JP4517286B2 - Cylinder controlled toroidal transmission - Google Patents

Description

  The present invention comprises a piston-type cylinder (also simply referred to as a “cylinder”) that includes a power roller between input and output disks and adjusts the power roller to advance and retreat, and a cylinder-controlled toroidal transmission that continuously transmits input power. It relates to a transmission device.

  As shown in Patent Document 1, a cylinder-controlled toroidal speed change transmission device that is applied to a work vehicle such as a tractor and is provided in a transmission case that performs speed change control of power and continuously variable transmission is known. This cylinder-controlled toroidal speed change transmission device includes an input / output disk that is coaxially supported in parallel, a power roller that is interposed between opposing surfaces of the both, and a power roller that is driven forward and backward to drive the power roller. It is composed of a cylinder that adjusts the inclination angle, and can efficiently and continuously transmit traveling power in a wide speed range including forward and reverse rotations.

However, in order to obtain the target output speed, the cylinder-controlled toroidal speed change transmission device needs to hydraulically control the cylinder based on the speed change result obtained as the rotational speed of the output disk. Because it is governed by complicated hydraulic response characteristics until it is reflected as a result of transmission by the power roller's forward / backward movement, in order to achieve high-precision and high-speed control, strict manufacturing specifications and A high degree of motion adjustment is required, which entails a problem that a large cost burden is imposed.
Japanese Patent Laid-Open No. 10-132047

  The problem to be solved is to provide a cylinder-controlled toroidal transmission device capable of high-speed and high-speed transmission control with a simple configuration.

The invention according to claim 1 comprises an input / output disk ( 41, 42, 43 ) axially and concentrically supported in parallel, a power roller ( 44 ) that is interposed between both opposing toroidal surfaces, In a cylinder-controlled toroidal transmission device comprising a piston-type cylinder ( 44a, 44b ) that drives the power roller ( 44 ) forward and backward to adjust its inclination angle, the piston ( 85a ) of the piston-type cylinder ( 44a, 44b ) , the rear end of 85b), comprising a coupling rod (86) for detectably advance and retract its stroke, the coupling rod (86) is attached detachably to the rear end of the piston (85a, 85b) In addition, an oil passage opening (85e) for guiding the lubricating oil to the movable portions (44, 44r) of the power roller through the pistons (85a, 85b) is provided. Wherein the drilled to Rukoto the base of the coupling rod (86).
The rotational power of the input disk is transmitted to the output disk at a gear ratio according to the inclination of the power roller, and the inclination angle of the power roller is adjusted by the forward / backward drive of the piston by hydraulic oil control of the piston type cylinder. It is grasped via the interlocking rod. Moreover, it can respond to the structure which does not have an interlocking rod, and when an interlocking rod is mounted | worn, lubrication of a power roller is ensured by opening of a base.

The cylinder-controlled toroidal transmission device of the present invention has the following effects.
According to the first aspect of the present invention, the rotational power of the input disk is transmitted to the output disk at a gear ratio corresponding to the inclination of the power roller, and the inclination angle of the power roller is adjusted by the forward / backward drive of the piston by hydraulic oil control of the piston cylinder. At this time, an interlocking rod connected to the piston at the rear end of the piston-type cylinder and moving back and forth so that the stroke can be detected is provided, so that the piston position is grasped through the interlocking rod.
Therefore, when controlling the gear ratio, direct piston position control of the piston-type cylinder can be performed via the interlocking rod without depending on the speed change result obtained as the rotational speed of the output disk having complicated hydraulic response characteristics. Therefore, it becomes possible to directly obtain the target gear ratio in correspondence with simple, high-speed and high-precision piston position control.
In addition, it is possible to deal with components that do not have interlocking rods while sharing parts, and it is possible to perform common hydraulic control based on components that have interlocking rods by combining such components. For the mounted one, lubrication of the power roller is ensured by the opening of the base. Therefore, in a cylinder-controlled toroidal transmission device having a plurality of power rollers, high-precision gear shifting control can be performed at low cost while ensuring lubrication of the power rollers.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a side view of an agricultural tractor showing an example of a work vehicle to which a cylinder-controlled toroidal transmission device according to the present invention is applied. The agricultural tractor is equipped with an engine (not shown) in the front part of the airframe having a front wheel a and a rear wheel b, and the rotational power of the engine is transmitted to the transmission 1 and appropriately decelerated by the transmission 1. Power is transmitted to the front wheel a and the rear wheel b, and is also output to the work machine K via the rear PTO shaft k. In addition, for operation by the operator, a monitor m that displays a driving state on the front side of the steering wheel h, a forward / reverse switching lever (not shown) on the lower side, an accelerator lever, a brake pedal, an accelerator pedal and other levers and pedals, A cockpit q provided on the upper part of the transmission 1 and a shift lever (not shown) are arranged beside the cockpit q, and are configured to be automatically shiftable by a control unit (not shown).

  As shown in FIG. 2, a sectional view of the main axis of the transmission gear transmission 1 includes a transmission case 2, a front case input shaft 3, a work transmission shaft 4, a travel transmission shaft 5, and an intermediate work intermediate shaft. 6. The front wheel output shaft 7 and the like are supported in parallel in the front-rear direction, and necessary transmission mechanisms are respectively configured to shift the received engine power to the traveling system and the working system. The transmission case 2 is made of a casting, and includes a front case 2a, a mid case 2b, and a rear case 2c. The front case 2a has a metal partition that is divided into front and rear sections A and B so as to cross the inside. A wall 9 is formed.

  The case input shaft 3 is supported by the front end portion of the transmission case 2 and receives engine power. The work transmission shaft 4 is provided with a gear 4a receiving power from the case input shaft 3 at the front end, extends rearward so as to pass through the partition wall 9 and run through the transmission case 2, and has a work transmission control at the rear end. A PTO clutch 12 or the like is provided as a part.

  The traveling transmission shaft 5 is provided with a gear 5a that receives rotational power in the same direction from the case input shaft 3 on the front stage side, a variator 21 by a cylinder-controlled toroidal transmission device, a planetary differential section 22 following the rear side of the partition wall 9, A high / low switching unit 23 composed of two HiLo clutches, a drive pinion 24 and the like are provided on the same axis.

  The work intermediate shaft 6 includes a switching unit 31 that switches from the middle position of the transmission case 2 to the rear end and switches the rotation direction of the work intermediate shaft 6 in the forward and reverse directions. The switching unit 31 switches the rotational direction of the power transmitted to the front portion of the work intermediate shaft 6 via the PTO clutch 12, and transmits the normal rotation power or the reverse rotation power.

  The front wheel output shaft 7 is provided with a gear 7a for receiving branching power from the rear stage portion of the traveling transmission shaft 5 at the rear end portion, and at the front portion is provided with a front wheel speed increasing clutch 32 for switching speed increase by hydraulic control. Front wheel power is output to the front part of 2.

  The variator 21 provided in the traveling transmission shaft 5 is arranged in the front section A of the mission case 2 with a pump 21a that supplies the dedicated hydraulic oil as a separate arrangement. This speed change transmission mechanism is constituted by a cylinder-controlled toroidal speed change transmission device, and includes two front and rear input disks 41 and 42, an output disk 43 disposed between them, and a toroidal curved surface having an annular concave surface. And a power roller 44... Interposed between these opposing surfaces at an equally divided interval of 120 °.

  The front input disk 41 is pivotally supported by the traveling transmission shaft 5 while receiving the end load hydraulic pressure in the axial direction from the end load drum 40, and the output disk 43 has a sleeve-like transmission member 45 extending rearward. By supporting the traveling transmission shaft 5 and the rear input disk 42 on the transmission member 45, continuously variable transmission power corresponding to the inclination angle of the power rollers 44 is provided by the output disk 43. Output. Each power roller 44 is provided with a master cylinder 44a or a slave cylinder 44b, which will be described later, and the inclination angle is controlled by the advance / retreat position, and dedicated hydraulic oil is received through an oil passage formed in each cylinder rod 44s. Ensure transmission.

  The planetary differential portion 22 is configured around a shaft end member 51 that is integrally attached to the rear end portion of the traveling transmission shaft 5. The shaft end member 51 is connected to the input disk 42 on the rear side and rotates together with the satellite gear 53 as a satellite carrier. The shaft member 51 includes a transmission member 45 that transmits the rotational force of the output disk 43 to the satellite gear 53. Receive through sun gear. At the rear stage of the satellite gear 53, the inner and outer transmission members 54, 55 that output the second speed differential power including the reverse rotation stop region are meshed and transmitted, and one of them is input to the high / low switching unit 23 by hydraulic operation for reverse rotation. By doing so, a continuous shift output is transmitted to the drive pinion 24 with the same rotational direction when switching the second-speed differential power. A travel output shaft 56 is arranged on the same axis line behind the inner transmission member 54 at the rear stage of the height switching unit 23.

  The PTO clutch 12 at the rear end of the work transmission shaft 4 is a transmission control unit that connects and disconnects the work system power by hydraulic control, and a switching unit 31 is provided to transmit to the work intermediate shaft 6 so that a forward / reverse output can be selected from the subsequent stage. Constitute. Further, intermediate gears 8a and 8b receiving branching power from an extension shaft 56e connected to the rear stage of the travel output shaft 56 are supported on the work intermediate shaft 6, and a gear 7a receiving rotational force of the intermediate gears 8a and 8b is output to the front wheels. By providing the shaft 7, the traveling power is branched from the traveling output shaft 56 and transmitted to the front wheel output shaft 7.

  The hydraulic system of the transmission system supplies hydraulic oil individually by configuring the hydraulic system for each of the sections A and B partitioned forward and backward by a partition wall 9 traversing the transmission case 2. The hydraulic system in the front section A has jurisdiction over the variator 21 at the front stage of the traveling transmission shaft 5 that requires a dedicated hydraulic oil (first hydraulic oil), and the hydraulic system in the other section B has a common hydraulic oil (first hydraulic oil). The second stage oil) has jurisdiction over the rear part of the traveling transmission shaft 5 and other transmission devices of the work machine system.

  The hydraulic system of the variator 21 constituted by the cylinder-controlled toroidal transmission will be described in detail. As shown in the hydraulic system diagram including the work vehicle components in FIG. The dedicated hydraulic fluid is supplied from the shaft end of the cylinder rod 44s of the hydraulic cylinders 44a and 44b. With this hydraulic oil, lubrication and cooling are performed in order to ensure transmission between the input disks 41 and 42 and the output disk 43.

  The master cylinder 44a is applied to one of the three power rollers 44 on the front side and the rear side of the output disk 43, and the other two are applied to the slave cylinder 44b. In order to control the expansion and contraction operation of these cylinders, electromagnetic proportional pressure reducing valves 61 and 61 for controlling the hydraulic oil from the pump 21a are provided, and a set pressure variable reduction valve that receives hydraulic pressure from the electromagnetic proportional pressure reducing valves 61 and 61 to the pilot piston. 62 and 62 are provided symmetrically in both directions of expansion and contraction, and hydraulic oil is supplied to the master cylinders 44a and 44a via the large-diameter dampers 44d and 44d and the check valves 44c and 44c, respectively, and a small-diameter damper is supplied from the master cylinders 44a and 44a. The slave cylinders 44b are interlocked and controlled via 44e, and the power roller 44 is driven forward and backward to control the transmission inclination angle. The large-diameter damper 44d is called a mode 1 damper and prevents hydraulic vibration due to the axial deflection of the travel transmission shaft 5, and the small-diameter damper 44e is called a mode 3 damper and prevents hydraulic pipe vibration between pistons.

  Further, by providing a shuttle valve 63 for receiving expansion / contraction control pressure and supplying the high pressure side thereof to the end load of the variator 21, the hydraulic pressure is linked to the operating pressure of the hydraulic cylinders 44a and 44b, and the internal piston for the end load is used. Supply to R1. The shuttle valve 63 ensures the responsiveness by pilot control based on the end load pressure, and prevents the overload pressure as substantially the same pressure as the higher one of the cylinder pressures while rolling the power rollers 44. Adjust pressure. These dedicated hydraulic fluids are circulated only in the front compartment A.

  The hydraulic system using other general hydraulic oil is used for controlling the work system of the work transmission shaft 4 such as the range of the rear section B of the transmission case 2, that is, the front wheel drive transmission clutch 32 at the rear stage of the travel transmission shaft 5. Lubricating and hydraulic control of equipment such as the PTO clutch 12 and the brake hydraulic control cylinder 71, working equipment lifting hydraulic cylinder 72, working equipment rolling hydraulic cylinder 73, power steering cylinder 74, and other working actuator pumps The supply is controlled by 70. Further, the high / low switching unit 23 using the HiLo clutch at the rear stage of the travel transmission shaft 5 performs the Hi-Lo switching shift by supplying the control hydraulic pressure from the hydraulic control valves 76 and 76 to the travel output shaft 56 at the subsequent stage.

  The hydraulic cylinder of the cylinder-controlled toroidal transmission will be described in detail. First, as shown in the longitudinal sectional view of FIG. 4, the master cylinder 44 a has a cylinder cavity 81 disposed in the mission case 2. 81c is drilled through. A front bushing 83b fixed to a retaining ring is fitted into the reduced diameter portion of the front end (left side of the figure) of the cylinder cavity 81c, and a liner member 82 is provided to form hollow pistons 85a and 85b described later therein. The cylinder rod 44s protrudes in front of the front bush 83b, and a roller holder 44h is attached. The power roller 44 is pivotally supported by a support shaft 44r.

  The cylinder block 81 is provided with a cylinder extension control oil passage 81f and a degeneration control oil passage 81b so as to communicate with the cylinder cavity 81c, and a large-diameter damper 44d and a small-diameter damper 44e are respectively provided in the oil passage. To intervene. The large-diameter damper 44d and the small-diameter damper 44e can be compactly configured by screwing from both sides and screwing and fixing in the oil passage. A rear cap 83r is provided on the rear side of the cylinder block 81 so as to close the cylinder cavity 81c. A lubricating chamber 83c adjacent to the cylinder cavity 81c and an introduction oil passage 83s are formed in the rear portion of the rear cap 83r, and a lubricating oil passage 81s communicating with the introduction oil passage 83s is formed in the cylinder block 81.

  In addition, a secondary oil passage 83f provided with a check valve 44c for guiding hydraulic oil branched from the extension control oil passage 81f only in the cylinder direction is communicated with the rear cap 83r to the rear side of the liner member 82. Further, a stroke sensor 84 such as a potentiometer for detecting the advance / retreat positions of the hollow pistons 85a and 85b is disposed at the cylinder rear position.

  In detail, as shown in the enlarged view of the main part of FIG. 5, the liner member 82 is formed with an enlarged diameter portion 82r at the rear end, and in the vicinity thereof, an opening / closing that defines the stroke rear end limit of the hollow pistons 85a and 85b. A control gate 82g that functions as a valve is opened. By adopting a configuration in which the axial position of the liner member 82 is fixed to the enlarged diameter portion 82r by a rear cap 83r via a shim 82s, the position of the liner member 82 can be adjusted only by removing the rear cap 83r.

  A hollow piston, in which two cylindrical members 85a and 85b are screwed in series in the front-rear direction, is slid on the inner peripheral portion of the liner member 82. The bush side of the spherical bearing 87 is fastened and fixed to an intermediate portion of the hollow pistons 85a and 85b, and a hollow bolt 88 is passed through the movable side of the spherical bearing 87, and a spherical surface is formed by a hollow cylinder rod 44s screwed with the hollow bolt 88. The bearing 87 is fastened and fixed. The cylinder rod 44s extends forward from the hollow portions of the hollow pistons 85a and 85b, and connects the holder 44h of the power roller 44 to the front end thereof. The hollow pistons 85a and 85b having the above-described structure are more stable in quality than the press-fitting structure having a quality problem due to sludge, and can be easily centered and ensure both sealing performance and assembling performance with the liner member 82. In addition, it is possible to configure a smaller diameter and more compact than the case where the cylinder rod 44s is inserted into the spherical bearing 87, and interference with the disk can be prevented.

  At the rear ends of the hollow pistons 85a and 85b, an interlocking rod 86 that extends and retracts integrally by a detachable screwing structure or the like is extended if necessary, and an opening 85e is formed at the base thereof to form the lubrication chamber 83c and the hollow piston 85a, It communicates with the interior of 85b. The interlocking rod 86 penetrates from the lubrication chamber 83c to the rear of the rear cap 83r and is connected to the stroke sensor 84.

Next, as shown in the longitudinal sectional view of FIG. 6, the slave cylinder 44b is configured in the same manner as the master cylinder 44a except for the system of the extension control oil passage 81f.
Specifically, the cylinder block 81 is formed with an extension control oil passage 81f provided with a small diameter damper 44e in communication with the cylinder cavity 81c without branching. The liner member 92 provided in the cylinder cavity 81c is in communication with the extension control oil passage 81f by forming an opening 92e at the rear end portion outside the stroke range of the hollow pistons 85a and 85b. A rear cap 93r is provided on the rear side of the cylinder block 81 so as to close the cylinder cavity 81c, and the rear cap 93r is fixed to the cylinder block 81 via an enlarged diameter portion 92r formed at the rear portion of the liner member 92. To do. The other members are configured in the same manner as described above, and the corresponding reference numerals are given and description thereof is omitted. In this way, the constituent members of the master cylinder 44a and the slave cylinder 44b can be shared.

  In the cylinder-controlled toroidal transmission having the above-described configuration, when the hydraulic oil is received by the extension control oil passage 81f of the master cylinder 44a and the slave cylinder 44b, the hydraulic oil is transferred from the large-diameter damper 44d or the small-diameter damper 44e to the rear end of the liner member 82. By acting on the side, the hollow pistons 85a and 85b operate on the extension side. At this time, the master cylinder 44a is moved to the extension side with the diversion of the auxiliary oil passage 83f provided with the check valve 44c.

  Further, when the hydraulic oil is received by the degeneration control oil passage 81b, the hydraulic oil acts on the front end side of the liner member 82 via the small diameter damper 44e, so that the hollow pistons 85a and 85b operate on the degenerate side. The position of the power roller 44 is changed by the forward / backward movement of the hollow pistons 85a and 85b, and the gear ratio is changed together with the inclination angle.

  By the advance / retreat operation of the power roller 44, the interlocking rod 86 connected to the rear part of the hollow pistons 85a, 85b integrally moves forward / backward, so that the stroke sensor 84 to be connected corresponds to the advance / retreat positions of the hollow pistons 85a, 85b. Thus, the advance / retreat position of the power roller 44 can be grasped.

  Therefore, when controlling the gear ratio, the position of the power roller 44 can be directly controlled via the interlocking rod 86 without depending on the speed change result obtained as the rotational speed of the output disk having complicated hydraulic response characteristics. This enables high-speed control with high accuracy.

  In the shift control, the lubricating oil received from the lubricating oil passage 81s reaches the lubricating chamber 83c from the introduction oil passage 83s of the rear cap 83r, and lubricates the spherical bearing 87 inside the hollow pistons 85a and 85b through the opening 85e. At the same time, lubricating oil is supplied from the hollow bolt 88 to the outer periphery of the power roller 44 through the cylinder rod 44s, and power transmission between the input / output disks 41, 42, 43 is ensured.

On the other hand, in the retracting operation of the master cylinder 44a, when the hollow pistons 85a and 85b reach the control gate 82g opened at the rear part of the liner member 82, the extension control oil passage 81f is closed, so that the position of the control gate 82g is changed. The hollow pistons 85a and 85b are forcibly stopped as the retraction limit. Due to the restriction action of the extension control oil passage 81f by the control gate 82g, the degeneration operation of the other slave cylinder 44b is regulated in conjunction with it.
Even when the interlock rod 86 and the stroke sensor 84 are eliminated and the slave cylinder 44b is configured by the blind rear cap 93r, the expansion and contraction can be controlled in the same manner as the master cylinder 44a by the interlock action.
In addition, the slave cylinder 44b having no interlocking rod can be used while sharing parts, and by combining such parts, common hydraulic control based on the master cylinder 44a having the interlocking rod can be performed. As for the master cylinder 44a, lubrication of the power roller is ensured by the base opening 85e. Therefore, in a cylinder-controlled toroidal transmission device having a plurality of power rollers, high-precision gear shifting control can be performed at low cost while ensuring lubrication of the power rollers.

Next, the output disk 43 will be described.
As shown in the enlarged vertical sectional view of the support portion of FIG. 7, the output disk 43 is spline-fitted to a sleeve-shaped transmission member 45 that is pivotally supported by the traveling transmission shaft 5, and the power roller 44 is positioned at the rear end position of the output disk 43. A diameter-enlarged portion 45a is formed in the transmission member 45 as a rear side roller fence that restricts the rolling range. Further, a diameter expanding collar 46 that enters the inner periphery of the front end of the output disk 43 as a front roller fence is fitted to the front end portion of the transmission member 45 and fixed by a retaining ring 46r. The front and rear roller fences formed by the diameter-enlarged collar 46 and the enlarged-diameter portion 45a of the transmission member 45 can regulate the rolling range of the power roller 44 and perform stable transmission, and the front-side enlarged collar 46 The output disk 43 can be fixed integrally while suppressing backlash due to the gap between the splines.

Next, the end load drum section will be described.
As shown in the enlarged vertical sectional view of FIG. 8, the end load drum section is spline-fitted with the end load drum 40 to the traveling transmission shaft 5 toward the upper transmission side (left side of the figure) of the input disk 41. The disc spring 96 and the disc spring seat 97 for biasing the disc toward the input disk 41 are fitted and slid on the boss 40b of the end load drum 40, and the spline fitting gear 5a is provided at the front end of the disc spring seat 97 to travel. The urging mechanism of the end load drum 40 is configured by being received by a lock nut 98 screwed and fixed to the transmission shaft 5.

  The end load drum 40 is formed in a ring shape with a flange 40g for receiving the disc spring 96, so that the disc spring 96 can be held at a predetermined position by an urging force. Can be prevented. Further, the spline of the traveling transmission shaft 5 is formed with a sliding margin of the end load drum 40 on the disk 41 side, so that the adjustment width of the lock nut 98 can be secured, and the end load drum 40 By restraining the length of the boss portion 41c, the disc spring seat 97 and the gear 5a can be brought into contact with each other to reliably transmit the urging force.

  As shown in the perspective view of FIG. 9, the input disk 41 is formed with fitting recesses 41 d that are easy to process on the outer peripheral portion of the upper surface 41 s in an equally divided manner. As shown in the perspective view of FIG. 2, the fitting protrusions 40p that can be fitted without gaps are formed by end milling, and are fitted together and assembled, thereby assuring the rotational force from the end load drum 40. Can tell.

It is a side view of the work vehicle of this invention. FIG. 3 is a cross-sectional view of an essential part of an axis development of the work vehicle transmission gear transmission. It is a hydraulic system diagram of work vehicle equipment. It is a longitudinal cross-sectional view of a master cylinder. It is a principal part enlarged view of FIG. It is a longitudinal cross-sectional view of a slave cylinder. It is a support part expansion longitudinal cross-sectional view of an output disk. It is an enlarged vertical sectional view of an end load drum part. FIG. 6 is a perspective view of the input disk 41 on the fitting side. It is a perspective view of the fitting side of an end load drum.

DESCRIPTION OF SYMBOLS 1 Shift transmission device 2 Mission case 5 Traveling transmission shaft 5a Gear 21 Variator 41, 42 Input disk 43 Output disk 44 Power roller 44a Master cylinder (hydraulic cylinder)
44b Slave cylinder (hydraulic cylinder)
44c Check valve 44d, 44e Damper 44s Cylinder rod 81 Cylinder block 81c Cylinder cavity 81s Lubricating oil passage 81b Degeneration control oil passage 81f Extension control oil passage 82s Shim 82 Liner member 82g Control gate 82r Expanded portion 83b Front bushing 83r Rear cap 83f Sub-cap Oil passage 83s Introducing oil passage 83c Lubrication chamber 84 Stroke sensor 85a, 85b Hollow piston (piston)
85e opening 86 interlocking rod 87 spherical bearing 88 hollow bolt 92 liner member 92r enlarged diameter portion 92e opening 93r rear cap a front wheel b rear wheel

Claims (1)

An input / output disk (41, 42, 43) axially supported in parallel and parallel, a plurality of power rollers (44) interposed between the opposing toroidal surfaces, and the power rollers (44) In a cylinder-controlled toroidal transmission device comprising a piston-type cylinder (44a, 44b) that adjusts the inclination angle by driving forward and backward.
At the rear end of the piston (85a, 85b) of the piston-type cylinder (44a, 44b), an interlocking rod (86) that moves forward and backward to detect the stroke is provided .
The interlocking rod (86) is detachably attached to the rear end portion of the piston (85a, 85b), and lubricating oil is supplied to the movable portion (44, 44r) of the power roller via the piston (85a, 85b). cylinder controlled toroidal speed change transmission apparatus according to claim bored to Rukoto the base of the guide to the oil passage opening of the (85e) the coupling rod (86).

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