WO2008029453A1

WO2008029453A1 - Rotary shaft supporting mechanism

Info

Publication number: WO2008029453A1
Application number: PCT/JP2006/317617
Authority: WO
Inventors: Ichiro Kitaura
Original assignee: Pascal Engineering Corporation
Priority date: 2006-09-06
Filing date: 2006-09-06
Publication date: 2008-03-13
Also published as: JPWO2008029453A1; JP5021652B2

Abstract

A rotary shaft supporting mechanism supports a rotary shaft (20) for supporting a work. The rotary shaft supporting mechanism comprises bearings (42) so provided as to be juxtaposed in the axial direction (in the direction of the arrow DR1) of the rotary shaft (20) and rotatably supporting the rotating shaft (20), roller members (43) abutting onto cam plates (21) serving as 'cam members' provided on the rotating shaft (20) and rotated following to the plates (21), and gas springs provided between the bearings (42) and biasing the roller members (43) toward the cam plates (21).

Description

Specification

Rotating shaft support mechanism

Technical field

TECHNICAL FIELD [0001] 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.

[0002] Conventionally known is a structure in which a rotating shaft is rotatably supported. 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, the driving force is also input to the rotating shaft, and the table unit is driven to rotate. 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.

[0003] Since workpieces to be set in the indexer device are planned to have various shapes and sizes, the center of gravity of the table unit and the workpiece mounted on the unit and the axis of the rotating shaft must be matched. It is difficult. 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.

[0004] In contrast, in WO 2005Z038291 pamphlet (Patent Document 3), using a gas spring, a rotational torque for balancing (hereinafter, “ A balancer mechanism capable of reducing the offset load moment by causing the offset moment to act on the rotating shaft is disclosed.

Patent Document 1: Japanese Patent Laid-Open No. 2005-28539

Patent Document 2: Japanese Utility Model Publication No. 6-3531

Patent Document 3: International Publication No. 2005Z038291 Pamphlet

Disclosure of the invention

Problems to be solved by the invention [0005] 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 will increase and as a result, the machining accuracy of the workpiece will decrease. Also in Patent Documents 1 and 2, a configuration for solving such a problem is disclosed.

[0006] The present invention has been made in view of the above-described problems, and an object of the present invention is to reduce the rotation by the biasing force of the biasing means force when reducing the influence of the rotational moment due to the unbalanced load. An object of the present invention is to provide a rotating shaft support mechanism capable of reducing the displacement of the shaft.

Means for solving the problem

[0007] 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 arranged in the axial direction of the rotary shaft, and the rotary shaft can be rotated. A rotation shaft support portion that supports the cam member, a cam follower member that contacts and rotates with the cam member provided on the rotation shaft, and a plurality of rotation shaft support portions. Biasing means for biasing the follower member toward the cam member.

[0008] According to the above configuration, the displacement of the rotating shaft due to the urging force of the urging means force can be reduced when reducing the influence of the rotating moment due to the offset load. As a result, the rotational axis is reduced and the position of the member can be accurately determined.

[0009] 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. By moving the cam follower member, the cam follower member is biased toward the cam member.

[0010] According to the above configuration, the urging force by the urging means can be amplified and transmitted to the cam following member. In addition, since the lever member is provided, the center of the cam member and the biasing means can be offset, so that the overall height of the rotating shaft support mechanism can be lowered and the apparatus can be miniaturized.

[0011] 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 a portion located between the cam follower member and the biasing means. In addition, the cam member has a bent portion or a bent portion which is bent by a force.

[0012] According to the above configuration, the space around the cam member can be effectively used to reduce the size of the rotating shaft support mechanism. 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 urging means are built in the casing.

[0014] Thereby, the entry 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 follow-up member as it is. In the above rotating shaft support mechanism, preferably, the urging member has a pressing member to which a cam follow-up member is coupled. Thus, the number of parts can be reduced while maintaining the output torque.

[0015] In the rotating shaft support mechanism, a gas spring is preferably used as the biasing 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 the 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.

[0017] In the rotating shaft support mechanism, as an example, a recess for receiving the cam follow-up member is provided on a side surface of the cam member. As a result, the target rotational position of the rotating shaft can be easily indexed.

The invention's effect

[0018] According to the present invention, in the rotating shaft support mechanism, when generating a moment that cancels the rotating moment due to the eccentric load, the displacement of the rotating shaft due to the biasing force from the biasing means can be reduced. .

Brief Description of Drawings

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

FIG. 2 is a cross-sectional view showing a rotating shaft support mechanism according to one embodiment 1 of the present invention.

FIG. 3 is a view of the rotating shaft support mechanism shown in FIG.

FIG. 4 is a diagram showing a planar shape of a cam plate. FIG. 5 is a view showing a modification of the planar shape of the cam plate.

FIG. 6 is a diagram for explaining a relationship between a rotation angle of a rotation shaft and a gas spring stroke.

FIG. 7 is a cross-sectional view of an indexer device including a rotary shaft support mechanism according to Embodiment 2 of the present invention.

FIG. 8 is a front view of a rotary shaft support mechanism according to the third embodiment.

9 is a cross-sectional view of the rotating shaft support mechanism shown in FIG.

FIG. 10 is a front view of the indexer device when the rotary shaft has made a half turn from the state shown in FIG.

FIG. 11 is a front view showing a modification of the rotating shaft support mechanism shown in FIG.

12 is a cross-sectional view of the rotary shaft support mechanism shown in FIG.

Explanation of symbols

[0020] 1 indexer device, 10 table unit, 20, 30 rotating shaft, 21 cam plate, 21 A cam curved surface portion, 21B R curved surface portion, 21C V notch, 22 end plate, 40, 50 rotating shaft support mechanism, 41 casing , 42 Bearing, 43 Roller member, 44 Lever part, 44A Recessed part, 44B Bent part, 45 pin, 46 Gas spring, 60 Drive mechanism, 0a Rotation angle.

BEST MODE FOR CARRYING OUT THE INVENTION

[0021] (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 symbols, 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 1 of the present invention.

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

[0024] The table unit 10 includes a turntable that can rotate around the axes of the rotary shafts 20 and 30, and a drive mechanism thereof. A workpiece W is detachably mounted on the turntable. The tab nole unit 10 is supported on the rotary shafts 20 and 30. And the rotating shafts 20, 30 rotate It is supported by shaft support mechanisms 40, 50. In the example of FIG. 1, the rotary shaft 30 is rotationally driven by a drive mechanism 60 that also serves as an electric motor, for example. As a result, the table unit 10 and the workpiece W rotate. The rotating shaft is stopped at the index position (target rotation position), and the workpiece W is machined at this position. The drive mechanism 60 may drive the rotary shaft 20 to rotate, or may drive both the rotary shafts 20 and 30 to rotate.

[0025] Here, the center of gravity of the table unit 10 and the workpiece W and the axes of the rotary shafts 20 and 30 do not necessarily match. Therefore, as the rotary shafts 20 and 30 rotate, the rotational moment (uneven load moment) due to the 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.

[0027] The rotating shaft support mechanism according to the first embodiment includes a balancer mechanism that cancels at least a part of the offset load moment, as described below.

Referring to FIGS. 2 and 3, cam plate 21 and end plate 22 are attached to rotating shaft 20. The rotating shaft support mechanism 40 includes a casing 41, a bearing 42, a roller member 43, a reno-grid material 44, a pin 45, and a gas spring 46.

[0029] The rotary 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 (arrow DR1 direction). The force 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 up and down (in the direction of the arrow DR2). The roller member 43 rotates following the rotation of the cam plate 21. The lever member 44 is provided with a recess 44A, and the roller member 43 is provided in the recess 44A of the lever member 44. Recess 44A functions as a “lubricant reservoir”. One end of the lever member 44 is rotatably supported on the casing by a pin 45. The other end of the lever member 44 is supported by a gas spring 46. Gass The roller member 43 is biased toward the cam plate 21 by the pulling 46. The uniform member 43 contacts 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 portion of the lever member 44 located between the roller member 43 and the gas spring 46 is provided with a bent portion 44B that is bent toward the cam plate 21.

[0030] 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 rotary 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 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. Can be reduced.

[0032] Incidentally, in general, the cam shaft torque (qc) generated by the work of the cam is obtained by the equation (1).

qc = (k-yh2) / 0 h X (S XV) + F0-yh / Θ h XV- (1)

k: Spring constant of gas spring

yh: Stroke (y: Spring displacement)

th: Rise time (t: time)

S: yz yh

V: (dy / dt) / (yh / th)

Θ h: Assignment angle (the angle at which the cam works)

F0: Gas spring initial load

In (1), inertia torque, viscous resistance, and frictional resistance are ignored.

[0033] By substituting S and V when S XV and V are maximum, respectively into the above equation (1), the maximum value of the force shaft torque is obtained. For the indexer device 1 according to the first embodiment! / In the meantime, when V is maximum, qc is maximum. This maximum value of qc and rotational moment The load on the drive mechanism 60 can be reduced most efficiently by making the heads substantially coincide with each other. The maximum value of qc can be adjusted as appropriate, for example, by changing the spring constants k and F0 of the gas spring.

FIG. 4 is a diagram showing a planar shape of the cam plate 21. Referring to FIG. 4, cam plate 21 has cam curved surface portion 21A (the portion where the rotation center and R center do not coincide) and R curved surface portion 21B (the portion where the rotation center and R center coincide). Including. The R curved surface portion 21B is provided at a position shifted by 90 ° in the circumferential direction. In the example of FIG. 6, since the gas spring 46 is displaced with respect to the cam plate 21 in the cam curved surface portion 21A, the gas spring 46 performs work. 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. In this way, when the rotary shaft is stopped at the index position, the latitudinal member 43 pushes the central portion of the cam plate 21 straight up, so that no rotational torque is generated. Therefore, an unintended twisting force is suppressed from acting on the workpiece W sandwiched between the table unit 10 and the counterpart member (for example, the index table) during the mechanical caulking. 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 rotational position can be easily indexed. Instead of the V notch 21C, a concave portion having a curved surface (R shape) on the bottom surface may be provided.

FIG. 6 is a view for explaining the relationship between the rotation angle Θa of the rotating shaft and the stroke of the gas spring 46. By rubbing 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 Lf standing is set every 90 ° of rotation angle 0a, and every 90 ° of rotation angle Θa. An allocation angle Θh of 80 ° is set. Note that the interval between the index positions can be appropriately changed, for example, 60 ° or 120 °. Similarly, the allocation angle Θh can be changed as appropriate. A plurality of index positions may be arranged at unequal angle intervals.

[0036] The contents described above are summarized as follows. That is, in the first embodiment The rotary shaft support mechanism 40 is a rotary shaft support mechanism that supports the rotary shaft 20 that supports the workpiece W as a “member”, and a plurality of the rotary shaft support mechanisms 40 are provided so as to be aligned in the axial direction of the rotary shaft 20 (arrow DR1 direction). The cam plate 21 is in contact with a bearing 42 as a “rotating shaft support portion” that rotatably supports the rotating shaft 20 and a cam plate 21 as a “cam member” provided on the rotating shaft 20. The roller member 43 as a “cam follower member” that rotates following the roller and a plurality of bearings 42, as “biasing means” that biases the roller member 43 toward the cam plate 21. Gas spring 46 is provided.

[0037] 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 with a low spring constant. Therefore, the load fluctuation due to the stroke of the gas spring 46 is relatively low.

[0038] Further, from a viewpoint different from the above, the rotating shaft support mechanism 40 according to the first embodiment includes a bearing 42 that rotatably supports the rotating shaft 20, and a cam plate provided on the rotating shaft 20. Roller member 43 that contacts 21 and rotates following cam plate 21, lever member 44 to which roller member 43 is mounted, and `` lever member support part '' that supports lever member 44 in a rotatable manner A pin 45 and a gas spring 46 that urges the roller member 43 toward the cam plate 21 by rotating the lever member 44 are 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, a canceling moment that cancels the offset load moment can be effectively generated. Further, by providing the lever member 44, the center of the cam plate 21 and the gas spring 46 can be offset, so that the overall height of the rotary shaft support mechanism 40 can be reduced and the apparatus can be downsized. .

In the rotating 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 44B bent toward the cam plate 21 is formed in a portion of the lever member 44 located between the roller member 43 and the gas spring 46. By doing so, the space around the cam plate 21 can be effectively utilized to further reduce the overall height of the rotary shaft support mechanism 40. It should be noted that a “bay curved portion” may be provided instead of the bent portion 44B.

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

[0043] As the "biasing means", a hydraulic cylinder may be provided instead of the gas spring 46, and an accumulator for supplying a substantially constant pressure to the hydraulic cylinder may be provided. Further, the mounting position and posture of the urging means can be changed as appropriate. For example, the urging means may be placed downward and attached above the lever member 44. Further, the urging force of the urging means may be adjusted according to the magnitude of the offset 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 rotary shaft support mechanism 40 has been mainly described. However, a similar balancer mechanism may be included in the rotary shaft support mechanism 50. In the above example, the rotating shaft support mechanism 40 is provided with one cam plate 21 and one roller member 43. However, the rotating shaft support mechanism 40 has a plurality of cam plates 21 and roller members that abut on the cam plate 21. 43 is provided.

[0045] (Embodiment 2)

FIG. 7 illustrates the indexer device 100 according to the second embodiment. Note that the same components as those shown in FIGS. 1 to 6 are denoted by the same reference numerals and description thereof is 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 on the rotating shaft 20 in a cantilever state.

[0047] 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 composed of a bearing (rotary shaft support portion) 42 arranged at an interval in the axial direction of the rotary shaft 20 (arrow DR1 direction) and a rotation located between the bearings 42. Outer circumference of shaft 20 And a cam plate 21 provided on the surface.

[0048] 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 that presses the roller member 43 against the cam plate (cam member). Force means) 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.

[0050] 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.

[0051] By accommodating the motor 80 and the gas spring 46 in one rotating shaft support mechanism 70 as described above, the shaft length of the rotating shaft 20 can be shortened, and the torsional distortion generated in the rotating shaft 20 can be reduced. In addition, vibration vibration can be reduced.

[0052] Further, by positioning the motor 80 and the cam plate in the pair of bearings, the number of bearings can be reduced, the frictional resistance generated in the rotating shaft 20 can be reduced, and the load on the motor 80 is reduced. Can be reduced.

[0053] (Embodiment 3)

The indexer device provided with the rotating shaft support mechanism 40 according to the third embodiment will be described with reference to FIG. 8 and FIG. Note that the same components as those shown in FIGS. 1 to 7 are denoted by the same reference numerals and description thereof is omitted. FIG. 8 is a front view of the rotary shaft support mechanism 40 according to the third embodiment, and FIG. 9 is a side sectional view of the rotary 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 with the cam plate 21 provided on the rotary shaft 2 in the axial direction of the rotary shaft 2 as shown in FIG. A bearing 42 and a bearing 42A that rotatably support the shaft 2, 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. I have.

The gas spring 46 includes a cylinder part 48 fixed to the casing 41 and a piston part 47 inserted into the cylinder part 48 so as to be able to advance and retreat. A high pressure gas is sealed in the cylinder portion 48. Note that, in the rotating shaft support mechanism 40 according to the third embodiment, the cam plate 21 has a disk shape whose center is located at a position away from the rotating shaft of the rotating 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 collects work on the roller member 43 are arranged in the vertical direction.

[0057] The gas spring 46 of the rotating shaft support mechanism 40 according to the third embodiment and the gas spring 46 of the rotating shaft support mechanism 40 according to the first embodiment have the same ability. To do. 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 cam shaft torque (qc) in the above equation (1). There is no. Therefore, also in the rotating shaft support mechanism 46 according to the third embodiment, as with the rotating shaft support mechanism 46 according to the first embodiment, the load on the drive mechanism 60 can be efficiently reduced.

[0058] 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 one member as in the first embodiment. The number of parts can be reduced and the manufacturing cost can be reduced without requiring 44.

In the third embodiment, the direct pressing of the roller member 43 by 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.

[0060] 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 is interposed between the bearing 42 and the bearing 42A. And a gas spring 46 is arranged.

For this reason, when generating a canceling moment that cancels the offset load moment, the displacement of the rotating shaft 20 due to the biasing force from the gas spring 46 can be reduced. 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. It is. [0063] As shown in FIGS. 11 and 12, a gear (cam member) 121 and a gear (cam follow-up member) 143 engaged with the gear 121 may be used 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.

[0064] Here, the cam (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 rotating shaft support mechanism including the balancer mechanism described above is not applied only to the indexer device 1. The rotary shaft support mechanism includes a rotary 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 rotary shaft that rotatably supports an arm portion of a robot arm, and the like. In addition, the present invention can be applied to various devices having a rotating shaft on which an eccentric load moment works.

[0066] The power described for the embodiment of the present invention has been described above. It should be understood that the embodiment disclosed herein is illustrative and not restrictive in all respects. 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

The scope of the claims

[1] A rotary shaft support mechanism that supports a rotary shaft that supports a member,

A plurality of rotation shafts arranged in the axial direction of the rotation shaft, and a rotation shaft support portion for rotatably supporting the rotation shaft;

A cam follower member that abuts on a cam member provided on the rotating shaft and rotates following the cam member;

A rotation shaft support mechanism, comprising: an urging unit that is provided between the plurality of rotation shaft support portions and urges the cam follower member toward the cam member.

[2] a lever member to which the cam follower member is attached;

A lever member supporting portion that rotatably supports the lever member; and the biasing unit biases the cam follower member toward the cam member by rotating the lever member. Item 2. The rotating shaft support mechanism according to Item 1.

[3] The urging means is provided on the opposite side of the lever support portion with respect to the cam following member,

The rotary shaft support according to claim 2, wherein the lever member has a bent portion or a curved portion bent by a force directed to the cam member at a portion located between the cam follow-up member and the biasing means. mechanism.

[4] The rotating shaft support is fixed to the casing,

The rotating shaft support mechanism according to claim 1, wherein the cam member and the biasing unit are built in the casing.

5. The rotating shaft support mechanism according to claim 1, wherein the urging member is disposed below the cam follower member.

6. The rotating shaft support mechanism according to claim 5, wherein the urging member has a pressing member to which the cam follower member is coupled.

7. The rotating shaft support mechanism according to claim 1, wherein a gas spring is used as the urging means.

8. The rotating shaft support mechanism according to claim 1, wherein the rotating shaft supports a turntable for machining. 9. 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.