JPH11139174A - Travel driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To support lateral epicyclic gear mechanisms in a compact state by horizontally laying a shaft support body in a casing, butt-supporting the inner end parts of lateral center shafts provided at the lateral epicyclic gear mechanisms, coaxially by the shaft support body so as to support each center shaft at both ends by the shaft support body and the side wall of the casing. SOLUTION: A cylindrical bearing boss part with its axis placed in a lateral direction, a front side connecting plate formed in a state of projecting downward to the front from the bearing boss part, and a rear side connecting plate formed in a state of projecting backward from the bearing boss part, are integrally formed to constitute a shaft support body 67, and the shaft support body 67 is horizontally provided in a casing 20. The inner end parts of lateral center shafts 45L, 45R are coaxially butt-supported by the shaft support body 67, and the lateral center shafts 45L, 45R are positively supported at both ends by the shaft support body 67 and the side walls of the casing 20. Lateral epicyclic gear mechanisms 25L, 25R can therefore be supported in a compact state.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to a traveling drive device.

[0002]

2. Description of the Related Art Conventionally, as one form of a traveling drive device, a traveling hydrostatic stepless transmission and a turning hydrostatic stepless transmission are individually mounted on a single casing, and are mounted inside the casing. A left and right planetary gear mechanism is provided to transmit the rotational power of the hydrostatic continuously variable transmission for traveling to the left and right ring gears of the left and right planetary gear mechanism, respectively, while the rotational power of the hydrostatic continuously variable transmission for turning is The power is transmitted to the left and right sun gears of the planetary gear mechanism, and the combined rotational power is transmitted to the left and right planetary gears interposed between the left and right ring gears and the left and right sun gears, via the left and right center shafts supporting the respective planetary gears. In some cases, rotational power can be transmitted to left and right drive shafts.

[0003] The left and right planetary gear mechanism has a support shaft mounted horizontally in a casing, and each component is attached to the support shaft.

[0004]

However, in the traveling drive device described above, when assembling the left and right planetary gear mechanisms in the casing, the left and right planetary gear mechanisms are previously attached to the support shaft to support the two planetary gear mechanisms. Since it is necessary to attach the planetary gear mechanism to the casing integrally with the shaft, the operation of attaching the two planetary gear mechanisms is complicated.

In addition, in order to reliably support the left and right planetary gear mechanisms, it is necessary to increase the outer diameter of the support shaft, particularly, the outer diameter of the central portion. The left and right planetary gear mechanisms have also been increased in size and weight, and the mounting work has been complicated from this point as well.

[0006]

Therefore, according to the present invention, a traveling hydrostatic continuously variable transmission and a turning hydrostatic continuously variable transmission are individually mounted on a single casing, and are mounted in the casing. A left and right planetary gear mechanism is provided to transmit the rotational power of the hydrostatic continuously variable transmission for traveling to the left and right ring gears of the left and right planetary gear mechanism, respectively, while the rotational power of the hydrostatic continuously variable transmission for turning is The power is transmitted to the left and right sun gears of the planetary gear mechanism, and the combined rotational power is transmitted to the left and right planetary gears interposed between the left and right ring gears and the left and right sun gears, via the left and right center shafts supporting the respective planetary gears. In a traveling drive device capable of transmitting rotational power to the left and right drive shafts, a shaft support is suspended in the casing, and the inner ends of the left and right center shafts provided on the left and right planetary gear mechanisms by the coaxial support are coaxial. On the line Supporting the mating shape, it is intended to St. provide a travel drive apparatus characterized by the central axis and supported in both ends state by the side wall of the casing and the shaft support, respectively.

In the present invention, the casing is formed by a substantially left-right symmetric casing forming body, and one of the left casing forming bodies is provided with a front connection seat and a rear connection seat.
The front and rear ends of the shaft support are connected to the two connection seats, respectively, and are horizontally mounted. The other right casing forming body is provided with a hydrostatic continuously variable transmission for traveling and a hydrostatic continuously variable transmission for turning. It is also characterized by being attached.

[0008]

Embodiments of the present invention will be described below.

That is, the traveling drive device according to the present invention comprises:
As a basic structure, a hydrostatic continuously variable transmission for traveling and a hydrostatic continuously variable transmission for turning are separately mounted on a single casing, and a left and right planetary gear mechanism is provided in the same casing, The rotational power of the hydrostatic continuously variable transmission is transmitted to the left and right ring gears of the left and right planetary gear mechanisms, respectively, while the rotational power of the turning hydrostatic continuously variable transmission is transmitted to the left and right sun gears of the left and right planetary gear mechanisms. The combined rotational power can be transmitted to the left and right planetary gears interposed between the left and right ring gears and the left and right sun gears, and can be transmitted to the left and right drive shafts via the left and right center shafts that support each planetary gear. And

The traveling drive device has a characteristic structure in which a shaft support is suspended in a casing, and the inner ends of the left and right center shafts provided on the left and right planetary gear mechanisms by the coaxial support are coaxial. The center shafts are supported by the side wall of the casing and the shaft support in a double-supported state.

In this way, the left and right planetary gear mechanisms can be supported compactly and reliably.

Further, the casing is formed by a substantially left-right symmetric casing forming body, and one left casing forming body is provided with a front connection seat and a rear connection seat, and the front and rear ends of the shaft support are provided on both connection seats. The parts are connected to each other and laterally mounted, and a hydrostatic continuously variable transmission for traveling and a hydrostatic continuously variable transmission for turning are mounted on the other right casing forming body.

In this way, the left and right planetary gear mechanisms are assembled to one of the left casing forming bodies via the shaft support, and the other right casing forming body is joined to the left casing forming body to form a casing. By doing so, the assembling work of the traveling drive device can be performed easily.

At this time, since the traveling hydrostatic continuously variable transmission and the turning hydrostatic continuously variable transmission, which are relatively heavy, are mounted on the right casing body, the left casing body is stabilized. The right casing forming body can be easily butt-connected to the left casing forming body in a state of being stood still, and the assembling work efficiency of the traveling drive device can be improved.

[0015]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows a combine B provided with a traveling drive device A according to the present invention.
A substantially horizontal frame-shaped body frame 3 is mounted on the upper surface of a traveling frame 2 equipped with a pair of left and right crawler traveling parts 1,
A mowing unit 4 is connected to the front of the vehicle body frame 3 so as to be able to move up and down, and a cabin 5 containing an operating unit is disposed above a front part of the vehicle body frame 3.
Is arranged, a Glen tank 7 is arranged on the upper right side of the center of the body frame 3, a threshing section 8 is arranged on the upper left side of the center of the body frame 3, and a swing sorting section 9 is arranged below the threshing section 8. The straw processing unit 10 is arranged behind the threshing unit 8.

The steering wheel 11 provided in the cabin 5 is used to drive the crawler-type traveling unit 1 by the power from the motor unit 6 so that the planting grain culm is moved by the cutting unit 4 while traveling in the field. The hulls are harvested and transferred to the threshing unit 8, and the grains are separated from the culm by the handling cylinder 12 and the auxiliary handling cylinder 13 of the threshing unit 8 to be threshed. The grains separated in the threshing unit 8 are separated into paddy and dust in the rocking sorting unit 9, the paddy is transferred to the Glen tank 7, and the dust is discharged out of the machine by the sorting wind The paddy stored in the Glen tank 7 is transferred to a truck or the like via the screw conveyor 14.

The crawler-type traveling unit 1 supports left and right driving wheels 15L and 15R on the front left and right sides of a traveling frame 2, respectively, and interlocks the left and right driving wheels 15L and 15R with a traveling driving device A to be described later. A driven wheel 16 is pivotally supported on the front left and right sides of the traveling frame 2, and a plurality of rolling wheels 17 are pivotally supported on the lower surface of the traveling frame 2, and each of these wheels 15 L, 15 R, 16, 17 The crawler belt 18 is wound around the outer circumference of.

Between the engine 19 of the motor unit 6 and the pair of left and right traveling units 1, not only the power from the engine 19 is transmitted to the left and right traveling units 1, but also the traveling speed of the left and right traveling units 1 is controlled. A traveling drive device A having a function of causing the body to turn differently is provided.

As shown in FIGS. 2 to 4, the traveling drive device A includes left and right casing forming bodies 20L,
20R is combined with a fastening bolt 21 and a nut 22 to form a single casing 20. Inside the casing 20, a sub-transmission mechanism 23, a forward / reverse rotation mechanism 24, left and right planetary gear mechanisms 25L, 25R,
The final deceleration mechanism 26 is housed, and a traveling hydrostatic continuously variable transmission 27 and a turning hydrostatic continuously variable transmission 28 are mounted on the outer surface of the left casing forming body 20L.

The traveling hydrostatic continuously variable transmission 27 and the turning hydrostatic continuously variable transmission 28 are connected to a variable displacement hydraulic pump and a constant displacement hydraulic motor. The hydraulic motor is driven by the pressure oil, and the rotational power from the input shaft 29 is changed from forward to backward by changing the inclination angle of the swash plate of the hydraulic pump. In the drawing, reference numerals 31 and 32 denote operation receiving portions for changing the inclination angle of the swash plate in conjunction with the swash plate, respectively.The operation receiving portion 31 of the hydrostatic continuously variable transmission 27 for traveling includes: It is interlockingly connected with the shift lever arranged in the cabin 5,
The operation receiving portion 32 of the turning hydrostatic continuously variable transmission 28 is connected to the steering wheel 11 in an interlocked manner.

As shown in FIG. 2, the sub-transmission mechanism 23 connects the output shaft 33 of the traveling hydrostatic continuously variable transmission 27 and the sub-transmission main shaft 34 in an interlocked manner via meshing gears 33a, 34a. Sub transmission main shaft 34
The first, second, and third transmission gears 35a, 35b, and 35c are coaxially and loosely fitted to the gears 35a, 35b, and 35c, respectively.
The second neutral gears 35d and 35e are mounted coaxially, and a first slider 36a is provided between the first transmission gear 35a and the first neutral gear 35d.
Forming a dog clutch through the second transmission gear
A dog clutch is formed between 35b, the second neutral gear 35e, and the third transmission gear 35c via a second slider 36b.

A high-, medium-, and low-speed gear 37a, 37b, 37
c, the high-speed gear 37a meshes with the first transmission gear 35a, the middle-speed gear 37b meshes with the second transmission gear 35b, and the low-speed gear 37c The transmission gear 35c is engaged with the transmission gear 35c.

Thus, the first and second sliders 36
a, 36b, respectively, to enable high, middle, and low speed three-stage shifting, and a hydrostatic continuously variable transmission 27 for traveling.
The transmission range has been extended. In the figure, reference numeral 40 denotes a brake device interlockingly connected to the subtransmission countershaft 37.

The left and right planetary gear mechanisms 25L and 25R have the same configuration and are arranged at symmetric positions with respect to the center line of the casing 20.

Each of the planetary gear mechanisms 25L and 25R has left and right ring gears 41L and 41R respectively attached to left and right central shafts 45L and 45R.
And left and right sun gears 42L and 42R and left and right planetary gears 43L and 43R are coaxially mounted.

At the center of the left and right casing forming bodies 20L, 20R, bulging forming parts 80L, 80R bulging outward are formed, and the bulging forming parts 80L, 80R have their left and right axes oriented in the left and right direction. Center axis
The outer ends of the 45L and 45R are pivotally supported via bearings 81L and 81R, and the inner ends of the left and right central shafts 45L and 45R are mounted on bearings 82L and It pivots via 82R.

The bearings 81L, 81R pivotally supporting the outer ends of the respective central shafts 45L, 45R and the bearings 83L, 83R arranged along the inner peripheral surfaces of the bulging portions 80L, 80R. The base gears of the left and right ring gears 41L, 41R are pivotally supported.

In the middle of each of the center shafts 45L, 45R, cylindrical left and right sun gears 42L, 42R are rotatably and loosely fitted, respectively.
L, 81R, the left and right central shafts 45L, 45R are provided with carriers 49L, 49R that support the left and right planetary gears 43L, 43R.
Are spline-fitted to the base edge of each carrier, and three planetary gears 43L, 43R are attached to the top edge of each carrier 49L, 49R by gear pivot pins 84L,
The planet gears 43L, 43R are rotatably mounted via 84R, and mesh with the ring gears 41L, 41R and the sun gears 42L, 42R.

As shown in FIG. 5, three pin insertion holes 85L and 85R are formed in the carrier 49L and 49R at intervals in the circumferential direction, and are inserted into the pin insertion holes 85L and 85R in the left and right directions. The outer ends of the gear pivot pins 84L, 84R whose axes are directed to the shaft are fitted into the gear pivot pins 84L, 84R, and the notch grooves 86L, 86R are inserted into the inner ends of the gear pivot pins 84L, 84R with the axes of the gear pivot pins 84L, 84R. It is formed in a direction substantially perpendicular to each notch groove 86L, 86R and has a ring-shaped detent plate 87L, 87R.
The outer peripheral edge of the carrier 49L,
49R is fixed to outer peripheral edges 88L, 88R via fixing bolts 89L, 89R.

The three stopper portions 90L, 90R which fit into the notch grooves 86L, 86R of the detent plates 87L, 87R to perform the detent and detent functions of the gear pivot pins 84L, 84R.
Are formed at intervals in the circumferential direction, and three long holes 91L and 91R for inserting bolts are formed at intervals in the circumferential direction.

Thus, the gear pivot pins 84L, 84R
The detent plate 87 has its base end inserted into the pin insertion holes 85L and 85R, and its distal end inserted into the cutout grooves 86L and 86R.
In order to fix to the carrier 49L, 49R by L, 87R, each gear pivot pin 84L, 84R can be supported in a face-to-face state, and the gear pivot pin 84L, 84R can be prevented from falling down, As a result, the meshing accuracy of the gears can be ensured well, and uneven wear and abnormal noise can be prevented.

At this time, the stopper portions 90L, 90R formed on the detent plates 87L, 87R are respectively connected to the gear pivot pins 84L, 84R.
The locking plates 87L, 87R are fixed to the carriers 49L, 49R through the bolt holes 91L, 91R while being pressed into the notch grooves 86L, 86R of the gears and pressed against the gear pivot pins 84L, 84R. Since it is fixed with the bolts 89L and 89R, there is no backlash around the axis of the gear pivot pins 84L and 84R, and microvibration friction can be prevented. As a result, durability can be improved. .

Left and right turning gears 46L and 46R are fitted to the inner ends of the left and right sun gears 42L and 42R, respectively, and bearing receivers 92L and 92R are mounted on the outer peripheral edge of each turning gear 46L and 46R.
R is formed so as to project toward the left and right ring gears 41L and 41R, and bearing receivers 93L and 93R are formed on the outer peripheral portions of the left and right ring gears 41L and 41R so as to project toward the left and right turning gears 46L and 46R. Both bearing receivers 92L, 92R, 93L, 93R are arranged in a superposed state in the radiation direction of the left and right central axes 45L, 45R, and bearings are placed between the two bearing receivers 92L, 92R, 93L, 93R, respectively.
94L and 94R are interposed.

Thus, the left and right ring gears 41L, 41R
Of the bearings 83L, 83R, which support the base edges of the ring gears 41L, 41R, by supporting the outer peripheral edge of the ring gears 41L, 41R in a double-supported state. The durability can be improved, and the left and right turning gears 46L, 46R are connected to the ring gears 41L, 41R.
Close to the R side, the width in the thrust direction can be reduced, and compactness can be achieved.

Further, on the outer surfaces of the left and right turning gears 46L, 46R, interference avoiding recesses 95L, 95R are formed along the circumference, and the gear pivots are provided in the interference avoiding recesses 95L, 95R. By accommodating the inner ends of the pins 84L and 84R and the heads of the fixing bolts 89L and 89R, the turning gears 46L and 46R can be brought closer to the respective ring gears 41L and 41R. The ring gears 41L and 41R can be compactly supported at both ends.

Output gears 50L, 50R of the left and right planetary gear mechanism are fitted to the inner ends of the left and right central shafts 45L, 45R, and the reduction gears of the final reduction mechanism 26 are attached to the left and right planetary gear mechanism output gears 50L, 50R. The left and right final reduction driving gears 53L and 53R fitted to the left and right final reduction passive gears 52L and 52R respectively mesh with the left and right final reduction passive gears 52L and 52R that are supported on the shaft 51, and the left and right driving shafts 54L and 52R.
The left and right drive shafts 54L, 54R are engaged with the left and right drive shaft gears 55L, 55R fitted to the inner end of the
It is linked to 15R.

As shown in FIGS. 3 and 4, the forward / reverse rotation mechanism 24 has an output gear 57 fitted on an output shaft 56 of a hydrostatic continuously variable transmission 28 for rotation fitted on an intermediate shaft 58. Passive positive rotation gear 59
And the passive positive rotation gear 59 is connected to the right turning gear 46.
R, and a passive reverse rotation gear 61 fitted on the counter shaft 60 with the passive forward rotation gear 59, and a reverse output gear spline fitted coaxially with the passive reverse rotation gear 61 and the counter shaft 60. 48 is meshed with the left turning gear 46L.

The inner ends of the left and right central shafts 45L, 45R are:
As shown in FIGS. 2 to 4, the shaft support 67 is supported by the shaft support 67 on the same axis in abutting manner.
As shown in FIGS. 6 and 7, a cylindrical bearing boss portion 100 whose axis is oriented in the left-right direction, and a plate-shaped front side connection formed to project forward and downward from the bearing boss portion 100. Board 10
1 and a front connecting plate 101 and a rear connecting plate 102, which is formed in a projecting shape rearward from the bearing boss 100, are integrally formed.

As shown in FIGS. 6 and 7, the bearing boss portion 100 accommodates a pair of left and right bearings 82L and 82R therein, and the left and right central shafts 45L and 45R via the bearings 82L and 82R.
The inner end of the bearing. 103 is a spacer.

The outer peripheral edges of the left and right ends of the bearing boss 100 are formed with tapered surfaces 104, 104.

In this way, the bearing boss portion 100 is formed as wide as possible on the left and right sides to ensure the support of the left and right center shafts 45L and 45R, and the left and right outer ends disposed on the left and right outer sides. The left and right end portions of the bearing boss portion 100 can be accommodated closely without interference in the interference avoiding concave portions 105, 105 formed on the inner surfaces of the reduction passive gears 52L, 52R.

The front connecting plate 101 is formed such that the connecting plate main body 106 extends forward and downward from the front peripheral surface of the bearing boss 100, and three connecting bolts are inserted through the front end edge of the connecting plate main body 106. The holes 107, 107, 107 are formed on the same virtual arc centered on the axis of the bearing boss 100, and the reinforcing ribs 108 are connected to each other on a virtual straight line connecting the center of each connecting bolt insertion hole 107 and the center of the bearing boss 100. Bolt insertion hole 107 and bearing boss 100
Are integrally formed with the connecting plate body 106, and each reinforcing rib 108,
Circular holes 109, 109 for reducing the load and relieving stress are formed between the openings 108 and at the front end side of the connecting plate body 106. 110 is a positioning pin insertion hole.

The rear connecting plate 102 is formed such that the connecting plate main body 111 projects rearward from the upper rear half of the front connecting plate 101 and the rear lower half of the bearing boss portion 100. Connecting plate body
Two connecting bolt insertion holes 107, 107 are formed on the imaginary vertical line at the rear edge of the rear end 111, and upper and lower reinforcing ribs 112, 113 extending substantially horizontally in the front-rear direction are integrally formed on the upper part of the connecting plate main body 111, and are connected together. At the lower edge of the plate body 111, the reinforcing ribs 11 are formed on an imaginary straight line connecting the middle of the reinforcing ribs 108 located on the rear side of the front connecting plate 101 and the lower connecting bolt insertion holes 107.
4 is integrally molded.

Here, the front and rear connecting plates 101 and 102 are the same as those in FIG.
As shown in the figure, the bearing boss portion 100 is deviated to the right side from the center line position of the left and right, and a left casing forming body described later is formed.
When connected to the front / rear connection seats 116, 117 formed in 20L, the left and right center lines of the bearing boss 100 are positioned on the butting surfaces 115L, 115R of the left and right casing forming bodies 20L, 20R.

FIG. 3 shows the inner surface of the left casing forming body 20L.
4, a front connection seat 116 and a rear connection seat 117 are formed close to the front edge and the rear edge, respectively, and the front connection seat 116 is connected to the front connection plate 101. A connection bolt hole 118 and a positioning pin 119 are formed to correspond to the bolt insertion hole 107 and the positioning pin insertion hole 110, respectively, and the rear connection seat 117 is provided with the connection bolt insertion hole 107 of the rear connection plate 102. A connecting bolt hole 118 and a positioning pin 119 corresponding to the positioning pin insertion hole 110 are formed. 123 is a reinforcing rib, and 124 is a connecting bolt.

In this manner, the shaft support 67 has the front and rear connection plates 101 and 102 with the front and rear ends of the front and rear connection plates 116 and 117 formed on the left casing forming body 20L, and the connection bolt insertion holes. 107 and the connecting bolt 124 via the connecting bolt hole 118, and the center boss
The inner ends of the 45L and 45R can be reliably supported.

At this time, a plurality of connecting bolt insertion holes 107 formed in the front and rear connecting plates 101 and 102 are formed at positions facing the front and rear with respect to the bearing boss portion 100, and the front connecting plates 107 which receive a large gear reaction force. The upper and lower widths of 101 are formed to be wider than the upper and lower widths of the rear connecting plate 102, and a number of connecting bolt insertion holes 107 are formed on the front connecting plate 101 side.
Is fixed more firmly than the rear connecting plate 102.

Here, the shaft support 67 traverses the left casing forming body 20L in the front-rear direction as described above, while the traveling hydrostatic continuously variable transmission 27 and the turning hydrostatic continuously variable transmission 27 are provided. 28
Are individually mounted on the upper part of the right casing forming body 20R.

In this manner, the left and right planetary gear mechanisms 25L and 25R are assembled to one left casing forming body 20L via the shaft support 67, and the other right casing forming body 20R is butted to the left casing forming body 20L. Connected to the casing 20
By assembling, the assembling work of the traveling drive device A can be easily performed.

At this time, since the traveling hydrostatic continuously variable transmission 27 and the turning hydrostatic continuously variable transmission 28, which are relatively heavy objects, are attached to the right casing forming body 20R, the left casing is formed. The right casing forming body 20R can be easily butt-connected to the left casing forming body 20L while the body 20L is standing still with good stability, and the assembling work efficiency can be improved.

Further, a cylindrical brake stay 120 is provided immediately above the bulging portion 80R formed on the right casing forming body 20R with a width substantially equal to the bulging width of the bulging forming portion 80R. By forming the lower side integrally with the bulge forming part 80R, the brake accommodation space is provided in the brake stay 120.
The brake device 40 is housed in the brake housing space 121, and the brake device 40 is detachably mounted on the brake stay 120 by mounting bolts 122. The brake device 40 is mounted on the right casing forming body 20R. It is interlockingly connected to a sub transmission sub shaft 37 that protrudes outward.

The brake device 40 is connected to the sub-transmission sub shaft 37.
Multi-disc brake body 40a linked to the right end 37d of the
And a brake operating arm 40b operatively connected to the multi-plate type brake main body 40a.
Further, a brake operating means (not shown) provided in the cabin 5 is interlockingly connected to operate the brake operating means, so that the multi-disc brake body 40a can be braked. 40c is a restoration spring.

In this way, the concave space as a dead space formed just above the bulging portion 80R is
Since the brake device 40 is housed in the brake housing space 121 via the brake stay 120 to form the brake housing space 121, the brake device 40 is traveled outward more than the right casing forming body 20R. It can be arranged compactly without the need.

As a result, the casing 20 itself can be made compact, and the entire traveling drive unit A can be made compact, so that the assembly work of the traveling drive unit A can be simplified.

Further, the brake device 40 is operated on the upstream side of the power transmission system, so that the brakes of the left and right drive shafts 54L, 54R can be surely braked. It is possible to reduce the size and to simplify the assembling work of the traveling drive device A from this point as well.

The embodiment of the present invention is constructed as described above. The power from the traveling hydrostatic continuously variable transmission 27 and the turning hydrostatic continuously variable transmission 28 is controlled by the following manner. Drive shaft 54
L, 54R.

That is, the rotational power of the traveling hydrostatic continuously variable transmission 27 is shifted to any one of a high speed, a medium speed, and a low speed by the auxiliary transmission mechanism 23, and the left and right ring gears of the left and right planetary gear mechanisms 25L and 25R. It is transmitted to 41L and 41R.

The rotational power of the hydrostatic continuously variable transmission 28 is divided into forward and reverse rotational power by the forward / reverse rotation mechanism 24, and the rotation of the hydrostatic continuously variable transmission 28 is rotated. The forward rotation power in the same direction is transmitted to the right sun gear 42R of the right planetary gear mechanism 25R, and the reverse rotation power is transmitted to the left sun gear 42L of the left planetary gear mechanism 25L.

The rotational power of the hydrostatic continuously variable transmission 27 for traveling and the rotational power of the hydrostatic continuously variable transmission 28 for turning are synthesized separately by the left and right planetary gear mechanisms 25L and 25R. ,
The power is transmitted to the left and right drive wheels 15L, 15R via the left and right drive shafts 54L, 54R.

Therefore, when the turning hydrostatic continuously variable transmission 28 is stopped, the left and right drive shafts 54L and 54R rotate at the same rotation speed to move the machine straight. When the steering wheel 11 is operated to rotate the turning hydrostatic continuously variable transmission 28, one of the left and right drive wheels 15L and 15R is accelerated, and the other is decelerated, so that the aircraft is decelerated. Will turn to the side.

Further, on the upper outer surface of the right casing forming body 20R, there is provided an electromagnetic hydraulic directional control valve 68 which operates in conjunction with the forward / reverse switching operation of the main shift lever, and the switching operation of the electromagnetic hydraulic directional control valve 68 is performed. By switching the reciprocating oil passage between the pump section and the motor section of the hydrostatic continuously variable transmission 28 for turning, the hydrostatic continuously variable transmission for turning
When the main transmission lever is operated in reverse and the main shift lever is operated in reverse, the hydrostatic continuously variable transmission for turning 28 is rotated in reverse to turn the steering wheel 11 in the direction in which the steering wheel 11 is turned regardless of forward / backward movement. I try to make it.

Further, the left end of the auxiliary transmission main shaft 34 is projected outside the left casing forming body 20L, and a one-way clutch 70 is mounted on the projected end, and a pulley 71 formed on the outer periphery of the one-way clutch 70 is attached to the one-way clutch 70. Power is supplied to the mowing unit 4 through the wound belt, and the one-way clutch 70
Is an inner race 72 fixedly fitted to the auxiliary transmission main shaft 34.
And an outer race 73 externally fitted to the inner race 72 so as to be rotatable in one direction and non-rotatable in the opposite direction, and the outer race 73 is a bearing provided at the inner and outer ends.
The auxiliary transmission main shaft 34 supports the sub transmission main shaft 34 in a double-supported state.

As described above, since the outer race 73 is supported in a double-supported state, the pulley 71 is stabilized, and the outer end of the outer race 73 is closed with the bore plug 76, and the oil seal 77 is provided at the inner end. The internal structure of the one-way clutch 70 and the one-way clutch 70 can be protected.

[0065]

According to the present invention, the following effects can be obtained.

According to the first aspect of the present invention, the shaft support is suspended in the casing, and the inner ends of the left and right central shafts provided on the left and right planetary gear mechanisms by the coaxial support are abutted on the same axis. , And each center shaft is supported in a double-supported state by the side wall of the casing and the shaft support, so that the left and right planetary gear mechanisms can be supported compactly and reliably.

According to the second aspect of the present invention, the casing is formed by a left-right casing forming body that is substantially symmetrical, and one of the left casing forming bodies is provided with a front connection seat and a rear connection seat. The front and rear ends of the shaft support are connected to each other, and the shaft support is laterally connected. A hydrostatic continuously variable transmission for traveling and a hydrostatic continuously variable transmission for turning are mounted on the other right casing forming body. For this purpose, the left and right planetary gear mechanisms are assembled to one left casing forming body via a shaft support, and the other right casing forming body is butt-connected to the left casing forming body to form a casing. The assembling work of the driving device can be easily performed.

At this time, since the traveling hydrostatic continuously variable transmission and the turning hydrostatic continuously variable transmission, which are relatively heavy objects, are mounted on the right casing body, the left casing body is stabilized. The right casing forming body can be easily butt-connected to the left casing forming body in a state of being stood still, and the assembling work efficiency of the traveling drive device can be improved.

[Brief description of the drawings]

FIG. 1 is a side view of a combine provided with a traveling drive device according to the present invention.

FIG. 2 is a sectional front view of the traveling drive device.

FIG. 3 is a sectional front view of the traveling drive device.

FIG. 4 is an explanatory side view showing a power transmission path of the traveling drive device.

FIG. 5 is an enlarged front view of a detent plate.

FIG. 6 is a side view of the shaft support.

FIG. 7 is a sectional view taken along line II of FIG. 6;

[Explanation of symbols]

 A traveling drive device 15L, 15R left and right drive wheels 20 casing 20L, 20R left and right casing forming body 23 auxiliary transmission mechanism 24 forward and reverse rotation mechanism 25L, 25R left and right planetary gear mechanism 27 hydrostatic continuously variable transmission for traveling 28 static hydraulic for turning Type continuously variable transmission 33 Output shaft of hydrostatic continuously variable transmission for traveling 41L, 41R Left and right ring gears 42L, 42R Left and right sun gears 43L, 43R Left and right planetary gears 45L, 45R Left and right center shafts 54L, 54R Left and right drive shafts 56 Output shaft of hydraulic continuously variable transmission 67 Shaft support

Claims (2)

[Claims] 1. A traveling hydrostatic continuously variable transmission (27) and a turning hydrostatic continuously variable transmission (28) are individually mounted on a single casing (20), and the casing (20) A left and right planetary gear mechanism (25L, 25R) is installed inside the
The rotational power of (7) is transmitted to the left and right ring gears (41L, 41R) of the left and right planetary gear mechanisms (25L, 25R), while the rotational power of the hydrostatic stepless transmission for turning (28) is transmitted to the left and right planetary gears. The right and left planetary gears (43L, 43R) are transmitted between the left and right ring gears (41L, 41R) and the left and right sun gears (42L, 42R) by transmitting the right and left sun gears (42L, 42R) of the mechanism (25L, 28R), respectively. ), And transmits the combined rotational power to the left and right drive shafts (54L, 5R) via the left and right center shafts (45L, 45R) that support each planetary gear (43L, 43R).
4R), the shaft drive (67) is laid horizontally in the casing (20), and the left and right planetary gear mechanisms (25L, 25R) are moved by the coaxial support (67). The inner ends of the left and right central shafts (45L, 45R) are supported in abutting fashion on the same axis, and each central shaft (45L, 45R) is
A traveling drive device characterized by being supported in a double-supported state by the side wall of (20) and the shaft support (67). 2. The casing (20) is formed by left and right casing forming bodies (20L, 20R) which are substantially symmetrical left and right, and one of the left casing forming bodies (20L) has a front connecting seat (116) and a rear connecting seat (20L). 117), the front and rear ends of the shaft support (67) are connected to both connection seats (116, 117), respectively, and are laterally mounted. The traveling drive device according to claim 1, wherein a continuously variable transmission (27) and a turning hydrostatic continuously variable transmission (28) are mounted.