CN201980291U - Rotating transmission device for operating vehicle - Google Patents
Rotating transmission device for operating vehicle Download PDFInfo
- Publication number
- CN201980291U CN201980291U CN2011200858669U CN201120085866U CN201980291U CN 201980291 U CN201980291 U CN 201980291U CN 2011200858669 U CN2011200858669 U CN 2011200858669U CN 201120085866 U CN201120085866 U CN 201120085866U CN 201980291 U CN201980291 U CN 201980291U
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- Prior art keywords
- friction lining
- bolster
- pushing portion
- driven wheel
- elastomeric element
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Abstract
The utility model provides a rotating transmission device for an operating vehicle, which cannot cause any abnormal sound under the half-separation/reunion state when in rotating and is provided with a wet type multi-sheet clutch (74) and an elastic component (31). The structure of the wet type multi-sheet clutch (74) is as follows: a movable pushing-pressing part (77) is arranged on a sliding component (73) and can be used for pushing and pressing a first friction sheet (74a) or a second friction sheet (74b) along a supporting shaft (71), and a static pushing-pressing part (74d) which is arranged at the side of a transmission box (MC) is opposite to the movable pushing-pressing part and is used for extruding the first friction sheet and the second friction sheet (74b). The elastic component (31) can generate elastic deformation due to compression along the supporting shaft (71) and an elastic force can be acted on the circle with the supporting shaft (71) as the center. After the first friction sheet and the second friction sheet (74b) are orderly arrayed without any gap through the pushing and pressing of the movable pushing-pressing part, extruding forces of the movable pushing-pressing part (77) and the static pushing-pressing part (74d) are acted on at least one of the first friction sheet and the second friction sheet (74b) through the elastic component (31).
Description
Technical field
The utility model relates to a kind of rotary actuator that can drive the Operation Van of pair of right and left mobile devices based on the manipulation of steering apparatus respectively.
Background technology
At present, known for example patent documentation 1 disclosed rotary actuator, it has: driven wheel (in the patent documentation for " sun gear "), it is supported in the bolster that is erected in the transmission gearbox, and the propulsive effort by driving engine is rotated driving; The slide unit of pair of right and left (being " path clutch gear " in the patent documentation), it is embedded on the bolster outside the left and right sides of driven wheel respectively can be with the relative rotation, can be separately always with drive transmitting gear (being " transmission gear travels " in the patent documentation) engagement of the pair of right and left that is linked to the pair of right and left mobile devices respectively, and manipulation that can be by steering apparatus relatively moves and meshes with driven wheel respectively along bolster.This patent documentation 1 disclosed rotating driving device disposes the multi-disc wet clutch (being " rotation assisted clutch " in the patent documentation) of pair of right and left in the left and right sides of driven wheel, this multi-disc wet clutch has a plurality of second friction linings that are sticked in first friction lining of slide unit sliding freely and are sticked in the parts of transmission gearbox side sliding freely in the left and right sides of driven wheel alternate configurations, after engaging of slide unit and driven wheel removed, separate from driven wheel by slide unit, be arranged on the slide unit and can push the mobile pushing portion of first friction lining or second friction lining and as the parts of transmission gearbox side and static pushing portion (being " big footpath clutch gear " in the patent documentation) extruding first friction lining and second friction lining mobile pushing portion along bolster.
In the rotary actuator of patent documentation 1 disclosed Operation Van, if multi-disc wet clutch is in the clutch engagement state, then speed be passed to slide unit via the different propulsive effort of the propulsive effort of sun gear transmission from the transmission gearbox side.Promptly, this rotary actuator passes through moving based on the slide unit of the control action of steering apparatus (being " steering arm " in the patent documentation), it is poor to make the ridden in left or right direction device produce driven in rotation, thereby Operation Van is rotated with the desirable radius of rotation of driver.This device can carry out following rotation: for example, and by the drive transmitting gear of cut-out hand of rotation side and the driving system between the driven wheel, with " the slow rotation " of bigger radius rotation; Braking by the drive transmitting gear to the hand of rotation side, is " the original place rotation " of center rotation with the mobile devices of hand of rotation side; Imposing and the oppositely directed propulsive effort of travel direction by the drive transmitting gear to the hand of rotation side, is " super original place rotates " of center rotation with the approximate centre of body.
Patent documentation 1:(Japan) spy opens 2007-303637 number
Multiple disk clutch constitutes, and when first friction lining contacts with no gap state with second friction lining, first friction lining and second friction lining is further applied extruding, makes the rotation of two friction lining one by its friction force, thereby exerts all one's strength transmission.In multiple disk clutch, first friction lining separates with second friction lining and the state of irregular alignment is called " disengaging of clutch state ", and first friction lining and second friction lining state (state that relative rotation stops) that seamlessly proper alignment and two friction linings can fully integrated rotations is called " clutch engagement state ".Between disengaging of clutch state and clutch engagement state, also there is first friction lining and second friction lining proper alignment and contact with each other and produce friction force but counterrotating " half-clutch state " still takes place two friction linings seamlessly.For example, in patent documentation 1 disclosed rotary actuator, under half-clutch state, first friction lining and second friction lining be proper alignment seamlessly, decides the size of the friction force between two friction linings by the extruding of mobile pushing portion and static pushing portion.
But, be equipped with under the situation of a plurality of parts, exist and to tilt with respect to bolster, and the mobile pushing portion on the slide unit of being arranged on is also with respect to bolster bevelled situation because of the Mismachining tolerance between each parts makes slide unit.If enter half-clutch state in mobile pushing portion as mentioned above under with respect to bolster bevelled state, the friction lining of then the most close mobile pushing portion side and mobile pushing portion part butt may cause producing abnormal sound.And, even slide unit does not tilt with respect to bolster, but on the pushing face of mobile pushing portion, exist under the concavo-convex situation, the part butt can take place too, may produce abnormal sound.
And the thrust pressure of mobile pushing portion is passed to static pushing portion via whole friction linings, and based on the counteractive relation of effect, static pushing portion is also with identical with the thrust pressure of the mobile pushing portion friction lining of trying hard to recommend the most close static pushing of pressure portion side.Therefore, on the pushing face of static pushing portion, exist under the concavo-convex situation, also can produce abnormal sound because of the friction lining of the most close static pushing portion side and static pushing portion part butt.
The utility model content
In view of above problem, the purpose of this utility model is to provide the rotary actuator that does not produce the Operation Van of abnormal sound under a kind of half-clutch state when rotated.
The rotary actuator of the Operation Van of the utility model first aspect, it has can separately-driven pair of right and left mobile devices based on the manipulation of steering apparatus, it is characterized in that, have: driven wheel, it is supported in the bolster that is erected in the transmission gearbox, and the propulsive effort by driving engine is rotated driving; Slide unit, it is a pair of right and left, be configured in the left and right sides of described driven wheel and can be embedded in described bolster outward with the relative rotation respectively, and separately always with the drive transmitting gear mesh of the pair of right and left of the described mobile devices that are linked to pair of right and left respectively, the manipulation by described steering apparatus relatively moves and can be respectively and described driven wheel engagement along described bolster; Multi-disc wet clutch, it is configured in the left and right sides of described driven wheel; Elastomeric element, it can be along the distortion of the described bolster generation elasticity of compression, makes resilient force in being on the circumference at center with described bolster.
The rotary actuator of the utility model second aspect Operation Van, its have can separately-driven pair of right and left based on the manipulation of steering apparatus mobile devices, it is characterized in that, have: driven wheel, it is supported in the bolster that is erected in the transmission gearbox, and the propulsive effort by driving engine is rotated driving; Slide unit, it is a pair of right and left, be configured in the left and right sides of described driven wheel and can be embedded in described bolster outward with the relative rotation respectively, and separately always with the drive transmitting gear mesh of the pair of right and left of the described mobile devices that are linked to pair of right and left respectively, the manipulation by described steering apparatus relatively moves and can be respectively and described driven wheel engagement along described bolster; Multi-disc wet clutch, it is a pair of right and left, the left and right sides at described driven wheel, alternate configurations has a plurality of second friction linings that are sticked in first friction lining of described slide unit sliding freely and are sticked in the parts of described transmission gearbox side sliding freely, after the engagement releasing of described slide unit and described driven wheel, described slide unit separates from described driven wheel, is arranged on thus on the described slide unit and can pushes the mobile pushing portion of described first friction lining or described second friction lining and push described first friction lining and described second friction lining as relative with the described mobile pushing portion static pushing portion of the parts of described transmission gearbox side along described bolster; Elastomeric element, it can be along the distortion of the described bolster generation elasticity of compression, makes resilient force in being on the circumference at center with described bolster.
The rotary actuator of the Operation Van of the utility model third aspect, its have can separately-driven pair of right and left based on the manipulation of steering apparatus mobile devices, it is characterized in that, have: driven wheel, it is supported in the bolster that is erected in the transmission gearbox, and the propulsive effort by driving engine is rotated driving; Slide unit, it is a pair of right and left, be configured in the left and right sides of described driven wheel and can be embedded in described bolster outward with the relative rotation respectively, and separately always with the drive transmitting gear mesh of the pair of right and left of the described mobile devices that are linked to pair of right and left respectively, the manipulation by described steering apparatus relatively moves and can be respectively and described driven wheel engagement along described bolster; Multi-disc wet clutch, it is a pair of right and left, the left and right sides at described driven wheel, alternate configurations has a plurality of second friction linings that are sticked in first friction lining of described slide unit sliding freely and are sticked in described transmission gearbox side component sliding freely, after the engagement releasing of described slide unit and described driven wheel, described slide unit separates from described driven wheel, is arranged on thus on the described slide unit and can pushes the mobile pushing portion of described first friction lining or described second friction lining and push described first friction lining and described second friction lining as relative with the described mobile pushing portion static pushing portion of the parts of described transmission gearbox side along described bolster; Elastomeric element, it can be along the distortion of the described bolster generation elasticity of compression, makes resilient force in being on the circumference at center with described bolster; Make described first friction lining and described second friction lining seamlessly after the proper alignment in the pushing by described mobile pushing portion, the squeese pressure of described mobile pushing portion and described static pushing portion acts at least one side in described first friction lining and described second friction lining via elastomeric element.
According to above-mentioned the utility model, make first friction lining and second friction lining seamlessly after the proper alignment in pushing by mobile pushing portion, promptly, after entering half-clutch state, the squeese pressure of mobile pushing portion and static pushing portion acts at least one side in first friction lining and second friction lining via elastomeric element.Because it is on the circumference at center that elastomeric element makes elastic force act on the bolster along bolster, therefore, even because of mobile pushing portion tilts with respect to bolster or there is the side's side part butt that causes mobile pushing portion and elastomeric element such as concavo-convex in the pushing face that moves pushing portion, the thrust pressure of mobile pushing portion also can act on friction lining with the state of dispersion along the circumferential direction at the opposite side of elastomeric element.That is, the area that contacts with the friction lining of the most close mobile pushing portion side of the opposite side that makes elastomeric element is greater than the area of a side contacts of mobile pushing portion and elastomeric element.Consequently, can prevent and friction lining generation part butt, thereby prevent under half-clutch state, to produce abnormal sound.
Exist at the pushing face of static pushing portion under the situation of concavo-convex grade too, even a side part butt of static pushing portion and elastomeric element, the thrust pressure of static pushing portion also can act on friction lining with the state that along the circumferential direction disperses at the opposite side of elastomeric element.That is, the area that contacts with the friction lining of the most close static pushing portion side of the opposite side that makes elastomeric element is greater than the area of a side contacts of static pushing portion and elastomeric element.Consequently, can prevent and friction lining generation part butt, thereby prevent under half-clutch state, to produce abnormal sound.
The rotary actuator of the Operation Van of the utility model fourth aspect, it is characterized in that, the elasticity modulus of described elastomeric element is set for, stopped with the relative rotation of described second friction lining up to described first friction lining, described squeese pressure is only via described elastomeric element effect.
Up to entering the clutch engagement state, that is, stop fully with the relative rotation of second friction lining up to first friction lining, might produce abnormal sound.If the elasticity modulus of elastomeric element is set according to mode of the present utility model, elastomeric element is played a role during half-clutch state always, can prevent and friction lining generation part butt, thereby prevent to produce abnormal sound.
The rotary actuator of the Operation Van of the utility model the 5th aspect is characterized in that, described elastomeric element is configured between the friction lining of the most close described mobile pushing portion side in described mobile pushing portion and described first friction lining and described second friction lining.
According to this formation, if elastomeric element is configured between the friction lining of mobile pushing portion and the most close mobile pushing portion side, even exist under the concavo-convex situation in mobile pushing portion's run-off the straight or pushing face, also can push first friction lining or second friction lining with suitable attitude, thereby can improve the reliability that prevents with friction lining generation part butt by elastomeric element.
The rotary actuator of the Operation Van of the utility model the 6th aspect, it is characterized in that, to be that the annular plate parts at center are sticked in described slide unit sliding freely with described bolster, and these annular plate parts will be installed between the friction lining of described elastomeric element and the most close described mobile pushing portion side.
According to this formation, elastomeric element is installed between mobile pushing portion and the plate member.And,, therefore can not rotate with respect to the mobile pushing portion that is sticked in slide unit equally because plate member is sticked in slide unit.Like this, because elastomeric element is set at and does not take place between counterrotating two parts, therefore, relative rotation does not all take place with mobile pushing portion and plate member in elastomeric element, makes each parts be difficult for wearing and tearing.And, because the plate member of ring-type is installed, therefore can make via the thrust pressure of the mobile pushing portion of elastomeric element effect and further along the circumferential direction disperse, compare, can further improve the reliability that prevents with friction lining generation part butt with the situation that plate member is not installed.
The rotary actuator of the Operation Van of the utility model the 7th aspect is characterized in that, described elastomeric element is configured between the friction lining of the most close described static pushing portion side in described static pushing portion and described first friction lining and described second friction lining.
The thrust pressure of mobile pushing portion is passed to static pushing portion via whole friction linings, and based on the counteractive relation of effect, static pushing portion is also with identical with the thrust pressure of the mobile pushing portion friction lining of trying hard to recommend the most close static pushing of pressure portion side.According to this formation, if elastomeric element is configured between the friction lining of static pushing portion and the most close static pushing portion side, even the pushing face in static pushing portion exists concavo-convex, also can pass through elastomeric element, push first friction lining or second friction lining with suitable attitude, thereby can improve the reliability that prevents with friction lining generation part butt.
The rotary actuator of the Operation Van of the utility model eight aspect, it is characterized in that, to be the parts that the annular plate parts at center are sticked in described transmission gearbox side sliding freely with described bolster, and these annular plate parts will be installed between the friction lining of described elastomeric element and the most close described static pushing portion side.
According to this formation, elastomeric element is installed between static pushing portion and the plate member.And,, therefore can not rotate with respect to the parts of transmission gearbox side because plate member is sticked in the parts of transmission gearbox side.So, because elastomeric element is configured in and does not take place between counterrotating two parts, therefore, elastomeric element can not rotate with respect to static pushing portion and plate member, makes each parts be difficult for wearing away.And, because the plate member of ring-type is installed, therefore can make via the thrust pressure of the static pushing portion of elastomeric element effect and further along the circumferential direction disperse, compare, can further improve the reliability that prevents to take place one-sided butt with friction lining with the situation of adapter plate parts not.
The rotary actuator of the Operation Van of the utility model the 9th aspect is characterized in that, described elastomeric element is to be the ring-type disc spring at center with described bolster.
Because disc spring is along the circumferential direction continuous, compressive force disperses along its circumferencial direction when therefore having compression, and near the compress variation the compressive part of effect is bigger, and the compressive part of self-applying away from the less character of compress variation of part.On the other hand, mobile pushing portion carries out the part butt and is meant that certain part of mobile pushing portion is side-prominent to friction lining on shaft core direction.
Constitute according to this, be provided with as elastomeric element under the situation of disc spring, make disc spring generation compressive deformation to the side-prominent part of friction lining in the mobile pushing portion, along with leaving from this outshot, the compress variation of disc spring reduces.Consequently, a side that in disc spring, contacts with friction lining, the influence of the outstanding size of the outshot of mobile pushing portion, that is, mobile pushing portion is weakened with respect to the concavo-convex influence of the inclination of friction lining or contact surface.Consequently, disc spring contacts on full week equably with friction lining, and, at least in certain part generating plane contact, thereby can prevent the part butt, thereby prevent to produce under the half-clutch state abnormal sound.
The rotary actuator of the Operation Van of the utility model the tenth aspect is characterized in that, described elastomeric element is that being configured in described bolster equably is a plurality of coil springs on the circumference at center.
Constituting according to this, is on the circumference at center if will be configured in equably as a plurality of coil springs of elastomeric element with the bolster, owing to play the effect close with described disc spring, therefore can prevent to produce under the half-clutch state abnormal sound equally.Using under a plurality of helical spring situations,, be easy to set elasticity modulus although aspect the continuity of circumferencial direction, be not so good as disc spring.
Description of drawings
Fig. 1 is a combination machine single-piece left view of the present utility model.
Fig. 2 is the figure of expression to the train of gears of the driving system of each transmission of drive force.
Fig. 3 is the hydraulic circuit diagram that transmits the manipulation of steering arm.
Fig. 4 is the vertical profile front view that the side brake in left side enters half braking state rotary actuator before.
Fig. 5 is the vertical profile front view of side brake that enters the left side of braking mode.
The state that Fig. 6 is based on each one illustrates the figure of the state of side brake.
Fig. 7 is the vertical profile front view of side brake in the left side of first variation.
Fig. 8 is near the figure of the train of gears of the rotary actuator of expression second variation.
Description of reference numerals
2 mobile devices
8 steering arms (steering apparatus)
31 disc springs (elastomeric element)
32 thrust collars
33 coil springs (elastomeric element)
62 rotary actuators
64 drive transmitting gears
71 bolsters
72 sun gears (driven wheel)
73 clutch gears (slide unit)
74 side brakes (multi-disc wet clutch)
74a first friction lining
74b second friction lining
The prominent portion's (transmission gearbox side component) that establishes of 74c
The static pushing of 74d portion
77 springs are accommodated parts (mobile pushing portion)
E-engine
The MC transmission gearbox
The specific embodiment
Below, based on accompanying drawing the embodiment that the utility model is applied to the rotary actuator of half feed combine harvester is described.
[integral structure of combination machine]
Combination machine of the present utility model is half feed combine harvester that is used to gather in the crops paddy rice, wheat etc., as shown in Figure 1, have: the bone lattice of body are that organism frame 1, the pair of right and left crawler type running device 2 that supports body are (under the special situation about distinguishing of needs, the mobile devices in left side note is made 2L, the mobile devices note on right side is made 2R), be linked to the front portion of organism frame 1 the portion that extracts 3, be arranged on the sheller unit 4 and the granary 5 of the rear side of organism frame 1.Sheller unit 4 is configured in the horizontal side in a body left side with feeding chain 9.And, dispose the Drive Section 6 that the driver's seat is arranged on the body right side in the front side of organism frame 1.
Driving engine E (with reference to figure 2) is configured in the below of Drive Section 6.And, dispose running transmission gear 7 at the leading section of organism frame 1.Be passed to mobile devices 2 from the propulsive effort of driving engine E output after via running transmission gear 7 speed changes.Thus, drive mobile devices 2, combination machine is travelled.
[driving system of engine drive power]
Based on Fig. 2 to the propulsive effort with driving engine E be passed to mobile devices 2, extract portion 3, the driving system of sheller unit 4 describes.
As shown in Figure 2, the input shaft of the output shaft of driving engine E and sheller unit 4 is linked by driving band, and the propulsive effort of driving engine E is passed to threshing feeding chain 9 (with reference to figure 1), not shown threshing tube, screening plant etc.
Below, to the propulsive effort with driving engine E be passed to mobile devices 2, the structure that extracts portion 3 describes.Running transmission gear 7 has as the hydrostatic formula continuously variable unit (below, be called " HST ") 50 of the main speed changing portion that travels and the driving section 60 of travelling.The output shaft of driving engine E and the input shaft of HST50 53 are linked by driving band.Thus, the propulsive effort of driving engine E is passed to HST50.HST50 is housed among the change speed gear box TC.And HST50 has the axial piston hydraulic motor 52 that the pressure oil of axial plunger type hydraulic pump 51, the origin self-hydraulic pump 51 of volume-variable drives.Input shaft 53 is connected with Hydraulic Pump 51, and rotation is supported in change speed gear box TC freely.The propulsive effort that is passed to the driving engine E of HST50 is converted into advancing drive power or retreats propulsive effort by HST50, from output shaft 54 outputs that are connected with HM Hydraulic Motor 52.In addition, no matter HST50 still is that the pusher side can both be carried out infinitely speed change to propulsive effort in advance side.
The driving section 60 of travelling is housed in the transmission gearbox MC of the body lower side of travelling that is disposed at change speed gear box TC.The driving section 60 of travelling has travel secondary speed changing portion 61, rotary actuator 62 and drive transmitting axle 63.Output shaft 54 rotations of HST50 are freely across being supported on change speed gear box TC and transmission gearbox MC.In transmission gearbox MC, output shaft 54 links with the input shaft gear of the input shaft of the portion of extracting 3 sides and the secondary speed changing portion 61 that travels respectively.Thus, the propulsive effort from HST50 output is passed to the portion of extracting 3 respectively and travels secondary speed changing portion 61.
The secondary speed changing portion 61 that travels slows down to the propulsive effort that transmits from HST50 with three kinds of reduction ratios, and is passed to the sun gear described later 72 in the rotary actuator 62.
In the body lower side of travelling of rotary actuator 62, drive transmission shaft 63 rotations and freely be supported in transmission gearbox MC.Be supported with the drive transmitting gear 64 (under the special situation about distinguishing of needs, the drive transmitting gear note in body left side is made 64L, the drive transmitting gear note on body right side is made 64R) of pair of right and left freely in rotation on the drive transmitting axle 63.Drive transmitting gear 64L, 64R about the propulsive effort that transmits from sun gear 72 is passed to respectively via rotary actuator 62.
About mobile devices 2 have respectively: make track propulsion wheel body 21 that mobile devices 2 rotation drives, be connected and rotate the axle drive shaft 22 that travels that is supported in transmission gearbox MC freely, be installed in the gear 23 that travels on the axle drive shaft 22 that travels (under the situation of the special differentiation of needs with track propulsion wheel body 21, the gear note of travelling in left side is made 23L, the gear note of travelling on right side is made 23R).Drive transmitting gear 64L and the gear 23L that travels in left side in left side always mesh, and when propulsive effort travelling during gear 23L on the left of the drive transmitting gear 64L in left side is passed to, the mobile devices 2L in left side is driven.Equally, the gear 23R that travels on the drive transmitting gear 64R on right side and right side always meshes, and when propulsive effort is passed to travelling during gear 23R of right side from the drive transmitting gear 64R on right side, the mobile devices 2R on right side is driven.
[rotary actuator]
Based on Fig. 2 to Fig. 4 rotary actuator 62 is elaborated.Driving device 62 moves by the steering arm 8 as steering apparatus (with reference to figure 3) that manipulation is arranged on Drive Section 6.By the action of rotary actuator 62, can be respectively to about mobile devices 2L, 2R carry out the propulsive effort of driving engine E is passed to the cut-out of the driving system of mobile devices 2, puts on the braking of mobile devices 2 on the basis that cuts off this transmission system.That is it is poor that mobile devices 2L, the 2R about, rotary actuator 62 makes produces actuating speed.Thus, the driver of combination machine can select to carry out " slow rotation " described later when rotated and reach " original place rotation ".
As Fig. 2 and shown in Figure 4, rotary actuator 62 has: rotation is supported in the bolster 71 of transmission gearbox MC freely, rotation is supported in the sun gear 72 as driven wheel of bolster 71 freely, be embedded in the clutch gear 73 as slide unit of the pair of right and left of bolster 71 respectively outside relatively rotatably in the left and right sides of sun gear 72, by the clutch gear on the bolster 71 73 move respectively to about mobile devices 2L, the side brake 74 as multi-disc wet clutch of the pair of right and left that 2R brakes, disc spring 31 as elastomeric element, thrust collar 32 as plate member.
As shown in Figure 4, the two ends of bolster 71 are supported in the brake casing BC that is installed on the transmission gearbox MC via bearing R.About brake casing BC be installed in freely on the transmission gearbox MC by a plurality of bolt loading and unloadings.Brake casing BC has bearing maintaining part BC1 and installation portion BC2.Bearing maintaining part BC1 forms outstanding laterally bag shape, and bearing R is embedded in the bearing maintaining part BC1.Installation portion BC2 extends and forms to radial outside from the peripheral part of bearing maintaining part BC1, is formed with a plurality of bolts hole on installation portion BC2, is threadably engaged brake casing BC is installed on the transmission gearbox MC.
As mentioned above, sun gear 72 rotates by the propulsive effort from the driving engine E of the secondary speed changing portion 61 that travels.On the two sides of sun gear 72, along the circumferential direction be formed with block concavo-convex by fastener 72a.
Since about clutch gear 73 be the center left-right symmetric with sun gear 72, so here only the clutch gear 73 in left side is described.As shown in Figure 4, on sun gear 72 side ends of clutch gear 73, be formed with shape with by the cooresponding fastener 73a of fastener 72a.By handling steering arm 8 clutch gear 73 is relatively moved along bolster 71, this relatively moves and makes by fastener 72a and the fastener 73a engagement (state of the clutch gear 73 on right side, the left side of Fig. 4), perhaps make this engagement releasing (state of the clutch gear 73 in left side, the right side of Fig. 4).On the outer peripheral face of clutch gear 73, be formed with gear part 73b, this gear part 73b always with the drive transmitting gear 64L in left side engagement.Thus, when by fastener 72a and fastener 73a engagement, clutch gear 73 and the rotation of sun gear 72 one, the propulsive effort of driving engine E is passed to drive transmitting gear 64.On the other hand, when by the engagement releasing of fastener 72a and fastener 73a, the propulsive effort of driving engine E can not be passed to the drive transmitting gear 64L in left side.
As shown in Figure 3, be passed to the driving system of clutch gear 73 as manipulation with steering arm 8, combination machine has: the Hydraulic Pump 12 of discharging the oil in the fuel tank 11, be switched and be used to control three position suitching type control cock 13 by steering arm 8 for row from the pressure oil of Hydraulic Pump 12, can make hydraulic cylinder 14 from the pressure oil inflow of control cock 13, discrepancy is embedded in a pair of plunger 15 of hydraulic cylinder 14 freely (under the special situation about distinguishing of needs, 15L is made with the plunger note in the body left side, 15R is made with the plunger note in the right side), be limited to the outer peripheral face of clutch gear 73 and pass through plunger 15L, the discrepancy of 15R rotate and the control arm 16 of clutch gear 73 about handling respectively (under the special situation about distinguishing of needs, 16L is made with the control arm note in the body left side, 16R is made with the control arm note in the right side).In addition, between hydraulic cylinder 14 and plunger 15, dispose spring 17, spring 17 so that plunger 15 to the mode of hydraulic cylinder 14 sides resignations to plunger 15 application of forces.
Although illustrate especially,, if steering arm 8 is transformed to state L1 from neutral N state, then the left side is outstanding with plunger 15L, left side control arm 16L rotation.The left side moves clutch gear 73 with control arm 16L to the left, so that the engagement releasing of clutch gear 73 and sun gear 72.Consequently, the propulsive effort that mobile devices 2L to the left transmits is cut off, and combination machine is rotation more lentamente to the left, promptly delays rotation.Then, transform to L2 if steering arm 8 is further swung to the left, then the left side further moves clutch gear 73 with control arm 16L to the left, and the side brake described later 74 in left side enters braking mode.Consequently, the mobile devices 2L in left side is braked, combination machine is that the center rotates to the left with mobile devices 2L, promptly carries out the original place rotation ".
The situation that steering arm 8 shakes to the right too, under the situation of state R1, the slow to the right rotation of combination machine, under the situation of state R2, combination machine original place rotation to the right.
[side brake]
As shown in Figure 4, side brake 74 has the first friction lining 74a and the second friction lining 74b of a plurality of alternate configurations, first friction lining 74a slip is sticked in clutch gear 73, the second friction lining 74b slip freely (one is rotated freely) and is sticked in transmission gearbox MC with (can not rotating) freely.
Particularly, the part relative with the side of sun gear 72 is on the installation portion BC2 in brake casing BC, upright establish be formed with a plurality of to the side-prominent prominent 74c of portion that establishes of flange part 73d as the transmission gearbox side component.Each is prominent, and to establish the 74c of portion be to be integrally formed at installation portion BC2 under the state disconnected from each other on the same circumference at center with axle core L.Flange part 73d makes the centre portion of the peripheral part axis core L direction of clutch gear 73 form to the radial outside projection.The 73d of opposing flanges portion is near a side of friction lining in the peripheral part of clutch gear 73, and spline is chimeric to be had as the spring of the ring-type of mobile pushing portion and accommodate parts 77.It is the parts of accommodating disc spring 31 described later that spring is accommodated parts 77.Accommodating on the relative installation portion BC2 of parts 77 with spring, integrally formed oriented spring is accommodated the static pushing 74d of portion that parts 77 sides are swelled in the form of a ring.The static pushing 74d of portion is formed at prominent relatively position of establishing the 74c of portion near the inboard.
A plurality of first friction lining 74a splines are embedded in the peripheral part of clutch gear 73.And, make the many places of circumferencial direction in the peripheral part of the second friction lining 74b outstanding to radial outside, so that inserting the prominent 74c of the portion mode each other of establishing, this protrusion make a plurality of second friction lining 74b establish the 74c of portion and engage with dashing forward.Near the leading section of establishing the 74c of portion of dashing forward inner peripheral surface embeds spacing ring 76, thereby has prevented coming off of the second friction lining 74b.The first friction lining 74a and the second friction lining 74b alternate configurations.After the engagement releasing of clutch gear 73 and sun gear 72, by clutch gear 73 is moved to the direction of separating from sun gear 72, make the thrust pressure of clutch gear 73 be passed to thrust collar 32 described later via flange part 73d and disc spring 31, make thrust collar 32 and the static pushing 74d of portion push the first friction lining 74a and the second friction lining 74b, thereby can make the drg braking.
[disc spring and thrust collar]
As Fig. 4 and shown in Figure 5, disc spring 31 is so that big footpath side and spring are accommodated the outer slidably clutch gear 73 that is embedded in of the mode of parts 77 butts.Spring is accommodated parts 77 the friction lining side towards sun gear 72 sides depressions and form recess 77a.The external diameter of the big footpath side of disc spring 31 is bigger than the internal diameter of recess 77a, and the big footpath side of disc spring 31 is housed in the recess 77a freely.The internal diameter of the path side of disc spring 31 is bigger slightly than the external diameter of clutch gear 73, and disc spring 31 slides freely along axle core L direction with respect to clutch gear 73, but is difficult to respect to clutch gear 73 run-off the straights.The thickness of disc spring 31 cup depth than recess 77a on axle core L direction is big.Thereby, shown in the right side of Fig. 4, in disc spring 31 is housed in recess 77a fully and under the not compressed state of disc spring 31, the path side of disc spring 31 is side-prominent to friction lining from recess 77a.
As Fig. 4 and shown in Figure 5, thrust collar 32 is an endless member, with the mode between the friction lining of accommodating parts 77 sides at disc spring 31 and the most close spring slidably spline be embedded in clutch gear 73.In addition, be provided with annular shim S between disc spring 31 and thrust collar 32, the path side of disc spring 31 can contact with this pad S.Pad S spline slidably is embedded in clutch gear 73.Because the design of disc spring 31 is very difficult usually, therefore, by the thickness of change pad S, the compression opportunity that can easily change disc spring 31.In addition, replace pad S, also can change the thickness of thrust collar 32.
By above structure, disc spring 31 is installed in not and the counterrotating spring of clutch gear 73 generations is accommodated between parts 77 and the thrust collar 32.Thereby, relative rotation does not take place between each parts, can descend because of the abrasion performance of disc spring 31 hardly.
[drg action]
At first, based on Fig. 6 each state of side brake 74 is described.If clutch gear 73 is based on the manipulation of steering arm 8, from the state of the side brake 74 on right side shown in Figure 4 promptly with sun gear 72 complete ingear states gradually to side brake 74 side shiftings, the engagement releasing of clutch gear 73 and sun gear 72 then.Thus, be cut off from the propulsive effort of driving engine E, combination machine delays rotation.If make clutch gear 73 further to side brake 74 side shiftings, then flange part 73d accommodates parts 77 with spring and contacts, and is housed in spring and accommodates the path thruster of the disc spring 31 in the parts 77 and press thrust collar 32.Then, thrust collar 32 moves along with moving of clutch gear 73, and contacts with the friction lining of the most close clutch gear 73 sides.Thereafter, the gap between the first friction lining 74a and the second friction lining 74b dwindles because of moving of clutch gear 73.Finally, the state of the side brake 74 in left side as shown in Figure 4 is such, and the gap between the first friction lining 74a and the second friction lining 74b disappears.Till this state, squeese pressure does not act on the first friction lining 74a and the second friction lining 74b, and the relative rotation with the second friction lining 74b of the first friction lining 74a freely.The state that this side brake 74 is braked is the non-braking mode of " disengaging of clutch state ".And during non-braking mode, compressive deformation does not take place in disc spring 31.
And if make clutch gear 73 continue pushing, then compressive deformation takes place because of the thrust pressure of clutch gear 73 in disc spring 31.Consequently, the resilient force that produces because of the compressive deformation of disc spring 31 in thrust collar 32, the first friction lining 74a and the second friction lining 74b by thrust collar 32 and the static pushing 74d of portion extruding.Along with the rising of this squeese pressure, the relative rotation of the first friction lining 74a and the second friction lining 74b descends because of friction each other, and final rotation relatively stops.That is, mobile devices 2 are braked fully.This state is the braking mode of " clutch engagement state ".If the braking mode of entering, then combination machine to the left and right either direction carry out original place rotation.The half braking state of counterrotating state for " half-clutch state " still takes place in the effect of the state between non-braking mode and the braking mode and the power that is squeezed but two friction linings.
[compressive deformation of disc spring]
Disc spring 31 is brought into play its effect under half braking state.Under half braking state (state of the side brake 74 in left side shown in Figure 4), there is not the gap between the first friction lining 74a and the second friction lining 74b.Therefore, disc spring 31 is accommodated parts 77 and thrust collar 32 extruding by spring, because of compressive deformation takes place for the thrust pressure of clutch gear 73.If disc spring 31 is compressed, compressive force (thrust pressure of clutch gear 73) is disperseed and the generation compressive deformation along its circumferencial direction.Near the contact part of the effect of disc spring 31 compressive big footpath side and recess 77a compress variation is bigger, the compressive part of the self-applying of disc spring 31 away from the compress variation of part less.Therefore, even because of the inclination of flange part 73d (clutch gear 73) or because of the concavo-convex part of flange part 73d that causes of the pushing face of flange part 73d side-prominent to friction lining, because the bigger compression of disc spring 31 quilts with this outshot touching position, therefore, thrust pressure is passed to thrust collar 32 under the weakened state of the influences such as inclination that make clutch gear 73.That is, disc spring 31 contacts on full week equably with thrust collar 32, and, at least in certain part generating plane contact.Consequently, thrust collar 32 contacts with friction lining with attitude suitably, can not divide contact because of generating unit and produce abnormal sound.
Thereafter, if the thrust pressure of clutch gear 73 continue to raise, then disc spring 31 continues to take place compressive deformation along with the rising of thrust pressure.Finally, as shown in Figure 5, if the braking mode of entering comprises that then the disc spring 31 of minor diameter part is housed in the recess 77a fully, spring is accommodated parts 77 and is contacted with thrust collar 32.But when just entering braking mode, the rotation of the first friction lining 74a definitely stops, and therefore, comes in contact with thrust collar 32 even spring is accommodated parts 77, also can not produce abnormal sound.So, disc spring 31 plays a role during half braking state always, can not produce abnormal sound.
[first variation]
In the above-described embodiment, disc spring 31 is set at that spring is accommodated parts 77 and the most close spring is accommodated between the friction lining of parts 77, but is not limited thereto.For example, as shown in Figure 7, disc spring 31 also can be set between the friction lining of static pushing 74d of portion and the most close static pushing 74d of portion, and is same, also thrust collar 32 can be arranged between the friction lining of disc spring 31 and the most close static pushing 74d of portion side.The squeese pressure that acts on the friction lining is the thrust pressure generation of the static pushing 74d of portion by the thrust pressure of clutch gear 73 and the antagonistic force of this thrust pressure, therefore constitutes as previously mentioned also can access same effect.In addition, in this variation, thrust collar 32 spline slidably is embedded in the prominent 74c of portion that establishes.
In above-mentioned embodiment and this variation, disc spring 31 towards decisions such as shape by other parts, where path side and big footpath side all can to configuration towards.And, also thrust collar 32 can be set and adopt the structure make disc spring 31 and friction lining direct contact.Disc spring 31 is not limited to one, also can use a plurality of elastic forces of adjusting.
[second variation]
In the above-described embodiment, show and use the embodiment of disc spring 31, still, replace disc spring 31, also can on the circumference that with bolster 71 is the center, dispose a plurality of coil spring 33 equably as elastomeric element as elastomeric element.In the case, the quantity of coil spring 33 is The more the better.As shown in Figure 8, coil spring 33 can be arranged between the friction lining of flange part 73d and the most close flange part 73d, also can be arranged between the friction lining of static pushing 74d of portion and the most close static pushing 74d of portion.
[other variation]
(1) in the above-described embodiment, the combination machine that has as the steering arm 8 of steering apparatus is illustrated, but steering apparatus also can be bearing circle.
(2) in the above-described embodiment, side brake 74 is used for mobile devices 2 are braked, but is not limited to this.Although it is not shown, but the propulsive effort that also can possess the driving engine that will obtain separately converts to than the propulsive effort high speed that is passed to mobile devices 2 via sun gear 72 or the change gear transmission of low-tach propulsive effort, when side brake 74 enters braking mode, will be passed to the mobile devices 2 of hand of rotation side from the propulsive effort of change gear transmission.In addition, the propulsive effort of change gear transmission generation also can be the propulsive effort of direction of retreat.
Industrial applicibility
Rotary actuator of the present utility model is not limited to united reaper, and agricultural machine, the back hoes such as seeder, hay mover etc. that also can be applied to have wet multi-plate formula clutch are built working rig.
Claims (10)
1. the rotary actuator of an Operation Van, it has can separately-driven pair of right and left mobile devices (2) based on the manipulation of steering apparatus (8), it is characterized in that having:
Driven wheel (72), it is supported in the bolster (71) that is erected at transmission gearbox (MC), and the propulsive effort by driving engine (E) is rotated driving;
Slide unit (73), it is a pair of right and left, outside the left and right sides of described driven wheel (72) respectively can be with the relative rotation, be embedded in described bolster (71), and always mesh separately with the pair of right and left drive transmitting gear (64) that is linked to the described mobile devices of pair of right and left (2) respectively, by the manipulation of described steering apparatus (8), it relatively moves and can mesh with described driven wheel (72) respectively along described bolster (71);
Multi-disc wet clutch (74), it is configured in the left and right sides of described driven wheel (72);
Elastomeric element (31,33), elasticity of compression distortion can take place along described bolster (71) in it, makes resilient force in being on the circumference at center with described bolster (71).
2. the rotary actuator of an Operation Van, its have can separately-driven pair of right and left based on the manipulation of steering apparatus (8) mobile devices (2), it is characterized in that having:
Driven wheel (72), it is supported in the bolster (71) that is erected at transmission gearbox (MC), and the propulsive effort by driving engine (E) is rotated driving;
Slide unit (73), it is a pair of right and left, outside the left and right sides of described driven wheel (72) respectively can be with the relative rotation, be embedded in described bolster (71), and always mesh separately with the pair of right and left drive transmitting gear (64) that is linked to the described mobile devices of pair of right and left (2) respectively, by the manipulation of described steering apparatus (8), it relatively moves and can mesh with described driven wheel (72) respectively along described bolster (71);
Multi-disc wet clutch (74), it is a pair of right and left, the left and right sides in described driven wheel (72), alternate configurations has a plurality of second friction linings (74b) that are sticked in first friction lining (74a) of described slide unit (73) sliding freely and are sticked in the parts (74c) of described transmission gearbox (MC) side sliding freely, after the engagement releasing of described slide unit (73) and described driven wheel (72), described slide unit (73) separates from described driven wheel (72), is arranged on thus that described slide unit (73) is gone up and can be along the mobile pushing portion (77) of described bolster (71) pushing described first friction lining (74a) or described second friction lining (74b) and as static pushing portion (74d) extruding described first friction lining (74a) and described second friction lining (74b) relative with described mobile pushing portion (77) of the parts of described transmission gearbox (MC) side;
Elastomeric element (31,33), elasticity of compression distortion can take place along described bolster (71) in it, makes resilient force in being on the circumference at center with described bolster (71).
3. the rotary actuator of an Operation Van, its have can separately-driven pair of right and left based on the manipulation of steering apparatus (8) mobile devices (2), it is characterized in that having:
Driven wheel (72), it is supported in the bolster (71) that is erected at transmission gearbox (MC), and the propulsive effort by driving engine (E) is rotated driving;
Slide unit (73), it is a pair of right and left, outside the left and right sides of described driven wheel (72) respectively can be with the relative rotation, be embedded in described bolster (71), and always mesh separately with the pair of right and left drive transmitting gear (64) that is linked to the described mobile devices of pair of right and left (2) respectively, by the manipulation of described steering apparatus (8), it relatively moves and can mesh with described driven wheel (72) respectively along described bolster (71);
Multi-disc wet clutch (74), it is a pair of right and left, the left and right sides in described driven wheel (72), alternate configurations has a plurality of second friction linings (74b) that are sticked in first friction lining (74a) of described slide unit (73) sliding freely and are sticked in described transmission gearbox (MC) side component (74c) sliding freely, after the engagement releasing of described slide unit (73) and described driven wheel (72), described slide unit (73) separates from described driven wheel (72), is arranged on thus that described slide unit (73) is gone up and can be along the mobile pushing portion (77) of described bolster (71) pushing described first friction lining (74a) or described second friction lining (74b) and as static pushing portion (74d) extruding described first friction lining (74a) and described second friction lining (74b) relative with described mobile pushing portion (77) of the parts of described transmission gearbox (MC) side;
Elastomeric element (31,33), elasticity of compression distortion can take place along described bolster (71) in it, makes resilient force in being on the circumference at center with described bolster (71);
Make described first friction lining (74a) and described second friction lining (74b) seamlessly after the proper alignment in the pushing by described mobile pushing portion (77), the squeese pressure of described mobile pushing portion (77) and described static pushing portion acts at least one side in described first friction lining (74a) and described second friction lining (74b) via elastomeric element (31,33).
4. according to the rotary actuator of claim 2 or 3 described Operation Vans, it is characterized in that, the elasticity modulus of described elastomeric element (31,33) is set for, stop up to the relative rotation of described first friction lining (74a) with described second friction lining (74b), described squeese pressure only acts on via described elastomeric element (31,33).
5. the rotary actuator of Operation Van according to claim 2, it is characterized in that, described elastomeric element (31,33) is configured between the friction lining of the most close described mobile pushing portion (77) side in described mobile pushing portion (77) and described first friction lining (74a) and described second friction lining (74b).
6. the rotary actuator of Operation Van according to claim 5, it is characterized in that, to be that the annular plate parts (32) at center are sticked in described slide unit (73) sliding freely with described bolster (71), and these annular plate parts (32) will be installed between the friction lining of described elastomeric element (31,33) and the most close described mobile pushing portion (77) side.
7. the rotary actuator of Operation Van according to claim 2, it is characterized in that, described elastomeric element (31,33) is configured between the friction lining of the most close described static pushing portion (74d) side in described static pushing portion (74d) and described first friction lining (74a) and described second friction lining (74b).
8. the rotary actuator of Operation Van according to claim 7, it is characterized in that, to be that the annular plate parts (32) at center are sticked in the parts of described transmission gearbox (MC) side sliding freely with described bolster (71), and these annular plate parts (32) will be installed between the friction lining of described elastomeric element (31,33) and the most close described static pushing portion (74d) side.
9. according to the rotary actuator of each the described Operation Van in the claim 1 to 3,5 to 8, it is characterized in that described elastomeric element is to be the ring-type disc spring (31) at center with described bolster (71).
10. according to the rotary actuator of each the described Operation Van in the claim 1 to 3,5 to 8, it is characterized in that described elastomeric element is that being configured in described bolster (71) equably is a plurality of coil springs (33) on the circumference at center.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010079633A JP2011208788A (en) | 2010-03-30 | 2010-03-30 | Turning transmission device for working vehicle |
| JP079633/10 | 2010-03-30 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201980291U true CN201980291U (en) | 2011-09-21 |
Family
ID=44607756
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200858669U Expired - Fee Related CN201980291U (en) | 2010-03-30 | 2011-03-29 | Rotating transmission device for operating vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2011208788A (en) |
| CN (1) | CN201980291U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107406103A (en) * | 2015-01-19 | 2017-11-28 | 株式会社神崎高级工机制作所 | Wheel steering system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6068867U (en) * | 1983-10-18 | 1985-05-16 | セイレイ工業株式会社 | Side clutch and brake device for traveling work equipment |
| JPH0225934Y2 (en) * | 1985-08-16 | 1990-07-16 | ||
| JPH082039Y2 (en) * | 1990-05-16 | 1996-01-24 | セイレイ工業株式会社 | Vehicle running device |
-
2010
- 2010-03-30 JP JP2010079633A patent/JP2011208788A/en active Pending
-
2011
- 2011-03-29 CN CN2011200858669U patent/CN201980291U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107406103A (en) * | 2015-01-19 | 2017-11-28 | 株式会社神崎高级工机制作所 | Wheel steering system |
| CN107406103B (en) * | 2015-01-19 | 2019-09-27 | 株式会社神崎高级工机制作所 | Wheel steering system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011208788A (en) | 2011-10-20 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
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