JPH0717879Y2 - Forward / reverse continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a forward / reverse continuously variable transmission that can be used in a transmission such as a combine. The present invention relates to a forward / reverse continuously variable transmission in which the variable speed input shaft support and the constant speed input shaft are connected by a planetary gear mechanism.

[Prior art]

As a forward / reverse continuously variable transmission having a planetary gear mechanism of this type, for example, JP-A-57-51050 has been proposed. This forward / reverse continuously variable transmission is provided with an intermediate shaft in parallel with an input shaft via a pulley type continuously variable transmission mechanism, an intermediate gear is fixed to the intermediate shaft, and a sun gear is fixed to the input shaft. An external gear provided on an outer peripheral surface of the sun gear and an external gear provided on an outer peripheral surface of the planetary gear that meshes with the intermediate gear and the internal gear and the sun gear. The carrier provided with is loosely fitted to the input shaft,
The output shaft, to which the output gear that meshes with the external gear of the carrier is fixed, is provided in parallel with the input shaft.

[Problems to be solved by the invention]

However, in the above-described conventional device, the input shaft having the sun gear and the output shaft having the carrier are separately arranged in parallel at different positions, so that the arrangement of each shaft becomes very complicated, and There is a drawback in that the planetary gear mechanism that connects these shafts is also complicated.

Therefore, the present invention was devised in view of the above-mentioned conventional circumstances to solve the problem, and connects a shift input shaft and a constant speed input shaft arranged on the same shaft core by a planetary gear mechanism,
The object of the present invention is to provide a forward / reverse continuously variable transmission that can have a simple structure.

[Means for solving problems]

Means for Solving the Problems The present invention that achieves the above object provides a gearshift input shaft that is rotatably supported on one side of a mission case and is provided with forward rotation, and a reverse input rotation that is rotatably supported on the other side of the mission case. The constant speed input shaft and the fixed speed input shaft are arranged on the same axis, and the opposite ends thereof are fitted in a concavo-convex shape so that the input shafts are rotatable, Each input shaft is provided with each pulley for inputting power respectively, both input shafts are connected by a planetary gear mechanism capable of forward and reverse rotation, and output from the gears of the planetary gear mechanism. It is a thing.

[Action]

The present invention is configured as described above, and the transmission input shaft and the constant speed input shaft are provided on the same shaft core, and both input shafts are connected through the planetary gear mechanism, and the gears of the planetary gear mechanism are connected to each other. Since the output is adopted, the arrangement of the respective axes and the connecting structure can be facilitated, and the structure of the device can be made extremely simple.

Also, because the pulleys that transmit power to both input shafts are provided outside the mission case, maintenance and inspection of the transmission mechanism that has pulleys can be performed easily. Since the weatherproof end of the high speed input shaft is fitted so that the mutual input shafts are rotatable,
The equipment installed in the mission case can be made compact, and both fitted input shafts are supported by the mission case. And can be firmly supported in the mission case.

〔Example〕

Hereinafter, the drawings showing the present invention as an embodiment will be described.

In FIG. 1, an engine pulley 2 of an engine 1 mounted on the machine body and an intermediate input pulley 5 fixed to an intermediate input shaft support 4 rotatably supported by an intermediate transmission case 3 fixed to the machine body are provided with a V belt. An intermediate shaft 7, an intermediate first output shaft 8 and an intermediate second output shaft 9 are rotatably supported on the intermediate transmission case 3 respectively. The large-diameter gear 7a fixed to the intermediate shaft 7 is meshed with the small-diameter gear 4a fixed to the intermediate input shaft 4 and the small-diameter gear 11 fixed to the intermediate first output shaft 8, and at the same time, the small-diameter gear 11 is engaged. By engaging the reverse rotation gear 12 fixed to the intermediate second output shaft 9, the intermediate first output shaft 8 and the intermediate second output shaft 9 are separated from each other when the intermediate first output shaft 8 rotates in the forward and reverse directions. The two output shafts 9 are configured as an intermediate output shaft 10 that rotates in the reverse direction.

The intermediate first output shaft 8 is projected to the right side of the intermediate transmission case 3, one intermediate second output shaft 9 is projected to the left side of the intermediate transmission case 3, and at the shaft end of the intermediate second output shaft 9. The constant speed output pulley 13 is fixed. On the other hand, at the shaft end of the intermediate first output shaft 8, an output side speed change pulley 15 composed of a fixed side pulley 15a and a moving side pulley 15b configured to be expandable / contractible along a shaft center direction of the shaft 8 by a split cam 14. Is provided. The split cam 14 is composed of a fixed split cam 14a and a movable split cam 14b, and an interlocking arm 16 is integrally protruded from the movable split cam 14b.

Further, a mission case 17 which is interlockingly connected to the intermediate transmission case 3 is fixed to the machine body. The mission case 17 is rotatably supported on one side of the mission case 17 and is provided with a forward rotation input. The shaft 19 and the constant speed input shaft 20 rotatably supported on the other side and to which reverse rotation is applied are arranged on the same shaft core, and their opposite ends are mutually input shafts 19, It has a configuration in which 20 is fitted in an uneven shape so as to be rotatable. A constant speed input pulley 21 fixed to the shaft end of a constant speed input shaft 20 projecting to the left outside the case 17,
By winding the V belt 22 around the constant speed output pulley 13, a belt type constant speed transmission mechanism 23 located on the right side of the intermediate transmission case 3 and the transmission case 17 is formed.

On the transmission input shaft 19 that protrudes to the right outside the mission case 17, the split cam from the inside that approaches the case 17
29, the clutch arm 24 that constitutes one of the split cams,
This is a multi-plate clutch that is intermittently operated by this clutch cam 24.
25, the input side speed change pulley 26 on the outside of this multi-plate clutch 25
Are provided in that order. This input side speed change pulley 26
Is composed of a fixed side pulley 26a and a moving side pulley 26b, but idles on the shaft 19 in the cut state of the clutch 25,
The input side speed change pulley 26 and the output side speed change pulley 15 are configured so as to rotate integrally with the shaft 19 in the closed state.
A V-belt 27 is wound between the
26b is always urged toward the fixed pulley 26a side by the spring 18, so that the intermediate transmission case 3 and the transmission case
A belt-type continuously variable transmission mechanism 28 located on the right side of 17 is configured.

A ring gear 30 having internal teeth is fixed to the speed change input shaft 19 in the case 17, and a plurality of planet gears 31 meshing with the internal teeth of the ring gear 30 are provided on the constant speed input shaft 20 so as to freely rotate. Carrier 32a integrally formed with the specified carrier gear 32
The planetary gear 31 is rotatably supported on the side, and the sun gear 33 fixed to the constant speed input shaft 20 located at the center of the planet gear 31 engages the fixed speed input shaft 20. They are connected by a planetary gear mechanism 35 capable of forward and reverse rotation.

The carrier gear 32 is meshed with a transmission gear 37 fixed on the left side of the sub-transmission shaft 36, and an idle gear 39 rotatably provided on the transmission gear 37 is meshed with a transmission gear 41 fixed on the brake shaft 40. There is. A free-wheel gear 43, which is provided on the right side of the sub-transmission shaft 36 so as to freely rotate, is meshed with a transmission gear 44 fixed to the brake shaft 40.
45 is selectively meshed with the idle gear 39 or the idle gear 43 by a shift fork (not shown) so that the brake shaft 40 can be changed in height. This shift fork is shown in FIGS. As shown in the figure, the auxiliary transmission lever 96 is moved in the guide groove 96a provided outside the main constant speed lever 84, centering around the neutral position N, to the upper high speed position H and the lower constant speed position L. Can be switched in conjunction with.

Further, the expandable brake 46 fixed to the right shaft end of the brake shaft 40 is adapted to brake the brake shaft 40 in conjunction with the rotation of the brake arm 47 at a fixed angle. It is interlockingly connected to the Petal 87 shown in the figure. The clutch arm 24 on the speed change input shaft 19 and the interlocking arm 16 on the intermediate first output shaft 9 are interlocked by an interlocking mechanism 85 described later.

The gear 49 integrally formed at the center of the brake shaft 40 is meshed with the center gear 51 fixed to the side clutch shaft 50.On both sides of the side clutch shaft 50, the right clutch gear 52 and the left clutch gear 53 are always provided. Center gear
The springs 54 are urged to the side of the dog 51 so that the dog is engaged, that is, the clutch is engaged.

The clutch gears 52, 53 come out of the center gear 51 against the spring 54 by a shift fork (not shown), and the clutch is cut off.
Transmission gears 56 and 57 on the brake shaft 55 are meshed with 53, respectively, and a small-diameter gear that fixes the transmission gears 56 and 57, respectively.
59 and 60 are rotatably supported on the brake shaft 55. The small-diameter gears 59 and 60 are a pair of left and right axles 61 and 62.
The gears are meshed with the final gears 63 and 64 which are fixed to the respective gears.

Therefore, when both clutch gears 52 and 53 are engaged, the clutch gears 52 and 53 drive the final gears 63 and 64 via the small-diameter gears 59 and 60 on the brake shaft 55, so that the left and right axle shafts are driven. 61 and 62 are driven at the same time, but when the clutch gear 52 or 53 is in the de-clutched state, the clutch gear 52 or 53 idles and the small-diameter gear 59 or 60 on the brake shaft 55 is not driven. The nut side axle 61 or 62 is not driven, and the aircraft turns to the right or left.

The inner shaft ends of the above-described axles 61 and 62 are connected and fixed by a differential mechanism 65 (hereinafter referred to as a differential mechanism), and the ring gear 66 that constitutes the differential mechanism 65 is
It is meshed with a drive gear 67 formed integrally with the brake shaft 55,
A multi-plate type brake 69 is provided on the shaft end of the brake shaft 55 protruding from the case 17, and the brake 69 has a pressing cylinder 71 provided inside the brake case 70 integrated with an arm 72 for a hydraulic expansion / contraction mechanism (not shown). The brake 69 is configured to be pressed by rotating a predetermined angle in conjunction with the operation of. At the outer shaft ends of the axles 61 and 62, a drive sprocket that drives a crawler (not shown) that drives the machine body.
73 are fixed respectively.

As shown in FIG. 2, an interlocking mechanism 85 is provided between the clutch arm 24 constituting one of the split cams on the speed change input shaft 19 side and the interlocking arm 16 having the split cam 14b on the intermediate first output shaft 8 side.
The interlocking mechanism 85 is configured as follows. That is, the other end of the connecting rod 75, one end of which is pivotally connected to the clutch arm 24, is extended longer than above the intermediate first output shaft 8 side and is rotatable about the fulcrum shaft 76. It is pivotally connected to the lower link 77a of the L-shaped link 77. A hydraulic expansion / contraction mechanism 80 including a double-acting hydraulic cylinder 79 and a hydraulic piston 81 is provided, and the upper link 77b of the L-shaped link 77 described above is
It is pivotally connected to the tip of the hydraulic piston 81 via a connecting pin 81a. Also, the hydraulic piston 8 is connected by the connecting pin 81a.
The other end of the connecting rod 82 coaxially connected to the tip of the shaft 1 is pivotally connected to the clutch arm 16 on the intermediate output shaft 8 side.

As shown in FIGS. 2 to 4, the hydraulic cylinder 79 is pivotally connected to the shift input shaft 19 side by a connecting pin 79a, and the neutral N state, the forward F state, and the reverse R state by switching a switching flight (not shown). The switching valve, which is configured to operate in each state, is provided near the driver's seat 83 behind the operation panel P as shown in FIGS. 5 and 8 so as to switch the oil passage to the hydraulic cylinder 79. The main gear shift lever 84 is switched in association with the operation of the main gear shift lever 84. The main gear shift lever 84 has a forward groove 84a and a backward groove 84b provided in the vertical direction as shown in FIG.
It is provided so as to move in a guide groove formed of a neutral groove 84c that connects these both grooves in the horizontal direction.

Therefore, when the hydraulic expansion / contraction mechanism 80 is moved to the neutral N state shown in FIG. 3 by the switching valve operated by operating the main speed change lever 84, the split width of the output side speed change pulley 15 becomes substantially in the middle,
Along with this, the split width of the input side speed change pulley 25 is also approximately in the middle, so the speed change input shaft 19 is driven at an intermediate speed. By setting this intermediate rotation speed to a position where the rotation speed of the axles 61, 62, that is, the rotation speed of the carrier gear 32 constituting the planetary gear mechanism 35 becomes 0 near the vehicle speed 0, the intermediate N speed is moved. Lower link of L-shaped link 77 by hydraulic expansion mechanism 80
Since the clutch arm 24 is moved to the cut position of the clutch 25 and the input side speed change pulley 26 is not driven by connecting the 77a and the connecting rod 75 to each other at a substantially right angle, the clutch 25 is cut as shown in FIG. By setting the position, the number of rotations of the carrier gear 32, that is, the neutral zone range near the vehicle speed 0 can be widened.

Thus, the number of rotations of the carrier gear 32 is 0, that is, the vehicle speed is 0.
Since the range of the neutral zone in the vicinity can be widened, even if the neutral zone in which the carrier rotational speed is 0 is set as in the Japanese Laid-Open Patent Publication No. 57-51050 mentioned at the beginning, the carrier rotational speed is as shown in FIG. Since the range of 0 points is 1 point, it is possible to solve the drawback that it is very difficult to set the vehicle speed to 0 in the neutral zone.

From the neutral N state shown in FIG. 3 to the operation of the main shift lever 84 to reduce the hydraulic expansion / contraction mechanism 80 to the forward F state shown in FIG. 2, the interlocking arm 16 rotates clockwise to shift to the output side shift. Since the split width of the pulley 15 gradually becomes maximum and the split width of the input side speed change pulley 26 also gradually becomes minimum accordingly, the speed change input shaft 19 is gradually shifted in the direction in which the rotational speed becomes slower, and the state shown in FIG. Then, the gear is driven at the minimum speed. On the other hand, when the clutch arm 24 slightly exceeds the position shown in FIG. 3, it rotates counterclockwise and holds the clutch 25 in the inserted state.

Further, while the main transmission lever 84 is operated from the neutral N state shown in FIG. 3 to extend the hydraulic expansion / contraction mechanism 80 to the reverse R state shown in FIG. 4, the split width of the output side transmission pulley 15 becomes gradually narrower. As a result, the split width of the input side speed change pulley 26 gradually increases, so that the speed change input shaft 19 is changed in the direction in which the rotation speed gradually increases, and in the state shown in FIG. . On the other hand, when the clutch arm 24 slightly exceeds the position shown in FIG. 3, it rotates counterclockwise and holds the clutch 25 in the inserted state.

Further, the relays amount of the split cam 29 shown in FIGS. 2 to 4 is set to a = c <b.

In the previous example, an example in which the sun gear 33 of the planetary gear mechanism 35 is fixed to the constant speed input shaft 20 side has been shown, but since both input shafts 19 and 20 are provided relatively rotatably on the same shaft core, the planetary gear mechanism 35
As shown in FIG. 7, the sun gear 33 constituting the
Fixed to the sun gear 33, the carrier 32a that supports the planet gear 31 that meshes with the sun gear 33 is rotatably provided on the speed change input shaft 19, and the ring gear 30 side that meshes with the planet gear 31 is fixed to the constant speed input shaft 20. It's also easy to do. Thus, even if the sun gear 33 is provided on either the speed change input shaft 19 or the constant speed input shaft 20, it is possible to output from the carrier 32a located on both input shafts 19 or 20 arranged on the same shaft core. In the case of FIG. 7, there is a transmission gear 37 on the auxiliary transmission shaft 36,
The idle gear 43 may be left and right interchanged with the case of the previous example.

[Effect of device]

As described above, according to the present invention, the gear shift input shaft rotatably supported on one side of the mission case is provided with normal rotation, and the reverse input rotation is rotatably supported on the other side of the mission case. The constant speed input shaft and the constant speed input shaft are arranged on the same axis, and the opposite ends thereof are fitted in a concavo-convex shape so that the input shafts can rotate freely. Since each input shaft is provided with each pulley for inputting power respectively, and the both input shafts are connected by a planetary gear mechanism capable of forward and reverse rotations and output from the gears of the planetary gear mechanism, the following excellent features are provided. It has a great effect.

That is, the speed-change input shaft and the constant-speed input shaft are arranged on the same axis, both input shafts are connected through the planetary gear mechanism, and the gears of the planetary gear mechanism are used for output. The structure of the device can be made extremely simple without complicating the arrangement and connection structure of the.

In addition, the pulleys that respectively transmit power to both input shafts are provided outside the mission case, so maintenance and inspection of the transmission mechanism is easy, and the end portions of the transmission input shaft and the constant speed input shaft that face each other are easy to maintain. By fitting the input shafts so that their input shafts are rotatable, the device disposed in the mission case can be made compact, and both the input shafts that are fitted are supported by the mission case. Therefore, similarly to the both-side support, the shift input shaft and the constant speed input shaft can be firmly supported on the mission case.

Further, since the ends of the speed-change input shaft and the constant-speed input shaft are rotatably fitted to each other in a concavo-convex shape, a rotation supporting member such as a bearing is not required, and the number of parts can be reduced.

[Brief description of drawings]

FIG. 1 shows an embodiment of the present invention, FIG. 1 is a plan development view of a power transmission device in a combine, FIG. 2 is an operation explanatory view showing a forward state of a continuously variable transmission mechanism, and FIG. 3 is a continuously variable transmission mechanism. 4 is a side view of the continuously variable transmission mechanism, FIG. 6 is a side view of the continuously variable transmission mechanism, and FIG. 6 is a carrier rotation speed and pulley split width. FIG. 7 is a partial plan development view of a power transmission device showing an example in which a carrier of a planetary gear mechanism is arranged on a shift input, FIG. 8 is a perspective view of an operation panel provided in a combine, and FIG. FIG. 6 is a plan view showing guide grooves of a main shift lever and a sub shift lever. FIG. 10 is a relationship diagram between the carrier rotation speed and the pulley split width in the conventional example. 1 ... Engine, 8 ... Intermediate first output shaft, 9 ... Intermediate second output shaft, 10 ... Intermediate output shaft, 14 ... Split cam, 16 ...
Interlocking arm, 17 …… Mission case, 19 …… Variable speed input shaft, 20 …… Constant speed input shaft, 21 …… Constant speed input pulley, 23 ……
Constant speed transmission mechanism, 24 …… clutch arm, 25 …… clutch, 26 …… input side speed change pulley, 28 …… continuously variable speed change mechanism, 29
...... Split cam, 30 ...... Ring gear, 31 ...... Planetary gear, 32
...... Carrier gear, 33 ...... Sun gear, 35 ...... Planetary gear mechanism, 75 ...... Connection rod, 77 ...... L-shaped link, 80 ...... Hydraulic expansion mechanism, 82 ...... Connection rod, 84 ...... Main transmission lever ,
85 ... interlocking mechanism.

Claims (1)

[Scope of utility model registration request] 1. A transmission input shaft that is rotatably supported on one side of a mission case and is provided with forward rotation, and a constant speed that is rotatably supported on the other side of the mission case and is provided with reverse rotation. While arranging the input shaft on the same axis,
The opposite ends are fitted in a concavo-convex shape so that the input shafts are rotatable, and pulleys for inputting power to the input shafts outside the mission case are provided. A forward / reverse continuously variable transmission having a structure in which the gears of the planetary gear mechanism are connected to each other by a planetary gear mechanism capable of forward and reverse rotation.