high efficiency large temperature rise compression heat pump set with a big inlet-outlet temperature difference at both a heat sink side and a head source side. The large temperature rise compression heat pump set is configured by assembling two water source heat pump devices, and each heat pump set comprises separately in series or in parallel a compressor, a condenser, an evaporator, a subcooler, and a throttling device, or an added economizer, and forms a separate working medium circulation loop. The inventive large temperature rise compression heat pump set can heat returned hot water step by step from a low temperature to a high temperature, the cold water is cooled step by step in a reverse direction of the temperature rise of the cooling water, and temperature difference between the hot water and cold water at the inlet and outlet of the heat pump is enlarged; and the performance coefficient of the heat pump set is further enhanced comparing with a simple two-stage compression heat pump in series, so that the comprehensive energy utilization efficiency and economy of the inventive system are increased greatly comparing with a common heat pump set.
Description
Technical field
The invention belongs to the device of heating, heat supply water, particularly can all obtain a kind of unit of large temperature rise compression heat pump efficiently of the big import and export temperature difference at hot and cold source.
Background technology
Along with reaching its maturity of heat pump techniques, various underground water, surface water or the industrial waste waters etc. of utilizing have been widely used in various heating and the hot water supply system for the heat pump techniques of low-temperature heat source.The coefficient of performance of source pump just is the key factor of decision efficiency of energy utilization.For heat pump assembly commonly used, the method of operation of " the big temperature difference, the low discharge " taked usually is under the certain situation of inflow temperature, can cause the rising of hot water supply water temperature and the reduction of cold water leaving water temperature, thereby cause the rising of condensing pressure and the reduction of evaporating pressure, cause systematic function coefficient (COP) to reduce, efficiency of energy utilization reduces.
Summary of the invention
The purpose of this invention is to provide a kind of large temperature rise compression heat pump unit, it is characterized in that, adopt the mode of many water resource heat pump equipment combinations, be that every source pump is made up of independent compressor C, condenser K, evaporimeter E, subcooler S, throttling arrangement VC, form independent working medium closed circuit respectively.Connect compressor C1 between first order condenser K1 and the evaporimeter E1, and subcooler S1, throttling arrangement VC1 series connection back is in parallel with compressor C1, connect compressor C2 between second level condenser K2 and the evaporimeter E2, and subcooler S2, throttling arrangement VC2 series connection back is in parallel with compressor C2; Low-temperature water heating by subcooler S1, subcooler S2, first order condenser K1 and the second level condenser K2 pipeline of series connection, is exported high-temperature-hot-water successively; Cold-water return by the evaporimeter E2 and the evaporimeter E1 pipeline of series connection, is exported low-temperature cold water successively; Share a water system, form the large temperature rise compression heat pump unit.
Described hot water line also is that subcooler S1, subcooler S2, first order condenser K1 connect with second level condenser K2 after parallel with one another again.
The described economizer G1 that between subcooler S1, throttling arrangement VC1, connects.
The described economizer G2 that between subcooler S2, throttling arrangement VC2, connects.
Cross a cold-producing medium subcooled liquid part after the cold throttling arrangement (Vg1 or Vg2) of flowing through through subcooler (S1 or S2), make all the other cold-producing mediums cold excessively, the refrigerant gas of evaporation enters the intergrade recompression of compressor (C1 or C2), and cold excessively refrigerant liquid enters evaporimeter (E1 or E2) by throttling arrangement (VC1 or VC2).The use of economizer, make compressor increase an additional compression process, the refrigerant gas that the economizer flash distillation is come out enters the middle pressure suction muffler of compressor as the tonifying Qi process of helical-lobe compressor, because gas air inlet after air entry complete closed of compressor low pressure of pressing the secondary suction chamber to cover in the screw compressor, therefore, compare with conventional heat pump, former inspiratory capacity is constant, and the gross exhaust gas of compressor has increased, so the heating capacity of unit must increase.The use of economizer has improved the coefficient of performance of unit.
Biggest advantage of the present invention is: lower hot water backwater's step can be heated to higher temperature, cold water is then according to the direction step cooling opposite with the cooling water intensification, strengthened hot water and cold water the temperature difference, made it by the big temperature difference, low discharge operation at the heat pump import and export; Compare with simple two-stage series connection compression heat pump simultaneously, the coefficient of performance of source pump has had further raising, so the system synthesis efficiency of energy utilization improves than ordinary hot pump assembly greatly with economy.The improvement of improved two-stage series connection compression heat pump unit performance is mainly reflected in: one, cooling water intensification direction is opposite with the cooling direction of chilled water, reduced the temperature difference of evaporimeter and condenser, reduced irreversible heat transfer loss, the coefficient of performance of unit integral body is improved; Two, the mode of employing two-stage series connection can be chosen different heat pump units according to the operating mode of different temperature rise sections, guarantees that every compressor moves under its efficient operating mode; Three, cold-producing medium does not carry out blending between the two-stage, and form is simple relatively, has fundamentally solved the oil return problem in the cold-producing medium blending; Four, the cold water temperature step reduces, and hot water temperature's step raises, and has reduced the heat transfer temperature difference of evaporation ends and condensation end, has reduced irreversible heat transfer loss; Five, the confession of chilled water and cooling water, backwater temperature difference increase, and have reduced the transmission ﹠ distribution energy consumption and the pipe network system investment of system.
Description of drawings
Fig. 1 (a) and (b) are the schematic flow sheet that two-stage series connection of the present invention added cold compression type heat pump assembly.
Fig. 2 added schematic flow sheet cold and economizer compression type heat pump assembly for two-stage series connection of the present invention.
Symbol among the figure: K-condenser; The E-evaporimeter; The C-compressor; VC-enters the cryogen throttling arrangement of evaporator inlet; The G-economizer; Vg-economizer throttling arrangement;
The specific embodiment
The invention provides a kind of large temperature rise compression heat pump unit.This compression type heat pump assembly adopts the mode of many water resource heat pump equipment combinations, and promptly every source pump is made up of independent compressor C, condenser K, evaporimeter E, subcooler S, throttling arrangement VC, forms independent working medium closed circuit respectively.Below in conjunction with accompanying drawing the specific embodiment of the present invention is described.
The series connection of embodiment one two-stage added cold compression type heat pump assembly
Shown in Fig. 1 (a), connect compressor C1 between first order condenser K1 and the evaporimeter E1, and subcooler S1, throttling arrangement VC1 series connection back is in parallel with compressor C1, connect compressor C2 between second level condenser K2 and the evaporimeter E2, and subcooler S2, throttling arrangement VC2 series connection back is in parallel with compressor C2; 40 ℃ of hot water backwaters enter subcooler S1 from the hot water inlet of subcooler S1, the subcooler S1 that flows through successively, and subcooler S2, condenser K1 and condenser K2, by condenser K2 hot water outlet output high-temperature-hot-water, the hot water temperature is at 50-55 ℃ by condensed in two stages device heating back.25 ℃ of cold-water return evaporimeter E2 and evaporimeter E1 10 ℃ of cold water of back output of lowering the temperature step by step of flowing through successively.Realize that the hot water step heats up, cold water is the step cooling in the two-stage evaporation device, and condensing pressure and evaporating pressure adapt with separately hot and cold water temperature respectively, thereby has reduced the irreversible heat transfer loss in evaporimeter and the condenser, and system effectiveness is improved.
Embodiment two two-stage series connections added cold compression type heat pump assembly
Shown in Fig. 1 (b), source pump basic structure is identical with embodiment 1, and its difference is that the hot water line is that subcooler S1, subcooler S2, first order condenser K1 connect with second level condenser K2 after parallel with one another again.40 ℃ of hot water backwaters through subcooler S1, subcooler S2, first order condenser K1 loop parallel with one another after, again through second level condenser K2, heating back output higher temperature hot water, the hot water temperature is at 50-55 ℃.25 ℃ of cold-water return evaporimeter E2 and evaporimeter E1 10 ℃ of cold water of back output of lowering the temperature step by step of flowing through successively.Realize that the hot water step heats up, cold water is the step cooling in the two-stage evaporation device, and condensing pressure and evaporating pressure adapt with separately hot and cold water temperature respectively, thereby has reduced the irreversible heat transfer loss in evaporimeter and the condenser, and system effectiveness is improved.
Embodiment three two-stage series connections added cold and economizer compression type heat pump assembly
In order further to improve the coefficient of performance of compression type heat pump assembly, as shown in Figure 2, source pump is combined by two heat pump units, and its basic structure is identical with embodiment 2, its difference is, economizer G1 of series connection between subcooler S1, throttling arrangement VC1; Economizer G2 of series connection between subcooler S2, throttling arrangement VC2.40 ℃ of hot water backwaters through subcooler S1, subcooler S2, first order condenser K1 loop parallel with one another after, again through second level condenser K2, be heated back output higher temperature hot water, the hot water temperature is at 50-55 ℃.25 ℃ of cold-water return evaporimeter E2 and evaporimeter E1 10 ℃ of cold water of back output of lowering the temperature step by step of flowing through successively.Realize that the hot water step heats up, cold water is the step cooling in the two-stage evaporation device, and condensing pressure and evaporating pressure adapt with separately hot and cold water temperature respectively, thereby has reduced the irreversible heat transfer loss in evaporimeter and the condenser, and system effectiveness is improved.
In economizer (G1 or G2), cold-producing medium subcooled liquid part after subcooler (S1 or S2) is cold excessively is through throttling arrangement (Vg1 or Vg2), make all the other cold-producing mediums cold excessively, the refrigerant gas of evaporation enters the intergrade recompression of compressor (C1 or C2), and cold excessively refrigerant liquid enters evaporimeter (E1 or E2) by throttling arrangement (VC1 or VC2).The use of economizer has improved the coefficient of performance of unit.
Claims (4)
1. large temperature rise compression heat pump unit, it is characterized in that, adopt the mode of many water resource heat pump equipment combinations, promptly every source pump is made up of independent compressor C, condenser K, evaporimeter E, subcooler S, throttling arrangement VC, forms independent working medium closed circuit respectively; Connect compressor C1 between first order condenser K1 and the evaporimeter E1, and subcooler S1, throttling arrangement VC1 series connection back is in parallel with compressor C1, connect compressor C2 between second level condenser K2 and the evaporimeter E2, and subcooler S2, throttling arrangement VC2 series connection back is in parallel with compressor C2; Low-temperature water heating by subcooler S1, subcooler S2, first order condenser K1 and the second level condenser K2 pipeline of series connection, is exported high-temperature-hot-water successively; Cold-water return by the evaporimeter E2 and the evaporimeter E1 pipeline of series connection, is exported low-temperature cold water successively; Share a water system, form the large temperature rise compression heat pump unit.
2. according to the described large temperature rise compression heat pump unit of claim 1, it is characterized in that described hot water line is that subcooler S1, subcooler S2, first order condenser K1 connect with second level condenser K2 after parallel with one another again.
3. according to the described large temperature rise compression heat pump unit of claim 1, it is characterized in that the described economizer G1 that between subcooler S1, throttling arrangement VC1, also connects.
4. according to the described large temperature rise compression heat pump unit of claim 1, it is characterized in that the described economizer G2 that between subcooler S2, throttling arrangement VC2, also connects.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008101042006A CN101256042A (en) | 2008-04-16 | 2008-04-16 | Large temperature rise compression heat pump units |
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| CNA2008101042006A CN101256042A (en) | 2008-04-16 | 2008-04-16 | Large temperature rise compression heat pump units |
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Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102022870A (en) * | 2010-12-09 | 2011-04-20 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| CN102080856A (en) * | 2010-12-08 | 2011-06-01 | 海尔集团公司 | Heat exchange system and central air-conditioning system and heat exchange method thereof |
| CN101619904B (en) * | 2009-08-02 | 2013-04-10 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
| CN103105016A (en) * | 2011-11-09 | 2013-05-15 | 高亚民 | Double working medium cascading directly-heated type heat pump hot water unit |
| CN106352586A (en) * | 2016-10-13 | 2017-01-25 | 南京工程学院 | Double machine head heat source tower heat pump unit |
| CN106766307A (en) * | 2016-12-20 | 2017-05-31 | 江苏世林博尔制冷设备有限公司 | A kind of water-cooling screw rod machine two-shipper group water route series connection, fluorine pass by cold combined system |
| CN111189099A (en) * | 2019-12-19 | 2020-05-22 | 陕西省煤田地质集团有限公司 | Efficient heating system for ground heating engineering for developing and utilizing pumping and filling type geothermal water |
| CN112648733A (en) * | 2020-12-16 | 2021-04-13 | 上海交通大学 | Graded partial pressure modular heat energy lifting system and control method thereof |
| WO2021103543A1 (en) * | 2019-11-29 | 2021-06-03 | 青岛海尔空调电子有限公司 | Multi-head cooling water unit |
| CN113646598A (en) * | 2019-02-27 | 2021-11-12 | 江森自控泰科知识产权控股有限责任合伙公司 | Condenser arrangement for a cooler |
| CN114738729A (en) * | 2022-04-18 | 2022-07-12 | 湖南麦思克科技有限公司 | Boiler feed water heating method and system |
| CN114909823A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Compression heat pump set |
| CN114909822A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Condenser parallel gas heat pump type steam unit |
| CN114909826A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Compression type steam unit |
| CN114909825A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Multi-evaporator gas heat pump type steam unit |
| CN114909824A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Condenser parallel compression steam unit |
-
2008
- 2008-04-16 CN CNA2008101042006A patent/CN101256042A/en active Pending
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101619904B (en) * | 2009-08-02 | 2013-04-10 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
| CN102080856A (en) * | 2010-12-08 | 2011-06-01 | 海尔集团公司 | Heat exchange system and central air-conditioning system and heat exchange method thereof |
| CN102022870B (en) * | 2010-12-09 | 2014-02-19 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| CN102022870A (en) * | 2010-12-09 | 2011-04-20 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| CN103105016A (en) * | 2011-11-09 | 2013-05-15 | 高亚民 | Double working medium cascading directly-heated type heat pump hot water unit |
| CN106352586A (en) * | 2016-10-13 | 2017-01-25 | 南京工程学院 | Double machine head heat source tower heat pump unit |
| CN106766307A (en) * | 2016-12-20 | 2017-05-31 | 江苏世林博尔制冷设备有限公司 | A kind of water-cooling screw rod machine two-shipper group water route series connection, fluorine pass by cold combined system |
| CN113646598A (en) * | 2019-02-27 | 2021-11-12 | 江森自控泰科知识产权控股有限责任合伙公司 | Condenser arrangement for a cooler |
| WO2021103543A1 (en) * | 2019-11-29 | 2021-06-03 | 青岛海尔空调电子有限公司 | Multi-head cooling water unit |
| CN111189099B (en) * | 2019-12-19 | 2022-01-28 | 陕西省煤田地质集团有限公司 | Efficient heating system for ground heating engineering for developing and utilizing pumping and filling type geothermal water |
| CN111189099A (en) * | 2019-12-19 | 2020-05-22 | 陕西省煤田地质集团有限公司 | Efficient heating system for ground heating engineering for developing and utilizing pumping and filling type geothermal water |
| CN112648733A (en) * | 2020-12-16 | 2021-04-13 | 上海交通大学 | Graded partial pressure modular heat energy lifting system and control method thereof |
| CN114909823A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Compression heat pump set |
| CN114909822A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Condenser parallel gas heat pump type steam unit |
| CN114909826A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Compression type steam unit |
| CN114909825A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Multi-evaporator gas heat pump type steam unit |
| CN114909824A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调***有限公司 | Condenser parallel compression steam unit |
| CN114738729A (en) * | 2022-04-18 | 2022-07-12 | 湖南麦思克科技有限公司 | Boiler feed water heating method and system |
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Open date: 20080903 |