EP0468605B1 - Scroll type fluid machinery - Google Patents

Scroll type fluid machinery Download PDF

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Publication number
EP0468605B1
EP0468605B1 EP91250153A EP91250153A EP0468605B1 EP 0468605 B1 EP0468605 B1 EP 0468605B1 EP 91250153 A EP91250153 A EP 91250153A EP 91250153 A EP91250153 A EP 91250153A EP 0468605 B1 EP0468605 B1 EP 0468605B1
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EP
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Prior art keywords
scroll
revolving
drive bushing
center
revolving scroll
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EP91250153A
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German (de)
French (fr)
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EP0468605A1 (en
Inventor
Hiroaki C/O Mitsubishi Jukogyo K.K. Kondo
Takahisa C/O Mitsubishi Jukogyo K.K. Hirano
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority claimed from JP8996990U external-priority patent/JPH0741843Y2/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/003Systems for the equilibration of forces acting on the elements of the machine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/02Rotary-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
    • F01C1/0207Rotary-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
    • F01C1/0215Rotary-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
  • O1 denotes a shaft center of a rotary shaft 01
  • O2 denotes a center of a pin 05
  • r denotes eccentricity between O1 and O2
  • 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 O2 of the pin 05.
  • 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 component of force F' of the composite force F is expressed by the following expression (4):
  • F' Fcos ( ⁇ + ⁇ ) (4)
  • the contact pressure F'' is expressed by the following expression (5):
  • the centrifugal force Fc acting on the revolving 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).
  • 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).
  • EP-A-91 544 as well as EP-A-122 066 disclose a scroll type fluid machinery in which a stationary scroll and a revolving scroll in which spiral wraps are set up at end plates, 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 said revolving scroll and a drive pin projecting from the rotary shaft is fitted slidably (in the sense of rotatably sliding) into a slide hole bored in the drive bushing, wherein a counter weight wich generates a centrifugal force having an opposite direction to a centrifugal force acting on said revolving scroll at the time of revolving motion in a solar motion thereof is provided on said drive bushing and wherein the centrifugal force generated by the counter weight is made to accord substantially with the centrifugal force acting by revolution in a solar motion of the revolving scroll.
  • the gist of the present invention is as described in the following item.
  • 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.
  • Fig. 1 and Fig. 2 show an example similar to prior art, 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 an 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.
  • Fig. 1 and Fig. 2 show examples similar to the prior art.
  • a stationary scroll 1 consists of an end plate 1a and a spiral wrap 1b 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 O1 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 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 O1 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 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 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 provides a scroll type fluid machinery in which above-described problems are solved.
  • Fig. 3 and Fig. 4 show an 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.

Description

    FIELD OF THE INVENTION AND RELATED ART STATEMENT
  • 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 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 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, O₁ denotes a shaft center of a rotary shaft 01, O₂ denotes a center of a pin 05, r denotes eccentricity between O₁ and O₂, and α 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 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. 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 O₂ of the pin 05.
  • Here, the centrifugal force Fc is expressed by the following expression (1):

    Fc = W g rω²   (1)
    Figure imgb0001


    where,
       W is the weight of the revolving scroll,
       r is a radius of revolution in a solar motion of the revolving scroll,
       ω 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 = √ Fg² + Fc² ¯    (2)
    Figure imgb0002


    An angle ϑ between the direction of the composite force F and the eccentric direction is expressed by the following expression (3):

    ϑ = tan⁻¹ {Fg/Fc}   (3)
    Figure imgb0003


       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 longitudinal 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 the wrap 04b of the revolving scroll 04 comes in contact with the wrap 06b 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 expression (4):

    F' = Fcos (α + ϑ)   (4)
    Figure imgb0004


       The contact pressure F'' is expressed by the following expression (5):

    F'' = F'cos α=Fcos(α+ϑ)·cosα   (5)
    Figure imgb0005


       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 ω of the revolving scroll 04 as it is apparent from the expression (1). Then, when the centrifugal force Fc becomes larger, the angle ϑ 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 ω, 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 the wraps 04b and 06b.
  • EP-A-91 544 as well as EP-A-122 066 disclose a scroll type fluid machinery in which a stationary scroll and a revolving scroll in which spiral wraps are set up at end plates, 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 said revolving scroll and a drive pin projecting from the rotary shaft is fitted slidably (in the sense of rotatably sliding) into a slide hole bored in the drive bushing, wherein a counter weight wich generates a centrifugal force having an opposite direction to a centrifugal force acting on said revolving scroll at the time of revolving motion in a solar motion thereof is provided on said drive bushing and wherein the centrifugal force generated by the counter weight is made to accord substantially with the centrifugal force acting by revolution in a solar motion of the revolving scroll.
  • 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 item.
  • 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.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • Fig. 1 and Fig. 2 show an example similar to prior art, 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 an 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.
  • DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
  • Preferred embodiments of the present invention will be described in detail illustratively with reference to the drawings 3, 4.
  • The first embodiment:
  • Fig. 1 and Fig. 2 show examples similar to the prior art.
  • In Fig. 1 and Fig. 2, a stationary scroll 1 consists of an end plate 1a and a spiral wrap 1b 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. 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 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 O₁ 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 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 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 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. 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 O₁ 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 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.
  • 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 O₁ of the rotary shaft 8 and the center O₂ 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 wrap 2b of the revolving scroll 2 against the side surface of the spiral wrap 1b of the stationary scroll 1, viz., the contact 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 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 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 provides a scroll type fluid machinery in which above-described problems are solved.
  • Fig. 3 and Fig. 4 show an 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 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 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.
  • 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 (1)

  1. A scroll type fluid machinery in wich a stationary scroll (1) and a revolving scroll (2) in which spiral wraps (1b, 2b) are set up at end plates (1a, 2a), respectively, are engaged with each other, a drive bushing (5) is fitted rotatably into a boss (4) projected at the central part of the outer surface of the end plate of said revolving scroll, and a drive pin (9) projecting from the rotary shaft (8) is fitted slidably into a slide hole (7) bored in the drive bushing,
    and
    a balance weight (10) for balancing dynamic unbalance caused by revolving motion in a solar motion of said revolving is provided on said drive bushing characterized in that the axial position of the center (G) of gravity of said balance weight is made to accord with the axial center of said drive bushing substantially.
EP91250153A 1990-07-24 1991-06-11 Scroll type fluid machinery Expired - Lifetime EP0468605B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP195701/90 1990-07-24
JP19570190 1990-07-24
JP89969/90U 1990-08-28
JP8996990U JPH0741843Y2 (en) 1990-08-28 1990-08-28 Scroll type fluid machinery

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EP0468605A1 EP0468605A1 (en) 1992-01-29
EP0468605B1 true EP0468605B1 (en) 1994-11-02

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KR (1) KR960000092B1 (en)
CN (1) CN1020497C (en)
AU (1) AU634059B2 (en)
CA (1) CA2042203C (en)
DE (1) DE69104927T2 (en)

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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
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

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JPS59120794A (en) * 1982-12-27 1984-07-12 Mitsubishi Electric Corp Scroll compressor

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JPS5979086A (en) * 1982-10-27 1984-05-08 Hitachi Ltd Scroll hydraulic machine
JPS59142480U (en) * 1983-03-15 1984-09-22 サンデン株式会社 Scroll type fluid device
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Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
JPS59120794A (en) * 1982-12-27 1984-07-12 Mitsubishi Electric Corp Scroll compressor

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DE69104927T2 (en) 1995-03-09
AU634059B2 (en) 1993-02-11
CA2042203C (en) 1996-02-13
CN1020497C (en) 1993-05-05
EP0468605A1 (en) 1992-01-29
KR920002929A (en) 1992-02-28
AU7645291A (en) 1992-01-30
CN1058456A (en) 1992-02-05
DE69104927D1 (en) 1994-12-08
CA2042203A1 (en) 1992-01-25
KR960000092B1 (en) 1996-01-03

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