JP2000062484A - Transmission for combine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the sizes of left and right directions by housing two continuously variable transmission units on a transmission case in a compact manner and especially arranging these side by side in the back and forth direction of a machine body, and to use the two continuously variable transmission units even for a compact combine for two or three lines. SOLUTION: A traveling first continuously variable transmission unit 25 having a traveling hydraulic pump and a traveling hydraulic motor arranged side by side in a back and forth direction and a turning second continuously variable transmission unit 28 having a turning hydraulic pump and a turning hydraulic motor arranged side by side in a back and forth direction are arranged side by side in a back and forth direction in one side face of an input case portion 22a facing the upper surface of a transmission case 22. Then, input shafts 23a and 26a for driving the two hydraulic pumps are connected by a transmission belt 30.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combine transmission equipped with a continuously variable transmission mechanism for changing the traveling speed of an aircraft and a continuously variable transmission mechanism for turning to change the traveling direction of the aircraft. is there.

[0002]

2. Description of the Related Art Conventionally, an operating unit is arranged on one side of a combine traveling by a crawler type traveling device, a Glen tank is arranged behind the operating unit, and a reaping unit is arranged on the side of a driver's seat. , There is a combine with a configuration in which the grain culms cut by the reaping unit are conveyed to the threshing device behind the reaping unit, and the straw after selection is discharged from the rear of the body, and for traveling in which the traveling speed of the body is changed. A combine equipped with a continuously variable transmission mechanism and a continuously variable transmission mechanism for turning which changes the traveling direction of the machine body is known. And HST for these continuously variable transmissions
Japanese Patent Laid-Open No. 10-54452 discloses a technique in which a transmission type continuously variable transmission mechanism is adopted and attached to a transmission case.

[0003]

However, a conventional transmission using a continuously variable transmission mechanism for traveling and turning has a large overall structure, and particularly in a small combine such as two-row or three-row. There is a problem in that it is difficult to fit these continuously variable transmission mechanisms in the body of the vehicle in the width in the left-right direction, and the structure of the combine body becomes large. Further, since the hydraulic pump for the continuously variable transmission mechanism for traveling and the hydraulic pump for the continuously variable transmission mechanism for turning are arranged side by side on the same axis in the left-right direction, the left-right width becomes large and the combine is required to be compact. It was a challenge.

[0004]

The problem to be solved by the present invention is as described above, and the means for solving this problem will be described below. That is, among the three elements of the pair of left and right planetary gear mechanisms housed in the mission case, each of the first elements is linked to the first continuously variable transmission unit, and each of the second elements is coupled to the first through the forward / reverse rotation imparting mechanism. (2) The continuously variable transmission unit is interlockedly connected, and each of the third elements is interlockedly connected to the left and right axles, and at the same time, the speed change arm of the first continuously variable transmission unit is interlocked with the traveling operation tool to change the speed of the second continuously variable transmission unit. In a combined transmission in which an arm is linked to a steering operation tool, a first continuously variable transmission unit and a second continuously variable transmission unit are attached to one side surface of the transmission case so as to be arranged in parallel in the longitudinal direction of the machine body.

Further, among the three elements of the pair of left and right planetary gear mechanisms housed in the mission case, each of the first elements is interlockingly connected to the first continuously variable transmission unit, and each of the second elements is provided with a forward and reverse rotation imparting mechanism. Via interlocking connection to the second continuously variable transmission unit, interlockingly connecting each of the third elements to the left and right axles,
In a combined transmission in which the speed change arm of the first continuously variable transmission unit is linked to the travel operation tool and the speed change arm of the second continuously variable transmission unit is linked to the steering operation tool, one of the left and right sides of the transmission case On the other hand, an input case portion extending upward from the upper surface of the mission case is provided, and on one side surface of the input case portion, the traveling system transmission mechanism and the power receiving portion of the forward / reverse rotation imparting mechanism are arranged side by side in the front-rear direction. The first continuously variable transmission unit and the second continuously variable transmission unit are arranged side by side in the front-rear direction on one side surface of the input case portion, and respective output shafts thereof are connected to respective power receiving portions.

Further, the input shafts of the first continuously variable transmission unit and the second continuously variable transmission unit are interlockingly connected through a first endless belt, and any one of the input shafts is mounted on a vehicle. The engine and the second endless belt are linked together.

Further, the input shaft and the output shaft of each of the first continuously variable transmission unit and the second continuously variable transmission unit are arranged in parallel in the longitudinal direction of the machine body so that they are parallel to each other.

[0008]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. Fig. 1 is an overall side view of the combine, Fig. 2
Is a plan view of the combine, FIG. 3 is a schematic front view of the combine, FIG. 4 is a skeleton view of the transmission,
5 is a schematic perspective view of the entire transmission, FIG. 6 is a schematic perspective view showing a state in which a continuously variable transmission unit is separated from the transmission, and FIG. 7 is a sectional development view of a transmission including a first continuously variable transmission unit for traveling, 8 is a sectional development view of a transmission including a second continuously variable transmission unit for turning, FIG. 9 is a sectional view of a planetary gear mechanism, FIG. 10 is a left side sectional view of the transmission, FIG. 11 is a left side view of the transmission, and FIG. 12 is a right side view of the transmission, FIG. 13 is a view showing another embodiment in which the first continuously variable transmission unit and the second continuously variable transmission unit are linked together, and FIG.
4 is an enlarged sectional view of an essential part of the oil filter, and FIG. 15 is a hydraulic circuit diagram.

First, the overall structure of the combine of the present invention will be described with reference to FIGS. 1 and 2. Left and right crawler type traveling devices 2L and 2R are mounted on the track frame 1. 3 is a machine stand installed on the truck frame 1, 4 is a threshing unit which is a threshing machine in which a feed chain 5 is stretched on the left side and a handling cylinder 6 and a processing cylinder 7 are incorporated, and 8 is a cutting blade 9 and a grain culm transfer. A mowing unit including the mechanism 10 and the like, 11 is a hydraulic cylinder that moves the mowing unit 8 up and down via the mowing frame 12. Reference numeral 13 is an straw processing unit that faces the end of the straw chain 14, 15 is a grain tank that carries the grains from the threshing unit 4 through a lifting cylinder 16, and 17 is the grain tank 15 that is outside the machine. To the discharge auger, 18 is a handle post that supports a round steering handle 19, 68 is a main speed change lever,
Reference numeral 20 denotes a driver's seat, and reference numeral 21 denotes an engine having an output shaft extending in the left-right direction of the machine body, which is configured to continuously mow the grain culms from the front of the combine and thresh.

Further, the combine is provided with a first continuously variable transmission unit of a traveling system and a second continuously variable transmission unit of a turning system, and each unit is configured to obtain a driving force from the engine 21. . And engine 21
The first continuously variable transmission unit which has obtained the driving force controls forward and reverse rotation directions and increases and decreases the number of revolutions, and then the driving force is transmitted to the differential mechanism 33 via the traveling system transmission mechanism R. . After the second continuously variable transmission unit that has received the driving force from the engine 21 controls the forward and reverse rotation directions and the rotation speed increase / decrease, the driving force is transmitted to the differential mechanism 33 via the forward / reverse rotation imparting mechanism S. Transmitted. With such a configuration, the differential mechanism 3
Left and right crawler type traveling device 2L ・ 2 linked to 3
The driving force is always transmitted to the driving sprocket 34L / 34R of the R for forward / backward traveling and the driving sprocket 34L for the left / right
The turning is made possible by the relative increase / decrease control of the rotation speed with respect to 34R. The traveling and turning mechanism will be described below.

Next, the structure of the transmission of the present invention will be described with reference to FIGS. 7 to 12. In this embodiment, a hydrostatic continuously variable transmission (hereinafter referred to as HST device) H is adopted as the continuously variable transmission unit, and the transmission M that drives the crawler type traveling devices 2L and 2R travels in the mission case 22. It is composed of a system transmission mechanism R, a forward / reverse rotation imparting mechanism S, planetary gear mechanisms 35L and 35R, and an HST device H mounted on the mission case 22. The HST device H is composed of a set of a traveling hydraulic pump 23 and a traveling hydraulic motor 24, and is a first continuously variable transmission unit 25 for traveling, which is a main transmission mechanism, and a pair of swing hydraulic pumps 2.
And a second continuously variable transmission unit 28 for turning, which is a turning mechanism constituted by 6 and a turning hydraulic motor 27. The mission case 22 is on the left side (on the left side in FIGS. 7 and 8).
The case part 22L and the right case part 22R are joined together, and the case parts 22L and 22R are joined together near the center of the mission case 22 in the left-right direction.

Further, as shown in FIGS. 10 and 11, the first continuously variable transmission unit 25 for traveling is provided with a traveling hydraulic pump 23 in a case laterally placed rearward (right side in FIG. 10) in the longitudinal direction of the machine body. And a traveling hydraulic motor 24 are arranged in parallel, and an input shaft 23a of the traveling hydraulic pump 23 and an output shaft 24a of the traveling hydraulic motor 24 are axially supported in the lateral direction of the machine body and are arranged in parallel in the front-rear direction. There is.

Further, in the second continuously variable transmission unit 28 for turning, the forward and backward directions of the machine body (see FIG. 10).
From the left side), a swing hydraulic pump 26 and a swing hydraulic motor 27 are installed side by side and installed in a horizontally placed case. Each of the input shaft 26a of the swing hydraulic pump 26 and the output shaft 27a of the swing hydraulic motor 27 is provided. Are rotatably supported in the left-right direction of the airframe and are juxtaposed in the front-rear direction.

On the other hand, as shown in FIGS. 3, 6 and 12, at the upper right portion of the right case portion 22R of the mission case 22, an input case portion 22a extending above the upper surface of the mission case 22 is provided. It is formed to project. The input case portion 22a is formed integrally with the right end portion of the case portion 22R, and a lid 22b is fixed to close the right end opening of the input case portion 22a. Then, on the left side surface of the input case portion 22a facing the upper surface of the mission case 22, the first continuously variable transmission unit 2 for traveling is sequentially installed from the rear of the machine body.
5 and the case of both continuously variable transmission units 25 and 28 are mounted so that the second continuously variable transmission unit 28 for turning can be arranged in parallel. Thus, the first and second continuously variable transmission units 25.2 for traveling and turning are mounted on the mission case 22.
Since the 8 are arranged side by side in the front-back direction of the airframe, the HST device H
Is compactly stored on the mission case 22,
In particular, by arranging them side by side in the front-rear direction of the machine body, the size in the left-right direction can be reduced, and even in the case of a small combine such as two-row or three-row, the two first and second continuously variable transmission units 25 and 28 can be used. Can be equipped. Also, each of the first and second continuously variable transmission units 25
Since the hydraulic pump and hydraulic motor, which are its constituent elements, are arranged in parallel in the machine body front-rear direction, the 28 has a small width in the left-right direction and is compact as a unit.

A traveling system transmission mechanism R and a forward / reverse rotation imparting mechanism S are arranged in the mission case 22, and a power receiving portion Ra of the traveling system transmission mechanism R and a power receiving portion of the forward / reverse rotation imparting mechanism S are arranged. Sa is provided in the input case portion 22a. Then, one end of the output shaft 24a of the traveling hydraulic motor 24 of the traveling first continuously variable transmission unit 25 is inserted and engaged with the transmission gear 42 constituting the power receiving portion Ra,
Further, one end of the output shaft 27a of the turning hydraulic motor 27 of the turning second continuously variable transmission unit 28 is connected to the power receiving portion S.
It is inserted and engaged with the transmission gear 97 which constitutes a.

Further, the power receiving portions Ra and Sa for receiving the power output from the traveling and turning hydraulic motors 24 and 27, which are arranged in parallel in the front-rear direction of the machine body, are provided at the front and rear of the left side surface of the input case portion 22a. Since it is installed in the power transmission, the structure of power transmission is very simple, and it is possible to configure a compact transmission that can be sufficiently mounted even in a small combine.

The first continuously variable transmission unit 25 for traveling
The input shaft 23a of the traveling hydraulic pump 23 projects from the case to the side opposite to the input case portion 22a, and a double input pulley 23b is integrally attached to the input shaft 23a at the end thereof. The input shaft 26a of the turning hydraulic pump 26 projects from the case of the second continuously variable transmission unit 28 for turning to the side opposite to the input case portion 22a, and a series of input pulleys 26b is provided at the end thereof. Are integrally mounted on the input shaft 26a. A transmission belt 30, which is a first endless belt, is wound between one of the input pulleys 23b and the input pulley 26b, and the input shaft 26a of the swing hydraulic pump 26 is connected to the transmission belt 30 and the input pulley 23b. -By 26b, it is interlockingly connected to the input shaft 23a of the traveling hydraulic pump 23. Reference numeral 31 is a tension pulley that adjusts the transmission belt 30 to an appropriate tension. An output pulley 21b is integrally mounted on the output shaft 21a of the engine 21, and a second endless belt is provided between the output pulley 21b and the other input pulley 23b of the traveling hydraulic pump 23. A certain transmission belt 29 is wound. In this way, the input shaft 23a of the traveling hydraulic pump 23 is linked to the engine 21 through the transmission belt 29, the pulley and the like.

Further, a mowing PTO shaft 55 is projected from the side surface of the left side case portion 22L of the mission case 22, and a mowing output pulley 55b which rotates integrally with the mowing PTO shaft 55 is fixedly provided. Output pulley 55
b and the cutting input pulley 1 of the cutting input gear box 120
The reaper transmission belt 122 is wound around 21.
Then, the output of the engine 21 is transmitted to the reaping input gearbox 120 from the auxiliary transmission shaft 53 in the mission case 22 via the gears 56 and 55a.

The first and second continuously variable transmission units 25,
On the upper surface of each of the cases 28, the speed change arms 23c, 26c for the traveling hydraulic pump 23 and the swing hydraulic pump 26 are provided.
Is provided, and the traveling hydraulic pump 23 and the swing hydraulic pump 2 are operated by rotating the speed change arms 23c and 26c.
The movable swash plates 145 and 146 of No. 6 tilt, respectively, and the rotational speed and the rotational direction of the traveling hydraulic motor 24 and the turning hydraulic motor 27 are controlled.

With such a structure, the output of the engine 21 is used for traveling and turning, and the first and second continuously variable transmission units 25, 28.
Input pulley 2 for traveling and turning
Since 3b and 26b are located close to each other and are arranged in substantially the same plane, the transmission belt 29 can be arranged in a narrow space on the side of the mission case 22, and the power transmission structure is simple. -It is possible to make the interconnection structure of the second continuously variable transmission units 25 and 28 compact. Further, the positional relationship in the front-rear direction of the first and second continuously variable transmission units 25 and 28 for traveling and turning, and the front-rear direction of the hydraulic pump and the hydraulic motor in the first and second continuously variable transmission units 25 and 28. The positional relationship is not limited to this embodiment, and can be changed in the front-rear direction as appropriate. Further, the transmission belt 29 that transmits power from the engine 21 may be wound around the input pulley 26b side by making the input pulley 26b a double pulley.

Further, as shown in another embodiment of FIG. 13, the extended end portion of the input shaft 23a which receives the power from the engine 21 in the input pulley 23b of the traveling hydraulic pump 23 and projects toward the input case portion 22a. Output pulley 23d
While mounting the input shaft 26a of the turning hydraulic pump 26
To the case input 22a side, and further, an input pulley 26b is attached to an extended end portion protruding through the input case portion 22a and the lid 22b, and the output pulley 23d and the input pulley 26b are first endless bands. The power of the engine 21 can be simultaneously transmitted to the traveling hydraulic pump 23 and the turning hydraulic pump 26 by winding the transmission belt 30.

Next, the structure of the differential mechanism 33 will be described with reference to FIGS. 4 and 7 to 9. Mission case 22
The differential mechanism 33 is a pair of left and right planetary gear mechanisms 35L.
35R, each planetary gear mechanism 35L / 35R has a sun gear 36L / 36R as a first element, and the sun gear 36L.
・ A plurality of planetary gears 37L meshing on the outer circumference of 36R
37R, the internal gears 38a and 38a that are integrally formed with the ring gears 38L and 38R that are the second elements and that mesh with the planetary gears 37L and 37R, and the sun gear shaft 39.
And carriers 41L and 41R, which are third elements fixed to the axles 40L and 40R on the coaxial line and pivotally supporting the planetary gears 37L and 37R. The planetary gears 37L and 37R are evenly arranged radially from the axles 40L and 40R and are rotatably supported by the carriers 41L and 41R, respectively, and the left and right carriers 41L and 41R are arranged with the left and right sun gears 36L and 36R interposed therebetween. At the same time, the internal gears 38a, 38a mesh with the planetary gears 37L, 37R, are arranged coaxially with the sun gear shaft 39, and are rotatably supported by the axles 40L, 40R.

Then, the left and right sun gears 36L and 36L
R is engraved on the outer peripheral surface of the common sun gear shaft 39, and is interlocked with the traveling system transmission mechanism R including the auxiliary transmission mechanism 32 and the like via a center gear 46 that is locked in the middle portion of both gears 36L and 36R. In addition, in the input part of the traveling system transmission mechanism R,
The transmission gear 42, which is the power receiving portion Ra, is linked to the first continuously variable transmission unit 25. The sub-transmission mechanism 32 has an input gear 44 fixedly mounted on one end of a sub-transmission drive shaft 53 extending laterally from the transmission case 22, and a low-speed gear 50 and a medium-speed gear 51 fixedly mounted on the sub-transmission drive shaft 53. Then
The high speed gear 52 is loosely fitted, and the clutch slider 81 capable of meshing with the high speed gear 52 is slidably spline fitted. Further, gears 47 and 48 are loosely fitted on the auxiliary transmission driven shaft 45 that is rotatably provided horizontally in parallel with the auxiliary transmission drive shaft 53, and the clutch slider 80 is spline-fitted therebetween so that the clutch slider 80 can be meshed therewith. Therefore, the output gear 49 is fixed. The gear 47 and the low speed gear 50, the gear 48 and the medium speed gear 51, and the gear 49 and the high speed gear 52 are constantly meshed with each other. These two clutch sliders 8
0.81 is linked to a single sub-transmission lever provided near the driver's seat, and when the sub-transmission lever is operated, the sub-transmission levers simultaneously slide on the respective shafts 53 and 45, and the clutch slider 80
. 81 is configured to engage with any of the gears 47, 48, 52, and thereby, the auxiliary transmission driven shaft 4
In FIG. 5, three stages of variable speed rotation are obtained and output from the output gear 49.

In this structure, the rotational output of the traveling hydraulic motor 24 is transferred from the output shaft 24a to the input case portion 22.
The gear 43a on the counter shaft 43 and the input gear 44 are transmitted to the sub-transmission mechanism 32 via the transmission gear 42 in the "a", and the sub-transmission mechanism 32 performs gear shifting, and then the output gear 49 to the counter gear 54 and the center gear. The left and right sun gears 36L and 36R are rotationally driven via 46. Then, by transmitting the left and right planetary gear mechanisms 35L and 35R to the axle 40, the left and right drive sprockets 34L and 34R are rotationally driven to drive the crawler type traveling devices 2L and 2R.

On the other hand, the left and right ring gears 38L, 38
R is interlocked with a forward / reverse rotation imparting mechanism S, which includes gears 63c and 63d loosely fitted on the support shaft 63, an idle gear 62a on the idle shaft 62, and the like. The transmission gear 97 which is the power receiving portion Sa for the second continuously variable transmission unit 28 is linked and linked.

Then, the second continuously variable transmission unit 2 for turning.
8, the rotation output of the swing hydraulic motor 27 is transmitted from the output shaft 27a to the transmission gear 97 and the drive gear 9 on the counter shaft 96.
6a, and further via the transmission gear 91 for input, the swing input shaft 90, and the clutch shaft 6 via the clutch device C.
It is transmitted to 1. The turning input shaft 90 is provided with drive gears 90a and 90b having the same number of teeth, and the clutch shaft 61
Clutch gears 61b and 61c, which mesh with the drive gears 90a and 90b at all times, are loosely fitted on the upper side. A clutch slider 61d, which is engageable and disengageable with respect to each of the clutch gears 61b and 61c, is provided between the clutch gears 61b and 61c so as not to rotate relative to the clutch shaft 61.
Moreover, the clutch device C is configured by being installed so as to be slidable in the axial direction. This clutch slider 61
d is the clutch slider 80.8 of the sub transmission mechanism 32 described above.
When the sub transmission mechanism 32 is in the neutral position, it is not engaged with any of the clutch gears 61b and 61c, and is engaged only when the sub transmission mechanism 32 is in the transmission state from the first speed to the third speed. The power from the turning input shaft 90 is transmitted to the clutch shaft 61, and the output gear 6 integrated with the clutch shaft 61.
It is configured to output from 1a.

The output gear 61 on the clutch shaft 61
The rotation of a is directly transmitted to the swing input gear 63b loosely fitted on the support shaft 63, and is transmitted through the gear 63d to the ring gear 38.
It is transmitted to R. With respect to the left ring gear 38L, after the rotation of the output gear 61a on the clutch shaft 61 is reversed by the idle gear 62a on the idle shaft 62,
It is transmitted to the swivel input gear 63a on the support shaft 63, and the gear 63
It is transmitted to the ring gear 38L via c. In this way, the rotation output of the swing hydraulic motor 27 is transmitted so as to drive the left and right ring gears 38L and 38R in mutually opposite rotation directions and at the same left and right rotation speed.

With such a structure, the speed change arm 23c for the movable swash plate 145 of the travel hydraulic pump 23 is interlocked with the main speed change lever 68, which is a travel operation tool arranged near the driver's seat, via a link mechanism. In the first continuously variable transmission unit 25 for traveling, the inclination angle of the movable swash plate 145 is changed by the rotation operation of the main transmission lever 68 so that the traveling hydraulic motor 24 rotates in the forward and reverse directions, and the rotation speed increases and decreases and the rotation is stopped. It is possible to control. Further, the speed change arm 26c for the movable swash plate 146 of the turning hydraulic pump 26 is linked to the steering handle 19 through a link mechanism, and the second continuously variable transmission unit 28 for turning rotates the steering handle 19. The tilt angle of the movable swash plate 146 is changed by the movement to control the forward / reverse rotation direction of the swing hydraulic motor 27, increase / decrease in rotation speed, and control of rotation stop.

When the steering handle 19 is placed in the straight traveling position, the swing hydraulic pump 26 is in the neutral position, the drive of the swing hydraulic motor 27 is stopped, and the left and right ring gears 38 are stationary and fixed. At 68, pressure oil is discharged from the traveling hydraulic pump 23 to drive the traveling hydraulic motor 2
4 is driven, the rotation is transmitted from the center gear 46 to the left and right sun gears 36L and 36R at the same number of revolutions, and the planetary gears 37L and 35L of the left and right planetary gear mechanisms 35L and 35R are transmitted.
The left and right drive sprockets 34L and 34R are driven at the same number of rotations in the same rotation direction in the left and right direction via the 37R and the carriers 41L and 41R, and the forward and straight traveling of the airframe is performed. Further, when the direction of pressure oil discharge from the traveling hydraulic pump 23 is reversed by the main speed change lever 68, the machine body travels straight in a reverse drive state.

When the steering handle 19 is turned to the right,
The swing hydraulic pump 26 is in an operating state and discharges pressure oil,
The turning hydraulic motor 27 is driven by receiving the pressure oil. The power output from the swing hydraulic motor 27 is the swing input shaft 90.
From the clutch device C to the forward / reverse rotation imparting mechanism S, the mechanism is divided into two parts with the same rotation speed, one of which rotates the ring gear 38L of the planetary gear mechanism 35 in the normal direction and the other of which rotates the ring gear 38R in the reverse direction. The rotation speed of the forward rotating ring gear 38L is added to the rotation speed of the left carrier 41L that is normally rotating by the sun gear 36L, while the rotation speed of the reverse rotating ring gear 38R is that of the right carrier 41R that is normally rotating by the sun gear 36R. Subtracts to a number. As a result, the rotational speed of the drive sprocket 34L becomes higher than that of the drive sprocket 34R, and the course is changed to the right while maintaining the drive state of both drive sprockets 34L and 34R.

The amount of oil discharged from the turning hydraulic pump 26 increases as the turning angle of the steering handle 19 increases.
In response to this, the rotation speed of the swing hydraulic motor 27 also continuously increases, so that the relative rotation difference between the left and right drive sprockets 34, 34 gradually increases, and the vehicle body swings with a smaller swing radius. Further, when the steering handle 19 is turned to the left, the pressure oil discharge direction of the swing hydraulic pump 26 is reversed and the rotation direction of the swing hydraulic motor 27 is reversed, which finally reduces the rotation speed of the carrier 41L. On the other hand, the rotation speed of the carrier 41R is added, the rotation speed of the drive sprocket 34R becomes higher than that of the drive sprocket 34L, and the course is changed to the left.

Further, the swing input shaft 90 of the forward / reverse rotation imparting mechanism S
Is equipped with a brake mechanism B for stabilizing straightness. The brake mechanism B is composed of a pair of rotating members, one rotating member is the transmission gear 91 that integrally rotates on the swivel input shaft 90, and the other rotating member is external to the swivel input shaft 90. The braking gear 92 is a friction plate that is fitted and has fewer teeth than the transmission gear 91.
The transmission gear 91 meshes with a drive gear 96a that transmits the power from the turning hydraulic motor 27, and the power is transmitted to the turning input shaft 90 via the transmission gear 91.

Also, a plurality of braking gears 92 (two in this embodiment) are fitted on the swivel input shaft 90 so as to mesh with the drive gear 96a, and a plurality of (three in this embodiment) mating sides are provided. The friction plates 93, 93, 93 are mounted so as to rotate integrally with the turning input shaft 90 so that the braking gear 92 is sandwiched therebetween.
2 is constantly pressed via a pressing plate 94 that receives the spring force of the disc spring 95 received by the lid 22b. Then, by receiving this pressing force, the transmission gear 91, the mating friction plate 93, and the braking gear 92 are always kept in pressure contact.

When power is transmitted from the drive gear 96a in such a configuration, the transmission gear 91 causes the turning input shaft 9 to rotate.
While the power is transmitted to 0, the braking gear 92 to which the power is transmitted by the drive gear 96a has a rotation speed different from that of the transmission gear 91 (the rotation speed is slightly higher than that of the transmission gear 91) on the turning input shaft 90. Rotate. At this time, a relative rotation difference is generated between the transmission gear 91 and the braking gear 92, and the plurality of braking gears 92 and the opposing friction plate 93 are superposed so as to sandwich each other, so that the transmission gear 91 and the opposing friction plate 93 are overlapped. A frictional resistance is generated between 93 and the braking gear 92, and the turning input shaft 9
The brake action against 0 occurs and the swing hydraulic pump 26
Even if the swing hydraulic motor 27 tries to rotate slightly, the swing input shaft 90 is braked, so that the left and right ring gears 38L and 38R are maintained stationary.

A parking brake mechanism T for applying a braking force to the traveling system transmission mechanism R by operating a hand brake (not shown) will be described. First, when the brake arm 113 interlockingly connected to the hand brake is rotationally operated, the cam shaft 110 is interlocked to rotate. And the camshaft 11
Rotation of 0 causes the pressure plate 111 to rotate and a thrust force to the left in FIG. 7 to be generated, so that the friction plate integrally mounted on the auxiliary transmission driven shaft 45 and the friction mounted on the mission case 22 side. The multi-plate friction brake 112 formed by superposition of the plates is pressed. This pressing gives resistance to the auxiliary transmission driven shaft 45 to generate a parking brake action.

Further, as shown in FIGS. 7, 8 and 12, the other end of the input shaft 23a of the traveling hydraulic pump 23 projects to the outside of the case, and the first and second continuously variable transmission units 25.
28 is provided with a charge pump CP for supplying hydraulic oil, and is driven by the power from the input shaft 23a,
Further, the other end of the input shaft 26a of the turning hydraulic pump 26 is also
It projects through the input case portion 22a and the lid body 22b, and an elevating pump SP for the cutting unit is attached to the outer surface of the lid body 22b to transmit power. With this configuration,
Since the input shafts 23a and 26a, which are always rotating, individually transmit the driving force from the engine 21 to the charge pump CP and the lifting pump SP, the structure is simple.
Further, the power of the engine 21 is efficiently transmitted. Further, contrary to the above configuration, the traveling hydraulic pump 2
It is also possible to connect the lifting pump SP to the third input shaft 23a and connect the charge pump CP to the input shaft 26a of the swing hydraulic pump 26.

Next, the hydraulic circuit will be described with reference to FIG. The charge pump CP, the lifting pump SP, the traveling hydraulic pump 23, and the swing hydraulic pump 26 are driven by the engine 21. The hydraulic fluid discharged from the charge pump CP is supplied to the closed circuit of the first continuously variable transmission unit 25 for traveling and the closed circuit of the second continuously variable transmission unit 28 for turning,
The hydraulic oil discharged from the lifting pump SP is introduced into the lifting valve unit 150. The hydraulic oil from the charge pump CP is used as the first continuously variable transmission unit 2 for traveling.
5, a check valve 130 and a throttle 131 are arranged in the portion supplied to the closed circuit, and a check valve 132 and a throttle 133 are arranged in the portion supplied to the closed circuit of the second continuously variable transmission unit 28 for turning. Has been done. A relief valve 143 is arranged at the entrance of the closed circuit of the first continuously variable transmission unit 25 for traveling, and adjusts the supply hydraulic pressure supplied into the closed circuit of the first and second continuously variable transmission units 25 and 28. is doing.

As shown in FIG. 12, the suction sides of the charge pump CP and the lifting hydraulic pump SP are provided with pipes C1 and C2 in suction ports 151 and 152 provided on the outer surface of the case portion 22R of the transmission case 22. Connected through. As shown in FIG. 14, inside the mission case 22, the first and second oil chambers 142 partitioned from each other are provided.
a. 142b is formed, and the first oil chamber 142a is opened to an oil reservoir in which lubricating oil that lubricates gears and the like housed in the transmission case 22 is stored, and a strainer 141 is horizontally installed therein. An exterior oil filter 140 is attached to the outer surface of the case portion 22L of the transmission case 22 via a filter attachment seat 144 so as to face the outlet 141a of the strainer 141. The filter mounting seat 144 receives the filtering oil flowing out from the outlet 141a of the strainer 141 to receive the oil filter 1
40 and the oil filter 14
The filtered oil flowing out from the outlet of 0
The second communication 144b that leads to the second oil chamber 142b via 2a is provided. By disposing the strainer 141 having a coarser mesh than the oil filter 140 on the upstream side of the pump, the frequency of replacement of the oil filter 140 is reduced.

Further, as shown in FIG. 11, on the outer surface of the mission case 22 near the front of the case portion 22L, the raising / lowering valve unit VU capable of raising / lowering the reaping portion 8 to the ground.
Are arranged. That is, the valve case 150 of the lifting valve unit VU is detachably attached to the outer surface of the case portion 22L, the pump port 153 and the cylinder port 155 are provided on the front surface of the valve case 150, the tank port is provided on the lower surface, and the tank port is provided on the upper surface. Is provided with a three-position switching type electromagnetically operated directional control valve 147. The hydraulic oil sent from the lifting pump SP is introduced into the pump port 153.

A directional control valve 147, a load check valve 134, and a slow return valve 135 are arranged in a circuit for supplying hydraulic oil to the hydraulic cylinder 11 for raising and lowering the mowing.
The supply and discharge of the hydraulic oil to and from the hydraulic cylinder 11 are controlled so that the hydraulic oil can be supplied to and discharged from the hydraulic cylinder 11 via the cylinder port 155. Also relief valve 1
The operating hydraulic pressure of the hydraulic cylinder 11 is adjusted by 48. Then, the hydraulic oil discharged from the hydraulic cylinder 11 side passes through the tank port 154 and the oil cooler 14
9 and is cooled in an oil cooler 149 to maintain an appropriate viscosity, and the first for turning and running.
It is returned to the mission case 22 via the insides of the cases of the second continuously variable transmission units 28 and 25.

[0041]

Since the present invention is constructed as described above,
It has the following effects. That is, as set forth in claim 1, of the three elements of the pair of left and right planetary gear mechanisms housed in the mission case, each of the first elements is interlockingly connected to the first continuously variable transmission unit, and each of the second elements is normally and reversely rotated. The second continuously variable transmission unit is interlockingly connected through the imparting mechanism, each of the third elements is interlockedly connected to the left and right axles, and the speed change arm of the first continuously variable transmission unit is interlockedly linked to the traveling operation tool. In a combine transmission in which a speed change arm of a continuously variable transmission unit is linked to a steering operation tool, a first continuously variable transmission unit and a second continuously variable transmission unit of the transmission case are arranged so as to be aligned in the longitudinal direction of the machine body. Since it is attached to one side, two continuously variable transmission units can be compactly stored in the transmission case, and in particular, by installing them side by side in the front-back direction of the machine, the size in the left-right direction can be reduced. Since it was possible to fence, for Nijo, it became possible to use two continuously variable transmission unit even in a small combine such a Sanjo.

Further, among the three elements of the pair of left and right planetary gear mechanisms housed in the mission case as claimed in claim 2, each of the first elements is linked to the first continuously variable transmission unit, and each of the second elements is connected. Interlockingly connected to the second continuously variable transmission unit via the forward and reverse rotation imparting mechanism, interlockingly connecting each of the third elements to the left and right axles, and at the same time interlocking the speed change arm of the first continuously variable transmission unit with the traveling operation tool, In a combine transmission in which a speed change arm of a second continuously variable transmission unit is interlocked with a steering operation tool, an input case portion extending upward from an upper surface of the transmission case is provided on one of left and right sides of the transmission case. , On one side of the input case part,
The traveling system transmission mechanism and the power receiving portions of the forward and reverse rotation imparting mechanism are arranged in parallel in the front-rear direction, and the first continuously variable transmission unit and the second continuously variable transmission unit are arranged in the front-rear direction on one side surface of the input case portion. Since each output shaft is connected in parallel and connected to each power receiving part, the structure of power transmission is very simple, and the transmission can be made compact so that it can be mounted sufficiently even in a small combine. It was.

According to a third aspect of the present invention, the input shafts of the first continuously variable transmission unit and the second continuously variable transmission unit are interlockingly connected via a first endless belt, and any one of the input shafts, Since the engine mounted on the vehicle is interlocked and coupled through the second endless belt, the input shafts of the first and second continuously variable transmission units are close to each other and are arranged on substantially the same plane. The first endless belt can be wound even in a narrow space on the side of the mission case, which simplifies the power transmission structure and enables a compact structure.

Since the input shaft and the output shaft of each of the first continuously variable transmission unit and the second continuously variable transmission unit are parallel to each other in the longitudinal direction of the machine body, It is possible to reduce the width in the left-right direction, and by arranging the input shaft and the output shaft of each unit in parallel, it is possible to arrange the connecting portions for the transmission mechanism of the traveling system and the turning system on substantially the same plane. It is possible, and it has become possible to have a configuration that is simple and has excellent maintainability.

[Brief description of drawings]

FIG. 1 is an overall side view of a combine.

FIG. 2 is also a plan view of the combine.

FIG. 3 is a schematic front view of the combine harvester.

FIG. 4 is a skeleton diagram of a transmission.

FIG. 5 is a schematic perspective view of the entire transmission.

FIG. 6 is a schematic perspective view showing a state in which a continuously variable transmission unit is separated from a transmission.

FIG. 7 is a sectional development view of a transmission including a first continuously variable transmission unit for traveling.

FIG. 8 is a sectional development view of a transmission including a second continuously variable transmission unit for turning.

FIG. 9 is a sectional view of the planetary gear mechanism.

FIG. 10 is a left side sectional view of the transmission.

FIG. 11 is a left side view of the transmission.

FIG. 12 is a right side view of the transmission.

FIG. 13 is a diagram showing another embodiment in which the first continuously variable transmission unit and the second continuously variable transmission unit are interlockedly connected.

FIG. 14 is an enlarged cross-sectional view of an essential part around the oil filter.

FIG. 15 is a hydraulic circuit diagram.

[Explanation of symbols]

22 mission case 22a Input case section 22b Lid (input case part) 23 Traveling hydraulic pump 23a Input shaft 24 Traveling hydraulic motor 24a output shaft 25 First continuously variable transmission unit 26 swing hydraulic pump 26a Input shaft 27 swing hydraulic motor 27a Output shaft 28 Second continuously variable transmission unit 29 Transmission belt (second endless belt) 30 transmission belt (first endless belt) H HST device M transmission Ra power receiving part Sa power receiving part

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Koji Kiyooka             2-18-1 Inadera, Amagasaki, Hyogo Stock             Company Kanzaki Luxury Machinery Works F term (reference) 2B076 AA03 DA02 DA03                 3D039 AA03 AA04 AB13 AB22 AC33                       AC65 AC77 AD33 AD36                 3D052 AA16 AA17 BB08 DD03 DD04                       EE01 FF01 GG03 HH01 HH02                       JJ00 JJ10 JJ21 JJ22 JJ25                       JJ26 JJ31

Claims (4)

[Claims] 1. A pair of left and right planetary gear mechanisms housed in a mission case, wherein each of the first elements is linked to a first continuously variable transmission unit and each of the second elements is provided with a forward and reverse rotation imparting mechanism. Interlockingly connected to the second continuously variable transmission unit via
Each of the third elements is interlocked with the left and right axles, the speed change arm of the first continuously variable transmission unit is interlocked with the traveling operation tool, and the speed change arm of the second continuously variable transmission unit is interlocked with the steering operation tool. The combined transmission, wherein the first continuously variable transmission unit and the second continuously variable transmission unit are attached to one side surface of the transmission case so as to be juxtaposed in the longitudinal direction of the machine body. 2. A pair of left and right planetary gear mechanisms housed in a mission case, of which three first elements are linked to a first continuously variable transmission unit, and each second element is a forward / reverse rotation imparting mechanism. Interlockingly connected to the second continuously variable transmission unit via
Each of the third elements is interlocked with the left and right axles, the speed change arm of the first continuously variable transmission unit is interlocked with the traveling operation tool, and the speed change arm of the second continuously variable transmission unit is interlocked with the steering operation tool. In the combined transmission, the input case portion extending upward from the upper surface of the mission case is provided on one side of the transmission case, and the traveling system transmission mechanism and the forward / reverse rotation are provided on one side surface of the input case portion. The power receiving portions of the applying mechanism are arranged in parallel in the front-rear direction, and the first continuously variable transmission unit and the second continuously variable transmission unit are arranged in parallel in the front-rear direction on one side surface of the input case portion, and their respective output shafts are arranged. A combine transmission characterized in that a power transmission unit is connected to each power receiving unit. 3. An input shaft of each of the first continuously variable transmission unit and the second continuously variable transmission unit is interlockingly coupled via a first endless belt, and is mounted on a vehicle together with any one of the input shafts. The combined transmission according to claim 1 or 2, wherein the engine and the engine are interlockingly connected via a second endless belt. 4. An input shaft and an output shaft of each of the first continuously variable transmission unit and the second continuously variable transmission unit are arranged in parallel in the longitudinal direction of the machine so that they are parallel to each other. 4. The combine transmission according to claim 3.