JP2005119662A - Traveling transmission device for combine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To make the right and left weight balance of a traveling transmission device for a combine sufficient while smoothly carrying out differential turning even in a crawling speed traveling state. <P>SOLUTION: A rotation driving force is inputted to a shaft (45) of a differential mechanism (50) in a transmission case (1) from a hydraulic speed change device (16) for traveling arranged at one side of right and left sides of the transmission case (1). Whereas, the rotation driving force is inputted to a receiving gear (55) at the outer periphery of the differential mechanism (50) from the hydraulic speed change device (61) for turning arranged at the other side of the right and left sides of the transmission case (1) through a control shaft (56) in the transmission case (1). Further, inputs of the rotation driving force from the hydraulic speed change device (16) for traveling and the hydraulic speed change device (61) for turning are synthesized by the differential mechanism (50) and outputted. Thereby, right and left axles (37, 37') are differentially moved and can be turned. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention belongs to a technical field related to a traveling drive device for a combine.

As a conventional combine traveling transmission device, for example, one disclosed in Patent Document 1 is known.
JP-A-4-103472

  However, since the combined transmission disclosed in the above-mentioned Patent Document 1 uses a belt-type transmission as a turning transmission, the belt transmission varies depending on the operation amount of the steering operation tool. However, if the belt transmission is not driven to rotate in the running state, the belt transmission consisting of this split pulley cannot be shifted, and in the low speed running state, There is a drawback in that the speed change operation of the belt transmission device is not performed smoothly and the turning cannot be performed accurately.

In order to solve the above-mentioned problems, the present invention takes the following technical means.
That is, a rotational driving force is applied to the shaft (45) of the differential mechanism (50) in the mission case (1) from the traveling hydraulic transmission (16) disposed on the left and right side of the mission case (1). And the differential from the turning hydraulic transmission (61) disposed on the left and right other side of the mission case (1) via the control shaft (56) in the mission case (1). The rotational drive force is input to the passive gear (55) on the outer periphery of the mechanism (50), and the rotational drive force input from the traveling hydraulic transmission (16) and the turning hydraulic transmission (61) is input to the differential mechanism (50). ), The combined transmission is transmitted and output, and the left and right axles (37, 37 ′) are made to be differential so that they can turn.

  According to the present invention, by using the hydraulic turning hydraulic transmission 61 instead of the belt transmission, it is possible to satisfactorily adjust the rotation of the differential mechanism 50 even in the slow speed running state, and to smoothly turn. Can be done.

  Further, it is possible to improve the left and right weight balance of the combined traveling transmission device including the mission case 1, the traveling hydraulic transmission device 16, and the turning hydraulic transmission device 61.

  An embodiment of the present invention will be described with reference to the drawings. Reference numeral 1 denotes a transmission case of a traveling device for a working machine such as a combine, and an input shaft 2 is provided horizontally at an upper position, and rotation from the engine is transmitted to the input shaft 2. An input pulley 3 is provided, a large gear 4 and a small gear 5 are loosely fitted to the input shaft 2 in the transmission case 1, and a speed increasing clutch 6 is provided between the large gear 4 and the small gear 5 and the input shaft 2. Provide. The speed increasing clutch 6 fixes a rotating drum 8 to the input shaft 2, and a partition member 9 that rotates integrally with the rotating drum 8 is provided at the center of the rotating drum 8. 11, pistons 12 and 13 are provided in the cylinder chambers 10 and 11, and a clutch disk provided on the inner periphery of the rotary drum 8 and a clutch disk provided on the large gear 4 and small gear 5 side are contacted and separated. It is configured so that A connecting rod 14 connects the piston 12 and the piston 13. Therefore, a hydraulic main transmission (hydrostatic transmission (travel hydraulic transmission)) 16 is provided on the side of the transmission case 1. The hydraulic main transmission 16 has a transmission shaft 15 as an input shaft of the HST pump 17 mounted on the transmission case 1, and an input gear 18 that always meshes with the large gear 4 is fixed to the transmission shaft 15. Reference numeral 19 denotes an HST motor of the hydraulic main transmission 16, which is connected to the HST pump 17 by an oil passage 20. The hydraulic main transmission 16 operates the HST pump 17 by the rotation of the transmission shaft 15, and the HST pump 17 supplies oil to the HST motor 19 while increasing or decreasing the oil supply amount steplessly to transmit the rotation. Reference numeral 23 denotes a main shift on / off clutch provided between the HST motor 19 and the output transmission shaft 22; 24, a transmission gear which is always meshed with the small gear 5 provided on the output transmission shaft 22, and 25 is a transmission drive gear.

  Reference numeral 26 denotes an auxiliary transmission shaft. A small gear 27 and a large gear 28 which are integrally formed are attached to the auxiliary transmission shaft 26 so as to be slidable. The small gear 27 and the transmission drive gear 25 or the large gear 28 and the transmission gear 24 are provided. Is selected (this is the auxiliary transmission mechanism S). Reference numeral 29 denotes a driving gear fixed to the auxiliary transmission shaft 26, and 30 denotes a passive gear fixed to the side clutch shaft 31, which is always meshed with the driving gear 29. Side clutch gears 32, 32 having left and right inner teeth (not shown) formed on the left and right sides of the passive gear 30, and side clutch shafts 31 having pawl portions (not shown) that are separable from the left and right inner teeth. 'Is slidably mounted, and left and right side clutches 33 and 33' are formed by the left and right inner teeth of the passive gear 30 and the claw portions of the side clutch gears 32 and 32 '. 34 and 34 'are shifters, 35 and 35' are cylinders, 36 and 36 'are solenoids of the cylinders 35 and 35', 37 and 37 'are axles, and 38 and 38' are always meshed with the side clutch gears 32 and 32 '. The gears. Accordingly, left and right output shafts 45 and 45 'divided into left and right are respectively mounted in the vicinity of the side clutch shaft 31, a left gear 46 is fixed to the left output shaft 45, and the right output shaft 45' is fixed to the right output shaft 45 '. The right gear 46 'is fixed, the left gear 46 always meshes with the gear 48 that rotates integrally with the side clutch gear 32, and the right gear 46' always meshes with the gear 48 'that rotates integrally with the side clutch gear 32'. . The output shafts 45 and 45 'between the left gear 46 and the right gear 46' are provided with a differential mechanism 50 for changing the rotational speed of the output shafts 45 and 45 '. The differential mechanism 50 is provided with a case 51 in the mission case 1 so as to be freely rotatable. The ends of the output shafts 45 and 45 ′ face the case 51, and the left and right bevel gears are disposed at the ends of the output shafts 45 and 45 ′. 52, 52 'are provided so as to face each other, and the intermediate bevel gears 54, 54' rotatably attached to the shafts 53, 53 'fixed to the case 51 are meshed with the left and right bevel gears 52, 52', respectively. A passive gear 55 is provided on the outer periphery of the case 51, and a drive transmission gear 57 fixed to the control shaft 56 is always meshed with the passive gear 55.

  The differential mechanism 50 is configured such that 2Z = X + Y, where X is the left output shaft 45, Y is the right output shaft 45 ', and Z is the case 51. That is, when the case 51 stops with respect to the left output shaft 45 and the right output shaft 45 ′, Z becomes 0, 0 = X + Y, and therefore X = −Y, X and Y are reversed from each other, and Y Y = 2Z-X. For example, if X is 100 and Z is 150, Y is 200, and Y is rotated twice as fast as X (the relationship between X and Y can be reversed). Therefore, a power steering hydraulic transmission (swivel hydraulic transmission) 61 that is actuated by a tilting operation of a power steering lever (steering operation tool) 60 is provided on the side of the transmission case 1. The control shaft 56 is configured to rotate and stop. The power steering hydraulic transmission 61 includes an HST pump 62 and an HST motor 63, the output transmission shaft 22 serves as an input shaft of the HST pump 62, and the control shaft 56 serves as an output shaft from the HST motor 63. Power steering clutches (devices) 64 and 65 are provided between the transmission shaft 22 and the HST pump 62 and between the control shaft 56 and the HST motor 63, respectively. Therefore, when the rotation of the case 51 is stopped by the power steering hydraulic transmission 61, the differential mechanism 50 can perform a spin turn that reverses the left and right axles 37 and 37 ', thereby causing the case 51 to perform the power steering hydraulic transmission. When the device 61 is rotated by a predetermined amount, a double-speed turn can be made by driving and rotating the axle on the outside of the turn faster than the axle on the inside of the turn.

  FIG. 5 shows a hydraulic circuit. A main switch lever 66 operated by the hydraulic main transmission 16 is provided with a differential switch 68 for operating the differential mechanism 50. The differential switch 68 is connected to the solenoid 36, by a relay 69. The operation of 36 'is reversed (FIG. 6). That is, the right side clutch 33 'is normally disengaged by the solenoid 36' during a right turn, but the left side clutch 33 is disengaged by the solenoid 36 and the right axle 37 'inside the turn is rotated at a constant speed during a double speed turn. Then, since the left axle 37 on the outer side of the turn is driven and rotated faster than the right axle 37 'on the inner side of the turn, the operations of the solenoids 36 and 36' are reversed. Reference numeral 70 denotes a lockup switch. When the lockup switch 70 is operated, the main shift on / off clutch 23 is disengaged, and the rotation of the input shaft 2 is increased by the speed increasing clutch 6 → the small gear 5 → the transmission gear 24 → the output transmission shaft. 22 → Transmission drive gear 25 → Small gear 27 → Sub-transmission shaft 26 → Drive gear 29 The rotation is directly transmitted without going through the hydraulic main transmission 16. FIG. 7 shows an embodiment relating to the operating mechanism of the power steering lever 60. The power steering lever 60 and the power steering hydraulic transmission 61 are connected, and the power steering lever 60 is moved left and right in the groove 71 as shown in FIG. When tilted, the left and right side clutches 33, 33 'are turned off, and the vehicle turns when it is tilted forward from this state. When it is tilted backward, a spin turn is performed (the combination of the tilt direction and the swing direction is arbitrary) Is). Reference numeral 72 denotes left and right crawlers of the traveling device. Further, when the power steering hydraulic transmission 61 is configured to operate due to the operation of the differential switch 68 and the on / off of the side clutches 33 and 33 ′ so as to operate when operated to perform a double speed turn, Horsepower loss for operating the power steering hydraulic transmission 61 can be avoided.

  FIG. 10 shows a configuration in which a brake mechanism 73 for stopping the case 51 of the differential mechanism 50 and a rotation mechanism 77 for rotating the case 51 with respect to the left and right output shafts 45 and 45 ′ are provided. Is provided with a brake case 74, and a disc that contacts and separates the brake case 74 and the control shaft 56 is provided to constitute the brake mechanism 73, and the drive transmission gear 57 is provided on the auxiliary transmission shaft 26. The transmission gear 76 is always meshed with the transmission gear 76 provided via the double speed turn clutch 75 and is transmitted to the rotational speed of the side clutch shaft 31 transmitted by the drive gear 29 and the passive gear 30 of the auxiliary transmission shaft 26. The rotation mechanism 77 is formed so that the differential mechanism 50 rotates fast by the engagement of the drive transmission gear 57 and the passive gear 55. Therefore, when the rotation of the case 51 is stopped by the brake mechanism 73, the differential mechanism 50 performs a spin turn that reverses the so-called left and right axles 37, 37 ′, and when the case 51 is rotated by the rotation mechanism 77 by a predetermined amount, A double speed turn can be made by driving and rotating the axle 37 'on the outside of the turn faster than the axle 37 on the inside of the turn. FIG. 11 shows a hydraulic circuit diagram of the second embodiment. Reference numeral 78 denotes an emergency stop switch provided on the main transmission lever 66, which operates the brake case 74 with the left and right side clutches 33 and 33 'disconnected. When the lockup switch 70 is operated, the lockup switch 70 not only locks up, but also sets the travel speed. When the speed drops below the set travel speed, the lockup switch 70 automatically opens the throttle at the set travel speed. In the automatic running speed control, when the maximum output state of the engine or the set running speed continues for a set time, the vehicle may be automatically locked up at the vehicle speed at that time. 79 is a throttle sensor, 80 is an engine speed detection sensor, and 81 is a speed sensor (FIG. 12). In FIG. 11, 82 is a hydraulic pressure adjustment valve that sets the initial hydraulic pressure of the hydraulic circuit. If the initial hydraulic pressure is set higher by the hydraulic pressure adjustment valve 82, the operation of each cylinder and the like is accelerated. Can do. And although illustration is abbreviate | omitted, the traveling apparatus is provided with the rolling mechanism which leveles an airframe with respect to the inclination of a field, the left-right horizontal sensor 83 which detects the oil pressure of the rolling cylinder which operates this mechanism is provided, When the weight is heavy, the pressure is raised by the hydraulic pressure adjusting valve 82, and when the weight is light, the pressure is lowered. Reference numeral 84 denotes a cereal sensor, which senses the presence / absence of the work of the cutting part, and makes the oil pressure zero by the oil pressure adjusting valve 82 during the work so as not to make a spin turn. Reference numeral 85 denotes an inclination sensor, which is not spin-turned when the aircraft is inclined more than a predetermined angle. Reference numeral 86 denotes an airframe subsidence sensor, and when the aircraft sinks, the turning torque increases, so that the pressure is increased by the hydraulic pressure adjusting valve 82. Reference numeral 87 denotes a front / rear balance sensor. When the front side is heavy, turning is not easy, so the pressure is increased. When the rear side is heavy, the pressure is decreased. Reference numeral 88 denotes a left / right balance sensor, which increases the pressure of the hydraulic pressure adjustment valve 82 when either the left or right heavy side of the airframe is outside the turning during turning.

  Next, the operation will be described. The rotation from the engine is transmitted to the input pulley 3, the rotation of the input shaft 2 rotated by the input pulley 3 is transmitted to the large gear 4 via the speed increasing clutch 6, and the large gear 4 is always meshed with the input gear 18. The input gear 18 rotates the transmission shaft 15, and the transmission shaft 15 operates the HST pump 17 of the hydraulic main transmission 16 to send oil to the HST motor 19 to transmit the rotation. The rotation is transmitted to the side clutch shaft 31 via the main transmission on / off clutch 23 → the output transmission shaft 22 → the transmission drive gear 25 → the small gear 27 → the auxiliary transmission shaft 26 → the drive gear 29 → the passive gear 30. In normal traveling, the left and right side clutches 33 and 33 'are turned on, and the rotation of the side clutch shaft 31 is transmitted to the side clutch gears 32 and 32'. The side clutch gears 32 and 32 'are always meshed gears 38, 38 'is rotated, and the gears 38, 38' transmit the rotation to the axles 37, 37 'to drive the traveling device to travel. Then, when one of the left and right side clutches 33, 33 'is turned off, the left side clutch 33 turns as the inside of the turn.

  Thus, when one of the left and right side clutches 33, 33 ', for example, the right side clutch 33' is disengaged, the side clutch gear 32 'is in a free state and a right output provided with a right gear 46' meshing with the gear 48 '. The shaft 45 ′ is also free with respect to the case 51 of the differential mechanism 50. When the power steering hydraulic transmission 61 is operated for double speed turning, the power steering clutch 64 and the power steering clutch 65 are turned on correspondingly, and the rotation of the control shaft 56 causes the drive transmission gear 57 and the passive gear 55 to rotate. And transmitted to the case 51 of the differential mechanism 50. The differential mechanism 50 is configured such that 2Z = X + Y where X is the left output shaft 45, Y is the right output shaft 45 ', and Z is the case 51. When Z is 150, Y becomes 200, and Y is rotated twice as fast as X. In this way, by rotating the power steering lever 60 in a stepless manner through the power steering hydraulic transmission 61 by tilting the power steering lever 60, the axle on the outside of the turn is driven to rotate faster than the axle on the inside of the turn. You can make double speed turns. That is, when turning left, the right crawler is on the outside of the turn, so the corresponding right side clutch 33 'is turned off, and the side clutch gear 32', gear 48 ', right gear 46', and right output shaft 45 'are turned off. Is made free with respect to the case 51, the right output shaft 45 ′ (Y side) rotates faster than the left output shaft 45 (X side) by the rotation of the case 51, and a double speed turn can be performed.

  Further, when the case 51 is stopped with respect to the left output shaft 45 and the right output shaft 45 ′ by the power steering hydraulic transmission 61, Z becomes 0, 0 = X + Y, and therefore X = −Y. Since Y reverses each other, when one of the left and right side clutches 33, 33 ′, for example, the right side clutch 33 ′ is disengaged, the corresponding right output shaft 45 ′ becomes free with respect to the case 51 and left The rotation of the output shaft 45 is reversely rotated by the differential mechanism 50 and transmitted to the right output shaft 45 ′, and the rotation of the right output shaft 45 ′ is transmitted to the right gear 46 ′, the gear 48 ′, the side clutch gear 32 ′, and the gear 38. So that the left axle 37 and the right axle 37 'rotate in the opposite directions to make a so-called spin turn. Thus, since the power steering hydraulic transmission 61 can operate the control shaft 56 to stop rotating and shift with the power steering lever 60, as described above, the power steering lever can be used to turn left and right, double speed turn, and spin turn. 60 can be done. Note that when the left clutch 33 of the left and right side clutches 33, 33 ′ is disengaged during normal travel, the other side turns by the driving force on the Y side, but at this time, the crawler returns to the opposite side on the X side. Since 2Z = X + Y is rotated by constant speed drive Y and X rotated by contact resistance, Z ≠ 0 and the case 51 of the differential mechanism 50 is operated to rotate. At this time, the HST motor 63 is operated. If is turned off, the case 51 rotates freely. In this case, if Z = Y / 2, X = 0. Thus, when the left clutch 33 is disengaged and the case 51 is rotated with respect to Y by the power steering hydraulic transmission 61, the X side is completely set. Turn while stopped. Further, when the power steering hydraulic transmission 61 is activated when one of the left and right side clutches 33, 33 'is operated, the output loss of the engine is prevented and the durability is improved.

  Therefore, in the second embodiment, instead of the power steering hydraulic transmission 61, the transmission gear 76 provided on the auxiliary transmission shaft 26, the drive transmission gear 57 meshed with the transmission gear 76, and the drive transmission gear 57 The case 51 rotates faster than the left and right output shafts 45 and 45 ′ corresponding to X and Y by the speed increasing ratio of the meshing passive gear 55, and can make a double speed turn. Further, by stopping the rotation of the control shaft 56 by the brake mechanism 73, the rotation of the case 51 is stopped, and the left output shaft 45 and the right output shaft 45 'are rotated in the reverse direction to perform a spin turn.

  As described above, the differential mechanism 50 not only allows the left and right axles 37 and 37 'to be rotated in the reverse direction, but also makes a double-speed turn by driving and rotating the axle on the outside of the turn faster than the axle on the inside of the turn. The

The longitudinal cross-sectional schematic of the unfolding state of a mission case. The same side view. FIG. Schematic of the operating mechanism. Hydraulic circuit diagram. circuit diagram. Perspective view. Power telebar configuration diagram. Action state diagram. FIG. Hydraulic circuit diagram of the second embodiment diagram. The block diagram of 2nd Example figure.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Mission case 16 Hydraulic transmission for driving 37 Axle 37 'Axle 45 Axle 50 Differential mechanism 55 Passive gear 56 Control shaft 61 Hydraulic transmission for turning

Claims (1)

  A rotational driving force is input to the shaft (45) of the differential mechanism (50) in the mission case (1) from the traveling hydraulic transmission (16) arranged on the left and right side of the mission case (1). In addition, the differential hydraulic mechanism (61) disposed on the left and right sides of the mission case (1) is connected to the differential mechanism (61) via the control shaft (56) in the mission case (1). 50) A rotational driving force is input to the outer peripheral passive gear (55), and the rotational driving force from the traveling hydraulic transmission (16) and the turning hydraulic transmission (61) is input by the differential mechanism (50). A combined traveling transmission device characterized in that the combined left and right axles (37, 37 ') can be rotated by being synthesized and output.

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