WO2006030768A1 - 負荷感応推力増幅機構を持つ動力伝達方法及び装置 - Google Patents
負荷感応推力増幅機構を持つ動力伝達方法及び装置 Download PDFInfo
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- WO2006030768A1 WO2006030768A1 PCT/JP2005/016818 JP2005016818W WO2006030768A1 WO 2006030768 A1 WO2006030768 A1 WO 2006030768A1 JP 2005016818 W JP2005016818 W JP 2005016818W WO 2006030768 A1 WO2006030768 A1 WO 2006030768A1
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- Prior art keywords
- female screw
- moving case
- feed screw
- screw
- load
- Prior art date
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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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
- F16H25/2285—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rings engaging the screw shaft with the inner perimeter, e.g. using inner rings of a ball bearing
- F16H25/229—Eccentric rings with their axis arranged substantially parallel to the screw shaft axis
-
- 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
- B30B1/18—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 screw means
-
- 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
- B30B1/18—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 screw means
- B30B1/186—Control arrangements
-
- 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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/2021—Screw mechanisms with means for avoiding overloading
-
- 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
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S100/00—Presses
- Y10S100/903—Pelleters
- Y10S100/904—Screw
-
- 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
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
- Y10T74/18296—Cam and slide
- Y10T74/18304—Axial cam
- Y10T74/18312—Grooved
- Y10T74/18328—Alternately rotated screw
-
- 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
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
-
- 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
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
-
- 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
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
- Y10T74/186—Alternate power path operable on failure of primary
-
- 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
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
- Y10T74/18624—Plural inputs, single output
Definitions
- the present invention relates to a power transmission method and apparatus for converting rotational motion into linear motion. More specifically, it is used when a required pressure is applied to the target object by linear motion.It moves at a high speed while moving from a stationary state to contact with the target object. After touching or restraining the target object, the load force is detected by the load force sensing mechanism using the panel, and when the load force exceeds the set load, the moving speed is autonomously reduced and high thrust is efficiently generated.
- the present invention relates to a power transmission method and apparatus, and a pressurizing apparatus.
- a press device using a pneumatic cylinder has the advantage that a stable pressure can be obtained by supplying pressurized compressed air to the cylinder, and that the mechanism is simple and can be manufactured relatively inexpensively.
- compressed air as a power source is required, and an air compressor must be installed.
- press fitting and force The amount of power required for the work is a force determined by the applied pressure at the work position and the moving speed.
- the thrust of the pneumatic cylinder is determined by the product of the cross-sectional area of the cylinder and the supplied air pressure. Air compression energy corresponding to the sum of the volume of the free running distance to the operating position and the volume of the return stroke is wasted.
- Patent Document 1 Power Transmission Method and Device for Converting Rotational Motion to Straight Movement
- Patent Document 2 Japanese Patent Laid-Open No. 11 15 1632 “ Machine "(Patent Document 2).
- Patent Document 1 JP-A-5-164209
- Patent Document 2 JP 11 151632 A
- Patent Document 3 Japanese Patent Laid-Open No. 61-180064
- the present invention has been made in view of the above-described problems, and with a simple mechanism, it is possible to autonomously switch the speed of linear movement and amplify the thrust, thereby reducing the cost of power.
- a method according to the present invention is a power transmission method for converting the rotational motion of an electric motor into linear motion.
- a feed screw that is rotated by the output of the electric motor, and the feed screw is provided so as to pass through in the axial direction and is rotatable relative to the feed screw, and generates a thrust along the axial direction of the feed screw.
- a moving case for transmitting to a load, and a female that is disposed inside the moving case, has an effective diameter larger than the effective diameter of the feed screw, and eccentrically engages with the feed screw to generate the thrust.
- the device according to the present invention is a device that converts the rotational motion of an electric motor into a linear motion, and has a feed screw connected to the output shaft of the motor for rotation, and an effective diameter larger than the effective diameter of the feed screw.
- a female case a moving case constrained in relative rotation with respect to the rotation of the feed screw, and a radial direction and an axial direction so that the female screw can rotate and slide in the axial direction within the moving case.
- the feed screw passes through bearings installed at both ends of the movable case, the feed screw and the female screw incorporated in the movable case are arranged eccentrically, and the movable case is loaded with force.
- the reaction force of When the thrust generated in the female screw becomes larger than the pressing force by the panel element, the female plate moves in the axial direction with respect to the moving case, so that the brake plate is moved to one of the moving cases.
- the inner side force is released, and this causes the moving screw of the female screw to move.
- the power transmission device is configured such that the restriction of the relative rotation with respect to the base is released, and the feed screw and the female screw rotate in a differential manner.
- the initial pressing force of the panel element is set to be equal to or less than a force for moving the female screw by a rotational torque of the feed screw in a state where the rotation of the female screw is constrained, and at the maximum deflection of the panel element.
- This spring force is made larger than the thrust generated by the differential rotation caused by the rotation of the female screw.
- the cross-sectional shape of the portion of the feed screw connected to the output shaft of the electric motor is a polygon.
- a load conversion unit for detecting an axial pressure force and converting it into an electrical signal is integrally provided on the end surface of the moving case.
- An apparatus is a power transmission device that converts a rotational motion of an electric motor into a linear motion and transmits the linear motion to a load, wherein the feed screw that rotates by the output of the motor and the feed screw are in the axial direction.
- a female screw having an effective diameter larger than the effective diameter of the feed screw and eccentrically screwing with the feed screw to generate the thrust; and provided inside the moving case, the female screw being attached to the moving case
- a bearing that is rotatably supported relative to the movable case and that is arranged so as to be axially movable with respect to the movable case, and is fixedly provided on the movable case, and the flange surface of the female screw is pressed against the bearing.
- Said female screw A brake shoe for restraining relative rotation with respect to the moving case, and an internal force provided in the moving case for urging the female screw in the axial direction via the bearing, A panel element that presses a surface against the brake shoe, and when the moving case receives a reaction force of a load force and a thrust generated in the female screw is larger than a biasing force by the panel element Further, when the female screw moves in the axial direction with respect to the moving case, the overflow surface is released by the brake force, thereby releasing the restriction of the relative rotation of the female screw with respect to the moving case.
- the feed screw and the female screw are configured to rotate differentially.
- the pressurizing device includes an upper frame to which the electric motor is attached, an output shaft cover, And a casing disposed between the upper frame and the output shaft cover, and the upper frame, the casing, and the output shaft cover are connected together by a tie bar and integrated.
- the moving case is slidable in the axial direction along the inner peripheral surface of the casing, and an output shaft that slidably penetrates the output shaft cover is attached to the moving case.
- FIG. 1 is a perspective view showing an appearance of a pressurizing device according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view of a pressure device.
- FIG. 3 is a perspective view showing an appearance of a clamp device according to an embodiment of the present invention.
- FIG. 4 is a perspective view showing an external appearance of a clamp unit according to an embodiment of the present invention.
- FIG. 5 is a cross-sectional view of a pressure device according to another embodiment.
- FIG. 6 is a conceptual structural diagram of a strain gauge.
- FIG. 7 is a diagram showing an embodiment of a bridge circuit that detects a load and obtains a voltage output.
- FIG. 8 is a cross-sectional view of a pressure device according to another embodiment.
- FIG. 9 is a bottom view of the pressure device in FIG.
- FIG. 10 is a cross-sectional view taken along line AA of the pressure applying device of FIG.
- FIG. 11 is a cross-sectional view showing an operating state of the power conversion unit moving case of the pressure device.
- FIG. 12 is an enlarged cross-sectional view of the vicinity of the dish panel.
- FIG. 13 is a view showing a compressed state of a small pan panel and a large pan panel.
- FIG. 14 is a diagram illustrating an example of a circuit of a control device.
- FIG. 15 is a diagram showing an example of a change in load current during operation of the pressurizing device.
- FIG. 1 is a perspective view showing an external appearance of a pressure device 1 according to an embodiment of the present invention
- FIG. 2 is a cross-sectional view of the pressure device 1
- FIG. 3 is an external view of a clamp device 1A according to an embodiment of the present invention.
- Indicates FIG. 4 is a perspective view showing the external appearance of the clamp unit IB of the embodiment according to the present invention
- FIG. 5 is a cross-sectional view of a pressure device 1C of another embodiment
- FIG. 6 is a conceptual structural diagram of the strain gauge
- FIG. 7 is a diagram showing an embodiment of a bridge circuit for detecting a load and obtaining a voltage output.
- a pressurizing device 1 to which a power transmission device according to the present invention is applied includes a base 2 and an upper frame 4 connected by two tie bars 5 and 5 and integrated with a pressurizing plate 3.
- the two guide bearings 6 and 6 that are properly mounted are configured to slide up and down using the tie bars 5 and 5 as guide shafts.
- the pressure plate 3 is assembled with an output shaft assembly 40 and a power conversion unit moving case 20 as a whole.
- An electric motor 8 is attached to the upper frame 4 via a plate 7.
- the rotational force of the electric motor 8 is transmitted to the large timing pulley 11 via the small timing pulley 9 and the timing belt 10, and further the feed screw 21 is rotated via the rotation transmission shaft 12.
- the rotary shaft 12 is rotatably supported on the upper frame 4 by a deep groove type ball bearing 13 and a thrust ball bearing 14, and is prevented from coming off by a retaining ring 15.
- the rotation transmission shaft 12 and the feed screw 21 are connected by a pin 16 and rotate integrally.
- the power conversion unit moving case 20 includes a cylindrical tube 24, a plate-shaped upper cover 25 disposed on the upper end surface of the tube 24, a plate-shaped lower cover 23 disposed on the lower end surface of the tube 24, And a housing constituted by four tie bolts connecting the upper cover 25 and the lower cover 23.
- a female screw 22 having an effective diameter larger than the effective diameter of the feed screw 21 and having a flange portion on one side, and a deep groove ball bearing 26 that rotatably supports the female screw 22 are provided. And is slidably incorporated.
- a panel receiver 27 is slidably incorporated on the inner peripheral surface of the tube 24, and a string spring 28 is mounted between the panel receiver 27 and the lower cover 23 in a compressed state. Therefore, the string spring 28 is moved by the biasing force between the panel receiver 27 and the deep groove ball bearing 26. Then, the female screw 22 is pushed up, and the brake lining 31 installed integrally with the flange portion of the female screw 22 is pressed against the brake shoe 32 installed integrally with the upper cover 25.
- the upper cover 25 and the lower cover 23 are provided with deep groove type ball bearings 29 and 30 for slidably supporting the feed screw 21 at a shaft center position eccentric to the shaft center of the female screw 22. It has been.
- the feed screw 21 is supported by the deep groove ball bearings 29 and 30 so as to be rotatable and movable in the axial direction, and is eccentric with respect to the female screw 22 and indented at one place in the circumferential direction. Matching.
- the female screw 22 is linearly driven in the axial direction by the mutual screw action.
- the female screw 22 is rotationally driven at a lower rotational speed than the feed screw 21 in a state in which the female screw 22 is inscribed.
- the female screw 22 and the feed screw 21 are The female screw 22 is linearly driven in the axial direction by the mutual screw action due to the difference in rotational speed.
- the lower cover 23 When the female screw 22 is linearly driven in the axial direction, the lower cover 23 is driven in the same direction via the flange portion, the deep groove ball bearing 26, the panel receiver 27, and the string rod spring 28.
- the lower force bar 23 is connected to the upper flange 41 of the output shaft assembly 40 by the four tie bolts described above.
- the output shaft assembly 40 includes an upper flange 41, an output shaft 42 sandwiched and connected by the upper flange 41 and the lower cover 23, and a lower flange 43 coupled to the output shaft 42 by screws.
- the lower flange 43 is connected to the pressure plate 3 by a bolt 44. Therefore, the pressure plate 3 moves integrally with the power conversion unit moving case 20.
- the feed screw 21 that rotates by receiving the driving force of the electric motor 8 moves the eccentric screwed female screw 22 at a rotational speed X screw pitch.
- the female screw 22 is moved by pressing the lower cover 23 of the power conversion unit moving case 20 via the deep groove ball bearing 26, the panel receiver 27, and the string spring 28, and pressing the pressure plate 3 connected to the lower cover 23. Move downwards at high speed.
- the rotational speed of the female screw 22 is determined by the amount of eccentricity between the feed screw 21 and the female screw 22, and if the radius of the contact point between the feed screw 21 and the female screw 22 is rl, respectively, the rotational speed of the feed screw Rotate at (rlZr2) times.
- the moving speed V of the female screw 22 is
- the applied pressure generated by the female screw 22 by the rotational torque of the feed screw 21 is [1Z (1-rl / r2)] times.
- the feed screw 21 and the female screw 22 are in sliding contact with each other in the same manner as a normal screw. Force to convert to motion When the pressure plate 3 contacts the workpiece and the brake that restricts the rotation of the female screw 22 is released and the female screw 22 starts to rotate, the contact point between the feed screw 21 and the female screw 22 is Rolling contact mainly makes it possible to reduce the loss due to sliding friction and effectively convert the motor rotation output to linear output.
- the friction plate element used to restrain the rotation of the female screw 22 is different from the clutch seen in the prior art, and the lead angle of the screw that does not need to transmit or restrain the maximum output of the electric motor 8 is required. Since it is only necessary to have a capacity capable of restraining the rotational torque generated in the female screw 22 by the frictional force at the contact point, the size can be reduced.
- the movement speed of the pressure plate and the caloric pressure are controlled by restricting or releasing the rotation of the female screw 22 according to the load force. It showed that it can switch autonomously.
- the initial pressing force of the string spring 28 that functions as a load force detecting element can restrain the rotational torque generated in the female screw 22 by the lead angle of the screw and the frictional force of the contact point in the idle running section.
- the female screw 22 when the feed screw 21 rotates at the maximum torque of the electric motor, the female screw 22 must be smaller than the thrust of the female screw 22 generated in a rotationally restrained state.
- the feed screw 21 that rotates by the output of the electric motor 8 and the feed screw 21 are provided so as to penetrate in the axial direction and are provided so as to be relatively rotatable with the feed screw 21.
- the brake lining 31 is separated from the brake shoe 32, thereby releasing the restriction of the relative rotation of the female screw 22 with respect to the moving case 20, and the feed screw 21 and the female screw 21.
- the screw 22 is configured to rotate differentially.
- the distance between the end surface of the panel receiver 27 and the upper end surface of the lower cover 23 of the power conversion unit moving case 20 is The panel stagnation amount to be determined should be 1mm or less, and the initial panel sag at the time of installation should be set large, and a panel with a small panel constant should be used.
- FIG. 3 is a perspective view showing the appearance of another preferred embodiment in which the power transmission mechanism of the present invention is used as the clamping device 1A.
- the clamping device 1A includes an output shaft cover 2a and an input shaft cover 4a that are connected and fixed to each other by a plurality of tie bars 5a, and a power conversion unit moving case 20a having a guide portion is connected to the tie bar 5a.
- a guide shaft As a guide shaft, it is assembled so that it can slide freely.
- the output shaft 42a is assembled on one end face of the power conversion moving case 20a so as to be slidable through the output shaft cover 2a.
- the output shaft 42a is also formed of a hollow cylindrical member like the output shaft 42 shown in FIG.
- the electric motor 8a is attached to the input shaft cover 4a using bolts or the like. As a preferred example, it is desirable to use a motor 8a in which a feed screw 21 is incorporated in the body.
- the output shaft cover 2a shown in Fig. 3 has a pin joint mounting shape generally used for pneumatic clamp cylinders and the like.
- the power transmission mechanism of the present embodiment converts the rotational motion into a linear motion by the screw mechanism, the feed screw is not rotated in the reverse direction by the reaction force on the load side! /. Therefore, the current position can be held simply by shutting off the power supply to the motor while the target workpiece is clamped, so that no position holding mechanism is required.
- the distance between the spring receiver 27 and the lower cover 23 of the power conversion moving case 20 shown in FIG. It is preferable to use a panel.
- the initial pressing force of the panel can restrain the rotational torque generated in the female screw 22, and the female screw generated in the female screw rotational restraint state when the feed screw 21 rotates with the maximum torque of the electric motor 8.
- the thrust force of the screw 22 should be smaller than that of the screw 22, and when the panel is fully squeezed, that is, when the panel receiver 27 and the lower cover 23 are in contact with each other, the feed screw 21 and the female screw 22 rotate differentially. It should be set larger than the maximum thrust output.
- the female screw 22 is differentially rotated at the maximum output of the electric motor 8, the target work is clamped, the electric power of the electric motor is shut off, and the female screw 22 is self-holding stopped at the position, When clamping the target workpiece for a long time, it can absorb the slight displacement caused by thermal deformation of the workpiece itself and perform reliable clamping.
- a force pan panel showing the string spring 28 as a load detection element (panel element) is used alone or a plurality of dish panels having different panel constants are used. An elastic body may be used. Such an example will be described later.
- FIG. 4 shows that the input shaft end of the power transmission mechanism of the embodiment described above is formed in a hexagonal shape or a quadrangular shape, and is clamped using an external drive source such as a small screw tightener.
- FIG. 3 is a perspective view showing the appearance of an embodiment that is sometimes a suitable clamp unit 1B.
- the output shaft cover 2b and the input shaft cover 4b are connected and fixed to each other by a plurality of tie bars 5a in the same manner as the clamp device shown in FIG.
- the power conversion unit moving case 20a is assembled and slidable with the tie bar 5a as a guide shaft.
- the output shaft 42a is assembled to the one end face of the power conversion unit moving case 20a so as to be slidable through the output shaft cover 2a.
- the output shaft 42a also has a hollow cylindrical member, which accommodates a feed screw 21 (see FIG. 2) inside, and at the same time has a female screw for attaching a tip fitting (not shown) to the outer peripheral surface of the tip. Is provided.
- the outer peripheral surface of the rotation transmission shaft 12b has a hexagonal shape or a quadrangular shape. The rotation transmission shaft 12b penetrates the input shaft cover 4b and is connected to the feed screw 21 inside the input shaft cover 4b. !
- a preferred embodiment of the load detecting unit 50 that detects an axial pressurizing force, that is, a load, and converts it into an electrical signal is shown!
- the upper end portion of the load detection unit 50 is fixed by the upper flange portion of the protective case 53 while being in contact with the lower end surface of the lower cover 23.
- the load detector 51 is provided with a thin-walled cylindrical portion 52 at the center in the axial direction, and the outer peripheral surface of the lower end thereof is held by the lower guide of the protective case 53 so as to be slidable in the axial direction.
- Protective case A retaining flange 54 is attached to the lower end of 53 by a plurality of bolts 58.
- a stepped collar 57 is fitted into a plurality of grooves provided on the outer peripheral portion of the retaining flange 54, and the lower end surface of the load detecting body 51 is pressed against the pressure plate by a bolt 56 inserted into the stepped collar 57.
- the bottom end of the load detection unit 50 is connected to the pressure plate 3 while being in contact with the pressure plate 3.
- strain gauges GU1, GU2, GU3, and GU4 are affixed to the outer circumferential surface at the center in the axial direction of the thin-walled cylindrical portion 52, and these strain gauges.
- the load detection unit 50 is configured by connecting G Ul to 4 to the external connection connector 55 by bridge connection.
- FIG. 6 shows a conceptual structure of the strain gauge GU, which is bonded to the outer peripheral surface of the thin-walled cylindrical portion 52 (see FIG. 5) in the direction shown in FIG.
- the strain gauge GU is also composed of the detection gauge B and the compensation gauge A, and has three lead wire connections indicated by TA, TB, and TC.
- FIG. 7 is a bridge circuit diagram in which strain gauges GU1 to GU4 bonded to the thin-walled cylindrical portion 52 of the load detector are connected. As described above, the strain gauges GU1 to GU4 are bonded to the outer peripheral surface of the thin-walled cylindrical portion 52 at positions shifted by 90 ° in order.
- strain gauge GU lead wire connections TA is connected to TA, TB is connected to TB, and TC is connected to nodes ⁇ , EB, UA, and UB of the bridge circuit, respectively. Strain is measured by applying a constant voltage of about 10 volts between nodes EA and EB and processing the voltage output between nodes UA and UB.
- the compensation gauge A compensates for output fluctuations due to temperature drift of the strain gauge itself and thermal deformation of the stagnation cylindrical portion. Strain gauges attached to the outer circumferential surface of the thin-walled cylindrical portion 52 in four equal positions may act on the load detector by bridge connection. It is effective to detect only the axial load.
- FIG. 8 is a cross-sectional view of a pressure device 1D according to another embodiment
- FIG. 9 is a bottom view of the pressure device 1D
- FIG. 10 is a cross-sectional view of the pressure device 1D in FIG. 11 is a cross-sectional view showing the operating state of the power conversion unit moving case 20D of the pressure device 1D
- FIG. 12 is a cross-sectional view showing the vicinity of the pan panel
- FIG. 13 is a view of the small pan panel 75 and the large pan panel 74.
- FIG. 14 is a diagram illustrating an example of a circuit of the control device 80
- FIG. 15 is a diagram illustrating an example of a change in the load current Id during operation of the pressurizing device 1D.
- the pressure device 1D includes an electric motor 8d, an upper frame 4d, an output shaft cover 2d, a power conversion unit moving case 20d, an output shaft 42d, a casing 71, and the like. ing.
- the upper plate 61 of the upper frame 4d is formed in a substantially square plate shape by a metal material such as iron, and is connected to the output shaft cover 2d also formed in a substantially square plate shape by a steel material.
- the four tie bars 5d are connected to each other.
- the electric motor 8d is fixed to the upper plate 61 with bolts.
- the block member 62 of the upper frame 4d has an outer shape formed in a rectangular parallelepiped shape by a metal material such as an aluminum alloy, and has a cylindrical hole for accommodating a joint member and the like to be described later in the center. .
- a metal material such as an aluminum alloy
- the annular portions 621 and 622 are provided between the annular portion 621 provided to project from the lower end surface of the block member 62 and the annular portion 622 provided to project from the upper end surface of the output shaft cover 2d.
- a casing 71 that is a rectangular cylinder having an inner peripheral surface of a square cross section that circumscribes each, and that also has a metal material force such as an aluminum alloy is mounted.
- a joint member 64 is attached to the output shaft of the electric motor 8d, and the joint member 64 is a joint part 212 that protrudes in a plate shape formed at the upper end part of the intermediate joint member 65 and the feed screw 21d.
- an Oldham coupling that transmits rotational force while absorbing eccentricity is formed. The rotational force of the electric motor 8d is transmitted to the feed screw 21d through the Oldham coupling.
- the upper end of the feed screw 21d is a screw shaft 211, which is tightened by a nut 212 with the inner ring of the ball bearing 13 sandwiched therebetween, and is supported rotatably by this. It is.
- the power conversion unit moving case 20d includes a housing body 25d formed in a downward container shape with a metal material such as an aluminum alloy, and a lower cover 23d attached to the lower end surface of the housing body 25d with a bolt 77.
- a housing A housing.
- the upper end surface of the housing body 25d and the lower cover 23d are provided with circular holes that coincide with the axis of the feed screw 21d, and ball bearings 29 and 30 are mounted in these holes.
- the feed screw 21d penetrates these ball bearings 29 and 30 so as to be slidable.
- the inner peripheral surface of the housing body 25d is formed as a cylindrical surface having an axis that is eccentric with respect to the axis of the feed screw 21d. Inside the inner peripheral surface, there are a bearing 26, a female screw 22, and a panel receiver. 73, large pan panel 74, and small pan panel 75 are installed!
- the large pan panel 74 and the small pan panel 75 have the same function as the string spring 28 described in FIG. 2. Two large pan panels 74 and small pan panels 75 with different panel constants are connected in series. By using it for operation, load detection can be performed accurately, speed and thrust can be switched smoothly, and the force can absorb shocks at the moving end well. is there. This will be described in detail later.
- the slider 72 is made of a synthetic resin having lubricity, etc., and has a cylindrical head having a large diameter and a fitting portion that is concentrically protruded from the end surface of the head with a cylindrical shape having a diameter smaller than the head. Consists of.
- the entire power conversion unit moving case 20d is inserted into the casing 71 with the insertion portion of the slider 72 being inserted into the hole provided in the lower cover 23d. When the head of the slider 72 comes into contact with the inner peripheral surface of the casing 71, the power conversion unit moving case 20d is positioned in the radial direction with respect to the casing 71 and is slidable in the axial direction. Yes.
- a plurality of circular holes are provided in the lower end surface of the block member 62, and a damper 63 formed in a columnar shape by synthetic rubber or the like is fitted into the hole, and is attached by an adhesive or the like. Is fixed.
- the power conversion unit moving case 20d abuts against the damper 63 when moved to the stroke end on the upper end side in FIG. 8, thereby reducing the impact and preventing the feed screw 21d from being caught.
- the damper 63 is not the block member 62 but the housing body 25. It may be fixed to d.
- the large pan panel 74 and the small pan panel 75 are in an initial stagnation state in which an initial pressing force is generated between the bearing 26 and the panel receiver 73 in the power conversion unit moving case 20d. It is installed with.
- the combined pressing force WD by the large pan panel 74 and the small pan panel 75 generates the initial pressing force WD1 at the initial stagnation position L1.
- the load curve changes depending on the spring constant of the small pan panel 75 up to the position L2 (the position shown in Fig. 11 (A)) where the pan pan 75 is squeezed to the maximum position L2
- the load curve changes depending on the pan constant of pan plate 74.
- the total amount of stagnation due to the large pan panel 74 and small pan panel 75 is the maximum stagnation stroke ST2 from the initial stagnation position L1 to the maximum stagnation position L4. It can move inside the housing body 25d.
- the maximum pressing force WD4 at the maximum stagnation position L4 is set to be larger than the maximum thrust generated in the female screw 22 (maximum operation pressing force WD3). Therefore, the large pan panel 74 and the small pan panel 75 are actually between the initial stroke position L1 and the maximum stroke position L3 (the position in the state shown in Fig. 11 (B)) during the stroke range ST1. Is compressed.
- the control device 80 includes a driver 81, a controller 82, a current detection circuit 83, and the like.
- the driver 81 is a power circuit that controls the electric motor 8d according to the contents of the control signals Dl and D2 when the external power is supplied with DC power.
- the 2-bit control signals Dl and D2 are ⁇ 00 '', ⁇ 01 '', ⁇ 10 '', and ⁇ 11 '' respectively, control is performed so that the operating state of the motor 8d is brake, forward rotation, reverse rotation, and stop. .
- the current Id supplied to the driver 81 appears as a voltage across the resistor R1, and this is compared with the set voltage by the comparator COM. When the current Id is larger than the threshold Is, an overcurrent detection signal D3 is output to the controller 82.
- the controller 82 receives a command of forward rotation, reverse rotation, or stop by the command signals SI and S2 input from the outside, and in response to this command, the controller 82 outputs the control signals Dl and D2. Output. However, when the excessive current detection signal D3 is input, the stop or brake control signals Dl and D2 are output even if the command signals SI and S2 are forward or reverse. The overcurrent detection signal D3 is output to the outside as the status signal S3.
- the output shaft 42d moves forward (extends) in the high speed mode, contacts the workpiece at time t2, and switches to the high thrust mode.
- the current Id is below the threshold Is in both the high speed mode and the high thrust mode.
- the current Id decreases at the time t2 when the high speed mode is switched to the high thrust mode.
- the output shaft 42d is moving forward in the high thrust mode, the current Id increases or decreases according to the load change.
- time t5 when the workpiece is fully cut and no further advance is possible, the current Id increases and exceeds the threshold Is.
- the motor 8d stops, and at the same time, the status signal S3 is output to the outside.
- control device 80 controls the motor 8d to stop when an excessive current flows in the motor 8d, so that the feed screw 21d rotates excessively and the female screw 22 is Grudge It ’s not going to be complicated!
- the current Id is the threshold value, which is less than or equal to the value Is, as close to the value Is as possible.
- pressurization or pressure increase is performed on the push side, that is, when the output shafts 42, 42a, and 42d are driven to extend is described.
- pressurization or pressure increase can be performed on the pull side, that is, when the output shafts 42, 42a, and 42d are driven to contract.
- the parts mounted inside the housing body 25d that is, the brake lining 31, the female screw 22, the bearing 26, the small pan panel 75, the large pan panel 74, and the panel receiver 73
- the damper 63 may be installed on the output shaft cover 2d, for example, so as to reduce the impact between the lower cover 23d and the output shaft cover 2d.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Press Drives And Press Lines (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/662,726 US7584678B2 (en) | 2004-09-16 | 2005-09-13 | Power transmission method and device having load sensing thrust augmentation mechanism |
EP05783160A EP1801457B1 (en) | 2004-09-16 | 2005-09-13 | Device for power transmission with load-sensing thrust amplifying mechanism |
DE602005017919T DE602005017919D1 (de) | 2004-09-16 | 2005-09-13 | Vorrichtung zur kraftübertragung mit lasterfassungs-schubverstärkungsmechanismus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-269802 | 2004-09-16 | ||
JP2004269802A JP3664406B1 (ja) | 2004-09-16 | 2004-09-16 | 負荷感応推力増幅機構を持つ動力伝達方法及び装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006030768A1 true WO2006030768A1 (ja) | 2006-03-23 |
Family
ID=34737364
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/016818 WO2006030768A1 (ja) | 2004-09-16 | 2005-09-13 | 負荷感応推力増幅機構を持つ動力伝達方法及び装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7584678B2 (ja) |
EP (1) | EP1801457B1 (ja) |
JP (1) | JP3664406B1 (ja) |
CN (1) | CN100458227C (ja) |
DE (1) | DE602005017919D1 (ja) |
WO (1) | WO2006030768A1 (ja) |
Cited By (2)
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JP2011169254A (ja) * | 2010-02-19 | 2011-09-01 | Aisin Seiki Co Ltd | 回転駆動装置 |
CN103962423A (zh) * | 2014-04-09 | 2014-08-06 | 西安交通大学 | 一种伺服直驱型谐波传动螺旋折弯机 |
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CN102401101A (zh) * | 2010-09-10 | 2012-04-04 | 张旸斌 | 扭力滑块 |
GB201016930D0 (en) * | 2010-10-07 | 2010-11-24 | Ishida Europ Ltd | Lifting apparatus |
PL2659164T3 (pl) * | 2011-09-14 | 2019-09-30 | Sintokogio, Ltd. | Siłownik elektryczny i układ siłownika elektrycznego |
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JP2017514603A (ja) | 2014-05-02 | 2017-06-08 | ノボ・ノルデイスク・エー/エス | 薬剤送達装置用の、伸縮式の駆動アレンジメント |
JP6159707B2 (ja) * | 2014-12-25 | 2017-07-05 | 平田機工株式会社 | 送りねじ装置及びこれを用いたアクチュエータ |
US11090894B2 (en) * | 2015-11-16 | 2021-08-17 | United Arab Emirates University | Metal chips compactor |
CN105515277B (zh) * | 2016-01-12 | 2018-04-17 | 马小安 | 一种调节机构 |
DE102016209161B4 (de) * | 2016-05-25 | 2019-08-01 | Zf Friedrichshafen Ag | Stelleinrichtung und Verwendung der Stelleinrichtung |
US20200132089A1 (en) * | 2018-10-31 | 2020-04-30 | Seiko Instruments Inc. | Thrust expansion device, expansion unit, connecting unit, and thrust expansion system |
CN109720610B (zh) * | 2019-03-20 | 2020-09-15 | 安徽德鑫源食品有限公司 | 一种粮食定重连续包装机 |
CN110350716B (zh) * | 2019-07-08 | 2022-09-06 | 明视智能科技(广州)有限公司 | 一种带推力或拉力感测的电动缸 |
JP7151671B2 (ja) * | 2019-09-06 | 2022-10-12 | 新東工業株式会社 | 電動シリンダシステム及び電動シリンダの異常検出方法 |
US11318696B2 (en) * | 2020-03-27 | 2022-05-03 | Calvin Fabrications Co. | Portable power-driven press |
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- 2005-09-13 EP EP05783160A patent/EP1801457B1/en not_active Expired - Fee Related
- 2005-09-13 CN CNB2005800311809A patent/CN100458227C/zh not_active Expired - Fee Related
- 2005-09-13 US US11/662,726 patent/US7584678B2/en not_active Expired - Fee Related
- 2005-09-13 WO PCT/JP2005/016818 patent/WO2006030768A1/ja active Application Filing
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CN103962423A (zh) * | 2014-04-09 | 2014-08-06 | 西安交通大学 | 一种伺服直驱型谐波传动螺旋折弯机 |
CN103962423B (zh) * | 2014-04-09 | 2016-01-20 | 西安交通大学 | 一种伺服直驱型谐波传动螺旋折弯机 |
Also Published As
Publication number | Publication date |
---|---|
EP1801457B1 (en) | 2009-11-25 |
DE602005017919D1 (de) | 2010-01-07 |
US20070251342A1 (en) | 2007-11-01 |
US7584678B2 (en) | 2009-09-08 |
JP3664406B1 (ja) | 2005-06-29 |
CN100458227C (zh) | 2009-02-04 |
EP1801457A4 (en) | 2008-01-16 |
JP2007192238A (ja) | 2007-08-02 |
CN101023284A (zh) | 2007-08-22 |
EP1801457A1 (en) | 2007-06-27 |
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