WO2021035945A1 - 回转式压缩机及冷冻循环装置 - Google Patents

回转式压缩机及冷冻循环装置 Download PDF

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Publication number
WO2021035945A1
WO2021035945A1 PCT/CN2019/115399 CN2019115399W WO2021035945A1 WO 2021035945 A1 WO2021035945 A1 WO 2021035945A1 CN 2019115399 W CN2019115399 W CN 2019115399W WO 2021035945 A1 WO2021035945 A1 WO 2021035945A1
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WIPO (PCT)
Prior art keywords
pressure
bypass
rotary compressor
cylinder
suction pipe
Prior art date
Application number
PCT/CN2019/115399
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English (en)
French (fr)
Inventor
小津政雄
高斌
王玲
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 CN201910785989.4A external-priority patent/CN112412791B/zh
Priority claimed from CN201910785885.3A external-priority patent/CN112412790B/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 CA3137384A priority Critical patent/CA3137384C/en
Publication of WO2021035945A1 publication Critical patent/WO2021035945A1/zh
Priority to US17/485,775 priority patent/US12110890B2/en

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    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the application relates to the field of compressors, and in particular to a rotary compressor and a refrigerating cycle device.
  • the rotary compressor with the motor speed fixed at 50Hz or 60Hz needs to be repeatedly started and stopped frequently due to the room temperature control of the air conditioner.
  • the problem of a rotary compressor with a high-pressure internal pressure in a closed casing is that if the casing pressure or discharge pressure is not equal to the suction pressure of the compression chamber, the motor cannot be started. If it is the same as before, it takes about 3 minutes to restart the compressor after it stops, and it takes time for the compressor shell pressure to change from low pressure to high pressure after restarting. This not only makes the air conditioner less comfortable, but also the APF of the air conditioner. Will get worse.
  • This application aims to solve one of the above technical problems in the prior art at least to a certain extent. For this reason, the present application proposes a rotary compressor to shorten the restart time of the compressor.
  • This application also proposes a refrigeration cycle device with the above-mentioned rotary compressor.
  • the rotary compressor according to the embodiment of the present application includes a casing that houses a motor and a compression mechanism, a discharge pipe connected to the high-pressure side of the refrigeration cycle device is connected to the casing, and a suction pipe connected to the low-pressure side of the refrigeration cycle device is connected
  • the compression mechanism part has a bypass device, and when the motor is stopped, the gas in the housing flows to the suction pipe or the low pressure circuit connected to the suction pipe.
  • the bypass device at least includes: a bypass hole communicating with the housing, a bypass valve that opens and closes the bypass hole due to the pressure difference between the housing and the suction pipe, and
  • the bypass valve is a spring that moves in a direction to open the bypass hole.
  • one of the bypass holes is connected to the inside of the exhaust silencing chamber of the compression mechanism unit, and the other of the bypass holes is connected to the suction pipe or a low pressure circuit communicated with the suction pipe.
  • one of the main shaft plate and the secondary shaft plate connecting the opening surfaces on both sides of the cylinder compression chamber in the compression mechanism part is provided with the above-mentioned bypass device.
  • the bypass valve opens the bypass hole; when the pressure difference between the housing and the suction pipe is greater than At a preset value, the bypass valve closes the bypass hole.
  • the compression mechanism includes: a cylinder, a main bearing, and an auxiliary bearing, the main bearing is located at one end of the cylinder, the auxiliary bearing is located at the other end of the cylinder, and the main bearing Both the main shaft plate and the secondary shaft plate of the secondary bearing are provided with the bypass device.
  • the side of the main bearing facing away from the cylinder is provided with a main muffler
  • the side of the auxiliary bearing away from the cylinder is provided with a sub-muffler
  • the compression mechanism has a communication with the main muffler.
  • One end of the bypass hole of the bypass device communicates with the silencing chamber of the corresponding silencer, and the other end of the bypass hole communicates with the suction pipe.
  • the compression mechanism part includes: a cylinder, a main bearing, and an auxiliary bearing, the main bearing is located at one end of the cylinder, the auxiliary bearing is located at the other end of the cylinder, and the bypass The device is arranged on the outer peripheral surface of the cylinder.
  • the bypass device is a pressure equalization device, and the pressure equalization device has a bypass hole that communicates the inside of the housing with the suction pipe;
  • the rotary compressor further includes an accumulator, one end of the accumulator is connected to the suction pipe, and the other end of the accumulator is connected to a first check valve device.
  • the first check valve device is a one-way valve or an electromagnetic switch valve.
  • a second check valve device is provided on the exhaust pipe, and the second check valve device is closed when the pressure inside the housing decreases.
  • the second check valve device is a one-way valve or an electromagnetic switch valve.
  • the pressure equalization device includes: a bypass valve that opens or closes the bypass hole, and a spring that expands and contracts using the pressure difference between the housing and the reservoir.
  • the high-pressure side opening end of the bypass hole is located in the muffler of the compression mechanism part.
  • the compression mechanism includes a cylinder, a main bearing, and a secondary bearing.
  • the main bearing is located at one end of the cylinder
  • the secondary bearing is located at the other end of the cylinder
  • a compression chamber is formed in the cylinder, so The suction pipe is in communication with the compression chamber.
  • the muffler has a muffler exhaust hole communicating with the inside of the housing.
  • the bypass valve utilizes the pressure difference between the housing pressure and the reservoir to selectively connect the bypass hole with the suction pipe, and the spring causes the The bypass valve moves in a direction to open the bypass hole.
  • the restart time of the compressor can be greatly shortened, and therefore, the temperature fluctuation of the air conditioner is small and the APF can be improved.
  • a refrigeration cycle device includes the above-mentioned rotary compressor.
  • FIG. 1 is a schematic diagram of the structure of the rotary compressor 1 of the present application and a refrigeration cycle device of an air conditioner connected to the rotary compressor 1;
  • FIG. 2 is a schematic diagram of the detailed structure of the bypass device
  • FIG. 3 is a detailed view of the components of the bypass device 30;
  • Figure 4 is a plan view of the inside of the cylinder and the compression chamber viewed from below the compression mechanism;
  • Figure 5 is an internal plan view of the main bearing and the compression chamber in the cylinder viewed from above the compression mechanism;
  • Figure 6 is a schematic diagram of the flow of gas refrigerant during stable operation of the rotary compressor
  • Fig. 7 is a schematic diagram of the rotary compressor just after stopping
  • FIG. 8 is a schematic diagram of the stopping time of the rotary compressor lasting about 10 seconds
  • Fig. 9 is a schematic diagram of the stopping time of the rotary compressor lasting and about 30 seconds have passed;
  • Fig. 10 is a state diagram of 15 seconds after restarting the rotary compressor after 30 seconds have passed from the state (stop) of Fig. 9;
  • Fig. 11 (1) compares the high-pressure side pressure (Pd) and the low-pressure side pressure (Ps) of the rotary compressor of the present application with a bypass device and the conventional rotary compressor without a bypass device after the motor has stopped. )
  • the change. 2It shows the pressure change graph of high pressure (Pd) and low pressure (Ps) when the rotary compressor is restarted after a complete stop for 30 seconds;
  • Figure 12 is a schematic diagram of bypass devices provided on both the main shaft board and the secondary shaft board;
  • Fig. 13 is a schematic diagram of the bypass device provided on the outer peripheral wall of the cylinder.
  • Figure 14 is a schematic diagram of an air conditioning refrigeration cycle in stable operation including the compressor of the present application.
  • Figure 15 is a schematic diagram of the internal structure of the compressor in operation
  • Fig. 16 is a schematic diagram of the X-X section of Fig. 15;
  • 17 is a schematic cross-sectional view of the compression mechanism, showing the structure of the pressure equalization device
  • Figure 18 is a schematic diagram of the internal structure of the compressor after the compressor is stopped
  • Figure 19 shows the pressure distribution diagram of the refrigeration cycle device when the pressures of the housing, accumulator, and compression chamber become equal after the compressor is stopped;
  • Fig. 20 is a schematic diagram of the change of the discharge of the casing and the change of the internal pressure of the accumulator after the compressor starts to stop in the stable operation until the restart is completed.
  • first and second are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features defined with “first” and “second” may explicitly or implicitly include one or more of these features.
  • a plurality of means at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection , Or integrated; it can be mechanically connected, or electrically connected, or can communicate with each other; it can be directly connected, or indirectly connected through an intermediate medium, it can be the internal communication of two components or the interaction between two components.
  • installed can be a fixed connection or a detachable connection , Or integrated; it can be mechanically connected, or electrically connected, or can communicate with each other; it can be directly connected, or indirectly connected through an intermediate medium, it can be the internal communication of two components or the interaction between two components.
  • the rotary compressor is represented by a rotary compressor in which a piston revolves and a sliding vane reciprocates, a rotary compressor in which a piston and a sliding vane rotate together, and a scroll compressor having a fixed plate and a movable plate.
  • the embodiments of the present application make technical announcements on the most popular rotary compressors in household air conditioners.
  • FIG. 1 shows the structure of a rotary compressor 1 of the present application, and a refrigeration cycle device of an air conditioner to which the rotary compressor 1 is connected.
  • the sealed case 2 accommodates the compression mechanism part 5, the motor 6 and the lubricating oil 8 at the bottom.
  • the outer circumference of the cylinder 10 of the compression mechanism 5 is fixed to the inner circumference of the sealed housing 2 by spot welding.
  • the circular compression chamber 11 in the center of the cylinder 10 is sealed by the main shaft plate 21 of the main bearing 20 and the secondary shaft plate 26 of the sub bearing 25.
  • the crankshaft 40 is in sliding fit with the main bearing 20 and the auxiliary bearing 25, and the eccentric shaft 40a of the crankshaft 40 is in the compression chamber 11 to drive the piston 15 to revolve.
  • the front end of the sliding piece 16 reciprocating in the sliding piece groove 14 of the cylinder 10 abuts against the outer circumference of the piston 15 (shown in Figs. 4 and 5).
  • the motor 6 is composed of a stator 6a fixed on the inner circumference of the sealed housing 2 by a heat jacket and a rotor 6b fixed on the crankshaft 40.
  • the motor 6 has a constant speed of one of 50 Hz or 60 Hz power.
  • the low-pressure accumulator 45 outside the sealed housing 2 is composed of a container suction pipe 47 connected to the upper part of the cylindrical container 46, a gas-liquid refrigerant separation plate 46a inside the low-pressure cylindrical container 46, and a central pipe 48 arranged in the center .
  • the curved pipe at the lower end of the central pipe 48 is connected to the suction pipe 13, and the suction pipe 13 is pressed into the suction hole 12 that opens the compression chamber 11 from the outer periphery of the cylinder 10.
  • the main muffler 23 is fixed to the main shaft plate 21 of the main bearing 20 by a plurality of screws, and a bypass device 30 is provided inside.
  • the lower end of the bypass hole 33 located at the center opens a U-shaped groove 12 a that is machined at the opening end of the suction hole 12 of the cylinder 10.
  • the upper end of the bypass hole 33 is opened and closed by the bypass valve 32.
  • the exhaust pipe 3 located at the center of the upper end of the sealed casing 2 is connected to the condenser 50 of the refrigeration cycle device.
  • the condenser 50 is connected in the order of the capillary tube 51, the evaporator 52, and the accumulator 45.
  • the feature of this refrigeration cycle device is that a check valve 53 is provided between the exhaust pipe 3 and the condenser 50.
  • the capillary 51 may be an electronic expansion valve.
  • the exhaust hole 21a (broken line, shown in FIG. 5) is exhausted to the main muffler 23. Therefore, the main muffler 23 is an exhaust muffler.
  • the high-pressure gas passing through the muffler exhaust hole 23a of the main muffler 23 flows into the lower space of the motor 6 and flows from the inner and outer gaps of the motor 6 to the upper space. During this period, most of the lubricating oil contained in the high-pressure gas separates and merges with the lubricating oil 8 at the bottom of the sealed casing 2.
  • the high-pressure gas passes through the check valve 53 from the exhaust pipe 3 and becomes a high-pressure liquid refrigerant in the condenser 50.
  • the low-pressure refrigerant that has passed through the capillary 51 evaporates in the evaporator 52 and flows into the circle from the housing suction pipe 47 of the accumulator 45. ⁇ 46 ⁇ Tube shell 46.
  • the liquid refrigerant that cannot be evaporated is stored at the bottom of the cylindrical shell 46, and the low-pressure gas refrigerant returns from the central pipe 48 to the suction pipe 13 of the cylinder 10.
  • the check valve 53 operates due to the pressure difference between the condenser 50 and the sealed housing 2 and closes the exhaust pipe 3. At this time, since the high-pressure gas in the sealed housing 2 passes through the sliding gap (about 5-10 ⁇ m) between the piston 15 and the sliding plate 16, etc., it flows backward from the suction pipe 13 opening the low-pressure compression chamber 11 to the accumulator 45, The internal pressure of the accumulator 45 rises, and the pressure of the sealed casing 2 falls.
  • the check valve 53 if the check valve 53 is closed, the high-pressure refrigerant of the condenser 50 cannot flow back into the sealed casing 2, and the condenser 50 stores the high-pressure liquid refrigerant at a high temperature during operation. However, since the liquid refrigerant of the condenser 50 releases heat and flows out to the evaporator 52 through the capillary tube 51, the pressure of the condenser 50 drops.
  • FIG. 2 is a detailed configuration diagram of the bypass device 30, and Fig. A (closed hole) and Fig. B (opened hole) show its operation.
  • FIG. 3 is a detailed diagram of the component parts of the bypass device 30.
  • the bypass device 30 has a bypass hole 33 in the center of the cylindrical hole 31 machined on the spindle plate 21, a valve seat 33 a is provided on the bypass hole 33, and the coil spring 34 is inserted into the outer peripheral groove.
  • the coil spring 34 is a compression spring and always moves the bypass valve 32 in a direction to open the bypass hole 33.
  • the lower end of the coil spring 34 is located in the spring limiting groove 31 b of the valve seat 33 a, and the upper end of the coil spring 34 is connected to the bypass valve 32.
  • the C-shaped retaining ring 35 serves as a stopper for the bypass valve 32 and is inserted into the retaining ring groove 31 a on the inner circumference of the cylindrical hole 31. Therefore, the bypass valve 32 moves up and down in the gap between the valve seat 33a and the C-shaped retaining ring 35 due to the pressure difference acting on the upper and lower surfaces thereof. As shown in FIG. 3, the four gas grooves 32a provided in the outer periphery of the bypass valve 32 become gas passages.
  • the design of the elastic force (spring number) of the coil spring 34 and the aperture of the bypass hole 33 is very important, and is a factor that determines the pressure difference ( ⁇ P) at which the bypass hole 33 opens and the flow rate through the bypass hole 33.
  • ⁇ P the high pressure (Pd) of the main muffler 23-the low pressure (Ps) of the U-shaped groove 12a, and the predetermined design pressure difference is ⁇ Pa.
  • FIG. A shows a state in which the bypass hole 33 is closed by the bypass valve 32. At this time, the pressure difference (Pd-Ps)> ⁇ Pa.
  • FIG. B shows a state in which the bypass hole 33 is opened by the bypass valve 32.
  • FIG. 4 is a plan view of the inside of the cylinder 10 and the compression chamber 11 viewed from below the compression mechanism part 5.
  • the lower end of the bypass hole 33 is opened to the U-shaped groove 12 a, and the U-shaped groove 12 a is located on the opening end of the suction hole 12 of the cylinder 10.
  • the pressure of the back hole 14 a of the sliding plate is equal to the pressure of the sealing housing 2, and the sliding plate 16 reciprocates along the sliding plate groove 14.
  • the inside of the piston 15 is also equal to the pressure of the sealed housing 2.
  • FIG. 5 is an internal plan view of the main bearing 20 and the compression chamber 11 in the cylinder 10 viewed from above the compression mechanism part 5, showing the bypass device 30 provided on the main shaft plate 21 of the main bearing 20, and opening and closing the exhaust The exhaust valve 24 of the hole 21a.
  • the bypass device 30 and the exhaust device 36 can be arranged on both sides of the sliding vane groove 16.
  • FIG. 6 shows the flow of the gas refrigerant during the stable operation of the rotary compressor 1.
  • the low-pressure gas (pressure Ps) flowing into the intake pipe 13 from the accumulator 45 is compressed into high-pressure gas (Pd) by the piston 15 and is discharged from the main muffler 23 through the exhaust hole 21a.
  • Pd high-pressure gas
  • the high-pressure gas discharged from the muffler exhaust hole 23 a is discharged into the inside of the sealed casing 2, it flows from the exhaust pipe 3 into the condenser 50 through the check valve 53.
  • Fig. 10 shows a state in which 15 seconds have passed after the rotary compressor 1 is restarted after 30 seconds have elapsed from the state (stopped) of Fig. 9. Since it is started from a state where the suction pressure is high (Ps++), the pressure between the main muffler 23 and the sealed housing 2 rises rapidly, and the pressure difference is greater than ⁇ Pa, so the bypass hole 33 is closed. That is, Pd-Ps> ⁇ Pa.
  • the bypass device 30 in the main muffler 23, (1) as described above, after the compressor is started, the bypass hole 33 is quickly closed, which has the effect of accelerating the increase in the pressure of the sealed casing 2.
  • the lubricating oil 8 of the sealed housing 2 flows into the bypass hole 33 to prevent the flow of the refrigerant in the bypass hole 33 from being weakened, and (3) to prevent the lubricating oil 8 flowing in from the bypass hole 33 from passing through the suction pipe 13 in advance. The effect of the problem of flowing out of the reservoir 45.
  • Fig. 111 For the rotary compressor 1 of the present application with a bypass device 30 and a conventional rotary compressor without a bypass device, the high-pressure side pressure (Pd) and the low-pressure side pressure (Ps) after the motor 6 is stopped are compared.
  • the change. 2 represents the pressure change of the high pressure (Pd) and low pressure (Ps) when the rotary compressor 1 is restarted after a complete stop for 30 seconds.
  • the horizontal axis is the elapsed time (minutes) after the compressor is stopped or restarted, and the vertical axis is the operating pressure (MPaG).
  • the solid line is the rotary compressor 1
  • the broken line is the conventional rotary compressor.
  • H1 (Pd) and L1 (Ps) are the high pressure and low pressure of the rotary compressor 1, respectively.
  • the dashed lines H2 (Pd) and L2 (Ps) are the high pressure (sealed shell pressure) and low pressure (suction pipe pressure) of a conventional rotary compressor, respectively.
  • the installation equipment of the rotary compressor 1 of Example 1 and the conventional rotary compressor is an air conditioner, and R410A refrigerant is used.
  • the operating pressure between the rotary compressor 1 and the conventional rotary compressor is the same before and when stopped, the high pressure (Pd) is 3.0 MPaG, and the low pressure (Ps) is 0.7 MPaG.
  • the balance time between the high pressure and the low pressure after the compressor stops is about 30% of the conventional one. And it can be confirmed that the pressure change characteristics of the compressor after restarting are not much different from the traditional compressor.
  • the rotary compressor 101 shown in FIG. 12 is characterized in that a bypass device 30A and a bypass device 30B are provided on both the main shaft plate 21 and the counter shaft plate 26, respectively.
  • the bypass device 30B of the secondary shaft plate 26 is covered by the secondary muffler 28.
  • the high-pressure gas of the main muffler 23 on the main shaft plate 21 is discharged from the compression chamber 11 and discharged into the sealed housing 2 from the muffler exhaust hole 23a.
  • the internal pressure of the sub muffler 28 becomes equal to the pressure of the main muffler 23.
  • the high-pressure gas discharged into the sealed casing 2 is discharged from the exhaust pipe 3 to the condenser 50 through the motor 6 as in the first embodiment.
  • the embodiment 2 can further shorten the time for the high pressure (Pd) and the low pressure (Ps) to become equal. In this way, compared with the first embodiment, the second embodiment has the effect of shortening the compressor stop time although the high pressure rising speed after the compressor is started is reduced.
  • a bypass device 30A and a bypass device 30B are respectively provided on the main shaft plate 21 and the counter shaft plate 26 connecting one cylinder 10, for example, in a two-cylinder rotary compressor, two cylinders can also be provided with openings.
  • the bypass device 30A and the bypass device 30B are provided.
  • FIG. 13 shows a design example in which a bypass device 30 is provided on the outer peripheral surface of the cylinder 10.
  • the lower side of the bypass hole 33 opens the inside of the suction pipe 13.
  • the U-shaped groove 12a necessary in Embodiment 1 can be omitted.
  • Example 3 Compared with Example 1, in Example 3, since the upper side of the bypass hole 33 is outside the main muffler 23, (1) the pressure increase (Pd+) at the time of compressor startup cannot be utilized. Therefore, the time to reach the pressure of the condenser 50 after the compressor is started is slightly delayed. (2) The lubricating oil 8 may flow into the bypass hole 33. However, there is no problem in a design with a small amount of oil.
  • the rotary compressor according to the embodiment of the present application includes: a casing 2, a motor 6, a compression mechanism 5, an exhaust pipe 3, an intake pipe 13, and a bypass device 30.
  • the casing 2 may be The housing is sealed, the motor 6 and the compression mechanism part 5 are arranged in the housing 2, and the compression mechanism part 5 is driven by the motor 6, the exhaust pipe 3 communicates with the inside of the housing 2, and one end of the suction pipe 13 is connected to the compression mechanism part. 5 is connected, and the other end is connected to the reservoir 45.
  • the bypass device 30 has a bypass hole 33.
  • the gas in the housing 2 flows through the bypass hole 33 to the suction pipe 13 or into the low-pressure circuit connected to the suction pipe 13, so that the housing The pressure of 2 is quickly reduced to be equal to the pressure of the compression chamber 11 of the compression mechanism part 5 to shorten the compressor restart time.
  • the bypass device 30 may include a bypass valve 32 and a spring 34.
  • the bypass valve 32 opens or closes the bypass hole due to the pressure difference between the sealing housing 2 and the suction pipe 13. 33.
  • the bypass valve 32 opens the bypass hole 33; when the pressure difference between the sealed housing 2 and the suction pipe 13 is greater than the preset value , The bypass valve 32 closes the bypass hole 33, and the spring 34 moves the bypass valve 32 in a direction to open the bypass hole 33.
  • the spring 34 is a compression spring located below the bypass valve 32 and always exerts an upward thrust on the bypass valve 32. In some unshown embodiments, the spring 34 may also be located above the bypass valve 32 and always exert an upward pulling force on the bypass valve 32.
  • ⁇ P ⁇ Pa as shown in FIG. 2B, the resilience of the spring 34 is sufficient to resist the pressure difference, the bypass valve 32 opens the bypass hole 33, and the high-pressure gas in the housing 2 can enter the suction pipe 13 through the bypass hole 33 .
  • the compression mechanism 5 includes: a cylinder 10, a main bearing 20, and a secondary bearing 25.
  • the main bearing 20 is located at one end of the cylinder 10, and the secondary bearing 25 is located at the other end of the cylinder 10.
  • the cylinder 10 has a compression chamber 11 and two compression chambers 11
  • the side opening surface is provided with the main shaft plate 21 of the main bearing 20 and the secondary shaft plate 26 of the secondary bearing 25, and at least one of the main shaft plate 21 and the secondary shaft plate 26 is provided with a bypass device 30.
  • a bypass device 30 is provided on the main shaft plate 21 of the main bearing 20.
  • the main shaft plate 21 of the main bearing 20 and the secondary shaft plate 26 of the auxiliary bearing 25 are both provided with a bypass device 30.
  • the main shaft plate 21 of the main bearing 20 is provided with a bypass device 30A
  • the secondary shaft plate 26 of the auxiliary bearing 25 is provided with a bypass device 30B, which can further accelerate the pressure drop speed of the housing 2 and the compression chamber 11 The speed of pressure rise, thereby further shortening the compressor restart time.
  • the side of the main bearing 20 facing away from the cylinder 10 is provided with a main muffler 23, and the side of the auxiliary bearing 25 facing away from the cylinder 10 is provided with an auxiliary muffler 28, and the compression mechanism part 5 has a communication main muffler 23 and an auxiliary muffler.
  • One end of the through hole 43 and the bypass hole 33 of the bypass hole 33 communicates with the muffler chamber of the corresponding muffler, and the other end of the bypass hole 33 communicates with the suction pipe 13 or the low pressure circuit connected with the suction pipe 13.
  • the upper end of the bypass device 30A communicates with the muffler chamber of the main muffler 23
  • the muffler chamber of the main muffler 23 communicates with the inside of the housing 2 through the muffler exhaust hole 23a
  • the lower end of the bypass hole 33 communicates Inspiratory pipe 13.
  • the upper end of the bypass device 30B communicates with the suction pipe 13
  • the lower end of the bypass device 30B communicates with the silencing chamber of the sub-muffler 28.
  • the silencing chamber of the sub-muffler 28 is connected to the housing 2 through the through hole 43 and the muffler exhaust hole 23a. Internal connectivity.
  • bypass device 30 may also be provided only on the secondary shaft plate 26 of the secondary bearing 25.
  • the compression mechanism 5 includes a cylinder 10, a main bearing 20, and a secondary bearing 25.
  • the main bearing 20 is located at one end of the cylinder 10
  • the secondary bearing 25 is located at the other end of the cylinder 10
  • the bypass device 30 It is provided on the outer peripheral surface of the cylinder 10, at this time, the upper end of the bypass hole 33 directly communicates with the inside of the housing 2 and the lower end of the bypass hole 33 communicates with the intake pipe 13.
  • the check valve 53 is a one-way valve or a solenoid switch valve to ensure that the gas in the exhaust pipe 3 can enter the high-pressure side of the refrigeration cycle device through the check valve 53, while the high-pressure gas on the high-pressure side of the refrigeration cycle device cannot flow back to Exhaust pipe 3 in.
  • a condenser 50 is connected to one end of the exhaust pipe 3, and a check valve 53 is provided between the condenser 50 and the exhaust pipe 3.
  • the check valve 53 prevents the high-pressure gas of the condenser 50 from flowing to the exhaust pipe 3, so as to ensure that the high-pressure gas in the casing 2 can enter the compression chamber 11 as soon as possible, thereby ensuring that the pressure in the casing 2 can be reduced as quickly as possible.
  • the pressure in the cavity 11 is equal to shorten the compressor restart time.
  • the bypass device 30 in the main muffler 23 on the upper side of the main bearing 20 has a bypass hole 33, a U-shaped groove 12a is opened at the connection between the suction pipe 13 and the cylinder 10, and the upper end of the bypass hole 33 is connected to the high-pressure main muffler 23 is in communication, and the lower end is in communication with the low-pressure U-shaped groove 12a.
  • the bypass device 30 of the present application can be added to a rotary compressor equipped with an inverter motor that changes the rotation speed.
  • the stop time of the compressor can be shortened during defrosting.
  • the bypass device 30 of the present application is also applicable to two-cylinder type and horizontal type rotary compressors.
  • a rotary compressor according to another embodiment of the present application will be described in detail with reference to Figs. 14-20.
  • the feature of the rotary compressor of the present application is to maintain the pressure of the housing 2 at a medium pressure. Stop and restart the compressor.
  • Representative examples of rotary compressors include rotary compressors and scroll compressors in which the internal pressure of the casing is high.
  • Fig. 14 shows a schematic diagram of an air-conditioning refrigeration cycle during steady operation including the compressor 1 of the present application.
  • the low-pressure refrigerant in the accumulator 45 is sucked into the compression chamber 11 from the suction pipe 13 of the compressor 1, and the high-pressure gas compressed in the compression chamber 11 is discharged to the closed casing 2.
  • the high-pressure refrigerant discharged from the exhaust pipe 3 moves to the condenser 50 through the second check valve device 53 (that is, the above-mentioned check valve 53), where the condensed liquid refrigerant passes through the electric expansion valve 51 to form a low-pressure refrigerant.
  • the evaporator 52 evaporates to form a low-pressure gas, which flows into the accumulator 45 from the low-pressure pipe 47 through the first check valve device 54.
  • the compressor 1 is characterized by a pressure equalization device 30 on the compression mechanism part 5 fixed inside the casing 2.
  • the pressure equalization device 30 is the bypass device 30 mentioned above. As shown in the following, the compressor 1 is in operation.
  • the bypass hole 33 of the pressure equalization device 30 is closed, and the high-pressure gas in the housing 2 does not flow to the suction pipe 13.
  • FIG. 15 shows the internal structure of the compressor 1 in operation.
  • Fig. 16 shows the X-X section in Fig. 15.
  • the housing 2 contains a motor 6 and a compression mechanism 5, and the bottom of the housing 2 contains a lubricating oil 8.
  • the outer circumference of the cylinder 10 of the compression mechanism 5 is fixed to the inner circumference of the housing 2 by spot welding, and the main bearing 20 and the sub-bearing 25 seal the cylindrical compression chamber 11 in the center of the cylinder 10.
  • the crankshaft 40 driven by the motor 6 is in sliding fit with the main bearing 20 and the auxiliary bearing 25, and the crankshaft 40 drives the rolling piston 15 in the compression chamber 11 to revolve.
  • the rolling piston 15 sucks in low-pressure gas and discharges it to the muffler 23 from the exhaust hole 21 a of the exhaust valve 24. After that, the high-pressure gas is discharged from the exhaust pipe 3 through the motor 6.
  • the cylindrical accumulator 45 fixed on the outer side of the housing 2 is the same as a general accumulator.
  • the upper part is connected with a low pressure pipe 47 and a central pipe 48 is arranged in the center.
  • the bent tube at the lower end of the center tube is connected to the suction pipe 13, and the suction pipe 13 is pressed into the suction hole 12 that opens the compression chamber 11 from the outer periphery of the cylinder 10.
  • a small amount of liquid refrigerant is stored in the accumulator 45.
  • the compressor 1 is equipped with a pressure equalization device 30 on the main shaft plate 21 of the main bearing 20.
  • the pressure equalization device 30 has a bypass hole 33, and the upper opening end of the bypass hole 33 is located inside the muffler 23. As shown in FIG. 16, the front end of the sliding piece 16 reciprocating in the sliding piece groove 14 of the cylinder 10 abuts against the outer circumference of the rolling piston 15 revolving in the compression chamber 11.
  • the pressure equalizing device 30 is arranged above the suction hole 12.
  • FIG. 17 is a cross-section of the compression mechanism part 5 and shows the structure of the pressure equalization device 30.
  • the pressure equalizing device 30 has a bypass hole 33 in the center of the cylindrical hole 31 machined on the spindle plate 21, and the lower end of the bypass hole 33 is in communication with the suction hole 12 of the cylinder 10.
  • the bypass valve 32 is stationary at the upper end of the bypass hole 33, and the bypass valve 32 is an on-off valve.
  • the bottom and the upper part of the cylindrical hole 31 are respectively provided with a coil spring 34 and a stopper 35.
  • the coil spring 34 presses the bypass valve 32 toward the stopper 35.
  • the pressure inside the casing 2 becomes high. Since the suction hole 12 is at a low pressure, the bypass valve 32 closes the bypass hole 33.
  • the compressor 1 is a rotary compressor. As shown in FIG. 16, the inner diameter of the rolling piston 15 sliding due to revolution and the back hole 14a of the sliding plate 16 reciprocating are high pressure, and the housing 2 passes through the sliding gap of the sliding surface of the part. The high-pressure gas leaked into the compression chamber 11. That is, when the compressor 1 is in operation, all the gas leaking to the compression chamber 11 is compressed again and discharged into the casing 2.
  • the pressure of the shell 2 becomes lower, the pressure of the shell 2 will be lower than the pressure of the condenser 50.
  • the second check valve device 53 is closed. Therefore, the condenser 50 can maintain a high-pressure state before stopping operation. At this time, the electric expansion valve 51 is closed by control. However, due to the capillary valve etc. being unable to perform valve control, the pressure of the condenser 50 slowly drops and the pressure of the evaporator 52 increases.
  • Fig. 19 shows the pressure distribution of the refrigeration cycle device when the pressures of the casing 2, the accumulator 45, the compression chamber 11, etc. become equal after the compressor 1 is stopped.
  • the pressure of the accumulator 45 is consistent with the pressure of the shell 2, and the pressure of the shell 2 is a high pressure, which is lower than the pressure of the condenser 50.
  • the space volume (C) of the housing 2 is approximately 2100cc, excluding the total volume of the compression mechanism 5, the motor 6, and the lubricating oil 8, and the accumulator 45 is provided.
  • the internal volume (A) is about 700cc, and the volume of the reservoir is 1/3 of the volume of the housing space.
  • the refrigerant used in the above-mentioned air conditioner is R410A
  • the internal pressure of the housing 2 before the operation is stopped is 3.0 MPaA
  • the internal pressure of the accumulator 45 is 1.0 MPaA
  • the compressor 1 stops to cause high-pressure gas from the housing 2 It flows to the accumulator 45, and as a result, the two become equal 2.5 MPaA at night.
  • the pressure of the casing 2 of the compressor 1 in operation is reduced from 3.0 MPaA to 2.5 MPaA, and the pressure of the accumulator 45 is increased from 1.0 MPaA to 2.5 MPaA.
  • the compressor 1 can be restarted, and the pressure increase speed is significantly increased.
  • the motor 6 is energized from the stationary state of FIG. 19, and after the compressor 1 is restarted, the rolling piston 15 revolves so that the high-pressure gas in the accumulator 45 flows into the compression chamber 11. At this time, the pressure of the accumulator 45 is equal to the gas pressure of the housing 2, which will not bring a large load to the motor and can be restarted.
  • the carrier of the second check valve device 53 decreases due to the pressure of the accumulator 45, and the first check valve device 54 is opened.
  • the electric expansion valve 51 optimizes the opening degree according to the temperature of the evaporator 52 and the condenser 50, and the refrigeration cycle device transitions to stable operation.
  • the compressor 1 in stable operation starts to stop after the restart is completed.
  • a solid line (A1) to draw the change in the exhaust gas of the housing 2, and the change in the internal pressure of the accumulator 45 is used
  • the solid line (A2) indicates.
  • the casing pressure change of the conventional compressor is indicated by a broken line (B1)
  • the pressure change of the accumulator is indicated by a broken line (B2).
  • the horizontal axis is the process time, and the number is minutes (min); the vertical axis is the pressure (MPaA). Set the time from compressor stop to restart to 10 seconds, and confirm whether the above two pressures are equal.
  • the arrow ⁇ indicates the time when the high-pressure side pressure and the low-pressure side pressure become equal after the compressor is stopped, and the arrow ⁇ indicates the time to complete the restart after the compressor is restarted and the pressure is equal to the pressure before the operation stops.
  • the high pressure (A1) and low pressure (A2) slowly drop or rise respectively.
  • the bypass hole 33 opens after about 20 seconds, and the high pressure (A1) and low pressure (A2) drop sharply or sharply respectively.
  • Ascending, the pressure becomes the same about 50 seconds after the operation stops. Its pressure is 2.5MPaA.
  • the compressor is restarted, and after 1 minute and 50 seconds from the stop of operation, the pressure is the same as the pressure before the compressor 1 stopped.
  • the compressor shell and condenser are high-pressure vessels, and the evaporator and accumulator are low-pressure vessels.
  • the high-pressure refrigerant (including liquid refrigerant) in the high-pressure vessel passes through the expansion valve ( Or capillary) flows out to the evaporator, and these containers reach equal pressure. Therefore, it takes a long time to reach pressure equalization.
  • its balance force is a medium pressure of 1.9 MPaA, and it takes a long time to return to the pressure before starting and stopping.
  • the above is the time difference between the start of the above-mentioned compressor.
  • the rotary compressor 1 may include: a housing 2, a motor 6, a compression mechanism 5, an exhaust pipe 3, and an air suction pipe 13. , Pressure equalization device 30, accumulator 45, the housing 2 can be a sealed housing, the motor 6 is arranged in the housing 2, the compression mechanism 5 is arranged in the housing 2 and is driven by the motor 6, the exhaust pipe 3 and The inside of the housing 2 is connected, the suction pipe 13 is connected to the compression mechanism 5, and the pressure equalization device 30 has a bypass hole 33 that communicates the inside of the housing 2 with the suction pipe 13, so as to selectively communicate the inside of the housing 2 with the suction In the pipe 13, one end of the reservoir 45 is connected to the suction pipe 13, and the other end of the reservoir 45 is provided with a first check valve device 54.
  • the pressure equalization device 30 and the first check valve device 54 use the pressure difference to automatically control the opening and closing, with low cost, high reliability, no need for power control, and energy saving.
  • the first check valve device 54 prevents the gas in the accumulator 45 from flowing back to the evaporator 52.
  • the first check valve device 54 is a one-way valve or an electromagnetic switch valve to ensure that the gas in the evaporator 52 can enter the accumulator 45 through the first check valve device 54 and the high pressure of the accumulator 45 The gas cannot flow back into the evaporator 52.
  • the exhaust pipe 3 is provided with a second check valve device 53.
  • the second check valve device 53 When the internal pressure of the housing 2 decreases, the second check valve device 53 is closed.
  • the second check valve device 53 prevents the high-pressure gas in the condenser 50 from flowing to the exhaust pipe 3, so as to ensure that the high-pressure gas in the casing 2 can enter the compression chamber 11 as soon as possible, thereby ensuring that the casing 2
  • the pressure can be reduced to be equal to the pressure in the compression chamber 11 as soon as possible, so as to shorten the compressor restart time.
  • the second check valve device 53 is a one-way valve or an electromagnetic switch valve to ensure that the gas in the exhaust pipe 3 can enter the condenser 50 through the second check valve device 53 while the high-pressure gas in the condenser 50 cannot Flow back into the exhaust pipe 3.
  • the compression mechanism 5 includes: a cylinder 10, a main bearing 20, and a secondary bearing 25.
  • the main bearing 20 is located at one end of the cylinder 10, and the secondary bearing 25 is located at the other end of the cylinder 10.
  • the cavity 11 is connected.
  • the compressor When the compressor is operating normally, the refrigerant in the accumulator 45 can enter the compression cavity 11 through the suction pipe 13, and be compressed into a high-pressure gas in the compression cavity 11 and then discharged into the casing 3.
  • the high-pressure gas in the housing 2 can enter the compression chamber 11 through the bypass hole 33, and then enter the accumulator 45 through the suction pipe 13, so that the pressure in the housing 2 can drop to the level of the liquid reservoir as soon as possible.
  • the pressure in the device 45 is equal.
  • a muffler 23 is provided above the main shaft plate 21 of the main bearing 20.
  • the high-pressure side opening end of the pressure equalization device 30 is opened in the muffler 23.
  • the muffler 23 has a cavity with the inner cavity of the housing 2 (ie, below the motor 6). Space) connected muffler exhaust hole.
  • the pressure equalization device 30 may include a bypass valve 32 and a spring 34.
  • the bypass valve 32 uses the pressure difference of the housing 2 and the pressure difference of the accumulator 45 to selectively connect the high-pressure side opening end with the bypass.
  • the hole 33 in other words, the bypass valve 32 is used to open or close the bypass hole 33.
  • the bypass valve 32 opens the bypass hole 33, the high-pressure gas in the housing 2 can enter the suction pipe 13 through the bypass hole 33.
  • the high-pressure gas in the housing 2 can enter the suction pipe 13 through the exhaust hole of the muffler, the high-pressure side opening end of the bypass hole 33, and the bypass hole 33, and then enter the reservoir 45 from the suction pipe 13 .
  • the spring 34 utilizes the difference between the pressure of the housing 2 and the pressure of the accumulator 45 to expand and contract, and the spring 34 moves the bypass valve 32 in a direction to open the bypass hole 33.
  • the spring 34 is a compression spring located below the bypass valve 32 and always exerts an upward thrust on the bypass valve 32.
  • the spring 34 may also be located above the bypass valve 32 and always exert an upward pulling force on the bypass valve 32.
  • the stopper 35 is used to limit the maximum moving distance of the bypass valve 32 and prevent the bypass valve 32 from falling off.
  • the pressure equalization device 30 may be located on the main shaft plate 21 of the main bearing 20.
  • the pressure equalization device 30 may also be located The auxiliary shaft plate of the auxiliary bearing 25. Or both the main shaft plate 21 and the secondary shaft plate are provided with a pressure equalizing device 30.
  • the high-pressure gas in the casing 2 leaks from the low-pressure compression chamber 11 to the suction pipe 13 via the sliding surfaces such as the rolling piston 15 and the sliding plate 16, and then diffuses to the accumulator 45.
  • the bypass hole 33 of the pressure equalization device 30 opens, and the pressures of the housing 2 and the accumulator 45 become equal rapidly, and the first check valve device 54 and The second check valve device 53 is closed. Therefore, the compressor 1 can be restarted in a short time, and the pressure of the casing 2 will quickly return to the high-pressure state before the stop.
  • the pressure equalization device 30 and the first check valve device 54 and the second check valve device 53 are all opened.
  • the restart time can be greatly shortened in the air conditioner (schematic description) that controls the temperature of the air conditioner, and the temperature fluctuation of the air conditioner can be greatly improved.
  • the defrosting operation time can be shortened.
  • the pressure equalization device 30, the first check valve device 54, the second check valve device 53, etc. are automatically controlled by the pressure difference, which is low in cost, high in reliability, and does not require power control, which is conducive to energy saving.
  • Inverter motors running at fixed speeds or variable speeds can be used.
  • the refrigeration cycle device includes a condenser 50, an expansion device 51 (ie, an electric expansion valve 51), an evaporator 52, and the rotary compressor of the above embodiment.

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Abstract

一种回转式压缩机及冷冻循环装置，该回转式压缩机(1)包括壳体(2)，壳体(2)收纳电机(6)和压缩机构部(5)，连通冷冻循环装置的高压侧的排气管(3)连接壳体(2)，连通上述冷冻循环装置的低压侧的吸气管(13)连接上述压缩机构部(5)，压缩机构部(5)具有旁通装置(30)，当上述电机(6)停止后，上述壳体(2)的气体流到上述吸气管(13)或上述吸气管(13)连通的低压回路中。

Description

回转式压缩机及冷冻循环装置
相关申请的交叉引用
本申请要求申请日为2019年8月23日、申请号为201910785989.4、专利申请名称为“回转式压缩机及冷冻循环装置”的优先权，以及申请日为2019年8月23日、申请号为201910785885.3、专利申请名称为“回转式压缩机及冷冻循环装置”的优先权。
技术领域
本申请涉及压缩机领域，具体而言，涉及一种回转式压缩机及冷冻循环装置。
背景技术
与可以自由更改电机转速的变频式回转压缩机相比，将电机转速固定在50Hz或60Hz的回转式压缩机，由于空调的室温控制，需要频繁地重复启动和停止。但是，密闭壳体的内部压力为高压的回转式压缩机的问题是：如果壳体压力或排气压力与压缩腔的吸入压力不相等，电机就不能起动。如果向以往一样，压缩机停止后重启的时间约为3分钟的长时间，而且重启后的压缩机的壳体压力从低压变到高压需要时间，这样不仅空调的舒适性较差，空调APF也会恶化。
发明内容
本申请旨在至少在一定程度上解决现有技术中的上述技术问题之一。为此，本申请提出一种回转式压缩机，以缩短压缩机重启的时间。
本申请还提出了一种具有上述回转式压缩机的冷冻循环装置。
根据本申请实施例的回转式压缩机包括壳体，壳体收纳电机和压缩机构部，连通冷冻循环装置的高压侧的排气管连接壳体，连通上述冷冻循环装置低压侧的吸气管连接上述压缩机构部，压缩机构部具有旁通装置，当上述电机停止后，上述壳体的气体流到上述吸气管或上述吸气管连通的低压回路中。
根据本申请的一些实施例，上述旁通装置至少包括：连通上述壳体的旁通孔、由于上述壳体与上述吸气管的压力差打开和关闭上述旁通孔的旁通阀、和使所述旁通阀向打开所述旁通孔的方向运动的弹簧。
进一步地，上述旁通孔的一方连接上述压缩机构部的排气消音室内部，上述旁通孔的另一方连接上述吸气管或上述吸气管连通的低压回路。
根据本申请的一些实施例，连接上述压缩机构部中的气缸压缩腔的两侧开孔面的主轴 板和副轴板的其中一个具备上述旁通装置。
根据本申请的一些实施例，上述冷冻循环装置的高压侧和上述排气管之间，具有当上述电机停止时，阻止上述冷冻循环装置的高压侧的高压气体逆流到上述排气管的止回阀。
具体地，当所述壳体与所述吸气管的压力差小于预设值时，所述旁通阀打开所述旁通孔；当所述壳体与所述吸气管的压力差大于预设值时，所述旁通阀关闭所述旁通孔。
根据本申请的一些实施例，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述主轴承的主轴板和所述副轴承的副轴板上均设置有所述旁通装置。
进一步地，所述主轴承的背离所述气缸的一侧设置有主消音器，所述副轴承的背离所述气缸的一侧设置有副消音器，所述压缩机构部具有连通所述主消音器与副消音器的通孔，所述旁通装置的旁通孔的一端连通对应消音器的消音室，所述旁通孔的另一端连通所述吸气管。
根据本申请的一些实施例，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述旁通装置设置在所述气缸的外周面上。
根据本申请的一些实施例，所述旁通装置为均压装置，所述均压装置具有连通所述壳体内部与所述吸气管的旁通孔；
所述回转式压缩机还包括：储液器，所述储液器的一端连接所述吸气管，所述储液器的另一端连接第一止回阀装置，所述电机停止时，所述均压装置的旁通孔打开，所述第一止回阀装置关闭，所述壳体内的气体流到所述吸气管或所述储液器中。
可选地，所述第一止回阀装置为单向阀或电磁开关阀。
根据本申请的一些实施例，所述排气管上设置有第二止回阀装置，所述壳体内部压力降低时，所述第二止回阀装置关闭。
可选地，所述第二止回阀装置为单向阀或电磁开关阀。
根据本申请的一些实施例，所述均压装置包括：打开或关闭所述旁通孔的旁通阀、利用所述壳体压力和所述储液器的压力差伸缩的弹簧。
进一步地，所述旁通孔的高压侧开孔端位于所述压缩机构部的消声器中。
具体地，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述气缸内形成压缩腔，所述吸气管与所述压缩腔连通。
进一步地，所述消声器具有与所述壳体内部连通的消声器排气孔。
根据本申请的一些实施例，所述旁通阀利用所述壳体压力和所述储液器的压力差可选 择地连通所述旁通孔与所述吸气管，所述弹簧使所述旁通阀向打开所述旁通孔的方向运动。
根据本申请实施例的回转式压缩机，可以大幅度缩短压缩机的重启时间，由此，空调温度的变动较小，可以提高APF。
根据本申请另一方面实施例的冷冻循环装置，包括上述的回转式压缩机。
所述回转式压缩机与上述的回转式压缩机相对于现有技术所具有的优势相同，在此不再赘述。
本申请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，或通过本申请的实践了解到。
附图说明
图1是本申请的旋转式压缩机1的构造和连接旋转式压缩机1的空调的冷冻循环装置示意图；
图2是旁通装置的详细结构示意图；
图3是旁通装置30的组成部件的详细图；
图4是从压缩机构部的下方看的气缸与压缩腔内部的平面图；
图5是从压缩机构部的上方看的主轴承和气缸中的压缩腔的内部平面图；
图6是旋转式压缩机稳定运行中气体冷媒的流动示意图；
图7是旋转式压缩机刚停止时的示意图；
图8是旋转式压缩机停止时间持续大约经过10秒的示意图；
图9是旋转式压缩机停止时间持续并且大约经过30秒的示意图；
图10是从图9的状态(停止)经过30秒后，重启旋转式压缩机后经过15秒的状态图；
图11的①是对于具有旁通装置的本申请的旋转式压缩机与无旁通装置的以往的旋转式压缩机，比较了在电机停止后的高压侧压力(Pd)与低压侧压力(Ps)的变化。②表示旋转式压缩机在完全停止30秒后重启时的高压(Pd)与低压(Ps)的压力变化图；
图12是主轴板和副轴板上均设置有旁通装置的示意图；
图13是旁通装置设置在气缸外周壁上的示意图。
图14是含有本申请的压缩机的稳定运转中的空调冷冻循环简图；
图15是运转中的压缩机内部构造示意图；
图16是图15的X-X截面的示意图；
图17是压缩机构部的截面示意图，表示均压装置的构造；
图18压缩机停止后，压缩机内部构造示意图；
图19表示压缩机停止后，壳体、储液器和压缩腔等的压力变均等时冷冻循环装置的压 力分布图；
图20是稳定运行中的压缩机开始停止后到重启完毕，壳体的排气变化以及储液器内部压力变化示意图。
具体实施方式
下面详细描述本申请的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本申请，而不能理解为对本申请的限制。
在本申请的描述中，需要理解的是，术语“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或可以互相通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
回转式压缩机以活塞公转且滑片往复运动的旋转式压缩机、活塞与滑片共同旋转的旋转式压缩机、具备定盘和动盘的涡旋式压缩机等为代表。本申请的实施例对家用空调中最普及的旋转式压缩机进行技术公示。
实施例1：
图1表示本申请的旋转式压缩机1的构造，和连接旋转式压缩机1的空调的冷冻循环装置。密封壳体2收纳压缩机构部5、电机6和底部的润滑油8。压缩机构部5的气缸10的外周通过点焊固定在密封壳体2的内周，气缸10中心的圆形压缩腔11被主轴承20的主轴板21和副轴承25的副轴板26密封。
曲轴40与主轴承20和副轴承25滑动配合，曲轴40的偏心轴40a在压缩腔11中，驱动活塞15公转。在气缸10的滑片槽14中往复运动的滑片16的前端抵接活塞15的外周(图 4和图5所示)。电机6由热套固定在密封壳体2内周的定子6a和固定在曲轴40的转子6b组成。另外，电机6具有50Hz或60Hz电源的其中一个的恒定速度。
密封壳体2外侧的低压储液器45，由连接圆筒容器46上部的容器吸气管47、低压的圆筒容器46内部的气液冷媒分离板46a，和设置在中心的中心管48组成。中心管48下端处的弯曲管连接吸气管13，吸气管13被压入从气缸10的外周对压缩腔11开孔的吸气孔12中。
主消音器23通过多个螺钉固定在主轴承20的主轴板21，内部设置旁通装置30。位于该中心的旁通孔33的下端对在气缸10的吸气孔12的开孔端加工的U形槽12a开孔。旁通孔33的上端由旁通阀32打开和关闭。
位于密封壳体2的上端中心的排气管3连接冷冻循环装置的冷凝器50。冷凝器50按毛细管51、蒸发器52和储液器45的顺序连接。该冷冻循环装置的特征是排气管3与冷凝器50之间具备止回阀53。另外，毛细管51可以是电子膨胀阀。
根据图1，说明旋转式压缩机1的运行中冷媒的流动。从储液器45的中心管48流向吸气管13的低压气体(冷媒)，流经在吸气孔12的出口侧加工的U形槽12a，通过活塞15的公转被压缩成高压气体，从排气孔21a(虚线，图5所示)排出到主消音器23。因此主消音器23为排气消音器。
通过主消音器23的消音器排气孔23a的高压气体流入电机6的下部空间，从电机6的内部和外部间隙流向上部空间。该期间，高压气体中含有的大部分润滑油分离出来，与密封壳体2底部的润滑油8汇合。
高压气体从排气管3通过止回阀53，在冷凝器50变成高压液体冷媒，通过了毛细管51的低压冷媒在蒸发器52蒸发，从储液器45的壳体吸气管47流入圆筒壳体46。蒸发不了的液体冷媒储存在圆筒壳体46的底部，低压的气体冷媒从中心管48返回气缸10的吸气管13。
当电机6停止时，止回阀53由于冷凝器50与密封壳体2的压力差而动作，关闭排气管3。这时，由于密封壳体2的高压气体通过活塞15与滑片16等的滑动间隙(约5～10μm)，从对低压的压缩腔11开孔的吸气管13逆流到储液器45，储液器45的内部压力上升，密封壳体2的压力下降。
另外，如果止回阀53关闭，冷凝器50的高压冷媒不能逆流到密封壳体2的内部，冷凝器50运行时在高温下储存高压液体冷媒。但是，由于冷凝器50的液体冷媒放热，并且经过毛细管51流出到蒸发器52，冷凝器50的压力下降。
图2为旁通装置30的详细结构图，图A(闭孔)和图B(开孔)表示其动作。其次，图3为旁通装置30的组成部件的详细图。图2的图A与图B中，旁通装置30在主轴板21 上加工的圆筒孔31的中心中具有旁通孔33，其上面有阀座33a，线圈弹簧34插入其外周槽。
线圈弹簧34为压缩弹簧，始终使旁通阀32向打开旁通孔33的方向运动。线圈弹簧34的下端位于阀座33a的弹簧限位槽31b中，线圈弹簧34的上端与旁通阀32相连接。C形挡圈35作为旁通阀32的限位器，嵌入圆筒孔31内周的挡圈槽31a中。因此，旁通阀32由于作用于其上下面的压差，在阀座33a与C形挡圈35的间隙中上下运动。如图3所示，旁通阀32外周具备的4个气体槽32a成为气体通道。
线圈弹簧34的弹力(弹簧定数)与旁通孔33的孔径的设计非常重要，是确定旁通孔33打开的压差(ΔP)和通过旁通孔33的流量的因素。另外，ΔP＝主消音器23的高压(Pd)-U形槽12a的低压(Ps)，预先决定的设计压差为ΔPa。
图A为旁通孔33被旁通阀32关闭的状态。这时的压差(Pd－Ps)＞ΔPa。另一方面，图B为旁通孔33被旁通阀32打开的状态。这时的压差(Pd－Ps)＜ΔPa。即，设计压差(ΔPa)是决定压缩机停止后和压缩机启动后的高压(Pd)与低压(Ps)变动的最重要的数值。
另外，压缩机运行中，由于通过消音器排气孔23a的高压气体的阻力，主消音器23的高压≧密封壳体2的压力，主消音器23的高压稍微上升。该特征有缩短压缩机重启时间的效果，成为在主消音器23中配置旁通装置30的理由之一。
图4为从压缩机构部5的下方看的气缸10与压缩腔11内部的平面图。旁通孔33下端对U形槽12a开孔，U形槽12a位于气缸10的吸气孔12的开孔端上。滑片背面孔14a的压力与密封壳体2的压力相等，滑片16沿滑片槽14进行往复运动。此外，活塞15的内侧也与密封壳体2的压力相等。
图5为从压缩机构部5的上方看的主轴承20和气缸10中的压缩腔11的内部平面图，表示设置在主轴承20的主轴板21上的旁通装置30，和打开、关闭排气孔21a的排气阀24。根据图5，可以在不干涉旁通装置30和排气阀36a等安装的情况下，在滑片槽16的两侧配置旁通装置30和排气装置36。
接下来，通过图6到图10的简图，对压缩机构部5中追加的旁通装置30的作用和效果进行说明。图6表示旋转式压缩机1稳定运行中气体冷媒的流动。从储液器45流入吸气管13的低压气体(压力Ps)被活塞15压缩成高压气体(Pd)，从排气孔21a排出主消音器23。从消音器排气孔23a排出的高压气体排出到密封壳体2的内部后，从排气管3通过止回阀53流入冷凝器50。
压缩机的运行中，由于主消音器23的压力为稳定的高压，主消音器23的压力(Pd)与U形槽12a的压力(低压Ps)的压差(ΔP)最大，旁通孔33关闭，所以主消音器23 的高压气体不流出到低压的U形槽12a。即，Pd－Ps＞ΔPa。
图7中，如果运行中的压缩机停止，由于高压气体从活塞15和滑片16的滑动间隙等泄漏到压缩腔11中，密封壳体2的压力逐渐降低，止回阀53关闭。这时，密封壳体2与主消音器23的压力相等，由于是稍微降低的高压(Pd－)，与低压的U形槽12a的ΔP减小，旁通孔33关闭。
如果停止时间持续大约经过10秒，如图8所示，密封壳体2的压力与活塞15的内径压力下降至Pd‐‐。另一方面，由于上述的气体泄漏，压缩腔11的压力上升至Ps+。其结果，主消音器23和U形槽12a的ΔP小于ΔPa(设计压差)。因此，旁通孔33开孔。即Pd－Ps＜ΔPa。
如果停止时间持续并且大约经过20秒(合计约30秒)，如图9所示，由于密封壳体2的压力降低至与压缩腔11的压力相等，密封壳体2的压力降低至Ps++。另一方面，压缩腔11的压力上升至Ps++，密封壳体2的压力与压缩腔11的压力相等。这时，由于Pd－Ps＜ΔPa，密封壳体2的压力与压缩腔11的压力变为相等的时间最早。
图10为从图9的状态(停止)经过30秒后，重启旋转式压缩机1后经过15秒的状态。由于是从吸气压力高的状态(Ps++)启动，主消音器23与密封壳体2的压力迅速上升，其压差大于ΔPa，所以旁通孔33关闭。即Pd－Ps＞ΔPa。
但是，由于旁通孔33开孔的15秒内Pd－Ps＜ΔPa，主消音器23的高压气体的一部分逆流到U形槽12a中。与无旁通孔33的以往的压缩机相比，密封壳体2的压力上升延迟。另外，如果密封壳体2的压力达到近似冷凝器50的压力(Pd)，止回阀53开孔，可以返回到图6的状态。
这里，实施例1通过将旁通装置30配置在主消音器23中，(1)如上述，压缩机启动后，快速关闭旁通孔33，有加速提高密封壳体2的压力的效果。并且，(2)密封壳体2的润滑油8流入旁通孔33，防止旁通孔33的冷媒流动减弱，(3)发挥预先防止从旁通孔33流入的润滑油8经吸气管13流出储液器45的问题的效果。
图11①对于具有旁通装置30的本申请的旋转式压缩机1与无旁通装置的以往的旋转式压缩机，比较了在电机6停止后的高压侧压力(Pd)与低压侧压力(Ps)的变化。②表示旋转式压缩机1在完全停止30秒后重启时的高压(Pd)与低压(Ps)的压力变化。这些旨在补充图6至图10中描述的对旁通装置30的动作说明。
图11的①中，横轴为压缩机停止后或重启后的经过时间(分)，纵轴为运行压力(MPaG)。实线为旋转式压缩机1，虚线为以往的旋转式压缩机。H1(Pd)与L1(Ps)分别是旋转式压缩机1的高压和低压。另一方面，虚线H2(Pd)与L2(Ps)分别为传统旋转式压缩机的高压(密封壳体压力)和低压(吸气管压力)。
另外，实施例1的旋转式压缩机1和传统旋转式压缩机的搭载设备为空调，使用R410A冷媒。上述①中，旋转式压缩机1与传统旋转式压缩机之间，停止前与停止时的运行压力相同，高压(Pd)为3.0MPaG、低压(Ps)为0.7MPaG。
①中，当旋转式压缩机1停止时，Pd降低，Ps上升。其后，大约经过20秒时，由于旁通孔33打开，H1(Pd)迅速降低，低压L1(Ps)迅速上升。其结果，高压和低压在52秒后成为1.6MPaG的平衡压力。另外，旋转式压缩机1停止时，旁通孔33保持开孔。
另一方面，传统旋转式压缩机(虚线)停止运行，大约在20秒之前H2(Pd)和L2(Ps)的变化与旋转式压缩机1相同。但是，其后的压力变化较小，约2分44秒后成为1.6MPaG的平衡压力。其结果，重启的经过时间大约是旋转式压缩机1的3倍。
其次，图11的②中，达到1.6MPaG的平衡压力，且经过30秒后重启的旋转式压缩机1，由于大约经过15秒时的压差大于ΔPa，旁通孔33关闭。其后的压力变化与传统压缩机相比没有太大差别。
另外，如上述，由于旋转式压缩机1停止时，冷凝器50的压力降低，即使关闭旁通孔33，高压(Pd)依然小于3.0MPaG。图11②的H1(Pd)线上的Δ符号表示止回阀53打开。
这样，具有旁通装置30的旋转式压缩机1中，压缩机停止后的高压和低压的平衡时间约为以往的30％。并且可以证实压缩机重启后的压力变化特性与传统压缩机没有太大差别。
实施例2：
图12表示的旋转式压缩机101的特征是，在主轴板21与副轴板26的两者分别设置旁通装置30A和旁通装置30B。副轴板26的旁通装置30B被副消音器28覆盖。
旋转式压缩机101启动后，从压缩腔11排出主轴板21上的主消音器23的高压气体，从消音器排气孔23a排出到密封壳体2的内部。这时，通过压缩机构部5中的通孔43，副消音器28的内部压力变得与主消音器23的压力相等。另外，排出到密封壳体2内部的高压气体与实施例1一样，通过电机6，从排气管3向冷凝器50排出。
与实施例1相同，当主消音器23与U形槽12a的压差(ΔP)大于预先决定的设计压力时，旁通装置30A和旁通装置30B同时闭孔。因此，密封壳体2的内压迅速上升，旋转式压缩机101从排气管3向冷凝器50排气。
其后，如果旋转式压缩机101停止，由于密封壳体2的内压降低，压缩腔11的压力上升，其压差变为设计压力(ΔPa)以下，旁通装置30A和旁通装置30B同时开孔。由于密封壳体2的内压下降速度为实施例1的旋转式压缩机1的2倍，实施例2可以进一步缩短高压(Pd)和低压(Ps)变得相等的时间。这样，实施例2与实施例1相比，虽然压缩机启动后的高压上升速度下降，但有缩短压缩机停止时间的效果。
实施例2在连接一个气缸10的主轴板21与副轴板26上分别设置旁通装置30A和旁通装置30B，例如在双缸旋转式压缩机中，也可以分别在两个气缸设置开孔的旁通装置30A和旁通装置30B。其结果，即使是双缸旋转式压缩机，也可以实现与单缸旋转式压缩机相当的压力平衡时间的减少。
实施例3：
图13表示在气缸10的外周表面设置旁通装置30的设计例。旁通孔33的下侧对吸气管13的内部开孔。另外，可以省略实施例1中必需的U形槽12a。
与实施例1相比，实施例3中，由于旁通孔33的上侧在主消音器23的外侧，(1)无法利用压缩机启动时的压力増加(Pd+)。因此，压缩机启动后达到冷凝器50的压力的时间稍有延迟。(2)润滑油油8可能流入旁通孔33。但是，油量少的设计中是没有问题的。
下面结合图1-图13详细描述根据本申请实施例的回转式压缩机。
参照图1所示，根据本申请实施例的回转式压缩机包括：壳体2、电机6、压缩机构部5、排气管3、吸气管13、旁通装置30，壳体2可以是密封壳体，电机6和压缩机构部5设置在壳体2内，且压缩机构部5由电机6驱动，排气管3与壳体2的内部连通，吸气管13的一端与压缩机构部5连接，另一端与储液器45连接。
旁通装置30具有旁通孔33，当电机6停止后，壳体2内的气体通过旁通孔33流到吸气管13或流到吸气管13连通的低压回路中，以使壳体2的压力快速降低至与压缩机构部5的压缩腔11的压力相等，以缩短压缩机重启时间。
具体地，如图2-图3所示，旁通装置30可以包括：旁通阀32和弹簧34，旁通阀32由于密封壳体2与吸气管13的压力差打开或关闭旁通孔33，且当密封壳体2与吸气管13的压力差小于预设值时，旁通阀32打开旁通孔33；当密封壳体2与吸气管13的压力差大于预设值时，旁通阀32关闭旁通孔33，弹簧34使旁通阀32向打开旁通孔33的方向运动。在图2所示的实施例中，弹簧34为压缩弹簧，位于旁通阀32的下方，始终对旁通阀32施加向上的推力。而在一些未示出的实施例中，弹簧34也可以位于旁通阀32的上方，始终对旁通阀32施加向上的拉力。
具体而言，壳体2的压力Pd与吸气管13的压力Ps的压力差为ΔP，ΔP＝Pd－Ps，当ΔP＞ΔPa时，如图2A所示，弹簧34的回弹力不足以抵抗压差，旁通阀32关闭旁通孔33。当ΔP＜ΔPa时，如图2B所示，弹簧34的回弹力足以抵抗压差，旁通阀32打开旁通孔33，壳体2内的高压气体可经旁通孔33进入吸气管13。
压缩机构部5包括：气缸10、主轴承20、副轴承25，主轴承20位于气缸10的一端，副轴承25位于气缸10的另一端，换言之，气缸10具有压缩腔11，压缩腔11的两侧开孔 面设置有主轴承20的主轴板21和副轴承25的副轴板26，主轴板21和副轴板26的至少一个上设置有旁通装置30。
例如在图1所示的实施例中，主轴承20的主轴板21上设置有旁通装置30。
又如在图12所示的实施例中，主轴承20的主轴板21和副轴承25的副轴板26上均设置有旁通装置30。具体而言，主轴承20的主轴板21上设置有旁通装置30A，副轴承25的副轴板26上设置有旁通装置30B，可以进一步加快壳体2的压力下降速度以及压缩腔11的压力上升速度，从而进一步缩短压缩机重启时间。
进一步地，主轴承20的背离气缸10的一侧设置有主消音器23，副轴承25的背离气缸10的一侧设置有副消音器28，压缩机构部5具有连通主消音器23与副消音器28的通孔43，旁通孔33的一端连通对应消音器的消音室，旁通孔33的另一端连通吸气管13或吸气管13连通的低压回路。如图12所示，旁通装置30A的上端连通主消音器23的消音室，主消音器23的消音室再通过消音器排气孔23a与壳体2内部连通，旁通孔33的下端连通吸气管13。旁通装置30B的上端连通吸气管13，旁通装置30B的下端连通副消音器28的消音室，副消音器28的消音室通过通孔43、消音器排气孔23a实现与壳体2内部的连通。
在一些未示出的实施例中，旁通装置30也可以仅设置在副轴承25的副轴板26上。
在图13所示的实施例中，压缩机构部5包括：气缸10、主轴承20、副轴承25，主轴承20位于气缸10的一端，副轴承25位于气缸10的另一端，旁通装置30设置在气缸10的外周面上，此时，旁通孔33的上端直接与壳体2内部连通，旁通孔33的下端与吸气管13连通。
冷冻循环装置的高压侧和排气管3之间具有止回阀53，当电机6停止时，止回阀53阻止冷冻循环装置高压侧的高压气体逆流到排气管3。可选地，止回阀53为单向阀或电磁开关阀，以保证排气管3内气体能够通过止回阀53进入冷冻循环装置高压侧，而冷冻循环装置高压侧的高压气体无法逆流到排气管3中。
参照图1、图6-图10、图12所示，排气管3的一端连接有冷凝器50，且冷凝器50与排气管3之间设置有止回阀53，当电机6停止时，止回阀53防止冷凝器50的高压气体向排气管3流动，以此保证壳体2内的高压气体可尽快进入压缩腔11，进而保证壳体2内的压力可尽快下降至与压缩腔11内的压力相等，以缩短压缩机重启时间。
主轴承20上侧主消音器23中的旁通装置30具有旁通孔33，吸气管13与气缸10的连接处开设有U形槽12a，旁通孔33的上端与高压的主消音器23连通，下端与低压的U形槽12a连通。当电机6停止，排气管3中的止回阀53关闭时，密封壳体2的高压压力降低，压缩腔11的低压压力上升。如果密封壳体2与压缩腔11的压力差的下降使旁通孔33开孔，那么密封壳体2的高压气体会经过主消音器23与旁通孔33，从U形槽12a流出吸气管13。 因此，由于密封壳体2的压力与吸气管13的压力在短时间内变得相等，回转式压缩机1可以迅速重启。
根据本申请图1-图13所示实施例的回转式压缩机的有益效果是：
1)在全球最普及的通过旋转式压缩机的On/Off(运行与停止)控制空调温度的空调(示意说明)中，由于可以将压缩机的停止时间减少到以往的约30％，因此可以大幅度缩短重启时间。
2)通过该效果，空调温度的变动较小，可以提高APF(年能源效率)。
3)可以在搭载改变转速的变频电机的旋转式压缩机中追加本申请的旁通装置30。该应用设计中，例如除霜时可以缩短压缩机的停止时间。
4)将小型的旁通装置30添加到以往的旋转式压缩机中的特征，可以通过小改造以及低成本实现缩短重启时间的目的。
5)本申请的旁通装置30还适用于双缸型和卧式旋转式压缩机。
下面结合图14-图20详细描述根据本申请另一实施例的回转式压缩机。为改善压缩机停止后重启时间长且重启后压缩机的壳体压力从低压变到高压需要时间长的问题，本申请的回转式压缩机的特点是将壳体2的压力保持在中压，停止及重启压缩机。具体内容在以下实施例中展示。回转式压缩机的代表例子有壳体内压为高压的旋转式压缩机和涡旋压缩机。
图14表示含有本申请的压缩机1的稳定运转中的空调冷冻循环简图。储液器45的低压冷媒从压缩机1的吸气管13吸入压缩腔11，在压缩腔11中压缩的高压气体排向密闭壳体2。
从排气管3排出的高压冷媒通过第二止回阀装置53(即上面所说的止回阀53)移动到冷凝器50，在此冷凝的液体冷媒通过电动膨胀阀51形成低压冷媒，在蒸发器52蒸发形成低压气体，通过第一止回阀装置54从低压管47流入储液器45。
压缩机1的特点是在固定于壳体2内部的压缩机构部5上具有均压装置30，均压装置30即上面所说的旁通装置30，如后记所示压缩机1在运转中，均压装置30的旁通孔33关闭，壳体2的高压气体不会流到吸气管13。
图15所示的是运转中的压缩机1内部构造。图16表示的是图15中X-X的截面。图15中，壳体2内置电机6和压缩机构部5，壳体2底部内置润滑油8。压缩机构部5的气缸10外周点焊固定在壳体2的内周，主轴承20和副轴承25密封气缸10中心的圆筒形压缩腔11。
由电机6所驱动的曲轴40与主轴承20及副轴承25滑动配合，曲轴40在压缩腔11中 驱动滚动活塞15公转。这时，滚动活塞15吸入低压气体，从排气阀24的排气孔21a向消声器23排出。之后，高压气体通过电机6从排气管3排出。
固定在壳体2外侧的圆筒储液器45与一般储液器一样，上部接低压管47，中心有中心管48。中心管下端的弯曲管连接吸气管13，吸气管13被压入从气缸10的外周对压缩腔11开孔的吸气孔12。储液器45内部存有少量液体冷媒。
压缩机1在主轴承20的主轴板21上配备有均压装置30，均压装置30具有旁通孔33，旁通孔33的上部开孔端位于消声器23的内部。如图16所示，在气缸10的滑片槽14做往复运动的滑片16前端抵接在压缩腔11公转的滚动活塞15外周。均压装置30配置在吸气孔12上方。
图17是压缩机构部5的截面，表示均压装置30的构造。均压装置30在加工在主轴板21上的圆筒孔31的中心上有旁通孔33，旁通孔33下端与气缸10的吸气孔12连通。压缩机1运转中，旁通阀32在旁通孔33上端静止，旁通阀32为开闭阀。
圆筒孔31底部和上部分别有线圈弹簧34和限位器35，线圈弹簧34把旁通阀32向限位器35方向按压。压缩机1在运转中，壳体2内部压力变高压，由于吸气孔12是低压，旁通阀32闭合旁通孔33。
但是，压缩机1停止后，壳体2压力降低，吸气孔12压力上升后，旁通孔33受到线圈弹簧34的按压力而打开，旁通阀32外周在限位器35处静止。因此，如图17右上图所示，壳体2的高压气体经由旁通孔33流出到达吸气孔12。
压缩机1停止后，壳体2压力降低，吸气孔12压力上升这种现象见于内置压缩机构部5的壳体2内为高压的回转式压缩机。例如压缩机1是旋转式压缩机，如图16所示，因公转滑动的滚动活塞15内径和往复滑动的滑片16的背面孔14a是高压，经由该部品滑动面的滑动间隙，壳体2的高压气体向压缩腔11泄露。即压缩机1在运转中，向压缩腔11泄露的气体全部被再次压缩排到壳体2中。
但是，如图18所示，压缩机1停止后，排气孔21a在排气阀24的作用下关闭，泄漏到压缩腔11的气体经由吸气管13流到储液器45。因此，壳体2的压力降低，储液器45的压力上升。另外，由于第一止回阀装置54会阻止流到储液器45的高压气体流向蒸发器52，蒸发器52保持低压。
壳体2压力变低后，壳体2的压力会低于冷凝器50的压力。这时，第二止回阀装置53关闭。因此，冷凝器50可以在停止运转前维持高压的状态。此时电动膨胀阀51通过控制关闭。但是，由于毛细管阀等不能进行阀控制，冷凝器50压力缓慢下降，蒸发器52压力提高。
图19表示压缩机1停止后，壳体2、储液器45和压缩腔11等的压力变均等时冷冻循 环装置的压力分布。储液器45的压力与壳体2压力一致，壳体2压力是高压，比冷凝器50压力要低。
此处举一例：家用空调搭载的旋转式压缩机中，除去压缩机构部5和电机6、润滑油8的合计容积，壳体2的空间容积(C)大约有2100cc，设储液器45的内部容积(A)约有700cc，则储液器容积是壳体空间容积的1/3。
另一方面，当上述空调使用的冷媒是R410A，运行停止前的壳体2的内压为3.0MPaA，储液器45的内压为1.0MPaA时，压缩机1停止使高压气体从壳体2流向储液器45，结果两者夜里变为相等的2.5MPaA。
结果，运转中的压缩机1的壳体2压力从3.0MPaA降到2.5MPaA，储液器45的压力从1.0MPaA升到2.5MPaA。压缩机1运转停止，储液器45的压力和压缩机1壳体2的压力等同后，压缩机1可以重启，并且升压速度显著增快。
接下来，从图19的静止状态向电机6通电，压缩机1重启之后，滚动活塞15公转使储液器45的高压气体流入压缩腔11。此时储液器45压力和壳体2的气体压力等同，不会给电机带来大的负荷，可以重启。
启动后，例如由于10秒内均压装置30的旁通孔33打开，壳体2和储液器45的压力差不会迅速增加，压缩腔11的高压气体被压缩后通过排气孔21a。之后，混入到壳体2的高压气体内。
压缩机1运转后，壳体2和储液器45的压差超过预先决定的设计值后，旁通孔33关闭，壳体2压力上升加快，储液器45压力下降加快。
此时，因壳体2压力上升，第二止回阀装置53载体因储液器45压力降低，第一止回阀装置54打开。同时，电动膨胀阀51依照蒸发器52和冷凝器50的温度优化开度，冷冻循环装置过渡到稳定运行。
设图20的冷冻循环装置为上述家用空调，稳定运行中的压缩机1开始停止后到重启完毕，用实线(A1)画出壳体2的排气变化，储液器45内部压力变化用实线(A2)表示。为与压缩机1比较，以往压缩机的壳体压力变化用虚线(B1)表示，储液器的压力变化用虚线(B2)表示。
横轴是过程时间，用数字表示分钟(min)；纵轴表示压力(MPaA)。将压缩机开始停止到重启的时间设为10秒，确认上述两个压力是否等同。
箭头↓表示压缩机停止后的高压侧压力和低压侧压力变得等同的时间，箭头↑表示压缩机重启后，压力与运转停止前压力等同，完成重启的时间。
压缩机1在停止运转后高压(A1)和低压(A2)分别缓慢下降或上升，依据箭头↑显示，约20秒后旁通孔33打开，高压(A1)和低压(A2)分别急剧降低或上升，在运转停 止约50秒后压力变等同。其压力为2.5MPaA。之后，再过10秒，重启压缩机，从运转停止1分50秒后，与压缩机1停止前的压力相同。
以往的压缩机在运转停止后，高压(B1)和低压(B2)分别缓慢下降及上升。但是之后气压的降低和上升变得缓慢，约2分40秒后等同。此时压力约为1.9MPaA。10秒后重启压缩机，从运转停止后经过约4分30秒等同于运转停止前的压力。其结果，压缩机1的运转停止到重启完毕的时间是以往压缩机的40％。
形成时间差的原因有两个：
(1)压缩机1停止运转后，壳体2和储液器45之间进行压力交换，压力变等同的时间加快。而且，平衡压力高，为2.5MPaA，所以恢复到起动停止前压力的时间短。
(2)以往压缩机运转中，压缩机壳体和冷凝器属高压容器，蒸发器和储液器属低压容器，压缩机停止后，因高压容器的高压冷媒(含液体冷媒)经由膨胀阀(或毛细管)向蒸发器流出，这些容器达到均压。所以，达到均压所耗时间长。而且，其平衡力是中压，为1.9MPaA，恢复到起动停止前压力所需时间长。以上就是上述压缩机启动的时间差。
参照图14-图15、图18-图19所示，根据本申请实施例的回转式压缩机1可以包括：壳体2、电机6、压缩机构部5、排气管3、吸气管13、均压装置30、储液器45，壳体2可以是密封壳体，电机6设置在壳体2内，压缩机构部5设置在壳体2内且由电机6驱动，排气管3与壳体2的内部连通，吸气管13与压缩机构部5连接，均压装置30具有连通壳体2内部与吸气管13的旁通孔33，以选择地连通壳体2内部与吸气管13，储液器45的一端与吸气管13连接，储液器45的另一端设置有第一止回阀装置54。
在电机6停止时，壳体2压力降低、储液器45压力升高，第一止回阀装置54关闭，均压装置30的旁通孔33打开，使得壳体2内部通过吸气管13与储液器45连通，直至壳体2内部压力与储液器45内部压力相等。均压装置30和第一止回阀装置54利用压力差自动控制开闭，成本低，可靠性高，无需电力控制，节约能源。
第一止回阀装置54阻止储液器45的气体逆流到蒸发器52。可选地，第一止回阀装置54为单向阀或电磁开关阀，以保证蒸发器52内气体能够通过第一止回阀装置54进入储液器45中，而储液器45的高压气体无法逆流到蒸发器52中。
进一步地，参照图15、图18-图19所示，排气管3上设置有第二止回阀装置53，壳体2内部压力降低时，第二止回阀装置53关闭。当电机6停止时，第二止回阀装置53防止冷凝器50的高压气体向排气管3流动，以此保证壳体2内的高压气体可尽快进入压缩腔11，进而保证壳体2内的压力可尽快下降至与压缩腔11内的压力相等，以缩短压缩机重启时间。
可选地，第二止回阀装置53为单向阀或电磁开关阀，以保证排气管3内气体能够通过第二止回阀装置53进入冷凝器50，而冷凝器50的高压气体无法逆流到排气管3中。
压缩机构部5包括：气缸10、主轴承20、副轴承25，主轴承20位于气缸10的一端，副轴承25位于气缸10的另一端，气缸10内形成压缩腔11，吸气管13与压缩腔11连通，压缩机正常运转时，储液器45的冷媒可经吸气管13进入压缩腔11，在压缩腔11内被压缩成高压气体后排放至壳体3内。压缩机停止时，壳体2内的高压气体可经旁通孔33进入压缩腔11，再经吸气管13进入储液器45中，以使壳体2内的压力尽快下降至与储液器45内的压力相等。
参照图15所示，主轴承20的主轴板21上方设置有消声器23，均压装置30的高压侧开孔端开设在消声器23中，消声器23具有与壳体2内部空腔(即电机6下方空间)连通的消声器排气孔。
如图17所示，均压装置30可以包括：旁通阀32、弹簧34，旁通阀32利用壳体2压力和储液器45的压力差可选择地连通高压侧开孔端与旁通孔33，换言之，旁通阀32用于打开或关闭旁通孔33，旁通阀32打开旁通孔33时，壳体2内的高压气体可经旁通孔33进入吸气管13。具体地，壳体2内的高压气体可经消声器排气孔、旁通孔33的高压侧开孔端、旁通孔33进入吸气管13，再从吸气管13进入储液器45中。
弹簧34利用壳体2压力和储液器45的压力差伸缩，弹簧34使旁通阀32向打开旁通孔33的方向运动。在图17所示的实施例中，弹簧34为压缩弹簧，位于旁通阀32的下方，始终对旁通阀32施加向上的推力。而在一些未示出的实施例中，弹簧34也可以位于旁通阀32的上方，始终对旁通阀32施加向上的拉力。限位器35用于限制旁通阀32的最大移动距离，防止旁通阀32脱落。
在图15、图17-图18所示的实施例中，均压装置30可位于主轴承20的主轴板21上，当然，在一些未示出的实施例中，均压装置30也可位于副轴承25的副轴板上。或者主轴板21和副轴板上均设置有均压装置30。
回转式压缩机1停止时，壳体2的高压气体经由滚动活塞15及滑片16等滑动面，从低压的压缩腔11泄漏到吸气管13，再扩散到储液器45。壳体2和吸气管13的压力差变小后，均压装置30的旁通孔33打开，壳体2和储液器45的压力急速变得等同，中途第一止回阀装置54和第二止回阀装置53关闭。所以压缩机1可以在短时间内重启，壳体2的压力会迅速恢复到停止前的高压状态。壳体2在升压过程中，均压装置30和第一止回阀装置54、第二止回阀装置53均打开。
根据本申请图14-图20所示实施例的回转式压缩机1的有益效果是：
1)可以在控制空调温度的空调(示意说明)中大幅缩短重启时间，大大改善空调温度 波动。此外，能够缩短除霜运转时间。
2)必要的运转时间变得准确，大幅缩短压缩机重启时间可以改善APF(年能效)。
3)均压装置30和第一止回阀装置54、第二止回阀装置53等利用压力差自动控制，成本低，可靠性高，而且无需电力控制，有利于节约能源。
4)无论是定速运转还是变速运转的变频器电机，都可以利用。
5)还可以应用于旋转式压缩机和涡旋压缩机等回转式压缩机、双缸式和卧式压缩机。
根据本申请另一方面实施例的冷冻循环装置，包括冷凝器50、膨胀装置51(即电动膨胀阀51)和蒸发器52以及上述实施例的回转式压缩机。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。此外，本领域的技术人员可以将本说明书中描述的不同实施例或示例进行接合和组合。
尽管上面已经示出和描述了本申请的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本申请的限制，本领域的普通技术人员在本申请的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (19)

  1. 一种回转式压缩机，其特征在于，包括壳体，所述壳体内部收纳电机和压缩机构部，连通冷冻循环装置的高压侧的排气管连接所述壳体，连通所述冷冻循环装置的低压侧的吸气管连接所述压缩机构部，所述压缩机构部具有旁通装置，当所述电机停止后，所述壳体的气体流到所述吸气管或所述吸气管连通的低压回路中。
  2. 根据权利要求1所述的回转式压缩机，其特征在于，所述旁通装置至少包括：连通所述壳体的旁通孔、由于所述壳体与所述吸气管的压力差打开和关闭所述旁通孔的旁通阀、和使所述旁通阀向打开所述旁通孔的方向运动的弹簧。
  3. 根据权利要求2所述的回转式压缩机，其特征在于，所述旁通孔的一方连接所述压缩机构部的排气消音室内部，所述旁通孔的另一方连接所述吸气管或所述吸气管连通的低压回路。
  4. 根据权利要求1所述的回转式压缩机，其特征在于，连接所述压缩机构部中的气缸压缩腔的两侧开孔面的主轴板和副轴板的其中一个具备所述旁通装置。
  5. 根据权利要求1所述的回转式压缩机，其特征在于，所述冷冻循环装置的高压侧和所述排气管之间，具有当所述电机停止时，阻止所述冷冻循环装置的高压侧的高压气体逆流到所述排气管的止回阀。
  6. 根据权利要求2所述的回转式压缩机，其特征在于，当所述壳体与所述吸气管的压力差小于预设值时，所述旁通阀打开所述旁通孔；当所述壳体与所述吸气管的压力差大于预设值时，所述旁通阀关闭所述旁通孔。
  7. 根据权利要求1所述的回转式压缩机，其特征在于，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述主轴承的主轴板和所述副轴承的副轴板上均设置有所述旁通装置。
  8. 根据权利要求7所述的回转式压缩机，其特征在于，所述主轴承的背离所述气缸的一侧设置有主消音器，所述副轴承的背离所述气缸的一侧设置有副消音器，所述压缩机构部具有连通所述主消音器与副消音器的通孔，所述旁通装置的旁通孔的一端连通对应消音器的消音室，所述旁通孔的另一端连通所述吸气管。
  9. 根据权利要求1所述的回转式压缩机，其特征在于，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述旁通装置设置在所述气缸的外周面上。
  10. 根据权利要求1所述的回转式压缩机，其特征在于，所述旁通装置为均压装置，所述均压装置具有连通所述壳体内部与所述吸气管的旁通孔；
    所述回转式压缩机还包括：储液器，所述储液器的一端连接所述吸气管，所述储液器的另一端连接第一止回阀装置，所述电机停止时，所述均压装置的旁通孔打开，所述第一止回阀装置关闭，所述壳体内的气体流到所述吸气管或所述储液器中。
  11. 根据权利要求10所述的回转式压缩机，其特征在于，所述第一止回阀装置为单向阀或电磁开关阀。
  12. 根据权利要求10所述的回转式压缩机，其特征在于，所述排气管上设置有第二止回阀装置，所述壳体内部压力降低时，所述第二止回阀装置关闭。
  13. 根据权利要求12所述的回转式压缩机，其特征在于，所述第二止回阀装置为单向阀或电磁开关阀。
  14. 根据权利要求10所述的回转式压缩机，其特征在于，所述均压装置包括：打开或关闭所述旁通孔的旁通阀、利用所述壳体压力和所述储液器的压力差伸缩的弹簧。
  15. 根据权利要求14所述的回转式压缩机，其特征在于，所述旁通孔的高压侧开孔端位于所述压缩机构部的消声器中。
  16. 根据权利要求15所述的回转式压缩机，其特征在于，所述压缩机构部包括：气缸、主轴承、副轴承，所述主轴承位于所述气缸的一端，所述副轴承位于所述气缸的另一端，所述气缸内形成压缩腔，所述吸气管与所述压缩腔连通。
  17. 根据权利要求15或16所述的回转式压缩机，其特征在于，所述消声器具有与所述壳体内部连通的消声器排气孔。
  18. 根据权利要求14所述的回转式压缩机，其特征在于，所述旁通阀利用所述壳体压力和所述储液器的压力差可选择地连通所述旁通孔与所述吸气管，所述弹簧使所述旁通阀向打开所述旁通孔的方向运动。
  19. 一种冷冻循环装置，其特征在于，包括权利要求1-18中任一项所述的回转式压缩机。
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