JP5021652B2 - Rotating shaft support mechanism - Google Patents

Description

  The present invention relates to a rotating shaft support mechanism, and more particularly to a rotating shaft support mechanism in which the center of gravity and the rotation center of a rotating body are shifted.

  2. Description of the Related Art A structure in which a rotating shaft is rotatably supported is conventionally known. For example, in the indexer device described in Japanese Patent Application Laid-Open No. 2005-28539 and Japanese Utility Model Laid-Open No. 6-3531, a pair of rotating shafts fixed to a table unit are rotatably supported by a shaft support portion. Then, a driving force is input from the electric motor to the rotating shaft, and the table unit is rotationally driven. The table unit includes a turntable that can rotate around the axis of the rotation shaft and a drive mechanism for the turntable. A work is detachably mounted on the turntable. The workpiece is then machined.

  Since workpieces to be set in the indexer device are planned to have various shapes and sizes, it is difficult to match the center of gravity of the table unit and the workpiece mounted on the unit with the axis of the rotary shaft. is there. Therefore, a rotational moment due to an unbalanced load (hereinafter sometimes referred to as “uneven load moment”) acts on the rotating shaft. As a result, the load on the electric motor increases.

On the other hand, in WO 2005/038291 pamphlet (Patent Document 3), a balancing rotational moment (hereinafter referred to as “cancellation”) that cancels at least a part of the offset load moment acting on the rotating shaft using a gas spring. A balancer mechanism is disclosed that can act on a rotating shaft to reduce the eccentric load moment.
JP 2005-28539 A Japanese Utility Model Publication No. 6-3531 International Publication No. 2005/038291 Pamphlet

  In the balancer mechanism of Patent Document 3, since a load is applied to the free end of the rotating shaft, the amount of displacement of the rotating shaft increases. Therefore, there is a concern that the tilt of the turntable is increased, and as a result, the machining accuracy of the workpiece is lowered. Patent Documents 1 and 2 do not disclose a configuration for solving such a problem.

  The present invention has been made in view of the above problems, and an object of the present invention is to reduce the displacement of the rotating shaft due to the urging force from the urging means when reducing the influence of the rotating moment due to the uneven load. An object of the present invention is to provide a rotating shaft support mechanism that can be made small.

The rotary shaft support mechanism according to the present invention is a rotary shaft support mechanism that supports a rotary shaft that supports a member, and a plurality of rotary shaft support mechanisms are provided so as to be aligned in the axial direction of the rotary shaft, and rotatably support the rotary shaft. A rotating shaft support, a turntable provided on the rotating shaft, on which a workpiece is detachably mounted;
A cam member provided on the rotary shaft and provided between the rotary shaft support portions; a cam follower member that contacts the cam member provided on the rotary shaft and rotates following the cam member; and a plurality of rotations Biasing means provided between the shaft support portions and biasing the cam follower member toward the cam member. The cam member includes a cam curved surface portion. The cam curved surface portion is formed so that the curvature center and the rotation center of the cam curved surface portion are shifted. When the rotating shaft rotates with the workpiece mounted on the turntable, the rotating shaft rotates while the cam follow-up member and the cam member abut. When the cam follower member and the cam curved surface portion come into contact with each other, the work and the turntable are pushed up by a force applied from the cam follower member to the cam curved surface portion.

  According to the above configuration, the displacement of the rotating shaft due to the urging force from the urging means can be reduced when reducing the influence of the rotational moment due to the uneven load. As a result, the shake of the rotating shaft is reduced, and the position of the member can be determined with high accuracy.

  Preferably, the rotating shaft support mechanism further includes a lever member to which the cam follower member is attached, and a lever member support portion that rotatably supports the lever member, and the urging means rotates the lever member. Thus, the cam follower member is biased toward the cam member.

  According to the above configuration, the urging force by the urging means can be amplified and transmitted to the cam following member. Further, by providing the lever member, the center of the cam member and the biasing means can be offset and provided, so that the overall height of the rotating shaft support mechanism can be reduced and the apparatus can be miniaturized.

  In the rotating shaft support mechanism, the biasing means is provided on the opposite side of the lever support portion with respect to the cam follower member, and the lever member is located at a portion located between the cam follower member and the biasing means. A bent portion or a bent portion that is bent toward.

  According to the above configuration, it is possible to reduce the size of the rotating shaft support mechanism by effectively utilizing the space around the cam member. In particular, the overall height of the rotating shaft support mechanism is reduced.

  In the rotary shaft support mechanism, preferably, the rotary shaft support portion is fixed to the casing, and the cam member and the biasing means are built in the casing.

  Thereby, invasion of foreign matter into the cam member and the biasing means is suppressed. In the rotating shaft support mechanism, preferably, an urging member is disposed below the cam follower member. Thereby, the expansion / contraction length of the urging member can be used as the displacement length of the cam following member as it is. In the rotating shaft support mechanism, preferably, the urging member has a pressing member to which a cam follow-up member is connected. Thereby, it is possible to reduce the number of parts while maintaining the output torque.

  In the rotating shaft support mechanism, a gas spring is preferably used as the urging means. Thereby, the biasing means which is small and has a low spring constant can be obtained. By reducing the spring constant of the urging means, it is possible to reduce load fluctuation due to the stroke of the urging means.

  In the rotary shaft support mechanism, as an example, the rotary shaft supports a turntable for machining. In this case, the accuracy of machining applied to the member can be improved.

  In the rotating shaft support mechanism, as one example, a recess for receiving the cam follower member is provided on the side surface of the cam member. Thereby, the target rotational position of the rotating shaft can be easily indexed.

  According to the present invention, in the rotating shaft support mechanism, when generating a moment that cancels the rotating moment due to the offset load, the displacement of the rotating shaft due to the urging force from the urging means can be reduced.

It is a front view of the indexer apparatus containing the rotating shaft support mechanism which concerns on one Embodiment 1 of this invention. It is sectional drawing which shows the rotating shaft support mechanism which concerns on one Embodiment 1 of this invention. It is the figure which looked at the rotating shaft support mechanism shown by FIG. 2 from the direction of arrow III. It is a figure which shows the planar shape of a cam plate. It is a figure which shows the modification of the planar shape of a cam plate. It is a figure explaining the relationship between the rotation angle of a rotating shaft, and a gas spring stroke. It is sectional drawing of the indexer apparatus containing the rotating shaft support mechanism which concerns on Embodiment 2 of this invention. It is a front view of the rotating shaft support mechanism which concerns on this Embodiment 3. It is sectional drawing of the rotating shaft support mechanism shown by FIG. FIG. 9 is a front view of the indexer device when the rotation shaft has made a half rotation from the state shown in FIG. 8. It is a front view which shows the modification of the rotating shaft support mechanism shown by FIG. It is sectional drawing of the rotating shaft support mechanism shown by FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Indexer apparatus, 10 Table unit, 20, 30 Rotating shaft, 21 Cam plate, 21A Cam curved surface part, 21BR R curved surface part, 21C V notch, 22 End plate, 40, 50 Rotating shaft support mechanism, 41 Casing, 42 Bearing, 43 roller member, 44 lever member, 44A recess, 44B bent part, 45 pin, 46 gas spring, 60 drive mechanism, θa rotation angle.

(Embodiment 1)
Embodiment 1 of the rotating shaft support mechanism according to the present invention will be described below. Note that the same or corresponding portions are denoted by the same reference numerals, and the description thereof may not be repeated.

  FIG. 1 is a front view of an indexer device that is a machining device including a rotary shaft support mechanism according to one embodiment of the present invention.

  Referring to FIG. 1, the indexer device 1 includes a table unit 10, rotary shafts 20 and 30, rotary shaft support mechanisms 40 and 50, and a drive mechanism 60.

  The table unit 10 includes a turntable that can rotate around the axis of the rotary shafts 20 and 30 and a drive mechanism thereof. A work W is detachably mounted on the turntable. The table unit 10 is supported on the rotary shafts 20 and 30. The rotating shafts 20 and 30 are supported by the rotating shaft support mechanisms 40 and 50. In the example of FIG. 1, the rotary shaft 30 is rotationally driven by a drive mechanism 60 formed of, for example, an electric motor. Thereby, the table unit 10 and the workpiece | work W rotate. The rotary shaft is stopped at the indexing position (target rotational position), and the workpiece W is machined at this position. In addition, the drive mechanism 60 may rotationally drive the rotating shaft 20, and may rotationally drive both of the rotating shafts 20 and 30.

  Here, the center of gravity of the table unit 10 and the workpiece W does not necessarily match the axis of the rotary shafts 20 and 30. Accordingly, as the rotary shafts 20 and 30 are rotated, a rotational moment (uneven load moment) due to an offset load of the table unit 10 and the workpiece W acts on the rotary shafts 20 and 30. As a result, the load on the drive mechanism 60 increases. Therefore, it is required to reduce the eccentric load moment.

  FIG. 2 is a cross-sectional view showing a rotating shaft support mechanism included in the indexer device 1 shown in FIG. FIG. 3 is a view of the rotating shaft support mechanism shown in FIG. 2 as viewed from the direction of arrow III.

  The rotating shaft support mechanism according to the first embodiment includes a balancer mechanism that cancels at least a part of the eccentric load moment, as will be described below.

  2 and 3, a cam plate 21 and an end plate 22 are attached to the rotating shaft 20. The rotating shaft support mechanism 40 includes a casing 41, a bearing 42, a roller member 43, a lever member 44, a pin 45, and a gas spring 46.

  The rotating shaft 20 is rotatably supported by the casing 41 by a bearing 42. A plurality of bearings 42 are provided so as to be aligned in the extending direction of the rotating shaft 20 (the direction of the arrow DR1). The cam plate 21, the roller member 43, the lever member 44, and the gas spring 46 are provided between the plurality of bearings 42 arranged in the arrow DR1 direction. The roller member 43 is in contact with the cam plate 21. As the rotary shaft 20 rotates, the roller member 43 reciprocates in the vertical direction (arrow DR2 direction). The roller member 43 rotates following the rotation of the cam plate 21. The lever member 44 is provided with a recess 44 </ b> A, and the roller member 43 is provided in the recess 44 </ b> A of the lever member 44. Recess 44A functions as a “lubricant sump”. One end of the lever member 44 is rotatably supported by the casing by a pin 45. The other end of the lever member 44 is supported by a gas spring 46. The roller member 43 is urged toward the cam plate 21 by the gas spring 46. The roller member 43 comes into contact with the cam plate 21. In other words, the gas spring 46 applies a load to the cam plate 21 via the lever member 44 and the roller member 43. A bent portion 44 </ b> B that bends toward the cam plate 21 is provided at a portion of the lever member 44 located between the roller member 43 and the gas spring 46.

  Next, the effect of the gas spring 46 applying a load to the cam plate 21 will be described.

  For example, when the rotation state of the rotating shaft 20 and the cam plate 21 is the state shown in FIG. 3, the roller member 43 attached to the lever member 44 pushes the cam plate 21 upward. That is, the gas spring 46 pushes up the cam plate 21 via the roller member 43 and the lever member 44 and promotes the rotation of the rotating shaft 20. Here, when the center of gravity of the table unit 10 and the workpiece W is at a position lower than the axis of the rotary shafts 20 and 30, the center of gravity can be lifted by the force that pushes up the cam plate 21, thereby reducing the load on the drive mechanism 60. can do.

By the way, in general, the cam shaft torque (qc) generated by the work of the cam is obtained by the equation (1).
qc = (k.yh2) /. theta.h.times. (S.times.V) + F0.yh / .theta.h.times.V (1)
k: spring constant of gas spring yh: stroke (y: spring displacement)
t h: rise time (t: time)
S: y / yh
V: (dy / dt) / (yh / th)
θh: Assignment angle (angle at which the cam works)
F0: Initial load for mounting the gas spring In (1), inertia torque, viscous resistance, and frictional resistance are ignored.

  The maximum value of the camshaft torque can be obtained by substituting S and V when S × V and V are maximized into the above equation (1). In the indexer device 1 according to the first embodiment, qc is maximized when V is maximized. By making the maximum value of qc substantially coincide with the rotational moment due to the offset load, the load on the drive mechanism 60 can be reduced most efficiently. The maximum value of qc can be appropriately adjusted by changing the spring constants k and F0 of the gas spring, for example.

  FIG. 4 is a diagram illustrating a planar shape of the cam plate 21. Referring to FIG. 4, cam plate 21 includes a cam curved surface portion 21A (a portion where the rotation center and the R center do not coincide) and an R curved surface portion 21B (a portion where the rotation center and the R center coincide). The R curved surface portion 21B is provided at a position shifted by 90 ° in the circumferential direction. In the example of FIG. 6, the gas spring 46 works on the cam curved surface portion 21 </ b> A because the gas spring 46 is displaced with respect to the cam plate 21. On the other hand, in the R curved surface portion 21B, the gas spring 46 does not move with respect to the cam plate 21, so the gas spring 46 does not work. Here, the R curved surface portion 21B is provided around the index position. By doing in this way, when the rotation shaft is stopped at the index position, the roller member 43 pushes up the central portion of the cam plate 21 so that no rotational torque is generated. Therefore, it is possible to suppress an unintended twisting force from acting on the workpiece W sandwiched between the table unit 10 and a counterpart member (for example, an index table) during machining. Further, as shown in FIG. 5, V notches 21C may be provided at positions shifted by 90 ° in the circumferential direction. In this case, when the roller member 43 enters the V notch 21C, the generation of the twisting force can be suppressed and the target rotation position can be easily indexed. Instead of the V notch 21C, a recess having a curved surface (R shape) on the bottom surface may be provided.

  FIG. 6 is a diagram for explaining the relationship between the rotation angle θa of the rotation shaft and the stroke of the gas spring 46. By making the planar shape of the cam plate 21 as shown in FIGS. 4 and 5, the stroke of the gas spring changes as shown in FIG. Referring to FIG. 6, in indexer device 1 according to the first embodiment, an indexing position is set for each 90 ° rotation angle θa, and 80 ° is assigned for each 90 ° rotation angle θa. The angle θh is set. In addition, about the space | interval of an index position, it can change suitably, for example to make it 60 degrees and 120 degrees. Similarly, the allocation angle θh can be changed as appropriate. A plurality of index positions may be arranged at unequal angle intervals.

The above contents are summarized as follows. That is, the rotating shaft support mechanism 40 according to the first embodiment is a rotating shaft support mechanism that supports the rotating shaft 20 that supports the workpiece W as a “member”, and is the axial direction of the rotating shaft 20 (the direction of the arrow DR1). And a bearing 42 as a “rotating shaft support portion” that rotatably supports the rotating shaft 20, and a “cam member provided between the bearings 42 and disposed between the bearings 42. Is provided between a roller member 43 as a “cam follow-up member” and a plurality of bearings 42, which abuts on the cam plate 21 and rotates following the cam plate 21, and the roller member 43 is attached to the cam plate 21. And a gas spring 46 as an “urging means” for urging the gas.

  According to the above configuration, the displacement of the rotating shaft 20 due to the urging force from the gas spring 46 can be reduced when generating a canceling moment that cancels the eccentric load moment. As a result, the tilt of the turntable can be reduced and the machining accuracy of the workpiece W can be improved. Further, the gas spring 46 used as the “biasing means” is small and can be set to have a low spring constant. Therefore, the load fluctuation due to the stroke of the gas spring 46 is relatively low.

  Further, from a viewpoint different from the above, the rotary shaft support mechanism 40 according to the first embodiment abuts on a bearing 42 that rotatably supports the rotary shaft 20 and a cam plate 21 provided on the rotary shaft 20. , A roller member 43 that rotates following the cam plate 21, a lever member 44 to which the roller member 43 is attached, a pin 45 as a “lever member support portion” that rotatably supports the lever member 44, a lever A gas spring 46 that urges the roller member 43 toward the cam plate 21 by rotating the member 44 is provided.

  According to the above configuration, the urging force by the gas spring 46 can be amplified and transmitted to the roller member 43. As a result, it is possible to effectively generate a canceling moment that cancels the offset load moment. Further, by providing the lever member 44, the center of the cam plate 21 and the gas spring 46 can be provided offset, so that the overall height of the rotary shaft support mechanism 40 can be reduced and the apparatus can be miniaturized.

  In the rotary shaft support mechanism 40, the gas spring 46 is provided on the opposite side of the pin 45 with respect to the roller member 43. A bent portion 44 </ b> B that is bent toward the cam plate 21 is formed at a portion of the lever member 44 located between the roller member 43 and the gas spring 46.

  By doing so, it is possible to further reduce the overall height of the rotary shaft support mechanism 40 by effectively utilizing the space around the cam plate 21. A “curved portion” may be provided instead of the bent portion 44B.

  Further, the cam plate 21, the roller member 43, the gas spring 46 and the like constituting the balancer mechanism are provided in the casing 41. Accordingly, the entry of foreign matter into these members, which are important parts, is suppressed.

  As the “urging means”, a hydraulic cylinder may be provided in place of the gas spring 46, and an accumulator for supplying a substantially constant pressure to the hydraulic cylinder may be provided. Moreover, the attachment position and attitude | position of an urging means can be changed suitably. For example, the urging unit may be attached to the upper side of the lever member 44 with the posture downward. Further, the urging force of the urging means may be adjusted according to the magnitude of the eccentric load moment. For example, a pressure adjustment valve for automatically adjusting the gas pressure according to the magnitude of the eccentric load moment may be provided.

  In the above example, the balancer mechanism included in the rotation shaft support mechanism 40 has been mainly described. However, a similar balancer mechanism may be included in the rotation shaft support mechanism 50. In the above example, the rotating shaft support mechanism 40 is provided with one cam plate 21, one roller member 43, and the like. However, the rotating shaft support mechanism 40 has a plurality of cam plates 21 and a roller member 43 that contacts the cam plate 21. May be provided.

(Embodiment 2)
FIG. 7 illustrates the indexer device 100 according to the second embodiment. In addition, about the same structure as the structure shown by the said FIGS. 1-6, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 7, the indexer device 100 includes a table unit 10, a rotating shaft 20, and a rotating shaft support mechanism 70. The table unit 10 is supported by the rotating shaft 20 in a cantilever state.

  The rotating shaft 20 is supported by a rotating shaft support mechanism 70. The rotary shaft 20 located in the rotary shaft support mechanism 70 is rotated between a bearing (rotary shaft support portion) 42 spaced apart in the axial direction (arrow DR1 direction) of the rotary shaft 20 and the bearing 42. And a cam plate 21 provided on the outer peripheral surface of the shaft 20.

  The rotary shaft support mechanism 70 includes a bearing 42, a roller member (cam follow-up member) 43, a lever member 44, a pin 45, and a gas spring (biasing means) that presses the roller member 43 against the cam plate (cam member). 46 and a motor 80 as a drive mechanism.

  The motor 80 includes a rotor 82 fixed to the rotary shaft 20 and a stator 81 fixed to the casing 41.

  The gas spring 46 and the motor 80 are provided between the bearings 42, and the cam plate 21 and the rotor 82 are provided between the rotary shafts 20 positioned between the bearings 42.

  Thus, by housing the motor 80 and the gas spring 46 in one rotating shaft support mechanism 70, the shaft length of the rotating shaft 20 can be shortened, and the torsional distortion and vibration vibration generated in the rotating shaft 20 can be reduced. Can be reduced.

  Further, by positioning the motor 80 and the cam plate within the pair of bearings, the number of bearings can be reduced, the frictional resistance generated on the rotary shaft 20 can be reduced, and the burden on the motor 80 can be reduced. You can plan.

(Embodiment 3)
The indexer device provided with the rotating shaft support mechanism 40 according to the third embodiment will be described with reference to FIGS. In addition, about the structure same as the structure shown by the said FIG. 1-FIG. 7, the same code | symbol is attached | subjected and the description is abbreviate | omitted. FIG. 8 is a front view of the rotating shaft support mechanism 40 according to the third embodiment, and FIG. 9 is a side sectional view of the rotating shaft support mechanism 40 shown in FIG.

  As shown in FIG. 8, the rotary shaft support mechanism 40 is provided so as to be aligned in the axial direction of the rotary shaft 2 as shown in FIG. 9 and the cam plate 21 provided on the rotary shaft 2. A bearing 42 and a bearing 42 </ b> A that are rotatably supported, a roller member 43 that is biased toward the cam plate 21, and a gas spring 46 that biases the roller member 43 toward the cam plate 21 are provided.

  The gas spring 46 includes a cylinder portion 48 fixed to the casing 41 and a piston portion 47 inserted into the cylinder portion 48 so as to be able to advance and retract. A high pressure gas is sealed in the cylinder portion 48.

  In the rotary shaft support mechanism 40 according to the third embodiment, the cam plate 21 has a disc shape whose center is located at a position away from the rotary shaft of the rotary shaft 20. FIG. 10 is a front view of the indexer device when the rotary shaft 2 is rotated halfway from the state shown in FIG. As shown in FIGS. 10 and 8, the gas spring 46 is disposed immediately below the roller member 43. A roller member 43 is coupled to the tip of the piston portion 47 and is urged toward the cam plate 21. That is, the operating point at which the roller member 43 applies work to the cam plate 21 and the operating point at which the piston portion 47 applies work to the roller member 43 are arranged in the vertical direction.

  Note that the gas spring 46 of the rotary shaft support mechanism 40 according to the third embodiment and the gas spring 46 of the rotary shaft support mechanism 40 according to the first embodiment have the same ability. For this reason, the work performed by the gas spring 46 according to the third embodiment is equivalent to the work performed by the gas spring 46 according to the first embodiment, and is different from the camshaft torque (qc) in the above equation (1). There is no. Therefore, also in the rotating shaft support mechanism 46 according to the third embodiment, similarly to the rotating shaft support mechanism 46 according to the first embodiment, the load on the drive mechanism 60 can be efficiently reduced.

  Furthermore, according to the rotating shaft support mechanism 40 according to the third embodiment, the roller member 43 is directly pressed against the cam plate 21 by the gas spring 46, so that the lever member 44 is not required as in the first embodiment. It is possible to reduce the number of parts and the manufacturing cost.

  In the third embodiment, directly pressing the roller member 43 with the gas spring 46 includes the case where the piston portion 47 and the roller member 43 are connected via a plate or the like.

  Also in the rotating shaft support mechanism 40 according to the third embodiment, the rotating shaft 20 is rotatably supported by the bearing 42 and the bearing 42A, and the roller member 43 and the gas spring are interposed between the bearing 42 and the bearing 42A. 46 is arranged.

  For this reason, the displacement of the rotating shaft 20 due to the urging force from the gas spring 46 can be reduced when generating a canceling moment that cancels the offset load moment. As a result, the tilt of the turntable can be reduced and the machining accuracy of the workpiece W can be improved.

  FIG. 11 is a front view showing a modification of the rotary shaft support mechanism 40 shown in FIGS. 8 to 10, and FIG. 12 is a side sectional view of the rotary shaft support mechanism 40 shown in FIG.

  As shown in FIGS. 11 and 12, a gear (cam member) 121 and a gear (cam follow-up member) 143 that meshes with the gear 121 may be employed instead of the cam plate and the roller member. A plurality of tooth portions 121A are formed on the peripheral surface of the gear 121, and a plurality of tooth portions 143A corresponding to the tooth portions 121A are formed on the peripheral surface of the gear 143. The gear 143 is rotatably provided on the housing 145, and the housing 145 is connected to the piston portion 47. Even with such a gear mechanism, the load on the drive mechanism 60 can be efficiently reduced.

  Here, the cam means a plate or a cylindrical mechanical part that transmits motion to the driven part by a groove formed on the edge or the surface. Therefore, the gear 121 is included in the “cam member”, and the gear 143 is included in the “cam following member”.

  The rotary shaft support mechanism including the balancer mechanism described above is not applied only to the indexer device 1. The rotating shaft support mechanism includes a rotating shaft that rotatably supports a crank shaft of a crank mechanism that reciprocally drives a movable plate up and down in a crank press device, a rotating shaft that rotatably supports an arm portion of a robot arm, and the like. The present invention can be applied to various devices having a rotating shaft on which an eccentric load moment acts.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

Claims (8)

A rotary shaft support mechanism for supporting a rotary shaft for supporting a member,
A plurality of rotating shaft support portions that are arranged in a line in the axial direction of the rotating shaft, and rotatably support the rotating shaft;
A turntable provided on the rotating shaft, on which a workpiece is detachably mounted;
A cam member provided on the rotary shaft and provided between the rotary shaft support portions;
A cam follow-up member that contacts the cam member and rotates following the cam member;
A biasing means provided between the plurality of rotating shaft support portions and biasing the cam follower member toward the cam member;
The cam member includes a cam curved surface portion,
The cam curved surface portion is formed such that the center of curvature of the cam curved surface portion and the rotation center are shifted,
The rotating shaft rotates while the work is mounted on the turntable, so that the rotating shaft rotates while the cam follower member and the cam member are in contact with each other.
A rotating shaft support mechanism that pushes up the work and the turntable by a force applied to the cam curved surface portion from the cam following member by abutting the cam following member and the cam curved surface portion . A lever member to which the cam follower member is attached;
A lever member support portion that rotatably supports the lever member;
The rotary shaft support mechanism according to claim 1, wherein the biasing unit biases the cam follower member toward the cam member by rotating the lever member. The biasing means is provided on the opposite side of the lever member support portion with respect to the cam follower member,
The rotating shaft support mechanism according to claim 2, wherein the lever member has a bent portion or a bent portion bent toward the cam member at a portion located between the cam follow-up member and the urging means. . The rotating shaft support is fixed to the casing;
The rotary shaft support mechanism according to claim 1, wherein the cam member and the biasing unit are built in the casing. The rotating shaft support mechanism according to claim 1, wherein the biasing unit is disposed below the cam follower member. The rotating shaft support mechanism according to claim 5, wherein the urging unit includes a pressing member to which the cam follower member is coupled.   The rotating shaft support mechanism according to claim 1, wherein a gas spring is used as the urging means.   The rotating shaft support mechanism according to claim 1, wherein a recess for receiving the cam follower member is provided on a side surface of the cam member.

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