WO2008007612A1 - compresseur à spirales - Google Patents

compresseur à spirales Download PDF

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Publication number
WO2008007612A1
WO2008007612A1 PCT/JP2007/063493 JP2007063493W WO2008007612A1 WO 2008007612 A1 WO2008007612 A1 WO 2008007612A1 JP 2007063493 W JP2007063493 W JP 2007063493W WO 2008007612 A1 WO2008007612 A1 WO 2008007612A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
fixed
volume ratio
orbiting
spiral wrap
Prior art date
Application number
PCT/JP2007/063493
Other languages
English (en)
Japanese (ja)
Inventor
Masami Negishi
Original Assignee
Sanden Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Corporation filed Critical Sanden Corporation
Priority to EP07768242A priority Critical patent/EP2039936A1/fr
Publication of WO2008007612A1 publication Critical patent/WO2008007612A1/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

Definitions

  • the present invention relates to a scroll compressor, and more particularly, to a scroll compressor suitable for compressing a working fluid whose working pressure is high.
  • This type of scroll compressor includes a scroll unit, and the scroll unit performs a series of processes from suction and compression of a working fluid to discharge.
  • the scroll unit includes a fixed scroll and an orbiting scroll, and each scroll has a spiral wrap and an end plate that support the spiral wrap.
  • the orbiting scroll revolves around the axis of the fixed scroll without rotating, that is, orbits.
  • the space defined between the fixed and orbiting scroll that is, the volume of the compression chamber is increased or decreased, and the above-described series of processes is performed.
  • a scroll unit (for example, see Patent Document 1) that prevents such overcompression of the working fluid is known.
  • This scroll unit has a plurality of communication passages as well as a discharge hole for discharging the working fluid compressed by the end plate of the fixed scroll to the discharge chamber.
  • the discharge hole is positioned substantially at the center of the end plate, and at the end of compression of the working fluid, the compression chamber and the discharge chamber are communicated with each other through the discharge valve.
  • the compression chamber and the discharge chamber are communicated with each other through a valve during the compression of the working fluid.
  • Patent Document 1 Japanese Patent No. 3635826
  • 2 2 may be over-compressed, and such over-compression will reduce the performance of the refrigeration cycle.
  • the scroll compressor of the present invention includes a scroll unit that performs a series of processes from suction of a working fluid to compression and discharge, and the scroll unit is a single unit.
  • a fixed scroll having a discharge hole and a orbiting scroll that orbits with respect to the fixed scroll, and forms two transient compression chambers into which working fluid is sucked in cooperation with the fixed scroll, and thereafter
  • a orbiting scroll that forms a compression chamber in a final compression chamber grouped together at the center of the scroll boot, and the final compression chamber has a capacity equal to the suction volume of the transient compression chamber when the working fluid is sucked.
  • the transient compression chamber has a volume ratio of 0.5 or more when the ratio of the volume of the immediately preceding transient compression chamber formed is expressed as a volume ratio.
  • the volume ratio of the two transient compression chambers formed in the scroll unit is maintained at 0.5 or more until the final compression chamber is formed. Therefore, even when the scroll unit compresses the working fluid having a high working pressure, the compression ratio of the working fluid is kept small, and excessive compression of the working fluid is prevented.
  • the fixed scroll of the present invention is formed as a fixed end plate having discharge holes formed therein, a fixed spiral wrap protruding toward the orbiting scroll from the fixed end plate, an inner peripheral end of the fixed spiral wrap, and And a volume ratio determining unit positioned in the vicinity of the discharge hole.
  • the volume ratio determining unit has an outer shape that fills a space near the discharge hole and partially surrounds the opening edge of the discharge hole.
  • the volume ratio determining unit includes an inner wall adjacent to the discharge hole, an outer wall connected to the inner wall and the outer wall of the fixed spiral wrap, and having an arc shape protruding outward in the radial direction of the fixed spiral wrap. .
  • the fixed scroll described above it is possible to easily obtain the volume ratio determining unit simply by improving the profile of the existing fixed spiral wrap. As a result, the manufacturing cost can be reduced while maintaining the performance of the scroll compressor.
  • the volume ratio determining section has a cavity, and in this case, the light weight of the scroll compressor can be achieved.
  • the orbiting scroll includes an orbiting end plate facing the fixed end plate, and an orbiting spiral wrap protruding from the orbiting end plate toward the fixed scroll and engaging with the fixed spiral wrap.
  • the swirling spiral wrap has an inner peripheral edge that periodically contacts the volume ratio determining portion.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention.
  • FIG. 2 is a front view of the fixed skeleton of FIG.
  • FIG. 4 is a diagram illustrating a compression process by the scroll unit of FIG.
  • FIG. 5 is a cross-sectional view of a fixed scroll according to another embodiment.
  • the scroll compressor 1 in FIG. 1 circulates a working fluid such as an air conditioner or a heat pump type hot water heater.
  • a working fluid such as an air conditioner or a heat pump type hot water heater.
  • CO refrigerant hereinafter referred to as refrigerant
  • the compressor 1 performs refrigerant suction from the circulation path, compression of the sucked refrigerant, and discharge of the compressed refrigerant to the circulation path, and circulates the refrigerant in the circulation path.
  • the compressor 1 includes a housing 2.
  • the housing 2 includes a cylindrical barrel portion 4 extending in the vertical direction, and an upper lid 6 and a lower lid 8 that hermetically close the upper end and the lower end of the barrel portion 4, respectively, and define an airtight chamber therein.
  • the lower part of the housing 2 is formed as an oil chamber 9 that stores lubricating oil.
  • An electric motor 10 is accommodated in the body 4, and the motor 10 has a hollow drive shaft 12 at the center thereof.
  • the drive shaft 12 is rotated in one direction.
  • An upper end portion of the drive shaft 12 is rotatably supported by the upper frame 14 via a bearing 16, and the upper frame 14 is fixed to the body portion 4.
  • the lower end portion of the drive shaft 12 is rotatably supported by the lower frame 18 via the bearing 20, and the lower frame 18 is also fixed to the trunk portion 4.
  • An oil pump 22 is attached to the lower end of the drive shaft 12, and the oil pump 22 is driven by the rotation of the drive shaft 12.
  • the oil pump 22 sucks the lubricating oil in the oil chamber 9 and discharges the sucked lubricating oil into the drive shaft 12, that is, the oil passage 24 defined in the drive shaft 12.
  • the oil passage 24 extends in the axial direction of the drive shaft 12, and the lubricating oil discharged into the oil passage 24 is transferred through the oil passage 24 and supplied toward the upper end of the drive shaft 12, and the upper end force of the drive shaft 12 is It is supplied to each sliding part of the motor 10 and a scroll unit described later.
  • the scroll unit 30 is disposed in the body portion 4 and is positioned above the motor 10.
  • the scroll unit 30 performs a series of processes from the suction input compression of the refrigerant to the discharge.
  • the scroll unit 30 includes a turning scroll 52 and a fixed scroll 32.
  • the orbiting scroll 52 has an end plate 54 and a spiral wrap 56 formed integrally with the end plate 54, and the spiral wrap 56 projects from the end plate 54 toward the end plate 34 of the fixed scroll 32.
  • the fixed scroll 32 has an end plate 34 and a spiral wrap 36 formed integrally with the end plate 34, and the spiral wrap 36 extends from the end plate 34 to the end of the orbiting scroll 52. Projects toward the plate 54.
  • the spiral wraps 34 and 56 have a spiral shape that squeezes together, and this spiral shape is substantially defined by the involute.
  • the spiral wraps 36 and 56 cooperate with each other to perform a plurality of compressions.
  • a box 66 is formed on the lower surface of the end plate 54 thereof.
  • the boss 66 is rotatably supported on an eccentric shaft 26 via a bearing 28, and the eccentric shaft 26 projects the upper end force of the drive shaft 12 together. Further, the rotation of the turning scroll 52 is prevented by a plurality of pins 68, which protrude from the end plate 54 toward the upper frame 14 and are positioned in the holes of the upper frame 14. This hole determines the turning radius of the pin 68.
  • the fixed scroll 32 is fixed to the upper frame 14, and a discharge chamber 80 is defined in the housing 2 between the end plate 34 of the fixed scroll 32 and the upper lid 6.
  • the end plate 34 has a single discharge hole 50, and this discharge hole 50 is positioned at a position slightly decentered from the center of the end plate 34 and penetrates the end plate 34. Speak.
  • a discharge valve 82 is attached to the end plate 34, and the discharge valve 82 opens and closes the discharge hole 82.
  • a suction pipe 84 is connected to the body 4, and the suction pipe 84 guides the refrigerant into the body 4.
  • the suction volume of the CO refrigerant in the scroll unit 30 is represented by Vc, and
  • the ratio of the volume V to the suction volume Vc that is, the volume ratio VZVc is set to 0.5 or more. Has been.
  • This volume ratio VZVc setting is optimal when compressors for heat pump water heaters that have been commercialized in recent years are used for CO refrigerant compression. Specifically, this
  • the volume ratio VZVc of 0.5 or more corresponds to a compression ratio of about 2.0 or less in terms of the compression ratio of the refrigerant.
  • the scroll unit 30 includes the inside of the spiral wrap 36 that discharges the compressed refrigerant from the scroll unit 30 at a crank angle at which the volume ratio VZVc is 0.5 or more. While the volume ratio setting portion is provided at the peripheral end, the position of the inner peripheral end of the spiral wrap 56, that is, the start position of the involute winding in the spiral wrap 56 is determined.
  • the volume ratio determining portion of the spiral wrap 36 is formed as a space filling portion 38 that increases the volume of the inner peripheral end of the spiral wrap 36.
  • the portion 38 fills the space in the substantially central portion of the end plate 34.
  • the space filling portion 38 protrudes from the end plate 34 toward the orbiting scroll 52 like the spiral wrap 36.
  • the outer shape of the space filling portion 38 is formed by an inner wall 40 facing the discharge hole 50 and an outer wall 42 having a convex arc shape toward the radially outer side of the spiral wrap 36. ing. After the inner wall 40 extends from the inner peripheral surface of the spiral wrap 36 toward the discharge hole 50, it surrounds approximately half the circumference of the opening edge of the discharge hole 50 (the right half of the opening edge of the discharge hole 50 as viewed in FIG. 2) Then, it extends from the discharge hole 50 toward the outer wall 42 and is connected to the end of the outer wall 42.
  • the inner peripheral end of the spiral wrap 56 is formed as a retracted end 58 that is retracted in the spiral direction of the spiral wrap 56 in order to avoid interference with the space filling portion 38 described above.
  • the retracted end 58 is brought into contact with and separated from the inner wall 40 of the space filling portion 38 located above the discharge hole 50 as seen in FIG. Turn. Therefore, at the end of the refrigerant compression process, the spiral wrap 56 and the space filling portion 38 of the spiral wrap 36 cooperate with each other to form a final compression chamber 74, which Refrigerant compression ratio corresponding to volume ratio VZVc is achieved.
  • the orbiting scroll 52 when the drive 12 is driven as described above, the orbiting scroll 52 performs the orbiting motion with respect to the fixed scroll 32 without rotating. Such a turning motion of the orbiting scroll 52 causes the refrigerant in the body 4 to be sucked into the scroll unit 30 from the outer peripheral side of the scroll unit 30, and thereafter, the scroll unit 30 starts a compression process of the sucked refrigerant. To do.
  • the compression chambers 70 and 72 are respectively generated at two refrigerant suction positions separated from each other in the diameter direction of the scroll unit 30, and moved to a position where the crank angle is 0 °.
  • the volume of the compression chamber 74 is reduced.
  • the crank angle of the orbiting scroll 52 shifts from 1800 ° to 270 °
  • the volume of the compression chamber 74 is reduced to a range less than 0.5 times the suction volume Vc (see Fig. 3).
  • the discharge valve 82 is opened. At this time, the compressed refrigerant in the compression chamber 74 is discharged to the discharge chamber 80 through the discharge valve 82.
  • a refrigerant discharge pressure corresponding to a compression ratio of about 2.0 or more is generated.
  • the compressed refrigerant discharged into the discharge chamber 80 circulates in the housing 2 and is then sent out through the discharge pipe 86.
  • the discharge pipe 86 is attached to the upper lid 6 and connected to the discharge chamber 80. That is, in the case of the present embodiment, the discharge chamber 80 is not defined in the housing 2 but communicates with the body 4 that houses the motor 10.
  • the compression chambers 70 and 72 immediately before the one compression chamber 74 is finally formed from the two compression chambers 70 and 72.
  • Each volume ratio is set to 0.5 or more. Therefore, even if the scroll unit 30 is operated during the summer when the refrigerant compression efficiency is low due to changes in the refrigerant density or during the severe winter when the refrigerant compression efficiency is high, The refrigerant discharge pressure is not increased excessively, and excessive compression of the refrigerant is prevented.
  • the large diameter of the discharge hole 50 becomes possible.
  • the large diameter of the discharge hole 50 reduces the pressure loss at the discharge hole 50 and greatly contributes to the reduction in power required by the scroll unit 30.
  • the condition that the volume ratio VZVc is 0.5 or more is that the space filling portion 38 is formed at the inner peripheral end of the spiral wrap 36 in the fixed scroll 32, while the inner peripheral end of the spiral wrap 56 in the orbiting scroll 52. This is accomplished simply by forming the receding end 58. Therefore, by simply improving the profile of the existing spiral wraps 36, 56, excessive refrigerant compression is prevented. As a result, it is possible to reliably achieve a reduction in manufacturing cost while maintaining the performance of the scroll unit 30.
  • the space filling portion 38 is not limited to a solid portion, and as shown in FIG. Can have. In this case, the light weight of the fixed scroll 32 can be achieved.
  • the starting angle of the spiral wraps 36, 56 can be delayed by about 10 ° to about 45 ° in terms of the crank angle.
  • the inner peripheral ends of the spiral wraps 36 and 56 are respectively formed as receding ends, the above-described condition of the volume ratio VZVc can be achieved.
  • the present invention is similar to the above-described embodiment.
  • the present invention can also be applied to an asymmetric scroll unit that forms compression chambers 70 and 72 having different shapes, as opposed to a symmetrical scroll unit that forms compression chambers 70 and 72 having different shapes.

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

Abstract

L'invention concerne un compresseur à spirales comprenant une unité à spirales (30) comprenant une spirale fixe (32) possédant un simple trou de décharge (50), et une spirale rotative (52) assurant un mouvement rotatif par rapport à la spirale fixe (32). Ces spirales (32, 52) coopèrent pour constituer deux chambres de compression transitoires (70, 72) dans lesquelles le fluide de travail est aspiré. Ces chambres de compression transitoires (70, 72) sont consolidées au niveau de la partie centrale de l'unité à spirales (30) en une chambre de compression finale (74). Lorsque le rapport entre le volume des chambres de compression transitoires (70, 72) juste avant la formation de la chambre de compression finale (74) et le volume d'aspiration des chambres de compression transitoires (70, 72) pendant l'aspiration du fluide de travail est représenté comme un rapport volumique, les chambres de compression transitoires (70, 72) présentent un rapport volumique supérieur ou égal à 0,5.
PCT/JP2007/063493 2006-07-10 2007-07-05 compresseur à spirales WO2008007612A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07768242A EP2039936A1 (fr) 2006-07-10 2007-07-05 Compresseur à spirales

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006189137A JP2008014288A (ja) 2006-07-10 2006-07-10 スクロール圧縮機
JP2006-189137 2006-07-10

Publications (1)

Publication Number Publication Date
WO2008007612A1 true WO2008007612A1 (fr) 2008-01-17

Family

ID=38923173

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/063493 WO2008007612A1 (fr) 2006-07-10 2007-07-05 compresseur à spirales

Country Status (3)

Country Link
EP (1) EP2039936A1 (fr)
JP (1) JP2008014288A (fr)
WO (1) WO2008007612A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5656691B2 (ja) * 2011-03-04 2015-01-21 三菱電機株式会社 冷凍装置
WO2021040360A1 (fr) 2019-08-27 2021-03-04 Samsung Electronics Co., Ltd. Compresseur à spirale
US11255325B2 (en) * 2019-11-04 2022-02-22 Lennox Industries Inc. Compressor for high efficiency heat pump system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03275901A (ja) * 1990-03-23 1991-12-06 Iwata Air Compressor Mfg Co Ltd スクロール式流体機械
JP2000130369A (ja) * 1998-10-23 2000-05-12 Denso Corp 圧縮機及び超臨界冷凍サイクル
JP2001107881A (ja) * 1999-10-06 2001-04-17 Daikin Ind Ltd 流体機械
JP2002221169A (ja) * 2001-01-25 2002-08-09 Nippon Soken Inc スクロール圧縮機
JP2006009640A (ja) * 2004-06-24 2006-01-12 Matsushita Electric Ind Co Ltd スクロール圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03275901A (ja) * 1990-03-23 1991-12-06 Iwata Air Compressor Mfg Co Ltd スクロール式流体機械
JP2000130369A (ja) * 1998-10-23 2000-05-12 Denso Corp 圧縮機及び超臨界冷凍サイクル
JP2001107881A (ja) * 1999-10-06 2001-04-17 Daikin Ind Ltd 流体機械
JP2002221169A (ja) * 2001-01-25 2002-08-09 Nippon Soken Inc スクロール圧縮機
JP2006009640A (ja) * 2004-06-24 2006-01-12 Matsushita Electric Ind Co Ltd スクロール圧縮機

Also Published As

Publication number Publication date
EP2039936A1 (fr) 2009-03-25
JP2008014288A (ja) 2008-01-24

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