JPS603486A - Vane motor or pump - Google Patents

Abstract

PURPOSE:To aim at reducing power loss, by providing projection on the inner peripheral surface of a rotor chamber so that no pressure differential comes about between both sides of a vane during extension and retraction of the vane, and the vane is prevented from extending and retracting during effective operation of the vane. CONSTITUTION:Each vane 52 does not extend and retract during the vane 52 slides on the front end face 28 of each projection 24 provided on a rotor inner peripheral surface 20. Further, both chambers on both sides of the vane 52 are communicated with a high pressure port 62 during sliding of the vane 52 on one side surface 26 of the projection 24 on the discharge side so that no pressure differential comes out between both sides of the vane 52 as well as on the low pressure inlet and outlet port 64 side. The vane 52 extends and retracts with respect to the rotor outer peripheral surface 36 only when the vane 52 slides on the other side surface 26 of the projection 24. During sliding of the vane 52 on the other side surface 26 of the projection 24, the pressures on both sides of the vane 52 are equal together. Accordingly, the smooth extention and retraction of the vane may be realized in order to aim at reducing power loss.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane motor pump of this type, which is housed in a rotor chamber of a housing and has vanes that are movably held in and out of the rotor.

Such vane motors and pumps include those in which a 20-meter motor is eccentrically arranged and has a cylindrical outer circumferential surface in a rotor chamber with a circular cross section, and one that has a cylindrical outer circumferential surface in the center of a rotor chamber with an elliptical cross section. It is generally known that the rotors are arranged concentrically. In either type, the vanes move in and out of the rotor outer circumferential surface as the rotor shaft rotates, and one vane has a volume surrounded by two adjacent vanes, the rotor outer circumferential surface, and the rotor indoor circumferential surface. It takes advantage of change. Inlets and outlets for the working fluid are provided on both sides of the point where the volume changes from increasing to decreasing and the point where the volume changes from decreasing to increasing. In the case of a motor, a fluid such as oil, suspension, or viscous fluid is supplied between two vanes to generate rotor rotational force in the direction of increasing volume, and fluid is discharged on the side of decreasing volume. be done. On the other hand, in the case of a pump, by rotating the opening and closing, fluid is sucked in on the volume increasing side, and high pressure fluid is discharged on the volume decreasing side.

The vane slides into contact with the rotor chamber circumferential surface at its tip, and moves in and out of the rotor outer circumferential surface as the distance between the rotor chamber circumference and the rotor outer circumferential surface changes. A lateral load from the high-pressure side to the low-pressure side, that is, a load perpendicular to the vane surface, increases the sliding resistance between the vane and rotor, which overcomes this sliding resistance. One drawback is that the power loss increases when moving the vanes in and out.

In most motors and pumps, the volume of the chamber surrounded by the vanes, the rotor outer circumferential surface, and the rotor inner circumferential surface changes according to a sinusoidal curve or a curve close to it. Torque fluctuations include discharge pulsation.

With this background in mind, the present invention has been developed so that no pressure difference occurs on both sides of the vane while the vane is moving in and out, and the
Vane motors are designed for the purpose of providing a pump in which the vanes do not move in or out of the rotor while the vanes are in effective operation.

To achieve this purpose, the vane motor pump according to the present invention is provided with: (1) a rotor chamber having a circular cross-sectional shape; a housing having at least two protrusions connected to its inner circumferential surface at equal angular intervals, and (i) a housing provided concentrically and rotatably within the rotor chamber, the outer circumferential surface of which is a cylindrical surface being a tip end surface of the protrusions; a rotor that contacts or approaches in front of the rotor; and a rotor shaft that protrudes concentrically from the center of both end faces of the rotor, is rotatably supported by the housing, and has at least one end protruding outside the housing; ■Vanes that can enter and exit the rotor from the outer circumferential surface of the rotor, are arranged at equal angular intervals that are an integral multiple of 2 or more of the protrusions, and whose tips can come into sliding contact with the inner circumferential surface of the rotor and the protrusions. and (1) a first fluid inlet/outlet and a second fluid inlet/outlet formed on both sides of the protrusion and having a size that communicates with the chambers on both sides of the vane while the vane is in sliding contact with both sides of the protrusion. It is configured to include.

In this construction, the vanes rotating together with the rotor pass over the protrusions and come into sliding contact with the circumferential surface of the rotor chamber. While the vanes are in sliding contact with the rotor's inner peripheral surface, they do not move in or out of the rotor's outer peripheral surface, but in the process of sliding against the vane insertion side of the protrusion, the vanes are pushed inward, causing the vanes on the protrusion to move inward. In the process of sliding into contact with the side surface on the extraction side, it protrudes to the outside i.

However, in the process in which the vane passes through both sides of the protrusion, a pressure difference is created on both sides of the vane as the vane simultaneously passes through the first fluid inlet/outlet and the second fluid inlet/outlet. There is no problem, and both chambers are maintained at substantially the same pressure. Accordingly, the sliding resistance between the vanes and the rotor is reduced, ensuring that the vanes can move in and out easily, resulting in the effect of reducing power loss.

During the torque generation process or high Lt fluid discharge process in which the vanes are effectively acting, a constant discharge amount is always obtained unless the vanes move in and out.

In addition, when two or more protrusions are provided and the number of vanes is an integral multiple of 2 or more than the number of protrusions, the gap between the protrusions and the vanes in the area between each protrusion is the same as that of two adjacent vanes. The forces acting in the radial direction of the rotor are balanced as a whole based on the pressure of the partitioned chambers, and it is avoided that a load is applied to the rotor shaft in a direction perpendicular to the axis. As a result, the bearing can be made smaller and the durability can be maintained at a high level.

Hereinafter, an embodiment in which the present invention is applied to a hydraulic vane motor will be described in detail based on the drawings.

In FIG. 1, 2 is a cylindrical rotor casing main body, the openings on both sides of which are closed by a front I side plate 4 and a rear side plate 6, and a front/S cow puffer 8 and a rear housing 10 are arranged outside of these. and each of them is fastened by a bolt 12 to form an integral housing 14. A space surrounded by the rotor casing body 2 and both sides 1 and plate 4.6 is the rotor chamber 16, and the O ring 1
8 ensures oil tightness from the outside.

As is clear from FIG. 2, the rotor chamber 16 has a circular cross-sectional shape, in other words, the rotor chamber circumferential surface 20 is a cylindrical surface. Two radially inwardly protruding protrusions 24,24 are provided at symmetrical positions with respect to the rotor chamber centerline.

These protrusions 24 are formed along the entire length of the rotor casing body 2 in a direction parallel to the rotor chamber center line, and both side surfaces 26 and 26 thereof are symmetrical with each other and are smoothly connected to the rotor chamber circumferential surface 20. It is like that.

A tip end surface 28 of the round protrusion 24 is constituted by a part of a cylindrical surface centered on the rotor chamber center line.

In this embodiment, the projections 24.24 are separate from the rotor casing main body 2, and are formed on the rotor chamber circumferential surface 20, and the projection forming members 82.82 are formed in the coupling grooves 30.30 as the four connecting parts. It was formed in honor of the fact that one of these was buried. Therefore, even if the protrusions 24.24 protrude from the rotor chamber circumferential surface 20, the rotor chamber circumferential surface 20 is cut into a cylindrical surface in advance and the grooves 80 are cut.
, 80 and 80 and then fit the protrusion forming members 82 and 82, which makes manufacturing easy.

Furthermore, although each protrusion forming member 32 is screwed in from the outside of the rotor casing body 2 and held by the tcoport 33, it is not completely tightened to the bottom surface of the fitting groove 30 (t [
The rotor chamber 16 is allowed to move slightly in the radial direction without being distorted. The sides of both side surfaces 26 of the protrusion forming member 320 and the back side are communicated with each other through the communication hole 34, and the space between the protrusion forming member 32 and the bottom surface of the fitting groove 30 is sealed by a string-shaped sealing member 35. As a result, the pressure inside the rotor chamber 16 is applied to the rear surface, and the difference Q between the back pressure and the pressure on the rotor chamber 16 side causes the protrusion forming member 82 to press against the outer peripheral surface 36 of the rotor 38.
The outer circumferential surface 36 is shaped like a circle with a certain width and contacts the tip surface 28.28 of the protrusion 24.24 with a certain width, and the rotor chamber 1
The space within 6 is divided into an A area and a JS area with both protrusions 24 as boundaries.

A rotor shaft 40 is provided passing through the center of the rotor 38, and a key 41 prevents relative rotation of the two shafts. The f-filtering rotor 38 and the rotor shaft 40 may be formed integrally. As is clear from FIG. 1, the rotor shaft 40 protrudes concentrically from the center of both end surfaces of the rotor 38, and is rotatably supported by the front housing 8 and rear housing 10 via bearings 42 and 44. The part of the rotor shaft 40 on the side supported by the bearing 42 is made to protrude outside from the front 1 hen 1 sink '8 through the bearing cover 46, and is directly attached to the 1 pseudo-moving object with the protruding part. are indirectly connected via a transmission system.

Note that 48 is a shaft seal, and 50 is an O-ring.

As is clear from FIG. 2, the rotor 38 is provided with four vanes 52 at equal angular intervals.
4 so as to be able to move in and out in the radial direction from the rotor outer peripheral surface 36. These vanes 52 have the same length as the axial length of the rotor 38, and are rounded and have a fifth end at the tip thereof, which connects the rotor indoor circumferential surface 20 and the protrusions.
24, 24, it is said to have been performed as Noh in Suri-nouchi-cho. The vane tips and the rotor indoor circumferential surface 20 are each biased by a spring 55 in a direction to protrude from the rotor outer circumferential surface 36.
The initial contact pressure between the two is given as follows.

On the inner surfaces of both sides I and plays 1 to 4 and 6, arcuate grooves 56, 58 and 60, which can communicate with the inner ends of the vane grooves 54, are provided in the Δ area and B area, respectively. Further, on both sides of each protrusion 24, hydraulic oil inlets and outlets 62 and 64 are provided (sliding) to open into the rotor chamber 16. When the rotation is to be made in the normal direction shown by the arrow, the inlet/outlet 62 becomes the inlet for hydraulic oil, and the inlet/outlet 64 is the outlet. However, when the rotation is to be made in the direction shown by the white arrow, the inlet/outlet 64 becomes the inlet, becomes the exit.

Each of the above circular arc grooves 56.56 is communicated with the entrance/exit 62.62, and the circular arc groove 60.60 is connected to the entrance/exit 64.64.
26 and 26 on both sides of each protrusion 24.
In the process of the vane 52 sliding in and out of the rotor outer circumferential surface 36, the pressure is made equal on the tip side and the inner end side of the vane 52, and when the vane 52 comes out, hydraulic oil is replenished into the vane groove 54. However, when the vane 54 enters, the loop 1 is energized to allow discharge of hydraulic oil from the vane groove 54. On the other hand, inlet pressure is constantly introduced into the arcuate grooves 58 and 58 via a communication path (not shown), thereby maintaining an appropriate contact pressure between the tip of the vane 52 and the rotor chamber circumferential surface 20 together with the biasing force of the spring 55. It is made to work.

In addition, this motor throttles the flow of hydraulic oil on the outlet side, and also connects the circular arc grooves 56, 513, and 60 to the downstream side of the throttle valve by switching the switching valve. It is also possible to keep the motor 52 in the retracted state 5 so that the motor does not rotate despite the supply of hydraulic oil.

The entrance/exit port 62 and the opening 64 are formed between the front sight plate 4 and the end of the protrusion 24,
While one of the vanes 52 is sliding in and out of sliding contact with either side surface 26 of the protrusion 24, a sufficient area can be communicated with both chambers on both sides of the vane 52. The entrances and exits 62 and 64 located on the A area side and the IS area side of the rotor chamber 16 form a pair. Even if it is, each vane is so thick that it is partitioned by two vanes 52 and does not communicate directly with each other. Both the entrances and exits 62 and 64 adjacent to each other with each protrusion 24 in between have a sealing effect between the protrusion 24 and the rotor 38, and the sealing member 3 described in Mtl.
5, they do not communicate with each other.

Next, the operation of the hydraulic vane pump constructed as described above will be explained.

When high-pressure hydraulic oil is supplied into the rotor chamber 16 from the entrances and exits 62 in both areas A and B, the pressure of the hydraulic oil is applied to the vane 5.
2, and a counterclockwise rotational force is applied to the rotor 38 in FIG.

When the vane 752 approaches the entrance/exit port 64, the trailing vane 52 comes off the entrance/exit port 62 and receives the pressure of the hydraulic oil. The hydraulic oil present on the side of the magnetic vane 520ijJ is carried to the inlet/outlet 64g40 as the vane 52 moves, and is discharged to the outside from the inlet/outlet 64 due to a decrease in the volume between the protrusion 24 and the vane 52. This action is repeated in both the Δ and B regions, and the rotor 38 is continuously rotated.

Although the vanes 52 do not move in and out of the rotor 38 during the sliding process on the rotor indoor circumferential surface 20, the vanes 52
2 slides onto the side surface 26 of the protrusion 24 on the rotation side, and then is pushed back inward in the process of climbing onto the distal end surface 28 of the protrusion 24.

During the process until the vane 52 rides on the tip surface 28 of the protrusion 24, the chambers on both sides of the vane 52 are both in communication with the low-pressure inlet/outlet 64.Secondly, the pressure on both sides of the vane is maintained at the same pressure. can come. During the filtering process, when the vane 52 slides on the tip surface 28 of the protrusion 24, the chambers on both sides of the vane both communicate with the high-pressure inlet/outlet 62, resulting in a state of
Low-pressure inlet/outlet 64 (Similar to full, no pressure difference occurs on both sides of the vane. 1° The vane 52 moves in and out of the rotor outer peripheral surface 36 due to the 1 lll of the projection 24.
11 Only when passing through 26, this side [m26
The process of passing -r is 1 where both sides of the vane 52 have the same pressure.
Therefore, no pressure in the perpendicular direction is applied to the vane 52, ensuring smooth movement in and out of the vane 52, resulting in less power loss compared to conventional smoker vanes, which are subjected to pressure in the perpendicular direction and move in and out while moving in and out. less.

If the rotational speed of the rotor 38 increases,
The vane 52 passing through the protrusion 24 may not be able to slide into immediate contact with the outlet side surface 26 due to its inertia, but if such a situation occurs, the hydraulic oil No leakage occurs and motor efficiency is not reduced.

Since the distance between the rotor indoor circumferential surface 20 and the rotor outer circumferential surface 86 is constant, the vanes 5 that receive the pressure of the hydraulic oil.
The effective area of No. 2 is also always constant, and a constant output torque without fluctuation can be obtained.

The vane motor of this embodiment has two protrusions 24 and four vanes 52 spaced at equal angular intervals.
In addition, in areas A and B, the phases of the high pressure areas partitioned by the protrusion 24 and one vane 52 or two adjacent vanes 52 are symmetrical with respect to the center of the rotor chamber 16, and are always in the radial direction of the rotor 38. The balance of forces is maintained. As a result, no bending moment is generated on the rotor shaft 40 in a direction perpendicular to the axis, and there is no risk of bending deformation of the rotor shaft 40 even when using high-pressure hydraulic oil, making it possible to use single-sided bearings. The load can also be small.

In particular, the chamber in area A, which is partitioned by two adjacent plates 752 in the high-pressure area, and the similar chamber in area 13, which is in a symmetrical phase position across the rotor center of rotation, are shown in Figure 2. to 2
If the rotor chamber 16 is communicated with each other through a communication path that has openings 66 and 66 as shown by the dashed line, even if there is a possibility that pressure imbalance may occur due to errors in machining or in the morning, this can be avoided. It can be completely resolved.

Note that when high-pressure hydraulic oil is supplied into the rotor chamber 16 from the inlet/outlet 64 and discharged from the inlet/outlet 62, a reverse driving force is applied to the rotor 38 in the direction indicated by the white arrow. The smooth effect is obtained in the same way as when rotating forward.

This concludes the description of Embodiment 1 of the present invention! Second, this is literally an example, and there are various other embodiments.

For example, in the embodiment described above, two protrusions 24 were provided on the rotor chamber circumferential surface 20, and four vanes 52 were provided on the rotor 38. For example, as briefly shown in FIG. Three protrusions 24 are provided at equal angular intervals on the circumferential surface 20 of the rotor chamber.
while six vanes 52 are installed on the rotor 38.
, and entrances and exits 62 and 6 on both sides of each protrusion 24, respectively.
4 may be formed in a size that does not directly communicate with the protrusions 24, and as shown in FIG.
The number of vanes 52 is 2 or more, and the number of vanes 52 is equal to 2 of the number of protrusions.
It may be an integer multiple of the above.

In addition to being provided in the radial direction of the rotor 38, the machining vanes 52 may be inclined relative to the radial direction.

However, it is not an essential requirement to apply pressure from the entrance and exit ports 62 and 64 to the back surface of the protrusion forming member 32 and to hold it in a floating state by the hole 1-33.
2 can be fixed by completely tightening 4 screws into the fitting groove 30 with bolts 33, or can be press-fitted into the fitting groove 30 by 11 screws.

Further, although it is desirable to form the protrusion 24 on the protrusion forming member 32 for ease of processing, it is not necessary to form the protrusion 24 integrally with the housing, such as the rotor casing body, on the periphery of the rotor chamber. It is also possible to form it by copying or the like together with the surface. The tip surface of the round protrusion does not have to be a concave curved surface corresponding to the curvature of the rotor's outer circumferential surface, but should be a curved surface that is convex toward the rotor's outer circumferential surface so that the two are in linear contact or very close to each other. It can also be configured as follows.

Furthermore, in addition to providing entrances and exits 62 and 64 that overlap part of the housing such as the front side plate 4 and the end of the projection 24, a portion of the entrance and exit is covered by the end surface of the projection 24. Configurations are also possible.

Furthermore, the present invention can be applied not only to vane motors but also to vane pumps, and in that case, 1
Fluid is sucked in from the fluid inlet and outlet of Mr. LEillIII,
The difference is that the fluid is discharged through the high-pressure side fluid inlet/outlet, but the principle is the same.i) A constant discharge pump without pulsation can be obtained.

It goes without saying that the present invention can be implemented in various ways by making various changes and improvements without departing from the scope of the claims.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of a hydraulic vane motor which is an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II--II in FIG. 3 and 4 are simplified diagrams each conceptually showing another embodiment of the present invention. 14: Housing 16: Loaf chamber 20: Rotor chamber inner peripheral surface 24: Projection 26: Projection side surface 28: Projection tip surface 30: Fitting groove 32: Projection forming part 88: Bolt 34: Communication hole 35: Seal member 36: Rotor Outer peripheral surface 38: rotor
40: Rotor shaft 52: Beneath 55: Sublinoge 62: Inlet/outlet (first fluid inlet/outlet) 64: Inlet/outlet (second fluid inlet/outlet) 66: Opening of communication passage Applicant Legal company Technol procedure amendment (Own Ship Patent Office Director Kazuo Wakasugi ■, small case indication 1982 Patent Application No. 11.0392 2, name of invention Vane motor or pump 3, person making amendment Relationship with the case Patent applicant name Title Chikunor Co., Ltd. 4, agent ■ 450 (1) Contents of the amendment to Detailed Explanation of the Invention in Book 811I of Mei 811I (1) Specification■ Page 6, line 20, "Aiha" is corrected to "or". (2) Same page, page 12, Insert “passage or tank” next to line 13 “downstream side”. (3) Same page 12, lines 15 to 16 “Despite the supply of hydraulic oil...” .j should be corrected to "It is possible to put the motor in a state where it can rotate freely regardless of the supply of hydraulic oil." and amend it to ``.''.

Claims (3)

[Claims] (1) A rotor chamber with a circular cross-sectional shape is provided, and at least two protrusions are provided on the inner circumferential surface of the rotor chamber at equal angles, parallel to the middle hair line of the rotor chamber, and both sides smoothly connected to the inner circumferential surface. a housing provided with a spacing; a rotor that is concentrically and rotatably disposed within the rotor chamber and whose outer peripheral surface, which is a cylindrical surface, contacts or closely approaches the tip surface of the protrusion; and both end surfaces of the rotor. The rotor shaft protrudes concentrically from the center, is rotatably supported by the housing, and has at least one end protruding outside the housing, and is capable of entering and exiting the rotor from its outer circumferential surface, and has a vanes that are provided at equal angular intervals in a number that is an integral multiple of 2 or more and that can slide on the RjJ rotor indoor circumferential surface and the protrusion at their tips; and vanes that slide on both sides of the protrusion; A vane motor pump comprising a first fluid inlet/outlet and a second fluid inlet/outlet formed in a size that communicates with chambers on both sides of the vane while in contact with each other. (2) The vane motor according to claim 1, wherein the protrusion is formed on the circumferential surface of the rotor chamber and is formed by a member separate from the housing, which is fixed by fitting into a recess. Mafko is a pump. (3) A chamber surrounded by two adjacent vanes, the rotor indoor circumferential surface and the rotor outer circumferential surface, and a similar chamber located in a symmetrical phase position with respect to the rotor center are communicated through a communication path. The vane motor according to the claims 1 to 2 is a pump.