WO2020238825A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2020238825A1
WO2020238825A1 PCT/CN2020/091986 CN2020091986W WO2020238825A1 WO 2020238825 A1 WO2020238825 A1 WO 2020238825A1 CN 2020091986 W CN2020091986 W CN 2020091986W WO 2020238825 A1 WO2020238825 A1 WO 2020238825A1
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WO
WIPO (PCT)
Prior art keywords
scroll
intermediate compression
compression chamber
end plate
fluid
Prior art date
Application number
PCT/CN2020/091986
Other languages
English (en)
French (fr)
Inventor
刘轩
张琼宇
Original Assignee
艾默生环境优化技术(苏州)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 CN201920765067.2U external-priority patent/CN210218102U/zh
Priority claimed from CN201910440249.7A external-priority patent/CN111980918B/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Priority to US17/614,261 priority Critical patent/US12000392B2/en
Priority to EP20812649.0A priority patent/EP3978754A4/en
Publication of WO2020238825A1 publication Critical patent/WO2020238825A1/zh

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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
    • F04C18/02—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
    • F04C28/10—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • 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
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • 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
    • 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
    • F04C28/14—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 rotating valves

Definitions

  • the present disclosure relates to the technical field of scroll compressors, and more specifically, to a scroll compressor with a variable volume ratio function.
  • Compressors may be used in application systems that require different pressures, such as air-conditioning systems and cold storage systems. Therefore, the discharge pressure of the compression chamber (the maximum pressure in the compression chamber) may be greater than the pressure required by the specific application system. Overcompression. In the case of overcompression, the fluid compressed to the discharge pressure will drop to the pressure required by the application system after being discharged from the compression chamber. Therefore, the compressor does unnecessary work, which will reduce the efficiency of the compressor.
  • VVR variable volume ratio
  • An object of one or more embodiments of the present disclosure is to provide a compressor in which a variable volume ratio mechanism is not restricted by the installation space and has a simple structure.
  • Another object of one or more embodiments of the present disclosure is to provide a compressor having a variable volume ratio mechanism suitable for a small displacement compressor provided with a fixed scroll hub.
  • Another object of one or more embodiments of the present disclosure is to provide a compressor that has a variable volume ratio mechanism that is highly compatible and can be implemented in a simple and quick manner.
  • Another object of one or more embodiments of the present disclosure is to provide a compressor that has a variable volume ratio mechanism that requires fewer new parts to be developed, and therefore has low development difficulty and high development speed.
  • Another object of one or more embodiments of the present disclosure is to provide a compressor that has a variable volume ratio mechanism that does not require a separate design, has no cover plate, and has a small leakage to operate reliably.
  • a scroll compressor including: a movable scroll including a movable scroll end plate and a movable scroll formed on one side of the movable scroll end plate And a fixed scroll, the fixed scroll includes a fixed scroll end plate and a fixed scroll formed on one side of the fixed scroll end plate, the fixed scroll and the movable scroll cooperate to be therebetween
  • a series of compression cavities are formed.
  • the series of compression cavities include a central compression cavity and an intermediate compression cavity located radially outside of the central compression cavity.
  • the intermediate compression cavity includes at least a set of a first intermediate compression cavity and a second intermediate compression cavity. Compression cavity; wherein, between the first intermediate compression cavity and the second intermediate compression cavity is provided with an optional fluid passage communicating with the exhaust area, the first intermediate compression cavity and the second intermediate compression cavity pass The fluid channel is directly connected.
  • the scroll compressor includes a main exhaust port and a sub-exhaust port provided at the fixed scroll end plate, the main exhaust port being in fluid communication with the central compression chamber And the auxiliary exhaust port shared by the first intermediate compression chamber and the second intermediate compression chamber is selectively in fluid communication with an exhaust area.
  • the fluid passage includes a first section connected to the first intermediate compression chamber, a second section connected to the second intermediate compression chamber, and a connection between the first section and the The connecting section of the second section.
  • the fluid channel is provided in the fixed scroll end plate, and the connecting section includes a first connecting section communicating with the first section and a second section communicating with the second section.
  • a connected second connecting section, the first connecting section and the second connecting section intersect, and the auxiliary exhaust port is connected to one of the first intermediate compression chamber and the second intermediate compression chamber Direct fluid communication.
  • the fluid passage is provided in the orbiting scroll end plate, and the connecting section is formed as a single section, and the auxiliary exhaust port is connected to the first intermediate compression chamber and the One of the second intermediate compression chambers is in direct fluid communication.
  • the connecting section has a first end penetrating the fixed scroll end plate or the movable scroll end plate, and a plug for preventing fluid leakage is provided at the first end.
  • the fluid channel is provided on at least one of the fixed scroll and the movable scroll.
  • the fluid channel includes a channel provided at the end surface of the free end of the fixed scroll and/or the movable scroll, and the channel extending from the channel is respectively connected to the first The first and second notches of the intermediate compression cavity and the second intermediate compression cavity.
  • the fixed scroll end plate is formed with an inner annular wall on the side opposite to the fixed scroll, and the main exhaust port and the auxiliary exhaust port are arranged in the inner annular wall.
  • the exhaust area is defined by the inner annular wall; and a variable volume ratio valve is provided at the secondary exhaust port, and the variable volume ratio valve allows fluid to flow from the first The intermediate compression chamber and the second intermediate compression chamber flow to the exhaust area and prevent fluid from flowing from the exhaust area to the first intermediate compression chamber and the second intermediate compression chamber.
  • variable volume ratio valve includes a single valve plate covering the variable volume ratio orifice and a valve stop controlling the maximum range of movement of the valve plate, and the valve plate includes a fixed portion and a single valve plate.
  • a movable part the movable part being able to move between an open position and a closed position with respect to the fixed part.
  • the compressor structure according to the present disclosure can not only not be restricted by the installation space but also can realize the VVR function in a simple structure.
  • Fig. 1 is a cross-sectional view schematically showing a compressor with a VVR function according to a first comparative example
  • FIG. 2 is a perspective view schematically showing the fixed scroll and the VVR valve of the compressor with VVR function according to the first comparative example
  • 3A is a perspective view schematically showing a fixed scroll and a VVR valve of a compressor with a VVR function according to a second comparative example
  • FIG. 3B shows in detail the VVR valve according to the second comparative example
  • Fig. 4 schematically shows the fixed scroll and the movable scroll of the compressor according to the first embodiment of the present disclosure
  • Fig. 5 schematically shows a plug installed in a transverse connecting section according to an embodiment of the present disclosure
  • FIG. 6 shows in detail a plug according to an embodiment of the present disclosure
  • Fig. 7 schematically shows a plug installed in a transverse connection section according to another embodiment of the present disclosure
  • FIG. 8 shows in detail a plug according to another embodiment of the present disclosure.
  • Fig. 9 schematically shows the fixed scroll of the compressor according to the second embodiment of the present disclosure.
  • Fig. 10 schematically shows a scroll mechanism of a compressor according to a second embodiment of the present disclosure
  • Fig. 11 schematically shows the fixed scroll of the compressor according to the third embodiment of the present disclosure
  • Fig. 12 schematically shows the movable scroll of the compressor according to the third embodiment of the present disclosure
  • Fig. 13 schematically shows a scroll mechanism of a compressor according to a third embodiment of the present disclosure.
  • 14A and 14B schematically show the discharge port arrangement of a compressor according to an embodiment of the present disclosure.
  • FIG. 1 is a cross-sectional view schematically showing the compressor with VVR function according to the first comparative example
  • Fig. 2 is A perspective view of a fixed scroll and a VVR valve of a compressor with a VVR function according to a first comparative example is schematically shown
  • FIGS. 3A and 3B schematically show a compressor with a VVR function according to a second comparative example The fixed scroll and VVR valve of the machine.
  • the compressor 1 includes a substantially closed casing 20.
  • the housing 20 may be composed of a substantially cylindrical body part 22, a top cover 24 provided at one end of the body part 22, and a bottom cover 26 provided at the other end of the body part 22.
  • a partition 30 is provided between the top cover 24 and the body portion 22 to partition the internal space of the housing 20 into a fluid suction chamber 21 and a fluid discharge chamber 23.
  • the space between the partition 30 and the top cover 24 constitutes a fluid discharge chamber 23, and the space between the partition 30, the body portion 22 and the bottom cover constitutes a fluid suction chamber 21.
  • An air inlet connector for sucking fluid is provided on one side of the fluid suction chamber 21, and an exhaust connector for discharging compressed fluid is provided on one side of the fluid discharge chamber 23.
  • the compression mechanism sucks fluid from the fluid suction chamber 21 of the housing 20 and compresses the fluid and discharges it into the fluid discharge chamber 23 of the housing 20.
  • the compression mechanism may include a fixed scroll 40 and a movable scroll 50, for example.
  • the movable scroll 50 includes an end plate 54 and a spiral scroll 56 formed on one side of the end plate.
  • the fixed scroll 40 includes an end plate 44 and a spiral scroll 46 formed on one side of the end plate.
  • the end plate 44 includes an exhaust port 42 formed at approximately the center of the end plate and located radially outside the exhaust port 42
  • the first variable volume ratio orifice 64 and the second variable volume ratio orifice 66 are provided in the housing 20.
  • the scroll 46 of the fixed scroll 40 and the scroll 56 of the movable scroll 50 mesh with each other to form a series of compression chambers in which the volume gradually decreases from the radial outer side to the radial inner side and the pressure increases.
  • the radially outermost compression chamber in the compression chamber has the smallest pressure
  • the radially innermost compression chamber that is, the central compression chamber C1 at the center of the scroll
  • the plurality of intermediate compression chambers between the inner positions have an intermediate pressure between the maximum pressure and the minimum pressure.
  • the exhaust port 42 is in fluid communication with the central compression chamber.
  • the fluid communication described in this section corresponds to direct fluid communication), and the first variable volume ratio orifice 64 and the second variable volume ratio orifice 66 are subdivided from the central compression chamber.
  • the two middle compression chambers C2 and C3 on both sides are in fluid communication.
  • a back pressure chamber 70 is provided on the side of the end plate 44 of the fixed scroll 40 opposite to the scroll 46. More specifically, an inner annular wall 43 and an outer annular wall 45 are formed on the end plate 44. The inner annular wall 43 is formed around the exhaust port 42.
  • the back pressure chamber 70 is constituted by a space surrounded by an end plate 44, an inner annular wall 43 and an outer annular wall 45, and is closed by a sealing assembly provided therein.
  • the back pressure chamber 70 is in fluid communication with one of the compression chambers between the movable scroll 50 and the fixed scroll 40 through an axially extending through hole (not shown) formed in the end plate 44, thereby forming a fixed
  • the force of the scroll 40 squeezing toward the movable scroll 50 can effectively press the fixed scroll 40 and the movable scroll 50 together by the pressure in the back pressure chamber 70.
  • a variable volume ratio valve 100 (hereinafter referred to as a VVR valve) is provided to prevent excessive compression of the working fluid.
  • the VVR valve 100 includes a valve plate 110, a valve plate 120, a valve holder 130, a pin 140 and a wave spring 150.
  • the valve plate 110 is provided with a first fluid through hole and a second fluid through hole at positions corresponding to the first variable volume ratio orifice 64 and the second variable volume ratio orifice 66, respectively.
  • a valve plate 120 is provided on the valve plate 110 to selectively open or close the fluid through hole.
  • the valve plate 120 has two symmetrical movable parts 126 and one fixed part 124.
  • the two movable parts 126 can be displaced relative to the fixed part 124 between an open position and a closed position.
  • a valve holder 130 is provided on the valve plate 120.
  • the pin 140 extends through pin holes formed in the valve plate, the valve plate, and the valve holder to circumferentially fix the valve plate 110, the valve plate 120, and the valve holder 130.
  • the wave spring 150 axially holds the valve plate, the valve plate, and the valve holder together.
  • the working fluid is sucked into the compression mechanism and compressed as it flows from the radially outermost position to the radially innermost position, and the compressed fluid is discharged through the exhaust port 42 to the inner ring
  • the exhaust area defined by the wall 43 is then exhausted to the exhaust chamber 23 via a one-way valve provided at the center of the partition 30.
  • the fluid can be discharged to the exhaust area through the VVR valve 100 before reaching the radially innermost position.
  • valve plate 120 when the pressure of the fluid in the compression chamber at the radial middle position is greater than the pressure of the fluid in the discharge chamber 23 (that is, excessive compression occurs), the pressure on the lower side of the valve plate 120 is greater than the pressure on the upper side, and the valve plate 120 is under pressure. It moves toward the open position under the differential action, allowing fluid to be discharged through the variable volume earlier than the orifices 64, 66 and the fluid through holes.
  • the valve plate 120 returns to the closed position under the action of the elastic restoring force and the pressure difference, thereby sealing the variable volume ratio hole ⁇ 64,66.
  • the back pressure chamber 70 in order to enable the back pressure chamber 70 to provide a stable and sufficient pressure to effectively prevent fluid leakage between the various compression chambers, it is necessary to ensure that the back pressure chamber 70 has sufficient space, so that the inner side of the annular wall 43 Space is very limited.
  • the space inside the annular wall 43 may only have a diameter of 20mm-30mm. In this case, it is difficult to fit the VVR valve 100 to the inside of the annular wall 43 to realize the compressor VVR function.
  • FIGS. 3A and 3B schematically show the fixed scroll and the VVR valve of the compressor with the VVR function according to the second comparative example.
  • the other configuration of the compressor is similar to that of the compressor according to the first comparative example.
  • the corresponding structure is basically the same.
  • the compressor according to the second comparative example uses the cover plate 220 to divide the exhaust area and the back pressure chamber into upper and lower parts, so that the installation space of the VVR valve is not limited by the size of the back pressure chamber as in the first comparative example.
  • FIG. 1 the cover plate 220 to divide the exhaust area and the back pressure chamber into upper and lower parts
  • the fixed scroll end plate 144 and the cover plate 220 are fastened together by a plurality of screws 210, wherein the fixed scroll end plate 144 is provided with a groove 208 on the opposite side of the scroll formation. 208 is formed around the exhaust port 202 and the variable volume ratio orifices 164, 166, thereby forming an exhaust area in the groove 208 (ie, the lower side of the cover plate 220).
  • Each variable volume ratio orifice 164, 166 is respectively provided with a corresponding VVR valve 200.
  • the VVR valve 200 allows fluid to flow from the compression chamber to the exhaust area, and prevents fluid from flowing from the exhaust area to the compression chamber.
  • the VVR valve 200 may include a valve plate 220 covering the variable volume ratio orifices 164 and 166 and a valve stop 230 that prevents the valve plate 220 from being excessively deformed.
  • the valve plate 220 has a movable part 226 and a fixed part 224, and the movable part 226 can be displaced relative to the fixed part 224 between an open position and a closed position.
  • the VVR valve 200 may be fixed to the valve fixing hole formed in the fixed scroll end plate 144 by a fastener 240 such as a screw.
  • a concave portion 222 is formed on the upper side of the cover plate 220, and the concave portion 222 is in fluid communication with the medium pressure cavity in the compression cavity through the medium pressure hole, and a sealing component may be provided in the concave portion 222 to form a back pressure cavity that provides axial sealing force to the fixed scroll .
  • a gasket 250 is provided between the cover plate 220 and the fixed scroll end plate 144.
  • the present inventors conceived an improved compressor structure, which not only can not be restricted by the installation space, but also can realize the VVR function in a simple structure.
  • the compressor according to the first embodiment of the present disclosure includes a fixed scroll 40A and a movable scroll 50A, similar to the fixed scroll 40 and the movable scroll 50 according to the first comparative example, the fixed scroll
  • the scroll 46 of the swirl 40A and the scroll 56 of the movable scroll 50A are meshed with each other to form a series of compression chambers in which the volume gradually decreases from the radial outside to the radial inside and the pressure increases.
  • the radially outermost compression chamber in the compression chamber has the smallest pressure
  • the radially innermost compression chamber that is, the central compression chamber at the center of the scroll, has the largest pressure, which is located between the radially outermost position and the innermost position.
  • the plurality of intermediate compression chambers between have an intermediate pressure between the maximum pressure and the minimum pressure.
  • the end plate 44A of the fixed scroll 40A is provided with a central exhaust port 42 and a variable volume orifice 64.
  • the central exhaust port 42 may be in fluid communication with the central compression chamber C1 in the compression chamber, and the variable volume orifice 64 may be in fluid communication with the first intermediate compression chamber C2 located radially outside the central compression chamber (right side in FIG. 4) .
  • a second intermediate compression cavity C3 is formed on the opposite side of the central compression cavity (ie, the left side in FIG. 4), and the second intermediate compression cavity C3 may be symmetrical to the first intermediate compression cavity C2 about the central compression cavity C1.
  • the intermediate compression chambers having approximately the same pressure and cavity volume during the operation of the compressor are referred to as a set of first and second intermediate compression chambers.
  • a group of intermediate compression chambers are exhausted at the same time to avoid over-compression or under-compression of a certain compression chamber caused by different exhaust at the same time, and to reduce the loss of equal volume compression of compressor.
  • the compression chamber is symmetrical with respect to the central compression chamber, and the pressure and volume in the two symmetrical compression chambers are basically the same, which can be used as a group of intermediate compression chambers.
  • the compressor according to the first embodiment of the present disclosure is provided with a fluid passage 300 between the first intermediate compression chamber C2 and the second intermediate compression chamber C3 to directly communicate the two compression chambers.
  • the fluid channel 300 may be formed in the end plate 54A of the movable scroll 50A, and the fluid channel 300 may include a first section 310, a second section 330 and a transverse connection section 320.
  • the first section 310 and the second section 330 may extend in the axial direction of the compressor and communicate with the first intermediate compression chamber C2 and the second intermediate compression chamber C3, respectively, and the transverse connection section 320 may extend along the axis of the compressor.
  • the fluid in the second intermediate compression chamber C3 can flow through the second axial section 330, the transverse connecting section 320, and the first axial section 310 to the first intermediate compression chamber C2 in sequence, and then can flow from The first intermediate compression chamber C2 is discharged to the exhaust area defined by the annular wall 43 through the variable volume orifice 64.
  • the transverse connection section 320 of the fluid channel 300 may be formed as a single section to reduce the clearance volume of the compressor.
  • first section 310 and the second section 330 extending in the axial direction of the compressor are described herein, it should be understood that the first section 310 and the second section 330 may also be slightly inclined along the In the direction of extension. Preferably, the first section 310 and the second section 330 extending axially are used to reduce the clearance volume of the compressor.
  • a VVR valve 200 may be provided on the variable volume orifice 64.
  • the VVR valve 200 may include a valve plate 220 covering the variable volume ratio orifice 64 and a valve stop 230 that prevents the valve plate 220 from being excessively deformed.
  • the valve disc 220 may have a movable portion 226 and a fixed portion 224. The movable portion 226 can be displaced relative to the fixed portion 224 between an open position and a closed position, wherein the valve disc 220 closes the variable volume hole in the closed position In the open position, the valve plate 220 opens the variable volume orifice 64 and allows fluid to flow from the first intermediate compression chamber C2 to the exhaust area defined by the annular wall 43.
  • the VVR valve 200 may be fixed to a valve fixing hole formed in the end plate 44A of the fixed scroll 40A by a fastener such as a screw.
  • the working fluid is sucked into the compression mechanism and compressed as it flows from the radially outermost position to the radially innermost position, and the compressed fluid passes through the exhaust
  • the air port 42 is discharged to the discharge area defined by the inner annular wall 43, and then discharged to the discharge chamber 23 through a one-way valve provided at the center of the partition 30.
  • the fluid can be discharged to the discharge area through the VVR valve 200 before reaching the radially innermost central compression chamber C1.
  • the lower side of the valve plate 220 when the pressure is greater than the upper pressure, the movable portion 226 of the valve plate 220 moves toward the open position under the action of the pressure difference, thereby allowing the fluid to pass through the variable volume ratio orifice 64 to be discharged from the intermediate compression chambers C2 and C3 to the discharge area in advance.
  • valve plate 220 When the pressure of the fluid in the first intermediate compression chamber C2 and the second intermediate compression chamber C3 is less than the pressure of the fluid in the discharge chamber 23, the valve plate 220 returns to the closed position under the action of the elastic restoring force and the pressure difference, so that the seal is variable Volume ratio orifice 64.
  • the compressor according to the first embodiment of the present disclosure exemplarily shows a case with a set of intermediate compression chambers C2, C3, in which only a single variable volume orifice 64 may be formed in the end plate 44A, and only A single valve plate with a single movable part can realize the selective opening and closing of the variable volume orifice 64, thereby greatly reducing the installation size of the VVR valve compared with the compressor according to the first comparative example, and avoiding the size It is limited to realize the VVR function.
  • the compressor according to the first embodiment of the present disclosure can avoid the use of additional cover plates 220, gaskets 250, and corresponding fasteners, reducing processing costs and zero The cost of components and prevent fluid leakage in the high-pressure exhaust area between the cover plate and the fixed scroll end plate.
  • the VVR valve 200 which has a simple structure and has been conceived by the inventor, is adopted according to the first embodiment disclosed, no new parts are required to be developed, so the development of the VVR function in the compressor is less difficult and fast.
  • the first embodiment of the present disclosure has high structural compatibility and is applicable to most scrolls, and the compressor can be quickly improved to have the VVR function by machining orifices on the original scroll.
  • a plug that reduces the clearance volume is provided in the transverse connection section 320.
  • the existing The processing method is difficult to directly punch holes from the positions P1 and P2 inside the end plate 54A to form the transverse channels, but must punch holes from the outer end of the end plate 54A (for example, the left end shown in Figure 5) to connect the channels transversely 320 extends to a point P1 intersecting the first axial section 310.
  • the first part the part between the intersections P1 and P2 in the transverse connecting section 320 is necessary for forming the connecting channel 300 (hereinafter referred to as the first part), and the part from the end punched on the left to the intersection P2
  • the remaining part (hereinafter referred to as the second part) is the invalid part due to the processing technology. Since the exhaust gas will remain in the transverse connecting section 320 after the VVR valve is closed, the ineffective second part will increase the clearance volume of the compressor, thereby reducing the efficiency of the compressor.
  • a plug may be provided in the transverse connection section 320 to separate the first part and the second part so as to reduce the clearance volume of the compressor.
  • the plug 400 has a short stud shape, and a tool engaging groove 410 is formed on one end surface of the plug 400.
  • An internal thread is formed on the entire length of the second part of the transverse connection section 320.
  • the length of the plug 400 is less than the length of the second part, and a tool such as a screwdriver can be used to engage with the tool engaging groove 410 on the plug 400 , So that the plug 400 is screwed into the second part and fixed at the position where the second part is adjacent to the first part to isolate the first part from the second part.
  • a tool such as a screwdriver
  • the plug 500 is in the shape of an elongated step, the transverse connecting section 320 is formed with internal threads only at its left end position, and the plug 500 includes a first cylindrical portion 510 and a second cylindrical portion 520 with a slightly smaller diameter than the first cylindrical portion.
  • the outer circumferential surface of the first cylindrical portion is formed with an external thread for engaging with an internal thread, and the length of the second cylindrical portion can fill the second portion.
  • the scroll mechanism of the compressor according to the second embodiment of the present disclosure is provided, wherein the fixed scroll 40B described in FIGS. 9-10 is used instead of the fixed scroll according to the first comparative example.
  • Scroll 40 the other structure of the scroll compressor is basically unchanged.
  • the end plate 44B of the fixed scroll 40B is provided with a fluid channel that directly communicates the first intermediate compression cavity with the second intermediate compression cavity.
  • the fluid channel of the end plate 44B may include a first axial section 310, a second axial section 330, and a transverse connection section 320B similarly to the fluid channel 300 in the first embodiment, wherein the first axial section
  • the section and the second axial section may extend in the axial direction of the compressor and communicate with the first intermediate compression chamber and the second intermediate compression chamber, respectively, and the transverse connection section 320B may be in a transverse direction perpendicular to the axial direction of the compressor. The direction extends and connects the first axial section and the second axial section.
  • the lateral connection section 320B according to the second embodiment may be formed as a single section similar to the lateral connection section 320 according to the first embodiment.
  • the transverse connecting section 320B may include the sections disposed in the row respectively.
  • the first transverse connecting section 322B and the second transverse connecting section 324B on both sides of the air port 42 are such that the transverse connecting section 320B is arranged around the exhaust port 42.
  • the first transverse connecting section 322B and the second transverse connecting section 324B may intersect at the outer end P3 of the end plate 44B of the fixed scroll 40B, and a seal 326B may be provided at the intersection P3 to prevent fluid from flowing from the first middle.
  • the compression chamber and the second intermediate compression chamber are discharged through the outer end P3.
  • the scroll 46C of the fixed scroll 40C is provided with a fluid channel 300C1, and the fluid channel 300C1 includes a first notch 310C1, a second notch 330C1, and a connecting section (ie, corresponding to The channel according to the present disclosure) 320C1, wherein the first notch 310C1 and the second notch 330C1 can communicate with the first intermediate compression cavity C2 and the second intermediate compression cavity C3, respectively, and the transverse connecting section 320C1 can be helically shaped
  • the scroll 46C extends and connects the first notch 310 and the second notch 330.
  • the scroll 56C of the orbiting scroll 50C is provided with a fluid passage 300C2, and the fluid passage 300C2 includes a first intermediate compression chamber C2 and a second intermediate compression chamber C3, respectively.
  • the notch 310C2 and the second notch 330C2 and the connecting section 320C2 extending along the spiral scroll 56C and connecting the first notch 310C2 and the second notch 330C2 (ie, corresponding to the channel according to the present disclosure).
  • the fluid channels 300C1 and 300C2 are formed at the free ends of the scrolls, thereby facilitating the processing of the fluid channels and reducing the influence on the strength of the scrolls.
  • the fluid channel 300C1 formed in the fixed scroll 46C and the fluid channel 300C2 formed in the movable scroll 56C are used to communicate with the first middle
  • a fluid channel can be formed only on one of the fixed scroll 46C and the movable scroll 56C to realize the first intermediate compression chamber.
  • the compression chamber is in fluid communication with the second intermediate compression chamber.
  • the exhaust port 42 is arranged in the center of the end plate 44 of the fixed scroll 40.
  • this centrally arranged exhaust port will affect the VVR valve
  • the setting causes interference, making the VVR valve at least partially extend through the central exhaust port 42, which will cause the high-pressure fluid discharged through the central exhaust port 42 to act on the valve plate of the VVR valve, which may cause the VVR valve to not be over-compressed In the case of, discharge the under-compressed fluid in advance.
  • the exhaust port 42 includes a first exhaust port portion 42A and a second exhaust port portion 42B that communicate with each other.
  • the first exhaust port portion 42A is located in the center of the end plate 44 of the fixed scroll 40 and is in fluid communication with the central compression chamber C1, and the second exhaust port portion 42B deviates from the first exhaust port portion 42A in the radial direction and is connected to the The exhaust area defined by the inner annular wall 43 is in fluid communication.
  • the second exhaust port portion 42B located above the axial direction is offset from the first exhaust port portion 42A located in the center of the end plate below, the effect of the exhaust port 42 on the VVR valve is reduced. Interference, and provides more installation space for the VVR valve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

一种涡旋压缩机，包括：具有动涡旋端板(54A)和形成在动涡旋端板的一侧的动涡卷(56C)的动涡旋(50A，50C)，以及具有定涡旋端板(44A，44B)和形成在定涡旋端板的一侧的定涡卷(46C)的定涡旋(40A，40B，40C)，定涡旋和动涡旋配合以在其间形成一系列压缩腔，一系列压缩腔包括中央压缩腔(C1)以及位于中央压缩腔的径向外侧的中间压缩腔，中间压缩腔至少包括一组第一中间压缩腔(C2)和第二中间压缩腔(C3)；第一中间压缩腔与第二中间压缩腔之间设置有可选择的与排气区域连通的流体通道(300，300C1，300C2)，第一中间压缩腔和第二中间压缩腔通过流体通道直接连通。

Description

涡旋压缩机
本申请要求以下中国专利申请的优先权：于2019年5月24日提交中国专利局的申请号为201910440249.7、发明创造名称为“涡旋压缩机”的中国专利申请；于2019年5月24日提交中国专利局的申请号为201920765067.2、发明创造名称为“涡旋压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及涡旋压缩机技术领域，更具体地，涉及具有可变容积比功能的涡旋压缩机。
背景技术
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。
压缩机可能应用于例如空调系统、冷库系统等需要不同压力的应用系统中，因此可能出现压缩腔的排出压力(压缩腔中的最大压力)大于特定的应用系统所需压力的情况，即出现了过压缩的情况。在过压缩的情况下，被压缩到排出压力的流体在排出压缩腔后会降低到应用系统所需的压力，因此，压缩机做了不必要的功，这将减小压缩机的效率。
为了减小或防止工作流体的过压缩，已经开发出了具有可变容积比(VVR)功能的压缩机。这种压缩机可以利用设置在VVR孔口中的VVR阀来实现可变的容积比，即，在系统所需压力较低时以低容积比运行并且在系统所需压力较高时以高容积比运行，从而有效地避免过压缩现象、提高压缩机的效率。然而，在压缩机领域中，仍然存在由于安装空间受限无法设置VVR阀导致不能实现VVR功能或者实现VVR功能的结构复杂且成本高等技术问题。
发明内容
本公开的一个或多个实施方式的一个目的是提供一种压缩机，在该压缩机中，具有不受安装空间限制且结构简单的可变容积比机构。
本公开的一个或多个实施方式的另一目的是提供一种压缩机，在该压缩机中，具有适用于设置有定涡旋毂部的小排量压缩机的可变容积比机构。
本公开的一个或多个实施方式的另一个目的是提供一种压缩机，在该压缩机中，具有兼容性高、能够以简单快速的方式实现的可变容积比机构。
本公开的一个或多个实施方式的另一个目的是提供一种压缩机，在该压缩机中，具有需要开发的新零部件较少从而开发难度低且开发速度快的可变容积比机构。
本公开的一个或多个实施方式的另一个目的是提供一种压缩机，在该压缩机中，具有不需要分体设计、无盖板和泄漏小从而运行可靠的可变容积比机构。
根据本公开的一个方面，提供了一种涡旋压缩机，包括：动涡旋，所述动涡旋包括动涡旋端板和形成在所述动涡旋端板的一侧的动涡卷；以及定涡旋，所述定涡旋包括定涡旋端板和形成在所述定涡旋端板的一侧的定涡卷，所述定涡旋和所述动涡旋配合以在其间形成一系列压缩腔，所述一系列压缩腔包括中央压缩腔以及位于所述中央压缩腔的径向外侧的中间压缩腔，所述中间压缩腔至少包括一组第一中间压缩腔和第二中间压缩腔；其中，所述第一中间压缩腔与第二中间压缩腔之间设置有可选择的与排气区域连通的流体通道，所述第一中间压缩腔和所述第二中间压缩腔通过所述流体通道直接连通。
根据本公开的一个方面，所述涡旋压缩机包括：设置在所述定涡旋端板处的主排气口和副排气口，所述主排气口与所述中央压缩腔流体连通，并且所述第一中间压缩腔和所述第二中间压缩腔共用的所述副排气口可选择的与排气区域流体连通。
根据本公开的一个方面，所述流体通道包括连通至所述第一中间压缩腔的第一部段、连通至所述第二中间压缩腔的第二部段以及连接所述第一部段和所述第二部段的连接部段。
根据本公开的一个方面，所述流体通道设置在所述定涡旋端板中，所述连接部段包括与所述第一部段连通的第一连接部段和与所述第二部段连通的第二连接部段，所述第一连接部段和所述第二连接部段相交，所述副排气口与所述第一中间压缩腔和所述第二中间压缩腔中的一个直接流体连通。
根据本公开的一个方面，所述流体通道设置在所述动涡旋端板中，并且所述连接部段形成为单个部段，所述副排气口与所述第一中间压缩腔和所述第二 中间压缩腔中的一个直接流体连通。
根据本公开的一个方面，所述连接部段具有贯穿所述定涡旋端板或所述动涡旋端板的第一端，所述第一端处设置有防止流体泄露的堵头。
根据本公开的一个方面，所述流体通道设置在所述定涡卷和所述动涡卷中的至少一者上。
根据本公开的一个方面，所述流体通道包括设置在所述定涡卷和/或所述动涡卷的自由末端端面处的槽道以及从所述槽道延伸的分别连通至所述第一中间压缩腔和所述第二中间压缩腔的第一槽口和第二槽口。
根据本公开的一个方面，所述定涡旋端板在与所述定涡卷相反的一侧形成有内环形壁，所述主排气口和所述副排气口设置在所述内环形壁的径向内侧，由所述内环形壁限定所述排气区域；并且在所述副排气口处设置有可变容积比阀，所述可变容积比阀允许流体从所述第一中间压缩腔和所述第二中间压缩腔流动至所述排气区域并且防止流体从所述排气区域流动至所述第一中间压缩腔和所述第二中间压缩腔。
根据本公开的一个方面，所述可变容积比阀包括覆盖所述可变容积比孔口的单个阀片和控制所述阀片最大运动范围的阀挡，所述阀片包括固定部和单个可动部，所述可动部能够相对于所述固定部在打开位置与关闭位置之间移动。
根据本公开的压缩机结构不仅能够不受安装空间的限制并且还能够以结构简单的方式实现VVR功能。
附图说明
此处描述的附图是仅出于说明的目的，而并非意在以任何方式限制本公开的范围。
图1为示意性地示出了根据第一比较示例的具有VVR功能的压缩机的剖视图；
图2为示意性地示出了根据第一比较示例的具有VVR功能的压缩机的定涡旋及VVR阀的立体图；
图3A为示意性地示出了根据第二比较示例的具有VVR功能的压缩机的定涡旋及VVR阀的立体图；
图3B详细示出了根据第二比较示例的VVR阀；
图4示意性地示出了根据本公开的第一实施方式的压缩机定涡旋和动涡旋；
图5示意性示出了根据本公开的一个实施方式的安装在横向连接部段中的堵头；
图6详细示出了根据本公开的一个实施方式的堵头；
图7示意性示出了根据本公开的另一实施方式的安装在横向连接部段中的堵头；
图8详细示出了根据本公开的另一实施方式的堵头；
图9示意性地示出了根据本公开的第二实施方式的压缩机的定涡旋；
图10示意性地示出了根据本公开的第二实施方式的压缩机的涡旋机构；
图11示意性地示出了根据本公开的第三实施方式的压缩机的定涡旋；
图12示意性地示出了根据本公开的第三实施方式的压缩机的动涡旋；
图13示意性地示出了根据本公开的第三实施方式的压缩机的涡旋机构；以及
图14A和图14B示意性地示出了根据本公开的一个实施方式的压缩机的排气口布置。
具体实施方式
下面对本公开各实施方式的描述仅仅是示例性的，而绝不是对本公开及其应用或用法的限制。在各个附图中采用相同的附图标记来表示相同的部件，因此相同部件的构造将不再重复描述。
下面将参照图1-3B对根据比较示例的具有VVR功能的压缩机进行描述，其中，图1为示意性地示出了根据第一比较示例的具有VVR功能的压缩机的剖视图；图2为示意性地示出了根据第一比较示例的具有VVR功能的压缩机的定涡旋及VVR阀的立体图；图3A和图3B示意性地示出了根据第二比较示例的具有VVR功能的压缩机的定涡旋及VVR阀。
如图1所示，压缩机1包括大致封闭的壳体20。壳体20可以由大致圆筒形的本体部22、设置在本体部22的一端的顶盖24、设置在本体部22的另一端的底盖26构成。在顶盖24和本体部22之间设置有隔板30以将壳体20的 内部空间分隔成流体吸入腔21和流体排出腔23。隔板30和顶盖24之间的空间构成流体排出腔23，而隔板30、本体部22和底盖之间的空间构成流体吸入腔21。在流体吸入腔21的一侧设置有用于吸入流体的进气接头，在流体排出腔23的一侧设置有用于排出压缩后的流体的排气接头。
在壳体20中设置有压缩机构和用于驱动压缩机构的驱动机构。压缩机构从壳体20的流体吸入腔21吸入流体并且将流体压缩后排出到壳体20的流体排出腔23中。更具体地，参见图1，压缩机构例如可以包括定涡旋40和动涡旋50。动涡旋50包括端板54和形成在端板一侧的螺旋状的涡卷56。定涡旋40包括端板44和形成在端板一侧的螺旋状的涡卷46，端板44包括形成在端板的大致中央位置处的排气口42以及位于排气口42径向外侧的第一可变容积比孔口64和第二可变容积比孔口66。定涡旋40的涡卷46和动涡旋50的涡卷56相互啮合以在其间形成一系列从径向外侧向径向内侧体积逐渐减小压力逐渐增大的压缩腔。具体来说，压缩腔中的径向最外侧的压缩腔内压力最小，径向最内侧的压缩腔即处于涡旋中央位置处的中央压缩腔C1内压力最大，位于径向最外侧位置与最内侧位置之间的多个中间压缩腔具有介于最大压力与最小压力之间的中间压力。排气口42与中央压缩腔流体连通该部分描述的流体连通对应于直接流体连通)，而第一可变容积比孔口64和第二可变容积比孔口66分部与位于中央压缩腔两侧的两个中间压缩腔C2、C3流体连通。
为了实现定涡旋40的涡卷46的顶端与动涡旋50的端板54之间以及动涡旋50的涡卷56的顶端与定涡旋40的端板44之间的轴向密封，通常，在定涡旋40的端板44的与涡卷46相反的一侧设置有背压腔70。更具体地，在端板44上形成有内环形壁43和外环形壁45。内环形壁43围绕排气口42形成。背压腔70由端板44、内环形壁43和外环形壁45围绕的空间构成并且由设置在其内的密封组件封闭。背压腔70通过端板44中形成的轴向延伸的通孔(未示出)与动涡旋50和定涡旋40之间的压缩腔中的一个中压腔流体连通，从而形成将定涡旋40朝向动涡旋50挤压的力，利用背压腔70中的压力可以有效地将定涡旋40和动涡旋50压在一起。
在由内环形壁43限定的排气区域中，设置有可变容积比阀100(以下简称VVR阀)以防止工作流体的过度压缩。如图2具体所示，VVR阀100包括阀板110、阀片120、阀保持件130、销140以及波形弹簧150。阀板110在与 第一可变容积比孔口64和第二可变容积比孔口66对应的位置处分别设置有第一流体通孔和第二流体通孔。阀板110上设置有阀片120以选择性地打开或闭合流体通孔。阀片120具有对称的两个可动部126和一个固定部124。两个可动部126能够相对于固定部124在打开位置与关闭位置之间移位。阀片120上设置有阀保持件130。销140延伸穿过阀片、阀板和阀保持件中形成的销孔以周向地固定阀板110、阀板120和阀保持件130。波形弹簧150将阀片、阀板和阀保持件轴向地保持在一起。
在压缩机1的操作期间，工作流体被吸入到压缩机构中并且随着从径向最外位置流动至径向最内位置而被压缩，压缩后的流体通过排气口42排出至由内环形壁43限定的排气区域，并且然后经由设置在隔板30中央位置处的单向阀而排出至排出腔23。而在发生过度压缩的情况下，流体可以在到达径向最内位置之前通过VVR阀100提前排出至排气区域。具体地，当处于径向中间位置的压缩腔中的流体的压力大于排出腔23中的流体压力(即发生过度压缩)时，阀片120下侧的压力大于上侧压力，阀片120在压力差作用下朝向打开位置移动，从而允许流体通过可变容积比孔口64、66和流体通孔提前排出。当容纳在径向中间位置处的压缩腔中的流体的压力小于排出腔23中的流体压力时，阀片120在弹性回复力及压力差作用下返回至关闭位置，从而密封可变容积比孔口64、66。
在压缩机1中，为使得背压腔70能够提供稳定且足够的压力以有效地防止各个压缩室之间的流体泄漏，需要确保背压腔70具有足够的空间，由此环形壁43内侧的空间十分有限。特别地，对于小排量的涡旋压缩机而言，环形壁43内侧空间可能仅具有20mm-30mm的直径，在此情况下难以将VVR阀100配装至环形壁43的内部以实现压缩机的VVR功能。
另一方面，图3A和图3B示意性地示出了根据第二比较示例的具有VVR功能的压缩机的定涡旋及VVR阀，该压缩机的其他构造与根据第一比较示例的压缩机的相应构造基本相同。根据第二比较示例的压缩机采用盖板220将排气区域与背压腔分成上下两部分，从而使得VVR阀的安装空间不会如第一比较示例那样受背压腔尺寸限制。具体地，参照图3A，定涡旋端板144和盖板220通过多个螺钉210紧固在一起，其中，定涡旋端板144在形成涡卷的相反侧设置有凹槽208，凹槽208围绕排气口202以及可变容积比孔口164、166 形成，从而在凹槽208(即盖板220的下侧)形成排气区域。
每一个可变容积比孔口164、166上分别设置有一个对应的VVR阀200。VVR阀200允许流体从压缩腔流动到排气区域，并且防止流体从排气区域流动到压缩腔。VVR阀200可以包括覆盖可变容积比孔口164、166的阀片220和防止阀片220过度变形的阀挡230。阀片220具有一个可动部226和一个固定部224，可动部226能够相对于固定部224在打开位置与关闭位置之间移位。VVR阀200可以通过诸如螺钉的紧固件240固定到定涡旋端板144中形成的阀固定孔中。
盖板220的上侧形成凹部222，凹部222通过中压孔与压缩腔中的中压腔流体连通，并且凹部222中可以设置密封组件以形成向定涡旋提供轴向密封力的背压腔。盖板220和定涡旋端板144之间设置有垫片250。
然而，在根据第二比较示例的压缩机中，由于需要使用额外的盖板220、密封垫250以及相应的紧固件，这使得结构复杂、增加了零部件成本和安装时间。并且由于盖板220与定涡旋端板144之间的排气区域具有很大的压力，因此螺纹相连的盖板220与定涡旋端板144存在无法实现完全密封而发生流体泄漏的风险。
为了解决上述问题，本发明人构想出了一种改进的压缩机结构，该压缩机构不仅能够不受安装空间的限制并且还能够以结构简单的方式实现VVR功能。
下面就结合图4至图14B对根据本公开的具有VVR功能的压缩机做进一步详细的说明，其中，附图中相同的附图标记表示相同的部件并将省略对这些部件的具体描述。
如图4中所示，根据本公开的第一实施方式的压缩机包括定涡旋40A和动涡旋50A，与根据第一比较示例的定涡旋40和动涡旋50类似地，定涡旋40A的涡卷46和动涡旋50A的涡卷56相互啮合以在其间形成一系列从径向外侧向径向内侧体积逐渐减小压力逐渐增大的压缩腔。其中，压缩腔中的径向最外侧的压缩腔内压力最小，径向最内侧的压缩腔即处于涡旋中央位置处的中央压缩腔内压力最大，位于径向最外侧位置与最内侧位置之间的多个中间压缩腔具有介于最大压力与最小压力之间的中间压力。
定涡旋40A的端板44A设置有中央排气口42和可变容积孔口64。中央 排气口42可以与压缩腔中的中央压缩腔C1流体连通，可变容积孔口64可以与位于中央压缩腔径向外侧(图4中的右侧)的第一中间压缩腔C2流体连通。在中央压缩腔的相反侧(即，图4中的左侧)形成有第二中间压缩腔C3，并且第二中间压缩腔C3可以与第一中间压缩腔C2关于中央压缩腔C1对称。在此应当指出的是，在本申请的描述中，将在压缩机的工作过程中具有大致相同压力和腔体体积的中间压缩腔称为一组第一中间压缩腔和第二中间压缩腔，一组中间压缩腔同时排气，以避免不同时排气引起的某一压缩腔的过压缩或欠压缩，减少压缩机等容压缩的损失。在对称式单涡圈压缩机中，压缩腔相对于中央压缩腔对称，两个对称的压缩腔中的压力和体积基本相同，可以作为一组中间压缩腔。在双涡圈压缩机中，可以同时存在压力和体积大致相同的两组(即四个)中间压缩腔。在非对称涡旋设计中，由定涡旋和动涡旋形成的压缩腔相对于中央压缩腔是不对称的，因此，第一中间压缩腔C2也与第二中间压缩腔C3不对称。然而，应当理解，在非对称的情况下，根据本公开的设置如下所述的流体通道的技术构思也同样适用。
根据本公开的第一实施方式的压缩机在第一中间压缩腔C2与第二中间压缩腔C3之间设置有流体通道300以使两压缩腔直接连通。如图4所示，流体通道300可以形成在动涡旋50A的端板54A中，并且流体通道300可以包括第一部段310、第二部段330以及横向连接部段320。第一部段310和第二部段330可以沿压缩机的轴向方向延伸并且分别与第一中间压缩腔C2和第二中间压缩腔C3连通，横向连接部段320可以沿与压缩机的轴向方向垂直的横向方向延伸并且连接第一轴向部段310和第二轴向部段330。由此，第二中间压缩腔C3中的流体可以依次穿过第二轴向部段330、横向连接部段320以及第一轴向部段310流动至第一中间压缩腔C2，并且然后可以从第一中间压缩腔C2经由可变容积孔口64排出至环形壁43限定的排气区域。优选地，流体通道300的横向连接部段320可以形成为单个部段，以减小压缩机的余隙容积。此外，尽管在此描述了沿压缩机的轴向方向延伸的第一部段310和第二部段330，但是应当理解的是，第一部段310和第二部段330也可以沿略微倾斜的方向延伸。优选地采用轴向延伸的第一部段310和第二部段330以减小压缩机的余隙容积。
在根据本公开的第一实施方式的压缩机中，在可变容积孔口64上可以设 置有一个VVR阀200。VVR阀200可以包括覆盖可变容积比孔口64的阀片220和防止阀片220过度变形的阀挡230。阀片220可以具有一个可动部226和一个固定部224，可动部226能够相对于固定部224在打开位置与关闭位置之间移位，其中，在关闭位置阀片220关闭可变容积孔口64，而在打开位置阀片220打开可变容积孔口64并且允许流体从第一中间压缩腔C2流动至由环形壁43限定的排气区域。VVR阀200可以通过诸如螺钉的紧固件固定到形成在定涡旋40A的端板44A中的阀固定孔。
在根据本公开的第一实施方式的压缩机的操作期间，工作流体被吸入到压缩机构中并且随着从径向最外位置流动至径向最内位置而被压缩，压缩后的流体通过排气口42排出到由内环形壁43限定的排气区域，然后通过设置在隔板30中央处的单向阀排出至排放腔23。在发生过度压缩的情况下，流体可以在到达径向最内侧的中央压缩腔C1之前通过VVR阀200提前排出至排出区域。具体地，当处于径向中间位置的第一中间压缩腔C2及第二中间压缩腔C3中的流体的压力大于排出腔23中的流体压力(即发生过度压缩)时，阀片220下侧的压力大于上侧压力，阀片220的可动部226在压力差作用下朝向打开位置移动，从而允许流体通过可变容积比孔口64可以从中间压缩腔C2、C3提前排出到排放区域。当第一中间压缩腔C2及第二中间压缩腔C3中的流体的压力小于排出腔23中的流体压力时，阀片220在弹性回复力及压力差作用下返回至关闭位置，从而密封可变容积比孔口64。
根据本公开的第一实施方式的压缩机示例性地示出了具有一组中间压缩腔C2、C3的情况，其中，在端板44A中可以仅形成单个可变容积孔口64，并且仅需具有单个可动部的单个阀片即可实现对可变容积孔口64的选择性开闭，从而与根据第一比较示例的压缩机相比能够大幅减小VVR阀的安装尺寸，避免因尺寸受限而无法实现VVR功能。此外，与根据第二比较示例的压缩机相比，根据本公开的第一实施方式的压缩机可以避免使用额外的盖板220、密封垫250以及相应的紧固件，减小加工成本和零部件成本，并且防止在盖板与定涡旋端板之间的高压排气区域发生流体泄漏。此外，由于根据公开的第一实施方式采用结构简单且例如发明人已经构思出的VVR阀200，不需要开发新零部件，因此在压缩机中实现VVR功能的开发难度低、开发速度快。并且根据本公开的第一实施方式的结构兼容性高、可适用于大部分涡旋，通过在原涡 旋上加工孔口等即可快速地改进压缩机使其具备VVR功能。
根据本公开的一个实施方式，在横向连接部段320中设置有减小余隙容积的堵头。如图5所示，由于第一轴向部段310和第二轴向部段330与横向连接部段320分别在位于端板的内部的第一位置P1、第二位置P2相交，现有的加工方法难以从端板54A内部的位置P1、P2直接打孔形成横向通道，而是必须从端板54A的外侧端部打孔(例如图5中所示的左侧端部)使横向连接通道320延伸至与第一轴向部段310相交的点P1。因此，横向连接部段320中仅在交点P1、P2之间的部分是形成连接通道300所必须的(以下称为第一部分)，而从左侧打孔的端部至交点P2的之间的其余部分(以下称为第二部分)是因加工工艺产生的无效部分。由于在VVR阀关闭后横向连接部段320内将残余有排气，因此无效的第二部分将导致压缩机的余隙容积增大，从而减小压缩机的效率。根据本公开的一个实施方式，在横向连接部段320中可以设置有堵头以将第一部分和第二部分分隔开从而减小压缩机的余隙容积。
参照图5至图8，对根据本公开的包括安装有堵头的横向连接部段的具体实施方式进行说明。在图5所示的实施方式中，堵头400呈短螺柱形状，并且在堵头400的一个端面上形成有工具接合凹槽410。在横向连接部段320的第二部分的整个长度上形成有内螺纹，堵头400的长度小于第二部分的长度，能够利用螺丝刀之类的工具与堵头400上的工具接合凹槽410接合，从而将堵头400旋拧到第二部分中并固定在第二部分与第一部分邻接的部位处，以将第一部分与第二部分隔离开。在图7和图8所示的实施方式中，堵头500呈长形的阶梯状，横向连接部段320仅在其左侧端部位置处形成有内螺纹，堵头500包括第一圆柱部分510和直径略小于第一圆柱部分的第二圆柱部分520，第一圆柱部分的外周表面上形成有用于与内螺纹接合的外螺纹，第二圆柱部分的长度能够填充第二部分。
参照图9和图10，提供了根据本公开的第二实施方式的压缩机的涡旋机构，其中，用图9-10所述的定涡旋40B代替了根据第一比较示例中的定涡旋40，涡旋压缩机的其他构造基本不变。
定涡旋40B的端板44B中设置有使第一中间压缩腔与第二中间压缩腔腔直接连通的流体通道。端板44B的流体通道可以与根据第一实施方式中的流体通道300类似地包括第一轴向部段310、第二轴向部段330以及横向连接部 段320B，其中，第一轴向部段和第二轴向部段可以沿压缩机的轴向方向延伸并且分别与第一中间压缩腔和第二中间压缩腔连通，横向连接部段320B可以沿与压缩机的轴向方向垂直的横向方向延伸并且连接第一轴向部段和第二轴向部段。根据第二实施方式的横向连接部段320B可以与根据第一实施方式的横向连接部段320类似地形成为单个部段。然而，由于排气口42形成在定涡旋40B的端板44B中，为了避免横向连接部段320B在端板44B中受排气口42的影响，横向连接部段320B可以包括分别设置在排气口42的两侧的第一横向连接部段322B和第二横向连接部段324B以使横向连接部段320B绕开排气口42设置。第一横向连接部段322B和第二横向连接部段324B可以在定涡旋40B的端板44B的外端部P3处相交，在相交的P3处可以设置密封件326B以避免流体从第一中间压缩腔和第二中间压缩腔经由外端部P3排出。
根据本公开的第二实施方式的压缩机的工作原理及优点与根据本公开的第一实施方式的压缩机的工作原理及优点相同，在此不再赘述。
下面参照图12-图14B，对根据本公开的第三实施方式的压缩机的涡旋机构进行描述。在根据本公开的第三实施方式中，定涡旋40C的涡卷46C中设置有流体通道300C1，流体通道300C1包括第一槽口310C1、第二槽口330C1以及连接部段(即，对应于根据本公开的槽道)320C1，其中，第一槽口310C1和第二槽口330C1可以分别与第一中间压缩腔C2和第二中间压缩腔C3连通，横向连接部段320C1可以沿螺旋状的涡卷46C延伸并且连接第一槽口310和第二槽口330。类似地，根据本公开的第三实施方式的动涡旋50C的涡卷56C中设置有流体通道300C2，流体通道300C2包括分别与第一中间压缩腔C2和第二中间压缩腔C3连通的第一槽口310C2和第二槽口330C2以及沿螺旋状的涡卷56C延伸并且连接第一槽口310C2和第二槽口330C2的连接部段(即，对应于根据本公开的槽道)320C2。优选地，在本公开的第三实施方式中，流体通道300C1和300C2形成在涡卷的自由末端处，从而一方面便于流体通道的加工并且减小对涡卷的强度的影响。
尽管在根据本公开的第三实施方式中，示出了利用定涡旋的涡卷46C中形成的流体通道300C1和动涡旋的涡卷56C中形成的流体通道300C2两者来连通第一中间压缩腔和第二中间压缩腔，但是本领域技术人员应当理解的是，可以仅在定涡旋的涡卷46C和动涡旋的涡卷56C中的一者上形成流体通道来 实现第一中间压缩腔与第二中间压缩腔的流体连通。
根据本公开的第三实施方式的压缩机的工作原理及优点与根据本公开的第一实施方式的压缩机的工作原理及优点相同，在此不再赘述。
在上述各实施方式中，排气口42设置在定涡旋40的端板44的中央，在内环形壁43限定的空间十分有限的情况下，这种中央布置的排气口会对VVR阀的设置造成干扰，使得VVR阀至少部分地延伸经过中央排气口42，这会使得经由中央排气口42排出的高压流体作用在VVR阀的阀片上，从而可能导致VVR阀在未发生过压缩的情况下提前将欠压缩的流体排出。为了解决上述问题，参照图14A和14B，在根据本公开的一个实施方式中，排气口42包括相互连通的第一排气口部分42A和第二排气口部分42B。第一排气口部分42A位于定涡旋40的端板44的中央并且与中央压缩腔C1流体连通，第二排气口部分42B在径向方向上偏离第一排气口部分42A并且与由内环形壁43限定的排气区域流体连通。在根据本公开的压缩机中，由于位于轴向上方的第二排气口部分42B偏离下方的位于端板中央的第一排气口部分42A，从而减小了排气口42对VVR阀的干扰，并且为VVR阀提供了更大的安装空间。
尽管上文已经具体描述了本公开的各种实施方式和变型，但是本领域技术人员应该理解，本公开并不局限于上述具体的实施方式和变型而是可以包括其他各种可能的组合和结合。在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其他的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (10)

  1. 一种涡旋压缩机，包括：
    动涡旋(50A，50C)，所述动涡旋包括动涡旋端板(54A)和形成在所述动涡旋端板的一侧的动涡卷(56C)；以及
    定涡旋(40A，40B，40C)，所述定涡旋包括定涡旋端板(44A，44B)和形成在所述定涡旋端板的一侧的定涡卷(46C)，所述定涡旋和所述动涡旋配合以在其间形成一系列压缩腔，所述一系列压缩腔包括中央压缩腔(C1)以及位于所述中央压缩腔的径向外侧的中间压缩腔，所述中间压缩腔至少包括一组第一中间压缩腔(C2)和第二中间压缩腔(C3)；
    其特征在于，所述第一中间压缩腔与第二中间压缩腔(C3)之间设置有可选择的与排气区域连通的流体通道(300，300C1，300C2)，所述第一中间压缩腔和所述第二中间压缩腔通过所述流体通道直接连通。
  2. 根据权利要求1所述的涡旋压缩机，其中，
    所述涡旋压缩机还包括：
    设置在所述定涡旋端板处的主排气口(42)和副排气口(64)，所述主排气口与所述中央压缩腔(C1)流体连通，并且所述第一中间压缩腔和所述第二中间压缩腔共用的所述副排气口可选择的与排气区域流体连通。
  3. 根据权利要求2所述的涡旋压缩机，其中，
    所述流体通道包括连通至所述第一中间压缩腔的第一部段(310)、连通至所述第二中间压缩腔的第二部段(330)以及连接所述第一部段和所述第二部段的连接部段(320，320B)。
  4. 根据权利要求3所述的涡旋压缩机，其中，
    所述流体通道设置在所述定涡旋端板(44B)中，所述连接部段包括与所述第一部段连通的第一连接部段(322B)和与所述第二部段连通的第二连接部段(324B)，所述第一连接部段和所述第二连接部段相交，所述副排气口与所述第 一中间压缩腔和所述第二中间压缩腔中的一个直接流体连通。
  5. 根据权利要求3所述的涡旋压缩机，其中，
    所述流体通道设置在所述动涡旋端板(54A)中，并且所述连接部段(320)形成为单个部段，所述副排气口与所述第一中间压缩腔和所述第二中间压缩腔中的一个直接流体连通。
  6. 根据权利要求4或5所述的涡旋压缩机，其中，
    所述连接部段具有贯穿所述定涡旋端板或所述动涡旋端板的第一端，所述第一端处设置有防止流体泄露的堵头。
  7. 根据权利要求1所述的涡旋压缩机，其中，
    所述流体通道(300C1，300C2)设置在所述定涡卷(46C)和所述动涡卷(56C)中的至少一者上。
  8. 根据权利要求7所述的涡旋压缩机，其中，
    所述流体通道(300C1，300C2)包括设置在所述定涡卷和/或所述动涡卷的自由末端端面处的槽道以及从所述槽道延伸的分别连通至所述第一中间压缩腔(C2)和所述第二中间压缩腔(C3)的第一槽口和第二槽口。
  9. 根据权利要求2所述的涡旋压缩机，其中，
    所述定涡旋端板(54A)在与所述定涡卷(56A，56B)相反的一侧形成有内环形壁(43)，所述主排气口和所述副排气口设置在所述内环形壁的径向内侧，由所述内环形壁限定所述排气区域；并且在所述副排气口处设置有可变容积比阀(200)，所述可变容积比阀允许流体从所述第一中间压缩腔(C2)和所述第二中间压缩腔(C3)流动至所述排气区域并且防止流体从所述排气区域流动至所述第一中间压缩腔和所述第二中间压缩腔。
  10. 根据权利要求9所述的涡旋压缩机，其中，
    所述可变容积比阀包括覆盖所述可变容积比孔口的单个阀片(220)和控制所述阀片最大运动范围的阀挡(230)，所述阀片包括固定部(224)和单个可动部(226)，所述可动部能够相对于所述固定部在打开位置与关闭位置之间移动。
PCT/CN2020/091986 2019-05-24 2020-05-25 涡旋压缩机 WO2020238825A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4198314A1 (en) * 2021-12-20 2023-06-21 LG Electronics, Inc. Scroll compressor

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04370383A (ja) * 1991-06-17 1992-12-22 Hitachi Ltd スクロール圧縮機
JPH11166490A (ja) * 1997-12-03 1999-06-22 Mitsubishi Electric Corp 容量制御スクロール圧縮機
CN1576602A (zh) * 2003-07-26 2005-02-09 Lg电子株式会社 变容量涡旋式压缩机
JP2007292030A (ja) * 2006-04-27 2007-11-08 Mitsubishi Heavy Ind Ltd スクロール圧縮機
US20080184733A1 (en) * 2007-02-05 2008-08-07 Tecumseh Products Company Scroll compressor with refrigerant injection system
CN103362802A (zh) * 2012-03-29 2013-10-23 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
JP2014208985A (ja) * 2013-04-16 2014-11-06 株式会社ケーヒン スクロール型圧縮機
CN204511881U (zh) * 2015-03-16 2015-07-29 艾默生环境优化技术(苏州)有限公司 定涡旋部件及包括该定涡旋部件的涡旋压缩机
CN107002674A (zh) * 2014-12-12 2017-08-01 大金工业株式会社 涡旋压缩机
CN210218102U (zh) * 2019-05-24 2020-03-31 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07293456A (ja) 1994-04-28 1995-11-07 Sanyo Electric Co Ltd スクロール圧縮機
US5996364A (en) * 1998-07-13 1999-12-07 Carrier Corporation Scroll compressor with unloader valve between economizer and suction
US6883341B1 (en) * 2003-11-10 2005-04-26 Carrier Corporation Compressor with unloader valve between economizer line and evaporator inlet
US8568118B2 (en) * 2009-05-29 2013-10-29 Emerson Climate Technologies, Inc. Compressor having piston assembly
FR2960948B1 (fr) * 2010-06-02 2015-08-14 Danfoss Commercial Compressors Compresseur frigorifique a spirales

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04370383A (ja) * 1991-06-17 1992-12-22 Hitachi Ltd スクロール圧縮機
JPH11166490A (ja) * 1997-12-03 1999-06-22 Mitsubishi Electric Corp 容量制御スクロール圧縮機
CN1576602A (zh) * 2003-07-26 2005-02-09 Lg电子株式会社 变容量涡旋式压缩机
JP2007292030A (ja) * 2006-04-27 2007-11-08 Mitsubishi Heavy Ind Ltd スクロール圧縮機
US20080184733A1 (en) * 2007-02-05 2008-08-07 Tecumseh Products Company Scroll compressor with refrigerant injection system
CN103362802A (zh) * 2012-03-29 2013-10-23 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
JP2014208985A (ja) * 2013-04-16 2014-11-06 株式会社ケーヒン スクロール型圧縮機
CN107002674A (zh) * 2014-12-12 2017-08-01 大金工业株式会社 涡旋压缩机
CN204511881U (zh) * 2015-03-16 2015-07-29 艾默生环境优化技术(苏州)有限公司 定涡旋部件及包括该定涡旋部件的涡旋压缩机
CN210218102U (zh) * 2019-05-24 2020-03-31 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3978754A4

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4198314A1 (en) * 2021-12-20 2023-06-21 LG Electronics, Inc. Scroll compressor
US12071947B2 (en) 2021-12-20 2024-08-27 Lg Electronics Inc. Scroll compressor

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