JP4592372B2 - Hydraulic PTO clutch with inertia braking mechanism - Google Patents

Description

  The present invention relates to a hydraulic PTO clutch with an inertia braking mechanism such as a tractor.

In the case of a tractor, a PTO propulsion shaft that is directly connected to the engine is linked to a PTO transmission shaft via a hydraulic PTO clutch with an inertia braking mechanism, and the PTO shaft for driving a work machine or the like is driven from this PTO transmission shaft. However, in the conventional hydraulic PTO clutch with an inertia braking mechanism, a plurality of pins (three) are welded to the clutch piston, and these pins penetrate through the cylinder chamber end wall of the clutch body. The brake plate is led out of the body, and a brake plate is connected to the lead-out end with a bolt (see Patent Document 1).
The clutch body is connected to a PTO transmission shaft, and a PTO transmission shaft and a PTO propulsion shaft are connected by operating a clutch piston fitted in the cylinder chamber of the clutch body in the clutch connection direction with hydraulic pressure. The At this time, the braked plate is separated from the brake disk (fixed and held in a part of the transmission case) by being connected to the clutch piston with a pin, so that the braking is released, and the PTO shaft from the PTO transmission shaft is released. It is comprised so that a work machine etc. can be driven via.

When the hydraulic pressure of the clutch piston is released, the clutch piston is returned to the clutch disconnection direction by the clutch spring, and the connection between the PTO transmission shaft and the PTO propulsion shaft is disconnected. At this time, the brake plate is configured to be braked by being pressed against the brake disc by the clutch spring and a brake spring provided separately from the brake spring, and to brake the inertia rotation of the PTO transmission shaft connected to the clutch body. ing.
The pin is a transmission member for causing the brake disc to be elastically pressed / separated from the brake disc in conjunction with the clutch disconnection / connection operation of the clutch piston, and a member for transmitting the braking force of the brake plate to the clutch body. It is something that doubles as well.
Japanese Patent Laid-Open No. 7-144549

  In the conventional hydraulic PTO clutch with an inertia braking mechanism, it is necessary to weld the clutch piston and one end of the pin (three pins) and to bolt the other end of the pin and the braked plate. In addition, pin support holes (three) must be formed through the cylinder end wall of the clutch body so as to coincide with the pin welding positions of the clutch piston, and bolt holes (three) are also provided in the brake plate. It was necessary to form a through-hole in conformity with the position. In other words, the welding position of the pin, the opening position of the pin support hole, and the opening position of the bolt hole need to be precisely machined with their circumferential positions coinciding with each other. In other words, the increase in the number of parts (in addition to the need for three bolts and a brake spring) and a complicated structure have been caused. Furthermore, seals (O-rings) are required (three places) to prevent oil leakage from the sliding parts (three places) between the pin support holes (three pieces) and the pins (three pieces) of the clutch body, The increase in the number of parts, the increase in processing and assembly man-hours, and the complexity of the structure have led to cost increases.

  The present invention has been developed in view of the above-described problems of a conventional hydraulic PTO clutch with an inertia braking mechanism, and its object is to achieve inertia braking that simplifies the structure, reduces the number of parts, and reduces costs. It is to provide a hydraulic PTO clutch with a mechanism.

In order to achieve the above object, the present invention provides a clutch mechanism that shuts off and connects a PTO propulsion shaft supported in a transmission case and a PTO transmission shaft to which power is transmitted from the PTO propulsion shaft, and is fixedly held in the transmission case. A clutch that slides within the clutch body when the clutch is disengaged, and the braked plate mounted on the clutch body so as to rotate integrally with the clutch body connected to the PTO transmission shaft. In the hydraulic PTO clutch having an inertia braking mechanism that brakes the PTO transmission shaft by applying pressure to the brake disc through a plurality of pins arranged at intervals in the circumferential direction by a return operation of the piston, in the clutch body The clutch piston, which is slidably inserted, has a small diameter inner periphery of the clutch body. And a large-diameter outer peripheral surface corresponding to the large-diameter inner peripheral surface of the clutch body, radially outside the cylinder chamber of the clutch piston and radially inward of the outer peripheral surface of the clutch body, A pin support hole that penetrates the clutch body in the axial direction from the step surface between the small-diameter inner peripheral surface and the large-diameter inner peripheral surface of the clutch body and slidably supports the pin is formed. A stepped surface corresponding to the stepped surface of the clutch body is formed between the small-diameter outer peripheral surface and the large-diameter outer peripheral surface and presses the pin toward the brake disc when the clutch is disengaged.
In addition, a clutch mechanism that cuts off and connects a PTO propulsion shaft supported in the transmission case and a PTO transmission shaft to which power is transmitted from the PTO propulsion shaft, and an approach and separation toward a brake disk fixedly held in the transmission case. A plurality of brake plates mounted on the clutch body so as to rotate integrally with the clutch body connected to the PTO transmission shaft are arranged at intervals in the circumferential direction by the return operation of the clutch piston when the clutch is disengaged. In a hydraulic PTO clutch having an inertia braking mechanism that brakes a PTO transmission shaft by applying pressure to a brake disc via a pin, the plurality of pins are slid on the clutch body at a position radially outside the cylinder chamber of the clutch piston. It is characterized by supporting it freely.

According to this configuration, the pin support portion of the clutch body that supports the plurality of pins is located away from the cylinder chamber to which the oil pressure to the clutch piston is supplied. No need to provide a seal (O-ring), processing of the seal groove can be omitted, assembly of the seal (O-ring) can be omitted, and the seal (O-ring) can also be omitted. Can be reduced.
Further, the pin is not connected to either the clutch piston or the braked plate, and contacts the clutch piston and the braked plate when the clutch is disconnected.

According to this configuration, the process of welding and bolting the three members of the clutch piston, the braked plate, and the pin can be omitted, and the mounting position accuracy (particularly the circumferential position accuracy) of these three members is exactly the same. In addition, since the clutch spring can also be used as a brake spring, the number of processing steps, the number of assembly steps, and the number of parts can be reduced.
Further, the clutch body and the braked plate are characterized in that concave and convex claws formed at a plurality of locations in the circumferential direction of the outer peripheral portion of both are engaged with each other.
According to this configuration, it is possible to simplify the structure in which the brake target plate is integrally rotated with the clutch body and is mounted so as to be able to approach and separate from the brake disc.

The pin is supported on the clutch body at a position corresponding to the convex portion of the concave-convex claw of the braked plate.
According to this configuration, the wall thickness between the pin support portion and the cylinder chamber can be increased without increasing the outer diameter of the clutch body or reducing the inner diameter of the cylinder chamber.

  As described above, according to the present invention, the structure of the hydraulic PTO clutch with an inertial braking mechanism can be simplified, the number of parts can be reduced, and the cost can be reduced.

Hereinafter, the present invention will be described based on the illustrated embodiments.
The illustrated embodiment shows a case where the hydraulic PTO clutch with an inertial braking mechanism of the present invention is incorporated in a tractor vehicle body. In the overall view of FIG. 3, 1 is a transmission case that constitutes the main part of the tractor vehicle body. In the transmission case 1, a traveling propulsion shaft 2 into which power from an engine (not shown) is introduced and a PTO propulsion shaft 3 inserted therein are rotatably supported via bearings. .
A traveling system transmission mechanism 6 for transmitting a predetermined transmission power to the drive shaft 5 of the rear wheel differential device 4 is assembled to the traveling system propulsion shaft 2. The traveling system transmission mechanism 6 includes a front wheel differential device. A mechanism for transmitting power to the drive shaft 7 (not shown) is also included.

The travel system transmission mechanism 6 includes a creep transmission (not shown) in addition to a hydraulic shuttle transmission 6a, a gear-type main transmission 6b, and a sub-transmission 6c.
The PTO propulsion shaft 3 transmits engine power to the PTO transmission shaft 9 via the clutch mechanism 8, and this PTO transmission shaft 9 transmits power to the PTO shaft 10 at the rear of the transmission case 1 via the PTO transmission mechanism 11. It is made like that.
The PTO propulsion shaft 3 and the PTO transmission shaft 9 are disposed opposite to each other on the same axis line in the mission case 1, and both are supported in the mission case 1 so as to be rotatable independently from each other via bearings.

  As shown in FIG. 1, the clutch mechanism 8 slides into a disc mounting body 12 connected to the PTO propulsion shaft 3, a clutch body 13 connected to the PTO transmission shaft 9, and a cylinder chamber 14 of the clutch body 13. The clutch disc 15 of the disc mounting body 12 and the drive plate 16 of the clutch body 13 are brought into pressure contact with each other by the forward movement in the clutch connection direction by the hydraulic pressure supplied and supplied into the cylinder chamber 14 so that the clutch is engaged. A clutch piston 17 to be in a state, and a clutch spring 18 in which the clutch piston 17 is moved backward in the clutch disengagement direction by releasing the oil pressure to release the pressure contact between the clutch disk 15 and the drive plate 16 to be in a clutch disengagement state. It has.

The clutch mechanism 8 is provided with an inertia braking mechanism 19 that brakes the inertia rotation of the PTO transmission shaft 9 via the clutch body 13 when the clutch is disconnected.
The inertial braking mechanism 19 includes a brake disk 20 fixedly held in the transmission case 1 and a braked plate 21 that can rotate integrally with the clutch body 13 and can be moved toward and away from the brake disk 20. I have.
The disc mounting body 12 has a cup shape, and a boss portion 12a is formed on the bottom of the cup shape. The boss portion 12a is splined to a spline shaft portion 3a formed on the outer peripheral surface of the rear end portion of the PTO propulsion shaft 3. And is positioned in the axial direction by a stopper ring 3b fixed to the spline shaft portion 3a. And the uneven | corrugated strip is formed in the axial direction by the predetermined length in the perimeter of the cup-shaped opening end side outer peripheral surface of the disc attachment body 12, and a plurality of sheets having the concave / convex strip engaging the concave / convex strip on the inner peripheral surface is formed. The clutch disk 15 is movable in the axial direction and is fitted so as to rotate integrally with the disk mounting body 12.

  The clutch body 13 has a cup shape with a diameter larger than that of the disc mounting body 12, and a boss portion 13 a is formed at the bottom of the cup shape so as to extend toward the rear end side in the axial direction, and the nose sleeve 13 b has a front end in the axial direction. Extends toward the side. The boss portion 13a and the nose sleeve 13b are spline-fitted to a spline shaft portion 9a formed on the outer peripheral surface of the front end side in the axial direction of the PTO transmission shaft 9. The outer peripheral surface of the boss portion 13 a is rotatably supported by a fuel collar 26 via a bearing 27, and the fuel collar 26 is fixedly supported by a support bracket 28 of the mission case 1.

A small-diameter shaft hole 3c is formed at the center of the rear end of the PTO propulsion shaft 3, and a small-diameter shaft 9b at the center of the front end of the PTO transmission shaft 9 is rotatably inserted into the small-diameter shaft hole 3c. Thus, the PTO propulsion shaft 3 and the PTO transmission shaft 9 are supported concentrically.
The clutch body 13 and the disc mounting body 12 are concentrically combined so that the cup-shaped opening portions face each other and the latter is covered with the former.
The nose sleeve 13 b of the clutch body 13 extends toward the cup shape of the disc mounting body 12, and the tip of the nose sleeve 13 b can rotate into the cup shape portion of the disc mounting body 12 via a bearing 29. It is supported.

The cup-shaped portion of the clutch body 13 has a small-diameter inner peripheral surface 13c and a large-diameter inner peripheral surface 13d formed with the former as the bottom and the latter as the opening.
On the entire periphery of the opening end side inner peripheral surface of the large-diameter inner peripheral surface 13d of the clutch body 13, an uneven strip is formed with a predetermined length in the axial direction, and an uneven strip that engages with the uneven strip is formed on the outer peripheral surface. A plurality of drive plates 16 are movable in the axial direction and are fitted so as to rotate together with the clutch body 13.
The plurality of clutch disks 15 and the plurality of drive plates 16 are alternately arranged in the axial direction.

A pressure plate 22 can be moved in the axial direction by a concave-convex engagement like a drive plate 16 via a stopper ring 23a and a disc spring 23b at an end portion on the opening side of the large-diameter inner peripheral surface 13d of the clutch body 13. The rotation is engaged with the clutch body 13 so as to be integrated.
A pin support hole 25 as a support portion for the pin 24 is formed through the stepped surface 13e at the boundary between the large diameter inner peripheral surface 13d and the small diameter inner peripheral surface 13c of the clutch body 13 in the axial direction. A plurality (three in the illustrated example) of pin support holes 25 are formed at equal intervals in the circumferential direction.

The clutch piston 17 is formed with a small-diameter outer peripheral surface 17a and a large-diameter outer peripheral surface 17b corresponding to the small-diameter inner peripheral surface 13c and the large-diameter inner peripheral surface 13d of the clutch body 13. Further, the inner peripheral surface 17 c of the clutch piston 17 is slidably fitted into the nose sleeve 13 b of the clutch body 13.
An annular seal 17d, such as an O-ring, is attached to a part of the small-diameter outer peripheral surface 17a of the clutch piston 17 in correspondence with the small-diameter inner peripheral surface 13d of the clutch body 13, and the outer peripheral surface of the nose sleeve 13b. An annular seal 13f such as an O-ring that keeps hermeticity corresponding to the inner peripheral surface 17c of the clutch piston 17 is attached to a part of the ring.

With this structure, the cylinder chamber 14 in which the clutch piston 17 is slidably fitted is kept airtight and prevents oil leakage.
Oil pressure is supplied and introduced into the cylinder chamber 14 through an oil supply port 26 a formed in the oil supply collar 26 and an oil passage 13 g formed in the boss portion 13 a of the clutch body 13. Supply / exclusion of the oil pressure into the cylinder chamber 14 is performed from a pump (not shown) via a control valve.
As the clutch spring 18, a coil-shaped compression spring is adopted, and this is placed between the end of the clutch piston 17 and the spring seat 30 mounted in the vicinity of the tip of the nose sleeve 13 b in the cup-shaped portion of the disc mounting body 12. Compression is interposed.

The brake disc 20 of the inertia brake mechanism 19 employs a disk-shaped plate, the outer peripheral portion of which is fixedly held by a part of the transmission case 1, and the axial end surface of the inner peripheral portion is a support bracket. The outer circumferential surface of the boss portion 13 a of the clutch body 13 is loosely fitted concentrically so as to be in contact with and supported by the front end portion in the axial direction of the oil supply collar 26 fixedly supported by the oil 28.
As shown in FIGS. 1 and 2, the brake plate 21 is a disc-like plate similar to the brake disc 20, and the outer circumferential surface has uneven claws 21a formed at equal intervals in the circumferential direction. Yes. Also, on the outer surface of the cup-shaped bottom side axial end of the clutch body 13, uneven claws 13h corresponding to the uneven claws 21a of the brake plate 21 are formed at equal intervals in the circumferential direction. By engaging the uneven claw 21 a of the brake plate 21 and the uneven claw 13 h of the clutch disk 13, the brake plate 21 can move in the axial direction with respect to the clutch disk 13 on the same axis as the clutch disk 13. The rotation is configured to be integrated with the clutch body 13. With this configuration, the brake plate 21 can be moved toward and away from the clutch body 13 toward the brake disc 20 and is engaged with the clutch body 13 so as to rotate integrally.

A brake lining is attached to one or both of the contact surfaces of the brake disc 20 and the braked plate 21.
The pin 24 is disconnected from both the clutch piston 17 and the braked plate 21, and abuts against the clutch piston 17 and the braked plate 21 when the clutch is disengaged so that the spring force of the clutch spring 18 is applied to the clutch piston 17. The brake plate 21 is slidably supported by the pin support hole 25 of the clutch body 13 so as to be transmitted to the braked plate 21 through the pin and to press the brake plate 21 against the brake disc 20.

  The pin 24 is also supplied with oil pressure into the cylinder chamber 14 and the clutch piston 17 moves in the clutch connecting direction, whereby an axial clearance is formed between the contact surfaces of the pin 24 and the clutch piston 17. Therefore, the brake plate 21 is provided with a function of releasing the braking force of the PTO transmission shaft 9 by releasing the braking force of the brake disc 20 by releasing the brake plate 21 from the spring force of the clutch spring 18. The axial length with respect to the support hole 25 is such that the pin 24 is longer than the pin support hole 25, and the pin 24 protrudes further toward the braked plate 21 than the pin support hole 25 during the clutch disengagement operation. The brake disc 20 can be repressed. The amount of protrusion of the pin 24 from the pin support hole 25 is set in consideration of the axial movement distance of the braked plate 21 relative to the brake disc 20, and is, for example, approximately the same as the axial movement distance of the braked plate 21. Has been.

The support position of the pin 24, that is, the formation position of the pin support hole 25 in the clutch body 13 is a position corresponding to the outer peripheral portion of the clutch piston 17 at a position radially outside the cylinder chamber 14. This position is a position corresponding to the boundary surface between the small-diameter outer peripheral surface 17a and the large-diameter outer peripheral surface 17b of the clutch piston 17 (the end surface of the large-diameter portion of the clutch piston 17).
Further, the support position of the pin 24 is a position corresponding to the convex portion of the concave and convex claw 21 a of the braked plate 21. By doing so, the radial thickness between the cylinder chamber 14 and the pin support hole 25 can be increased without increasing the outer diameter of the clutch body 13 or decreasing the inner diameter of the cylinder chamber 14. Can be bigger.

  In the hydraulic PTO clutch with an inertia braking mechanism of the present invention having the above-described configuration, the clutch piston 17 has a cup shape of the clutch body 13 by the spring force of the clutch spring 18 when no oil pressure is supplied to the cylinder chamber 14. Pushed to the bottom side, the pressure contact between the clutch disk 15 and the drive plate 16 is released, and the clutch disengaged state is maintained. In this state, the braked plate 21 is elastically pressed toward the brake disc 20 via the clutch piston 17 and the pin 24 by the spring force of the clutch spring 18 to maintain the braking state. Accordingly, no power is transmitted to the PTO transmission shaft 9.

When hydraulic pressure is supplied to the cylinder chamber 14, the clutch piston 17 is pushed toward the cup-shaped opening end side of the clutch body 13 against the spring force of the clutch spring 18, and the clutch disk 15, the drive plate 16, Is pressed toward the pressure plate 22 to establish a clutch engaged state. In this state, the braked plate 21 is released from the pressure applied from the clutch piston 17 and the pin 24 and can be rotated away from the brake disk 20. Accordingly, the power from the PTO propulsion shaft 3 is transmitted to the PTO transmission shaft 9.
When the hydraulic pressure in the cylinder chamber 14 is removed, the clutch piston 17 is pushed toward the cup-shaped bottom side of the clutch body 13 by the spring force of the clutch spring 18 to release the pressure contact between the clutch disk 15 and the drive plate 16. The clutch-disengaged state is established, the braked plate 21 is pressed against the brake disc 20 via the clutch piston 17 and the pin 24, and the PTO transmission shaft 9 is braked via the braked plate 21 and the clutch body 13, so that the PTO The inertial rotation of the transmission shaft 9 is braked.

The above embodiment exemplifies a case where the hydraulic PTO clutch with an inertial braking mechanism of the present invention is applied to a traveling system transmission of a tractor. However, the present invention relates to a driving side shaft and a driven shaft that are arranged opposite to each other on the same axis. You may apply to the general purpose clutch which transmits and interrupts | rotates a rotational torque between side shafts.
Next, the bearing structure of the PTO transmission mechanism 11 applied to the traveling system transmission of the tractor will be described.
As shown in FIG. 4, the PTO transmission mechanism 11 has a rear end portion of the transmission case 1 with transmission gears 31 and 32 engaged with both shafts in order to shift the output from the PTO transmission shaft 9 to the PTO shaft 10 for output. It is installed on the end cover 33.

  Conventionally, one transmission gear 31 is formed integrally with a short shaft (not shown), and the front end of this short shaft and the rear end of the PTO transmission shaft 9 are connected by a coupling shaft joint (not shown). Moreover, the short shaft is supported by the end cover 33 on both sides of the transmission gear 31 with a double-supported structure. The other transmission gear 32 is also conventionally supported by the end cover 33 in a double-sided structure. Therefore, conventionally, the end cover 33 has a two-sided wall structure in which support walls (not shown) are formed in parallel on both sides of the transmission gears 31 and 32. As described above, the conventional PTO transmission mechanism 11 has a complicated bearing structure and a large number of parts, which has been an obstacle to cost reduction.

  In the present invention, in order to improve the above points, as shown in FIG. 4, the transmission gears 31 and 32 are both supported by the end cover 33 in a cantilever structure, and the end cover 33 has a single wall structure. It is. The transmission gear 31 is formed with a spline shaft hole 31a at the center instead of the conventional short shaft, and a spline shaft portion 9c at the rear end of the PTO transmission shaft 9 is inserted into the spline shaft hole 31a. The rear end side of the cover 33 is supported by a single bearing 36 in a cantilever structure. Further, the PTO shaft 10 is rotatably supported at two locations separated in the axial direction by a bearing sleeve 33 a in the center of the end cover 33 via bearings 37 and 38. The bearing sleeve 33a is formed on the end cover 33 so as to protrude inward and outward in the axial direction. The transmission gear 32 is fixed to a bearing sleeve 33 a via a bearing 37, 38 on the inner end portion of the PTO shaft 10 that is penetrated and supported in the inner and outer directions of the end cover 33 by a tightening nut 39. With the above structure, the transmission gear 32 is supported by the bearing sleeve 33a of the end cover 33 in a cantilever structure at a position protruding inward from the bearing sleeve 33a. In addition, the upper part of the end cover 33 is formed with an oil supply port 33b obliquely upward, and a cap 33c is attached so as to be openable and closable.

In this way, the rear end of the PTO transmission shaft 9 is directly splined to the transmission gear 31 of the PTO transmission mechanism 11 to omit the short shaft of the transmission gear 31, and the transmission gears 31 and 32 are connected to the end cover 33. By supporting the end cover 33 with a cantilever structure, it is possible to make the end cover 33 have a single-side wall structure and reduce the number of parts. Therefore, the bearing structure of the PTO transmission mechanism 11 can be simplified and the cost can be reduced. it can.
Next, a description will be given of a pump power take-off structure attached to the transmission case 1 as a hydraulic pressure supply means for a power steering hydraulic supply means for the tractor and a three-point link hitch mechanism driving hydraulic pressure supply means installed at the rear of the tractor.

  Conventionally, pump power has been extracted from a PTO propulsion shaft that is constantly rotating using three flat gears (not shown). That is, conventionally, the pump input shaft (not shown) is parallel to the PTO propulsion shaft, an intermediate shaft (not shown) is arranged between the two shafts, and a flat gear is mounted on each of these three shafts. Was driving the pump. In this case, the gear mounted on the pump input shaft and the gear mounted on the intermediate shaft are rotatably mounted in a mounting case (not shown), and the pump body (not shown) is mounted on one side surface of the mounting case. ) Is attached, and the side surface orthogonal to the side surface is attached to the side surface of the mission case.

Therefore, the conventional pump power take-out structure has a large number of parts, is complicated in structure, and has been an obstacle to cost reduction.
Therefore, in the present invention, as shown in FIG. 5, power is extracted from the PTO propulsion shaft 3 by a pair of bevel gears 41 and 42 and the pump input shaft 43 is rotationally driven.
In this case, the pump power take-out position is between the support bracket 45 of the transmission case 1 that rotatably supports the vicinity of the rear end of the PTO propulsion shaft 3 via the bearing 44 and the installation position of the clutch mechanism 8. Yes.

One bevel gear 41 has a short cylindrical shaft-like boss portion 41a extending in one axial direction, and this boss portion 41a is splined to a spline shaft portion 3a formed on the outer peripheral surface of the rear end of the PTO propulsion shaft 3. The stopper ring 46 fitted to the PTO propulsion shaft 3 is axially positioned by being fitted, rotatably supported by the support cylinder portion 45 of the transmission case 1 via a bearing 44.
The other bevel gear 42 has a cylindrical shaft-shaped boss portion 42a extending in one of the axial directions to have a hollow shaft structure, and a mounting case 49 via bearings 47 and 48 at two locations where the boss portion 42a is separated in the axial direction. The positioning rings 50 and 51 are used for axial positioning. A spline groove 42b is formed on the inner peripheral surface of one end of the boss portion 42a, and the pump input shaft 43 is spline-fitted into the spline groove 42b.

  The mounting case 49 includes a cylindrical portion 49a, an outer mounting flange portion 49b formed to extend radially outward at one end outer peripheral portion of the cylindrical portion 49a, and an inner peripheral portion at one end of the cylindrical portion 49a. The pump mounting portion 49c is formed with a repetitively formed pump mounting portion 49c. The pump mounting portion 49c is fastened with a mounting flange portion 53 of the pump main body 52 by bolts, and the outer mounting flange portion 49b is attached to a mounting seat on the side surface of the transmission case 1. It is bolted to the surface (not shown). In addition, the mounting seat surface (not shown) of the mission case 1 is formed with an opening for inserting the cylindrical portion 49a.

In this case, the pump input shaft 43 is attached to the side surface of the mission case 1 in an orthogonal state with respect to the PTO propulsion shaft 3.
With the above-described configuration, the pump power take-off structure has a reduced number of parts and a simplified structure, so that the cost can be reduced.
FIG. 6 shows another embodiment of the pump power take-out structure. The mounting case 49 is omitted, and the mounting flange portion 53 of the pump body 52 is directly attached to the mounting seat surface 54 on the side surface of the transmission case 1. It is what I did. In this case, a cylindrical portion 55 that rotatably supports the bevel gear 42 connected to the pump input shaft 43 is integrally formed on the mounting seat surface 54 on the side surface of the transmission case 1, and the bevel gear 42 is formed on the cylindrical portion 55. Is incorporated rotatably through bearings 47 and 48. Other configurations are the same as those in FIG.

  With the above configuration, the pump power take-out structure is further simplified, the number of parts is reduced, and the cost can be further reduced.

It is a principal part vertical side view which shows embodiment of the hydraulic type PTO clutch with an inertia braking mechanism of this invention. FIG. 2 is a front view showing an engagement portion structure between a clutch body and a braked plate in FIG. 1. It is a vertical side view of the whole transmission mechanism of the tractor to which the present invention is applied. It is a principal part vertical side view of a PTO transmission mechanism. It is a principal part vertical side view of a pump power extraction part. It is a principal part vertical side view of the pump power extraction part which shows the deformation | transformation Example of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Mission case 2 Driving system propulsion shaft 3 PTO propulsion shaft 4 Rear wheel differential device 5 Driving shaft of rear wheel differential device 6 Traveling system transmission mechanism 7 Driving shaft of front wheel differential device 8 Clutch mechanism 9 PTO transmission shaft 10 PTO shaft 11 PTO transmission Mechanism 12 Disc mounting body 13 Clutch body 14 Cylinder chamber 15 Clutch disc 16 Drive plate 17 Clutch piston 18 Clutch spring 19 Inertia brake mechanism 20 Brake disc 21 Plate to be braked 22 Pressure plate 23a Stopper ring 23b Belleville spring 24 Pin 25 Pin support hole ( Pin support)

Claims (3)

A clutch mechanism (8) for disconnecting and connecting a PTO propulsion shaft (3) supported in the mission case (1) and a PTO transmission shaft (9) to which power is transmitted from the PTO propulsion shaft (3); The clutch body (13) is configured to rotate integrally with the clutch body (13) connected to the PTO transmission shaft (9), which can be moved toward and away from the brake disk (20) fixedly held by the case (1). A plurality of pins (24) arranged at intervals in the circumferential direction by the return operation of the clutch piston (17) that slides in the clutch body (13) when the clutch is disengaged. A hydraulic PTO clutch having an inertia braking mechanism (19) for braking the PTO transmission shaft (9) by applying pressure to the brake disc (20) via
A clutch piston (17) slidably fitted in the clutch body (13) includes a small diameter outer peripheral surface (17a) corresponding to the small diameter inner peripheral surface (13c) of the clutch body (13), and a clutch body. A large-diameter outer peripheral surface (17b) corresponding to the large-diameter inner peripheral surface (13d) of (13),
A small-diameter inner peripheral surface (13c) and a large-diameter inner surface of the clutch body (13) are arranged on the radially outer side of the cylinder chamber (14) of the clutch piston (17) and on the radially inner side of the outer peripheral surface of the clutch body (13). A pin support hole (25) is formed through the clutch body (13) in the axial direction from the step surface (13e) between the peripheral surface (13d) and slidably supporting the pin (24);
Between the small-diameter outer peripheral surface (17a) and the large-diameter outer peripheral surface (17b) of the clutch piston (17), the pin (24) corresponds to the step surface (13e) of the clutch body (13) and when the clutch is disengaged. A hydraulic PTO clutch with an inertia braking mechanism is characterized in that a stepped surface is formed to repress the brake disc (20) toward the brake disc (20). Before SL clutch body (13) and a braked plate (21) is uneven claw (13h, 21a) formed in the circumferential direction a plurality of positions in the outer circumferential portion of both Yes and mutually engaged with,
The support position of the pin (24) to the clutch body (13) is a position corresponding to the convex portion of the concave and convex claw (21a) of the braked plate (21) . Hydraulic PTO clutch with inertia braking mechanism.   The pin (24) is not connected to either the clutch piston (17) or the braked plate (21), and contacts the clutch piston (17) and the braked plate (21) when the clutch is disengaged. The hydraulic PTO clutch with an inertial braking mechanism according to claim 1 or 2, wherein the hydraulic PTO clutch is in contact with the hydraulic brake.

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