JPH08121353A - Rotary vane type pump - Google Patents

Abstract

PURPOSE: To easily keep a side gap between the side of a rotor and the inner surface of a side housing at a constant value without needing high-grade arts by correcting the error of a product manufacturing size and the error of a press-in size during assembly through simple regulation of a screw. CONSTITUTION: A drive shaft 7 to support a rotor 6 is rotatably supported through a deep groove ball bearings 9 and 10 arranged in drive shaft insertion spaces 8 and 8 in side housings 2 and 3. Engagement between the outer ring 9b of the deep groove ball bearing 9 and a drive shaft insertion space inner surface 8a in the side housing 2 is axially movable through intermediate fitting or clearance fit. An inner ring 9a constrains the drive shaft through interference fit, a coil spring 11 is disposed at the inner ring 9b of the deep groove ball bearing 9 and a coil spring 12 and a regulating screw 13 are disposed at the outer ring 10b of the deep groove ball bearing 10, and gaps 5 and 5 are regulated through rotation of the regulating screw 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotor supported by a drive shaft which is rotatably supported through a deep groove ball bearing arranged in a drive shaft insertion space in a side housing, and the rotor has a plurality of vanes. A rotary vane type pump in which a vane is slidably provided in a groove and is arranged with a certain gap between the inner surface of both side housings in a rotor chamber formed by a center housing and both side housings. The present invention relates to one in which a gap between a rotor and a side housing can be easily adjusted to a constant gap.

[0002]

2. Description of the Related Art Rotary vane type pumps have side gaps (indicated by 100 in the figure) of 3 in order to maintain pump function.
The metal contact is prevented by keeping the thickness between 0 μ and 50 μ, and in order to keep the side surface gap 100 constant, the following conventional techniques have been adopted.

For example, the outer ring 201 of the deep groove ball bearing 200 and the inner surface 501 of the drive shaft insertion space in the side housing 500 are fitted by an intermediate fit or a clearance fit, so that they can be moved in the axial direction. The side gap 100 is maintained by pushing the outer ring 201 with the spring 400 to offset the axial play (about 0.1) of the bearing 200 (FIGS. 3 and 4).
reference).

[0004]

However, in the above-mentioned prior art, the precision control of the dimension 600 of the side housing 500 and the press-fit dimension 70 of the inner ring 202 which is a tight fit with the drive shaft are performed.
Management of 0 required advanced technology. I.e. spring 40
0 means that it is necessary to appropriately select the optimum one (the number of spring threads) for the accuracy control and press-fit dimension control, which requires a high level of skill and skill, and it is necessary to prepare a large number of springs to support it. Yes, there was a problem that the cost increased and it became complicated.

The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to eliminate an error in a component manufacturing dimension and an error in a press-fit dimension during assembly by a simple screw adjustment. By enabling correction,
(EN) A rotary vane type pump capable of easily maintaining a constant side surface gap between a rotor side surface and an inner surface of a side housing without requiring a high technology as in the past.

[0006]

The technical means of the present invention for achieving the above object is rotatably supported via a deep groove ball bearing arranged in a drive shaft insertion space in a side housing. The rotor is supported by the drive shaft, the vanes are slidably provided in the plurality of vane grooves, and a constant clearance is provided between the inner surface of both side housings in the rotor chamber formed by the center housing and both side housings. In a rotary vane pump arranged with a space, an outer ring of one bearing is provided with an elastic body capable of pressing the outer ring side surface in one direction, and an outer ring of the other bearing is pressed in one direction the outer ring side surface. In addition to arranging a flexible elastic body, an adjustment screw that can be pushed forward and backward to the inner surface of the drive shaft insertion space in the side housing and presses the opposite side surface It is that you composed.

In addition, the tension of the first elastic body is weaker than that of the second elastic body.

[0008]

With the above technical means, the fit between the outer ring of the deep groove ball bearing and the inner surface of the drive shaft insertion space in the housing can be moved in the axial direction by an intermediate fit or clearance fit, and the inner ring fits tightly. The drive shaft is restrained with the purpose.
Then, by rotating the adjusting screw to adjust the pressing force of the outer ring side surface of the bearing, the play in the axial direction of the bearing is canceled and the position of the drive shaft is completely determined in the axial direction. Therefore, when the position of the drive shaft is improper and the side surface gap cannot be properly held due to an error in the component size, the side surface gap can be adjusted to a constant interval (30 μ to 50 μ) by the above-described action.

[0009]

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

FIG. 1 shows an example of a rotary vane type pump according to the present invention, which is located in a rotor chamber 4 formed by a center housing 1 and side housings 2 and 3 and between inner surfaces of the side housings 2 and 3. The rotor 6 is eccentrically supported by the drive shaft 7 with a constant gap 5 and 5 left therebetween.

Although not shown, the rotor 6 is also provided.
A large number of vane grooves orthogonal to the outer peripheral direction of the rotor are bored in the direction of the central axis, and the vanes are slidably fitted in the vane grooves. Due to the centrifugal force or the fluid pressure accompanying the rotation of the rotor 6, it makes a radial movement and also rotates together with the rotor 6 while being in contact with the inner wall surface of the center housing 1.

The drive shaft 7 supporting the rotor 6 is rotatably supported via deep groove ball bearings 9 and 10 arranged in the drive shaft insertion spaces 8 and 8 in the side housings 2 and 3, respectively. The shaft 7 is provided with bearing stop portions 7a, 7b having a larger diameter than the other portions, and the inner rings 9a, 10a of the bearings 9, 10 have one side surface 9a ', 10a'.
Are in contact. The outer rings 9b and 10b of the deep groove ball bearings 9 and 10 have a first elastic body 11 and a second elastic body 12, respectively.
And the adjusting screw 13 is provided.

That is, the outer ring 9b of the deep groove ball bearing 9 and the inner peripheral surface 8a of the drive shaft insertion space in the side housing 3 can be axially moved by an intermediate fit or a clearance fit. 9a restrains the drive shaft 7 with an interference fit.

As the first elastic body 11 and the second elastic body 12, for example, coil springs are used as shown in the drawing, and the first elastic body 1
1 is an outer ring 9 b and a receiving member 14 of one bearing 9.
And the side surface of the outer ring 9b can always be pressed in one direction (axial direction).

The second elastic body 12 is disposed between the outer ring 10b of the other bearing 10 and the inner wall 8'of the drive shaft insertion space, and always presses the side surface 10b 'of the outer ring 10b in one direction (axial direction). It is possible.

Further, the first elastic body 11 and the second elastic body 12 can be changed to a known elastic body such as a leaf spring or a rubber material in place of the coil spring, and are not particularly limited.

The adjusting screw 13 has, for example, a threaded portion 13a on its outer peripheral surface as shown in the drawing, and a ring which can be screwed onto a threaded portion 8b provided on the inner peripheral surface 8a of the drive shaft insertion space 8 in the side housing 2. The adjustment screw 13 is screwed onto the inner peripheral surface 8a of the drive shaft insertion space 8 so as to be movable back and forth so that the side surface 10b "on the opposite side of the bearing 10 can be pressed. The shape of the screw 13 is not limited to the above shape, and may be, for example, longer or shorter than the illustrated shape, and the groove depth of the screwing portion 13a is arbitrary and can be changed appropriately.

Therefore, with the above structure, the load is applied to the bearings 9 and 10 and is determined at a position deviated from the center of the track of the rolling elements 15 of the bearings 9 and 10, that is, a position indicated by x in the figure (bearing 9). The axial play of the rotor 6 is offset), and the axial movement of the rotor 6 is prevented. For example, if the position of the drive shaft 7 is improper and the gap 5 cannot be held properly due to an error in the component dimensions, the position can be corrected by turning the adjusting screw 13.

As a result, it becomes easy to control the press-fitting dimension y of the inner ring 9a which is a tight fit with the drive shaft 7. That is, it is not necessary to appropriately select the coil spring that is most suitable for the press-fitting dimension control, and it does not require high skill and skill.
Further, it is not necessary to prepare many springs so that the adjustment can be made by simply adjusting the adjusting screw 13.

FIG. 2 shows another embodiment of the present invention. In this embodiment, the first elastic body 11 and the bearing 9 are used.
Is arranged over the outer ring 9b and the inner wall 8'of the drive shaft insertion space 8 so that the side surface of the outer ring 9b can be constantly pressed in one direction (axial direction). The other structures and operations are the same as those of the embodiment shown in FIG. 1 and described in detail above, and the same parts are designated by the same reference numerals and the description thereof will be omitted.

Further, in this embodiment, the first elastic body 1
1 makes the tension weaker than the second elastic body 12 (1/2
The first elastic body 11 prevents the bearing 9 from moving.

[0022]

The present invention has the above-mentioned structure,
By adjusting the pressing of the outer ring side surface of the bearing by turning the adjusting screw, the axial play of the bearing is offset together with the spring action, and the position of the drive shaft is completely determined in the axial direction. Even if the position of the drive shaft is incorrect due to an error in the component dimensions and the side surface gap cannot be properly held, the side surface gap can be adjusted to a constant interval (30 μ to 50 μ).

Therefore, it is necessary to appropriately select the optimum spring (number of springs) for controlling the accuracy of the dimensions of the side housing and controlling the press-fitting dimension of the inner ring that is tightly fitted to the drive shaft. In contrast to the conventional technology, which required a high level of skill and technology, and required a large number of springs to be prepared for it, which resulted in high costs and complexity, there was an error in the manufacturing dimensions of parts and assembly. By making it possible to correct the error in the press-fitted dimension at the time by simple screw adjustment,
It is possible to easily maintain a constant side surface gap between the rotor side surface and the side housing inner surface without requiring a high-level technique as in the past.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing an embodiment of the present invention.

FIG. 2 is a vertical sectional front view showing another embodiment.

FIG. 3 is a vertical sectional front view showing a conventional technique.

FIG. 4 is a vertical sectional front view showing another example of the prior art.

[Explanation of symbols]

 1: Center housing 2, 3: Side housing 4: Rotor chamber 5: Gap 6: Rotor 7: Drive shaft 8: Drive shaft insertion space 9, 10: Deep groove ball bearings 9a, 10a: Inner ring 9b, 10b: Outer ring 11: No. One elastic body 12: Second elastic body 13: Adjustment screw 13a: Threaded portion

Claims (2)

[Claims] 1. A rotor is supported by a drive shaft rotatably supported via deep groove ball bearings arranged in a drive shaft insertion space in a side housing, and the rotor slides vanes in a plurality of vane grooves. In a rotary vane type pump that is movably provided and has a constant gap between the inner surfaces of both side housings in a rotor chamber formed by a center housing and both side housings, the outer ring of one bearing is the outer ring. A first elastic body is arranged so that the side surface can be pressed in one direction, a second elastic body that can press the outer ring side surface in one direction is arranged in the outer ring of the other bearing, and a drive shaft insertion space in the side housing A rotary vane type pump having an inner surface provided with an adjusting screw that can be screwed back and forth and can press the opposite side surface. 2. The rotary vane type pump according to claim 1, wherein the tension of the first elastic body is weaker than that of the second elastic body.