JPS58192980A - Radial piston type hydraulic pressure rotary machine - Google Patents

Abstract

PURPOSE:To make the separate provision of a cam ring unnecessary because of a constitution making the capacity thereof variable by a method wherein a distribution shaft, having suction and discharging ports communicating intermittently with a cylinder bored in a rotor, is operated to rotate. CONSTITUTION:The distribution shaft 32 is formed with the suction and discharging prts 35, 36 which are communicating intermittently with the cylinder 4 bored in the rotor 3 while the ports 35, 36 are communicated with suction and discharging ports 40 through communicating paths 37, 38 (not shown in fig.). When discharging and suction paths 42 are under a low pressure, the rotating angle theta of the distributing shaft 32 becomes maximum and the capacity of a hydraulic motor becomes minimum, however, when pressure oil is supplied to one of the suction and discharging paths 42 and the pistons 5 are displaced upwardly, the distributing shaft 32 is displaced into a direction reducing the rotating angle theta thereof and the capacity of the hydraulic motor becomes maximum.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic rotary machine such as a radial piston type hydraulic motor/hydraulic cylinder equipped with a variable capacity mechanism.

1 and 2 show a hydraulic motor as a hydraulic rotary machine according to the prior art.

In the same figure, 1 is the upper plate IA, the lower plate IB, and the upper plate IA.
and a cylindrical body 1c provided between a lower plate IB, and a cam ring 2 is disposed inside the casing l, and a rotor 3 is rotatably disposed inside the cam ring 2. has been done. A plurality of cylinders 4.4, . . . are bored in the rotor 3 in its radial direction, and a piston 5. s, . . . are slidably provided.

A shoe 6 has one end swingably attached to the tip of the piston 5, and the other end of each shoe 6 is brought into sliding contact with two sliding surfaces formed on the inner circumferential wall of the cam ring 2. Reference numeral 7 denotes a distribution shaft connected to the casing upper plate IA, and the distribution shaft 7 is slidably fitted into a sliding hole 3 formed at the center of rotation of the rotor 3, allowing the rotor 3 to rotate freely. I support it.

Further, the distribution shaft 7 is provided with a suction/discharge/-) 8.9 for switching the supply and discharge of pressure oil as the rotor 3 rotates.

Next, 10.11 is a cylinder/m formed on both left and right sides of the casing cylinder portion 1c, and a piston 12.13 is slidably disposed in each cylinder chamber 10.11. The tip surfaces of each piston 12, 13 abut against both sides of the cam ring 2, and the casing cylinder portion 1c
Guide surface ID formed on the inner wall at the upper and lower positions in Figure 1
, ID (the upper guide surface ID does not appear in the drawing)
When it comes into contact with K, the cam ring 2 is supported at four points. In addition, there is a piston 1 in the cylinder chamber 10.11.
Oil chambers 14.15 are formed by the base end surfaces of the pistons 12.13 and 14.15, and in each oil chamber 14.15, a spring is inserted between the inner wall of the casing cylinder portion 1c and the base end surface of the piston 12.13. 16 and 17 are tensioned, respectively, and each spring 16 and 17 is tensioned.
Therefore, each piston 12, 13 is always urged in the direction of pressing against the cam ring 2. Furthermore, oil chamber 14°15
Pipes 18 and 19 are connected to each of the pipes 18 and 19, respectively.
．． The other end of the piping 19 is connected to a directional switching valve 2o so that the pipes 18 and 19 are communicated with a hydraulic bonder 21 or a tank 22 by the directional switching valve 2o. In addition, in the figure, 23 is an id for guiding the sea-6 along the two guide surfaces, and 24 is a mounting part for attaching a rotating shaft that is fitted into the rotor 3 and is rotationally driven by the rotor 3. show.

The hydraulic rotary machine according to the prior art has the above-mentioned configuration, and next, the operation as a hydraulic motor will be explained.

First, among the suction/discharge/-) 8.9 formed on the distribution shaft 7, for example, port 8 is connected to a hydraulic pump, port 9 is connected to a tank, and pressure oil from the hydraulic pump is supplied through port 8. Supplied into cylinder 4. This pushes the piston 5, but if the rotor 3 is eccentric with respect to the cam ring 2, the piston 5 is forced to protrude from the cylinder 4, and the piston 5 attached to the piston 5 is moved from the cam ring 2. The rotor 3 rotates by slidingly guiding it along the sliding surface 2 of the rotor 2. When the rotor 3 rotates half a rotation, the cylinder 4 communicates with the other port 9, the piston 5 enters the cylinder 4, and the pressure oil in the cylinder 4 flows through the 7-
) 9 and returned to the tank. In this way, by intermittently communicating the cylinder 4 with the ports 8 and 9, the rotor 3 is rotated, and the rotor 3 is fitted into the mounting portion 24 and the rotating shaft is rotationally driven.

In this case, the piston 5 strokes inside the cylinder 4 by an amount corresponding to the eccentricity of the rotor 3, and the displacement by the piston 5, that is, the capacity as a hydraulic motor changes depending on the eccentricity of the rotor 3. do. Therefore, in order to change the capacity of the hydraulic motor, the directional control valve 20 must be
Switch to the state shown in the figure to transfer pressure oil from the hydraulic pump 21 to the oil chamber 1.
At the same time, the oil in the oil chamber 16 is supplied to the tank 22.
Reflux to. Accordingly, the piston 13 is in the cylinder M
The piston 12 protrudes from the cylinder surface l.
0, and the cam ring 2 is slid to the left in the figure along the guide umlD.

As a result, the amount of eccentricity of the rotor 3 with respect to the cam ring 2 increases, and the stroke amount of the piston 50, that is, the capacity of the hydraulic motor can be increased.

\ On the other hand, when the directional control valve 20 is switched to the left position in Fig. 1, the piston 12 protrudes and the piston 13 enters the cylinder 1ill, so the cam ring 2 is displaced to the right in the drawing, and the amount of eccentricity is reduced. decreases, and the capacity t changes in a decreasing direction.

However, in the hydraulic rotating machine according to the prior art described above,
Since the capacity of the cam ring 2 can be varied by eccentrically displacing the cam ring 2, it is necessary to make the length inside the casing 1 in the eccentric direction sufficient to enable eccentric movement of the cam ring 2. There is. Moreover, since the cam ring 2 receives the reaction force of the piston 50 through the cam ring 2 and the piston 50, it is necessary to increase the wall thickness of the cam ring 2 to strengthen its rigidity. There is a drawback to becoming a great saint. Furthermore, since the pressing force of each piston 5 against the cam ring 2 changes depending on the hydraulic pressure within the cylinder 4, the pressing force varies during one rotation of the piston 5.

As a result, when the motor rotates at high speed, the cam ring 2 vibrates violently in the eccentric direction together with the piston 12.13, generating a noise), and the piston 12.13 and cylinder 10.
There is a drawback that it causes seizure in the sliding parts etc. with 11.

Furthermore, when the motor rotates at a low speed, an uneven load is applied to the pistons 12 and 13, and there is also a drawback that the adjustment of the Jtf thickness cannot be carried out smoothly.

The present invention eliminates the drawbacks of the prior art described above, and includes forming a sliding surface that serves as a cam surface on the inner circumferential wall of the casing,
In addition, a distribution shaft supporting the rotor is attached to the casing at a position 1-center from the sliding surface, and a distribution shaft rotation mechanism for rotating the distribution shaft is provided on the distribution shaft, so that the cough distribution shaft can be directly rotated. To provide a radial piston type hydraulic rotating machine in which the capacity can be made variable by relatively displacing the switching position of each suction/exhaust port that plays a role as a distribution shaft and the stroke position of the piston. .

Embodiment 0 of the present invention will be described below based on FIGS. 3 to 7.

First, FIGS. 3 and 4 show a first embodiment of the present invention, and the same components as in FIGS. However, in the hydraulic rotating machine according to the present invention, the upper plate 31A,
A cam ring is not installed in the casing 31, which consists of a lower plate 31B and a joint 31C provided between the upper plate 31B and the lower plate 31B. A sliding surface 31D serving as a cam surface is directly formed.

Next, 32 is eccentric from the center 0 of the sliding surface 310 and the ninth position #t
The distribution shaft 32 is formed separately from the casing upper plate 31 and is rotatably supported via bearings 33, 34 of the upper plate 31AK. The rotor 3 is supported at an eccentric position with respect to the sliding surface 310 by fitting the distribution shaft 32 into the sliding hole 3A.

Also, the distribution shaft 32 has a low! Suction/exhaust ports) 35, 36 are formed intermittently in communication with the cylinder 4 bored in the distribution shaft 32, and the suction/exhaust ports (-) 35, 3 are formed inside the distribution shaft 32 in the axial direction.
Communication passages 37 and 38 communicating with the communication passages 37 and 38 are bored, and suction and exhaust ports 39 and 40 communicate with the communication passages 37 and 38, respectively.
is formed. The suction/exhaust ports 39.40 are formed in the casing upper plate 31A and communicated with the nine suction/exhaust passages 41.42. It can communicate with passages 41 and 42. In addition, suction/exhaust/-)36. Suction and exhaust port 40. The suction/discharge passage 41) is not shown in the drawing.

Further, reference numeral 43 denotes a lever as a distribution shaft rotation mechanism attached to the upper end of the distribution shaft 32, and the tip of the lever 43 protrudes from a slit (#444) drilled in the upper plate 31A. It can be rotated mechanically.

The radial piston type hydraulic rotating machine according to the present invention has the above-mentioned configuration, and since the rotor 3 is eccentrically disposed with respect to the sliding surface 31D formed in the casing cylinder portion 31C and in good condition, The operation itself as a hydraulic motor is not particularly different from that of the prior art described above.

Next, the operation of making the capacity of the hydraulic motor variable will be explained based on FIG. 5. First, Fig. 5 (A) shows an expanded view of the rotor 3 and the distribution shaft 32 when the lever 43 is in the position shown in Fig. 3. In this state, for example, if the suction/exhaust port 35 is connected to the hydraulic pressure inlet and the other (2) a exhaust zle -) 36 is connected to the tank, then the piston 5 is at the position where it has entered the cylinder 4 the most. The hole in the trench from 7 to the most protruding position from the cylinder 4 communicates with the suction/exhaust port 35, and the 7-
) 35, and when the piston 50 is in the fully protruding position, the cylinder 4 switches from 4-) 35 to /-) 36 to start the approach, and at the gradual approach position, the pressure inside the cylinder 4 continues until it switches to port 35 again. Continue to drain pressure oil.

Therefore, the flow value Q per revolution of the hydraulic motor in this state is (D is the inner diameter of the piston 5, N is the number of pistons 5, and sH piston 50 strokes). The capacity of 9 per revolution is the size of a moth.

Therefore, the lever 43 is rotated from the position shown in FIG. 3 by an angle θ in the direction of the arrow. As a result, the distribution shaft 32 is rotated by an angle υ, and as shown in FIG. As a result, the piston 5 is cylinder/4
Port 35 after entering the ejection stroke from the inward gradually advancing position
The port 35 is in communication with the port 35, and the port 35 is in the most protruding position, and after starting the approach stroke, the port 35 is switched to the port 7-) 36. Therefore, the stroke of the piston 5 is apparently reduced by the stroke S (which corresponds to the distance between the position when switching from port 36 to port 35 and the position when switching from port 35 to port 36). , the flow rate Q' of the hydraulic motor in this state, = Q g" g1 m' (L is the distance from the center of oscillation of -6 to its center of revolution, R (θ) is the rotor rotation at the position of θ center and shi,
-6 and the distance from the center of oscillation respectively indicate the amount of eccentricity of the rotor 3. Therefore, the flow jt Q' is
As the zero rotation angle e increases, it decreases in proportion to it.

In this way, the capacity of the hydraulic motor changes steplessly as a function of the rotation angle of the distribution shaft 320, and the capacity is maximum when the rotation angle is zero, and the capacity also increases as the rotation angle increases. Decrease.

Next, Figures 6 and 7 show a second embodiment of the present invention, and the same components as in Figures 3 and 4 are given the same reference numerals and their explanations will be omitted. shall be.

However, in this embodiment, the distribution shaft rotation mechanism uses a cylinder device operated by the fluid pressure of the suction/discharge passage 41 or 42. That is, in the figure, 51 is a rod whose one end is fitted into a hole 32A drilled in the radial direction of the distribution shaft 320, 52 is a cylinder chamber bored in the casing upper plate 31A, and 53 is a rod that slides into the cylinder chamber 52. The other end of the rod P51 is connected to a piston 53 via a spherical bearing 54. The inside of the cylinder chamber 52 is defined by the piston 53 into a hydraulic pressure chamber 55 and a spring chamber 56. The piston 53 is biased downward in FIG. 6 by the provided spring 57. By pressing the piston 53 in this direction, the distribution shaft 320 is pushed through the door 51.
The rotation angle 0 is configured to be the maximum. on the other hand,
The hydraulic chamber 55 is connected to the suction and exhaust passages 41 and 42 via a high pressure selection valve 58 such as a shuttle valve.
1. When either passage of 42 becomes high pressure, the pressure oil is supplied to the hydraulic pressure chamber 55 via the high pressure iA selection valve 58, and the piston 53 is slid against the biasing force of the spring 57. Displace. As a result, the rod 51 is formed to be able to displace the distribution shaft 32 in a direction in which its rotation angle θ decreases. In the figure, reference numerals 59 and 60 indicate stops for regulating the range of movement of the piston 53, which are protruding from both end surfaces of the piston.

By configuring the hydraulic rotating machine as described above, when the suction and discharge passages 41 and 42 are at low pressure, the piston 5
3 is in a position where the stop horn 459 is in contact with the inner wall of the hydraulic chamber 55, and the rotation angle θ of the distribution shaft 320 is at its maximum, allowing switching between a-3 and the suction/discharge port provided on the distribution shaft 32. The surface is in the state shown in Figure 5 (b), the capacity of the hydraulic motor is at its minimum, and either one of the suction and exhaust passages 41 and 42 is connected to the hydraulic pressure When pressure oil is supplied from the pump, pressure oil is supplied into the hydraulic pressure '455 through the high pressure selection valve 58, and the piston 53 is moved by the spring 57.
6 and displace it upward in FIG. Since the rod 51 is attached to the piston 53 via a spherical bearing 54, it rotates along with the displacement of the piston 53, displacing the distribution shaft 32 in the direction in which the rotation angle θ becomes smaller, and the rod 51 is rotated in the direction in which the rotation angle θ becomes smaller.
60 comes into contact with 41i [fi of the cylinder chamber 52, the rotation angle θ becomes zero, that is, the state shown by fg5 (Fig. 0) is reached, and the capacity of the hydraulic motor becomes maximum.

In each of the above-mentioned embodiments, the case where the hydraulic rotary machine of the present invention is used as a hydraulic motor is explained, but the hydraulic rotating machine of the present invention is used as a hydraulic motor.
Of course, it can also be used as In addition, when the hydraulic rotary machine shown in the second embodiment is used as a hydraulic pump, the distribution shaft 320 rotation angle θ may be configured to increase when pressure oil is supplied into the hydraulic chamber 55. For example, it is possible to have a small Jt when the pressure is high and a maximum capacity when the pressure is low. Furthermore, the supply of pressure oil into the hydraulic pressure chamber 55 does not necessarily have to be carried out through the suction and discharge passages 41 and 42;
It can also be configured to be supplied from an external hydraulic source.

As described in detail above, in the radial piston reduced hydraulic pressure rotary machine according to the present invention, the distribution shaft is rotated by a distribution shaft having suction/exhaust (/-) which intermittently communicates with a cylinder bored in the rotor. Since a distribution shaft rotating mechanism is installed and the distribution shaft is rotated to make the capacity variable, there is no need to provide a cam ring to make the capacity of the hydraulic rotary machine variable. The structure is simple, and the entire hydraulic rotating machine can be formed into a compact structure. Moreover, since the reaction force of the piston provided in the rotor does not act on the mechanism that makes the capacity variable, the capacity can be changed smoothly with a light load. Furthermore, since the sliding members are not supported by hydraulic pressure as in the conventional technology, large vibration noises may be generated during the operation of the hydraulic rotating machine, and the supporting parts of the sliding members may seize up. No inconveniences such as problems will occur.

[Brief explanation of the drawing]

Fig. 1 and Fig. 2 show the prior art, in which Fig. 1 is a half-sectional view of a hydraulic rotating machine, and the second factor is shown in Fig. 1.
3 to 5 show the first embodiment of the present invention, FIG. 3 is a half sectional view of the hydraulic rotating machine, and FIG. - ■ Cross-sectional view in the direction of the arrow; Figures 5 (F) and (B) are explanatory diagrams of the operation of the hydraulic rotating machine showing different operating states; Figures 6 and 7 are the second embodiment of the present invention; Figure 6 is a sectional view of the main parts of the hydraulic rotating machine;
FIG. 7 is a sectional view taken in the direction of the -1 arrow in FIG. 6. 3...Rotor, 4-Cylinder, 5...Piston,
6...shi, -131...casing, 31D...
Sliding surface, 32...Distribution shaft, 35.36-Suction/exhaust β-to, 43...Lever, 51...Port, C, 52-Cylinder chamber, 53...Piston, 55...・Hydraulic pressure chamber, 58
...High pressure selection valve. Procedural amendment document July 1980 2711 Japan Patent Office Chief Tomi Kazuo Chikusugi l Case description Showa s7 1 Patent Application No. 69085 2 Title of invention Radial piston type hydraulic rotating machine 3, Amendment with the case of the person making the amendment Related Patent applicant 4th attorney: 160 Name (7944) Patent attorney Kazuhiko Hirose 5;
hli + TE command Hf person Spontaneous 6 Number of inventions increases due to oil stoppage No increase or decrease Specification page 12, line 12 1it(θ)=0T2/;5'' is r)L(θ)
-fEF2e" 5iniP -t cosθ".

Claims (4)

[Claims] (1) The casing has a sliding surface formed on the inner wall of the casing, and the axillary casing has a pair of suction/exhaust shafts that are rotatable by -6 relative to the sliding surface. The rotor is rotatably supported by being fitted into the distal end of the distribution shaft into a rotor disposed in the casing, and the rotor is provided with a plurality of cylinders intermittently communicating with each of the suction and discharge ports. A piston is slidably provided in each of the cylinders, and a shaft, which comes into sliding contact with the sliding surface, is swingably attached to each piston. A radial thruster hydraulic rotating machine equipped with a distribution shaft rotation mechanism for rotating the distribution shaft. (2) The radial piston type hydraulic rotating machine according to claim (1), wherein the distribution shaft rotation mechanism is attached to the distribution shaft by a nine lever. (3) The radial piston hydraulic pressure according to claim (1), wherein the distribution shaft rotation mechanism is constituted by a rod attached to the distribution shaft and a cylinder device for rotating the CI-de. Rotating machine. (4) The hydraulic chamber of the cylinder device and each of the suction/exhaust ports are communicated via a high pressure selection valve, and the cylinder device is driven by the hydraulic pressure supplied from the high pressure side port among the ports. A radial piston mtett pressure rotating machine according to claim (3).