JP2001278106A - Turning operation device of mobile vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve on the inefficiently-used power and unsafety of a less- frequently-used hydraulic continuously variable transmission for turning, caused because a hydraulic continuously variable transmission for traveling mounted on a conventional traveling transmission device and the hydraulic continuously variable transmission for turning are provided with constantly-driven transmission compositions. SOLUTION: In a turning operation device of a mobile vehicle, the hydraulic continuously variable transmissions 7, 8 for traveling and turning are connected for input to a transmission case 3 for transmitting rotational power to traveling crawlers 1, 1'. The transmission 8 is driven for output in a rotational manner in the case of the gear shifting operation of a power steering lever 9 under the condition that a main gear-shifting lever 10 for the shift operation of the transmission 7 is located in a gear-shifting-operation position.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turning operation device for a moving vehicle, and belongs to the technical field of a vehicle traveling mission device.

[0002]

2. Description of the Related Art Conventionally, a traveling mission device for a mobile vehicle equipped with a traveling crawler is disclosed, for example, in Japanese Patent Laid-Open No. 10-95.
No. 362, JP-A-11-291935, rotational power is input from a hydraulic stepless transmission for traveling and a hydraulic stepless transmission for turning, and a planetary gear mechanism as a turning mechanism, or A technology that enables a straight traveling and a turning traveling using a differential mechanism has been disclosed. The traveling transmission device according to the prior art operates the main transmission lever, the steering lever (steering handle), and the auxiliary transmission lever independently, so that not only straight traveling but also normal turning traveling (brake). (Turn), gentle turning, sharp turning (spin turn, spin turn), and the like.

[0003]

According to the above-mentioned prior art disclosed in the prior art, a hydraulic continuously variable transmission for inputting power for traveling to a traveling transmission device and a hydraulic continuously variable transmission for inputting power for turning, It has a transmission configuration that is always driven.
In particular, the hydraulic continuously variable transmission for turning is constantly driven despite its less frequent use as compared with the hydraulic continuously variable transmission for traveling. There was a problem that went against efficient use.

The hydraulic continuously variable transmission for traveling and the hydraulic continuously variable transmission for turning operate in association with each other at the time of turning traveling. However, in the conventional device, the interlocking mechanism between the two is complicated and adjustment is required. Was difficult to maintain. In the configuration according to the prior art, when the sub-transmission is operated to change the traveling speed in the field at the time of work and switch to turning traveling, the left and right traveling crawler shifts at each traveling speed (medium speed, low speed). There was a problem that the turning radius was different due to a change in the ratio.

[0005]

The present invention employs the following technical means to solve the above-mentioned problems. First, the invention according to claim 1 is based on the traveling crawler 1, 1 '.
A pair of left and right wheel shafts 2 for transmitting rotational power to
The transmission case 3 on which the 2 'is mounted has an auxiliary transmission 4
And a pair of left and right side clutches 5 and 5 'and a differential gear device 6 are provided therein.
A hydraulic continuously variable transmission 7 for traveling inputted from the side of the auxiliary transmission 4 and a hydraulic continuously variable transmission 8 for turning inputted from the side of the differential gear device 6 are provided so as to be connected to each other. Power steering 9 for shifting the hydraulic continuously variable transmission 8 for turning
And a main transmission lever 10 for shifting the hydraulic continuously variable transmission 7 for traveling is provided by a restricting device 11. The restricting device 11 is configured such that the main transmission lever 10 controls the speed of the transmission. The power transmission device 8 is connected to the operation force transmission means 12 so that the operation force of the power telescopic lever 9 is transmitted to the turning hydraulic continuously variable transmission 8 only when the power telescopic lever 9 is in the position. A turning operation device for a mobile vehicle, which is configured to be driven and output when the power steering lever 9 is shifted, provided that the main shift lever 10 is at a shift operation position.

Next, a second aspect of the present invention is directed to
The transmission position transmission means 13 and the operation adjusting device 14 of the power telescopic transmission 9 can adjust the operation amount from the power telescopic transmission 9 to the hydraulic stepless transmission 8 for turning according to the transmission position of the auxiliary transmission 4. The hydraulic continuously variable transmission 8 for turning is provided with an interlocking device 15 so that the speed ratio of the left and right traveling crawlers 1, 1 'is substantially equal regardless of the shift position of the auxiliary transmission 4. The turning operation device for a mobile vehicle according to claim 1, wherein the turning operation device is configured to output a rotating power capable of obtaining substantially the same turning radius while holding the turning power.

Next, according to the third aspect of the present invention, one of the turning amount adjusting links 16 constituting the operating force transmitting means 12 is pivotally supported on the power telescopic lever 9, and the other is a hydraulic stepless turning step. The turning amount adjusting link 16 is provided so as to be pivotally connected to a lot 17 that transmits an operating force to the transmission 8.
A position where the pivot point a of the power steering lever 9 coincides with an imaginary extension line of the operation rotation fulcrum shaft 18 of the power telescopic lever 9 is configured as a neutral position where no operation force is transmitted.
The turning operation device for a mobile vehicle according to claim 1, wherein the turning operation device is configured to be connected to the main transmission lever 10 via a regulating device 11 so as to be interlocked therewith.

Next, a fourth aspect of the present invention relates to a main transmission lever.
ON in connection with the speed change operation between the power transmission 10 and the power steering 9;
Two detection switches 19a and 19b that are turned off are provided, and the detection switches 19a and 19b are connected by a circuit wired in series, and both the main transmission lever 10 and the power steering lever 9 are in the transmission position. , The rotational power is transmitted to the hydraulic stepless transmission 8 for turning.

[0009]

As described above, the present invention is configured as described above, so that the turning hydraulic continuously variable transmission can be transmitted to the traveling transmission device when turning power is required when the turning power is required. Therefore, the configuration according to the present invention was able to improve safety, effectively use power without wasting power, and increase mechanical efficiency.

[0010] The hydraulic continuously variable transmission for traveling and the hydraulic continuously variable transmission for turning according to the present invention can relatively easily form an interlocking mechanism between them.
, The maintenance such as adjustment can be easily performed as compared with the conventional device.

Further, according to the configuration of the present invention, the turning radius at the time of work in the field can be changed regardless of the traveling speed by selecting the medium speed or the low speed by switching the sub-transmission. It is characterized in that the vehicle can turn on a similar trajectory while keeping the speed ratio of the left and right traveling rollers substantially equal.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be specifically described below. First, the traveling mission device 20 is shown in FIG.
As shown in FIG. 1, a hydraulic stepless transmission 7 for traveling and a hydraulic stepless transmission 8 for turning are provided outside a transmission case 3 in which a series of transmission mechanisms are installed.
The hydraulic continuously variable transmission 7 for traveling uses the engine 21
The rotational driving force transmitted to the transmission shaft 24 via the two pulleys 22 and 22 'and the belt 23 from the traveling hydraulic pump 7
a is transmitted. The hydraulic continuously variable transmission 7 is configured to supply hydraulic oil from the traveling hydraulic pump 7a to the traveling hydraulic motor 7b so as to switch between forward and reverse rotations and to output variable speed rotational power from the output shaft 25. The main transmission lever 10 (see FIG. 9) is operably connected to the traveling hydraulic pump 7a, and is configured to be capable of switching between acceleration / deceleration shift and forward / reverse (switching between forward and reverse rotation).

Next, the hydraulic stepless transmission 8 for turning is
As shown in FIG. 1, the swing hydraulic pump 8a and the swing hydraulic motor
The rotary hydraulic pump 8a has a transmission configuration in which the rotational driving force from the engine 21 is input from the pulley 26 of the transmission shaft 24 via the belt 27 and the pulley 28. . As shown in FIG. 1, the clutch 29 is provided between the pulley 28 and the swing hydraulic pump 8a, and is connected in connection with the steering operation of the power steering lever 9 and the main transmission lever 10. And

In the case of the embodiment, as shown in FIG. 1, detection switches 19a and 19b are provided below the main speed lever 10 and the power telescopic lever 9, and both levers 9 and 1 are provided.
It is configured to detect a shift operation position of 0 (a position other than the neutral position). Then, the two detection switches 1
9a and 19b are connected by a circuit wired in series, and when it is detected that both the main transmission lever 10 and the power steering lever 9 are in the transmission position, the clutch 29 is engaged to be in the transmission state, and the vehicle turns. The rotational power is transmitted to the hydraulic stepless transmission 8 for use.

With the above configuration, the turning hydraulic continuously variable transmission 8 is driven only when turning output is required,
There is an advantage that unnecessary power loss is eliminated and the efficiency of the machine is improved. Further, the hydraulic continuously variable transmission 8 is characterized in that the clutch 29 fulfills a safety function, the neutral width of the power telescopic lever 9 can be widened, and safety is improved.

The power steering lever 9 is operably connected to the slewing hydraulic pump 8a so that the output from the slewing hydraulic motor 8b can be adjusted by a speed-change operation. In the case of the embodiment, as shown in FIG. 1, the hydraulic stepless transmission 8 for turning is provided at a lower position of the transmission case 3 to transmit rotational power to the differential gear device 6. Will be described later in detail.

The hydraulic continuously variable transmission 7 for traveling is
The transmission power of the transmission case 3 is arranged on the upstream side of the transmission case 3, and the rotational power is transmitted from the output shaft 25 of the traveling hydraulic motor 7b into the transmission case 3. A series of transmission mechanisms in the transmission case 3 are provided in the order of the auxiliary transmission 4, the parking brake 30, the side clutches 5, 5 ′, and the differential gear 6, and the left and right wheel shafts 2, 2 '
From the driving sprocket 31, 31 '
1 and 1 '.

Therefore, first, as shown in FIG. 1, the auxiliary transmission 4 is transmitted from the transmission gear 32 axially mounted on the output shaft 25 to the large gear 34 on the transmission shaft 33.
A middle gear 35 and a small gear 36 are integrally provided on the upper part, and are mounted so as to be freely slidable in the axial direction so as to be capable of shifting. As shown in FIG. 1, the transmission shaft 33 has an end extending outward from the transmission case 3 to extend the reaping transmission pulley 37.
(Mowing PTO pulley) is mounted on the shaft so that the rotational power synchronized with the vehicle speed can be input to a pre-cutting device 38 described later.

As shown in FIG. 1, the auxiliary transmission shaft 39 is mounted on the lower transmission side of the transmission shaft 33, and
A large transmission gear 40 meshing with the transmission gear 41, a transmission middle gear 41 meshing with the middle gear 35, and a small transmission gear 42 meshing with the large gear 34 are axially attached to each other. ing.

The parking brake 30 is provided at an end of the auxiliary transmission shaft 39. Next, as shown in FIG. 1, the left and right side clutches 5 and 5 ′ have an intermediate shaft 43 mounted on the lower transmission side of the auxiliary transmission shaft 39, and the transmission small gear 42 to the intermediate gear 44, The rotation power is transmitted to the center gear 46 via the shaft 43 and the transmission gear 45. And the side clutches 5, 5 '
On the clutch shaft 47, a driving-side rotating body 48 integrated with the center gear 46, and output gears 49,
A multi-plate clutch is provided between the left and right driven rotating bodies 50, 50 'on which the shaft 9' is mounted, and the traveling rollers 1, 1 'are provided.
The rotation power to the side is cut off and the operation is continued.

Although not shown, the side clutches 5, 5 'are supplied with hydraulic oil switched by a solenoid valve connected to a controller to operate the multi-plate clutch (pressing and separating). Configuration. In the case of the embodiment, the side clutches 5 and 5 'are in a clutch-disengaged state (the multi-plate clutch is separated) when hydraulic oil is supplied, and are pressed by the tension spring mechanism when hydraulic oil is not supplied. (Connection) state. Due to this configuration, the aforementioned parking brake 30
Can exert a braking action while the combine is stopped (while the engine 21 is stopped).

The electromagnetic valves, not shown, are provided with detection switches 51, 51 '(FIG. 2) mounted at positions for detecting the rotation of the operation pivot shaft 18 of the power telescopic lever 9.
(See Reference). In the case of the embodiment, the side clutches 5 and 5 ′ are operated by steering the power steering lever 9 (see FIG. 2 or FIG. 9) to the left (downward operation).
Then, the left side clutch 5 is disengaged, and if it is operated to the right, the right side clutch 5 'is disengaged.

The wheel shafts 2, 2 'are connected to the output gears 49, 49' of the driven-side rotating bodies 50, 50 'mounted on the clutch shaft 47 in a loosely fitted state. Is transmitted to the drive sprockets 31, 31 'to drive the traveling rollers 1, 1'.

Next, as shown in FIG. 1, the differential gear device 6 is a conventionally known differential mechanism, in which a pair of left and right side gears and a pair of left and right side gears are mounted on a rotation support shaft 53. And an intermediate gear that meshes with and transmits power. The differential gear device 6 is configured such that a ring gear 54 provided on the outer periphery of the intermediate gear meshes with a turning gear 55 and rotational power is input from the hydraulic stepless transmission 8 for turning.

In the differential gear device 6, left and right side gears 56 and 56 'are fixed to the pair of left and right side gears so that they can rotate integrally with each other. It is configured so as to be able to transmit to the driven gears 57, 57 'of the driven-side rotating bodies 50, 50'.
In this case, as shown in FIG.
56 ′ and the left and right driven gears 57 and 57 ′ form a transmission system on both the left and right sides.
A reverse gear 58 is interposed between the driven gear 57 and the driven gear 57 so as to mesh with each other, and the power of the reverse rotation is transmitted in the left transmission system.

Next, an interlocking configuration of the main transmission lever 10 and the power telescopic lever 9 (a configuration for restricting the transmission of the operating force via the restriction device 11) will be described. First, as shown in FIG. 2, the power telescoping 9 has an intermediate portion that is rotatably supported in the front-rear direction by a horizontal shaft 59, and is further supported on a vertical operation turning fulcrum shaft 18 to be left and right. It is configured to be tiltable in any direction. The horizontal shaft 59 is provided with a pair of upper and lower mowing elevating switches 60 and 60 'facing the side, and is configured to operate a mowing pre-processing device 38 to be described later.

As shown in FIG. 2, the operating force transmitting means 12 has a lower portion pivotally supported on a lower end portion of the power telescopic lever 9 and an upper portion pivotally connected to a lot 17 with a turning amount adjusting link 16.
The lower end of the lot 17 has a turning adjustment arm.
It is connected to the base of the drum 62. The turning adjustment arm 62 pivotally connects the intermediate portion to a fixed position of the vehicle so as to be freely rotatable, and has a distal end provided with an operation arm 63 of a turning hydraulic pump 8a of the hydraulic stepless transmission 8 for turning. The connected connecting rod 64 is pivotally connected. In this way, the power telescope
9 can be transmitted to the turning hydraulic pump 8a when the operation force is tilted in the left and right directions with the vertical operation rotation fulcrum shaft 18 as a fulcrum.

As shown in FIG. 2, the turning amount adjusting link 16 is located at a position where a pivot point a with the lot 17 coincides with an imaginary extension of the operation turning fulcrum shaft 18 of the power telescopic lever 9. In this case, the neutral position where the operating force from the power telescopic lever 9 is not transmitted to the turning adjusting arm 62 (the power telescopic lever 9 and the turning amount adjusting link 16 only rotate).
The configuration is as follows. Then, the regulating device 11
As shown in the figure, the interlocking wire 65 includes an inner 65a and an outer 65b.
0, the other is operatively connected to an intermediate portion of the turning amount adjusting link 16. In the case of the embodiment, one end of the outer-65b is connected to the power
Attached to the outer holder.

Next, an interlocking structure between the shift position transmitting means 13 of the auxiliary transmission 4 and the operation adjusting device 14 of the power steering 9 will be described. First, as described in the traveling transmission device 20 of FIG.
6, the large gear 34, the middle gear 35, and the small gear 36 are switched by a sub-transmission lever 67 (see FIG. 9) to select a high speed (road running speed), a medium speed, or a low speed. As shown in FIG. 5, the shift position transmitting means 13 is formed of a plate-like arm, and operates integrally with the above-described switching operation of the auxiliary transmission device 4 to form a high-speed position and a medium-speed position. , And move to a low-speed position.

As shown in FIG. 5, the interlocking device 15 is constituted by an interlocking wire 68 comprising an inner 68a and an outer 68b, one of which is connected to the upper part of the shift position transmitting means 13, and the other is connected to the other. Is connected to the distal end of the operation adjusting device 14 on the power steering 9 side. Then, as shown in FIGS. 5 and 6, the operation adjusting device 14 shifts the shift position transmitting means 13 (high speed, medium speed, low speed).
, The tip portion is pushed and pulled to change the position, and pivots up and down with the base (pivot point) as a fulcrum. The operation amount of the swing hydraulic pump 8a changes in conjunction with the shift change of the speed. In the case of the embodiment, the connecting rod 64 and the operation adjusting device 14
The pivoting position with is changed up and down.

As described above, in the hydraulic continuously variable transmission 8 for turning, the operation angle of the operation arm 63 is previously displaced in conjunction with the shift switching of the auxiliary transmission 4. It is possible to output rotational power so that the speed ratio of the left and right traveling rollers 1, 1 'is kept substantially equal at both the medium speed position and the low speed position. it can.

The traveling transmission device 2 configured as described above
As shown in FIGS. 10 and 11, a combine equipped with a threshing device 70 is mounted on a traveling body 69 having traveling crawlers 1, 1 ', and a harvesting pre-processing device 38 is provided in front of the threshing device.
Is provided to enable mowing and threshing work. As shown in FIGS. 9 to 11, the control seat 66 is provided on the front right side of the traveling vehicle body 69, and the operation levers are arranged from the front side to the side portions. In the case of the embodiment, as shown in FIG. 9, a power steering lever 9 is provided at the front right end of the control seat 66, and a main transmission lever 10 and a sub transmission lever 67 are provided at the left front side to perform steering operation and forward / backward movement. Switching, vehicle speed adjustment, and sub-shifting can be switched.

With the above construction, the traveling transmission device 20 stops the turning hydraulic continuously variable transmission 8 (in the embodiment shown in FIG. 1, the main transmission lever 10 and the power steering lever 9).
Is not operated, the clutch 29 mounted on the side of the pulley 28 cannot be connected. Then, the main transmission lever 10 is operated to operate the traveling hydraulic continuously variable transmission 7 with the rotational power transmitted from the engine 21. Then, the rotational power reaches the transmission shaft 33, the auxiliary transmission shaft 39, and the intermediate shaft 43 from the traveling hydraulic motor 7b via the output shaft 25, and the transmission gear 4
5 to the center gear 46. Further, the rotational power is transmitted from the driving-side rotating body 48 to the left and right driven-side rotating bodies 50 via the side clutches 5 and 5 ′ in which the multi-plate clutch maintains the pressed state by the action of a tension spring mechanism (not shown). 5
It is transmitted to 0 '.

In this way, the rotational power reaches the wheel gears 52, 52 'from the left and right output gears 49, 49'.
The right and left traveling rollers 1, 1 'are driven at the same speed via the wheel shafts 2, 2' to drive the combine straight. Then, the combine operates the sub-transmission lever 67 and the main transmission lever 10 to select the medium speed or the low speed, and the hydraulic continuously variable transmission 7 for traveling.
The work is performed while driving straight ahead by changing the speed. During such work, the reaping transmission pulley 37 outputs rotation power synchronized with the vehicle speed from the transmission shaft 33 to the reaping pre-processing device 38.
Can be transmitted to each rotating part. And the mowing transmission pulley-3
When the main transmission lever 10 is operated, the traveling hydraulic continuously variable transmission 7 is switched to the reverse rotation to reverse the combine, and a one-way clutch (not shown) is operated to stop the operation. The transmission to the device 38 is interrupted.

Next, a turning operation of the combine (a turning to the left will be described as an example) will be specifically described with reference to FIGS. First, in the graph of FIG. 8, the vertical axis (reference position) indicates the rotation speed, and the horizontal axis indicates the power steering 9.
The operation amount [tilt angle (operation angle) of the lever] is shown. The horizontal axis (0) indicates the zero point of the rotation speed, and the rotation is displayed with the upper part in the forward rotation and the lower part in the reverse rotation based on the zero point. The rotation speed is shown to be one half and one above and below, respectively, for easy understanding.

Next, in the graph, (L) indicates the left output gear 49, (R) indicates the right output gear 49 ', (N) indicates the ring gear 54, (nL) indicates the left side gear 56, and (nR) indicates the right side gear 56'. Is a sign indicating A corresponding display line on the graph indicates a change in each rotation speed.

If the power steering lever 9 is operated to the left to make a left turn while driving the hydraulic continuously variable transmission 7 for driving, the transmission of the left side clutch 5 is cut off. The rotational power reaching the side rotating body 48 is transmitted only to the right driven side rotating body 50 '.
At that time, the right traveling crawler 1 'continues to travel by being transmitted along the same transmission path as in the straight traveling state, and the other left crawler 1'
The rotational power from the right driven gear 57 ′ via the right side gear 56 ′ and the differential gear device 6 reaches the left side gear 56, the reverse gear 58, the left driven gear 57, and the left driven rotator 50,
Output gear 49, wheel gear 52, wheel shaft 2
(See the graph, the vertical axis position in FIG. 2).

As described above, the differential gear device 6 receives the rotational power at a constant speed from the right driven gear 57 'via the right side gear 56', and turns the intermediate gear from the ring gear 54 through the ring gear 54. Of the hydraulic continuously variable transmission 8 is input. In this way, the differential gear device 6
As shown in the graph, when the operation of the power telesaver 9 is continued and N is sequentially increased, nL is sequentially reduced, and L is gradually reduced accordingly.

As described above, the traveling rollers 1, 1 '
Is R (right output gear 4) as can be read from the graph.
9 ′) is constant, while L (left output gear 4
Since 9) is transmitted by deceleration, the combine starts gently turning left. Then, the traveling rollers 1, 1 '
When the rotation speed of reaches half of nR, the output of nL becomes 0 (L = rotation speed 0, see the graph of FIG. 2).

Accordingly, as can be seen from the graph, the traveling crawlers 1, 1 'have the R (right output gear 49') continuously rotating at a constant speed, while the L (left output gear 49) has a constant rotation. Becomes 0 and stops, so the combine enters the brake lock state and turns to the left (brake-turn).
I do.

When the operation of the power steering 9 is further continued to sequentially increase the rotation speed of N, as shown in the graph, nL enters the lower reverse rotation zone, and L also moves in the same direction (reverse rotation). Is transmitted. Therefore, as shown in the graph, the combine performs a spin turn because R continues to rotate forward at a constant speed while L rotates reversely. Then, when the power telesaver 9 is tilted to the highest operation position, the combine performs a super turning as shown in the graph.

As described above, the combine according to the embodiment is
The hydraulic continuously variable transmission 7 for traveling and the hydraulic continuously variable transmission 8 for turning allow the vehicle to travel in accordance with work conditions and surrounding conditions of the field while adding turning to straight traveling, and continue cutting and threshing work. it can. As shown in FIG. 1, when the power steering lever 9 is shifted when the main shift lever 10 is in the shift position (other than the neutral position), the hydraulic stepless transmission 8 for turning is connected in series. The two detection switches 19a and 19b connected by the wired circuit are energized to engage the clutch 29, and the rotational power is transmitted from the pulley 28. Therefore, the turning hydraulic continuously variable transmission 8 has an advantage that the power from the engine 21 can be used effectively and efficiently, mechanical efficiency can be improved, and further, operational safety can be ensured. Conventionally, a hydraulic continuously variable transmission has been
Although it was difficult to secure the neutral position of the operation lever, it was regarded as a problem. However, as described above, it is configured to be driven only when output is required, and the condition of the two hydraulic continuously variable transmissions is satisfied. When it is driven, the safety can be significantly improved.

Further, as shown in FIG. 3, the power steering lever 9 has the turning amount adjusting link 16 along the lever 9, and the pivot 17a of the lot 17 is connected to the operating rotation fulcrum shaft 18.
When the lever is operated on the virtual extension line, the operating force is not transmitted to the turning adjustment arm 62 side. The turning amount adjusting link 16 is connected to the main shift lever 10 that has been shifted.
When the shift position is transmitted to the operating force transmitting means 12 via the regulating device 11 and the pivot point a shifts to the point b or c shown in FIG. 4, the operating force from the power telescopic lever 9 turns. The state can be transmitted to the adjustment arm 62.

When the power steering lever 9 is shifted when the main speed lever 10 is in the operating position, the turning adjustment arm 62 operates as shown in FIG. 4 to operate the turning hydraulic pump 8a. Can be operated. In the case of this embodiment, as shown in FIG. 4, when the main transmission lever 10 is switched to forward or backward, the turning adjustment arm 62 is switched to forward or backward around the neutral position.

As described above, the power telescopic lever 9 and the main transmission lever 10 are interlocked with each other via the restricting device 11 so that an appropriate related operation can be performed. Since the operating force transmitting means 12 and the members related thereto are concentrated in the vicinity of the base of the power telescopic lever 9, maintenance such as adjustment can be performed relatively easily by opening the upper body cover. There are also features.

Further, the power steering lever 9 is provided with a sub-transmission lever.
When the high speed, medium speed and low speed are selected by switching operation of 67,
Each time, the operation adjusting device 14 is interlocked via the interlocking device 15, and as shown in FIG. 5 and FIG.
The operation interval between the arm 62 and the operation arm 63 changes. When the power steering 9 is operated in this state, the hydraulic continuously variable transmission 8 for turning is operated more sensitively at low speeds than at medium and high speeds.

In the case of the embodiment, as shown in FIG. 7, the right and left traveling rollers 1, 1 'at the time of turning traveling have substantially the same gear ratio and substantially coincide with the point (0). it can. This point (0) is the position where the output to the left running crawler 1 already described in FIG. 8 is 0, that is, the position of the brake return.

As described above, according to the present invention, the turning operation device is constituted by relating the speed change operations of the two hydraulic continuously variable transmissions 7 and 8 and the auxiliary transmission 4 so that the operator can feel comfortable and comfortable. -Allows safe steering operation under the ring.

[Brief description of the drawings]

FIG. 1 is an embodiment of the present invention and is a diagram of a transmission mechanism shown in a diagram.

FIG. 2 is a perspective view illustrating an interlocking mechanism according to the embodiment of the present invention.

FIG. 3 is an operation diagram of an interlocking mechanism according to the embodiment of the present invention.

FIG. 4 is an embodiment of the present invention and is an operation change diagram of an interlocking mechanism.

FIG. 5 is a perspective view illustrating an interlocking mechanism according to the embodiment of the present invention.

FIG. 6 is a diagram showing a change in operation according to the embodiment of the present invention.

FIG. 7 is a graph showing a rotation speed according to the embodiment of the present invention.

FIG. 8 is a graph showing a change in rotation speed according to the embodiment of the present invention.

FIG. 9 is a plan view of a pilot seat according to an embodiment of the present invention.

FIG. 10 is a plan view of a combine according to an embodiment of the present invention.

FIG. 11 is a side view of the combine according to the embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1, 1 'Traveling cradle 2, 2' Wheel shaft 3 Transmission case 4 Auxiliary transmission 5, 5 'Side clutch 6 Actuating gear device 7 Continuously variable transmission for running 8 Hydraulic continuously variable transmission for turning Apparatus 9 Power telescopic lever 10 Main transmission lever 11 Restriction device 12 Operating force transmission means 13 Shift position transmission means 14 Operation adjustment device 15 Interlocking device 16 Turning amount adjustment link 17 Lot 18 Operation rotation fulcrum shaft 19a, 19b Detection switch (L) Left output gear 49 (R) Right output gear 4
9 '(N) Ring gear 54 (nL) Left side gear 56 (nR) Right side gear 56'.

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (reference) B62D 11/08 B62D 11/08 J F term (reference) 2B043 AA03 AB13 AB19 BA02 BA05 BB14 DA05 DB04 DB05 DB08 DB18 2B076 AA03 DA02 DA03 DA15 DC01 DD04 3D040 AA12 AA22 AB04 AC29 AC50 AC53 AF07 3D052 AA05 AA11 AA16 AA18 BB10 BB11 DD04 EE01 FF01 FF02 GG04 HH01 HH02 HH03 JJ08 JJ14

Claims (4)

[Claims] A transmission case (3) having a pair of left and right wheel shafts (2, 2 ') for transmitting rotational power to the traveling rollers (1) and (1') has an auxiliary transmission (4) and a pair of left and right wheels. Side clutches 5 and 5 ′ and a differential gear device 6 are provided inside, and a transmission hydraulic continuously variable transmission 7 input from the auxiliary transmission 4 is provided on the transmission case 3. ,
A power steering lever 9 for shifting the hydraulic continuously variable transmission 8 for turning is provided in connection with a hydraulic continuously variable transmission 8 for turning inputted from the differential gear device 6 side, and Main shift lever 10 for shifting the hydraulic continuously variable transmission 7
Side is provided by being connected with a regulating device 11.
Is connected to the operating force transmitting means 12 so that the operating force of the power telescopic lever 9 is transmitted to the hydraulic stepless transmission 8 for turning only when the main shift lever 10 is at the shift operating position. The turning hydraulic continuously variable transmission 8 is a turning operation device for a mobile vehicle that is driven and outputs when the power steering lever 9 is shifted, provided that the main shift lever 10 is at a shift operation position. . 2. The transmission position transmission means 13 of the auxiliary transmission 4.
And an operation adjusting device 14 of the power teles 9 are connected by an interlocking device 15 so that the operation amount from the power teles 9 to the turning hydraulic continuously variable transmission 8 can be adjusted according to the shift position of the auxiliary transmission 4. Hydraulic stepless transmission 8 for turning
, Regardless of the shift position of the sub-transmission 4, the rotational power is output so as to obtain substantially the same turning radius while maintaining the speed ratio of the left and right traveling rollers 1, 1 'substantially equal. Item 4. The turning operation device for a moving vehicle according to Item 1. 3. A turning amount adjusting link 16 constituting the operating force transmitting means 12 is pivotally supported on one of the power telescopic levers 9 and transmits the operating force to the hydraulic stepless transmission 8 for turning the other. The pivot amount adjustment link 16 is provided at the position where the pivot point a with the lot 17 coincides with the virtual extension line of the operation rotation fulcrum shaft 18 of the power telesaver 9. The turning operation device for a mobile vehicle according to claim 1, wherein the turning amount adjusting link (16) is configured to be linked to a main speed lever (10) via a regulating device (11) so as to be interlocked with the main speed lever (10). . 4. Two detection switches 19a and 19b which are turned ON and OFF in relation to a shift operation between the main transmission lever 10 and the power steering lever 9 are provided.
a and 19b are connected by a circuit wired in series, and when it is detected that both the main transmission lever 10 and the power steering lever 9 are in the transmission position, the rotational power is transmitted to the hydraulic stepless transmission 8 for turning. The turning operation device for a mobile vehicle according to claim 1, wherein the transmitting operation is performed.