WO2005038291A1 - 回転軸用バランサ機構 - Google Patents
回転軸用バランサ機構 Download PDFInfo
- Publication number
- WO2005038291A1 WO2005038291A1 PCT/JP2003/013388 JP0313388W WO2005038291A1 WO 2005038291 A1 WO2005038291 A1 WO 2005038291A1 JP 0313388 W JP0313388 W JP 0313388W WO 2005038291 A1 WO2005038291 A1 WO 2005038291A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotating shaft
- cam
- rotating
- gas spring
- shaft
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/043—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means acting on a cam follower
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/44—Movable or adjustable work or tool supports using particular mechanisms
- B23Q1/50—Movable or adjustable work or tool supports using particular mechanisms with rotating pairs only, the rotating pairs being the first two elements of the mechanism
- B23Q1/52—Movable or adjustable work or tool supports using particular mechanisms with rotating pairs only, the rotating pairs being the first two elements of the mechanism a single rotating pair
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
- B23Q11/001—Arrangements compensating weight or flexion on parts of the machine
- B23Q11/0017—Arrangements compensating weight or flexion on parts of the machine compensating the weight of vertically moving elements, e.g. by balancing liftable machine parts
- B23Q11/0021—Arrangements compensating weight or flexion on parts of the machine compensating the weight of vertically moving elements, e.g. by balancing liftable machine parts the elements being rotating or pivoting
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/0064—Counterbalancing means for movable press elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/22—Compensation of inertia forces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/22—Compensation of inertia forces
- F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
- F16F15/261—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system where masses move linearly
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2122—Flywheel, motion smoothing-type with fluid balancing means
Definitions
- the present invention relates to a balancer mechanism for reducing a rotational moment acting on a rotating shaft rotatably supported by a shaft support from a member supported by the rotating shaft.
- a rotating shaft is rotatably supported by a shaft supporting portion, and members such as a table unit, a movable platen, and an arm portion are mounted on the rotating shaft. Supported.
- a pair of rotating shafts fixed to a table unit are rotatably supported by a shaft support, and a driving force is input from an electric motor to the rotating shaft, and the table unit is rotated. Driven.
- the table unit is provided with a turntable rotatable around an axis orthogonal to the axis of the rotary shaft and a drive mechanism thereof.
- the work is detachably mounted on the turntable, and the work is machined. Will be applied.
- the workpieces set in the indexer unit are assumed to be workpieces of various shapes and sizes, so the table unit and the center of rotation of the workpiece mounted on the table unit (the axis of the rotating shaft) It is difficult to match the center of gravity. Therefore, the rotational moment due to the unbalanced load of the table unit and the work acts on the rotating shaft, and the load on the electric motor increases.
- Japanese Patent Laid-Open Publication No. 2001-277059 discloses a rotary table provided with a pressing mechanism.
- this pressurizing mechanism an air working hole is formed at the end of the rotating shaft, and first and second pressure receiving surfaces are formed on the wall surface of the hole.
- An air supply member is inserted into the air operation hole of the rotating shaft, and the first or second pressure receiving surface receives pressurized air supplied from the first or second port of the air supply member, and the first or second pressure receiving surface is received by the rotating shaft. 2
- Rotational moment acts in the rotation direction. In this way, a rotating moment for balancing that cancels at least a part of the rotating moment due to the unbalanced load of the rotating table and the work is generated.
- an air working hole is formed at the end of the rotating shaft, first and second pressure receiving surfaces are formed on the wall surfaces of the hole, an air supply member is provided, and the air supply member is connected to the air supply member. Since the air hole and the pressurized air supply device are required to enter the working hole, the structure is complicated and the manufacturing cost is high. In order to cope with the rotational moment that changes according to the rotation angle of the rotating shaft, an air valve and a control device are provided, and the pressure of the pressurized air supplied to the air operation hole is adjusted to adjust the rotational moment for balancing. However, the structure becomes more complicated and the manufacturing cost becomes higher.
- An object of the present invention is to use a gas spring to apply a rotating moment for balancing to cancel at least a part of the rotating moment acting on the rotating shaft to the rotating shaft, and to easily and surely reduce the rotating moment. Reducing the load on the driving mechanism that drives the rotating shaft, improving the responsiveness when rotating and stopping the members supported by the rotating shaft, and increasing the size according to the magnitude of the rotating moment.
- To apply the rotating moment for balancing on the rotating shaft to simplify the structure, and to be easily attached to various existing devices where the rotating moment acts on the rotating shaft from the members supported by the rotating shaft. And so on. Disclosure of the invention
- the present invention relates to a balancer mechanism for reducing a rotating moment acting on a rotating shaft rotatably supported by a shaft supporting portion from a member supported by the rotating shaft, wherein the balancer mechanism is fixed to an end of the rotating shaft.
- a gas spring for applying a rotating torque for balancing to cancel at least a part of the rotational moment on the shaft is provided (claim 1).
- This rotary shaft balancer mechanism is a rotary shaft that rotatably supports a table unit on which a work is detachably mounted in an indexer device, and a crank shaft of a crank mechanism that reciprocates a movable plate up and down in a crank press device.
- the present invention can be applied to a device provided with a rotating shaft on which a rotating moment acts from a member supported by the rotating shaft, such as a rotating shaft for rotatably supporting a rotating shaft, a rotating shaft for rotatably supporting an arm portion of a robot arm, and the like. it can.
- a cam member is fixed to the end of the rotary shaft, and the cam follower is elastically urged toward the cam member by gas spring, and is pressed against and abuts against the cam member, thereby causing the cam follower to abut.
- the member follows a cam member that rotates integrally with the rotation shaft.
- the rotating moment can be easily and reliably reduced.
- the load on the drive mechanism for driving the shaft can be reduced, and the responsiveness when the member supported by the rotating shaft is rotated and stopped is improved.
- the balancer mechanism has a simple structure including the cam member, the cam follower member, and the gas spring, which is advantageous in terms of manufacturing cost. Further, since the member supported by the rotating shaft can be easily attached to various existing devices in which a rotating moment acts on the rotating shaft, the device is excellent in versatility. ⁇ Next, a preferred configuration and a practicable configuration of the configuration of the present invention will be described.
- the force member is formed of a disk member centered on a position eccentric with respect to the axis of the rotation shaft, and the cam follower member is configured to contact the outer peripheral surface of the disk member. Claim 2).
- the cam member can have a simple shape, and the cam following member can smoothly follow the cam member.
- a gas spring applies the rotating moment for balancing to the rotating shaft via a cam follower member and a cam member over substantially the entire range of rotation angles of the rotating shaft of 0 to 360 degrees, thereby rotating the rotating shaft. The moment can be reduced. Further, the magnitude of the rotational moment varies according to the rotational angle of the rotating shaft. However, the input position where the force is input from the cam follower to the cam member by the gas spring, and the direction and magnitude of the force are appropriate. And a rotating moment for balancing having a magnitude corresponding to the magnitude of the rotating moment can be applied to the rotating shaft.
- the cam follower member is a roller member rotatably mounted on the gas spring (Claim 3).
- the roller member (cam follower) is brought into contact with the outer peripheral surface of the disk member (cam member) so that it can follow more smoothly. The wear and damage of the cam member and the cam follower are prevented as much as possible to extend the life. be able to.
- the direction in which the cam follower is biased by the gas spring in a neutral direction is directed toward the axis of the rotating shaft (Claim 4). Since the gas spring can be fixedly mounted, the assembly of the gas spring is simplified, and a rotating moment for balancing having a magnitude corresponding to the magnitude of the rotational moment can be applied to the rotating shaft.
- the elastic biasing force of the gas spring that elastically biases the cam follower toward the cam member that is, the gas pressure in the gas spring
- gas pressure adjusting means for automatically adjusting the gas pressure according to the magnitude of the rotational moment may be provided.
- the direction in which the cam follower is elastically biased by the gas spring, that is, the position (posture) of the gas spring may be adjustable.
- a gas spring position adjusting means for automatically adjusting the position of the gas spring according to the magnitude of the rotational moment may be provided.
- FIG. 1 is a front view of an indexer device provided with a balancer mechanism according to an embodiment of the present invention.
- FIG. 2 is a left side view of the indexer device.
- FIG. 3 is a sectional view taken along the line III-III of FIG.
- FIGS. 4 to 7 are explanatory diagrams of the operation of the rotating shaft balancer mechanism.
- FIG. 4 shows a rotation angle of the rotating shaft of 0 °
- FIG. 5 shows a rotating angle of the rotating shaft of about 30, and
- FIG. 6 shows a rotating shaft.
- the rotation angle of the rotating shaft is 90 degrees
- FIG. 7 shows a state where the rotation angle of the rotating shaft is about 150 degrees.
- FIG. 8 is an explanatory diagram of a balancing rotational moment and the like acting on the rotating shaft.
- FIG. 1 is a front view of an indexer device provided with a balancer mechanism according to an embodiment of the present invention.
- FIG. 2 is a left side view of the indexer device.
- FIG. 10 is a left side view of an indexer apparatus provided with a balancer mechanism according to a modified embodiment. Best shape bear for carrying out the invention
- This embodiment is an example of a case where the rotating shaft balancer mechanism of the present invention is applied to an indexer device for detachably mounting a workpiece to be machined by a machine tool.
- Note that the arrows a and b in FIG. 1 are described as upward and leftward.
- the indexer unit 1 includes a table unit 2, a pair of left and right rotating shafts 3 and 4 fixed to the table unit 2, and a left side including a shaft supporting portion for rotatably supporting the rotating shaft 3.
- the right shaft support mechanism 6, which includes a shaft support part that rotatably supports the shaft support mechanism 5 and the rotation shaft 4, the table unit 2, and the rotation shafts 3 and 4 are turned around the axis A of the rotation shafts 3 and 4.
- a rotary drive mechanism 7 having an electric motor 7a that is driven and driven, and a rotating shaft balancer mechanism 8 unique to the present invention (hereinafter referred to as a balancer mechanism 8) are provided.
- the table unit 2, the rotating shaft 3, and the shaft support mechanism 5 have slightly different structures between FIG. 1 and FIGS. 2 to 7, but are substantially the same, and therefore are described with the same reference numerals.
- the rotation drive mechanism 7 is provided near the right shaft support mechanism 6, and a driving force is input to the rotation shaft 4 from the rotation drive mechanism 7, and the table unit 2 is rotated.
- the tape unit 2 has a turn that can rotate around an axis perpendicular to the axis A of the rotating shafts 3 and 4.
- a table and a drive mechanism (not shown) are provided.
- the work W is detachably mounted on the turntable, and the work W is machined.
- the balancer mechanism 8 includes a rotating shaft 3, 4 rotatably supported by the shaft supporting mechanisms 5, 6, and a rotating mechanism acting from the members (table unit 2 and work W) supported by the rotating shafts 3, 4. This is a mechanism to reduce the moment Ml.
- the balancer mechanism 8 will be described in detail.
- the balancer mechanism 8 includes a cam member 10 fixed to the left end of the rotating shaft 3, and a cam follower member 15 that contacts and follows the cam member 10 from substantially below.
- a gas spring 20 for applying a rotational moment M 2 for balancing which cancels at least a part of M 1 is provided.
- the left end surface of the rotating shaft 3 is exposed to the outside from the left end of the shaft supporting mechanism 5, and a short shaft member 14 eccentric to the axis A of the rotating shaft 3 is fixed to the left end surface of the rotating shaft 3.
- the cam member 10 is fixed to the left end face of the shaft member 14.
- the cam member 10 is composed of a disc member 10 having a center B at a position eccentric with respect to the axis A of the rotating shaft 3, and a cam follower member 15 is provided on an outer peripheral surface of the disc member 10. It is configured to abut.
- the cam follower member 15 comprises a roller member 15 rotatably mounted on a gas spring 20.
- the disk member The center B of 10 is set to be directly below the axis A of the rotating shaft 3 (see Figs. 2 and 4).
- the gas spring 20 is disposed in an upright position below the cam member 10 and the shaft member 14, and the cylinder member 21 of the gas spring 20 is fixed to the frame of the shaft support mechanism 5 by a bracket 19 or the like. Have been. Output member of gas spring 20 0 2 2 Protrudes upward from the cylinder member 21, and is elastically urged upward by a pressurizing roller filled in the cylinder member 21. A bracket 25 is fixed to the upper end of the output member 22. Both ends of a roller shaft 26 oriented in the left-right direction are fixed to the bracket 25, and the roller member 15 is rotatably supported by the roller shaft 26.
- the balancing rotational moment M2 acting on the rotating shaft 3 will be described with reference to FIG.
- the radius of the disk member 10 is R and the radius of the roller member 15 is! :
- the eccentricity of the center B of the disk member 10 is m
- the angle of ZACB is 0,
- the urging force for elastically urging the roller member 15 upward by the gas spring 20 is F.
- the trajectory of the center B of the disk member 10 is a circle t, and 0 changes in a range of 0 to about 25 degrees.
- the rotating angle 0a of the rotating shaft 3 when B is located at the lowermost position is 0 degrees
- ⁇ is the minimum angle
- the rotation angle ⁇ a of the rotating shaft 3 is 90 degrees or 270 degrees
- a force f F Xcos ⁇ from p to B is input from the roller member 15 to the disc member 10.
- M2 F Xcos ⁇ X [(R + r) Xcos ⁇ + [(R + r) 2 Xcos 2 ⁇ — (R + r) 2 + m 2 ] 1/2 ] Xsin ⁇
- M2 F Xcos ⁇ X [21/6 X r Xcos ⁇ + (21 2/6 2 X cos 2 ⁇ X r 2 - 21 2/6 2 +8 2/6 2 X r 2 ) 1/2 ] X sin ⁇
- a cam member 10 consisting of a disk member 10 having a center B at a position eccentric with respect to the axis ⁇ of the rotating shaft 3 is fixed to the left end of the rotating shaft 3.
- a gas spring 20 is disposed in a vertical position below the cam member 10, and a cam follower member 15 including a roller member 15 rotates at an upper end of the output member 22 of the gas spring 20. It is freely attached.
- the cam follower member 15 is elastically urged toward (upward) the cam member 10 by the gas spring 20 and is pressed against the outer peripheral surface of the cam member 10 to come into contact therewith. It follows the cam member 10 that rotates integrally with 3.
- the magnitude of the rotating moment Ml acting on the rotating shaft 3 changes according to the rotating angle 0a of the rotating shaft 3, and when the maximum value of the rotating moment Ml is Mo, the magnitude of the rotating moment Ml is The size is IM o sin ga
- the rotation angle of the rotating shaft 3 is 0 a.
- the force increases between 0 and 90 degrees.
- the rotational moment Ml increases, and the rotational moment M2 for balancing also increases.
- the rotation angle 0a of the rotation shaft 3 decreases between 90 and 180 degrees, the rotation moment Ml decreases, and the rotation for balancing The moment M 2. also decreases.
- the rotating torque M 2 for canceling at least a part of the rotational moment M 1 is applied to the rotating shaft 3 using the gas spring 20.
- the rotational moment Ml can be easily and reliably reduced, and therefore, the load on the rotary drive mechanism 7 for driving the rotary shaft 4 is reduced, and the table supported by the rotary shafts 3 and 4 The responsiveness when the unit 2 and the work W are rotated and stopped is improved.
- the balancer mechanism 8 has a simple structure including the cam member 10, the cam follower member 15, and the gas spring 20, which is advantageous in terms of manufacturing cost. Furthermore, the member supported by the rotating shaft can be easily attached to various existing devices in which a rotating moment acts on the rotating shaft and used, and the versatility is improved.
- the cam member 10 is composed of a disk member 10 having a center B at a position eccentric with respect to the axis A of the rotating shaft 3, and a force follower member 15 contacts the outer peripheral surface of the disk member 10. Since it is configured to be in contact, the cam member 10 can be formed in a simple shape, and the cam follower member 15 can smoothly follow the cam member 10.
- the gas spring 20 applies the rotation angle ⁇ a of the rotating shaft 3 to the rotating shaft 3 via the cam follower member 15 and the cam member 10 over substantially the entire range of 0 to 360 degrees. By applying the rotating moment M2 for balancing, the rotating moment M1 can be reduced.
- the magnitude of the rotation moment ⁇ 1 changes according to the rotation angle ⁇ a of the rotating shaft 3, but a force is input from the cam follower member 15 to the cam member 10 by the gas spring 20.
- the balancing rotational moment M2 having a magnitude corresponding to the magnitude of the rotational moment Ml can be reliably applied to the rotating shaft 2.
- the cam follower member 15 is composed of the roller member 15 rotatably mounted on the gas spring 20, the roller member 15 is brought into contact with the outer peripheral surface of the disk member 10 to form a more circular shape.
- the cam member 10 and the cam follower member 15 can be smoothly followed and wear and damage of the cam member 10 and the cam follower member 15 can be prevented as much as possible to extend the life.
- the gas spring 20 Since the direction in which the force follower member 15 is elastically urged by the gas spring 20 is directed toward the axis A of the rotating shaft 2, the gas spring 20 can be fixed and mounted. The assembling of the spring 20 is simplified, and the rotating torque M2 for balancing having a magnitude corresponding to the magnitude of the rotational moment Ml can be reliably applied to the rotary shaft 2.
- a hydraulic cylinder 40 A may be provided, and the hydraulic cylinder may be provided with an accumulator 45 for supplying a substantially constant hydraulic pressure to 4 OA. Good.
- the hydraulic cylinder 40 and the accumulator 45 force the rubber follower member 15 toward the cam member 10, and the rotational moment M is applied to the rotating shaft 3 via the cam follower member 15 and the cam member 10.
- a balancing rotational moment M2 that cancels at least a part of l is applied.
- the hydraulic cylinder 40 is disposed in an upright position below the cam member 10 and the shaft member 14, and the cylinder member 41 of the hydraulic cylinder 40 is supported by a bracket 19 or the like. Fixed to 5 frames.
- the output member 4 2 (piston rod 42) of the hydraulic cylinder 40 protrudes upward from the cylinder member 41, and hydraulic pressure is supplied to the hydraulic working chamber (not shown) in the cylinder member 41 by the accumulator 45 to output.
- the member 42 is urged toward the cam member 10 (upward).
- a roller member 15 (cam follower member 15) is rotatably mounted on the upper end of the output member 42.
- the other configuration, operation, and effect of the balancer mechanism 8A are the same as those of the balancer mechanism 8.
- the cam member 10 does not need to be a disk member so that the cam follower member 15 comes into contact with the rotating shaft 3 and the rotating moment M2 acts on the rotating shaft 3. It may be configured in various shapes such as an elliptical plate member, a partial elliptical plate member, and the like.
- the roller member 15 it is not necessary to use the roller member 15, and it may be configured as a follower that can simply contact and follow the force member 10.
- the mounting positions and postures of the gas spring 20 and the hydraulic cylinder 40 can be changed as appropriate.
- the gas spring 20 and the hydraulic cylinder 40 may be mounted on the side of the cam member 10 in a horizontal position, or the gas spring 20 and the hydraulic cylinder 40 may be mounted on the cam member 10 in a downward position. Good.
- a pair of balancer mechanisms 8 and 8 A may be provided corresponding to the pair of rotating shafts 3 and 4 so that rotating moments for balancing act on the rotating shafts 3 and 4.
- a plurality of balancer mechanisms 8, 8A may be provided for each of the rotating shafts 3, 4.
- the elastic biasing force of the gas spring 20 for elastically biasing the cam follower member 15, that is, the gas pressure of the gas spring 20 ⁇ may be adjustable.
- gas pressure adjusting means including a pressure adjusting valve and a control device for automatically adjusting the gas pressure according to the size of the rotation moment Ml may be provided.
- the direction in which the cam follower 15 is elastically biased by the gas spring 20 and the hydraulic cylinder 40, that is, the position (posture) of the gas spring 20 and the hydraulic cylinder 40 may be adjustable.
- a position adjusting means including a position adjusting mechanism and a control device for automatically adjusting the positions of the gas spring 20 and the hydraulic cylinder 40 according to the magnitude of the rotational moment Ml may be provided.
- the above-mentioned balancer mechanisms 8, 8A are used not only in the indexer unit 1, but also in the rotary shaft and ropot arm for rotatably supporting the crankshaft of the crank mechanism for reciprocating the movable platen up and down in the crank press device.
- the present invention can be applied to various devices having a rotating shaft on which a rotating moment acts from a member supported by the rotating shaft, such as a rotating shaft rotatably supporting the arm portion.
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Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2003/013388 WO2005038291A1 (ja) | 2003-10-20 | 2003-10-20 | 回転軸用バランサ機構 |
EP03754202A EP1677028A4 (en) | 2003-10-20 | 2003-10-20 | BALANCING MECHANISM FOR A ROTARY SHAFT |
JP2005509611A JPWO2005038291A1 (ja) | 2003-10-20 | 2003-10-20 | 回転軸用バランサ機構 |
CNA2003801103058A CN1771402A (zh) | 2003-10-20 | 2003-10-20 | 旋转轴用平衡器机构 |
AU2003273058A AU2003273058A1 (en) | 2003-10-20 | 2003-10-20 | Balancer mechanism for rotating shaft |
US10/561,289 US20060185470A1 (en) | 2003-10-20 | 2003-10-20 | Balancer mechanism for rotating shaft |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2003/013388 WO2005038291A1 (ja) | 2003-10-20 | 2003-10-20 | 回転軸用バランサ機構 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005038291A1 true WO2005038291A1 (ja) | 2005-04-28 |
Family
ID=34452324
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/013388 WO2005038291A1 (ja) | 2003-10-20 | 2003-10-20 | 回転軸用バランサ機構 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20060185470A1 (ja) |
EP (1) | EP1677028A4 (ja) |
JP (1) | JPWO2005038291A1 (ja) |
CN (1) | CN1771402A (ja) |
AU (1) | AU2003273058A1 (ja) |
WO (1) | WO2005038291A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2009131082A1 (ja) * | 2008-04-21 | 2009-10-29 | 津田駒工業株式会社 | インデックステーブル |
JP2010173000A (ja) * | 2009-01-29 | 2010-08-12 | Kondo:Kk | 一対の給油孔を備えたドリル用ワーク、及び孔付ワークの芯出し方法、並びに芯出し装置 |
WO2016143408A1 (ja) * | 2015-03-12 | 2016-09-15 | パスカルエンジニアリング株式会社 | 回転軸用バランサ機構 |
JP2016221648A (ja) * | 2015-06-02 | 2016-12-28 | パスカルエンジニアリング株式会社 | バランサ機構 |
JP2017030100A (ja) * | 2015-08-03 | 2017-02-09 | パスカルエンジニアリング株式会社 | 回転軸用バランサ装置 |
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GB2478302B (en) * | 2010-03-02 | 2012-02-15 | Cinetic Landis Ltd | A machine axis including a counterbalance and methods of operation thereof |
WO2011128988A1 (ja) * | 2010-04-14 | 2011-10-20 | トヨタ自動車株式会社 | ダイナミックダンパ |
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- 2003-10-20 WO PCT/JP2003/013388 patent/WO2005038291A1/ja active Application Filing
- 2003-10-20 CN CNA2003801103058A patent/CN1771402A/zh active Pending
- 2003-10-20 AU AU2003273058A patent/AU2003273058A1/en not_active Abandoned
- 2003-10-20 JP JP2005509611A patent/JPWO2005038291A1/ja active Pending
- 2003-10-20 EP EP03754202A patent/EP1677028A4/en not_active Withdrawn
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US5544576A (en) * | 1993-10-26 | 1996-08-13 | Sankyo Seisakusho Co. | Mechanical pressing machine having a load fluctuating torque cancelling device |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009131082A1 (ja) * | 2008-04-21 | 2009-10-29 | 津田駒工業株式会社 | インデックステーブル |
JP2009255266A (ja) * | 2008-04-21 | 2009-11-05 | Tsudakoma Corp | インデックステーブル |
US8528447B2 (en) | 2008-04-21 | 2013-09-10 | Tsudakoma Kogyo Kabushiki Kaisha | Index table |
KR101365335B1 (ko) * | 2008-04-21 | 2014-02-19 | 쓰다고마 고교 가부시끼가이샤 | 인덱스 테이블 |
JP2010173000A (ja) * | 2009-01-29 | 2010-08-12 | Kondo:Kk | 一対の給油孔を備えたドリル用ワーク、及び孔付ワークの芯出し方法、並びに芯出し装置 |
WO2016143408A1 (ja) * | 2015-03-12 | 2016-09-15 | パスカルエンジニアリング株式会社 | 回転軸用バランサ機構 |
US10252387B2 (en) | 2015-03-12 | 2019-04-09 | Pascal Engineering Corporation | Balancer mechanism for rotating shaft |
JP2016221648A (ja) * | 2015-06-02 | 2016-12-28 | パスカルエンジニアリング株式会社 | バランサ機構 |
JP2017030100A (ja) * | 2015-08-03 | 2017-02-09 | パスカルエンジニアリング株式会社 | 回転軸用バランサ装置 |
Also Published As
Publication number | Publication date |
---|---|
US20060185470A1 (en) | 2006-08-24 |
JPWO2005038291A1 (ja) | 2007-01-11 |
AU2003273058A1 (en) | 2005-05-05 |
CN1771402A (zh) | 2006-05-10 |
EP1677028A1 (en) | 2006-07-05 |
EP1677028A4 (en) | 2007-09-26 |
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