JPS6139880Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention provides an oil passage for supplying lubricating oil between a planetary gear and a support shaft that supports the planetary gear, in which an inlet is opened at the shaft end of the support shaft. A disc-shaped oil passage forming member, which is formed of At the same time, a roll pin for fixing the oil passage forming member to the support shaft is attached to the outer peripheral part of the oil passage forming member, and lubricating oil from the relay oil passage is used for supplying the lubricating oil. The present invention relates to a planetary transmission in which a cover body for guiding an oil passage to an entrance thereof is fixed to the oil passage forming member.

In the above transmission, in order to prevent the roll pin from slipping out, conventionally a wire is passed through the roll pin and wound around the support shaft and the oil passage forming member, but the wire is wound in a desired state. The work of attaching it was time-consuming and troublesome.

The present invention was developed with the above-mentioned circumstances in mind, and its purpose is to prevent the roll pin from coming out without requiring any special work by making effective use of existing members and making simple modifications. This is what I want to do.

The configuration of the present invention is that in the planetary transmission described above,
A stopper for preventing the roll pin from coming off is provided on the cover body and integrally formed therewith.

That is, the focus is on the cover body for guiding lubricating oil,
Since the stopper that prevents the roll pin from falling out is formed integrally with the cover body, the roll pin can be prevented from falling out simply by assembling the cover body after engaging the roll pin, without performing any special work for preventing the roll pin from falling out, thereby resulting in a planetary speed change device that is even more convenient to use.

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

As shown in Fig. 1, it is equipped with left and right front wheels 1, 1 that can be driven and rotated, and an arm 2 that can be operated to swing above the vehicle body using a hydraulic cylinder 2a, and an arm 2 that can be operated to swing up and down relative to the vehicle body using a hydraulic cylinder 3a. A front vehicle body is provided with a front loader device 4 consisting of a bucket 3, etc., and is equipped with left and right rear wheels 5, 5 that can be driven and rotated, and an engine 7 is mounted below the driver's seat 6, and a driving transmission is provided. The case 8 is connected to the front part of the engine 7, and the mounting base 10 is capable of freely sliding left and right with respect to the vehicle body and can swing horizontally with respect to the vehicle body, and the boom 11 is operable to swing vertically with respect to the mounting base using a hydraulic cylinder 11a. A backhoe device 14 includes an arm 12 that can be operated to swing up and down against the boom with a hydraulic cylinder 12a, a bucket 13 that can be operated to swing up and down against the arm with a hydraulic cylinder 13a, etc.
A rear vehicle body is provided behind the driver's seat 6, and left and right hydraulic cylinders 15, 15 rotatably support the front vehicle body and the rear vehicle body around the vertical axis X, and perform bending and rocking operations of both vehicle bodies. is installed between both vehicle bodies, and a steering handle 17 is provided on the rear vehicle body for rotating an orbiter 16 for telescopically operating the left and right hydraulic cylinders 15, 15.
The driver's seat 6 is mounted so that its direction can be changed forward and backward, and an operating section for the front loader device 4 and an operating section for the backhoe device 4 are provided at the front and rear of the driver's seat 6, respectively. The work vehicle is configured to perform work of scooping up, transporting and discharging earth and sand in the state where the driver's seat 6 is facing backward, and to perform work of excavating a trench etc. with the driver's seat 6 facing rearward.

The traveling transmission case 8 is equipped with a fluid pressure-operated planetary transmission that changes the forward speed into five stages and the reverse speed into two stages, and has an output shaft 18 whose axis is oriented in the longitudinal direction. , telescopic and bendable transmission shafts 19, 19 are provided which are supported through the transmission case 8 and which connect the output shaft 18 and the front and rear wheels 1, 5.

As shown in FIG. 2, in configuring the fluid pressure operated planetary transmission, an input shaft 20, a first intermediate shaft 21, and a second intermediate shaft 22 are arranged concentrically along the front-rear direction. The first intermediate shaft 21 is provided with the reverse cylinder shaft 23, and the second intermediate shaft 22 is provided with the output cylinder shaft 24.
are attached relatively rotatably to each other, and disk-shaped support members 25a for a plurality of planetary gear supporting spindles 25 are attached to the second intermediate shaft 22 so as to be relatively rotatable, and between the input shaft 20 and the first intermediate shaft 21. The first multi-plate type
A transmission clutch 26, a multi-plate second transmission clutch 27 between the input shaft 20 and the reverse cylinder shaft 23,
A multi-plate type third power transmission clutch 28 is provided between the second intermediate shaft 22 and the output cylindrical shaft 24, and first and second transmission clutches 28 are respectively fixed to the first and second intermediate shafts 21 and 22, respectively. The first and second planetary gears 29, 30, which are always engaged with the two sun gears 21a, 22a, are externally fitted onto the support shaft 25 so as to be relatively rotatable, and the third planetary gears are separately fixed to the two cylindrical shafts 23, 24, respectively. and third and fourth planetary gears 31 and 32 that engage with the fourth sun gears 23a and 24a separately and engage with the first and second planetary gears 29 and 30, respectively, are rotatable relative to the support shaft 25. Installation, said reverse cylinder shaft 2
3 to the case 8, a multi-plate fifth transmission clutch 35 to fix to the case 8 an internal gear 34 that is always engaged with the first planetary gear 29, and a fifth transmission clutch 35 to fix the second A sixth transmission clutch 36 is provided which fixes the intermediate shaft 22 to the case 8. Furthermore, the input shaft 20 is operatively connected to the engine 7 via a travel clutch 37 and a gear interlocking mechanism, and the output cylinder shaft 24 is connected to the engine 7 through a gear interlocking mechanism. The output shaft 1 through the mechanism
8 is interlocked and connected. And Figures 2 and 3
As shown in the figure, the first to sixth transmission clutches 2
Hydraulic pistons 26A and 27 that press and operate each of 6, 27, 28, 33, 35, and 36 separately.
A, 28A, 33A, 35A, and 36A are provided in a state in which the clutch disengagement operation position is covered and biased, and in a state in which the clutch engagement operation position is moved to the side by oil supply, and the plurality of A control valve 38 that switches the operating state of each piston 26A, and a gear shift lever 39 that switches the control valve 38.
As the gear shift lever 39 is moved forward from the neutral position N to positions F ₁ , F ₂ , F ₃ , F ₄ , F ₅ corresponding to forward 1st forward speed to 5th forward speed, forward movement is performed. Positions that perform 5-speed gear shifting and correspond to reverse 1st speed and reverse 2nd speed from neutral position N toward the rear.
It is configured so that as the gear is operated to R ₁ and R ₂ , a two-speed reverse gear shift is performed.

More specifically, in the first forward speed state _F1 , the first, third, and fifth transmission clutches 26, 28, and 35 are engaged.

In the second forward speed state, the first, third, and fourth transmission clutches 26, 28, and 33 are engaged.

In the third forward speed state, the first, second, and third transmission clutches 26, 27, and 28 are engaged.

In the fourth forward speed state, the first, fourth, and sixth transmission clutches 26, 33, and 36 are engaged.

In the fifth forward speed state, the first, second, and sixth transmission clutches 26, 27, and 36 are engaged.

In the first reverse speed state, the second, third, and fifth transmission clutches 27, 28, and 36 are engaged.

In the second reverse speed state, the second, fifth, and sixth transmission clutches 27, 35, and 36 are engaged.

And large diameter hydraulic pistons 33A, 35A,
4th, 5th, 6th power transmission clutch 3 with 36A
The amount of fluid supplied to the piston at the time of switching to a shift state in which any one of the transmission clutches 3, 35, and 36 is operated is controlled by the first, second, and third transmission clutches 26, each equipped with a small-diameter hydraulic piston 26A, 27A, and 28A. 27,2
The amount of fluid supplied to the piston is larger than the amount of fluid supplied to the piston at the time of switching to the forward three-speed shift state in which only 8 is engaged. The discharge amount of the shift hydraulic pump 40 that supplies pressurized oil to the control valve 38 is determined so that switching to a shift state in which a large amount of fluid is supplied to the piston can be performed appropriately in a short period of time.

As shown in FIG. 3, one accurator 41 is provided for accumulating a portion of the oil from the control valve 38, and the control valve 38 is placed in the first forward speed state and the third forward speed state as it is switched. , and a port 43 for connecting the accumulator 41 is provided so as to connect the accumulator 41 to the pump 40 in the reverse 1st speed state and to connect the accumulator 41 to the tank 42 in other speed change states. The pistons 26A, 27A, and 28A are configured to be able to suppress unnecessary high-speed operation when switching to the third forward speed state. The pistons 26A, 2
8A and 35A are configured so that they can be operated slowly.

In Fig. 3, 44 is a main relief valve that determines the maximum clutch engagement pressure, and 45 is a pilot-operated switch that provides resistance to the flow of drained oil at the beginning of gear shifting to ensure smooth gear shifting. It is a valve.

As shown in FIG. 4, the first and second intermediate shafts 21,
22, first and second oil flow passages 46a and 46b are supplied with return oil from the control valve 18, respectively.
are formed in a state where they communicate with each other, and the oil in both flow oil passages 46a, 46b is transferred to the first and second intermediate shafts 21,
First and second oil discharge oil passages 47a and 47b are formed on the outer periphery of the 22, and the oil from the first oil discharge oil passage 47a is transferred to the first intermediate shaft 21 and the reverse cylinder. After flowing between the shafts 23 in the axial direction, the first outlet 48a formed on the reverse cylinder shaft 23
In addition to being configured to discharge more outward,
The oil from the second oil discharge oil passage 47b is configured to be discharged outward from a second outlet 48b formed in the output cylinder shaft 24. An oil passage 49 for supplying lubricating oil between each of the first to fourth planetary gears 29 and the support shaft 25 that supports them,
The support shaft 25 has an inlet 49a at its shaft end.
A disc is formed in an open state and is provided with a relay oil passage 50 for causing the lubricating oil supplied from the two cylindrical shafts 23 and 24 as the transmission shaft for supporting the sun gear to flow outward from the end of the support shaft 25. A roll pin 52 for fitting the shaped oil passage forming member 51 onto the end of the support shaft 25 and fixing the oil passage forming member 51 to the support shaft 25.
A cover body 53 is fitted from the outer circumference of the oil passage forming member 51 to guide lubricating oil from the relay oil passage 50 to the inlet 49a of the lubricating oil supply oil passage 49.
is fixed to the oil passage forming member 51 by a rivet 54, and then the support shaft 25 and each planetary gear 29...
The structure is such that lubricating oil can be supplied between the

Further, a stopper 55 for preventing the roll pin 52 from coming off is provided on the cover body 53 in a state where it is bent integrally with the cover body 53, thereby making it possible to prevent the roll pin 52 from coming off with a simple structure that makes effective use of the cover body 53. It is structured as follows.

In the above embodiment, a planetary transmission for performing multi-stage gear shifting is illustrated, but the present invention can be applied to various forms of planetary transmission, such as a planetary transmission used for deceleration transmission, for example.

[Brief explanation of the drawing]

FIG. 1 is a side view of the working vehicle, FIG. 2 is a schematic diagram of the planetary transmission, FIG. 3 is a hydraulic circuit diagram, and FIG. 4 is a longitudinal side view showing the lubricating oil supply structure. 23... Transmission shaft for sun gear support, 25... Support shaft, 29... Planetary gear, 49... Oil passage for lubricating oil supply, 49a... Inlet, 50... Relay oil passage, 51...
...Oil passage forming member, 52... Roll pin, 53...
Cover body, 55...stopper.

Claims (1)

[Scope of utility model registration request] An oil passage 49 for supplying lubricating oil between the planetary gear 29 and the support shaft 25 that supports it is formed in the support shaft 25 with an inlet 49a opened at the shaft end thereof, and the oil passage 49 is connected to the sun gear. A disc-shaped oil passage forming member 51 equipped with a relay oil passage 50 for causing lubricating oil supplied from the support transmission shaft 23 to flow outward toward the end of the support shaft 25 is attached to the end of the support shaft 25. At the same time, a roll pin 52 for fixing the oil passage forming member 51 to the support shaft 25 is attached to the outer circumference of the oil passage forming member 51, and the relay oil passage 5
A planetary transmission in which a cover body 53 for guiding lubricating oil from 0 to the entrance 49a of the lubricating oil supply passage 49 is fixed to the oil passage forming member 51, and the roll pin 52 is prevented from coming off. stopper 5
5 is provided on the cover body 53 so as to be integrally formed therewith.