TWI331107B - - Google Patents

Description

[Technical Field] The present invention relates to a work vehicle for a hydraulic control device having a hydraulic clutch having a versatile operation of a garden. . . [Prior Art] A work handle for agricultural, construction, and transportation uses a left and right moving axle, and a shifting device that changes the driving force of the traveling axle. This shifting device is configured to switch engine power. The main clutch and the reverse mechanism for switching the wheel forward and backward, and the synchronous reversing main transmission and the auxiliary transmission are respectively disposed downstream and downstream of the transmission of the reverse mechanism. In the above-mentioned work vehicle, there is also a hydraulic clutch that is used as a master and a reverse mechanism for switching between forward and reverse, in which the oil pressure is separated from the device and the operation of the stepping or advancing and retracting lever Linked to control the actuation, non-actuation, forward and reverse of the transmission. The configuration disclosed in Japanese Laid-Open Patent Publication No. Hei No. 7-127668 is to switch the hydraulic clutch of the shifting device in conjunction with the pedaling of the clutch 2, so that the amount of depression of the clutch pedal required for the hydraulic pressure to be activated is increased to The setting current of the electromagnetic proportional control valve for the piston of the hydraulic clutch is smaller, j, the return operation amount of the clutch is larger during the return operation from the clutch open position to the clutch closed position. The current control of the electromagnetic proportional control valve gradually increases the current value of the set current value for the piston actuation. When the return operation of the clutch pedal is performed quickly, j the hydraulic actuation state of the pedal in the initial operation phase is prone to delay with respect to the pedal operation, causing the pedal return operation to be excessively performed due to the excessive crimping action of the clutch motor 7 1331107 wiper. Variable speed shock, upper (four) This kind of bad condition. In the configuration of the aforementioned Patent Document 1, the shifting shock of the clutch pedal is not a peak when the shifting shock is not generated. This will occur, but does not take into account that the centrifugal force generated by the rotation of the hydraulic clutch shaft exerts a thrust on the clutch hydraulic piston. The two thrusts will affect the operational feel of the clutch pedal. An object of the present invention is to provide a hydraulic clutch that is capable of taking into account the rotation of the input shaft of the oil clutch when starting from the state in which the transmission torque is substantially 〇 and the pressure is increased from the connection of the hydraulic pressure to the human body. The problem of the centrifugal force of i and the hydraulic pressure control device that smoothly pressurizes the problem of the present invention is solved by the following solutions. The invention of the patent scope 帛i is a traveling vehicle having: an engine (62), a hydraulic oil pressure by a clutch cylinder (85): an adjustment to make the connection state of the engine (62) power from non- The hydraulic clutch (9) whose connection state is continuously changed to the connected state, the power transmission mechanism (A, B, C) that is operated by the power of the hydraulic clutch (D), and the hydraulic pressure for adjusting the hydraulic oil to make the hydraulic pressure The clutch (D) is a clutch operating means (115, 119) that is in a connected state or a non-connected state, and applies an elastic force to the hydraulic clutch (D) under the condition that no hydraulic pressure acts on the hydraulic clutch (1). In the non-connected state = the moving arm (77F, 77R) and the 'hydraulic pressure control device ((10)), when the hydraulic pressure is applied to the hydraulic clutch (D) in the non-connected state, the output is output at a predetermined time. 1107 The hydraulic pressure greater than the elastic force of the return spring (77F, 77R), and then the hydraulic pressure of the return spring (77F, 77R) is approximately the same as the hydraulic pressure, and then gradually output more than the return spring (77F, 77R) The elastic pressure of the hydraulic pressure makes The hydraulic clutch (D) is in a connected state; the input shaft (2) of the clutch cylinder (85) is rotated by the power of the engine (62), and the hydraulic control device (100) is provided to calculate the clutch The centrifugal force of the hydraulic oil in the clutch cylinder (85) generated by the rotation of the cylinder (85), and then the hydraulic pressure of the hydraulic clutch (D) is corrected according to the thrust of the hydraulic oil caused by the centrifugal force, and corrected The subsequent hydraulic pressure causes the hydraulic clutch (D) to be actuated from the non-connected state to the connected state. According to the invention of the scope of claim i, when the hydraulic clutch (D) is opened, the hydraulic pressure greater than the elastic force of the return spring (77F, 77R) is output for a predetermined time. After the output and the return magazine (77f, the elastic force is large

The hydraulic pressure for opening the thrust correction hydraulic clutch (D).

After the connection pressure of H, (13) is actuated, the connection of the hydraulic clutch (D) becomes the rotation of the good 9 clutch cylinder (85), which affects the hydraulic pressure of the oil-actuating oil to adjust the hydraulic pressure. 9 1331107 Get a good sense of operation. [Embodiment] Hereinafter, embodiments and drawings of the present invention will be described. Fig. 1 is a left side view of the traction machine oil of the traveling vehicle, and Fig. 2 is a power transmission diagram of the transmission device of the traction machine of the figure, the hydraulic circuit diagram of the force transmission diagram, the head 4 is Figure 〗: The construction of the hydraulic clutch for the power switch, Figure 5 is the control block diagram of the hydraulic clutch for the forward and reverse power switch of the shifting device of Figure 4, the pedal pedaling position and the forward and backward pedaling The diagram of the relationship, ... shows: the force of the two-in-one device is not the same as the circle of the engine's speed caused by the centrifugal force of the oil-carrying clutch. Figure 1 is a side view of the tractor of the present embodiment. With a four-wheel drive for passengers, the body of the traction machine is T-turned to the following:: There are 7;: The direction of the longitudinal front wheel 61 is running. In the body of the car τ! : 2 = down two turn ploughing" 84 work machine can be carried on the ground to carry the engine =: lead; end 6: through the front axle outer box of the engine bracket m to 2 behind One-piece connection clutch outer box or transmission phase 6 5 etc. The rear outer casing 75 is set at the last part of the left-handed heart, and the rear wheel 63 is mounted on the left and right sides. The power transmission system diagram of the traction machine of the embodiment. The engine 62 has an engine shaft protruding toward the rear side and coupled to the clutch outer casing, and the furnace engine shaft Ί ^ ^ Λ ^ is input to the shaft 2. The transmission mechanism is transmitted through the transmission box 65. Make the rear end of the wheel 铋 2 η κ move the lower part of the box 65 before the I!: 14 linkage 'and make the transmission month - ~ the output shaft 5 linkage. The wheel output shaft 3 along the transmission box μ 10 1331107 =: :T is substantially axially supported in the front and rear directions and has a drive i gear 53 at the rear end, and the differential ring gear μ biting mechanism with the rear differential device 45 will be followed by the rear material 1G and the rear axle 62. The lower front wheel output shaft 5 passes the engine from the lower part of the gearbox 65

. The 卩 is connected to the front portion of the front outer casing and is connected to the front axle 13 through the differential material 12 and the planetary deceleration mechanism 4 along the front casing shaft. Further, the power take-out gear drive shafts 15, 17 from the input shaft 2 to the oil pump _3) are arranged side by side on the wheel-in shaft 2. The transmission of the present embodiment is provided with the cymbal clutch assembly 66 disposed on the cymbal sub-pump 9 having the ρτ〇 sub-transmission gear 44 coupled to the input gear 31 from the input shaft 2 driven by the engine shaft 1. In the forward and reverse switching of the input and retraction of the input shaft, the forward and reverse switching gears 42 and 42 are moved forward and backward on the backward side.

The change gear 42 is disposed on the counter gear 8 after being disposed in parallel with the input shaft 2, and the counter gear 43 is engaged with the counter gear 8 on the forward side. The forward/reverse switching gear 42 on the forward side is provided to the input gear 48 fixed to the main shift shaft 19 and the main shift shaft. The main shifting gear 33 having four different effective diameters is loosely arranged on the 19th. The four main shifting gears 33 are configured as four-stage shifting, and are switched by the clutch unit 76, and the shifting device constituted by the four main shifting gears 33 is referred to as a main shifting device Α. On the main shifting shaft 19, the main shifting gear 33 (the first speed) having the smallest effective diameter among the four main shifting gears 33 of the main shifting device A and the main shifting gear 33 having the effective small third smallest gear (the third speed) The clutch unit 76 is fixedly disposed therebetween, and the clutch unit 76 is fixedly disposed between the main-speed shifting gear 33 (for the second speed) having the second largest effective diameter and the main shifting gear 33 (for the fourth speed) having the largest effective diameter. 11 1331107: The two clutch assemblies 76 are provided with friction clutches for integrally rotating the main shift gears ’, ', and the main slamming shaft 19, respectively. Further, the input gear 48 that can be engaged with the forward side gear before the forward/backward switching gear 42 and the gear of the reverse side of the forward/backward switching gear 42 are engaged with the countershaft gear 43 after the rear countershaft $, and the forward/backward switching gear 42 is advanced. The side gear 42 and the reverse side gear 42 are integrated with the input shaft 2 by the switching of the two forward/reverse switching clutch assemblies 6 () formed by the friction clutches of the front and rear, and can be switched forward and backward. These gears 42 including the hydraulic cylinder 85 (FIG. 3) to be described later, the clutch assembly 60, and the like are referred to as forward/reverse clutches D. Further, in the column portion of the steering handle 73, an advance/reverse switching lever 115 for manually switching between the forward and backward clutches D is provided, and the clutch pedal ι 9 is provided below the handle post 73, and the clutch pedal 121 is provided near the handle. Yu sighed with the main speed car by! 9 The auxiliary shifting shaft of the concentric position is provided with two high and low speed cutting and gears 34 which are different from the effective diameter which is changed by the switching of the assembly 76, and the driving force after the main shifting can be further reduced and the high speed and low change=switching . The gear set capable of switching between high speed and low speed is referred to as high and low v speed device B. An output shaft 3 having a fixed-speed transmission gear 35 having a different effective diameter is additionally disposed coaxially with the auxiliary shifting shaft 2''. The output shaft 3 is composed of a three-speed shift of the auxiliary shifting gear. This three-stage shifting gear 35 device C. The 具备 疋 ’ 具备 具备 具备 潜 潜 潜 潜 潜 潜 潜 潜 = = = = = = = = = = = = = = = = = = = = = = = = Further, the travel sub-shaft 6 provided with the main transmission sub-shaft gear 39 12 engaged with the main 33 or the lower-low-switch # wheel 34 is attached to the main shift shaft 19, and is rotated from the main shift shaft to the shift gear. The 33 shifting 'this rotation is sequentially transmitted to the high and low speed switching gears 34 provided on the auxiliary shifting shaft 经过 through the main shifting sub-shaft gear π and the still low speed switching gear 4G. The transmission mechanism transmits the transmission mechanism to the low speed switching gear 34 and the power transmission through the clutch assembly 76 and the transmission mechanism of the aj speed gear 35 provided on the auxiliary shift shaft 20 > 3丨丨_| Axis 3.

In the ordering power transmission system of the present embodiment, there is a setting to provide Μ. The positive and negative switching gear 37 mechanism is rotated and the rotation of the shaft 4 is rotated.

And the high-low speed switching gear 4 或 or the auxiliary shifting shaft 20 is juxtaposed, and the front wheel linkage shaft 28 is provided, and the rotatively supporting the sub-shift ω wheel 35 is rotatively moved [the shifting auxiliary shaft tooth @ 38 sub-shifting The counter shaft 27 has a front wheel interlocking gear 51 that is coupled to the input (four) 3 through the front wheel take-up gear 36, and is provided on the extension shaft center of the front wheel linkage shaft 28 and has a reduction gear 5...Τ0 deceleration shaft 23. Further, a ρτ〇 linkage axis 4 is disposed at a parallel position of the front wheel linkage shaft 28, and the ρτ〇 linkage shaft 4 and the concentric upper end portion are provided with a ρτ〇 forward and reverse switching for the forward rotation and the reverse rotation of the ΡΤ〇 linkage shaft 4 The 370 of the gear 37 is the front and rear switching shaft 22 and the PTO shifting shaft 18 of the slamming shifting gear. Further, the ΡΤΟ ΡΤΟ reverse countershaft 24 having the ρτ〇 reverse countershaft gear 52 engaged with the PTO forward/reverse switching gear 37 is provided. The side portion of the ρτ〇 forward and reverse switching shafts ' passes through the ΡΤΟ clutch assembly 66, and passes through the ΡΤΟ speed gear 32, the ρτο shifting counter gear 44, and the ρτ〇 forward and reverse switching gears 3" from the input shaft 2, The power is transmitted to the front and rear switching shaft 22. The forward/reverse switching 1331107 gear 3 7 is in the form of a clutch ring of the same form as the P Τ 0 shifting gear 3 2. On the side of the front and rear switching shaft 22 The reverse countershaft 2 4 having the ρ Τ〇 reverse counter gear 5 2 is provided, and the Ο Ο Ο reverse counter gear 52 can receive the interlocking of the ΡΤΟ reduction gear 50 to reverse the ΡΤΟ forward and reverse switching gear 37. 'The deceleration shaft 23 is disposed behind the sub-shaft 9 of the cymbal. The front wheel output shaft 5 is mounted on the lower portion of the lower portion of the transmission case 65 at the bottom of the rear portion of the transmission case 65, and is coupled to the input shaft 26 of the front differential device 47 via the front wheel linkage shaft 25 or the link. The front wheel output shaft The front wheel drive shaft 7 is disposed on the side of the front wheel drive shaft 7. The front wheel gear 55 is disposed at the rear end of the front wheel drive shaft 7. Further, the ith front wheel linkage gear 51 on the front wheel linkage shaft 28 is engaged with the front end of the output shaft 3 The driving force of the gear 36 transmitted to the output shaft 3 of the front wheel linkage shaft 28 through the first front wheel interlocking gear 51 is transmitted to the second front wheel interlocking gear 54' that is rotated with the front wheel linkage shaft 28, and the gear is interlocked from the front wheel. 54 is transmitted to the front wheel drive shaft 7. ^%Zhen Ke Ke Leping is connected from the front end of the drive shaft 7 to the front wheel output shaft 5 gear. It is also effective to switch gears by two different front wheel drive. The 41 series are disposed on the left and right sides of the front-wheel-displacement clutch Is unit 67. The two-wheel drive switching gears 41 are respectively engaged with the effective diameter of the sub-shaft 59. Rescue round 56, by choosing one to connect to the front wheel, he helped the benefit group Item 67, the front wheel drive shaft can be driven at any of the 2 reduction ratios. When the switch to the neutral position is not driven, the front wheel drive clutch assembly is set to be about 1 with respect to the rear wheel 63. The second drive form 67 of the rear wheel drive of the clutch assembly front wheel 61 is switched to the low position 14 1331107 by the hydraulic operation to drive the four-wheel drive form of the front wheel 61 at the same speed, and (4) "(4) ^ έ 错 由 油 [#二乍When switching to the catch position, it can travel in a four-drive form that drives the front wheel 6 1 with respect to the rear wheel: 3 about 2 times.

With the above-described snap-in shifting device, the engine 62 passes through the Φ 构成 of the forward-reverse clutch D constituting the main clutch, and the speed of the squirrel-and-spindle speed is 4 stages of slamming = high-speed shifting of the shifting gear. After any of the two shifting sections of the rear difference, the rear wheel W and the shifting force of the shifting force are also transmitted to the front wheel drive clutch assembly. 〇 51 51 51 51 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆 駆The main change of the travel system is the high and low speed switching of the 嵩 wheel 34, and the auxiliary shifting gear: 3, 53 of the output shaft ^ 夕 Crawl / 〇 eight drive pinion through the output: 3: Γ. The drive system of the travel system From the input shaft 2 gears 34, and 1 to the 逹 ' '. The upper main gear 3, high and low speed switch 53. In addition, ΡΤΛ 5 and other multi-speed shift linkage to drive the pinion system, the transmission system is set to the output The front end of the shaft 3: the shift gear 32 is interlocked. The shaft, the upper = 3 shows the hydraulic circuit diagram of the tractor of the present embodiment. The hydraulic circuit diagram of the left and right 2nd is provided with 4> independent cylinders for the left and right rear wheels, and the "speed increase" to be transmitted to the front wheels 61. The four-wheel drive clutch cylinder 99, the swing gate operated by the steering hand two or the turning operation, the swinging lever eight-power steering device 103 of the handle 73, the clutch clutch steam clutch pressure control...6, etc. :Key 15 1331107

The line part of the circuit l〇1 A flat and external main hydraulic circuit (worker lift 'work machine water (staring, braking, differential locking, ") has little relationship, so the illustration of the circuit is omitted From the hydraulic pump 80, spit + 仏 < the engine oil is supplied to the variable transmission clutch unit 76 through the pressure reducing valve 81a, and the gears 33 for the second speed are actuated. The 4-2 speed switch of the steam (10) is equipped with a steam red 87 and a hydraulic clutch, and a shift control valve 89, and is further provided with a shift control valve for the final summer/three-speed switching, to the first speed of the second shift. The 'close-to-close cylinders 91 and the hydraulic clutch cylinders 92 of the gears 3 for the third speed are supplied to the shut-off control valve 12 9 through the pressure-reducing valve 81a. The switching valve 86 of the clutch D of the forward fish retreating side before the advancing and retracting clutch cylinder 85 is switched. Which of the clutches D of the forward and reverse sides of the forward and reverse clutch steam rainbow has a working oil supply to the forward clutch pressure sense (4) UG and the retreating side clutch ^ 111 measured. The knife is the same as 'provided The hydraulic oil supplied to the cylinders of the above-mentioned and below-described hydraulic clutches can be measured by the oil-circuit force sensors on the population side of the cylinders of the spicy hydraulic clutch cylinders respectively. The valve 8ia and the brake valve 82a are distributed and supplied to the left and right brake cylinders 83. The brake valve 82a is a switching control valve for selecting the rear wheel 63, and the brake valve 82& is integrally formed with a pressure control valve 82b for adjusting the braking force. Further, the hydraulic oil that has passed through the pressure reducing valve 81b is supplied to the control valve _, 16 1331107 96', which is used to switch the transmission clutch assembly % so that the speed of each of the gears 33 for the speed to the fourth speed is " The high and low hydraulic clutch cylinders 95 of the two gears of the "high speed" and "low speed" are operated. The oil is also actuated by the pressure reducing valve 81b, and is dispersed to the front differential device via the differential lock control. 47 front differential differential locking cylinders... and rear differential device 45 are locked by the rear wheel differential locking cylinder 9. The operating oil passes through the switching oil of the gear 41 of the switching control valve 67.

Further, the aforementioned pressure reducing valve 8 1 b 94 is supplied to the front wheel drive clutch element pressure cylinder 99. Similarly, the hydraulic oil passing through the pressure reducing valve 81b is transmitted through the ρτ〇 valve 1〇5, i〇6 is supplied to the 离合器0 clutch cylinder 1〇4 to adjust the pressure of the ρτ〇 clutch. Further, the hydraulic system from the hydraulic pump 8G shown in Fig. 3 supplies the operating oil to the orbital roller 1〇7 which is operated by the power steering handle 73. 4 is a cross-sectional view showing the configuration of the forward and reverse clutch cylinders 85 for switching the forward and backward gears 42, 42. After the π-cylinder 85, the pistons 78 and 78r are respectively actuated by the inflowing actuating oil (0IL) in the steam rainbows 85F and 85r, and are contacted by the pistons 78 and 7 The multi-array friction plate constitutes an advance and retreat switching clutch assembly 6〇, 60. When the clutch $ pedal 119 is not in operation (when the stepping operation of the (four) type pedal 119 is not performed), one of the forward and backward reversing steam reds 85F, 85R has a hydraulic oil inflow and the piston 78p is violent/8F or 78R In the actuated state, the forward and backward switching clutch assemblies 60, 60 are in a connected state, and the engine power is transmitted to the front side drive mechanism or the reverse side drive mechanism in the shifting device 17 1331107. Further, a return spring (compression spring) 77F is provided in each of the cylinders 85F and 85R. 7R, the reversing springs 77F and 77R are respectively actuated to the side of the connection state in which the forward and reverse clutch assemblies 6A and 6〇 are released. Therefore, if the clutch pedal is operated (the pedaling operation of the pedal pedal 119 is performed), the oil in the cylinder 85F or 85R flows out, and the piston 78F or 78R is moved in the opposite direction by the elastic force of the return spring 77F or 77R. The forward or reverse clutch assembly 6 is connected. In the above-described forward/backward switching clutch assembly 6A, the centrifugal force caused by the rotation of the input shaft 2 of the clutch input shaft causes the oil in the piston 78F or 78R to apply a thrust to the piston 78F or 78R. Thereby, a power transmission torque which is generated by the pressure of the oil pressure to the torque of the input shaft 2 plus the thrust caused by the centrifugal force is generated. The aforementioned centrifugal force can be obtained by the following formula. First, the pressure in the k direction of the input shaft 2 when the oil in the clutch cylinder 85F or 85R is completely rotated integrally with the forward side clutch group | the cow 60 or the reverse side clutch unit 6 可以 can be expressed by the following equation (forced vortex type, pressure p The radial direction distribution of the wheel I* 2 is shown in Fig. 6. The value of the pressure ρ on the outer side in the radial direction is larger. Ρ=Ρ〇+1/2 ρ τ2ω2 (1) , one of which is the axial pressure (Pa ) ρ is the density (kg/m3), r is the slave axis. The distance (m)' (1) is the clutch angular velocity (rad/s). Therefore, the thrust of the piston 78F < 78R can be (1) along the half The direction surface 18 1331107 is integrated to obtain the following formulas (2) and (3). f /1 1 P ~ \PdA = P0A + U - ρτ2ύ)2 χIjtrdr (2) 2 2 F = PqA + ^ ρπω1 - φ^) ( 3) where 'F is the piston thrust (n) 'A is the piston area (m2), 0 1 is the live φ inner rib (m), and 0 2 is the piston outer diameter (m). The first term of the formula (3) is the thrust of the control pressure of the unillustrated hydraulic valve operated by the electromagnetic coil 86F or 86R against the piston 78F or 78R, and the second term is the thrust caused by the centrifugal force of the oil in the cylinder 85F or 85R. . According to the formula (3) 'Because even if the pressure caused by the oil pressure valve is 〇, as long as the forward side clutch unit 60 or the reverse side clutch unit 6 is rotating, the thrust is still generated, so the set load of the return spring 77F or 77R is set. Must be greater than the thrust caused by centrifugal force. Moreover, although the thrust cannot be measured by the pressure sensor φ 疋, since it can be obtained from the rotational speed of the input shaft 2, it can be estimated based on the engine rotational speed (detected by the engine rotational speed sensor 丨12 shown in Fig. 5), and Carry out the corresponding 'control. I - Here, in the present embodiment, with respect to the operation of the clutch pedal 丨 9 or the like, the hydraulic clutch 6 进 of the forward-reverse hydraulic clutch D is opened and closed, and the hydraulic clutch is changed in accordance with the operating position of the clutch pedal 119. The pressure of D can operate the half clutch and correct the pressure of the forward side clutch assembly 6 〇 or the reverse side clutch assembly 60 under the engine speed (or the rotational speed of the input shaft 2) and the position of the clutch pedal 1 19 . 19 1331107 shows the relationship between the position of the clutch pedal U9 and the clutch connection pressure, and the position of the clutch pedal 119 is when the pedal 119 is fully depressed (the forward side clutch assembly 60 or the reverse side clutch assembly 6 is completely non-contact; pedal) The clutch engagement pressure at position P1 of 119 is a predetermined value (lkgf/cm2) 'The forward side clutch assembly 6〇 or the reverse side clutch assembly returns the pedal u 9 from the full non-contact state to the forward side clutch assembly (9) or backward The side clutch assembly 60 is in a full contact state (position P2 of the pedal i丨9). The forward side clutch assembly 6 or the reverse side clutch assembly 6 must be present before the clutch engagement pressure reaches a predetermined value (for example, i〇kgf/cm2). The load is added to the hydraulic pressure of the corrected pressure α caused by the centrifugal force. Figure 7 shows the relationship between the engine speed and the correction pressure α. The corrected pressure α is the maximum value in the idle state, and gradually decreases during the engine speed rise to the rated value (for example, 220 rpm), and the engine speed reaches the rated value. The value (for example, 2200 rpm) is 〇. Since the lower the engine speed, the smaller the thrust of the pistons 78F and 78r is, the smaller the centrifugal force is. Therefore, the correction pressure α must be made large. Further, since the piston thrust can be obtained from the product of the sectional area of the clutch pistons 78F and 78R and the engine rotational speed, the piston thrust of the hydraulic clutch D can be calculated based on the configuration of the pistons 78F and 78R of the hydraulic clutch D. The engine speed is corrected by the correction pressure α as the data stored in the memory of the controller 100. When the pressure of the clutch pedal i 19 is controlled, the saved data is read by the engine speed to cause the forward clutch assembly 6 to 〇 Or the reverse side clutch assembly 60 is actuated. Alternatively, the rotational speed of the input shaft 2 or the thrust (torque) of the input shaft 2 may be calculated by inputting the rotational speed of the shaft 2 instead of the engine rotational speed. At this time, the correction pressure α or the thrust (torque) of the input shaft 2 can be calculated from the rotational speed of the input shaft 2 calculated from the engine speed and the reduction ratio of the input shaft 2 of the target to the target shaft 2 of 20 1331107.

As described above, the rotation of the W engine or the rotation of the input shaft 2 causes the force of the formula (3) to cause the oil in the clutches a of the cylinders 85F, 85R to apply a thrust to the movable jaws 78F, 78R 'by this' to the forward clutch The component 6〇 or the reverse side clutch assembly 60 generates a power transmission torque of the torque of the input shaft 2 generated by the oil leakage force plus the thrust generated by the centrifugal force, so only the engine speed or the input shaft 2 speed and the pair of pistons 78F The supply pressure of the emblem cannot give the predetermined clutch connection torque. Here, if the clutch is operated with the engine shaft speed or the torque of the input shaft 2 generated by the hydraulic pressure plus the thrust of the centrifugal force, a good operational feeling can be obtained. Further, since the pistons 78F and 78R of the forward/reverse clutch D are subjected to the centrifugal force of the above formula (3), the arrangement in the return direction of the piston can generate the engine speed (or the speed reduction ratio from the engine speed to the speed of the clutch input shaft 2). The calculated returning springs 77F, 77R of the thrust of the centrifugal force on the piston thrust force generated by the maximum speed of the clutch wheel entering the vehicle 4 2 . The forward/reverse hydraulic clutch (reverse mechanism) D of the present embodiment is used in a large number of clutch assemblies 6 〇 for a forward and backward arrangement in a cylinder case, and a clutch having a 2 system and a reduction ratio. Under the & brother, when the centrifugal force generated by the rotation speed of the forward and reverse clutch D is greater than the elastic force of the return springs 77F, 77R, the forward and backward clutch D will become a double-engaged state, and the non-output side clutch assembly 60 will gradually Wear and tear. Therefore, by giving the piston returning force of the return springs 77F, 77R as described above and adding a large elastic force of the centrifugal force, the connection state of each of the clutch assemblies 6〇, 6〇 of the retracting and disengaging person 21 can be smoothly released. β, on the other hand, if the piston returning force of the return springs 77F, 77R is given as described above plus the large elastic force of the centrifugal force, when the clutch assembly 6 is disconnected from the disconnected state, the current flowing through is generated to be larger than The electromagnetic force (10) or hemp of the elastic force (thrust) of the springs 77F, 77R is returned, and the time is slightly shorter than the initial output of the stroke time of the piston 78F'78R. Thereby, the actuation of the pistons 78f, 78r can be started with a thrust greater than the elastic force of the rebound springs 77F, 77R in the non-connected state of the incoming and outgoing crying n + you pass I, and then can be reversed by The elastic force of the springs 77F, 77R can be obtained, and the clutch return pressure (reaction force) can be substantially equal. The pressure of the clutch group #6〇, 6〇 is gradually supplied to exceed the reaction pressure, and the pressure of the force is increased, so that the forward and reverse clutch D For the connection status. In this manner, the transmission torque in the non-connected state of the forward/reverse clutch D can be substantially increased until the pistons 78F and 78R are actuated to connect the advancing and retracting device D. ° Further, the boost pressure from the unactuated piston of the hydraulic clutch D is corrected by the input rotational speed of the clutch input shaft 2 (the input shaft rotational speed can be obtained by using the engine rotational speed and the reduction ratio). The reason is as follows. Also, since the torque of the clutch wheel 2 caused by the aforementioned hydraulic pressure and the thrust caused by the centrifugal force are transmitted to the piston 78F'7, the input torque of the clutch input shaft 2 is supplied only. The pressure does not give the predetermined clutch connection torque. If the above-mentioned engine rotation or the speed of the clutch input shaft 2 is used to correct the thrust of the forward and reverse clutch D t connection, the difference in engine speed caused by the difference in engine speed during the operation of the forward and reverse clutch D can be corrected. Even when the forward and reverse clutch D is actuated, even if the elastic force with respect to the return springs 77F, 77R is added, the thrust generated by the maximum rotational speed of the clutch input shaft 2 of the heart force and the increase in the value of the supply oil are stolen. When the elastic forces of the moving springs 77F and 77R are substantially the same, the enthalpy is started, and the configuration is such that the change in the repeated force change is gentle and the hydraulic pressure is gradually increased, and the smoothing can be performed smoothly. The above-mentioned gradual increase in the proportion of oil sputum is about 1 kgf/cni2 per 〇5 to 丨2 〇. Thus, when the forward and reverse clutch D starts to act, if it can be lifted from the dust force which is substantially equal to the elastic force of the spring nut The pressure can be smoothed 'even if the forward and reverse clutch 0 is actuated to reduce the pressure change of the clutch assembly (9). Further, in the configuration in which the hydraulic pressure control pressure of the forward/reverse clutch D is determined in accordance with the operation position of the clutch pedal 119, the engine oil control waste force is corrected to be lower as the engine speed is higher. This is due to the influence of the centrifugal force ^ engine turn (four) high piston 78F, the greater the transmission torque of the collapse, the harder to push the direction of the pavilion to stop the action. ° 'When the engine is high speed 2 output torque also becomes larger, beyond the engine torque When the clutch is engaged, the shifting speed == the light effect is also less significant. Therefore, with the above configuration, the transmission torque can be suppressed when the engine is rotated at a high speed. The body can also be operated according to the centrifugal force 119. The operation is not shown to perform the vehicle forward, neutral, forward and backward switching lever 115' according to the preset advance and retreat operation amount and the device Connection or non-connection relationship curve (not shown), so that the speed of the clutch input shaft 2 when the oil pressure is boosted by 23 1331107 (the speed of the input shaft 21 can be obtained by using the engine speed and the reduction ratio) . from. The operation of the pedal 8 will be used to operate the foot with the feeling of the vehicle starting to move in a human sense. If the foot is operated and the centrifugal force is repaired; the engine speed change caused by the load change on the start of the walking and the throttle operation and the clutch operation are all corrected, and even the control system that requires no complete reaction delay is required to "highly" in order to achieve such a demand. Control system. In contrast, in use, c & oil pressure control by the upper extension and retraction 11 5 is artificially processed in the artificial operation section 'only in the advance and retreat rod 115 < control according to the centrifugal force correction, can provide low price and feel good The system. The heavier the engine speed, the lower the correction pressure of the oil pressure control pressure of the forward and reverse clutch 造成 caused by the centrifugal force. Further, the correction of the hydraulic pressure control pressure is corrected only by the low pressure, and at least the pressure is not corrected after the pressure rises. The reason is that if the torque applied to the input shaft 2 of the clutch is different at the time of the subtle torque control, the impact at the time of shifting becomes large, but the pressure is not required. Thus, the calculation of the hydraulic pressure control pressure is performed only when necessary. Females Conversely, this correction can also be made in the full oil pressure control domain. At this time, the thrust caused by the centrifugal force becomes auxiliary. Even if it is performed in the full oil pressure control domain, the control current can be suppressed and energy can be saved. In addition, the suppression of the pressure (current) has the effect of saving energy. The sub-low oil can obtain the tractor and the like, and the control unit can control the vehicle with better precision than the I know. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view of a transmission device of the tractor of FIG. Figure 3 is a diagram showing the power transmission diagram of the hydraulic circuit of the power transmission diagram of Figure 2. Fig. 4 is a view showing the configuration of the hydraulic clutch of the θ,,,, π 圯 刀 knife switch of the shifting device of Fig. 2; Figure 5 is a control block diagram of the hydraulic clutch for the forward and reverse power switch of the wheat speed device of Figure 2; Fig. 6 is a view showing the relationship between the pedal depression position of the tractor of Fig. 2 and the operating pressure of the hydraulic clutch for the forward and backward power switch. Fig. 7 is a view showing the relationship between the correction value α and the engine speed caused by the centrifugal force when the hydraulic clutch for the forward and reverse power switch of the variable device of Fig. 2 is actuated. [Main component symbol description] 1 Engine shaft 2 Input shaft 3 Output shaft 62 Engine 65 Gearbox 76 Clutch assembly 77F, 77R Return spring 78F, 78R Piston 100 Control device 112 Engine speed sensor 115 Forward and reverse switching lever 25 1331107 119 Clutch pedal A Main gear B High and low gear C Vice gear D Forward and reverse clutch T Tractor body 26

Claims (1)

1331107 Application No. 096133648 Replacement Patent Application Range (May 99) X. Application Patent Range: 1. A traveling vehicle with: engine (62); hydraulic clutch (D), which passes through the clutch cylinder (85) The hydraulic oil pressure is adjusted to continuously change the connection state of the engine (62) from the non-connected state to the connected state; the power transmission mechanism (A, B, C) 'is the hydraulic clutch (D) Power operation in the connected state; The clutch operating means (1 15,1 19) is used to adjust the hydraulic pressure of the hydraulic oil to make the hydraulic clutch (D) into a connected state or a non-connected state; the return spring (77F, 77R) is operated without oil pressure In the state of the hydraulic clutch (D), the elastic force is applied to the hydraulic clutch to make it unconnected; and the hydraulic control device (100) is applied to the hydraulic clutch (D) in the non-connected state. When the hydraulic pressure is used, the output is greater than the return spring at a given time. 77R) The hydraulic pressure of the elastic force, and then output the oil pressure which is approximately the same as the elastic force of the return spring (77F, 77Rj) and then gradually output the oil pressure greater than the elastic force of the return spring (7?F, claw) The pressure makes the oil house clutch into the state; the soldier is characterized by: the rotation of the engine (62) is set to rotate the clutch shaft (2), and the oil pressure control device is provided (1〇5 into 1 Ding well out, thus clutching:: and A (85) The clutch cylinder generated by the rotation. a. If the centrifugal force of the oil is changed by the force of the oil, the oil pressure is adjusted according to the knife of the oil moving away from the heart force, and the oil pressure of the hydraulic pressure clutch 27 1331107 (D) is activated. And the hydraulic pressure clutch (D) is actuated from the non-connected state to the connected state with the corrected hydraulic pressure. XI. Schema: For example, page 28 1331107 VII. Designated representative map: (1) The representative representative of the case is: (2) Diagram of the symbol of the representative diagram: 1 Engine shaft 2 Input shaft 3 Output shaft 4 PTO linkage shaft 5 Front wheel output shaft 6 Traveling auxiliary shaft 7 Front wheel drive shaft 8 Rear countershaft 9 PTO pair Axis 10. Rear differential shaft 11 Rear axle 12 Front differential shaft 13 Front axle 14 PTO shaft 15 Gear drive shaft 17 Gear drive shaft 18 PTO shifting shaft 19 Main shifting shaft 20 Vice shifting shaft 21 Submersible countershaft 22 PTO forward and reverse switching Axis 23 PTO deceleration shaft 1331107 24 PTO reversing countershaft 25 front wheel linkage rut 2 6 input shaft 27 28 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48 Auxiliary shifting auxiliary shaft front wheel linkage shaft input gear ΡΤΟ shifting gear main shifting gear high and low speed switching gear pair shifting gear · front wheel take-up gear ΡΤΟ forward and reverse switching Gear pair transmission countershaft gear main gear sub-shaft gear high and low speed switching gear front wheel drive switching gear forward and backward switching gear rear countershaft gear ΡΤΟ speed countershaft gear rear differential device differential ring gear front differential device input gear submerged countershaft gear 5 49 1331107 50 PTO reduction gear 5 1 Front wheel linkage gear 52 PTO reverse countershaft gear 53 Drive pinion 54 Front wheel linkage gear 55 Front wheel gear 56 Switching 59 Countershaft 60 Forward and backward 61 Front wheel 62 Engine 63 Rear wheel 66 Clutch 67 Front wheel 76 Clutch A power B power C power D hydraulic drive countershaft gear shift clutch assembly component drive clutch assembly unit transmission mechanism transmission mechanism transmission mechanism clutch eight, in this case, if there is a chemical formula, please reveal the chemical formula that best shows the characteristics of the invention: C ( No) 6