JP2015010575A - Eccentric swing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an eccentric swing device in which a force acting against a ball-bearing at a working part rotatably supporting a swing shaft is small.SOLUTION: A weight plate 32 is rotatably attached to a part between the first ball-bearing for a swing shaft 11 and a working part, a center of gravity OD of the weight plate 32 is positioned on an eccentric line LD crossing at a right angle with a rotation center line O1 of a rotating shaft 6 and a rotation center line O2 of the swing shaft 11, and the center of gravity OD of the weight plate 32 is positioned at a side opposite to the rotation center line O2 of the swing shaft 11 of the rotation center line O1 of the rotating shaft 6, the rotating shaft 6 is provided with a cavity part 33, the weight plate 32 is provided with a projection 34, the projection 34 is inserted into the cavity part 33 and the projection 34 can be moved only in a direction of the eccentric line LD in respect to the rotating shaft 6.

Description

  The present invention relates to an eccentric revolving device in which an operating part performs an eccentric orbiting motion, for example, a scroll compressor in which an orbiting scroll performs an eccentric orbiting motion. Here, the eccentric turning motion is a motion that makes an eccentric turning around a predetermined axis and does not rotate.

  The scroll compressor disclosed in Patent Document 1 will be described with reference to FIGS. As shown in the figure, bearing supports 2 and 3 are fixed to the casing 1. The rotary shaft 6 is rotatably supported by the bearing supports 2 and 3 via the bearings 4 and 5. That is, the rotating shaft 6 is rotatably supported by the casing 1. A rotor 7 is fixed to the rotating shaft 6. A stator 8 is fixed to the casing 1. The rotor 7 and the stator 8 constitute a motor.

  A rotating shaft 11 is rotatably supported on the rotating shaft 6 via angular ball bearings 9 and 10. The rotation center line of the rotation shaft 6 and the rotation center line of the turning shaft 11 are parallel to each other, and the rotation center line of the rotation shaft 6 and the rotation center line of the turning shaft 11 are deviated. In other words, the turning shaft 11 is supported so as to be rotatable eccentrically with the rotating shaft 6. A swivel plate 12 is fixed to the end of the swivel shaft 11 on the angular ball bearing 10 side. An Oldham ring 13 is provided between the bearing support 3 and the swivel plate 12. A protrusion 14 is provided on one surface of the Oldham ring 13, and a protrusion 15 is provided on the other surface of the Oldham ring 13. A line passing through the center of the width of the protrusion 14 and a line passing through the center of the width of the protrusion 15 are orthogonal to each other. A groove 16 is provided in the bearing support 3, and a groove 17 is provided in the swivel plate 12. The groove 16 and the groove 17 are orthogonal to each other. The protrusion 14 is engaged with the groove 16, and the protrusion 15 is engaged with the groove 17. And the rotation prevention device which permits the eccentric turning of the turning shaft 11 around the rotation center line of the rotating shaft 6 and prevents the turning shaft 11 from rotating by the bearing support 3, the turning plate 12, the Oldham ring 13, and the like. It is configured.

  A fixed scroll 18 is fixed to the casing 1. The fixed scroll 18 is provided with a spiral wrap. A turning scroll 19 is attached to the end of the turning shaft 11 on the angular ball bearing 9 side. The orbiting scroll 19 is provided with a wrap having the same shape as that of the fixed scroll 18. The wrap of the fixed scroll 18 and the wrap of the orbiting scroll 19 overlap each other, and a plurality of compression chambers are formed between the wrap of the fixed scroll 18 and the wrap of the orbiting scroll 19. A suction pipe 20 and a discharge pipe 21 are connected to the fixed scroll 18. The suction pipe 20 and the discharge pipe 21 communicate with the compression chamber. And the compressor main body is comprised by the fixed scroll 18 and the turning scroll 19 grade | etc.,.

  In this scroll compressor, when the windings of the stator 8 are energized, the rotor 7 and the rotating shaft 6 rotate, and the turning shaft 11 turns eccentrically around the rotation center line of the rotating shaft 6. Since the rotation prevention device which consists of is provided, the turning shaft 11 does not rotate. For this reason, the orbiting shaft 11 and the orbiting scroll 19 make an eccentric orbiting motion with respect to the casing 1 and the fixed scroll 18, so that the compression chamber formed between the fixed scroll 18 and the orbiting scroll 19 is gradually reduced. Therefore, a compressed gas such as air is sucked from the suction pipe 20, compressed in the compression chamber, and discharged from the discharge pipe 21.

JP 2001-304143 A

In the scroll compressor shown in FIGS. 5 and 6, the center of gravity of the orbiting scroll 19, the orbiting shaft 11, and the orbiting plate 12 is eccentric with respect to the rotation center line of the rotating shaft 6. In such a case, centrifugal force acts on the orbiting scroll 19, the orbiting shaft 11, and the orbiting plate 12. The force acting on each member when the scroll compressor is operated, and the force in the direction perpendicular to the center line of the length method of the orbiting shaft 11 is applied to the orbiting scroll 19 as shown in FIG. Centrifugal force F1 acting on the pivot shaft 11, centrifugal force F2 acting on the pivot plate 11, centrifugal force F3 acting on the pivot plate 12, force R1 acting on the pivot shaft 11 from the angular ball bearing 9, and acting on the pivot shaft 11 from the angular ball bearing 10 Force R2. Further, moments due to the forces F1, F2, F3, R1, and R2 at arbitrary points on the rotation center line of the turning shaft 11 are balanced. Therefore, if the distances between the points at which the forces F3, R2, F2, R1, and F1 act are L1, L2, L3, and L4 as shown in FIG. 7, the moment balance equation at the point C at which the force R2 acts Is as follows.
F3 · L1 + R1 (L2 + L3) = F2 · L2 + F1 (L2 + L3 + L4)
Therefore, the force R1 is expressed by the following equation.
R1 = {F2 · L2 + F1 (L2 + L3 + L4) −F3 · L1} / (L2 + L3)
Since the mass of the orbiting shaft 11 and the orbiting scroll 19 is larger than the mass of the orbiting plate 12, the forces F1 and F2 are larger than the force F3. For this reason, the force R1 which acts on the rotating shaft 11 from the angular ball bearing 9 which is a ball bearing by the side of an action | operation part becomes large.

  In this case, as shown in FIG. 8, since the radial force acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is R1 / 2, the thrust force acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is S1. Then, the force FB1 acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is a resultant force of the force S1 and the force R1 / 2. And since radial force R1 / 2 is large, force FB1 which acts on the outer race 23 from the ball | bowl 22 of the angular ball bearing 9 becomes large. For this reason, the angular ball bearing 9 may be damaged in a short time.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an eccentric swiveling device that exerts a small force acting on a ball bearing on the operating portion side that rotatably supports the swivel shaft.

  According to a first aspect of the present invention, there is provided a casing, a rotating shaft rotatably supported by the casing, a rotor fixed to the rotating shaft, a stator fixed to the casing, and at least a radial on the rotating shaft. A pivot shaft that is eccentrically supported via first and second ball bearings that receive a direction force, a rotation prevention device that prevents the rotation of the pivot shaft, and the first of the pivot shaft. An eccentric swivel device having an operation portion provided at an end portion on the ball bearing side of the swivel shaft and rotatably attached to a portion of the swivel shaft between the first ball bearing and the operation portion. A weight plate is provided, and the center of gravity of the weight plate is located on an eccentric line perpendicular to the rotation center line of the rotation shaft and the rotation center line of the pivot shaft, and the center of gravity of the weight plate is the rotation Located on the opposite side of the rotation center line of the pivot axis Cage, and having a movement restriction mechanism which the weight plate is allowed to move only in the direction of the polarized core relative to the rotation axis.

  As a second aspect of the present invention, it is preferable that the first ball bearing is an angular ball bearing.

  According to the first aspect, the center of gravity of the weight plate is located on the eccentric line, and the center of gravity of the weight plate is located on the opposite side of the rotation center line side of the rotation axis of the rotation axis of the rotation axis. The weight plate is movable only in the direction of the eccentric line with respect to the rotation axis. For this reason, the direction of the centrifugal force acting on the weight plate when the eccentric turning device operates is opposite to the direction of the centrifugal force acting on the turning shaft and the operating portion. As a result, the force acting on the first ball bearing is reduced.

  Further, according to the second aspect, the first ball bearing can also receive a thrust force, and the operating angle of the force acting on the outer race from the ball of the first ball bearing is reduced. The force acting on the outer race from the ball of the ball bearing acts on the thick portion of the outer race. For this reason, it is possible to reliably prevent the first ball bearing from being damaged in a short time.

FIG. 1 is a schematic sectional view showing a scroll compressor according to an embodiment of the present invention. FIG. 2 is an enlarged cross-sectional view taken along the line AA in FIG. FIG. 3 is a view for explaining forces acting on each member of the scroll compressor shown in FIG. FIG. 4 is a view for explaining the force acting on the angular ball bearing of the scroll compressor shown in FIG. FIG. 5 is a schematic sectional view showing a conventional scroll compressor. 6 is a cross-sectional view taken along line BB in FIG. FIG. 7 is a view for explaining the force acting on each member of the scroll compressor shown in FIG. FIG. 8 is a view for explaining the force acting on the angular ball bearing of the scroll compressor shown in FIG.

  A scroll compressor according to an embodiment of the present invention will be described with reference to FIGS. As shown in the figure, a weight plate 32 is rotatably attached to the pivot shaft 11 via a bearing 31. The weight plate 32 is located between the angular ball bearing 9 and the orbiting scroll 19. The center of gravity OD of the weight plate 32 is located on an eccentric line LD that intersects the rotation center line O1 of the rotation shaft 6 and the rotation center line O2 of the turning shaft 11 at right angles. Further, the center of gravity OD of the weight plate 32 is located on the opposite side of the rotation center line O1 from the rotation center line O2 side.

A recess 33 is provided on the end surface of the rotary shaft 6 on the orbiting scroll 19 side. A protrusion 34 is provided on the side of the rotary shaft 6 of the weight plate 32. A protrusion 34 is inserted into the recess 33. The opposing flat surface 33a of the recess 33 is parallel to the eccentric line LD. The opposing flat surface 34a of the protrusion 34 is parallel to the eccentric line LD. The flat surface 33a and the flat surface 34a are in contact with each other. There is a gap between the opposing surface 33b of the recess 33 and the opposing surface 34b of the protrusion 34. The recess 33 and the protrusion 34 constitute a movement restricting mechanism that allows the weight plate 32 to move only in the direction of the eccentric line LD with respect to the rotation shaft 6.
The other structure is the same as that of the eccentric turning apparatus shown in FIGS.

In this scroll compressor, when the rotary shaft 6 rotates, the weight plate 32 rotates around the rotation center line O2. In this case, the center of gravity OD of the weight plate 32 is located on the eccentric line LD, and the center of gravity OD of the weight plate 32 is located on the side opposite to the rotation center line O2 side of the rotation center line O1. For this reason, the centrifugal force FW in the direction of arrow D shown in FIG. That is, the direction of the centrifugal force acting on the weight plate 32 when the scroll compressor is operated is opposite to the direction of the centrifugal force acting on the orbiting shaft 11 and the orbiting scroll 19.
Other operations are the same as those of the eccentric turning device shown in FIGS.

The force acting on each member when the scroll compressor shown in FIGS. 1 and 2 is operated, and the force perpendicular to the rotation center line O2 of the turning shaft 11 is as shown in FIG. From the centrifugal force F1 acting on the orbiting scroll 19, the centrifugal force F2 acting on the orbiting shaft 11, the centrifugal force F3 acting on the orbiting plate 12, the centrifugal force FW acting on the weight plate 32, and the angular ball bearing 9 on the orbiting scroll 19 side. A force R1 acting on the turning shaft 11 and a force R2 acting on the turning shaft 11 from the angular ball bearing 10 on the turning plate 12 side. Further, moments due to the forces F1, F2, F3, FW, R1, and R2 at arbitrary points on the rotation center line O2 of the turning shaft 11 are balanced. From this, if the distances between the points where the forces F3, R2, F2, R1, FW, F1 act are L1, L2, L3, L5, L6 as shown in FIG. 3, the point at the point C where the force R2 acts The moment balance formula is as follows.
F3 · L1 + R1 (L2 + L3) + FW (L2 + L3 + L5) = F2 · L2 + F1 (L2 + L3 + L5 + L6)
Therefore, the force R1 is expressed by the following equation.
R1 = {F2 · L2 + F1 (L2 + L3 + L5 + L6) −F3 · L1-FW (L2 + L3 + L5)} / (L2 + L3)
The force FW can be arbitrarily determined by changing the mass of the weight plate 32 and the gravity center position OD. As a result, the value of “F 2 · L 2 + F 1 (L 2 + L 3 + L 5 + L 6) −F 3 · L 1 −FW (L 2 + L 3 + L 5)” in the above formula can be reduced. For this reason, the force R <b> 1 acting on the pivot shaft 11 from the angular ball bearing 9 can be reduced. That is, when the scroll compressor is operated, the direction of the centrifugal force acting on the weight plate 32 is opposite to the direction of the centrifugal force acting on the orbiting shaft 11 and the orbiting scroll 19. The force R1 acting on the shaft 11 can be reduced.

  In this case, as shown in FIG. 4, a radial force R1 / 2 acts on the outer race 23 from the ball 22 of the angular ball bearing 9. Therefore, if the thrust force acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is S1, the force FB1 acting on the outer race 23 from the ball 22 of the first angular ball bearing 9 is the force S1 and the force R1 / 2. Will be the combined force. Since the radial force R1 / 2 acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is small, the force FB1 acting on the outer race 23 from the ball 22 of the angular ball bearing 9 is small. For this reason, the angular ball bearing 9 on the orbiting scroll 19 side, which is the operating portion, is not damaged in a short time.

  Further, in the conventional scroll compressor shown in FIG. 5, as shown in FIG. 8, the angle in the direction of the force FB1 with respect to the longitudinal direction of the turning shaft 11, that is, the working angle θ of the force FB1 is large. In the scroll compressor according to the present embodiment shown in FIG. 1, the working angle θ of the force FB1 is small as shown in FIG. For this reason, the force FB1 does not act on the thin portion of the outer race 23, but acts on the thick portion of the outer race 23. Therefore, it is possible to reliably prevent the angular ball bearing 9 from being damaged in a short time.

  Although the scroll compressor has been described in the above embodiment, it is obvious that the present invention can be applied to other eccentric turning devices. For example, the present invention can be applied to components of a vacuum pump, a generator, and a reduction gear of an automobile in which a gear is attached to an operating part. In the above-described embodiment, the angular ball bearings 9 and 10 are used as the first and second ball bearings that receive at least a radial force, but the radial ball bearings as the first and second ball bearings described above. May be used.

  Furthermore, in the above-described embodiment, the movement restricting mechanism that allows the weight plate 32 to move only in the direction of the eccentric line LD with respect to the rotating shaft 6 includes the concave portion 33 and the protruding portion 34. Although used, a movement restricting mechanism or the like in which a concave portion is provided on the weight plate, a protruding portion is provided on the rotating shaft, and the protruding portion is inserted into the concave portion may be used.

  While embodiments of the invention have been disclosed, it will be apparent to those skilled in the art that changes may be made without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

  DESCRIPTION OF SYMBOLS 1 ... Casing, 6 ... Rotating shaft, 7 ... Rotor, 8 ... Stator, 9 ... Angular ball bearing, 10 ... Angular ball bearing, 11 ... Turning shaft, 12 ... Turning plate, 13 ... Oldham ring, 18 ... Fixed scroll, 19 ... orbiting scroll, 22 ... ball, 23 ... outer ring, 32 ... weight plate, 33 ... recess, 34 ... protrusion

Claims (2)

A casing, a rotating shaft rotatably supported by the casing, a rotor fixed to the rotating shaft, a stator fixed to the casing, and first and second receiving at least a radial force on the rotating shaft. Provided at the end of the swivel shaft on the first ball bearing side, a swivel shaft that is eccentrically supported via the ball bearing 2 and rotatably supported, a rotation prevention device that prevents the swivel shaft from rotating. An eccentric swivel device having an actuated portion,
Comprising a weight plate rotatably attached to a portion of the pivot shaft between the first ball bearing and the operating portion;
The center of gravity of the weight plate is located on an eccentric line perpendicularly intersecting the rotation center line of the rotation shaft and the rotation center line of the turning shaft, and the center of gravity of the weight plate is the rotation center line of the rotation shaft. It is located on the opposite side to the rotation center line side of the swivel axis,
An eccentric swiveling device comprising a movement restricting mechanism that allows the weight plate to move only in the direction of the eccentric line with respect to the rotation shaft.   The eccentric swivel device according to claim 1, wherein the first ball bearing is an angular ball bearing.

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