JP2004108260A - Eccentric cam ring support structure for radial type variable displacement fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an eccentric cam ring support structure for a radial type variable displacement fluid machine capable of constantly feeding pressure oil to a static bearing provided between a cam ring and a casing while operating. <P>SOLUTION: In this eccentric cam ring support structure, an eccentric cam ring 2 is slidably supported by thrust bearing surfaces 13a and 13b and flat surfaces 12a and 12b formed at the outer circumferential wall of the eccentric cam ring 2, and the static bearing is disposed between the thrust bearing surface 13a and the flat surface 12a. A pressure chamber in the static bearing is communicated with a pressure oil introducing hole formed in the casing, and pressure oil from a pressure oil port at high pressure flows into the pressure oil introducing hole. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an eccentric cam ring support mechanism for supporting movement of a cam ring in a casing of a fluid type variable displacement fluid machine such as a variable pump, a variable motor or a variable swing pump.
[0002]
[Prior art]
BACKGROUND ART Conventionally, as a radial type variable displacement fluid machine, a radial type variable pump, a radial type variable motor, a radial type variable double swing pump, and the like have been known (for example, see Patent Document 1). Here, a radial type variable pump described in Patent Document 1 will be described as an example of a radial type variable displacement fluid machine with reference to FIG.
[0003]
The casing 40 of the radial type variable pump is closed by a cover (not shown). The casing 40 includes a thrust receiving surface 41 formed on the inner peripheral wall of the casing 40 and a thrust receiving surface 42 provided on the opposite side. Support the bearing surfaces 45 and 46 formed on the outer peripheral wall of the cam ring 44. The thrust receiving surfaces 41 and 42 and the bearing surfaces 45 and 46 are arranged symmetrically with respect to the center line of the cam ring 44, and support the cam ring 44 so that the cam ring 44 can slide in a direction perpendicular to the thrust direction.
[0004]
As shown in FIG. 6, a pressure chamber 47 constituting a hydrostatic bearing is provided between the thrust receiving surface 42 and the bearing surface 46, and the pressure chamber 47 is provided through a passage 43 provided in a wall of the cam ring 44. It communicates with the inside of the cam ring 44 on the high pressure load side. That is, one end of the passage 43 opens to the pressure chamber 47, and the other end opens to the sliding surface 58 of the cam ring 44.
[0005]
The cam ring 44 is slid and positioned by a stopper 48 that forms a moving mechanism disposed in the casing 40 in a diametrically opposed manner and a pressing piston 49 urged by a spring 50.
[0006]
The bearing surfaces 45 and 46 of the cam ring 44 and the thrust receiving surfaces 41 and 42 provided on the inner peripheral wall of the casing 40 are provided in parallel with the sliding direction of the cam ring 44 by the moving mechanism. It serves as a guide when sliding in the direction and at the same time prevents the cam ring 44 from rotating.
[0007]
The inner peripheral surface of the cam ring 44 is formed in a substantially cylindrical shape, and a cylinder block 55 is rotatably supported by a fixed valve 54 provided in the casing and provided with passages 52 and 53 in the inner peripheral surface. A rotating shaft (not shown) supported by the casing 40 is connected to the cylinder block 55 via a clutch or the like. As shown in FIG. 6, a plurality of radially extending cylinders 51 are bored in the cylinder block 55, and a working piston 56 slides in each of the cylinders 51. Each of the working pistons 56 is pivotally connected to a piston shoe 57. The piston shoe 57 projects from the cylinder 51 of the cylinder block 55 and is movable along the inner peripheral surface of the cylindrical cam ring 44 by a retaining ring (not shown). Being restrained. The inner peripheral surface of the cam ring 44 forms a sliding surface 58 for the piston shoe 57.
[0008]
By sliding the cam ring 44 by the moving mechanism, the center of the inner peripheral surface of the cam ring 44 and the rotation center of the cylinder block 55 can be decentered by a predetermined amount. The discharge capacity of the radial variable pump can be adjusted according to the amount of eccentricity.
[0009]
Longitudinal passages 52 and 53 provided in the fixed valve 54 are a suction passage and a discharge passage, and pressurized fluid is introduced into the radial type variable pump and discharged after being pressurized.
[0010]
The operation of the fluid machine as a pump will be described.
When the cylinder block 55 is rotated via the rotation shaft, the cam ring 44 is at an eccentric position with respect to the cylinder block 55, so that the piston shoe 57 slides on the sliding surface 58 of the cam ring 44, and accordingly, the operating piston 56 reciprocates in the cylinder 51. By this operation, the low-pressure fluid sucked from the passage 52 is compressed to a high pressure, and the high-pressure fluid is discharged through the passage 53. At this time, as shown in FIG. 6, the high-pressure fluid in the cylinder 51 is guided to the pressure chamber 61 formed by the piston shoe 57 and the sliding surface 58 through the passages 59 and 60. The pressure oil guided to the pressure chamber 61 flows into the pressure chamber 47 via the passage 43.
[0011]
By the way, the pressure oil flowing into the pressure chamber 47 forming the hydrostatic bearing can flow when the pressure chamber 61 formed by the piston shoe 57 and the sliding surface 58 of the cam ring 44 communicates with the passage 43. When the piston shoe 57 moves away from the passage 43, the pressure oil in the pressure chamber 47 flows out into the space between the cam ring 44 and the cylinder block 55 through the passage 43, and the pressure in the pressure chamber 47 decreases.
Therefore, when the pressure chamber 61 formed by the piston shoe 57 and the sliding surface 58 communicates with the passage 43, the pressure oil from the cylinder 51 can flow into the pressure chamber 47, and the pressure oil at this time Inflow is intermittent. For this reason, it is impossible to continuously obtain a good static pressure balance as the hydrostatic bearing, and the pressing force against the cam ring in the hydrostatic bearing varies. For this reason, the sliding resistance when the cam ring is slid in the direction perpendicular to the thrust direction is increased, causing galling, seizure and other defects.
[0012]
[Patent Document 1]
JP-A-55-160182 (page 3, upper left column, line 17 to same page lower right column, line 3, FIGS. 3 and 4)
[0013]
[Problems to be solved by the invention]
SUMMARY OF THE INVENTION It is an object of the present invention to provide an eccentric cam ring support structure for a radial type variable displacement fluid machine capable of solving the above-mentioned conventional problems and constantly supplying hydraulic oil to a hydrostatic bearing provided between a cam ring and a casing during operation.
[0014]
[Means for Solving the Problems]
The object of the present invention is achieved by the inventions described in claims 1 to 3 of the present application.
That is, the invention according to claim 1 of the present invention is directed to an eccentric cam ring support mechanism for a radial type variable displacement fluid machine, wherein the fluid machine has a flat surface provided on an outer peripheral wall of an eccentric cam ring whose capacity is variable; A thrust receiving surface formed on the inner peripheral surface of the casing, and a hydrostatic bearing formed between the flat surface and the thrust receiving surface, wherein the hydrostatic bearing has a pressure oil introduction hole provided in the casing. An eccentric cam ring support mechanism for a radial type variable displacement fluid machine characterized in that it is in communication.
[0015]
According to the present invention, by always introducing pressure oil from the pressure oil introduction hole provided in the casing to the hydrostatic bearing formed between the flat surface of the eccentric cam ring and the thrust receiving surface of the casing during operation, the operation machine is always operated during operation. The pressure oil may be introduced into the static pressure bearing. As a result, good sliding characteristics of the eccentric cam ring can be obtained, the sliding resistance of the eccentric cam ring can be kept low, and the occurrence of galling or seizure can be prevented.
[0016]
The pressure chamber constituting the hydrostatic bearing can be formed on a flat surface on the eccentric cam ring side or on a thrust receiving surface on the casing side. The pressure oil introduced into the pressure chamber may be a pilot pressure, a pressure oil used in a radial type variable displacement fluid machine, a pressure oil generated for a static pressure bearing, or a radial type variable displacement fluid machine. The generated pressure oil or the like can be used.
[0017]
The invention according to claim 2 is the eccentric cam ring support mechanism in which, in addition to the features of claim 1, the matters in which the high pressure side hydrostatic bearing communicates with the high pressure side port of the pintle provided in the casing are limited.
[0018]
In the present invention, since the static pressure bearing communicates with the high pressure side port of the pintle provided in the casing, the pressure oil in the high pressure port can be introduced into the pressure chamber of the static pressure bearing arranged on the high pressure side, Good sliding characteristics of the eccentric cam ring can be obtained. The communication between the high pressure side port of the pintle and the pressure chamber of the static pressure bearing is configured by connecting a passage branched from a communication port between the pressure oil passage in the pintle and the casing to the pressure oil introduction hole according to claim 1. be able to. In any configuration other than the above, an appropriate configuration can be adopted as long as the pressure oil from the high-pressure port can always be introduced into the pressure chamber of the hydrostatic bearing during operation. The pressure chamber may be formed on a flat surface on the eccentric cam ring side, or may be formed on a thrust receiving surface on the casing side.
[0019]
According to a third aspect of the present invention, in addition to the features described in the first or second aspect, the pair of flat surfaces and the thrust receiving surfaces respectively supporting the flat surfaces are positioned symmetrically with respect to the center line of the eccentric cam ring. The hydrostatic bearing between one flat surface and the thrust receiving surface communicates with the port on the pressure side applied to one hydrostatic bearing of the pintle, and the hydrostatic bearing between the other flat surface and the thrust receiving surface is An eccentric cam ring support mechanism in which matters connected to a port on the pressure side applied to the other hydrostatic bearing are limited.
[0020]
In the present invention, in particular, a hydrostatic bearing is provided between a pair of flat surfaces and a thrust receiving surface that supports the flat surfaces with respect to the eccentric cam ring in the swing pump or the hydraulic motor. The pressure oil of the high pressure side port of the pintle is introduced into the pressure chamber of the static pressure bearing on the high pressure part side, and the pressure oil of the low pressure side port of the pintle is introduced into the pressure chamber of the static pressure bearing on the low pressure part side. Pressure oil has been introduced. Communication between the high pressure side port of the pintle and the pressure chamber of the static pressure bearing and communication between the low pressure side port of the pintle and the pressure chamber of the static pressure bearing are performed on the high pressure side and the low pressure side between the pressure oil passage in the pintle and the casing. The passage branched from the port can be configured to communicate with the pressure oil introduction hole according to claim 1. As a result, the sliding response of the eccentric cam ring when the capacity of the fluid machine is made variable is improved, and it is possible to prevent the occurrence of unexpected situations such as galling and burning caused by the sliding of the eccentric cam ring.
That is, even if the rotation direction of the cylinder block is changed, the eccentric cam ring can be always supported by the hydrostatic bearing, and the eccentric cam ring can slide smoothly.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of the present invention will be specifically described with reference to the accompanying drawings. The present invention provides, for example, a radial variable displacement fluid machine such as a radial variable pump, a radial variable motor or a radial variable double swing pump, and movably supports an eccentric cam ring having a variable capacity in a casing of the fluid machine. It can be effectively applied as an eccentric cam ring support mechanism.
[0022]
As an embodiment of the present invention, an example in which the invention is applied to a radial variable pump will be described with reference to FIGS. 1 and 2, and an example in which the invention is applied to a radial variable displacement motor will be described with reference to FIGS. The eccentric cam ring support mechanism of the radial type variable displacement fluid machine of the present invention is not limited to a radial type variable displacement pump or a radial type variable displacement motor, but a radial type vane type fluid machine having a variable displacement mechanism. The present invention can be applied to a radial type variable displacement fluid machine such as a radial type variable swing pump.
[0023]
FIG. 1 shows a sectional plan view of the radial type variable pump, and FIG. 2 shows a sectional view taken along line AA of FIG. The position of the eccentric cam ring in FIG. 1 is shown in a displacement diagram. The configuration of the pump of this radial type variable pump is basically the same as that of the radial type variable pump described in the above-mentioned JP-A-55-160182.
[0024]
As shown in FIG. 2, an eccentric cam ring 2 is slidably supported in a casing 1 of the radial type variable pump in a direction perpendicular to the thrust direction (the left-right direction in FIG. 2). In FIG. 1, the two eccentric cam rings 2 are slidable in a direction perpendicular to the paper surface. The flat surfaces 12a and 12b formed on the outer peripheral wall of the eccentric cam ring 2 are supported by the thrust receiving surface 13a formed on the inner peripheral wall of the casing 1 and the thrust receiving surface 13b provided on the opposite side. The thrust receiving surfaces 13a, 13b and the flat surfaces 12a, 12b are arranged symmetrically with respect to the center line of the eccentric cam ring 2.
[0025]
A static pressure bearing 14 is provided between the thrust receiving surface 13a and the flat surface 12a, and a pressure chamber 15 of the static pressure bearing 14 is formed on the flat surface 12a on the eccentric cam ring 2 side. The pressure chamber 15 may be formed on the thrust receiving surface 13a on the casing 1 side. The pressure chamber 15 of the hydrostatic bearing 14 communicates with a pressure oil introduction hole 16 formed in the casing 1.
[0026]
The eccentric cam ring 2 is a direction perpendicular to the thrust direction (the left-right direction in FIG. 2) by a variable piston 25 forming a moving mechanism opposed to the diametrical direction in the casing 1 and a pressing piston 26 pressed by a spring 27. Sliding and positioning are performed. The moving mechanism is not limited to the above-described structure, but may employ a structure known as a moving mechanism.
[0027]
The flat surfaces 12a, 12b and the thrust receiving surfaces 13a, 13b, which are provided in parallel with the sliding direction of the eccentric cam ring 2 by the moving mechanism, serve as a guide when the eccentric cam ring 2 slides in a direction perpendicular to the thrust direction. At the same time, the eccentric cam ring 2 is prevented from rotating by the operation of the piston 6 and the piston shoe 7 provided in the eccentric cam ring.
[0028]
The inner peripheral surfaces of the eccentric cam rings 2, 2 'are formed in a substantially cylindrical shape. In the inner peripheral surface, a cylinder block 4 is supported in the casing 1, and passages 10, 11, 10', 11 'are formed. The cylinder block 4 is rotatably supported on the provided pintle 3, and a rotary shaft 17 supported on the casing 1 is connected to the cylinder block 4. The cylinder block 4 is provided with a plurality of radially extending cylinders 18 and 18 ′.
[0029]
Although nine cylinders 18 are shown in FIG. 2, the number of cylinders 18 is nine and is not limited to an odd number, and any number of odd and even numbers can be used. The passages 10 and 11 communicate with each other when the cylinders 18 in the cylinder row on the left side of FIG. 1 reach predetermined positions, and the passages 10 ′ and 11 ′ communicate with the cylinders 18 ′ in the cylinder row on the right side in FIG. They are in communication when they come to their respective predetermined positions.
[0030]
In this embodiment of the radial type variable pump, two rows of pistons using two eccentric cam rings are arranged. However, the number of pistons arranged in each eccentric ring is limited to two rows. However, the present invention can be applied to one row and three or more rows.
[0031]
In the case of the embodiment shown in FIGS. 1 and 2, there are two piston rows, but the other configuration is the same except that the arrangement relationship between the high-pressure side and the low-pressure side in the first and second piston rows is reversed by 180 degrees. , The relationship between the piston 6 and the eccentric cam ring 2 will be described below for the left piston row in FIG.
[0032]
The piston 6 slides in each cylinder 18, and a piston shoe 7 is pivotally connected to each piston 6. Each piston shoe 7 protrudes from the radially extending cylinder 18 of the cylinder block 4 and is movably constrained by a retaining ring 20 along the inner peripheral surface of the cylindrical eccentric cam ring 2. The inner peripheral surface of the eccentric cam ring 2 forms a sliding surface for each piston shoe 7.
[0033]
By moving the eccentric cam ring 2 in a direction perpendicular to the thrust direction by the moving mechanism, the center O ′ of the inner peripheral surface of the eccentric cam ring 2 and the rotation center O of the cylinder block 4 can be decentered by a predetermined amount. The discharge capacity of the radial type variable pump can be adjusted according to the eccentricity d.
[0034]
The longitudinal passages 10 and 11 provided in the pintle 3 are a suction passage and a discharge passage, and are used as a passage for introducing a pressurized fluid into the radial type variable pump, pressurizing the pump, and discharging the pressurized fluid again. The passages 10 'and 11' are a suction passage and a discharge passage in the right piston row in FIG. As shown in FIG. 1, the vertical passages 10 and 11 penetrate the pintle 3, and are illustrated outside the casing 1 via a suction port 22 and a discharge port 23 provided on the one end side of the pintle 3. It is connected to a braided pipeline. Similarly, the passages 10 ′ and 11 ′ are connected to a pipe (not shown) outside the casing 1.
[0035]
Further, the pressure oil can be introduced into the pressure chamber 15 by communicating with the pressure oil introduction hole 16 via a passage in the casing 1 branched from the discharge port 23.
[0036]
Although the example in which the static pressure bearing 14 is formed between the flat surface 12a and the thrust receiving surface 13a is shown, a static pressure bearing may be formed between the other flat surface 12b and the thrust receiving surface 13b. In this case, the low pressure side suction port 22 can communicate with the pressure chamber of the hydrostatic bearing provided between the other flat surface 12b and the thrust receiving surface 13b.
[0037]
In addition, as the pressure oil introduced into the pressure chamber of the hydrostatic bearing, the pressure oil from the suction port is used. It can also be introduced.
[0038]
Next, the operation of the radial variable pump as a pump will be described.
When the cylinder block 4 is rotated via the rotation shaft 17, the piston shoes 7, 7 'are moved by the eccentric amount d between the center position of the inner peripheral surface of the eccentric cam ring 2, 2' and the rotation center position of the cylinder block 4. The pistons 6, 6 'slide on the inner peripheral surfaces of the eccentric cam rings 2, 2' and reciprocate with a predetermined stroke in the cylinders 18, 18 '.
By this operation, the low-pressure fluid sucked from the passages 11 and 11 'is compressed to a high pressure, and the high-pressure fluid is discharged through the passages 10 and 10'. The high-pressure oil is introduced into the pressure chamber of the hydrostatic bearing to form a hydrostatic bearing.
[0039]
For the hydrostatic bearing for the left eccentric cam ring 2 in FIG. 1, pressure oil from the discharge port 23 is introduced, and for the static pressure bearing for the right eccentric cam ring 2 ′, pressurized oil from the discharge port 23 ′ is introduced. However, pressure oil from one discharge port can be introduced into the hydrostatic bearing.
[0040]
With this configuration, high-pressure oil can be supplied to the pressure chamber of the hydrostatic bearing at all times during operation, and the eccentric cam ring can smoothly slide.
A static pressure bearing is provided between the low pressure side flat surface 12b and the thrust receiving surface 13b, and pressure oil from the low pressure side pressure port (suction port 22) is supplied to the pressure chamber of the static pressure bearing. 'Can also be introduced into the pressure chamber of each of the above hydrostatic bearings.
[0041]
Next, an example in which the present invention is applied to a radial type variable displacement motor will be described with reference to FIGS. FIG. 3 is a sectional plan view of the radial variable displacement motor, and FIG. 4 is a view obtained by rotating the BB sectional view of FIG. 3 clockwise by 90 degrees.
As shown in FIG. 4, the configurations of the eccentric cam ring 2, the piston 6, the piston shoe 7, the cylinder block 4, and the pintle 3 are basically the same as those of the radial type variable displacement pump shown in FIG. The same reference numerals are used to denote the same elements, and a description thereof will be omitted.
[0042]
The rotation direction of the cylinder block 4 can be reversed by supplying the pressure oil supplied to the cylinder 18 to the cylinder on the upper half side or the cylinder on the lower half side in FIG. Now, when high-pressure oil is supplied from the vertical passage 10 of the pintle 3 to the cylinder 18 on the upper half side of FIG. 4 and the return pressure oil from the cylinder 18 on the lower half side is recovered through the vertical passage 11, The cylinder block rotates clockwise in FIG.
[0043]
At this time, the pressure chamber 15a in the hydrostatic bearing 14a between the flat surface 12a and the slide surface 13a arranged on the high pressure side is supplied with high pressure from the pressure oil introduction hole 16a through a passage branched from the discharge port 23 of the casing 1. Pressure oil is introduced. The pressure chamber 15b of the hydrostatic bearing 14b between the flat surface 12b and the slide surface 13b arranged on the low pressure side is connected to the cylinder 18 via a passage branched from the suction port 22 of the casing 1 through the pressure oil introduction hole 16b. Low pressure oil, which is the return pressure oil from the pump, is introduced. The rotation speed, rotation torque, and the like of the cylinder block 4 are controlled according to the amount of eccentricity between the center of the inner peripheral surface of the eccentric cam ring 2 and the rotation center of the cylinder block. The pressure chambers 15a and 15b are formed on the flat surface 12a of the eccentric cam ring 2 on the high pressure side, and formed on the thrust receiving surface 13b of the casing 1 on the low pressure side. It may be formed on either side of the surface, and the high pressure side and the low pressure side may be formed on the same surface side.
[0044]
In the radial variable displacement motor according to the present embodiment, a speed change mechanism configured by a gear mechanism integrally with the motor is provided, and a casing of the speed change mechanism meshes with an external driven mechanism to transmit rotation of the motor. are doing.
[0045]
In the above embodiment, an example in which the present invention is applied to a radial variable displacement pump and a motor has been described. However, the present invention is not limited to the above embodiment, and supports an eccentric cam ring in a radial variable displacement fluid machine. The present invention is not limited to the above-described embodiment, but also includes a configuration that can be appropriately applied by those skilled in the art.
[0046]
By applying the present invention, pressure oil can be always introduced into the pressure chamber of the hydrostatic bearing during operation, and the eccentric cam ring slides smoothly in the direction perpendicular to the thrust direction. It is possible to prevent the occurrence of galling, seizure and the like during sliding.
[0047]
In the case of rotating a cylinder block in both directions, such as a radial variable displacement motor or a double swing pump, it is desirable to provide static pressure bearings on the high pressure side and the low pressure side, respectively, whereby the eccentric cam ring is perpendicular to the thrust direction. Sliding in the direction can be performed smoothly.
[Brief description of the drawings]
FIG. 1 is a cross-sectional plan view of a radial type variable displacement pump.
FIG. 2 is a sectional view taken along line AA of FIG.
FIG. 3 is a sectional plan view of a radial type variable displacement motor.
FIG. 4 is a sectional view taken along line BB of FIG. 3;
FIG. 5 is a cross-sectional side view of a conventional radial type variable displacement pump.
FIG. 6 is a partially enlarged view of FIG. 5;
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Casing 2, 2 'Eccentric cam ring 3 Pintle 4 Cylinder block 6, 6' Piston 7, 7 'Piston shoe 10, 11 Passage 10', 11 'Passage 12a, b Flat surface 13a, b Thrust receiving surface 14 Static pressure bearing 15 Pressure chambers 15a, b Pressure chambers 16 Pressure oil introduction holes 16a, b Pressure oil introduction holes 17 Rotating shafts 18, 18 'Cylinder 20 Holding ring 22 Suction ports 23, 23' Discharge port 25 Variable piston 26 Pressing piston 27 Spring 40 Casing 41 Thrust receiving surface 42 Thrust receiving surface 43 Passage 44 Cam ring 45 Bearing surface 46 Bearing surface 47 Pressure chamber 48 Stopper 49 Pressing piston 50 Spring 51 Cylinder 52 Passage 53 Passage 54 Fixed valve 55 Cylinder block 56 Operation Stone 57 inner circumferential surface center d eccentricity of the rotation center O 'eccentric cam ring of the piston shoe 58 sliding surface 59 passage 60 passage 61 pressure chambers O cylinder block

Claims (3)

In the eccentric cam ring support mechanism of the radial type variable capacity fluid machine,
A flat surface provided on the outer peripheral wall of the eccentric cam ring whose fluid machine makes its capacity variable,
A thrust receiving surface formed on the inner peripheral surface of the casing, supporting the flat surface,
A hydrostatic bearing formed between the flat surface and the thrust receiving surface,
With
An eccentric cam ring support mechanism for a radial type variable displacement fluid machine, wherein the static pressure bearing communicates with a pressure oil introduction hole provided in the casing. The eccentric cam ring support mechanism according to claim 1, wherein the high pressure side static pressure bearing communicates with a high pressure side port of a pintle provided in the casing. Thrust receiving surfaces respectively supporting the pair of flat surfaces and the flat surfaces are arranged at symmetrical positions with respect to a center line of the eccentric cam ring,
A hydrostatic bearing between the flat surface and the thrust receiving surface communicates with a port on the pressure side applied to one of the pintle hydrostatic bearings, and the hydrostatic bearing between the other flat surface and the thrust receiving surface is connected to the pintle. 3. The eccentric cam ring support mechanism according to claim 2, wherein the eccentric cam ring support mechanism communicates with a pressure side port applied to the other hydrostatic bearing.

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