KR102346663B1 - HYDRAULIC rotator - Google Patents

Abstract

The present invention relates to a variable swash plate type hydraulic rotary device, and the hydraulic rotary device according to an embodiment of the present invention includes a cylinder block rotating with a plurality of cylinders, a first stage for rotating the cylinder block at low speed, and the first stage The swash plate has a swash plate divided into two stages for rotating the cylinder block at high speed with a smaller swash plate angle, a piston shoe in contact with a region of the swash plate, and a piston body jointly connected to the piston shoe to reciprocate. It includes a variable speed piston for changing the angle of the swash plate.

Description

Hydraulic Rotator {HYDRAULIC rotator}

An embodiment of the present invention relates to a hydraulic rotating device, and more particularly, to a variable swash plate type hydraulic rotating device.

In general, a hydraulic rotary device, such as a hydraulic pump or a hydraulic motor, compresses or expands the volume in several cylinders installed perpendicular or parallel to a rotating shaft according to the rotational direction of the shaft to convert mechanical energy into pressure or pressure to mechanical energy. device that converts it into

And among various types of hydraulic rotary devices, the variable swash plate hydraulic rotary device is equipped with a plurality of drive pistons reciprocating in the direction of the rotation axis on a rotatable cylinder block, and by changing the angle of the swash plate opposite to the end of each drive piston. It is formed so that the capacity is variable.

At this time, the angle of the swash plate is changed from low speed to high speed by pressing the rear surface of one side of the swash plate with a speed change piston. That is, when the speed change piston presses one side of the swash plate to reduce the angle of the swash plate, the rotation speed increases and the torque decreases.

Therefore, when a hydraulic rotary device is applied to a construction machine such as a crawler, when a high torque is required for the construction machine, the hydraulic rotary device rotates at a low speed to increase the torque. It rotates at high speed so that it can move quickly at high speed.

As such, in order for the hydraulic rotary device to have a speed change function, the variable swash plate type hydraulic rotary device is provided with a speed change piston. By changing the volume of the hydraulic rotary device by the shifting piston pushing the swash plate, the speed of the hydraulic rotary device can be changed at a high speed or a low speed.

However, the contact angle between the shift piston and the swash plate is different at high speed and at low speed. Typically, when the shift piston pushes the swash plate and the swash plate angle of the swash plate is reduced, the speed becomes high, and at this time, the contact angle between the shift piston and the swash plate is inclined. Therefore, a lateral load is generated in the speed change piston. In addition, since the swash plate is supported by the shifting piston at high speed, a relatively large load is applied to the shifting piston at high speed than at low speed. As described above, the lateral load generated on the shifting piston at high speed locally increases the surface pressure between the piston shoe in contact with the swash plate in the shifting piston and the reciprocating piston body, thereby causing uneven wear. The occurrence of such uneven wear has a problem in that the efficiency of the hydraulic rotating device is lowered, and the operation efficiency is also lowered by causing the equipment to run unbalanced. In addition, a phenomenon in which the shift piston is intermittently caught in the casing may occur due to an increase in local surface pressure. If the shifting piston gets caught in the casing, shifting becomes impossible or if only one of the shifting pistons among the hydraulic rotating units arranged on the left and right is caught, the construction machine rotates and falls due to the speed difference between the left and right hydraulic rotating units can also cause

An embodiment of the present invention provides a hydraulic rotating device with improved lifespan by minimizing the occurrence of wear.

According to an embodiment of the present invention, the variable swash plate type hydraulic rotation device includes a cylinder block rotating with a plurality of cylinders, a first stage for rotating the cylinder block at a low speed, and a swash plate angle smaller than the first stage to rotate the cylinder block A swash plate operating in two stages for rotating at high speed, a piston shoe in contact with a region of the swash plate, and a piston body jointly connected with the piston shoe to reciprocate, and a variable speed piston for changing the swash plate angle of the swash plate do. And when the swash plate operates in the first stage, the piston shoe and the swash plate are in contact with the piston shoe and the swash plate when the swash plate operates in the second stage than the pier between the contact surface and the rotation axis of the cylinder block The pier between the surface and the rotation axis of the cylinder block is formed to be relatively closer to 90 degrees.

The hydraulic rotating device may further include a casing having a support surface facing the swash plate to support the swash plate and a variable-speed piston receiving part recessed in a region of the support surface to accommodate the variable-speed piston.

And when the swash plate operates in the first stage, one surface of the swash plate opposite to the casing is supported by the support surface of the casing, and when the swash plate operates in the second stage, the swash plate facing the casing One surface may be supported by the piston shoe of the variable speed piston.

In addition, one surface of the swash plate rotates around a support point and is relatively close to the support surface of the casing when operating in the first stage and the first surface relatively close to the support surface of the casing when operating in the first stage, and when operating in the second stage The bearing may include a second surface and a third surface in contact with the piston shoe of the variable speed piston.

At this time, the first surface may be parallel to the support surface of the casing when the swash plate operates in the first stage, and the second surface may be parallel to the support surface of the casing when the swash plate operates in the second stage have.

And the pier between the first surface and the second surface and the pier between the first surface and the third surface may be the same.

According to embodiments of the present invention, the hydraulic rotating device can improve the lifespan by minimizing the occurrence of wear.

1 is a cross-sectional view of a hydraulic rotating device according to an embodiment of the present invention.
Figure 2 is a cross-sectional view showing a state in which the hydraulic rotary device of Figure 1 is operating in two stages.
3 is a cross-sectional view showing the swash plate used in the hydraulic rotation device of FIG.
FIG. 4 is a rear view of the swash plate of FIG. 1 .
5 is a rear view of a swash plate used in a hydraulic rotary device according to a modified example of an embodiment of the present invention.
6 and 7 are cross-sectional views of a hydraulic rotation device according to a comparative example.
8 shows lateral force analysis points of Examples and Comparative Examples according to an embodiment of the present invention.
9 is a graph showing a comparison of the lateral force analysis of FIG.

Hereinafter, with reference to the accompanying drawings, the embodiments of the present invention will be described in detail so that those of ordinary skill in the art to which the present invention pertains can easily implement them. The present invention may be embodied in many different forms and is not limited to the embodiments described herein.

It is noted that the drawings are schematic and not drawn to scale. Relative dimensions and proportions of parts in the drawings are shown exaggerated or reduced in size for clarity and convenience in the drawings, and any dimensions are illustrative only and not limiting. And the same reference numerals are used to denote like features to the same structure, element, or part appearing in two or more drawings.

The embodiment of the present invention specifically represents an ideal embodiment of the present invention. As a result, various modifications of the diagram are expected. Accordingly, the embodiment is not limited to a specific shape of the illustrated area, and includes, for example, a shape modification by manufacturing.

Hereinafter, a hydraulic rotation device 101 according to an embodiment of the present invention will be described with reference to FIGS. 1 to 4 . The hydraulic rotating device 101 according to an embodiment of the present invention is a variable swash plate type, and may be operated by a motor or a pump. That is, the hydraulic rotary device 101 may be a hydraulic motor or a hydraulic pump, or a hydraulic motor and a pump.

1 and 2 , the hydraulic rotary device 101 according to an embodiment of the present invention includes a cylinder block 200 , a swash plate 400 , and a variable speed piston 500 .

In addition, the hydraulic rotating device 101 according to an embodiment of the present invention may further include a casing 600 , a driving piston 350 , and a rotating shaft 310 .

The cylinder block 200 rotates with a plurality of cylinders 250 . The plurality of cylinders 250 may be formed at equal intervals in the circumferential direction of the cylinder block 200 . That is, the plurality of cylinders 250 are radially arranged at equal intervals from the center of rotation of the cylinder block 200 .

The rotating shaft 310 is coupled to the cylinder block 200 to transmit the rotational force of the cylinder block 200 to the outside or transmit the rotational force supplied from the outside to the cylinder block 200 .

The driving piston 350 is inserted into each of the plurality of cylinders 250 of the cylinder block 200 and rotates the cylinder block 200 while reciprocating with the pressure of the hydraulic oil or reciprocating according to the rotation of the cylinder block 200 . It generates pressure and discharges hydraulic oil. At this time, one end of the driving piston 350 slidably contacts the swash plate 400 to be described later. Therefore, when the hydraulic rotary device 101 operates as a motor, hydraulic oil flows into the driving piston 350 and the driving piston 350 reciprocates in the cylinder 250 , one end of the driving piston 350 is The cylinder block 200 rotates while sliding along the inclined surface of the swash plate 400 . On the other hand, when the hydraulic rotary device 101 operates as a pump, when the cylinder block 200 rotates by receiving the rotational force of the engine, one end of the driving piston 350 slides along the inclined surface of the swash plate 400 and the cylinder It reciprocates within 250 , and the driving piston 350 generates pressure while reciprocating to discharge hydraulic oil.

The swash plate 400 controls the rotation speed when the hydraulic rotation device 101 operates as a motor or controls the flow rate of hydraulic oil discharged when operating as a pump. That is, the rotation speed of the hydraulic rotation device 101 or the flow rate of the discharged hydraulic oil is determined according to the inclination of the swash plate 400 .

In one embodiment of the present invention, the swash plate 400 is divided into a first stage for rotating the cylinder block 200 at a low speed and a second stage for rotating the cylinder block 200 at a high speed because the swash plate angle is smaller than the first stage. .

The shift piston 500 adjusts the swash plate angle of the swash plate 400 . When the shift piston 500 presses the swash plate 400 to push one side of the swash plate 400 , the swash plate angle of the swash plate 400 decreases, the rotation speed of the cylinder block 200 increases, and the torque decreases. That is, when the swash plate 400 operates in the first stage having a preset inclination and is shifted to the second stage in which the inclination of the swash plate 400 is smaller than the first stage by the shift piston 500, the speed of the hydraulic rotating device 101 is increases and the torque decreases.

Specifically, the shift piston 500 includes a piston shoe 540 in contact with a region of the swash plate 400 , and a piston body 510 articulated with the piston shoe 540 to reciprocate. The piston body 510 reciprocates in the same direction as the rotation axis CL of the cylinder block 200 , and the contact surface of the piston shoe 540 and the swash plate 400 is inclined according to the operating state of the piston body 510 . will change Also, as an example, the piston body 510 may press the piston shoe 540 toward the swash plate 400 by the elastic force of an elastic member such as a spring.

In particular, in one embodiment of the present invention, when the swash plate 400 operates in one stage, the piston shoe 540 and the swash plate 400 contact the surface and the rotation axis CL of the cylinder block 200 rather than the pier. When the swash plate 400 operates in two stages, the pier between the surface where the piston shoe 540 and the swash plate 400 are in contact and the rotation axis CL of the cylinder block 200 is formed to be relatively closer to 90 degrees. .

Figure 1 shows a state in which the hydraulic rotary device 101 according to an embodiment of the present invention is operating in the first stage, Figure 2 shows the state in operation in the second stage.

That is, as shown in FIG. 1 , when the swash plate 400 operates in one stage, the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 is 90 As shown in FIG. 2 , when the swash plate 400 operates in two stages, between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 220 The piers are relatively close to 90 degrees.

At this time, as the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 approaches 90 degrees, the lateral load applied to the variable speed piston 500 is reduced. And as shown in Figure 2, when the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees, the lateral load applied to the variable speed piston 500 is Theoretically, it becomes O.

The casing 600 is a support surface 640 facing the swash plate 400 to support the swash plate 400 and a variable speed piston receiving part ( 650). That is, the piston body 510 of the variable speed piston 500 reciprocates within the variable speed piston receiving part 650 of the casing 600 .

For example, when the swash plate 400 operates in one stage, one surface of the swash plate 400 opposite to the casing 600 is supported by the support surface 640 of the casing 600, and the swash plate 400 is 2 When operating in stages, one surface of the swash plate 400 facing the casing 600 is supported by the piston shoe 540 of the speed change piston 500 .

As shown in FIG. 1 , when the swash plate 400 operates in one stage, the contact surface between the swash plate 400 and the piston shoe 540 is inclined, so that a lateral load may be applied to the variable speed piston 500 . However, when the swash plate 400 operates in one stage, since the swash plate 400 is mainly supported by the support surface 640 of the casing 600 , the piston shoe 540 of the variable speed piston 500 has the swash plate 400 . ), a relatively very small load is applied compared to when it is operated in two stages. Therefore, when the swash plate 400 operates in the first stage, the lateral load applied to the shift piston 500 is relatively very insignificant, so uneven wear occurs less and has a relatively very small effect on the lifespan of the shift piston 500 .

In addition, as shown in FIG. 2 , in the case of the second stage in which the piston shoe 540 of the variable speed piston 500 supports the swash plate 400 and a relatively large load is applied to the piston shoe 540 , the swash plate 400 and the piston The pier between the contact surface of the shoe 540 and the rotation axis CL of the cylinder block 200 is relatively closer to 90 degrees than in the case of one stage. Most preferably, the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees. Therefore, even when a large load is applied to the piston shoe 540 , the lateral load becomes zero or is very insignificant, so that the occurrence of uneven wear in the variable speed piston 500 can be minimized.

As described above, in order to adjust the inclination of the contact surface of the piston shoe 540 of the swash plate 400 and the variable speed piston 500, one surface of the swash plate 400, as shown in FIG. The first surface 410 that is relatively close to the support surface 640 of the casing 600 when it is rotated and operated in one stage, and the support surface 640 of the casing 600 and relative when operating in two stages and a second surface 420 that approaches to , and a third surface 430 in contact with the piston shoe 540 of the variable speed piston 500 .

For example, in the first stage, the first surface 410 of the swash plate 400 is in contact with the support surface 640 of the casing 600, and in the second stage, the second surface 420 of the swash plate 400 is the casing ( 600 may be in contact with the support surface 640 .

In addition, the first surface 410 of the swash plate 400 is parallel to the support surface 640 of the casing 600 when the swash plate 400 operates in one stage, and the second surface 420 of the swash plate 400 . When the silver swash plate 400 operates in two stages, it may be formed to be parallel to the support surface 640 of the casing 600 .

In addition, the pier θ1 between the first surface 410 and the second surface 420 of the swash plate 400 and the pier θ2 between the first surface 410 and the third surface 430 of the swash plate 400 are They may be formed to have the same angle. In this case, when the swash plate 400 operates in two stages, the surface in which the piston shoe 540 of the variable speed piston 500 and the third surface 430 of the swash plate 400 are in contact and the rotation axis of the cylinder block 200 are As the pier between (CL) becomes 90 degrees, the lateral load applied to the shift piston 500 becomes O theoretically.

4 shows a rear view of the swash plate 400 used in the hydraulic rotating device 101 according to an embodiment of the present invention, and FIG. 5 is a hydraulic rotating device 101 according to a modification of an embodiment of the present invention. A rear view of the used swash plate 401 is shown. In FIG. 4 , the third surface 430 of the swash plate 400 may be formed close to a circular shape, and in FIG. 5 , the third surface 431 of the swash plate 401 may be formed close to a long hole shape.

By such a configuration, the hydraulic rotation device 101 according to an embodiment of the present invention can minimize the occurrence of wear and improve the lifespan.

In particular, by minimizing the lateral load applied to the shifting piston 500 to suppress the occurrence of uneven wear in the shifting piston 500 , the lifespan of the shifting piston 500 is improved, and accidents caused by malfunction of the shifting piston 500 . can prevent

Hereinafter, Examples and Comparative Examples will be described with reference to FIGS. 6 to 9 .

The embodiment has the configuration as previously shown in FIGS. 1 to 3 . On the other hand, the comparative example has the configuration as shown in FIGS. 6 and 7 . That is, one surface of the swash plate 400 used in the hydraulic rotary device 101 according to the embodiment is divided into a first surface 410 , a second surface 420 , and a third surface 430 as described above. , One surface of the swash plate used in the hydraulic rotary device 10 according to the comparative example has one flat surface.

In the case of the embodiment, as described above, when the swash plate 400 operates in one stage, as shown in FIG. 1 , between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 . The piers are less than 90 degrees. Accordingly, a lateral load may be applied to the shifting piston in the first stage. However, when the swash plate 400 operates in one stage, since the swash plate 400 is mainly supported by the support surface 640 of the casing 600 , the piston shoe 540 of the variable speed piston 500 has the swash plate 400 . ), a relatively very small load is applied compared to when it is operated in two stages. Therefore, when the swash plate 400 operates in the first stage, the lateral load applied to the shift piston 500 is relatively very insignificant, so uneven wear occurs less and has a relatively very small effect on the lifespan of the shift piston 500 .

In addition, when the swash plate 400 operates in two stages, as shown in FIG. 2 , the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 220 is 90 degrees. As the angle between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 approaches 90 degrees, the lateral load applied to the variable speed piston 500 is reduced. And when the pier between the contact surface of the swash plate 400 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees, the lateral load applied to the variable speed piston 500 becomes O theoretically. Accordingly, when the swash plate 400 operates in two stages, the occurrence of uneven wear of the shift piston 500 is minimized, and thus the lifespan of the shift piston 500 is greatly improved.

On the other hand, in the case of the comparative example, as shown in FIG. 6 , when the swash plate 40 operates in one stage, the contact surface of the swash plate 40 and the piston shoe 540 and the rotation axis CL of the cylinder block 200 ) The pier between them is 90 degrees. That is, the contact surface of the swash plate 40 and the piston shoe 540 and the support surface 640 of the casing 600 are the same or parallel.

However, as shown in FIG. 7 , when the swash plate 40 operates in two stages, more than 90 degrees between the contact surface of the swash plate 40 and the piston shoe 540 and the rotation axis CL of the cylinder block 220 . gets smaller Accordingly, when the swash plate 40 presses the piston shoe 540 by the force transmitted by the driving piston 500 , a lateral load is applied to the shift piston 500 . In FIG. 7 , reference numeral F denotes a load applied by the swash plate 40 to the variable speed piston 500 , and Fr denotes a lateral load, Fa denotes a longitudinal load. In particular, when the swash plate 40 operates in two stages, since the piston shoe 540 of the shift piston 500 supports the swash plate 40 , a large load is applied to the shift piston 500 , and thus the shift piston 500 ) will also increase the lateral load. This means that, in the case of the comparative example, when the swash plate 40 is operated in two stages, uneven wear occurring in the speed change piston 500 is relatively large.

8 shows the lateral force analysis points of Examples and Comparative Examples. And Figure 9 is a graph showing the comparison of the lateral force analysis of the Example and Comparative Example.

Looking at Comparative Example F1 and Comparative Example F2 in FIG. 9 , it can be confirmed as an analysis result that a relatively very large lateral force is applied as compared to Examples F1 and F2. That is, in the embodiment, it can be confirmed that the lateral force is temporarily generated only in the shift section, and almost no lateral force is generated when the second gear is operated.

Although the embodiments of the present invention have been described above with reference to the accompanying drawings, those skilled in the art to which the present invention pertains will understand that the present invention may be embodied in other specific forms without changing the technical spirit or essential characteristics thereof. will be.

Therefore, the embodiments described above are to be understood as illustrative and not restrictive in all respects, and the scope of the present invention is indicated by the following claims, the meaning and scope of the claims, and All changes or modifications derived from the equivalent concept should be construed as being included in the scope of the present invention.

101: hydraulic rotation device
200: cylinder block
250: cylinder
310: rotation shaft
350: drive piston
400: swash plate
410: first side
420: second side
430: the third side
500: variable speed piston
510: piston body
540: piston shoe
600: casing
640: support surface
650: variable speed piston receiver

Claims (6)

In the variable swash plate type hydraulic rotation device,
A cylinder block rotating with a plurality of cylinders;
a driving piston inserted into each of the plurality of cylinders to reciprocate;
a swash plate divided into a first stage for rotating the cylinder block at a low speed and a second stage for rotating the cylinder block at a high speed because the angle of the swash plate is smaller than that of the first stage;
a variable speed piston having a piston shoe in contact with a region of the swash plate, a piston body jointly connected to the piston shoe and reciprocating, and varying an angle of the swash plate of the swash plate; and
A casing having a support surface facing the swash plate and supporting the swash plate
including,
One surface of the swash plate rotates around a support point and is a first surface that is relatively close to the support surface of the casing when operating in the first stage, and a first surface that is relatively close to the support surface of the casing when operating in the second stage a second surface and a third surface in contact with the piston shoe of the variable speed piston;
A hydraulic rotary device in which the pier between the first face and the second face and the pier between the first face and the third face are the same. According to claim 1,
The casing may further include a variable speed piston receiving portion recessed in a region of the support surface to accommodate the variable speed piston. 3. The method of claim 2,
When the swash plate operates in the first stage, one surface of the swash plate opposite to the casing is supported by the support surface of the casing,
When the swash plate operates in the two stages, one surface of the swash plate facing the casing is supported by the piston shoe of the variable speed piston. delete 4. The method of claim 3,
The first surface is parallel to the support surface of the casing when the swash plate operates in the first stage,
The second surface is a hydraulic rotation device, characterized in that parallel to the support surface of the casing when the swash plate operates in the second stage. delete

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