JP5049915B2 - Dog clutch device - Google Patents

Description

  The present invention relates to a dog clutch device having claw portions that mesh with each other and transmitting rotational power.

  The dog clutch device is a device in which the claw portions provided at each end of the pair of rotating shafts mesh with each other to transmit rotational power, and since the structure is simple and reliable power transmission is possible, automobiles, motorcycles, Widely used in tillage machines. In an agricultural machine such as a field cultivator, the rotary shaft on the other input shaft side moves along an arc-shaped track with respect to the rotary shaft on one output shaft side, and these rotary shafts can be connected to each other. A pair of dog clutches (dog clutch devices) have been developed.

  From the viewpoint of improving the ease of coupling of the dog clutch, this dog clutch can guide the movement of the tip of the other claw portion approaching the axially facing surface of the claw portion, thereby enabling the engagement of both claw portions. An inclined surface is formed (see Patent Document 1). The claw portion having the inclined surface is formed with a meshing surface extending in the axial direction of the rotating shaft at the front end portion, and an inclined surface inclined from the front end portion of the meshing surface to the shaft end surface is formed on the upper surface. It is formed in a shape.

  In the dog clutch configured in this way, for example, when one rotary shaft moves along an arcuate track with respect to the other fixed rotary shaft, the tip of one triangular claw portion approaching the One rotating shaft rotates so as to abut against the inclined surface of the other triangular claw portion and is guided by the inclined surfaces of both triangular claw portions, and finally the other triangular portion where one triangular claw portion abuts The pair of dog clutches are connected by meshing with the meshing surface of the triangular claw portion adjacent to the claw portion.

JP-A-8-191609 (paragraphs 0010 to 0014, FIGS. 1 and 2)

  In this conventional dog clutch, there is no means for adjusting the misalignment of the axis of the rotating shaft when the two rotating shafts are joined. Therefore, if the movement of one rotating shaft deviates from the arc-shaped track, There may be a large deviation of the shaft center. In this case, since there is a possibility that the machine may be damaged, the conventional dog clutch needs to be centered using a jig or the like when disassembling / adjusting / assembling during initial assembly or maintenance. The problem arises.

  The present invention has been made in view of such a problem, and when a dog clutch provided at each end of a pair of rotating shafts is joined, the pair of rotating shafts are automatically centered. It is an object of the present invention to provide a dog clutch device that can be easily pulled out.

In order to solve such a problem, the feature of the present invention is that it is provided at each distal end portion of a pair of rotating shafts (for example, the drive shafts 53 and 54 and the driven shaft 62 in the embodiment), and the claw portions are meshed to rotate. In the dog clutch device for transmitting power, the rotation center axis of the dog clutch is located on the inner side of the claw portion of the dog clutch (for example, the front passive clutch 20 and the rear passive clutch 21 in the embodiment) provided on one of the pair of rotary shafts. A centering portion chamfered in an R shape over the entire circumference of the peripheral end portion having a predetermined diameter from the axially opposed surface of the dog clutch pawl portion provided on the other of the pair of rotating shafts Then, a centering contact surface (for example, the contact surface 15a2 in the embodiment) that is inclined radially inward from the inner peripheral side to the outer peripheral side with respect to the rotation center axis of the dog clutch is formed. Is that this centering abutment surface in contact with the centering portion to guide its movement, and configuration requirements to carry out centering of a pair of rotating shafts.

The centering portion chamfered in the R shape is disposed inside the claw portion, but the chamfered R shape portion needs to be positioned in the vicinity of the inside of the claw portion, and has a peripheral end portion having a predetermined diameter. Is located in the vicinity of the inside of the claw portion. The centering portion may be formed integrally with the dog clutch, or may be provided as a separate body from the dog clutch (see claim 2 ).

If the contact surface for centering is inclined from the inner peripheral side to the outer peripheral side radially inward with respect to the rotation center axis of the dog clutch, among the axially facing surfaces of the dog clutch pawls, It may be either linear or curved. In addition, when the centering contact surface is formed in a straight line, contact surfaces with different inclination angles are formed continuously, with a large inclination angle on the inner peripheral side and a large inclination angle on the outer peripheral side. You may make it do.

The present invention, centering unit, may be detachably attached to a dog clutch provided on one of the pair of rotary shaft (Claim 2). If it is technically difficult to form the centering part integrally with the dog clutch, and the manufacturing cost is high, the centering part is separated from the dog clutch, and the dog clutch can be attached and detached. Can be facilitated and the manufacturing cost can be reduced.

According to the present invention, a dog clutch provided on one of the pair of rotating shafts is supported by the rotating shaft so as to be movable in the direction of the rotating shaft, and an elastic body provided between the dog clutch and the rotating shaft. (e.g., a compression spring 53a in the embodiment, 54a) by, optionally biased dog clutch side connected to the other of said pair of rotary shafts (claim 3).

  As the approaching dog clutch approaches the stationary dog clutch, when the chamfered portion comes into contact with the axially opposed surface of the claw portion of the other dog clutch, the other dog clutch approaches the spring against the spring. It can evacuate to the side away from. For this reason, it is possible to prevent the claw portion of the other dog clutch with which the chamfered portion comes into contact from being damaged.

  According to the dog clutch device of the present invention, having the above-described characteristics, when the dog clutch provided at each end of the pair of rotating shafts is joined, the pair of rotating shafts are automatically centered. It is possible to provide a dog clutch device that facilitates the unloading operation.

  Embodiments of a dog clutch device according to the present invention will be described below with reference to FIGS. First, before explaining the dog clutch device, an outline of a coater equipped with the dog clutch device will be described.

  As shown in FIG. 7 (plan view), the hull coater 50 is connected to a three-point link connecting mechanism (not shown) provided at the rear of the traveling machine body 90 so that the traveling machine body 90 moves forward and backward. In accordance with the above, the paintwork is performed. The wrinkle coater 50 is mounted on the traveling machine body 90 and includes a mounting part 51 having an input shaft to which power from the traveling machine body 90 is input, and a parallel provided on the mounting part 51 and swingable in the mounting part width direction. A link 55, and a glazing operation portion 60 that is disposed so as to be rotatable in a horizontal direction around a rotation fulcrum O provided on the moving end side (rear end side) of the parallel link 55 and performs a glazing operation. Have.

  A transmission frame 61 is provided on the glazing operation portion 60 so as to project, and a front end portion of the transmission frame 61 is pivotally supported by a rear frame 56 provided on the moving end side of the parallel link 55. The hulling work unit 60 can be rotated in the horizontal direction with the pivot position of the rear frame 56 as a pivot fulcrum O, the forward work position Pf offset to one side (right side) of the traveling machine body 90, and the forward work position. It is possible to move between the reverse work position Pb rotated about 180 ° from Pf.

Two drive shafts 53, 54 that are arranged at a predetermined distance in the longitudinal direction and horizontally project to the rear side are arranged in a rotatable manner in the middle portion in the longitudinal direction of the main frame 52 provided in the mounting portion 51. It is attached with. The drive shaft 53 is disposed substantially directly behind the input shaft so that power from the input shaft can be transmitted through a universal joint (not shown). The drive shaft 54 is configured such that the power transmitted to the drive shaft 53 is transmitted via the drive shaft 53 and a gear attached to the drive shaft 54. For this reason, when power is transmitted to the drive shaft 53, both the drive shafts 53 and 54 rotate. The front drive clutch 10 is attached to the tip of the drive shaft 53 via a compression spring 53a, and the rear drive clutch 11 is attached to the tip of the drive shaft 54 via a compression spring 54a. These drive shafts 53 and 54 extend from the main frame 52 to the rear side with substantially the same distance, and the front drive clutch 10 and the rear drive clutch 11 are arranged at substantially the same distance from the main frame 52 to the rear side. ing.

  On the rotation fulcrum side of the transmission frame 61, a driven shaft 62 extending in the front-rear and horizontal directions at a position closer to the moving end side than the rotation fulcrum O is rotatably supported. The driven shaft 62 is provided so as to penetrate the transmission frame 61 and extends from the front side surface and the rear side surface of the transmission frame 61 with substantially the same length. The front passive clutch 20 is attached to the front end portion of the driven shaft 62, and the rear passive clutch 21 is attached to the rear end portion of the driven shaft 62. The front passive clutch 20 is configured to be connectable to the front drive clutch 10, and the rear passive clutch 21 is configured to be connectable to the rear drive clutch 11.

  The front-side passive clutch 20 swings the parallel link 55 to one side (right side) in the body width direction so that the parallel link 55 is most folded and the wrinkle working unit 60 is centered on the rotation fulcrum O of the traveling body 90. When moved to the forward operation position Pf on one side in the machine body width direction, the front drive clutch 10 is connected (see FIG. 1). Further, the rear side passive clutch 21 rotates the glazing operation portion 60 about 180 ° from the forward operation position Pf around the rotation fulcrum O with the parallel link 55 most folded to one side (right side) in the body width direction. If it moves to the reverse work position Pb, it will be in the state connected with the rear side drive clutch 11 (refer FIG. 9).

When the parallel link 55 is swung to one side (right side) in the body width direction and the parallel link 55 is in the most folded state (hereinafter referred to as “working posture”) (see FIG. 7 ), the hulling work unit The 60 rotation fulcrums O are configured so as to be positioned approximately at the center between the two drive shafts 53 and 54 in plan view. For this reason, the front passive clutch 20 can be connected to the front drive clutch 10 by moving the hulling work part 60 around the rotation fulcrum O to the forward work position Pf with the parallel link 55 in the working posture. Further, when the hulling work part 60 is moved to the reverse work position Pb around the rotation fulcrum O with the parallel link 55 in the working posture (see FIG. 9), the rear passive clutch 21 is moved to the rear drive clutch 11. Can be connected to.

  The front drive clutch 10 and the front passive clutch 20, and the rear drive clutch 11 and the rear passive clutch 21 are used as a pair, and are configured as a dog clutch device 1. The front drive clutch 10 and the rear drive clutch 11 are formed in the same shape, and the front passive clutch 20 and the rear passive clutch 21 are formed in the same shape. Therefore, the dog clutch device 1 including the front drive clutch 10 and the front passive clutch 20 will be described, and the description of the dog clutch device including the rear drive clutch 11 and the rear passive clutch 21 will be omitted.

As shown in FIG. 1, the dog clutch device 1 is attached to the front drive clutch 10 attached to the distal end portion of the drive shaft 53 and the distal end portion of the driven shaft 62 extending from one side surface of the transmission frame 61. And a front passive clutch 20. The front drive clutch 10 and the front passive clutch 20 include pawl clutch members 12 and 22, respectively. The claw clutch members 12 and 22 are shown in FIG. 2 (a) (front view), FIG. 2 (b) (cross-sectional view), FIG. 3 (a) (front view), and FIG. 3 (b) (cross-sectional view). The drive shaft 53 and the driven shaft 6 are cylindrical and correspond to the inside on the base side.
Spline portions 13 and 23 are formed by spline-joining the two distal end portions, and hook-shaped end portions 14 and 24 are formed in an annular shape on the distal end side of the claw clutch members 12 and 22. Three claw portions 15 and 25 are arranged at equal intervals in the circumferential direction on the opposed surfaces on the front end side of the end portions 14 and 24, and meshing surfaces 16 and 26 formed on the circumferential side end portions are engaged with each other. Thus, the rotational force is transmitted.

  As shown in FIGS. 2 (a) and 2 (b), the claw portion 15 of one claw clutch member 12 has meshing surfaces 16 at both ends in the circumferential direction, and the rotation center axis of the claw clutch member 12 This is a protrusion that has a rectangular cross section with respect to L and is formed in a fan shape in a front view. From the viewpoint of preventing the pawl clutch member 12 from escaping, the meshing surface 16 is formed in a reverse taper shape so as to recede inward from the tip portion. Of the axially facing surface 15a of the claw portion 15, a flat portion 15a1 is formed on the radially outer side with respect to the rotation center axis L, and the radially inner side advances radially outward with respect to the inner peripheral surface 15b of the claw portion 15. Accordingly, a contact surface 15a2 that is inclined toward the axially opposed surface side is provided. The contact surface 15a2 may be continuously provided with an R shape or a C surface that is inclined from the radially inner side to the outer side toward the axially facing surface side. In this case, the inclination angle of the adjacent C surface is made smaller on the outer side than on the inner side.

  As shown in FIGS. 3 (a) and 3 (b), the claw portion 25 of the other claw clutch member 22 has engagement surfaces 26 at both ends of the claw portion 25 and has a rectangular cross section in the radial direction. The protrusion is formed in a fan shape when viewed from the front. From the viewpoint of preventing the claw clutch member 22 from escaping, the meshing surface 26 is formed in a reverse taper shape so as to recede inward from the tip portion, and the rotation center axis of the axially facing surfaces 25 a of the claw portion 25. An R-shaped chamfered portion 25b having a convex surface is formed on the outer peripheral portion on the radially outer side with respect to L, and an inclined surface in which the radially inner portion is inclined toward the surface side of the end portion 24. 25c is formed. When the claw portions 15 and 25 are in contact with each other and foreign matter such as soil adheres between the claw portions 15 and 25, the inclined surface 25 c This is to suppress the situation in which 15 and 25 are damaged.

  On the inner side of the claw portion 25 of the claw clutch member 22, a hole portion 27 whose outer periphery is formed on the same surface as the inner peripheral surface of the claw portion is formed. The hole portion 27 has a large-diameter hole portion 27a and a small-diameter hole portion 27b formed in a step shape toward the spline portion side. A disc-shaped centering member 29 (see FIG. 4) is inserted into the hole 27. As shown in FIG. 4 (cross-sectional view), the centering member 29 includes a head portion 29a inserted into the large-diameter hole portion 27a and a small-diameter hole extending from one end side of the head portion 29a and having a smaller diameter than the head portion 29a. And an insertion portion 29b inserted into the portion 27b. The head portion 29a has an outer diameter that can be inserted with a small gap in the large-diameter hole portion 27a.

  A centering portion 29c that is chamfered in an R shape is formed around the entire periphery of the head portion 29a. The centering portion 29c is not limited to the R shape, and may be a C shape. The centering member 29 has a height that fits in the hole 27 in a state in which the centering member 29 is attached to the hole 27. A through hole 29 d for passing the shaft portion of the bolt 30 is formed in the center portion of the centering member 29. The centering member 29 can be detachably attached to the driven shaft 62 by inserting the centering member 29 into the hole 27 and inserting the shaft portion of the bolt 30 into the through hole 29d.

  The coupling operation of the dog clutch device 1 that accompanies the movement of the hull coater 60 of the hull coater 50 on which the dog clutch device 1 configured as described above is moved to the forward work position Pf will be described. As shown in FIG. 8 (plan view), when the smearing work unit 60 is rotated counterclockwise with the smearing work part 60 positioned behind the traveling machine body 90 (see FIG. 7), the smearing work is performed. The portion 60 rotates about the rotation fulcrum O, and the front passive clutch 20 also rotates counterclockwise about the rotation fulcrum O.

Then, when the glazing operation portion 60 moves to the vicinity of the forward operation position Pf (see FIG. 7), the front passive clutch 20 moves counterclockwise around the rotation fulcrum O as shown in FIG. The chamfered portion 25b of the claw portion 25 of the front passive clutch 20 comes into contact with the contact surface 15a2 of the claw portion 15 of the front drive clutch 11 by rotating and approaching the front drive clutch 10.

  Then, as the glazing operation portion 60 further rotates, as shown in FIG. 5B, the outer periphery of the axially facing surface 15a of the contact surface 15a2 while the chamfered portion 25b slides on the contact surface 15a2. And the front drive clutch 10 is urged in the drive shaft direction. As a result, the front drive clutch 10 moves toward the drive shaft against the biasing force of the compression spring 53a.

  Here, since the chamfered portion 25b is formed in a curved surface having a convex surface, when the chamfered portion 25b rotates counterclockwise around the rotation fulcrum O of the transmission frame 61, the contact surface 15a2 is formed. Move (slide) while making line contact on the top. For this reason, the chamfered portion 25b stops on the contact surface 15a2, and most of the force that the chamfered portion 25b acts on the contact surface 15a2 does not act on the contact surface 15a2, and the chamfered portion 25b and the contact surface 15a2 There is no risk of damage.

  When the chamfered portion 25b moves on the axially opposed surface 15a on the radially inner side, the chamfered portion 25b moves on the axially opposed surface 15a while urging the axially opposed surface 15a obliquely forward as shown in FIG. As shown in FIG. 5C, the claw portions 25 and 15 of the front drive clutch 10 and the front passive clutch 20 are in contact with each other.

  When the claws of the front drive clutch 10 and the front passive clutch 20 come into contact with each other, the front drive clutch 10 is further pushed from the front passive clutch 20 and driven against the compression spring 53a (see FIG. 5B). It further moves to the shaft 53 side.

  In this state, when either the drive shaft 53 to which the front drive clutch 10 is attached or the driven shaft 62 (see FIG. 1) to which the front passive clutch 20 is attached rotates, the front drive is performed by the restoring force of the compression spring 53a in the compressed state. The clutch 10 moves to the front passive clutch 20 side.

  When the front drive clutch 10 moves to the front passive clutch 20 side, the centering portion 29c of the centering member 29 provided on the front passive clutch 20 contacts the contact surface 15a2 provided on the front drive clutch 10, and further on the front side When the drive clutch 10 moves closer to the front passive clutch side in the axial direction, the centering portion 29c can be engaged with the contact surface 15a2 to perform the centering action. As shown in FIG. The claws engage with each other, and the coupling operation of the dog clutch device 1 is completed. As described above, even when the front passive clutch 20 approaches the rotational center axis of the front drive clutch 10 while being shifted, the drive shaft 53 and the driven shaft 62 are automatically centered by the centering portion 29c. It can be easily centered without using a jig.

  Further, when the claws are in contact with each other, the inclined surface 25c is formed on the inner side of the axially facing surface 25 of the pawl 25 of the front passive clutch 20, so that there is little possibility that foreign matter may be engaged between the claws. Thus, damage to the claw portions 25 and 15 due to the engagement of foreign matter can be prevented.

  In addition, in the case where the hulling work unit 60 is moved from the forward work position Pf to the reverse work position Pb (see FIG. 8), the action of centering by connecting the rear passive clutch 21 to the rear drive clutch 11 is as follows. Since it is based on the action | operation which couple | bonds the front side passive clutch 20 with the front side drive clutch 10 mentioned above, the description is abbreviate | omitted.

The top view of a dog clutch apparatus in the state where a pair of claw clutch members of a dog clutch apparatus were connected is shown. 1 shows one pawl clutch member of a dog clutch device according to an embodiment of the present invention, in which FIG. 1 (a) is a front view of the pawl clutch member, and FIG. 2 (b) is II-II in FIG. 1 (a). It is sectional drawing equivalent to an arrow view. The other claw clutch member of the dog clutch apparatus concerning one Embodiment of this invention is shown, The same figure (a) is a front view of a claw clutch member, The same figure (b) is III-III in the same figure (a). It is sectional drawing equivalent to an arrow view. Sectional drawing of one claw clutch member provided with the centering member is shown. The top view of the dog clutch apparatus for demonstrating the coupling | bonding operation | movement of a dog clutch apparatus is shown. The top view of the dog clutch apparatus which drew the locus | trajectory of one dog clutch in order to demonstrate the coupling | bonding operation | movement of a dog clutch apparatus is shown. The top view of the hulling machine which mounted the dog clutch apparatus and the hulling work part moved to the advance work position is shown. FIG. 3 is a plan view of the coater in a state where the dog clutch device is mounted and the coater unit is positioned between the forward work position and the reverse work position. The top view of the hulling machine which mounted the dog clutch apparatus and the hulling work part moved to the reverse work position is shown.

1 Dog clutch device 10 Front drive clutch (dog clutch)
11 Rear drive clutch (dog clutch)
15, 25 Claw portions 15a, 25a Axial facing surface 15a2 Contact surface (contact surface for centering)
20 Front passive clutch (dog clutch)
21 Rear passive clutch (dog clutch)
25b Chamfered portion 29c Centering portion 53, 54 Drive shaft (rotary shaft)
53a, 54a Compression spring 62 Driven shaft (rotating shaft)
L Rotation center axis

Claims (3)

In the dog clutch device that is provided at each tip of the pair of rotating shafts, and the claw portions mesh with each other to transmit rotational power,
A centering portion chamfered in an R shape over the entire circumference of the peripheral end portion having a predetermined diameter from the rotation center axis of the dog clutch inside the claw portion of the dog clutch provided on one of the pair of rotation shafts Is provided ,
Of the opposing surfaces in the axial direction of the claw portions of the dog clutch provided on the other of the pair of rotating shafts, an inclination is given radially inward from the inner peripheral side to the outer peripheral side with respect to the rotation center axis of the dog clutch. 2. A centering contact surface is formed, the centering contact surface contacts the centering portion to guide the movement thereof, and the pair of rotating shafts are centered. The dog clutch device described in 1. The centering section, the dog clutch device according to claim 1, characterized in that it is detachably attached to the dog clutch provided on one of the pair of rotary shafts. The dog clutch provided on one of the pair of rotating shafts is supported by the rotating shaft so as to be movable in the direction of the rotating shaft, and the pair of rotating shafts is supported by an elastic body provided between the dog clutch and the rotating shaft. The dog clutch device according to claim 1 or 2 , wherein the dog clutch device is biased toward a dog clutch connected to the other of the rotating shafts.

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