US20010000211A1 - Electric power operated clamp with spring lock - Google Patents
Electric power operated clamp with spring lock Download PDFInfo
- Publication number
- US20010000211A1 US20010000211A1 US09/730,667 US73066700A US2001000211A1 US 20010000211 A1 US20010000211 A1 US 20010000211A1 US 73066700 A US73066700 A US 73066700A US 2001000211 A1 US2001000211 A1 US 2001000211A1
- Authority
- US
- United States
- Prior art keywords
- drive member
- clamp
- power operated
- stated
- slot
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
- B23K37/00—Auxiliary devices or processes, not specially adapted to a procedure covered by only one of the preceding main groups
- B23K37/04—Auxiliary devices or processes, not specially adapted to a procedure covered by only one of the preceding main groups for holding or positioning work
- B23K37/0426—Fixtures for other work
- B23K37/0435—Clamps
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B5/00—Clamps
- B25B5/06—Arrangements for positively actuating jaws
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B5/00—Clamps
- B25B5/06—Arrangements for positively actuating jaws
- B25B5/12—Arrangements for positively actuating jaws using toggle links
Definitions
- the present invention relates to an electric power operated clamp for moving at least one clamp arm between a clamped position and a released position, and in particular, an adjustable mechanism that converts the rotary motion of an electric power source into linear reciprocal movement of a drive member and then into rotary motion of the clamp arm.
- Compressed air generally requires the use of fixed or flexible conduits to communicate the compressed air with the actuator, and may produce compressed air leaks increasing operating costs. Furthermore, it is difficult to obtain a harmonic motion clamp action with a hydraulic or pneumatic actuator, sometimes referred to as a “soft-touch” clamp, where the clamp decelerates adjacent the clamped and/or released position thereby eliminating the need for “bumpers” or other shock absorbing elements.
- hydraulic and pneumatic actuated clamps require complex control mechanisms to adjust the rate of actuation of the clamp to eliminate or reduce the amount of shock absorbed as the clamp reaches the clamped position and/or the released position.
- the present invention provides a power operated clamp including an electric motor means for imparting a rotary motion driving force.
- a drive member is operably associated with the electric motor means.
- First converting means connects the drive member to the electric motor means.
- the first converting means converts the rotary motion driving force of the electric motor means into a linear reciprocal motion of the drive member.
- a clamp member is operably associated with the drive member.
- Second converting means connects the clamp member to the drive member.
- the second converting means converts the linear reciprocal motion of the drive member into rotary motion of the clamp arm to move the clamp member between a clamped position and a released position.
- the first converting means includes an elongate arm connected to a shaft of the electric motor means which extends radially outward for rotation with the shaft.
- a cam follower is connected to the elongate arm spaced radially from the shaft.
- the drive member is mounted for linear reciprocal movement along a fixed path.
- the drive member has a cam surface defining a slot adjacent one longitudinal end of the elongate drive member. The slot extends generally normal to the fixed path of the drive member.
- the cam follower operably engages within the slot for converting the rotational movement of the cam follower into linear movement of the drive member.
- the first converting means can include an eccentric member connected to the electric motor means for rotation therewith and having an external periphery.
- the drive member can include a connecting rod and slide block.
- the connecting rod has a complementary aperture formed therein for operably receiving the external periphery of the eccentric member.
- the connecting rod also includes a pivot pin for operably connecting to the slide block, such that the slide block is driven in reciprocal motion by the connecting rod in response to rotation of the eccentric member.
- the first converting means having a barrel cam connected to the electric motor means for rotation therewith.
- the barrel cam has a generally helical cam surface formed on an external periphery.
- the drive member has an aperture for receiving the barrel cam.
- a cam follower is supported by the drive member and is engageable with the cam surface for driving the drive member in linear motion in response to rotary motion of the barrel cam.
- the generally helical cam surface is formed having reduced longitudinal spacing between turns adjacent one or both longitudinal ends to impart a harmonic motion to the clamp arm while approaching the respective end limit of movement corresponding to the clamped position and the released position.
- the present invention provides an adjustable converting means for converting the rotary motion of the power means into linear reciprocal motion of the drive member.
- the adjustable converting means includes the first converting means having a crank arm connected to the power means and extending radially outward for rotation about an axis of rotation.
- the follower is connected to the crank arm and spaced radially from the axis of rotation.
- the drive member is mounted for reciprocal movement along a fixed path wherein the cam surface of the drive member defines the slot.
- the follower operably engages the slot to convert the rotational movement of the follower into linear movement of the drive member.
- the second converting means converts the linear reciprocal motion of the drive member into rotary motion of the clamp member.
- a manual adjustment means is also provided in the preferred embodiment for adjusting the stroke of the linear reciprocal motion of the drive member.
- the manual adjustment means provides the crank arm with a plurality of apertures radially spaced from the axis of rotation wherein the follower is removably inserted in at least one of the apertures of the crank arm.
- the drive member includes a threaded rod and an outer shaft wherein the outer shaft threadingly receives the rod. The outer shaft and the rod threadingly adjust along the longitudinal axis of the drive member to adjust the length of the drive member in response to the position of the follower in the crank arm.
- the preferred embodiment also provides an automatic adjustment means to automatically adjust the length of the drive member in response to the driving force of the power means and the position of the clamp member.
- the automatic adjustment means provides the drive member with a telescopic portion telescopically moveable along the longitudinal axis of the drive member between an extended position and a contracted position.
- a positive stop limits the telescopic movement of the telescopic portion between the extended position and the contracted position.
- At least one compression spring biases the telescopic portion of the drive member toward the extended position.
- FIG. 1 is a perspective view of an electric power operated clamp according to the present invention.
- FIG. 2 is a simplified internal view of the clamp with one half of the housing removed in order to show the internal mechanism
- FIG. 3 is a top view of the electric power operated clamp illustrated in FIG. 2 with the housing in place enclosing the internal mechanism;
- FIG. 4 is a simplified schematic view of an alternative embodiment of first converting means for converting the rotary motion driving force of the electric motor means into a linear reciprocal motion of a drive member according to the present invention
- FIG. 5 is a simplified schematic view of an alternative embodiment of the first converting means
- FIG. 6 is a perspective cut away view of an electric power operated clamp according to the present invention.
- FIG. 7 is a front view of the power means and the drive member of the present invention.
- FIG. 8 is an exploded view of the drive member of the present invention.
- FIG. 9 is a sectional view taken in the direction of arrows 9 — 9 in FIG. 7;
- FIG. 10 is a plan view of the crank arm.
- a power operated clamp 10 is illustrated in perspective view in FIG. 1.
- the power operated clamp 10 includes an electric motor means 12 for imparting a rotary motion driving force to the clamp assembly.
- a gear box 14 can be provided, if required, between the electric motor means 12 and the clamp actuator housing 16 .
- a clamp member 18 is operably associated with the housing 16 for movement between a clamped position and a released position.
- a drive member 20 is operably associated with the electric motor means 12 .
- First converting means 22 connects the drive member 20 to the electric motor means 12 .
- the first converting means 22 is for converting the rotary motion driving force of the electric motor means 12 into a linear reciprocal motion of the drive member 20 .
- Second converting means 24 connects the clamp member 18 to the drive member 20 .
- the second converting means 24 is for converting the linear reciprocal motion of the drive member 20 into rotary motion of the clamp member 18 to move the clamp member 18 between a clamped position and a released position.
- the first converting means 22 can include an elongate arm 26 connected to an output shaft 28 of the electric motor means 12 .
- the elongate arm 26 extends radially outward for rotation with the shaft 28 .
- a follower 30 is connected to the elongate arm 26 and is spaced radially from the longitudinal axis of the shaft 28 .
- the drive member 20 is mounted for linear reciprocal movement along a fixed path and has a cam surface 32 adjacent one longitudinal end of the elongate drive member 20 .
- the cam surface 32 defines a slot 34 , and more preferably, the slot 34 extends generally normal to the fixed path of travel for the drive member 20 .
- the follower 30 operably engages within the slot 34 for converting the rotational movement of the follower 30 into linear movement of the drive member 20 .
- the slot 34 is linear and generally perpendicular to the fixed path of the drive member 20 . This configuration provides the desired harmonic motion clamp action.
- FIG. 4 An alternative configuration of the first converting means 22 a is illustrated in FIG. 4.
- an eccentric member 36 is connected to the shaft 28 a of the electric motor means for rotation therewith.
- the eccentric member 36 has an external periphery 38 .
- the drive member 20 a includes a connecting rod 40 and a slide block 42 .
- the connecting rod 40 has a complementary aperture 44 formed therein for operably receiving the external periphery 38 of the eccentric member 36 .
- the connecting rod 40 also includes a pivot point or pin 46 for operably connecting the connecting rod 40 to the slide block 42 .
- the slide block 42 is driven in reciprocal motion by the connecting rod 40 in response to rotation of the eccentric member 36 .
- This configuration for the first converting means 22 a also provides the desirable harmonic motion clamp action, sometimes referred to as a “soft-touch” clamp.
- both the embodiment depicted in FIGS. 2 and 3, and the alternative configuration of the first converting means 22 a of FIG. 4 provide a clamp that decelerates adjacent the clamped position and the released position, while achieving maximum acceleration generally midway between the clamped position and released position. This configuration eliminates the need for “bumpers” or other shock absorbing elements at the end limit of movement of the clamp.
- the first converting means 22 b includes a barrel cam 48 .
- the barrel cam 48 includes an aperture 50 for receiving an output shaft of the electric motor means, so that the barrel cam 48 is driven in rotation in response to rotation of the shaft of the electric motor means.
- the barrel cam 48 includes a generally helical cam surface 52 formed on an external periphery 54 .
- the drive member 20 b includes an aperture 56 for receiving the barrel cam 48 .
- a cam follower 58 is supported by the drive member 20 b and is engagable with the cam surface 52 for driving the drive member 20 b in linear motion in response to rotary motion of the barrel cam 48 .
- the generally helical cam surface 52 is formed having reduced longitudinal spacing between turns adjacent one or both longitudinal ends of the barrel cam 48 to impart a harmonic motion to the clamp member 18 while approaching one or both end limits of movement corresponding to either or both of the clamped position and the released position.
- This embodiment also provides the first converting means 22 with the desirable harmonic motion driving force provided in the previously described embodiments.
- the second converting means 24 can include a pivot pin 60 operably connected to the clamp member 18 for moving the clamp member 18 between a released position and a clamped position about a rotational axis.
- the pivot pin 60 has a radially extending arm 62 .
- An elongate link 64 has a first pivot connection 66 to the radially extending arm 62 of the pivot pin 60 and a second pivot connection 68 to the drive member 20 , 20 a, or 20 b opposite from the first converting means 22 , 22 a, or 22 b.
- the second converting means 24 can be similar in construction for each of the alternative embodiments discussed in detail above.
- the second converting means 24 converts the harmonic linear reciprocal motion of the drive member 20 , 20 a, or 20 b into rotational harmonic motion, or “soft-touch” motion of the clamp member 18 as it approaches one or both end limits of travel.
- the power operated clamp 10 includes an electric motor connected to an output shaft with a longitudinal axis.
- the shaft can be connected to the first converting means 22 , 22 a, or 22 b, directly or through a gear box 14 as appropriate for the particular power operated clamp.
- An elongate arm 26 is connected to the shaft 28 and extends radially outwardly from the longitudinal axis for rotation with the shaft 28 .
- a follower 30 is connected to the elongate arm 26 and is spaced radially from the longitudinal axis of the shaft.
- a housing 16 at least partially encloses the elongate arm 26 and follower 30 .
- An elongate drive member 20 is mounted for linear reciprocal movement along a fixed path with respect to the housing 16 .
- the drive member 20 has a cam surface 32 defining a linear slot 34 adjacent one longitudinal end of the elongate drive member 20 .
- the slot 34 preferably extends normal to the fixed path of reciprocal movement for the drive member 20 .
- the follower 30 operably engages within the slot 34 for converting the rotational movement of the follower 30 into linear movement of the drive member 20 .
- At least one elongate link member 64 is pivotally connected to a longitudinal end of the drive member 20 opposite from the slot 34 .
- a pivot pin 60 includes an arm 62 connected thereto for rotational movement therewith. The pin 60 is supported in the housing 16 for rotation with respect to the housing 16 .
- the arm 62 is pivotally connected to the link member 64 for converting linear movement of the elongate drive member 20 into rotational movement of the pivot pin 60 through the link member 64 .
- a clamp member 18 is connected to the pivot pin 60 for movement between a clamped position and a released position in response to movement of the drive member 20 operably engaging the follower 30 driven by the electric motor 12 .
- the first converting mechanism includes a elongate arm driven by the rotatable shaft of the electric motor and extending radially outwardly with a follower connected to the elongate arm spaced from the axis of rotation.
- a cam surface is formed on the drive member and is engaged by the follower for driving the drive member in reciprocal linear harmonic motion in response to rotation of the shaft.
- the first converting mechanism includes an eccentric member connected to the shaft driven by the electric motor and the drive member including a connecting rod and slide block, where the connecting rod has a complementary aperture for operably receiving the internal periphery of the eccentric member and a pivot point for operably connecting to the slide block, so that the slide block is driven in reciprocal linear harmonic motion by the connecting rod in response to rotation of the eccentric member.
- the first converting mechanism includes a barrel cam connected to the shaft driven by the electric motor for rotation.
- the barrel cam has a generally helical cam surface formed on an external periphery, and the drive member has an aperture for receiving the barrel cam.
- the cam follower is supported by the drive member and is engageable with the cam surface for driving the drive member in reciprocal linear harmonic motion in response to rotary motion of the barrel cam.
- the power operated clamp 10 includes the electric motor means 12 for imparting a rotary motion driving force to the clamp assembly.
- the electric motor means 12 may be utilized in conjunction with the gear box 14 in order to provide the desired torque and speed characteristics of the power clamp 10 .
- the present invention is best suited for use with an electric motor as the power means, any number of power sources may be utilized which render the characteristics associated with an electric motor.
- the electric motor means 12 is connected to the clamp actuator housing 16 , and the housing 16 has a cover assembly 17 for enclosing the housing 16 .
- the clamp member 18 c is operably associated with the housing 16 for movement between the clamped position and the released position.
- the drive member 20 c is operably associated with the electric power means 12 .
- An adjustable converting means 70 converts the rotary motion of the electric power means 12 into linear reciprocal motion of the drive member 20 c.
- the adjustable converting means 70 includes the first converting means 22 c which connects the drive member 20 c to the electric motor means 12 .
- the first converting means 22 c converts the rotary motion driving force of the electric motor means 12 into a linear reciprocal motion of the drive member 20 c.
- the second converting means 24 c connects the clamp member 18 c to the drive member 20 c.
- the second converting means 24 c is for converting the linear reciprocal motion of the drive member 20 c into rotary motion of the clamp member 18 c and to move the clamp member 18 c between the clamped position and the released position.
- the adjustable converting means 70 also includes a manual adjusting means 72 for adjusting the stroke of the linear reciprocal motion of the drive member 20 c and an automatic adjusting means 74 for automatically adjusting the length of the drive member 20 c in response to the driving force of the electric power means 12 and the position of the clamp member 18 c.
- the first converting means 22 c may include a crank arm 76 connected to the output shaft 28 of the electric motor means 12 .
- the electric motor means 12 is connected to the clamp actuator housing 16 , and the output shaft 28 of the electric motor means 12 extends through an aperture 78 provided in the clamp actuator housing 16 .
- the crank arm 76 has a disk shaped configuration having an aperture 80 extending therethrough along the centerline axis 81 of the crank arm 76 for receiving the output shaft 28 of the electric motor means 12 .
- the clamp actuator housing 16 has a recessed portion 82 for receiving the disk shaped crank arm 76 .
- a set screw 84 extends through a radially extending aperture 86 provided in the crank arm 76 to secure the crank arm 76 to the output shaft 28 of the electric motor means 12 .
- a corresponding aperture 88 is provided in the clamp actuator housing 16 to access the set screw 84 from outside the clamp actuator housing 16 .
- the crank arm 76 is connected to the drive member 20 c by the follower or roller 30 c.
- the follower 30 c is rollably mounted to a roller shaft 92 which is inserted into a corresponding aperture 90 provided in the crank arm 76 .
- the aperture 90 is one of a plurality of apertures 90 which are radially spaced from the longitudinal axis 81 of the drive shaft 28 and which will be described in detail later.
- the drive member 20 c is mounted for linear reciprocal movement along a fixed path wherein a bore 93 extending through a portion of the housing 16 slidingly receives the drive member 20 c.
- a bushing 95 lines the bore 93 and is retained by a retaining clip 97 .
- a cam bar 94 is adjacent one longitudinal end of the drive member 20 c for operably engaging the follower 30 c.
- the cam bar 94 provides a cam surface 32 which defines a linear slot 34 c for receiving the follower 30 c.
- the slot 34 c extends substantially normal to the fixed path of travel for the drive member 20 c.
- This configuration provides the desired harmonic motion clamp action, previously referred to as a “soft-touch” clamp.
- the clamp member 18 c decelerates adjacent the clamp position and the released position, while achieving maximum acceleration generally midway between the clamped position and the released position.
- the crank arm 76 To manually adjust the stroke of the linear reciprocal motion of the drive member 20 c, the crank arm 76 provides the plurality of radially spaced apertures 90 , as seen in FIG. 10. To lengthen the stroke of the linear reciprocal motion of the drive member 20 c and correspondingly expand the rotary motion of the clamp member 18 c, the follower 30 c is moved radially outward toward an outwardly extending aperture 90 in the crank arm 76 . To shorten or contract the stroke of the linear reciprocal motion of the drive member 20 c and correspondingly reduce the rotary motion of the clamp member 18 c, the follower 30 c is moved radially inward toward an inwardly extending aperture 90 in the crank arm 76 . The radial distance of the follower 30 c translates the rotational movement of the crank arm 76 into linear motion of the follower 30 c in the slot 34 c of the cam bar 94 of the drive member 20 c.
- the drive member 20 c has a threaded rod 100 having opposite ends, wherein one end threadingly engages a threaded tubular portion 101 of the cam bar 94 , and the opposite end threadingly engages an outer shaft 102 of the drive member 20 c.
- the length of the drive member 20 c may be adjusted to correspond with the adjusted stroke of the linear reciprocal motion of the drive member 20 c.
- the drive member 20 c provides a telescopic portion 104 having the outer shaft 102 telescopically receive a connector sleeve or inner shaft 106 .
- the connector sleeve 106 has a smooth cylindrical configuration 107 at one end and a larger cylindrical, threaded portion 108 at its other end.
- the smooth cylindrical portion 107 of the connector sleeve 106 is telescopically received by the tubular cylindrical configuration of the outer shaft 102 .
- the threaded portion 108 of the connector sleeve 106 does not extend into the outer shaft 102 .
- the telescopic relationship of the outer shaft 102 and the connector sleeve 106 is maintained by the outer shaft 102 having a slot 110 extending through a wall of the outer shaft 102 .
- the connector sleeve 106 has an aperture extending through the smooth cylindrical portion 107 of the connector sleeve 106 and coaxially aligned with the slot 110 in the outer shaft 102 .
- a holding pin 112 extends through the slot 110 and into the aperture provided in the connector sleeve 106 .
- the holding pin 112 limits the telescopic movement of the drive member 20 c by abuting the portions of the outer shaft 102 defining the ends of the slot 110 when the connector sleeve 106 telescopically slides within the outer shaft 102 of the drive member 20 c between the extended position and the contracted position of the drive member 20 c.
- At least one compression spring 114 is mounted between the outer shaft 102 and the connector sleeve 106 of the drive member 20 c.
- the spring 114 has a compressive spring force equal to a desired clamping force of the clamp member 18 c.
- the crank arm 76 may continue to drive the drive member 20 c against the clamp member 18 c so that the telescopic portion 104 compresses, and the spring force of the spring 114 applies a constant force to the clamp member 18 c.
- the spring 114 essentially locks the clamp member 18 c into the clamped position until the crank arm 76 drives the drive member 20 c toward the released position.
- the second converting means may include one end of a rod end 116 threadingly connected to the threaded portion 108 of the connector sleeve 106 .
- the opposite end of the rod end 116 includes a slot (not shown) defined by two opposed protruding portions 118 of the rod end 116 .
- a pair of coaxial apertures having a common axis extend through the protruding portions 118 of the rod end 116 .
- the elongate link 64 is pivotally connected to the rod end 116 by pivot connection 68 extending through the apertures in the protruding portions 118 of the rod end 116 and through one aperture in the elongate link 64 .
- the opposite end of the elongate link 64 is pivotally connected to the radially extending arm 62 of the pivot pin 60 by pivot connection 66 .
- the pivot pin 60 is operably connected to the clamp member 18 c for moving the clamp member 18 c between the released position and the clamped position.
- the electric power means 12 of the power clamp 10 is actuated to impart rotary motion to the output shaft 28 .
- the output shaft 28 rotates the crank arm 76 thus rolling the follower 30 c along the slot 34 c provided in the cam bar 94 of the drive member 20 c.
- the rotational movement of the crank arm 76 imparts a linear reciprocal harmonic motion to drive member 20 c along its longitudinal axis 98 .
- the linear reciprocal harmonic motion of the drive member 20 c is transferred to the second converting means 24 c and transformed into harmonic rotary motion of the clamp member 18 c.
- the roller shaft 92 is inserted into one of the radially spaced apertures 90 in the crank arm 76 .
- the threaded rod 100 is threadingly adjusted within the outer shaft 102 of the drive member 20 c to correlate and complement the stroke of the linear reciprocal motion of the drive member 20 c.
- the position of the follower 30 c is preferably approaching the longitudinal axis 98 of the drive member 20 c.
- the pivot pin 60 typically engages a positive stop to prevent the clamp member 18 c from extending beyond the clamped position, and thus, the electric power means 12 increases the driving force of the drive member 20 c against the clamp member 18 c.
- the telescopic portion 104 of the drive member 20 c contracts against the spring force provided by spring 114 , and the holding pin 112 moves within the slot 110 as the outer shaft 102 telescopically slides relative to the connector sleeve 106 .
- the spring force of spring 114 applies a constant spring force against clamp member 18 c thus locking the clamp member 18 c in the clamped position.
- the spring 114 biases the telescopic portion 104 of the drive member 20 c towards the expanded position, and the holding pin 112 moves back relative to the slot 110 .
- the holding pin 112 engages the ends of the slot 110 provided in the outer shaft 102 of the drive member 20 c to define the contracted and extended positions of the telescopic portion 104 of drive member 20 c.
- the crank arm 76 continues to rotate thus bringing the clamp member 18 c to the released position and then back toward the clamped position.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Optics & Photonics (AREA)
- Transmission Devices (AREA)
- Jigs For Machine Tools (AREA)
- Gripping Jigs, Holding Jigs, And Positioning Jigs (AREA)
Abstract
A clamping apparatus includes a housing and a pivot pin mounted for pivoting movement about an axis of rotation with respect to the housing. A clamp member is connected to the pivot pin and is moveable between a clamped position and a released position in response to rotation of the pivot pin. The pivot pin has an arm extending radially outwardly from the axis of rotation. A drive member is mounted for linear reciprocal movement along a fixed path with respect to the housing, and a linkage connects the drive member to the arm of the pivot pin for converting reciprocal movement of the drive member into pivoting movement of the pivot pin. An electric motor is connected to an output shaft with an axis of rotation, and an adjustable converting mechanism connects the drive member to the electric motor for adjustably converting the rotary motion driving force into a linear reciprocal harmonic motion of the drive member. The adjustable converting mechanism allows the stroke of the linear reciprocal motion to be adjusted. In addition, an automatic adjusting mechanism allows the drive member to adjust its length in response to the driving force of the electric motor and the position of the clamp member.
Description
- 1. The following patent application is related to U.S. patent application Ser. No. 09/067,203 filed on Apr. 28, 1998.
- 2. The present invention relates to an electric power operated clamp for moving at least one clamp arm between a clamped position and a released position, and in particular, an adjustable mechanism that converts the rotary motion of an electric power source into linear reciprocal movement of a drive member and then into rotary motion of the clamp arm.
- 3. Various clamping devices have been provided for immovably securing a workpiece or workpieces with respect to a stationary support during a machining and/or welding operation. Most of these devices have incorporated fluid operated actuators, such as hydraulic or pneumatic operated piston and cylinder actuators. While these devices are satisfactory for clamping workpieces to a stationary support, difficulties arise in using clamps of this configuration for use in non-stationary support situations, such as moving transfer devices, conveyors, shuttles of the like. In addition, the use of hydraulic fluid in non-stationary applications can be the source of hydraulic fluid leaks, while the use of pneumatic actuators increases cost of operation by requiring the production of sufficient quantities of compressed air of predefined quality for operating clamping devices. Compressed air generally requires the use of fixed or flexible conduits to communicate the compressed air with the actuator, and may produce compressed air leaks increasing operating costs. Furthermore, it is difficult to obtain a harmonic motion clamp action with a hydraulic or pneumatic actuator, sometimes referred to as a “soft-touch” clamp, where the clamp decelerates adjacent the clamped and/or released position thereby eliminating the need for “bumpers” or other shock absorbing elements. Typically, hydraulic and pneumatic actuated clamps require complex control mechanisms to adjust the rate of actuation of the clamp to eliminate or reduce the amount of shock absorbed as the clamp reaches the clamped position and/or the released position.
- 4. It is desirable in the present invention to provide an electric power operated clamp to eliminate the recognized deficiencies in hydraulic and/or pneumatic operated clamps. In addition, it is desirable in the present invention to provide an electric power operated clamp having harmonic clamp motion, where the clamp decelerates as it approaches the clamped position and/or released position. The present invention provides a power operated clamp including an electric motor means for imparting a rotary motion driving force. A drive member is operably associated with the electric motor means. First converting means connects the drive member to the electric motor means. The first converting means converts the rotary motion driving force of the electric motor means into a linear reciprocal motion of the drive member. A clamp member is operably associated with the drive member. Second converting means connects the clamp member to the drive member. The second converting means converts the linear reciprocal motion of the drive member into rotary motion of the clamp arm to move the clamp member between a clamped position and a released position.
- 5. In the first configuration, the first converting means includes an elongate arm connected to a shaft of the electric motor means which extends radially outward for rotation with the shaft. A cam follower is connected to the elongate arm spaced radially from the shaft. The drive member is mounted for linear reciprocal movement along a fixed path. The drive member has a cam surface defining a slot adjacent one longitudinal end of the elongate drive member. The slot extends generally normal to the fixed path of the drive member. The cam follower operably engages within the slot for converting the rotational movement of the cam follower into linear movement of the drive member.
- 6. In an alternative configuration, the first converting means can include an eccentric member connected to the electric motor means for rotation therewith and having an external periphery. The drive member can include a connecting rod and slide block. The connecting rod has a complementary aperture formed therein for operably receiving the external periphery of the eccentric member. The connecting rod also includes a pivot pin for operably connecting to the slide block, such that the slide block is driven in reciprocal motion by the connecting rod in response to rotation of the eccentric member.
- 7. Another alternative embodiment can include the first converting means having a barrel cam connected to the electric motor means for rotation therewith. The barrel cam has a generally helical cam surface formed on an external periphery. The drive member has an aperture for receiving the barrel cam. A cam follower is supported by the drive member and is engageable with the cam surface for driving the drive member in linear motion in response to rotary motion of the barrel cam. Preferably, the generally helical cam surface is formed having reduced longitudinal spacing between turns adjacent one or both longitudinal ends to impart a harmonic motion to the clamp arm while approaching the respective end limit of movement corresponding to the clamped position and the released position.
- 8. In the preferred embodiment, the present invention provides an adjustable converting means for converting the rotary motion of the power means into linear reciprocal motion of the drive member. The adjustable converting means includes the first converting means having a crank arm connected to the power means and extending radially outward for rotation about an axis of rotation. The follower is connected to the crank arm and spaced radially from the axis of rotation. The drive member is mounted for reciprocal movement along a fixed path wherein the cam surface of the drive member defines the slot. The follower operably engages the slot to convert the rotational movement of the follower into linear movement of the drive member. The second converting means converts the linear reciprocal motion of the drive member into rotary motion of the clamp member.
- 9. A manual adjustment means is also provided in the preferred embodiment for adjusting the stroke of the linear reciprocal motion of the drive member. The manual adjustment means provides the crank arm with a plurality of apertures radially spaced from the axis of rotation wherein the follower is removably inserted in at least one of the apertures of the crank arm. The drive member includes a threaded rod and an outer shaft wherein the outer shaft threadingly receives the rod. The outer shaft and the rod threadingly adjust along the longitudinal axis of the drive member to adjust the length of the drive member in response to the position of the follower in the crank arm.
- 10. The preferred embodiment also provides an automatic adjustment means to automatically adjust the length of the drive member in response to the driving force of the power means and the position of the clamp member. The automatic adjustment means provides the drive member with a telescopic portion telescopically moveable along the longitudinal axis of the drive member between an extended position and a contracted position. A positive stop limits the telescopic movement of the telescopic portion between the extended position and the contracted position. At least one compression spring biases the telescopic portion of the drive member toward the extended position.
- 11. Other objects, advantages and applications of the present invention will become apparent to those skilled in the art when the following description of the best mode contemplated for practicing the invention is read in conjunction with the accompanying drawings.
- 12. The description herein makes reference to the accompanying drawings wherein like reference numerals refer to like parts throughout the several views, and wherein:
- 13.FIG. 1 is a perspective view of an electric power operated clamp according to the present invention;
- 14.FIG. 2 is a simplified internal view of the clamp with one half of the housing removed in order to show the internal mechanism;
- 15.FIG. 3 is a top view of the electric power operated clamp illustrated in FIG. 2 with the housing in place enclosing the internal mechanism;
- 16.FIG. 4 is a simplified schematic view of an alternative embodiment of first converting means for converting the rotary motion driving force of the electric motor means into a linear reciprocal motion of a drive member according to the present invention;
- 17.FIG. 5 is a simplified schematic view of an alternative embodiment of the first converting means;
- 18.FIG. 6 is a perspective cut away view of an electric power operated clamp according to the present invention;
- 19.FIG. 7 is a front view of the power means and the drive member of the present invention;
- 20.FIG. 8 is an exploded view of the drive member of the present invention;
- 21.FIG. 9 is a sectional view taken in the direction of
arrows 9—9 in FIG. 7; and - 22.FIG. 10 is a plan view of the crank arm.
- 23. A power operated
clamp 10 is illustrated in perspective view in FIG. 1. The power operatedclamp 10 includes an electric motor means 12 for imparting a rotary motion driving force to the clamp assembly. Agear box 14 can be provided, if required, between the electric motor means 12 and theclamp actuator housing 16. Aclamp member 18 is operably associated with thehousing 16 for movement between a clamped position and a released position. - 24. Referring now to FIGS. 2 and 3, a
drive member 20 is operably associated with the electric motor means 12. First convertingmeans 22 connects thedrive member 20 to the electric motor means 12. The first convertingmeans 22 is for converting the rotary motion driving force of the electric motor means 12 into a linear reciprocal motion of thedrive member 20. Second convertingmeans 24 connects theclamp member 18 to thedrive member 20. The second convertingmeans 24 is for converting the linear reciprocal motion of thedrive member 20 into rotary motion of theclamp member 18 to move theclamp member 18 between a clamped position and a released position. - 25. In the embodiment depicted in FIGS. 2 and 3, the first converting
means 22 can include anelongate arm 26 connected to anoutput shaft 28 of the electric motor means 12. Theelongate arm 26 extends radially outward for rotation with theshaft 28. Afollower 30 is connected to theelongate arm 26 and is spaced radially from the longitudinal axis of theshaft 28. Thedrive member 20 is mounted for linear reciprocal movement along a fixed path and has acam surface 32 adjacent one longitudinal end of theelongate drive member 20. Preferably, thecam surface 32 defines aslot 34, and more preferably, theslot 34 extends generally normal to the fixed path of travel for thedrive member 20. Thefollower 30 operably engages within theslot 34 for converting the rotational movement of thefollower 30 into linear movement of thedrive member 20. In the preferred configuration illustrated in FIGS. 2 and 3, theslot 34 is linear and generally perpendicular to the fixed path of thedrive member 20. This configuration provides the desired harmonic motion clamp action. - 26. An alternative configuration of the first converting means 22 a is illustrated in FIG. 4. In this configuration, an
eccentric member 36 is connected to theshaft 28 a of the electric motor means for rotation therewith. Theeccentric member 36 has anexternal periphery 38. In this embodiment, thedrive member 20 a includes a connectingrod 40 and aslide block 42. The connectingrod 40 has acomplementary aperture 44 formed therein for operably receiving theexternal periphery 38 of theeccentric member 36. The connectingrod 40 also includes a pivot point or pin 46 for operably connecting the connectingrod 40 to theslide block 42. Theslide block 42 is driven in reciprocal motion by the connectingrod 40 in response to rotation of theeccentric member 36. This configuration for the first converting means 22 a also provides the desirable harmonic motion clamp action, sometimes referred to as a “soft-touch” clamp. In this respect, both the embodiment depicted in FIGS. 2 and 3, and the alternative configuration of the first converting means 22 a of FIG. 4 provide a clamp that decelerates adjacent the clamped position and the released position, while achieving maximum acceleration generally midway between the clamped position and released position. This configuration eliminates the need for “bumpers” or other shock absorbing elements at the end limit of movement of the clamp. - 27. Another alternative configuration for the first converting means 22 b is illustrated in FIG. 5. In this embodiment, the first converting means 22 b includes a
barrel cam 48. Thebarrel cam 48 includes anaperture 50 for receiving an output shaft of the electric motor means, so that thebarrel cam 48 is driven in rotation in response to rotation of the shaft of the electric motor means. Thebarrel cam 48 includes a generallyhelical cam surface 52 formed on anexternal periphery 54. The drive member 20 b includes anaperture 56 for receiving thebarrel cam 48. Acam follower 58 is supported by the drive member 20 b and is engagable with thecam surface 52 for driving the drive member 20 b in linear motion in response to rotary motion of thebarrel cam 48. Preferably, the generallyhelical cam surface 52 is formed having reduced longitudinal spacing between turns adjacent one or both longitudinal ends of thebarrel cam 48 to impart a harmonic motion to theclamp member 18 while approaching one or both end limits of movement corresponding to either or both of the clamped position and the released position. This embodiment also provides the first convertingmeans 22 with the desirable harmonic motion driving force provided in the previously described embodiments. - 28. Referring now to FIG. 2, the second converting means 24 can include a
pivot pin 60 operably connected to theclamp member 18 for moving theclamp member 18 between a released position and a clamped position about a rotational axis. Thepivot pin 60 has aradially extending arm 62. Anelongate link 64 has afirst pivot connection 66 to theradially extending arm 62 of thepivot pin 60 and asecond pivot connection 68 to thedrive member means drive member clamp member 18 as it approaches one or both end limits of travel. - 29. In the configuration illustrated in FIGS. 1-3, the power operated
clamp 10 includes an electric motor connected to an output shaft with a longitudinal axis. The shaft can be connected to the first convertingmeans gear box 14 as appropriate for the particular power operated clamp. Anelongate arm 26 is connected to theshaft 28 and extends radially outwardly from the longitudinal axis for rotation with theshaft 28. Afollower 30 is connected to theelongate arm 26 and is spaced radially from the longitudinal axis of the shaft. Ahousing 16 at least partially encloses theelongate arm 26 andfollower 30. Anelongate drive member 20 is mounted for linear reciprocal movement along a fixed path with respect to thehousing 16. Thedrive member 20 has acam surface 32 defining alinear slot 34 adjacent one longitudinal end of theelongate drive member 20. Theslot 34 preferably extends normal to the fixed path of reciprocal movement for thedrive member 20. Thefollower 30 operably engages within theslot 34 for converting the rotational movement of thefollower 30 into linear movement of thedrive member 20. At least oneelongate link member 64 is pivotally connected to a longitudinal end of thedrive member 20 opposite from theslot 34. Apivot pin 60 includes anarm 62 connected thereto for rotational movement therewith. Thepin 60 is supported in thehousing 16 for rotation with respect to thehousing 16. Thearm 62 is pivotally connected to thelink member 64 for converting linear movement of theelongate drive member 20 into rotational movement of thepivot pin 60 through thelink member 64. Aclamp member 18 is connected to thepivot pin 60 for movement between a clamped position and a released position in response to movement of thedrive member 20 operably engaging thefollower 30 driven by theelectric motor 12. - 30. In one embodiment, the first converting mechanism includes a elongate arm driven by the rotatable shaft of the electric motor and extending radially outwardly with a follower connected to the elongate arm spaced from the axis of rotation. A cam surface is formed on the drive member and is engaged by the follower for driving the drive member in reciprocal linear harmonic motion in response to rotation of the shaft. In a second embodiment, the first converting mechanism includes an eccentric member connected to the shaft driven by the electric motor and the drive member including a connecting rod and slide block, where the connecting rod has a complementary aperture for operably receiving the internal periphery of the eccentric member and a pivot point for operably connecting to the slide block, so that the slide block is driven in reciprocal linear harmonic motion by the connecting rod in response to rotation of the eccentric member. In a third embodiment, the first converting mechanism includes a barrel cam connected to the shaft driven by the electric motor for rotation. The barrel cam has a generally helical cam surface formed on an external periphery, and the drive member has an aperture for receiving the barrel cam. The cam follower is supported by the drive member and is engageable with the cam surface for driving the drive member in reciprocal linear harmonic motion in response to rotary motion of the barrel cam.
- 31. In the preferred embodiment illustrated in FIGS. 6-10, the power operated
clamp 10 includes the electric motor means 12 for imparting a rotary motion driving force to the clamp assembly. As previously noted, the electric motor means 12 may be utilized in conjunction with thegear box 14 in order to provide the desired torque and speed characteristics of thepower clamp 10. Although the present invention is best suited for use with an electric motor as the power means, any number of power sources may be utilized which render the characteristics associated with an electric motor. The electric motor means 12 is connected to theclamp actuator housing 16, and thehousing 16 has acover assembly 17 for enclosing thehousing 16. The clamp member 18 c is operably associated with thehousing 16 for movement between the clamped position and the released position. - 32. As seen in FIGS. 6-9, the drive member 20 c is operably associated with the electric power means 12. An adjustable converting
means 70 converts the rotary motion of the electric power means 12 into linear reciprocal motion of the drive member 20 c. The adjustable convertingmeans 70 includes the first converting means 22 c which connects the drive member 20 c to the electric motor means 12. The first converting means 22 c converts the rotary motion driving force of the electric motor means 12 into a linear reciprocal motion of the drive member 20 c. The second converting means 24 c connects the clamp member 18 c to the drive member 20 c. The second converting means 24 c is for converting the linear reciprocal motion of the drive member 20 c into rotary motion of the clamp member 18 c and to move the clamp member 18 c between the clamped position and the released position. The adjustable convertingmeans 70 also includes a manual adjusting means 72 for adjusting the stroke of the linear reciprocal motion of the drive member 20 c and an automatic adjusting means 74 for automatically adjusting the length of the drive member 20 c in response to the driving force of the electric power means 12 and the position of the clamp member 18 c. - 33. To convert the rotary motion of the electric power means 12 into linear reciprocal motion of the drive member 20 c, the first converting means 22 c may include a
crank arm 76 connected to theoutput shaft 28 of the electric motor means 12. The electric motor means 12 is connected to theclamp actuator housing 16, and theoutput shaft 28 of the electric motor means 12 extends through anaperture 78 provided in theclamp actuator housing 16. Thecrank arm 76 has a disk shaped configuration having anaperture 80 extending therethrough along thecenterline axis 81 of thecrank arm 76 for receiving theoutput shaft 28 of the electric motor means 12. The clamp actuatorhousing 16 has a recessedportion 82 for receiving the disk shapedcrank arm 76. Aset screw 84 extends through aradially extending aperture 86 provided in thecrank arm 76 to secure thecrank arm 76 to theoutput shaft 28 of the electric motor means 12. A correspondingaperture 88 is provided in theclamp actuator housing 16 to access theset screw 84 from outside theclamp actuator housing 16. - 34. The
crank arm 76 is connected to the drive member 20 c by the follower or roller 30 c. The follower 30 c is rollably mounted to aroller shaft 92 which is inserted into a correspondingaperture 90 provided in thecrank arm 76. Theaperture 90 is one of a plurality ofapertures 90 which are radially spaced from thelongitudinal axis 81 of thedrive shaft 28 and which will be described in detail later. The drive member 20 c is mounted for linear reciprocal movement along a fixed path wherein abore 93 extending through a portion of thehousing 16 slidingly receives the drive member 20 c. Abushing 95 lines thebore 93 and is retained by a retainingclip 97. Acam bar 94 is adjacent one longitudinal end of the drive member 20 c for operably engaging the follower 30 c. Thecam bar 94 provides acam surface 32 which defines a linear slot 34 c for receiving the follower 30 c. The slot 34 c extends substantially normal to the fixed path of travel for the drive member 20 c. This configuration provides the desired harmonic motion clamp action, previously referred to as a “soft-touch” clamp. In this regard, the clamp member 18 c decelerates adjacent the clamp position and the released position, while achieving maximum acceleration generally midway between the clamped position and the released position. - 35. To manually adjust the stroke of the linear reciprocal motion of the drive member 20 c, the
crank arm 76 provides the plurality of radially spacedapertures 90, as seen in FIG. 10. To lengthen the stroke of the linear reciprocal motion of the drive member 20 c and correspondingly expand the rotary motion of the clamp member 18 c, the follower 30 c is moved radially outward toward an outwardly extendingaperture 90 in thecrank arm 76. To shorten or contract the stroke of the linear reciprocal motion of the drive member 20 c and correspondingly reduce the rotary motion of the clamp member 18 c, the follower 30 c is moved radially inward toward an inwardly extendingaperture 90 in thecrank arm 76. The radial distance of the follower 30 c translates the rotational movement of thecrank arm 76 into linear motion of the follower 30 c in the slot 34 c of thecam bar 94 of the drive member 20 c. - 36. To correspondingly adjust the length of the drive member 20 c to the stroke of the linear reciprocal motion of the drive member 20 c, the drive member 20 c has a threaded
rod 100 having opposite ends, wherein one end threadingly engages a threadedtubular portion 101 of thecam bar 94, and the opposite end threadingly engages anouter shaft 102 of the drive member 20 c. By threadingly engaging and adjusting theouter shaft 102 with the threadedrod 100, the length of the drive member 20 c may be adjusted to correspond with the adjusted stroke of the linear reciprocal motion of the drive member 20 c. - 37. To automatically adjust the length of the drive member 20 c in response to the driving force of the electric power means 12 and the position of the clamp member 18 c, the drive member 20 c provides a
telescopic portion 104 having theouter shaft 102 telescopically receive a connector sleeve orinner shaft 106. Theconnector sleeve 106 has a smoothcylindrical configuration 107 at one end and a larger cylindrical, threadedportion 108 at its other end. The smoothcylindrical portion 107 of theconnector sleeve 106 is telescopically received by the tubular cylindrical configuration of theouter shaft 102. The threadedportion 108 of theconnector sleeve 106 does not extend into theouter shaft 102. The telescopic relationship of theouter shaft 102 and theconnector sleeve 106 is maintained by theouter shaft 102 having aslot 110 extending through a wall of theouter shaft 102. Theconnector sleeve 106 has an aperture extending through the smoothcylindrical portion 107 of theconnector sleeve 106 and coaxially aligned with theslot 110 in theouter shaft 102. A holdingpin 112 extends through theslot 110 and into the aperture provided in theconnector sleeve 106. The holdingpin 112 limits the telescopic movement of the drive member 20 c by abuting the portions of theouter shaft 102 defining the ends of theslot 110 when theconnector sleeve 106 telescopically slides within theouter shaft 102 of the drive member 20 c between the extended position and the contracted position of the drive member 20 c. - 38. To bias the
telescopic portion 104 toward the extended position, at least onecompression spring 114 is mounted between theouter shaft 102 and theconnector sleeve 106 of the drive member 20 c. Thespring 114 has a compressive spring force equal to a desired clamping force of the clamp member 18 c. When the clamp member 18 c moves into the clamped position, thecrank arm 76 may continue to drive the drive member 20 c against the clamp member 18 c so that thetelescopic portion 104 compresses, and the spring force of thespring 114 applies a constant force to the clamp member 18 c. Thespring 114 essentially locks the clamp member 18 c into the clamped position until thecrank arm 76 drives the drive member 20 c toward the released position. - 39. The second converting means may include one end of a
rod end 116 threadingly connected to the threadedportion 108 of theconnector sleeve 106. The opposite end of therod end 116 includes a slot (not shown) defined by two opposed protrudingportions 118 of therod end 116. A pair of coaxial apertures having a common axis extend through the protrudingportions 118 of therod end 116. Theelongate link 64 is pivotally connected to therod end 116 bypivot connection 68 extending through the apertures in the protrudingportions 118 of therod end 116 and through one aperture in theelongate link 64. The opposite end of theelongate link 64 is pivotally connected to theradially extending arm 62 of thepivot pin 60 bypivot connection 66. Thepivot pin 60 is operably connected to the clamp member 18 c for moving the clamp member 18 c between the released position and the clamped position. - 40. In operation, the electric power means 12 of the
power clamp 10 is actuated to impart rotary motion to theoutput shaft 28. Theoutput shaft 28 rotates thecrank arm 76 thus rolling the follower 30 c along the slot 34 c provided in thecam bar 94 of the drive member 20 c. The rotational movement of thecrank arm 76 imparts a linear reciprocal harmonic motion to drive member 20 c along itslongitudinal axis 98. The linear reciprocal harmonic motion of the drive member 20 c is transferred to the second converting means 24 c and transformed into harmonic rotary motion of the clamp member 18 c. - 41. To adjust the stroke of the linear reciprocal harmonic motion of the drive member 20 c, the
roller shaft 92 is inserted into one of the radially spacedapertures 90 in thecrank arm 76. The further the follower 30 c is radially spaced from theoutput shaft 28, the longer the stroke of the linear reciprocal motion. Since the clamp assembly is stationarily positioned, the length of the drive member 20 c must be manually adjusted to compensate for the stroke of the linear actuator motion. The threadedrod 100 is threadingly adjusted within theouter shaft 102 of the drive member 20 c to correlate and complement the stroke of the linear reciprocal motion of the drive member 20 c. - 42. When the
power clamp 10 reaches the clamped position, the position of the follower 30 c is preferably approaching thelongitudinal axis 98 of the drive member 20 c. In the clamped position, thepivot pin 60 typically engages a positive stop to prevent the clamp member 18 c from extending beyond the clamped position, and thus, the electric power means 12 increases the driving force of the drive member 20 c against the clamp member 18 c. In response to the driving force of the electric power means 12 and the clamp member 18 c in the clamped position, thetelescopic portion 104 of the drive member 20 c contracts against the spring force provided byspring 114, and the holdingpin 112 moves within theslot 110 as theouter shaft 102 telescopically slides relative to theconnector sleeve 106. As the follower 30 c approaches, reaches, and extends just beyond thelongitudinal axis 98 of the drive member 20 c such that the clamp member 18 c remains in the clamped position, the spring force ofspring 114 applies a constant spring force against clamp member 18 c thus locking the clamp member 18 c in the clamped position. Once the follower 30 c travels far enough towards the released position to release the clamp member 18 c from the clamped position, thespring 114 biases thetelescopic portion 104 of the drive member 20 c towards the expanded position, and the holdingpin 112 moves back relative to theslot 110. As previously noted, the holdingpin 112 engages the ends of theslot 110 provided in theouter shaft 102 of the drive member 20 c to define the contracted and extended positions of thetelescopic portion 104 of drive member 20 c. Thecrank arm 76 continues to rotate thus bringing the clamp member 18 c to the released position and then back toward the clamped position. - 43. While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiments but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as is permitted under the law.
Claims (30)
1. A power operated clamp comprising:
power means for imparting a rotary motion driving force;
a drive member operably associated with said power means;
a clamp member operably associated with said drive member for moving said clamp member between a clamped position and a released position; and
adjustable means for converting said rotary motion of said power means into a linear reciprocal motion of said drive member.
2. The power operated clamp stated in , wherein said adjustable converting means comprises:
claim 1
means for automatically adjusting the length of said drive member in response to said driving force of said power means and the position of said clamp member.
3. The power operated clamp stated in , wherein said automatic adjusting means comprises:
claim 2
said drive member having a telescopic portion telescopically movable along a longitudinal axis between an extended position and a contracted position;
a positive stop for limiting the telescopic movement of said telescopic portion between said extended position and said contracted position; and
at least one spring biasing said telescopic portion toward said extended position.
4. The power operated clamp stated in , wherein said positive stop comprises:
claim 3
said telescopic portion having an outer shaft and an inner shaft;
a pin connected to either one of said inner shaft and said outer shaft; and
a slot formed in the other of said outer shaft and said inner shaft, and said slot receiving said pin for defining said telescopic movement of said telescopic portion between said extended position and said contracted position.
5. The power operated clamp stated in , wherein said adjustable converting means comprises:
claim 1
a crank arm connected to said power means and extending radially outward for rotation about an axis of rotation;
a follower connected to said crank arm; and
said drive member mounted for linear reciprocal movement along a fixed path, said drive member having a cam surface defining a slot, and said follower operably engageable within said slot for converting the rotational movement of said follower into linear movement of said drive member.
6. The power operated clamp stated in , further comprising:
claim 5
manual means for adjusting the stroke of said linear reciprocal motion of said drive member.
7. The power operated clamp stated in , further comprising:
claim 6
said crank arm having a plurality of apertures radially spaced from said axis of rotation; and
said follower removably inserted in at least one of said apertures of said crank arm.
8. The power operated clamp stated in , wherein said slot extends substantially normal to said fixed path.
claim 5
9. A power operated clamp stated in , wherein said slot is substantially linear.
claim 5
10. The power operated clamp stated in , further comprising:
claim 1
means, connecting the clamp member to said drive member, for converting said linear reciprocal motion of said drive member into rotary motion of said clamp member.
11. The power operated clamp stated in , wherein said power means is electrical.
claim 1
12. A power operated clamp comprising:
electrical power means of for imparting a rotational driving force;
a drive member operably associated with said electric power means;
first converting means, connecting the drive member to said electric power means, for converting said rotational driving force into a linear reciprocal motion of said drive member;
a clamp member operably associated with said drive member for moving said clamp member between a clamped position and a released position; and
said drive member having means for automatically adjusting the length of said drive member in response to said driving force of said electric power means and the position of said clamp member.
13. The power operated clamp stated in , wherein said automatic adjusting means comprises:
claim 12
said drive member having an outer shaft and an inner shaft wherein said outer shaft telescopically receives said inner shaft for telescopic movement of said inner shaft relative to said outer shaft between an extended position and a contracted position;
a positive stop for limiting telescopic movement of said drive member between said extended position and said contracted position; and
at least one compression spring operably connected to said outer shaft and said inner shaft for biasing said drive member toward said extended position.
14. The power operated clamp stated in , wherein said positive stop comprises:
claim 13
a pin connected to one of either said outer shaft and said inner shaft of said drive member; and
a slot formed in the other of said outer shaft and said inner shaft, and said slot receiving said pin and defining said extended and contracted positions by said pin engaging the ends of said slot.
15. The power operated clamp as stated in , wherein said first converting means comprises:
claim 12
a crank arm connected to said electric power means and extending radially outward for rotation about an axis of rotation;
a follower connected to said crank arm; and
said drive member mounted for linear reciprocal movement along a fixed path, said drive member having a cam surface defining a slot, and said follower operably engageable within said slot for converting the rotational movement of said follower into linear movement of said drive member.
16. The power operated clamp as stated in , further comprising:
claim 15
manual means for adjusting the stroke of said linear reciprocal motion of said drive member.
17. The power operated clamp as stated in , wherein said manual adjusting means comprises:
claim 16
said crank arm having a plurality of apertures radially spaced from said axis of rotation; and
said follower removably inserted in at least one of said apertures of said crank arm.
18. The power operated clamp as stated in , further comprising:
claim 17
said drive member having an outer shaft and a threaded shaft wherein said outer shaft threadingly receives said threaded shaft for threadingly adjusting the length of said drive member in response to the position of said follower relative to said crank arm.
19. The power actuated clamp as stated in , wherein said slot extends substantially normal to said fixed path.
claim 15
20. The power operated clamp stated in , wherein said slot is substantially linear.
claim 15
21. The power operated clamp stated in , further comprising:
claim 12
second converting means, connecting said clamp member to said drive member, for converting said linear reciprocal motion of said drive member into rotary motion of said clamp member.
22. The power operated clamp stated in , wherein said linear reciprocal motion of said drive member is harmonic.
claim 12
23. A power operated clamp comprising:
an electrical motor for imparting a rotational driving force;
a crank arm connected to said electrical motor and extending radially outward for rotation about an axis of rotation;
a follower connected to said crank arm;
said drive member mounted for linear reciprocal movement along a fixed path and having a cam surface defining a slot, and said follower operably engageable within said slot for converting the rotational movement of said follower into harmonic linear movement of said drive member;
a clamp member operably associated with said drive member for moving said clamp member between a clamped position and a released position;
means for automatically adjusting the length of said drive member in response to said driving force of said electric motor and the position of said clamp member; and
manual means for adjusting the stroke of said linear reciprocal harmonic motion of said drive member.
24. The power operated clamp as stated in , wherein said automatic adjusting means comprises:
claim 23
said drive member having an outer shaft and an inner shaft wherein said outer shaft telescopically receives said inner shaft for telescopic movement between an extended position and a contracted position;
a positive stop for limiting said telescopic movement of said drive member between said extended position and said contracted position; and
at least one compression spring operably connected to said outer shaft and said inner shaft of said drive member, and said spring biasing said drive member toward said extended position.
25. The power operated clamp as stated in , wherein said positive stop comprises:
claim 24
a pin connected to said inner shaft of said drive member; and
a slot formed in said outer shaft of said drive member for receiving said pin wherein said extended and contracted positions are defined by said pin engaging the ends of said slot.
26. The power operated clamp as stated in , wherein said manual adjusting means comprises:
claim 23
said crank arm having a plurality of apertures radially spaced from said axis of rotation; and
said follower removably inserted in at least one of said apertures of said crank arm.
27. The power operated clamp as stated in , further comprising:
claim 26
said drive member having an outer shaft and a threaded shaft wherein said outer shaft threadingly receives said threaded shaft for threadingly adjusting the length of said drive member in response to the position of the follower relative to the crank arm.
28. The power operated clamp as stated in , wherein said slot extends substantially normal to said fixed path.
claim 25
29. The power operated clamp as stated in , wherein said slot is substantially linear.
claim 25
30. The power operated clamp as state in , further comprising:
claim 23
second converting means, connecting said clamp member to said drive member for converting said linear reciprocal harmonic motion of said drive member into rotary harmonic motion of said clamp member.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/730,667 US6422549B2 (en) | 1998-04-28 | 2000-12-06 | Electric power operated clamp with spring lock |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/067,203 US6003850A (en) | 1998-04-28 | 1998-04-28 | Electric power operated clamp |
US09/140,172 US6199846B1 (en) | 1998-04-28 | 1998-08-26 | Electric power operated clamp with spring lock |
US09/730,667 US6422549B2 (en) | 1998-04-28 | 2000-12-06 | Electric power operated clamp with spring lock |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/140,172 Continuation US6199846B1 (en) | 1998-04-28 | 1998-08-26 | Electric power operated clamp with spring lock |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010000211A1 true US20010000211A1 (en) | 2001-04-12 |
US6422549B2 US6422549B2 (en) | 2002-07-23 |
Family
ID=22490055
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/140,172 Expired - Fee Related US6199846B1 (en) | 1998-04-28 | 1998-08-26 | Electric power operated clamp with spring lock |
US09/730,667 Expired - Fee Related US6422549B2 (en) | 1998-04-28 | 2000-12-06 | Electric power operated clamp with spring lock |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/140,172 Expired - Fee Related US6199846B1 (en) | 1998-04-28 | 1998-08-26 | Electric power operated clamp with spring lock |
Country Status (2)
Country | Link |
---|---|
US (2) | US6199846B1 (en) |
EP (1) | EP0982099A3 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1350591A1 (en) * | 2002-04-02 | 2003-10-08 | Luciano Migliori | clamping device for laser welding |
US20040150149A1 (en) * | 2003-01-31 | 2004-08-05 | Smc Corporation | Electric clamping device |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001310225A (en) * | 2000-04-28 | 2001-11-06 | Smc Corp | Electric clamp device |
US6488273B2 (en) * | 2001-04-20 | 2002-12-03 | Btm Corporation | Powered pivot unit |
US7156385B2 (en) * | 2003-06-03 | 2007-01-02 | Norgren Automotive, Inc. | Linearly adjustable apparatus for locating a workpiece |
US7815176B2 (en) | 2003-09-11 | 2010-10-19 | Phd, Inc. | Lock mechanism for pin clamp assembly |
US7182326B2 (en) * | 2004-04-02 | 2007-02-27 | Phd, Inc. | Pin clamp |
US7516948B2 (en) * | 2004-04-02 | 2009-04-14 | Phd, Inc. | Pin clamp accessories |
FR2871715B1 (en) * | 2004-06-22 | 2007-10-05 | Robotic Sa | DEVICE FOR CLAMPING A BUILDING WORKPIECE |
US7448607B2 (en) * | 2004-12-15 | 2008-11-11 | Phd, Inc. | Pin clamp assembly |
US20070138724A1 (en) * | 2005-12-16 | 2007-06-21 | Black & Decker | Clamp Device |
US20070267795A1 (en) * | 2006-02-06 | 2007-11-22 | Parag Patwardhan | Pin clamp transfer assembly and method of transferring a workpiece |
US8413970B2 (en) | 2007-06-19 | 2013-04-09 | Phd, Inc. | Pin clamp assembly |
ES2343868T3 (en) * | 2007-12-18 | 2010-08-11 | Nestec S.A. | DEVICE TO PREPARE A DRINK THAT INCLUDES A REGULABLE CLOSURE MECHANISM. |
MX2010014266A (en) * | 2008-06-18 | 2011-03-29 | Phd Inc Star | Strip off pin clamp. |
JP5887680B2 (en) * | 2012-01-27 | 2016-03-16 | Smc株式会社 | Electric clamp device |
DE102014111344A1 (en) * | 2014-08-08 | 2016-02-11 | De-Sta-Co Europe Gmbh | jig |
US10882148B2 (en) * | 2017-08-01 | 2021-01-05 | Caromation, Inc. | Pivot unit |
CN107876257B (en) * | 2017-12-13 | 2024-01-09 | 昆山钴瓷金属科技有限公司 | Ball core surface uniform thermal spraying rotary fixing device |
CN114986039B (en) * | 2022-07-20 | 2022-10-25 | 江苏永成汽车零部件股份有限公司 | Multi-station clamping type welding equipment for machining automobile bumper |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3147004A (en) | 1959-02-02 | 1964-09-01 | Leland F Blatt | Work securing clamp |
US3599957A (en) | 1969-04-28 | 1971-08-17 | Leland F Blatt | Cam wedge power swing away with guided arm |
US4459945A (en) * | 1981-12-07 | 1984-07-17 | Chatfield Glen F | Cam controlled reciprocating piston device |
US4494739A (en) | 1983-03-04 | 1985-01-22 | State Die & Engineering, Inc. | Power operated rotatable clamping assembly |
US4635911A (en) * | 1985-08-30 | 1987-01-13 | Lovrenich Rodger T | Motorized over center clamp |
DE3613644A1 (en) * | 1986-04-23 | 1987-10-29 | Josef Gerhard Tuenkers | POWER DRIVEN TOGGLE TENSIONER |
US4723767A (en) | 1986-08-08 | 1988-02-09 | De-Sta-Co Division, Dover Resources, Inc. | Rotary powered linear actuated clamp |
US4700936A (en) * | 1986-08-26 | 1987-10-20 | Lamb Technicon Corp. | Clamp mechanism |
DE3638526C1 (en) * | 1986-11-11 | 1987-07-30 | Sta Co Mettallerzeugnisse Gmbh | Workpiece clamping device that can be driven by an electric motor |
US5575462A (en) | 1994-08-17 | 1996-11-19 | Blatt; John A. | Rotary clamp for a linear actuator |
DE19732600C2 (en) * | 1997-07-29 | 2000-03-30 | Benteler Werke Ag | Component clamp |
JP4310525B2 (en) * | 1998-10-20 | 2009-08-12 | Smc株式会社 | Cylinder device |
DE29901363U1 (en) * | 1999-01-27 | 1999-05-06 | Festo AG & Co, 73734 Esslingen | Toggle clamp device |
GB2359512B (en) * | 1999-11-26 | 2004-01-21 | Hmc Brauer Ltd | Power clamps |
-
1998
- 1998-08-26 US US09/140,172 patent/US6199846B1/en not_active Expired - Fee Related
-
1999
- 1999-08-23 EP EP99306664A patent/EP0982099A3/en not_active Withdrawn
-
2000
- 2000-12-06 US US09/730,667 patent/US6422549B2/en not_active Expired - Fee Related
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1350591A1 (en) * | 2002-04-02 | 2003-10-08 | Luciano Migliori | clamping device for laser welding |
US6812428B2 (en) | 2002-04-02 | 2004-11-02 | Luciano Migliori | Clamping device for laser welding |
US20040150149A1 (en) * | 2003-01-31 | 2004-08-05 | Smc Corporation | Electric clamping device |
US6869068B2 (en) | 2003-01-31 | 2005-03-22 | Smc Corporation | Electric clamping device |
Also Published As
Publication number | Publication date |
---|---|
EP0982099A3 (en) | 2002-05-02 |
US6199846B1 (en) | 2001-03-13 |
US6422549B2 (en) | 2002-07-23 |
EP0982099A2 (en) | 2000-03-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6199846B1 (en) | Electric power operated clamp with spring lock | |
US7443121B2 (en) | Actuator control system | |
US5575462A (en) | Rotary clamp for a linear actuator | |
US5938257A (en) | Power actuated parallel gripper | |
BRPI1003595A2 (en) | optically effective surface finish machining device, in particular eyeglass lenses | |
CN112606030A (en) | Exhibition arm adjustable gripper and intelligent robot | |
KR100250243B1 (en) | Universal support and positioning structure for tools used by an elongate element bending machine | |
US20040140294A1 (en) | Driving device and clamping tool equipped with same | |
US4939983A (en) | Fluid pressure operated positioning apparatus | |
US6726194B2 (en) | Electrically-operated clamping device | |
US6003850A (en) | Electric power operated clamp | |
CN117359358A (en) | Multi-station oil pressure combined clamp device for machining upper shaft of planetary reducer | |
KR100397294B1 (en) | Clamping device with mechanical power amplifier | |
US2573403A (en) | Fluid operated chuck | |
EP1849559B1 (en) | Positioning and/or clamping apparatus, with adjustable opening position of the working arm | |
CN215432515U (en) | Rotary position adjuster | |
US5224747A (en) | Chuck device with multistage degree of opening | |
US4593573A (en) | Inversion cam and cylinder power means | |
CN217619026U (en) | Lathe with conical body internal expansion type clamp | |
US5033555A (en) | Fluid cylinder powered tool | |
KR102004251B1 (en) | Electro-mechanic tread braking apparatus for railway vehicle | |
CN207431781U (en) | A kind of clamp system of universal joint | |
US4493245A (en) | Rotary and linear actuating device | |
US5216930A (en) | Power work arm | |
CN2738925Y (en) | Finial device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: NORGREN AUTOMOTIVE, INC., MICHIGAN Free format text: CHANGE OF NAME;ASSIGNOR:ISI NORGREN INC.;REEL/FRAME:011898/0927 Effective date: 20010530 |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
FPAY | Fee payment |
Year of fee payment: 8 |
|
SULP | Surcharge for late payment |
Year of fee payment: 7 |
|
REMI | Maintenance fee reminder mailed | ||
LAPS | Lapse for failure to pay maintenance fees | ||
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Expired due to failure to pay maintenance fee |
Effective date: 20140723 |