JPS58185983A - Hydraulic axial-flow piston machine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic axial flow bison concealment machine as defined in claim 1.

Various axial piston machines of the above type are known.

In general, known axial piston machines provide roller bearings between a stator and a rotor formed by a cylinder body. The roller bearing produces a relatively large amount of noise. In the case of such axial piston machines, sliding bearings are not used because of the severe stresses they generate and the short useful life. This is particularly due to the following circumstances: Thus, functionally, the center-point sliding bearing includes a stationary bearing bushing and a rotating shaft whose eccentric movement, as the shaft rotates, forms a fluid lubrication/PI film in the pressurized zone.

The difficulties in using oriented sliding bearings in high pressure axial flow piston machines are, for example, highly dependent on speed, pressure, temperature and the like. lt viscosity, i.e. the viscosity of the supplied hydraulic fluid in all types of equipment, is due to wide variations in the manipulated variable. Even limited wear to the contact openings due to mixed friction can contaminate the hydraulic fluid and cause wear to other parts of the machine or to the components of the next connecting mechanism. This should be avoided at all costs under any operating conditions.

Similarly, the fluid/1gI synovial contact capacity of sliding bearings is also significantly influenced by misalignment. That is, the line pressure will significantly reduce the contact volume and will also result in harmful mixing friction.

Generally, these difficulties can be avoided by using multifaceted sliding bearings, which are expensive and expensive to construct.

The object of the invention is to provide an axial piston machine of the above type in which the noise generated by the bearing between the stator and the cylinder body is reduced, without significantly reducing the useful life of the bearing. .

This object is basically solved by the characterizing parts of claim 1.

According to the invention, it is possible to take advantage of the construction principles and advantages of sliding bearings while avoiding their disadvantages.

The bearing ring rotates in proportion to both the stator and the rotor, ie the cylinder body. This construction significantly reduces noise in the area, yet does not reduce bearing life compared to roller bearings. Furthermore, such a bearing construction is extremely inexpensive. This impressive result was demonstrated in tests under extreme conditions. The test was conducted after confirming that the wet part of the bearing was not worn at all (minimum value of Sommerfeld number: 0, 1, maximum value: 30). The width of the lubrication gap at the inner and outer peripheries was calculated as a function of the material properties so that the gap had the same width at an operating temperature of about 100°C. The results obtained were excellent from a soundproofing point of view. The useful life was not less than that of conventional roller bearings.

The bearing structure according to the invention is not an ordinary sliding bearing. In the case of the present invention, the bearing ring rotates relative to the stator and cylinder body without fixing a portion of the bearing to other rotating members.

Claims 2 to 4 relate to an advantageously constructed bearing ring.

Claim 5 relates to the protection of certain structural parts of the bearing ring by providing an additional sleeve between the bearing ring and the cylinder body.

Claims 7 and 8 relate to the particular construction and mounting of the stator as a central tube together with the support.

Other features and advantages of the invention will be detailed below, by way of non-limiting example, with reference to the accompanying drawings, in which: FIG.

The axial piston pump has a flange 1 which ensures a secure connection with a corresponding hydraulic oil line. Flange 1
is connected to the housing 2 by screws.

An oil distribution device 3 carrying a control plate 6 is fixed within the housing 2 . The drive shaft 5 passes through the oil distribution device 3 and the control board 6.

The drive shaft drives a cylinder body 7 with a piston 8 . The drive shaft 5 and the cylinder body 7 are connected by a toothed sleeve 38 made of plastic or a similar cushioning material.
in which the inner and outer teeth of the sleeve are shaped to transmit torque. A helical spring 39 ensures a corresponding bias.

Spring lid 4 surrounding other components of the axial piston pump
is fixed by inserting a gasket 37 and using a slap 35. The components are mainly pressure capano
It includes a rotating swash plate 10 that supports II. The pressure capacitor 11 applies a prestress against the rotating swash plate 10 by the pressure plate 9.

The drive shaft 5 emerging from one side of the housing 2 is mounted in a sliding bearing 52 with a corresponding bearing bush and bearing ring. Gasket 53, which also rotates, ensures a corresponding seal. The prestress is implemented by a plurality of springs 56. A bottle 55 is provided to ensure the rotation of the gasket 53. The housing 2 is sealed by a cover 54.

The actual stator of the axial piston pump is formed by a central tube 41 attached to the housing 2 by a 21-tight plastic buffer ring 57. The central tube 41 forms a support frame for receiving all hydraulic forces, including axial and radial forces. The central tube guides the rotating swashplate 10 and for fixing the control base 22, the inclined yoke mounting supports the trunnion ring 42 which absorbs the axial forces of the support and the cylinder barrel 7 forming the rotor.

The cylinder body is supported by a swivel bearing ring 43 with a plurality of radial lubrication holes 48 . The cylinder body 7 is accommodated by a sleeve 45 that is supported axially and radially against a bearing ring 43 . Cooperative with the outer surface of the cylinder body 7, the sleeve is shaped to allow relative axial movement. pin 46
is to prevent relative rotational movement.

The axially biased wave spring 47 ensures that noise when the bearing ring 43 runs is avoided. This bias creates static pressure in the cylinder body 7 on the control plate 6 .

The freely rotatable bearing ring 43 forms an inner lubrication gap Si together with the sleeve 45, and an outer lubrication gap Sa together with the central pipe 41, so functionally the two gaps are located in series. . The average resultant lateral force of all the pistons loaded on the delivery side of the pump is oriented in the direction of arrow Z (FIG. 6) and loads the bearing ring 43 in the center.

The strong hydrodynamic hydraulic membrane formed in the gaps St and Sa is supported by pressurized oil forced from the high-pressure side of the pump via a flow restriction in front of the pressurization zone. The pressurized oil is supplied by an oil supply line 51. The lubrication gap Si is the radial lubrication hole 4B of the bearing ring 43.
Lubricated by. In order to create a load-bearing hydrolubrication film on the side surface of the bearing ring 43, a correspondingly constructed lubrication duct with a shape that changes with the direction of rotation is formed on the collar of the sleeve 45. Thus, during operation, the bearing ring 43 is flooded with stirring oil from the pump housing.

On the other side, the bearing ring 43 is supported against a thrust ring 49 with an opening. As mentioned above, the bearing ring 43 overflows, so during operation, the thrust I.
A strong fluid lubricant film is also formed in the gap with the ring 49.

Central pipe 41, trunnion ring 42, thrust ring 4
9 and the control plate 6 are considered stator members. The cylinder body 7 and sleeve 45 rotate at pump speed. The viscous friction in the lubrication gaps Si and Sa is strong and the bearing ring 4 is
3, there is a moment of forward resistance, so in normal operating conditions (approximately 100° C.) the bearing ring rotates at approximately half the pump speed.

Since the stroke volume of the axial piston pump according to the invention is variable, the piston stroke changes when the pivotably mounted rotating swashplate 10 pivots about the corresponding transverse axis.

In the illustrated embodiment, the rotating swash plate 10 is screwed onto the inclined yoke 12. In either case, ('J oblique joke 12
All guide arms 13 are provided with sliding rings 15 rotatably mounted on two trunnions 14 of a trunnion ring 42.
Tighten laterally.

0 The axis of rotation is the same as the transverse axis or trunnion axis M-M. Since the radius of the rear area 11 of the inclined yoke 12 is R, the yoke 12 is centered on the 1-runion axis M-M.
When rotates, the rotating disk 16 moves linearly. Since a high axial piston force occurs in the pressurizing zone, the inclined yoke 1
2 and the rotating disk 16 are in frictional engagement, and the load roller similarly moves on a flat base, but the difference in the latter is that the roller, i.e. the yoke 12, is fixed to the axis M-M and , that is, the disk 16 moves perpendicular to the axis M-M. The inclined yoke 12 and the rotary disk 16 are connected by a guide groove and a roller 17.

Referring to FIG. 4, rotating disk 16 moves vertically. The rotating disk 16 clamps the linear roller bearings in the same manner as the frame supported by the two linear roller bearings 18 which rotate on the fixed plate 19, with no play between them at any particular position. The cage 20, which is fixed so as not to be provided, plays the role of fixing the position of the bearing 18.

1 When the pivoting movement begins, the rotating disk 16 moves over a range twice the distance of the cage 20 or the linear roller bearing 18.

The fixed plate 19 is placed on a plastic buffer plate 21,
The buffer plate is arranged in a corresponding chamber of the control base 22 screwed onto the trunnion ring 42.

When the rigidities of the rotating disk 16, fixed plate 19, and buffer plate 21 are calculated relative to each other, the elastic deviation at this point of complete contact is the linear contact (electromagnetic pressure) between the inclined yoke 12 and the rotating disk 16.
It is possible to ensure that the contact force due to the contact force is uniformly distributed over the roll body of the linear roller bearing. The plastic buffer plate 21 prevents noise and vibration from being transmitted to the control base 22 during operation of the pump mechanism.

A cage 2 comprising two linear roller bearings 18 and a rotating disk 16 that change according to the turning angle of the inclined yoke 12.
The 0 position is the screws 2 and 4 screwed onto the outside of the retainer 20.
It is determined geometrically accurately by the rotatable cover plate 23 at t14. At the connection point,
The cover plate is attached to a plastic bushing.

A pump regulating device 24 with a regulating piston 25 is positioned within the control base 22 . The adjustment piston 25 has a structure as a differential piston.

A fork-shaped yoke 26 surrounding the bolt 27
It is screwed onto the rod end of the straightening piston. The bolt is rotatably mounted within a horizontal frame 28 screwed onto the inclined yoke 12.

By means of the pump regulator 24, the position of the pressure-dependent regulating screw 25 is transferred to the tilting yoke 12 in such a way that it results in a positive engagement. That is, the specific position of the adjusting screw 1 corresponds to a specific angle of the rotary swash plate 10 and thus to a specific stroke volume of the pump.

The tilting yoke 12 is supported by a support mounted as described above with linear roller bearings on the control base 22, which also contains a complete pump control with adjustment piston.
It is possible to create a machine that is extremely compact, robust, and has a structure with little vibration, and since it is screwed onto the trunnion ring 42 and the central pipe 41, it is particularly effective from the standpoint of noise prevention.

As is clear from FIG. 3, the control slot 32.
33 is provided to ensure connection to the suction line 30 or the delivery line 31. The plastic sleeve 34 noise-isolates the oil distribution device 3 from the housing 2 and thus serves as a sound barrier. Pressurized oil is supplied to the line 36 from the pressurizing side, and it is sent to the pump control device 24 and the duct 5.
Supply to 1.

[Brief explanation of drawings]

1 is a longitudinal sectional view of an embodiment of an axial piston machine according to the invention, in particular an axial piston pump, and FIG. 2 shows the axial piston pump of FIG. 1 rotated by 90°. 3 is a cross-sectional view taken along line A--A in FIG. 1; FIG. 4 is a cross-sectional view along line A--A in FIG. 2; FIG. 5 is a view taken from the direction of arrow X in FIG. 2, FIG. 6 is a detailed view of the sectional view in FIG. 1, and FIG. 7 is a side view of FIG. 4. FIG. 8 shows only the main components of FIG. 6 in a non-sectional view. 1...flange, 2...housing,
3... Oil distribution device, 4... Spring lid, 5...
... Drive shaft, 6 ... Control fall h, 7
・・・・・・Cylinder body, 8・・・・・・Bis 1-N,
9... Pressure plate, 10... Rotating swash plate, 1
1... Pressure pad, 12... Inclined yoke, 13... Guide arm, 14... Trunnion, 15... Sliding ring , 16...
... Rotating disc, 17... Guide roller, 18...
...Roller bearing (linear type), 19...Fixing plate (2), 20...Cage, 21...
Buffer plate (2), 22... Control stand, 23...
... Covering plate, 24 ... Pump control device, 25.
...Iris circumference adjustment piston, 26...Yoke,
27...Bolt, 28...Bridge part, 2
9... Curved surface, 30... Suction line, 3
1... Delivery line, 32. 33... Control throttle 1-134... Plastic sleeve, 35... Strap, 36... Lubricating hole, 37... Gasket, 38... Toothed sleeve, 39... Spiral spring, 40...
...Spring lid, 41...Central tube, 42...
...Second trunnion ring, 43...Bearing 5 ring, 44...45 top, 45...
・Sleeve, 46...Pin, 47...
Wave spring, 48...Oil oil hole, 49...
Thrust 1-ring, 50... Oil duct, 51
...Refueling line for 50, 52...Sliding bearing, 53...Gasket, 54...
Covering body, 55... Bottle, 56... Spring, 57... Buffer ring. Patent ratio M person Ahex Corporation 6 Fig, 4 Fig, 5 I+4'>0 41:l 507- Fiq, 8

Claims (1)

[Claims] +1. ) a shaft for the cylinder body mounted in the housing and reaching the outside on one side, with a bearing between the stator and the cylinder body; between the stator and the cylinder body, the bearing; A rotating swash plate type hydraulic axial flow piston machine, characterized in that the machine has an idler bearing arranged to rotate freely. (2) The axial flow piston machine according to claim 1, wherein the bearing ring is provided with a radial oiling hole for supplying pressurized oil. (3) The axial flow piston machine according to claim 2, characterized in that pressurized oil is supplied just in front of the pressurized zone of the bearing when viewed from the rotational direction. (4) The axial flow piston machine according to claim 3, characterized in that pressurized oil is supplied by a flow restrictor. (5) A sleeve is positioned between the bearing ring and the cylinder body, the sleeve being prestressed against an adjacent side of the cough bearing ring by a laminated spring with a collar. An axial flow piston machine according to claim 1. (6) Forming a lubrication duct within the collar, the duct comprising:
6. Axial piston machine according to claim 5, characterized in that it is inclined in the direction of rotation and points towards the side of the bearing ring. (7) The stator has a central tube, the bearing ring is supported on the central tube, and the central tube is connected to the swash plate mounting portion. The axial flow piston machine according to item 1. 8. An axial piston machine according to claim 1, characterized in that at least one damping ring made of plastic or the like is positioned between the central tube and the housing.