WO2014134961A1 - Composant de volute et compresseur à volute - Google Patents

Composant de volute et compresseur à volute Download PDF

Info

Publication number
WO2014134961A1
WO2014134961A1 PCT/CN2013/090720 CN2013090720W WO2014134961A1 WO 2014134961 A1 WO2014134961 A1 WO 2014134961A1 CN 2013090720 W CN2013090720 W CN 2013090720W WO 2014134961 A1 WO2014134961 A1 WO 2014134961A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
component
scroll member
blade
step portion
Prior art date
Application number
PCT/CN2013/090720
Other languages
English (en)
Chinese (zh)
Inventor
孙庆丰
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 CN 201320097796 external-priority patent/CN203114634U/zh
Priority claimed from CN201310068431.7A external-priority patent/CN104033386B/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
Publication of WO2014134961A1 publication Critical patent/WO2014134961A1/fr

Links

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
    • 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
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C28/28—Safety arrangements; Monitoring

Definitions

  • the present invention relates to a scroll member and a scroll compressor including the scroll member. Background technique
  • Scroll compressors typically include a fixed scroll component and an orbiting scroll component.
  • the fixed scroll member and the movable scroll member respectively include an end plate and a substantially spiral scroll blade disposed on the end plate.
  • the scroll vanes of the fixed scroll member and the scroll vanes of the orbiting scroll member are engaged with each other to form a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side, thereby realizing compression of the fluid.
  • the lateral seal between the scroll vanes of the fixed scroll member and the scroll vanes of the orbiting scroll member is achieved by the centrifugal force of the orbiting scroll member.
  • the orbiting scroll member is driven to rotate relative to the fixed scroll member (ie, the central axis of the orbiting scroll member is rotated about the central axis of the scroll member, but The scroll member itself does not rotate about its central axis, so that the scroll blades of the orbiting scroll member abut against the scroll blades of the fixed scroll member under the centrifugal force, thereby achieving a seal between the two .
  • the scroll blades of the orbiting scroll member or the fixed scroll member may be broken due to excessive centrifugal force. Therefore, there is a need for a scroll member that is more durable and a scroll compressor. Summary of the invention
  • a scroll member for a scroll compressor comprising: an end plate; and a spiral wrap blade formed on the end plate, the wrap blade being on the shaft Included in the direction of a proximal end adjacent the end plate and a distal end remote from the end plate, the scroll blade including an inner end near the substantially central position of the end plate and adjacent in the circumferential direction An outer end portion of the outer peripheral side of the end plate, and the scroll blade includes a radially inner side surface facing a center position of the end plate and a radially outer side surface facing an outer peripheral side of the end plate, wherein At least one of the radially inner side surface and the radially outer side surface is formed with a protrusion adapted to contact the scroll blade of the mating other scroll member, the position of the protrusion portion in the axial direction It is designed such that the distal end of the scroll blade does not come into contact with the scroll blades of the other scroll member during operation of the scroll compressor.
  • FIG. 1 is a longitudinal cross-sectional view of a conventional scroll compressor
  • 3 is a perspective view showing an orbiting scroll member according to an embodiment of the present invention
  • FIG. 4 is a view showing an embodiment of the present invention.
  • FIG. 5A is a partially cutaway perspective view showing a movable scroll member according to an embodiment of the present invention
  • FIG. 5B is a partially enlarged view of a portion B of FIG. 5A
  • FIG. 7 is a schematic view showing a compression state of an orbiting scroll member and a fixed scroll member according to an embodiment of the present invention;
  • FIG. 8 is a schematic view showing a compression process of an orbiting scroll member and a fixed scroll member according to an embodiment of the present invention
  • 9 is a perspective view showing a movable scroll member according to a modification of the embodiment of the present invention
  • FIG. 10 is a perspective view showing an orbiting scroll member according to another modification of the embodiment of the present invention
  • FIG. Is a perspective view showing a fixed scroll member according to still another modification of the embodiment of the present invention.
  • a conventional scroll compressor 100 generally includes a housing 110, a top cover 112 disposed at the end of the housing 110, a bottom cover 114 disposed at the other end of the housing 110, and a top cover 112 and
  • the partitions 116 between the housings 110 partition the internal space of the compressor into a high pressure side and a low pressure side.
  • a high pressure side is formed between the partition 116 and the top cover 112
  • a low pressure side is formed between the partition 116, the casing 110 and the bottom cover 114.
  • An intake joint 118 for sucking a fluid is provided on the low pressure side, and an exhaust joint 119 for discharging the compressed fluid is provided on the high pressure side.
  • a motor 120 composed of a stator 122 and a rotor 124 is disposed in the housing 110.
  • a drive shaft 130 is provided in the rotor 124 to drive a compression mechanism composed of the fixed scroll member 150 and the movable scroll member 160.
  • the movable scroll member 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate.
  • the fixed scroll member 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate.
  • a series of compression chambers C1, C2, and C3 whose volume gradually decreases from the radially outer side to the radially inner side are formed.
  • the radially outermost compression chamber C1 is at the suction pressure
  • the radially innermost compression chamber C3 is at the exhaust pressure.
  • the intermediate compression chamber C2 is between the suction pressure and the discharge pressure, and is also referred to as a medium pressure chamber.
  • One side of the movable scroll member 160 is supported by an upper portion of the main bearing housing 140 (which constitutes a thrust member), and one end of the drive shaft 130 is supported by a main bearing 144 provided in the main bearing housing 140.
  • One end of the drive shaft 130 is provided with an eccentric crank pin 132, and the eccentric crank pin 132 and the movement
  • An unloading bushing 142 is disposed between the hub portions 162 of the scroll member 160.
  • the above translational rotation is achieved by the cross slip ring 190 disposed between the fixed scroll member 150 and the movable scroll member 160.
  • the fluid compressed by the fixed scroll member 150 and the orbiting scroll member 160 is discharged to the high pressure side through the exhaust port 152.
  • a check valve or exhaust valve 170 is provided at the exhaust port 152.
  • an effective seal must be provided between the fixed scroll member 150 and the orbiting scroll member 160.
  • the distal end portion of the scroll blade 156 of the fixed scroll member 150 and the end plate 164 of the orbiting scroll member 160 and the distal end portion of the scroll blade 166 of the orbiting scroll member 160 and the fixed scroll member 150 An axial seal is required between the end plates 154.
  • a back pressure chamber 158 is provided on the opposite side of the end plate 154 of the fixed scroll member 150 from the scroll vanes 156.
  • a seal assembly 180 is disposed in the back pressure chamber 158, and the axial displacement of the seal assembly 180 is limited by the diaphragm 116.
  • the back pressure chamber 158 is in fluid communication with the intermediate pressure chamber C2 through an axially extending through bore (not shown) formed in the end plate 154 to form a force that urges the fixed scroll member 150 toward the orbiting scroll member 160. Since one side of the orbiting scroll member 160 is supported by the upper portion of the main bearing housing 140, the fixed scroll member 150 and the orbiting scroll member 160 can be effectively pressed together by the pressure in the back pressure chamber 158. When the pressure in each compression chamber exceeds a set value, the resultant force generated by the pressure in these compression chambers will exceed the downward pressure provided in the back pressure chamber 158 to cause the fixed scroll member 150 to move upward.
  • the fluid in the compression chamber will pass through the gap between the distal end portion of the scroll vane 156 of the fixed scroll member 150 and the end plate 164 of the orbiting scroll member 160 and the scroll vane 166 of the orbiting scroll member 160.
  • the gap between the distal end portion and the end plate 154 of the fixed scroll member 150 leaks to the low pressure side to effect unloading, thereby providing axial flexibility to the scroll compressor.
  • a radial seal is also required between the side surface of the scroll vane 156 of the fixed scroll member 150 and the side surface of the scroll vane 166 of the orbiting scroll member 160.
  • This radial sealing between the two is typically achieved by the centrifugal force of the orbiting scroll member 160 during operation and the driving force provided by the drive shaft 130.
  • the orbiting scroll member 160 will rotate in translation with respect to the fixed scroll member 150, so that the orbiting scroll member 160 will generate centrifugal force.
  • the eccentric crank pin 132 of the drive shaft 130 also generates a drive that facilitates radial sealing of the fixed scroll member and the orbiting scroll member during rotation. Force component.
  • the scroll vanes 166 of the orbiting scroll member 160 abut against the scroll vanes 156 of the fixed scroll member 150 by means of the above-described centrifugal force and driving force components, thereby achieving radial sealing therebetween.
  • the scroll vanes 156 and the scroll vanes 166 can be temporarily radially They are separated from each other to allow foreign matter to pass, thus preventing the scroll blades 156 or 166 from being damaged.
  • This ability to be radially separated provides radial flexibility to the scroll compressor, increasing compressor reliability.
  • the scroll blades of the orbiting scroll member or the fixed scroll member may be broken due to excessive centrifugal force and driving force. More specifically, as shown in FIG.
  • the orbiting scroll member 60 includes an end plate 64 and a spiral wrap blade 66 formed on the end plate 64.
  • the orbiting scroll member 60 may also include a hub portion 62 formed on the other side of the end plate 64 to receive the eccentric crank pin 132 and the unloading bushing 142 of the drive shaft 130.
  • the scroll blade 66 includes a proximal end portion 66A proximate the end plate 64 and a distal end portion 66B distal from the end plate 64 in an axial direction (ie, a direction parallel to the axis of rotation of the orbiting scroll member 60).
  • the scroll blade 66 includes an inner end portion 66C near a substantially central position of the end plate and an outer end portion 66D near the outer peripheral side of the end plate in the circumferential direction (more precisely, the extending direction of the spiral of the scroll blade 66) .
  • the scroll blade 66 further includes a radially inner side surface 66E facing the center position of the end plate and a radially outer side surface 66F facing the outer peripheral side of the end plate.
  • the radially inner side surface 66E and the radially outer side The side faces 66F are formed with protrusions 70 adapted to contact the matching scroll members 56 of the other scroll member, such as the fixed scroll member 50, the positions of the protrusions 70 in the axial direction are designed such that the scrolls The distal end portion 66B of the vane 66 does not contact the scroll vanes 56 of the fixed scroll member 50 during operation of the scroll compressor.
  • the projection 70 is spaced apart from the distal end portion 66B of the scroll vane 66 by a predetermined distance so that the projection 70 can come into contact with the scroll vane 56 of the fixed scroll member during operation of the scroll reducer .
  • the distance between the projection 70 and the end plate 64 is smaller than the distance between the distal end portion 66B and the end plate 64, in the case of the same centrifugal force, due to the force arm (from the contact point to the end plate) The distance is reduced, so that the bending moment at the proximal end portion 66A of the scroll blade 66 can also be reduced, thereby making it possible to reduce the possibility of the vortex blade breaking.
  • the projection 70 forms a step 80 on the radially inner side 66E and the radially outer side 66F. That is, the projections 70 are formed in the range from the proximal end portion 66A to the step portion 80 on the radially inner side surface 66E and the radially outer side surface 66F. More specifically, the thickness of the scroll blade 66 in the radial direction of the first portion 66-1 of the step portion 80 near the proximal end portion 66A side is larger than the near distal end portion 66B of the scroll blade 66 at the step portion 80.
  • the thickness of the second portion 66-2 of the side is in the radial direction, whereby a step portion 80 is formed between the first portion 66-1 having a larger thickness and the second portion 66-2 having a smaller thickness.
  • the longitudinal sections of the first portion 66-1 and the second portion 66-2 in a plane parallel to the axial direction are both rectangular, as shown in Figs. 5A and 5B.
  • the thickness T of the step portion 80 in the radial direction may be designed such that the end portion 66B of the scroll blade 66 does not contact the vortex of the fixed scroll member 50 under the action of temperature and gas force during operation of the scroll compressor. Blade 56.
  • the thickness T of the step portion 80 in the radial direction may be between 0.01 mm and 0.1 mm.
  • the seal between the second portion 66-2 of the scroll blade 66 of the orbiting scroll member 60 and the scroll blade 56 of the fixed scroll member 50 can be achieved, for example, by a lubricant therebetween, thus the two scroll blades 56 and The compression chamber between 66 can still effectively maintain a seal.
  • the extending range of the step portion 80 shown by a thick black solid line in FIG. 8) in the circumferential direction of the scroll blade 66 (the direction in which the spiral extends) may be designed as follows.
  • the step portion 80 may be designed in a portion of the scroll blade 66 that is relatively easily broken.
  • the step portion 80 can be disposed at least radially in outermost contact of the scroll vanes 66 of the driven scroll member 60 with the scroll vanes 56 of the other scroll member (i.e., the fixed scroll member 50).
  • the point P1 extends inwardly within a range of 360 degrees in the circumferential direction. That is, the step portion 80 The extent in the circumferential direction extends from the outermost contact point P1 to the point P2.
  • the spiral of the scroll blade 66 extends at an angle of approximately 720 degrees, then the point P1 to The angle between points P2 is greater than or equal to 360 degrees.
  • the radial direction of the portion of the scroll blade 66 of the orbiting scroll member 60 where the step portion 80 is not formed i.e., the portion near the center of the orbiting scroll member 60, or in other words, the portion extending inward from the point P2
  • the thickness may be designed to be the same as the thickness in the radial direction of the first portion 66-1. That is, the portion of the scroll blade 66 where the step portion 80 is not formed is also formed thicker, thereby making it less likely to be broken.
  • Figure 7 shows the relative position between the orbiting scroll member 60 and the fixed scroll member 50 during operation.
  • the position of the fixed scroll member 50 remains unchanged, and the orbiting scroll member 60 is rotated relative to the fixed scroll member 50 as indicated by the arrow in Fig. 7.
  • the outermost compression chamber C 1 is in an inhaled state.
  • the outermost compression chamber C1 is still in the inhalation state and is about to close.
  • the outermost compression chamber C 1 has been closed.
  • the height H of the step portion 80 may be between 40% and 60% of the height h (see Fig. 2) of the scroll vanes 66 of the orbiting scroll member 60 in the axial direction. More preferably, the height H of the step portion 80 may be approximately 50% of the height h of the scroll blade 66. As shown in FIG.
  • the height H of the step portion 80 is designed to be 50% of the height h of the scroll blade 66
  • the bending moment M2 at the proximal end portion 66A of the scroll blade 66 is only the existing design without the step portion 80.
  • the bending moment M1 (see Fig. 2) at the proximal end portion of the scroll blade is 50%, whereby the scroll blade 66 according to the embodiment of the present invention is less likely to be broken under the same high rotation speed condition.
  • the height H of the step portion 80 is generally designed to be in the vortex
  • the height of the rotor blade 66 is between 10% and 90%.
  • the orbiting scroll member 60 of the above configuration may be manufactured by, for example, a die casting process, or may be formed by milling, for example, by using an existing orbiting scroll member, and thus the production of the orbiting scroll member constructed in accordance with the present invention The process is still relatively simple and the manufacturing is lower.
  • the bending moment at the proximal end portion of the scroll blade can be effectively reduced, thereby effectively reducing the possibility of the vortex blade rupture, thereby improving the vortex The durability of the rotating parts.
  • the gap between the second portion of the scroll blade having a small thickness of the orbiting scroll member and the scroll blade of the fixed scroll member can be effectively sealed by the lubricant, the compression efficiency of the compressor is not Will decrease.
  • the thickness of the portion of the scroll blade 66 of the orbiting scroll member 60 where the step portion is not formed is designed to have a relatively large thickness.
  • the thickness of the first portion 66-1 in the radial direction is the same, but the thickness of the portion of the scroll blade 66 of the orbiting scroll member 60 in which the step portion is not formed may be the thickness of the second portion having a relatively small thickness.
  • the thickness of the 66-2 in the radial direction is the same.
  • the step portion 90 is provided at least at the radially outermost side of the scroll blade 66 of the driven scroll member 60 and the scroll blade 56 of the other scroll member 50.
  • the contact point P1 extends inwardly in the circumferential direction by 360 degrees, but in the symmetrical design of the scroll member shown in FIG. 9, the step portion 80 may be provided at least at the scroll blade 66 of the driven scroll member 60.
  • the outer end portion 66D extends inwardly within a range of 360 degrees in the circumferential direction.
  • the thickness of the portion of the scroll blade 66 of the movable scroll member 60 in which the step portion is not formed may be designed to have the same thickness as the radial direction of the first portion 66-1, or It may be designed to be the same thickness as the radial direction of the second portion 66-2.
  • the step portion 80 may be disposed within the range from the outer end portion 66D of the scroll blade 66 of the driven scroll member 60 to the inner end portion 66C, as shown in FIG.
  • the projection 70 formed with the step portion 80 is formed in the radial direction of the scroll blade 66, and the surface 66 is formed on the radially outer side surface 66F, but is formed on the step side surface 66F.
  • the protrusion 70 in which the step portion 80 is formed is formed on the orbiting scroll member 60, but the protrusion portion 70 in which the step portion 80 is formed may also form a fixed scroll member. 50, as shown in Figure 11.
  • the fixed scroll member 50 may include an end plate 54 and a spiral wrap vane 56 formed on the end plate 54.
  • the scroll vanes 56 include a proximal end portion 56A proximate the end plate 54 and a distal end portion 56B distal from the end plate 54 in an axial direction (ie, a direction parallel to the central axis of the fixed scroll member 50).
  • the scroll blade 56 includes an inner end portion 56C near a substantially central position of the end plate and an outer end portion 56D near the outer peripheral side of the end plate in the circumferential direction (more precisely, the extending direction of the spiral of the scroll blade 56) .
  • the scroll blade 56 further includes a radially inner side surface 56E facing the center position of the end plate and a radially outer side surface 56F facing the outer peripheral side of the end plate.
  • both the radially inner side surface 56E and the radially outer side surface 56F are formed with projections 70 adapted to contact the corresponding scroll member of the other scroll member, such as the orbiting scroll member 60.
  • the projection 70 forms a step portion 80 on the radially inner side surface 56E and the radially outer side surface 56F.
  • Parameters such as the thickness, height, and circumferential extent of the step portion 80, as well as other variations, can be determined with reference to the configuration and variations of the orbiting scroll member 60 described above.
  • the protrusion 70 is configured in the form of a step portion 80, but the protrusion 70 may be configured in other forms, for example, the protrusion 70 may be configured to be formed on the radially inner side surface 66E of the scroll blade 66. And/or a raised portion on the radially outer side 66F.
  • the ridge portion may be provided at least in a range extending 360 degrees inward from the radially outermost contact point of the scroll blade of the scroll member and the scroll blade of the other scroll member in the circumferential direction. .
  • the ridge height of the ridge may be between 0.01 mm and 0.1 mm.
  • the height of the ridge portion in the axial direction from the end plate may be between 10% and 90% of the height in the axial direction of the scroll blade of the scroll member.
  • a scroll member for a scroll compressor comprising: an end plate; and a spiral wrap blade formed on the end plate, the wrap blade
  • the axial direction includes a proximal end portion adjacent the end plate and a distal end portion remote from the end plate, the scroll blade including an inner end portion in a circumferential direction near a substantially central position of the end plate and An outer end portion on an outer peripheral side of the end plate, and the scroll blade includes a radially inner side surface facing a center position of the end plate and a radially outer side surface facing an outer peripheral side of the end plate, wherein At least one of the radially inner side surface and the radially outer side surface may be formed with a protrusion adapted to contact a corresponding scroll blade of another scroll member, the protrusion being axially oriented The position is such that the distal end of the scroll vane does not contact the scroll vanes of the other scroll member during operation of the scroll compressor.
  • the protrusion may be configured to be on the radially inner side and/or Or a step portion is formed on the radially outer side surface.
  • the thickness of the scroll blade of the scroll member in the radial direction of the first portion of the step portion near the proximal end portion may be larger than the vortex of the scroll member
  • the thickness of the spiral blade in the radial direction of the second portion of the step portion near the distal end portion may be larger than the vortex of the scroll member
  • the step portion may be provided at least in a circumferential direction from a radially outermost contact point of the scroll blade of the scroll member and the scroll blade of the other scroll member The inside extends within a range of 360 degrees.
  • the thickness of the portion of the scroll blade of the scroll member where the step portion is not formed may be the same as the thickness of the first portion in the radial direction.
  • the thickness of the portion of the scroll blade of the scroll member where the step portion is not formed may be the same as the thickness of the second portion in the radial direction.
  • the step portion may be provided at least in a range extending 360 degrees inward from the outer end portion of the scroll blade of the scroll member in the circumferential direction.
  • the thickness of the portion of the scroll blade of the scroll member where the step portion is not formed may be the same as the thickness of the first portion in the radial direction.
  • the thickness of the portion of the scroll blade of the scroll member where the step portion is not formed may be the same as the thickness of the second portion in the radial direction.
  • the step portion may be provided in a range from an outer end portion of the scroll blade of the scroll member to the inner end portion.
  • the thickness of the step portion in the radial direction may be
  • the height of the step portion from the axial direction of the end plate may be between 10% and 90% of the height of the scroll blade in the axial direction of the scroll member .
  • the height of the step portion may be between 40% and 60% of the height of the scroll blade of the scroll member.
  • the height of the step portion may be the scroll member 50% of the height of the vortex blade.
  • the longitudinal section of the first portion and the second portion in a plane parallel to the axial direction may be both rectangular.
  • the protrusion portion may be formed on both the radially inner side surface and the radially outer side surface.
  • the scroll member may be a movable scroll member, and the other scroll member may be a fixed scroll member.
  • the scroll member is a fixed scroll member, and the other scroll member is a movable scroll member.
  • the scroll member may be an asymmetrically designed scroll member.
  • the scroll member may be a vortex member of a symmetrical design.
  • the protrusion may be formed as a ridge on the radially inner side surface and/or the radially outer side surface.
  • the ridge portion may be disposed at least in a circumferential direction from a radially outermost contact point of the scroll blade of the scroll member and the scroll blade of the other scroll member The direction extends inward by 360 degrees.
  • the ridge height of the ridge portion may be between 0.01 mm and 0.1 mm.
  • the height of the ridge portion from the axial direction of the end plate may be 10% to 90% of the height of the scroll blade in the axial direction of the scroll member. between.
  • a scroll compressor comprising the above scroll member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention porte sur un composant de volute (60, 50) pour compresseur à volute, le composant de volute comprenant : un flasque (64, 54); et une lame de volute hélicoïdale (66, 56) formée sur le flasque, la lame de volute comprenant une partie d'extrémité proche et une partie d'extrémité distante dans une direction axiale, comprenant une partie d'extrémité intérieure et une partie d'extrémité extérieure dans une direction circonférentielle, et comprenant également une face latérale intérieure radiale (66E, 56E) et une face latérale extérieure radiale (66F, 56F), et une partie saillante (70) qui est appropriée pour entrer en contact avec une lame de volute (56, 66) d'un autre composant de volute correspondant (50, 60) étant formée sur au moins l'une de la face latérale intérieure radiale et de la face latérale extérieure radiale. L'invention concerne aussi un compresseur à volute, qui comporte le composant de volute. Ce composant de volute peut réduire efficacement le risque de rupture de la lame de volute, en prolongeant ainsi la durabilité du composant de volute.
PCT/CN2013/090720 2013-03-04 2013-12-27 Composant de volute et compresseur à volute WO2014134961A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201320097796.8 2013-03-04
CN 201320097796 CN203114634U (zh) 2013-03-04 2013-03-04 涡旋部件和涡旋压缩机
CN201310068431.7 2013-03-04
CN201310068431.7A CN104033386B (zh) 2013-03-04 2013-03-04 涡旋部件和涡旋压缩机

Publications (1)

Publication Number Publication Date
WO2014134961A1 true WO2014134961A1 (fr) 2014-09-12

Family

ID=51490608

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2013/090720 WO2014134961A1 (fr) 2013-03-04 2013-12-27 Composant de volute et compresseur à volute

Country Status (1)

Country Link
WO (1) WO2014134961A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633198A1 (fr) * 2016-04-26 2020-04-08 LG Electronics Inc. Compresseur à spirales
US11209001B2 (en) 2016-04-26 2021-12-28 Lg Electronics Inc. Scroll compressor having wrap with reinforcing portion

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5958791U (ja) * 1982-10-09 1984-04-17 サンデン株式会社 スクロ−ル圧縮機
JPH1089268A (ja) * 1996-09-19 1998-04-07 Hitachi Ltd スクロール型流体機械
JP2001329974A (ja) * 2000-05-19 2001-11-30 Fujitsu General Ltd スクロール圧縮機
CN203114634U (zh) * 2013-03-04 2013-08-07 艾默生环境优化技术(苏州)有限公司 涡旋部件和涡旋压缩机

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5958791U (ja) * 1982-10-09 1984-04-17 サンデン株式会社 スクロ−ル圧縮機
JPH1089268A (ja) * 1996-09-19 1998-04-07 Hitachi Ltd スクロール型流体機械
JP2001329974A (ja) * 2000-05-19 2001-11-30 Fujitsu General Ltd スクロール圧縮機
CN203114634U (zh) * 2013-03-04 2013-08-07 艾默生环境优化技术(苏州)有限公司 涡旋部件和涡旋压缩机

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633198A1 (fr) * 2016-04-26 2020-04-08 LG Electronics Inc. Compresseur à spirales
US10648470B2 (en) 2016-04-26 2020-05-12 Lg Electronics Inc. Scroll compressor having wrap with an offset portion
US11209001B2 (en) 2016-04-26 2021-12-28 Lg Electronics Inc. Scroll compressor having wrap with reinforcing portion
US11408423B2 (en) 2016-04-26 2022-08-09 Lg Electronics Inc. Scroll compressor

Similar Documents

Publication Publication Date Title
JP6395059B2 (ja) スクロール圧縮機
US20100135836A1 (en) Scroll Compressor Having Capacity Modulation System
US10156236B2 (en) Scroll compressor with unloader assembly
KR101472664B1 (ko) 스크롤 압축기 및 그 스크롤의 가공 방법
US9353751B2 (en) Sealed scroll compressor for helium
JP4142418B2 (ja) スクロール式流体機械
KR101810903B1 (ko) 회전형 압축 기구
WO2017159393A1 (fr) Compresseur à volutes
WO2015018268A1 (fr) Compresseur à volutes
JP2008514865A (ja) スクリュー圧縮機シール
EP2484909B1 (fr) Machine à fluide avec volutes
WO2014134961A1 (fr) Composant de volute et compresseur à volute
US7559750B2 (en) Overheating protection apparatus of scroll compressor
JP2006307699A (ja) 圧縮機
US8092199B2 (en) Scroll compressor including a plurality of shoulder sections
JPH05248371A (ja) スクロール流体機械及びスクロール圧縮機
US9903368B2 (en) Scroll compressor
JP6409910B1 (ja) スクロール圧縮機
CN215256803U (zh) 旋转式压缩机
CN113700648B (zh) 旋转式压缩机
JPS62182486A (ja) スクロ−ル型圧縮機
CN215292888U (zh) 旋转式压缩机
KR102201409B1 (ko) 로터리 압축기
CN203114634U (zh) 涡旋部件和涡旋压缩机
CN104033386B (zh) 涡旋部件和涡旋压缩机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13877301

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13877301

Country of ref document: EP

Kind code of ref document: A1