KR20020096760A - Reducer - Google Patents

Abstract

PURPOSE: A reducer is provided to reduce the load ratio of input and output bearings by rotating a roller as a linear contact and using a parallel hydraulic pump and a parallel hydraulic motor. CONSTITUTION: A cartridge of a hydraulic pump and a cartridge of a hydraulic motor are comprised as serial independent shafts(103,203) in both ends of a separating body in a reducer body(10) by sharing one separating member(20). A discharge passage and a suction passage of the hydraulic pump are formed in one side of the separating body. A supply passage(21) and a drain passage of the hydraulic motor are formed in the other side of the separating body. Many connecting passages are punched to connect the passages. A discharge hole, a suction hole, a supply hole and a drain hole are connected with the passages directly for a discharge operation of the hydraulic pump and a hydraulic operation of the hydraulic motor. A drain of hydraulic pressure in the hydraulic pump and a suction of hydraulic pressure in the hydraulic pump are performed simultaneously. The cartridges of the hydraulic pump and the hydraulic motor are fixed between the separating member and a pressurizing member by protruding the pressurizing member in a right cover of the reducer body. Bearing installation recessed grooves are formed in the separating member. Inner plates(130,230), a cam ring and external plates(120) are stuck to the separating member by the pressurizing member. Rotors(210,220) store cylindrical rollers(102,202) by penetrating roller guiding grooves through the inner wall of the cam ring. The rotors are rotated by separating the rollers between gaps of the inner plates and the outer plates and supporting the shafts of the rotor with the separating member and a bearing of the right cover. The discharge of the hydraulic pressure and the suction of oil are guided into the rollers by connecting the discharge hole and the suction hole through the roller guiding grooves. Fluid is moved through an input/output passage in the walls of the roller guiding grooves.

Description

Reducer {REDUCER}

The present invention relates to a speed reducer in which the speed is reduced by volume ratio, and more particularly, the hydraulic pump and the hydraulic motor are each composed of a series of independent shafts in one reducer main body, so that the hydraulic discharge elimination volume of the hydraulic pump and the discharge elimination volume ratio of the hydraulic motor. It is to provide a three-dimensional reducer in which the deceleration is performed by the amount of fluid in the liver and the stability of the driving is secured at the same time.

Conventional gear reducers have gear reducers, belt reducers, chain reducers, worm gear reducers, etc., but most gear reducers, belt reducers, and chain reducers have a drive diameter on the input side. Since the reduction ratio is a one-dimensional reducer only as the circumferential ratio between the driven diameters on the driven side, when the reduction ratio is to be increased, the circumferential ratio of the driving body and the driven shaft driven member of the input shaft is largely made one-dimensionally, Since the follower had to be used in multiple stages, the reduction ratio was limited.

In addition, the worm gear type reducer can obtain a relatively high deceleration ratio, but has a problem of high power loss and abrasion rate and high heat generation due to the frictional power transmission method due to the inclination angle of the worm gear. Due to the difficulty in driving the input stage, the worm screw is frequently damaged by the worm gear rotational inertia force of the output stage, which is a fatal problem.

In addition, since the carrier plate is used as a centering means between planetary gears, ring gears and sun gears in the planetary gear reducer with a relatively large reduction gear ratio, there is complexity in manufacturing and power loss. The manufacturing cost of the is increased, the wear rate of the gear is high, there is a problem such as durability degradation due to the heat treatment change of the metal due to frictional heat.

In addition, although there was a deceleration means of a hydraulic system in which a deceleration type was formed between an input shaft drive and a hydraulic motor output shaft drive of a conventional hydraulic pump and a hydraulic pump that is used as a remote power transmission medium using a hydraulic motor, the hydraulic pump and the hydraulic motor are separate. As it is composed of components to drive remote hydraulic motor, there is a drawback that power loss is large due to the inevitable complicated system such as flow control valve, directional valve, pressure regulating valve, relief valve, connection line, etc. The vane pump and the vane motor are guided by vanes 4 entering and exiting the vane guide groove 5 of the rotor 3 by an eccentricity between the cam ring 2 and the rotor 3, as illustrated in FIG. The contact resistance of the vanes 4 is increased due to the surface contact between the grooves 5 and the inner wall, so that the power loss is large. The wear rate increases rapidly, and the tip of the vane 4 rotates along the cam ring 2 while always being in pressure contact with the cam ring 2, so that the tip end wear of the vane 4 is large and the life of the vane pump and vane motor is short. Was becoming.

The present invention relates to a volume reducer using hydraulic pressure,

The hydraulic pump cartridge (hydraulic pump cartridge collectively refers to the hydraulic pump unit) and the hydraulic motor cartridge (hydraulic motor cartridge collectively refer to the hydraulic motor unit) share the separator of the reducer body in each of both ends of the separator. An independent axis in series; Hydraulic separation of the hydraulic pump and the hydraulic motor and a drain communication path of the oil are formed in the separating body so that the hydraulic pressure is generated by the operation of the hydraulic pump and the hydraulic pressure acts on the hydraulic motor so that the hydraulic motor is interlocked with the hydraulic pump; It has a function of the oil storage tank which forms a space portion in the input shaft direction of the hydraulic pump and the output shaft direction of the hydraulic motor to store the oil of the hydraulic oil; Purifying a part of the oil drained from the hydraulic motor to the outside while circulating it through a filter and circulating it again through the suction check valve of the hydraulic pump to remove impurities and cool the oil;

The rotation of the hydraulic motor is reversed and driven according to the rotation reversal action of the hydraulic pump;

A cylindrical roller is built into the rotor of the hydraulic pump and the hydraulic motor to make contact with the inner wall of the cam ring, and the roller is pressed to rotate the roller by the rotation of the rotor; The roller moves in and out of the roller guide groove inner wall of the rotor by rotating the rotor in a line contact with the inner wall of the roller guide groove; The suction and discharge of oil between the hydraulic pump and the hydraulic motor, the supply and drain of the hydraulic pressure are made from the roller guide groove of the rotor, and the roller is rolled up by the cam ring; The hydraulic pump and the hydraulic motor are composed of balanced cam rings to reduce the one-side load of the bearing; The hydraulic pump and the roller of the hydraulic motor are composed of a small quantity of 9-17 sheets, and the deceleration is reduced by a three-dimensional volume of three elements consisting of eccentricity of the cam ring, diameter of the diameter of the rotor, and width of the rotor. It is a problem to provide a high ratio reducer.

1 is a longitudinal cross-sectional view of the reducer of the present invention.

2 is an explanatory view of the main parts of the hydraulic pump of the present invention.

Figure 3 is an explanatory view of the main operation of the hydraulic motor of the present invention.

4 is a cross-sectional view illustrating a hydraulic pump on the line B-B 'of FIG.

5 is a cross-sectional view illustrating a hydraulic motor on the line AA ′ of FIG. 1.

6 is a longitudinal sectional view illustrating the hydraulic pump and the motor rotor of FIG.

7 is a cross-sectional view illustrating the inner plate of the hydraulic pump and the inner plate of the hydraulic motor on the line C-C 'of FIG.

8 is a cross-sectional view illustrating the inner plate and the separating body of the hydraulic motor on the line D-D 'of FIG.

FIG. 9 is a cross sectional view illustrating the gear reducer on the line E-E 'of FIG. 6. FIG.

10 is a cross-sectional view illustrating a hydraulic pump on the line F-F 'of FIG.

FIG. 11 is a view illustrating a rotor with the roller removed on the line G-G 'of FIG.

12 is a roller accommodated in the rotor of FIG.

FIG. 13 is a view illustrating a rotor with the roller removed on the line H-H 'of FIG.

14 is an operation relationship diagram of the hydraulic pump and the hydraulic motor of the present invention reducer.

15 is another operational relationship between the hydraulic pump and the hydraulic motor of the present invention reducer.

16 is a view illustrating a part of a conventional vane hydraulic motor

<Code Description of Major Codes in Drawing>

1: vane motor 2: cam ring 3: rota

4: vane 5: vane guide home 6: spring

10: reducer body 11: outlet port 20: separate

21: supply guide 22: drain guide 25: discharge guide

26: suction guide 29: communication path 30: the right cover

31, 41: pressurizer 32: inlet 40: left cover

50, 60: discharge check valve 51, 61: flow path 70: bypass line

80: oil filter 91, 92, 93, 94, support

100: hydraulic pump cartridge 101, 201: cam ring

102, 202: roller 103, 203: shaft

110, 210: Rota 112, 212: Spring

111, 211: Roller guide groove 113, 213: Outflow and entrance

120, 220: Outer plate 121, 122: Suction check valve

130, 230: inner plate 131, 133: discharge window

132, 134: suction window 231, 233: supply window

232, 234: drain window

As illustrated in detail in FIG. 1, a separator 20 having an integral part with the reducer body is configured inside the main body of the reducer 10, and is illustrated in FIG. 6 as the center of the separator 20. As shown, the central shaft bearing guide members 45 and 46 of the hydraulic pump and the hydraulic motor are formed, and the communication path 29 through which the oil and oil flow in and out between the hydraulic pump cartridge and the hydraulic motor cartridge is perforated. As the curved paper, the suction guide passage 26, the drain guide passage 22, the discharge guide passage 25, and the supply guide passage 21 are respectively formed to be independently formed as illustrated in FIGS.

The inner side plate 130 in which the hydraulic pump discharge / suction windows 131, 132, 133, and 134 are shown to the right of the separator 20 of the main body of the reducer 10 in a solid line of FIG. ), The rota 110 in which the cam ring 101 and the roller 102 are accommodated, and the pressurized body in which the outer plate 120 protrudes to the right cover 30 of the reducer while the hydraulic pump outer plate 120 is sequentially arranged. The inner side plate 130, the cam ring 101, and the outer side plate 120 are tightly fixed to the right side of the separator 20 by 31, and the rota 110 is attached to the second drawing, As illustrated in FIGS. 11 and 13, the roller guide groove 111 formed to be curved toward the center from the outer circumference of the rota 110 is axially penetrated to receive the cylindrical roller 102 in the axial direction. The rotor 110 and the roller 102 accommodated in the rotator 110 in the axial direction are spaced apart from each other as a minimum gap between the inner side plate 130 and the outer side plate 120, and the separator 20. The shaft 103 of the rotor 110 is supported by the bearing of the right cover 30 to rotate the rotor 110 between the inner plate 130 and the outer plate 120 of the hydraulic pump cartridge. .

On the left side of the separator 20 of the main body of the reducer 10, an inner side plate formed with hydraulic motor supply / drain windows 231, 232, 233, and 234 shown in a dotted line in FIG. 230, the cam ring 201 and the rotor 210 in which the rollers 202 are accommodated, and the hydraulic motor outer plate 220 are sequentially disposed, and the outer plate 220 is disposed on the left cover 40 of the reducer 10. The inner side plate 230, the cam ring 201, and the outer side plate 220 are tightly fixed to the left side of the separator 20 by the protruding pressurizer 41. As illustrated in FIGS. 3, 11, and 13, the roller guide groove 211 is formed to be curved in the groove from the outer circumference of the rotor 210 toward the center to axially penetrate the cylindrical roller 202. Rota 210 accommodated in the direction and the roller 202 accommodated in the rotator 210 in the axial direction are spaced apart as a minimum gap between the inner plate 230 and the outer plate 220, the separator ( 20) And the shaft 203 of the rotor is supported by the bearing of the left cover 40 to rotate the rotor 210 between the inner plate 230 and the outer plate 220 of the hydraulic motor cartridge.

In the cover 30 having the right end of the reducer 10 main body, a rectangular pressurizer 31 having an empty space in the inner space for tightly supporting the outer plate 120 of the hydraulic pump extends in the axial direction so that the outer plate ( Since the pressure is fixed to 120, a certain space is secured between the hydraulic pump outer plate 120 and the right cover 30 inside, so that oil is stored, and oil is introduced into one surface of the pressure body 31 in a radial direction. A plurality of inlets 32 are drilled to place the oil filter 80.

Oil chambers 34 and 44 to prevent oil leakage from the input shaft 103 and the output shaft 203 of the reducer 10, and dust covers 35 and 43 to block foreign substances from outside are installed. The oil is filled in the body of the reducer 10.

In addition, the flow ports 11 and 12 illustrated in FIG. 9 are drilled at both edges of the lower side of the separator 20 of the reducer body so that the hydraulic pump input side and the hydraulic motor output side communicate with each other. A function of circulating the oil leaked in small amounts to the outer plate 220 to the suction side of the hydraulic pump and circulating the lubricating oil of the output shaft 203 of the hydraulic motor is carried out.

On the other hand, flow paths 51 and 61 which bypass the supply guide flow path 21 and the drain guide flow path 24 formed on the separator 20 of the reducer 10 main body 24, respectively, are formed in each of these flow paths. Lot type discharge check valve (50) and (60) are respectively installed and communicated with the bypass line (70) so as to communicate with the outside of the pressurizer (31) of the hydraulic pump, so that a part of the oil drained from the hydraulic motor to the outside By purifying the bypass to induce heat exchange due to contact with outside air, foreign substances are removed from the oil filter 80, and separate suction check valves 121 and 122 are disposed on the outer plate 120 of the hydraulic pump. Part of the oil passing through the filter is sucked into the suction check valves 121 and 122 of the outer plate 120.

The simple configuration and operation of the above-described hydraulic pump cartridge 100 will be described in detail with reference to FIGS. 2 and 4 of the accompanying drawings.

4 is a view illustrating a hydraulic pump on the line B-B 'of FIG. 1, and the main body of the reducer 10 has a rectangular inner cylindrical shape, and has a horizontally symmetrical equilibrium with suction windows 132 and 134. ) And the inner plate 130 through which the discharge windows 131 and 133 are perforated are tightly fixed to the inner walls of the four rectangular cylinders of the reducer 10 main body, and the cam ring 101 and the outer plate (not shown) are the reducer 10. ) Is firmly fixed to the supports 91, 92, 93, and 94 protruding into the rectangular body of the main body, and the rotor 110 is installed inside the cam ring 101. As illustrated in FIGS. 2, 11, and 13, the roller guide groove 111 formed to be curved toward the center from the outer circumference of the rotor 110 is formed to penetrate in the axial direction. In the roller guide groove 111 of the 110 is a cylindrical roller 102 which receives the spring force of the spring is housed on the inner wall of the cam ring 101, the structure of the roller of the rotor 110 An outflow passage 113 through which fluid enters and exits the left side wall of the guide groove 111 is formed as illustrated in FIGS. 11 to 13 of the accompanying drawings to inhale oil and discharge hydraulic pressure.

Since the hydraulic pump is a balanced pump, when the rotor 11 of the hydraulic pump is rotated counterclockwise as illustrated in FIG. 2, the roller 102 is rotated by the eccentricity of the cam ring 101. Since the oil is pressurized into the roller guide groove 111 to pressurize the oil, the oil pressure is generated and the oil pressure is drawn to the discharge window 131 formed as the inner plate, while the eccentric reduction action between the cam ring 101 and the rota 110 is made. Some of the oil is replenished by an increase in volume generated by the roller 102 entering the roller guide groove 111, and the remaining oil is reduced in volume change due to the eccentricity between the cam ring 101 and the rotor 110. As a result of the pressure action of the oil is generated, the hydraulic pressure is generated through the roller guide groove 111 of the rota 110 through the outflow passage 113, the discharge window 131 of the inner plate communicated in the axial direction of the rota 110 Hydraulic pressure is discharged.

Therefore, as shown in FIG. 4 of the accompanying drawings, since the volume is reduced in two places of the first hydraulic chamber ① and the third hydraulic chamber ③ where the eccentricity between the rotor 110 and the cam ring 101 is reduced, the inner plate ( Hydraulic pressure is discharged through the discharge window 131, 133 and the outflow passage 113 of the roller guide groove 111 of the 130, the second hydraulic pressure to expand the eccentric between the rotor 110 and the cam ring 101 Since the volume is increased at two places of the seal ② and the fourth hydraulic chamber ④, the inlet and outflow paths 113 of the suction windows 132 and 134 of the inner plate 130 and the roller guide groove 111 are opened. The oil is sucked through.

In addition, when the rotor 110 of the hydraulic pump rotates counterclockwise, as shown in detail in FIG. 2, the roller 102 is closely supported by the linear contact with the cam ring 101 by the elastic force of the spring 112. Since the rotor 110 rotates in the opposite direction of rotation, the contact frictional resistance between the roller 102 and the inner wall of the cam ring 101 due to the rotation of the rotor 110 is greatly reduced while the hydraulic pressure generated by the operation of the hydraulic pump described above. The roller 102 is always held in close contact with the right side wall of the roller guide groove 111 of the rotor 110 by the action of the rotor 110 and rotates in accordance with the rotation of the rotor 110 while rotating the center of the rotor 110 in the cam ring 101. Since the roller guide groove 111 is drawn toward the roller guide groove 111, the leakage of hydraulic pressure is blocked to the right wall of the roller guide groove 111, while the roller 102 and the rotor 110 when the foreign material is chipped in by the rotation of the roller 102 described above. Roller guide groove (111) of the wall between the debris action and roller guide groove (111) The foreign material can be evacuated to the escape groove of the inflow passage 113 formed by the left wall, so that a large amount of damage caused by chipping of the foreign matter by the surface contact of the vane in the conventional vane pump is greatly reduced. .

On the other hand, when the roller 102 is located inside the points ⓐ, ⓑ, ⓒ and ⓓ of the cam ring 101 as shown in the example of FIG. 2, the points ⓐ, ⓑ, ⓒ, The hydraulic pressure is applied to the entire circumference of the roller 102 located in the section, and the roller 102 is pressed against the cam ring 101 by the elastic force of the spring 112, and the roller 102 is located near the ⓓ point of the cam ring 101. Since the hydraulic pressure acts downward of the roller 102 and the left side of the roller 102 when the roller 102 is positioned, the roller 102 is pressed against the cam ring 101 by the spring force of the spring 112 and the pressure of the hydraulic pressure. The spring 112 elasticity of the hydraulic pump should be about the minimum elasticity of rolling the roller 102 with the cam ring 101 under no load, and the diameter d of the roller 102 is the inner wall of the cam ring 101 and the rotor ( 110) If the maximum amount of eccentricity generated in the outer circumference is h,

The roller diameter d ≥ 11 / 5h ........ (≥: size or the same) relationship is desirable,

This induces the roller 102 to enter and exit the center of the cam ring 101 and the rota 110 with a minimum clearance within the width b of the roller guide groove 111 of the rota 110 so that the roller 102 and the roller 102 It is to maintain a constant play between the guide groove (111).

If the relationship of the diameter d≤2h of the roller 102 is made,

The clearance between the roller guide groove 111 and the roller 102 is enlarged by releasing the roller 102 diameter 1/2 or more to the outer circumference of the roller guide groove 111 of the rotor 110.

In the example of FIG. 4, when the rotation of the rotor 110 is reversed in the clockwise direction, the rollers 102 at two positions of the second hydraulic chamber ② and the fourth hydraulic chamber ④ of the hydraulic pump are cam rings 101. Since the oil is pressurized as described above by reducing the eccentricity of), the oil pressure is generated and the oil pressure is drawn to the suction windows 132 and 134, while the first oil pressure chamber ① and the third oil pressure are derived. In the seal ③, oil is sucked from the two discharge windows 131 and 133 of the inner side plate 130 by the eccentricity extending between the cam ring 101 and the rotor 110.

5 is a view illustrating the hydraulic motor cartridge 200 on the line AA ′ of FIG. 1, wherein the main body of the reducer 10 has a rectangular inner cylindrical shape and a balanced cam ring 201 having a left-right symmetry. The inner and outer plates (not shown) are tightly fixed to the inner wall of the rectangular cylinder, and the rota 210 is installed inside the cam ring 201, and the rota 210 is attached to FIGS. 3, 11, and 13. As illustrated, the roller guide groove 211 formed to be curved toward the center from the outer circumference of the rota 210 is formed to penetrate in the axial direction, and the roller guide groove 211 of the rota 210 is burnt in the spring. The cylindrical roller 202, which receives the force, is housed in the cam ring 201 and has a structure in which the outflow passage 213 is attached to the left wall of the roller guide groove 211 of the rotor 210. It is formed as shown in the example of the 13 to 13 to the drain of the oil and supply of hydraulic pressure.

When the hydraulic motor is supplied with hydraulic pressure from the supply window 231 of the inner plate to the roller guide groove 211 communicating with the axial direction of the rotor 210, as illustrated in detail in FIG. The hydraulic pressure acts on the lower portion of the roller 202 of the roller guide groove 211 to act as a compaction force on the cam ring 201 and at the same time the outflow path 213 formed by the rota roller guide groove 211. Since the hydraulic pressure is supplied to the outer circumference of the rotor 210 and the inner wall of the cam ring 201 to pressurize the cylindrical roller 202, the roller 202 by the amount of eccentricity generated between the rotor 210 and the cam ring 201. Is rotated by the cam ring 201 to rotate the rotor in a clockwise direction under the action of hydraulic pressure.

When the rotor 210 rotates by the action of hydraulic pressure, the roller 202 is rotated in the opposite direction of rotation of the rotor 210 while being supported in close contact with the cam ring 201 by the elastic force of the spring 212 and the pressure of the hydraulic pressure. Therefore, the contact frictional resistance between the roller 202 and the inner wall of the cam ring 201 due to the rotation of the rotor 210 is greatly reduced, and also the roller always keeps the roller guide groove 211 of the rotor 210 under the action of hydraulic pressure. Since the roller 202 is rolled around the roller guide groove 211 from the center of the rotor 210 toward the cam ring 201 while rotating according to the rotation of the rotor 210 while being closely supported by the line contact with the right wall, the roller While leakage of hydraulic pressure is blocked to the right side wall of the guide groove 211, foreign matter is removed between the roller 202 and the wall of the roller guide groove 211 of the rotor 201 when the foreign matter invades by the rotation of the roller 202 described above. And the escape of foreign matter into the outflow passage 213 of the left wall of the roller guide groove 211 In the vane motor during intrusion of the foreign matter by the contact surface of the vane it is made as action that can significantly reduce the damage caused is greater.

On the other hand, when the roller 202 is located inside the ⓔ, ⓕ, ⓖ, and ⓗ points of the cam ring 201 as shown in the example of FIG. 3, the cam ring 201 is located at the ⓔ, ⓕ, ⓖ points of the cam ring. The hydraulic pressure is applied to the entire circumference of the roller 202, so that the roller 202 is pressed against the cam ring 201 by the spring force of the spring 212, and the roller 202 is positioned near the point ⓗ, the vertex of the cam ring 201. At this time, since the hydraulic pressure acts on the lower side of the roller 202 and the left side of the roller 202, the roller 202 is pressed against the cam ring 201 by the elastic force of the spring 212 and the pressure of the hydraulic pressure. The spring 212 elasticity may be about the minimum elasticity force that rolls up the roller 202 with the cam ring 201 in a no load state.

The first hydraulic chamber (⑤) and the third hydraulic chamber through the two supply windows 231, 233 formed of the inner plate of the hydraulic motor, as illustrated in detail in FIG. (⑦) When the hydraulic pressure acts on each of the roller guide groove 211 of the rotor (201) while the hydraulic pressure acts on the lower portion of the roller 202 acting the pressing force of the roller 202 to the cam ring (201) Since the hydraulic pressure is supplied to the outer circumference of the rotor 210 and the inner wall of the cam ring 201 through the simultaneous inflow and outflow path 213 and pressurizes the cylindrical roller 202, it is generated between the rotor 210 and the cam ring 201. The roller 202 is pressed against the cam ring 201 by the amount of eccentricity that has been set to rotate the rotor 210 in a clockwise direction under the action of hydraulic pressure.

The eccentricity is reduced between the rotor 210 and the cam ring 201 in the second hydraulic chamber ⑥ and the fourth hydraulic chamber ⑧ of the hydraulic motor by the clockwise rotation of the rotor 210. As an example of the hydraulic discharge operation of the pump, the oil is drained into two drain windows 232 and 234 of the hydraulic motor inner plate.

When the hydraulic pressure acts on each of the second hydraulic chamber ⑥ and the fourth hydraulic chamber ⑧ through two drain windows 232 and 234 formed by the inner plate of the hydraulic motor, the roller guide of the rotor 210 is operated. As the hydraulic pressure is supplied to the groove 211, the hydraulic pressure acts on the lower portion of the roller 202 to act as a pressure force on the roller 202 to the cam ring 201, and the hydraulic pressure is rotated through the simultaneous inflow and outflow path 213. Since the roller 202 is supplied to the outer circumference of the cam ring and the inner wall of the cam ring 201 to press the circular roller 202, the roller 202 is pressed into the cam ring 201 by the amount of eccentricity generated between the rotor 210 and the cam ring 201. Rota 210 rotates counterclockwise under the action of hydraulic pressure.

In the counterclockwise rotation of the rotor 210, the eccentricity is reduced between the rotor 210 and the cam ring 201 in the first hydraulic chamber ⑤ and the third hydraulic chamber ⑦ of the hydraulic motor. As an example of the hydraulic discharge operation process of the hydraulic pump, the oil is drained into two supply windows 231 and 233 of the hydraulic motor inner plate.

On the other hand, since the one-turn elimination volume (discharge amount) of the hydraulic pump is a balanced hydraulic pump, if the diameter of the rotor is D, the width of the rotor is W, and the eccentricity between the rotor and the cam ring is e,

The exclusion volume Q = 4πDeW,

In addition, the 1-turn elimination volume Q = 4πDeW of the balanced hydraulic motor,

Rotameter diameter Dcm of the hydraulic pump, width Wcm of the rotor, eccentricity ecm

Rotor diameter D'cm of hydraulic motor, width W'cm of rotor, and eccentricity e'cm

The rejection volume ratio N between the hydraulic pump and the hydraulic motor is

N = (Exclusion volume of hydraulic motor) ÷ (Exclusion volume of hydraulic pump)

N = (4π × D'cm × e'cm × W'cm = 4πD'e'W'cm 3)

÷ (4π × Dcm × ecm × Wcm = 4πDeW cm)

The exclusion volume ratio between the hydraulic pump and the hydraulic motor is represented by a three-dimensional formula of (D'e'W'cm 3) = (DeW cm 3), so the reduction ratio between the input shaft of the hydraulic pump and the output shaft of the hydraulic motor is three-dimensional. .

Since the volume reduction gear of the present invention is represented by the one-turn elimination volume (volume) of the hydraulic pump and the hydraulic motor, the speed reduction is performed by three elements: (diameter of the rotor), (width of the rotor), and (eccentricity).

Therefore, the volume reducer can perform a high rate of deceleration by three factors that determine the reduction ratio.

FIG. 7 illustrates the relationship between oil suction and drain, hydraulic discharge, and supply of the hydraulic pump inner plate 130 and the hydraulic motor inner plate 230 on the line C-C 'of FIG.

The inner side plate 130 of the hydraulic pump and the inner side plate 230 of the hydraulic motor are provided with the suction window 132 of the hydraulic pump with the separator 20 of the reducer main body interposed therebetween as shown in FIGS. 1 and 6 of the accompanying drawings. , 134 and the drain windows 232 and 234 of the hydraulic motor correspond to each other, and the discharge windows 121 and 133 of the hydraulic pump and the supply windows 231 and 233 of the hydraulic motor mutually correspond to each other. Since it is configured in a corresponding relationship, the integrated oil is sucked and drained from the suction windows 132 and 134 of the hydraulic pump to the drain windows 232 and 234 of the hydraulic motor. The drain resistance can be greatly reduced, and the hydraulic pressure can be supplied while discharging the integrated hydraulic pressure from the discharge windows 131 and 133 of the hydraulic pump to the supply windows 231 and 233 of the hydraulic motor. The discharge resistance is greatly reduced.

The rotation of the hydraulic pump is reversed to suck oil from the discharge windows 131 and 133 of the hydraulic pump, and the hydraulic pressure is discharged from the suction windows 132 and 134 to drain the hydraulic windows 232 and 234. ) Is supplied to the hydraulic pressure and the rotational direction of the hydraulic motor in which oil is drained to the supply windows 231 and 233 of the hydraulic motor is reversed.

8 is a separator of the supply windows 231 and 233 and the drain windows 232 and 234 of the hydraulic motor inner plate 230 on the line D-D 'of FIG. (20) A diagram illustrating the relationship between the supply guide flow passages 21, 23 and the drain guide flow passages 22, 24, wherein the supply guide flow passages 21 are formed in the separator of the main body of the reducer 10 indicated by a dotted line. , 23 and drain guide passages 22 and 24 form four independent guide passages corresponding to the supply windows 231 and 233 and the drain windows 232 and 234 of the hydraulic motor. The guide passage 21 of the separator 20 is configured to be larger than an area of the supply windows 231, 233 and the drain windows 232, 234 of the hydraulic motor inner plate 230. The supply windows 231, 233 and the drain windows 232, 234 formed on the inner plate 230 of the hydraulic motor while smoothing the supply and drain of the hydraulic pressure at the 22, 23, and 24, respectively. Hydraulic action by inducing the hydraulic action area to the outer surface of the inner plate 230 subtracting the area of Areas of the guide passages 21, 22, 23, and 24 of the separating body 20 so that the inner plate 230 of the hydraulic motor is in constant contact with the axial direction of the cam ring 201 of the hydraulic motor. This is determined.

Also in the hydraulic pump, the guide passages 25, 26, 27, and 27 of the body 20 of the reducer main body so that the above-described inner plate 130 of the hydraulic pump is held in constant contact with the cam ring 101 in the axial direction. 28) Area is determined.

9 is a diagram illustrating the separator 20 of the reducer body on the line E-E 'of FIG.

Drain guide flow paths 22, 24 and supply guide flow paths of the hydraulic motor corresponding to the suction guide flow paths 26 and 28 and the discharge guide flow paths 25 and 27 of the hydraulic pump shown by a dotted line. ), 23 are communicated with each other by a plurality of communication paths 29a, 29b, 29c, 29d, so that oil suction and oil drain, hydraulic discharge and hydraulic pressure between the hydraulic pump and the hydraulic motor The supply of is done integrally.

Meanwhile, flow paths 51 and 61 communicating with the outside of the reducer 10 main body are formed at each of the hydraulic motor drain guide flow path 24 and the supply guide flow path 21 of the separator 20. The reducer illustrated in FIG. 1 of the accompanying drawings through the bypass line 70 is provided with discharge hydraulic valves 50 and 60 of the pilot hydraulic type in each of the flow paths 51 and 61 outside the reducer body. (10) The oil is drained to the oil filter 80 arranged on the hydraulic pump side of the main body.

The hydraulic motor is supplied to the hydraulic motor supply guide passage 21 of the separator 20 and the discharge check valve 50 is opened by the pilot hydraulic pressure through the oil passage 61 so that the hydraulic motor drain guide passage of the separator 20 is opened. A part of the oil drained through the 24 is heat-exchanged with the outside of the reducer through the flow path 51 and the bypass line 70 and is drained to the oil filter 80 described above.

Since the rotation of the hydraulic motor is reversed and the output shaft of the reducer 10 also rotates in the reverse direction, when the hydraulic pressure is acted on the hydraulic motor drain guide passage 24 of the separator 20, the pilot hydraulic pressure is passed through the flow path 51. Another discharge check valve 60 is opened so that a part of the oil is drained from the supply guide flow passage 21 to the flow passage 61 and the bypass line 70.

On the other hand, at the lower edge of the separator 20 of the reducer body, flow ports 11 and 12 through which oil flows to the outer plate of the hydraulic pump and the outer plate of the hydraulic motor are perforated.

10 is a diagram illustrating a relationship between the pressurizer 31 and the oil filter 80 that pressurize the outer plate 120 of the hydraulic pump on the line F-F 'of FIG.

The outer plate 120 of the hydraulic pump is rectangular and tightly fixed to the supports 92, 93 and 94 of the inner wall of the reducer main body, and the press body of the reducer right cover 30 illustrated in FIG. 31 is pressurized fixed to the outer plate 120 of the hydraulic pump, the pressurizing body 31 is formed in a cylindrical shape consisting of a space inside the square as shown in the example of Figure 10 attached to the hydraulic pump outer plate ( The outer surface of the 120 is fixed by pressure, and the inlet 32 is drilled to the right side of the press body 31 so that the oil filter 80 is installed in close contact with the inside of the hydraulic pump outer plate 120. Intake guide 123 and the outlet guide 124 is indicated by a dotted line is formed as a groove as shown in the example of Figure 6 attached to the suction check valve 121 is in communication with the outside of the outer plate 120 of the hydraulic pump (122) is installed.

When the hydraulic pump rotates, since the suction pressure is always applied to any one of the outer plate 120, the suction check valves 121 and 122 of the hydraulic pump, the oil is sucked through the suction check valve 122 described above. While foreign substances of oil are removed by the oil filter 80 while the oil is sucked into the inlet 32 of the pressurizer 31, the suction check valve 121 and the other suction check valve 121 are provided. Since hydraulic pressure is applied, another suction check valve 121 is blocked.

When the rotation direction of the hydraulic pump is reversed, the functions of the two suction check valves 121 and 122 described above are reversed to always suck some oil into the oil filter 80.

11 is a diagram illustrating a rotary rotor 210 along the line G-G 'of FIG.

The roller guide groove 211 through which the cylindrical roller 202 as shown in FIG. 12 can enter and exit is formed through the axial direction so as to be bent into the groove from the outer periphery of the rotor toward the center, and the rotor 210 The guide flow path 213, 214 of the groove through which the fluid as shown in the example of FIG. 13 attached to the wall of the roller guide groove 211 is formed to be curved, and also the roller guide groove 211 of the rotor 210 Grooves 215 and 216 for mounting the springs 212 and 217 to the bottom are formed.

14 is a view illustrating an operation relationship between a hydraulic pump and a hydraulic motor of the speed reducer.

When the input shaft of the balanced hydraulic pump rotates counterclockwise, in the second hydraulic chamber (②) and the fourth hydraulic chamber (④) of the two hydraulic pumps, the eccentricity between the rotor 110 and the inner wall of the cam ring 101 increases. While the volume is expanded and the oil is sucked, the volume is reduced in the first hydraulic chamber (①) and the third hydraulic chamber (③) of the two hydraulic pumps in accordance with the reduction of the eccentricity of the rotor 110 and the cam ring 101 to reduce the hydraulic pressure. Is generated.

The hydraulic pressure acts on the first hydraulic chamber (⑤) and the third hydraulic chamber (⑦) of the two hydraulic motors by the two communication paths 29a and 29c, so that the rotor 210 and the cam ring of the hydraulic motor are operated. The rotor 210 is rotated in the clockwise direction which is the eccentric enlargement direction between the 201, and the second hydraulic chamber ⑥ and the fourth hydraulic chamber of the two hydraulic motors are rotated by the clockwise rotation of the rotor 210 of the hydraulic motor. ⑧), the volume is reduced in accordance with the reduction of the eccentricity of the rotor 210 and the cam ring 201, the oil drain action to pressurize the oil is made by the two hydraulic passages (29b, 29d) of the hydraulic pump described above It is sucked into two 2nd hydraulic chamber (2) and a 4th hydraulic chamber (4).

In accordance with the rotation of the reducer input shaft, the direction of rotation of the hydraulic pump and the direction of rotation of the hydraulic motor reverse each other.

The pilot type suction check valve 50 is opened by the hydraulic pressure of the communication path 29a generated in the first hydraulic chamber ① of the hydraulic pump and drained to the communication path 29d of the hydraulic motor fourth hydraulic chamber ⑧. A part of the oil to be drained to the flow path 51 and the bypass line 70 is exchanged with the outside air and is sucked through the fourth hydraulic chamber ④ suction check valve 122 of the hydraulic pump via the oil filter 80. .

The ratio of the amount of oil generated by one revolution of the balanced hydraulic pump input shaft and the amount of oil consumed by one revolution of the balanced hydraulic motor output shaft becomes the rotation ratio between the input shaft and the output shaft of the reducer. If the motor's one-turn elimination capacity is increased, the reduction ratio is established between the input shaft and the output shaft of the reducer.

The one-turn elimination capacity of the balanced hydraulic pump and hydraulic motor

D is the diameter of the rotor, W is the width of the rotor, and e is the amount of eccentricity between the rotor and cam ring.

The exclusion volume Q = 4πDeW,

Rotameter diameter D = 7cm of the hydraulic pump, width W = 1.5cm of the rotor, eccentricity e = 0.3cm

If the rotor diameter D = 20cm, the rotor width W = 10cm, and the eccentricity e = 0.8cm, the rejection volume ratio N between the hydraulic pump and the hydraulic motor is

N = (Exclusion volume of hydraulic motor) ÷ (Exclusion volume of hydraulic pump)

N = (4π × 20cm × 10cm × 0.8cm = 2009.6 cm 3)

÷ (4π × 7cm × 1.5cm × 0.3cm = 39.5cm) = 50.7

From the above equation, the ratio of exclusion volume between the hydraulic pump and the hydraulic motor is 50.7, so the reduction ratio between the input shaft of the hydraulic pump and the output shaft of the hydraulic motor is 50.7.

Since the three-dimensional reducer of the present invention is represented by the one-turn elimination volume (volume) of the hydraulic pump and the hydraulic motor, the deceleration is performed by three elements: (diameter of the rotor), (width of the rotor), and (eccentricity). The speed reducer of high speed is achieved by three factors that determine the reduction ratio.

Since the input shaft load of the reducer is made symmetrically in many areas in the first hydraulic chamber (①) and the third hydraulic chamber (③) of two hydraulic pumps, the load ratio of the reducer input shaft is greatly reduced, and Since the output shaft load is made symmetrically in many areas in the first hydraulic chamber ⑤ and the third hydraulic chamber ⑦ of the two hydraulic motors, the output shaft single load ratio of the reducer is greatly reduced.

Hydraulic pumps and hydraulic motors are generally 9 to 17 cylindrical rollers that enter and exit the roller guide groove of the rota due to the eccentricity of the rotor and cam ring, and are connected to the inner wall of the cam ring and the guide groove wall of the rotor. It is rotated by the rotation of the rotor while making contact, so it is not affected by foreign matters. Only the roller can be replaced if necessary.

Figure 15 illustrates another operation relationship between the hydraulic pump and the hydraulic motor of the reducer,

When the input shaft of the balanced hydraulic pump rotates in the clockwise direction, in the first hydraulic chamber (①) and the third hydraulic chamber (③) of the two hydraulic pumps, the volume is reduced according to the eccentric expansion of the rotor 110 and the cam ring 101. While the oil is sucked to expand, the volume is reduced in the second hydraulic chamber (②) and the fourth hydraulic chamber (④) of the two hydraulic pumps in accordance with the reduction of the eccentricity of the rotor 110 and the cam ring 101 to generate the hydraulic pressure Discharged.

Since the hydraulic pressure acts as the 2nd operating chamber (6) and the 4th hydraulic chamber (8) of two hydraulic motors by the two communication paths (29b) and (29d), the rotor 210 and cam ring of a hydraulic motor The rotor 210 is rotated in the counterclockwise direction, which is the eccentric enlargement direction between the 201, and the first hydraulic chamber ⑤ and the third hydraulic pressure at the two hydraulic motors are rotated by the counterclockwise rotation of the rotor 210 of the hydraulic motor. In the seal (⑦), the volume is reduced in accordance with the reduction in the eccentricity of the rotor 210 and the cam ring 201, and an oil drain action is performed to pressurize the oil. Thus, the oil is described by the two communication paths 29a and 29c. It is suctioned into the 2nd hydraulic chamber (2) and the 4th hydraulic chamber (4) of two hydraulic pumps.

In accordance with the rotation of the reducer input shaft, the direction of rotation of the hydraulic pump and the direction of rotation of the hydraulic motor reverse each other.

The pilot type suction check valve 60 is opened by the hydraulic pressure of the communication path 29d generated in the fourth hydraulic chamber ④ of the hydraulic pump and drained from the hydraulic motor first hydraulic chamber ⑤ to the communication path 29a. A part of the oil to be drained to the flow path 61 and the bypass line 70 is sucked through the suction check valve 121 through the oil filter to the third hydraulic chamber (③) of the hydraulic pump.

As described in detail in the hydraulic pump cartridge 100 and the cartridge 200 of the hydraulic motor, as illustrated in FIG. 1 of the accompanying drawings, the rotor 110 of the hydraulic pump has a roller 102 on the inner wall of the cam ring 101. It is supported by the bearing on both sides while receiving the rotation is made as a minimum gap between the inner plate 130 and the outer plate 120, the rotor 110 is rotated by the drive of the input shaft 103 to rotate the rotor ( As the volume changes between the rotor 110 and the cam ring 101 according to the rotation of the 110, the oil is sucked in two places of the equilibrium type and the hydraulic pressure is generated and discharged in two places to connect the communication path of the separator 20. Since the hydraulic pressure is supplied to the hydraulic motor through the hydraulic pump, the discharge resistance of the hydraulic pressure is greatly reduced between the hydraulic pump and the hydraulic motor.

Rotor 210 of the hydraulic motor is supported by the bearings on both sides while receiving the roller on the inner wall of the cam ring 201 is rotated as a minimum gap between the inner plate 230 and the outer plate 220, The hydraulic pressure is applied at two places where the volume change between the 210 and the cam ring 201 is made, and the rotor 210 is rotated, and the volume of the rotor 210 and the cam ring 201 is changed by the rotation of the rotor 210. Since the oil is pressurized at two places to drain the integrated oil through the communication path of the separator 20, the oil drain resistance of the hydraulic motor and the suction resistance of the hydraulic pump are greatly reduced.

When the input shaft 103 of the reducer is rotated so that the rotor 110 of the hydraulic pump is rotated, the rotor 102 rotates to the inner wall of the cam ring 101, which is a fixed body, and the roller 102 rotates according to the amount of eccentricity of the cam ring 101. Since the entry and exit changes, the oil suction action is performed in two balanced hydraulic pumps and the two suction windows formed by the inner plate 130 of the hydraulic pump through two communication paths of the separator 20 are used. In addition to the suction action, the hydraulic pressure is generated in two hydraulic pumps.

When the hydraulic pressure is generated at two hydraulic pumps, the hydraulic pressure is discharged to the discharge windows of the two hydraulic pumps, and the hydraulic motor 2 is supplied through the two communication paths of the separator 20 and the supply windows of the two inner plates 230 of the hydraulic motor. Hydraulic action is applied to the rota 210, the cam ring 201 and the roller 202 at the position, and the hydraulic motor is rotated in the direction opposite to the rotation of the input shaft of the reducer. The oil is drained by the action of reducing the volume between the rotor 210 and the cam ring 201, and the oil is drained into the drain windows of the two places of the hydraulic motor inner plate 230 so that two of the separators 20 The suction of the oil is made to the location communication path and the suction window of the two places of the hydraulic pump inner plate (130).

Some of the oil drained into the drain window of the hydraulic motor is bypassed to the bypass line 70 by the pilot type discharge check valves 50 and 60 to exchange heat with the outside air, passing through the oil filter 80 and passing through the hydraulic pump. It is sucked by the hydraulic pump through the suction check valve 122 provided to the outer plate (120).

The hydraulic pressure acts on the groove of the discharge guide path of the separator 20 of the reducer to pressurize the inner plate 130 to the cam ring 101 from the outside of the inner plate 130 of the hydraulic pump and to maintain the pressure of the reducer. (20) Since the hydraulic pressure acts on the groove of the supply guide, the inner plate 230 is constantly pressed against the cam ring 201 at the outer side of the inner plate 230 of the hydraulic motor, so that the cam rings 101, 201 and the rota The minimum clearance between the 110 and 210 and the two inner and outer plates 120, 130, 220, and 230 reduces hydraulic leakage.

Since the oil is filled in the main body of the reducer 10 by the oil rings 34 and 44 which prevent the leakage of oil to the input shaft 103 and the output shaft 203, the input shaft of the reducer 10 Bearing lubrication of the output shaft consists of hydraulic oil.

The volumetric reducer includes a three-dimensional gearbox in which the rotational ratio of the input shaft and the output shaft is increased by increasing the one-turn elimination volume of the hydraulic pump rather than the exclusion volume of the hydraulic motor.

The three-dimensional reducer is a volumetric power transmission method in which the operating force and the load force are generated by the pressure of the liquid between the input shaft and the output shaft as described in detail in the configuration and operation of the invention.

The rotational reduction ratio between the input shaft and the output shaft is very large in three dimensions, and the rotating rollers of about 9-17 sheets are driven by hydraulic action instead of many gears that require precision machining by the hydraulic pump cartridge and hydraulic motor cartridge that form the reduction gear. Since the driving resistance of the reducer is small because of the method of delivering, the configuration of the reducer is simple, and only the rotating roller can be replaced if necessary.

The hydraulic pump cartridge and the hydraulic motor cartridge are connected to each other by a short communication path of the separate body in the reducer body, and the discharge and supply of hydraulic pressure and the drain and suction of oil are integrated, so that a complicated valve system is omitted. It is a three-dimensional reducer that achieves high efficiency, and the three-dimensional reducer has excellent load adaptability on the output shaft, and because of the balanced hydraulic pump and hydraulic motor type, the one-load rate is greatly reduced, which reduces the load on the bearing side of the reducer input / output shaft. do.

Claims (5)

The hydraulic pump cartridge and the hydraulic motor cartridge in the reducer body are configured as series independent shafts at both ends of the separator while sharing one separator; A discharge guide flow path and a suction guide flow path through which the hydraulic discharge and the oil suction of the hydraulic pump are formed at one end of the separator are formed as grooves, and the hydraulic supply guide flow path and the drain guide flow path of the hydraulic motor are formed at the other end of the separator. Grooves formed to correspond to the discharge guide passage and the suction guide passage of the hydraulic pump, respectively; A plurality of communication paths for connecting the discharge guide flow path and the supply guide flow path of the hydraulic pump and the hydraulic motor, the drain guide flow path and the suction guide flow path to each of the separators; The discharge pump and the suction window, the supply window and the drain window corresponding to the discharge guide flow path and the suction guide flow path, the supply guide flow path and the drain guide flow path, respectively, are separated into the hydraulic pump and the hydraulic motor inner plate. A hydraulic action is performed at the same time as the discharge action and the hydraulic motor, and a hydraulic drain is performed at the hydraulic motor and a hydraulic pressure is sucked at the simultaneous hydraulic pump; A press body protrudes inside the right side cover of the reducer body such that a hydraulic pump cartridge is press-fixed between the separator and the press body; A press body is formed to protrude inside the left side cover of the reducer main body so that a hydraulic motor cartridge is press-fixed between the separator and the press body; Bearing mounting recesses are formed at each end of the separator in the reducer body, and bearing members are formed on the left and right covers of the reducer body to discharge the hydraulic pressure by driving the input shaft of the hydraulic pump and simultaneously to drive the hydraulic motor. Reducer, characterized in that the drive shaft of the hydraulic motor is interlocked. The method of claim 1 An inner plate in which the discharge window and the suction window of the hydraulic pump cartridge are perforated on the separator of the reducer main body, a cam ring composed of two equilibrium eccentrics, and the outer plate are sequentially arranged to be tightly fixed by the pressing body of the reducer right cover. ; The roller guide groove which is formed to be bent into the groove from the outer periphery of the rotor to the center by the cam ring inner wall of the hydraulic pump cartridge penetrates in the axial direction and receives the cylindrical roller in the axial direction, and the shaft in the roller guide groove of the rotor. The roller accommodated in the direction is spaced apart as the smallest gap between the inner plate and the outer plate, and the shaft of the hydraulic pump rotor is supported by the bearing of the separator and the right cover so that the rotation of the rotor between the inner plate and the outer plate is prevented. Done; The discharge window and the suction window of the inner plate communicate with an end portion in the axial direction of the roller guide groove of the rotor so that the hydraulic discharge and the suction of the oil are formed on the lower portion of the roller accommodated in the rotor roller guide groove; And an outflow path through which the fluid flows in and out of the roller guide groove wall of the rotary rotor, wherein the fluid flows in and out of the inner wall of the cam ring and the outer space of the rotor through the outflow path. The method of claim 2 A reducer having a feature in that a roller is pressed against the inner wall of a cam ring by a spring force in a rota roller guide groove of a hydraulic pump cartridge, and the diameter of the roller is larger than 11/5 of the maximum eccentricity between the rota and the cam ring. The method of claim 1, An inner plate in which the supply window and the suction window of the hydraulic motor cartridge are perforated on the separator of the reducer main body, a cam ring composed of two equilibrium eccentrics, and the outer plate are sequentially arranged to be tightly fixed by the pressing body of the reducer left cover. ; The roller guide groove which is formed to be bent into the groove from the outer circumference of the rotor to the center by the cam ring inner wall of the hydraulic motor cartridge penetrates in the axial direction and receives the cylindrical roller in the axial direction, and the axial direction in the roller guide arc of the rotor. The roller accommodated in the roller is spaced apart from the inner plate and the outer plate as a minimum gap, and the rotor shaft of the hydraulic motor is supported by the bearing of the separator and the left cover to rotate the rotor between the inner plate and the outer plate. With; The supply window and the drain window of the inner plate communicate with an end portion in the axial direction of the roller guide groove of the rotor so that the hydraulic supply and the drain of the oil are formed in the lower portion of the roller accommodated in the rotor roller guide groove; And a flow inlet and outflow path through which the fluid flows in and out of the roller guide groove wall of the rotary rotor, and the fluid flows in and out of the inner wall of the cam ring and the outer circumferential space of the rotor through the outflow path. The method of claim 1, A flow path communicating with the outside of the reducer main body is formed in each of the separate hydraulic supply guide and drain guide paths of the reducer main body, and a pilot discharge check valve is installed, and each bypass check valve outlet contacts the outside air. A part of the oil drained from the hydraulic motor to the outside of the pressurized body of the reducer right cover to communicate with the drain; An inlet is drilled to one surface of the pressurizing body projecting into the right side cover of the reducer so that an oil filter is installed outside the inlet of the pressurizing body; An outflow guide and an inflow guide are formed in the inner side of the outer plate of the hydraulic pump cartridge, and an intake check valve communicating with the outflow guide and the inlet guide is provided on the outer side of the outer plate, respectively, to drive the hydraulic pump. A reducer, characterized in that part of the fluid suction consists of a suction check valve.