JP4532250B2 - Hydraulic motor with reduction gear - Google Patents

Description

  The present invention relates to a hydraulic motor with a speed reducer that is preferably used in a traveling device, a turning device, and the like that are installed in a construction machine such as a hydraulic excavator.

  In general, a construction machine such as a hydraulic excavator is roughly constituted by a lower traveling body that can be self-propelled and an upper revolving body that is rotatably mounted on the lower traveling body. In general, a hydraulic motor with a speed reducer is used for a traveling device for traveling the lower traveling body and a turning device for turning the upper revolving body on the lower traveling body.

  Here, a hydraulic motor with a speed reducer according to this type of conventional technology is generally composed of a hydraulic motor that is rotated by pressure oil from a hydraulic power source and a speed reducer that decelerates the rotation of the hydraulic motor (for example, , See Patent Document 1).

Japanese Patent Laid-Open No. 10-9118

  And the hydraulic motor with a reduction gear by patent document 1 has a communicating path which connects between the motor chamber formed in the casing, and the reduction gear chamber, and the hydraulic oil which leaked from the motor chamber at the time of the action | operation of a hydraulic motor A part (leak oil) is configured to be supplied to the reduction gear chamber through the communication path.

  Thus, leakage oil from the hydraulic motor is used to lubricate and cool the speed reducer, and wear powder generated by the meshing of the gears constituting the speed reducer can be discharged to the outside using the lubricating oil. .

  On the other hand, other conventional hydraulic motors with reduction gears are provided with an inflow port and an outflow port that open to the reduction gear chamber, and supply the pressure oil discharged from the charge pump to the reduction gear chamber through the inflow port. By discharging to the tank through the service port, the speed reduction mechanism is lubricated, cooled, etc. (see, for example, Patent Document 2).

JP 2000-161195 A

  However, the above-described prior art disclosed in Patent Document 1 is configured to lubricate and cool the speed reduction mechanism by supplying leaked oil from the hydraulic motor to the speed reducer room. There is a problem that it is difficult to supply the lubricating oil, and the shortage of the lubricating oil causes premature wear of the speed reduction mechanism, temperature rise, and the like. Further, when the lubricating oil supplied to the speed reducer chamber is insufficient, the wear powder generated by the meshing of the gears constituting the speed reduction mechanism stays in the speed reducer chamber, and this wear powder causes the speed reduction mechanism and the hydraulic pressure to be reduced. There is a problem that the life of the motor is reduced.

  In particular, recent hydraulic motors tend to reduce leakage oil during operation due to improvements in design technology, component accuracy, etc., so it is important to supply sufficient lubricating oil to the reduction gear chamber using this leakage oil. It has become difficult.

  In an environment where the outside air temperature is low, such as in a cold region, it is necessary to circulate the hydraulic oil between the tank and the hydraulic motor to reduce its viscosity by performing a warm-up operation. When leak oil is supplied to the reducer chamber and then returned to the tank, smooth circulation of the hydraulic oil is impeded and its viscosity cannot be reduced quickly. There is a problem that you have to continue.

  On the other hand, the prior art disclosed in Patent Document 2 described above is configured to supply the pressure oil discharged from the charge pump into the reduction gear chamber through an inflow port and an outflow port provided in the motor casing, and thus is connected to the motor casing. There is a problem that the number of hydraulic pipes to be increased increases, resulting in a complicated configuration and an increase in cost.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to provide a hydraulic motor with a speed reducer that can always properly perform lubrication, cooling, and the like for the speed reducer.

The present invention for solving the above problems, a variable displacement hydraulic motor and, the rotatably supported to the hydraulic motor of the motor casing reduction gear casing having a variable displacement mechanism for switching the rotation speed of the output shaft in the motor casing The present invention is applied to a hydraulic motor with a speed reducer comprising a speed reducer in which a speed reduction mechanism for reducing the rotation of the hydraulic motor is disposed .

The feature of the configuration invention of claim 1 is adopted, the motor casing, the lubricating oil introducing passage for introducing into the motor casing part of the tilting hydraulic signal for operating the variable displacement mechanism as lubricating oil A communication passage that communicates between the motor casing of the hydraulic motor and the reduction gear casing of the reduction gear and that supplies the lubricating oil introduced into the motor casing through the lubricating oil introduction passage into the reduction gear casing. The throttle means for restricting the flow rate of the lubricating oil introduced into the motor casing is provided in the middle of the lubricating oil introduction passage.

  According to the second aspect of the present invention, in the middle of the oil passage for supplying the tilting hydraulic signal, the flow rate control is switched between the open position for opening the oil passage and the throttle position for restricting the oil passage according to the tilt position of the capacity variable mechanism. The valve is provided.

  According to a third aspect of the present invention, the tilting hydraulic pressure signal uses pressure oil supplied from a hydraulic pressure source to the variable capacity mechanism.

  According to a fourth aspect of the present invention, there is provided a shuttle valve for selecting a high-pressure side main pipeline among the pair of main pipelines between the pair of main pipelines connecting the hydraulic power source to the hydraulic motor, and the capacity of the shuttle valve and the variable capacity A hydraulic pilot type directional control valve that switches the direction of the pressure oil supplied to the variable capacity mechanism is provided in the middle of the oil passage connecting with the mechanism, and the tilting hydraulic signal is the hydraulic pressure of the directional control valve. The pilot signal supplied to the pilot unit is used.

According to the first aspect of the present invention, a part of the tilting hydraulic signal for operating the variable capacity mechanism is introduced as lubricating oil into the motor casing through the lubricating oil introduction passage, and into the reduction gear casing through the communication passage. By supplying, the reduction gear can be lubricated, cooled, and the like. Therefore, without relying on leak oil from the hydraulic motor, it is possible to always supply sufficient lubricating oil to the reduction gear using the tilting hydraulic signal for operating the variable displacement mechanism, and the reduction gear is always appropriate. Can be lubricated and cooled. In this case, since the throttle means is provided in the middle of the lubricating oil introduction passage, the tilting hydraulic signal can be supplied to the variable capacity mechanism and the motor casing, respectively.

According to the invention of claim 2, when the flow rate control valve is switched to the throttle position and the flow rate of the tilting hydraulic signal is limited, the tilting hydraulic signal is lubricated in the motor casing while the variable displacement mechanism is maintained in the non-operating state. Can be supplied as oil. On the other hand, when the flow control valve is switched to the open position, the displacement variable mechanism can be operated by the tilting hydraulic signal, and a part of the tilting hydraulic signal can be supplied into the motor casing as lubricating oil. Therefore, even when the flow control valve is switched to the throttle position or to the open position, a part of the tilting hydraulic signal can always be supplied into the motor casing as lubricating oil.

According to the invention of claim 3, by introducing a part of the pressure oil for operating the capacity variable mechanism into the motor casing through the lubricating oil introduction passage, the pressure oil is lubricated, cooled, etc. using this pressure oil. Can be performed.

According to the fourth aspect of the present invention, by introducing a part of the pilot signal supplied to the direction control valve to switch the direction of the pressure oil for operating the variable capacity mechanism into the motor casing through the lubricating oil introduction passage. The pilot signal can be used to lubricate and cool the speed reducer.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of a hydraulic motor with a reduction gear according to the present invention will be described in detail with reference to FIGS.

  First, FIG. 1 to FIG. 4 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a hydraulic motor with a reduction gear according to the present embodiment. The hydraulic motor 1 with a reduction gear is a traveling device (not shown) that travels a lower traveling body of a tracked vehicle such as a hydraulic excavator. ). The reduction gear-equipped hydraulic motor 1 is roughly constituted by a hydraulic motor 2 and a reduction gear 18 which will be described later.

  Reference numeral 2 denotes a variable displacement swash plate hydraulic motor. The hydraulic motor 2 includes a motor casing 3, an output shaft 6, a cylinder block 9, a piston 12, a variable displacement mechanism 14 and the like which will be described later. The hydraulic motor 2 rotates the output shaft 6 with pressure oil supplied from a hydraulic pump 34, which will be described later, and changes the rotational speed of the output shaft 6 with the variable capacity mechanism 14.

  Reference numeral 3 denotes a hollow motor casing that forms an outer shell of the hydraulic motor 2. The motor casing 3 is formed in a bottomed cylindrical shape by a cylindrical portion 3A and a bottom portion 3B. The opening end side of the cylindrical portion 3 </ b> A is closed by the lid body 4. An annular flange 3C is integrally formed on the outer peripheral side of the cylindrical portion 3A. The flange 3C is formed by using bolts or the like for a track frame (none of which is shown) constituting the lower traveling body of the excavator. It is fixed.

  On the other hand, on the outer peripheral side of the bottom portion 3B, a shaft spline 3D to which a carrier 33 of a planetary gear reduction mechanism 30 described later is spline-coupled and a male screw 3E to which a nut 23 described later is screwed are formed. A shaft insertion hole 3F through which an output shaft 6 described later is inserted is formed in the center of the bottom 3B.

  Reference numeral 5 denotes a motor chamber provided in the motor casing 3, and the motor chamber 5 is formed on the inner peripheral side of the cylindrical portion 3 </ b> A constituting the motor casing 3 and is closed by a lid 4. In the motor chamber 5, an output shaft 6, a cylinder block 9, a swash plate 15, and the like, which will be described later, are arranged.

  An output shaft 6 is rotatably provided in the motor chamber 5, and one end side of the output shaft 6 is supported by a bearing 7 provided on the lid 4, and the other end side is a shaft insertion hole 3 </ b> F of the motor casing 3. Is supported by a bearing 8 provided on the surface. A shaft portion 27A of a sun gear 27 described later is spline-coupled to the other end side of the output shaft 6.

  Reference numeral 9 denotes a cylinder block located in the motor chamber 5 and provided on the outer peripheral side of the output shaft 6. The cylinder block 9 is splined to the output shaft 6 and rotates integrally with the output shaft 6. . The cylinder block 9 is provided with a plurality of cylinders 10 that are spaced apart in the circumferential direction and extend in the axial direction, and pistons 12 to be described later are slidably fitted into the cylinders 10.

  Reference numeral 11 denotes a valve plate that is positioned between the lid 4 and the cylinder block 9 and is attached to the lid 4. The valve plate 11 is a pair of supply / discharge valves that intermittently communicate with the cylinders 10 of the cylinder block 9. It has a port 11A. Each supply / discharge port 11 </ b> A communicates with a pair of supply / discharge passages 4 </ b> A formed in the lid 4.

  A plurality of pistons 12 are inserted into the cylinders 10 of the cylinder block 9 so as to be slidable in the axial direction. The pistons 12 reciprocate in the cylinders 10 by the rotation of the cylinder block 9. .

  Reference numeral 13 denotes a disk-like shoe that is swingably provided on the tip side (projecting end side) of each piston 12, and each shoe 13 is pressed against the surface of a swash plate 15 described later by the piston 12. As the cylinder block 9 rotates, it slides on the swash plate 15 so as to draw an annular locus.

  Reference numeral 14 denotes a variable capacity mechanism provided in the motor casing 3, and the variable capacity mechanism 14 includes a swash plate 15, a tilt actuator 16, and the like which will be described later. The capacity variable mechanism 14 adjusts the capacity of the pressure oil supplied into each cylinder 10 of the cylinder block 9 by changing the tilt angle of the swash plate 15 by the tilt actuator 16, and The speed and output torque are changed.

  Reference numeral 15 denotes a swash plate that is positioned on the protruding end side of each piston 12 and is tiltable in the motor chamber 5. The swash plate 15 is formed in a disc shape surrounding the output shaft 6. The rear surface side of the swash plate 15 is tiltably supported by the bottom portion 3B of the motor casing 3, and the front surface side of the swash plate 15 is such that each shoe 13 draws an annular locus as the cylinder block 9 rotates. It is a sliding surface that slides.

  Here, the swash plate 15 always holds the large tilt position shown in FIG. 2 by the resultant force (pressing force) of the pressing force acting from each piston 12 and is pressed by the tilt actuator 16 described later. It tilts to the small tilt position shown in FIG. In this case, when the swash plate 15 is in the large tilt position (position in FIG. 2), the output shaft 6 rotates at a low speed with high torque due to an increase in the stroke amount of the piston 12, and the swash plate 15 is in the small tilt position. When in the (position of FIG. 3), the output shaft 6 is configured to rotate at a high speed with a low torque as the stroke amount of the piston 12 decreases.

  Reference numeral 16 denotes a tilting actuator that constitutes the variable capacity mechanism 14 together with the swash plate 15, and the tilting actuator 16 is separated from the output shaft 6 in the radial direction, as shown in FIGS. 2 and 3, and the bottom of the motor casing 3. The bottomed tilting cylinder 16A drilled in 3B and the tilting piston 16B whose base end side is slidably fitted into the tilting cylinder 16A and whose distal end abuts against the back surface of the swash plate 15 are configured. Yes. Then, the tilting actuator 16 causes the tilting piston 16B to press the back side of the swash plate 15 according to the pressure oil supplied into the tilting cylinder 16A. The rotation speed of the output shaft 6 is changed by tilting between the rotation positions.

  Reference numeral 17 denotes a tilting oil passage provided in the motor casing 3, and the tilting oil passage 17 supplies pressure oil as a tilting pressure oil signal to the tilting cylinder 16A. Here, the tip end side of the tilting oil passage 17 opens to the bottom side of the tilting cylinder 16A, and the base end side of the tilting oil passage 17 is connected to a hydraulic pump 34 described later. A part of the pressure oil discharged from the hydraulic pump 34 is supplied to the tilting cylinder 16A through the tilting oil passage 17 as tilting pressure oil (tilting pressure oil signal). .

  Reference numeral 18 denotes a speed reducer integrally attached to the hydraulic motor 2, and the speed reducer 18 decelerates the rotation of the output shaft 6 and outputs a large torque. Here, the speed reducer 18 is roughly constituted by a speed reducer casing 19 to be described later and planetary gear speed reduction mechanisms 26 and 30.

  Reference numeral 19 denotes a reduction gear casing that forms an outer shell of the reduction gear 18. The reduction gear casing 19 includes a stepped cylindrical drum 20 disposed on the outer peripheral side of the motor casing 3, and bolts or the like used for the drum 20. It is constituted by a covered cylindrical ring gear 21 which is fixed and has inner teeth 21A formed on the entire inner circumference side.

  Reference numerals 22 and 22 denote bearings fitted on the outer peripheral side of the motor casing 3, and each of the bearings 22 rotatably supports the drum 20 of the reduction gear casing 19 with respect to the motor casing 3. And the bearing 22 is attached to the motor casing 3 in a retaining state by screwing a nut 23 onto the male screw 3E of the motor casing 3.

  A reduction gear chamber 24 is provided in the reduction gear casing 19. The reduction gear chamber 24 is provided between the cylinder portion 3 </ b> A of the motor casing 3 and the drum 20, and between the bottom portion 3 </ b> B of the motor casing 3 and the ring gear 21. Is formed. In the reduction gear chamber 24, planetary gear reduction mechanisms 26 and 30 to be described later are accommodated.

  Reference numeral 25 denotes a mechanical seal (floating seal) provided between the motor casing 3 and the drum 20 of the speed reducer casing 19. The mechanical seal 25 seals the inside of the speed reducer chamber 24 in a liquid-tight manner. The lubricating oil in 24 is prevented from leaking from the engaging portion between the motor casing 3 and the reduction gear casing 19 to the outside.

  Reference numeral 26 denotes a first-stage planetary gear reduction mechanism disposed in the reduction gear chamber 24. The planetary gear reduction mechanism 26 includes a shaft portion 27A that is spline-coupled to the output shaft 6 of the hydraulic motor 2. A sun gear 27 that rotates integrally with the sun gear 27, a plurality of planetary gears 28 that mesh with the sun gear 27 and the internal teeth 21A of the speed reducer casing 19 (ring gear 21) and revolve around the sun gear 27, and A carrier 29 that rotatably supports each planetary gear 28 is formed.

  A planetary gear reduction mechanism 30 is a second stage planetary gear reduction mechanism. The planetary gear reduction mechanism 30 includes a sun gear 31 meshed with the carrier 29 of the planetary gear reduction mechanism 26, and the sun gear 31 and the internal teeth 21 A of the reduction gear casing 19. And a plurality of planetary gears 32 that revolve while rotating around the sun gear 31 and a carrier 33 that rotatably supports each planetary gear 32. One end side of the carrier 33 in the axial direction is meshed with a shaft spline 3D formed in the motor casing 3.

  The planetary gear reduction mechanisms 26 and 30 reduce the rotation of the hydraulic motor 2 by two stages and transmit it to the reduction gear casing 19 to rotate the reduction gear casing 19 with high torque. In this case, a sprocket (none of which is shown) for driving the crawler belt of the crawler excavator is attached to the drum 20 of the speed reducer casing 19, and the hydraulic excavator is driven by rotating the sprocket to drive the crawler belt. It can be made to run.

  Next, FIG. 4 shows a hydraulic circuit for driving the hydraulic motor 2. In the figure, 34 is a hydraulic pump that constitutes a hydraulic source together with a tank 35. The hydraulic pump 34 is an engine mounted on a hydraulic excavator, etc. Driven by (not shown), the hydraulic oil in the tank 35 is discharged toward the hydraulic motor 2 as high pressure oil.

  Reference numerals 36A and 36B denote a pair of main pipes that connect the hydraulic pump 34 and the tank 35 to the hydraulic motor 2, and a directional control valve 37 is provided in the middle of the main pipes 36A and 36B. The direction control valve 37 switches the direction of the pressure oil supplied and discharged from the hydraulic pump 34 to the hydraulic motor 2 by being switched from the neutral position (A) to the switching position (B) or (C) by an operator or the like. The hydraulic motor 2 is rotated forward or reverse.

  38A and 38B are a pair of check valves provided between the hydraulic motor 2 and the direction control valve 37 and provided in the middle of the main pipelines 36A and 36B, and 39 is in parallel with the check valves 38A and 38B. A counter balance valve provided in the middle of the main pipelines 36A and 36B is shown. The counter balance valve 39 is switched substantially in conjunction with the direction control valve 37 due to the differential pressure between the main pipes 36A and 36B, and is closed during the inertial rotation of the hydraulic motor 2 before and after the hydraulic motor 2. The brake pressure is generated in the main pipeline 36A or the main pipeline 36B.

  40A and 40B are a pair of overload relief valves located between the hydraulic motor 2 and the counter balance valve 39 and provided in the middle of the main pipelines 36A and 36B. The overload relief valves 40A and 40B are hydraulic motors. When the brake pressure generated in the main pipeline 36A or the main pipeline 36B rises to a predetermined set pressure during inertial rotation 2, the valve is opened, and the excess pressure at this time is relieved.

  41 is a flow control valve provided in the middle of the tilting oil passage 17, and the flow control valve 41 is provided with an open position (a) for opening the tilting oil passage 17 by manual operation of an operator, for example, and a tilting oil. The flow is switched to the throttle position (b) for restricting the passage 17 and the flow rate of the pressure oil (inclination hydraulic signal) flowing through the inclination oil passage 17 is controlled.

  Here, when the flow control valve 41 is switched to the throttle position (b), the flow rate of the pressure oil flowing through the tilting oil passage 17 is limited, so that the pressing force acting on the swash plate 15 from the tilting piston 16B is reduced. The swash plate 15 is configured to hold the large tilt position shown in FIG. 2 by the pressing force from each piston 12.

  On the other hand, when the flow rate control valve 41 is switched to the open position (a), the pressure oil flowing through the tilting oil passage 17 is supplied into the tilting cylinder 16A without limiting the flow rate. Thereby, the tilting piston 16B presses the swash plate 15 against the pressing force from each piston 12, and the swash plate 15 is configured to hold the small tilting position shown in FIG.

  When the hydraulic motor 2 is operated, the pressure in the tilting oil passage 17 is the same regardless of whether the flow control valve 41 is switched to the throttle position (b) or the flow control valve 41 is switched to the open position (a). It is always higher than the tank pressure.

  Reference numeral 42 denotes a lubricating oil introduction passage that communicates between the tilting oil passage 17 and the motor chamber 5, and the lubricating oil introduction passage 42 receives a part of the pressure oil (tilting hydraulic signal) flowing through the tilting oil passage 17. It is introduced into the motor chamber 5 as lubricating oil. A throttle valve 43 described later is provided in the middle of the lubricating oil introduction passage 42.

  43 is a throttle valve provided as a throttle means provided in the middle of the lubricating oil introduction passage 42. The throttle valve 43 is formed by, for example, a small hole formed in a plug screwed into the lubricating oil introduction passage 42. Yes. The throttle valve 43 limits the flow rate of the lubricating oil introduced from the tilting oil passage 17 into the motor chamber 5 through the lubricating oil introduction passage 42. Thus, when the flow control valve 41 is switched to the open position (a), the tilting pressure oil is reliably supplied into the tilting cylinder 16A through the tilting oil passage 17, and a part of the pressure oil is lubricated. The oil can be introduced into the motor chamber 5 as oil.

  44 is a communication path that communicates between the motor chamber 5 of the hydraulic motor 2 and the speed reducer chamber 24 of the speed reducer 18, and the communication path 44 includes an outer ring 8A constituting the bearing 8 as shown in FIG. It is formed between the inner ring 8B. The communication passage 44 supplies the lubricating oil introduced into the motor chamber 5 through the lubricating oil introduction passage 42 into the reduction gear chamber 24.

  Reference numeral 45 denotes a drain passage formed in the cylinder portion 3 </ b> A constituting the motor casing 3 so as to bypass the motor chamber 5. As shown in FIG. 2, one end side of the drain passage 45 is decelerated at a position near the mechanical seal 25. The other end side of the drain passage 45 opens to the machine room 24 and is connected to the tank 35 via a drain port 46 provided in the lid 4. The drain passage 45 discharges the lubricating oil supplied into the reduction gear chamber 24 to the tank 35 through the drain port 46.

  The hydraulic motor with a reduction gear according to the present embodiment has the above-described configuration, and the operation thereof will be described below.

  First, in a state where the hydraulic pump 34 is operated, the directional control valve 37 is switched from the neutral position (A) to the switching position (B) or (C), so that the pressure oil discharged from the hydraulic pump 34 is supplied to the main line 36A, The hydraulic motor 2 is supplied and discharged through 36B.

  As a result, pressure oil is supplied into each cylinder 10 of the cylinder block 9 through the supply / discharge port 11A of the valve plate 11, and the piston 12 inserted into the cylinder 10 extends toward the swash plate 15 side. Then, the shoe 13 provided at the tip of each piston 12 slides on the sliding surface of the swash plate 15 so as to draw an annular locus while pressing the swash plate 15, whereby the cylinder block 9 rotates. The output shaft 6 splined to the cylinder block 9 rotates.

  On the other hand, a part of the pressure oil discharged from the hydraulic pump 34 is led out to the tilting oil passage 17 and supplied to the tilting cylinder 16A through the tilting oil passage 17. At this time, the flow rate of the pressure oil flowing in the tilting oil passage 17 is controlled by switching the flow control valve 41 provided in the middle of the tilting oil passage 17 to the open position (a) or the throttle position (b). The

  Here, when the flow rate control valve 41 is switched to the throttle position (b), the flow rate of the pressure oil flowing through the tilting oil passage 17 is limited, so that the tilting piston 16B becomes inoperative and the tilting piston The pressing force acting on the swash plate 15 from 16B is suppressed. As a result, the swash plate 15 maintains the large tilt position shown in FIG. 2 by the pressing force from each piston 12, and the stroke of each piston 12 becomes maximum, and the output shaft 6 rotates at a low speed with high torque.

  On the other hand, when the flow control valve 41 is switched to the open position (a), the tilt piston 16B is actuated by the pressure oil supplied into the tilt cylinder 16A, and the tilt piston 16B presses the swash plate 15. Thereby, the swash plate 15 maintains the small tilt position shown in FIG. 3, the stroke of each piston 12 is minimized, and the output shaft 6 rotates at high speed with low torque.

  The rotation of the output shaft 6 is transmitted to the speed reducer casing 19 while being decelerated by two stages by the planetary gear speed reduction mechanisms 26 and 30 of the speed reducer 18, and the speed reducer casing 19 can rotate with a large torque. .

  Here, when the flow control valve 41 is switched to the throttle position (b), the tilting piston 16B remains inactive, but the pressure in the tilting oil passage 17 becomes higher than the tank pressure, so that the tilting oil The pressure oil flowing through the passage 17 is introduced into the motor chamber 5 as the lubricant through the lubricant introduction passage 42.

  On the other hand, when the flow rate control valve 41 is switched to the open position (a), the flow rate of the pressure oil flowing through the tilting oil passage 17 increases, so that a large amount of lubricating oil is introduced into the motor chamber 5 through the lubricating oil introduction passage 42. can do.

  Thus, the lubricating oil introduced into the motor chamber 5 flows into the reduction gear chamber 24 through the communication path 44 and is accommodated in the reduction gear chamber 24 as indicated by an arrow F in FIG. The planetary gear speed reduction mechanisms 26 and 30 are guided to the drain passage 45 so as to bypass the motor chamber 5 while being lubricated and cooled, and return to the tank 35 from the drain passage 45 through the drain port 46 of the hydraulic motor 2.

  Accordingly, sufficient lubricating oil can be supplied into the reduction gear chamber 24 using the tilting pressure oil flowing through the tilting oil passage 17 without relying on leak oil from the hydraulic motor 2, and the reduction gear. Lubrication and cooling of the planetary gear reduction mechanisms 26, 30 and the like housed in the chamber 24 can be performed appropriately.

  Further, even when wear powder is generated by the meshing of the gears constituting the planetary gear speed reduction mechanisms 26 and 30, the wear powder is diverted from the motor chamber 5 together with the lubricating oil flowing through the drain passage 45. 35 can be discharged. Therefore, the reduction gear chamber 24 and the motor chamber 5 can always be filled with clean oil, and the life of the reduction gear 18 and the hydraulic motor 2 can be extended.

  Furthermore, since sufficient lubricating oil can be supplied into the reduction gear chamber 24 using the tilting pressure oil flowing in the tilting oil passage 17, even when a warm-up operation is performed in a cold region, for example, The hydraulic oil can be smoothly circulated between the hydraulic motor 2 and the tank 35. As a result, the hydraulic oil can be quickly warmed and its viscosity can be quickly reduced, and the time required for warm-up operation can be shortened.

  Thus, according to the present embodiment, a part of the tilting pressure oil (tilting hydraulic signal) flowing through the tilting oil passage 17 is introduced into the motor chamber 5 as the lubricating oil through the lubricating oil introduction passage 42. It is said. Thereby, the lubricating oil introduced into the motor chamber 5 flows into the reduction gear chamber 24 through the communication passage 44, lubricates and cools the planetary gear reduction mechanisms 26, 30, etc., and then passes through the drain passage 45. It is discharged into the tank 35. For this reason, without relying on the leaked oil from the hydraulic motor 2 and without using a pump or the like for supplying lubricating oil to the reduction gear chamber 24, the pressure oil flowing through the tilting oil passage 17 is used for deceleration. Sufficient lubricating oil can always be supplied to the machine room 24, and the reduction gear 18 can be always properly lubricated and cooled.

  Next, FIG. 5 shows a second embodiment of the present invention. The feature of the present embodiment is that it includes a hydraulic pilot type directional control valve that controls the direction of the pressure oil supplied to the capacity variable mechanism, The reduction gear is lubricated and cooled using a pilot signal supplied to the hydraulic pilot portion of the directional control valve. In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

  In the figure, 51 is a shuttle valve located between the hydraulic motor 2 and the directional control valve 37 and provided between the main pipelines 36A and 36B. The shuttle valve 51 is connected to the high pressure side of the main pipelines 36A and 36B. And the pressure oil flowing through the high-pressure side main pipe 36A or 36B is led out to the oil path 52.

  53 is a directional control valve provided in the middle of the oil passage 52 connecting between the shuttle valve 51 and the tilting cylinder 16A of the tilting actuator 16, and this directional control valve 53 is a three port having a hydraulic pilot part 53A. It is configured as a two-position hydraulic pilot valve. The direction control valve 53 is switched between an open position (c) for opening the oil passage 52 and a closed position (d) for closing the oil passage 52 in accordance with a pilot signal supplied to the hydraulic pilot unit 53A. .

  Here, when the directional control valve 53 is in the closed position (d), the supply of the pressure oil to the tilting cylinder 16A is cut off, so that the tilting piston 16B becomes inoperative and the swash plate 15 is moved. The applied pressing force is suppressed, and the swash plate 15 maintains the large tilt position. On the other hand, when the directional control valve 53 is in the open position (c), a part of the pressure oil flowing through the high-pressure side main pipeline selected by the shuttle valve 51 among the main pipelines 36A and 36B is inclined through the oil passage 52. By being supplied to the rolling cylinder 16A, the tilting piston 16B is activated to press the swash plate 15, and the swash plate 15 is configured to hold the small tilt position.

  A pilot passage 54 connects the hydraulic pilot portion 53A of the direction control valve 53 and the pilot pump 55. The pilot passage 54 outputs a pilot signal as a tilting hydraulic signal discharged from the pilot pump 55 to the direction control valve 53. The hydraulic pilot unit 53A is supplied.

  A flow control valve 56 is provided in the middle of the pilot passage 54. The flow control valve 56 includes an open position (e) for opening the pilot passage 54 and a throttle position for restricting the pilot passage 54 by manual operation of an operator or the like. It can be switched to (f).

  Here, when the flow control valve 56 is switched to the throttle position (f), the flow rate of the pilot signal flowing through the pilot passage 54 is limited, the direction control valve 53 is in the closed position (d), and the swash plate 15 tilts greatly. Hold position. On the other hand, when the flow control valve 56 is switched to the open position (e), the direction control valve 53 is switched to the open position (c) by the pilot signal flowing through the pilot passage 54, and the swash plate 15 maintains the small tilt position. It has a configuration.

  When the hydraulic motor 2 is operated, the pressure in the pilot passage 54 is always maintained regardless of whether the flow control valve 56 is switched to the throttle position (f) or the flow control valve 56 is switched to the open position (e). It is higher than the pressure.

  A lubricating oil introduction passage 57 communicates between the intermediate portion of the pilot passage 54 and the motor chamber 5. The lubricating oil introduction passage 57 lubricates a part of a pilot signal (tilting hydraulic signal) flowing through the pilot passage 54. The oil is introduced into the motor chamber 5 as oil. A throttle valve 58, which will be described later, is provided in the middle of the lubricating oil introduction passage 57.

  A throttle valve 58 is provided as a throttle means provided in the middle of the lubricating oil introduction passage 57. The throttle valve 58 controls the flow rate of the lubricating oil introduced from the pilot passage 54 into the motor chamber 5 through the lubricating oil introduction passage 57. It is a limitation. Thus, when the flow control valve 56 is switched to the open position (e), the direction control valve 53 is reliably switched to the open position (c) by the pilot signal flowing through the pilot passage 54, and a part of the pilot signal is lubricated. It can be introduced into the motor chamber 5 as follows.

  Then, the lubricating oil introduced into the motor chamber 5 through the lubricating oil introduction passage 57 flows into the reduction gear chamber 24 through the communication passage 44 and lubricates the planetary gear reduction mechanism and the like housed in the reduction gear chamber 24. After the cooling, the motor chamber 5 is bypassed and guided to the drain passage 45 and is returned to the tank 35 from the drain passage 45.

  The hydraulic motor with a reduction gear according to the present embodiment has the above-described configuration, and the operation thereof will be described below.

  First, in a state where the hydraulic pump 34 is operated, the direction control valve 37 is switched from the neutral position (A) to the switching position (B) or (C). As a result, the pressure oil discharged from the hydraulic pump 34 is supplied to and discharged from the hydraulic motor 2 through the main pipelines 36A and 36B, and the output shaft 6 rotates.

  Here, when the flow rate control valve 56 is switched to the throttle position (f), the flow rate of the pilot signal supplied from the pilot passage 54 to the hydraulic pilot portion 53A of the direction control valve 53 is limited, and thus the direction control valve 53 Holds the closed position (d). Accordingly, when the oil passage 52 is blocked and the supply of pressure oil to the tilt cylinder 16A is cut off, the swash plate 15 maintains the large tilt position, and the output shaft 6 rotates at a low speed with high torque.

  On the other hand, when the flow control valve 56 is switched to the open position (e), the direction control valve 53 is switched to the open position (c) by the pilot signal supplied from the pilot passage 54 to the hydraulic pilot portion 53A of the direction control valve 53. Change. Accordingly, a part of the pressure oil flowing through the high pressure side main pipeline selected by the shuttle valve 51 among the main pipelines 36A and 36B is supplied to the tilting cylinder 16A through the oil passage 52, so that the swash plate 15 is small. The tilting position is maintained, and the output shaft 6 rotates at high speed with low torque.

  Here, when the flow control valve 56 is switched to the throttle position (f), the flow rate of the pilot signal flowing through the pilot passage 54 is limited and the direction control valve 53 maintains the closed position (d). Therefore, the pilot signal flowing through the pilot passage 54 is introduced into the motor chamber 5 as lubricating oil through the lubricating oil introduction passage 57.

  The lubricating oil introduced into the motor chamber 5 flows into the speed reducer chamber 24 through the communication path 44, and lubricates and cools the planetary gear speed reduction mechanism and the like housed in the speed reducer chamber 24. Then, it bypasses the motor chamber 5, is guided to the drain passage 45, and returns to the tank 35 from the drain passage 45.

  As a result, sufficient lubricating oil can be supplied into the reduction gear chamber 24 using the pilot signal (inclination hydraulic signal) flowing through the pilot passage 54 without depending on the leaked oil from the hydraulic motor 2, and deceleration. The machine 18 can be properly lubricated and cooled.

  On the other hand, when the flow rate control valve 56 is switched to the open position (e), the flow rate of the pilot signal flowing through the pilot passage 54 increases, so that the lubricating oil introduced into the motor chamber 5 through the lubricating oil introduction passage 57 is increased. be able to. Thereby, a large amount of lubricating oil can be supplied into the reduction gear chamber 24, and the reduction gear 18 can be lubricated and cooled more efficiently.

  Thus, according to the present embodiment, a part of the pilot signal (tilting hydraulic signal) flowing through the pilot passage 54 is introduced into the motor chamber 5 through the lubricating oil introduction passage 57 as lubricating oil, and this lubricating oil is connected. After being supplied into the reduction gear chamber 24 through the passage 44, it is discharged to the tank 35 through the drain passage 45. For this reason, sufficient lubricating oil can always be supplied to the reduction gear chamber 24 using the pilot signal flowing through the pilot passage 54, and the reduction gear 18 can be always lubricated and cooled properly.

  In the first embodiment described above, the case where the fixed throttle valve 43 formed of a small hole drilled in the plug is used as the throttle means provided in the middle of the lubricating oil introduction passage 42 is exemplified. Yes. However, the present invention is not limited to this. For example, a flow rate adjusting valve 59 with temperature compensation may be used as the throttle means as in the modification shown in FIG. In this case, for example, even when the viscosity of the working oil is high in the initial stage of the warm-up operation in a cold region, a part of the pressure oil can be reliably introduced into the motor chamber 5 through the lubricating oil introduction passage 42.

  Further, instead of the throttle valve 43 and the flow rate adjusting valve 59 described above, a thin blade orifice that has little influence on the oil temperature (viscosity) may be used as the throttle means. When this thin blade orifice is used, an appropriate flow rate can be secured even at low temperatures. The same applies to the throttle valve 58 used in the second embodiment.

  Further, in each of the above-described embodiments, a description is given by taking as an example a hydraulic motor with a reduction gear used in a traveling device for a tracked vehicle. However, the present invention is not limited to this, and can be applied to, for example, a turning device for turning an upper turning body such as a hydraulic excavator, a winch device mounted on a hydraulic crane, and the like.

It is sectional drawing which shows the hydraulic motor with a reduction gear by the 1st Embodiment of this invention. FIG. 2 is an enlarged cross-sectional view showing a motor chamber, a reduction gear chamber, a capacity variable mechanism, a lubricating oil introduction passage, a throttle valve, and the like in FIG. 1 in a state where a swash plate is in a large tilt position. FIG. 3 is an enlarged sectional view similar to FIG. 2 showing a state where the swash plate is in a small tilt position. It is a hydraulic circuit diagram including the hydraulic motor with a reduction gear according to the first embodiment. It is a hydraulic circuit diagram containing the hydraulic motor with a reduction gear by 2nd Embodiment. It is a hydraulic circuit diagram similar to FIG. 1 using a flow rate adjusting valve as a modification of the throttle means.

Explanation of symbols

2 Hydraulic motor 3 Motor casing (casing)
6 Output shaft 14 Variable capacity mechanism 17 Oil passage for tilting 18 Reduction gear 34 Hydraulic pump (hydraulic power source)
35 Tank (hydraulic power source)
36A, 36B Main pipeline 41, 56 Flow rate control valve 42, 57 Lubricating oil introduction passage 43, 58 Throttle valve (throttle means)
51 Shuttle valve 52 Oil passage 53 Direction control valve 53A Hydraulic pilot section 54 Pilot passage 59 Flow rate adjusting valve (throttle means)

Claims (4)

Deceleration to decelerate the variable displacement hydraulic motor, the rotation of the hydraulic motor to the rotatably supported to the hydraulic motor of the motor casing reducer casing having a variable displacement mechanism for switching the rotational speed of the output shaft in the motor casing In a hydraulic motor with a speed reducer comprising a speed reducer in which a mechanism is arranged ,
The motor casing is provided with a lubricating oil introduction passage for introducing a part of the tilting hydraulic signal for operating the variable capacity mechanism into the motor casing as lubricating oil,
Providing a communication path that communicates between the motor casing of the hydraulic motor and the speed reducer casing of the speed reducer and that supplies the lubricating oil introduced into the motor casing through the lubricating oil introduction path;
Hydraulic motor with reduction gear in the middle of the lubricating oil introducing passage, characterized in that a configuration in which a throttle means for limiting the flow rate of lubricating oil to be introduced into the motor casing.   In the middle of the oil passage for supplying the tilting hydraulic signal, a flow control valve that is switched between an open position for opening the oil passage and a throttle position for restricting the oil passage according to the tilt position of the capacity variable mechanism is provided. The hydraulic motor with a reduction gear according to claim 1, which is configured.   The hydraulic motor with a reduction gear according to claim 1 or 2, wherein the tilt hydraulic signal is pressure oil supplied from a hydraulic source to the capacity variable mechanism. A shuttle valve is provided between a pair of main pipes connecting a hydraulic power source to the hydraulic motor to select a high-pressure side main pipe among the pair of main pipes, and between the shuttle valve and the capacity variable mechanism. In the middle of the connecting oil path, a hydraulic pilot type directional control valve for switching the direction of the pressure oil supplied to the capacity variable mechanism is provided,
The hydraulic motor with a reduction gear according to claim 1 or 2, wherein the tilt hydraulic signal is a pilot signal supplied to a hydraulic pilot section of the directional control valve.

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