JPS58135302A - Rotation blocking mechanism for use in rotary piston type fluid apparatus - Google Patents

Abstract

PURPOSE:To provide a rotation blocking mechanism designed for use in a rotary piston type fluid apparatus and the like in which a movable member must be moved along a circular orbit while preventing its rotation, the mechanism being adapted to ensure an easy loading thereof regardless whether there are inevitable machining errors caused by manufacturing operations and to permit a motion to be converted without any mechanical loss. CONSTITUTION:In a rotary piston type fluid apparatus 1, a crank-shaft 14 penetrates through a central opening of end plate 11 forming a housing 10 together with a cup- like casing 12. The shaft 14 is supported by ball bearings 13a and 13b, and a rotary member 16 is supported on an eccentric driving pin 141 of inner edge of the shaft 14 by a rotary bearing 15. In this case, a plurality of recesses 111 is spaced in equal pitches along an inner end face of end plate 11 for respectively urging a first bearing 17 thereto. A rotary member 16 has a recess 163 provided at an end face of side plate 161 opposing against the recess 111, the recess 163 being positioned to be opposable against the recess 111 for respectively urging a second bearing 18 thereto. A rotation blocking mechanism can be obtained by arranging a crank-element 19 including an eccentric pin 192 between these bearings 17 and 18 opposing to each other.

Description

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, a driven member is driven to draw a circular orbit with a radius Ror near its central axis position, and the driven member is prevented from rotating during the circular orbital movement. The present invention relates to a rotating piston type fluid device having a driven member that requires rotation of the driven member, and particularly relates to an improvement in a rotation prevention mechanism that prevents rotation of the driven member.

In general, a feature of a rotating piston type fluid device is that the rotating piston performs circular orbital motion using a crankshaft with a small crank radius, but in this device, the rotating piston attempts to rotate when performing circular orbital motion. Since a force is exerted on the piston, a rotation prevention mechanism is required that can resist this force and prevent rotation while always keeping the pivot piston vertical.

Examples of such rotation prevention mechanisms include the Oldham coupling, which has been known for a long time, the ball coupling shown in U.S. Pat. No. 4,259,046, and the ball coupling shown in U.S. Pat.
The crank coupling shown in No. 125031 is used.

Here, an example will be explained in which the ball coupling structure is used in a last scroll type fluid device.

The front end plate 1 is arranged on the outer periphery of the front end plate 62 of 311, and the outer periphery is joined to the inner wall surface of the cup-shaped portion 6 constituting the housing.
- A ring-shaped fixing race 601 is provided on the end face of the filter 2, and a fixing ring 502 is attached to the end face so as to cover the fixing race 301. is fixed. on the other hand,
Boss roller 11 near side plate roller 12 of movable scroll member 61
It has a ring-shaped movable race 604 on its outer periphery, and a movable ring roller 05 that is in contact with the end surface of the fixed ring roller 02 so as to cover the movable race 604 with a slight gap between it and the end surface of the fixed ring roller 02. These are fixed to the side plate filter 12 by pin loops 06.

As is clear from the M-stand perspective view shown in FIG. 2, the movable ring 605 and the fixed ring 602 each have a plurality of ball holes 305a, 3 with equal diameters, pinch circles, and pitch circles.
02a is drilled in the axial direction.

Here, the rotation prevention effect will be explained with reference to FIG. 3, which shows the relationship between the movable ring and the fixed ring as viewed from the movable scroll member side.

Rotation is prevented by sandwiching the ball element 307 between the edge of the ball hole 602a of the fixed ring roller 02 and the edge of the ball hole 605a of the movable ring roller 05. That is, when the movable scroll member is driven counterclockwise in the figure, the movable ring 605 also moves in a circular orbit so that its central axis draws a circle with a radius ratio of Or, but the movable scroll member also moves in the same direction due to the reaction force of the compressive force. Since rotational force is generated in the direction, the movable ring 6
It attempts to rotate counterclockwise around the central axis of 05. However, since the nine ball elements 307 on the right side of the figure are sandwiched between the edge of the ball hole 302a of the fixed ring 602 and the edge of the ball hole 605a of the movable ring roller 05, the movable ring 605 cannot rotate. This prevents the movable scroll member from rotating.

Note that the diameter of the ball hole 305a of the movable ring roller 05 is a radius of 1 (,1 free movable range) with respect to the ball element 307.
The diameter of the ball hole 602a of the fixed ring roller 02 is set to define a free movable range of radius 1 (2) with respect to the ball element 607, and
1 to perform circular orbital motion with a radius of Ror, the radius needs to be set so that R1 + R2 = Ror. When the movable scroll member 31 is driven by the crankshaft 35 rotatably supported by It is necessary to determine the size to minimize the relative angle deviation between the movable scroll member 31 and the fixed scroll member 36 within a range that is not limited.

Here, the optimum hole diameter assuming there is no stacking angular error or eccentricity is given by the circular orbit radius Ror+2X. Therefore, the allowable ring hole diameter within the range where the above orbital radius fltor is not limited is the above optimum hole diameter "-α
(However, α is the maximum amount of stacked eccentricity.)

FIG. 4(a) is a schematic diagram showing the stationary state of the ball element roller 07 at the ring hole diameter taking α into consideration, where 0 is the axial center of the crankshaft roller 5, and P is the axial center of the crankshaft roller 5. A drive pin (not shown) coupled to the movable scroll member 61
indicates the center of the axis.

FIG. 4(b) is a schematic diagram showing a state in which the crankshaft filter 5 is rotating, and as the crank pin receiver I filter 5 rotates, a driving force 1.1 is applied to the drive pin center 13. At the same time, compressive reaction forces 1 and 2, which are equal in magnitude to the driving force F1, act in the opposite direction to the direction of forces 1 and 1 at the Q point between 0 and 1, that is, +Ror. As a result, a moment M in the same direction as the driving direction acts, and the movable ring 305 receives a moment l-
In the same direction as M, move the center P of the drive pin from the state shown in Fig. 4(a).
Since the angle θ is shifted around , the relative angle between the movable scroll member 31 and the fixed scroll member 66 is shifted.

In addition, in the scroll type fluid system, the above-mentioned moment may not act once during one rotation, and as shown in FIG. The ring has a degree of freedom in the radial direction within the gap A, which causes backlash during the orbiting movement of the movable scroll member 61, and furthermore, a ball element is generated that does not contribute to rotation prevention.

In this way, in the ball coupling mechanism using the movable ring roller 05, fixed ring roller 02, and Hihole element roller 07,
There were problems such as angular misalignment of the movable member due to angular misalignment of the movable ring 305, ring wear due to backlash, and occurrence of abnormal noise.

On the other hand, the crank coupling mechanism has a simple structure in which at least six small rank element rollers 7 are disposed between a fixed member roller 8 and a rotating member 69, as shown in FIG. It had not been put into practical use. This is because if the crank radius of the crankshaft 65 and all the crank elements of the crank element 67 do not exactly match, there will be a large mechanical loss in the turning motion. Even if the radii were made exactly equal, the position of the hole 381 of all the crank element pin holders formed in the fixed part hole 68 would be the same as the position of the hole 91 of all the crank element pin holders formed in the revolving part hole 39. It is thought that this is because if they are not in the corresponding positions, there is a risk of causing a large mechanical loss in the turning movement. It should be noted that in order to be able to use the device easily even with all such errors and to convert rotational motion to pivoting motion without mechanical loss, it is necessary to change the position between the fixed member 38 and the pivoting member filter 9. If the hole diameter of one or both of the crank pin bearings is machined to a large diameter, paraclarity will occur in the rotating member of the assembled device, causing rotational vibration around the center axis of the rotating member during operation, which may cause noise problems. was there.

Therefore, it is an object of the present invention to be applicable to all rotating piston type fluid devices in which a movable member needs to move in a circular orbit while preventing rotation, and to be easy to install even with unavoidable machining errors. It is an object of the present invention to provide a rotation prevention mechanism capable of converting motion without causing any physical loss.

Another object of the present invention is to provide a rotation prevention mechanism that has no backlash in the rotating member and can prevent noise generation even in a wide range of driving rotational speeds.

That is, in the present invention, the radius R, or
A fixed member that supports a plurality of crank elements and a crankshaft, which has a circular orbit similar to the circular orbit of A rotation prevention mechanism of the rotating member is constituted by a plurality of first bearings disposed on the rotating member and the same number of second bearings as the first bearings disposed on the rotating member. Since the part and the pin are press-fitted into the first and second bearings, the axial dimension of the entire device can be shortened, and by using a 7-wheel bearing, it is no longer necessary to attach the rotation prevention part to the conventional rotation prevention part. This means that the lubrication mechanism can be omitted.

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 6 is an exploded perspective view of a coupling mechanism according to an embodiment of the present invention, and FIG. 7 is a sectional view of this mechanism. 12, and a front end plate 11 arranged to close the opening.
have.

A crankshaft 14 passes through a central opening bored in the center of the front end play 1-11, and the crankshaft 14 has two ball bearings 13a disposed in the central opening.

It is rotatably supported by 13b. crank 7
A drive pin 141 is located at the inner end of the shaft 14 at a distance R from the axis.
, or eccentrically provided. The drive pin 141
A rotating member 16 is supported on the top via a bearing 15. The rotating member 16 is composed of a side plate 161 and a rotating piston 162 provided on one side of the side plate 161, and performs a rotating movement with a radius Ror by rotation of the crankshaft 14.

A plurality of recesses 111 for bearing bearings are formed at equal pitches on the inner end surface of the front end plate 11, and the first bearing 17 is press-fitted into the recesses 111. Also, the front end plate 11 of the rotating member 16
On the end face of the side plate 161 facing the front end plate 161, there is a concave part 166 for the bearing receiver.
11 and a second bearing 18
is press-fitted. Between the front end plate 11 and the side plate 161 of the rotating member 16, there is a pin that protrudes in the axial direction and has its center at a position offset by a distance R,or from the center of the disc part 191. 192 is disposed, the crank element 190 disk portion 191 is press-fitted into the inner ring of the first bearing 17, and the pin 192 is press-fitted into the inner ring of the second bearing 18.

Two such bearings 17, 18 prevent the crank movement.

Next, the rotation prevention effect will be explained. To prevent rotation, the disc part of the crank element 19 is attached to the front end plate 1.
This is done by disposing the pin 192 of the crank element 19 in a second bearing inner ring press-fitted into the recess 166 of the rotating member 16. Here, the pin 192 is provided eccentrically by Ror from the center of the disc portion 191,
The drive pin 141 and its eccentricity are equal. Therefore, when the central axis of the rotating member 16 is driven so as to draw a circular orbit with a radius through the drive bearing 15 provided on the end face of the side plate 161 of the rotating member 16, the pin 192 of the crank element 19 also draws a circular orbit with a radius Ror around the central axis of the disk portion 191 of the crank element.

This results in a rotating movement.

In the rotation prevention mechanism of the present invention, unlike the ball coupling mechanism, angular deviation does not occur, and the crank element 19
The circular orbit drawn by the pin 192 also has a constant radius Ror, so that the rotating member 16 can stably rotate. In addition, the first. By using a grease seal bearing as the second bearing, a lubrication mechanism is not required and the rotation prevention mechanism is simplified.

By the way, the pin 192 of the crank element 19 is connected to the disc part 19.
However, it is difficult in terms of manufacturing to match this eccentricity Ror with the eccentricity Ror of the drive pin 141 provided on the crankshaft 14. Become. Therefore, if the amount of eccentricity between the two is different, the movement of the rotating member 16, which is driven so that the central axis draws a circular orbit with a radius Ror, is restricted by the crank element 19, resulting in a large mechanical loss in the rotating movement of the rotating member 16. This will be accompanied by Further, the relative misalignment of the positions of the recesses 111 and 165 formed in the front end plate 11 and the side plate 161 of the rotating member 16 also causes a mechanical loss in the rotating movement of the rotating member 16.

Therefore, it is necessary to absorb the difference in eccentricity or the relative positional deviation of the concave portion, but in the present invention, as shown in FIG. Errors and positional deviations are absorbed by placing an elastic member between them.

That is, as shown in FIG. 8(a), the side plate 1 of the rotating member 16
By arranging the elastic sleeve 20 between the inner ring of the second bearing 18 press-fitted into the concave portion 16 formed in the groove 61 and the pin 192 of the crank element 19, the amount of eccentricity of the drive pin 141 can be reduced. and pin 1 of crank element 19
Even if an error occurs in the amount of eccentricity of the rotating member 92, or a relative shift occurs in the positions of the recessed portions 111 and 163 formed in the front end plate 11 and the side plate 161 of the rotating member 16, the error or shift occurs due to elasticity. This can be absorbed by the elasticity of the sleeve 20, and also prevents the occurrence of vasocrasy in the pivoting member 16. However, the error or shift must be suppressed within the elastic range of the elastic sleeve 20. By arranging such an elastic sleeve, the trajectory drawn by the pin of the crank element 19 is always kept equal to the traveling movement drawn by the rotating member 16 with a radius Ror. For example, if the eccentricity of the pin of the crank element 19 is different from that of the drive pin 141 (not shown), the difference in eccentricity is absorbed by the elastic sleeve, and the circular orbit drawn by the drive pin and the circle drawn by the pin of the crank element 19 are absorbed by the elastic sleeve. The orbits remain equal.

Here, the elastic sleeve 20 is made of a steel sleeve 201 and rubber 202, and the elastic sleeve 20 is made of a steel sleeve 201 and rubber 202.
The rubber 202 is burnt between the steel sleeve 201 and the crank element 19, and is integrated with the crank element 19. This is to prevent slippage between the crank element 19 and the inner ring of the bearing in which it is arranged.

FIG. 8 (1) shows an elastic sleeve 20 disposed between the inner ring of the first bearing 17, which is press-fitted into a concave portion 111 formed in the front end plate 11, and the disc portion 191 of the crank element 19. This embodiment shows an example in which the same effects as those described above can be obtained.

Further, FIG. 9 shows another embodiment of the present invention (a)
In the configuration (b) in which an elastic sleeve 20 is disposed between the outer ring of the second bearing 18 which is press-fitted into the side plate 161 of the rotating member 16 and the concave portion 16, the elastic sleeve 20 is press-fitted into the front end plate 11. In this configuration, an elastic sleeve 20 is disposed between the outer ring of the first bearing 17 and the concave portion 111, but each of the configurations shown in FIG. 8(a)
It is possible to obtain the actions and effects as explained using.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view of a typical scroll-type fluid device;
The figure is an assembled perspective view of the ball coupling mechanism used in the scroll-type fluid device shown in Fig. 1, and Fig. 6 is an assembled perspective view of the ball coupling mechanism used in the scroll-type fluid device shown in Fig. 1.
FIG. 4 is a cross-sectional view of the electric wire. (a) is a diagram for explaining the operation of the ball coupling mechanism, and shows the movable scroll member at rest, and (b) shows the movable scroll member being driven. 5 shows a conventional example of a crank coupling mechanism, (a) is an assembled perspective view, (b) is a sectional view, and FIG. 6 is a cup showing an embodiment of the present invention. Fig. 7 is an exploded perspective view of the ring mechanism, Fig. 7 is a sectional view of the coupling mechanism showing an embodiment of the present invention, and Fig. 8 shows another embodiment of the present invention. A cross-sectional view when the elastic sleeve is installed on the inner ring of the ball bearing, °(b) is a cross-sectional view when the elastic sleeve is installed on the inner ring of the ball bearing with the elastic sleeve placed on the fixed member side,
FIG. 9 shows still another embodiment of the present invention (a)
(b) is a cross-sectional view when the elastic sleeve is installed on the outer ring of a ball bearing that is placed on the rotating member side, and (b) is a cross-sectional view when the elastic sleeve is installed on the outer ring of a ball bearing that is placed on the stationary member side. It is a diagram. Front end plate 14...Crankshaft 16...Swivel member 1
7.18 Bearing 19 Crank element 14
1... Drive pin 111, 163... Concave portion 192
・Crank pin 201-・Steel sleeve 20
2. Rubber (α Figure S (a))

Claims (1)

[Scope of Claims] (11) A movable piston member that performs circular orbital motion, a drive mechanism coupled to the movable piston member for imparting circular orbital motion to the movable piston member, and a circular orbit of the movable piston member. In a rotating piston type fluid device including a rotation prevention mechanism that prevents rotational movement of the movable piston member during movement, an inner wall surface facing the movable piston of a fixed member rotatably supporting a main shaft constituting the drive mechanism. A plurality of first recesses are formed thereon, and a first bearing is disposed within the recesses, and a second recess corresponding to the recesses is also formed on the end surface of the movable piston member facing the recesses. and a second bearing is disposed within the second concave portion, and is located at a position eccentric from the center of the disk portion and the disk portion by substantially the same radius as the circular orbit drawn by the movable piston member. A rotation prevention mechanism used in a rotating piston type fluid device, characterized in that a crank element having a central axis and a pin protruding in the axial direction is supported by bearings disposed in two opposing recesses. (2) The rotating piston type fluid device according to claim 1, characterized in that a sleeve having an elastic force is disposed between the inner ring of at least one bearing and the crank element fitted and supported by the bearing. (3) The rotating piston type fluid according to claim 1, characterized in that a sleeve having elastic force is disposed between at least the outer ring of one of the bearings and the concave portion. Rotation prevention mechanism used in equipment.