JPH11139172A - Travel driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To install a gear pivoting pin pivoting a planetary gear with high precision. SOLUTION: A carrier is connected interlockingly to each of left and right central shafts 45L, 45R, and in the carrier, a plurality of pin insertion holes are bored at certain intervals in the circumferential direction. In each of the pin insertion holes, one side end part of a gear pivoting pin is inserted parallelly to the central shafts 45L, 45R, and in the other side end part of the gear pivoting pin, a notch groove is formed substantially orthogonally to the axial line of each gear pivoting pin. In each of the notch grooves, the outer circumferential edge part of a ring type stopper plate is inserted, while each stopper plate is fixed to each carrier. In this way, the respective gear pivoting pins are supported while held in their both sides, and left and right planetary gears are installed freely rotationally in the respective gear pivoting pins.

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 carrier is interlockedly connected to each of left and right central axes, and a plurality of pin insertion holes are formed in the carrier at circumferential intervals.
One end of the gear pivot pin is inserted into each pin insertion hole in parallel with the central axis, and a cutout groove is formed at the other end of each gear pivot pin so as to be substantially orthogonal to the axis of each gear pivot pin. Forming in the direction,
The outer peripheral edge of the ring-shaped detent plate is fitted into each notch groove, fixed to each detent plate, and both ends of each gear pivot pin are supported, and the left and right planetary gears are mounted on each gear pivot pin. Some are mounted to roll freely.

[0003] In the planetary gears, a carrier is mounted on a center shaft, and a plurality of gear pivot pins are provided on the carrier at intervals in the circumferential direction and protrude in parallel with the center shaft. It is mounted on a pivot pin so that it can roll freely.

Here, each gear pivot pin is welded to the carrier.

[0005]

However, in the traveling drive device described above, since each gear pivot pin is welded to the carrier, each gear pivot pin falls down due to welding distortion, and is in a state parallel to the central axis. As a result, the planetary gears mounted on the gear pivot pins may not mesh with the ring gear or the sun gear with high accuracy, resulting in uneven wear or abnormal noise.

[0006]

Therefore, according to the present invention, the rotating power of the hydrostatic continuously variable transmission for traveling is transmitted to the left and right ring gears of the left and right planetary gear mechanisms, respectively, while the hydrostatic continuously variable transmission for turning is transmitted. The rotational power of the machine is transmitted to the left and right sun gears of the left and right planetary gear mechanisms, respectively, 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. In a traveling drive device capable of transmitting rotational power to the left and right drive shafts via the supported left and right center shafts, a carrier is interlocked to each of the left and right center shafts, and a plurality of pin insertion holes are circumferentially spaced in the carrier. The gear pivot pin is inserted into each pin insertion hole with one end of the gear pivot pin parallel to the central axis, and a cutout groove is formed in the other end of each gear pivot pin. In a direction substantially perpendicular to the axis of The outer peripheral edge of the ring-shaped detent plate is fitted into each notch groove, each detent plate is fixed to each carrier, and each gear pivot pin is supported in a double-supported state. A traveling drive device characterized in that left and right planetary gears are rotatably mounted on gear pivot pins.

In the present invention, left and right turning gears for transmitting the rotational power of the hydrostatic stepless transmission for rotation to left and right sun gears are mounted on the left and right central shafts, and each turning gear is formed of a left and right planetary gear. The turning gears are mounted close to each other, and interference avoiding recesses are formed on the outer surface of each turning gear along the circumference. Another feature is that the other end is accommodated.

[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, the rotational power of the hydrostatic continuously variable transmission for traveling is transmitted to the left and right ring gears of the left and right planetary gear mechanisms, respectively, while the rotational power of the hydrostatic continuously variable transmission for turning is
To the left and right sun gears of the left and right planetary gear mechanisms,
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, and the rotational power can be transmitted to the left and right drive shafts via the left and right center shafts supporting each planetary gear. .

The traveling drive device has a characteristic structure in which a carrier is interlockedly connected to the left and right central shafts, and a plurality of pin insertion holes are formed in the carrier at intervals in a circumferential direction. One end of the gear pivot pin is fitted in the hole in parallel with the central axis, and a cutout groove is formed in the other end of each gear pivot pin in a direction substantially orthogonal to the axis of each gear pivot pin. Forming and fitting the outer peripheral edge of the ring-shaped detent plate into each notch groove, fixing each detent plate to each carrier, and supporting each gear pivot pin in a double-supported state,
Left and right planetary gears are rotatably mounted on each gear pivot pin.

In this way, it is possible to prevent each gear pivot pin from falling down. As a result, it is possible to ensure good meshing accuracy of the gears and prevent uneven wear and abnormal noise. can do.

In addition, right and left turning gears for transmitting the rotational power of the turning hydrostatic continuously variable transmission to the left and right sun gears are mounted on the left and right central shafts, and each turning gear is brought close to the left and right planetary gears. Attachment, interference avoidance recesses are formed along the circumference on the outer surface of each turning gear, and the other end of the left and right gear pivot pins that support the left and right planetary gears are accommodated in each interference avoidance recess. doing.

In this way, each turning gear is brought closer to each planetary gear side and further to each ring gear side so that the width in the thrust direction can be reduced and the left and right planetary gear mechanism can be made compact. Can be.

[0014]

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 crawler is driven by a steering wheel 11 provided in the cabin 5 to drive the crawler type traveling unit 1 by the power from the prime mover unit 6 so that the planted 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, 15R on the front left and right sides of a traveling frame 2, respectively, and interlocks the left and right driving wheels 15L, 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 type hydraulic pump and a constant displacement type 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.

The auxiliary transmission mechanism 23, as shown in FIG. 2, connects the output shaft 33 of the traveling hydrostatic continuously variable transmission 27 and the auxiliary 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.

Then, high, middle, and low speed gears 37a, 37b, 37 are mounted on a subtransmission sub shaft 37 which is laid laterally below the sub transmission main shaft 34.
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, 25R has left and right ring gears 41L, 41R on left and right central shafts 45L, 45R, respectively.
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 portions 80L, 80R bulging outward are formed, and the bulging forming portions 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 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 central 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, 85R are formed in the carrier 49L, 49R at intervals in the circumferential direction, and are inserted into the pin insertion holes 85L, 85R in the left-right direction. 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 stopper plates 87L, 87R are fitted into the respective notches 86L, 86R, and are provided with three stopper portions 90L, 90R which function to prevent the rotation of the gear pivot pins 84L, 84R and prevent them from falling off.
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 attached to the outer peripheral edge of each turning gear 46L and 46R.
The left and right ring gears 41L, 41R are formed so as to project toward the left and right ring gears 41L, 41R, and bearing receivers 93L, 93R are provided on outer peripheral edges of the left and right ring gears 41L, 41R.
Formed in the shape of an overhang to the R side, and both bearing receivers 92L, 92R, 93
L and 93R are arranged in a superposed state in the radiation direction of the left and right central axes 45L and 45R, and bearings 94L and 94R are interposed between the bearing receivers 92L, 92R, 93L and 93R, respectively.

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.

In addition, 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 for the left and right planetary gear mechanisms are fitted to the inner ends of the left and right center shafts 45L, 45R, and the final reduction mechanism 26 is driven by the output gears 50L, 50R for the left and right planetary gear mechanisms. 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 manner, 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 projects from the front peripheral surface of the bearing boss 100 toward the front lower side, 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 by projecting the connecting plate body 111 rearward from the rear upper half of the front connecting plate 101 and the rear lower half of the bearing boss 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 shown 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 is provided with the front and rear end portions of the front and rear connection plates 101 and 102 on the front and rear connection seats 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 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 the one left casing forming body 20L via the shaft support 67, and the other right casing forming body 20R is abutted 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 mounted on 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.

At a position directly above the bulging portion 80R formed on the right casing forming body 20R, a cylindrical brake stay 120 is provided 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 as the brake housing space 121 via the brake stay 120, the brake device 40 is traveled to a larger outside than the right casing forming body 20 </ b> R. 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, by operating the brake device 40 on the upstream side of the power transmission system, the braking of the left and right drive shafts 54L, 54R can be reliably performed. 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, and 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 subtransmission 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 turning hydrostatic continuously variable transmission 28 is divided into forward rotation power and reverse rotation power by the forward / reverse rotation mechanism 24, and the rotation of the turning 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 combined 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, 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, 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.

[0064]

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

According to the first aspect of the present invention, the carrier is interlockedly connected to the left and right central shafts, and a plurality of pin insertion holes are formed in the carrier at intervals in the circumferential direction, and the gear is inserted in each pin insertion hole. One end of the pivot pin is fitted in parallel with the central axis, and a notch groove is formed in the other end of each gear pivot pin in a direction substantially orthogonal to the axis of each gear pivot pin. The outer peripheral edge of the ring-shaped detent plate is fitted into each notch groove, each detent plate is fixed to each carrier, each gear pivot pin is supported in a double-supported state, and each gear pivot pin is supported. Since the left and right planetary gears are mounted rotatably on the gears, it is possible to prevent each gear pivot pin from falling down, and as a result, it is possible to ensure good meshing accuracy between the gears, resulting in uneven wear. And abnormal noise can be prevented.

According to the second aspect of the present invention, left and right turning gears for transmitting the rotational power of the hydrostatic stepless transmission for turning to the left and right sun gears are attached to the left and right central shafts, and the turning gears are It is mounted close to the planetary gears, and an interference avoiding recess is formed on the outer surface of each turning gear along the circumference, and the left and right planetary gears (4
To accommodate the other ends of the left and right gear pivot pins that support the gears, each turning gear should be close to each planetary gear side and further to each ring gear side to reduce the width in the thrust direction. The left and right planetary gear mechanism can be made compact.

[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] The rotational power of a traveling hydrostatic continuously variable transmission (27) is transmitted to a left and right ring gear (4) of a left and right planetary gear mechanism (25L, 25R).
1L, 41R), while transmitting the rotational power of the hydrostatic stepless transmission (28) for turning to the left and right sun gears (42L, 42R) of the left and right planetary gear mechanisms (25L, 28R), respectively. The combined rotational power is transmitted to the left and right planetary gears (43L, 43R) interposed between the left and right ring gears (41L, 41R) and the left and right sun gears (42L, 42R), and the respective planetary gears (43L, 43R) The left and right drive shafts (54L, 5R) via the left and right center shafts (45L, 45R)
4R), the carrier (49L, 49R) is interlocked to the left and right central shafts (45L, 45R), and a plurality of pin insertion holes are inserted in the carrier (49L, 49R).
(85L, 85R) are formed at intervals in the circumferential direction, and one end of the gear pivot pin (84L, 84R) is inserted into each pin insertion hole (85L, 85R) by the center shaft (45L, 45R). ) And the notch groove (86L, 86R) at the other end of each gear pivot pin (84L, 84R) in a direction substantially orthogonal to the axis of each gear pivot pin (84L, 84R). Formed, and a ring-shaped detent plate (87L, 8R) is inserted into each notch groove (86L, 86R).
7R) and the detent plates (87
L, 87R) to each carrier (49L, 49R), support each gear pivot pin (84L, 84R) in a double-supported state, and attach the left and right planetary gears to each gear pivot pin (84L, 84R). (43L, 43R) is mounted so as to roll freely. 2. Rotational power of a hydrostatic stepless transmission for turning (28) is applied to left and right central shafts (45L, 45R) by left and right sun gears (42L, 42R).
The right and left turning gears (46L, 46R) for transmitting to the left and right planetary gears (4L, 46R)
3L, 43R), and each turning gear (46L, 46R)
An interference avoiding recess (95L, 95R) is formed along the circumference on the outer surface of the left and right gear pivots for supporting the left and right planetary gears (43L, 43R) in each interference avoiding recess (95L, 95R). The traveling drive device according to claim 1, wherein the other end of the support pin (84L, 84R) is housed.