WO2017063503A1 - 涡旋压缩机的变容机构及涡旋压缩机 - Google Patents

涡旋压缩机的变容机构及涡旋压缩机 Download PDF

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Publication number
WO2017063503A1
WO2017063503A1 PCT/CN2016/100558 CN2016100558W WO2017063503A1 WO 2017063503 A1 WO2017063503 A1 WO 2017063503A1 CN 2016100558 W CN2016100558 W CN 2016100558W WO 2017063503 A1 WO2017063503 A1 WO 2017063503A1
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WO
WIPO (PCT)
Prior art keywords
varactor
passage
plunger
hole
scroll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2016/100558
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English (en)
French (fr)
Inventor
江国彪
李小雷
单彩侠
胡余生
方琪
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US15/767,788 priority Critical patent/US10941774B2/en
Publication of WO2017063503A1 publication Critical patent/WO2017063503A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • 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
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
    • 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
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to a varactor mechanism for a scroll compressor and an associated scroll compressor, and more particularly to an scroll compressor for improving the motion synchronism of a blocking member of a varactor mechanism Varactors and related scroll compressors.
  • variable capacity (varactor) scroll compressors are characterized by high energy efficiency at low loads and high reliability and low vibration. It is used more and more widely in air conditioner systems with adjustable capacity.
  • the scroll compressor generally includes: a housing; a compression mechanism including an orbiting scroll and a fixed scroll; a driving mechanism including a motor, a crankshaft, and an anti-rotation device; and a support mechanism including a main bearing housing (upper housing).
  • the profiles of the movable and fixed scrolls are all vortex-shaped, and the orbiting scroll is eccentric with respect to the fixed scroll and can be mounted, for example, at a difference of 180 degrees.
  • the fixed and fixed scrolls will contact in a plurality of straight lines in the axial direction (in the cross section, they appear to contact at several points).
  • the ends of the scroll lines are in contact with the bottoms of the respective scrolls, thereby forming a series of crescent-shaped spaces (i.e., the elementary volume or compression chamber) between the movable and fixed scrolls.
  • crescent-shaped spaces i.e., the elementary volume or compression chamber
  • the outer crescent-shaped space continuously moves toward the center and the volume is continuously reduced.
  • the working fluid e.g., refrigerant
  • the crescent shaped space is compressed and the pressure is continuously increased until the crescent shaped space communicates with the central venting opening to discharge the high pressure working fluid out of the compression mechanism.
  • a bypass variator hole communicating with the compression chamber is opened in the scroll, so that the compression chamber communicates with the suction region (or other low-pressure fluid region), thereby reducing The displacement of the small compression chamber.
  • An object of the present invention is to provide a varactor for a scroll compressor that can reliably realize the motion synchronism of a plurality of blocking members.
  • Another object of the present invention is to provide a varactor mechanism for a scroll compressor which is simple in overall structure and capable of improving reliability of capacity adjustment switching.
  • Another object of the present invention is to provide a varactor for a scroll compressor that can avoid an increase in power consumption or a leakage of a working fluid due to uneven gas force in the compression mechanism.
  • Another object of the present invention is to provide a varactor mechanism for a scroll compressor capable of reducing leakage resistance and reducing power consumption.
  • Another object of the present invention is to provide a varactor mechanism for a scroll compressor capable of reducing processing difficulty and processing cost.
  • Another object of the present invention is to provide a varactor for a scroll compressor which can improve the sealing performance of a compression mechanism and thereby improve the energy efficiency of the compressor.
  • Another object of the present invention is to provide a variable volume for a scroll compressor that allows the blocking member to have radial flexibility and/or axial flexibility so as to eliminate over-positioning problems to reduce assembly difficulty and reduce component machining accuracy. mechanism.
  • Another object of the present invention is to provide a scroll compressor that allows the blocking member to have radial flexibility and/or axial flexibility to facilitate axial sealing of the compression mechanism and also to prevent the blocking member from interfering with the movable scroll.
  • the varactor is to provide a scroll compressor that allows the blocking member to have radial flexibility and/or axial flexibility to facilitate axial sealing of the compression mechanism and also to prevent the blocking member from interfering with the movable scroll.
  • Another object of the present invention is to provide a scroll compressor including the varactor mechanism as described above.
  • a varactor mechanism for a scroll compressor including a compression mechanism adapted to compress a working fluid
  • the compression mechanism includes a fixed scroll and a movable scroll to define a series of compression chambers between the fixed scroll and the movable scroll.
  • the varactor mechanism includes a bleed passage adapted to communicate a medium pressure compression chamber in the compression chamber with a low pressure region, an occlusion member adapted to selectively open and close a venting passage; and an actuating device comprising an actuating member coupled to the actuating member to selectively open and close the venting as the actuating member moves aisle.
  • the blocking member is a plurality of blocking members, the performing member being a single executing member coupled to the single executing member to be simultaneously movable with the action of the single executing member.
  • the blocking member is a plunger.
  • one end of the plurality of the plungers is coupled to a lower surface of the actuator member.
  • the actuating device further comprises a driving portion, the driving portion comprising a pressure channel capable of being selectively supplied with a high pressure fluid and a low pressure fluid;
  • the pressure passage is supplied with a high pressure fluid
  • the high pressure fluid supplied via the pressure passage pushes the actuator member to actuate the actuator member.
  • variable volume cylinder connected to the fixed scroll end plate of the fixed scroll is further included.
  • an annular channel opening toward the fixed scroll end plate is formed in the variable volume cylinder, and the actuating member is disposed in the annular channel.
  • a communication hole is formed in the variable volume cylinder, and the pressure passage passes through the communication hole
  • the annular channel is in communication to enable introduction of high pressure fluid to the upper portion of the annular channel to drive the actuator member.
  • the venting passage includes: a plurality of first passages formed in the fixed scroll end plate and capable of communicating with the intermediate pressure compression chamber; and being disposed at the variable volume cylinder and capable of being a second passage in which the first passage and the low pressure region communicate.
  • each of the first passages includes a variable hole and a bleed hole that communicate with each other, and the varisible hole is formed at a lower portion of the fixed scroll end plate so as to be able to communicate with the intermediate pressure compression chamber.
  • a drain hole formed in an upper portion of the fixed scroll end plate;
  • the plunger is adapted to selectively open and close the variable aperture.
  • a guide hole formed in an upper portion of the fixed scroll end plate and capable of communicating with the variable aperture, wherein the guide hole defines the plunger together with the variable aperture A transition path suitable for moving therein.
  • the leakage hole is disposed on an upper side of the variable volume, the leakage hole is a blind hole, and the leakage hole partially overlaps the guiding hole, and passes through the guiding hole The variable pores are connected.
  • the second passage is defined in the annular channel by the fixed scroll end plate, the variable volume cylinder and the actuating member.
  • the scroll compressor further includes an air suction pipe;
  • the compression mechanism further includes an inhalation chamber
  • variable displacement cylinder is provided with an intake passage and a discharge hole, and the intake passage communicates with the intake pipe and the suction chamber, and the intake passage and the intake pipe constitute the low pressure region, and The second passage communicates with the intake passage via the discharge hole.
  • biasing means mounted between said fixed scroll end plate and said actuating member, said biasing means comprising a direction adapted to move said actuating member away from said fixed scroll end plate Offset biasing member.
  • a sealing device adapted to seal the plunger relative to the varactor hole is also included.
  • the sealing device includes: a seal groove provided at an outer circumferential surface of the plunger; a seal ring disposed in the seal groove; and a guide disposed through the plunger and the execution member Pressure channel.
  • the pressure guiding passage is configured to be capable of guiding a high pressure fluid supplied through the pressure passage Into the sealing groove, thereby forcing the sealing ring to open and abut against the inner cylindrical surface of the variable orifice.
  • the actuating member is an annular piston.
  • the annular piston includes a piston body and a fixing ring fixedly coupled together, and a receiving hole is disposed at the fixing ring;
  • the plunger includes a plunger barrel portion and a flange portion extending radially outward from an end of the plunger barrel portion;
  • the plunger is coupled to the annular piston such that the flange portion is placed in an axial gap formed by the piston body and the retaining ring and the plunger barrel portion is inserted in the receiving bore.
  • the axial gap is greater than the axial thickness of the flange portion; and/or
  • the inner diameter of the receiving hole is designed to be larger than the outer diameter of the plunger barrel.
  • a receiving hole is formed at one end of the plunger barrel portion where the flange portion is provided;
  • a biasing member is disposed, the biasing member being received in the receiving hole and preloaded such that one end of the biasing member abuts the piston body and the other end abuts the plunger barrel Thereby the plunger is biased towards the direction away from the annular piston.
  • variable volume cylinder is integrally formed with the fixed scroll.
  • a scroll compressor includes a varactor mechanism as described above.
  • a single actuating device e.g., a single actuator such as a single annular piston
  • a single control structure actuating structure
  • the effective area of the venting passage is not limited to the fixed vortex structure, so that the escaping resistance can be reduced, the power consumption can be reduced, and the performance of the scroll compressor having the varactor function can be improved.
  • the processing difficulty and the processing cost are also reduced.
  • the guide hole is provided and the guide hole and the variable orifice define a travel passage in which the blocking member (for example, the plunger) is adapted to travel, the reliability of the plunger action can be ensured to ensure reliable operation of the annular piston. Sex. At the same time, the radial matching clearance between the plunger and the variable orifice can be further reduced, which is advantageous for improving the sealing performance of the compression mechanism under full capacity operation.
  • the blocking member for example, the plunger
  • FIG. 1 is a longitudinal sectional view showing a scroll compressor including a varactor according to a first embodiment of the present invention
  • FIG. 2 is an exploded perspective view showing a varactor according to a first embodiment of the present invention
  • Figure 3 is a top view and a perspective view showing a fixed scroll according to a first embodiment of the present invention
  • FIG. 4 is a perspective view mainly showing an annular piston according to a first embodiment of the present invention
  • Figure 5 is a cross-sectional view showing a varactor in a non-variable state according to a first embodiment of the present invention
  • Figure 6 is a cross-sectional view showing a varactor in a variable state according to a first embodiment of the present invention
  • Figure 7 is a perspective view showing an annular piston and a plunger according to a second embodiment of the present invention.
  • Figure 8 is a cross-sectional view showing a varactor in a non-variable state according to a second embodiment of the present invention.
  • Figure 9 is a longitudinal sectional view showing a scroll compressor including a varactor according to a third embodiment of the present invention.
  • Figure 10 is an exploded perspective view showing a varactor mechanism according to a third embodiment of the present invention.
  • Figure 11 is an assembled perspective view and an exploded perspective view mainly showing an annular piston according to a third embodiment of the present invention.
  • Figure 12 is a cross-sectional view showing a varactor in a non-variable state according to a third embodiment of the present invention.
  • Figure 13 is a cross-sectional view showing a varactor in a variable state according to a third embodiment of the present invention.
  • Figure 14 is a top view and a perspective view showing a fixed scroll according to a fourth embodiment of the present invention.
  • the scroll compressor 1 may include a housing assembly, a compression mechanism, a drive mechanism 3, a support mechanism, an intake pipe 7, and an exhaust pipe 15.
  • the scroll compressor 1 is shown as a fully enclosed high pressure side scroll compressor.
  • the present invention is not limited to a fully enclosed high pressure side scroll compressor, but may be applied to, for example, a fully enclosed low pressure side scroll compressor and a semi-closed scroll compressor.
  • the housing assembly can include a housing body 8, a top cover and a bottom cover 29 that can define a confined space for receiving, for example, a compression mechanism and a drive mechanism 3.
  • the compression mechanism may include a fixed scroll 5, an orbiting scroll 6, and an anti-rotation device 10.
  • the fixed scroll 5 may include an end plate and a fixed scroll.
  • a discharge port for discharging the compressed high pressure working fluid from the compression mechanism may be disposed at substantially the center of the fixed scroll end plate.
  • the movable scroll 6 may include an end plate and a movable scroll.
  • the hub of the eccentric pin of the crankshaft (drive shaft) may be disposed to protrude from the lower surface of the driven scroll end plate.
  • the fixed scroll and the movable scroll can be meshingly engaged to define a series of compression chambers (working chambers) between the fixed scroll 5 and the movable scroll 6.
  • the anti-rotation device 10 can be implemented as an Euclidean ring (cross slip ring) for limiting the rotation of the movable scroll 6 while allowing the orbiting scroll 6 to perform a translational translation motion with respect to the fixed scroll 5.
  • the drive mechanism 3 may include: a motor 4 composed of a stator 19 and a rotor 18; and a crankshaft 13.
  • the crankshaft 13 may be arranged to be rotatable integrally with the rotor 18, and the crankshaft 13 may include an eccentric pin adapted to drive the movable scroll 6 at the upper end.
  • the support mechanism may include a main bearing housing 9 and a sub-bearing housing 22.
  • the main bearing housing 9 is adapted to axially support the movable scroll 6 (specifically to support the movable scroll end plate).
  • a main bearing 14 (for example implemented as a plain bearing) may also be provided at the main bearing housing 9, and the main bearing 14 is adapted to support the upper portion of the crankshaft 13.
  • a drive bearing 12 (for example implemented as a plain bearing) may be provided between the hub of the movable scroll 6 and the eccentric pin of the crankshaft 13, whereby the eccentric pin of the crankshaft 13 drives the vortex via the drive bearing 12
  • the hub of the screw 6 in turn drives the translational translation of the orbiting scroll 6.
  • a secondary bearing 24 (for example embodied as a rolling bearing) and a thrust plate 25 for radial and axial support of the lower portion of the crankshaft 13 can be provided at the secondary bearing housing 22.
  • the suction pipe 7 can be connected to the fixed scroll 5 so that the low pressure working fluid from the external working circuit can flow through the suction pipe 7 to the compression mechanism for compression.
  • the exhaust pipe 15 may be coupled to the casing body 8 of the casing assembly such that the high pressure working fluid compressed by the compression mechanism may flow to the external working circuit via the exhaust pipe 15.
  • the operation of the scroll compressor 1 will be briefly described below with reference to FIG. 1.
  • the motor 4 When the motor 4 is energized, the rotor 18 rotates integrally with the crankshaft 13, and the eccentric pin of the crankshaft 13 drives the hub of the movable scroll 6 via the drive bearing 12 to drive the movable scroll 6 to perform a translational translation motion.
  • the working fluid enters the suction chamber S1 of the compression mechanism via the suction pipe 7 (see FIG. 5), and as the movable scroll 6 continues to rotate, the suction chamber S1 closes to become a compression chamber and moves toward the center. The volume is continuously reduced, so that the working fluid in the compression chamber is compressed and the pressure is increased.
  • the working fluid is discharged from the center discharge port of the fixed scroll 5 into the upper portion of the closed space defined by the casing assembly, and then passes through the fixed scroll 5 and the flow passage provided in the main bearing housing 9. It enters the middle and lower parts of the closed space, and then discharges the scroll compressor 1 via the exhaust pipe 15.
  • the varactor mechanism 2 is provided in the scroll compressor 1.
  • the varactor mechanism 2 may include: a venting passage (bypass passage) P; an occlusion member; And actuating the device.
  • the bleed passage P is adapted to compress a specific compression chamber of the compression mechanism (eg, a medium pressure compression chamber having a pressure between the pressure of the low pressure suction chamber S1 and a pressure of the central high pressure compression chamber to be discharged or being discharged) and the compression mechanism
  • the suction chamber S1 or other low pressure fluid region (low pressure region) is in communication.
  • the bleed passage P may include a first passage P1 (see FIG. 6) formed at the fixed scroll end plate and an actuator member of the fixed scroll end plate, the variable displacement cylinder 30 of the varactor mechanism 2, and the actuating device (see For example, the second passage P2 defined by the annular piston 31) (see Fig. 6).
  • the first passage P1 may include: a variable-capacity hole 5a formed at a lower portion of the fixed scroll end plate to be in communication with a specific compression chamber; and an upper portion formed at the fixed scroll end plate such that the lower end thereof is adapted to be adapted to the variable-capacity hole 5a
  • the upper end is connected (for example, via a guide hole 5c which will be described later) and the upper end is adapted to communicate with the second passage P2.
  • a guide hole 5c may also be provided.
  • the guide hole 5c may be formed at an upper portion of the fixed scroll end plate.
  • the lower end of the guide hole 5c may communicate with the upper end of the variable aperture 5a, so that the guide hole 5c together with the variable aperture 5a defines a transition passage in which the blocking member is adapted to travel therein.
  • the inner diameter of the guide hole 5c may coincide with the inner diameter of the variable aperture 5a, so that the guide hole 5c and the variable aperture 5a can smoothly engage to form a uniform inner diameter passage, which facilitates stable guiding of the plunger to make the plunger The movements are smoother and more reliable.
  • each of the variable apertures 5a there may be provided a leakage opening 5b communicating therewith, the relief opening 5b being disposed on the upper side of the variable aperture 5a, preferably in the Two relief holes 5b are provided on both sides of the variable aperture 5a.
  • the leakage hole 5b may be disposed at a side of the guiding hole 5c, and the leakage hole 5b is a blind hole partially overlapping the guiding hole 5c, and passes through the guiding hole 5c and the variable capacitance hole 5a Connected.
  • the blocking member can be embodied as a plunger 37 in a generally cylindrical shape.
  • the plunger 37 is adapted to travel in a travel path defined by the pilot hole 5c and the variable aperture 5a so as to be in a closed position and an open position.
  • the end (lower end) 37c of the plunger 37 is located below the lower end of the bleed hole 5b (for example, as shown in Fig. 5, the end 37c of the plunger 37 abuts the end of the orbiting scroll of the movable vortex 6 The upper end) thereby blocks the first passage P1 and prevents the medium pressure working fluid from escaping from the specific compression chamber (medium pressure compression chamber) to the low pressure fluid region.
  • the end 37c of the plunger 37 is located above the lower end of the bleed hole 5b (as shown in Figure 6), thereby opening the first passage P1 to allow the medium pressure working fluid to pass from the specific compression chamber via the varactor
  • the hole 5a and the bleed hole 5b (i.e., the first passage P1) and the second passage P2 are vented to the low pressure fluid region.
  • the actuation device can include an actuator member and a drive portion.
  • the actuating member can be embodied as an annular piston 31.
  • the upper end of the plunger 37 may be fixedly coupled to the lower surface of the annular piston 31, for example.
  • variable volume cylinder 30 can be provided in the varactor mechanism 2.
  • the variable volume cylinder 30 can be substantially annular.
  • An annular groove G (see FIG. 5) having a downward opening (i.e., opening toward the compression mechanism) may be formed in the variable displacement cylinder 30, and the annular piston 31 may be fitted in the annular groove G in a snug manner.
  • grooves 31c, 31d (see FIG. 4) may be provided at a radially inner circumferential surface and/or a radially outer circumferential surface of the annular piston 31, and an O-ring 32 may be disposed in the groove such that the ring The piston 31 is sealingly coupled to the annular channel G of the variable displacement cylinder 30.
  • the drive portion can include a pressure passage 34 and a high pressure fluid supplied to the pressure passage 34.
  • the lower end of the pressure passage 34 may be connected to a communication hole 30a (see FIG. 2) provided at an upper portion of the variable displacement cylinder 30, so that the pressure passage 34 may pass through the communication hole 30a and the annular groove G (specifically, the annular groove G) Upper) connected.
  • the pressure passage 34 can be selectively supplied with a high pressure fluid and a low pressure fluid. In the case where the pressure passage 34 is supplied with the high pressure fluid, the high pressure fluid supplied via the pressure passage 34 pushes the annular piston 31 downward, thereby pushing the plunger 37 fixedly coupled to the annular piston 31 downward to be in the closed position.
  • the high pressure fluid supplied to the pressure passage 34 may be a high pressure working fluid that is compressed by a compression mechanism of the scroll compressor 1.
  • a discharge orifice PH (see FIG. 5) may be provided at the variable displacement cylinder 30, and the second passage P2 (specifically, the lower portion of the annular passage G constituting the second passage P2) may pass through the discharge port PH It is in communication with a low pressure fluid region, such as the intake passage of the variable displacement cylinder 30 which will be described below.
  • variable displacement cylinder 30 may also be provided with an intake passage S2 (see FIG. 6) such that the lower end of the intake duct 7 may be connected to the upper end of the intake passage S2, and the lower end of the intake passage S2 may be It is connected to the suction chamber S1 provided at the fixed scroll 5 (the intake passage S2 of the variable displacement cylinder 30 and the suction chamber S1 of the fixed scroll 5 may together define a so-called suction zone or low pressure fluid zone).
  • variable displacement cylinder 30 for example, sealingly and fixedly
  • the variable displacement cylinder 30 is connected to the upper surface of the fixed scroll end plate in a state where the annular piston 31 is disposed in the annular groove G
  • the fixed vortex The upper surface of the end plate and the lower surface of the annular piston 31 define a second passage P2 of the bleed passage P at a lower portion of the annular groove G of the varactor cylinder 30, and on the other hand, the upper surface of the annular piston 31
  • a pressure passage U is defined in an upper portion of the annular groove G of the variable displacement cylinder 30 (see Fig. 5).
  • a biasing device can also be provided.
  • the biasing means may comprise a biasing member 33 (for example embodied as a spring such as a coil spring) and a mounting hole 5d provided at the fixed scroll end plate adapted to mount the biasing member 33.
  • the biasing member 33 is adapted to push the annular piston 31 upward.
  • the biasing member 33 can push the annular piston 31 together with the plunger 37 such that the plunger 37 is in the open position.
  • the biasing means can be omitted, in which case the plunger 37 is urged upwardly together with the annular piston 31 by the pressure difference between the intermediate pressure compression chamber and the low pressure fluid region.
  • variable apertures 5a may be provided, and accordingly, two or more plungers 37 connected to the annular piston 31 may be provided to achieve a larger variable volume Adjustment range.
  • a single actuating device (a single actuator member such as a single annular piston 31) for two or more blocking members (plungers 37) is provided such that two or more The plunger 37 simultaneously moves with the movement of the single annular piston 31.
  • the end 37c of the plunger 37 can abut against the end of the orbiting scroll of the movable scroll 6 to achieve axial sealing of the (medium pressure) compression chamber, while the outer peripheral surface (cylindrical surface) of the plunger 37 is changed
  • the bore 5a cooperates to achieve a radial seal of the (medium pressure) compression chamber.
  • the variable orifice 5a of the first passage is blocked to prevent the medium pressure working fluid from leaking out from the specific compression chamber (medium pressure compression chamber) to the low pressure fluid region.
  • a low pressure fluid is supplied to the pressure passage 34 of the actuator (eg, the pressure passage 34 is selectively vortexed)
  • the low pressure suction side of the rotary compressor 1 is connected).
  • the annular piston 31 and the plurality of plungers 37 can be lifted upward by, for example, the biasing force of the biasing member 33 and/or by the intermediate pressure of the (medium pressure) compression chamber Pushing is such that the plurality of plungers 37 are simultaneously in the open position.
  • variable orifice 5a of the first passage is opened to allow the medium pressure working fluid to escape from the specific compression chamber to the low pressure fluid from the specific compression hole 5a and the discharge hole 5b (ie, the first passage P1) and the second passage P2. region.
  • the amount of inhalation and the internal volume ratio (compression ratio) are reduced by shortening the length of the profile line (i.e., the end point of the advance profile line) with the exhaust demagnetization point unchanged.
  • the capacity adjustment of the scroll compressor 1 is achieved.
  • a single actuating device e.g., a single actuator such as a single annular piston
  • a single control structure actuating structure
  • venting passage of the varactor is defined by the fixed vortex rear surface (upper surface), the annular piston, and the variable volume cylinder (in other words, not all of the venting passages are opened in the fixed vortex), the venting is performed.
  • the effective area of the passage is not limited to the fixed scroll structure, so that the discharge resistance can be reduced, the power consumption can be reduced, and the performance of the scroll compressor having the variable capacity function can be improved.
  • the processing difficulty and the processing cost are also reduced.
  • the guide hole 5c is provided and the guide hole 5c together with the variable hole 5a defines a travel passage in which the blocking member (for example, the plunger) is adapted to travel, the reliability of the plunger action can be ensured and the reliability of the annular piston can be ensured. .
  • the radial fit clearance between the plunger 37 and the variable aperture 5a can be further reduced, which is advantageous for improving the sealing performance of the compression mechanism in the full capacity operation state.
  • a varactor mechanism 2 according to a second embodiment of the present invention will now be described with reference to Figs. 7 and 8.
  • a sealing device L is added to the plunger 37 as compared with the first embodiment.
  • the sealing device L may include: a seal groove 31f provided at an outer circumferential surface of the plunger 37; a seal ring 35 adapted to be disposed in the seal groove 31f; and a plunger 37 and an annular piston 31 provided The pressure guiding passage 31e in the middle.
  • the pressure guiding passage 31e may include an axial passage that axially penetrates the annular piston 31 such that one end (upper end) of the axial passage opens to the upper surface of the annular piston 31.
  • the pressure guiding passage 31e may further include one or more radial passages that extend from the lower end of the axial passage to the sealing groove 31f.
  • the scroll compressor 1 when the scroll compressor 1 is operated in the full capacity state, the high pressure fluid introduced from the pressure passage 34 enters the pressure guiding passage 31e via the pressure applying passage and enters the sealing groove 31f, thereby forcing the sealing ring 35 to open and close.
  • the seal ring 35 can be implemented as a U-shaped cross-section open-inward seal ring having a U-shaped cross section. Thereby, when the high-pressure fluid is introduced into the seal groove 31f, the seal ring 35 can be effectively opened and adhered to the inner cylindrical surface of the variable-receiving hole 5a to improve the sealing property.
  • the sealing device L assisted by the high-pressure fluid is added, the gap leakage between the outer cylindrical surface of the plunger 37 and the inner cylindrical surface of the variable-capacity hole 5a can be reduced during the full-load operation, thereby improving the sealing property of the compression mechanism. Improve the energy efficiency of the compressor.
  • the scroll compressor is switched from the full capacity state to the partial capacity state, the supply of the high pressure fluid is cut off, and the seal ring 35 is appropriately retracted to also facilitate the smooth movement of the plunger 37 to the open position.
  • a varactor mechanism 2 according to a third embodiment of the present invention will now be described with reference to Figs.
  • the difference between the varactor mechanism 2 according to the third embodiment of the present invention and the varactor mechanism 2 according to the first embodiment of the present invention will be mainly described below.
  • the annular piston 31 serving as the actuating member of the actuating device takes the form of a split annular piston such that the plunger 37 is provided with respect to the annular piston
  • the radial flexibility and axial flexibility of 31 are thus adjustable.
  • the annular piston 31 may include a ring (piston body) 36, a fixing plate (fixing ring) 38, a fastening bolt 40, and an O-ring 32.
  • the fastening bolt 40 is adapted to fixedly couple the fixed plate 38 with the collar 36 to form the annular piston 31.
  • a receiving hole 38a adapted to receive a portion of the plunger 37 may be formed at the fixing plate 38.
  • the plunger 37 may include a plunger barrel portion 37a (see Fig. 11).
  • a receiving hole may be opened from one end in the axial direction of the plunger barrel portion 37a, and a flange portion 37b extending radially outward from the plunger barrel portion 37a is provided at one end of the axial direction (see Fig. 11).
  • the flange portion 37b is adapted to prevent the plunger 37 from coming off the annular piston 31.
  • An axial compensation spring (biasing member) 39 is provided, and the spring 39 can be received in the accommodating hole at the plunger 37.
  • the flange portion 37b of the plunger 37 is placed in the axial gap formed by the collar 36 and the fixed plate 38 and is surrounded by the collar 36.
  • the fixing plate 38 is sandwiched, and the plunger barrel portion 37a of the plunger 37 is inserted in the receiving hole 38a.
  • the spring 39 is placed in the accommodating hole at the plunger 37 and is preloaded so that one end (upper end) of the spring 39 abuts against the lower surface of the ring 36 and the other end (lower end) abuts against the plunger 37, so that the column
  • the plug 37 is biased toward the direction away from the annular piston 31.
  • the axial gap formed by the collar 36 and the fixed plate 38 is designed to be larger than the axial thickness of the flange portion 37b, and/or the inner diameter of the receiving hole 38a is designed to be larger than the plunger barrel portion.
  • the outer diameter of the 37a i.e., the plunger 37 and the fixed plate 38 are radially fitted with a large clearance.
  • the plunger 37 is adjustable in the radial direction, so that two states inserted in the respective variable-capacity holes 5a can be eliminated. Over-positioning problem between one or more plungers 37 and loops 36.
  • the plunger 37 in the axial direction between the plunger 37 (specifically, the flange portion 37b of the plunger 37) and the fixing plate 38 and the collar 36 (specifically, the axial gap formed by the collar 36 and the fixing plate 38)
  • a large clearance fit is employed, so the plunger 37 is adjustable in the axial direction.
  • the plunger 37 is always protruded toward the end of the movable scroll of the movable scroll 6 by the action of the spring 39, thereby The end of the plunger 37 is always in close contact with the end of the orbiting scroll of the movable scroll 6, whereby the end of the movable scroll of the plunger 37 and the movable scroll 6 is prevented from being abnormally operated, for example, while improving the sealing property. Mutual interference occurs in the state.
  • the plunger has the characteristics of radial flexibility and axial flexibility, so that over-positioning problems can be eliminated to reduce assembly difficulty and reduce component machining accuracy.
  • the end of the plunger is brought into contact with the end of the movable scroll, thereby facilitating the axial direction of the compression mechanism Sealing and also avoiding interference between the plunger and the movable scroll.
  • variable displacement cylinder 30 is integrally formed with the fixed scroll 5, in other words, the back surface of the fixed scroll 5 is integrally formed with a variable displacement cylinder Parts of body 30. As shown in FIG. 14, the annular groove G and the discharge hole PH are integrally formed on the back surface of the fixed scroll 5.
  • the cover covering the variable displacement cylinder may also be integrally formed, while in other examples, the cover may be separately formed and then the cover may be sealingly coupled to the variable displacement cylinder.
  • variable-capacity cylinder 30 is integrally formed with the fixed scroll 5
  • components for positioning and connecting the positioning pin and the bolt of the variable-capacity cylinder 30 can be reduced and the positioning problem is not considered, which is advantageous for processing and assembly. Especially suitable for application in mass production.
  • the varactor mechanism according to the invention allows for a number of different variants.
  • the actuating device of the varactor mechanism 2 employs a pressure passage 34 and a high pressure fluid as the drive portion.
  • the actuation device can be implemented in other suitable forms.
  • a solenoid device can be provided such that the movable plunger of the solenoid device drives a single actuator (annular piston).
  • the actuating member of the varactor mechanism 2 is embodied as an annular piston 31.
  • the actuators can be implemented in other suitable forms.
  • an arc-shaped segment piston in the form of a non-complete ring may be provided as a single actuator member, a single actuator member in a linear plate shape may be provided, or a single actuator member in a bent plate shape may be provided as long as a plurality of blocking members are provided
  • a single actuator member e.g., a plunger
  • bleed passage P is disposed outside the fixed vortex.
  • all of the bleed passages may be provided in a fixed vortex (original vortex). In this case, it is still possible to provide a single actuating device for a plurality of blocking members to achieve the technical effect of simultaneous operation of the plurality of blocking members.
  • the blocking member is embodied as a plunger 37.
  • the blocking member can be implemented in other suitable forms.
  • a valve plate and a valve seat may be provided as the blocking member, and each valve plate may be coupled to a single actuator member.
  • the sealing device L according to the second embodiment of the present invention and the radial and axial flexible structures according to the third embodiment of the present invention can be independent of other implementations.
  • the method (for example, the first embodiment) is implemented in a related configuration.
  • the sealing device L according to the second embodiment of the present invention may be implemented in a varactor having a plurality of blocking members and a plurality of corresponding actuator members, for example, radial and axial directions according to the third embodiment of the present invention.
  • the flexible structure can be implemented in a varactor having a single blocking member and a single actuator.

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Abstract

一种用于涡旋压缩机（1）的变容机构（2），涡旋压缩机（1）包括压缩机构，压缩机构包括限定一系列压缩腔的定涡旋（5）和动涡旋（6）。变容机构（2）包括：泄出通道（P），其适于将压缩腔中的中压压缩腔与低压区连通；阻塞构件，其适于选择性地打开和闭合泄出通道（P）；以及致动装置，其包括执行构件，阻塞构件连接至执行构件从而能够随着执行构件的动作而选择性地打开和闭合泄出通道（P）。阻塞构件为多个阻塞构件，执行构件为单个执行构件，多个阻塞构件连接于单个执行构件从而能够同时随着单个执行构件的动作而运动。这种变容机构能够可靠地实现多个阻塞构件的动作同步性。以及一种包括这种变容机构（2）的涡旋压缩机（1）。

Description

涡旋压缩机的变容机构及涡旋压缩机
本申请要求于2015年10月15日提交中国专利局、申请号为201510676945.X、发明名称为“涡旋压缩机的变容机构及涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及用于涡旋压缩机的变容机构和相关的涡旋压缩机，更具体地，涉及对变容机构的阻塞构件的动作同步性等方面做出改进的用于涡旋压缩机的变容机构和相关的涡旋压缩机。
背景技术
随着对高效性和节能性的要求越来越高，空调作为主要的能耗产品，高效、节能和舒适性是不断追求的目标。涡旋压缩机已逐渐朝向更大匹数和更高能效方向发展，容量可调节(变容)涡旋压缩机由于能够实现低负荷时的高能效并且具有高可靠性和低振动等特点，因而在容量可调节的空调系统等中的应用越来越广泛。
涡旋压缩机通常包括：壳体；包括动涡旋盘和定涡旋盘的压缩机构；包括马达、曲轴和防自转装置的驱动机构；包括主轴承座(上轴承座)的支承机构。动、定涡旋盘的型线均是涡旋形的，动涡旋盘相对于定涡旋盘偏心并且可以例如相差180度安装。这样，理论上动、定涡旋盘在轴向方向上会在若干条直线上接触(在横截面中则呈现为在若干个点处接触)。同时，涡旋体型线的端部与相应的涡旋体的底部相接触，由此在动、定涡旋盘之间形成一系列月牙形空间(即基元容积或压缩腔)。当动涡旋盘以定涡旋盘的中心为旋转中心并且以一定的旋转半径作无自转的回转平动时，外侧月牙形空间便会不断地向中心移动并且容积不断缩小，此时，该月牙形空间中的工作流体(例如制冷剂)被压缩而压力不断升高，直至该月牙形空间与中心排气孔连通而将高压工作流体排出压缩机构。
另一方面，在常规的容量可调节涡旋压缩机中，在涡旋盘开设与压缩腔连通的旁通变容孔，使得压缩腔与吸气区(或其它低压流体区域)连通，从而减小压缩腔的排量。由此，实现压缩机的部分负荷进而实现压缩机的容量调节。
然而，在常规的容量可调节涡旋压缩机中，当例如变容调节范围较大而需 要增加另一个或更多个辅助变容孔时，需要增加另一套或更多套变容致动机构，这导致变容结构与控制系统复杂且可靠性下降。另外，对于涡旋体型线对称的对称压缩机构而言，设置多套变容致动机构(例如多个活塞)易于使多套变容致动机构之间的动作不同步，这导致泵体(压缩机构)受力不均，从而导致功耗增加或泄漏。
另外，在常规的容量可调节涡旋压缩机中，尤其对于高压侧涡旋压缩机而言，通常需要在定涡旋盘上开设泄出回流通道。由此，一方面，受定涡旋盘的结构影响泄出回流通道的横截面积受到限制，因此对工作流体的泄出产生阻力从而造成功耗增加，而另一方面，泄出回流通道需要在定涡旋盘中径向延伸而直径小，因此造成加工困难。
另外，在常规的容量可调节涡旋压缩机中，存在变容活塞或柱塞的运动导向精度低、变容活塞或柱塞与变容孔端面相互碰撞等情况从而影响变容活塞或柱塞的动作可靠性，此外，当增大变容活塞或柱塞与变容孔的配合间隙以期改进动作可靠性时，又会导致工作流体泄漏。
这里，应当指出的是，本部分中所提供的技术内容旨在有助于本领域技术人员对本发明的理解，而不一定构成现有技术。
发明内容
在本部分中提供本发明的总概要，而不是本发明完全范围或本发明所有特征的全面公开。
本发明的一个目的是提供一种能够可靠地实现多个阻塞构件的动作同步性的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种整体结构简单并且能够提高容量调节切换的可靠性的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种能够避免压缩机构气体力不均而造成功耗增加或工作流体泄漏的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种能够减小泄出阻力以及减小功耗的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种能够降低加工难度和加工成本的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种能够提高压缩机构的密封性进而提高压缩机的能效的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种允许阻塞构件具备径向柔性和/或轴向柔性从而能够消除过定位问题以减小装配难度和降低零部件加工精度的用于涡旋压缩机的变容机构。
本发明的另一目的是提供一种允许阻塞构件具备径向柔性和/或轴向柔性从而有利于压缩机构的轴向密封并且也避免阻塞构件与动涡旋相互干涉的用于涡旋压缩机的变容机构。
本发明的其它目的在于提供一种包括如上所述的变容机构的涡旋压缩机。
为了实现上述目的中的一个或多个，根据本发明的一个方面，提供一种用于涡旋压缩机的变容机构，所述涡旋压缩机包括适于对工作流体进行压缩的压缩机构，所述压缩机构包括定涡旋和动涡旋从而在所述定涡旋与所述动涡旋之间限定一系列压缩腔。所述变容机构包括：泄出通道，所述泄出通道适于将所述压缩腔中的中压压缩腔与低压区连通；阻塞构件，所述阻塞构件适于选择性地打开和闭合所述泄出通道；以及致动装置，所述致动装置包括执行构件，所述阻塞构件连接至所述执行构件从而能够随着所述执行构件的动作而选择性地打开和闭合所述泄出通道。所述阻塞构件为多个阻塞构件，所述执行构件为单个执行构件，所述多个阻塞构件连接于所述单个执行构件从而能够同时地随着所述单个执行构件的动作而运动。
优选地，所述阻塞构件为柱塞。
优选地，多个所述柱塞的一端连接在所述执行构件的下表面上。
优选地，所述致动装置还包括驱动部，所述驱动部包括压力通道，所述压力通道能够被选择性地供给高压流体和低压流体；以及
在所述压力通道被供给高压流体的情况下，经由所述压力通道供给的高压流体推压所述执行构件从而致动所述执行构件。
优选地，还包括与所述定涡旋的定涡旋端板连接的变容缸体。
优选地，在所述变容缸体中形成有朝向所述定涡旋端板开口的环形槽道，所述执行构件布置在所述环形槽道中。
优选地，在所述变容缸体中形成有连通孔，所述压力通道经由所述连通孔 与所述环形槽道连通从而能够将高压流体引入至所述环形槽道的上部以便驱动所述执行构件。
优选地，所述泄出通道包括：形成在所述定涡旋端板并且能够与所述中压压缩腔连通的多个第一通道；以及设置在所述变容缸体并且能够与所述第一通道和低压区连通的第二通道。
优选地，每个所述第一通道包括相互连通的变容孔和泄出孔，所述变容孔形成在所述定涡旋端板的下部从而能够与所述中压压缩腔连通，所述泄出孔形成在所述定涡旋端板的上部；以及
所述柱塞适于选择性地打开和闭合所述变容孔。
优选地，还包括导向孔，所述导向孔形成在所述定涡旋端板的上部并且能够与所述变容孔相通，从而所述导向孔与所述变容孔一起限定所述柱塞适于在其中移行的移行通路。
优选地，所述泄出孔设置在所述变容孔的上侧，所述泄出孔为盲孔，所述泄出孔与所述导向孔部分重叠，并通过所述导向孔与所述变容孔连通。
优选地，所述第二通道由所述定涡旋端板、所述变容缸体和所述执行构件限定在所述环形槽道中。
优选地，所述涡旋压缩机还包括吸气管；
所述压缩机构还包括吸气腔；以及
所述变容缸体设置有进气孔道和排放孔，所述进气孔道与所述吸气管和吸气腔连通从而所述进气孔道与所述吸气管构成所述低压区，并且所述第二通道经由所述排放孔与所述进气孔道连通。
优选地，还包括安装在所述定涡旋端板与所述执行构件之间的偏置装置，所述偏置装置包括适于将所述执行构件朝向离开所述定涡旋端板的方向偏置的偏置构件。
优选地，还包括适于使所述柱塞相对于所述变容孔密封的密封装置。
优选地，所述密封装置包括：设置在所述柱塞的外周面处的密封槽；布置在所述密封槽中的密封圈；以及设置成穿过所述柱塞和所述执行构件的引压通道。
优选地，所述引压通道构造成能够将经由所述压力通道供给的高压流体引 入至所述密封槽，从而迫使所述密封圈张开并且紧贴于所述变容孔的内圆柱面。
优选地，所述执行构件为环形活塞。
优选地，所述环形活塞包括固定地连接在一起的活塞本体和固定环，在所述固定环处设置有接纳孔；
所述柱塞包括柱塞筒部和从所述柱塞筒部的一端径向向外延伸的凸缘部；以及
所述柱塞连接至所述环形活塞，使得所述凸缘部置于由所述活塞本体与所述固定环形成的轴向间隙中并且所述柱塞筒部插在所述接纳孔中。
优选地，所述轴向间隙大于所述凸缘部的轴向厚度；并且/或者
所述接纳孔的内径设计为大于所述柱塞筒部的外径。
优选地，在所述柱塞筒部的设置有所述凸缘部的一端形成有容置孔；以及
设置有偏压构件，所述偏压构件容置在所述容置孔中并且被预加载，使得所述偏压构件的一端抵接所述活塞本体而另一端抵接所述柱塞筒部，从而所述柱塞朝向离开所述环形活塞的方向被偏压。
优选地，所述变容缸体与所述定涡旋一体地形成。
为了实现上述目的中的一个或多个，根据本发明的另一方面，提供一种涡旋压缩机。所述涡旋压缩机包括如上所述的变容机构。
根据本发明，在变容机构中采用单个致动装置(例如单个执行机构比如单个环形活塞)，从而实现多个阻塞构件(例如多个柱塞)的同时(同步)动作。因此，对于需要开设两个或更多个变容孔的压缩机而言，可以通过单套控制结构(致动结构)进行控制，从而整体结构简单并且可以提高容量调节切换的可靠性。特别地，对于采用对称型线的涡旋压缩机而言，可以避免由于变容孔不同时打开或闭合而使得压缩机构气体力不均(尤其是动涡旋受力不平衡)而造成功耗增加或工作流体泄漏。
另外，根据本发明，由于变容机构的泄出通道的至少一部分由定涡旋背面(上表面)、环形活塞以及变容缸体限定(换言之，不是在定涡旋中开设全部泄出通道)，因此泄出通道的有效面积不受限于定涡旋结构，从而可以减小泄出阻力、减小功耗并且有利于提高具有变容功能的涡旋压缩机的性能。另一方 面，由于无需在定涡旋中加工径向工作流体泄出通道，因此也降低了加工难度和加工成本。
另外，根据本发明，由于设置导向孔并且导向孔与变容孔一起限定出阻塞构件(例如柱塞)适于在其中移行的移行通路，因此可以确保柱塞动作可靠性进而确保环形活塞动作可靠性。同时，也可以进一步缩小柱塞与变容孔之间的径向配合间隙，这有利于提高全容量运转状态下压缩机构的密封性。
附图说明
通过以下参照附图对本发明实施方式的详细描述，本发明的上述以及其它的目的、特征和优点将更为清楚，在附图中：
图1是示出包括根据本发明第一实施方式的变容机构的涡旋压缩机的纵剖图；
图2是示出根据本发明第一实施方式的变容机构的分解立体图；
图3是示出根据本发明第一实施方式的定涡旋盘的顶视图和立体图；
图4是主要示出根据本发明第一实施方式的环形活塞的立体图；
图5是示出根据本发明第一实施方式的处于非变容状态的变容机构的剖视图；
图6是示出根据本发明第一实施方式的处于变容状态的变容机构的剖视图；
图7是示出根据本发明第二实施方式的环形活塞和柱塞的立体图；
图8是示出根据本发明第二实施方式的处于非变容状态的变容机构的剖视图；
图9是示出包括根据本发明第三实施方式的变容机构的涡旋压缩机的纵剖图；
图10是示出本发明第三实施方式的变容机构的分解立体图；
图11是主要示出本发明第三实施方式的环形活塞的组装立体图和分解立体图；
图12是示出根据本发明第三实施方式的处于非变容状态的变容机构的剖视图；
图13是示出根据本发明第三实施方式的处于变容状态的变容机构的剖视 图；以及
图14是示出根据本发明第四实施方式的定涡旋的顶视图和立体图。
附图标记说明：
1－涡旋压缩机；2－变容机构；3－驱动机构；4－马达；5－定涡旋,5a－变容孔；5b－泄出孔；5c－导向孔；5d－安装孔；6－动涡旋；7－吸气管；8－壳体本体；9－主轴承座；10－防自转装置；12－驱动轴承；13－曲轴；14－主轴承；15－排气管；18－转子；19－定子；22－副轴承座；24－副轴承；25－止推板；29－底盖；30－变容缸体；30a－连通孔；31－环形活塞；31c、d－凹槽；31e－引压通道；31f－密封槽；32－O型密封圈；33－偏置构件；34－压力通道；35－密封圈；36－活塞本体；37－柱塞；37a－柱塞筒部；37b－凸缘部；37c－柱塞的末端；38－固定板；38a－接纳孔；39－轴向补偿弹簧；40－紧固螺栓；G－环形槽道；L－密封装置；P－泄出通道；P1－第一通道；P2－第二通道；PH－排放孔；U－施压通道；S1－吸气腔；S2－进气孔道。
具体实施方式
下面参照附图、借助示例性实施方式对本发明进行详细描述。对本发明的以下详细描述仅仅是出于说明目的，而绝不是对本发明及其应用或用途的限制。
首先，参照图1至图6描述根据本发明第一实施方式的涡旋压缩机1以及该涡旋压缩机1所包括的变容机构2。
涡旋压缩机1可以包括：壳体组件；压缩机构；驱动机构3；支承机构；吸气管7；以及排气管15。
在图示的示例中，涡旋压缩机1示出为全封闭式高压侧涡旋压缩机。然而，应当理解，本发明并不限于全封闭式高压侧涡旋压缩机，而是也可以应用于例如全封闭式低压侧涡旋压缩机和半封闭式涡旋压缩机。
壳体组件可以包括壳体本体8、顶盖和底盖29，壳体组件可以限定密闭的空间用于容纳例如压缩机构和驱动机构3。
压缩机构可以包括定涡旋5、动涡旋6和防自转装置10。定涡旋5可以包括端板和定涡卷。用于从压缩机构排出经过压缩的高压工作流体的排出口可以设置在定涡旋端板的大致中心处。动涡旋6可以包括端板和动涡卷。用于容纳 曲轴(驱动轴)的偏心销的毂部可以设置成从动涡旋端板的下表面突出。定涡卷和动涡卷可以啮合地接合，从而在定涡旋5与动涡旋6之间限定一系列压缩腔(工作腔)。防自转装置10可以实施为欧氏环(十字滑环)，用于限制动涡旋6的自转同时允许动涡旋6相对于定涡旋5进行回转平动运动。
驱动机构3可以包括：由定子19和转子18构成的马达4；以及曲轴13。曲轴13可以设置成能够与转子18一体地旋转，并且曲轴13可以在上端处包括适于驱动动涡旋6的偏心销。
支承机构可以包括主轴承座9和副轴承座22。主轴承座9适于轴向地支承动涡旋6(具体为支承动涡旋端板)。在主轴承座9处还可以设置有主轴承14(例如实施为滑动轴承)，主轴承14适于支承曲轴13的上部。在一些示例中，在动涡旋6的毂部与曲轴13的偏心销之间可以设置有驱动轴承12(例如实施为滑动轴承)，由此曲轴13的偏心销经由驱动轴承12而驱动动涡旋6的毂部进而驱动动涡旋6的回转平动。在副轴承座22处可以设置副轴承24(例如实施为滚动轴承)和止推板25，用于对曲轴13的下部进行径向和轴向支承。
吸气管7可以连接至定涡旋5，从而来自外部工作回路的低压工作流体可以经由吸气管7流动至压缩机构以进行压缩。排气管15可以连接至壳体组件的壳体本体8，从而经过压缩机构压缩的高压工作流体可以经由排气管15流动至外部工作回路。
下面参照图1简单地描述涡旋压缩机1的工作过程。在马达4通电的情况下，转子18与曲轴13一体地旋转，从而曲轴13的偏心销经由驱动轴承12而驱动动涡旋6的毂部进而驱动动涡旋6进行回转平动运动。与此同时，工作流体经由吸气管7进入压缩机构的吸气腔S1(参见图5)，随着动涡旋6的继续回转平动该吸气腔S1闭合而成为压缩腔并且向中心移动而容积不断缩小，从而该压缩腔中的工作流体被压缩而压力升高。当达到预定压缩比时，工作流体从定涡旋5的中心排出口排出而进入由壳体组件所限定的密闭空间的上部，然后经过定涡旋5和主轴承座9中所设置的流动通道而进入密闭空间的中下部，然后经由排气管15排出涡旋压缩机1。
根据本发明第一实施方式，在涡旋压缩机1中设置变容机构2。
如图2所示，变容机构2可以包括：泄出通道(旁通通道)P；阻塞构件； 以及致动装置。
泄出通道P适于将压缩机构的特定压缩腔(例如压力介于低压吸气腔S1的压力与待排放或正在排放的中心高压压缩腔的压力之间的中压压缩腔)与压缩机构的吸气腔S1或其它低压流体区域(低压区)连通。泄出通道P可以包括形成在定涡旋端板处的第一通道P1(参见图6)以及由定涡旋端板、变容机构2的变容缸体30和致动装置的执行构件(例如环形活塞31)限定的第二通道P2(参见图6)。
第一通道P1可以包括：形成在定涡旋端板的下部从而适于与特定压缩腔连通的变容孔5a；以及形成在定涡旋端板的上部从而其下端适于与变容孔5a连通(例如经由下文将做描述的导向孔5c)而其上端适于与第二通道P2连通的泄出孔5b。
在优选的示例中，还可以设置导向孔5c。导向孔5c可以形成在定涡旋端板的上部。导向孔5c的下端可以与变容孔5a的上端相通，从而导向孔5c与变容孔5a一起限定阻塞构件适于在其中移行的移行通路。导向孔5c的内径可以与变容孔5a的内径一致，从而导向孔5c与变容孔5a能够平滑地衔接以形成内径一致的移行通路，这有利于对柱塞进行稳定地引导从而使柱塞的动作更加平稳和可靠。
在优选的示例中，对于每个变容孔5a，可以设置有与之相连通的泄出孔5b，所述泄出孔5b设置在所述变容孔5a的上侧，优选地，在所述变容孔5a的两侧设置有两个泄出孔5b。所述泄出孔5b可以设置在导向孔5c的侧部，所述泄出孔5b为盲孔，其与所述导向孔5c部分重叠，并通过所述导向孔5c与所述变容孔5a连通。通过设置成对的泄出孔5b，可以有效地减小泄出阻力。
阻塞构件可以实施为呈大致圆柱形状的柱塞37。柱塞37适于在由导向孔5c与变容孔5a限定的移行通路中移行，从而可以处于闭合位置和打开位置。在闭合位置处，柱塞37的末端(下端)37c位于泄出孔5b的下端以下(例如，如图5所示，柱塞37的末端37c抵接动涡旋6的动涡卷的末端即上端)，由此阻塞第一通道P1而阻止中压工作流体从特定压缩腔(中压压缩腔)泄出至低压流体区域。在打开位置处，柱塞37的末端37c位于泄出孔5b的下端以上(如图6所示)，由此打开第一通道P1而允许中压工作流体从特定压缩腔经由变容 孔5a和泄出孔5b(即第一通道P1)以及第二通道P2而泄出至低压流体区域。
致动装置可以包括执行构件和驱动部。执行构件可以实施为环形活塞31。柱塞37的上端可以例如固定地连接至环形活塞31的下表面。
在优选的示例中，在变容机构2中可以设置变容缸体30。变容缸体30可以呈大致环体。在变容缸体30中可以形成有朝下开口(即朝向压缩机构开口)的环形槽道G(参见图5)，环形活塞31可以贴合地布置在环形槽道G中。在一些示例中，可以在环形活塞31的径向内周面和/或径向外周面处设置凹槽31c、31d(参见图4)，O型密封圈32可以布置在凹槽中，使得环形活塞31密封地接合至变容缸体30的环形槽道G。
在优选的示例中，驱动部可以包括压力通道34和供给至压力通道34的高压流体。压力通道34的下端可以连接至设置在变容缸体30的上部处的连通孔30a(参见图2)，从而压力通道34可以经由连通孔30a与环形槽道G(具体为环形槽道G的上部)连通。压力通道34可以选择性地被供给高压流体和低压流体。在压力通道34被供给高压流体的情况下，经由压力通道34供给的高压流体将环形活塞31向下推压，从而将与环形活塞31固定地连接的柱塞37向下推压而处于闭合位置。在一些示例中，供给至压力通道34的高压流体可以是经过涡旋压缩机1的压缩机构压缩的高压工作流体。
在优选的示例中，可以在变容缸体30处设置有排放孔PH(参见图5)，第二通道P2(具体为构成第二通道P2的环形槽道G的下部)可以经由排放孔PH与低压流体区域(例如下文将做描述的变容缸体30的进气孔道)连通。
在优选的示例中，变容缸体30还可以设置有进气孔道S2(参见图6)，从而吸气管7的下端可以连接至进气孔道S2的上端，而进气孔道S2的下端可以连接至设置在定涡旋5处的吸气腔S1(变容缸体30的进气孔道S2与定涡旋5的吸气腔S1可以一起限定所谓的吸气区或低压流体区域)。
由此，当在环形活塞31布置在环形槽道G中的状态下将变容缸体30(例如密封地且固定地)连接至定涡旋端板的上表面时，一方面，由定涡旋端板的上表面和环形活塞31的下表面在变容缸体30的环形槽道G的下部限定出泄出通道P的第二通道P2，而另一方面，由环形活塞31的上表面在变容缸体30的环形槽道G的上部限定出施压通道U(参见图5)。
在优选的示例中，还可以设置偏置装置。偏置装置可以包括偏置构件33(例如实施为弹簧比如螺旋弹簧)以及设置在定涡旋端板处的适于安装偏置构件33的安装孔5d。偏置构件33适于将环形活塞31向上推压。由此，在涡旋压缩机1需要执行变容运转而例如使压力通道34被供给低压流体时，偏置构件33能够将环形活塞31连同柱塞37推压成使得柱塞37处于打开位置。这里，应当指出，可以省略偏置装置，在这种情况下，借助中压压缩腔与低压流体区域之间的压力差将柱塞37连同环形活塞31向上推压。
根据本发明第一实施方式，可以设置两个或更多个变容孔5a，并且相应地，可以设置连接至环形活塞31的两个或更多个柱塞37，以便实现较大的变容调节范围。
特别地，根据本发明第一实施方式，设置用于两个或更多个阻塞构件(柱塞37)的单个致动装置(单个执行构件比如单个环形活塞31)，使得两个或更多个柱塞37同时地随着单个环形活塞31的运动而运动。
下面描述根据本发明第一实施方式的涡旋压缩机1的变容机构2的工作过程。
当涡旋压缩机1需要以非变容(全容量)状态运转时，如图5所示，将高压流体供给至致动装置的驱动部/压力通道34(例如，使压力通道34选择性地与涡旋压缩机1的高压排气侧连通)。由此，经由压力通道34供给的高压流体(例如克服偏置构件33的偏置力)将环形活塞31向下推压(此时，由环形活塞31的上表面在变容缸体30的环形槽道G的上部限定出施压通道)，从而同时地将与环形活塞31固定地连接的多个柱塞37向下推压而处于闭合位置。由此，柱塞37的末端37c可以抵接动涡旋6的动涡卷的末端以实现(中压)压缩腔的轴向密封，同时，柱塞37的的外周面(圆柱面)与变容孔5a配合以实现(中压)压缩腔的径向密封。由此，阻塞第一通道的变容孔5a而阻止中压工作流体从特定压缩腔(中压压缩腔)泄出至低压流体区域。
当涡旋压缩机1需要以变容(部分容量/负荷)状态运转时，如图6所示，将低压流体供给至致动装置的压力通道34(例如，使压力通道34选择性地与涡旋压缩机1的低压吸气侧连通)。由此，例如通过偏置构件33的偏置力并且/或者借助(中压)压缩腔的中压而能够将环形活塞31以及多个柱塞37向上 推压成使得多个柱塞37同时地处于打开位置。由此，打开第一通道的变容孔5a而允许中压工作流体从特定压缩腔经由变容孔5a和泄出孔5b(即第一通道P1)和第二通道P2而泄出至低压流体区域。由此，如同改变型线的终点，从而在排气脱啮点不变的情况下通过缩短型线长度(即提前型线的终点)而减小吸气量与内容积比(压缩比)以实现涡旋压缩机1的容量调节。
根据本发明第一实施方式的涡旋压缩机及其变容机构，至少可以获得如下有益效果。
在变容机构中采用单个致动装置(例如单个执行机构比如单个环形活塞)，从而实现多个阻塞构件(例如多个柱塞)的同时(同步)动作。因此，对于需要开设两个或更多个变容孔的压缩机而言，可以通过单套控制结构(致动结构)进行控制，从而整体结构简单并且可以提高容量调节切换的可靠性。特别地，对于采用对称型线的涡旋压缩机而言，可以避免由于变容孔不同时打开或闭合而使得压缩机构气体力不均(尤其是动涡旋受力不平衡)而造成功耗增加或工作流体泄漏。
另外，由于变容机构的泄出通道的至少一部分由定涡旋背面(上表面)、环形活塞以及变容缸体限定(换言之，不是在定涡旋中开设全部泄出通道)，因此泄出通道的有效面积不受限于定涡旋结构，从而可以减小泄出阻力、减小功耗并且有利于提高具有变容功能的涡旋压缩机的性能。另一方面，由于无需在定涡旋中加工径向工作流体泄出通道，因此也降低了加工难度和加工成本。
另外，由于设置导向孔5c并且导向孔5c与变容孔5a一起限定出阻塞构件(例如柱塞)适于在其中移行的移行通路，因此可以确保柱塞动作可靠性进而确保环形活塞动作可靠性。同时，也可以进一步缩小柱塞37与变容孔5a之间的径向配合间隙，这有利于提高全容量运转状态下压缩机构的密封性。
下面参照图7和图8描述根据本发明第二实施方式的变容机构2。
出于简洁，下文将主要描述根据本发明第二实施方式的变容机构2与根据本发明第一实施方式的变容机构2的不同之处。
与第一实施方式相比，在根据第二实施方式的变容机构2中，为柱塞37增设密封装置L。密封装置L可以包括：设置在柱塞37的外周面处的密封槽31f；适于布置在密封槽31f中的密封圈35；以及设置在柱塞37和环形活塞31 中的引压通道31e。引压通道31e可以包括轴向通道，轴向通道轴向地贯穿环形活塞31从而轴向通道的一端(上端)开口于环形活塞31的上表面。引压通道31e还可以包括一个或更多个径向通道，径向通道从轴向通道的下端延伸至密封槽31f。由此，当涡旋压缩机1在全容量状态下运转时，从压力通道34引入的高压流体经由施压通道而进入引压通道31e进而进入密封槽31f，从而迫使密封圈35张开并且紧贴于定涡旋5处的变容孔5a的内圆柱面。
在一些示例中，密封圈35可以实施为具有U形横截面的、U形截面的开口朝内的密封圈。由此，当高压流体引入至密封槽31f时，可以有效地使密封圈35张开并且紧贴于变容孔5a的内圆柱面从而提高密封性。
根据本发明第二实施方式，除了上文所描述的与本发明第一实施方式相关联的有益效果之外，还可以获得如下有益效果。
由于增设由高压流体辅助的密封装置L，因此在全容量运转时可以减小柱塞37的外圆柱面与变容孔5a的内圆柱面之间的间隙泄漏，从而提高压缩机构的密封性进而提高压缩机的能效。另一方面，当使涡旋压缩机从全容量状态切换至部分容量状态时，切断高压流体的供给，密封圈35适当地回缩从而也有助于柱塞37顺利地移行至打开位置。
下面参照图9至图13描述根据本发明第三实施方式的变容机构2。
出于简洁，下文将主要描述根据本发明第三实施方式的变容机构2与根据本发明第一实施方式的变容机构2的不同之处。
与第一实施方式相比，在根据第三实施方式的变容机构2中，用作致动装置的执行构件的环形活塞31采用分体式环形活塞的形式，使得柱塞37具备相对于环形活塞31的径向柔性和轴向柔性从而具备可调节特点。
如图11所示，环形活塞31可以包括环圈(活塞本体)36、固定板(固定环)38、紧固螺栓40以及O型密封圈32。紧固螺栓40适于将固定板38与环圈36固定地连接在一起从而环形活塞31。在固定板38处可以开设适于接纳柱塞37的一部分的接纳孔38a。
柱塞37可以包括柱塞筒部37a(参见图11)。可以从柱塞筒部37a的轴向一端开设有容置孔，并且在该轴向一端处设置有从柱塞筒部37a径向向外延伸的凸缘部37b(参见图11)。凸缘部37b适于阻止柱塞37脱离环形活塞31。
设置有轴向补偿弹簧(偏压构件)39，弹簧39可以容置在柱塞37处的容置孔中。
如图12所示，在环形活塞31与柱塞37组装在一起的状态下，柱塞37的凸缘部37b置于由环圈36与固定板38形成的轴向间隙中并且被环圈36和固定板38夹在中间，并且柱塞37的柱塞筒部37a插在接纳孔38a中。同时，弹簧39置于柱塞37处的容置孔中并且被预加载，从而弹簧39的一端(上端)抵接环圈36的下表面而另一端(下端)抵接柱塞37，使得柱塞37朝向离开环形活塞31的方向而被偏压。
特别地，根据第三实施方式，由环圈36与固定板38形成的轴向间隙设计为大于凸缘部37b的轴向厚度，并且/或者，接纳孔38a的内径设计为大于柱塞筒部37a的外径(亦即，柱塞37与固定板38之间在径向上采用较大间隙配合)。换言之，在环形活塞31与柱塞37组装在一起的状态下，允许柱塞37相对于环形活塞31轴向移位，并且/或者，允许柱塞37相对于环形活塞31径向移位。
根据本发明第三实施方式，除了上文所描述的与本发明第一实施方式相关联的有益效果之外，还可以获得如下有益效果。
一方面，由于柱塞37与固定板38之间在径向上采用较大间隙配合，因此柱塞37在径向上是可调节的，从而可以消除在插入在各自的变容孔5a的状态下两个或更多个柱塞37与环圈36之间的过定位问题。另一方面，由于柱塞37(具体为柱塞37的凸缘部37b)与固定板38和环圈36(具体为由环圈36与固定板38形成的轴向间隙)之间在轴向上采用较大间隙配合，因此柱塞37在轴向上是可调节的。特别地，由于在柱塞37与环圈36之间设置有轴向补偿弹簧39，因此在弹簧39的作用下，总使柱塞37朝向动涡旋6的动涡卷的末端突出，从而使柱塞37的末端总与动涡旋6的动涡卷的末端紧贴，由此，在提高密封性的同时，也避免柱塞37与动涡旋6的动涡卷的末端例如在异常工作状态下发生相互干涉的情况。
总之，根据本发明第三实施方式，柱塞具备径向柔性和轴向柔性特点，从而可以消除过定位问题以减小装配难度和降低零部件加工精度。另外，在弹簧的作用下，使得柱塞的末端与动涡卷的末端贴合，因此有利于压缩机构的轴向 密封并且也避免柱塞与动涡旋相互干涉的情况。
下面参照图14描述根据本发明第四实施方式的变容机构2。
出于简洁，下文将主要描述根据本发明第四实施方式的变容机构2与根据本发明第一实施方式的变容机构2的不同之处。
与第一实施方式相比，在根据第四实施方式的变容机构2中，变容缸体30与定涡旋5一体地形成，换言之，定涡旋5的背面一体地形成有变容缸体30的零部件。如图14所示，环形槽道G和排放孔PH一体地形成在定涡旋5的背面。
在一些示例中，还可以一体地形成覆盖在变容缸体上的盖体，而在其它示例中，则可以单独地形成盖体然后再将盖体密封地连接至变容缸体。
根据本发明第四实施方式，除了上文所描述的与本发明第一实施方式相关联的有益效果之外，还可以获得如下有益效果。
由于变容缸体30与定涡旋5一体地形成，因此可以减少用于定位和连接变容缸体30的定位销及螺栓等零部件并且不需考虑定位问题，这有利于加工与装配，尤其适于在批量生产中应用。
根据本发明的变容机构容许多种不同变型。
上文描述的是变容机构2的致动装置采用压力通道34以及高压流体作为驱动部。然而，可以构想，致动装置可以以其它合适形式实施。例如，可以设置螺线管装置，使得螺线管装置的活动柱塞驱动单个执行构件(环形活塞)。
上文描述的是变容机构2的执行构件实施为环形活塞31。然而，可以构想，执行构件可以以其它合适形式实施。例如，可以设置非完全圆环形式的弧形区段式活塞作为单个执行构件、可以设置呈直线板状的单个执行构件、或者可以设置呈弯折板状的单个执行构件，只要多个阻塞构件(例如柱塞)连接至该单个执行构件而使得多个阻塞构件同时地随着该单个执行构件的运动而运动即可。
上文描述的是泄出通道P的至少一部分设置在定涡旋的外部。然而，可以构想，泄出通道的全部可以设置定涡旋(原有定涡旋)中。在这种情况下，仍然可以设置用于多个阻塞构件的单个致动装置而实现多个阻塞构件同时动作的技术效果。
上文描述的是阻塞构件实施为柱塞37。然而，可以构想，阻塞构件可以以其它合适形式实施。例如，可以设置包括阀片和阀座作为阻塞构件，并且各个阀片可以与单个执行构件连接。
另外，可以理解，根据本发明第二实施方式的密封装置L以及根据本发明第三实施方式的径向和轴向柔性结构(即分体式环形活塞31和柱塞37)均可以独立于其它实施方式(例如第一实施方式)的相关结构而实施。例如，根据本发明第二实施方式的密封装置L可以在具有多个阻塞构件和多个相应的执行构件的变容机构中实施，又例如，根据本发明第三实施方式的径向和轴向柔性结构可以在具有单个阻塞构件和单个执行构件的变容机构中实施。
应当说明的是，在本申请文件中，方位术语“顶”、“底”、“上”和“下”等的使用仅仅出于便于描述的目的，而不应视为是限制性的。特别地，在本申请文件中，“上”和“下”一般是参照图1和图9所示的涡旋压缩机的定向来确定的。
还应当说明的是，在本申请文件中，诸如“第一”和“第二”等之类的关系术语仅仅用来将某个实体或操作与另一实体或操作区分开来，而不一定要求或者暗示这些实体或操作之间存在任何这种实际的关系或者顺序。另外，术语“包括”、“包含”或者其任何其它变体意在涵盖非排他性的包含，从而使得包括一系列要素的过程、方法、物品或者设备不仅包括那些要素，而且还包括没有明确列出的其它要素，或者是还包括为这种过程、方法、物品或者设备所固有的要素。
还应当说明的是，在本说明书中，每当提及“示例性实施方式”、“一些示例”、“其它示例”、“优选的示例”和“图示的示例”等时意味着针对该实施方式/示例描述的具体的特征、结构或特点包括在本发明的至少一个实施方式/示例中。这些用词在本说明书中不同地方的出现不一定都指代同一实施方式/示例。此外，当针对任一实施方式/示例描述具体的特征、结构或特点时，应当认为本领域技术人员也能够在所有所述实施方式/示例中的其它实施方式/示例中实现这种特征、结构或特点。
最后应说明的是：显然，上述实施方式/示例仅仅是为清楚地说明本发明所作的举例，而并非对实施方式/示例的限定。对于本领域技术人员来说，在 上述说明的基础上还可以做出其它不同形式的变化或变动。这里无需也无法对所有的实施方式/示例予以穷举。而由此所引申出的显而易见的变化或变动仍处于本发明的保护范围之中。

Claims (23)

  1. 一种用于涡旋压缩机(1)的变容机构(2)，所述涡旋压缩机(1)包括适于对工作流体进行压缩的压缩机构，所述压缩机构包括定涡旋(5)和动涡旋(6)从而在所述定涡旋(5)与所述动涡旋(6)之间限定一系列压缩腔，其特征在于，所述变容机构(2)包括：
    泄出通道(P)，所述泄出通道(P)适于将所述压缩腔中的中压压缩腔与低压区连通；
    阻塞构件，所述阻塞构件适于选择性地打开和闭合所述泄出通道(P)；以及
    致动装置，所述致动装置包括执行构件，所述阻塞构件连接至所述执行构件从而能够随着所述执行构件的动作而选择性地打开和闭合所述泄出通道(P)，
    其中，所述阻塞构件为多个阻塞构件，所述执行构件为单个执行构件，所述多个阻塞构件连接于所述单个执行构件从而能够同时地随着所述单个执行构件的动作而运动。
  2. 根据权利要求1所述的变容机构(2)，其特征在于，所述阻塞构件为柱塞(37)。
  3. 根据权利要求2所述的变容机构(2)，其特征在于，多个所述柱塞(37)的一端连接在所述执行构件的下表面上。
  4. 根据权利要求2所述的变容机构(2)，其特征在于：
    所述致动装置还包括驱动部，所述驱动部包括压力通道(34)，所述压力通道(34)能够被选择性地供给高压流体和低压流体；以及
    在所述压力通道(34)被供给高压流体的情况下，经由所述压力通道(34)供给的高压流体推压所述执行构件(31)从而致动所述执行构件(31)。
  5. 根据权利要求4所述的变容机构(2)，其特征在于，还包括与所述定涡旋(5)的定涡旋端板连接的变容缸体(30)。
  6. 根据权利要求5所述的变容机构(2)，其特征在于，在所述变容缸体(30)中形成有朝向所述定涡旋端板开口的环形槽道(G)，所述执行构件(31)布置在所述环形槽道(G)中。
  7. 根据权利要求6所述的变容机构(2)，其特征在于，在所述变容缸体(30)中形成有连通孔(30a)，所述压力通道(34)经由所述连通孔(30a)与所述环形槽道(G)连通从而能够将高压流体引入至所述环形槽道(G)的上部以便驱动所述执行构件(31)。
  8. 根据权利要求7所述的变容机构(2)，其特征在于，所述泄出通道(P)包括：形成在所述定涡旋端板并且能够与所述中压压缩腔连通的多个第一通道(P1)；以及设置在所述变容缸体(30)并且能够与所述第一通道(P1)和低压区连通的第二通道(P2)。
  9. 根据权利要求8所述的变容机构(2)，其特征在于：
    每个所述第一通道(P1)包括相互连通的变容孔(5a)和泄出孔(5b)，所述变容孔(5a)形成在所述定涡旋端板的下部从而能够与所述中压压缩腔连通，所述泄出孔(5b)形成在所述定涡旋端板的上部；以及
    所述柱塞(37)适于选择性地打开和闭合所述变容孔(5a)。
  10. 根据权利要求9所述的变容机构(2)，其特征在于，还包括导向孔(5c)，所述导向孔(5c)形成在所述定涡旋端板的上部并且能够与所述变容孔(5a)相通，从而所述导向孔(5c)与所述变容孔(5a)一起限定所述柱塞(37)适于在其中移行的移行通路。
  11. 根据权利要求10所述的变容机构(2)，其特征在于，所述泄出孔(5b) 设置在所述变容孔(5a)的上侧，所述泄出孔(5b)为盲孔，所述泄出孔(5b)与所述导向孔(5c)部分重叠，并通过所述导向孔(5c)与所述变容孔(5a)连通。
  12. 根据权利要求11所述的变容机构(2)，其特征在于，所述第二通道(P2)由所述定涡旋端板、所述变容缸体(30)和所述执行构件(31)限定在所述环形槽道(G)中。
  13. 根据权利要求12所述的变容机构(2)，其特征在于：
    所述涡旋压缩机还包括吸气管(7)；
    所述压缩机构还包括吸气腔(S1)；以及
    所述变容缸体(30)设置有进气孔道(S2)和排放孔(PH)，所述进气孔道(S2)与所述吸气管(7)和吸气腔(S1)连通从而所述进气孔道(S2)与所述吸气管(7)构成所述低压区，并且所述第二通道(P2)经由所述排放孔(PH)与所述进气孔道(S2)连通。
  14. 根据权利要求5至13中任一项所述的变容机构(2)，其特征在于，还包括安装在所述定涡旋端板与所述执行构件之间的偏置装置，所述偏置装置包括适于将所述执行构件(31)朝向离开所述定涡旋端板的方向偏置的偏置构件(33)。
  15. 根据权利要求9至13中任一项所述的变容机构(2)，其特征在于，还包括适于使所述柱塞(37)相对于所述变容孔(5a)密封的密封装置(L)。
  16. 根据权利要求15所述的变容机构(2)，其特征在于，所述密封装置(L)包括：设置在所述柱塞(37)的外周面处的密封槽(31f)；布置在所述密封槽(31f)中的密封圈(35)；以及设置成穿过所述柱塞(37)和所述执行构件(31)的引压通道(31e)。
  17. 根据权利要求16所述的变容机构(2)，其特征在于，所述引压通道(31e)构造成能够将经由所述压力通道(34)供给的高压流体引入至所述密封槽(31f)，从而迫使所述密封圈(35)张开并且紧贴于所述变容孔(5a)的内圆柱面。
  18. 根据权利要求3至13中任一项所述的变容机构(2)，其特征在于：所述执行构件为环形活塞(31)。
  19. 根据权利要求18所述的变容机构(2)，其特征在于：
    所述环形活塞(31)包括固定地连接在一起的活塞本体(36)和固定环(38)，在所述固定环(38)处设置有接纳孔(38a)；
    所述柱塞(37)包括柱塞筒部(37a)和从所述柱塞筒部(37a)的一端径向向外延伸的凸缘部(37b)；以及
    所述柱塞(37)连接至所述环形活塞(31)，使得所述凸缘部(37b)置于由所述活塞本体(36)与所述固定环(38)形成的轴向间隙中并且所述柱塞筒部(37a)插在所述接纳孔(38a)中。
  20. 根据权利要求19所述的变容机构(2)，其特征在于：
    所述轴向间隙设计为大于所述凸缘部(37b)的轴向厚度；并且/或者
    所述接纳孔(38a)的内径大于所述柱塞筒部(37a)的外径。
  21. 根据权利要求20所述的变容机构(2)，其特征在于：
    在所述柱塞筒部(37a)的设置有所述凸缘部(37b)的一端形成有容置孔；以及
    设置有偏压构件(39)，所述偏压构件(39)容置在所述容置孔中并且被预加载，使得所述偏压构件(39)的一端抵接所述活塞本体(36)而另一端抵接所述柱塞筒部(37a)，从而所述柱塞(37)朝向离开所述环形活塞(31)的方向被偏压。
  22. 根据权利要求5所述的变容机构(2)，其特征在于，所述变容缸体(30)与所述定涡旋(5)一体地形成。
  23. 一种涡旋压缩机(1)，其特征在于，所述涡旋压缩机(1)包括根据权利要求1至22中任一项所述的所述变容机构(2)。
PCT/CN2016/100558 2015-10-15 2016-09-28 涡旋压缩机的变容机构及涡旋压缩机 Ceased WO2017063503A1 (zh)

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