WO2018188269A1 - 一种冷量回收式变容量空气源热泵系统 - Google Patents

一种冷量回收式变容量空气源热泵系统 Download PDF

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Publication number
WO2018188269A1
WO2018188269A1 PCT/CN2017/102002 CN2017102002W WO2018188269A1 WO 2018188269 A1 WO2018188269 A1 WO 2018188269A1 CN 2017102002 W CN2017102002 W CN 2017102002W WO 2018188269 A1 WO2018188269 A1 WO 2018188269A1
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Prior art keywords
heat exchanger
refrigerant
valve
compressor
heat
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PCT/CN2017/102002
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English (en)
French (fr)
Inventor
吴运运
王玉军
王颖
李俊红
杨奕
王天舒
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江苏天舒电器股份有限公司
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Priority claimed from CN201710245733.5A external-priority patent/CN106871479B/zh
Priority claimed from CN201720393029.XU external-priority patent/CN206618147U/zh
Application filed by 江苏天舒电器股份有限公司 filed Critical 江苏天舒电器股份有限公司
Priority to US16/604,943 priority Critical patent/US11137178B2/en
Publication of WO2018188269A1 publication Critical patent/WO2018188269A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves

Definitions

  • the traditional temperature control generally supplies heat through electric heating, steam heating or combustion boilers, and the process required for different temperatures is often realized by different heating methods, which increases the operating cost of the enterprise and reduces the working efficiency.
  • intelligent control cannot be realized, and a large amount of manpower is required. Therefore, it is necessary to transform the original energy-consuming production process and develop a combined system of heating and cooling that meets the requirements of the food processing process.
  • the existing heat pump system with heat recovery function usually uses a separate condenser and an independent heat recovery unit to form a heat exchanger, which not only takes up a lot of space but also has high cost.
  • the utility model patent "shell heat exchanger and air conditioner” discloses a shell and tube heat exchanger and an air conditioner including the shell and tube heat exchanger, the shell tube Heat exchanger including condenser and heat recovery At one end of the condenser, there is a cooling water inlet and a cooling water outlet, and the other end is sealed; the heat recovery unit has a hot water inlet and a hot water outlet at one end, and the other end is fixedly connected to the sealed end of the condenser:
  • the respective sealed ends of the heat recovery devices are fixedly connected, and the heat recovery device is connected with the refrigerant passage of the condenser through the connecting pipe, thereby ensuring the normal condensation function and heat recovery function of the shell and
  • a cold recovery type variable capacity air source heat pump system comprising a first subsystem consisting of a first compressor and a cold recovery heat exchanger, and a second subsystem consisting of a second compressor and a finned heat exchanger, Characterized by;
  • the first subsystem and the second subsystem jointly use a two-channel variable-capacity heat exchanger as a water-cooled condenser;
  • the two-channel variable-capacity heat exchanger includes a heat exchanger body and a set of solenoid valves a control valve group composed of a one-way valve;
  • the heat exchanger body includes two mutually independent refrigerant tube passages disposed in the same shell-side passage, and the refrigerant in the two refrigerant tube passages simultaneously and in the shell-side passage The water exchanges heat;
  • the shell side passage of the heat exchanger body establishes a water medium heating cycle through the hot water circulation line and the hot water circulation pump;
  • the first subsystem and the second subsystem are connected to the two refrigerant tube passages through the control valve group to establish a dynamically controllable refrigerant circulation loop; the heat pump system controls the control of the dual channel variable capacity heat exchanger
  • the switch state of the valve group enables dynamic multi-mode operation of the heat pump system.
  • a preferred technical solution of the dual-channel variable-capacity heat exchanger of the present invention is characterized in that the heat exchanger body adopts a vertical structure in which the shell-side passages are connected up and down, and the first refrigerant passage is placed in the shell-side passage.
  • the upper portion of the second refrigerant passage is disposed at a lower portion of the shell-side passage; the high-temperature sensible heat of the refrigerant is transferred to the water in the upper portion of the shell-side passage in the first refrigerant passage to form a high-temperature sensible heat exchange region; condensation of the refrigerant
  • the latent heat is transferred to the water in the lower portion of the shell-side passage in the second refrigerant passage to form a condensation latent heat exchange zone.
  • a better technical solution of the cold recovery type variable capacity air source heat pump system of the present invention is characterized in that a first liquid storage device is disposed on the connecting line between the first refrigerant passage and the first expansion valve, A second reservoir is disposed on the connecting line between the second refrigerant passage and the second expansion valve.
  • the first subsystem is in the hot and cold equalization mode: the first compressor is started, the second compressor is stopped, the first solenoid valve is opened, and the second solenoid valve is closed.
  • the refrigerant circulation path of this mode is as follows:
  • the second subsystem air source hot water mode the first compressor is stopped, the second compressor is started, the second solenoid valve is closed, and the third solenoid valve is opened.
  • the refrigerant circulation path of this mode is as follows:
  • Second compressor second four-way valve - first check valve - second refrigerant passage - third solenoid valve - second reservoir - second expansion valve - finned heat exchanger - second four pass Valve - second gas-liquid separator - second compressor;
  • Second compressor second four-way valve - first check valve - second refrigerant passage - third solenoid valve - second reservoir - second expansion valve - finned heat exchanger - second four pass Valve - second gas-liquid separator - second compressor;
  • the heat exchange area S of the finned heat exchanger ranges from 0 to W 2 /q
  • unit heat quantity Q 1 W 1 + P i , kw;
  • W 1 is the cooling capacity on the evaporator side during system heating operation, kw;
  • P i is the system heating operation input power, kw;
  • W 2 is refrigeration recovery Cooling capacity, kw;
  • q is the cooling capacity per unit heat exchange area on the evaporation side under heating conditions, kw/m 2 ;
  • S 1 (W 1 -W 2 )/q 1 is the heat exchange area of the cold recovery heat exchanger, m 2 ;
  • q 1 is the cooling capacity per unit heat exchange area of the cold recovery heat exchanger, kw/m 2 .
  • the cold-recoverable variable-capacity air source heat pump system of the present invention realizes a dual-channel varactor mode through a two-channel variable-capacity heat exchanger, and can effectively utilize the heat exchange area of the shell-and-tube heat exchanger, thereby being able to satisfy a large
  • the requirements of stable load capacity and the overall operating efficiency of the unit are greatly improved, thus achieving energy-efficient operation of the heat pump system.
  • the cold-recoverable variable-capacity air source heat pump system of the present invention realizes partial cooling recovery by using a dual-channel variable-capacity heat exchanger and a cold-recovery heat exchanger operated in a variable capacity mode, which can greatly improve refrigeration in the subsystem.
  • the degree of subcooling of the agent thereby increasing the cooling capacity of the system.
  • the cold recovery type variable capacity air source heat pump system of the present invention realizes coupling operation by sharing a set of water-cooled condensers by two sets of refrigeration systems, and uses a cold recovery heat exchanger to reduce the size of the finned evaporator, thereby achieving
  • the purpose of reducing the size of the system is to make the cold and heat cogeneration system run stably under different cooling and heat loads, and achieve the goal of high efficiency and energy saving operation.
  • Figure 4 is a schematic structural view of a two-channel variable capacity heat exchanger of the present invention.
  • 1-first subsystem 10-first compressor, 11-first four-way valve, 12-first expansion valve, 13-cooling recovery heat exchanger, 14- Cold water circulation pipeline, 15-first gas-liquid separator, 16-first temperature sensing package, 17-first liquid storage device, 18-first defrost one-way electromagnetic valve, 2-second subsystem, 20- Second compressor, 21-second four-way valve, 22-second expansion valve, 23-fin heat exchanger, 24-fan, 25-second gas-liquid separator, 26-second temperature sensor package, 27-Second reservoir, 28-second defrost one-way solenoid valve, 3-two-channel variable capacity heat exchanger, 30-heat exchanger body, 31-first refrigerant passage, 32-second refrigeration Agent channel, 33-first solenoid valve, 34-second solenoid valve, 35-third solenoid valve, 36-first one-way valve, 37-second one-way valve, 38-hot water circulation line, 39- Hot water circulation pump.
  • FIG. 2 and 3 are an embodiment of a cold recovery type variable capacity air source heat pump system of the present invention, comprising a first subsystem 1 composed of a first compressor 10 and a cold recovery heat exchanger 13, and a second compressor 20 and a second subsystem 2 composed of a finned heat exchanger 23, as shown in FIG.
  • the production process of 1T raw materials from processing to final packaging into products needs to stabilize 100KW heat and 50KW cooling capacity.
  • the first subsystem 1 uses a casing type evaporator as the cold recovery heat exchanger 13, and recovers a part of the cooling amount for the cooling process in the process of casting, cooling hardening and packaging of chocolate processing.
  • the second subsystem 2 uses the finned heat exchanger 23 to extract heat from the air source, and increases the overall heating capacity of the heat pump system according to the difference in cold heat demand.
  • the heat exchanger body 30 adopts a vertical structure in which the shell-side passages communicate with each other, and the first refrigerant passage 31 is disposed at an upper portion of the shell-side passage.
  • the second refrigerant passage 32 is disposed at a lower portion of the shell-side passage; the high-temperature sensible heat of the refrigerant is transferred to the water in the upper portion of the shell-side passage in the first refrigerant passage 31 to form a high-temperature sensible heat exchange zone; the latent heat of condensation of the refrigerant The water transferred to the lower portion of the shell-side passage in the second refrigerant passage 32 forms a condensation latent heat exchange zone.
  • the first accumulator 17 is provided on the connecting line between the first refrigerant passage 31 and the first expansion valve 12.
  • a second accumulator 27 is provided on the connecting line between the second refrigerant passage 32 and the second expansion valve 22.
  • the dynamic multi-mode operation includes the following four operation modes:
  • the refrigerant in the first refrigerant passage 31 exchanges heat with the water in the shell-side passage, and the heat energy recovered by the cold recovery heat exchanger 13 in the cold water process of the first subsystem 1 is transferred to the exchange.
  • the second subsystem air source hot water mode the first compressor 10 is stopped, the second compressor 20 is started, the second solenoid valve 34 is closed, and the third solenoid valve 35 is opened.
  • the refrigerant circulation path of this mode is as follows:
  • Second compressor 20 second four-way valve 21 - first check valve 36 - second refrigerant passage 32 - third solenoid valve 35 - second reservoir 27 - second expansion valve 22 - fin change Heater 23 - second four-way valve 21 - second gas-liquid separator 25 - Two compressors 20;
  • the refrigerant in the second refrigerant passage 32 exchanges heat with the water in the shell path, and the heat energy absorbed by the finned heat exchanger 23 of the second subsystem 2 from the air source is transferred to the heat exchanger.
  • First compressor 10 first four-way valve 11 - first refrigerant passage 31 - first solenoid valve 33 - first accumulator 17 - first expansion valve 12 - cold recovery heat exchanger 13 - first four Pass valve 11 - first gas-liquid separator 15 - first compressor 10;
  • the refrigerant circulation path of the second subsystem 2 is as follows:
  • the refrigerant in the first refrigerant passage 31 exchanges heat with the water in the shell-side passage, and the first subsystem 1 is in the process of producing cold water in the cold water recovery process.
  • the recovered thermal energy is transferred to the hot water prepared in the shell path of the heat exchanger body 30; at the same time, the refrigerant in the second refrigerant passage 32 exchanges heat with the water in the shell path, and the second subsystem 2
  • the heat energy absorbed by the finned heat exchanger 23 from the air source is transferred to the hot water produced in the shell path of the heat exchanger body 30.
  • First compressor 10 first four-way valve 11 - first refrigerant passage 31 - second solenoid valve 34 - second refrigerant passage 32 - second check valve 37 - first accumulator 17 - first expansion Valve 12 - Cooling Recovery Heat Exchanger 13 - First Four-Way Valve 11 - First Gas-Liquid Separator 15 - First Compressor 10.
  • the high temperature and high pressure refrigerant gas discharged from the exhaust port of the first compressor 10 of the cold recovery type variable capacity air source heat pump system of the present invention enters the two-channel variable through the first four-way valve 11.
  • the capacity heat exchanger 3 After flowing through the first refrigerant passage 31 for the first stage heat exchange, a refrigerant gas-liquid mixture is formed and returned to the two-channel variable-capacity heat exchanger 3 through the second electromagnetic valve 34.
  • the high temperature and high pressure refrigerant gas discharged from the exhaust port of the first compressor 10 of the cold recovery type variable capacity air source heat pump system of the present invention enters the two-channel variable through the first four-way valve 11.
  • the capacity heat exchanger 3 After flowing through the first refrigerant passage 31 for the first stage heat exchange, a refrigerant gas-liquid mixture is formed and returned to the two-channel variable-capacity heat exchanger 3 through the second electromagnetic valve 34.
  • the cold-recoverable variable-capacity air-source heat pump system of the present invention utilizes a dual-channel variable-capacity heat exchanger 3 operating in a variable capacity mode, which can greatly improve the degree of subcooling of the refrigerant in the first subsystem 1, thereby improving the system Cooling capacity.
  • the dual-channel varactor mode can effectively utilize the heat exchange area of the shell-and-tube heat exchanger, so that it can meet the requirements of stable load output under large load conditions, and the overall operating efficiency of the unit is greatly improved, thereby realizing the heat pump.
  • the energy efficient operation of the system is provided.
  • the air source heat pump system changes the heat exchange area of the finned heat exchanger according to the refrigeration recovery refrigeration amount, while ensuring the unit heat generation. Reduce the overall system size of the heat pump system:
  • the heat exchange area S of the fin-type heat exchanger 23 varies from 0 to W 2 /q
  • the heat exchange area S 1 of the cold recovery heat exchanger 13 varies from 0 to (W 1 -W 2 )/q 1 .

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

一种冷量回收式变容量空气源热泵系统，涉及交替或同时运转的加热和制冷组合系统，第一子系统(1)和第二子系统(2)共用双通道可变容量换热器(3)；换热器主体(30)包括两个互相独立的制冷剂管程通道，两个通道的制冷剂同时与壳程通道的热媒水进行热交换；壳程通道通过热水循环管路(38)和热水循环泵(39)建立水媒供热循环；第一子系统(1)和第二子系统(2)通过控制阀组连接到两个制冷剂管程通道，建立动态可控的制冷剂循环回路；热泵系统通过控制双通道可变容量换热器(3)的控制阀组的开关状态，通过双通道可变容量换热器(3)实现双通道变容模式，能够有效利用壳管式换热器的换热面积，实现热泵系统的高能效运行。

Description

一种冷量回收式变容量空气源热泵系统 技术领域
本发明涉及交替或同时运转的加热和制冷组合系统，尤其涉及一种以供热为主，同时兼顾冷量供给的热泵式冷热联供系统。
背景技术
集约型社会建设口号的提出，促使建筑物本体内功能集成化程度更高，做到最大化能源利用已经成为当今议题。如今，商业和商务场所要求越来越高：空气侧要求控制适宜的温湿度和空气洁净度；用水侧水温度要求全年适宜。而传统的冷热源单独供给的方式在不同季节中显然造成了资源的错置，与此同时设备初投资成本亦大大提升。如图1所示的巧克力加工工艺，巧克力产品经过原料混合融化、精磨、精炼、过筛、保温、调温、浇模成型和冷却硬化最后包装成产品，不仅需要大量的热量和冷量供应，而且各个工艺环节对温度有着严格的要求。传统的温度控制一般通过电加热、蒸汽加热或是燃烧锅炉供给热量，而对不同温度要求得工艺往往是通过不同的供热方式来实现，这就增加了企业的运营成本且降低了工作效率，同时不能实现智能控制，需要大量人力投入。因此，需要对原有的耗能生产工艺流程进行改造，研发能够满足食品加工工艺要求的加热和制冷的联合系统。中国发明专利“饭店后厨热泵系统多模式运行控制方法及其控制装置”(发明专利号：201410478406.0，授权公告号：CN104197584B)公开了一种饭店后厨热泵系统多模式运行控制方法及其控制装置，涉及加热和制冷的联合系统的控制，尤其涉及一种适用于饭店后厨的热水供应、降温除湿和冷藏保鲜的热泵综合系统的控制方法及设备，控制装置通过检测和比较运行模式参数的实测值和设定值，控制多模式制冷剂循环回路切换机构改变制冷剂的循环路径，控制饭店后厨热泵系统按照预设的运行模式运行，实现自动多模式运行。
另一方面，现有具有热回收功能的热泵系统通常采用一个独立的冷凝器和一个独立热回收器连接组成制热换热器，不仅占用空间大而且成本高。中国实用新型专利“壳管换热器及空调”(实用新型专利号：201420417296.2，授权公告号：CN204084963U)公开了一种壳管换热器及包括该壳管换热器的空调，该壳管换热器包括冷凝器和热回收 器，冷凝器一端设有冷却进水口与冷却出水口，另一端密封设置；热回收器一端设有热水进口与热水出口，另一端与冷凝器密封的一端固定连接：通过将冷凝器与热回收器各自的密封端固定连接，并通过连接管将热回收器与冷凝器的冷媒通道连接起来,既能保证壳管换热器正常的冷凝功能及热回收功能，还能使壳管换热器的结构紧凑，节省安装空间，降低成本。但是，该现有技术方案实质上只是把两个独立的功能部件机械上设计为一体，其各自的功能仍然是互相独立的，并不能提高换热器的整体换热效率。
发明内容
本发明的目的是要提供一种冷量回收式变容量空气源热泵系统，用于解决热泵冷热联供系统取代传统加热方式过程中缩减设备尺度、节约设备投入和运行成本，提高换热效率和机组能效的技术问题。
本发明解决上述技术问题所采用的技术方案是：
一种冷量回收式变容量空气源热泵系统，包括第一压缩机和冷量回收换热器组成的第一子系统，第二压缩机和翅片式换热器组成的第二子系统，其特征在于；
所述的第一子系统和第二子系统共同使用一个双通道可变容量换热器作为水冷冷凝器；所述的双通道可变容量换热器包括换热器主体和一组由电磁阀与单向阀组成的控制阀组；换热器主体包括置于同一壳程通道的两个互相独立的制冷剂管程通道，两个制冷剂管程通道内的制冷剂同时与壳程通道中的水进行热交换；换热器主体的壳程通道通过热水循环管路和热水循环泵建立水媒供热循环；
第一子系统和第二子系统通过所述的控制阀组连接到两个制冷剂管程通道，建立动态可控的制冷剂循环回路；热泵系统通过控制双通道可变容量换热器之控制阀组的开关状态，实现热泵系统的动态多模式运行。
本发明的冷量回收式变容量空气源热泵系统的一种较佳的技术方案，其特征在于所述的双通道可变容量换热器包括作为换热器主体的壳管式换热器和连接到壳管换热器之制冷剂管程通道的控制阀组；所述的换热器主体内设有两个互相独立的第一制冷剂通道和第二制冷剂通道，两个制冷剂管程通道置于一个共用的壳程通道内；所述的控制阀组包括连接在制冷剂管程通道的三个电磁阀和两个单向阀；所述的电磁阀包括连接在第一制冷剂通道出口的第一电磁阀，连接在第一制冷剂通道出口和第二制冷剂通道入口之间的第二电磁阀，以及连接在第二制冷剂通道出口的第三电磁阀；所述的单向阀包括连接在第二制冷剂通道入口的第一单向阀，以及并联连接在第二制冷剂通道出口和第一电磁阀出口之间的第二单向阀；第一压缩机的排气口通过第一四通阀连接到第一制冷剂通 道的入口；第一电磁阀的出口和第二单向阀的出口并联连接后，通过第一膨胀阀连接到冷量回收换热器的制冷剂通道，再通过第一四通阀连接到第一压缩机的进气口；第二压缩机的排气口通过第二四通阀连接到第一单向阀的入口；第三电磁阀的出口通过第二膨胀阀连接到翅片式换热器的制冷剂通道，再通过第二四通阀连接到第二压缩机的进气口。
本发明的双通道可变容量换热器的一种优选的技术方案，其特征在于所述的换热器主体采用壳程通道上下连通的立式结构，第一制冷剂通道置于壳程通道的上部，第二制冷剂通道置于壳程通道的下部；制冷剂的高温显热在第一制冷剂通道中传递给壳程通道上部的水，形成高温显热换热区；制冷剂的冷凝潜热在第二制冷剂通道中传递给壳程通道下部的水，形成冷凝潜热换热区。
本发明的冷量回收式变容量空气源热泵系统的一种更好的技术方案，其特征在于在第一制冷剂通道与第一膨胀阀之间的连接管路上设有第一储液器，在第二制冷剂通道与第二膨胀阀之间的连接管路上设有第二储液器。
本发明的冷量回收式变容量空气源热泵系统的一种改进的技术方案，其特征在于所述的动态多模式运行包括以下四种运行模式：
(1)第一子系统冷热均衡模式：第一压缩机启动，第二压缩机停止，第一电磁阀打开，第二电磁阀关闭，本模式的制冷剂循环路径如下：
第一压缩机-第一四通阀-第一制冷剂通道-第一电磁阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机；
(2)第二子系统空气源热水模式：第一压缩机停止，第二压缩机启动，第二电磁阀关闭，第三电磁阀打开，本模式的制冷剂循环路径如下：
第二压缩机-第二四通阀-第一单向阀-第二制冷剂通道-第三电磁阀-第二储液器-第二膨胀阀-翅片式换热器-第二四通阀-第二气液分离器-第二压缩机；
(3)双系统定容冷热水模式：第一压缩机和第二压缩机同时启动，第一电磁阀打开，第二电磁阀关闭，第三电磁阀打开，第一子系统的制冷剂循环路径如下：
第一压缩机-第一四通阀-第一制冷剂通道-第一电磁阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机；
第二子系统的制冷剂循环路径如下：
第二压缩机-第二四通阀-第一单向阀-第二制冷剂通道-第三电磁阀-第二储液器-第二膨胀阀-翅片式换热器-第二四通阀-第二气液分离器-第二压缩机；
(4)双通道变容运行模式：第一压缩机启动，第二压缩机停止，第一电磁阀关闭， 第二电磁阀打开，第三电磁阀关闭，本模式的制冷剂循环路径如下：
第一压缩机-第一四通阀-第一制冷剂通道-第二电磁阀-第二制冷剂通道-第二单向阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机。
本发明的冷量回收式变容量空气源热泵系统的一种进一步改进的技术方案，其特征在于所述的空气源热泵系统根据制冷回收冷量改变翅片式换热器的换热面积，在保证机组制热量的同时缩减热泵系统的整体系统尺寸：
翅片式换热器之换热面积S的变化范围为0～W2/q，
冷量回收换热器之换热面积S1的变化范围为0～(W1-W2)/q1，
其中，机组制热量Q1＝W1+Pi，kw；W1为系统制热运行时蒸发器侧的制冷量，kw；Pi为系统制热运行输入功率，kw；W2为制冷回收冷量，kw；S＝W2/q为翅片式换热器的换热面积，m2；q为制热工况下蒸发侧单位换热面积制冷量，kw/m2；S1＝(W1-W2)/q1为冷量回收换热器的换热面积，m2；q1为冷量回收换热器单位换热面积制冷量，kw/m2。
本发明的有益效果是：
1、本发明的冷量回收式变容量空气源热泵系统，通过双通道可变容量换热器实现双通道变容模式，能够有效利用壳管式换热器的换热面积，因而能够满足大负荷工况稳定出力的要求，机组整体运行效率大大提升，从而实现热泵系统的高能效运行。
2、本发明的冷量回收式变容量空气源热泵系统，利用变容量模式运行的双通道可变容量换热器和冷量回收换热器实现部分冷量回收，能够大大提升子系统中制冷剂的过冷度，从而提高系统的制冷量。
3、本发明的冷量回收式变容量空气源热泵系统，通过两套制冷系统共用一套水冷冷凝器实现耦合运行，利用冷量回收换热器以减小翅片式蒸发器尺寸，从而达到降低系统尺寸的目的，使冷热联供系统在不同冷热负荷下低耗稳定运行，达到高效节能运行的目的。
附图说明
图1是巧克力加工工艺流程图；
图2是本发明的冷量回收式变容量空气源热泵系统的系统原理图；
图3是本发明的冷量回收式变容量空气源热泵系统的装配结构示意图；
图4是本发明的双通道可变容量换热器的结构示意图；
图5是本发明的冷量回收式变容量空气源热泵系统的运行模式示意图。
以上图中各部件的附图标记：1-第一子系统，10-第一压缩机，11-第一四通阀，12-第一膨胀阀，13-冷量回收换热器，14-冷水循环管路，15-第一气液分离器，16-第一感温包，17-第一储液器，18-第一除霜单向电磁阀，2-第二子系统，20-第二压缩机，21-第二四通阀，22-第二膨胀阀，23-翅片式换热器，24-风机，25-第二气液分离器，26-第二感温包，27-第二储液器，28-第二除霜单向电磁阀，3-双通道可变容量换热器，30-换热器主体，31-第一制冷剂通道，32-第二制冷剂通道，33-第一电磁阀，34-第二电磁阀，35-第三电磁阀，36-第一单向阀，37-第二单向阀，38-热水循环管路，39-热水循环泵。
具体实施方式
为了能更好地理解本发明的上述技术方案，下面结合附图和实施例进行进一步地详细描述。图2和图3是本发明的冷量回收式变容量空气源热泵系统的一个实施例，包括第一压缩机10和冷量回收换热器13组成的第一子系统1，第二压缩机20和翅片式换热器23组成的第二子系统2，如图2所示，所述的第一子系统1和第二子系统2共同使用一个双通道可变容量换热器3作为水冷冷凝器；所述的双通道可变容量换热器3包括换热器主体30和一组由电磁阀与单向阀组成的控制阀组；换热器主体30包括置于同一壳程通道的两个互相独立的制冷剂管程通道，两个制冷剂管程通道内的制冷剂同时与壳程通道中的水进行热交换；换热器主体30的壳程通道通过热水循环管路38和热水循环泵39建立水媒供热循环；第一子系统1和第二子系统2通过所述的控制阀组连接到两个制冷剂管程通道，建立动态可控的制冷剂循环回路；热泵系统通过控制双通道可变容量换热器3之控制阀组的开关状态，实现热泵系统的动态多模式运行。以某巧克力加工产线为例，1T原料从加工至最后包装成产品的生产过程需要稳定100KW热量和50KW冷量需求。在本实施例中，第一子系统1采用套管式蒸发器作为冷量回收换热器13，回收部分冷量用于巧克力加工的浇模成型、冷却硬化和包装等工艺过程中的冷量供应；第二子系统2采用翅片式换热器23从空气源吸取热量，根据冷热量需求的差异增加热泵系统的整体制热能力。
在图4所示的实施例中，所述的双通道可变容量换热器3包括作为换热器主体30的壳管式换热器和连接到壳管换热器之制冷剂管程通道的控制阀组；所述的换热器主体30内设有两个互相独立的第一制冷剂通道31和第二制冷剂通道32，两个制冷剂管程通道31和32置于一个共用的壳程通道内；所述的控制阀组包括连接在制冷剂管程通道的 三个电磁阀和两个单向阀；所述的电磁阀包括连接在第一制冷剂通道31出口的第一电磁阀33，连接在第一制冷剂通道31出口和第二制冷剂通道32入口之间的第二电磁阀34，以及连接在第二制冷剂通道32出口的第三电磁阀35；所述的单向阀包括连接在第二制冷剂通道32入口的第一单向阀36，以及并联连接在第二制冷剂通道32出口和第一电磁阀33出口之间的第二单向阀37；第一压缩机10的排气口通过第一四通阀11连接到第一制冷剂通道31的入口；第一电磁阀33的出口和第二单向阀37的出口并联连接后，通过第一膨胀阀12连接到冷量回收换热器13的制冷剂通道，再通过第一四通阀11连接到第一压缩机10的进气口；第二压缩机20的排气口通过第二四通阀21连接到第一单向阀36的入口；第三电磁阀35的出口通过第二膨胀阀22连接到翅片式换热器23的制冷剂通道，再通过第二四通阀21连接到第二压缩机20的进气口。
根据本发明的双通道可变容量换热器的一个实施例，所述的换热器主体30采用壳程通道上下连通的立式结构，第一制冷剂通道31置于壳程通道的上部，第二制冷剂通道32置于壳程通道的下部；制冷剂的高温显热在第一制冷剂通道31中传递给壳程通道上部的水，形成高温显热换热区；制冷剂的冷凝潜热在第二制冷剂通道32中传递给壳程通道下部的水，形成冷凝潜热换热区。
根据图2所示的本发明的冷量回收式变容量空气源热泵系统的实施例，在第一制冷剂通道31与第一膨胀阀12之间的连接管路上设有第一储液器17，在第二制冷剂通道32与第二膨胀阀22之间的连接管路上设有第二储液器27。
根据图5所示的本发明的冷量回收式变容量空气源热泵系统的实施例，所述的动态多模式运行包括以下四种运行模式：
(1)第一子系统冷热均衡模式：第一压缩机10启动，第二压缩机20停止，第一电磁阀33打开，第二电磁阀34关闭，本模式的制冷剂循环路径如下：
第一压缩机10-第一四通阀11-第一制冷剂通道31-第一电磁阀33-第一储液器17-第一膨胀阀12-冷量回收换热器13-第一四通阀11-第一气液分离器15-第一压缩机10；
本模式下，第一制冷剂通道31内的制冷剂与壳程通道中的水进行热交换，将第一子系统1制取冷水过程中冷量回收换热器13回收的热能，传递给换热器主体30壳程通道中制取的热水。
(2)第二子系统空气源热水模式：第一压缩机10停止，第二压缩机20启动，第二电磁阀34关闭，第三电磁阀35打开，本模式的制冷剂循环路径如下：
第二压缩机20-第二四通阀21-第一单向阀36-第二制冷剂通道32-第三电磁阀35-第二储液器27-第二膨胀阀22-翅片式换热器23-第二四通阀21-第二气液分离器25-第 二压缩机20；
本模式下，第二制冷剂通道32内的制冷剂与壳程通道中的水进行热交换，将第二子系统2之翅片式换热器23从空气源吸收的热能，传递给换热器主体30壳程通道中制取的热水。
(3)双系统定容冷热水模式：第一压缩机10和第二压缩机20同时启动，第一电磁阀33打开，第二电磁阀34关闭，第三电磁阀35打开，第一子系统1的制冷剂循环路径如下：
第一压缩机10-第一四通阀11-第一制冷剂通道31-第一电磁阀33-第一储液器17-第一膨胀阀12-冷量回收换热器13-第一四通阀11-第一气液分离器15-第一压缩机10；
第二子系统2的制冷剂循环路径如下：
第二压缩机20-第二四通阀21-第一单向阀36-第二制冷剂通道32-第三电磁阀35-第二储液器27-第二膨胀阀22-翅片式换热器23-第二四通阀21-第二气液分离器25-第二压缩机20；
在双系统定容冷热水模式下，第一制冷剂通道31内的制冷剂与壳程通道中的水进行热交换，将第一子系统1冷水制取过程中冷量回收换热器13回收的热能，传递给换热器主体30壳程通道中制取的热水；同时，第二制冷剂通道32内的制冷剂与壳程通道中的水进行热交换，将第二子系统2之翅片式换热器23从空气源吸收的热能，传递给换热器主体30壳程通道中制取的热水。
(4)双通道变容模式：第一压缩机10启动，第二压缩机20停止，第一电磁阀33关闭，第二电磁阀34打开，第三电磁阀35关闭，本模式的制冷剂循环路径如下：
第一压缩机10-第一四通阀11-第一制冷剂通道31-第二电磁阀34-第二制冷剂通道32-第二单向阀37-第一储液器17-第一膨胀阀12-冷量回收换热器13-第一四通阀11-第一气液分离器15-第一压缩机10。
在双通道变容模式下，本发明的冷量回收式变容量空气源热泵系统之第一压缩机10排气口排出的高温高压制冷剂气体，经第一四通阀11进入双通道可变容量换热器3中，流经第一制冷剂通道31进行第一段换热后，形成制冷剂气液混合物并通过第二电磁阀34回到双通道可变容量换热器3中，在第二制冷剂通道32中再次与换热器主体30的水侧充分换热，冷凝为高压常温的制冷剂液体，流经第二单向阀37后经第一膨胀阀12的节流作用，变为低压制冷剂液体，进入作为冷量回收换热器13的套管式蒸发器，吸热蒸发为低压制冷剂气体通过第一四通阀11进入第一气液分离器15，最终进入第一压缩机10进气口，形成双通道变容模式运行的制冷剂循环路径；在本模式下，制冷剂 通过第一制冷剂通道31和第二制冷剂通道32，与壳程通道中的水进行两次热交换，将第一子系统1冷水制取过程中冷量回收换热器13回收的热能，传递给换热器主体30壳程通道中制取的热水。
在双通道变容模式下，本发明的冷量回收式变容量空气源热泵系统之第一压缩机10排气口排出的高温高压制冷剂气体，经第一四通阀11进入双通道可变容量换热器3中，流经第一制冷剂通道31进行第一段换热后，形成制冷剂气液混合物并通过第二电磁阀34回到双通道可变容量换热器3中，在第二制冷剂通道32中再次与换热器主体30的水侧充分换热，冷凝为高压常温的制冷剂液体，流经第二单向阀37后经第一膨胀阀12的节流作用，变为低压制冷剂液体，进入作为冷量回收换热器13的套管式蒸发器，吸热蒸发为低压制冷剂气体通过第一四通阀11进入第一气液分离器15，最终进入第一压缩机10进气口，形成双通道变容模式运行的制冷剂循环路径。
本发明的冷量回收式变容量空气源热泵系统，利用变容量模式运行的双通道可变容量换热器3，能够大大提升第一子系统1中制冷剂的过冷度，从而提高系统的制冷量。在第二子系统2停机时，双通道变容模式能够有效利用壳管式换热器的换热面积，因而能够满足大负荷工况稳定出力的要求，机组整体运行效率大大提升，从而实现热泵系统的高能效运行。
根据本发明的冷量回收式变容量空气源热泵系统的一个实施例，所述的空气源热泵系统根据制冷回收冷量改变翅片式换热器的换热面积，在保证机组制热量的同时缩减热泵系统的整体系统尺寸：
翅片式换热器23之换热面积S的变化范围为0～W2/q，
冷量回收换热器13之换热面积S1的变化范围为0～(W1-W2)/q1，
其中，机组制热量Q1＝W1+Pi，kw；W1为系统制热运行时蒸发器侧的制冷量，kw；Pi为系统制热运行输入功率，kw；W2为制冷回收冷量，kw；S＝W2/q为翅片式换热器23的换热面积，m2；q为制热工况下蒸发侧单位换热面积制冷量，kw/m2；S1＝(W1-W2)/q1为冷量回收换热器13的换热面积，m2；q1为冷量回收换热器13单位换热面积制冷量，kw/m2。
本技术领域中的普通技术人员应当认识到，以上的实施例仅是用来说明本发明的技术方案，而并非用作为对本发明的限定，任何基于本发明的实质精神对以上所述实施例所作的变化、变型，都将落在本发明的权利要求的保护范围内。

Claims (6)

  1. 一种冷量回收式变容量空气源热泵系统，包括第一压缩机和冷量回收换热器组成的第一子系统，第二压缩机和翅片式换热器组成的第二子系统，其特征在于：
    所述的第一子系统和第二子系统共同使用一个双通道可变容量换热器作为水冷冷凝器；所述的双通道可变容量换热器包括换热器主体和一组由电磁阀与单向阀组成的控制阀组；换热器主体包括置于同一壳程通道的两个互相独立的制冷剂管程通道，两个制冷剂管程通道内的制冷剂同时与壳程通道中的水进行热交换；换热器主体的壳程通道通过热水循环管路和热水循环泵建立水媒供热循环；
    第一子系统和第二子系统通过所述的控制阀组连接到两个制冷剂管程通道，建立动态可控的制冷剂循环回路；热泵系统通过控制双通道可变容量换热器之控制阀组的开关状态，实现热泵系统的动态多模式运行。
  2. 根据权利要求1所述的冷量回收式变容量空气源热泵系统，其特征在于所述的双通道可变容量换热器包括作为换热器主体的壳管式换热器和连接到壳管换热器之制冷剂管程通道的控制阀组；所述的换热器主体内设有两个互相独立的第一制冷剂通道和第二制冷剂通道，两个制冷剂管程通道置于一个共用的壳程通道内；所述的控制阀组包括连接在制冷剂管程通道的三个电磁阀和两个单向阀；所述的电磁阀包括连接在第一制冷剂通道出口的第一电磁阀，连接在第一制冷剂通道出口和第二制冷剂通道入口之间的第二电磁阀，以及连接在第二制冷剂通道出口的第三电磁阀；所述的单向阀包括连接在第二制冷剂通道入口的第一单向阀，以及并联连接在第二制冷剂通道出口和第一电磁阀出口之间的第二单向阀；第一压缩机的排气口通过第一四通阀连接到第一制冷剂通道的入口；第一电磁阀的出口和第二单向阀的出口并联连接后，通过第一膨胀阀连接到冷量回收换热器的制冷剂通道，再通过第一四通阀连接到第一压缩机的进气口；第二压缩机的排气口通过第二四通阀连接到第一单向阀的入口；第三电磁阀的出口通过第二膨胀阀连接到翅片式换热器的制冷剂通道，再通过第二四通阀连接到第二压缩机的进气口。
  3. 根据权利要求2所述的冷量回收式变容量空气源热泵系统，其特征在于在第一制冷剂通道与第一膨胀阀之间的连接管路上设有第一储液器，在第二制冷剂通道与第二膨胀阀之间的连接管路上设有第二储液器。
  4. 根据权利要求2所述的冷量回收式变容量空气源热泵系统，其特征在于所述的换热 器主体采用壳程通道上下连通的立式结构，第一制冷剂通道置于壳程通道的上部，第二制冷剂通道置于壳程通道的下部；制冷剂的高温显热在第一制冷剂通道中传递给壳程通道上部的水，形成高温显热换热区；制冷剂的冷凝潜热在第二制冷剂通道中传递给壳程通道下部的水，形成冷凝潜热换热区。
  5. 根据权利要求1所述的冷量回收式变容量空气源热泵系统，其特征在于所述的动态多模式运行包括以下四种运行模式：
    (1)第一子系统冷热均衡模式：第一压缩机启动，第二压缩机停止，第一电磁阀打开，第二电磁阀关闭，本模式的制冷剂循环路径如下：
    第一压缩机-第一四通阀-第一制冷剂通道-第一电磁阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机；
    (2)第二子系统空气源热水模式：第一压缩机停止，第二压缩机启动，第二电磁阀关闭，第三电磁阀打开，本模式的制冷剂循环路径如下：
    第二压缩机-第二四通阀-第一单向阀-第二制冷剂通道-第三电磁阀-第二储液器-第二膨胀阀-翅片式换热器-第二四通阀-第二气液分离器-第二压缩机；
    (3)双系统定容冷热水模式：第一压缩机和第二压缩机同时启动，第一电磁阀打开，第二电磁阀关闭，第三电磁阀打开，第一子系统的制冷剂循环路径如下：
    第一压缩机-第一四通阀-第一制冷剂通道-第一电磁阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机；
    第二子系统的制冷剂循环路径如下：
    第二压缩机-第二四通阀-第一单向阀-第二制冷剂通道-第三电磁阀-第二储液器-第二膨胀阀-翅片式换热器-第二四通阀-第二气液分离器-第二压缩机；
    (4)双通道变容运行模式：第一压缩机启动，第二压缩机停止，第一电磁阀关闭，第二电磁阀打开，第三电磁阀关闭，本模式的制冷剂循环路径如下：
    第一压缩机-第一四通阀-第一制冷剂通道-第二电磁阀-第二制冷剂通道-第二单向阀-第一储液器-第一膨胀阀-冷量回收换热器-第一四通阀-第一气液分离器-第一压缩机。
  6. 根据权利要求1所述的冷量回收式变容量空气源热泵系统，其特征在于所述的空气源热泵系统根据制冷回收冷量改变翅片式换热器的换热面积，在保证机组制热量的同时缩减热泵系统的整体系统尺寸：
    翅片式换热器之换热面积S的变化范围为0～W2/q，
    冷量回收换热器之换热面积S1的变化范围为0～(W1-W2)/q1，
    其中，机组制热量Q1＝W1+Pi，kw；W1为系统制热运行时蒸发器侧的制冷量，kw；Pi为系统制热运行输入功率，kw；W2为制冷回收冷量，kw；S＝W2/q为翅片式换热器的换热面积，m2；q为制热工况下蒸发侧单位换热面积制冷量，kw/m2；S1＝(W1-W2)/q1为冷量回收换热器的换热面积，m2；q1为冷量回收换热器单位换热面积制冷量，kw/m2。
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