WO2020019608A1 - 压缩机和制冷装置 - Google Patents

压缩机和制冷装置 Download PDF

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Publication number
WO2020019608A1
WO2020019608A1 PCT/CN2018/117592 CN2018117592W WO2020019608A1 WO 2020019608 A1 WO2020019608 A1 WO 2020019608A1 CN 2018117592 W CN2018117592 W CN 2018117592W WO 2020019608 A1 WO2020019608 A1 WO 2020019608A1
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WO
WIPO (PCT)
Prior art keywords
port
state
compressor
valve
bypass valve
Prior art date
Application number
PCT/CN2018/117592
Other languages
English (en)
French (fr)
Inventor
高斌
Original Assignee
广东美芝制冷设备有限公司
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
Priority claimed from CN201821192720.2U external-priority patent/CN208456860U/zh
Priority claimed from CN201810828639.7A external-priority patent/CN110762009A/zh
Priority claimed from CN201821192650.0U external-priority patent/CN208456859U/zh
Priority claimed from CN201810827208.9A external-priority patent/CN110762008A/zh
Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to CA3107528A priority Critical patent/CA3107528C/en
Publication of WO2020019608A1 publication Critical patent/WO2020019608A1/zh
Priority to US17/153,367 priority patent/US11933526B2/en

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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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • 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
    • 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
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/07—Details of compressors or related parts
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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

Definitions

  • the present disclosure belongs to the technical field of compressor manufacturing, and in particular, relates to a compressor and a refrigeration device having the same.
  • the compression of the compressor and the throttling effect of the throttling structure convert the refrigerant between low temperature and low pressure and high temperature and high pressure, and use the heat exchanger to achieve heat exchange with the surrounding environment to achieve refrigeration or refrigeration. Thermal effect.
  • the compressor is one of the very important parts in the refrigeration device. The design of the compressor has an important impact on the energy efficiency and operating reliability of the refrigeration device.
  • the pressure difference between the suction side and the exhaust side of the compressor must be within a certain range before it can be restarted, especially for rolling-rotor compressors.
  • the pressure difference must reach a smaller value, such as within 1 kgf / cm 2 , otherwise the compressor cannot be started and restarted again, and the fast start function cannot be realized.
  • the compressor when the compressor is stopped, the refrigerant in the high-pressure side heat exchanger will quickly return to the low-pressure side through the gap between the compressor components, thereby increasing the temperature in the low-pressure side heat exchanger. And pressure, in this case, the heat in the high-pressure side heat exchanger is wasted and the cooling capacity in the low-pressure side heat exchanger is lost, which is not conducive to the operating efficiency of the refrigeration device.
  • the compression of the compressor and the throttling effect of the throttling structure convert the refrigerant between low temperature and low pressure and high temperature and high pressure, and use the heat exchanger to achieve heat exchange with the surrounding environment to achieve refrigeration or refrigeration. Thermal effect.
  • the compressor is one of the very important parts in the refrigeration device. The design of the compressor has an important impact on the energy efficiency and operating reliability of the refrigeration device.
  • the present disclosure aims to solve at least one of the technical problems existing in the prior art.
  • a compressor includes: a sealed container; a motor portion and a compression mechanism portion, the motor portion and the compression mechanism portion are both disposed in the sealed container; a bypass valve; wherein the compressor has A separate exhaust side and an intake side, the exhaust side is connected to the bypass valve, and the exhaust side is adapted to exhaust external components through the bypass valve or through the bypass A valve is in communication with the suction side.
  • the compressor can be quickly restarted, and the residual heat can be utilized after the compressor is stopped, which has high energy efficiency.
  • the bypass valve includes a valve body defining a valve cavity, and the valve body is provided with a plurality of ports communicating with the valve cavity.
  • a valve core Connected to the exhaust side, the suction side, and the external parts; a valve core, the valve core is movably disposed in the valve body, the valve core has a flow channel, and a plurality of the valve cores Ports are selectively connectable through the flow channel.
  • the bypass valve further includes: an electromagnetic control portion, and the electromagnetic control portion is electromagnetically connected with the valve core.
  • the bypass valve includes a first port, a second port, and a third port, and the first port is selectively connectable with the second port and the third port.
  • the first port is in communication with the exhaust side
  • the third port is in communication with the suction side
  • the exhaust side is adapted to exhaust external components through the second port.
  • At least a part of the valve body is movably provided in the valve body along an axial direction of the valve body, and the first port is provided in an axial direction of the valve body.
  • a first end, the second port is provided on a first side of the valve body
  • the third port is provided on a second side of the valve body
  • the flow channel has a A first open end, a second open end toward the first side, and a third open end toward the second side; wherein when the second open end is opposite to the second port, the first open end A port is in communication with the second port; when the third open end is opposite to the third port, the first port is in communication with the third port.
  • the bypass valve includes a first port, a second port, a third port, and a fourth port, and the first port is selectively connectable with the second port and the second port.
  • One of the third ports is in communication
  • the fourth port is selectively in communication with the third port
  • the first port is in communication with the exhaust side
  • the third port is in communication with the intake side
  • the exhaust side is adapted to exhaust external components through the second port, so The suction side is adapted to suck air to external components through the fourth port.
  • the valve core has a first flow passage, a second flow passage, and a third flow passage, and the first port and the second port are adapted to communicate through the first flow passage and The third port and the fourth port are adapted to communicate through the second flow channel, or the first port and the third port are adapted to communicate through the third flow channel.
  • At least a part of the valve body is movably provided in the valve body along an axial direction of the valve body, and the first port and the third port are provided in the valve body.
  • the first side of the valve body is arranged at intervals in the axial direction
  • the second port and the fourth port are arranged at the second side of the valve body and are arranged at intervals in the axial direction.
  • Open ends and two open ends of the second flow path respectively face the first side and a second side of the valve body, and both open ends of the third flow path face the first side of the valve body side.
  • the first flow path and the second flow path are spaced apart along the axial direction of the valve core, and the second flow path is along the axial direction of the valve core.
  • the width is larger than the width of the first flow channel in the axial direction of the valve core.
  • the bypass valve has a first state and a second state.
  • the exhaust side communicates with external components through the bypass valve, and in the second state In the state, the exhaust side communicates with the intake side through the bypass valve;
  • the compressor is configured to switch the bypass valve from the first state to The second state;
  • the compressor is configured to switch the bypass valve from the second state to the first state when the motor section is started from a stopped state.
  • the bypass valve has a first state, a second state, and a third state.
  • the exhaust side communicates with external components through the bypass valve.
  • the exhaust side is disconnected from the intake side
  • the second state the exhaust side is disconnected from external components, and the exhaust side is connected to the intake side through the bypass valve The side is connected.
  • the third state the exhaust side is disconnected from external components, and the exhaust side is disconnected from the intake side.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state, and when P1 ⁇ P2, the bypass valve is switched to the first state.
  • P1 ⁇ P2 if If the motor section is not stopped, the bypass valve is maintained in a third state, and if the motor section is stopped, the bypass valve is switched to a second state; where P1 is the pressure at the first port and P2 is all The pressure at the second port is described.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state and is maintained for a preset time t. If the motor part is not stopped, the bypass valve is switched to the first state. If the motor part is stopped, the bypass valve is switched to the second state.
  • the compressor according to an embodiment of the present disclosure satisfies: 1 second ⁇ t ⁇ 10 seconds.
  • the compressor according to an embodiment of the present disclosure further includes: a reservoir, an outlet of the reservoir is in communication with an air inlet of the compression mechanism portion, and an suction pipe is provided on the reservoir, and
  • the suction side includes the reservoir and the suction pipe;
  • the sealed container defines a high-pressure receiving cavity, and the sealed container is provided with an exhaust pipe, and the exhaust side includes the receiving cavity and the Mentioned exhaust pipe.
  • the sealed container defines a low-pressure first cavity and a high-pressure second cavity
  • the sealed container is provided with an air suction pipe communicating with the first cavity
  • the seal is provided with an exhaust pipe communicating with the second cavity
  • the suction side includes the first cavity and the suction tube
  • the exhaust side includes the second cavity and the exhaust tube.
  • the present disclosure also provides a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • the throttle valve Connected to the bypass valve, the throttle valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the first interface of the second heat exchanger Two interfaces are connected to the suction port of the compressor.
  • the present disclosure also provides a refrigeration device including: a reversing device, a first heat exchanger, a throttle valve, a second heat exchanger, and the compressor according to any one of the above, wherein the reversing device includes a first One port, second port, third port, and fourth port, the first port is connected to the bypass valve, the second port is connected to the first interface of the first heat exchanger, and the node
  • the flow valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the second interface of the second heat exchanger is connected to the fourth port.
  • the third port is connected to the suction port of the compressor.
  • the refrigeration device and the above-mentioned compressor have the same advantages over the prior art, and are not repeated here.
  • FIG. 1 to 5 are schematic structural diagrams of a refrigeration device according to a first embodiment of the present disclosure
  • FIG. 6 is a schematic structural diagram of a bypass valve in a first state according to a first embodiment of the present disclosure
  • FIG. 7 is a schematic structural diagram of a bypass valve according to a first embodiment of the present disclosure in a second state
  • FIG. 8 is a schematic structural diagram of a bypass valve according to a first embodiment of the present disclosure in a third state
  • FIG. 9 to 13 are schematic structural diagrams of a refrigeration device according to an embodiment of the present disclosure.
  • FIG. 14 is a schematic structural diagram of a bypass valve in a first state according to an embodiment of the present disclosure
  • FIG. 15 is a schematic structural diagram of a bypass valve in a second state according to an embodiment of the present disclosure.
  • 16 is a schematic structural diagram of a bypass valve in a third state according to an embodiment of the present disclosure.
  • Compressor 1 sealed container 11, exhaust pipe 12, exhaust side pipe 12a, suction pipe 13, suction side pipe 13a, first heat exchanger 2, second heat exchanger 3, throttle valve 4 Reversing device 5, first port 5a, second port 5b, third port 5c, fourth port 5d, bypass valve 6, first port 6a, second port 6b, third port 6c, valve body 6d,
  • a compressor 1 according to an embodiment of the present disclosure is described below with reference to FIGS. 1 to 8.
  • the compressor 1 includes a sealed container 11, a motor portion, a compression mechanism portion, and a bypass valve 6.
  • the compressor 1 has a separate exhaust side and an intake side.
  • the exhaust side is a high-pressure side and the intake side is a low-pressure side.
  • the motor part and the compression mechanism part are both provided in a sealed container 11.
  • the motor part is used for The compression mechanism is driven to realize the intake and compression of exhaust.
  • the bypass valve 6 includes a first port 6a, a second port 6b, and a third port 6c.
  • the first port 6a can be selectively connected to the second port 6b and the third port.
  • One of 6c is connected, wherein the first port 6a is in communication with the exhaust side of the compressor 1, the third port 6c is in communication with the suction side of the compressor 1, and the exhaust side is adapted to be discharged to external parts through the second port 6b gas.
  • the compressor 1 is connected to the external pipeline through the second port 6b.
  • the exhaust side of the compressor is disconnected from the external pipeline, and the high-pressure side heat exchanger The remaining heat can be reused.
  • the motor part works, the first port 6a of the bypass valve 6 communicates with the second port 6b, the third port 6c of the bypass valve 6 is disconnected from the first port 6a, and the third port 6c is disconnected from the first port 6a, the high-pressure gas output from the compressor 1 is output from the exhaust side to the exhaust-side pipe 12a of the refrigeration device through the first port 6a and the second port 6b, and the suction side of the compressor 1 The air is sucked through the suction-side pipe 13a.
  • the bypass valve 6 When the compressor 1 stops operating, the motor section is not operated, the first port 6a of the bypass valve 6 is communicated with the third port 6c, and the first port 6a is disconnected from the second port 6b. That is, the bypass valve 6 communicates the exhaust side and the intake side of the compressor 1 and disconnects the exhaust side of the compressor 1 from other components of the refrigeration device.
  • the bypass valve 6 cuts off the communication between the exhaust side of the compressor 1 and the refrigeration device.
  • the high-pressure side heat exchanger maintains a high pressure state, and the throttle valve 3 is at a differential pressure. Still has a certain flow rate, so that the remaining heat of the high-pressure side heat exchanger can still be radiated and the low-pressure side heat exchanger can still have the ability to absorb heat by evaporation.
  • the refrigeration device The remaining heat in the heat exchanger can still be used, thereby improving the overall efficiency of the refrigeration device, enabling the remaining heat of the system to be utilized, and being simple, reliable, and energy-efficient.
  • the bypass valve 6 disconnects the high-pressure side of the compressor from the high-pressure side heat exchanger and directly communicates with the low-pressure side of the compressor. And the bypass valve 6 has a direct communication channel. In this way, the high pressure side and the low pressure side of the compressor 1 can quickly achieve pressure balance, and meet the requirements of the compressor when the pressure difference is less than 1kgf / cm2, thereby achieving the compressor shutdown. After quick restart function.
  • the pressure equilibration time obtained by the inventor through a large number of experimental tests can achieve the pressure equilibrium requirement in the fastest 1 minute according to the size of the bypass channel of the selected bypass valve 6.
  • the compressor 1 of the embodiment of the present disclosure can achieve the dual effects of waste heat utilization and rapid pressure balance of the system by only adding a bypass valve 6, and is particularly suitable for being sensitive to the starting pressure difference.
  • a bypass valve 6 In the case of relatively large starting torque and fast restart requirements, it is especially effective for the application of rotor compressors, which has the advantages of low cost, wide application range, simple and reliable control.
  • a rapid restart of the compressor 1 can be achieved, and the remaining heat can be utilized after the compressor 1 is stopped, which has high energy efficiency.
  • bypass valve 6 The structure of the bypass valve 6 according to the embodiment of the present disclosure is described below with reference to FIGS. 6 to 8.
  • the bypass valve 6 includes a valve body 6 d, a valve core 6 e, and an electromagnetic control unit 6 g.
  • the valve body 6d defines a valve cavity, and the first port 6a, the second port 6b, and the third port 6c are provided on the valve body 6d, and the first port 6a, the second port 6b, and the third port 6c are connected to the valve cavity.
  • the valve core 6e is movably provided in the valve body 6d.
  • the valve core 6e has a flow channel 6f.
  • the flow channel 6f is always in communication with the first port 6a, and the flow channel 6f can be selectively connected with the second port 6b and the third Port 6c is connected.
  • At least part of the valve body 6e is movably provided in the valve body 6d along the axial direction of the valve body 6d, and the first port 6a is provided at the first axial end portion of the valve body 6d (that is, the left end in FIGS. 6 to 8). ),
  • the second port 6b is provided on the first side of the valve body 6d (that is, the upper side in FIG. 6 to FIG. 8), and the third port 6c is provided on the second side of the valve body 6d (that is, in FIG. 6 to FIG. 8) (Lower side),
  • the flow channel 6f has a first open end toward the first end, a second open end toward the first side, and a third open end toward the second side.
  • the flow channel 6f includes The first section extending axially of the valve body 6d and the second section extending radially of the valve body 6d.
  • the first section may be a blind hole type
  • the second section is a through hole type
  • the open end of the first section is formed as The first open end
  • the two ends of the second section are formed into a second open end and a third open end
  • the second open end and the third open end are respectively connected to the second open end and the second open end.
  • Port 6b and third port 6c are directly opposite.
  • the electromagnetic control portion 6g is electromagnetically connected to the valve core 6e.
  • the valve core 6e may include a control rod protruding from the axial second end portion of the valve body 6d (that is, the right end in FIGS. 6 to 8).
  • the electromagnetic control portion 6g is sleeved outside the control lever.
  • the control lever is made of ferromagnetic material. When the electromagnetic control unit 6g is energized, the control lever can move in the axial direction.
  • the electromagnetic control section 6g is electrically connected to the motor section, that is, the electromagnetic control section 6g can be controlled by the power-on signal of the motor section.
  • the bypass valve 6 has a first state and a second state: as shown in FIG. 6, in the first state, the first port 6 a communicates with the second port 6 b, and the first port 6 a communicates with the third port. 6c is disconnected; as shown in FIG. 7, in the second state, the first port 6a is communicated with the third port 6c, and the first port 6a is disconnected from the second port 6b.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state Switch to the first state.
  • the bypass valve 6 is automatically switched to the first state, so that the compressor 1 is exhausted to the outside.
  • the bypass valve 6 is automatically switched to the second state, which is convenient for the compressor. The pressure on the exhaust side and the suction side of 1 is quickly balanced to facilitate quick start next time.
  • the bypass valve 6 has a first state, a second state, and a third state: as shown in FIG. 6, in the first state, the first port 6a communicates with the second port 6b, and the first port 6a is disconnected from the third port 6c; as shown in FIG. 7, in the second state, the first port 6a is communicated with the third port 6c, and the first port 6a is disconnected from the second port 6b; as shown in FIG. 8, In the third state, the first port 6a is disconnected from the second port 6b, and the first port 6a is disconnected from the third port 6c.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state Switch to the third state, and when P1 ⁇ P2, the bypass valve 6 switches to the first state.
  • P1 ⁇ P2 the bypass valve 6 remains in the third state if the motor section is not stopped, and if the motor section is stopped, the bypass valve 6 is bypassed.
  • the on-off valve 6 is switched to the second state; wherein, P1 is the pressure at the first port 6a, and P2 is the pressure at the second port 6b.
  • the electric signal of the electromagnetic control section 6g of the bypass valve 6 may be connected to the control signal of the motor section, or a control section may be separately provided for control.
  • the bypass valve 6 has a first state, a second state, and a third state: as shown in FIG. 6, in the first state, the first port 6a communicates with the second port 6b, and the first port 6a is disconnected from the third port 6c, as shown in FIG. 7, in the second state, the first port 6a is communicated with the third port 6c, and the first port 6a is disconnected from the second port 6b; as shown in FIG. 8, In the third state, the first port 6a is disconnected from the second port 6b, and the first port 6a is disconnected from the third port 6c.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state After switching to the third state and maintaining the preset time t, the bypass valve 6 is switched to the first state if the motor section is not stopped, and the bypass valve 6 is switched to the second state if the motor section is stopped, where: 1 second is satisfied ⁇ t ⁇ 10 seconds, or meet: 2 seconds ⁇ t ⁇ 6 seconds.
  • the compressor 1 further includes a reservoir, the outlet of the reservoir is in communication with the air inlet of the compression mechanism part, and the suction pipe 13 is provided on the reservoir.
  • the suction side includes a liquid reservoir and a suction pipe 13; the sealed container 11 defines a high-pressure receiving cavity, the sealed container 11 is provided with an exhaust pipe 12, and the exhaust side includes the receiving cavity and the exhaust pipe 12.
  • the sealed container 11 forms a high-pressure internal space
  • the sealed container 11 is provided with an exhaust pipe 12 communicating with the high-pressure internal space.
  • the internal space of the sealed container 11 and the exhaust pipe 12 together constitute the high-pressure of the compressor 1
  • the motor part and the compression mechanism part are provided in the internal space of the high-pressure sealed container 11;
  • the accumulator is provided outside the sealed container 11, and the outlet of the accumulator communicates with the air inlet of the compressor 1 and is on the accumulator
  • An air suction pipe 13 is provided.
  • the air suction pipe 13 is in communication with the air suction pipe 13a (low pressure pipe) of the refrigeration device, and the accumulator and the air suction pipe 13 collectively constitute the low pressure side of the compressor 1.
  • the first port 6a of the bypass valve 6 communicates with the high-pressure side of the compressor 1.
  • the second port 6b of the bypass valve 6 communicates with the exhaust-side pipe 12a (high-pressure pipe) of the refrigeration device.
  • the three ports 6c communicate with the suction side compressor 13 and the suction side pipe 13a (low-pressure pipe) of the refrigeration device.
  • the sealed container 11 defines a low-pressure first cavity and a high-pressure second cavity.
  • the sealed container 11 is provided with an air suction pipe 13 communicating with the first cavity, and the sealed container 11
  • An exhaust pipe 12 is provided on the second cavity.
  • the suction side includes the first cavity and the suction pipe 13, and the exhaust side includes the second cavity and the exhaust pipe 12.
  • the sealed container 11 surrounds a low-pressure internal space.
  • the sealed container 11 is provided with an air suction pipe 13 communicating with the low-pressure internal space, and the air suction pipe 13 and the suction-side pipe 13a (low-pressure pipe) of the refrigerating device.
  • the communication, low-pressure internal space and the suction pipe 13 together constitute the low-pressure side of the compressor 1; the motor section and the compression mechanism section are arranged in the low-pressure sealed container 11 internal space.
  • the internal space of the sealed container 11 is divided into a large volume of low-pressure internal space and a small volume of high-pressure internal space.
  • One end of the compressor 1 is located in the low-pressure internal space, and The other end is located in the high-pressure internal space.
  • the compressor 1 mechanism is located in the low-pressure internal space, and the compressor 1 is a low-pressure structure in the sealed container 11.
  • Compressor 1 is a low-pressure structure in the sealed container 11.
  • the compressor 1 with a low-pressure structure in the sealed container 11 also has a high-pressure exhaust chamber and an exhaust pipe 12.
  • the high-pressure exhaust chamber serves as a space for containing high-pressure gas compressed by the compressor 1 to seal the low-pressure internal space.
  • the exhaust pipe 12 communicates with a high-pressure exhaust chamber.
  • the high-pressure exhaust chamber may be provided in the internal space of the sealed container 11, or may be provided outside the sealed container 11.
  • the high-pressure exhaust chamber and the exhaust pipe 12 together constitute the high-pressure side of the compressor 1.
  • the first port 6a of the bypass valve 6 communicates with the high-pressure side of the compressor 1.
  • the second port 6b of the bypass valve 6 communicates with the exhaust-side pipe 12a (high-pressure pipe) of the refrigeration device.
  • the three ports 6c communicate with the suction side compressor 13 and the suction side pipe 13a (low-pressure pipe) of the refrigeration device.
  • the compressor 1 of the embodiment of the present disclosure can achieve the dual effects of waste heat utilization and rapid pressure balance of the system by only adding a bypass valve 6, and is particularly suitable for being sensitive to the starting pressure difference.
  • a bypass valve 6 In the case of relatively large starting torque and fast restart requirements, it is especially effective for the application of rotor compressors, which has the advantages of low cost, wide application range, simple and reliable control.
  • the refrigeration apparatus of the embodiment of the present disclosure may be an air conditioner, a refrigerator, or the like.
  • a refrigeration device includes: a compressor 1, a first heat exchanger 2, a throttle valve 4, and a second heat exchanger 3, wherein the compressor 1 is any of the foregoing.
  • the first port of the first heat exchanger 2 is connected to the second port 6b of the bypass valve 6, and the first port of the first heat exchanger 2 is connected to the second port 6b of the bypass valve 6.
  • the two sides communicate with each other through the exhaust-side pipe 12a (high-pressure pipe), and the throttle valve 4 is connected between the second interface of the first heat exchanger 2 and the first interface of the second heat exchanger 3, and the second heat exchanger
  • the second interface of 3 is connected to the suction port of the compressor 1, and the second interface of the second heat exchanger 3 and the suction port of the compressor 1 are connected through the suction side pipe 13a (low pressure pipe) to compress
  • the suction port of the machine 1 may be formed at an end of the suction pipe 13 of the compressor 1.
  • a refrigeration device includes a compressor 1, a reversing device 5, a first heat exchanger 2, a throttle valve 4, and a second heat exchanger 3.
  • the reversing device 5 includes a first port 5a, a second port 5b, a third port 5c, and a fourth port 5d.
  • the reversing device 5 may be a four-way valve.
  • the first port 5a is connected to the second port 6b and the second port 5b.
  • the second port 5b and the first interface of the first heat exchanger 2 communicate through an exhaust-side pipe 12a (high-pressure pipe), and the throttle valve 4 is connected at Between the second interface of the first heat exchanger 2 and the first interface of the second heat exchanger 3, the second interface of the second heat exchanger 3 is connected to the fourth port 5d, and the third port 5c is connected to the compressor 1
  • the suction port is connected, and the third port 5c communicates with the suction port of the compressor 1 through the suction side pipe 13a (low-pressure pipe).
  • the suction port of the compressor 1 may be formed in the suction pipe of the compressor 1. 13's end.
  • the first heat exchanger 2 When the first port 5a communicates with the second port 5b, and the third port 5c communicates with the fourth port 5d, the first heat exchanger 2 is a high-pressure side heat exchanger, and the second heat exchanger 3 is a low-pressure side heat exchanger. ;
  • the second heat exchanger 3 When the first port 5a communicates with the fourth port 5d and the second port 5b communicates with the third port 5c, the second heat exchanger 3 is a high-pressure side heat exchanger, and the first heat exchanger 2 is a low-pressure side heat exchanger Device.
  • a compressor includes: a sealed container; a motor portion and a compression mechanism portion, the motor portion and the compression mechanism portion are both disposed in the sealed container; a bypass valve, the bypass valve includes A first port, a second port, and a third port, the first port being selectively communicable with one of the second port and the third port; wherein the compressor has a separate exhaust Side and the suction side, the first port is in communication with the exhaust side, the third port is in communication with the suction side, and the exhaust side is adapted to discharge external components through the second port gas.
  • the compressor can be quickly restarted, and the residual heat can be utilized after the compressor is stopped, which has high energy efficiency.
  • the bypass valve includes a valve body, the valve body defines a valve cavity, and the first port, the second port, and the third port are all provided at The valve body is in communication with the valve cavity; a valve core, the valve core is movably disposed in the valve body, the valve core has a flow channel, and the flow channel is in communication with the first port, and The flow channel can be selectively communicated with the second port and the third port.
  • At least a part of the valve body is movably provided in the valve body along an axial direction of the valve body, and the first port is provided in an axial direction of the valve body.
  • a first end, the second port is provided on a first side of the valve body
  • the third port is provided on a second side of the valve body
  • the flow channel has a A first open end, a second open end toward the first side, and a third open end toward the second side; wherein when the second open end is opposite to the second port, the first open end A port is in communication with the second port; when the third open end is opposite to the third port, the first port is in communication with the third port.
  • the bypass valve further includes: an electromagnetic control portion, and the electromagnetic control portion is electromagnetically connected with the valve core.
  • the bypass valve has a first state and a second state.
  • the first state the first port is in communication with the second port, and the first port is in communication with all the ports.
  • the third port is disconnected, and in the second state, the first port is in communication with the third port, and the first port is disconnected from the second port;
  • the compressor is configured to act as the motor
  • the bypass valve is switched from the first state to the second state; and the compressor is configured to switch the bypass valve from the second state to when the motor unit is started from the stopped state.
  • the bypass valve has a first state, a second state, and a third state.
  • the first state the first port is in communication with the second port, and the first port is in communication with the second port.
  • a port is disconnected from the third port.
  • the second state the first port is in communication with the third port, and the first port is disconnected from the second port.
  • the third state The first port is disconnected from the second port, and the first port is disconnected from the third port.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state, and when P1 ⁇ P2, the bypass valve is switched to the first state.
  • P1 ⁇ P2 if If the motor section is not stopped, the bypass valve is maintained in a third state, and if the motor section is stopped, the bypass valve is switched to a second state; where P1 is the pressure at the first port and P2 is all The pressure at the second port is described.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state and is maintained for a preset time t. If the motor part is not stopped, the bypass valve is switched to the first state. If the motor part is stopped, the bypass valve is switched to the second state.
  • the compressor according to an embodiment of the present disclosure satisfies: 1 second ⁇ t ⁇ 10 seconds.
  • the compressor according to an embodiment of the present disclosure satisfies: 2 seconds ⁇ t ⁇ 6 seconds.
  • the compressor according to an embodiment of the present disclosure further includes: a reservoir, an outlet of the reservoir is in communication with an air inlet of the compression mechanism portion, and an suction pipe is provided on the reservoir, and
  • the suction side includes the reservoir and the suction pipe;
  • the sealed container defines a high-pressure receiving cavity, and the sealed container is provided with an exhaust pipe, and the exhaust side includes the receiving cavity and the Mentioned exhaust pipe.
  • the sealed container defines a low-pressure first cavity and a high-pressure second cavity
  • the sealed container is provided with an air suction pipe communicating with the first cavity
  • the seal is provided with an exhaust pipe communicating with the second cavity
  • the suction side includes the first cavity and the suction tube
  • the exhaust side includes the second cavity and the exhaust tube.
  • the present disclosure also provides a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • the throttle valve Connected to the second port, the throttle valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the first port of the second heat exchanger Two interfaces are connected to the suction port of the compressor.
  • the present disclosure also provides a refrigeration device including: a reversing device, a first heat exchanger, a throttle valve, a second heat exchanger, and the compressor according to any one of the above, wherein the reversing device includes a first One port, second port, third port, and fourth port, the first port is connected to the second port, the second port is connected to the first interface of the first heat exchanger, and the node
  • the flow valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the second interface of the second heat exchanger is connected to the fourth port.
  • the third port is connected to the suction port of the compressor.
  • a compressor 1 according to an embodiment of the present disclosure is described below with reference to FIGS. 9 to 16.
  • the compressor 1 includes a sealed container 11, a motor portion, a compression mechanism portion, and a bypass valve 6.
  • the compressor 1 has a separate exhaust side and an intake side.
  • the exhaust side is a high-pressure side and the intake side is a low-pressure side.
  • the motor part and the compression mechanism part are both provided in a sealed container 11.
  • the motor part is used for The compression mechanism is driven to realize the intake and compression of exhaust.
  • the bypass valve 6 includes a first port 6a, a second port 6b, a third port 6c, and a fourth port 6h.
  • the first port 6a can be selectively connected to the second port. 6b.
  • One of the third ports 6c is in communication
  • the fourth port 6h is selectively in communication with the third port 6c.
  • the first port 6a is in communication with the exhaust side of the compressor 1, and the third port 6c is in communication with the compressor 1
  • the suction side communicates.
  • the exhaust side is suitable for exhausting external components through the second port 6b. Inhale air to external parts through the fourth port 6h.
  • the compressor is connected to the external pipeline through the second port 6b and the fourth port 6h.
  • the discharge side of the compressor is disconnected from the external pipeline, and the high pressure
  • the residual heat of the side heat exchanger can be continuously used.
  • the first port 6a of the bypass valve 6 communicates with the second port 6b
  • the third port 6c of the bypass valve 6 communicates with the fourth port 6h
  • the output of the compressor 1 The high-pressure gas from the exhaust side is output to the exhaust side pipe 12a of the refrigeration device through the first port 6a and the second port 6b, and the intake side of the compressor 1 passes through the intake side pipe 13a, the fourth port 6h, and the first Three-port 6c inhales.
  • the bypass valve 6 When the compressor 1 is stopped, the motor part is not operated, the first port 6a of the bypass valve 6 is communicated with the third port 6c, the first port 6a is disconnected from the second port 6b, and the third port 6c is connected to the fourth port 6h. disconnect. That is, the bypass valve 6 communicates the exhaust side and the intake side of the compressor 1 and disconnects the exhaust side of the compressor 1 from other components of the refrigeration device.
  • the bypass valve 6 cuts off the communication between the exhaust side of the compressor 1 and the refrigeration device, and the second port 6b cannot return to the first port 6a.
  • the throttle valve 3 still has a certain flow rate under the effect of the pressure difference, so that the remaining heat of the high-pressure side heat exchanger can still be radiated and the low-pressure side heat exchanger can still have the ability to absorb heat by evaporation.
  • the refrigeration device can still use the remaining heat in the heat exchanger, thereby improving the overall efficiency of the refrigeration device, enabling the remaining heat of the system to be utilized, and being simple, reliable, and highly energy-saving.
  • the bypass valve 6 disconnects the high-pressure side of the compressor from the high-pressure side heat exchanger and directly communicates with the low-pressure side of the compressor. And the bypass valve 6 has a direct communication channel. In this way, the high pressure side and the low pressure side of the compressor 1 can quickly achieve pressure balance, and meet the requirements of the compressor when the pressure difference is less than 1kgf / cm2, thereby achieving the compressor shutdown. After quick restart function.
  • the pressure equilibration time obtained by the inventor through a large number of experimental tests can achieve the pressure equilibrium requirement in the fastest 1 minute according to the size of the bypass channel of the selected bypass valve 6.
  • the compressor 1 of the embodiment of the present disclosure can achieve the dual effects of waste heat utilization and rapid pressure balance of the system by only adding a bypass valve 6, and is particularly suitable for being sensitive to the starting pressure difference.
  • a bypass valve 6 In the case of relatively large starting torque and fast restart requirements, it is especially effective for the application of rotor compressors, which has the advantages of low cost, wide application range, simple and reliable control.
  • a rapid restart of the compressor 1 can be achieved, and the remaining heat can be utilized after the compressor 1 is stopped, which has high energy efficiency.
  • bypass valve 6 The structure of the bypass valve 6 according to the embodiment of the present disclosure is described below with reference to FIGS. 14 to 16.
  • the bypass valve 6 includes a valve body 6d, a valve core 6e, and an electromagnetic control unit 6g.
  • the valve body 6d defines a valve cavity, and the first port 6a, the second port 6b, the third port 6c, and the fourth port 6h are all provided in the valve body 6d, and the first port 6a, the second port 6b, and the third port 6c, the fourth port 6h are in communication with the valve cavity.
  • the spool 6e is movably disposed in the valve body 6d.
  • the spool 6e has a first flow passage 6i, a second flow passage 6j, and a third flow passage 6k.
  • the first port 6a and the second port 6b are adapted to pass through the first flow passage 6i.
  • the third port 6c and the fourth port 6h are adapted to communicate through the second flow path 6j, or the first port 6a and the third port 6c are adapted to communicate through the third flow path 6k.
  • At least a part of the valve body 6e is movably provided in the valve body 6d along the axial direction of the valve body 6d (that is, the left-right direction in FIGS. 14 to 16), and the first port 6a and the third port 6c are provided in the valve body 6a.
  • the first side ie, the lower side in FIGS. 14 to 16
  • the first port 6a and the third port 6c are spaced apart in the axial direction
  • the second port 6b and the fourth port 6h are provided on the second side of the valve body 6a.
  • the first port 6a may be disposed opposite the second port 6b
  • the third port 6c may be disposed opposite the first port 6b.
  • the four-port 6h is set directly.
  • the two open ends of the first flow passage 6i face the first and second sides of the valve body 6a, respectively, and the two open ends of the second flow passage 6j face the first and second sides of the valve body 6a, respectively.
  • Both open ends of the channel 6k face the first side of the valve body 6a.
  • the first flow passage 6i and the second flow passage 6j are spaced apart along the axial direction of the spool 6e, and the width of the second flow passage 6j along the axial direction of the spool 6e is greater than the width of the first flow passage 6i along the axial direction of the spool 6e. In this way, when the first port 6a and the second port 6b are disconnected, the third port 6c and the fourth port 6h can maintain communication.
  • the first flow passage 6i and the second flow passage 6j penetrate the spool 6e in the radial direction of the spool 6e
  • the third flow passage 6k includes a first section and two sections extending along the axial direction of the spool 6e.
  • the radially extending second segment of the spool 6e, the two second segments are respectively connected to both ends of the first segment, and the two second segments are open away from the ends of the first segment.
  • the electromagnetic control portion 6g is electromagnetically connected to the valve core 6e.
  • the valve core 6e may include a control rod protruding from the axial second end portion of the valve body 6d (that is, the right end in FIGS. 14 to 16).
  • the electromagnetic control portion 6g is sleeved outside the control lever.
  • the control lever is made of ferromagnetic material. When the electromagnetic control unit 6g is energized, the control lever can move in the axial direction.
  • the electromagnetic control section 6g is electrically connected to the motor section, that is, the electromagnetic control section 6g can be controlled by the power-on signal of the motor section.
  • the bypass valve 6 has a first state and a second state: as shown in FIG. 14, in the first state, the first port 6a communicates with the second port 6b, and the fourth port 6h communicates with the third port. As shown in FIG. 15, in the second state, the first port 6a is in communication with the third port 6c, the first port 6a is disconnected from the second port 6b, and the third port 6c is disconnected from the fourth port 6h.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state Switch to the first state.
  • the bypass valve 6 is automatically switched to the first state, which is convenient for the compressor 1 to exhaust and suck air.
  • the bypass valve 6 is automatically switched to the second state. It is convenient for the pressure on the exhaust side and the suction side of the compressor 1 to quickly balance, and it is convenient to start quickly next time.
  • the bypass valve 6 has a first state, a second state, and a third state: as shown in FIG. 14, in the first state, the first port 6a communicates with the second port 6b, and the fourth port 6h communicates with the third port 6c; as shown in FIG. 15, in the second state, the first port 6a is communicated with the third port 6c, the first port 6a is disconnected from the second port 6b, and the third port 6c is connected with the fourth port Port 6h is disconnected; as shown in FIG. 16, in the third state, the first port 6a is disconnected from the second port 6b, and the fourth port 6h is communicated with the third port 6c.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state Switch to the third state, and when P1 ⁇ P2, the bypass valve 6 switches to the first state.
  • P1 ⁇ P2 the bypass valve 6 remains in the third state if the motor section is not stopped, and if the motor section is stopped, the bypass valve 6 is bypassed.
  • the on-off valve 6 is switched to the second state; wherein, P1 is the pressure at the first port 6a, and P2 is the pressure at the second port 6b.
  • the electric signal of the electromagnetic control section 6g of the bypass valve 6 may be connected to the control signal of the motor section, or a control section may be separately provided for control.
  • the bypass valve 6 has a first state, a second state, and a third state: as shown in FIG. 14, in the first state, the first port 6a communicates with the second port 6b, and the fourth port 6h communicates with the third port 6c; as shown in FIG. 15, in the second state, the first port 6a is communicated with the third port 6c, the first port 6a is disconnected from the second port 6b, and the third port 6c is connected with the fourth port Port 6h is disconnected; as shown in FIG. 16, in the third state, the first port 6a is disconnected from the second port 6b, and the fourth port 6h is communicated with the third port 6c.
  • the compressor 1 is set to switch the bypass valve 6 from the first state to the second state when the motor section is stopped from the running state; the compressor 1 is set to the bypass valve 6 from the second state when the motor section is started from the stopped state After switching to the third state and maintaining the preset time t, the bypass valve 6 is switched to the first state if the motor section is not stopped, and the bypass valve 6 is switched to the second state if the motor section is stopped, where: 1 second is satisfied ⁇ t ⁇ 10 seconds, or meet: 2 seconds ⁇ t ⁇ 6 seconds.
  • the compressor 1 further includes a reservoir, the outlet of the reservoir is in communication with the air inlet of the compression mechanism part, and the suction pipe 13 is provided on the reservoir.
  • the suction side includes a liquid reservoir and a suction pipe 13; the sealed container 11 defines a high-pressure receiving cavity, the sealed container 11 is provided with an exhaust pipe 12, and the exhaust side includes the receiving cavity and the exhaust pipe 12.
  • the sealed container 11 forms a high-pressure internal space
  • the sealed container 11 is provided with an exhaust pipe 12 communicating with the high-pressure internal space.
  • the internal space of the sealed container 11 and the exhaust pipe 12 together constitute the high-pressure of the compressor 1
  • the motor part and the compression mechanism part are provided in the internal space of the high-pressure sealed container 11;
  • the accumulator is provided outside the sealed container 11, and the outlet of the accumulator communicates with the air inlet of the compressor 1 and is on the accumulator
  • An air suction pipe 13 is provided.
  • the air suction pipe 13 is in communication with the air suction pipe 13a (low pressure pipe) of the refrigeration device, and the accumulator and the air suction pipe 13 collectively constitute the low pressure side of the compressor 1.
  • the first port 6a of the bypass valve 6 communicates with the high-pressure side of the compressor 1.
  • the second port 6b of the bypass valve 6 communicates with the exhaust-side pipe 12a (high-pressure pipe) of the refrigeration device.
  • the three ports 6c communicate with the suction side of the compressor 1, and the fourth port 6h of the bypass valve 6 communicates with the suction side pipe 13a (low-pressure pipe) of the refrigeration device.
  • the sealed container 11 defines a low-pressure first cavity and a high-pressure second cavity.
  • the sealed container 11 is provided with an air suction pipe 13 communicating with the first cavity, and the sealed container 11
  • An exhaust pipe 12 is provided on the second cavity.
  • the suction side includes the first cavity and the suction pipe 13, and the exhaust side includes the second cavity and the exhaust pipe 12.
  • the sealed container 11 surrounds a low-pressure internal space.
  • the sealed container 11 is provided with an air suction pipe 13 communicating with the low-pressure internal space, and the air suction pipe 13 and the suction-side pipe 13a (low-pressure pipe) of the refrigerating device.
  • the communication, low-pressure internal space and the suction pipe 13 together constitute the low-pressure side of the compressor 1; the motor section and the compression mechanism section are arranged in the low-pressure sealed container 11 internal space.
  • the internal space of the sealed container 11 is divided into a large volume of low-pressure internal space and a small volume of high-pressure internal space.
  • One end of the compressor 1 is located in the low-pressure internal space, and The other end is located in the high-pressure internal space.
  • the compressor 1 mechanism is located in the low-pressure internal space, and the compressor 1 is a low-pressure structure in the sealed container 11.
  • Compressor 1 is a low-pressure structure in the sealed container 11.
  • the compressor 1 with a low-pressure structure in the sealed container 11 also has a high-pressure exhaust chamber and an exhaust pipe 12.
  • the high-pressure exhaust chamber serves as a space for containing high-pressure gas compressed by the compressor 1 to seal the low-pressure internal space.
  • the exhaust pipe 12 communicates with a high-pressure exhaust chamber.
  • the high-pressure exhaust chamber may be provided in the internal space of the sealed container 11, or may be provided outside the sealed container 11.
  • the high-pressure exhaust chamber and the exhaust pipe 12 together constitute the high-pressure side of the compressor 1.
  • the first port 6a of the bypass valve 6 communicates with the high-pressure side of the compressor 1.
  • the second port 6b of the bypass valve 6 communicates with the exhaust-side pipe 12a (high-pressure pipe) of the refrigeration device.
  • the three ports 6c communicate with the suction side of the compressor 1, and the fourth port 6h of the bypass valve 6 communicates with the suction side pipe 13a (low-pressure pipe) of the refrigeration device.
  • the compressor 1 of the embodiment of the present disclosure can achieve the dual effects of waste heat utilization and rapid pressure balance of the system by only adding a bypass valve 6, and is particularly suitable for being sensitive to the starting pressure difference.
  • a bypass valve 6 In the case of relatively large starting torque and fast restart requirements, it is especially effective for the application of rotor compressors, which has the advantages of low cost, wide application range, simple and reliable control.
  • the refrigeration device according to an embodiment of the present disclosure may be an air conditioner, a refrigerator, or the like.
  • a refrigeration device includes: a compressor 1, a first heat exchanger 2, a throttle valve 4, and a second heat exchanger 3, wherein the compressor 1 is any of the foregoing.
  • the first port of the first heat exchanger 2 is connected to the second port 6b of the bypass valve 6, and the first port of the first heat exchanger 2 is connected to the second port 6b of the bypass valve 6.
  • the two sides communicate with each other through the exhaust-side pipe 12a (high-pressure pipe), and the throttle valve 4 is connected between the second interface of the first heat exchanger 2 and the first interface of the second heat exchanger 3, and the second heat exchanger
  • the second interface of 3 is connected to the fourth port 6h.
  • the second interface of the second heat exchanger 3 and the fourth port 6h are connected through the suction side pipe 13a (low-pressure pipe).
  • the fourth port 6h can be formed as The suction port of the compressor 1.
  • a refrigeration device includes a compressor 1, a reversing device 5, a first heat exchanger 2, a throttle valve 4, and a second heat exchanger 3.
  • the reversing device 5 includes a first port 5a, a second port 5b, a third port 5c, and a fourth port 5d.
  • the reversing device 5 may be a four-way valve.
  • the first port 5a is connected to the second port 6b and the second port 5b.
  • the second port 5b and the first interface of the first heat exchanger 2 communicate through an exhaust-side pipe 12a (high-pressure pipe), and the throttle valve 4 is connected at Between the second interface of the first heat exchanger 2 and the first interface of the second heat exchanger 3, the second interface of the second heat exchanger 3 is connected to the fourth port 5d, and the third port 5c is connected to the fourth port 6h.
  • the third port 5c communicates with the fourth port 6h through the suction side pipe 13a (low-pressure pipe), and the fourth port 6h can be formed as the suction port of the compressor 1.
  • the first heat exchanger 2 When the first port 5a communicates with the second port 5b, and the third port 5c communicates with the fourth port 5d, the first heat exchanger 2 is a high-pressure side heat exchanger, and the second heat exchanger 3 is a low-pressure side heat exchanger. ;
  • the second heat exchanger 3 When the first port 5a communicates with the fourth port 5d and the second port 5b communicates with the third port 5c, the second heat exchanger 3 is a high-pressure side heat exchanger, and the first heat exchanger 2 is a low-pressure side heat exchanger Device.
  • a compressor includes: a sealed container; a motor portion and a compression mechanism portion, the motor portion and the compression mechanism portion are both disposed in the sealed container; a bypass valve, the bypass valve includes A first port, a second port, a third port, and a fourth port, the first port may be selectively connected with one of the second port and the third port, and the fourth port may be selectively Ground is in communication with the third port; wherein the compressor has a separate exhaust side and an intake side, the first port is in communication with the exhaust side, and the third port is in communication with the intake Side communication, when the first port communicates with the second port and the third port communicates with the fourth port, the exhaust side is adapted to exhaust external components through the second port, so The suction side is adapted to suck air to external components through the fourth port.
  • the compressor can be quickly restarted, and the residual heat can be utilized after the compressor is stopped, which has high energy efficiency.
  • the bypass valve includes a valve body defining a valve cavity, the first port, the second port, the third port, the first port Four ports are provided in the valve body and are all in communication with the valve cavity; a valve core, the valve core is movably disposed in the valve body, and the valve core has a first flow path, a second flow path, a first Three flow paths, the first port and the second port are adapted to communicate through the first flow path and the third port and the fourth port are adapted to communicate through the second flow path, or the The first port and the third port are adapted to communicate through the third flow channel.
  • At least a part of the valve body is movably provided in the valve body along an axial direction of the valve body, and the first port and the third port are provided in the valve body.
  • the first side of the valve body is arranged at intervals in the axial direction
  • the second port and the fourth port are arranged at the second side of the valve body and are arranged at intervals in the axial direction.
  • Open ends and two open ends of the second flow path respectively face the first side and a second side of the valve body, and both open ends of the third flow path face the first side of the valve body side.
  • the first flow path and the second flow path are spaced apart along the axial direction of the valve core, and the second flow path is along the axial direction of the valve core.
  • the width is larger than the width of the first flow channel in the axial direction of the valve core.
  • the bypass valve further includes: an electromagnetic control portion, and the electromagnetic control portion is electromagnetically connected with the valve core.
  • the bypass valve has a first state and a second state.
  • the first state the first port is in communication with the second port, and the fourth port is in communication with all the ports.
  • the third port is connected.
  • the second state the first port is connected to the third port, the first port is disconnected from the second port, and the third port is connected to the fourth port.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; the compressor is set to start when the motor section is stopped from a stopped state At that time, the bypass valve is switched from the second state to the first state.
  • the bypass valve has a first state, a second state, and a third state.
  • the first state the first port is in communication with the second port, and the first port is in communication with the second port.
  • Four ports are in communication with the third port.
  • the second state the first port is in communication with the third port, the first port is disconnected from the second port, and the third port is in communication with all ports.
  • the fourth port is disconnected.
  • the third state the first port is disconnected from the second port, and the fourth port is communicated with the third port.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state, and when P1 ⁇ P2, the bypass valve is switched to the first state.
  • P1 ⁇ P2 if If the motor section is not stopped, the bypass valve is maintained in a third state, and if the motor section is stopped, the bypass valve is switched to a second state; where P1 is the pressure at the first port and P2 is all The pressure at the second port is described.
  • the compressor is set to switch the bypass valve from a first state to a second state when the motor section is stopped from an operating state; and the compressor is set to when the When the motor part is started from the stopped state, the bypass valve is switched from the second state to the third state and is maintained for a preset time t. If the motor part is not stopped, the bypass valve is switched to the first state. If the motor part is stopped, the bypass valve is switched to the second state.
  • the compressor according to an embodiment of the present disclosure satisfies: 1 second ⁇ t ⁇ 10 seconds.
  • the compressor according to an embodiment of the present disclosure further includes: a reservoir, an outlet of the reservoir is in communication with an air inlet of the compression mechanism portion, and an suction pipe is provided on the reservoir, and
  • the suction side includes the reservoir and the suction pipe;
  • the sealed container defines a high-pressure receiving cavity, and the sealed container is provided with an exhaust pipe, and the exhaust side includes the receiving cavity and the Mentioned exhaust pipe.
  • the sealed container defines a low-pressure first cavity and a high-pressure second cavity
  • the sealed container is provided with an air suction pipe communicating with the first cavity
  • the seal is provided with an exhaust pipe communicating with the second cavity
  • the suction side includes the first cavity and the suction tube
  • the exhaust side includes the second cavity and the exhaust tube.
  • the present disclosure also provides a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • a refrigeration device including: a first heat exchanger, a throttle valve, a second heat exchanger, the compressor according to any one of the above, and a first interface of the first heat exchanger.
  • the throttle valve Connected to the second port, the throttle valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the first port of the second heat exchanger Two interfaces are connected to the fourth port.
  • the present disclosure also provides a refrigeration device including: a reversing device, a first heat exchanger, a throttle valve, a second heat exchanger, and the compressor according to any one of the above, wherein the reversing device includes a first One port, second port, third port, and fourth port, the first port is connected to the second port, the second port is connected to the first interface of the first heat exchanger, and the node
  • the flow valve is connected between the second interface of the first heat exchanger and the first interface of the second heat exchanger, and the second interface of the second heat exchanger is connected to the fourth port.
  • the third port is connected to the fourth port.

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Abstract

一种压缩机（1）和制冷装置，压缩机（1）包括：密封容器（11）；电机部和压缩机构部，电机部和压缩机构部均设置在密封容器（11）内；旁通阀（6）；其中压缩机（1）具有分隔开的排气侧和吸气侧，排气侧与旁通阀（6）相连，排气侧适于通过旁通阀（6）向外部零部件排气或者通过旁通阀（6）与吸气侧连通。

Description

压缩机和制冷装置
相关申请的交叉引用
本申请要求广东美芝制冷设备有限公司于2018年7月25日提交的、发明名称为“压缩机和制冷装置”的中国专利申请号“201810827208.9”、“201821192650.0”、“201810828639.7”及“201821192720.2”的优先权，其全部内容通过引用结合在本申请中。
技术领域
本公开属于压缩机制造技术领域，具体而言，涉及一种压缩机和具有该压缩机的制冷装置。
背景技术
在制冷装置中，通过压缩机的压缩和节流结构的节流作用，从而将制冷剂在低温低压和高温高压之间转化，并利用换热器实现与周围环境的换热，实现制冷或制热的效果。其中，压缩机是制冷装置中十分重要的零部件之一，压缩机的设计对制冷装置的能效和运行可靠性有着重要的影响。
压缩机从上一回运行后停机到可以再次启动时，压缩机的吸气侧与排气侧的压力差必须要达到某个要求的范围内才可以重新启动，特别是对于滚动转子式压缩机来说，该压力差必须达到一个较小的数值例如1kgf/cm 2以内，否则将无法启动再次启动压缩机，从而无法实现快速启动功能。另一方面，相关技术中，当压缩机停机后，高压侧换热器内的制冷剂会通过压缩机零部件的间隙快速的回到低压侧中，从而升高低压侧换热器内的温度和压力，这种情况下，会浪费高压侧换热器中的热量并损失低压侧换热器中的制冷量，不利于制冷装置的运行效率。
在制冷装置中，通过压缩机的压缩和节流结构的节流作用，从而将制冷剂在低温低压和高温高压之间转化，并利用换热器实现与周围环境的换热，实现制冷或制热的效果。其中，压缩机是制冷装置中十分重要的零部件之一，压缩机的设计对制冷装置的能效和运行可靠性有着重要的影响。
发明内容
本公开旨在至少解决现有技术中存在的技术问题之一。
根据本公开实施例的压缩机，包括：密封容器；电机部和压缩机构部，所述电机部和 所述压缩机构部均设置在所述密封容器内；旁通阀；其中所述压缩机具有分隔开的排气侧和吸气侧，所述排气侧与所述旁通阀相连，所述排气侧适于通过所述旁通阀向外部零部件排气或者通过所述旁通阀与所述吸气侧连通。
根据本公开实施例的压缩机，可以实现压缩机的快速重启，且在压缩机停机后还能利用剩余热量，能效高。
根据本公开一个实施例的压缩机，所述旁通阀包括：阀体，所述阀体限定出阀腔，所述阀体设有多个与所述阀腔连通的端口，所述端口用于与所述排气侧、所述吸气侧、所述外部零部件相连；阀芯，所述阀芯可活动地设在所述阀体内，所述阀芯具有流道，多个所述端口可选择性地通过所述流道连通。
根据本公开一个实施例的压缩机，所述旁通阀还包括：电磁控制部，所述电磁控制部与所述阀芯电磁连接。
根据本公开一个实施例的压缩机，所述旁通阀包括第一端口、第二端口、第三端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，所述排气侧适于通过所述第二端口向外部零部件排气。
根据本公开一个实施例的压缩机，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口设在所述阀体的轴向的第一端部，所述第二端口设在所述阀体的第一侧面，所述第三端口设在所述阀体的第二侧面，所述流道具有朝向所述第一端部的第一敞开端、朝向所述第一侧面的第二敞开端、朝向所述第二侧面的第三敞开端；其中，在所述第二敞开端与所述第二端口相对时，所述第一端口与所述第二端口连通；在所述第三敞开端与所述第三端口相对时，所述第一端口与所述第三端口连通。
根据本公开一个实施例的压缩机，所述旁通阀包括第一端口、第二端口、第三端口、第四端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通，所述第四端口可选择性地与所述第三端口连通，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，在所述第一端口与所述第二端口连通且所述第三端口与所述第四端口连通时，所述排气侧适于通过所述第二端口向外部零部件排气，所述吸气侧适于通过所述第四端口向外部零部件吸气。
根据本公开一个实施例的压缩机，所述阀芯具有第一流道、第二流道、第三流道，所述第一端口和所述第二端口适于通过所述第一流道连通且所述第三端口和所述第四端口适于通过所述第二流道连通，或者所述第一端口和所述第三端口适于通过所述第三流道连通。
根据本公开一个实施例的压缩机，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口和所述第三端口设在所述阀体的第一侧面且沿轴向间隔开布 置，所述第二端口和所述第四端口设在所述阀体的第二侧面且沿轴向间隔开布置，所述第一流道的两个敞开端和所述第二流道的两个敞开端分别朝向所述阀体的第一侧面和第二侧面，所述第三流道的两个敞开端均朝向所述阀体的第一侧面。
根据本公开一个实施例的压缩机，所述第一流道和所述第二流道沿所述阀芯的轴向间隔开布置，且所述第二流道沿所述阀芯的轴向的宽度大于所述第一流道沿所述阀芯的轴向的宽度。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态和第二状态，在第一状态时，所述排气侧通过所述旁通阀与外部零部件连通，在第二状态时，所述排气侧通过所述旁通阀与所述吸气侧连通；所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第一状态。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态、第二状态和第三状态，在第一状态时，所述排气侧通过所述旁通阀与外部零部件连通，且所述排气侧与所述吸气侧断开，在第二状态时，所述排气侧与外部零部件断开，所述排气侧通过所述旁通阀与所述吸气侧连通，在第三状态时，所述排气侧与外部零部件断开，且所述排气侧与所述吸气侧断开。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，且当P1≥P2时，所述旁通阀切换为第一状态，当P1＜P2时，若所述电机部未停机则所述旁通阀保持第三状态，若所述电机部停机则所述旁通阀切换为第二状态；其中，P1为所述第一端口处的压力，P2为所述第二端口处的压力。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，并保持预设时间t后，若所述电机部未停机则所述旁通阀切换为第一状态，若所述电机部停机则所述旁通阀切换为第二状态。
根据本公开一个实施例的压缩机，满足：1秒≤t≤10秒。
根据本公开一个实施例的压缩机，还包括：储液器，所述储液器的出口与所述压缩机构部的进气口连通，所述储液器上设置有吸气管，所述吸气侧包括所述储液器和所述吸气管；所述密封容器限定出高压的容纳腔，所述密封容器上设有排气管，所述排气侧包括所述容纳腔和所述排气管。
根据本公开一个实施例的压缩机，所述密封容器限定出低压的第一腔和高压的第二腔，所述密封容器上设有与所述第一腔连通的吸气管，所述密封容器上设有与所述第二腔连通 的排气管，所述吸气侧包括所述第一腔和所述吸气管，所述排气侧包括所述第二腔和所述排气管。
本公开还提出了一种制冷装置，包括：第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述第一换热器的第一接口与所述旁通阀相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述压缩机的吸气口相连。
本公开还提出了一种制冷装置，包括：换向装置、第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述换向装置包括第一口、第二口、第三口和第四口，所述第一口与所述旁通阀相连，所述第二口与所述第一换热器的第一接口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述第四口相连，所述第三口与所述压缩机的吸气口相连。
所述制冷装置与上述的压缩机相对于现有技术所具有的优势相同，在此不再赘述。
本公开的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本公开的实践了解到。
附图说明
本公开的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1-图5是根据本公开第一个实施例的制冷装置的结构示意图；
图6是根据本公开第一个实施例的旁通阀在第一状态的结构示意图；
图7是根据本公开第一个实施例的旁通阀在第二状态的结构示意图；
图8是根据本公开第一个实施例的旁通阀在第三状态的结构示意图；
图9-图13是根据本公开实施例的制冷装置的结构示意图；
图14是根据本公开实施例的旁通阀在第一状态的结构示意图；
图15是根据本公开实施例的旁通阀在第二状态的结构示意图；
图16是根据本公开实施例的旁通阀在第三状态的结构示意图。
附图标记：
压缩机1，密封容器11，排气管12，排气侧管路12a，吸气管13，吸气侧管路13a，第一换热器2，第二换热器3，节流阀4，换向装置5，第一口5a，第二口5b，第三口5c，第四口5d，旁通阀6，第一端口6a，第二端口6b，第三端口6c，阀体6d，阀芯6e，流道6f，电磁控制部6g，第四端口6h，第一流道6i，第二流道6j，第三流道6k。
具体实施方式
下面参考图1-图8描述根据本公开实施例的压缩机1。
如图1-图8所示，根据本公开一个实施例的压缩机1包括：密封容器11、电机部、压缩机构部、旁通阀6。
其中，压缩机1具有分隔开的排气侧和吸气侧，排气侧为高压侧，吸气侧为低压侧，电机部和压缩机构部均设置在密封容器11内，电机部用于驱动压缩机构部以实现吸气和压缩排气，旁通阀6包括第一端口6a、第二端口6b、第三端口6c，第一端口6a可选择性地与第二端口6b、第三端口6c中的一个连通，其中第一端口6a与压缩机1的排气侧连通，第三端口6c与压缩机1的吸气侧连通，排气侧适于通过第二端口6b向外部零部件排气。换言之，压缩机1通过第二端口6b与外界管路相连，当第一端口6a与第二端口6b断开时，压缩机的排气侧断开与外部管路的连通，高压侧换热器残存的热量可以继续利用。
在压缩机1正常启动工作时，电机部工作，旁通阀6的第一端口6a与第二端口6b连通，旁通阀6的第三端口6c与第一端口6a断开，且第三端口6c与第一端口6a断开，压缩机1的输出的高压气体从排气侧通过第一端口6a、第二端口6b输出到制冷装置的排气侧管路12a，压缩机1的吸气侧通过吸气侧管路13a吸气。
在压缩机1停止运行时，电机部不工作，旁通阀6的第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开。也就是说，旁通阀6将压缩机1的排气侧与吸气侧连通，且将压缩机1的排气侧与制冷装置的其他部件断开。
这样，在压缩机1停机时，可以使压缩机1的排气侧与吸气侧的压力快速平衡，便于快速再次启动压缩机1。
另一方面，在压缩机1停机时，旁通阀6切断了压缩机1的排气侧和制冷装置的连通，高压侧换热器内部保持较高的压力状态，节流阀3在压差的作用下仍然具有一定的流量，从而使得高压侧换热器剩余的热量仍然可以进行放热而低压侧换热器仍然能够具有蒸发吸热的能力，这样，在压缩机1停机时，制冷装置仍然能够利用换热器内剩余的热量，从而提升了制冷装置的总体效率，能使系统的剩余热量得到利用，具有简单可靠，高效节能的特点。
在本公开中，由于压缩机1停机后，旁通阀6将压缩机的高压侧与高压侧换热器断开并且直接连通至压缩机的低压侧，由于压缩机的高压侧容积较小，并且旁通阀6具有直接的连通通道，这样的话，压缩机1的高压侧与低压侧可以快速实现压力平衡，满足压缩机启动时的压差如小于1kgf/cm2的要求，从而实现压缩机停机后快速重新启动的功能。发明人通过大量实验测试得到的压力平衡时间根据选用的旁通阀6的旁通通道的尺寸大小，可以实现最快1分钟内达到压力平衡的要求。
从上述描述可以看出，本公开实施例的压缩机1，仅通过增加一个旁通阀6，便可同时实现系统的余热利用和快速压力平衡的双重效果，特别适合于对启动压差比较敏感、启动力矩比较大以及有快速重新启动要求的场合，对转子式压缩机的应用尤其有效，具有成本低、适用范围广、控制简单可靠的优点。
根据本公开实施例的压缩机1，可以实现压缩机1的快速重启，且在压缩机1停机后还能利用剩余热量，能效高。
下面参考图6-图8描述本公开实施例的旁通阀6的结构。
如图6-图8所示，旁通阀6包括：阀体6d、阀芯6e和电磁控制部6g。
其中，阀体6d限定出阀腔，第一端口6a、第二端口6b、第三端口6c均设在阀体6d，且第一端口6a、第二端口6b、第三端口6c均与阀腔连通，阀芯6e可活动地设在阀体6d内，阀芯6e具有流道6f，流道6f始终与第一端口6a连通，且流道6f可选择性地与第二端口6b、第三端口6c连通。当流道6f与第二端口6b连通时，第一端口6a、第二端口6b连通；当流道6f与第三端口6c连通时，第一端口6a、第三端口6c连通。
阀芯6e的至少部分沿阀体6d的轴向可活动地设在阀体6d内，第一端口6a设在阀体6d的轴向的第一端部(即图6-图8中的左端)，第二端口6b设在阀体6d的第一侧面(即图6-图8中的上侧面)，第三端口6c设在阀体6d的第二侧面(即图6-图8中的下侧面)，流道6f具有朝向第一端部的第一敞开端、朝向第一侧面的第二敞开端、朝向第二侧面的第三敞开端，在一些实施例中，流道6f包括沿阀体6d的轴向延伸的第一段和沿阀体6d的径向延伸的第二段，第一段可以为盲孔型，第二段为通孔型，第一段的敞开端形成为第一敞开端，第二段的两端形成为第二敞开端和第三敞开端，且在阀芯6e位于图6所示的位置时，第二敞开端和第三敞开端分别与第二端口6b、第三端口6c正对。在第二敞开端与第二端口6b相对时，第一端口6a与第二端口6b连通；在第三敞开端与第三端口6c相对时，第一端口6a与第三端口6c连通。
电磁控制部6g与阀芯6e电磁连接，阀芯6e可以包括伸出从阀体6d的轴向的第二端部(即图6-图8中的右端)伸出的控制杆，电磁控制部6g套设在控制杆外，控制杆为铁磁性材料制成，当电磁控制部6g通电时，控制杆可以沿轴向移动。电磁控制部6g与电机部电连接，也就是说，电磁控制部6g可以由电机部的得电信号控制。
在一些实施例中，旁通阀6具有第一状态和第二状态：如图6所示，在第一状态时，第一端口6a与第二端口6b连通，第一端口6a与第三端口6c断开；如图7所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第一状态。也就是说，压缩机1 启动时，旁通阀6自动切换到第一状态，便于压缩机1向外排气，压缩机1停机时，旁通阀6自动切换到第二状态，便于压缩机1的排气侧和吸气侧的压力迅速平衡，便于下次迅速启动。
在另一些实施例中，旁通阀6具有第一状态、第二状态和第三状态：如图6所示，在第一状态时，第一端口6a与第二端口6b连通，第一端口6a与第三端口6c断开；如图7所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开；如图8所示，在第三状态时，第一端口6a与第二端口6b断开，第一端口6a与第三端口6c断开。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第三状态，且当P1≥P2时，旁通阀6切换为第一状态，当P1＜P2时，若电机部未停机则旁通阀6保持第三状态，若电机部停机则旁通阀6切换为第二状态；其中，P1为第一端口6a处的压力，P2为第二端口6b处的压力。在本实施例中，由于增加压力控制信号，因此，旁通阀6的电磁控制部6g的电信号可以与电机部的控制信号连接，也可以独立设置控制部进行控制。
在又一些实施例中，旁通阀6具有第一状态、第二状态和第三状态：如图6所示，在第一状态时，第一端口6a与第二端口6b连通，第一端口6a与第三端口6c断开，如图7所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开；如图8所示，在第三状态时，第一端口6a与第二端口6b断开，第一端口6a与第三端口6c断开。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第三状态，并保持预设时间t后，若电机部未停机则旁通阀6切换为第一状态，若电机部停机则旁通阀6切换为第二状态，其中满足：1秒≤t≤10秒，或者满足：2秒≤t≤6秒。
下面参考图2-图4描述根据本公开实施例的两种类型的压缩机1的结构。
如图2和图3所示，在一些实施例中，压缩机1还包括：储液器，储液器的出口与压缩机构部的进气口连通，储液器上设置有吸气管13，吸气侧包括储液器和吸气管13；密封容器11限定出高压的容纳腔，密封容器11上设有排气管12，排气侧包括容纳腔和排气管12。
也就是说，密封容器11围成高压的内部空间，在密封容器11上设置有连通高压内部空间的排气管12，密封容器11的内部空间及排气管12共同构成了压缩机1的高压侧，电机部及压缩机构部设置在高压的密封容器11内部空间中；储液器设置在密封容器11外部，储液器的出口与压缩机1构的进气口连通，在储液器上设置有吸气管13，吸气管13与制冷装置的吸气侧管路13a(低压管路)连通，储液器、吸气管13共同构成了压缩机1的低 压侧。
旁通阀6的第一端口6a与压缩机1的高压侧连通，旁通阀6的第二端口6b与制冷装置的排气侧管路12a(高压管路)连通，旁通阀6的第三端口6c与压缩机1的吸气侧及制冷装置的吸气侧管路13a(低压管路)连通。
如图4所示，在另一些实施例中，密封容器11限定出低压的第一腔和高压的第二腔，密封容器11上设有与第一腔连通的吸气管13，密封容器11上设有与第二腔连通的排气管12，吸气侧包括第一腔和吸气管13，排气侧包括第二腔和排气管12。
也就是说，密封容器11围成低压的内部空间，在密封容器11上设置有连通低压内部空间的吸气管13，吸气管13与制冷装置的吸气侧管路13a(低压管路)连通，低压的内部空间、吸气管13共同构成了压缩机1的低压侧；电机部及压缩机构部设置在低压的密封容器11内部空间中。
特别地，某些设计中，将密封容器11的内部空间分隔成较大容积的低压的内部空间和较小容积的高压内部空间两部分，压缩机1构的一端位于低压的内部空间中，而另一端位于高压的内部空间中，这种情况下，由于低压的内部空间较大，我们仍然认为压缩机1机构位于低压的内部空间中，而该压缩机1为密封容器11内低压力结构的压缩机1。
密封容器11内低压力结构的压缩机1还具有高压排气腔及排气管12，高压排气腔作为容纳经过压缩机1构压缩后的高压气体的空间用以与低压的内部空间进行密封分隔，排气管12连通高压排气腔。在实际设计中，高压排气腔可以设置在密封容器11的内部空间中，也可以设置在密封容器11的外部。高压排气腔及排气管12共同构成了压缩机1的高压侧。
旁通阀6的第一端口6a与压缩机1的高压侧连通，旁通阀6的第二端口6b与制冷装置的排气侧管路12a(高压管路)连通，旁通阀6的第三端口6c与压缩机1的吸气侧及制冷装置的吸气侧管路13a(低压管路)连通。
从上述描述可以看出，本公开实施例的压缩机1，仅通过增加一个旁通阀6，便可同时实现系统的余热利用和快速压力平衡的双重效果，特别适合于对启动压差比较敏感、启动力矩比较大以及有快速重新启动要求的场合，对转子式压缩机的应用尤其有效，具有成本低、适用范围广、控制简单可靠的优点。
下面参考图1-图8描述根据本公开实施例的制冷装置，本公开实施例的制冷装置可以为空调器、冰箱等。
如图5所示，根据本公开一个实施例的制冷装置包括：压缩机1、第一换热器2、节流阀4、第二换热器3，其中该压缩机1为上述任一种实施例的压缩机1，第一换热器2的第一接口与旁通阀6的第二端口6b相连，第一换热器2的第一接口与旁通阀6的第二端口6b之间通过排气侧管路12a(高压管路)连通，节流阀4连接在第一换热器2的第二接口 与第二换热器3的第一接口之间，第二换热器3的第二接口与压缩机1的吸气口相连，第二换热器3的第二接口与压缩机1的吸气口之间通过吸气侧管路13a(低压管路)连通，压缩机1的吸气口可以形成于压缩机1的吸气管13的端部。
根据本公开实施例的制冷装置，可以实现快速重启，且在压缩机1停机后还能利用剩余热量，能效高。
如图1-图4所示，根据本公开另一个实施例的制冷装置包括：压缩机1、换向装置5、第一换热器2、节流阀4、第二换热器3。
换向装置5包括第一口5a、第二口5b、第三口5c和第四口5d，换向装置5可以为四通阀，第一口5a与第二端口6b相连，第二口5b与第一换热器2的第一接口相连，第二口5b与第一换热器2的第一接口之间通过排气侧管路12a(高压管路)连通，节流阀4连接在第一换热器2的第二接口与第二换热器3的第一接口之间，第二换热器3的第二接口与第四口5d相连，第三口5c与压缩机1的吸气口相连，第三口5c与压缩机1的吸气口之间通过吸气侧管路13a(低压管路)连通，压缩机1的吸气口可以形成于压缩机1的吸气管13的端部。
当第一口5a与第二口5b连通，且第三口5c与第四口5d连通时，第一换热器2为高压侧换热器，第二换热器3为低压侧换热器；当第一口5a与第四口5d连通，且第二口5b与第三口5c连通时，第二换热器3为高压侧换热器，第一换热器2为低压侧换热器。
根据本公开实施例的压缩机，包括：密封容器；电机部和压缩机构部，所述电机部和所述压缩机构部均设置在所述密封容器内；旁通阀，所述旁通阀包括第一端口、第二端口、第三端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通；其中所述压缩机具有分隔开的排气侧和吸气侧，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，所述排气侧适于通过所述第二端口向外部零部件排气。
根据本公开实施例的压缩机，可以实现压缩机的快速重启，且在压缩机停机后还能利用剩余热量，能效高。
根据本公开一个实施例的压缩机，所述旁通阀包括：阀体，所述阀体限定出阀腔，所述第一端口、所述第二端口、所述第三端口均设在所述阀体且均与所述阀腔连通；阀芯，所述阀芯可活动地设在所述阀体内，所述阀芯具有流道，所述流道与所述第一端口连通，且所述流道可选择性地与所述第二端口、所述第三端口连通。
根据本公开一个实施例的压缩机，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口设在所述阀体的轴向的第一端部，所述第二端口设在所述阀体的第一侧面，所述第三端口设在所述阀体的第二侧面，所述流道具有朝向所述第一端部的第一敞开端、朝向所述第一侧面的第二敞开端、朝向所述第二侧面的第三敞开端；其中， 在所述第二敞开端与所述第二端口相对时，所述第一端口与所述第二端口连通；在所述第三敞开端与所述第三端口相对时，所述第一端口与所述第三端口连通。
根据本公开一个实施例的压缩机，所述旁通阀还包括：电磁控制部，所述电磁控制部与所述阀芯电磁连接。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态和第二状态，在第一状态时，所述第一端口与所述第二端口连通，所述第一端口与所述第三端口断开，在第二状态时，所述第一端口与所述第三端口连通，所述第一端口与所述第二端口断开；所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第一状态。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态、第二状态和第三状态，在第一状态时，所述第一端口与所述第二端口连通，所述第一端口与所述第三端口断开，在第二状态时，所述第一端口与所述第三端口连通，所述第一端口与所述第二端口断开，在第三状态时，所述第一端口与所述第二端口断开，所述第一端口与所述第三端口断开。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，且当P1≥P2时，所述旁通阀切换为第一状态，当P1＜P2时，若所述电机部未停机则所述旁通阀保持第三状态，若所述电机部停机则所述旁通阀切换为第二状态；其中，P1为所述第一端口处的压力，P2为所述第二端口处的压力。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，并保持预设时间t后，若所述电机部未停机则所述旁通阀切换为第一状态，若所述电机部停机则所述旁通阀切换为第二状态。
根据本公开一个实施例的压缩机，满足：1秒≤t≤10秒。
根据本公开一个实施例的压缩机，满足：2秒≤t≤6秒。
根据本公开一个实施例的压缩机，还包括：储液器，所述储液器的出口与所述压缩机构部的进气口连通，所述储液器上设置有吸气管，所述吸气侧包括所述储液器和所述吸气管；所述密封容器限定出高压的容纳腔，所述密封容器上设有排气管，所述排气侧包括所述容纳腔和所述排气管。
根据本公开一个实施例的压缩机，所述密封容器限定出低压的第一腔和高压的第二腔，所述密封容器上设有与所述第一腔连通的吸气管，所述密封容器上设有与所述第二腔连通的排气管，所述吸气侧包括所述第一腔和所述吸气管，所述排气侧包括所述第二腔和所述排气管。
本公开还提出了一种制冷装置，包括：第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述第一换热器的第一接口与所述第二端口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述压缩机的吸气口相连。
本公开还提出了一种制冷装置，包括：换向装置、第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述换向装置包括第一口、第二口、第三口和第四口，所述第一口与所述第二端口相连，所述第二口与所述第一换热器的第一接口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述第四口相连，所述第三口与所述压缩机的吸气口相连。
下面参考图9-图16描述根据本公开实施例的压缩机1。
如图9-图16所示，根据本公开一个实施例的压缩机1包括：密封容器11、电机部、压缩机构部、旁通阀6。
其中，压缩机1具有分隔开的排气侧和吸气侧，排气侧为高压侧，吸气侧为低压侧，电机部和压缩机构部均设置在密封容器11内，电机部用于驱动压缩机构部以实现吸气和压缩排气，旁通阀6包括第一端口6a、第二端口6b、第三端口6c、第四端口6h，第一端口6a可选择性地与第二端口6b、第三端口6c中的一个连通，第四端口6h可选择性地与第三端口6c连通，其中第一端口6a与压缩机1的排气侧连通，第三端口6c与压缩机1的吸气侧连通，在第一端口6a与第二端口6b连通且第三端口6c与第四端口6h连通时，排气侧适于通过第二端口6b向外部零部件排气，吸气侧适于通过第四端口6h向外部零部件吸气。换言之，压缩机通过第二端口6b和第四端口6h与外界管路相连，当第一端口6a与第二端口6b断开时，压缩机的排气侧断开与外部管路的连通，高压侧换热器残存的热量可以继续利用。
在压缩机1正常启动工作时，电机部工作，旁通阀6的第一端口6a与第二端口6b连通，旁通阀6的第三端口6c与第四端口6h连通，压缩机1的输出的高压气体从排气侧通过第一端口6a、第二端口6b输出到制冷装置的排气侧管路12a，压缩机1的吸气侧通过吸气侧管路13a、第四端口6h、第三端口6c吸气。
在压缩机1停止运行时，电机部不工作，旁通阀6的第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开，第三端口6c与第四端口6h断开。也就是说，旁通阀6将压缩机1的排气侧与吸气侧连通，且将压缩机1的排气侧与制冷装置的其他部件断开。
这样，在压缩机1停机时，可以使压缩机1的排气侧与吸气侧的压力快速平衡，便于快速再次启动压缩机1。
另一方面，在压缩机1停机时，旁通阀6切断了压缩机1的排气侧和制冷装置的连通，第二端口6b无法回流到第一端口6a，高压侧换热器内部保持较高的压力状态，节流阀3在压差的作用下仍然具有一定的流量，从而使得高压侧换热器剩余的热量仍然可以进行放热而低压侧换热器仍然能够具有蒸发吸热的能力，这样，在压缩机1停机时，制冷装置仍然能够利用换热器内剩余的热量，从而提升了制冷装置的总体效率，能使系统的剩余热量得到利用，具有简单可靠，高效节能的特点。
在本公开中，由于压缩机1停机后，旁通阀6将压缩机的高压侧与高压侧换热器断开并且直接连通至压缩机的低压侧，由于压缩机的高压侧容积较小，并且旁通阀6具有直接的连通通道，这样的话，压缩机1的高压侧与低压侧可以快速实现压力平衡，满足压缩机启动时的压差如小于1kgf/cm2的要求，从而实现压缩机停机后快速重新启动的功能。发明人通过大量实验测试得到的压力平衡时间根据选用的旁通阀6的旁通通道的尺寸大小，可以实现最快1分钟内达到压力平衡的要求。
从上述描述可以看出，本公开实施例的压缩机1，仅通过增加一个旁通阀6，便可同时实现系统的余热利用和快速压力平衡的双重效果，特别适合于对启动压差比较敏感、启动力矩比较大以及有快速重新启动要求的场合，对转子式压缩机的应用尤其有效，具有成本低、适用范围广、控制简单可靠的优点。
根据本公开实施例的压缩机1，可以实现压缩机1的快速重启，且在压缩机1停机后还能利用剩余热量，能效高。
下面参考图14-图16描述本公开实施例的旁通阀6的结构。
如图14-图16所示，旁通阀6包括：阀体6d、阀芯6e和电磁控制部6g。
其中，阀体6d限定出阀腔，第一端口6a、第二端口6b、第三端口6c、第四端口6h均设在阀体6d，且第一端口6a、第二端口6b、第三端口6c、第四端口6h均与阀腔连通。
阀芯6e可活动地设在阀体6d内，阀芯6e具有第一流道6i、第二流道6j、第三流道6k，第一端口6a和第二端口6b适于通过第一流道6i连通且第三端口6c和第四端口6h适于通过第二流道6j连通，或者第一端口6a和第三端口6c适于通过第三流道6k连通。
阀芯6e的至少部分沿阀体6d的轴向(即图14-图16中的左右方向)可活动地设在阀体6d内，第一端口6a和第三端口6c设在阀体6a的第一侧面(即图14-图16中的下侧面)且第一端口6a和第三端口6c沿轴向间隔开布置，第二端口6b和第四端口6h设在阀体6a的第二侧面(即图14-图16中的上侧面)且第二端口6b和第四端口6h沿轴向间隔开布置，第一端口6a可以与第二端口6b正对设置，第三端口6c可以与第四端口6h正对设置。
第一流道6i的两个敞开端分别朝向阀体6a的第一侧面和第二侧面，第二流道6j的两个敞开端分别朝向阀体6a的第一侧面和第二侧面，第三流道6k的两个敞开端均朝向阀体 6a的第一侧面。
第一流道6i和第二流道6j沿阀芯6e的轴向间隔开布置，且第二流道6j沿阀芯6e的轴向的宽度大于第一流道6i沿阀芯6e的轴向的宽度，这样当第一端口6a与第二端口6b断开时，第三端口6c与第四端口6h可以保持连通。
在一些实施例中，第一流道6i和第二流道6j沿阀芯6e的径向贯穿阀芯6e，第三流道6k包括沿阀芯6e的轴向延伸的第一段和两段沿阀芯6e的径向延伸的第二段，两个第二段分别与第一段的两端相连，两个第二段背离第一段的端部敞开。
电磁控制部6g与阀芯6e电磁连接，阀芯6e可以包括伸出从阀体6d的轴向的第二端部(即图14-图16中的右端)伸出的控制杆，电磁控制部6g套设在控制杆外，控制杆为铁磁性材料制成，当电磁控制部6g通电时，控制杆可以沿轴向移动。电磁控制部6g与电机部电连接，也就是说，电磁控制部6g可以由电机部的得电信号控制。
在一些实施例中，旁通阀6具有第一状态和第二状态：如图14所示，在第一状态时，第一端口6a与第二端口6b连通，第四端口6h与第三端口6c连通；如图15所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开，第三端口6c与第四端口6h断开。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第一状态。也就是说，压缩机1启动时，旁通阀6自动切换到第一状态，便于压缩机1向外排气和吸气，压缩机1停机时，旁通阀6自动切换到第二状态，便于压缩机1的排气侧和吸气侧的压力迅速平衡，便于下次迅速启动。
在另一些实施例中，旁通阀6具有第一状态、第二状态和第三状态：如图14所示，在第一状态时，第一端口6a与第二端口6b连通，第四端口6h与第三端口6c连通；如图15所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开，第三端口6c与第四端口6h断开；如图16所示，在第三状态时，第一端口6a与第二端口6b断开，第四端口6h与第三端口6c连通。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第三状态，且当P1≥P2时，旁通阀6切换为第一状态，当P1＜P2时，若电机部未停机则旁通阀6保持第三状态，若电机部停机则旁通阀6切换为第二状态；其中，P1为第一端口6a处的压力，P2为第二端口6b处的压力。在本实施例中，由于增加压力控制信号，因此，旁通阀6的电磁控制部6g的电信号可以与电机部的控制信号连接，也可以独立设置控制部进行控制。
在又一些实施例中，旁通阀6具有第一状态、第二状态和第三状态：如图14所示，在第一状态时，第一端口6a与第二端口6b连通，第四端口6h与第三端口6c连通；如图15 所示，在第二状态时，第一端口6a与第三端口6c连通，第一端口6a与第二端口6b断开，第三端口6c与第四端口6h断开；如图16所示，在第三状态时，第一端口6a与第二端口6b断开，第四端口6h与第三端口6c连通。压缩机1设置为当电机部从运行状态停机时，旁通阀6从第一状态切换为第二状态；压缩机1设置为当电机部从停机状态启动时，旁通阀6从第二状态切换为第三状态，并保持预设时间t后，若电机部未停机则旁通阀6切换为第一状态，若电机部停机则旁通阀6切换为第二状态，其中满足：1秒≤t≤10秒，或者满足：2秒≤t≤6秒。
下面参考图10-图12描述根据本公开实施例的两种类型的压缩机1的结构。
如图10和图11所示，在一些实施例中，压缩机1还包括：储液器，储液器的出口与压缩机构部的进气口连通，储液器上设置有吸气管13，吸气侧包括储液器和吸气管13；密封容器11限定出高压的容纳腔，密封容器11上设有排气管12，排气侧包括容纳腔和排气管12。
也就是说，密封容器11围成高压的内部空间，在密封容器11上设置有连通高压内部空间的排气管12，密封容器11的内部空间及排气管12共同构成了压缩机1的高压侧，电机部及压缩机构部设置在高压的密封容器11内部空间中；储液器设置在密封容器11外部，储液器的出口与压缩机1构的进气口连通，在储液器上设置有吸气管13，吸气管13与制冷装置的吸气侧管路13a(低压管路)连通，储液器、吸气管13共同构成了压缩机1的低压侧。
旁通阀6的第一端口6a与压缩机1的高压侧连通，旁通阀6的第二端口6b与制冷装置的排气侧管路12a(高压管路)连通，旁通阀6的第三端口6c与压缩机1的吸气侧连通，旁通阀6的第四端口6h与制冷装置的吸气侧管路13a(低压管路)连通。
如图12所示，在另一些实施例中，密封容器11限定出低压的第一腔和高压的第二腔，密封容器11上设有与第一腔连通的吸气管13，密封容器11上设有与第二腔连通的排气管12，吸气侧包括第一腔和吸气管13，排气侧包括第二腔和排气管12。
也就是说，密封容器11围成低压的内部空间，在密封容器11上设置有连通低压内部空间的吸气管13，吸气管13与制冷装置的吸气侧管路13a(低压管路)连通，低压的内部空间、吸气管13共同构成了压缩机1的低压侧；电机部及压缩机构部设置在低压的密封容器11内部空间中。
特别地，某些设计中，将密封容器11的内部空间分隔成较大容积的低压的内部空间和较小容积的高压内部空间两部分，压缩机1构的一端位于低压的内部空间中，而另一端位于高压的内部空间中，这种情况下，由于低压的内部空间较大，我们仍然认为压缩机1机构位于低压的内部空间中，而该压缩机1为密封容器11内低压力结构的压缩机1。
密封容器11内低压力结构的压缩机1还具有高压排气腔及排气管12，高压排气腔作为容纳经过压缩机1构压缩后的高压气体的空间用以与低压的内部空间进行密封分隔，排气管12连通高压排气腔。在实际设计中，高压排气腔可以设置在密封容器11的内部空间中，也可以设置在密封容器11的外部。高压排气腔及排气管12共同构成了压缩机1的高压侧。
旁通阀6的第一端口6a与压缩机1的高压侧连通，旁通阀6的第二端口6b与制冷装置的排气侧管路12a(高压管路)连通，旁通阀6的第三端口6c与压缩机1的吸气侧连通，旁通阀6的第四端口6h与制冷装置的吸气侧管路13a(低压管路)连通。
从上述描述可以看出，本公开实施例的压缩机1，仅通过增加一个旁通阀6，便可同时实现系统的余热利用和快速压力平衡的双重效果，特别适合于对启动压差比较敏感、启动力矩比较大以及有快速重新启动要求的场合，对转子式压缩机的应用尤其有效，具有成本低、适用范围广、控制简单可靠的优点。
下面参考图9-图16描述根据本公开实施例的制冷装置，本公开实施例的制冷装置可以为空调器、冰箱等。
如图13所示，根据本公开一个实施例的制冷装置包括：压缩机1、第一换热器2、节流阀4、第二换热器3，其中该压缩机1为上述任一种实施例的压缩机1，第一换热器2的第一接口与旁通阀6的第二端口6b相连，第一换热器2的第一接口与旁通阀6的第二端口6b之间通过排气侧管路12a(高压管路)连通，节流阀4连接在第一换热器2的第二接口与第二换热器3的第一接口之间，第二换热器3的第二接口与第四端口6h相连，第二换热器3的第二接口与第四端口6h之间通过吸气侧管路13a(低压管路)连通，第四端口6h可以形成为压缩机1的吸气口。
根据本公开实施例的制冷装置，可以实现快速重启，且在压缩机1停机后还能利用剩余热量，能效高。
如图9-图12所示，根据本公开另一个实施例的制冷装置包括：压缩机1、换向装置5、第一换热器2、节流阀4、第二换热器3。
换向装置5包括第一口5a、第二口5b、第三口5c和第四口5d，换向装置5可以为四通阀，第一口5a与第二端口6b相连，第二口5b与第一换热器2的第一接口相连，第二口5b与第一换热器2的第一接口之间通过排气侧管路12a(高压管路)连通，节流阀4连接在第一换热器2的第二接口与第二换热器3的第一接口之间，第二换热器3的第二接口与第四口5d相连，第三口5c与第四端口6h相连，第三口5c与第四端口6h之间通过吸气侧管路13a(低压管路)连通，第四端口6h可以形成为压缩机1的吸气口。
当第一口5a与第二口5b连通，且第三口5c与第四口5d连通时，第一换热器2为高压侧换热器，第二换热器3为低压侧换热器；当第一口5a与第四口5d连通，且第二口5b 与第三口5c连通时，第二换热器3为高压侧换热器，第一换热器2为低压侧换热器。
根据本公开实施例的压缩机，包括：密封容器；电机部和压缩机构部，所述电机部和所述压缩机构部均设置在所述密封容器内；旁通阀，所述旁通阀包括第一端口、第二端口、第三端口、第四端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通，所述第四端口可选择性地与所述第三端口连通；其中所述压缩机具有分隔开的排气侧和吸气侧，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，在所述第一端口与所述第二端口连通且所述第三端口与第四端口连通时，所述排气侧适于通过所述第二端口向外部零部件排气，所述吸气侧适于通过所述第四端口向外部零部件吸气。
根据本公开实施例的压缩机，可以实现压缩机的快速重启，且在压缩机停机后还能利用剩余热量，能效高。
根据本公开一个实施例的压缩机，所述旁通阀包括：阀体，所述阀体限定出阀腔，所述第一端口、所述第二端口、所述第三端口、所述第四端口均设在所述阀体且均与所述阀腔连通；阀芯，所述阀芯可活动地设在所述阀体内，所述阀芯具有第一流道、第二流道、第三流道，所述第一端口和所述第二端口适于通过所述第一流道连通且所述第三端口和所述第四端口适于通过所述第二流道连通，或者所述第一端口和所述第三端口适于通过所述第三流道连通。
根据本公开一个实施例的压缩机，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口和所述第三端口设在所述阀体的第一侧面且沿轴向间隔开布置，所述第二端口和所述第四端口设在所述阀体的第二侧面且沿轴向间隔开布置，所述第一流道的两个敞开端和所述第二流道的两个敞开端分别朝向所述阀体的第一侧面和第二侧面，所述第三流道的两个敞开端均朝向所述阀体的第一侧面。
根据本公开一个实施例的压缩机，所述第一流道和所述第二流道沿所述阀芯的轴向间隔开布置，且所述第二流道沿所述阀芯的轴向的宽度大于所述第一流道沿所述阀芯的轴向的宽度。
根据本公开一个实施例的压缩机，所述旁通阀还包括：电磁控制部，所述电磁控制部与所述阀芯电磁连接。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态和第二状态，在第一状态时，所述第一端口与所述第二端口连通，所述第四端口与所述第三端口连通，在第二状态时，所述第一端口与所述第三端口连通，所述第一端口与所述第二端口断开，所述第三端口与所述第四端口断开；所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第一状态。
根据本公开一个实施例的压缩机，所述旁通阀具有第一状态、第二状态和第三状态，在第一状态时，所述第一端口与所述第二端口连通，所述第四端口与所述第三端口连通，在第二状态时，所述第一端口与所述第三端口连通，所述第一端口与所述第二端口断开，所述第三端口与所述第四端口断开，在第三状态时，所述第一端口与所述第二端口断开，所述第四端口与所述第三端口连通。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，且当P1≥P2时，所述旁通阀切换为第一状态，当P1＜P2时，若所述电机部未停机则所述旁通阀保持第三状态，若所述电机部停机则所述旁通阀切换为第二状态；其中，P1为所述第一端口处的压力，P2为所述第二端口处的压力。
根据本公开一个实施例的压缩机，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，并保持预设时间t后，若所述电机部未停机则所述旁通阀切换为第一状态，若所述电机部停机则所述旁通阀切换为第二状态。
根据本公开一个实施例的压缩机，满足：1秒≤t≤10秒。
根据本公开一个实施例的压缩机，还包括：储液器，所述储液器的出口与所述压缩机构部的进气口连通，所述储液器上设置有吸气管，所述吸气侧包括所述储液器和所述吸气管；所述密封容器限定出高压的容纳腔，所述密封容器上设有排气管，所述排气侧包括所述容纳腔和所述排气管。
根据本公开一个实施例的压缩机，所述密封容器限定出低压的第一腔和高压的第二腔，所述密封容器上设有与所述第一腔连通的吸气管，所述密封容器上设有与所述第二腔连通的排气管，所述吸气侧包括所述第一腔和所述吸气管，所述排气侧包括所述第二腔和所述排气管。
本公开还提出了一种制冷装置，包括：第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述第一换热器的第一接口与所述第二端口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述第四端口相连。
本公开还提出了一种制冷装置，包括：换向装置、第一换热器、节流阀、第二换热器、如上述任一种所述的压缩机，所述换向装置包括第一口、第二口、第三口和第四口，所述第一口与所述第二端口相连，所述第二口与所述第一换热器的第一接口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述第四口相连，所述第三口与所述第四端口相连。

Claims (18)

  1. 一种压缩机，其特征在于，包括：
    密封容器；
    电机部和压缩机构部，所述电机部和所述压缩机构部均设置在所述密封容器内；
    旁通阀；其中
    所述压缩机具有分隔开的排气侧和吸气侧，所述排气侧与所述旁通阀相连，所述排气侧适于通过所述旁通阀向外部零部件排气或者通过所述旁通阀与所述吸气侧连通。
  2. 根据权利要求1所述的压缩机，其特征在于，所述旁通阀包括：
    阀体，所述阀体限定出阀腔，所述阀体设有多个与所述阀腔连通的端口，所述端口用于与所述排气侧、所述吸气侧、所述外部零部件相连；
    阀芯，所述阀芯可活动地设在所述阀体内，所述阀芯具有流道，多个所述端口可选择性地通过所述流道连通。
  3. 根据权利要求2所述的压缩机，其特征在于，所述旁通阀还包括：电磁控制部，所述电磁控制部与所述阀芯电磁连接。
  4. 根据权利要求2或3所述的压缩机，其特征在于，所述旁通阀包括第一端口、第二端口、第三端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，所述排气侧适于通过所述第二端口向外部零部件排气。
  5. 根据权利要求4所述的压缩机，其特征在于，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口设在所述阀体的轴向的第一端部，所述第二端口设在所述阀体的第一侧面，所述第三端口设在所述阀体的第二侧面，所述流道具有朝向所述第一端部的第一敞开端、朝向所述第一侧面的第二敞开端、朝向所述第二侧面的第三敞开端；其中，
    在所述第二敞开端与所述第二端口相对时，所述第一端口与所述第二端口连通；在所述第三敞开端与所述第三端口相对时，所述第一端口与所述第三端口连通。
  6. 根据权利要求2或3所述的压缩机，其特征在于，所述旁通阀包括第一端口、第二端口、第三端口、第四端口，所述第一端口可选择性地与所述第二端口、所述第三端口中的一个连通，所述第四端口可选择性地与所述第三端口连通，所述第一端口与所述排气侧连通，所述第三端口与所述吸气侧连通，在所述第一端口与所述第二端口连通且所述第三端口与所述第四端口连通时，所述排气侧适于通过所述第二端口向外部零部件排气，所述吸气侧适于通过所述第四端口向外部零部件吸气。
  7. 根据权利要求6所述的压缩机，其特征在于，所述阀芯具有第一流道、第二流道、第三流道，所述第一端口和所述第二端口适于通过所述第一流道连通且所述第三端口和所述第四端口适于通过所述第二流道连通，或者所述第一端口和所述第三端口适于通过所述第三流道连通。
  8. 根据权利要求7所述的压缩机，其特征在于，所述阀芯的至少部分沿所述阀体的轴向可活动地设在所述阀体内，所述第一端口和所述第三端口设在所述阀体的第一侧面且沿轴向间隔开布置，所述第二端口和所述第四端口设在所述阀体的第二侧面且沿轴向间隔开布置，所述第一流道的两个敞开端和所述第二流道的两个敞开端分别朝向所述阀体的第一侧面和第二侧面，所述第三流道的两个敞开端均朝向所述阀体的第一侧面。
  9. 根据权利要求8所述的压缩机，其特征在于，所述第一流道和所述第二流道沿所述阀芯的轴向间隔开布置，且所述第二流道沿所述阀芯的轴向的宽度大于所述第一流道沿所述阀芯的轴向的宽度。
  10. 根据权利要求1-9中任一项所述的压缩机，其特征在于，所述旁通阀具有第一状态和第二状态，在第一状态时，所述排气侧通过所述旁通阀与外部零部件连通，在第二状态时，所述排气侧通过所述旁通阀与所述吸气侧连通；
    所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第一状态。
  11. 根据权利要求1-9中任一项所述的压缩机，其特征在于，所述旁通阀具有第一状态、第二状态和第三状态，在第一状态时，所述排气侧通过所述旁通阀与外部零部件连通，且所述排气侧与所述吸气侧断开，在第二状态时，所述排气侧与外部零部件断开，所述排气侧通过所述旁通阀与所述吸气侧连通，在第三状态时，所述排气侧与外部零部件断开，且所述排气侧与所述吸气侧断开。
  12. 根据权利要求11所述的压缩机，其特征在于，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，且当P1≥P2时，所述旁通阀切换为第一状态，当P1＜P2时，若所述电机部未停机则所述旁通阀保持第三状态，若所述电机部停机则所述旁通阀切换为第二状态；其中，
    P1为所述第一端口处的压力，P2为所述第二端口处的压力。
  13. 根据权利要求12所述的压缩机，其特征在于，所述压缩机设置为当所述电机部从运行状态停机时，所述旁通阀从第一状态切换为第二状态；所述压缩机设置为当所述电机部从停机状态启动时，所述旁通阀从第二状态切换为第三状态，并保持预设时间t后，若 所述电机部未停机则所述旁通阀切换为第一状态，若所述电机部停机则所述旁通阀切换为第二状态。
  14. 根据权利要求13所述的压缩机，其特征在于，满足：1秒≤t≤10秒。
  15. 根据权利要求1-14中任一项所述的压缩机，其特征在于，还包括：储液器，所述储液器的出口与所述压缩机构部的进气口连通，所述储液器上设置有吸气管，所述吸气侧包括所述储液器和所述吸气管；
    所述密封容器限定出高压的容纳腔，所述密封容器上设有排气管，所述排气侧包括所述容纳腔和所述排气管。
  16. 根据权利要求1-5中任一项所述的压缩机，其特征在于，所述密封容器限定出低压的第一腔和高压的第二腔，所述密封容器上设有与所述第一腔连通的吸气管，所述密封容器上设有与所述第二腔连通的排气管，所述吸气侧包括所述第一腔和所述吸气管，所述排气侧包括所述第二腔和所述排气管。
  17. 一种制冷装置，其特征在于，包括：第一换热器、节流阀、第二换热器、如权利要求1-16中任一项所述的压缩机，所述第一换热器的第一接口与所述旁通阀相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述压缩机的吸气口相连。
  18. 一种制冷装置，其特征在于，包括：换向装置、第一换热器、节流阀、第二换热器、如权利要求1-16中任一项所述的压缩机，所述换向装置包括第一口、第二口、第三口和第四口，所述第一口与所述旁通阀相连，所述第二口与所述第一换热器的第一接口相连，所述节流阀连接在所述第一换热器的第二接口与所述第二换热器的第一接口之间，所述第二换热器的第二接口与所述第四口相连，所述第三口与所述压缩机的吸气口相连。
PCT/CN2018/117592 2018-07-25 2018-11-27 压缩机和制冷装置 WO2020019608A1 (zh)

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