JPS6220767Y2 - - Google Patents

Description

[Detailed description of the invention] (a) Industrial application field The present invention relates to a transmission device for a mobile working machine such as a tractor or a construction machine. More specifically, this invention relates to a hydraulic clutch type transmission device that incorporates a plurality of hydraulic clutches as a transmission device, and selects one of a plurality of gear trains that are constantly engaged to change speed by selecting engagement/disengagement of the hydraulic clutches. It is.

(b) Prior Art A technology related to a small hydraulic clutch type transmission has been known by the same applicant.

For example, Utility Model Application Publication No. 145130/1983. However, in this known technique, an oil passage plate is interposed between the clutch housing and the transmission case, and the gear pump and seal case are gathered in this area.

(c) Problems to be solved by the invention The purpose of the invention is to create a hydraulic clutch type transmission by using parts that existed in conventional gear type mesh sliding transmissions, such as the transmission case components and shafts. Configure A, omit parts and reduce the number of points,
Hydraulic clutch, hydraulic pump, seal case, etc. 1
By fitting the oil passage-related parts together as much as possible by fitting them onto the first shaft of the book, the oil passages are carved or drilled to shorten them, and the parts that require attention during assembly are placed on the first axis.
This is a compact hydraulic clutch device that is concentrated on the shaft and is easy to assemble.

In addition, a seal case and a hydraulic pump are arranged before and after the first shaft, where multiple hydraulic clutches are arranged, and a hydraulic switching valve V is arranged on the outer wall of the transmission case between them. The oil path up to the case can be configured to be extremely short, which is advantageous in processing the oil path.

In addition, since the oil passage from the hydraulic pump to the seal case can be formed short, the hydraulic clutch can be operated reliably without causing pressure drop due to resistance in the pipeline.

(d) Means for solving the problem The purpose of the present invention is as described above. Next, the configuration for achieving the purpose will be explained.

A transmission case 2 is connected to the rear end of the main clutch housing 3, and a hydraulic clutch type transmission A is arranged between the rear end wall 3a of the main clutch housing 3 and the wall 2c of the transmission case 2. In this structure, a first shaft 19 in the transmission case 2 that protrudes through the wall portion 3a is connected to the rear end of the main clutch shaft 16 of the main clutch housing 3.
A seal case 71 is attached to the protrusion of the shaft 19, a plurality of hydraulic clutches are arranged on the first shaft 19 in the mission case 2, and a wall portion 2c is installed at the rear of the first shaft 19.
A hydraulic pump 18 for a hydraulic clutch attached to the transmission case 2 is installed between the walls 3a and 2c.
A hydraulic switching valve V for controlling the pressure oil from the hydraulic pump 18 toward the seal case 71 is mounted on the outer wall.

(E) Embodiment The purpose and structure of the present invention are as described above. Next, the structure of the embodiment will be explained based on the attached drawings.

FIG. 1 is an overall side view of a tractor equipped with the hydraulic clutch type transmission of the present invention.

An engine 1 is contained within a bonnet 10, and the rear end of the engine 1 is fastened to the tip of a main clutch housing 3, and a transmission case 2 is fixedly installed at the rear of the main clutch housing 3. Furthermore, a rear axle housing 13 is fastened to the rear part of the housing, and the whole constitutes a chassis.

A front wheel 4 is provided at the bottom of the bonnet 10, a rear wheel 5 is provided at the bottom of the rear axle housing 13, a three-point link hitch device 6 for attaching a work machine is provided at the rear of the rear axle housing 13, a seat device 8 is placed on the top surface, and the rear wheel 5 is provided at the bottom of the rear axle housing 13. A fender 7 is installed on the Furthermore, a control device 9 is disposed above the main clutch housing 3.

The main parts of the present invention are inside the mission case 2. At the top of the transmission case 2, a main shift lever 14 projects upward from the main shift chamber 2a, and a sub-shift lever 15 projects upward from the sub-shift chamber 2b.

A muffler 11 is provided to protrude above the bonnet from the side of the engine 1.

FIG. 2 is a power transmission diagram of the hydraulic clutch type transmission of the present invention.

The driving force from the engine 1 is transmitted through the hydraulic clutch type transmission A to the auxiliary transmission B, and from the rear axle housing to the rear shaft 5, and the other transmission system is transmitted through the PTO transmission D to the PTO shaft 25. Used to drive work equipment. The hydraulic clutch type transmission A in the transmission diagram is the main part of the present invention.

In particular, in the present invention, the rotational force of the engine 1 is connected and disconnected by the main clutch 90, and the main clutch shaft 16
is connected to the first shaft 19 by a coupling 91, and two pairs of hydraulic clutch devices 26a, 26b, 27a, and 27b are installed back to back within the main transmission chamber 2a on the first shaft 19. It is.

A hydraulic pump 18 as a hydraulic pressure generating section is attached to the wall portion 2c of the transmission case 2 at the portion where the first shaft projects into the sub-transmission chamber 2b. The first shaft 19 passes through the gear-meshing sliding sub-transmission device B, reaches the rear axle housing 13, and reaches the PTO transmission shaft 23 through a coupling 24. PTO
PTO shifting is performed between the shifting shaft 23 and the PTO shaft 25.

The first shaft 19 in the hydraulic clutch type main transmission A
A second shaft 20 is installed parallel to the lower part of the hydraulic clutch free rotating gears 33, 34, 35, 36 on the first shaft.
and fixed gears 28, 29, 30, 31 on the second shaft.
always mesh together. Only, the free rotating gear 33 and the fixed gear 28
Since the combination is a gear train for reverse movement, they are meshed with each other via a reverse gear 32. The combination of the free rotating gear 34 and the fixed gear 29 is the first forward speed, the combination of the free rotating gear 35 and the fixed gear 30 is the second forward speed, and the combination of the free rotating gear 36 and the fixed gear 31 is the second forward speed. This is the third forward speed.

Idle gears 33, 34, 35, 36 are connected to driven friction plates 33b, 34b, 35b, 36b of hydraulic clutches 26a, 26b, 27a, 27b, and hydraulic pistons 33c, 34c, 35c, 36
By the operation of c, the driving friction plates 33a, 34a, 3
5a, 36a are driven friction plates 33b, 34b, 35
b, 36b, the fixed gears 28, 29, 36b transmit power to the idle gears 33, 34, 35, 36 through the hydraulic cylinder, and are always in mesh with the fixed gears 28, 29, 36b.
The second shaft 20 is rotated from 30 and 31.

The hydraulic clutches 26a and 26b are integrally constructed back to back, and similarly the hydraulic clutches 27a and 27b are integrally constructed back to back, which is effective in downsizing the hydraulic clutch device. The second shaft 20 is further protruded from the wall 2c of the mission case 2, and the hydraulic pump 1 is provided on the protrusion on the first shaft.
At the end position of 8, the traveling drive shaft 22 is loosely fitted and supported.

The first shaft 19 is supported by a bearing on the mission case wall 20, and then connected to the pump shaft 17 and the hydraulic pump 18a.
are connected as a coupling.

A sub-transmission small-diameter gear 37 is fixed to the rear end of the second shaft, and the sub-transmission loose-fitting gear 4 is loosely fitted to the pump shaft 17.
Among the gears 0, 41, 42, and 43, the gears are always in mesh with the large diameter gear 40. The auxiliary transmission loose fitting gear 41 is the auxiliary transmission 3
A sliding gear 2 on the traveling drive shaft 22.
By meshing with 9, a third auxiliary gear shift is constructed. The auxiliary transmission loosely fitted gear 41 and the sliding gear 44 constitute the auxiliary transmission second speed, and the auxiliary transmission loosely fitted gear 42 and the sliding gear 4
5 constitutes the sub-shift first speed. Further, by directly connecting the sliding internal gear 38 to the auxiliary transmission small diameter gear 37, a fourth auxiliary transmission speed is constructed.

A bevel gear 46 is provided at the rear end of the traveling drive shaft 22, and the bevel gear 46 and the differential gear bevel gear 47 are connected to each other.
are engaged, and after being decelerated by traveling reduction gears 49 and 50 via a differential device 48, power is transmitted to the rear wheels 5. A brake device 1 is installed on the outside of the travel reduction gear 49.
00 is set.

The pump shaft 17 is connected to the PTO speed change shaft 23 by a coupling 24, and spline sliding gears 51 and 52 are slid on the front portion of the PTO speed change shaft 23, and loosely fitted gears 56 and 57 are loosely fitted on the rear half of the PTO speed change shaft 23. do.

On the PTO shaft 25 are idle gears 53, 54, 55,
58, and sliding clutch pieces 60 and 62 that are spline-fitted and slide on the PTO shaft 25 are provided.
Furthermore, a fixed clutch piece 59 is attached to the base of the loosely fitted gear 55.
A fixed clutch piece 61 is provided at the base of the loosely fitted gear 58. Freely fitted gears 56, 5 on the PTO transmission shaft 23
7 and the loosely fitted gears 55 and 58 on the PTO shaft are always engaged.

The first stage of PTO transmission is a sliding gear 51 and a loosely fitted gear 5.
3 are engaged, and the sliding clutch piece 62 and the fixed clutch piece 61 are engaged.In the second PTO gear shift, the sliding gear 51 is similarly engaged with the loosely fitted gear 53, and the sliding clutch piece 60 is engaged with the sliding clutch piece 62. Fixed clutch piece 5
This is the case when the mesh is engaged with 9. When the third stage PTO gear meshes the sliding gear 52 with the loosely fitted gear 54 and the sliding clutch piece 62 meshes with the fixed clutch piece 61, the fourth stage PTO gear similarly engages the sliding gear 52 and the loosely fitted gear. 54 and the sliding clutch piece 60 is engaged with the fixed clutch piece 59.

The transmission system is as described above.

FIG. 3 is a side longitudinal cross-sectional view showing the main clutch housing 3, transmission case 2, rear axle housing 13, and hydraulic switching valve V section.

Hydraulic clutches 26a, 26b, 27a, 27b are installed in the main transmission chamber 2a on the first shaft 19, and fixed gears 28, 29, 30, 31 are mounted on the second shaft below.
will be permanently installed.

The reversing gear 32 is supported by a cantilever on the wall 3a of the main clutch housing 3. Main clutch shaft 1
A seal case 71 is installed in the clutch housing 3 immediately after the coupling 91 that connects the first shaft 19 and the first shaft 19.
is installed protrudingly. The seal case 71 is closely fixed to the front surface of the wall 3a, and the hydraulic clutch 26
It serves to transfer high-pressure oil for a, 26b, 27a, and 27b to the oil passage in the first shaft 19.

As a path for high-pressure oil, the hydraulic oil that also serves as lubricating oil is sucked by the oil filter 81 in the rear axle housing 13, and is passed through piping or an oil passage carved or drilled in the wall 2c of the transmission case 2. The hydraulic direction switching valve V provided at the top of the transmission case 2 is reached, and the direction of the oil path is determined by the spool 65. After passing through the oil passage in the seal case 71 due to an oil passage (not shown) formed between the front wall of the clutch housing wall 3a and the clutch housing wall 3a,
Reverse, 1st speed, and 2nd speed openings at the front end of the
The oil enters oil passages 67, 68, 69, and 70 for speed and third speed. These oil passages 67, 68, 69, and 70 pass through an in-shaft oil passage fitted within the shaft, and then reach hydraulic clutch pistons 33c, 34c, 35c, and 36c. Therefore, hydraulic clutches 26a, 26b, 27
The oil passage for moving a and 27b is a hydraulic pump 18.
An oil passage for the transmission case 2 is provided on the wall 2c of the transmission case 2, an oil passage for the hydraulic directional control valve V is provided on the upper wall of the transmission case 2, and an oil passage for the clutch to be transferred to the seal case 71 is provided on the upper wall of the transmission case 2. It is engraved on the wall 3a of the housing 3. Therefore, the oil passage-related parts necessary for hydraulic clutch type shifting are the first.
They will be lined up on axis 19. First, the seal case 71 is placed inside the clutch housing 3, and the main transmission chamber 2
Hydraulic clutches 26a, 26b, 27a, 2 in a
7b, a hydraulic pump 18 is provided in the sub-transmission chamber 2b.

Further, on the front wall surface of the wall portion 3a of the main clutch housing 3, an inertial slip prevention brake device 93 is provided at the lower part of the seal case 71. When the main clutch 90 is disengaged in order to change the sub-transmission, the inertial slip prevention brake 93 continues to inertially rotate the shaft due to the weight of the gears, hydraulic clutch, etc., even if the clutch is disengaged. If you try to make the auxiliary transmission sliding gears 38, 39, 44, and 45 mesh with the stationary gear, you will notice that at the moment of engagement, the chamfer part, which has a sloped meshing surface to facilitate gear meshing, Since accidents such as breakage may occur, the main clutch is disengaged and the free shaft is kept stationary.

The inertial slip prevention brake device 13 has a piston 93
a, a cylinder 93b, and a friction plate 93c fixed to the tip of the piston 93a. High-pressure oil from a gear pump is fed into the cylinder in conjunction with the operation of the clutch pedal 94, and the friction plate 93
c is pressed against the tip of the second shaft to forcibly stop the rotation of the second shaft, thereby stopping idling.

An oil passage for an inertial slip prevention brake is also carved in the front wall of the wall portion 3a of the main clutch housing 3.

Figure 4 shows the installation inside the rear axle housing.
It is a detailed diagram of the PTO transmission device D.

(f) Effects of the invention Since the invention is constructed as described above, it has the following effects.

First, since the seal case 71, hydraulic clutch devices 26, 27, and gear pump 18 can be arranged side by side on one axis, the length of the oil passage carved into the mission case wall is shorter than before. It is.

In particular, in the past, oil was sent from the oil filter 81 to the gear pump at the front end of the transmission case 2 through an oil path such as piping, converted into pressurized oil, and reciprocated to the hydraulic switching valve V, resulting in a long oil path. In the present invention, pressure oil can be sent to the oil filter 81, gear pump, and hydraulic switching valve in order, and the oil path can be shortened to one direction.

Secondly, the front and rear walls 3a and 2c of the hydraulic clutch
The seal case 71 and the hydraulic pump 18 are placed in the
Mission case 2 between front and rear walls 3a and 2c
By mounting the hydraulic switching valve V that connects the hydraulic pump 18 and the seal case 71 on the outer wall, the oil passage between the hydraulic pump 18, the hydraulic switching valve V, and the seal case 71 can be configured to be very short. This made processing easier.

Furthermore, since the oil passage from the hydraulic pump 18 to the seal case 71 can be formed short, there is no pressure drop due to resistance in the pipeline, so the hydraulic clutch can be operated reliably.

[Brief explanation of the drawing]

Figure 1 is an overall side view of a tractor equipped with a hydraulic clutch type transmission, Figure 2 is a transmission line diagram of the hydraulic clutch type transmission, Figure 3 is a side longitudinal sectional view of the transmission case, and Figure 4 is a PTO. It is a detailed diagram of the transmission D. 1... Engine, 2... Mission case, 2
a... Main transmission chamber, 2b... Sub-transmission chamber, 2c... Wall, 3... Main clutch housing, 3a... Wall, A... Hydraulic clutch type transmission, B... Sub-transmission, 18 ... Hydraulic pump, 19 ... First shaft,
20...2nd shaft, V...hydraulic switching valve.

Claims (1)

[Scope of utility model registration request] A transmission case 2 is connected to the rear end of the main clutch housing 3, and a hydraulic clutch type transmission A is arranged between the rear end wall 3a of the main clutch housing 3 and the wall 2c of the transmission case 2. In this structure, a first shaft 19 in the transmission case 2 that protrudes through the wall portion 3a is connected to the rear end of the main clutch shaft 16 of the main clutch housing 3.
A seal case 71 is attached to the protrusion of the shaft 19, a plurality of hydraulic clutches are arranged on the first shaft 19 in the mission case 2, and a wall portion 2c is installed at the rear of the first shaft 19.
A hydraulic pump 18 for a hydraulic clutch attached to the transmission case 2 is installed between the walls 3a and 2c.
A hydraulic clutch type transmission device characterized in that a hydraulic switching valve V for controlling pressure oil from a hydraulic pump 18 toward a seal case 71 is mounted on an outer wall.