JPS591116Y2 - hydraulic machinery - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates to a hydraulic motor, particularly a radial cylinder type hydraulic motor.

Radial cylinder hydraulic motors, such as those described in British Patent No. 1,085,232 by the applicant,
and is sold under the trademark rSTAFFA, owned by the applicant.

This hydraulic motor is powered by an electric motor driven pump.

The speed and output of this hydraulic motor can be varied by changing the pump output, or displacement, but this requires a relatively large and expensive pump to provide high speed and low torque. It is necessary to supply sufficient low pressure to the hydraulic motor.

However, if the displacement of the hydraulic motor can be varied, the dimensions of the pump can be reduced.

Therefore, an object of the present invention is to provide a hydraulic motor whose displacement can be sufficiently varied.

The radial cylinder type hydraulic motor according to the present invention has a plurality of reciprocating screws arranged around an eccentric ring attached to an output shaft, and a ring body driven by the piston is provided on the eccentric ring, The eccentric position of the eccentric wheel, that is, the displacement amount, can be adjusted by moving the ring body closer to the axis of the output shaft or away from the same axis using hydraulically actuated pistons and cylinders placed on the output shaft and facing each other. It is characterized by changing the

The amount of eccentricity can be changed steplessly.

Thus, the ring can be moved between two positions, for example high and low, in other words between drive and neutral.

The neutral position is used to allow the shaft to rotate freely, for example when operating a winch and requires free fall.

It is also possible to move the ring until it passes the neutral (or zero travel) position.

By doing so, the hydraulic motor can be reversed without changing the direction of fluid supply.

In this way, part of the hydraulic circuit is simplified, since the need for expensive control valves is eliminated.

Furthermore, it has been found that the piston and cylinder described above can also be applied to a crankshaft having the same dimensions as that installed in the above-mentioned hydraulic motor in the United States.

This is of great practical importance, as in a conventional hydraulic motor, simply replacing its crankshaft,
and can be easily retrofitted by adding the necessary supplementary hydraulic control and supply systems, i.e. with only minor changes to the current production line.

The present invention relates to a hydraulic motor, and more particularly to a radial cylinder type hydraulic motor.

The invention provides a hydraulic motor in which at least one reciprocating piston 34.101 abuts in such a way as to drive an eccentric wheel 22 mounted on an output shaft 20, which eccentric wheel has the aforementioned Hydraulically actuated screws 1 to 24 and cylinders 24/27 are provided with an annular body 23 driven by a piston, and are placed on the output shaft and are opposed to each other.
．． 25/2B, by moving the ring body 23 closer to the axis of the output shaft or farther away from the coaxial line, the eccentric position of the eccentric wheel 22, and therefore the displacement amount, can be changed. It is something that makes you

Next, embodiments of the present invention will be described based on the accompanying drawings.

Crankshaft-like output shaft 2 shown in FIGS. 1 to 3
0 is used, for example, in the radial cylinder type hydraulic motor shown in FIG. There is.

In the illustration, the eccentric 22 comprises a circular ring 23 whose outer surface slidably abuts the connecting rod slipper 34B (FIG. 4), and whose inner surface also includes the outer end surfaces of the pistons 24, 25 facing each other. is supported by

The piston 24 , 25 is biased outwardly by a positioning spring 26 and is in contact with the annulus 23 .

Further, the pistons 24 and 25 are connected to the crank portion 2 of the output shaft 20.
9 can be slid in a cylindrical recess 27.2B formed in it.

As shown in FIG. 2, a flat part 30 is formed on the side surface of the crank part 29, and a pad 31 is fixed to the ring body 23 by a plurality of keys 32.

Pad 31 is in slidable contact with planar portion 30 to maintain static hydrodynamic balance.

For example, by supplying high-pressure fluid to the recess 33 from a hole 34C formed in the connecting rod slipper 34B (FIG. 4) through a duct (not shown) formed in the pad, Balance is maintained.

If necessary, a projection 35 is formed on the arcuate outer surface of the piston 24 , 25 , and is fitted into a fixing groove 36 formed on the inner surface of the ring body 23 .

As can be seen in FIGS. 1 and 3, hydraulic fluid is supplied from the ducts 37.38 to the respective recesses 27.2B.

duct) 37.3B is provided in a part of the main body 39 of the hydraulic motor and supplies fluid to the recess 27.2B via a groove 40.41 communicating with 7L42.43 provided in the output shaft 20. .

Grooves 4G and 41 are sealed with rings 44 to prevent leakage.
The groove, ring, and casing assembly constitutes an effective sliding ring assembly 45.

Although the assembly 45 is located at one end of the output shaft 20 as shown in FIGS. 1 and 3, it may be located at any other suitable location.

When using this hydraulic motor, the displacement is
It can be changed by changing the eccentric position of the reciprocating piston 34 (the fourth
Figure) is determined.

This eccentric position can also be changed by moving the ring body 23.

To do this, differential fluid pressure is applied to the recesses 27, 28 to move the pistons 24, 25 that support the annulus.

As shown in FIGS. 1 and 2, the high pressure fluid is
37 to move the piston 24 outward;
On the other hand, low pressure fluid is sent to the piston 25.

At the position where the amount of eccentricity is maximum, the driving torque generated by the operation of the slipper 34B on the outer surface of the ring body is transmitted to the output shaft 20 via the pad 31 and the flat part 30, and as a result, the output shaft 20 rotates.

FIG. 3 shows the position when high pressure fluid is supplied to piston 25 through duct 43 and low pressure fluid is supplied to piston 24.

In this position, the ring body 23 is in contact with the crank part 29,
The eccentric wheel 22 is held on the output shaft 20, creating a zero stroke, ie, a neutral drive effect, and the output shaft 20 will idle.

- Alternatively, a spacer 46, shown in broken lines in FIGS. 1 and 2, may be provided to limit the inward movement of the piston 24.

Similarly, the same spacer is provided in the recess 28 and the piston 2
It is also possible to limit the movement of 5 and reduce the maximum stroke.

The supply of hydraulic fluid to the duct) 37.38 is carried out by a pump driving a hydraulic motor.

That is, it is preferable to separately provide an auxiliary pump for this purpose.

The dimensions of the pistons 24,25 are determined by the effective hydraulic fluid supply pressure, but must be large enough to balance the driving force supplied to the annulus 23.

It should be noted that the diameter of piston 25 is only slightly larger than the diameter of piston 24.

The hydraulic motor shown in Figure 4 is based on the above-mentioned British Patent No.
Five radial cylinders 47, of the same type as described in No. 85,232, are fed through axial valves 48 (test distributors) which direct hydraulic fluid to supply and return conduits 48. lead.

A piston 34 in the cylinder 41 drives an eccentric wheel via a connecting rod 34A provided with a slipper 34B,
The slipper 34B is in sliding contact with the ring body 23,
In addition, static hydrodynamic balance is maintained via the hole 34C.

The hydraulic motor cooperates with the output shaft 20 shown in FIGS. 1 to 3, but as shown in FIG.
Groove 40.41 is fed by duct) 50.51.

These ducts are connected to a high pressure source 5 via a two-position control valve 52.
3 and a drain 54, respectively.

The control valve 52 is provided outside the casing of the motor.

It is particularly important to note that the overall dimensions of the eccentric 22 are the same as those of the rSTAFFA, (trademark) hydraulic motor currently in use, so that it is possible to simply replace its output shaft 20 and control valve 52. The only modification involved is the insertion of parallel opposed portions of the body 39 which are connected to the hydraulic power source of the motor via the .

There is no need to change other components of the hydraulic motor in the current production line.

The control valve 52 may be mounted directly on the casing of the hydraulic motor, or may be separate from it.

A single valve can control multiple hydraulic motors.

For example, one or more control valves 52 may be provided for the control of the driver of a vehicle equipped with a hydraulic motor.

Hereinafter, a hydraulic motor equipped with a servo control valve device according to the present invention shown in FIG. 5 will be described.

A person skilled in the art can easily equip the hydraulic motor shown in FIG. 4 with such a servo control valve device.

The output shaft 20 shown in FIG.
The same as shown in Fig. 3, but in Fig. 5.
The arrangement shown in the figure allows the stroke to be varied steplessly within predetermined limits.

For this purpose, a servo control device is provided.

In the servo control device, the valve spool 55 is connected to the valve body 5.
It is housed in the hole 56 at 7.

The spool 55 is pushed towards the center by a spring 58.

The spool 55 has four sliding piston parts, thereby forming chambers A, B, C, D and E.

A high pressure fluid and a low pressure fluid flow through the two supply pipes 59, respectively.

A shuttle valve 60 provided at the connecting portion of the two supply pipes 59 allows the higher pressure fluid of the two supply pipes to flow into the conduit 6.
Selected to be sent to 9.

High pressure fluid is then supplied to conduit 62 via first restraint 61 to pressurize chamber E and then to slide ring assembly 45.
It reaches the relief valve 63 through .

The relief valve 63 is loaded by a spring 64.

The degree of compression of the spring 64 corresponds to the degree to which the ring body 23 is eccentric.

High pressure fluid from the shuttle valve 60 passes through a second restraint 65 to a manual control valve 66 having an outlet 67 and to a conduit 6.
8 and reaches inside the pressurized chamber A.

The restraining portions 61 and 66 connect the supply pipe 59 to the shuttle valve 60.
are provided to control the pressure of the fluid sent to chambers E and A, respectively, through the chambers E and A.

This prevents pressure losses within the conduit and increases efficiency.

Therefore, the fluid pressures influenced by the valves 63, 66 act in opposite directions on the valve spool 55.

High pressure fluid from shuttle valve 60 enters bore 56 via tube 69 and, depending on the position of valve spool 55, selectively
conduit 42 or 43 and further piston 24 or 2
Sent to 5.

FIG. 5 is a view in equilibrium, with the piston part of the spool valve 55 closing the conduit 42, 43 and the chamber C also being closed.

Chambers B and D open into the motor crankcase via a conduit 70 and a drain.

The position shown is the maximum eccentricity position of the motor.

In this position, piston 24 is extended and piston 25 is retracted.

By setting the relief valve 63 to a minimum pressure, the pressure in chamber E is kept in balance with the pressure in chamber A.

This position corresponds to the minimum positioning of the manual control valve 66.

As the annulus 23 moves to decrease the amount of eccentricity, the compressive force of the spring 64 increases, causing the pressure in the chamber E to increase.

If it is desired to reposition the eccentric, the valve spool 55 gradually returns to its balanced intermediate position.

It is preferable to provide an r-th restraint part 71 to act as a dashpot to weaken the movement of the valve spool 55.

To increase the amount of eccentricity, the steps described above are reversed.

If it is desired to reduce the amount of eccentricity of the motor, it is preferable to manually adjust the spring pressure to increase the set pressure of the manual control valve 66.

The fluid pressure in chamber A is thereby greater than the fluid pressure in chamber E, and the valve spool 55 is moved downwardly from the arrangement shown in FIG. 64 communicates with the conduit 43, and through the chamber B, the conduit 7u for fluid discharge and the conduit 42 come into communication.

Due to the inflow of high pressure fluid, the amount of eccentricity of the piston 25 increases, while the amount of eccentricity of the piston 24 decreases.

In the crankshaft shown in FIG. 6, the piston rod 72 supports the annulus 23 and passes through the crank part 29 of the output shaft 20 via mutually aligned holes 73,74.

A piston 75 is attached to a rod 72 and is movable within a chamber 76 in the crank part 29, changing the eccentric position of the annulus 23 under the action of fluid pressure supplied to the upper and lower compartments of the chamber.

In this case, the upper part 72A of the piston rod 72 is
Since it has a slightly larger diameter than 2B, the effective area of the upper surface of the screw I/N 75 is smaller than that of its lower surface.

The piston 75 is formed with a portion 77 that cooperates with a recess 78, thereby allowing the dash board!・Effect occurs.

In the one shown in FIG.
1 are formed and they have pistons 24 facing each other.
．． The protrusions 82 and 83 provided on the head of 25 are fitted.

In this case, a lower surface 84 is formed on the inner surface of the ring body 23, and this lower surface 84 is in direct contact with the lower surface 30 of the crank portion 29 of the shaft.

Therefore, there is no need for auxiliary pad 31 as in the case of FIGS. 5 and 6.

FIG. 8 is a modification of that shown in FIG. 7, in which the opposing pistons 24.25 are arranged around a circular projection 90.91 formed in the crank part 29 of the shaft.

The eccentricity of the annulus 23 is varied by means of a fluid that is pumped into the pressurized chamber 92.93 via a duct 94.95 leading to the bore 42.43.

FIG. 9 shows the present invention in a radial cylinder hydraulic motor with a piston sleeve, for example British Patent No. 886.9.
An example will be shown in which the present invention is applied to a hydraulic motor as described in the specification of No. 23.

In FIG. 9, a pentagonal body 100 is inserted between the eccentric rings 23, and five piston sleeves 101 are inserted into the pentagonal body 1.
It is in contact with the outer lower surface 102 of 00.

The ring body 23 is rotated within the orbiting pentagonal body 100, and the eccentricity of the ring body 23 is controlled in the same manner as shown in FIG.

However, in FIG. 9 the pressure fluid supply duct 103 is first axially and then laterally through the crank part 29 of the shaft, further through the annulus 23 and from there through the duct 104 in the pentagonal body 100. It extends into the piston sleeve 101.

The piston sleeve 101 is constantly pushed inward by a compression spring 105 and sealingly abuts the outer lower surface 102 .

FIG. 10 shows a crank-shaped output shaft 20 used in a rotary casing motor, for example an intermittent motor.

This structure is the same as the structure in Figures 1 to 3, but
Since the output shaft 20 is stationary, the design can be simplified and the fluid is supplied via holes 130, 131 in the shaft directly to the mutually opposing pistons 24, 25.

In this example, when modifying a currently used hydraulic motor, it is only necessary to replace the output shaft and provide an appropriate supply pipe for the holes 130, 131, and the above-mentioned section of the hydraulic motor body 39 (first 4) are no longer necessary.

FIG. 11 shows another type of stationary or rotary crank-shaped output shaft with an eccentric wheel, the eccentricity of which can be varied steplessly within limits.

The servo valve device 140 in this case is similar to that designated by the reference numeral 55 in FIG.

With each of the above-mentioned structures, a displaceable radial cylinder hydraulic motor is provided, whereby the object of the present invention is satisfactorily related.

For example, the dimensions of the drive pump can be reduced.

Further, when the ring body is placed in the neutral position, that is, in the zero stroke, the output shaft can be idled.

Therefore, by connecting an object to the output shaft, it can be used to pull up or pull down.

Next, embodiments of the present invention will be listed.

(1) A hydraulic motor according to the claims of the utility model registration, characterized in that the piston and cylinder combination device 24/27°25, /28 is moved by pressure fluid supplied from the hydraulic supply pipe 59'.

(2) The piston and cylinder combination device 24/27゜25/2B consists of two pistons and cylinders arranged opposite each other to move the ring body in the opposite direction with respect to the output shaft, and is also servo controlled. Valve device 55.56.57.5B
is adapted to selectively supply pressurized fluid toward either one of the piston and cylinder, or the above (1)
Hydraulic motors listed in ).

(3) The ring body 2 is arranged so that the effective area of the piston and cylinder combination device 25/28 for moving the ring body in the axial direction of the output shaft is far from the axis of the output shaft.
A piston and cylinder combination device 24 for moving 3
The hydraulic motor according to item (2) above, wherein the effective area is larger than /27.

[Brief explanation of the drawing]

FIG. 1 and FIG. 2 are an example of a crank-shaped output shaft of a variable stroke hydraulic power motor, and a cross-sectional front view and a longitudinal cross-sectional side view on the axis showing a case where the eccentric wheel is in the maximum eccentric state, respectively, and FIG. The figure is a longitudinal sectional front view similar to Figure 1, also showing the case where the eccentric wheel is in the minimum eccentric state, and Figure 4 is the same as Figure 1.
5 shows a cross-sectional front view on the axis of the radial cylinder hydraulic motor that cooperates with the crank-shaped output shaft shown in FIG. A system diagram showing a crank-shaped output shaft and a system for supplying hydraulic power to an eccentric wheel on this output shaft,
6, 7, and 8 are longitudinal sectional side views showing other embodiments of the eccentric ring in the crank-shaped output shaft, and FIG. 9 is another embodiment of the crank-shaped output shaft in the piston sleeve type radial cylinder hydraulic motor. FIG. 10 is a longitudinal sectional side view showing an embodiment, FIG. 10 is a longitudinal sectional front view showing a crank-shaped output shaft in a rotary casing type motor, and FIG. 11 is a longitudinal sectional side view showing a crank-shaped output shaft in a continuously variable stroke hydraulic motor. It is a vertical front view showing a complete collapse. 20... Output shaft, 21... Roller bearing, 22... Eccentric ring, 23... Annular body, 24.25... Piston, 2
6...Positioning spring, 27°28...Cylindrical recess,
29... Crank part, 30... Plane part, 31...
Pad, 32...key, 33...recess, 34...
Piston, 34A...Connecting rod, 34B...Connecting rod slipper, 34C...Hole, 35...Protrusion, 36...
Fixing groove, 37.38...Duct, 39...Body, 4
0.41... Groove, 42.43... Hole, 44... Ring, 45... Sliding ring assembly, 46... Spacer, 47... Radial cylinder, 48... Shaft valve, 49・
・・Supply and return conduit, 50° 51 ・・Duct, 52
...Control valve, 53...High pressure source, 54...Drain, 55...Valve spool, 58...Spring, 59...
Supply pipe, 60... Shuttle valve, 61... First restraint part, 62... Conduit, 63... Relief valve, 64...
Spring, 65... Second restraint part, 66... Manual control valve,
67... Outlet, 6B, 69.70... Conduit, 71
...Restraint part, 72... Piston rod, 73.74
... hole, 75 ... piston, 76 ... chamber, 77.
... part, 78 ... recess, 80.81 ... recess, 8
2.83... Protrusion, 84... Plane, 90.91.
...Circular protrusion, 92.93...Pressure chamber, 94.95
... Duct, 100 ... Pentagonal body, 101 ... Piston sleeve, 102 ... Outer lower surface, 103 ... Duct), 105 ... Compression spring, 130.131 ... Hole, 140. ...Servo valve.

Claims (1)

[Claims for Utility Model Registration] At least one reciprocating piston is disposed around an eccentric ring attached to an output shaft, and the eccentric ring is provided with an annular body driven by the piston, A pair of hydraulically actuated piston and cylinder combinations mounted on an output shaft and facing each other moves the ring toward or away from the axis of the output shaft. The hydraulic motor is configured to change the stroke and displacement of the eccentric wheel by causing the eccentric wheel to move, and includes a relief valve 63 that is biased by a spring 64 connected between the output shaft 20 and the ring body 23. ,Thereby,
The pressure for actuating the relief valve 63 varies with the eccentric position of the annulus 23, and a manual control valve 66 is provided, which is adjustable to predetermine the force for actuating the relief valve 63, and cylinder combination device 24/27.
25/2B, the piston and cylinder combination device 24/27, 2 is provided with a servo control valve device 55, 56, 57.5B for controlling the pressure of high pressure fluid sent to the piston and cylinder combination device 24/27, 2.
To control the supply of fluid to 5/2B, the servo control valves 55, 56, 57, 58 are made responsive to the pressure differential of the high pressure fluid controlled by the relief valve 63 and the manual control valve 66. The actuation of the piston and cylinder combination device 24/27. keep it,
A hydraulic motor characterized in that the rotational position of the hydraulic motor corresponds to the operating position of the manual control valve 66.