WO2020103271A1 - 一种热泵系统 - Google Patents

一种热泵系统

Info

Publication number
WO2020103271A1
WO2020103271A1 PCT/CN2018/123015 CN2018123015W WO2020103271A1 WO 2020103271 A1 WO2020103271 A1 WO 2020103271A1 CN 2018123015 W CN2018123015 W CN 2018123015W WO 2020103271 A1 WO2020103271 A1 WO 2020103271A1
Authority
WO
WIPO (PCT)
Prior art keywords
interface
pump system
heat pump
centrifugal compressor
unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2018/123015
Other languages
English (en)
French (fr)
Inventor
张洪亮
张捷
赵雷
谢吉培
刘乾坤
徐志强
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Haier Air Conditioning Electric Co Ltd
Original Assignee
Qingdao Haier Air Conditioning Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Haier Air Conditioning Electric Co Ltd filed Critical Qingdao Haier Air Conditioning Electric Co Ltd
Priority to EP18928989.5A priority Critical patent/EP3712541B1/en
Priority to ES18928989T priority patent/ES2932365T3/es
Publication of WO2020103271A1 publication Critical patent/WO2020103271A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F25B31/00—Compressor arrangements
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • 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
    • F25B2313/001—Compression machines, plants or systems with reversible cycle not otherwise provided for with two or more accumulators
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0251—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units being defrosted alternately
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2600/2501—Bypass valves
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • 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

Definitions

  • the invention relates to the technical field of air conditioning equipment, in particular to a heat pump system.
  • an air-cooled screw heat pump system uses a four-way reversing valve to switch between cooling and heating conditions.
  • it needs to operate according to the refrigeration cycle and turn off the fan.
  • the pressure on the suction and exhaust sides of the unit changes drastically, so it cannot be applied to the magnetic suspension centrifuge unit.
  • the embodiment of the present invention provides a heat pump system, so that the magnetic suspension centrifugal unit has the functions of cooling and heating, and can quickly and stably perform the defrosting operation.
  • a brief summary is given below. This summary section is not a general comment, nor is it to determine key / important elements or to describe the scope of protection of these embodiments. Its sole purpose is to present some concepts in a simple form as a preface to the detailed description that follows.
  • a heat pump system is provided.
  • the heat pump system includes a magnetic suspension centrifugal compressor, and further includes a switching communication device and a first electric valve; the exhaust pipe of the magnetic suspension centrifugal compressor is connected to the first part of the switching communication device through a first check valve An interface, the suction pipe is connected to the third interface of the switching communication device; the first electric valve is arranged in parallel with the magnetic suspension centrifugal compressor.
  • the heating function of the magnetic levitation centrifugal compressor unit is realized by switching the communication device; at the same time, by setting the first electric valve, the magnetic levitation centrifugal compressor is opened before the start, which is used to adjust the high and low pressure side of the compressor Differential pressure; opened before the compressor is turned off, used to reduce the shutdown pressure ratio, so that the compressor can run smoothly.
  • Figure 1 is a schematic diagram of an alternative implementation structure of a heat pump system.
  • FIG. 2 is a schematic diagram of another optional implementation structure of a heat pump system.
  • Fig. 3 is a schematic diagram of another optional implementation structure of a heat pump system.
  • FIG. 4 is a schematic diagram of another optional implementation structure of a heat pump system.
  • FIG. 5 is a schematic diagram of another optional implementation structure of a heat pump system.
  • Figure 1 shows an alternative embodiment of a heat pump system.
  • the heat pump system includes: a magnetic suspension centrifugal compressor 1, which is characterized in that it further includes a switching communication device 3 and a first electric valve 14;
  • the exhaust pipe of the magnetic levitation centrifugal compressor 1 is connected to the first interface of the switching communication device 3 through the first check valve 2, and the suction pipe is connected to the third interface of the switching communication device 3;
  • the first electric valve 14 is arranged in parallel with the magnetic levitation centrifugal compressor 1 and is used to reduce the high-low side pressure difference when the magnetic levitation centrifugal compressor 1 is started and closed.
  • the second interface of the switching communication device 3 is connected to a gas-liquid separator 4, and the gas-liquid separator 4 is connected to an evaporator 13; the gas-liquid separator 4 is also connected to a heat exchange component and a flash tank 9 in turn.
  • the heat exchange assembly is also connected to the first one-way valve 2; the gas outlet of the flash tank 9 is connected to the intermediate air supply port of the magnetic suspension centrifugal compressor 1; the flash tank 9 is also connected to the liquid storage tank 12 and the evaporator 13 in sequence;
  • the evaporator 13 is connected to the fourth interface of the switching communication device 3.
  • a second electric valve 15 is provided on the pipeline between the gas-liquid separator 4 and the evaporator 13 for reducing the load of the unit.
  • the heat exchange assembly includes a conducting device 5, a heat exchanger 6, a filter 7, and a first electronic expansion valve 8 connected in sequence, and the conducting device 5 is controllably connected to the first one-way valve 2 and The heat exchanger 6 or the gas-liquid separator 4 and the heat exchanger 6; the first electronic expansion valve 8 is connected to the flash tank 9.
  • the heat exchange component is a plurality of heat exchange components arranged in parallel.
  • the heat pump system further includes a control device, and the control device includes:
  • the first unit is used to control the conduction and closing of the first electric valve 14;
  • the second unit is used to control the switching and connecting device 3 to conduct according to the operation instruction.
  • the magnetic levitation centrifugal compressor 1 executes a start or close command. After the execution is completed, the first unit controls the first electric valve 14 to close.
  • the second unit controls the first interface of the switching and connecting device 3 to communicate with the second interface, and the third interface to communicate with the fourth interface; when the operation command is the second In the mode operation instruction, the second unit controls the first interface of the switching and connecting device 3 to communicate with the fourth interface, and the second interface to communicate with the third interface.
  • control device further includes a third unit.
  • the third unit controls the conducting device 5 to communicate the first check valve 2 and the heat exchanger 6, or the Gas-liquid separator 4 and the heat exchanger 6.
  • the third unit controls the conducting device 5 to communicate the first check valve 2 and the heat exchanger 6.
  • the magnetic levitation centrifugal compressor may include one or more compressors.
  • the two-stage magnetic levitation centrifugal compressor with large pressure ratio is adopted to optimize the design of the system, which solves the problem that the air-cooled magnetic levitation centrifugal water chiller in the prior art can only be cooled and cannot heat, on the other hand, it also solves the traditional air-cooled screw
  • the heat pump screw unit and air-cooled scroll heat pump unit have many problems such as low coefficient of performance, high noise, difficulty in heating and oil return, and lubricating oil affecting heat transfer performance. They have high efficiency, high reliability, low noise, and heating comfort. Significant advantages.
  • the heating function of the unit of the magnetic levitation centrifugal compressor 1 is realized by switching the communication device 3; meanwhile, by setting the first electric valve 14, it is opened before the start of the magnetic levitation centrifugal compressor 1. It is used to adjust the pressure difference between the high and low pressure side of the compressor; it is opened before the compressor is turned off, and it is used to reduce the shutdown pressure ratio, so that the compressor can run smoothly.
  • control device further includes a fourth unit for controlling the logical opening of the second electric valve 15.
  • the second electric valve 15 is logically controlled for opening degree to reduce the pressure ratio of the unit and maintain the operation of the unit.
  • the fourth unit opens the second electric valve 15 in accordance with logic control to reduce the unit pressure ratio, so that the compressor can Safe and stable operation.
  • Figure 2 shows another alternative embodiment of a heat pump system.
  • the heat pump system includes: a magnetic suspension centrifugal compressor 1, which is characterized in that it further includes a switching communication device 3 and a first electric valve 14;
  • the exhaust pipe of the magnetic levitation centrifugal compressor 1 is connected to the first interface of the switching communication device 3 through the first check valve 2, and the suction pipe is connected to the third interface of the switching communication device 3;
  • the first electric valve 14 is arranged in parallel with the magnetic levitation centrifugal compressor 1 and is used to reduce the high-low side pressure difference when the magnetic levitation centrifugal compressor 1 is started and closed.
  • the switching communication device 3 includes an electric four-way valve, which is used for cooling and heating switching when the unit is stopped, to avoid switching the four-way directional valve during the operation of the compressor, resulting in high and low pressure Sudden changes cause compressor failure.
  • the second interface of the switching communication device 3 is connected to a gas-liquid separator 4, and the gas-liquid separator 4 is connected to an evaporator 13; the gas-liquid separator 4 is also connected to a heat exchange component and a flash tank 9 in turn.
  • the heat exchange assembly is also connected to the first one-way valve 2; the gas outlet of the flash tank 9 is connected to the intermediate air supply port of the magnetic suspension centrifugal compressor 1 through the first solenoid valve 16; the flash tank 9 is also connected to the liquid storage tank 12 in turn Evaporator 13; the evaporator 13 is connected to the fourth interface of the switching communication device 3.
  • a second electric valve 15 is provided on the pipeline between the gas-liquid separator 4 and the evaporator 13 for reducing the pressure ratio of the magnetic suspension centrifugal compressor 1.
  • the heat exchange assembly includes a conducting device 5, a heat exchanger 6, a filter 7, and a first electronic expansion valve 8 connected in sequence, and the conducting device 5 is controllably connected to the first one-way valve 2 and The heat exchanger 6 or the gas-liquid separator 4 and the heat exchanger 6; the first electronic expansion valve 8 is connected to the flash tank 9.
  • a temperature sensor 18 and a pressure sensor 17 provided on the suction pipe and the exhaust pipe of the magnetic levitation centrifugal compressor 1 are also included.
  • the pressure sensor 17 is used to detect the pressure of the unit.
  • the second electric valve 15 is logically controlled to open before the shutdown command is executed.
  • a temperature sensor 18 disposed between the heat exchanger 6 and the filter 7 is also included. It is used to detect the ambient temperature to determine whether the heat exchanger 6 needs to be defrosted.
  • it further includes a drying filter 11 and a second electronic expansion valve 10 connected in series between the liquid storage tank 12 and the flash tank 9 for filtering impurities and throttling, respectively.
  • the heating function of the unit of the magnetic levitation centrifugal compressor 1 is realized by switching the communication device 3; meanwhile, by setting the first electric valve 14, it is opened before the start of the magnetic levitation centrifugal compressor 1. It is used to adjust the pressure difference between the high and low pressure side of the compressor; it is opened before the compressor is turned off, and it is used to reduce the shutdown pressure ratio, so that the compressor can run smoothly.
  • the cooling and heating cycle of the unit adopts an electric four-way valve to switch when the compressor is stopped, which has no impact on the compressor, and realizes the dual-operating mode of cooling and heating of the magnetic suspension centrifugal compressor 1 with high reliability ;
  • the magnetic suspension centrifugal compressor 1 which is equipped with gearless and rolling bearings, is adjusted by frequency conversion, has ultra-high pneumatic and mechanical efficiency, so the heat pump system is oil-free circulation, which solves the fin replacement during heating
  • the temperature of the heater 6 is low, the viscosity of the lubricating oil is large, which affects the heat exchange efficiency and the speed of frost formation.
  • control device further includes a fourth unit for controlling the logical opening of the second electric valve 15.
  • the second electric valve 15 is logically controlled for opening degree to reduce the pressure ratio of the unit and maintain the operation of the unit.
  • the fourth unit opens the second electric valve 15 in accordance with logic control to reduce the unit pressure ratio, so that the compressor can Safe and stable operation.
  • the conducting device 5 includes an electric three-way valve, the first interface of the electric three-way valve is connected to the gas-liquid separator 4 through a pipe, and the second interface is connected to the heat exchanger 6 through a pipe
  • the third interface is connected to the first one-way valve 2 through a pipeline, and a controllable conduction pipeline between the heat exchanger 6 and the first one-way valve 2, or the heat exchanger 6 and the gas-liquid separator 4.
  • the conduction device 5 includes a first two-way solenoid valve and a second two-way solenoid valve, the first two-way solenoid valve is connected in series on the pipeline between the gas-liquid separator 4 and the heat exchanger 6, the second The two-way solenoid valve is connected in series on the pipeline between the heat exchanger 6 and the first one-way valve 2, the controllable conduction heat exchanger 6 and the gas-liquid separator 4, or the heat exchanger 6 and the first one-way valve 2.
  • Figure 3 shows another alternative embodiment of a heat pump system.
  • the heat pump system includes: a magnetic suspension centrifugal compressor 1, which is characterized in that it further includes a switching communication device 3 and a first electric valve 14; the exhaust pipe of the magnetic suspension centrifugal compressor 1 passes through the first unit
  • the valve 2 is connected to the first interface of the switching and communication device 3, and the suction pipe is connected to the third interface of the switching and communication device 3; the first electric valve 14 is provided in parallel with the magnetic suspension centrifugal compressor 1 for centrifuging the magnetic suspension
  • the compressor 1 is started and closed, the pressure difference between the high and low sides is reduced.
  • the first unit controls the first electric valve 14 to open, the second unit controls the first interface of the switching communication device 3 to communicate with the second interface, and the third interface communicates with the fourth interface to start the magnetic suspension centrifugal compressor 1; the first unit After the magnetic suspension centrifugal compressor 1 is started, the first electric valve 14 is controlled to be logically closed;
  • the heat pump system starts to cool, and the low-temperature and low-pressure medium is discharged through the exhaust pipe of the magnetic levitation centrifugal compressor 1 to become a high-temperature and high-pressure superheated gas.
  • the second interface is discharged, enters the gas-liquid separator 4 through the pipeline, and enters the heat exchange component; specifically, the gaseous medium is in the heat exchange component, enters the heat exchanger 6 through the conduction device 5, and transfers heat to the heat exchange
  • the gaseous medium is condensed into a high-temperature and high-pressure liquid at this time, and the medium becomes saturated after being throttled once by the first electronic expansion valve 8, and enters the flash tank 9 and the medium is divided into liquid and gaseous parts.
  • the liquid medium is output from the flash tank 9 and then throttled again by the second electronic expansion valve 10, then passes through the drying filter 11, the liquid storage tank 12 and enters the evaporator 13, and becomes a low-temperature superheated gaseous medium after evaporating and absorbing heat.
  • Switch the fourth port of the communication device into, exit from the third port, and return to the suction pipe of the magnetic levitation centrifugal compressor 1 through the pipeline.
  • the system continuously circulates cold water to dissipate the heat into the air; the gaseous medium comes from the flash tank 9 After output, through the first solenoid valve 16, through the pipeline into the intermediate air inlet of the magnetic levitation centrifugal compressor 1, mixed with the refrigerant after the completion of the first stage of compression, and then the second stage of compression, so that the second stage of compression
  • the refrigerant temperature is lowered, and the suction volume of the second stage compression is increased, thereby increasing the cooling capacity of the unit.
  • the first unit controls the first electric valve 14 to open, and the magnetic suspension centrifugal compressor 1 executes the shutdown command. After the shutdown is completed, the first unit controls the first electric valve 14 to logically close.
  • the first electric valve 14 it is opened before the magnetic levitation centrifugal compressor 1 is started, which is used to adjust the pressure difference between the high and low pressure sides of the compressor; it is opened before the compressor is turned off, Used to reduce the shutdown pressure ratio, so that the compressor can run smoothly.
  • the gaseous medium is directly passed into the intermediate air supply port of the magnetic suspension centrifugal compressor 1, mixed with the refrigerant after the first stage of compression, and then subjected to the second stage of compression, so that the temperature of the refrigerant entering the second stage of compression is reduced , At the same time, the suction volume of the second stage compression is increased, thereby increasing the cooling capacity of the unit and improving the cooling performance of the unit.
  • the fourth unit Open the second electric valve 15 according to logic control to reduce the pressure ratio of the unit, so that the compressor can run safely and smoothly; after the shutdown is completed, the fourth unit controls the second electric valve 15 to logically close.
  • Figure 4 shows another alternative embodiment of a heat pump system.
  • the heat pump system includes: a magnetic suspension centrifugal compressor 1, which is characterized in that it further includes a switching communication device 3 and a first electric valve 14; the exhaust pipe of the magnetic suspension centrifugal compressor 1 passes through the first unit
  • the valve 2 is connected to the first interface of the switching and communication device 3, and the suction pipe is connected to the third interface of the switching and communication device 3; the first electric valve 14 is provided in parallel with the magnetic suspension centrifugal compressor 1 for centrifuging the magnetic suspension
  • the compressor 1 is started and closed, the pressure difference between the high and low sides is reduced.
  • the first unit controls the first electric valve 14 to open, the second unit controls the first interface of the switching communication device 3 to communicate with the fourth interface, and the second interface communicates with the third interface to start the magnetic levitation centrifugal compressor 1; the first unit After the magnetic suspension centrifugal compressor 1 is started, the first electric valve 14 is controlled to be logically closed;
  • the heat pump system starts heating.
  • the low-temperature and low-pressure medium is discharged through the exhaust pipe of the magnetic levitation centrifugal compressor 1 and becomes a high-temperature and high-pressure superheated gas.
  • the gaseous medium passes through the first check valve 2 and enters through the first interface of the switching communication device 3. It is discharged from the fourth port and enters the evaporator 13 through the pipeline.
  • the gaseous medium is condensed into a high-temperature and high-pressure liquid through heat exchange in the evaporator 13, and then passes through the liquid storage tank 12, the drying filter 11, and the second electronic expansion valve 10 After the throttling is performed once, the medium becomes saturated, and after entering the flash tank 9, the medium in the saturated state is separated into two parts of liquid and gas.
  • the liquid medium After the liquid medium is output from the flash tank 9, it enters the heat exchange component, that is, after throttling again through the first electronic expansion valve 8, it enters the heat exchanger 6 through the filter 7, and becomes a low-temperature superheated gas after evaporating and absorbing heat.
  • the system continuously absorbs the air Heat to produce hot water by circulation; after being output from the flash tank 9, the gaseous medium passes through the first solenoid valve 16 and enters the intermediate air supply port of the magnetic levitation centrifugal compressor 1 through the pipeline, and is mixed with the refrigerant after the first stage of compression After the second stage of compression, the temperature of the refrigerant entering the second stage of compression is lowered, and at the same time, the air intake of the second stage of compression is increased, thereby increasing the unit's heating capacity.
  • the first unit controls the first electric valve 14 to open, and the magnetic suspension centrifugal compressor 1 executes the shutdown command. After the shutdown is completed, the first unit controls the first electric valve 14 to logically close.
  • the heating function of the unit of the magnetic levitation centrifugal compressor 1 is realized by switching the communication device 3; meanwhile, by setting the first electric valve 14, it is opened before the start of the magnetic levitation centrifugal compressor 1, It is used to adjust the pressure difference between the high and low pressure side of the compressor; it is opened before the compressor is turned off, and it is used to reduce the shutdown pressure ratio, so that the compressor can run smoothly.
  • the gaseous medium is directly passed into the intermediate air supply port of the magnetic suspension centrifugal compressor 1, mixed with the refrigerant after the first stage of compression, and then subjected to the second stage of compression, so that the temperature of the refrigerant entering the second stage of compression is reduced , At the same time, the suction volume of the second stage compression is increased, thereby increasing the heating capacity of the unit and improving the heating performance of the unit.
  • the fourth unit Open the second electric valve 15 according to logic control to reduce the pressure ratio of the unit, so that the compressor can run safely and smoothly; after the shutdown is completed, the fourth unit controls the second electric valve 15 to logically close.
  • the fourth unit opens the second electric valve under logical control, Reduce the unit pressure ratio to maintain unit operation.
  • Figure 5 shows another alternative embodiment of a heat pump system.
  • the heat pump system includes: a magnetic suspension centrifugal compressor 1, which is characterized in that it further includes a switching communication device 3 and a first electric valve 14; the exhaust pipe of the magnetic suspension centrifugal compressor 1 passes through the first unit
  • the valve 2 is connected to the first interface of the switching and communication device 3, and the suction pipe is connected to the third interface of the switching and communication device 3; the first electric valve 14 is provided in parallel with the magnetic suspension centrifugal compressor 1 for centrifuging the magnetic suspension
  • the compressor 1 is started and closed, the pressure difference between the high and low sides is reduced.
  • the temperature sensor 18 provided on the pipeline detects the ambient temperature.
  • the control device judges according to the logic to defrost the heat exchanger 6 that needs to be defrosted.
  • the specific connection relationship of the heat pump system is: turn off the fan 19 of the heat exchanger 6; the third unit controls the conduction device 5 to switch to the first unidirectional Valve 2 and the heat exchanger 6.
  • one end of the conducting device 5 is connected to the high-pressure pipe before the first check valve 2 and the switching communication device 3 through a pipe, and the other end is connected to the heat exchanger 6, and the other end of the heat exchanger 6 is connected to the The flash tank 9 is connected.
  • the pressure in the flash tank 9 is lower than the pressure in the high-pressure pipeline before the first one-way valve 2 and the switching communication device 3.
  • the heat exchanger 6 performs condensation heat exchange, the temperature of the heat exchanger 6 rises, and the frost melts to achieve the purpose of defrosting; and the condensed liquid medium returns to the flash tank 9 through the filter 7 and the first electronic expansion valve 8 to continue Participate in the cycle.
  • the heat pump system still maintains the heating mode and performs the heating cycle, and does not absorb heat from the evaporator 13 for defrosting.
  • the third unit controls the conduction device 5 to switch the heat exchanger 6 that needs to be defrosted, which is equivalent to Make it run in cooling mode and stop the fan 19 for defrosting. Because the other heat exchangers 6 still maintain the heating cycle.
  • the small pressure change of the system ensures the smooth operation of the magnetic levitation centrifugal compressor 1, and solves the problem of defrosting of the magnetic levitation centrifugal compressor 1. At the same time, the water temperature changes little during the defrosting process, and user comfort is improved.
  • the refrigerant directly communicates with the flash tank 9 through the first electronic expansion valve 8 of the liquid return pipeline, accurately controlling the refrigerant flow rate, increasing the discharge speed, and reducing the defrosting process
  • the amount of liquid stored in the middle heat exchanger 6; speeding up the heating speed of the fin heat exchanger 6 to quickly melt the ice layer on the fins, shortening the defrosting time, compared with other hot gas bypass defrosting solutions, this embodiment of the Defrost is faster.
  • the defrosting is performed one by one according to the order from the time when the defrost conditions are satisfied, and the third unit controls the conduction device in the heat exchange component where it is located. 5. Connect the pipeline.
  • the third unit controls the conducting device 5 in the heat exchange assembly one by one to conduct pipeline communication. Only one fin heat exchanger 6 is switched at a time, and the system pressure change is small, which ensures stable and reliable operation of the magnetic levitation centrifugal compressor 1, and solves the problem of defrosting of the heating operation of the magnetic levitation centrifugal compressor 1.
  • the fourth unit Open the second electric valve 15 according to logic control to reduce the pressure ratio of the unit, so that the compressor can run safely and smoothly; after the shutdown is completed, the fourth unit controls the second electric valve 15 to logically close.
  • the fourth unit opens the second electric valve 15 under logical control To reduce the pressure ratio of the unit and maintain the operation of the unit.
  • the conducting device 5 includes an electric three-way valve, the first interface of the electric three-way valve is connected to the gas-liquid separator 4 through a pipe, and the second interface is connected to the heat exchanger 6 through a pipe
  • the third interface is connected to the first one-way valve 2 through a pipeline, and a controllable conduction pipeline between the heat exchanger 6 and the first one-way valve 2, or the heat exchanger 6 and the gas-liquid separator 4.
  • the conduction device 5 includes a first two-way solenoid valve and a second two-way solenoid valve, the first two-way solenoid valve is connected in series on the pipeline between the gas-liquid separator 4 and the heat exchanger 6, the second The two-way solenoid valve is connected in series on the pipeline between the heat exchanger 6 and the first one-way valve 2, the controllable conduction heat exchanger 6 and the gas-liquid separator 4, or the heat exchanger 6 and the first one-way valve 2.
  • the disclosed products may be implemented in other ways.
  • the device embodiments described above are only schematic.
  • the division of the units is only a division of logical functions.
  • there may be other divisions for example, multiple units or components may be combined or Can be integrated into another system, or some features can be ignored, or not implemented.
  • the displayed or discussed mutual coupling or direct coupling or communication connection may be indirect coupling or communication connection through some interfaces, devices or units, and may be in electrical, mechanical or other forms. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

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Abstract

一种热泵系统，属于热泵机组技术领域。热泵系统包括磁悬浮离心压缩机（1），还包括切换连通装置（3）和第一电动阀（14）；磁悬浮离心压缩机（1）的排气管通过第一单向阀（2）连接该切换连通装置（3）的第一接口，吸气管连接该切换连通装置（3）的第三接口；第一电动阀（14）与磁悬浮离心压缩机（1）并联设置。通过切换连通装置（3）实现磁悬浮离心压缩机机组的制热功能；同时，通过设置第一电动阀（14），在磁悬浮离心压缩机的启动前开启，用于调整压缩机高低压侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。

Description

一种热泵系统
本申请基于申请号为201811382510.4、申请日为2018年11月20日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本发明涉及空调设备技术领域，特别涉及一种热泵系统。
背景技术
常规的风冷磁悬浮离心冷水机组，由于采用的磁悬浮离心压缩机不能承受压力的剧烈变化，没有可靠的制冷、制热切换方案，也无法解决制热过程中的除霜问题。
现有技术中，一种风冷螺杆热泵系统，通过使用四通换向阀进行制冷、制热的工况切换，但其进行机组除霜作业时，需按制冷循环运行，并关掉风机，制冷、制热工况的切换，及其逆循环除霜过程中，机组吸、排气侧压力变化剧烈，因此，无法应用于磁悬浮离心机组。
发明内容
本发明实施例提供了一种热泵系统，使得磁悬浮离心机组具备制冷、制热功能的同时，能快速稳定的进行除霜作业。为了对披露的实施例的一些方面有一个基本的理解，下面给出了简单的概括。该概括部分不是泛泛评述，也不是要确定关键/重要组成元素或描绘这些实施例的保护范围。其唯一目的是用简单的形式呈现一些概念，以此作为后面的详细说明的序言。
根据本发明实施例，提供了一种热泵系统。
在一些可选实施例中，该热泵系统包括磁悬浮离心压缩机，还包括切换连通装置和第一电动阀；该磁悬浮离心压缩机的排气管通过第一单向阀连接该切换连通装置的第一接口，吸气管连接该切换连通装置的第三接口；该第一电动阀与磁悬浮离心压缩机并联设置。
采用上述可选实施例，通过切换连通装置实现磁悬浮离心压缩机机组的制热功能；同时，通过设置第一电动阀，在该磁悬浮离心压缩机的启动前开启，用于调整压缩机高低压 侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。
应当理解的是，以上的一般描述和后文的细节描述仅是示例性和解释性的，并不能限制本发明。
附图说明
此处的附图被并入说明书中并构成本说明书的一部分，示出了符合本发明的实施例，并与说明书一起用于解释本发明的原理。
图1是一种热泵系统的一个可选实施结构示意图。
图2是一种热泵系统的另一个可选实施结构示意图。
图3是一种热泵系统的另一个可选实施结构示意图。
图4是一种热泵系统的另一个可选实施结构示意图。
图5是一种热泵系统的另一个可选实施结构示意图。
具体实施方式
以下描述和附图充分地示出本发明的具体实施方案，以使本领域的技术人员能够实践它们。实施例仅代表可能的变化。除非明确要求，否则单独的部件和功能是可选的，并且操作的顺序可以变化。一些实施方案的部分和特征可以被包括在或替换其他实施方案的部分和特征。本发明的实施方案的范围包括权利要求书的整个范围，以及权利要求书的所有可获得的等同物。在本文中，各实施方案可以被单独地或总地用术语“发明”来表示，这仅仅是为了方便，并且如果事实上公开了超过一个的发明，不是要自动地限制该应用的范围为任何单个发明或发明构思。本文中，诸如第一和第二等之类的关系术语仅仅用于将一个实体或者操作与另一个实体或操作区分开来，而不要求或者暗示这些实体或操作之间存在任何实际的关系或者顺序。而且，术语“包括”、“包含”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的过程、方法或者设备不仅包括那些要素，而且还包括没有明确列出的其他要素。本文中各个实施例采用递进的方式描述，每个实施例重点说明的都是与其他实施例的不同之处，各个实施例之间相同相似部分互相参见即可。对于实施例公开的结构、产品等而言，由于其与实施例公开的部分相对应，所以描述的比较简单，相关之处参见方法部分说明即可。
图1示出一种热泵系统的一个可选实施例。
该可选实施例中，该热泵系统，包括：包括磁悬浮离心压缩机1，其特征在于，还包括切换连通装置3和第一电动阀14；
该磁悬浮离心压缩机1的排气管通过第一单向阀2连接该切换连通装置3的第一接口，吸气管连接该切换连通装置3的第三接口；
该第一电动阀14与该磁悬浮离心压缩机1并联设置，用于在该磁悬浮离心压缩机1启动、关闭时，减小高低侧压差。
可选的，该切换连通装置3的第二接口连接气液分离器4，该气液分离器4连接蒸发器13；该气液分离器4还依次连接换热组件、闪蒸罐9，该换热组件还连接第一单向阀2；该闪蒸罐9的气体出口连接该磁悬浮离心压缩机1的中间补气口；该闪蒸罐9还依次连接储液罐12、蒸发器13；该蒸发器13连接该切换连通装置3的第四接口。
可选的，该气液分离器4与该蒸发器13之间的管道上设有第二电动阀15，用于降低机组负荷。
可选的，该换热组件包括依次连接的导通装置5、换热器6、过滤器7和第一电子膨胀阀8，该导通装置5可控的连接该第一单向阀2与该换热器6，或，该气液分离器4与该换热器6；该第一电子膨胀阀8连接闪蒸罐9。可选的，该换热组件为多个并联设置的换热组件。
可选的，该热泵系统还包括控制装置，该控制装置包括：
第一单元，用于控制该第一电动阀14的导通、关闭；
第二单元，用于控制该切换连通装置3根据运行指令导通。
可选的，该第一单元控制该第一电动阀14导通后，该磁悬浮离心压缩机1执行启动或关闭指令，执行完毕后，该第一单元控制该第一电动阀14关闭。
可选的，当运行指令为第一模式运行指令，该第二单元控制该切换连通装置3的第一接口与第二接口连通，第三接口与第四接口连通；当该运行指令为第二模式运行指令，该第二单元控制该切换连通装置3的第一接口与第四接口连通，第二接口与第三接口连通。
可选的，该控制装置还包括第三单元，当该运行指令为第二模式时，该第三单元控制该导通装置5连通该第一单向阀2和该换热器6，或该气液分离器4和该换热器6。
可选的，当需要对换热器6进行除霜时，该第三单元控制该导通装置5连通该第一单 向阀2和该换热器6。
可选的，该磁悬浮离心压缩机可以包括1台或多台压缩机。采用大压比双级型磁悬浮离心压缩机，通过系统优化设计，很好的解决现有技术中风冷磁悬浮离心冷水机组只能制冷不能制热的问题，另一方面也解决了传统风冷螺杆热泵螺杆机组和风冷涡旋热泵机组存在的综合部分性能系数偏低、噪声大、制热回油困难、润滑油影响换热性能等诸多问题，具有高效、高可靠性、低噪、制热舒适性好等显著优势。
采用图1示出的可选实施例，通过切换连通装置3实现磁悬浮离心压缩机1机组的制热功能；同时，通过设置第一电动阀14，在该磁悬浮离心压缩机1的启动前开启，用于调整压缩机高低压侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。
在另一个可选实施例中，该控制装置还包括第四单元，用于对该第二电动阀15进行逻辑开度控制。可选的，当环境温度低于第一阈值时，对第二电动阀15按逻辑进行开度控制，降低机组压比，维持机组运行。可选的，当机组在高压比工况条件下运行时，在该磁悬浮离心压缩机1停机前，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，使该压缩机能够安全平稳运行。
图2示出一种热泵系统的另一个可选实施例。
该可选实施例中，该热泵系统包括：包括磁悬浮离心压缩机1，其特征在于，还包括切换连通装置3和第一电动阀14；
该磁悬浮离心压缩机1的排气管通过第一单向阀2连接该切换连通装置3的第一接口，吸气管连接该切换连通装置3的第三接口；
该第一电动阀14与该磁悬浮离心压缩机1并联设置，用于在该磁悬浮离心压缩机1启动、关闭时，减小高低侧压差。
可选的，该切换连通装置3包括电动四通阀，在机组停机时通过该电动四通阀进行制冷、制热切换，避免压缩机运行过程中切换四通换向阀，使高、低压力剧烈变化导致压缩机故障。
可选的，该切换连通装置3的第二接口连接气液分离器4，该气液分离器4连接蒸发器13；该气液分离器4还依次连接换热组件、闪蒸罐9，该换热组件还连接第一单向阀2；该闪蒸罐9的气体出口通过第一电磁阀16连接该磁悬浮离心压缩机1的中间补气口；该 闪蒸罐9还依次连接储液罐12、蒸发器13；该蒸发器13连接该切换连通装置3的第四接口。
可选的，该气液分离器4与该蒸发器13之间的管道上设有第二电动阀15，用于降低该磁悬浮离心压缩机1的压比。
可选的，该换热组件包括依次连接的导通装置5、换热器6、过滤器7和第一电子膨胀阀8，该导通装置5可控的连接该第一单向阀2与该换热器6，或，该气液分离器4与该换热器6；该第一电子膨胀阀8连接闪蒸罐9。
可选的，还包括设置在该磁悬浮离心压缩机1吸气管、排气管上的温度传感器18、压力传感器17。该压力传感器17用于检测机组压力，当机组在高压比工况下运行时，执行停机指令前，逻辑控制打开第二电动阀15。
可选的，还包括设置在换热器6与过滤器7之间的温度传感器18。用于检测环境温度，以判断换热器6是否需要进行除霜作业。
可选的，还包括串联连接在该储液罐12与闪蒸罐9之间的干燥过滤器11、第二电子膨胀阀10，分别用于过滤杂质和节流。
采用图2所示的可选实施例，通过切换连通装置3实现磁悬浮离心压缩机1机组的制热功能；同时，通过设置第一电动阀14，在该磁悬浮离心压缩机1的启动前开启，用于调整压缩机高低压侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。一方面，机组制冷、制热循环采用电动四通阀在压缩机停机时切换，对压缩机完全无冲击，实现了磁悬浮离心压缩机1制冷、制热双工况运行，具有较高的可靠性；另一方面，采用磁悬浮离心压缩机1，其设有无齿轮和滚动轴承，通过变频调节，有超高的气动和机械效率，因此该热泵系统为无油循环，解决了制热时翅片换热器6温度较低时润滑油粘度大，影响换热效率、结霜速度快等问题。
在另一个可选实施例中，该控制装置还包括第四单元，用于对该第二电动阀15进行逻辑开度控制。可选的，当环境温度低于第一阈值时，对第二电动阀15按逻辑进行开度控制，降低机组压比，维持机组运行。可选的，当机组在高压比工况条件下运行时，在该磁悬浮离心压缩机1停机前，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，使该压缩机能够安全平稳运行。
在另一个可选实施例中，该导通装置5包括电动三通阀，该电动三通阀的第一接口通 过管道与气液分离器4连接，第二接口通过管道与换热器6连接，第三接口通过管道与第一单向阀2连接，可控的导通换热器6与第一单向阀2，或换热器6与气液分离器4之间的管路。可选的，该导通装置5包括第一双向电磁阀、第二双向电磁阀，该第一双向电磁阀串联连接在气液分离器4与换热器6之间的管路上，该第二双向电磁阀串联连接在换热器6与第一单向阀2之间的管路上，可控的导通换热器6与气液分离器4，或换热器6与第一单向阀2。
图3示出一种热泵系统的另一个可选实施例。
该可选实施例中，该热泵系统包括：包括磁悬浮离心压缩机1，其特征在于，还包括切换连通装置3和第一电动阀14；该磁悬浮离心压缩机1的排气管通过第一单向阀2连接该切换连通装置3的第一接口，吸气管连接该切换连通装置3的第三接口；该第一电动阀14与该磁悬浮离心压缩机1并联设置，用于在该磁悬浮离心压缩机1启动、关闭时，减小高低侧压差。
结合图3，当运行指令为第一模式运行指令，进入制冷模式时，该热泵系统具体连通关系为：
第一单元控制该第一电动阀14开启，第二单元控制该切换连通装置3的第一接口与第二接口连通，第三接口与第四接口连通，启动磁悬浮离心压缩机1；第一单元在该磁悬浮离心压缩机1启动后控制该第一电动阀14逻辑关闭；
热泵系统开始进行制冷，低温低压介质经磁悬浮离心压缩机1排气管排出，成为高温高压过热的气体，该气态介质经过第一单向阀2，通过切换连通装置3的第一接口进入，自第二接口排出，经管道进入气液分离器4后，进入换热组件；具体的，该气态介质在换热组件内，经导通装置5进入换热器6，通过热交换将热量传递至空气中，此时气态介质冷凝为高温高压的液态，经第一电子膨胀阀8进行一次节流后变为饱和状态的介质，进入闪蒸罐9中该介质分为液态、气态两部分。其中，液态介质自闪蒸罐9输出后经第二电子膨胀阀10再次节流后，经过干燥过滤器11、储液罐12进入蒸发器13，蒸发吸热后变为低温过热气态介质，经切换联通装置的第四接口进入，自第三接口排出，通过管道回到该磁悬浮离心压缩机1的吸气管，系统不断循环制取冷水，把热量散发至空气中；气态介质自闪蒸罐9输出后，经第一电磁阀16，通过管道进入该磁悬浮离心压缩机1的中间补气口，与完成第一级压缩后的制冷剂混合后进行第二级压缩，使进入第二级压缩的制冷剂温度得到降低，同时提升了第二级压缩的吸气量，从而增加机组制冷量。
当热泵系统接收停机指令时，第一单元控制该第一电动阀14开启，磁悬浮离心压缩机1执行停机指令，停机完成后，第一单元控制该第一电动阀14逻辑关闭。
采用图3所示的可选实施例，通过设置第一电动阀14，在该磁悬浮离心压缩机1的启动前开启，用于调整压缩机高低压侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。另一方面，将气态介质直接通入磁悬浮离心压缩机1的中间补气口，与完成第一级压缩后的制冷剂混合后进行第二级压缩，使进入第二级压缩的制冷剂温度得到降低，同时提升了第二级压缩的吸气量，从而增加机组制冷量，提高了机组的制冷性能。
在另一个可选实施例中，当设置在该磁悬浮离心压缩机1前后的压力传感器17检测到机组在高压比工况条件下运行时，在该磁悬浮离心压缩机1停机前，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，使该压缩机能够安全平稳运行；停机完成后，第四单元控制该第二电动阀15逻辑关闭。
图4示出一种热泵系统的另一个可选实施例。
该可选实施例中，该热泵系统包括：包括磁悬浮离心压缩机1，其特征在于，还包括切换连通装置3和第一电动阀14；该磁悬浮离心压缩机1的排气管通过第一单向阀2连接该切换连通装置3的第一接口，吸气管连接该切换连通装置3的第三接口；该第一电动阀14与该磁悬浮离心压缩机1并联设置，用于在该磁悬浮离心压缩机1启动、关闭时，减小高低侧压差。
结合图4，当运行指令为第二模式运行指令，进入制热模式时，该热泵系统具体连通关系为：
第一单元控制该第一电动阀14开启，第二单元控制该切换连通装置3的第一接口与第四接口连通，第二接口与第三接口连通，启动磁悬浮离心压缩机1；第一单元在该磁悬浮离心压缩机1启动后控制该第一电动阀14逻辑关闭；
热泵系统开始进行制热，低温低压介质经磁悬浮离心压缩机1排气管排出，成为高温高压过热的气体，该气态介质经过第一单向阀2，通过切换连通装置3的第一接口进入，自第四接口排出，经管道进入蒸发器13，该气态介质在蒸发器13中通过热交换，冷凝为高温高压液体，依次经过储液罐12、干燥过滤器11，在第二电子膨胀阀10进行一次节流后变为饱和状态的介质，进入闪蒸罐9后，该饱和状态的介质分离为液态、气态两部分。 其中，液态介质自闪蒸罐9输出后，进入换热组件，即经过第一电子膨胀阀8进行再次节流后，经过滤器7进入换热器6，蒸发吸热后变为低温过热气体，经导通装置5进入气液分离罐后，自切换连通装置3的第二接口进入，自第三接口排出，通过管道回到该磁悬浮离心压缩机1的吸气管，系统不断吸收空气中的热量，循环制取热水；气态介质自闪蒸罐9输出后，经第一电磁阀16，通过管道进入该磁悬浮离心压缩机1的中间补气口，与完成第一级压缩后的制冷剂混合后进行第二级压缩，使进入第二级压缩的制冷剂温度得到降低，同时提升了第二级压缩的吸气量，从而增加机组制热量。
当热泵系统接收停机指令时，第一单元控制该第一电动阀14开启，磁悬浮离心压缩机1执行停机指令，停机完成后，第一单元控制该第一电动阀14逻辑关闭。
采用图4所示的可选实施例，通过切换连通装置3实现磁悬浮离心压缩机1机组的制热功能；同时，通过设置第一电动阀14，在该磁悬浮离心压缩机1的启动前开启，用于调整压缩机高低压侧的压差；在压缩机关闭前开启，用于降低停机压比，使得压缩机能够平稳运行。另一方面，将气态介质直接通入磁悬浮离心压缩机1的中间补气口，与完成第一级压缩后的制冷剂混合后进行第二级压缩，使进入第二级压缩的制冷剂温度得到降低，同时提升了第二级压缩的吸气量，从而增加机组制热量，提高了机组的制热性能。
在另一个可选实施例中，当设置在该磁悬浮离心压缩机1前后的压力传感器17检测到机组在高压比工况条件下运行时，在该磁悬浮离心压缩机1停机前，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，使该压缩机能够安全平稳运行；停机完成后，第四单元控制该第二电动阀15逻辑关闭。
在另一个可选实施例中，当设置在该磁悬浮离心压缩机1前后的温度传感器18检测到机组在低温条件下进行制热模式运行时，该第四单元按逻辑控制打开第二电动阀，降低机组压比，维持机组运行。
图5示出一种热泵系统的另一个可选实施例。
该可选实施例中，该热泵系统包括：包括磁悬浮离心压缩机1，其特征在于，还包括切换连通装置3和第一电动阀14；该磁悬浮离心压缩机1的排气管通过第一单向阀2连接该切换连通装置3的第一接口，吸气管连接该切换连通装置3的第三接口；该第一电动阀14与该磁悬浮离心压缩机1并联设置，用于在该磁悬浮离心压缩机1启动、关闭时，减小高低侧压差。
可选的，当运行指令为第二模式运行指令，进入制热模式时，设置在管道上的温度传感器18对环境温度进行检测。其中，当设置在换热器6与过滤器7之间的温度传感器18检测到环境温度较低时，控制装置根据看逻辑判断对需要进行除霜的换热器6进行除霜。
结合图5，当对换热器6进行除霜时，该热泵系统具体连通关系为：关闭该换热器6的风机19；第三单元控制导通装置5，切换至连该第一单向阀2和该换热器6。此时，因导通装置5的一端通过管道连接在第一单向阀2与切换连通装置3之前的高压管道上，另一端与换热器6连接，换热器6的另一端通过管道与闪蒸罐9连接，此时闪蒸罐9中的压力低于第一单向阀2与切换连通装置3之前的高压管道中的压力，磁悬浮离心压缩机1排出管排出的高温高压介质进入换热器6进行冷凝换热，换热器6的温度升高，霜融化，达到除霜的目的；而冷凝后的液态介质经过滤器7、第一电子膨胀阀8回到闪蒸罐9中继续参与循环。
在除霜过程中，该热泵系统仍然保持制热模式，进行制热循环，不会从蒸发器13中吸收热量用于除霜。
通过采用图5所示的可选实施例，当系统中某个换热器6满足除霜条件时，通过第三单元控制导通装置5对需要除霜的换热器6进行切换，相当于使其运行制冷模式并停风机19进行除霜。因其它换热器6仍然保持制热循环。系统压力变化小，确保了磁悬浮离心压缩机1平稳运行，解决了磁悬浮离心压缩机1除霜问题；同时在除霜过程中水温度变化小，用户舒适性得到提升。另一方面，换热器6除霜时，制冷剂直接通过回液管道的第一电子膨胀阀8与闪蒸罐9连通，精确控制冷剂流量，提高了排液速度，降低了除霜过程中换热器6的存液量；加快了翅片换热器6的升温速度，使翅片上的冰层迅速融化，缩短了除霜时间，较其它热气旁通除霜方案，本实施例的除霜速度更快。
在另一个可选实施例中，当多个换热组件中的多个换热器6需要进行除霜时，每次只对一组换热组件中的换热器6进行除霜，该换热器6除霜完成后再对其他满足条件的换热器6进行除霜。可选的，多个待除霜的换热组件间，按照满足除霜条件的时间由先到后的顺序，逐一进行除霜，该第三单元逐一控制其所在换热组件内的导通装置5，进行管路连通。可选的，当多个换热组件中的多个换热器6需要进行除霜时，按照各换热组件内温度传感器18所检测的温度值，按照由低向高的顺序，逐一进行除霜，该第三单元逐一控制其所在换热组件内的导通装置5进行管路连通。每次仅对一个翅换热器6进行切换，系统压力变化小，确保了磁悬浮离心压缩机1稳定可靠运行，解决了磁悬浮离心压缩机1系统 制热运行的除霜问题。
在另一个可选实施例中，当设置在该磁悬浮离心压缩机1前后的压力传感器17检测到机组在高压比工况条件下运行时，在该磁悬浮离心压缩机1停机前，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，使该压缩机能够安全平稳运行；停机完成后，第四单元控制该第二电动阀15逻辑关闭。
在另一个可选实施例中，当设置在该磁悬浮离心压缩机1前后的温度传感器18检测到机组在低温条件下进行制热模式运行时，该第四单元按逻辑控制打开第二电动阀15，降低机组压比，维持机组运行。
在另一个可选实施例中，该导通装置5包括电动三通阀，该电动三通阀的第一接口通过管道与气液分离器4连接，第二接口通过管道与换热器6连接，第三接口通过管道与第一单向阀2连接，可控的导通换热器6与第一单向阀2，或换热器6与气液分离器4之间的管路。可选的，该导通装置5包括第一双向电磁阀、第二双向电磁阀，该第一双向电磁阀串联连接在气液分离器4与换热器6之间的管路上，该第二双向电磁阀串联连接在换热器6与第一单向阀2之间的管路上，可控的导通换热器6与气液分离器4，或换热器6与第一单向阀2。
本文所披露的可选实施例中，应该理解到，所揭露的产品(包括但不限于装置、设备等)，可以通过其它的方式实现。例如，以上所描述的装置实施例仅仅是示意性的，例如，所述单元的划分，仅仅为一种逻辑功能划分，实际实现时可以有另外的划分方式，例如多个单元或组件可以结合或者可以集成到另一个系统，或一些特征可以忽略，或不执行。另一点，所显示或讨论的相互之间的耦合或直接耦合或通信连接可以是通过一些接口，装置或单元的间接耦合或通信连接，可以是电性，机械或其它的形式。可以根据实际的需要选择其中的部分或者全部单元来实现本实施例方案的目的。
应当理解的是，本发明并不局限于上面已经描述并在附图中示出的流程及结构，并且可以在不脱离其范围进行各种修改和改变。本发明的范围仅由所附的权利要求来限制。

Claims (10)

  1. 一种热泵系统，包括磁悬浮离心压缩机，其特征在于，还包括切换连通装置和第一电动阀；
    所述磁悬浮离心压缩机的排气管通过第一单向阀连接所述切换连通装置的第一接口，吸气管连接所述切换连通装置的第三接口；
    所述第一电动阀与所述磁悬浮离心压缩机并联设置。
  2. 根据权利要求1所述的热泵系统，其特征在于，所述切换连通装置的第二接口连接气液分离器，所述气液分离器连接蒸发器；所述气液分离器还依次连接换热组件、闪蒸罐，所述换热组件还连接第一单向阀；所述闪蒸罐的气体出口连接所述磁悬浮离心压缩机的中间补气口；所述闪蒸罐还依次连接储液罐、蒸发器；所述蒸发器连接所述切换连通装置的第四接口。
  3. 根据权利要求2所述的热泵系统，其特征在于，所述气液分离器与所述蒸发器之间的管道上设有第二电动阀，用于降低机组负荷。
  4. 根据权利要求2所述的热泵系统，其特征在于，所述换热组件包括依次连接的导通装置、换热器、过滤器和第一电子膨胀阀，所述导通装置可控的连接所述第一单向阀与所述换热器，或，所述气液分离器与所述换热器；所述第一电子膨胀阀连接闪蒸罐。
  5. 根据权利要求2所述的热泵系统，其特征在于，所述换热组件为多个并联设置的换热组件。
  6. 根据权利要求1所述的热泵系统，其特征在于，所述热泵系统还包括控制装置，所述控制装置包括：
    第一单元，用于控制所述第一电动阀的导通、关闭；
    第二单元，用于控制所述切换连通装置根据运行指令导通。
  7. 根据权利要求6所述的热泵系统，其特征在于，所述第一单元控制所述第一电动阀导通后，所述磁悬浮离心压缩机执行启动或关闭指令，执行完毕后，所述第一单元控制所述第一电动阀关闭。
  8. 根据权利要求6所述的热泵系统，其特征在于，当运行指令为第一模式运行 指令，所述第二单元控制所述切换连通装置的第一接口与第二接口连通，第三接口与第四接口连通；
    当所述运行指令为第二模式运行指令，所述第二单元控制所述切换连通装置的第一接口与第四接口连通，第二接口与第三接口连通。
  9. 根据权利要求8所述的热泵系统，其特征在于，所述控制装置还包括第三单元，当所述运行指令为第二模式时，所述第三单元控制所述导通装置连通所述第一单向阀和所述换热器，或所述气液分离器和所述换热器。
  10. 根据权利要求9所述的热泵系统，其特征在于，当需要对换热器进行除霜时，所述第三单元控制所述导通装置连通所述第一单向阀和所述换热器。
PCT/CN2018/123015 2018-11-20 2018-12-24 一种热泵系统 Ceased WO2020103271A1 (zh)

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