EP0534891B1 - Scroll compressor with dual pocket axial compliance - Google Patents

Scroll compressor with dual pocket axial compliance Download PDF

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Publication number
EP0534891B1
EP0534891B1 EP92630087A EP92630087A EP0534891B1 EP 0534891 B1 EP0534891 B1 EP 0534891B1 EP 92630087 A EP92630087 A EP 92630087A EP 92630087 A EP92630087 A EP 92630087A EP 0534891 B1 EP0534891 B1 EP 0534891B1
Authority
EP
European Patent Office
Prior art keywords
scroll
back pressure
pressure chamber
scroll means
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92630087A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0534891A1 (en
Inventor
Jeffrey J. Nieter
Anthony J. Marchese
Raymond L. Beblois
Thomas R. Barito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Publication of EP0534891A1 publication Critical patent/EP0534891A1/en
Application granted granted Critical
Publication of EP0534891B1 publication Critical patent/EP0534891B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • This invention relates to scroll compressors, and more particularly to improving axial compliance between scroll elements thereby achieving higher efficiency in scroll compressors.
  • a conventional scroll compressor includes a motor, which drives a shaft with an eccentric crank, causing orbiting motion of an orbiting scroll element.
  • the orbiting scroll element has a scroll or spiral shaped protruding wrap, which interacts with a similarly shaped protruding wrap on a mating fixed element. Compression is achieved when the meshing coaction between the two protruding wraps shifts the gaseous fluid radially inward and simultaneously reduces the volume of the fluid.
  • Another approach to decrease tip leakage is to apply compensating back pressure to force mating elements together.
  • Higher pressure fluid is purposely bled from the compression chamber through a vent port into a back chamber, which is typically a single, relatively large chamber located behind the orbiting scroll.
  • This provides a body of pressurized fluid which pushes the orbiting element against the fixed element and thus, reduces the gap between the tips of the protruding scrolls and the bases of the elements. Reducing the gap minimizes the leakage of fluid, resulting in the increase of pressure in the compression chamber.
  • Commonly-assigned U.S. Pat. Nos. 4,992,032 and 4,993,928 also disclose scroll compressors using the back pressuring technique.
  • two sealed pressure chambers one at intermediate pressure and another at discharge pressure, are disposed behind the orbiting scroll element and are designed to counteract the gas compression forces within the compression chamber and to bias the orbiting scroll element toward the fixed scroll element.
  • the prior art back pressuring technique is designed to overcome the highest overturning moment experienced during the orbiting cycle and leads to excessive thrust force over the remainder of the cycle. The large thrust force causes excessive friction between the two mating parts and results in reduced efficiency of the scroll compressors.
  • U.S. Pat. No. 4,557,675 discloses a method of adjusting pressure in the back chamber by positioning pressure-equalizing ports so that the pressure vented into the back chamber varies with changes in operating conditions.
  • the back pressure remains relatively constant during any given steady-state condition, thus, the change in pressure, as the operating conditions vary, is intended to overcome the highest overturning moment and axial force, resulting in excessive thrust force during the remainder of the cycle and causing excessive friction, thereby reducing the efficiency of the scroll compressor.
  • An object of the invention is to increase the efficiency of scroll compressors by reducing frictional forces between the scrolls.
  • pressurized fluid is vented from the compression chamber into at least one dynamic back chamber through a port in the scroll element, so that the back pressure will vary on a sub-cycle basis.
  • a dynamic back chamber characterized by a relatively small volume of the chamber and a large flow area port for supplying pressure fluid thereto, is located behind the orbiting element.
  • a scroll compressor 10 includes a fixed scroll 11 which is engaged with an orbiting scroll 13.
  • the orbiting scroll 13 is driven by a shaft 17 which is driven by motor 15 in orbital movement relative to the fixed scroll 11.
  • Fluid compression is achieved as scroll wraps 18, 20 protruding from the orbiting scroll 13 and the fixed scroll 11, respectively, mesh to form a plurality of compression pockets 19 therebetween to trap volumes of fluid. This orbital action displaces the pockets of trapped fluid spirally inward while simultaneously reducing fluid volume of the pockets thereby compressing the fluid trapped therein.
  • a flow of pressurized fluid is bled through the ports 21, 23 into back chambers 25, 27, respectively.
  • the fluid in these chambers produces back pressure which pushes the orbiting scroll 13 towards the fixed scroll 11 in order to reduce tip leakage and counteract overturning moment.
  • the back pressure produced is not constant over the entire cycle. Instead, it varies during the cycle to follow the fluctuations in the overturning moment, which acts on the orbiting scroll 13 and causes it to tip with respect to the fixed scroll 11.
  • the back pressure created is just enough to counteract the overturning moment.
  • the overturning moment is high, greater back pressure is available to hold the orbiting scroll in place to avoid leakage.
  • the back pressure is also less and thus, does not cause excessive friction loss. This effect is attained by providing at least one dynamic chamber in which the pressure fluctuates in proportion to the overturning moment.
  • Port 23 supplies pressurized fluid into the static chamber 27.
  • Port 21 supplies pressurized fluid into dynamic chamber 25.
  • static chamber has a relatively constant fluid pressure throughout the entire cycle, while the dynamic chamber has widely varying fluid pressure during the cycle.
  • the static port/chamber combination has a small port diameter and a large chamber volume. The dimensions are selected in such a way as to produce sufficient damping so that pressure is nearly constant throughout the cycle.
  • the variation of pressure on a sub-cycle basis in the dynamic chamber is attained by properly sizing the port diameter and chamber volume parameters relative to each other.
  • the dynamic port/chamber pair has a large diameter port 21 and small chamber volume 25.
  • the dimensions are selected in such a way as to produce very little damping so that the pressure in the dynamic chamber follows the compression process. This achieves the pressure variation on a sub-cycle basis.
  • the ratio of port diameter to the cubed root of chamber volume should be relatively small. In order to provide widely varying pressure in the dynamic chamber the ratio should be relatively large. For example, when a compressor designed with a static chamber having the ratio of .05 and dynamic chamber having a ratio of .22 was tested, it exhibits a roughly 45% reduction in net axial force.
  • the embodiment illustrated has one dynamic and one static chamber/port combination, other combinations are possible.
  • This invention encompasses any number of dynamic chamber/port combinations that is one or more, with or without any number of static chambers. Since the total back pressure force on the scroll is the sum of the forces generated by the constant pressure in the static chamber and the varying pressure in the dynamic chamber, the total back pressure varies over the orbiting cycle instead of remaining constant, as in the prior art.
  • one port may lead to more than one chamber and vice-versa, more than one port may lead into one chamber, as long as the appropriate ratios of effective port diameter/cubed root of effective chamber volume are maintained.
  • Another variation that may yield substantially similar results is that back pressure may be applied to the fixed scroll, as opposed to the orbiting scroll, wherein the fixed scroll is able to move axially.
  • the exact position of ports is not critical to this invention and may depend on characteristics of each compressor, the port location selection should utilize the pressure variation inside the compression chamber in order to produce sufficient pressure in the back chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP92630087A 1991-09-23 1992-09-17 Scroll compressor with dual pocket axial compliance Expired - Lifetime EP0534891B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US76369191A 1991-09-23 1991-09-23
US763691 1991-09-23

Publications (2)

Publication Number Publication Date
EP0534891A1 EP0534891A1 (en) 1993-03-31
EP0534891B1 true EP0534891B1 (en) 1996-04-17

Family

ID=25068542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92630087A Expired - Lifetime EP0534891B1 (en) 1991-09-23 1992-09-17 Scroll compressor with dual pocket axial compliance

Country Status (8)

Country Link
EP (1) EP0534891B1 (es)
JP (1) JP3004483B2 (es)
KR (1) KR960004246B1 (es)
AU (1) AU650570B2 (es)
BR (1) BR9203702A (es)
DE (1) DE69209955T2 (es)
MX (1) MX9205379A (es)
TW (1) TW223674B (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2009272155B2 (en) * 2008-07-15 2012-06-14 Daikin Industries, Ltd. Scroll compressor

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5791887A (en) * 1996-10-17 1998-08-11 Scroll Technologies Scroll element having a relieved thrust surface
JP2001055988A (ja) 1999-06-08 2001-02-27 Mitsubishi Heavy Ind Ltd スクロール圧縮機
JP5499841B2 (ja) * 2010-03-31 2014-05-21 ダイキン工業株式会社 回転式圧縮機
US10995754B2 (en) 2017-02-06 2021-05-04 Emerson Climate Technologies, Inc. Co-rotating compressor
US11111921B2 (en) 2017-02-06 2021-09-07 Emerson Climate Technologies, Inc. Co-rotating compressor
WO2018145091A1 (en) * 2017-02-06 2018-08-09 Emerson Climate Technologies, Inc. Scroll compressor with axial flux motor
CN114729637A (zh) 2019-11-15 2022-07-08 艾默生环境优化技术有限公司 共旋转的涡旋式压缩机
US20230101084A1 (en) * 2021-09-30 2023-03-30 Samsung Electronics Co., Ltd. Scroll compressor
US11624366B1 (en) 2021-11-05 2023-04-11 Emerson Climate Technologies, Inc. Co-rotating scroll compressor having first and second Oldham couplings
US11732713B2 (en) 2021-11-05 2023-08-22 Emerson Climate Technologies, Inc. Co-rotating scroll compressor having synchronization mechanism

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6073080A (ja) * 1983-09-30 1985-04-25 Toshiba Corp スクロ−ル型圧縮装置
GB2162899B (en) * 1984-06-27 1988-06-15 Toshiba Kk Scroll compressors
US4600369A (en) * 1985-09-11 1986-07-15 Sundstrand Corporation Positive displacement scroll type apparatus with fluid pressure biasing the scroll
JPS63106388A (ja) * 1986-10-23 1988-05-11 Daikin Ind Ltd スクロ−ル流体装置
US4992032A (en) * 1989-10-06 1991-02-12 Carrier Corporation Scroll compressor with dual pocket axial compliance
US4993928A (en) * 1989-10-10 1991-02-19 Carrier Corporation Scroll compressor with dual pocket axial compliance
US5085565A (en) * 1990-09-24 1992-02-04 Carrier Corporation Axially compliant scroll with rotating pressure chambers

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2009272155B2 (en) * 2008-07-15 2012-06-14 Daikin Industries, Ltd. Scroll compressor

Also Published As

Publication number Publication date
DE69209955D1 (de) 1996-05-23
TW223674B (es) 1994-05-11
AU2529592A (en) 1993-03-25
JP3004483B2 (ja) 2000-01-31
AU650570B2 (en) 1994-06-23
DE69209955T2 (de) 1996-10-24
BR9203702A (pt) 1993-04-20
EP0534891A1 (en) 1993-03-31
KR930006329A (ko) 1993-04-21
MX9205379A (es) 1993-07-30
KR960004246B1 (ko) 1996-03-28
JPH05202865A (ja) 1993-08-10

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