JP2004142710A - Workpiece positioning mechanism of conveyance device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a positioning mechanism of a conveyance device which positions different kinds of workpieces by switching a protrusion length of a positioning pin for positioning the workpiece by a turning means provided at a predetermined position. <P>SOLUTION: A moving member 44 is attached to a rod tip of an actuator fixed to a bracket 42, and a decelerator 48, an electric motor 46, and a guide sleeve 58 are mounted on the moving member 44. A guide bearing 66 forming a spline 72 is mounted on a turn member 64 supported turnably on the guide sleeve 58 through a slide bearing 62, and the spline 72 is meshed with a spline 76. A small diameter part 74b of a shaft member 74 and an output shaft 48b of the decelerator 48 are tightened by a shaft joint 78 through a key 80. A compression spring member 82 is provided between a spring receiver 86 fixed to the moving member 44 and a bearing 84 supporting a flange part 66a of a guide member 66. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a work positioning mechanism of a transfer device for transferring a work such as an automobile body. More particularly, the present invention relates to the same production line for different kinds of works by varying the work positioning height. The present invention relates to a work positioning mechanism of a transfer device that can be transferred by using a device.
[0002]
[Prior art]
Conventionally, for example, in a hanger of a transfer device that transfers a work such as an automobile body on a transfer rail, a cable that prevents the work from being displaced by engaging the work near a work receiving portion that constitutes the hanger; A positioning pin which is movable by a spring is provided to position the hanger and the work (for example, see Patent Document 1).
[0003]
[Patent Document 1]
Japanese Patent Publication No. 5-65391 (pages 2 to 3, Fig. 3)
[0004]
[Problems to be solved by the invention]
However, in the above-described hanger of the transfer device, when positioning works having different positioning heights on the hanger, it is necessary to replace the positioning pins themselves with positioning pins having different lengths. could not.
[0005]
SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problem, and a positioning pin for a work is provided on a hanger so as to be freely adjustable in protruding length, and the positioning pin is provided by rotating means provided at a predetermined position on a hanger transport path. It is an object of the present invention to provide a work positioning mechanism of a transfer device that can easily handle works of different types by switching the height of the work.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a work positioning mechanism that is provided in a transfer device that transfers a work, and includes a positioning pin for positioning the work.
A positioning pin with a variable protruding length,
A drive mechanism for switching the projecting length of the positioning pin to a predetermined position on the work path,
Has,
The drive mechanism includes:
A concave portion that engages with a reference pin member provided on the positioning pin;
Rotating means for rotating the reference pin member provided in the recess,
It is characterized by having.
[0007]
According to the present invention, the protrusion length of the positioning pin for positioning the work can be switched by the drive mechanism provided at a predetermined position on the hanger transport path. For this reason, even if different types of workpieces are transported, positioning can be performed efficiently in a short time, and the transport and processing efficiency of the workpieces on a production line or the like can be improved, and the unit production cost of the workpieces can be reduced.
[0008]
In this case, when the reference pin member is provided with a rotary socket member that makes the protrusion length of the positioning pin variable, and when the rotating means is engaged with the rotary socket member, switching of the protrusion length of the positioning pin is performed. This is preferred because it is performed quickly.
[0009]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a preferred embodiment of a work positioning mechanism of a transport device according to the present invention will be described in detail with reference to the accompanying drawings.
[0010]
FIG. 1 is a schematic structural front view of a work positioning mechanism 10 of a transfer device according to an embodiment of the present invention, FIG. 2 is a longitudinal sectional view of a main part of FIG. 1, and FIG. is there.
[0011]
The work positioning mechanism 10 of the transfer device according to this embodiment mounts a body 14 as a work transferred by a rail 12 on a mounting portion 18b of an arm 18 constituting a hanger 16 via a body receiving table 20. In addition, a positioning pin mechanism 22 for preventing the displacement of the vehicle body 14 is provided.
[0012]
As shown in FIG. 2, the positioning pin mechanism 22 includes a mounting plate 24 fixed to the mounting portion 18 b of the arm 18 via the body receiving base 20, and a stepped cylindrical portion in a hole 24 a of the mounting plate 24. The guide member 26 has the guide member 26 inserted therein.
[0013]
A pin holding cylinder (reference pin member) 28 having a positioning function is provided on the lower surface of the mounting plate 24, and the pin holding cylinder 28 includes a bush 30. The bush 30 is inserted into a stepped cylindrical portion 26 a constituting the guide member 26. A holding cam (rotary socket member) 32 is inserted into the hole of the pin holding cylinder 28, and a positioning pin 34 is loosely inserted into the bush 30 and the holding cam 32. The guide member 26 and the pin holding cylinder 28 are fixed to the mounting plate 24 via a screw member 36.
[0014]
As shown in FIG. 4, a pair of guide grooves 35 are formed on the outer peripheral surface of the pin holding cylinder 28 in the axial direction so as to face 180 ° in the radial direction. The holding cam 32 has a pair of spiral grooves 41 formed on the outer peripheral surface thereof facing each other, and a pair of cutout grooves 32a and projections 32b formed on one end thereof.
[0015]
The spiral groove 41 includes flat grooves 41a and 41b which are substantially orthogonal to the axial direction at the lower end position and the upper end position, and an inclined groove 43 which is inclined in the axial direction between the flat groove parts 41a and 41b.
[0016]
As shown in FIG. 2, the protrusion 63 (see FIG. 3) of the turning member 64 is engaged with the notch groove 32 a of the holding cam 32, and when the holding cam 32 is turned by the turning member 64, The guide pin 33 is displaced in the vertical direction (the direction of the arrow X and the direction of the arrow Y in FIG. 4), and the amount of expansion and contraction of the positioning pin 34 in the axial direction is adjusted.
[0017]
One end of the positioning pin 34 has a conical shape, and a hole 45 is formed near the other end. A guide pin 33 is attached to the hole 45.
[0018]
The guide pin 33 is inserted into the spiral groove 41 of the holding cam 32 and is guided by the guide groove 35 of the pin holding cylinder 28 so as to be displaceable along the axial direction.
[0019]
The drive mechanism 38 for switching the height of the positioning pin 34 includes a set of actuators 40 provided at predetermined positions on the hanger transport path. The actuators 40 are fixed to a bracket 42 mounted on a pedestal 39 and move up and down. Direction (the arrow X direction and the arrow Y direction in FIG. 1). The pedestal 39 is mounted on the pedestal 15 and has a centering mechanism (not shown) at a substantially central portion thereof, and can be slightly displaced within a range of 360 degrees in the radial direction along the vertical direction.
[0020]
A moving member 44 is fixed to the rod end of the actuator 40. The moving member 44 includes a housing 44a, a horizontal plate 44b that is provided substantially horizontally at both ends of the housing 44a, and is fixed to a rod end of the actuator 40, and a moving member 44 that hangs below the housing 44a. And a vertical plate body 44c provided.
[0021]
A drive source, for example, an electric motor (rotating means) 46 provided on the vertical plate body 44c is connected via a shaft coupling 50 to an input shaft 48a of a speed reducer 48 whose drive shaft 46a is fixed to the lower surface of the housing 44a. Are linked. The output shaft 48b of the speed reducer 48 is inserted into a slide bearing 52 provided on the lower surface of the housing 44a.
[0022]
A guide sleeve 58 is fixed to the upper surface of the housing 44a by a screw member 56. The bottom of the guide sleeve 58 enters the opening 54 of the housing 44a. The guide sleeve 58 has a hole 58a (see FIGS. 2 and 3) that engages with the outer peripheral portion of the pin holding tube 28, and a guide function for inserting the pin holding tube 28 into the hole 58a. And a tip taper portion 58b (see FIGS. 2 and 3).
[0023]
As shown in FIGS. 2 and 3, the cylindrical rotating member 64 that is rotated by the electric motor 46 has a large-diameter portion 64 a and a small-diameter portion 64 b, and the small-diameter portion 64 b is an inner hole of the guide sleeve 58. The slide bearing 62 is rotatably supported by a slide bearing 62 inserted into the slide bearing 60. On the other hand, one end of the large diameter portion 64a contacts the end face of the slide bearing 62, and the other side extends through the opening 54 of the housing 44a into the housing 44a. A protrusion 63 (see FIGS. 2 and 3) that engages with the notch groove 32a of the holding cam 32 is formed at one end of the rotating member 64.
[0024]
As shown in FIG. 3, the guide bearing 66 has a flange 66 a at a lower end thereof, and the flange 66 a is fixed to the other end of the rotating member 64 by a screw member 68. The boss 66 b of the guide bearing 66 is inserted into the inner hole 70 of the rotating member 64.
[0025]
A plurality of splines 72 are formed in the inner peripheral surface of the guide bearing 66 in the axial direction.
[0026]
The shaft member 74 integrally engages with the guide bearing 66 and has a function of guiding the rotating member 64. Therefore, the shaft member 74 has a spline 76 formed along the axial direction of the large diameter portion 74a, and the spline 76 meshes with the spline 72 formed on the boss 66b. The output shaft 48b of the speed reducer 48 is connected to the small diameter portion 74b of the shaft member 74 via a shaft joint 78.
[0027]
In this case, the output shaft 48b, the small diameter portion 74b, and the shaft joint 78 are directly connected integrally by the key 80.
[0028]
As shown in FIG. 3, the spline 72 and the spline 76 are meshed with each other, and the spline 72 is slidably disposed on the spline 76 in the vertical direction (the arrow X direction and the arrow Y direction). The rotating member 64 can be displaced in the vertical direction (the arrow X direction and the arrow Y direction) using the shaft member 74 as a guide.
[0029]
One end of the compression spring member 82 surrounding the shaft coupling 78 is seated on a flange portion 84a of a bearing 84 that contacts the guide bearing 66, and the other end portion is a flange portion 86a of a spring receiver 86 fixed to the inner surface of the housing 44a. Sitting.
[0030]
The inner holes of the bearing 84 and the spring receiver 86 have a gap with respect to the outer peripheral surface of the shaft coupling 78, and the upper surface of the flange portion 84 a of the bearing 84 is formed by the resilient force of the compression spring member 82 of the guide bearing 66. It is in contact with the lower surface of the flange 66a.
[0031]
In this case, for example, a thrust bearing (not shown) is provided between the upper surface and the lower surface in order to reduce a frictional force caused by contact between the lower surface of the flange portion 66a and the upper surface of the flange portion 84a. Good.
[0032]
Here, the compression spring member 82 supports the turning member 64 so as to face upward, and makes the large-diameter portion 64 a of the turning member 64 abut on the slide bearing 62.
[0033]
Therefore, when the projection 63 of the rotating member 64 engages with the notch groove 32a of the holding cam 32, the rotating member 64 is vertically displaced by the spline connection between the guide bearing 66 and the shaft member 74, and the projection 63 The impact force at the time of engagement between the portion 63 and the notch groove 32a is reduced by the compression spring member 82.
[0034]
The work positioning mechanism 10 of the transfer device according to the embodiment of the present invention is basically configured as described above. Next, the operation and operation and effect thereof will be described.
[0035]
As shown in FIG. 1, a vehicle body 14 as a work placed on a body receiving table 20 of an arm 18 is conveyed via a rail 12, and when the vehicle body 14 is moved to a predetermined position, the arm 18 is stopped.
[0036]
Next, the lower portion 18a of the arm 18 is clamped by the stopper 11 (see FIG. 1) under the driving action of an actuator (not shown), and the position of the arm 18 in the transport direction (perpendicular to the plane of FIG. 1) is regulated. You. Further, a different actuator (not shown) is driven, and the stopper 13 (see FIG. 1) presses the side surface of the mounting portion 18b of the arm 18 to regulate the position of the arm 18 in the width direction (left and right direction in FIG. 1). You. For this reason, the position of the arm 18 in the transport direction and the width direction is regulated, and the arm 18 is positioned at a predetermined position.
[0037]
When the actuator 40 is driven and the moving member 44 rises a predetermined distance in the arrow X direction as shown in FIG. 2, the outer peripheral portion of the holding cylinder 28 is connected to the guide sleeve 58 via the distal end tapered portion 58b of the guide sleeve 58. The protrusion 63 of the rotating member 64 is engaged with or abuts on the notch groove 32 a or the protrusion 32 b of the holding cam 32.
[0038]
In this case, the guide sleeve 58 is slightly displaced in the radial direction under the action of the centering mechanism of the pedestal 39 so that the axis of the guide sleeve 58 and the axis of the holding cylinder 28 coincide with each other. 38 can be made to coincide with the axial center position.
[0039]
In addition, the rotating member 64 is configured to be vertically displaceable (arrow X direction and arrow Y direction in FIG. 3) using the shaft member 74 as a guide by spline fitting between the guide bearing 66 and the shaft member 74, and Since the compression spring member 82 is provided between the bearing 84 and the spring receiver 86, the impact when the protrusion 63 of the rotating member 64 engages or abuts the notch groove 32 a or the protrusion 32 b of the holding cam 32. The power is eased.
[0040]
Next, when the electric motor 46 is driven, the number of rotations of the electric motor 46 reduced to a predetermined value by the speed reducer 48 via the shaft coupling 50 is changed via the output shaft 48 b of the speed reducer 48, the shaft coupling 78 and the key 80. The power is transmitted to the member 74, and the shaft member 74 rotates at a predetermined rotation speed.
[0041]
Thus, the rotation of the shaft member 74 causes the rotation member 64 to rotate via the guide bearing 66, and the end surface of the projection 63 of the rotation member 64 rotates while contacting the end surface of the projection 32 b of the holding cam 32. Start. When the projection 63 of the rotating member 64 engages with the notch groove 32a of the holding cam 32, the rotating member 64 and the holding cam 32 are connected. In this case, the engagement between the notch groove 32 a of the holding cam 32 and the projection 63 of the rotating member 64 is held by the elastic force of the compression spring member 82.
[0042]
When the rotating member 64 is rotated via the shaft member 74 and the guide bearing 66, the guide pin 33 guides the guide groove 35 of the pin holding cylinder 28 in cooperation with the holding cam 32, as shown in FIG. Then, the guide groove 35 is displaced from the lower end to the upper end, and the guide pin 33 is displaced from the flat groove 41a to the flat groove 41b. Therefore, the positioning pin 34 switches from the lower end position (solid line) to the upper end position (two-dot chain line) (see FIG. 2).
[0043]
In this state, the positioning pin 34 is inserted into a hole (not shown) of the vehicle body 14, and the vehicle body 14 is positioned.
[0044]
Thereafter, the moving member 44 is moved down (in the direction of the arrow Y in FIG. 2) by the driving action of the actuator 40 to disengage the hole 58a of the guide sleeve 58 from the outer peripheral portion of the pin holding cylinder 28, and the notch groove 32a of the holding cam 32 is formed. The engagement between the rotating member 64 and the protrusion 63 is released.
[0045]
Next, when a vehicle body 14a different from the vehicle body 14 is conveyed via the rail 12 (see FIG. 1), the height between the upper surface of the body receiver 20 and the bottom surface of the vehicle body 14a placed on the body receiver 20 is increased. The case where the projection length of the positioning pin 34 to be engaged with the vehicle body 14a is to be shortened corresponding to the length H (see FIG. 1) will be described.
[0046]
When the actuator 40 is driven to raise the moving member 44 by a predetermined distance, the outer peripheral portion of the pin holding cylinder 28 is inserted into the hole 58a of the guide sleeve 58 via the tapered end portion 58b of the guide sleeve 58, and the rotating member The projections 63 of 64 are engaged with the cutout grooves 32 a of the holding cam 32. In this case, when the positioning pin 34 is located at the upper end, the guide pin 33 is engaged with the flat groove portion 41b, so that the phase of the notch groove 32a of the holding cam 32 and the protrusion 63 of the rotating member 64 are synchronized in advance. are doing.
[0047]
The engagement between the notch groove 32 a of the holding cam 32 and the projection 63 of the rotating member 64 is held by the elastic force of the compression spring member 82.
[0048]
Next, when the guide sleeve 58 is rotated under the driving action of the electric motor 46, the guide pin 33 guides the guide groove 35 of the pin holding cylinder 28 to cooperate with the holding cam 32, as shown in FIG. The guide groove 35 is displaced from the upper end to the lower end, and the positioning pin 34 switches from the upper end position (two-dot chain line) to the lower end position (solid line).
[0049]
Thereby, the vehicle body 14a is mounted on the mounting portion 18b of the arm 18 via the body receiving base 20 (see FIG. 1).
[0050]
In the embodiment of the present invention, an example has been described in which the projecting length of the positioning pin 34 for positioning the vehicle bodies 14 and 14a as different works mounted on the arm 18 to the arm 18 is variable. The present invention is not limited to this, and can be applied to a positioning structure for a work or the like on a transport pallet.
[0051]
【The invention's effect】
As described above, according to the present invention, different types of works can be automatically positioned by switching the protrusion length of the positioning pin for positioning the work by the rotating means provided at a predetermined position. . For this reason, even if different types of workpieces are transported, accurate positioning can be performed in a short time, and as a result, the transporting and processing efficiency of the workpieces on a production line or the like can be improved, and the unit production cost of the workpieces can be reduced. it can.
[Brief description of the drawings]
FIG. 1 is a schematic structural front view of a work positioning mechanism of a transfer device according to an embodiment of the present invention.
FIG. 2 is a longitudinal sectional view of a main part of FIG.
FIG. 3 is an enlarged longitudinal sectional view of a main part of FIG. 2;
FIG. 4 is a schematic structural perspective view of a pin holding cylinder, a holding cam, and a positioning pin shown in FIG. 2;
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 ... Work positioning mechanism of a transfer apparatus 14, 14a ... Body 16 ... Hanger 18 ... Arm 20 ... Body receiving stand 22 ... Positioning pin mechanism 28 ... Pin holding cylinder 32 ... Holding cam 33 ... Guide pin 34 ... Positioning pin 38 ... Drive mechanism 40 ... actuator 46 ... electric motor 64 ... rotating member

Claims (2)

A work positioning mechanism that is provided in a transfer device that transfers the work and includes a positioning pin for positioning the work.
A positioning pin with a variable protruding length,
A drive mechanism for switching the projecting length of the positioning pin to a predetermined position on the work path,
Has,
The drive mechanism includes:
A concave portion that engages with a reference pin member provided on the positioning pin;
Rotating means for rotating the reference pin member provided in the recess,
A work positioning mechanism for a transfer device, comprising: The work positioning mechanism of the transfer device according to claim 1,
A work positioning mechanism for a transfer device, wherein a rotation socket member that allows a protrusion length of the positioning pin to be variable is disposed on the reference pin member, and the rotation unit is engaged with the rotation socket member.

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