EP0049495A1 - Appareil à déplacement de fluide à volutes imbriquées - Google Patents

Appareil à déplacement de fluide à volutes imbriquées Download PDF

Info

Publication number
EP0049495A1
EP0049495A1 EP19810107856 EP81107856A EP0049495A1 EP 0049495 A1 EP0049495 A1 EP 0049495A1 EP 19810107856 EP19810107856 EP 19810107856 EP 81107856 A EP81107856 A EP 81107856A EP 0049495 A1 EP0049495 A1 EP 0049495A1
Authority
EP
European Patent Office
Prior art keywords
wrap means
fluid
scroll
scroll type
center portion
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.)
Granted
Application number
EP19810107856
Other languages
German (de)
English (en)
Other versions
EP0049495B1 (fr
Inventor
Kiyoshi Terauchi
Masaharu Hiraga
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP0049495A1 publication Critical patent/EP0049495A1/fr
Application granted granted Critical
Publication of EP0049495B1 publication Critical patent/EP0049495B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0215—Rotary-piston machines or engines 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

Definitions

  • This invention relates to a fluid displacement apparatus of the scroll type,such as a compressor,expander,or pump.
  • Scroll type fluid displacement apparatus are well known in the prior art.
  • U.S.Patent No. 801,182 discloses a scroll type fluid displacement apparatus including two scroll members,each having a circular end plate and a spiroidal or involute spiral element. These scroll members are maintained angularly and radially offset so that both spiral elements interfit to make a plurality of line contacts between spiral curved surfaces to thereby seal off and define at least one pair of fluid pockets.
  • the relative orbital motion of the two scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the fluid pockets change in volume.
  • the volume of the fluid pockets increases or decreases depending on the direction of the orbiting motion. Therefore, the scroll type fluid displacement apparatus is applicable to compress,expand or pump fluids.
  • the discussion which follows deals only with scroll type devices used as compressors for the sake of convenience.
  • the scroll type compressor In comparison with a conventional compressor of the piston-type, the scroll type compressor has certain advantages,such as fewer parts and continuous compression of fluid.
  • the sealing of the fluid pockets primarily in the sealing of the fluid pockets. Sealing of the fluid pockets must be sufficiently maintained at axial and radial interfaces in the scroll type fluid apparatus, because the fluid pockets are defined by the line contacts between the interfitting spiral elements and axial contact between the axial end surfaces of the spiral elements and the inner end surfaces of the end plates.
  • Figs. 1a-1d schematically illustrate the relative movement of interfitting spiral elements to compress the fluid.
  • Fig. 2 diagrammatically illustrates the compression cycle in the each of the fluid pockets.
  • Fig. 3 schematically illustrates the typical interfitting relationship of prior art spiral elements.
  • Figs.1a-1d may be considered to be end view of a compressor wherein the end plates are removed and only the spiral elements are shown.
  • .Two spiral elements 1 and 2 are angularly offset and interfit with one another. As shown in Fig. 1a, the orbiting spiral element 1 and fixed spiral element 2 make four line contacts as shown at four points A-D. A pair of fluid pockets 3a and 3b are defined between line contacts D-C and line contacts A-B, as shown by the dotted regions. The fluid pockets 3a and 3b are defined not only by the wall of spiral elements 1 and 2 but also by the end plates from which these spiral elements extend.
  • both pockets 3a and 3b merge at the center portion 5 and are completely connected to one another to form a single pocket.
  • the volume of the connected single pocket is further reduced by further revolution of 90° as shown in Figs. 1b,1c and 1d.
  • outer spaces which open in the state shown in Fig. 1b change as shown in Figs. 1c,1d and 1a, to form new sealed off pockets in which fluid is newly enclosed.
  • FIG.2 shows the relationship of fluid pressure in the fluid pocket to crank angle, and shows that the one compression cycle is completed at a crank angle of 4 ⁇ in this case.
  • the compression cycle begins (Fig.1a) with the outer end of each spiral element in contact with the opposite spiral element, the suction stroke having finished.
  • the state of fluid pressure in the fluid pocket is shown at point K in Fig.2.
  • the volume of the fluid pocket is reduced and compressed by the revolution of the orbiting scroll member until the crank angle reaches 2 ⁇ , which state is shown by the point L in Fig. 2.
  • the pair of fluid pockets are connected to one another and simultaneously are connected to the space filled with high pressure,which is connected to the discharge chamber and is formed at the center of both spiral elements At this time,if the compressor is not provoded with a discharge valve,the fluid pressure in the connected fluid pockets suddenly rises to equal the pressure in the discharge chamber.
  • the compressor is provided with a discharge valve
  • the fluid pressure in the connected fluid pockets rises slightly due to the mixing of the high pressure fluid and the fluid in the connecting fluid pockets. This state is shown at point M in Fig.2.
  • the fluid in the high pressure space is further compressed by revolution of the orbiting scroll member until it reaches the discharge pressure. This state is shown at point N in Fig. 2.
  • the fluid pressure in the high pressure space reaches the discharge pressure
  • the fluid is discharged to the discharge chamber through the discharge hole by the operation of the discharge valve. Therefore,fluid pressure in the high pressure space is maintained at the discharge pressure until a crank angle of 4 1T (point 0).
  • Line contact between spiral elements is dinned by several pairs of points, as shown in Fig.3. However,it is very difficult to attain complete contact at all points. If the line contact between spiral elements is imperfect at one or more points to form a gap,fluid leakage through the gap will occur during operation to allow the outer pockets to contain gas with high pressure than the ideal case. The volumetric efficiency of the compressor and, hence, its refrigeration capacity will thereby be reduced. Especially, fluid leakage across the line contact separating pair of fluid pockets from the high pressure space is very serious problem.
  • the curve of the spiral elements is usually an involute curve of a circle,each spiral having the same pitch (the pitch shown as distance a 1 -a 2 , a 2 -a n , or b 1 -b 2 , b 2 -b n in Fig.3),and these two spiral elements interfit at an angular and radial offset,so that the spiral elements make a plurality of line contacts which are represented by points a 1 -a n and b 1 -b n in Fig.3.
  • a scroll type fluid displacement apparatus includes a housing and a pair of scroll members.
  • One of the scroll members is fixedly disposed relative to the housing and has an end plate from which a first spiral wrap extends into the interior of the housing.
  • the other scroll member is movably disposed for non-rotative orbital movement within the interior of the housing and has an end plate from which a second spiral wrap extends.
  • the first and second wrap are interfitted at an angular and radial offset to make a plurality of line contacts to define at least one pair of sealed off fluid pockets.
  • a driving mechanism is operatively connected to the other scroll member to effect its orbital motion, whereby the fluid pockets move inwardly and change in volume.
  • the two innermost pockets eventually are merged into a single pocket near the center of the wrap.
  • the center portions of the wrap are thicker than the remaining portions thereof.
  • the center portions extend substantially from the inner ends of the wrap outwardly at least throughout the portions thereof which contact one another when the two innermost fluid pockets are merged into a
  • a refrigerant compressor unit which includes a compressor housing 10 comprising a front end plate 11 and a cup-shaped casing 12 disposed on the end surface of front end plate 11.
  • a fixed scroll member 13,an orbiting scroll member'14, a driving mechanism and a rotation preventing/thrust bearing mechanism of orbiting scroll member 14 are disposed within an inner suction chamber of cup-shaped casing 12. These mechanisms are-described in detail below.
  • the inner chamber is defined by the side wall of cup-shaped casing 12, the inner end surface of front end plate 11, and fixed scroll member 13.
  • Fixed scroll member 13 includes a circular end plate 131 and a involute wrap or spiral element 132 affixed to and extending from one major end surface of end plate 131.
  • End plate 131 of fixed scroll member 13 is formed with a plurality of internally threaded bosses 133 axially projecting from a major end surface of plate 131 opposite the side thereof from which spiral element 132 extends.
  • the end of each boss 133 abuts the inner surface 121 of cup-shaped casing 12, and is fixed to casing 12 by screws 15 which screw into bosses 133 from the outside of casing 12.
  • fixed scroll member 13 is fixedly disposed within cup shaped casing 12.
  • End plate 131 of fixed scroll member 13 partitions the interior of cup-shaped casing 12 into two chambers, a discharge chamber 16 and a suction chamber 17,and a sealing member 135 is disposed between the outer periphery of end plate 131 and the inner wall of cup-shaped casing 12 to isolate these two chambers.
  • Orbiting scroll member 14 is disposed in suction chamber 17 and also comprises a circular end plate 141 and a involut wrap or spiral element 142 affixed to and extending from one end surface of end plate 141. Spiral element 142 and spiral element 132 of fixed scroll member 13 are interfitted at an angular offset of 180° and a predetermined radial offset. A pair of fluid pockets are thereby defined between spiral elements 132,142. Orbiting scroll member 14 is connected to the driving mechanism and the rotaion preventing/thrust bearing mechanism. These mechanisms effect the orbital motion of orbiting scroll member 14 at a circular radius R 0 by the rotation of a drive shaft 18,to thereby compress the fluid in the fluid pockets,as described in connection with Figs.1a-1d.
  • Drive shaft 18 is rotatably supported by a sleeve portion 111 of front end plate 11 through a bearing 21 and is formed with a disk portion 181 at its inner end portion. Disk portion 181 is also rotatably supported by front end plate 11 through a bearing 22 which is disposed within an opening of front end plate 11.
  • a crank pin or drive pin 182 projects axially from an end surface of disk portion 181 and,hence,from an end of drive shaft 18, and is radially offset from the center of drive shaft 18.
  • End plate 141 of orbiting scroll member 14 is provided with a tubular boss 143 axially projecting from the end surface opposite to the surface thereof from which spiral element 142 extends.
  • a discoid or short axial bushing 23 is fitted into boss 143,and is rotatably supported therein by bearing,such as a needle bearing 24.
  • Bushing 23 has a balance weight 231 which is shaped as a portion of a disc or ring and extends radially from bushing 23 along a front surface thereof.
  • An eccentric hole 232 is formed in bushing 23 radially offset from the center of.bushing 23.
  • Drive pin 182 is fitted into the eccentrically disposed hole 232 within which bearing 25 may be applied.
  • Bushing 23 is therefore driven by the revolution of drive pin 182 and permitted to rotate by the needle bearing 24.
  • FIG.6 Respective location of center 0 of drive shaft 18, center 0 c of bushing 23,and center 0 d of hole 232 and thus drive pin 182 is shown in Fig.6.
  • the distance between 0 s and 0 c is the representative radius R o of orbital motion of the orbiting scroll member 14,and when drive pin 182 is placed in eccentric hole 232,center 0 d of drive pin 182 is placed, with respect to 0 s , on the opposite side of a line L 1 ,which is through 0 and perpendicular to a line L 2 through 0 and 0 s , and also beyond the line through 0 c and 0 in direction of rotation A of drive shaft 18.
  • center 0 c of bushing 23 is permitted to swing about the center 0 d of drive pin 182 at a radius E 2 .
  • such swing motion of center 0 c is illustrated as arc 0 c '-0 c " in Fig.6.
  • This permitted swing motion allows the orbiting scroll member 14 to compensate its motion for changes in radius R due to wear on the spiral elements or due to dimentional inaccuracies of the spiral elements.
  • a drive force F d is applied to the left at tenter 0 d of drive pin 182 and a reaction force F r of gas compression appears to the right at center 0 of bushing 33, both forces being parallel to line L 1 . Therefore,the.
  • arm 0 d -0 c can swing outwardly by creation of the movement generated by the two forces.
  • Spiral element 142 of orbiting scroll member 14 is thereby forced . toward spiral element 132 of fixed scroll member 13 to make at least one pair of contact among several pair of sealing points which will be explained later,and the center of orbiting scroll member 14 orbits with the representative radius R o around center 0 s of drive shaft 18.
  • the rotation of orbiting scroll member 14 is prevented by the rotation preventing/thrust bearing mechanism 26 (Fig.7),whereby orbiting scroll member 14 orbits while maintaining its angular orientation relate to fixed scroll member 13.
  • a rotation preventing/thrust bearing mechanism 26 surrounds boss 143 and comprises a fixed ring 261 and Oldham ring 262.
  • Fixed ring 261 is secured to an inner surface of housing 10.
  • Fixed ring 261 is provided with a pair of keyways 261a,261b in an axial end surface facing orbiting scroll member 1 4.
  • Oldham ring 262 is disposed in a hollow portion between fixed ring 261 and end plate'141 of orbiting scroll member 14.
  • Oldham ring 262 is provided with a pair of keys 262a,262b on the surface facing fixed ring 261,which are received in keyways 261a,262b.
  • Oldham ring 262 is linearly slidable relative to fixed ring 261 by the guide of keys 262a,262b within keyways 261a,261b.
  • Oldham ring 262 is also provided with a pair of keys 262c,262d on its opposit surface. Keys 262c,262d are arranged along a diameter perpendicular to the diameter along which keys 262a,262b are arranged.
  • Circular end plate 141 of orbiting scroll member 14 is provided with a pair of keyways (in Fig.7 only one keyway 141a is shown; the other keyway is disposed diametrically opposite keyway 141a) on the surface facing Oldham ring 262 in which are received keys 262c,262d. Therefore,orbiting scroll member 14 is linearly slidable relative to Oldham ring 262.by the guide of keys 262c,262d within the keyways of end plate 141.
  • Oldham ring 262 is provided with a plurality of holes or pockets 27, and a bearing element , such as balls 28 ) having a diameter which is greater than the thickness of Oldham ring 262,is retained in each pocket 27. Balls 28 contact and roll on the surface of fixed ring 261 and circular end plate 141 of orbiting scroll member 14. Therefore,the thrust load from orbiting scroll member 14 is supported on fixed ring 261 through balls 28.
  • the radius R of orbital motion is determined by one contact point between the spiral elements having the minimum of the angle ⁇ 0 c 0 d 0 s .
  • Bushing 23 is supported to permit swing motion about drive pin 182,and this swing motion allows the orbiting scroll member 14 to compensate its motion for variation of radius R .
  • spiral element 142 of orbiting scroll member 14 is forced toward spiral element 132 of fixed scroll member 13 by the driving moment.
  • the radius R is determined by the combination of the errors of the spiral elements, for example by,either a combination of the maximum inward deviation of the inner wall of the fixed spiral element 132 and the maximum outward deviation of the outer wall of the orbiting spiral element 142 or a combination of the maximum outward deviation of the outer wall of the fixed spiral element 132 and the maximum inward deviation of the inner wall of the orbiting spiral element 142, from the theoretical involute curve for each wall.
  • Fig.8 shows the configuration of spiral elements according to one embodiment of the present invention.
  • the wall of the center portion of each spiral elements is made slightly thicker (by ⁇ in Fig.8) by making a slight step along the inner wall thereof.
  • the thicker portion of each spiral element extends from the inner, end portion or tip of the spiral element (shown at point A in Fig.8) to a location along the spiral which is spaced from the tip by an involut angle of at least 2 7F (shown at point B in Fig.8).
  • the outer portion of each spiral element extends from point B to the outermost end of the spiral element (shown at point D in Fig.8)with a reduced thickness.
  • portion B-D when the thickness of portion B-D has a dimentional error ( ⁇ E) of less than the step ( ⁇ ) between portion A-B and portion B-D will not disturb the sealing of the high pressure space.
  • the fluid leakage across the gap at the line contacts between the outer portion (B-D) of the spirals is considered to be minimal because the pressure difference between outer fluid poukets is small. Deterioation of resultant volumetric efficiency of the compressor is thereby permissible.
  • Fig.9 shows a modification of the embodiment shown in Fig.8, wherein the center portion of each spiral element is made thicker by a slight step ( ⁇ ) on the inner and outer walls thereof.
  • These thicker portion extend from the inner end portion.or tip of each spiral element 132,142 (shown at point A in Fig.9) at least throughout the portion of the spiral elements which contact one another when the pair of fluid pockets are connected to the high pressure space (shown at points B and C in Fig.9).
  • the slightly thinner outer portion extends from the points B or C to the terminal ends of both spiral elements 132,142 (shown at point D and E in Fig. 9).
  • the transition between the thicker portion and the thinner portion of each spiral is shown in Figs. 8 and 9 to be steplike. However,the transition can be arcuate,rather than stepped,as shown in Fig.10.
  • the radius of curvature of the arcuate transition portion is determined by the radius of the milling tool M used to form the spiral element.
  • the arcuate transition portion is formed when the milling tool reaches the end of its travel after forming an adjacent portion of spiral.
  • Fig.11a shows another embodiment of the present invention, which is charactrized in that the inner wall of the outer portion of the spiral element starts deviating from a true involut curve at point B to form a portion of gradually reduced thickness.
  • the wall thickness of the inner portion which is between the inner end portion or tip of each spiral element (point A) and point B, is uniform. Since the wall thickness between point B and the outer terminal end (point D) gradually reduces, the gap ( ⁇ ) between the spiral elements will be a function of the involut angle.
  • Figs. 11b and 11c show modifications of the embodiment shown in Fig.11a, wherein the center portion of each spiral elements is formed to a true involute curve and the outer wall of the outer portion of the spiral element starts deviating from a true involute curve at point C to form a portion of gradually reduced thickness (shown in Fig.11b) or the inner and outer wall of the outer portion of the spiral elements starts devisting from a true involute curve at points B and C to form a portion of gradually reduced thickness (shown in Fig.11c).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Rotary Pumps (AREA)
EP19810107856 1980-10-03 1981-10-02 Appareil à déplacement de fluide à volutes imbriquées Expired EP0049495B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP138289/80 1980-10-03
JP13828980A JPS586075B2 (ja) 1980-10-03 1980-10-03 スクロ−ル型圧縮機

Publications (2)

Publication Number Publication Date
EP0049495A1 true EP0049495A1 (fr) 1982-04-14
EP0049495B1 EP0049495B1 (fr) 1985-03-27

Family

ID=15218407

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810107856 Expired EP0049495B1 (fr) 1980-10-03 1981-10-02 Appareil à déplacement de fluide à volutes imbriquées

Country Status (7)

Country Link
EP (1) EP0049495B1 (fr)
JP (1) JPS586075B2 (fr)
AU (1) AU546511B2 (fr)
CA (1) CA1222987A (fr)
DE (1) DE3169565D1 (fr)
MY (1) MY8700531A (fr)
SG (1) SG26687G (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538464A1 (fr) * 1982-12-23 1984-06-29 Copeland Corp Machine du type a spirale
FR2574870A1 (fr) * 1983-11-04 1986-06-20 Sanden Corp Appareil de deplacement de fluide de type a spirale
EP0244183A2 (fr) * 1986-04-28 1987-11-04 Sanden Corporation Elément de volute pour machine déplaçant des fluides à volutes imbriquées
EP0295480A2 (fr) * 1987-06-15 1988-12-21 Agintec AG Machine à déplacement positif
EP0318189A2 (fr) * 1987-11-23 1989-05-31 Copeland Corporation Machine à volutes
EP0623733A1 (fr) * 1993-05-04 1994-11-09 Copeland Corporation Moyens de suppression du bruit pour machines à spirale
US6916162B2 (en) 2003-02-25 2005-07-12 The Boc Group Plc Scroll compressor
DE10335637B4 (de) * 2002-08-05 2006-07-27 Kabushiki Kaisha Toyota Jidoshokki, Kariya Spiralverdichter
EP3239527A1 (fr) * 2016-04-26 2017-11-01 LG Electronics Inc. Compresseur à spirales
CN113544383A (zh) * 2019-03-19 2021-10-22 三菱电机株式会社 涡旋压缩机

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5964488U (ja) * 1982-10-22 1984-04-27 サンデン株式会社 スクロ−ル型流体装置
JPS6098185A (ja) * 1983-11-02 1985-06-01 Hitachi Ltd スクロール圧縮機
JPH0212316Y2 (fr) * 1985-10-11 1990-04-06
JPS6463682A (en) * 1987-09-04 1989-03-09 Toshiba Corp Scroll compressor
US4927341A (en) * 1987-11-23 1990-05-22 Copeland Corporation Scroll machine with relieved flank surface
US5221198A (en) * 1990-07-18 1993-06-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Scroll type compressor with intake port aligned with counterweight
JP3882343B2 (ja) 1998-06-12 2007-02-14 株式会社デンソー スクロール型圧縮機
JP6956131B2 (ja) 2019-03-28 2021-10-27 株式会社豊田自動織機 スクロール型圧縮機

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1165435A (en) * 1966-10-06 1969-10-01 Paul Vulliez Improvements in or relating to Rotary Positive Displacement Pumps
US3874827A (en) * 1973-10-23 1975-04-01 Niels O Young Positive displacement scroll apparatus with axially radially compliant scroll member

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1165435A (en) * 1966-10-06 1969-10-01 Paul Vulliez Improvements in or relating to Rotary Positive Displacement Pumps
US3874827A (en) * 1973-10-23 1975-04-01 Niels O Young Positive displacement scroll apparatus with axially radially compliant scroll member

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538464A1 (fr) * 1982-12-23 1984-06-29 Copeland Corp Machine du type a spirale
FR2574870A1 (fr) * 1983-11-04 1986-06-20 Sanden Corp Appareil de deplacement de fluide de type a spirale
EP0244183A2 (fr) * 1986-04-28 1987-11-04 Sanden Corporation Elément de volute pour machine déplaçant des fluides à volutes imbriquées
EP0244183A3 (en) * 1986-04-28 1988-09-14 Sanden Corporation Scroll member for scroll type fluid displacement apparatus
EP0295480A2 (fr) * 1987-06-15 1988-12-21 Agintec AG Machine à déplacement positif
EP0295480A3 (en) * 1987-06-15 1989-07-26 Agintec Ag Positive displacement machine
EP0318189A2 (fr) * 1987-11-23 1989-05-31 Copeland Corporation Machine à volutes
EP0318189A3 (en) * 1987-11-23 1989-12-27 Copeland Corporation Scroll machine
EP0623733A1 (fr) * 1993-05-04 1994-11-09 Copeland Corporation Moyens de suppression du bruit pour machines à spirale
DE10335637B4 (de) * 2002-08-05 2006-07-27 Kabushiki Kaisha Toyota Jidoshokki, Kariya Spiralverdichter
US6916162B2 (en) 2003-02-25 2005-07-12 The Boc Group Plc Scroll compressor
EP3239527A1 (fr) * 2016-04-26 2017-11-01 LG Electronics Inc. Compresseur à spirales
CN107313930A (zh) * 2016-04-26 2017-11-03 Lg电子株式会社 涡旋式压缩机
KR20170122011A (ko) * 2016-04-26 2017-11-03 엘지전자 주식회사 스크롤 압축기
US10724521B2 (en) 2016-04-26 2020-07-28 Lg Electronics Inc. Scroll compressor with wrap having gradually decreasing thickness
EP3696419A1 (fr) * 2016-04-26 2020-08-19 LG Electronics Inc. Compresseur à spirales
KR20230005080A (ko) * 2016-04-26 2023-01-09 엘지전자 주식회사 스크롤 압축기
US11668303B2 (en) 2016-04-26 2023-06-06 Lg Electronics Inc. Scroll compressor with wrap having gradually decreasing thickness
CN113544383A (zh) * 2019-03-19 2021-10-22 三菱电机株式会社 涡旋压缩机
CN113544383B (zh) * 2019-03-19 2022-10-28 三菱电机株式会社 涡旋压缩机

Also Published As

Publication number Publication date
SG26687G (en) 1987-07-10
JPS5762988A (en) 1982-04-16
EP0049495B1 (fr) 1985-03-27
DE3169565D1 (en) 1985-05-02
CA1222987A (fr) 1987-06-16
JPS586075B2 (ja) 1983-02-02
MY8700531A (en) 1987-12-31
AU546511B2 (en) 1985-09-05
AU7576181A (en) 1982-04-08

Similar Documents

Publication Publication Date Title
US4490099A (en) Scroll type fluid displacement apparatus with thickened center wrap portions
US4477238A (en) Scroll type compressor with wrap portions of different axial heights
EP0049495A1 (fr) Appareil à déplacement de fluide à volutes imbriquées
US4547137A (en) Scroll type fluid compressor with thickened spiral elements
EP0077214B1 (fr) Compresseur à volutes imbriquées avec rendement élevé
US4303379A (en) Scroll-type compressor with reduced housing radius
US4580956A (en) Biased drive mechanism for an orbiting fluid displacement member
US3874827A (en) Positive displacement scroll apparatus with axially radially compliant scroll member
US5051075A (en) Gearing system having interdigited teeth with convex and concave surface portions
US4781549A (en) Modified wrap scroll-type machine
EP0099740B1 (fr) Machine à déplacement de fluide à volutes imbriquées et procédé d'assemblage
US4548555A (en) Scroll type fluid displacement apparatus with nonuniform scroll height
EP0133891B1 (fr) Machine à volutes imbriquées
EP0069531B1 (fr) Compresseur à volutes ayant un mécanisme de refoulement corrigé
US4477239A (en) Scroll type fluid displacement apparatus with offset wraps for reduced housing diameter
US4432708A (en) Scroll type fluid displacement apparatus with pressure communicating passage between pockets
US4551078A (en) Scroll-type fluid displacement apparatus with angular offset varying means
EP0192351A1 (fr) Compresseur à fluide du type à volutes imbriquées
US4585402A (en) Scroll-type fluid machine with eccentric ring drive mechanism
EP0012614A1 (fr) Améliorations à des compresseurs à fluide du type à volutes imbriquées
US4548556A (en) Interfitting mechanism of spiral elements for scroll-type fluid displacement apparatus
JPH03172594A (ja) 改変型スクロール形状を有するスクロール装置
US5090874A (en) Fluid compressor
GB2143904A (en) Scroll-type rotary positive- displacement fluid machine
US6179593B1 (en) Displacement fluid machine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19820323

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SANDEN CORPORATION

ITF It: translation for a ep patent filed

Owner name: MARCHI & MITTLER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 3169565

Country of ref document: DE

Date of ref document: 19850502

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 81107856.7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20000925

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000927

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20001009

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20001010

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20011001

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Effective date: 20011001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 20011030

EUG Se: european patent has lapsed

Ref document number: 81107856.7