CN203661633U - Differential mechanism type track combine-harvester gearbox - Google Patents
Differential mechanism type track combine-harvester gearbox Download PDFInfo
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- CN203661633U CN203661633U CN201320867719.6U CN201320867719U CN203661633U CN 203661633 U CN203661633 U CN 203661633U CN 201320867719 U CN201320867719 U CN 201320867719U CN 203661633 U CN203661633 U CN 203661633U
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Abstract
本实用新型属于农业机械领域，尤其涉及一种差速器式履带联合收割机变速箱，包括箱体，箱体内依次包括动力输入轴、三档变速装置换挡轴、差速器轴、转向控制轴、差速器控制轴、动力输出轴和位于动力输出轴下部并分别与动力输出轴两端通过齿轮连接的两动力输出半轴，及设置在各轴上且相互啮合的齿轮传动机构及液压控制系统；本实用新型几乎没有制动功率损失，转向时更加容易，转向半径更小，更易于田间作业，且翻车几率大大降低，且当车辆进行大半径或原地转向时，制动差速器齿轮即可实现，操作更加简单方便；左右微调时无需用到摩擦片，大大减小摩擦片的损耗，进一步提高了变速箱的寿命以及可靠性。
The utility model belongs to the field of agricultural machinery, in particular to a gearbox for a differential crawler combine harvester, which includes a box body, which sequentially includes a power input shaft, a shift shaft of a three-speed transmission device, a differential shaft, and a steering control shaft. Shaft, differential control shaft, power take-off shaft, two power take-off half shafts located at the lower part of the power take-off shaft and respectively connected to both ends of the power take-off shaft through gears, and the gear transmission mechanism and hydraulic pressure mechanism arranged on each shaft and intermeshing with each other Control system; the utility model has almost no braking power loss, easier steering, smaller steering radius, easier field work, and greatly reduced chance of overturning, and when the vehicle is turning with a large radius or in situ, the braking differential It can be realized by using only gears, and the operation is more simple and convenient; there is no need to use friction plates when fine-tuning left and right, which greatly reduces the loss of friction plates, and further improves the life and reliability of the gearbox.
Description
Technical field
The utility model belongs to agricultural mechanical field, relates to a kind of single current caterpillar combine Side Gearbox Transmission System, has especially adopted the gear box steering mechanism of crawler type harvester of differential mechanism.
Background technology
The steering mechanism of current domestic caterpillar combine mainly adopts single current one side brake steering principle, this steering principle adopts and separates interposed clutch axle and brake a side crawler belt and complete and turn to, by the control of brake on the semiaxis of clutch left and right is completed to turning to of various radiuses.
But have at present very large problem, in the time of a side crawler belt braking, it produces sliding friction completely to ground in the time turning to, and paddy field soil is destroyed serious; It is in the time turning to, and the crawler belt of brake side can cause that the heap soil or fertilizer over and around the roots of soil is long-pending, thereby causes and turn to difficulty, and cause oil inflame insufficient, simultaneously due to the demand for large feed quantity combined harvester on market, under same chassis aspect ratio, the weight that increases complete machine, can make to turn to more difficult; Farm work need to be finely tuned course, and traditional one side brake steering adopts point braking type steering mode to finely tune, and does like this for the loss of internal friction sheet comparatively seriously, and the life-span greatly reduces.Inside while turning to there is braking power loss in crawler belt, and outside needs engine that more power is provided, once load increases, one-sided crawler belt resistance increment, will cause engine misses.
Patent ZL03245493.9 discloses a kind of travel steering device, by the braking of left and right clutch gear and parallel planet wheel mechanism is realized and turns to and keep straight on, this structure can realize pivot stud function, but can not directly use in actual farm work, because what it adopted is that clutch shaft completes the switching that turns to and keep straight on, once left and right semiaxis is oppositely in conjunction with doing great damage to the clutch gear on clutch shaft, and it also will stop after pivot stud completes, unfavorable to the fluency of farm work.
Patent ZL240640024088.7 discloses a kind of double-current method steering mechanism, turn to input power and craspedodrome power to converge by both sides planetary gear, can smooth and easyly complete the conversion that turns to and keep straight on, but it is double-flow design, need to separately add an independent power completes and turns to, the power distribution of existing combined harvester is very nervous, there is no unnecessary power distribution to steering mechanism, and price is comparatively expensive.
Patent application 241324140240.4 discloses the lazy shaft type pivot stud of a kind of single current class mechanism, it is realized idle pulley of similar increase by double-sliding gear and realizes reverse effect, this kind of steering mode is more serious for the damage ratio of gear, and owing to being the mode that adopts mechanical type balladeur train, quite require great effort, increased the intensity of farm work.
Utility model content
The purpose of this utility model is to overcome the defect that prior art exists, and provides a kind of novel structure, easy to operate differential type crawler-type combine harvester gearbox.
The technical scheme that realizes the utility model object is: a kind of differential type crawler-type combine harvester gearbox; Comprise casing, the two power output axle shafts that comprise successively power input shaft, three class gear shift device shifting shaft, differential axle, steering controlling shaft, differential controls axle, power take-off in described casing and be positioned at power take-off bottom and be connected by gear with power take-off two ends respectively, and be arranged on each axle and pitch wheel transmission mechanism and hydraulic control system;
Described three class gear shift device shifting shaft comprises the first three class gear shift device shifting shaft and the second three class gear shift device shifting shaft;
On described power input shaft, be provided with power input gear, the first triple gear and three class gear shift device input gear are set on the first three class gear shift device shifting shaft, wherein on the first three class gear shift device shifting shaft, be free to slide, the second three class gear shift device shifting shaft middle part is provided with the second triple gear, the second three class gear shift device shifting shaft two ends are respectively provided with a power output gear, and described two power output gears link with the second three class gear shift device shifting shaft spline;
Described differential axle middle part is provided with center differential gear, center differential gear empty set is on differential axle, the each cover in differential axle two ends in described center differential gear outside has a bevel gear, two large clutch gears link with two bevel gear splines respectively, and the upper also symmetry of described two bevel gears is set with two little clutch gears;
On described steering controlling shaft, be symmetrically arranged with successively from outside to inside two hydraulic clutches, two spragging gears, two shift forks and check ring, wherein two spragging gears and two shift fork empty sets are on steering controlling shaft, described two shift forks are controlled respectively two little clutch gears, and described check ring is fixed by positioning device in the centre position of steering controlling shaft;
The output gear that is provided with liquid braking device on described differential controls axle and engages with differential gear, wherein output gear links with axle spline;
Described power take-off two ends are respectively provided with a duplicate gear, and wherein two duplicate gear empty sets are on power take-off; On described power output axle shaft, be respectively arranged with an output gear, wherein output gear links with power output axle shaft difference spline;
Described hydraulic control system comprises liquid braking device, many hydraulic circuits and hydraulic control device, and the above liquid braking device of described liquid braking device comprises the first liquid braking device that is positioned at steering controlling shaft two ends and the second liquid braking device that is positioned at differential controls axle one end; Described hydraulic circuit comprises and is positioned at many articles of the first hydraulic circuits, second hydraulic circuit at steering controlling shaft two ends and is positioned at the 3rd hydraulic circuit on differential controls axle; Described hydraulic control device is arranged on shift fork.
Technique scheme, power input gear described in described gear drive engages with three class gear shift device input gear, described the first triple gear engages with the second triple gear, two power output gears engage with two large clutch gears respectively, described two large clutch gears are combined with two denticle cogwheel dental inlays, described denticle cogwheel engages with two duplicate gears respectively, described two duplicate gears are meshed with two output gears, two spragging gears are meshed with two little clutch gears respectively, and described center differential gear engages with output gear.
Technique scheme, described center differential gear includes 4 optical axises, and described 4 optical axis cross layout, is set with a bevel gear on every axle, and bevel gear engages with left and right conical geared sleeve respectively.
Technique scheme, described the first liquid braking device ecto-entad is provided with the first oil circuit, the first outer end cap, the first sealing baffle, first piston, the first friction plate, the first back-moving spring and spragging gear successively, and described the first back-moving spring top is also provided with the first friction plate; Described first piston is provided with groove, and the extension of described spragging gear is greater than 5mm from bottom portion of groove distance, is less than 24mm; Described the second liquid braking device ecto-entad is provided with the 3rd oil circuit, the second outer end cap, the second sealing baffle, the second piston, the second back-moving spring successively, and described the second back-moving spring is provided with the second friction plate.
Technique scheme, on described two shift forks, outside is equipped with the 3rd piston and sealing baffle, is provided with the 3rd back-moving spring between described two shift forks, and described the 3rd back-moving spring middle part is also provided with check ring, and between described check ring and shift fork, gap is greater than 10mm.
Technique scheme, hydraulic oil is applied to the pressure of hydraulic oil on first piston, the second piston and the 3rd piston by the first hydraulic circuit, the second hydraulic circuit and the 3rd hydraulic circuit, and the oil circuit exit opening of controlling shift fork is greater than controls the first liquid braking device oil circuit outlet, and described the first hydraulic circuit, the second hydraulic circuit and the 3rd hydraulic circuit porch are provided with reversal valve.
Adopt after technique scheme, the utlity model has following positive effect:
The utility model useful effect compared with existing one side brake steering mechanism is that the utility model adopts differential type steering mechanism, in the time that needs turn to, stir little clutch gear by shift fork, make it to depart from large clutch gear, thereby interrupt power input, due to the existence of differential gear, differential gear is braked, the bevel gear of one side drives opposite side bevel gear constant speed to rotate backward, in the time that differential gear is not checked completely, to complete variable speed rotates backward, when in high speed operation shelves, can not brake differential gear, it is rotated arbitrarily, if the now crawler belt of braking one side, opposite side crawler belt will be not can speedup, the advantage of this kind of steering mode is that differential mechanism work schedule moves a side crawler belt, engine input power all proceeds to opposite side crawler belt, almost there is no braking power loss, while turning to, be more prone to, turning radius is less, be easier to farm work, and differential steering meeting causes the danger of overturning when considering that vehicle high-speed is advanced, so being set on differential axle, an axle controls specially its motion, when differential gear is during in slave mode not, to not realize differential mechanism function, in the time of braking differential gear, just understand practical function, the utility model and traditional differential mechanism difference are, tradition differential mechanism power is delivered to via bevel planet gear on the bevel gear semiaxis of both sides, belonging to trailing type turns to, uncontrollable differential mechanism is kept straight on or is turned to, in the time that crawler belt suffered resistance in both sides is inconsistent, vehicle will commutate voluntarily, and farm work requires vehicle to have good linear driving performance, and traditional differential design cannot realize.
In the utility model, on shifting shaft, be provided with a pair of triple gear of dynamic branch, both sides crawler belt will respectively have independent power stream to drive, like this, in the time that differential gear is not worked, both sides crawler belt will be in constant speed state, guaranteed the craspedodrome of vehicle, in the time of the large radius of needs or pivot stud, braking differential gear can be realized.Fine setting when farm work above left and right directions is frequent especially, traditional one side brake steering adopts point braking type steering mode to finely tune, do like this for the loss of internal friction sheet comparatively serious, life-span greatly reduces, the utility model only need to be to fork controls oil circuit injection liquid force feed in the time carrying out left and right fine setting, throw off the power input of a side, rely on ground to finely tune in the face of the resistance of crawler belt completes left and right turn, without using friction plate, greatly reduce the loss of friction plate, further improved life-span and the reliability of gearbox.
Accompanying drawing explanation
For content of the present utility model is more easily expressly understood, according to specific embodiment also by reference to the accompanying drawings, the utility model is described in further detail, wherein below
Fig. 1 is the utility model vertical structure schematic diagram;
Fig. 2 is the utility model partial structurtes schematic diagrames;
Fig. 3 is the utility model end view;
In figure 1, power input gear; 2, power input shaft; 3, three class gear shift device input gear; 4, shifting shaft; 41, the first three class gear shift device shifting shaft; 42, the second three class gear shift device shifting shaft; 5, the first triple gear; 6, the second triple gear; 7, output gear; 8, large clutch gear; 9, little clutch gear; 10, differential axle; 11, bevel gear cover; 12, duplicate gear; 13, power take-off; 14, output gear; 15, power output axle shaft; 16, check ring; 17, steering controlling shaft; 18, the first friction plate; 19, the first back-moving spring; 20, the first outer end cap; 21, the first sealing baffle; 22, first piston; 23, spragging gear; 24, the 3rd piston; 25, shift fork; 26, the second outer end cap; 27, the second piston; 28, the second back-moving spring; 29, the second friction plate; 30, differential gear; 31, differential controls axle; 32, output gear; 33, the first hydraulic circuit; 34, the second hydraulic circuit; 35, the 3rd hydraulic circuit; 36, the 3rd back-moving spring.
Embodiment
(embodiment 1)
See Fig. 1 to Fig. 3, the utility model differential type crawler-type combine harvester gearbox; Comprise casing, the two power output axle shafts 15 that comprise successively power input shaft 2, three class gear shift device shifting shaft 4, differential axle 10, steering controlling shaft 17, differential controls axle 31, power take-off 13 in casing and be positioned at power take-off 13 bottoms and be connected by gear with power take-off 13 two ends respectively, and be arranged on each axle and pitch wheel transmission mechanism and hydraulic control system.
Described three class gear shift device shifting shaft 4 comprises the first three class gear shift device shifting shaft 41 and the second three class gear shift device shifting shaft 42.
On described power input shaft 2, be provided with power input gear 1, the first triple gear 5 and three class gear shift device input gear 3 are set on the first three class gear shift device shifting shaft 41, wherein on the first three class gear shift device shifting shaft 41, be free to slide, the second three class gear shift device shifting shaft 42 middle parts are provided with the second triple gear 6, the second three class gear shift device shifting shaft 42 two ends are respectively provided with a power output gear 7, and described two power output gears 7 link with the second three class gear shift device shifting shaft 42 splines.
Described differential axle 10 middle parts are provided with center differential gear 30, center differential gear 30 empty sets are on differential axle 10, the each cover in differential axle 10 two ends in described center differential gear 30 outsides has a bevel gear, two large clutch gears 8 link with two bevel gear splines respectively, and the upper also symmetry of described two bevel gears is set with two denticle cogwheels 9.
On described steering controlling shaft 17, be symmetrically arranged with successively from outside to inside two hydraulic clutches 18, two spragging gears 23, two shift forks 25 and check ring 16, wherein two spragging gears 23 and two shift fork 25 empty sets are on steering controlling shaft 17, described two shift forks 25 are controlled respectively two denticle cogwheels 9, and described check ring 16 is fixed by positioning device in the centre position of steering controlling shaft 17.
The output gear 32 that is provided with liquid braking device 26 on described differential controls axle 31 and engages with differential gear 30, wherein output gear 32 links with axle 31 splines.
Described power take-off 13 two ends are respectively provided with a duplicate gear 12, and wherein two duplicate gear 12 empty sets are on power take-off 13; On described power output axle shaft 15, be respectively arranged with an output gear 14, wherein output gear 14 links with power output axle shaft 15 difference splines.
Described hydraulic control system comprises liquid braking device, many hydraulic circuits and hydraulic control device, and the above liquid braking device of described liquid braking device comprises the first liquid braking device that is positioned at steering controlling shaft 17 two ends and the second liquid braking device that is positioned at differential controls axle 31 one end; Described hydraulic circuit comprises and is positioned at many articles of the first hydraulic circuits 33, second hydraulic circuits 34 at steering controlling shaft 17 two ends and is positioned at the 3rd hydraulic circuit 35 on differential controls axle 31; Described hydraulic control device is arranged on shift fork 25.
Power input gear 1 described in described gear drive engages with three class gear shift device input gear 3, described the first triple gear 5 engages with the second triple gear 6, two power output gears 7 engage with two large clutch gears 8 respectively, described two large clutch gears 8 are combined with two denticle cogwheel 9 dental inlays, described denticle cogwheel 9 engages with two duplicate gears 12 respectively, described two duplicate gears 12 are meshed with two output gears 14, two spragging gears 23 are meshed with two denticle cogwheels 9 respectively, and described center differential gear 30 engages with output gear 32.
Described center differential gear 30 includes 4 optical axises, and described 4 optical axis cross layout, is set with a bevel gear on every axle, and bevel gear engages with left and right conical geared sleeve 11 respectively.
Described the first liquid braking device ecto-entad is provided with the first oil circuit 33, the first outer end cap 20, the first sealing baffle 21, first piston 22, the first friction plate 18, the first back-moving spring 19 and spragging gear 23 successively, and described the first back-moving spring 19 tops are also provided with the first friction plate 18; Described first piston 22 is provided with groove, and the extension of described spragging gear 23 is greater than 5mm from bottom portion of groove distance, is less than 24mm; Described the second liquid braking device 26 ecto-entads are provided with the 3rd oil circuit 35, the second outer end cap 26, the second sealing baffle, the second piston 27, the second back-moving spring 28 successively, and described the second back-moving spring 28 is provided with the second friction plate 29.
On described two shift forks 25, outside is equipped with the 3rd piston 24 and sealing baffle, between described two shift forks 25, is provided with the 3rd back-moving spring 36, and described the 3rd back-moving spring 36 middle parts are also provided with check ring 16, and between described check ring 16 and shift fork 25, gap is greater than 10mm.
Hydraulic oil is applied to the pressure of hydraulic oil on first piston 22, the second piston 27 and the 3rd piston 24 by the first hydraulic circuit 33, the second hydraulic circuit 34 and the 3rd hydraulic circuit 35, and the oil circuit exit opening of controlling shift fork 25 is greater than controls the first liquid braking device 20 oil circuit outlets, and described the first hydraulic circuit 33, the second hydraulic circuit 34 and the 3rd hydraulic circuit 35 porch are provided with reversal valve.
Operation principle of the present utility model is: in the time that crawler belt combined harvester is kept straight on, power is delivered to three class gear shift device input gear 3 via power input gear 1, three class gear shift device input gear 3 drives the first three class gear shift device shifting shaft 41 to rotate, the first triple gear 1 rotates thereupon, power is delivered on the second triple gear 6 via the first triple gear 5, the second triple gear 6 drives the second three class gear shift device shifting shaft 42 to rotate, thereby drive two output gears 7 to rotate, output gear 7 is with two large clutch gears 8 on dynamic bevel gear cover 11 to rotate, two large clutch gears 8 engage with two denticle cogwheel 9 dental inlays respectively, thereby drive two denticle cogwheels 9 to rotate, two denticle cogwheels 9 engage with two duplicate gears 12 respectively, thereby drive two duplicate gears 12 to rotate, two duplicate gears 12 drive two output gears 14 to rotate again, two output gears 14 make respectively two power output axle shaft 15 constant speed rotations, thereby vehicle is kept straight on,
In the time that crawler belt combined harvester need to be braked, open the reversal valve of controlling left and right sides steering controlling shaft 17 simultaneously, hydraulic oil first injects by the second hydraulic circuit 34, therefore, hydraulic oil will first promote two the 3rd pistons 24, shift fork two 25 is moved to centre, thereby make two denticle cogwheels 9 depart from two large clutch gears 8, thereby cut off the power of HST output, subsequently, hydraulic oil also promotes first piston 22 through the first hydraulic circuit 33 and compresses the first friction plate 18, two spragging gears 23 are braked, because two spragging gears 23 engage with two denticle cogwheels 9 respectively, so two denticle cogwheels 9 are also braked, because two denticle cogwheels 9 engage with two duplicate gears 12 respectively, two duplicate gears 12 engage with two output gears 14, two output gears 14 link with two power output axle shaft 15 splines, therefore effect output axle shaft 15 in left and right is braked, thereby complete braking procedure.
In the time that crawler belt combined harvester needs minor radius to turn to greatly, first open the reversal valve of the second hydraulic circuit 34 of controlling steering controlling shaft top, left side, hydraulic oil injects by the second hydraulic circuit 34, therefore left side shift fork 25 can first move right, thereby drive left side denticle cogwheel 9 to move right, depart from the large clutch gear 8 in left side, thereby cut off the power input of left track, subsequently, hydraulic oil is delivered on the first piston 22 of left side by left side the first hydraulic circuit 33, thereby promoting left side the first friction plate 18 is braked left side spragging gear 23, because left side gear 23 engages with left side denticle cogwheel 9, therefore left side denticle cogwheel 9 is also braked, thereby left track is braked, thereby vehicle completes large radius left steering.
In the time that crawler belt combined harvester needs large radius right turn, first open the reversal valve of controlling the second hydraulic oil circuit 34 on right hand steering Control Shaft, hydraulic oil injects by right side the second hydraulic oil circuit 34, therefore shift fork right side 25 can first be moved to the left, thereby drive right side denticle cogwheel 9 to be moved to the left, depart from the large clutch gear 8 in right side, thereby cut off the power input of right side crawler belt, subsequently, hydraulic oil is delivered on right side first piston 22 by oil circuit right side the first hydraulic oil circuit 33, thereby promoting right side the first friction plate 18 is braked right side spragging gear 23, because right side spragging gear 23 engages with right side denticle cogwheel 9, therefore right side denticle cogwheel 9 is also braked, thereby right side crawler belt is braked, thereby vehicle completes large radius right turn.
In the time that crawler belt combined harvester needs minor radius left steering or pivot stud, open the reversal valve of controlling the second hydraulic circuit 34 on the steering controlling shaft of left side, hydraulic oil injects by left side the second hydraulic circuit 34, therefore left side shift fork 25 can first move right, thereby drive left side denticle cogwheel 9 to move right, depart from the large clutch gear 8 in left side, thereby cut off the power input of left track, brake subsequently differential controls axle 31, because output gear 32 links with differential controls axle 31 splines, therefore output gear 31 is braked, again because output gear 32 engages with differential gear 30, therefore differential gear 30 is braked, therefore differential mechanism is also braked, and the power in left side is cut off, therefore the bevel gear on right side cover 11 can drive bevel gear cover 11 reverse rotations in left side, thereby realize large radius left steering or the function of pivot stud.
In the time that crawler belt combined harvester needs minor radius right turn or pivot stud, open the reversal valve of controlling the second hydraulic circuit 34 on right hand steering Control Shaft, hydraulic oil injects by right side the second hydraulic circuit 34, therefore shift fork right side 25 can first be moved to the left, thereby drive right side denticle cogwheel 9 to be moved to the left, depart from the large clutch gear 8 in right side, thereby cut off the power input of right side crawler belt, brake subsequently differential controls axle 31, because output gear 32 links with differential controls axle 31 splines, therefore output gear 31 is braked, again because output gear 32 engages with differential gear 30, therefore differential gear 30 is braked, therefore differential mechanism is also braked, and the power in left side is cut off, therefore the bevel gear in left side cover 11 can drive bevel gear cover 11 reverse rotations on right side, thereby realize minor radius right turn or the function of pivot stud.
About in the time that crawler belt combined harvester need to be kept straight on to when fine setting.Only need respectively to exert pressure in the second hydraulic circuit 34 to the left and right, make left and right sides shift fork 25 or be moved to the left to the right, left and right two denticle cogwheels 9 are thrown off with the large clutch gear 8 in left and right two respectively, cut off the power on one side, can realize fine setting, without loss friction plate.
Above-described specific embodiment; the purpose of this utility model, technical scheme and beneficial effect are further described; institute is understood that; the foregoing is only specific embodiment of the utility model; be not limited to the utility model; all within spirit of the present utility model and principle, any modification of making, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (6)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320867719.6U CN203661633U (en) | 2013-12-27 | 2013-12-27 | Differential mechanism type track combine-harvester gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320867719.6U CN203661633U (en) | 2013-12-27 | 2013-12-27 | Differential mechanism type track combine-harvester gearbox |
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| Publication Number | Publication Date |
|---|---|
| CN203661633U true CN203661633U (en) | 2014-06-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320867719.6U Expired - Lifetime CN203661633U (en) | 2013-12-27 | 2013-12-27 | Differential mechanism type track combine-harvester gearbox |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103703938A (en) * | 2013-12-27 | 2014-04-09 | 江苏大学 | Differential mechanism type track combine-harvester gearbox |
| CN104871739A (en) * | 2015-04-23 | 2015-09-02 | 洛阳理工学院 | Power gearshift transmission assembly used for combine harvester |
| CN105202124A (en) * | 2015-10-22 | 2015-12-30 | 吉首市宗南重工制造有限公司 | Mechanical in-situ steering gearbox |
| CN105864389A (en) * | 2016-06-01 | 2016-08-17 | 浙江柳林农业机械股份有限公司 | Hydraulic brake device for differential mechanism |
| CN106900284A (en) * | 2017-03-29 | 2017-06-30 | 星光农机股份有限公司 | Transmission case |
| CN112524221A (en) * | 2020-11-28 | 2021-03-19 | 黑龙江省农业机械工程科学研究院 | Agricultural machinery walking drive gearbox |
-
2013
- 2013-12-27 CN CN201320867719.6U patent/CN203661633U/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103703938A (en) * | 2013-12-27 | 2014-04-09 | 江苏大学 | Differential mechanism type track combine-harvester gearbox |
| CN103703938B (en) * | 2013-12-27 | 2016-01-27 | 江苏大学 | A kind of differential mechanism type track combine-harvester gearbox |
| CN104871739A (en) * | 2015-04-23 | 2015-09-02 | 洛阳理工学院 | Power gearshift transmission assembly used for combine harvester |
| CN105202124A (en) * | 2015-10-22 | 2015-12-30 | 吉首市宗南重工制造有限公司 | Mechanical in-situ steering gearbox |
| CN105864389A (en) * | 2016-06-01 | 2016-08-17 | 浙江柳林农业机械股份有限公司 | Hydraulic brake device for differential mechanism |
| CN106900284A (en) * | 2017-03-29 | 2017-06-30 | 星光农机股份有限公司 | Transmission case |
| CN112524221A (en) * | 2020-11-28 | 2021-03-19 | 黑龙江省农业机械工程科学研究院 | Agricultural machinery walking drive gearbox |
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