CN102887171B - Riding work machine - Google Patents
Riding work machine Download PDFInfo
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- CN102887171B CN102887171B CN201210216698.1A CN201210216698A CN102887171B CN 102887171 B CN102887171 B CN 102887171B CN 201210216698 A CN201210216698 A CN 201210216698A CN 102887171 B CN102887171 B CN 102887171B
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- working rig
- joystick
- swing arm
- steering angle
- speed change
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- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
- Guiding Agricultural Machines (AREA)
- Harvester Elements (AREA)
- Steering Controls (AREA)
- Arrangement Or Mounting Of Control Devices For Change-Speed Gearing (AREA)
Abstract
A riding work machine (10) comprises a steering wheel (31), an engine (11), a hydraulic stepless transmission mechanism (62) for transmitting power of the engine (11) to a driving wheel (14, 14), and a pivotable operation lever (71) for operating the hydraulic stepless transmission mechanism (62) to change the running speed of the work machine (10). A return mechanism for returning the hydraulic stepless transmission mechanism (62) to a position of reducing the running speed of the work machine (10) when the hydraulic stepless transmission mechanism (62) is operated by the operation lever (71) and the steering wheel (31) is turned is mounted at a base (71a) of the operation lever (71).
Description
Technical field
The present invention relates to a kind of that driven by engine, automatically can reduce gait of march when turning to riding type working rig.
Background technology
Recently, can work coordinated with each other between the steering swivel system of riding type working rig and work system, thus also can work safely, effectively when working rig is turned to safely.As the one of this type of working rig, agricultural machinery needs to have sufficient durability can use under harsh service conditions.In order to provide a kind of working rig such as with the agricultural machinery of abundant durability, in Japanese patent application JP-A-51-42218 and JP-A-57-91414, disclose a kind of only need without the need to using electric control system and use mechanical system just can make the technical scheme of the working rig automatic retarding when working rig turns to.
Disclosed in Japanese patent application JP-A-51-42218 riding type working rig be a kind of have accelerate joystick and the traction machine of crew-served left and right steering hardware with bearing circle respectively.Accelerating joystick by operation makes acceleration pull bar regulate governor and Fuel Injection Device, regulates the speed of engine thus.When steering wheel rotation to the left or to the right, described left and right steering hardware is driven to control governor and Fuel Injection Device, to make engine deceleration by acceleration pull bar.Thus, the moving velocity of working rig is automatically reduced.
For working rig structural considerations, described left and right steering hardware must be arranged on and accelerate near pull bar.This means that the structure automatically reducing working rig gait of march according to turning to of working rig is quite complicated, and bulky.Accelerate near pull bar because left and right steering hardware is arranged on, this working rig only remains very limited space for installing miscellaneous part.That is, the installation degree of freedom of this working rig miscellaneous part is very low.In addition, this reduction engine speed and cannot be applied in order to the mechanism of the automatic retarding according to turning to of working rig and both driven driving system to drive the riding type working rig of work system by single engine.In other words, working rig automatic retarding mechanism be not suitable for and not only driven driving system by single engine but also driven the riding type working rig of work system disclosed in Japanese patent application JP-A-51-42218.
Disclosed in Japanese patent application JP-A-57-91414, riding type working rig comprising gear drive for engine outputting power being passed to wheel, being arranged at Belt-type Adjustable-speed Drive mechanism (belt-type continuously-variabletransmission) between engine and gear drive and speed reduction gearing crew-served with bearing circle, and this speed reduction gearing is for controlling belt infinitely variable speed gearing to reduce working rig moving velocity.Specifically, when cam (cam) detects that the rotation of bearing circle exceedes predetermined angular, start speed reduction gearing to control the moving velocity that belt infinitely variable speed gearing reduces working rig.Thus, working rig automatic retarding is made when working rig turns to.
Because of disclosed in Japanese patent application JP-A-57-91414 working rig except there is gear drive, also there is Belt-type Adjustable-speed Drive mechanism, make the speed reduction gearing reducing working rig moving velocity when working rig turns to inevitably have complicated structure and huge volume thus.In addition, this working rig comprising two kinds of transmission devices only remains very limited space for installing miscellaneous part.This means that the installation degree of freedom of this working rig miscellaneous part is very low.
Thus, for riding type working rig disclosed in Japanese patent application JP-A-51-42218 and JP-A-57-91414, its labyrinth for the speed reduction gearing of reduction working rig moving velocity when working rig turns to and bulkiness are problem demanding prompt solutions.
Patent documentation
[patent documentation 1] JP 51-42218;
[patent documentation 2] is real opens clear 57-91414.
Summary of the invention
Main purpose of the present invention is that providing a kind of can be drive the riding type working rig of driving system and work system automatically to reduce the simple mechanism of turning velocity by single engine.
The invention provides a kind of riding type working rig, this riding type working rig comprises: bearing circle; Engine; Drive wheel; Hydraulic stepless speed change transmission device, for passing to drive wheel by engine outputting power; Swingable joystick, changes the moving velocity of described working rig for operating hydraulically operated infinitely variable speed gearing, this joystick comprises base portion; Bringing-back mechanism, for described hydraulic stepless speed change transmission device by joystick manipulation and steering wheel rotation time, make described hydraulic stepless speed change transmission device be back to the position reducing described working rig moving velocity, wherein said Bringing-back mechanism is arranged on the base portion of joystick.
Bringing-back mechanism when described working rig turns to for automatically reducing described working rig moving velocity is arranged on the base portion of described joystick.Because described Bringing-back mechanism is arranged on the base portion of described joystick, therefore the Bringing-back mechanism that arranges independent of described joystick of its structural rate is simple.In addition, because described Bringing-back mechanism is arranged on the base portion of described joystick, therefore easily can guarantee that described working rig has enough spaces to install the miscellaneous part except described Bringing-back mechanism, which thereby enhances the installation degree of freedom of described working rig miscellaneous part.
Described Bringing-back mechanism is applicable to the riding type working rig driving work system and driving system with single engine.This is because when described working rig turns to, described speed reduction gearing does not make engine deceleration, but reduce the moving velocity of described working rig, even if thus when described working rig turns to the moving velocity reduced, the work speed of described work system also can be maintained.
Drive described Bringing-back mechanism by steering wheel rotation, thus be back to the position that the output shaft rotating speed of described hydraulic stepless speed change transmission device is reduced by hydraulic stepless speed change transmission device described in joystick manipulation.Thus, the moving velocity of described working rig can automatically be reduced equally.
In a preferred embodiment of the invention, described hydraulic stepless speed change transmission device comprises transmission actuating spindle, described Bringing-back mechanism comprises: supporting member, and it is connected with the base portion of described joystick, and can swing with described joystick with the moving velocity changing described working rig in one direction; Swing arm, by described supporting members support, and the direction that can swing at described supporting member swings; Pull bar, is connected with described swing arm, for the power handling described joystick being passed to the transmission actuating spindle of described hydraulic stepless speed change transmission device; And steering angle transmission mechanism, the steering angle for being turned over by bearing circle passes to described swing arm, swings according to described steering angle to make described swing arm.
Described Bringing-back mechanism has a simple structure, and this structure comprises: supporting member, can swing so that operating hydraulically operated infinitely variable speed gearing changes working rig moving velocity with joystick in one direction; The swing arm that can swing, by described supporting members support; Pull bar, is connected with described swing arm; And steering angle transmission mechanism, for the steering angle turned over to described swing arm direction of transfer dish.
When described bearing circle is positioned at the position making described working rig keep straight on, steering angle is 0.In this case, due to joystick along with supporting member swings together, therefore described swing arm swings along with joystick together with supporting member.The wobbling action of swing arm handles the transmission actuating spindle of described hydraulic stepless speed change transmission device by pull bar, to change the moving velocity of described working rig.When rotating described bearing circle subsequently, by described steering angle transmission mechanism, the steering angle that described bearing circle turns over is passed to described swing arm.Afterwards, described swing arm swings according to described steering angle relative to described supporting member, to handle the transmission actuating spindle of described hydraulic stepless speed change transmission device by described pull bar, thus reduces the moving velocity of described working rig.
In another preferred embodiment of the present invention, described steering angle transmission mechanism comprises: wirerope, for steering angle is passed to described swing arm; And retracing spring, for promoting described swing arm in one direction, the transmission actuating spindle of described hydraulic stepless speed change transmission device to be recalled to the position to reducing working rig moving velocity.
Steering angle transmission mechanism for steering angle being passed to swing arm comprises wirerope.The beneficial effect that this technical characteristic brings to limit the position of swing arm relative to bearing circle, can improve the installation degree of freedom of described Bringing-back mechanism thus.In addition, always described swing arm is promoted in one direction described transmission actuating spindle to be recalled to the position to reducing working rig moving velocity by retracing spring.That is, always promote described swing arm in one direction by described retracing spring, to provide failure protection function.Therefore, even if meet accident in described steering angle transmission mechanism, described retracing spring all can apply a propelling thrust to described swing arm, to swing described swing arm in one direction, thus described transmission actuating spindle is recalled to the position to reducing working rig moving velocity.Therefore, described steering angle transmission mechanism provides the failure protection function of improvement.
Below, with reference to following accompanying drawing, only the preferred embodiments of the present invention are introduced in detail by way of example.
Accompanying drawing explanation
Fig. 1 is the lateral plan of riding type working rig of the present invention;
Fig. 2 is the schematic diagram of steering swivel system, driving system and Bringing-back mechanism in Fig. 1;
Fig. 3 is the section-drawing of the steering angle transmission mechanism shown in Fig. 2;
Fig. 4 is the exploded view of the steering angle transmission mechanism shown in Fig. 3;
Fig. 5 is the front view of the steering angle transmission mechanism shown in Fig. 3;
Fig. 6 is the serviceability front view of the steering angle transmission mechanism shown in Fig. 5;
Fig. 7 is the transparent view of traveling mechanism and Bringing-back mechanism;
Fig. 8 is the lateral plan of the Bringing-back mechanism shown in Fig. 7;
Fig. 9 is the front elevation of the Bringing-back mechanism shown in Fig. 8;
Figure 10 is the exploded view of the Bringing-back mechanism shown in Fig. 8;
Figure 11 be joystick be positioned at working rig is travelled with maximum travel speed progressive position on schematic diagram;
Figure 12 is the skeleton diagram of the Bringing-back mechanism shown in Fig. 8;
Figure 13 is the skeleton diagram of the Bringing-back mechanism shown in Figure 11.
Detailed description of the invention
As shown in Figure 1, 2, riding type working rig 10 comprises work system 20, steering swivel system 30 and driving system 60.Described working rig 10 drives traveling by single engine 11 together with work system 20.Specifically, described engine 11 passes through work system 20 described in a belt drive, by driving system 60 described in another belt drive.In the present embodiment, described work system 20 comprises mowing portion.
Described engine 11 is arranged on the top at described working rig 10 body 12 rear portion.Described body 12 is provided with left and right front-wheel 13,13 and left and right trailing wheel 14,14.Described front-wheel 13,13 is controlled to turn to by the bearing circle 31 being arranged on body 12 front portion.Described trailing wheel 14,14 is the drive wheel that engine 11 outputting power drives.
As shown in Figure 1, the mowing portion of described maneuvering system 20 is arranged on the below in the middle part of body 12, and comprises the cutter 21 being transmitted the described engine 11 outputting power driving come by belt.Described mowing portion also comprises the under shed cutter cabin 22 for receiving described cutter 21.The grass cut off by described cutter 21 is admitted to careless collecting bag 23.
Described steering swivel system 30 comprises the bearing circle 31 for rotating described left and right front-wheel 13,13.The driven wheel 34 that described steering swivel system 30 also comprises the steering shaft 32 be connected with described bearing circle 31, the steering gear 33 be connected with described steering shaft 32 and engages with described steering gear 33.Described steering swivel system 30 also comprises the tween drive shaft 35 be connected with described driven wheel 34, the pitman arm (spindle arm) 36 be connected with tween drive shaft 35, the left and right intermediate rod 37 that is connected with described pitman arm 36,37, respectively with described left and right intermediate rod 37, the 37 left and right track arms 38 connected, 38 and left and right front-wheel 13,13.Described steering gear 33 is spur gear.Described driven wheel 34 is quadrant gear.
The steering torque being rotated generation by described bearing circle 31 is passed to left and right front-wheel 13,13 through steering shaft 32, steering gear 33, driven wheel 34, tween drive shaft 35, pitman arm 36, left and right intermediate rod 37,37 and left and right track arm 38,38.Thus, make described left and right front-wheel 13,13 turn to.
As shown in Figure 2, described steering swivel system 30 also comprises steering angle transmission mechanism 39.The steering angle that described steering angle transmission mechanism 39 allows swing arm 73 to turn over according to bearing circle 31 swings.Described steering angle transmission mechanism 39 comprises steering angle switching mechanism 40, wirerope 51 and retracing spring 57.
Described steering angle switching mechanism 40 is for converting steering angle to linear displacement.As shown in Figures 3 to 5, described steering angle switching mechanism 40 comprises sliding pin 41, connecting pin 42, slide 43, first arm 44 and the second arm 45.
Described sliding pin 41 and described connecting pin 42 are parallel to described tween drive shaft 35 and extend.Described slide 43 is arranged on described body 12, and has the guide part 43a of elongation, and this guide part constitutes a linearity elongated hole (elongated slot) extended on the direction perpendicular to described tween drive shaft 35.Described sliding pin 41 is arranged in the linearity elongated hole of described guide part 43a, and can slide in this linearity elongated hole.One end of described first arm 44 is connected with described sliding pin 41, and can slide with described sliding pin 41.The other end of described first arm 44 is connected with one end of described second arm 45 by described connecting pin 42, and so arrange and can make first, second arm 44 described, 45 swing toward each other.The other end of described second arm 45 is connected with described driven wheel 34.
When steering angle is 0, namely during described working rig 10 straight-line travelling, as shown in Figure 5, described sliding pin 41 and described connecting pin 42 are positioned on the first straight line L1.Described guide part 43a extends along described first straight line L1.Described sliding pin 41 is positioned on the straight-line motion position Ps that is made up of away from one end of tween drive shaft 35 described guide part 43a.
When described in turning clockwise during bearing circle 31, described steering shaft 32, steering gear 33 and driven wheel 34 rotate a certain amount of, and this amount of spin is identical with the steering angle that bearing circle 31 turns over to the right.The rotation of described driven wheel 34 causes the swing of first, second arm 44,45, guides described sliding pin 41 straight-line motion on the direction towards described tween drive shaft 35 thus by described guide part 43a.By described straight-line motion, described sliding pin 41 arrives position as shown in Figure 6.The linear slide amount of described sliding pin 41 or sliding distance correspond to the steering angle that described bearing circle 31 turns over.When described bearing circle 31 turns left, the sliding type of described sliding pin 41 is identical with the mode that sliding pin during bearing circle turning clockwise 41 slides.Therefore, by steering angle switching mechanism 40, the steering angle that bearing circle 31 turns over can be converted to rectilinear movement amount or the straight-line displacement amount of described sliding pin 42.
Need the ratio that the spacing between tween drive shaft 35 and connecting pin 42 and the spacing between connecting pin 42 and sliding pin 41 are suitably set.Can arrange this ratio with provide the slippage of sliding pin 41 to change and the steering angle that turns over of bearing circle 31 change between optimal proportion.Described ratio is set in the following manner: when described steering angle close to 0 time, the slippage change of described sliding pin 41 is less with the ratio of steering angle change; When described steering angle is larger, the slippage change of described sliding pin 41 is greatly with the ratio of steering angle change.
The inner cable 53 that described wirerope 51 comprises outer tube 52 and extends in described outer tube 52.One end 52a of described outer tube 52 is connected with described body 12 and is positioned on the first straight line L1 of extending along described guide part 43a length direction.Specifically, the end 52a of described outer tube 52 is set than the front portion (tween drive shaft 35) of guide part 43a closer to body 12.Described end 52a has the open end 52b towards described body 12 rear portion (direction away from described tween drive shaft 35).
Described inner cable 53 has an exposed end portion 53a, and this exposed end portion 53a and rear portion of to described body 12 protruding from the open end 52b of outer tube 52 end 52a extends.The exposed end portion 53a of described inner cable 53 is connected with cable connecting pin 55 one end with described first arm 44 by adaptor 54.Described cable connecting pin 55 and described sliding pin 41 always in the vertical direction align.
When not using adaptor 54, described sliding pin 41 can be used to serve as described connecting pin 55, realize the function of described connecting pin 55.
As shown in Figure 1, 2, the power driven that the left and right trailing wheel 14,14 in described driving system 60 is exported by engine 11.Specifically, described driving system 60 comprises belt gear 61, hydrostatic transmissions mechanism (HST, Hydraulic Static Transmission) or hydraulic stepless speed change transmission device 62 and left and right trailing wheel 14,14.Described hydraulic stepless speed change transmission device 62 is connected with the lower end at body 12 rear portion, for the outputting power of engine 11 being passed to described left and right trailing wheel 14,14.Thus, by belt gear 61 and hydraulic stepless speed change transmission device 62, the outputting power of engine 11 is passed to described left and right trailing wheel 14,14.
The direction forward or backward that the hand of rotation of the input shaft 62a driven by described engine 11 can be converted to output shaft 62b by described hydraulic stepless speed change transmission device 62 rotates, and rotates in direction forward or backward to drive described left and right trailing wheel 14,14.In addition, described hydraulic stepless speed change transmission device 62 constantly can change the rotating speed transmission ratio of described input shaft 62a and described output shaft 62b.In other words, described hydraulic stepless speed change transmission device 62 can provide one of Three models according to the position of the swingable gear shift lever 63 being connected to transmission actuating spindle 62c.The Three models of described hydraulic stepless speed change transmission device 62 comprises neutral mode, and in this mode, described gear shift lever 63 is positioned at neutral position Tn (stop bit), and described output shaft 62b stops the rotation; Rotate transmission mode forward, in this mode, described output shaft 62b can rotate forward with infinite variable speed form; And the transmission mode that rotates backward, in this mode, described output shaft 62b can rotate backward with infinite variable speed form.According to the position of described gear shift lever 63, described transmission actuating spindle 62c can be devoted to control described hydraulic stepless speed change transmission device 62, to switch between above-mentioned Three models.
When described gear shift lever 63 is positioned at neutral position Tn, described output shaft 62b stops the rotation.When described gear shift lever 63 is shown from neutral position Tn in one direction, described hydraulic stepless speed change transmission device 62 is switched to and rotates transmission mode forward, with the pendulum angle shown from neutral position Tn in a direction according to described gear shift lever 63 to described output shaft 62b stepless change time, rotate forward described output shaft 62b.When described gear shift lever 63 a direction reverse on hang up from neutral position Tn time, described hydraulic stepless speed change transmission device 62 is switched to the transmission mode that rotates backward, with according to described gear shift lever 63 in a direction reverse on the angle shown from neutral position Tn to described output shaft 62b stepless change time, rotate backward described output shaft 62b.
The moving velocity that described hydraulic stepless speed change transmission device 62 travels to change described working rig 10 can be handled by transmission controlling mechanism 70.As shown in Fig. 2, Fig. 7, described transmission controlling mechanism 70 mainly comprises joystick 71, supporting member 72, swing arm 73 and pull bar 74.
Described hydraulic stepless speed change transmission device 62 is handled, to change the moving velocity of described working rig 10 by swinging described joystick 71.As shown in Figure 1, described hydraulic stepless speed change transmission device 62 can be arranged on the side of working rig 10, for the operator's manual control be sitting on seat 15.Described joystick 71 can swing in the longitudinal direction of body 12.
Fig. 7, Fig. 8 show the joystick 71 be positioned on neutral position Mn (stop bit).Described joystick 71 on the Mn of neutral position described hydraulic stepless speed change transmission device 62 is remained on described working rig 10 stop travel described neutral mode or stop mode on.Described joystick 71 can be swung forwards, backwards from described neutral position Mn, make described working rig 10 advance or retreat to handle described hydraulic stepless speed change transmission device 62, and change the moving velocity of described working rig 10.That is, when described joystick 71 is from described neutral position Mn forward rocking motion, then handle described hydraulic stepless speed change transmission device 62 and described working rig 10 is moved forward.Described joystick 71 can swing in the district Fm that advances forward be made up of described neutral position Mn and a Mf that advances forward.When advance forward described in described joystick 71 is in Mf time, described working rig 10 moves forward with maximum travel speed.Along with described joystick 71 move closer to described in advance forward a Mf, described hydraulic stepless speed change transmission device 62 is handled the moving velocity improving described working rig 10 and move forward.
When described joystick 71 swings backward from described neutral position Mn, described hydraulic stepless speed change transmission device 62 is handled to be controlled described working rig 10 and moves backward.Described joystick 71 can swing in the district Rm that advances backward be made up of described neutral position Mn and a Mr that advances backward.When advance backward described in described joystick 71 is in Mr time, described working rig 10 travels backward with maximum travel speed.Along with described joystick 71 move closer to described in advance backward a Mr, described hydraulic stepless speed change transmission device 62 is handled the moving velocity improving described working rig 10 and travel backward.
As shown in Figure 7 to 10, described supporting member 72 bolster 72b from described supporting mass 72a to working rig 10 that comprise supporting mass 72a and extend laterally from.Described supporting member 72 also comprises the flat bearing plate 72c from the sidepiece of described supporting mass 72a to downward-extension.Described joystick 71 comprises the base portion 71a be connected with described supporting mass 72a.Described joystick 71 upwards extends from described supporting mass 72a, and the longitudinal direction being inhibited in described body 12 swings relative to described supporting mass 72a.In other words, described supporting member 72 is arranged on the base portion 71a of described joystick 71.Described supporting member 72 can together with described joystick 71 in one direction (longitudinal direction of described body 12) swing, to handle described hydraulic stepless speed change transmission device 62.Described bolster 72b is supported by the bearing 75 be connected with body 12, and can rotate relative to bearing 75.Described flat bearing plate 72c has the side surface facing described working rig 10 side direction.The side surface of described flat bearing plate 72c comprises the vertical extension guide groove 72d being formed in its front lower portion.
Described swing arm 73 is one block of elongation plate extended on described working rig 10 is longitudinal.Described swing arm 73 has one by the lower back-connected longitudinal middle part of rest pin 76 with described flat bearing plate 72c, and described swing arm 73 thus can vertical oscillation.That is, the longitudinal middle part of described swing arm 73 is supported by supporting member 72, can swing to make swing arm 73 on the direction identical with supporting member 72 swaying direction.Described swing arm 73 have one be tilted under front portion.
What be connected with the leading section of described swing arm 73 is the pilot pin 77 extended laterally along described working rig 10.As shown in Figure 8, described pilot pin 77 is located across the front of the second line L2 of bolster 72b center point P 1 and rest pin 76 center point P 2.Described center point P 1 constitutes the center-point that supporting member 72 swings.Described center point P 2 constitutes the center-point that swing arm 73 swings.Described pilot pin 77 is arranged in described guide groove 72d.When described swing arm 73 is on described rest pin 76 during vertical oscillation, described pilot pin 99 guides by described guide groove 72d.
As shown in Figure 7 to 10, described outer tube 52 have one be connected to described supporting member 72 to end 52c (opposite end portion).Described swing arm 73 is had one and to be connected to rearward end on inner cable 53 couples of end 53b by cable connecting pin 78.The steering angle that bearing circle 31 turns over can be passed to described swing arm 73 by described wirerope 51, hereafter will introduce this process in detail.
As shown in Figure 8, described cable connecting pin 78 is positioned at the rear of the second line L2, and is deflected downwardly the 3rd line L3 through described center point P 2 and pilot pin 77 center point P 3.Rest pin 76, pilot pin 77 and cable connecting pin 78 are parallel to the bolster 72b of described supporting member 72.
As shown in Figure 7 to 10, pull bar 74 is connected with described swing arm 73, the power handling described joystick 71 to be passed to the transmission actuating spindle 62c of described hydraulic stepless speed change transmission device 62.Specifically, described pull bar 74 has the end 74a that is connected to described pilot pin 77.
As shown in Figure 9, described transmission controlling mechanism 70 is by cover 16 shade covering body 12 top.That is, described transmission controlling mechanism 70 be arranged on by body 12 side formed in the space of under shed.Described transmission controlling mechanism 70 is placed on by body 12 side formed to this set in the space of under shed, can make described working rig 10 easily for the installation of the miscellaneous part outside described transmission controlling mechanism 70 provides space.Thus, improve the installation degree of freedom of the miscellaneous part outside transmission controlling mechanism 70.
As shown in Figure 7, described pull bar 74 extends back from pilot pin 77, it has rearward end 74b, and described rearward end 74b is connected to the gear shift lever 63 of described hydraulic stepless speed change transmission device 62 by the first swingable intermediate arm 81, intermediary operation axle 82, the second swingable intermediate arm 83 and hinge 84.The transmission actuating spindle 62c of described middle control lever shaft 82 and described hydraulic stepless speed change transmission device 62 is parallel to described pilot pin 77, towards extending laterally of described working rig 10.Described first intermediate arm 81 extends forward from middle control lever shaft 82.
Described middle control lever shaft 82 is positioned at the front of described hydraulic stepless speed change transmission device 62, is supported and rotatable by body 12.Described first intermediate arm 81 has the close end that is connected to described middle control lever shaft 82 one end, and is connected to the distal portion 81a of described pull bar 74 rearward end 74b.Described second intermediate arm 83 has the close end that is connected to described middle control lever shaft 82 other end, and is connected to the distal portion of described hinge 84 one end.The other end of described hinge 84 is connected with described gear shift lever 63.
As shown in Figure 7 to 10, described supporting mass 72a comprises the front upper part that carry upper springs convergence piece 86.The leading section of described swing arm 73 is connected with lower springs convergence piece 87 by described pilot pin 77.Retracing spring 57, at described upper and lower part spring engagement member 86, extends between 87, and is connected with described upper and lower part spring engagement member 86,87.Described retracing spring 57 (extends between its front upper part at described supporting mass 72a and described swing arm 73 leading section, and be connected mutually with the front upper part of described supporting mass 72a and described swing arm 73 leading section) in one direction (anticlockwise direction in Fig. 8) promote the leading section of described swing arm 73, be raised to make the leading section of described swing arm 73 always or move up relative to described supporting member 72.In other words, the transmission actuating spindle 62c (Fig. 2) of described hydraulic stepless speed change transmission device 62 can recalled to side's upwardly described swing arm 73 of the position to the moving velocity reducing described working rig 10 by described retracing spring 57.
The leading section of described swing arm 73 is promoted by described retracing spring 57, to haul the inner cable 53 of described wirerope 51 always.Thus, described inner cable 53 always pulls described sliding pin 41 (Fig. 3 and Fig. 5) along described guide part 43a towards the direction of described tween drive shaft 35.
When described steering angle is 0 (or described bearing circle 31 is under beating positive status), namely during described working rig 10 straight-line travelling, described tween drive shaft 35, sliding pin 41 and connecting pin 42 are all positioned on described First Line L1.Described sliding pin 41 remains on the straight-line motion position Ps away from tween drive shaft 35.
Described swing arm 73 always by described retracing spring 57 described transmission actuating spindle 62c is recalled to reduce described working rig 10 moving velocity position side upwardly.That is, described swing arm 73 can provide the side of failure protection function upwardly by described retracing spring 57 always.Therefore, even if in described steering angle transmission mechanism 39, something unexpected happened, such as described inner cable 53 is disconnected, described swing arm 73 also can swing on the direction of position of described transmission actuating spindle 62c being recalled to the moving velocity to the described working rig 10 of reduction because being subject to the thrust of retracing spring 57, described transmission actuating spindle 62c is recalled to the position to the moving velocity reducing described working rig 10.Described steering angle transmission mechanism 39 thus provides the failure protection function of improvement.
According to the relative angle between pull bar 74 and swing arm 73 or the relative angle between pull bar 74 and the first intermediate arm 81, the propelling thrust of described retracing spring 57 is set, to guarantee transmission actuating spindle 62c to be recalled to the position to the moving velocity reducing described working rig 10.
Supporting member 72, swing arm 73, pull bar 74 and steering angle transmission mechanism 39 together constitute the Bringing-back mechanism 90 be arranged on base portion 71a, so that by the operating hydraulically operated infinitely variable speed gearing 62 of joystick 71 and steering wheel rotation 31 time, namely handle described working rig 10 when turning to, make described hydraulic stepless speed change transmission device 62 be back to the position of the moving velocity reducing described working rig 10.
When by joystick 71 operating hydraulically operated infinitely variable speed gearing 62, the mode of operation of described hydraulic stepless speed change transmission device 62 is as follows.
As shown in Figure 8, when described joystick 71 from neutral position Mn forwards Fr swing or enter advance forward district Fm time, supporting member 72 and swing arm 73 in center point P 1 with joystick 71 together clockwise oscillation.Figure 11 shows described swing arm 73 and has been rocked to a Mf that advances forward.
The clockwise oscillation of described swing arm 73 makes described pull bar 74 move backward, makes the first intermediate arm 81 clockwise oscillation thus.The clockwise oscillation of described first intermediate arm 81 makes middle control lever shaft 82 rotate clockwise, and causes the second intermediate arm 83 and hinge 84 (Fig. 7) clockwise oscillation gear shift lever 63 thus.So, described hydraulic stepless speed change transmission device 62 is converted into from the neutral mode that output shaft 62b stops operating the transmission mode of rotation forward that output shaft 62b rotates forward, thus described working rig 10 is moved forward, wherein, the angle that joystick 71 is crossed from neutral position Mn to forward swing is depended in the increase of described output shaft 62b rotating speed.
As shown in Figure 8, when described joystick 71 from neutral position Mn rearward Rr swing or enter advance district Rm backward time, described hydraulic stepless speed change transmission device 62 is converted into from described neutral mode the transmission mode that rotates backward that output shaft 62b rotates backward, thus described working rig 10 is travelled backward, wherein, the angle that joystick 71 was put backward from neutral position Mn is depended in the increase of described output shaft 62b rotating speed.
When rotating described bearing circle 31 (Fig. 2), the mode of operation of described hydraulic stepless speed change transmission device 62 is as follows.
As shown in Figure 8, when described joystick 71 is positioned at neutral position Mn, the stopping of described working rig 10 (Fig. 2) travels.As shown in Figure 5, tween drive shaft 35, sliding pin 41 and connecting pin 42 coexist on First Line L1.Described sliding pin 41 is on the Ps of straight-line motion position.
When at described joystick 71 under the state of neutral position Mn, to the left or to the right steering wheel rotation 31 time, the angle that described bearing circle 31 turns over is depended in the swing of the first arm 44 and the second arm 45 (Fig. 6).The swing of first, second arm 44,45 described causes sliding pin 41 to slide, this is because sliding pin 41 guides by guide part 43a to the direction of tween drive shaft 35.Slippage or the sliding distance of described sliding pin 41 are corresponding with rotational angle.Therefore, steering angle can be converted to linear slide or the displacement of sliding pin 41 by steering angle switching mechanism 40.
Sliding pin 41 relaxes described inner cable 53 (Fig. 3) towards the slip of tween drive shaft 35, thus makes described swing arm 73 position that the position of solid line mark marks to dotted line in Figure 12 from Figure 12 under the effect of the propelling thrust of retracing spring 57 (Fig. 8) do counter-clockwise swing.In the counter-clockwise swing process of described swing arm 73, the center point P 3 of pilot pin 77, by mobile along the curved line Los (little curved line Los) with center point P 2, moves to position P3a.The center point P 3 of pilot pin 77 makes described pull bar 74 conter clockwise move to the position of (in Figure 12) dotted line mark to the movement at P3a place, position.
Afterwards, be connected to the end 74a (Fig. 8, Figure 10) of the pull bar 74 of pilot pin 77 by mobile along the curved line Lom (large curved line Lom) with center point P 4, move to position P3a, described center point P 4 is the point of connection between described pull bar 74 and the first intermediate arm 81.Described large curved line Lom overlaps with described little curved line Los substantially.That is, even if when the center point P 3 of described pilot pin 77 is shifted one's position according to steering angle, described little curved line Los and described large curved line Lom is separated from one another, and there is no gap.In other words, described pull bar 74 can not move in a longitudinal direction thereof.Therefore, the position of center point P 4 remains unchanged (that is, the change of the described hydraulic stepless speed change transmission device 62 that can not make a difference) substantially.Thus, under the output shaft 62a of described hydraulic stepless speed change transmission device 62 remains on the idle condition that can not rotate.Therefore, under described working rig 10 remains on the idle condition stopping travelling.
The position of described center point P 1, the position of P2, P3, P4 and the center point P 5 of middle control lever shaft 82 is set, even if to make the first intermediate arm 81 when the center point P 3 of pilot pin 77 moves to position P3a, also can not swing when joystick 71 is positioned at neutral position Mn.Therefore, no matter steering angle is how many, even if when engine 11 (Fig. 2) runs, described working rig 10 can keep quiescence when joystick 71 is positioned at neutral position.
When described joystick 71 is put to a Mf that such as advances forward from neutral position Mn through the district Fm that advances forward, described first intermediate arm 81 has a down dip loxosis (marked by the long and short dash line in Figure 13) pendulum to vertical position (marked by the short solid line in Figure 13) in the past, thus described working rig 10 (Fig. 2) is moved forward with maximum travelling speed.When described bearing circle 31 (Fig. 2) turns over certain steering angle subsequently left or to the right, inner cable 53 is loosened, to make the position counter-clockwise swing of swing arm 73 position long dashed lines labeled in Figure 13 of long solid marks under the effect of the propelling thrust of retracing spring 57 (Figure 11), from Figure 13 according to this steering angle.In the counter-clockwise swing process of described swing arm 73, the center point P 3 of pilot pin 77 moves to position P3a along the little curved line with center point P 2.That is, described pilot pin 77 has moved forward relatively large or distance δ.
The center point P 3 of pilot pin 77 makes described pull bar 74 move to the position of long dotted line mark from the inverse position hour hands that long solid line marks to the movement at P3a place, position.Then, because pilot pin 77 moves relatively large δ, therefore described pull bar has moved forward large segment distance.Thus, center point P 4 makes the first intermediate arm 81 swing back to moving forward to position P4a or keeps from the vertical position conter clockwise that short solid line marks to working rig 10 the inclination position of quiescence to swing.Finally, intermediate arm 81 arrives by the deceleration position of marked with dotted lines.On this deceleration position, gear shift lever 63 swings to control the moving velocity that described hydraulic stepless speed change transmission device 62 (Fig. 7) reduces described working rig 10 in one direction.
As can be seen from above, by rotating described bearing circle 31 to drive described Bringing-back mechanism 90, thus the position hydraulic stepless speed change transmission device 62 handled by joystick 71 being back to the output shaft 62b rotating speed of hydraulic stepless speed change transmission device 62 is reduced.Thus, the moving velocity of described working rig 10 is also automatically reduced.
When should be noted that the bolster 72b shown in Fig. 7 can exist a scheduled volume friction force between bearing 75, rotate relative to bearing 75.Even if when the hand of operator leaves joystick 71, this friction force can keep the position of joystick 71 not change.For example, described friction force is set, the position of described joystick 71 is remained unchanged, not by the impact of the steering effort making bearing circle 31 (Fig. 2) rotate.Because joystick 71 and supporting member 72 be not by the impact of steering effort, therefore, rotate bearing circle 31 can be made and drive described Bringing-back mechanism 90 thus under making described hydraulic stepless speed change transmission device 62 be back to the prerequisite of the position reducing working rig 10 moving velocity, can described steering effort be arranged less.
Below, description is above summed up.
In a preferred embodiment, as shown in Figure 2, the Bringing-back mechanism 90 that automatically can reduce working rig 10 gait of march when working rig 10 turns to is arranged on the base portion 71a of joystick 71.Because Bringing-back mechanism 90 is arranged on described base portion 71a, therefore the structure of Bringing-back mechanism 90 is compared with the structure that itself and joystick 71 are installed separately, more simply.And then being arranged on the base portion 71a of described joystick 71 due to Bringing-back mechanism 90, described working rig 10 miscellaneous part that also can be except Bringing-back mechanism 90 provides enough installing spaces.Thus, the installation degree of freedom of other parts is greatly increased.
Described Bringing-back mechanism 90 is very useful for driving the riding type working rig of work system 20 (Fig. 1) and driving system 60 by single engine 11.This is because described Bringing-back mechanism 90 can not only reduce the speed of described engine 11, also can reduce the moving velocity of working rig 10 when working rig 10 turns to, thus the running velocity of work system 20 can be kept when working rig 10 slows down and turns to.
In the present embodiment, described Bringing-back mechanism 90 has a simple structure, this structure comprise can swing, change with operating hydraulically operated infinitely variable speed gearing 62 working rig 10 moving velocity in one direction together with joystick 71 supporting member 72, to be supported by described supporting member 72 and swingable swing arm 73, the pull bar 74 be connected with described swing arm 73 and the steering angle for being turned over by bearing circle 31 pass to the steering angle transmission mechanism 39 of swing arm 73.
When bearing circle is positioned at the position that working rig 10 can be made to keep straight on, steering angle is 0.In this case, because joystick 71 swings together with supporting member 72, therefore swing arm 73 swings together with supporting member 72 with joystick 71.The swing of described swing arm 73 by the transmission actuating spindle 62c of the operating hydraulically operated infinitely variable speed gearing 62 of pull bar, thus changes the moving velocity of described working rig 10.When in hydraulic stepless speed change transmission device 62 operational process during steering wheel rotation 31, the steering angle that described bearing circle 31 turns over passes to swing arm 73 by steering angle transmission mechanism 39.Afterwards, described swing arm 73, according to described steering angle, swings relative to described supporting member 72, to handle the transmission actuating spindle 62c of described hydraulic stepless speed change transmission device 62 by pull bar 74 to reduce the moving velocity of described working rig 10.
In the present embodiment, the steering angle transmission mechanism transmitting steering angle to swing arm 73 comprises wirerope 51.Such beneficial effect is, can not limit the location of the described swing arm 73 relative to bearing circle 31.Thus, improve the installation degree of freedom of Bringing-back mechanism 90.
Should be noted that described steering angle transmission mechanism 39 must not comprise steering angle switching mechanism 40.If wirerope 51 and retracing spring 57 designed to be used transmission steering angle, then wirerope 51 and retracing spring 57 have been enough to the needs transmitting steering angle to swing arm 73.For example, wirerope 51 being set without the need to converting steering angle change to linear displacement, just steering angle change can being passed to swing arm 73.
Although above-mentioned transmission controlling mechanism 70 has the first intermediate arm 81, middle control lever shaft 82, second intermediate arm 83 and hinge 84, these parts (the first intermediate arm 81, middle control lever shaft 82, second intermediate arm 83 and hinge 84) are not required for working rig 10.Can according to the consideration of working rig 10 integral layout design, what suitably use in these parts is one or more.For example, the pull bar 74 rearward end 74b of transmission controlling mechanism 70 is directly connected with gear shift lever 63, and in this case, described gear shift lever 63 and the first intermediate arm 81 have identical length, and can arrange in the same direction.
Riding type working rig 10 provided by the invention is preferably riding type lawnmower.
Claims (2)
1. a riding type working rig (10), comprising:
Bearing circle (31);
Engine (11);
Drive wheel (14,14);
Hydraulic stepless speed change transmission device (62), for by the transmission of power of engine (11) to drive wheel (14,14);
Swingable joystick (71), for handling described hydraulic stepless speed change transmission device (62) to change described working rig (10) moving velocity, described joystick (71) comprises base portion (71a);
Bringing-back mechanism (90), for to be handled by joystick (71) described hydraulic stepless speed change transmission device (62) and steering wheel rotation (31) time, described hydraulic stepless speed change transmission device (62) is back to and reduces the position of described working rig (10) moving velocity;
Wherein, described Bringing-back mechanism (90) is arranged on the base portion (71a) of described joystick (71);
Described hydraulic stepless speed change transmission device (62) comprises transmission actuating spindle (62c);
Described Bringing-back mechanism (90) comprising:
Supporting member (72), is connected with the base portion (71a) of described joystick (71), and swings the moving velocity changing described working rig (10) in a certain direction together with described joystick (71);
Swing arm (73), is supported by described supporting member (72), and swings on the direction identical with the direction that described supporting member (72) swings;
Pull bar (74), is connected with described swing arm (73), for the power handling described joystick (71) being passed to the transmission actuating spindle (62c) of described hydraulic stepless speed change transmission device (62); And
Steering angle transmission mechanism (39), the steering angle for being turned over by described bearing circle (31) passes to described swing arm (73), swings according to described steering angle to make described swing arm (73).
2. working rig according to claim 1, is characterized in that, described steering angle transmission mechanism (39) comprising:
Wirerope (51), for transmitting described steering angle to described swing arm (73); And
Retracing spring (57), for promoting described swing arm (73) in a certain direction, the transmission actuating spindle (62c) of described hydraulic stepless speed change transmission device (62) to be recalled to the position to reducing working rig (10) moving velocity.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011157324A JP5700824B2 (en) | 2011-07-18 | 2011-07-18 | Riding type work machine |
| JP2011-157324 | 2011-07-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102887171A CN102887171A (en) | 2013-01-23 |
| CN102887171B true CN102887171B (en) | 2015-02-25 |
Family
ID=47530897
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210216698.1A Expired - Fee Related CN102887171B (en) | 2011-07-18 | 2012-06-26 | Riding work machine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5700824B2 (en) |
| CN (1) | CN102887171B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8997902B2 (en) * | 2013-05-30 | 2015-04-07 | Cnh Industrial America Llc | Windrower steering system |
| CN104285529B (en) * | 2014-09-13 | 2016-06-22 | 东北农业大学 | Paddy field banking machine is built ridge parts and is turned to governor motion |
| US9616893B2 (en) | 2014-10-15 | 2017-04-11 | Honda Motor Co., Ltd. | Automatic turn-sensing ground speed reduction systems and related methods for walk-behind machines |
| CN104429304A (en) * | 2014-12-17 | 2015-03-25 | 王鑫 | Vehicle-mounted automatic mower equipment |
| JP6224756B2 (en) | 2016-03-18 | 2017-11-01 | 本田技研工業株式会社 | Working machine |
| JP6305453B2 (en) | 2016-03-18 | 2018-04-04 | 本田技研工業株式会社 | Working machine |
| JP6224757B2 (en) | 2016-03-18 | 2017-11-01 | 本田技研工業株式会社 | Working machine |
| CN107018697B (en) * | 2017-03-14 | 2018-04-17 | 黄河科技学院 | A kind of mono-lever control device of agricultural walking machine |
| CN111186487B (en) * | 2019-11-21 | 2021-04-27 | 中国北方车辆研究所 | Equal-angle pump motor pull arm reversing device |
| CN114223380B (en) * | 2021-12-14 | 2023-09-01 | 陕西丹山源农业科技有限公司 | Weed removal device before paddy field planting |
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| US5850886A (en) * | 1995-07-20 | 1998-12-22 | Honda Giken Kogyo Kabushiki Kaisha | Steering control device for vehicle having continuously variable transmission |
| CN101365617A (en) * | 2005-08-22 | 2009-02-11 | 因芬尼查克有限责任公司 | Driving and steering of motor vehicles |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5142218A (en) * | 1974-10-02 | 1976-04-09 | Kubota Ltd | SENKAIJIGEN SOKUSOCHI |
| JPH0741802B2 (en) * | 1989-05-19 | 1995-05-10 | 本田技研工業株式会社 | Work vehicle |
| JP2000025637A (en) * | 1998-07-08 | 2000-01-25 | Kanzaki Kokyukoki Mfg Co Ltd | Steering and driving device for traveling vehicle |
| JP3028481B1 (en) * | 1998-12-16 | 2000-04-04 | ヤンマー農機株式会社 | Moving agricultural machine |
| JP2004161132A (en) * | 2002-11-13 | 2004-06-10 | Kawasaki Heavy Ind Ltd | Transmission device for rough ground traveling vehicle |
| EP2174816B1 (en) * | 2008-02-13 | 2012-06-06 | Kanzaki Kokyukoki Mfg. Co., Ltd. | Wheel motor device |
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2011
- 2011-07-18 JP JP2011157324A patent/JP5700824B2/en not_active Expired - Fee Related
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2012
- 2012-06-26 CN CN201210216698.1A patent/CN102887171B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5850886A (en) * | 1995-07-20 | 1998-12-22 | Honda Giken Kogyo Kabushiki Kaisha | Steering control device for vehicle having continuously variable transmission |
| CN101365617A (en) * | 2005-08-22 | 2009-02-11 | 因芬尼查克有限责任公司 | Driving and steering of motor vehicles |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013022987A (en) | 2013-02-04 |
| CN102887171A (en) | 2013-01-23 |
| JP5700824B2 (en) | 2015-04-15 |
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