JP4896321B2 - Continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a structure of a belt pulley type continuously variable transmission for continuously changing output from a prime mover.
[0002]
[Prior art]
Conventionally, as a belt pulley type continuously variable transmission for shifting the power of an engine (prime mover) and transmitting it to a drive wheel or various working parts (PTO shaft) in a farm work machine or the like, for example, Japanese Patent Laid-Open No. 5-49852 In the publication, a driven side movable pulley comprising a movable sheave that moves to and away from a fixed sheave fixed to the drive shaft, and a driven sheave that includes a movable sheave that moves to and away from a fixed sheave fixed to the driven shaft. A continuously variable transmission constructed by winding a belt around a movable pulley and shifting the movement direction of the movable sheave in the driving pulley and the movement direction of the movable sheave in the driven pulley opposite to each other. In the apparatus, each pulley has a movable sheave approaching and separating from the fixed sheave to change the pulley diameter of the pulley (the effective radius of the belt with respect to the pulley). By connecting the movable sheaves in both pulleys with one connecting rod and rotating the both movable sheaves in the same direction with an operation lever that moves one movable sheave, A configuration in which the speed is changed continuously is disclosed.
[0003]
In this configuration, the movable cams of the two cam mechanisms are interlocked and connected to each other by a single connecting rod, so that each of the movable pulleys of the drive and driven pulleys can be moved at the time of shifting between the rotary shafts of the drive shaft and the driven shaft. The sheaves open and close (broad and narrow) in synchronization with each other in the opposite direction, the opening and closing force between the two pulleys is reversed, and the opening and closing forces between both pulleys partially cancel each other, reducing the speed change operation between the two rotating shafts. It could be done with operating force.
[0004]
[Problems to be solved by the invention]
By the way, in the prior art, as described in the publication, the initial tension acting on the belt is generally divided into the tension side and the slack side tension by the rotational torque input to the driving pulley, and both these tensions are applied. Due to this difference, power is transmitted from the driving pulley to the driven pulley. The thrust generated by each pulley (the force that the pulley pushes the belt) is substantially the same in a static state where the pulley does not rotate or in a rotating state where the transmission load is small, but when the transmission load increases, the belt Due to the change in tension distribution, the thrust of the driving pulley always becomes greater than the thrust of the driven pulley, and there is a difference between the two thrusts, and it is necessary to perform a speed change operation with an operating force larger than the difference between the two thrusts.
[0005]
When the cam means (movable cam) of the driving pulley and the cam means (movable cam) of the driven pulley are moved in the opposite directions with one operating portion for shifting operation, Forces opposite to each other act on the rod and the driven-side operation rod. In that case, if the amount of movement of the movable sheave with respect to the fixed sheave in the driving pulley is equal to the amount of movement of the movable sheave with respect to the fixed sheave in the driven pulley, the speed is changed from the low speed state to the high speed state. When the movable sheave in the driving pulley is to open against the driving force of the belt (the thrust of the driving pulley) is larger than the thrust of the driven pulley, it acts on the driving rod. The tensile force becomes larger than the force that the driven side operating rod is pushed. Therefore, there is a problem that the resistance force acting on the one operation portion is different between a speed change operation from a low speed to a high speed and a speed change operation from a high speed to a low speed.
[0006]
Then, as in the prior art, when the cam mechanism of both pulleys is rotated by the same angle around the rotation axis through one connecting rod for shifting, the cam mechanism in the drive side pulley and the driven side pulley Combined with having the same size and shape, there has been a problem that the operating force when shifting from the low speed side to the high speed side becomes large and difficult to operate.
[0007]
Such a problem arises when the cam mechanisms of both movable sheaves are replaced by a single connecting rod, and separate operating mechanisms are used, and both operating mechanisms are operated by one operating unit to perform a shifting operation. Is the same. In order to solve such a problem, it is conceivable to reduce the operating force by using a so-called torque cam, but there is a problem that the number of parts increases and the cost also increases.
[0008]
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a belt pulley type continuously variable transmission capable of extremely reducing the operating force.
[0009]
[Means for Solving the Problems]
In order to solve this technical problem, the continuously variable transmission according to the first aspect of the present invention includes a drive pulley including a movable sheave that moves toward and away from a fixed sheave fixed to the drive shaft, and is fixed to the driven shaft. A belt is wound around a driven pulley comprising a movable sheave that moves far and away with respect to the fixed sheave, and the movement direction of the movable sheave in the driving pulley and the movement direction of the movable sheave in the driven pulley are mutually In the continuously variable transmission configured to be reversely operated and shifted, an operating mechanism for moving the movable sheave in the driving pulley and an operating mechanism for moving the movable sheave in the driven pulley are provided as one operating unit. The amount of movement of the movable sheave with respect to the fixed sheave in the driving pulley is set to be movable with respect to the fixed sheave in the driven pulley. Set to be smaller than the amount of movement over blanking the two actuating mechanism consists cam means provided on the movable sheave, rotatably movable cam in contact with the fixed cam of the cam means about the axis of rotation of the pulleys The arm length of the operating arm for rotating the movable cams is set so that the driving pulley is longer than the driven pulley .
[0010]
[0011]
[0012]
[0013]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EXEMPLARY EMBODIMENTS Embodiments of the invention will be described below with reference to the drawings.
[0014]
1 is a side view of a rice transplanter as an agricultural working machine to which the present invention is applied, FIG. 2 is a plan view, FIG. 3 is a perspective view of an engine, a transmission case, and a belt pulley type continuously variable transmission according to the present invention, FIG. Is a perspective view of the vehicle body frame, FIG. 5 is a plan view showing the continuously variable transmission and its operation unit, FIG. 6 is a side view of the continuously variable transmission, FIG. 7 is a cross-sectional view, and FIG. FIG. 9 is a plan view of the driven pulley, FIG. 10 is a side view for explaining the speed change operation, FIG. 11 is a side view of the operation part of the continuously variable transmission, and FIG. 12 is a perspective view of the operation part of the continuously variable transmission. It is.
[0015]
The rice transplanter in the present invention is a four-row type riding type rice transplanter (see FIG. 2), and the rice transplanter is constituted by a traveling machine body 1 and a seedling planting device 9 connected to the rear part thereof. A pair of left and right front wheels 3 and 3 and rear wheels 4 and 4 are suspended from the front and rear portions of the vehicle body frame 2 of the traveling machine body 1. As shown in FIGS. 3 to 5, the vehicle body frame 2 includes a pair of left and right main frames 80 and 81 that are long in the front-rear direction of the traveling machine body 1, a front frame 82 that is substantially U-shaped in plan view that connects the front ends thereof, An engine base 84 having a front end connected to the center of the left and right sides of the front frame 82, a rear side portion connected to a front connection frame 83 extending laterally from the pair of left and right main frames 80, 81, and the pair of left and right main frames 80. , 81 and a downward U-shaped rear frame 85 connected between the rear ends of the main frames 80, 81. The middle portions of the main frames 80, 81 are connected by center connecting frames 86, The left and right rear ends of the front frame 82 are connected to form a strong frame.
[0016]
An engine 5 as a prime mover is mounted on an engine stand 84 at the front portion of the vehicle body frame 2, and the front and rear (in the traveling direction of the traveling vehicle body 1) are arranged at the left and right central portions of the vehicle body frame 2 behind the engine 5. A long mission case 6 is arranged in the direction). The front end of the transmission case 6 is attached to a mounting member 87 at the rear end of the engine base 84, and the front and rear intermediate portions of the transmission case 6 are connected to the lower part of a mounting member 88 fixed to the left and right central portions of the center connecting frame 86. The rear end portion of the transmission case 6 is connected to the lower end of the rear frame 85 by a mounting plate 89 via a rear axle case 6a provided integrally.
[0017]
The power of the engine 5 is transmitted to the transmission case 6 via a belt pulley type continuously variable transmission 10 which will be described in detail later, and then left and right front wheels via a front axle case 6b provided at the front of the transmission case 6. 3 and 3, and is also transmitted to the left and right rear wheels 4 and 4 via a rear axle case 6 a provided at the rear portion of the transmission case 6.
[0018]
A driver's seat 7 is provided above the vehicle body cover 11 covering the mission case 6 and the like, and an operator sitting on the driver's seat 7 holds a steering round handle 8 erected at the rear end of the bonnet cover 12 covering the engine 5. Operate and steer the front wheels 3 and 3. The square pipe-shaped mounting members 14, 14 provided outside the side deck panels 13, 13 disposed on the left and right sides of the lower part of the bonnet cover 12 and at the outer ends of the front connection frame 83 have spare parts. A columnar support 16 (only one is shown in FIG. 1) for the seedling mounts 15 and 15 is provided upright.
[0019]
In addition, the seedling planting device 9 is connected to the rear end of the traveling machine body 1 so as to be movable up and down via a parallel link mechanism 17. The seedling planting device 9 is configured to be movable up and down with a hydraulic cylinder 18 for raising and lowering, and from a planted PTO shaft (not shown) projecting rearward to the mission case 6 to a universal joint transmission shaft (not shown) and the like. Transmission cases 50 and 50 (two in the embodiment) that transmit power via the upper side of the transmission case 50, 50 between the upper rails and the upper surfaces of the right and left transmission cases 50 and 50. The seedling platform 51 placed on the mounted lower rail so as to be slidable in the left-right direction is arranged in a forward inclined manner so that its upper end approaches the rear part of the traveling machine body 1, and is configured to reciprocate left and right. ing.
[0020]
A rotary seedling planting mechanism 53 that rotates up and down is disposed on the left and right side surfaces of the transmission cases 50 and 50. The planting rods 54 of these seedling planting mechanisms 53 move up and down between the lower end of the seedling platform 51 and the field scene, and the seedling platforms 51 are planted by the planting claws at the tips of the respective planting cages 22. 1 seedling is taken out from the plant and the seedling is planted in a field (see FIGS. 1 and 2).
[0021]
In addition, floats 55 (three in the embodiment) that slide on the mud surface of the field are disposed below the seedling planting device 9, and the right and left balance of the seedling planting device 9 is kept good, and seedling planting is performed. It is designed to stabilize the posture.
[0022]
As shown in FIGS. 1 and 2, the fertilizer application device 60 includes a plurality of (four in the embodiment) fertilizer storage hoppers arranged side by side on the left and right (the lateral width direction of the traveling machine body 1) behind the driver seat 7. 61, a feeding mechanism 62 provided in the lower part of each hopper 61, a feeding pipe 64 that connects each feeding mechanism 62, and a groove forming device 63 disposed on the side of the float 55, and the like. The compressed air (air) is blown through a horizontally long air tank 66 toward a hose joint (not shown) below each feeding mechanism 62. Thereby, the fertilizer discharged | emitted in each hose joint is discharge | released to the side part of the planting strip in a farm field from the corresponding grooving device 63 through each conveyance pipe | tube 64 with the said pressurized wind.
[0023]
A planting elevating lever 66 that also serves as a sub-transmission is disposed on the side of the driver's seat 7 (right side in the embodiment) in the vehicle body cover 11, and a main transmission lever 67 and a seedling lever 68 are provided in the driving portion. A main clutch petal 69 and a brake petal 70 are arranged on the side deck panels 13 and 13.
[0024]
Next, the configuration of the belt pulley type continuously variable transmission 10 will be described with reference to FIGS. 3 and 5 to 10. The continuously variable transmission 10 is disposed between one side (left side surface in the embodiment) of the engine 5 and the transmission case 6 and one (left side) main frame 80, and protrudes from the side surface of the engine 5. The drive side pulley 21 provided on the side, the driven side pulley 23 provided on the driven shaft (input shaft) 22 protruding from the side surface of the transmission case 6, the belt 24 wound around the pulleys 21, 23, and the like. Yes.
[0025]
The fixed sheave 25 and the movable sheave 26 in the driving pulley 21 and the fixed sheave 39 and the movable sheave 41 in the driven pulley 23 are both arranged with conical surfaces facing each other.
[0026]
The fixed sheave 25 in the driving pulley 21 is disposed on the side close to the side surface of the engine 5, and the boss portion 25 a is fitted on the driving shaft 20, and is fixed so as not to move in the axial direction by a key or the like. It is configured to rotate integrally. A key groove formed on the inner diameter of the boss portion of the movable sheave 26 is slidably fitted to a sliding key 27 fixed to the outer periphery of the boss portion 25a. As another embodiment, the boss portion 25a of the fixed sheave 25 and the movable sheave 25 are fixed. The movable sheave 26 is configured to be able to approach and separate from the fixed sheave 25 by forming a spline groove and a spline shaft on the boss portion 26. The movable sheave 26 is disposed closer to the inner surface side of the one main frame 80 than the fixed sheave 25.
[0027]
A cover-supporting body 29 having a base end fixed to the side surface of the engine 5 with a bolt or the like is disposed between the inner surface side of the one main frame 80 and the side surface of the engine 5 in plan view (FIG. 3). 5 and FIG. 7), a fixed cam 31 as one element of the cam means 30 in the operating mechanism is fixed to the support 29 with a bolt 28, and the inner diameter portion of the fixed cam 31 is fixed to the support 29. Thus, the boss portion 25a of the fixed sheave 25 is pivotally supported via a bearing 32 so as to be relatively rotatable. On the other hand, a movable cam 34 as the other element of the cam means 30 is mounted on the back side of the movable sheave 26 via a bearing bearing 33 so as to be relatively rotatable. In the embodiment, the cam means 30 is rotated via a support base 36 on the inclined cam surface 34a formed on the back surface of the movable cam 34 and the disk surface of the fixed cam 31 so as to contact the inclined cam surface 34a. It consists of rolling elements 35, such as a bearing provided so that it is possible. In the embodiment, the three inclined cam surfaces 34a divided into three equal parts in the circumferential direction are set to a predetermined inclination angle θ1 with respect to a plane orthogonal to the central axis of the drive shaft 20 (see FIG. 8). As shown in FIG. 10, the distal end portion of the drive side operating rod 37 is rotatably mounted on the arm portion 34 b at a location separated from the central axis of the drive shaft 20 by the radius r <b> 1. Thus, the movable sheave 26 is operated so as to move toward and away from the fixed sheave 25.
[0028]
A bolt 38a and a retaining ring 38b screwed to the drive shaft 20 are arranged on the inner diameter portion of the boss 25a of the fixed sheave 25, and the position of the retaining ring 38b is pressed against the boss 25a by the head of the bolt 38a. Then, the fixed sheave 25 can be attached and detached in the axial direction of the drive shaft 20 by removing the bolt 38a and the retaining ring 38b (see FIG. 7).
[0029]
The fixed sheave 39 in the driven pulley 23 is disposed on the side away from the side surface of the mission case 6 (in other words, the side close to the inner surface of one main frame 80), and the boss portion 39a is disposed on the driven shaft 22. And is fixed so as to be immovable in the axial direction by a key or the like and is integrally rotated. A bolt 40a and a retaining ring 40b screwed to the driven shaft 22 are disposed on the inner diameter portion of the boss portion 39a of the fixed sheave 39 (see FIG. 7). The position of the retaining ring 40b is pressed against the boss 39a by the head of the bolt 40a and the position is fixed. By removing the bolt 40a and the retaining ring 40b, the fixed sheave 39 can be removed in the axial direction of the driven shaft 22. The movable sheave 41 in the driven pulley 23 is disposed on the side close to the side surface of the transmission case 6, and a sliding key 42 in which a key groove formed on the inner diameter of the boss portion of the movable sheave 41 is fixed to the outer periphery of the boss portion 39 a of the fixed sheave 39. The movable sheave 41 is fixed to the fixed sheave by, for example, forming a spline groove and a spline shaft on the boss 39a of the fixed sheave 39 and the boss of the movable sheave 41 as another embodiment. It is configured to be able to approach and separate from 39.
[0030]
Then, the cam means 43 of the operating mechanism is disposed between the back surface of the movable sheave 41 and the side surface of the transmission case 6. In the embodiment, the fixed cam 44 as one element of the cam means 43 is fixed to the side surface of the transmission case 6 with a bolt or the like, while the movable cam 45 as the other element of the cam means 43 is interposed via the bearing bearing 46. The movable sheave 41 is mounted so as to be rotatable relative to the back side. In the embodiment, as shown in FIG. 9, the cam means 43 is formed on the inclined cam surface 45a formed on the back surface of the movable cam 45, and on the disk surface of the fixed cam 44 so as to come into contact with the inclined cam surface 45a. It comprises a rolling element 47 such as a bearing provided rotatably via a support base 36. In the embodiment, the cam means 30 and 43 arranged on the driving pulley 21 and the driven pulley 23 share the same size and shape. Therefore, the inclination angle θ2 of the inclined cam surface 45a is designed to be equal to θ1. However, as shown in FIG. 10, the distal end portion of the driven-side actuating rod 48 is rotatably attached to the arm portion 45b at a location separated from the central axis of the driven shaft 22 by a radius r2 (<r1). This driven side actuating rod 48 is operated so as to move the movable sheave 41 toward and away from the fixed sheave 39. Accordingly, the moving direction of the movable sheave 26 in the driving pulley 21 and the moving direction of the movable sheave 41 in the driven pulley 23 are in an arrangement relationship in which they are oppositely operated.
[0031]
A base end shaft 72 of an arm 71 that rotatably supports a tension roller 49 for maintaining the tension of the belt 24 wound around the driving pulley 21 and the driven pulley 23 substantially constant is provided on the engine base 84. It is fixed to the side surface and is biased by a spring 73 so as to press the tension roller 49 against the outer periphery of the belt 24 on the loose side (see FIGS. 6 and 7).
[0032]
Further, the operation unit 90 of the continuously variable transmission is performed by the auxiliary transmission / planting lifting lever 66 as shown in FIGS. 5, 10, 11, and 12. That is, each of the driving-side operating rod 37 and the driven-side operating rod 48 is respectively connected to a pipe-like common operating shaft 92 that is rotatably fitted to a round shaft 91 provided between the left and right main frames 80, 81. Output brackets 93a and 93b to which the base ends are connected are fixed in the same phase (see FIGS. 5 and 10). In addition, the input bracket 94 is fixed to the common operation shaft 92 at a portion close to the right main frame 81 facing the traveling direction, and the input bracket 94 and the operation link 96 are connected via a rod 95. The operation link 96 can be rotated around the support shaft 99 on the outer peripheral side of the dedent body 98 that rotates integrally with the auxiliary transmission / planting lifting lever 66 around the support shaft 97. The roller 101 provided in the middle part is urged by the spring 100 so as to always contact the outer peripheral edge of the dedent body 98 (see FIG. 11). It should be noted that the base end of the press link 102 is rotatable around the support shaft 99 so that the roller 103 at the tip end of the press link 102 is always in contact with the dedent portion 98a on the outer peripheral edge of the dedent body 98. It is biased by a torsion spring that does not.
[0033]
In FIG. 11, when the auxiliary transmission / planting lifting / lowering lever 66 is in the rightmost position UP (corresponding to a position opposite to the traveling direction of the traveling machine body 1 in FIG. 2), the seedling planting device 9 is greatly raised from the field scene. In the DW position on the left side, the float 55 of the seedling planting device 9 is the seedling lowering position in contact with the field scene. Then, when the auxiliary transmission / planting lifting / lowering lever 66 is tilted forward to the left LO position, an unillustrated planting clutch is turned on, and in FIG. 11, the dedent body 98 is rotated clockwise, When 98 is in a two-dot chain line state, the roller 101 comes into contact with a portion having a small radius of the dedent body 98. The upper end of the operating link 96 faces downward through the roller 101, and the input bracket 94 rotates clockwise through the rod 95. As a result, as shown in FIG. 10, the output bracket 93a (93b) is rotated clockwise through the common operation shaft 92 to be in a solid line state, so that the driving side operating rod 37 and the driven side operating rod 48 are illustrated. 10 to the left, the continuously variable transmission 10 enters a low speed state (LO). That is, when the drive side actuating rod 37 is moved in the left direction (arrow A) in FIG. 10, the movable cam 34 rotates clockwise, and the movable sheave 26 is moved by the movable cam 34 in the position of the solid line in FIG. The effective winding diameter of the belt 24 with respect to the driving pulley 21 is reduced away from the fixed sheave 25. On the other hand, when the driven side operating rod 48 is moved in the left direction (arrow A ′) in FIG. 10, the movable cam 45 is also rotated in the clockwise direction, and is movable by the movable cam 45 in the position of the solid line in FIG. As the sheave 41 approaches the fixed sheave 39, the effective winding radius of the belt 24 with respect to the driven pulley 23 is increased, and thereby the driven shaft 22 rotates at a lower speed than the drive shaft 20.
[0034]
When the auxiliary transmission / planting lifting lever 66 is tilted forward to the position of HI in FIG. 11, the dedent body 98 rotates counterclockwise to the solid line state in FIG. Since the roller 101 comes into contact with a large portion and pulls up the tip (upper end) of the operating link 96, the rod 95 is pulled upward. As a result, as shown in FIG. ) Rotates counterclockwise and enters a two-dot chain line state. Therefore, the drive side actuating rod 37 and the driven side actuating rod 48 are pulled to the right in FIG. 10, and the continuously variable transmission 10 is in a high speed state (HI). It becomes.
[0035]
That is, when shifting from the low speed state to the high speed state, if the drive side actuating rod 37 is moved in the right direction (arrow B) in FIG. 10, the movable cam rotated counterclockwise as in the two-dot chain line state in FIG. 34, the movable sheave 26 approaches the fixed sheave 25, and the effective winding radius of the belt 24 is increased. On the other hand, when the driven side operation rod 48 is moved in the right direction (arrow B ') in FIG. Similarly, the movable cam 45 rotates counterclockwise, and the movable sheave 41 is moved away from the fixed sheave 39 by the movable cam 45 in the position of the two-dot chain line in FIG. Rotates at high speed.
[0036]
By the way, as described above, the thrust generated in each of the pulleys 21 and 23 (the force that the pulley pushes the belt 24 = the belt generated thrust) has a small transmission load even in a static state where the pulley does not rotate or in a rotating state. Although the state is substantially the same, when the transmission load increases, the thrust of the driving pulley 21 is always larger than the thrust of the driven pulley 23 due to the change in the tension distribution in the belt, and there is a difference between the two thrusts. It was necessary to change the speed with an operating force larger than the difference between the two.
[0037]
In particular, when shifting from the low speed state to the high speed state, the force that the movable sheave 26 of the driving pulley 21 tries to open against the propulsive force of the belt 24 (the thrust of the driving pulley 21) is the driven pulley. It becomes larger than the thrust of 23. Then, as in the present invention, the cam means 30 (movable cam 34) of the driving pulley 21 and the cam means 43 (movable cam 45) of the driven pulley 23 are combined into one operating portion 90 for shifting operation. When they are moved in opposite directions, a force pulled leftward (in the direction of arrow A in FIG. 10) acts on the drive side operation rod 37, and a force (rightward on the driven side operation rod 48 is pushed rightward ( The arrow B ′ direction in FIG. 10 acts. In that case, if the moving amount of the movable sheave 26 with respect to the fixed sheave 25 in the driving pulley 21 is equal to the moving amount of the movable sheave 41 with respect to the fixed sheave 39 in the driven pulley 23, as described above. Since the thrust of the drive side pulley 21 is larger than the thrust of the driven side pulley 23, the tensile force acting on the drive side operating rod 37 becomes larger than the force pushed by the driven side operating rod 48. Therefore, when the rotation radii of the output brackets 93a and 93b fixed to the common operating shaft 92 are made equal to move the driving side operating rod 37 and the driven side rod 48 by the same amount, the common operating shaft 92 However, in FIG. 10, a moment to rotate clockwise acts, and when shifting from low speed to high speed, it is necessary to increase the force to operate the auxiliary transmission / planting lifting lever 66, On the contrary, when shifting from high speed to low speed, the operating force of the lever 66 is reduced, and the operating feeling of the auxiliary shifting and planting elevating lever 66 is staggered. That is, the speed change operation cannot be performed with the same operation force (rotational moment).
[0038]
For example, the resistance force of the dedent body 98 to the detent portion 98a must be set to be different between a low speed → high speed operation and a high speed → low speed operation. The ring was different.
[0039]
Therefore, in the present invention, the cam means 30 (movable cam 34) of the driving pulley 21 and the cam means 43 (movable cam 45) of the driven pulley 23 are reversed with respect to each other by a single operation unit 90 for a shifting operation. When moving in the direction, the moving amount of the movable sheave 26 with respect to the fixed sheave 25 in the driving pulley 21 is set to be smaller than the moving amount of the movable sheave 41 with respect to the fixed sheave 39 in the driven pulley 23. The continuously variable transmission 10 is operated with a light operating force by reducing the difference between the two thrusts as much as possible (preferably making them both equal).
[0040]
In the first embodiment, the fixed cams 31 and 44 in both the cam means 30 and 43 have the same size and shape (common parts) (therefore, the inclination angle θ1 of the inclined cam surface 31a (44a) of the both fixed cams 31 and 44). And θ2 are set equal to each other, and the radial arrangement position and the contact radius with the rolling elements 35 and 47 are also made equal, while the distal end portion of the drive side operating rod 37 is connected to the arm portion 34a of the movable cam 34. The distance (operating arm length) r1 between the attachment location and the axis of the drive shaft 20 is set so that the tip of the driven side operating rod 48 is located between the attachment location of the movable cam 45 on the arm portion 45a and the axis of the driven shaft 22. By setting it larger than the distance (operating arm length) r2, the cam means 30 (movable cam 34) of the driving pulley 21 and the cam means 43 (movable cam 4) of the driven pulley 23 for shifting operation. 5) are moved in opposite directions by one operating portion 90, the output brackets 93a and 93b fixed to the common operating shaft 92 have the same turning radius, and the driving side operating rod 37 and the driven side When the rod 48 is moved by the same amount, the movement amount of the movable sheave 26 with respect to the fixed sheave 25 in the driving pulley 21 is smaller than the movement amount of the movable sheave 41 with respect to the fixed sheave 39 in the driven pulley 23. With this configuration, the operating forces acting on the drive side actuating rod 37 and the driven side actuating rod 48 are opposite in magnitude and are equal in magnitude, so that the operating forces are offset. The attached lifting lever 66 can be operated with a light force, and the operation feeling of the auxiliary transmission / planting raising / lowering lever 66 serving as the operation unit 90 is the same. A marked effect of bets can be.
[0041]
As a second embodiment in which the moving amount of the movable sheave 26 with respect to the fixed sheave 25 in the driving pulley 21 is less than the moving amount of the movable sheave 41 with respect to the fixed sheave 39 in the driven pulley 23, both the movable cams 34 and 45 are used. While the arm length r1 = r2 is set, the inclination angle θ1 of the inclined cam surface 34a of the cam means 30 in the driving pulley 21 is set to be smaller than the inclination angle θ2 of the inclined cam surface 45a of the cam means 43 in the driven pulley 23. As a result, both the movable cams 34 and 45 are rotated by the same rotation angle via the output brackets 93a and 93b fixed to the common operation shaft 92, the drive side operation rod 37 and the driven side operation rod 48. The amount of movement can be varied, and operation can be performed with the same operating force (rotational moment).
[0042]
In the third embodiment, the output bracket 93a of the drive side actuating rod 37 fixed to the common operation shaft 92 while the tilt angle θ1 = θ2 and the arm length r1 = r2 of both the movable cams 34, 45 are set. Arm length (radius from the rotation center of the common operation shaft 92 to the connection point of the drive side actuating rod 37 with respect to the output bracket = actuating arm length), and the arm length of the output bracket 93b of the driven side actuating rod 48 (common operation). By making the radius shorter than the rotation center of the shaft 92 to the connecting point of the driven side actuating rod 48 to the output bracket = actuating arm length), both the movement amounts can be changed.
[0043]
3, 5, 6, 7, and 8, the hydraulic pump 104 is fixed to the outer surface of the support 29 having a cover function that covers the front and side surfaces of the driving pulley 21, and the engine 5 is connected in series to the input shaft of the hydraulic pump 104 via a coupling means 105 such as an Oldham coupling, with respect to the tip of the drive shaft 20 which is the output shaft of the power transmission means. Can be made compact. Further, the support state of the hydraulic pump 104 can be strengthened by fixing it to the one main frame 80 via a connecting bracket 106 that is bolt-connected to the rear end portion of the support 29 (see FIGS. 6 and 7). .
[0044]
Both the fixed cam and the movable cam may be in contact with each other by the inclined cam surface. However, when the inclined cam surface and the rolling element are in contact, the fixed cam can reduce the contact resistance force with the movable cam and reduce the shifting operation force. There is an effect that can be done. In the above embodiment, the inclined cam surfaces 34a and 45a are formed on the movable cams 34 and 45, and the rolling elements 35 and 47 as followers are provided on the fixed cams 31 and 44. An inclined cam surface may be formed on 44, and rolling elements 35 and 47 as followers may be provided on the movable cams 34 and 45, respectively. Furthermore, one cam may be an inclined cam surface, and the other cam may be formed on a sliding body or cam surface as a follower.
[0045]
It goes without saying that the present invention can be applied not only to agricultural machines but also to other industrial working units. In that case, the operation lever only needs to rotate the common operation shaft 92.
[0046]
【Effect of the invention】
As described in detail above, the continuously variable transmission according to the first aspect of the present invention is fixed to the drive shaft pulley, which is composed of the movable sheave that moves toward and away from the fixed sheave fixed to the drive shaft, and to the driven shaft. A belt is wound around a driven pulley comprising a movable sheave that moves far and away relative to the fixed sheave, and the moving sheave movement direction of the driving pulley and the moving sheave movement direction of the driven pulley are opposite to each other. In the continuously variable transmission configured to be operated and shifted, an operating mechanism for moving the movable sheave in the driving pulley and an operating mechanism for moving the movable sheave in the driven pulley are provided with one operating unit. The amount of movement of the movable sheave with respect to the fixed sheave in the driving pulley is set to the amount of movement of the movable sheave with respect to the fixed sheave in the driven pulley. Set to be less than the momentum, the two actuating mechanism consists cam means provided on the movable sheave, and configured to be rotatable and movable cams that contact the fixed cam of the cam means about the axis of rotation of the pulleys, The arm length of the operating arm for rotating the movable cams is set so that the driving pulley is longer than the driven pulley .
[0047]
With this configuration, the operating force acting on the operating mechanism that operates the movable sheave on the driving side and the operating mechanism that operates the movable sheave on the driven side are reversed and equal in magnitude, and the operating force is offset. Therefore, there is a remarkable effect that one operation unit can be operated with a light force and the operation feeling of the operation unit can be made the same.
[0048]
[0049]
In particular, in the first aspect of the present invention, the two operating mechanisms are composed of cam means provided on the movable sheave, and the movable cam contacting the fixed cam in the cam means is configured to be rotatable around the rotation axis of each pulley. Since the arm length of the actuating arm for rotating the movable cam is set so that the driving pulley is longer than the driven pulley, the configuration and dimensions of both the driving and driven cam means Can be used except for the length of the operating arm . Therefore, in addition to the above effects, the effect also Kanade of reducing the manufacturing cost of the continuously variable transmission.
[0050]
[0051]
[Brief description of the drawings]
FIG. 1 is a side view of a rice transplanter.
FIG. 2 is a plan view of a rice transplanter.
FIG. 3 is a schematic perspective view of a vehicle body frame, an engine, a transmission case, and a continuously variable transmission.
FIG. 4 is a perspective view of a vehicle body frame.
FIG. 5 is a schematic plan view of a vehicle body frame, an engine, a transmission case, and a continuously variable transmission.
FIG. 6 is a side view of the continuously variable transmission.
FIG. 7 is a cross-sectional view of a continuously variable transmission.
FIG. 8 is an enlarged plan view of a drive pulley portion.
FIG. 9 is an enlarged plan view of a location of a driven pulley portion.
FIG. 10 is an operation explanatory diagram.
FIG. 11 is a side view of an operation unit of the continuously variable transmission.
FIG. 12 is a perspective view of an operation unit of the continuously variable transmission.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Traveling machine body 5 Engine 6 Mission case 10 Continuously variable transmission 15 Seedling device 20 Drive shaft 21 Drive side pulley 22 Drive shaft 23 Drive side pulley 24 Belt 25, 39 Fixed sheave 26, 41 Movable sheave 30, 43 Cam means 31, 44 Fixed cams 34, 45 Movable cams 34a, 45a Inclined cam surfaces 35, 47 Rolling bodies 37 Driving side operating rods 48 Driven side operating rods 66 Sub-shifting / planting lifting levers 90 Operating units 92 Common operating shafts 93a, 93b Output brackets 98 Detent body

Claims (1)

A belt on a drive-side pulley comprising a movable sheave that moves toward and away from a fixed sheave fixed to the drive shaft, and a driven-side pulley that comprises a movable sheave that moves toward and away from a fixed sheave fixed to the driven shaft In the continuously variable transmission configured to shift the movement direction of the movable sheave in the driving pulley and the movement direction of the movable sheave in the driven pulley in reverse operation with each other,
The actuating mechanism for moving the movable sheave in the driving pulley and the actuating mechanism for moving the movable sheave in the driven pulley are configured to be operated via one operation unit,
The amount of movement of the movable sheave relative to the fixed sheave in the driving pulley is set to be smaller than the amount of movement of the movable sheave relative to the fixed sheave in the driven pulley ,
Each of the operating mechanisms is composed of cam means provided on the movable sheave. The movable cam contacting the fixed cam in the cam means is configured to be rotatable about the rotation axis of each pulley, and each movable cam is operated to rotate. The arm length of the operating arm is set so that the driving pulley is longer than the driven pulley.
Continuously variable transmission.

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