EP0468605A1 - Scroll type fluid machinery - Google Patents
Scroll type fluid machinery Download PDFInfo
- Publication number
- EP0468605A1 EP0468605A1 EP91250153A EP91250153A EP0468605A1 EP 0468605 A1 EP0468605 A1 EP 0468605A1 EP 91250153 A EP91250153 A EP 91250153A EP 91250153 A EP91250153 A EP 91250153A EP 0468605 A1 EP0468605 A1 EP 0468605A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- scroll
- revolving
- drive bushing
- centrifugal force
- revolving scroll
- 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
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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
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/003—Systems for the equilibration of forces acting on the elements of the machine
-
- 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
- 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
- the present invention relates to a scroll type fluid machinery used as a compressor, an expansion machinery and the like.
- a radius of revolution variable mechanism for varying a radius of revolution in a solar motion of a revolving scroll automatically in accordance with the variation in gas pressure and a centrifugal force applied to the revolving scroll of a scroll type compressor has been disclosed in Japanese Patent Provisional Publication No. 59-120794 (No. 120794/1984).
- an oscillating bearing 03 is fitted into a slide hole 02 bored on an upper end surface of a rotary shaft 01 so as to be slidable in a longitudinal direction but unable to rotate on its axis, and a pin 05 projecting downward from a central part of an underside of an end plate 04a of a revolving scroll 04 is inserted into this oscillating bearing 03 so as to be able to rotate relatively as shown in Fig. 5 and Fig. 6.
- a spiral wrap 06b set up on an inner surface of an end plate 06a of a stationary scroll 06 is engaged mutually with a spiral wrap 04b set up on an inner surface of the end plate 04a of the revolving scroll 04 so as to delimit a compression chamber 07.
- a numeral 08 denotes a frame
- 09 denotes a thrust bearing for supporting thrust acting on the revolving scroll 04
- 010 denotes a bearing for supporting the upper end of the rotary shaft 01
- 0 1 denotes a shaft center of a rotary shaft 01
- 0 2 denotes a center of a pin 05
- r denotes eccentricity between 0 1 and 0 2
- a denotes an inclination of a slide hole 02 with respect to the direction of eccentricity.
- the rotation is transmitted to the revolving scroll 04 through the slide hole 02, the oscillating bearing 03 and the pin 05.
- the revolving scroll 04 revolves in a solar motion while making its circular orbit with eccentricity r as a radius in a state that the rotation on its axis is checked by a mechanism for checking the rotation on its axis not shown.
- a gas is suctioned into a compression chamber 07 and moves toward the center of the spiral while the compression chamber 07 is reducing the volume thereof, the gas is compressed gradually and reaches a central chamber 012, and is discharged therefrom through a discharge port 011.
- a centrifugal force Fc is applied in an eccentric direction to the revolving scroll 04 by the revolution in a solar motion of the revolving scroll 04, and a gas force Fg acts in a direction which meets at right angles with the centrifugal force Fc by the gas pressure in the compression chamber 07.
- a composite force F of these centrifugal force Fc and gas force Fg is applied to the center 0 2 of the pin 05.
- centrifugal force Fc is expressed by the following expression (1): where, W is the weight of the revolving scroll,
- the composite force F is expressed by the following expression (2):
- the contact pressure F" is expressed by the following expression (5):
- the gist of the present invention is as described in the following items (1) and (2), as follows.
- a stationary scroll 1 consists of an end plate 1 a and a spiral wrap 1 b set up on the inner surface thereof.
- a revolving scroll 2 consists of an end plate 2a and a spiral wrap 2b set up on the inner surface thereof.
- a cylindrical boss 4 is projected at the central part of the outer surface of the end plate 2a of the revolving scroll 2, and a drive bushing 5 is fitted rotatably into the boss 4 through a bearing 6.
- a slide hole 7 is bored in the drive bushing 5, and a drive pin 9 projecting from an end surface of a rotary shaft 8 with eccentricity by r from a shaft center 0 1 thereof is fitted into the slide hole 7.
- the section of the slide hole 7 is formed into a notched circle obtained by notching a circle with a straight line which is inclined in a particular direction as shown in Fig. 2.
- the section of the eccentric drive pin 9 is also formed into a notched circle having a diameter smaller than that of above-mentioned notched circle and having a same configuration as the notched circle.
- a straight line portion 9a of the drive pin 9 comes in contact along a straight line portion 7a of the slide hole 7, and thus, the drive pin 9 may slide therealong and move in all directions within a range of a clearance between the inner peripheral surface of the slide hole 7 and the outer peripheral surface of the pin 9.
- a counter weight 10 is attached fixedly to the drive bushing 5, and the counter weight 10 generates a centrifugal force in a direction opposite to that of a centrifugal force acting on the revolving scroll 2 at the time of revolution in a solar motion thereof.
- the driving force is transmitted to the drive bushing 5 from the straight line portion 9a of the drive pin 9 through the straight line portion 7a of the slide hole 7, and transmitted further to the revolving scroll 2 through the bearing 6 and the boss 4.
- the revolving scroll 2 revolves in a solar motion while making a circular orbit with the eccentricity r as a radius and with the shaft center 0 1 of the rotary shaft 8 as the center.
- the gas taken into the compression chambers 3 is compressed gradually and reaches a central chamber 11 as the compression chambers 3 move toward the center of the spiral while reducing volumes thereof, and is discharged therefrom through a discharge port 12.
- the present invention also provides a scroll type fluid machinery in which above-described problems are solved.
- Fig. 3 and Fig. 4 show a second embodiment of the present invention.
- the axial position of the center of gravity G of the balance weight 10 is made to almost accord with the center in an axial direction of the drive bushing 5 by increasing the thickness in a vertical direction of the balance weight 10.
- the drive bushing 5 and the balance weight 10 fixed thereto also revolves in a solar motion with above-mentioned revolving motion, and a centrifugal force F acts on the balance weight 10 at the center of gravity G. Since the axial position of the center of gravity G is in accord with the center in an axial direction of the drive bushing 5 substantially, however, the moment of inclined rotation of the drive bushing 5 based on the centrifugal force F disappears or reduces remarkably.
- the axial position of the center of gravity of the balance weight is made to accord substantially with the axial center of the drive bushing as described above.
Abstract
Description
- The present invention relates to a scroll type fluid machinery used as a compressor, an expansion machinery and the like.
- A radius of revolution variable mechanism for varying a radius of revolution in a solar motion of a revolving scroll automatically in accordance with the variation in gas pressure and a centrifugal force applied to the revolving scroll of a scroll type compressor has been disclosed in Japanese Patent Provisional Publication No. 59-120794 (No. 120794/1984).
- In this mechanism, an oscillating
bearing 03 is fitted into aslide hole 02 bored on an upper end surface of arotary shaft 01 so as to be slidable in a longitudinal direction but unable to rotate on its axis, and apin 05 projecting downward from a central part of an underside of anend plate 04a of a revolvingscroll 04 is inserted into this oscillatingbearing 03 so as to be able to rotate relatively as shown in Fig. 5 and Fig. 6. - In Fig. 5 and Fig. 6, a
spiral wrap 06b set up on an inner surface of an end plate 06a of astationary scroll 06 is engaged mutually with a spiral wrap 04b set up on an inner surface of theend plate 04a of the revolvingscroll 04 so as to delimit acompression chamber 07. Anumeral 08 denotes a frame, 09 denotes a thrust bearing for supporting thrust acting on the revolvingscroll 04, 010 denotes a bearing for supporting the upper end of therotary shaft 01, 01 denotes a shaft center of arotary shaft 01, 02 denotes a center of apin 05, r denotes eccentricity between 01 and 02, and a denotes an inclination of aslide hole 02 with respect to the direction of eccentricity. - When the
rotary shaft 01 is driven to rotate by a motor and the like not shown, the rotation is transmitted to the revolvingscroll 04 through theslide hole 02, the oscillatingbearing 03 and thepin 05. Therevolving scroll 04 revolves in a solar motion while making its circular orbit with eccentricity r as a radius in a state that the rotation on its axis is checked by a mechanism for checking the rotation on its axis not shown. As a result, as a gas is suctioned into acompression chamber 07 and moves toward the center of the spiral while thecompression chamber 07 is reducing the volume thereof, the gas is compressed gradually and reaches acentral chamber 012, and is discharged therefrom through adischarge port 011. - A centrifugal force Fc is applied in an eccentric direction to the revolving
scroll 04 by the revolution in a solar motion of the revolvingscroll 04, and a gas force Fg acts in a direction which meets at right angles with the centrifugal force Fc by the gas pressure in thecompression chamber 07. A composite force F of these centrifugal force Fc and gas force Fg is applied to the center 02 of thepin 05. -
- r is a radius of revolution in a solar motion of the revolving scroll,
- w is a revolving angular velocity of the revolving scroll,
- g is acceleration of gravity.
- The composite force F is expressed by the following expression (2):
-
-
- When the composite force F is applied to the oscillating
bearing 03 through thepin 05, the oscillating bearing 03 slides in theslide hole 02 along the longitudinal direction thereof by means of a component of force F' in the longitudinal direction of theslide hole 02 of the composite force F in the direction that the radius of revolution r in a solar motion increases, and the wrap 04b of therevolving scroll 04 comes in contact with thewrap 06b of thestationary scroll 06 by means of a contact pressure F". -
-
- In above-mentioned conventional scroll type compressor, the centrifugal force Fc acting on the revolving
scroll 04 becomes larger in accordance with increase of revolving angular velocity", of therevolving scroll 04 as it is apparent from the expression (1). Then, when the centrifugal force Fc becomes larger, the angle 0 becomes smaller as it is apparent from the expression (3). Accordingly, the component of force F' and the contact pressure F" become larger as it is apparent from the expressions (4) and (5). - Since the contact pressure F" becomes larger in proportion to a square of the revolving angular velocity there has been a problem that the contact pressure F" becomes excessive at the time of high speed rotation of the
rotary shaft 01, thus increasing wear and noise of thewraps 04b and 06b. - It is an object of the present invention which has been made in view of such points to provide a scroll type fluid machinery which solves above-mentioned problems.
- It is another object of the present invention to provide a scroll type fluid machinery in which above-mentioned fluid machinery is improved further.
- In order to achieve above-described objects, the gist of the present invention is as described in the following items (1) and (2), as follows.
- (1) A scroll type fluid machinery in which a stationary scroll and a revolving scroll in which spiral wraps are set up at end plates, respectively, are engaged with each other, a drive bushing is fitted rotatably into a boss projected at the central part of the outer surface of the end plate of the revolving scroll, and a drive pin projecting from the rotary shaft is fitted slidably into a slide hole bored in the drive bushing, characterized in that a counter weight which generates a centrifugal force having an opposite direction to a centrifugal force acting on the revolving scroll at the time of revolving motion in a solar motion thereof is provided on the drive bushing. Above-described construction being provided in the present invention, the counter weight generates a centrifugal force having an opposite direction to a centrifugal force acting on the revolving scroll at the time of revolving motion in a solar motion thereof. Thus, it is possible to prevent the contact pressure between the wrap of the revolving scroll and the wrap of the stationary scroll from becoming excessive notwithstanding high speed rotation of the rotary shaft.
- (2) A scroll type fluid machinery in which a stationary scroll and a revolving scroll in which spiral wraps are set up at end plates, respectively, are engaged with each other, a drive bushing is fitted rotatably into a boss projected at the central part of the outer surface of the end plate of the revolving scroll, and a drive pin projecting from the rotary shaft is fitted slidably into a slide hole bored in the drive bushing, characterized in that a balance weight for balancing dynamic unbalance caused by revolving motion in a solar motion of the revolving scroll is provided on the drive bushing, and an axial position of the center of gravity of the balance weight is made to accord with the axial center of the drive bushing substantially. Above-described construction being provided in the present invention, it is possible to prevent the contact pressure between the wrap of the revolving scroll and the wrap of the stationary scroll from becoming excessive by means of the action of the balance weight, and the moment inclined rotation of the drive bushing based on the centrifugal force working on the balance weight disappears or diminishes, thus suppressing inclined rotation of the drive bushing.
-
- Fig. 1 and Fig. 2 show a first embodiment of the present invention, wherein Fig. 1 is a longitudinal sectional view of a principal part and Fig. 2 is a cross-sectional view taken along a line II-II in Fig. 1.
- Fig. 3 and Fig. 4 show a second embodiment of the present invention, wherein Fig. 3 is a longitudinal sectional view of a principal part and Fig. 4 is a front view in a state that the revolving scroll is removed.
- Fig. 5 and Fig. 6 show an example of a conventional scroll type compressor, wherein Fig. 5 is a partial longitudinal sectional view and Fig. 6 is a cross-sectional view taken along a line VI-VI in Fig. 5.
- Preferred embodiments of the present invention will be described in detail illustratively with reference to the drawings.
- The first embodiment:
- Fig. 1 and Fig. 2 show first embodiment of the present invention.
- In Fig. 1 and Fig. 2, a stationary scroll 1 consists of an end plate 1 a and a spiral wrap 1 b set up on the inner surface thereof. A revolving
scroll 2 consists of anend plate 2a and aspiral wrap 2b set up on the inner surface thereof. These stationary scroll 1 and the revolvingscroll 2 are made eccentric from each other by the radius r of revolution in a solar motion and engaged with each other as shown in the figures while shifting the angle by 180°, thereby to delimit a plurality ofcompression chambers 3 to form point symmetry with respect to the center of the spiral. Acylindrical boss 4 is projected at the central part of the outer surface of theend plate 2a of the revolvingscroll 2, and a drive bushing 5 is fitted rotatably into theboss 4 through abearing 6. Aslide hole 7 is bored in the drive bushing 5, and adrive pin 9 projecting from an end surface of arotary shaft 8 with eccentricity by r from a shaft center 01 thereof is fitted into theslide hole 7. The section of theslide hole 7 is formed into a notched circle obtained by notching a circle with a straight line which is inclined in a particular direction as shown in Fig. 2. Further, the section of theeccentric drive pin 9 is also formed into a notched circle having a diameter smaller than that of above-mentioned notched circle and having a same configuration as the notched circle. Thus, a straight line portion 9a of thedrive pin 9 comes in contact along astraight line portion 7a of theslide hole 7, and thus, thedrive pin 9 may slide therealong and move in all directions within a range of a clearance between the inner peripheral surface of theslide hole 7 and the outer peripheral surface of thepin 9. - Further, a
counter weight 10 is attached fixedly to the drive bushing 5, and thecounter weight 10 generates a centrifugal force in a direction opposite to that of a centrifugal force acting on therevolving scroll 2 at the time of revolution in a solar motion thereof. - When the
rotary shaft 8 is rotated, the driving force is transmitted to the drive bushing 5 from the straight line portion 9a of thedrive pin 9 through thestraight line portion 7a of theslide hole 7, and transmitted further to the revolvingscroll 2 through thebearing 6 and theboss 4. Thus, the revolving scroll 2 revolves in a solar motion while making a circular orbit with the eccentricity r as a radius and with the shaft center 01 of therotary shaft 8 as the center. Then, the gas taken into thecompression chambers 3 is compressed gradually and reaches a central chamber 11 as thecompression chambers 3 move toward the center of the spiral while reducing volumes thereof, and is discharged therefrom through adischarge port 12. - Now, with the revolution in a motion of the revolving
scroll 2, an unbalanced weight consisting of the revolvingscroll 2, theboss 4, thebearing 6 and the drive bushing 5 generates a centrifugal force toward the eccentric direction with respect to the shaft center 01 of therotary shaft 8 and the center 02 of the drive bushing 5, but a centrifugal force in a direction opposite to that of above-mentioned centrifugal force is generated at the same time in thecounter weight 10. - Thus, it is possible to make a force which presses the side surface of the
spiral wrap 2b of the revolvingscroll 2 against the side surface of the spiral wrap 1 b of the stationary scroll 1, viz., the contact pressure constant irrespective of the number of rotation of therotary shaft 8. - Thus, since a counter weight which generates a centrifugal force in a direction opposite to that of the centrifugal force acting on the revolving scroll at the time of revolution in a solar motion thereof is provided on the drive bushing, it is possible to prevent the contact pressure between the wrap of the revolving scroll and the wrap of the stationary scroll from becoming excessive even at the time of high speed rotation of the rotary shaft.
- As a result, abnormal wear of the wrap can be prevented. Therefore, it is possible to prevent lowering of performance of a scroll type fluid machinery as well as to extend the life thereof. The second embodiment:
- In the scroll type fluid machinery shown in Fig. 1 of the above-described first embodiment, the axial position of the center of gravity G of the
balance weight 10 is located at a lower part in an axial direction of the drive bushing 5, and the drive bushing 5 and thebalance weight 10 are just placed so as to slide on the upper end surface of therotary shaft 8 and theeccentric drive pin 9 is just fitted into theslide hole 7 slidably. Therefore, thebalance weight 10 and the drive bushing 5 formed in one body therewith are rotated inclining clockwise in Fig. 1 by the centrifugal force F acting on the center of gravity of thebalance weight 10 at the time of revolution in a solar motion of the revolvingscroll 2. As a result, there have been such problems that offset working is produced on therotary bearing 6 and the lower end surface of the drive bushing 5 also works on the upper end face of therotary shaft 8 in an offset manner. - The present invention also provides a scroll type fluid machinery in which above-described problems are solved.
- Fig. 3 and Fig. 4 show a second embodiment of the present invention.
- As shown in Fig. 3 and Fig. 4, the axial position of the center of gravity G of the
balance weight 10 is made to almost accord with the center in an axial direction of the drive bushing 5 by increasing the thickness in a vertical direction of thebalance weight 10. - Other construction is almost similar to those shown in Fig. 1 and Fig. 2, and same symbols are assigned to corresponding members.
- At the time of revolution in a solar motion of the revolving
scroll 2, thedrive bushing 5 and thebalance weight 10 fixed thereto also revolves in a solar motion with above-mentioned revolving motion, and a centrifugal force F acts on thebalance weight 10 at the center of gravity G. Since the axial position of the center of gravity G is in accord with the center in an axial direction of thedrive bushing 5 substantially, however, the moment of inclined rotation of thedrive bushing 5 based on the centrifugal force F disappears or reduces remarkably. - In the present invention, the axial position of the center of gravity of the balance weight is made to accord substantially with the axial center of the drive bushing as described above. Thus, the moment of inclined rotation of the drive bushing based on the centrifugal force acting on the balance weight disappears or reduces, thus suppressing inclined rotation of the drive bushing.
- As a result, it is possible to prevent offset working of a rotary bearing which supports the drive bushing and offset working of the end surface of the drive bushing against the end surface of the rotary shaft so as to prevent abnormal wear and damages caused by above-mentioned offset working, thereby to improve reliability of a scroll type fluid machinery.
Claims (3)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19570190 | 1990-07-24 | ||
JP195701/90 | 1990-07-24 | ||
JP8996990U JPH0741843Y2 (en) | 1990-08-28 | 1990-08-28 | Scroll type fluid machinery |
JP89969/90U | 1990-08-28 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0468605A1 true EP0468605A1 (en) | 1992-01-29 |
EP0468605B1 EP0468605B1 (en) | 1994-11-02 |
Family
ID=26431347
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91250153A Expired - Lifetime EP0468605B1 (en) | 1990-07-24 | 1991-06-11 | Scroll type fluid machinery |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP0468605B1 (en) |
KR (1) | KR960000092B1 (en) |
CN (1) | CN1020497C (en) |
AU (1) | AU634059B2 (en) |
CA (1) | CA2042203C (en) |
DE (1) | DE69104927T2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0643224A1 (en) * | 1993-09-14 | 1995-03-15 | Nippondenso Co., Ltd. | Scroll type Compressor |
EP0656477A1 (en) * | 1993-12-02 | 1995-06-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor |
US5496157A (en) * | 1994-12-21 | 1996-03-05 | Carrier Corporation | Reverse rotation prevention for scroll compressors |
AU669646B2 (en) * | 1994-05-31 | 1996-06-13 | Mitsubishi Jukogyo Kabushiki Kaisha | Scroll type fluid machine |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3105714B2 (en) * | 1993-09-03 | 2000-11-06 | 三菱重工業株式会社 | Drive bush for scroll type fluid machine |
LU91082B1 (en) * | 2004-06-04 | 2005-12-05 | Wurth Paul Sa | Device to replace the main channel of a blast furnace. |
US9909586B2 (en) | 2012-03-23 | 2018-03-06 | Bitzer Kuehlmaschinenbau Gmbh | Crankshaft with aligned drive and counterweight locating features |
CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0091544A2 (en) * | 1980-03-18 | 1983-10-19 | Sanden Corporation | Movement synchronizing means for scroll-type fluid displacement apparatus |
DE3338737A1 (en) * | 1982-10-27 | 1984-05-03 | Hitachi, Ltd., Tokio/Tokyo | FLOWING MACHINE IN SPIRAL DESIGN |
EP0122066A1 (en) * | 1983-03-15 | 1984-10-17 | Sanden Corporation | Scroll type fluid displacement apparatus with axial moving prevent device of bearing for driving mechanism |
EP0365132A2 (en) * | 1988-10-18 | 1990-04-25 | Copeland Corporation | Scroll compressor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59120794A (en) * | 1982-12-27 | 1984-07-12 | Mitsubishi Electric Corp | Scroll compressor |
-
1991
- 1991-05-09 CA CA002042203A patent/CA2042203C/en not_active Expired - Fee Related
- 1991-05-10 AU AU76452/91A patent/AU634059B2/en not_active Ceased
- 1991-06-03 CN CN91103680A patent/CN1020497C/en not_active Expired - Fee Related
- 1991-06-11 DE DE69104927T patent/DE69104927T2/en not_active Expired - Fee Related
- 1991-06-11 EP EP91250153A patent/EP0468605B1/en not_active Expired - Lifetime
- 1991-07-24 KR KR1019910012679A patent/KR960000092B1/en not_active IP Right Cessation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0091544A2 (en) * | 1980-03-18 | 1983-10-19 | Sanden Corporation | Movement synchronizing means for scroll-type fluid displacement apparatus |
DE3338737A1 (en) * | 1982-10-27 | 1984-05-03 | Hitachi, Ltd., Tokio/Tokyo | FLOWING MACHINE IN SPIRAL DESIGN |
EP0122066A1 (en) * | 1983-03-15 | 1984-10-17 | Sanden Corporation | Scroll type fluid displacement apparatus with axial moving prevent device of bearing for driving mechanism |
EP0365132A2 (en) * | 1988-10-18 | 1990-04-25 | Copeland Corporation | Scroll compressor |
Non-Patent Citations (2)
Title |
---|
PATENT ABSTRACTS OF JAPAN, vol. 12, no. 286 (M-727)[3133], 5th August 1988; & JP-A-63 61 786 (SHIN MEIWA IND. CO.) 17-03-1988 * |
PATENT ABSTRACTS OF JAPAN, vol. 14, no. 42 (M-925)[3985], 25th January 1990; & JP-A-1 273 890 (MATSUSHITA) 01-11-1989 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0643224A1 (en) * | 1993-09-14 | 1995-03-15 | Nippondenso Co., Ltd. | Scroll type Compressor |
EP0656477A1 (en) * | 1993-12-02 | 1995-06-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor |
US5547354A (en) * | 1993-12-02 | 1996-08-20 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll compressor balancing |
AU669646B2 (en) * | 1994-05-31 | 1996-06-13 | Mitsubishi Jukogyo Kabushiki Kaisha | Scroll type fluid machine |
US5496157A (en) * | 1994-12-21 | 1996-03-05 | Carrier Corporation | Reverse rotation prevention for scroll compressors |
USRE37837E1 (en) * | 1994-12-21 | 2002-09-10 | Carrier Corporation | Reverse rotation prevention for scroll compressors |
Also Published As
Publication number | Publication date |
---|---|
KR960000092B1 (en) | 1996-01-03 |
EP0468605B1 (en) | 1994-11-02 |
CA2042203A1 (en) | 1992-01-25 |
KR920002929A (en) | 1992-02-28 |
AU634059B2 (en) | 1993-02-11 |
DE69104927T2 (en) | 1995-03-09 |
DE69104927D1 (en) | 1994-12-08 |
CA2042203C (en) | 1996-02-13 |
CN1058456A (en) | 1992-02-05 |
AU7645291A (en) | 1992-01-30 |
CN1020497C (en) | 1993-05-05 |
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