CA2042203C - Scroll type fluid machinery - Google Patents
Scroll type fluid machineryInfo
- Publication number
- CA2042203C CA2042203C CA002042203A CA2042203A CA2042203C CA 2042203 C CA2042203 C CA 2042203C CA 002042203 A CA002042203 A CA 002042203A CA 2042203 A CA2042203 A CA 2042203A CA 2042203 C CA2042203 C CA 2042203C
- Authority
- CA
- Canada
- Prior art keywords
- scroll
- revolving
- drive bushing
- drive
- slide hole
- 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 - Fee Related
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 15
- 230000005484 gravity Effects 0.000 claims description 8
- 230000014509 gene expression Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 239000002131 composite material Substances 0.000 description 6
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
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
- 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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
According to the present invention, there is provided a scroll type fluid machinery in which a sta-tionary 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.
Further, the contact pressure between the wrap of the revolving scroll and the wrapof the stationary scroll is prevented to become excessive even at the time of high speed rotation of the rotary shaft.
Further, the contact pressure between the wrap of the revolving scroll and the wrapof the stationary scroll is prevented to become excessive even at the time of high speed rotation of the rotary shaft.
Description
~ ~ 2042203 SPECIFICATION
1. TITLE OF THE INVENTION
SCROLL TYPE FLUID MACHINERY
1. TITLE OF THE INVENTION
SCROLL TYPE FLUID MACHINERY
2. FIELD OF THE INVENTION AND RELATED ART STATEMENT
The present invention relates to a scroll type fluid machinery used as a compressor, an expansion machi-nery 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 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.
In Fig. 5 and Fig. 6, a spiralwrap 06b set up on an inner surface of an end plate 06a of a stationary f .
~ 20422~3 scroll 06 is engaged mutually with a spiralwrap04b 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, l denotes a shaft center of a rotary shaft 01, 02 denotes a center of a pin 05, r denotes eccentricity between l and 02, and a denotes an inclination of a slide 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 trans-mitted to the revolving scroll 04 through the slide hole lS 02, the oscillating bearing 03 and the pin 05. The re-volving 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 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 2 of the pin 05.
Here, the centrifugal force Fc is expressed by the following expression (1):
Fc = W r~2 ... (1) where, W is the weight of the revolving scroll, r is a radius of revolution in a solar motion of the revolving scroll, 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):
F = ~Fg + Fc ... (2) An angle ~ between the direction of the composite force F and the eccentric direction is expressed by the following expression (3):
~ = tan l {Fg/Fc} ... (3) When the composite force F is applied to the oscillating bearing 03 through the pin 05, the oscillating bearing 03 slides in the slide hole 02 along the longi-tudinal direction thereof by means of a component of force F' in the longitudinal direction of the slide hole 02 of the composite force F in the direction that the radius of revolution r in a solar motion increases, and thewrap04b of the revolving scroll 04 comes in contact with thewrap06b of the stationary scroll 06 by means of a contact pressure F".
Besides, the component of force F' of the composite force F is expressed by the following exp-ression (4):
F' = Fcos (~ + ~) -- (4) The contact pressure F" is expressed by the following expression (5):
F" = F'cos ~=Fcos(~+~) cos~ ... (5) In above-mentioned conventional scroll type compressor, the centrifugal force Fc acting on the re-volving scroll 04 becomes larger in accordance with increase of revolving angular velocity ~ of the revolving scroll 04 as it is apparent from the expression (1). Then, when the centrifugal force Fc becomes larger, the angle ~ 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.
The present invention relates to a scroll type fluid machinery used as a compressor, an expansion machi-nery 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 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.
In Fig. 5 and Fig. 6, a spiralwrap 06b set up on an inner surface of an end plate 06a of a stationary f .
~ 20422~3 scroll 06 is engaged mutually with a spiralwrap04b 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, l denotes a shaft center of a rotary shaft 01, 02 denotes a center of a pin 05, r denotes eccentricity between l and 02, and a denotes an inclination of a slide 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 trans-mitted to the revolving scroll 04 through the slide hole lS 02, the oscillating bearing 03 and the pin 05. The re-volving 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 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 2 of the pin 05.
Here, the centrifugal force Fc is expressed by the following expression (1):
Fc = W r~2 ... (1) where, W is the weight of the revolving scroll, r is a radius of revolution in a solar motion of the revolving scroll, 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):
F = ~Fg + Fc ... (2) An angle ~ between the direction of the composite force F and the eccentric direction is expressed by the following expression (3):
~ = tan l {Fg/Fc} ... (3) When the composite force F is applied to the oscillating bearing 03 through the pin 05, the oscillating bearing 03 slides in the slide hole 02 along the longi-tudinal direction thereof by means of a component of force F' in the longitudinal direction of the slide hole 02 of the composite force F in the direction that the radius of revolution r in a solar motion increases, and thewrap04b of the revolving scroll 04 comes in contact with thewrap06b of the stationary scroll 06 by means of a contact pressure F".
Besides, the component of force F' of the composite force F is expressed by the following exp-ression (4):
F' = Fcos (~ + ~) -- (4) The contact pressure F" is expressed by the following expression (5):
F" = F'cos ~=Fcos(~+~) cos~ ... (5) In above-mentioned conventional scroll type compressor, the centrifugal force Fc acting on the re-volving scroll 04 becomes larger in accordance with increase of revolving angular velocity ~ of the revolving scroll 04 as it is apparent from the expression (1). Then, when the centrifugal force Fc becomes larger, the angle ~ 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.
3. OBJECT AND SUMMARY OF THE INVENTION
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 sta-tionary 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 ~` 2042203 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 wrapof the revolving scroll and the wrapof the sta-tionary scroll from becoming excessive notwithstanding high speed rotation of the rotary shaft.
(2) A scroll type fluid machinery in which a sta-tionary 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, ~'~ 2042203 21326-167 characterlzed ln that a balance welght for balanclng dynamlc unbalance caused by revolvlng motlon ln a solar motlon of the revolvlng scroll ls provlded on the drlve bushlng, and an axlal posltlon of the center of gravlty of the balance welght ls made to accord wlth the axlal center of the drlve bushlng substantlally.
Above-descrlbed constructlon belng provlded ln the present lnventlon, lt ls posslble to prevent the contact pressure between the wrap of the revolvlng scroll and the wrap of the statlonary scroll from becomlng excesslve by means of the actlon of the balance welght, and the moment lncllned rotatlon of the drlve bushlng based on the centrlfugal force worklng on the balance welght dlsappears or dlmlnlshes, thus suppresslng lncllned rotatlon of the drlve bushlng.
In accordance wlth the present lnventlon there ls provlded, a scroll type fluld machlnery comprlslng a statlonary scroll and a revolvlng scroll havlng splral wraps set up at end plates, respectlvely, the splral wraps belng engaged wlth each other, a drlve bushlng belng fltted rotatably lnto a boss pro~ected at a central part of an outer surface of the end plate of sald revolvlng scroll, a drlve pln pro~ectlng from a rotary shaft belng fltted slldably lnto a sllde hole bored ln the drlve bushing, a cross sect lon of the sllde hole havlng a notched clrcular shape and the drlve pln havlng a notched clrcular shape correspondlng to the shape of the sllde hole but wlth a smaller clrcumference, both the sllde hole and drlve pin havlng generally stralght llne ~- 7 ~' ~ 2042~0~
portlons whlch mate wlth one another, and a balance welght belng dlrectly attached to the drlve bushlng, the balance welght balanclng dynamlc unbalance caused by revolvlng motlon ln a solar motlon of sald revolvlng scroll, and an axlal posltlon of the center of gravlty of sald balance welght belng made to substantlally accord wlth the axlal center of sald drlve bushlng to thereby reduce a moment of lncllned rotatlon of the drlve bushlng resultlng from centrlfugal force durlng rotatlon thereof, the generally stralght llne portlons of the drlve pln sllde along the generally stralght llne portlons of the sllde hole durlng rotatlon of the revolvlng scroll.
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 sta-tionary 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 ~` 2042203 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 wrapof the revolving scroll and the wrapof the sta-tionary scroll from becoming excessive notwithstanding high speed rotation of the rotary shaft.
(2) A scroll type fluid machinery in which a sta-tionary 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, ~'~ 2042203 21326-167 characterlzed ln that a balance welght for balanclng dynamlc unbalance caused by revolvlng motlon ln a solar motlon of the revolvlng scroll ls provlded on the drlve bushlng, and an axlal posltlon of the center of gravlty of the balance welght ls made to accord wlth the axlal center of the drlve bushlng substantlally.
Above-descrlbed constructlon belng provlded ln the present lnventlon, lt ls posslble to prevent the contact pressure between the wrap of the revolvlng scroll and the wrap of the statlonary scroll from becomlng excesslve by means of the actlon of the balance welght, and the moment lncllned rotatlon of the drlve bushlng based on the centrlfugal force worklng on the balance welght dlsappears or dlmlnlshes, thus suppresslng lncllned rotatlon of the drlve bushlng.
In accordance wlth the present lnventlon there ls provlded, a scroll type fluld machlnery comprlslng a statlonary scroll and a revolvlng scroll havlng splral wraps set up at end plates, respectlvely, the splral wraps belng engaged wlth each other, a drlve bushlng belng fltted rotatably lnto a boss pro~ected at a central part of an outer surface of the end plate of sald revolvlng scroll, a drlve pln pro~ectlng from a rotary shaft belng fltted slldably lnto a sllde hole bored ln the drlve bushing, a cross sect lon of the sllde hole havlng a notched clrcular shape and the drlve pln havlng a notched clrcular shape correspondlng to the shape of the sllde hole but wlth a smaller clrcumference, both the sllde hole and drlve pin havlng generally stralght llne ~- 7 ~' ~ 2042~0~
portlons whlch mate wlth one another, and a balance welght belng dlrectly attached to the drlve bushlng, the balance welght balanclng dynamlc unbalance caused by revolvlng motlon ln a solar motlon of sald revolvlng scroll, and an axlal posltlon of the center of gravlty of sald balance welght belng made to substantlally accord wlth the axlal center of sald drlve bushlng to thereby reduce a moment of lncllned rotatlon of the drlve bushlng resultlng from centrlfugal force durlng rotatlon thereof, the generally stralght llne portlons of the drlve pln sllde along the generally stralght llne portlons of the sllde hole durlng rotatlon of the revolvlng scroll.
4. BRIEF DESCRIPTION OF THE DRAWINGS
Flg. 1 and Flg.2 show a flrst embodlment of the present lnventlon, whereln Flg. 1 ls a longltudlnal sectlonal vlew of a prlnclpal part and Flg. 2 ls a cross-sectlonal vlew taken along a llne II-II ln Flg. 1.
Flg. 3 and Flg. 4 show a second embodlment of the present lnventlon, whereln Flg. 3 ls a longltudlnal sectlonal vlew of a prlnclpal part and Flg. 4 ls a front vlew ln a state that the revolvlng scroll ls removed.
~,.
~ 7a ,.,, ~
~_` 2042203 Fig. 5 and Fig. 6 show an example of a con-ventional 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.
Flg. 1 and Flg.2 show a flrst embodlment of the present lnventlon, whereln Flg. 1 ls a longltudlnal sectlonal vlew of a prlnclpal part and Flg. 2 ls a cross-sectlonal vlew taken along a llne II-II ln Flg. 1.
Flg. 3 and Flg. 4 show a second embodlment of the present lnventlon, whereln Flg. 3 ls a longltudlnal sectlonal vlew of a prlnclpal part and Flg. 4 ls a front vlew ln a state that the revolvlng scroll ls removed.
~,.
~ 7a ,.,, ~
~_` 2042203 Fig. 5 and Fig. 6 show an example of a con-ventional 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.
5. DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
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 la and a spiralwrap lb set up on the inner surface thereof. A revolving scroll 2 consists of an end plate 2a and a spiralwrap 2b set up on the inner surface thereof. These stationary scroll 1 and the revolving scroll 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 of compression chambers 3 to form point symmetry with respect to the center of the spiral. 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 ~, 2042203 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 l 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. Further, the section of the eccentric drive pin 9 is also formed into a notched circle ~having a dia-meter smaller than that of above-mentioned notched circle and having a same configuration as the notched circle.
Thus, 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.
Further, 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.
When the rotary shaft 8 is rotated, the driving force is transmitted to the drive bushing 5 from the ~ 20~2203 .
straight line portion 9a of the drive pin 9 through the straight line portion 7a of the slide hole 7, and trans-mitted further to the revolving scroll 2 through the bearing 6 and the boss 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 l of the rotary shaft 8 as the center.
Then, the gas taken into the compression chambers 3 is compressed gradually and reaches a central chamber I1 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.
Now, with the revolution in a motion of the revolving scroll 2, an unbalanced weight consisting of the revolving scroll 2, the boss 4, the bearing 6 and the drive bushing 5 generates a centrifugal force toward the eccentric direction with respect to the shaft center l of the rotary 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 the counter weight 10.
Thus, it is possible to make a force which presses the side surface of the spiral wrap2b of the revolving scroll 2 against the side surface of the spiral wraplb of the stationary scroll 1, viz., the contact ~_` 2042203 ,, ~
pressure constant irrespective of the number of rotation of the rotary 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 wrapof the revolving scroll and thewrapof the stationary scroll from becoming excessive even at the time of high speed rotation of the rotary shaft.
As a result, abnormal wear of thewrapcan 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 iower part in an axial direction of the drive bushing 5, and the drive bushing 5 and the balance weight 10 are just placed so as to slide on the upper end surface of the rotary shaft 8 and the eccentric drive pin 9 is just fitted into the slide hole 7 slidably.
Therefore, the balance 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 the balance weight 10 at the time of revolution in a solar motion of the revolving scroll 2. As a result, there have been such problems that offset working is produced on the rotary bearing 6 and the lower end surface of the drive bushing 5 also works on the upper end face of the rotary 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 posi-tion 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.
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, the drive bushing 5 and the balance weight 10 fixed thereto also revolves in a solar motion with above-mentioned revolving motion, and a ~ 2042203 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 substan-tially, however, the moment of inclined rotation of the drive bushing 5 based on the centrifugal force F dis-appears 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 bush-ing 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.
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 la and a spiralwrap lb set up on the inner surface thereof. A revolving scroll 2 consists of an end plate 2a and a spiralwrap 2b set up on the inner surface thereof. These stationary scroll 1 and the revolving scroll 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 of compression chambers 3 to form point symmetry with respect to the center of the spiral. 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 ~, 2042203 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 l 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. Further, the section of the eccentric drive pin 9 is also formed into a notched circle ~having a dia-meter smaller than that of above-mentioned notched circle and having a same configuration as the notched circle.
Thus, 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.
Further, 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.
When the rotary shaft 8 is rotated, the driving force is transmitted to the drive bushing 5 from the ~ 20~2203 .
straight line portion 9a of the drive pin 9 through the straight line portion 7a of the slide hole 7, and trans-mitted further to the revolving scroll 2 through the bearing 6 and the boss 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 l of the rotary shaft 8 as the center.
Then, the gas taken into the compression chambers 3 is compressed gradually and reaches a central chamber I1 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.
Now, with the revolution in a motion of the revolving scroll 2, an unbalanced weight consisting of the revolving scroll 2, the boss 4, the bearing 6 and the drive bushing 5 generates a centrifugal force toward the eccentric direction with respect to the shaft center l of the rotary 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 the counter weight 10.
Thus, it is possible to make a force which presses the side surface of the spiral wrap2b of the revolving scroll 2 against the side surface of the spiral wraplb of the stationary scroll 1, viz., the contact ~_` 2042203 ,, ~
pressure constant irrespective of the number of rotation of the rotary 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 wrapof the revolving scroll and thewrapof the stationary scroll from becoming excessive even at the time of high speed rotation of the rotary shaft.
As a result, abnormal wear of thewrapcan 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 iower part in an axial direction of the drive bushing 5, and the drive bushing 5 and the balance weight 10 are just placed so as to slide on the upper end surface of the rotary shaft 8 and the eccentric drive pin 9 is just fitted into the slide hole 7 slidably.
Therefore, the balance 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 the balance weight 10 at the time of revolution in a solar motion of the revolving scroll 2. As a result, there have been such problems that offset working is produced on the rotary bearing 6 and the lower end surface of the drive bushing 5 also works on the upper end face of the rotary 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 posi-tion 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.
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, the drive bushing 5 and the balance weight 10 fixed thereto also revolves in a solar motion with above-mentioned revolving motion, and a ~ 2042203 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 substan-tially, however, the moment of inclined rotation of the drive bushing 5 based on the centrifugal force F dis-appears 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 bush-ing 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 (2)
1. A scroll type fluid machinery comprising a stationary scroll and a revolving scroll having spiral wraps set up at end plates, respectively, the spiral wraps being engaged with each other, a drive bushing being fitted rotatably into a boss projected at a central part of an outer surface of the end plate of said revolving scroll, a drive pin projecting from a rotary shaft being fitted slidably into a slide hole bored in the drive bushing, a cross section of the slide hole having a notched circular shape and the drive pin having a notched circular shape corresponding to the shape of the slide hole but with a smaller circumference, both the slide hole and drive pin having generally straight line portions which mate with one another, and a balance weight being directly attached to the drive bushing, the balance weight balancing dynamic unbalance caused by revolving motion in a solar motion of said revolving scroll, and an axial position of the center of gravity of said balance weight being made to substantially accord with the axial center of said drive bushing to thereby reduce a moment of inclined rotation of the drive bushing resulting from centrifugal force during rotation thereof, the generally straight line portions of the drive pin slide along the generally straight line portions of the slide hole during rotation of the revolving scroll.
2. The scroll type fluid machinery according to claim 1, wherein the balance weight has a generally semicircular shape.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19570190 | 1990-07-24 | ||
| JP195701/1990 | 1990-07-24 | ||
| JPU.M.89969/1990 | 1990-08-28 | ||
| JP8996990U JPH0741843Y2 (en) | 1990-08-28 | 1990-08-28 | Scroll type fluid machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2042203A1 CA2042203A1 (en) | 1992-01-25 |
| CA2042203C true CA2042203C (en) | 1996-02-13 |
Family
ID=26431347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002042203A Expired - Fee Related CA2042203C (en) | 1990-07-24 | 1991-05-09 | 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) |
Families Citing this family (8)
| 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 |
| JP3236144B2 (en) * | 1993-09-14 | 2001-12-10 | 株式会社デンソー | Compressor |
| JP2682790B2 (en) * | 1993-12-02 | 1997-11-26 | 株式会社豊田自動織機製作所 | Scroll compressor |
| JPH07324689A (en) * | 1994-05-31 | 1995-12-12 | Mitsubishi Heavy Ind Ltd | Scroll type fluid compressor |
| US5496157A (en) * | 1994-12-21 | 1996-03-05 | Carrier Corporation | Reverse rotation prevention for scroll compressors |
| US9909586B2 (en) * | 2012-03-23 | 2018-03-06 | Bitzer Kuehlmaschinenbau Gmbh | Crankshaft with aligned drive and counterweight locating features |
| CN111089055B (en) * | 2018-10-23 | 2024-09-06 | 谷轮环境科技（苏州）有限公司 | Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a |
| JP7439690B2 (en) * | 2020-08-05 | 2024-02-28 | 株式会社デンソー | Compressor, compressor manufacturing method |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5819875B2 (en) * | 1980-03-18 | 1983-04-20 | サンデン株式会社 | Scroll compressor |
| JPS5979086A (en) * | 1982-10-27 | 1984-05-08 | Hitachi Ltd | scroll fluid machine |
| JPS59120794A (en) * | 1982-12-27 | 1984-07-12 | Mitsubishi Electric Corp | Scroll compressor |
| JPS59142480U (en) * | 1983-03-15 | 1984-09-22 | サンデン株式会社 | Scroll type fluid device |
| US4954057A (en) * | 1988-10-18 | 1990-09-04 | Copeland Corporation | Scroll compressor with lubricated flat driving surface |
-
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 Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| AU7645291A (en) | 1992-01-30 |
| EP0468605A1 (en) | 1992-01-29 |
| CA2042203A1 (en) | 1992-01-25 |
| KR920002929A (en) | 1992-02-28 |
| AU634059B2 (en) | 1993-02-11 |
| CN1020497C (en) | 1993-05-05 |
| CN1058456A (en) | 1992-02-05 |
| DE69104927T2 (en) | 1995-03-09 |
| EP0468605B1 (en) | 1994-11-02 |
| KR960000092B1 (en) | 1996-01-03 |
| DE69104927D1 (en) | 1994-12-08 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |