CN211288622U - Auxiliary speed changer of harvester and harvester - Google Patents

Abstract

The utility model discloses a vice derailleur of harvester and harvester belongs to harvesting equipment technical field. The utility model discloses a harvester auxiliary transmission, the first shaft is connected with the second shaft in a transmission way, and a plurality of groups of gear pairs with matched transmission ratios are arranged between the second shaft and the third shaft; in each gear pair, a key groove is formed on a driving gear of each gear pair, a limiting hole is formed in the shaft body of the second shaft at a position corresponding to the key groove, and a ball key is movably arranged on the limiting hole; a sliding sleeve is sleeved on the second shaft, a sliding rod is arranged in the shaft body, and a connecting rod on the sliding sleeve penetrates through the sliding groove to be connected with the sliding rod; the sliding rod slides axially to enable the flange on the sliding rod to prop out the ball keys in different gear pairs, so that the second shaft is in transmission fit with the driving gear key corresponding to the propped-out ball key, and the harvester can be switched without stopping the harvester when in use. The utility model discloses a harvester with above-mentioned auxiliary transmission, its convenient to use reaps efficiency higher.

Description

Auxiliary speed changer of harvester and harvester

Technical Field

The utility model relates to a harvesting equipment technical field, more specifically say, relate to a vice derailleur of harvester and harvester.

Background

The speed changer is an important component of the power transmission of the harvester, the speed change of the existing harvester is divided into a main speed change part and an auxiliary speed change part, the main speed change part generally adopts a hydraulic stepless speed changer (HST), and the auxiliary speed change part is a speed changer. The power is output to the hydraulic stepless speed changer by the engine, then is output to the speed changer by the hydraulic stepless speed changer, and finally is output to the driving wheel by the speed changer, and the driving wheel drives the whole harvester to move forward or backward. In the related art, a transmission is shifted in a manner that a shift fork is used for shifting a shift gear to axially move to realize engagement and disengagement of the shift gear.

For example, the invention provides a Chinese patent document named as a clutch transmission gear shifting fork mechanism (application number 2018215444672), the gear shifting fork mechanism of the application comprises a transmission box body, a locking device, a shifting fork shaft, a shifting fork and a gear lever, an input shaft and an output shaft are arranged in an inner cavity of the transmission box body, the input shaft and the output shaft are provided with gear sets which are meshed up and down, and a reverse gear is sleeved on the input shaft; the shifting fork shaft is positioned at the top of the inner cavity of the transmission box body, a linear bearing is sleeved on the shifting fork shaft, the shifting fork shaft penetrates through the locking device, a shifting fork is fixedly connected to the shifting fork shaft, and a shifting block is fixedly connected to the right end of the shifting fork shaft; the lower end of the gear shift lever is positioned in a gear shift groove of the gear shift shifting block.

However, unlike a common automobile, after the harvester is started, the auxiliary transmission is shifted to a corresponding gear, and an operator controls a control lever of the hydraulic stepless transmission to control the forward or backward movement and the speed of the equipment. When the auxiliary transmission gear needs to be switched, the operating lever of the hydraulic stepless transmission must return to the neutral position, and the auxiliary transmission gear can be switched after the equipment stops moving. At this time, the shift gears of the sub-transmission have phase angle deviation, and the problem that the shift gear cannot be engaged and the shift resistance is large exists, which affects the working efficiency.

SUMMERY OF THE UTILITY MODEL

1. Technical problem to be solved by the utility model

The utility model aims to overcome the auxiliary transmission gear shift of harvester among the prior art and switch not convenient enough, provide a harvester auxiliary transmission. According to the scheme, the sliding rod slides axially to enable the flange to prop out different ball keys, so that the second shaft is in transmission fit with the driving gear key corresponding to the propped-out ball key, the gear switching of the auxiliary speed changer of the harvester can be conveniently realized, and the harvester is convenient to use.

Another object of the utility model is to provide a harvester, its main transmission is hydraulic pressure buncher, and its auxiliary transmission can realize not shutting down keep off the position and switch to convenient in the use of harvester, improve the efficiency of reaping of harvester.

2. Technical scheme

In order to achieve the above purpose, the utility model provides a technical scheme does:

the utility model discloses a pair of harvester derailleur, including primary shaft, secondary shaft, third axle and engage in gear shift fork, the primary shaft is connected with the secondary shaft transmission, be provided with the gear pair that multiunit transmission ratio phase complex between secondary shaft and the third axle, the gear pair includes the driving gear that sets up on the secondary shaft and sets up the driven gear on the third axle, driving gear and driven gear intermeshing; a key groove is formed in the driving gear, a limiting hole is formed in the shaft body of the second shaft at a position corresponding to the key groove, and a ball key is movably arranged on the limiting hole; a sliding sleeve matched with the gear engaging shifting fork is sleeved on the second shaft, a sliding rod is arranged in the shaft body, a flange is arranged on the sliding rod, an axial sliding groove is formed in the shaft body, and a connecting rod on the sliding sleeve penetrates through the sliding groove to be connected with the sliding rod;

the subtransmission is configured to: the sliding rod slides axially to enable the flange to push out different ball keys, so that the second shaft is in transmission fit with the driving gear key corresponding to the pushed ball key.

Further, the middle part of the flange is sunken to form an arc-shaped groove matched with the ball key.

Furthermore, a transition surface is arranged at the joint of the rod body of the sliding rod and the flange, and the transition surface is an arc surface.

Further, the distance from the inner side wall of the shaft body to the rod body is smaller than the radius of the ball key.

Further, the shape of the key slot corresponds to the shape of the ball key, and the height of the key slot is equal to the radius of the ball key.

Furthermore, the gear pair is provided with three groups, and the second shaft is sequentially provided with a first driving gear, a second driving gear and a third driving gear which correspond to the three groups of gear pairs; the distance from the third driving gear to the second driving gear is larger than the distance from the second driving gear to the first driving gear.

Furthermore, a first flange, a second flange and a third flange which are matched with ball keys corresponding to the first driving gear, the second driving gear and the third driving gear are arranged on the slide bar; the distance from the first flange to the second flange is greater than the distance from the first driving gear to the second driving gear and less than the distance from the first driving gear to the third driving gear; the distance from the second flange to the third flange is greater than the distance from the second driving gear to the third driving gear.

Further, the distance from the end of the sliding chute to the third driving gear is equal to the distance from the joint of the connecting rod and the sliding chute to the third flange.

Further, a driving gear is arranged on the first shaft, a transmission gear is arranged on the second shaft, and the driving gear is meshed with the transmission gear.

The utility model discloses a harvester, it realizes the infinitely variable speed in the movement and keeps off the position variable speed by main gear and auxiliary transmission cooperation, main gear is hydraulic pressure buncher, auxiliary transmission is foretell auxiliary transmission.

3. Advantageous effects

Adopt the technical scheme provided by the utility model, compare with prior art, have following beneficial effect:

(1) the utility model discloses a harvester auxiliary transmission, the first shaft is connected with the second shaft in a transmission way, and a plurality of groups of gear pairs with different transmission ratios are arranged between the second shaft and the third shaft; in each gear pair, a key groove is formed on the driving gear, a limiting hole is formed in the shaft body of the second shaft at a position corresponding to the key groove, and a ball key is movably arranged on the limiting hole; a sliding sleeve is sleeved on the second shaft, a sliding rod is arranged in the shaft body, an axial sliding groove is formed in the shaft body, and a connecting rod on the sliding sleeve penetrates through the sliding groove to be connected with the sliding rod; the sliding rod slides axially to enable the flange on the sliding rod to prop out the ball keys in different gear pairs, so that the second shaft is in transmission fit with the driving gear key corresponding to the propped-out ball key, and therefore when the harvester is used, gear switching can be achieved without stopping the harvester, and the harvester is convenient to use.

(2) In the utility model, the middle part of the flange is sunken to form an arc-shaped groove matched with the ball key, the connecting part of the rod body of the slide rod and the flange is provided with a transition surface, the transition surface is an arc surface, the shape of the key groove corresponds to the ball key, and the height of the key groove is equal to the radius of the ball key, so that when the slide rod slides axially, the ball key slides towards the flange from the transition surface and then is clamped into the arc-shaped groove in the middle part of the flange, thereby the ball key is tightly propped in the key groove, and the stability of matching between the second shaft and the driving gear is; the distance from the inner side wall of the shaft body to the rod body is smaller than the radius of the ball key, so that the ball key can be temporarily arranged between the limiting hole and the sliding rod after being separated from the matching with the flange, and the ball key is prevented from being separated from the limiting hole.

(3) The utility model discloses a harvester, it realizes the infinitely variable speed in the movement and keeps off a position the variable speed by main derailleur and auxiliary transmission cooperation, and main derailleur is hydraulic pressure infinitely variable transmission, is provided with in auxiliary transmission's the secondary shaft can the axial slip slide bar, and the ball key of difference is supported out to the flange of slide bar to make secondary shaft and the cooperation of the driving gear key transmission of difference, thereby realize keeping off a position and switch, conveniently in the use of harvester, improve the efficiency of reaping of harvester.

Drawings

FIG. 1 is a schematic structural view of an auxiliary transmission according to the present invention;

FIG. 2 is a schematic structural view of a first shaft of the present invention;

FIG. 3 is a schematic structural view of a driving gear of the present invention;

fig. 4 is a schematic structural view of the second shaft of the present invention;

FIG. 5 is a schematic view of the engagement relationship between the middle flange and the first driving gear according to the present invention;

FIG. 6 is a schematic view of the engagement relationship between the middle flange and the second driving gear according to the present invention;

fig. 7 is a schematic view of the fitting relationship between the middle flange and the third driving gear according to the present invention.

The reference numerals in the schematic drawings illustrate: 1. a first shaft; 2. a second shaft; 3. a third axis; 4. a gear engaging shifting fork; 5. a second bearing; 6. a gear shaft; 7. a first bearing; 8. a collar; 9. a first clamp spring; 10. a second clamp spring; 11. a transmission gear; 12. a first drive gear; 13. a second driving gear; 14. a third driving gear; 15. a sliding sleeve; 16. a shaft body; 17. a slide bar; 18. a ball key; 19. a chute; 20. a keyway.

Detailed Description

For a further understanding of the present invention, reference will be made to the following detailed description taken in conjunction with the accompanying drawings and examples.

The structure, ratio, size and the like shown in the drawings of the present specification are only used for matching with the content disclosed in the specification, so as to be known and read by people familiar with the technology, and are not used for limiting the limit conditions which can be implemented by the present invention, so that the present invention does not have the substantial significance in the technology, and any structure modification, ratio relationship change or size adjustment should still fall within the scope which can be covered by the technical content disclosed by the present invention without affecting the efficacy which can be produced by the present invention and the achievable purpose. In addition, the terms "upper", "lower", "left", "right" and "middle" used in the present specification are for clarity of description, and are not intended to limit the scope of the present invention, and the relative relationship between the terms and the terms is not to be construed as a scope of the present invention.

Referring to fig. 1, the sub-transmission of the harvester of the present embodiment specifically includes a first shaft 1, a second shaft 2, and a third shaft 3. Wherein, the primary shaft 1 is connected with the main transmission of harvester, and the primary shaft 1 is connected with the transmission of secondary shaft 2, and the third shaft 3 is depended on the setting of secondary shaft 2, is provided with the multiunit gear pair between secondary shaft 2 and the third shaft 3, and the drive ratio is different between the multiunit gear pair, realizes the switching that vice derailleur kept off the position through the switching between the multiunit gear pair.

Referring to fig. 2, the first shaft 1 includes a gear shaft 6, and the gear shaft 6 is drivingly connected to an output shaft of the main transmission and transmits power of the main transmission to the sub-transmission. The gear shaft 6 is mounted on a box body of the auxiliary gearbox through a first bearing 7, and the bearing 7 is axially and fixedly connected with the gear shaft 6 through a first clamp spring 9, namely, the first bearing 7 and the gear shaft 6 do not slide axially. Further, a plurality of first bearings 7 may be provided on the first shaft 1, and a collar 8 may be provided between the plurality of first bearings 7 to restrict axial sliding between the first bearings 7 and the gear shaft 6.

The second shaft 2 may be disposed on a casing of the sub-transmission through a second bearing 5, and the second shaft 2 may be disposed with a transmission gear 11. The transmission gear 11 is engaged with a driving gear on the first shaft 1, thereby realizing transmission between the first shaft 1 and the second shaft 2.

Referring to fig. 1, the gear pair includes a driving gear and a driven gear, the driven gear is disposed on the third shaft 3, the driven gear is in keyed connection with the third shaft 3, and the driven gear and the third shaft 3 are fixed to each other, i.e. relative rotation and relative sliding cannot occur. The driving gear is rotatably arranged on the second shaft 2, and meanwhile, a second clamping spring 10 is arranged between the driving gear and the second shaft 2, and the second clamping spring 10 is used for preventing the driving gear and the second shaft 2 from sliding.

Referring to fig. 3, the driving gear is provided with a key slot 20, and the key slot 20 is specifically provided on the inner side wall of the driving gear. A position of the shaft body 16 of the second shaft 2 corresponding to the key groove 20 is provided with a limit hole, and a ball key 18 is movably arranged on the limit hole. The ball key 18 can slide along the retaining hole so that it partially escapes from the retaining hole and snaps into the keyway 20. When the ball key 18 is pressed tightly in the key slot 20 by an external force, the second shaft 2 is in key transmission connection with the driving gear to transmit torque, otherwise, no torque is transmitted between the second shaft 2 and the driving gear. Therefore, when the ball keys 18 in different gear pairs are matched with the corresponding key slots 20, the second shaft 2 is in transmission connection with the driving gear keys of different gear pairs, so that the transmission ratio conversion between the second shaft 2 and the third shaft 3 is realized.

Specifically, a slide bar 17 may be provided in the shaft body 16 of the second shaft 2, and the slide bar 17 may be provided with a flange. When the sliding rod 17 moves along the axial direction, the flange can push out the ball key 18 corresponding to the driving gear of one of the gear pairs, so that the driving gear of the gear pair is in transmission connection with the second shaft key.

As a further refinement of this embodiment, the middle of the flange may be recessed, forming an arcuate slot that mates with the ball key 18. After the ball key 18 is pushed out by the flange, one side of the ball key 18 is tightly propped in the key groove 20, and the other side of the ball key 18 is tightly propped in the arc-shaped groove, so that the ball key 18 can be fixed between the flange and the key groove 20, and the stability of key transmission connection between the second shaft 2 and the driving gear is improved. In addition, the arc-shaped groove has a limiting function, and the flange of the sliding rod 17 is prevented from being disengaged from the ball key 18 in the movement process of the harvester.

Furthermore, a transition surface is arranged at the joint of the rod body of the sliding rod 17 and the flange, and the transition surface is specifically an arc surface. Therefore, when the sliding rod 17 slides relative to the shaft body 16, the ball key 18 can gradually enter the arc-shaped groove of the flange through the transition surface, and the flange and the ball key 18 are prevented from being hard pressed and damaged.

In addition, the distance from the inner side wall of the shaft body 16 to the rod body can be smaller than the radius of the ball key 18, so that the ball key 18 is prevented from completely falling out of the shaft body 16 from the limiting hole or completely entering the shaft body 16 from the limiting hole; meanwhile, the distance from the inner side wall of the shaft body 16 to the rod body can be smaller than the radius of the ball key 18, when the ball key 18 slides, the outer wall of the ball key 18 can be always in contact with the hole wall of the limiting hole, and therefore the limiting hole can provide the axial limiting effect for the ball key 18.

The shape of the key groove 20 corresponds to the ball key 18, and the height of the key groove 20 is equal to the radius of the ball key 18. Specifically, the keyway can be the first semi-cylinder structure, and the radius of this semi-cylinder mechanism can equal with the radius of ball key 18, and when ball key 18 was offset by the flange, in the keyway 20 was gone into to ball key 18 card for keyway 20 is under the prerequisite that does not hinder the motion of ball key 18, maximize the area of contact of keyway 20 cell body and ball key 18, thereby further improve the stability that the key drive of secondary shaft 2 and driving gear is connected, and then more be favorable to the transmission of moment.

In order to realize the axial sliding of the sliding rod 17 relative to the second shaft 2, a sliding sleeve 15 can be arranged on the second shaft 2, the sliding sleeve 15 can slide relative to the shaft body 16 and is connected with the gear shift fork 4; meanwhile, an axial sliding groove 19 is formed in the shaft body 16, and a connecting piece is arranged on the sliding sleeve 15 and penetrates through the sliding groove 19 to be connected with the sliding rod 17, so that a user can drive the sliding sleeve 15 to slide relative to the shaft body 16 through the gear engaging shifting fork 4, and further drive the sliding rod 17 to slide relative to the shaft body 16, and flanges on the sliding rod 17 are matched with different ball keys 18.

As an embodiment, the gear sets may be specifically arranged in three sets. Specifically, referring to fig. 4, the second shaft 2 is sequentially provided with a first driving gear 12, a second driving gear 13 and a third driving gear 14 corresponding to three gear pairs, and a distance from the third driving gear 14 to the second driving gear 13 is greater than a distance from the second driving gear 13 to the first driving gear 12. The shaft body 16 is provided with a limiting groove at a position corresponding to the keyways 20 of the first driving gear 12, the second driving gear 13 and the third driving gear 14, and a ball key 18 capable of being matched with the keyways 20 of the first driving gear 12, the second driving gear 13 and the third driving gear 14 is slidably arranged in the limiting groove. The sliding bar 17 is provided with three flanges which are capable of engaging with ball keys 18 which are engaged with keyways 20 of the first driving gear 12, the second driving gear 13 and the third driving gear 14, respectively.

More specifically, the distance from the first flange to the second flange is greater than the distance from the first driving gear 12 to the second driving gear 13, and is less than the distance from the first driving gear 12 to the third driving gear 14; the distance from the second flange to the third flange is greater than the distance from the second drive gear 13 to the third drive gear 14. It should be noted that the distance between the flanges refers to the distance between the centers of the flanges, and the distance between the gears refers to the distance between the centers of the gears.

Referring to fig. 4, when the slide bar 17 slides from the initial position to the right in the figure, the first flange of the slide bar 17 comes into contact with the ball key 18 corresponding to the first driving gear 12; referring to fig. 5, the first flange pushes the ball key 18 out relative to the shaft body 16 to push the ball key 18 against the key slot 20 of the first driving gear 12, and the second flange and the third flange are not matched with the ball key 18, so that the second shaft 2 is only in key transmission connection with the first driving gear 12, and the auxiliary transmission is in the first gear; referring to fig. 6, the slide bar 17 continues to move rightward, the first flange is separated from contact with the ball key 18 corresponding to the first driving gear 12, the second flange is brought into contact with the ball key 18 corresponding to the second driving gear 13, the ball key 18 is pushed out relative to the shaft body 16 to press the ball key 18 against the key slot 20 of the second driving gear 13, the first flange and the third flange are not matched with the ball key 18, so that the second shaft 2 is in keyed connection with the second driving gear 13 only, and the auxiliary transmission is in the second gear; referring to fig. 7, the slide bar 17 continues to move rightward, the second flange is separated from the ball key 18 corresponding to the second driving gear 13, the third flange is brought into contact with the ball key 18 corresponding to the third driving gear 14, the ball key 18 is pushed out relative to the shaft body 16 to press the ball key 18 against the key slot 20 of the third driving gear 14, the first flange and the third flange are not matched with the ball key 18, so that the second shaft 2 is in keyed connection with the third driving gear 14 only, and the range gearbox is in a third gear.

It should be noted that, since the driving gears and the driven gears of the three gear pairs on the second shaft 2 and the third shaft 3 are meshed with each other, during the transmission, the driving gear which is not chain-driven connected with the second shaft 2 can also synchronously rotate with the second shaft 2 due to the action of the driven gear meshed with the driving gear; due to the functions of the sliding groove and the connecting piece, the sliding sleeve, the sliding rod and the second shaft 2 also synchronously rotate, namely the first driving gear 12, the second driving gear 13, the third driving gear 14, the sliding sleeve 15, the sliding rod 17 and the ball key 18 synchronously rotate and are relatively static, so that gear switching of the auxiliary gearbox in the non-stop state is more convenient.

In order to limit the sliding range of the sliding rod 17, the distance from the end of the sliding slot 19 to the third driving gear 14 may be equal to the distance from the connection point of the connecting rod and the sliding rod 17 to the third flange, so that when the third flange pushes out the ball key 18 corresponding to the third driving gear 14, the connection between the sliding rod 17 and the sliding sleeve 15 is pushed against the end of the sliding slot 19, thereby limiting the maximum sliding distance of the sliding rod 17 relative to the shaft 16.

The embodiment also provides a harvester. The harvester of the embodiment is provided with a speed change mechanism between an engine and a driving wheel, and the speed change mechanism is composed of a main transmission and an auxiliary transmission. The main transmission can be a hydraulic stepless transmission, which can be a hydraulic stepless transmission commonly used in the related field, and the specific structure and the using method can be implemented according to the content disclosed in the related field or the mode suggested by manufacturers, so the related content is not described in detail in the embodiment. A sliding rod capable of axially sliding is arranged in a second shaft of the auxiliary transmission, and different ball keys are pushed out by flanges of the sliding rod, so that the second shaft is in transmission fit with different driving gear keys, and gear switching is achieved.

Therefore, the harvester of the embodiment can control the sliding of the sliding rod through the gear shifting fork to enable the second shaft to be in transmission connection with the driving gear keys of different gear pairs under the condition of no shutdown in the running process, so that the switching of units is realized, the resistance in the switching process is small, and the harvesting efficiency of the harvester can be effectively improved.

The present invention and its embodiments have been described above schematically, and the description is not limited thereto, and what is shown in the drawings is only one of the embodiments of the present invention, and the actual structure is not limited thereto. Therefore, if the person skilled in the art receives the teaching of the present invention, without departing from the inventive spirit of the present invention, the person skilled in the art should also design the similar structural modes and embodiments without creativity to the technical solution, and all shall fall within the protection scope of the present invention.

Claims (10)

1. A harvester auxiliary speed changer is characterized in that: the gear comprises a first shaft (1), a second shaft (2), a third shaft (3) and a gear engaging shifting fork (4), wherein the first shaft (1) is in transmission connection with the second shaft (2), a plurality of groups of gear pairs matched in transmission ratio are arranged between the second shaft (2) and the third shaft (3), each gear pair comprises a driving gear arranged on the second shaft (2) and a driven gear arranged on the third shaft (3), and the driving gear is meshed with the driven gear; a key groove (20) is formed in the driving gear, a limiting hole is formed in the position, corresponding to the key groove (20), of the shaft body (16) of the second shaft (2), and a ball key (18) is movably arranged on the limiting hole; a sliding sleeve (15) matched with the gear engaging shifting fork (4) is sleeved on the second shaft (2), a sliding rod (17) is arranged in the shaft body (16), a flange is arranged on the sliding rod (17), an axial sliding groove (19) is formed in the shaft body (16), and a connecting rod on the sliding sleeve (15) penetrates through the sliding groove (19) to be connected with the sliding rod (17);

the subtransmission is configured to: the sliding rod (17) slides axially to enable the flange to push out different ball keys (18), so that the second shaft (2) is in transmission fit with driving gear keys corresponding to the pushed ball keys (18).

2. The auxiliary harvester transmission as in claim 1, wherein: the middle part of the flange is sunken to form an arc-shaped groove matched with the ball key (18).

3. The auxiliary harvester transmission as in claim 2, wherein: and a transition surface is arranged at the joint of the rod body of the sliding rod (17) and the flange, and the transition surface is an arc surface.

4. The auxiliary harvester transmission as in claim 3, wherein: the distance from the inner side wall of the shaft body (16) to the shaft body is smaller than the radius of the ball key (18).

5. The auxiliary harvester transmission as in claim 4, wherein: the shape of the key groove (20) corresponds to the shape of the ball key (18), and the height of the key groove (20) is equal to the radius of the ball key (18).

6. The auxiliary harvester transmission as claimed in any one of claims 1 to 5, wherein: the gear pair is provided with three groups, and the second shaft (2) is sequentially provided with a first driving gear (12), a second driving gear (13) and a third driving gear (14) which correspond to the three groups of gear pairs; the distance from the third driving gear (14) to the second driving gear (13) is larger than the distance from the second driving gear (13) to the first driving gear (12).

7. The auxiliary harvester transmission as in claim 6, wherein: the sliding rod (17) is provided with a first flange, a second flange and a third flange which are matched with ball keys (18) corresponding to the first driving gear (12), the second driving gear (13) and the third driving gear (14); the distance from the first flange to the second flange is greater than the distance from the first driving gear (12) to the second driving gear (13) and less than the distance from the first driving gear (12) to the third driving gear (14); the distance from the second flange to the third flange is larger than the distance from the second driving gear (13) to the third driving gear (14).

8. The auxiliary harvester transmission as in claim 6, wherein: the distance from the tail end of the sliding groove (19) to the third driving gear (14) is equal to the distance from the joint of the connecting rod and the sliding rod (17) to the third flange.

9. The auxiliary harvester transmission as in claim 1, wherein: the driving gear is arranged on the first shaft (1), the transmission gear (11) is arranged on the second shaft (2), and the driving gear is meshed with the transmission gear (11).

10. A harvester, characterized by: the main transmission is a hydraulic stepless transmission, and the auxiliary transmission is the auxiliary transmission according to any one of claims 1-9.

Images