CN101625176B - Quasi three-stage compressed air source heat pump system - Google Patents
Quasi three-stage compressed air source heat pump system Download PDFInfo
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- CN101625176B CN101625176B CN2009100699570A CN200910069957A CN101625176B CN 101625176 B CN101625176 B CN 101625176B CN 2009100699570 A CN2009100699570 A CN 2009100699570A CN 200910069957 A CN200910069957 A CN 200910069957A CN 101625176 B CN101625176 B CN 101625176B
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- 239000007788 liquid Substances 0.000 claims abstract description 53
- 239000003507 refrigerant Substances 0.000 claims abstract description 44
- 238000010438 heat treatment Methods 0.000 abstract description 10
- 230000006835 compression Effects 0.000 abstract description 3
- 238000007906 compression Methods 0.000 abstract description 3
- 230000001502 supplementing effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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Abstract
Description
技术领域technical field
本发明涉及一种空气源热泵系统，更具体的说，是涉及一种准三级压缩空气源热泵系统。The invention relates to an air source heat pump system, more specifically, relates to a quasi-three-stage compressed air source heat pump system.
背景技术Background technique
目前，压缩空气源热泵系统一般为双级。普通的双级压缩空气源热泵在冬季运行时，在冷凝温度不变的情况下，当室外环境温度下降时，随着吸气比容的增加，压比增加，排气压力增加，比功增加，单位容积制冷量减小，机组制热量和制热性能系数都减小，影响机组的稳定运行。At present, the compressed air source heat pump system is generally two-stage. When the ordinary two-stage compressed air source heat pump is running in winter, when the condensing temperature remains unchanged, when the outdoor ambient temperature drops, as the suction specific volume increases, the pressure ratio increases, the exhaust pressure increases, and the specific power increases. , the cooling capacity per unit volume decreases, the heating capacity and heating coefficient of performance of the unit decrease, which affects the stable operation of the unit.
发明内容Contents of the invention
本发明是为了克服现有技术中的不足之处，提供一种能够提高空气源热泵的制热量，扩大空气源热泵的应用范围，降低能耗的准三级压缩空气源热泵系统。The present invention aims to overcome the deficiencies in the prior art and provide a quasi-three-stage compressed air source heat pump system capable of increasing the heating capacity of the air source heat pump, expanding the application range of the air source heat pump, and reducing energy consumption.
本发明通过下述技术方案实现：The present invention realizes through following technical scheme:
一种准三级压缩空气源热泵系统，其特征在于，包括低压级压缩机、高压级压缩机、低压级四通阀、高压级四通阀、室外换热器、室内换热器、高压储液器、闪蒸器、气液分离器、中间冷却器，低压级四通阀的第一接口与低压级压缩机的出口连接，低压级四通阀的第二接口与室外换热器的出口连接，低压级四通阀的第三接口与气液分离器的进口连接，低压级四通阀的第四接口与高压级四通阀的第三接口连接，高压级四通阀的第一接口与高压级压缩机的出口连接，高压级四通阀的第二接口与中间冷却器的中温中压制冷剂出口并联后与高压级压缩机的进口连接，高压级四通阀的第四接口与室内换热器的进口连接，室内换热器的出口一路通过第二单向阀与高压储液器的进口连接，室内换热器的出口另一路与第二电子膨胀阀的进口连接，高压储液器的高压液体出口一路与中间冷却器的高温高压制冷剂进口连接，高压储液器的高压液体出口另一路通过第三电子膨胀阀与中间冷却器的中温中压制冷剂进口连接，中间冷却器的高温高压制冷剂出口与一路与闪蒸器的进口连接，中间冷却器的高温高压制冷剂出口另一路与截止阀的进口连接，截止阀的出口与闪蒸器的液体出口并联后再与第二电子膨胀阀的出口并联后与第一电子膨胀阀的进口连接，第一电子膨胀阀的出口一路与室外换热器的进口连接，第一电子膨胀阀的出口另一路通过第一单向阀与高压储液器的进口连接，闪蒸器的气体出口与低压级压缩机的补气口连接，气液分离器的排气接口与低压级压缩机的进口连接。A quasi-three-stage compressed air source heat pump system is characterized in that it includes a low-pressure stage compressor, a high-pressure stage compressor, a low-pressure stage four-way valve, a high-pressure stage four-way valve, an outdoor heat exchanger, an indoor heat exchanger, and a high-pressure storage Liquid tank, flash evaporator, gas-liquid separator, intercooler, the first port of the low-pressure stage four-way valve is connected to the outlet of the low-pressure stage compressor, and the second port of the low-pressure stage four-way valve is connected to the outlet of the outdoor heat exchanger , the third port of the low-pressure stage four-way valve is connected to the inlet of the gas-liquid separator, the fourth port of the low-pressure stage four-way valve is connected to the third port of the high-pressure stage four-way valve, and the first port of the high-pressure stage four-way valve is connected to the The outlet of the high-pressure stage compressor is connected, the second port of the high-pressure stage four-way valve is connected in parallel with the medium-temperature and medium-pressure refrigerant outlet of the intercooler, and then connected to the inlet of the high-pressure stage compressor, the fourth port of the high-pressure stage four-way valve is connected to the indoor The inlet of the heat exchanger is connected, the outlet of the indoor heat exchanger is connected to the inlet of the high-pressure liquid storage through the second one-way valve, and the other outlet of the indoor heat exchanger is connected to the inlet of the second electronic expansion valve, and the high-pressure liquid storage One way of the high-pressure liquid outlet of the intercooler is connected to the high-temperature and high-pressure refrigerant inlet of the intercooler, and the other way of the high-pressure liquid outlet of the high-pressure liquid receiver is connected to the medium-temperature and medium-pressure refrigerant inlet of the intercooler through the third electronic expansion valve. The outlet of the high-temperature and high-pressure refrigerant is connected to the inlet of the flash evaporator, and the other outlet of the high-temperature and high-pressure refrigerant of the intercooler is connected to the inlet of the shut-off valve. The outlet of the expansion valve is connected in parallel with the inlet of the first electronic expansion valve, one way of the outlet of the first electronic expansion valve is connected with the inlet of the outdoor heat exchanger, and the other outlet of the first electronic expansion valve passes through the first one-way valve and the high pressure The inlet of the liquid receiver is connected, the gas outlet of the flash evaporator is connected to the gas supply port of the low-pressure compressor, and the exhaust port of the gas-liquid separator is connected to the inlet of the low-pressure compressor.
在高压储液器的液体出口与干燥过滤器进口连接，干燥过滤器出口一路与中间冷却器的高温高压制冷剂进口连接，干燥过滤器出口另一路通过第三电子膨胀阀与中间冷却器的中温中压制冷剂进口连接。The liquid outlet of the high-pressure liquid receiver is connected to the inlet of the dry filter, the outlet of the dry filter is connected to the high-temperature and high-pressure refrigerant inlet of the intercooler, and the other outlet of the dry filter passes through the third electronic expansion valve and the intermediate temperature of the intercooler. Medium pressure refrigerant inlet connection.
在中间冷却器的中温中压制冷剂进口与高压储液器的高压液体出口之间连接有电磁阀。A solenoid valve is connected between the medium-temperature and medium-pressure refrigerant inlet of the intercooler and the high-pressure liquid outlet of the high-pressure accumulator.
本发明具有下述技术效果：The present invention has following technical effect:
本发明的热泵系统，在低压级压缩部分增加了一个由闪蒸器构成的补气系统用于热泵制热时补气。由闪蒸器出来的得到充分过冷饱和的气体，其温度明显低于压缩机吸气口气体温度，与气液分离器中的气体混合后，温度明显降低，降低了压缩机的排气温度，即使在环境温度极低的情况下，仍能有效的提高制热量，提高系统的COP，可以有效改进空气源热泵在环境温度较低的工况下的工作性能，扩大了空气源热泵的使用范围，降低了能耗。In the heat pump system of the present invention, an air supply system composed of a flash evaporator is added to the compression part of the low-pressure stage to supply air when the heat pump is heating. The temperature of the fully subcooled and saturated gas from the flasher is significantly lower than the gas temperature at the compressor suction port. After mixing with the gas in the gas-liquid separator, the temperature is significantly lowered, which reduces the exhaust temperature of the compressor. Even in the case of extremely low ambient temperature, it can still effectively increase the heating capacity and improve the COP of the system, which can effectively improve the working performance of the air source heat pump under the condition of low ambient temperature, and expand the application range of the air source heat pump , reducing energy consumption.
附图说明Description of drawings
图1为本发明准三级压缩空气源热泵系统的示意图。Fig. 1 is a schematic diagram of a quasi-three-stage compressed air source heat pump system of the present invention.
具体实施方式Detailed ways
以下结合附图和具体实施例对本发明详细说明。The present invention will be described in detail below in conjunction with the accompanying drawings and specific embodiments.
图1为本发明准三级压缩空气源热泵系统的示意图，包括低压级压缩机1、高压级压缩机2、低压级四通阀3、高压级四通阀4、室外换热器5、室内换热器6、高压储液器9、闪蒸器8、气液分离器7、中间冷却器10，低压级四通阀3的第一接口19与低压级压缩机的出口连接，低压级四通阀的第二接口20与室外换热器5的出口连接，低压级四通阀的第三接口21与气液分离器7的进口连接，低压级四通阀的第四接口22与高压级四通阀4的第三接口25连接，高压级四通阀的第一接口23与高压级压缩机2的出口连接，高压级四通阀的第二接口24与中间冷却器10的中温中压制冷剂出口并联后与高压级压缩机的进口连接，高压级四通阀的第四接口26与室内换热器6的进口连接，室内换热器6的出口一路通过第二单向阀16与高压储液器9的进口连接，室内换热器6的出口另一路与第二电子膨胀阀13的进口连接，高压储液器9的高压液体出口一路与中间冷却器10的高温高压制冷剂进口连接，高压储液器9的高压液体出口另一路通过第三电子膨胀阀14与中间冷却器10的中温中压制冷剂进口连接，中间冷却器10的高温高压制冷剂出口与一路与闪蒸器8的进口连接，中间冷却器的高温高压制冷剂出口另一路与截止阀18的进口连接，截止阀18的出口与闪蒸器8的液体出口并联后再与第二电子膨胀阀13的出口并联后与第一电子膨胀阀12的进口连接，第一电子膨胀阀12的出口一路与室外换热器5的进口连接，第一电子膨胀阀的出口另一路通过第一单向阀15与高压储液器9的进口连接，闪蒸器8的气体出口与低压级压缩机1的补气口连接，气液分离器7的排气接口与低压级压缩机1的进口连接。Fig. 1 is the schematic diagram of the quasi-three-stage compressed air source heat pump system of the present invention, including low-pressure stage compressor 1, high-pressure stage compressor 2, low-pressure stage four-way valve 3, high-pressure stage four-way valve 4, outdoor heat exchanger 5, indoor Heat exchanger 6, high-pressure liquid receiver 9, flash evaporator 8, gas-liquid separator 7, intercooler 10, the first port 19 of the low-pressure stage four-way valve 3 is connected to the outlet of the low-pressure stage compressor, and the low-pressure stage four-way The second port 20 of the valve is connected to the outlet of the outdoor heat exchanger 5, the third port 21 of the low-pressure stage four-way valve is connected to the inlet of the gas-liquid separator 7, and the fourth port 22 of the low-pressure stage four-way valve is connected to the high-pressure stage four-way valve. The third port 25 of the through valve 4 is connected, the first port 23 of the high-pressure stage four-way valve is connected to the outlet of the high-pressure stage compressor 2, and the second port 24 of the high-pressure stage four-way valve is connected to the medium-temperature and medium-pressure refrigeration unit of the intercooler 10. The agent outlet is connected in parallel with the inlet of the high-pressure stage compressor, the fourth port 26 of the high-pressure stage four-way valve is connected with the inlet of the indoor heat exchanger 6, and the outlet of the indoor heat exchanger 6 passes through the second one-way valve 16 to connect with the high-pressure compressor. The inlet of the accumulator 9 is connected, the other outlet of the indoor heat exchanger 6 is connected to the inlet of the second electronic expansion valve 13, and the outlet of the high-pressure liquid of the high-pressure accumulator 9 is connected to the high-temperature and high-pressure refrigerant inlet of the intercooler 10 The high-pressure liquid outlet of the high-pressure accumulator 9 is connected to the medium-temperature and medium-pressure refrigerant inlet of the intercooler 10 through the third electronic expansion valve 14, and the high-temperature and high-pressure refrigerant outlet of the intercooler 10 is connected to the outlet of the flash evaporator 8 through the third electronic expansion valve 14. Inlet connection, the high temperature and high pressure refrigerant outlet of the intercooler is connected to the inlet of the shut-off valve 18 in another way, the outlet of the shut-off valve 18 is connected in parallel with the liquid outlet of the flash evaporator 8 and then connected in parallel with the outlet of the second electronic expansion valve 13 and then connected with the second electronic expansion valve 13 The inlet of an electronic expansion valve 12 is connected, the outlet of the first electronic expansion valve 12 is connected to the inlet of the outdoor heat exchanger 5, and the outlet of the first electronic expansion valve is connected to the high-pressure liquid reservoir 9 through the first one-way valve 15 The gas outlet of the flash evaporator 8 is connected to the gas supply port of the low-pressure compressor 1, and the exhaust port of the gas-liquid separator 7 is connected to the inlet of the low-pressure compressor 1.
为了对高压储液器流出的高压液体制冷剂进行干燥，在高压储液器9的液体出口处设置有干燥过滤器11，将高压储液器9的液体出口与干燥过滤器11进口连接，干燥过滤器11出口一路与中间冷却器10的高温高压制冷剂进口连接，干燥过滤器出口另一路通过第三电子膨胀阀14与中间冷却器10的中温中压制冷剂进口连接。In order to dry the high-pressure liquid refrigerant flowing out of the high-pressure accumulator, a dry filter 11 is provided at the liquid outlet of the high-pressure accumulator 9, and the liquid outlet of the high-pressure accumulator 9 is connected to the inlet of the dry filter 11, and the One outlet of the filter 11 is connected to the high-temperature and high-pressure refrigerant inlet of the intercooler 10 , and the other outlet of the dry filter is connected to the medium-temperature and medium-pressure refrigerant inlet of the intercooler 10 through the third electronic expansion valve 14 .
在中间冷却器10的中温中压制冷剂进口与高压储液器9的高压液体出口之间连接有电磁阀17，可以控制旁通路的开关，当中间冷却器容器内的制冷剂可以使盘管内制冷剂过冷时，可关闭电磁阀，反之，则应打开电磁阀。A solenoid valve 17 is connected between the medium-temperature and medium-pressure refrigerant inlet of the intercooler 10 and the high-pressure liquid outlet of the high-pressure liquid receiver 9, which can control the switch of the bypass passage. When the refrigerant is supercooled, the solenoid valve can be closed, otherwise, the solenoid valve should be opened.
本系统在制冷时打开截止阀18，低压级四通阀的第一接口19与第二接口20连通，第三接口21与第四接口22连通，高压级四通阀的第一接口23与第二接口26连通，第三接口26与第四接口25连通，工作过程与一般的双级压缩蒸气式制冷系统一样。The system opens the shut-off valve 18 during refrigeration, the first port 19 of the low-pressure stage four-way valve communicates with the second port 20, the third port 21 communicates with the fourth port 22, and the first port 23 of the high-pressure stage four-way valve communicates with the second port. The second port 26 is connected, the third port 26 is connected to the fourth port 25, and the working process is the same as that of a general two-stage compression vapor refrigeration system.
在制热工况，将低压级四通阀的第一接口19与第四接口22连通，第二接口20与第三接口21连通，高压级四通阀的第一接口23与第四接口24连通，第二接口25与第三接口26连通。由室外换热器5排出低温低压的气态制冷剂经低压级四通阀3、气液分离器7进入低压级压缩机1，由低压级压缩机1压缩成为温度较高的中压气态制冷剂，经高压级四通阀4流向高压级压缩机2吸气管，并与由中间冷却器10排出的中温中压制冷剂混合，混合后的气态制冷剂进入高压级压缩机2，压缩成高温高压气态制冷剂，再经高压级四通阀4进入室内换热器6，与室内空气换热，达到制热目的。高温高压的制冷剂蒸气在此冷却、冷凝成为低温高压液体，再通过第二单向阀16进入高压贮液器9中。由高压贮液器9流出的高压液态制冷剂，一小部分经电磁阀17、第三电子膨胀阀14进入中间冷却器的中温中压制冷剂通道，大部分高压液态制冷剂流经中间冷却器高温高压制冷剂通道，吸收中温中压制冷剂通道内制冷剂的蒸发潜热而实现大幅度的过冷。然后进入闪蒸器8，在闪蒸器8内被蒸发为气态的制冷剂进入低压级压缩机1完成补气过程。从闪蒸器8下端排出的得到充分过冷的高压液态制冷剂与从第二电子膨胀阀流出的气态制冷剂混合，经制热用第一电子膨胀阀12节流降压成为中温低压的液态，再进入室外换热器5，吸收室外空气的热量蒸发成低温低压的气态制冷剂，再流经低压级四通阀3、气液分离器7返回低压级压缩机，完成制热循环。安装第一单向阀15，可防止由室内换热器出来的低温高压气体未经中间冷却器直接进入室外换热器，从而无法进行补气。In heating mode, connect the first port 19 of the low-pressure four-way valve to the fourth port 22, the second port 20 to the third port 21, and the first port 23 of the high-pressure four-way valve to the fourth port 24 The second interface 25 communicates with the third interface 26. The low-temperature and low-pressure gaseous refrigerant discharged from the outdoor heat exchanger 5 enters the low-pressure stage compressor 1 through the low-pressure stage four-way valve 3 and the gas-liquid separator 7, and is compressed by the low-pressure stage compressor 1 to become a medium-pressure gaseous refrigerant with a higher temperature , flows through the high-pressure stage four-way valve 4 to the suction pipe of the high-pressure stage compressor 2, and mixes with the medium-temperature and medium-pressure refrigerant discharged from the intercooler 10, and the mixed gaseous refrigerant enters the high-pressure stage compressor 2 and is compressed into a high-temperature The high-pressure gaseous refrigerant enters the indoor heat exchanger 6 through the high-pressure four-way valve 4, and exchanges heat with the indoor air to achieve the purpose of heating. The high-temperature and high-pressure refrigerant vapor is cooled and condensed here to become a low-temperature and high-pressure liquid, and then enters the high-pressure liquid receiver 9 through the second one-way valve 16 . A small part of the high-pressure liquid refrigerant flowing out of the high-pressure liquid receiver 9 enters the medium-temperature and medium-pressure refrigerant channel of the intercooler through the solenoid valve 17 and the third electronic expansion valve 14, and most of the high-pressure liquid refrigerant flows through the intercooler The high-temperature and high-pressure refrigerant channel absorbs the latent heat of evaporation of the refrigerant in the medium-temperature and medium-pressure refrigerant channel to achieve substantial subcooling. Then it enters the flash evaporator 8, and the refrigerant evaporated into a gaseous state in the flash evaporator 8 enters the low-pressure stage compressor 1 to complete the gas supplement process. The fully subcooled high-pressure liquid refrigerant discharged from the lower end of the flash evaporator 8 is mixed with the gaseous refrigerant flowing out of the second electronic expansion valve, and is throttled and depressurized by the first electronic expansion valve 12 for heating to become a medium-temperature and low-pressure liquid. Then enter the outdoor heat exchanger 5, absorb the heat of the outdoor air and evaporate into low-temperature and low-pressure gaseous refrigerant, and then flow through the low-pressure stage four-way valve 3 and gas-liquid separator 7 to return to the low-pressure stage compressor to complete the heating cycle. Installing the first one-way valve 15 can prevent the low-temperature and high-pressure gas coming out of the indoor heat exchanger from directly entering the outdoor heat exchanger through the intercooler, thereby making it impossible to replenish air.
尽管参照实施例对所公开的涉及一种准三级压缩空气源热泵系统进行了特别描述，以上描述的实施例是说明性的而不是限制性的，在不脱离本发明的精神和范围的情况下，所有的变化和修改都在本发明的范围之内。Although the disclosed quasi-three-stage compressed air source heat pump system has been specifically described with reference to the embodiments, the above-described embodiments are illustrative and not restrictive, without departing from the spirit and scope of the present invention Below, all changes and modifications are within the scope of the present invention.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100699570A CN101625176B (en) | 2009-07-30 | 2009-07-30 | Quasi three-stage compressed air source heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009100699570A CN101625176B (en) | 2009-07-30 | 2009-07-30 | Quasi three-stage compressed air source heat pump system |
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| CN101625176A CN101625176A (en) | 2010-01-13 |
| CN101625176B true CN101625176B (en) | 2011-01-19 |
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| CN2009100699570A Expired - Fee Related CN101625176B (en) | 2009-07-30 | 2009-07-30 | Quasi three-stage compressed air source heat pump system |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013004298A1 (en) * | 2011-07-05 | 2013-01-10 | Carrier Corporation | Refrigeration circuit, gas-liquid separator and heating and cooling system |
| CN102331112B (en) * | 2011-09-20 | 2013-09-11 | 王正鹏 | Heat pump working condition system |
| CN102620463B (en) * | 2012-03-27 | 2014-03-26 | 美的集团股份有限公司 | Novel low-temperature strong-heating multi-split system |
| CN103423919B (en) * | 2012-05-23 | 2016-06-29 | 约克广州空调冷冻设备有限公司 | Air source heat pump system and the defrost fluid-discharge method for this air source heat pump system |
| CN107514830A (en) * | 2016-06-18 | 2017-12-26 | 上海春至新能源科技有限公司 | A kind of single multi-stage compression automatic conversion Multifunctional heat pump system |
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| CN201014625Y (en) * | 2007-03-23 | 2008-01-30 | 大连中星科技开发有限公司 | Household air source heat pump heating system and device in winter in cold northern regions |
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| CN101387456A (en) * | 2008-10-31 | 2009-03-18 | 大连理工大学 | Air source heat pump device with integrated heating and cooling bath in cold regions |
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| Publication number | Publication date |
|---|---|
| CN101625176A (en) | 2010-01-13 |
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