阅读说明：本技术 液压旋转装置 (Hydraulic rotary device ) 是由 金广门 金成训 于 2020-03-31 设计创作，主要内容包括：本发明涉及一种可变型斜盘式的液压旋转装置,本发明的一实施例的液压旋转装置包括：缸体,其具有多个缸而旋转；斜盘,其区分为用于使所述缸体以低速旋转的一档和斜盘角变得小于所述一档而使所述缸体以高速旋转的二档来进行动作；以及变速柱塞,其具有与所述斜盘的一区域接触的柱塞滑靴和与所述柱塞滑靴关节连接并进行往复运动的柱塞本体,使所述斜盘的斜盘角可变。(The present invention relates to a variable swash plate type hydraulic rotating apparatus, and a hydraulic rotating apparatus according to an embodiment of the present invention includes: a cylinder block which rotates with a plurality of cylinders; a swash plate that is divided into a first speed stage for rotating the cylinder block at a low speed and a second speed stage for operating the cylinder block at a high speed with a swash plate angle smaller than the first speed stage; and a variable-speed plunger having a plunger shoe contacting an area of the swash plate and a plunger body being articulated to the plunger shoe and reciprocating, the variable-speed plunger varying a swash plate angle of the swash plate.)

1. A hydraulic rotating apparatus which is a variable swash plate type hydraulic rotating apparatus, comprising:

a cylinder block which rotates with a plurality of cylinders;

a swash plate that is divided into a first speed stage for rotating the cylinder block at a low speed and a second speed stage for operating the cylinder block at a high speed with a swash plate angle smaller than the first speed stage; and

a variable-speed plunger having a plunger shoe contacting an area of the swash plate and a plunger body being articulated to the plunger shoe and reciprocating, the variable-speed plunger varying a swash plate angle of the swash plate,

an intersection angle between a surface of the plunger shoes in contact with the swash plate and the rotation axis of the cylinder block when the swash plate is operated in the second gear is relatively closer to 90 degrees than an intersection angle between a surface of the plunger shoes in contact with the swash plate and the rotation axis of the cylinder block when the swash plate is operated in the first gear.

2. The hydraulic rotary device of claim 1, further comprising:

a housing having a support surface facing the swash plate and supporting the swash plate, and a shift plunger accommodating portion recessed in an area of the support surface and accommodating the shift plunger.

3. Hydraulic rotating device according to claim 2,

when the swash plate operates at the first gear, one surface of the swash plate facing the housing is supported by the support surface of the housing;

when the swash plate is operated in the second gear, one surface of the swash plate facing the housing is supported by the piston shoes of the transmission pistons.

4. Hydraulic rotating device according to claim 3,

one surface of the swash plate includes a first surface that rotates about a support point and is relatively close to the support surface of the housing when the first gear is operated, a second surface that is relatively close to the support surface of the housing when the second gear is operated, and a third surface that contacts the plunger shoes of the transmission plungers.

5. Hydraulic rotating device according to claim 4,

the first surface is parallel to a support surface of the housing when the swash plate operates at the first gear,

the second surface is parallel to the support surface of the housing when the swash plate is operated at the second speed.

6. Hydraulic rotating device according to claim 4,

an intersection angle between the first face and the second face is the same as an intersection angle between the first face and the third face.

Technical Field

Embodiments of the present invention relate to a hydraulic rotating apparatus, and more particularly, to a variable swash plate type hydraulic rotating apparatus.

Background

In general, a hydraulic rotating device refers to a device that converts mechanical energy into pressure or converts pressure into mechanical energy by compressing or expanding volumes within a plurality of cylinders, which are disposed perpendicular to or parallel to a rotating shaft, according to the rotating direction of the shaft, like a hydraulic pump or a hydraulic motor.

In many types of hydraulic rotary devices, a variable swash plate type hydraulic rotary device is configured such that a plurality of drive plungers reciprocating in a rotation axis direction are attached to a rotatable cylinder block, and the capacity can be varied by changing the angle of a swash plate facing the end of each drive plunger.

At this time, the swash plate is changed from a low speed to a high speed by pressurizing one side back surface of the swash plate with a shift plunger. That is, when the shift plunger pressurizes one side of the swash plate to reduce the angle of the swash plate, the torque is reduced as the rotation speed increases.

Therefore, when the hydraulic rotary device is applied to a construction machine such as a Crawler (Crawler), the hydraulic rotary device rotates at a low speed to increase torque when a high torque is required in the construction machine, and the hydraulic rotary device can rotate at a high speed and move at a high speed when a motive power is required in the construction machine.

In this way, in order to provide the hydraulic rotating apparatus with a speed change function, the variable swash plate type hydraulic rotating apparatus is provided with a speed change plunger. By changing the volume of the hydraulic rotary device by pushing the swash plate by the variable speed plunger, the speed of the hydraulic rotary device can be changed to a high speed or a low speed.

However, the contact angle of the shift plunger and the swash plate is different at high speed and low speed. Generally, when the shift plunger pushes the swash plate so that the swash plate angle of the swash plate becomes small to a high speed, the contact angle of the shift plunger and the swash plate is inclined at this time. Therefore, a lateral load is generated in the shift plunger. Further, at high speed, the swash plate is supported by the shift plunger, and therefore a relatively larger load is applied to the shift plunger at high speed than at low speed. In this way, the lateral load generated in the shift plunger at high speed locally increases the surface pressure between the plunger shoe and the reciprocating plunger body, which are in contact with the shift plunger and the swash plate, and single-side wear is caused. The occurrence of such one-side wear has a problem that the efficiency of the hydraulic rotating device is lowered, and one-side running of the equipment is caused, and further, the working efficiency is lowered. In addition, a phenomenon may occur in which the shift plunger is intermittently caught by the housing due to a local increase in the surface pressure. If the shift plunger is caught by the housing, if the shift becomes impossible or if the jam occurs only in one of the shift plungers disposed on one of the left and right hydraulic rotating devices, there is a possibility that the speed difference between the left and right hydraulic rotating devices causes the construction machine to rotate and reverse.

Disclosure of Invention

Technical problem

Embodiments of the present invention provide a hydraulic rotating apparatus that minimizes the occurrence of wear to improve the lifespan.

Technical scheme

According to an embodiment of the present invention, a variable swash plate type hydraulic rotating apparatus includes: a cylinder block which rotates with a plurality of cylinders; a swash plate that is divided into a first speed stage for rotating the cylinder block at a low speed and a second speed stage for operating the cylinder block at a high speed with a swash plate angle smaller than the first speed stage; and a variable-speed plunger having a plunger shoe contacting an area of the swash plate and a plunger body being articulated to the plunger shoe and reciprocating, the variable-speed plunger varying a swash plate angle of the swash plate. In addition, the variable swash plate type hydraulic rotating apparatus is formed such that an intersection angle between a surface where the plunger shoes and the swash plate contact and the rotation axis of the cylinder block is relatively closer to 90 degrees when the swash plate operates in the second gear than an intersection angle between a surface where the plunger shoes and the swash plate contact and the rotation axis of the cylinder block when the swash plate operates in the first gear.

The hydraulic rotating apparatus may further include: a housing having a support surface facing the swash plate and supporting the swash plate, and a shift plunger accommodating portion recessed in an area of the support surface and accommodating the shift plunger.

In addition, when the swash plate operates at the first speed, one surface of the swash plate facing the housing may be supported by the support surface of the housing; when the swash plate is operated in the second gear, one surface of the swash plate facing the housing may be supported by the piston shoes of the transmission pistons.

Further, the one surface of the swash plate may include a first surface that rotates about a support point and is relatively close to the support surface of the housing when operating in the first gear, a second surface that is relatively close to the support surface of the housing when operating in the second gear, and a third surface that contacts the plunger shoe of the transmission plunger.

In this case, the first surface may be parallel to a support surface of the housing when the swash plate operates in the first gear, and the second surface may be parallel to the support surface of the housing when the swash plate operates in the second gear.

In addition, an intersection angle between the first surface and the second surface and an intersection angle between the first surface and the third surface may be the same.

ADVANTAGEOUS EFFECTS OF INVENTION

According to some embodiments of the present invention, the hydraulic rotating apparatus may minimize the occurrence of wear to improve the lifespan.

Drawings

Fig. 1 is a sectional view of a hydraulic rotating apparatus according to an embodiment of the present invention.

Fig. 2 is a cross-sectional view showing a state in which the hydraulic rotating apparatus of fig. 1 is operating in the second gear.

Fig. 3 is a sectional view showing a swash plate used in the hydraulic rotary device of fig. 1.

FIG. 4 is a rear view of the swashplate of FIG. 1.

Fig. 5 is a back view of a swash plate used in a hydraulic rotary device according to a modification of the embodiment of the present invention.

Fig. 6 and 7 are sectional views of a hydraulic rotary device of a comparative example.

Fig. 8 shows the lateral force analysis points of an example of an embodiment of the present invention and a comparative example.

Fig. 9 is a graph comparatively illustrating the lateral force analysis of fig. 8.

Description of the symbols

101: hydraulic rotating apparatus, 200: cylinder, 250: cylinder, 310: rotation axis, 350: drive plunger, 400: a swash plate, 410: first side, 420: second side, 430: third face, 500: shift plunger, 510: plunger body, 540: plunger shoe, 600: outer shell, 640: bearing surface, 650: a shift plunger receiving portion.

Detailed Description

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings so that those skilled in the art to which the present invention pertains can easily carry out the embodiments. 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 diagrammatic and not to scale. Relative dimensions and proportions of parts shown in the figures have been shown exaggerated or reduced in size for the sake of clarity and convenience in the drawings, and any dimensions are exemplary only and not limiting. In addition, the same reference numerals are used for the same structures, elements, or components appearing in two or more drawings to represent similar features.

The embodiments of the present invention specifically show desirable embodiments of the present invention. As a result, various modifications of the illustration are expected. Therefore, the embodiments are not limited to the specific form of the illustrated region, and include, for example, variations in form due to manufacturing.

A hydraulic swing apparatus 101 according to an embodiment of the present invention will be described with reference to fig. 1 to 4. The hydraulic rotating apparatus 101 according to an embodiment of the present invention is a variable swash plate type, and can be operated by a motor or a pump. That is, the hydraulic rotating device 101 may be a hydraulic motor or a hydraulic pump, or may be a combination of a hydraulic motor and a pump.

As illustrated in fig. 1 and 2, a hydraulic rotary device 101 according to an embodiment of the present invention includes a cylinder block 200, a swash plate 400, and a shift plunger 500.

In addition, the hydraulic rotating apparatus 101 according to an embodiment of the present invention may further include a housing 600, a driving plunger 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 the same interval in the circumferential direction of the cylinder block 200. That is, the plurality of cylinders 250 are radially arranged at equal intervals at the rotation center of the cylinder block 200.

The rotation shaft 310 is coupled to the cylinder block 200 and transmits a rotation force of the cylinder block 200 to the outside or transmits a rotation force supplied from the outside to the cylinder block 200.

The driving plungers 350 are respectively inserted into the plurality of cylinders 250 of the cylinder block 200, and rotate the cylinder block 200 by reciprocating the pressure of the operating oil or discharge the operating oil by generating pressure as the cylinder block 200 reciprocates by rotating. At this time, one end of the driving plunger 350 slidably contacts with a swash plate 400 to be described later. Therefore, when the hydraulic rotary device 101 is operated by the motor, if the hydraulic oil flows into the driving plunger 350 and the driving plunger 350 reciprocates in the cylinder 250, one end of the driving plunger 350 slides along the inclined surface of the swash plate 400 and rotates the cylinder block 200. On the contrary, 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 plunger 350 slides along the inclined surface of the swash plate 400 to reciprocate in the cylinder 250, and the driving plunger 350 reciprocates to generate pressure to discharge the hydraulic oil.

The swash plate 400 adjusts the rotation speed of the hydraulic rotating device 101 when the motor is operated or the amount of hydraulic oil discharged when the pump is operated. That is, the rotation speed of the hydraulic rotating device 101 and the amount of hydraulic oil discharged are determined according to the inclination of the swash plate 400.

In one embodiment of the present invention, the swash plate 400 is operated in a first gear for rotating the cylinder block 200 at a low speed and a second gear for rotating the cylinder block 200 at a high speed with the swash plate angle smaller than the first gear.

The shift plunger 500 adjusts a swash plate angle of the swash plate 400. When the shift plunger 500 pressurizes the swash plate 400 to push one side of the swash plate 400, as the swash plate angle of the swash plate 400 becomes smaller, the rotation speed of the cylinder block 200 increases and the torque decreases. That is, when the swash plate 400 is operated at the first speed having the set inclination and then shifted to the second speed, in which the inclination of the swash plate 400 is smaller than the first speed, by the shift plunger 500, the speed of the hydraulic rotating device 101 is increased and the torque is decreased.

Specifically, the shift plunger 500 includes a plunger shoe 540 that contacts a region of the disc 400 and a plunger body 510 that articulates with the plunger shoe 540 and reciprocates. The plunger body 510 reciprocates in the same direction as the rotation axis CL of the cylinder block 200, and the inclination of the contact surface between the plunger shoe 540 and the swash plate 400 changes according to the operating state of the plunger body 510. Further, for example, the plunger body 510 may pressurize the plunger shoe 540 in the direction of 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, the intersection angle between the surface of the swash plate 400 in contact with the plunger shoes 540 when the swash plate 400 operates in the second gear and the rotation axis CL of the cylinder block 200 is formed to be relatively closer to 90 degrees than the intersection angle between the surface of the swash plate 400 in contact with the plunger shoes 540 when the swash plate 400 operates in the first gear and the rotation axis CL of the cylinder block 200.

Fig. 1 shows a state in which a hydraulic rotating apparatus 101 according to an embodiment of the present invention is operating in first gear, and fig. 2 shows a state in which the hydraulic rotating apparatus 101 is operating in second gear.

That is, as illustrated in fig. 1, when the swash plate 400 operates at first gear, the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 becomes less than 90 degrees; as illustrated in fig. 2, when the swash plate 400 operates in the second gear, the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 220 becomes relatively close to 90 degrees.

At this time, as the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 approaches 90 degrees, the lateral load applied to the shift plunger 500 decreases. As shown in fig. 2, when the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees, the lateral load applied to the shift plunger 500 is theoretically 0.

The housing 600 has a support surface 640 facing the swash plate 400 and supporting the swash plate 400, and a shift plunger accommodating portion 650 recessed in a region of the support surface 640 and accommodating the shift plunger 500. That is, plunger body 510 of shift plunger 500 reciprocates within shift plunger receiving portion 650 of housing 600.

For example, when the swash plate 400 operates at the first gear, one surface of the swash plate 400 facing the housing 600 is supported by the support surface 640 of the housing 600; when the swash plate 400 operates in the second gear, one surface of the swash plate 400 facing the housing 600 is supported by the plunger shoe 540 of the transmission plunger 500.

As shown in fig. 1, when the swash plate 400 is operated at the first speed, a lateral load may be applied to the shift plunger 500 due to the inclination of the contact surface between the swash plate 400 and the plunger shoe 540. However, when the swash plate 400 is operated in the first gear, since the swash plate 400 is mainly supported by the support surface 640 of the housing 600, a relatively small load is applied to the plunger shoes 540 of the shift plunger 500, as compared to when the swash plate 400 is operated in the second gear. Therefore, when the swash plate 400 is operated at the first gear, the lateral load applied to the shift plunger 500 is relatively insignificant, and thus the one-side wear occurs less, so that the influence on the life of the shift plunger 500 is relatively small.

As shown in fig. 2, in the second gear in which the plunger shoes 540 of the shift plunger 500 support the swash plate 400 and a relatively large load is applied to the plunger shoes 540, the intersection angle between the contact surface between the swash plate 400 and the plunger shoes 540 and the rotation axis CL of the cylinder block 200 is closer to 90 degrees with respect to the first gear. Most preferably, the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees. Accordingly, even if a large load is applied to the plunger shoe 540, the lateral load is 0 or is generated very little, and thus the occurrence of one-side wear in the shift plunger 500 can be minimized.

As described above, in order to adjust the inclination of the contact surface of the swash plate 400 and the plunger shoe 540 of the shift plunger 500, as illustrated in fig. 3, one surface of the swash plate 400 includes: a first surface 410 relatively close to the support surface 640 of the casing 600 when operating in the first gear, a second surface 420 relatively close to the support surface 640 of the casing 600 when operating in the second gear, and a third surface 430 in contact with the plunger shoe 540 of the shift plunger 500 while rotating about the support point.

For example, in the first gear, the first face 410 of the swash plate 400 may be in contact with the support face 640 of the housing 600; in the second gear, the second face 420 of the swash plate 400 may contact the support face 640 of the housing 600.

Further, the first surface 410 of the swash plate 400 may be formed to be parallel to the supporting surface 640 of the housing 600 when the swash plate 400 operates in the first gear, and the second surface 420 of the swash plate 400 may be formed to be parallel to the supporting surface 640 of the housing 600 when the swash plate 400 operates in the second gear.

In addition, the intersection angle θ 1 between the first surface 410 and the second surface 420 of the swash plate 400 and the intersection angle θ 2 between the first surface 410 and the third surface 430 of the swash plate 400 may be formed to be the same angle. In this case, when the swash plate 400 is operated in the second gear, the intersection angle between the surface of the shift plunger 500 where the plunger shoe 540 and the third surface 430 of the swash plate 400 contact and the rotation axis CL of the cylinder block 200 is 90 degrees, and the lateral load applied to the shift plunger 500 is theoretically 0.

Fig. 4 shows a back view of a swash plate 400 used in the hydraulic rotary device 101 according to the embodiment of the present invention, and fig. 5 shows a back view of a swash plate 401 used in the hydraulic rotary device 101 according to the modification of the embodiment of the present invention. The third face 430 of the swash plate 400 of fig. 4 may be formed to be approximately circular, and the third face 431 of the swash plate 401 of fig. 5 may be formed to be approximately a long hole shape.

With such a configuration, the hydraulic rotary device 101 of an embodiment of the present invention can improve the life by minimizing the occurrence of wear.

In particular, by minimizing the lateral load applied to the shift plunger 500, the occurrence of one-sided wear in the shift plunger 500 is suppressed, so that the life of the shift plunger 500 can be increased, and the occurrence of an accident due to the erroneous activation of the shift plunger 500 can be prevented.

The following describes examples and comparative examples in comparison with reference to fig. 6 to 9.

The embodiment has the configuration as illustrated in the aforementioned fig. 1 to 3. In contrast, the comparative example has the configuration as illustrated in fig. 6 and 7. That is, as described above, one surface of the swash plate 400 used in the hydraulic rotary device 101 of the embodiment is divided into the first surface 410, the second surface 420, and the third surface 430, and one surface of the swash plate used in the hydraulic rotary device 10 of the comparative example has a relatively flat surface.

In the case of the embodiment, as described above, when the swash plate 400 operates at first gear, as shown in fig. 1, the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 becomes smaller than 90 degrees. Therefore, in the first gear, a lateral load may be applied to the shift plunger. However, when the swash plate 400 is operated in the first gear, since the swash plate 400 is mainly supported by the support surface 640 of the housing 600, a relatively small load is applied to the plunger shoes 540 of the shift plunger 500 as compared to when the swash plate 400 is operated in the second gear. Therefore, when the swash plate 400 is operated at the first gear, the lateral load applied to the shift plunger 500 is relatively insignificant, and thus the one-side wear occurs less, so that the influence on the life of the shift plunger 500 is relatively small.

When the swash plate 400 is operated in the second gear, as shown in fig. 2, the angle of intersection between the contact surface between the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 220 is 90 degrees. As the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 approaches 90 degrees, the lateral load applied to the shift plunger 500 decreases. When the intersection angle between the contact surface of the swash plate 400 and the plunger shoe 540 and the rotation axis CL of the cylinder block 200 is 90 degrees, the lateral load applied to the shift plunger 500 is theoretically 0. Therefore, when the swash plate 400 is operated in the second gear, the occurrence of wear on one side of the shift plunger 500 is minimized, and the life of the shift plunger 500 is greatly improved.

In contrast, in the case of the comparative example, as illustrated in fig. 6, when the swash plate 40 operates at first gear, the intersection angle between the contact surface of the swash plate 40 and the plunger shoes 540 and the rotation axis CL of the cylinder block 200 is 90 degrees. That is, the contact surface of the swash plate 40 and the plunger shoe 540 is the same as or parallel to the support surface 640 of the housing 600.

However, as illustrated in fig. 7, when the swash plate 40 operates in the second gear, the intersection angle between the contact surface of the swash plate 40 and the plunger shoe 540 and the rotation axis CL of the cylinder block 220 becomes smaller than 90 degrees. Therefore, when the swash plate 40 pressurizes the plunger shoe 540 by the force transmitted from the drive plunger 500, a lateral load is applied to the shift plunger 500. In fig. 7, reference symbol F denotes a load applied to the shift plunger 500 by the swash plate 40, Fr denotes a lateral load, and Fa denotes a longitudinal load. In particular, when the swash plate 40 is operated in the second gear, the plunger shoes 540 of the shift plunger 500 support the swash plate 40, and therefore a large load is applied to the shift plunger 500, and a lateral load generated in the shift plunger 500 also increases. This means that, in the case of the comparative example, when the swash plate 40 is operated in the second gear, one-side wear generated in the shift plunger 500 becomes relatively large.

Fig. 8 shows the lateral force analysis points of the examples and comparative examples. Fig. 9 is a graph showing a comparison between the lateral force analyses of the examples and the comparative examples.

From the observation of comparative example F1 and comparative example F2 in fig. 9, it can be confirmed as an analysis result that a relatively large lateral force is exerted as compared with example F1 and example F2. That is, in the embodiment, the lateral force is generated only temporarily in the shift range, and hardly generated when the second gear is operated.

Although the embodiments of the present invention have been described above with reference to the drawings, those skilled in the art to which the present invention pertains will appreciate that the present invention can be implemented in other specific forms without departing from the technical idea or essential features of the invention.

Therefore, the above-described embodiments should be construed as illustrative in all aspects and not restrictive, the scope of the present invention being indicated by the following claims, and all changes and modifications derived from the meaning and scope of the claims and the equivalent concepts thereof should be construed as falling within the scope of the present invention.