EP2359984B1 - Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement - Google Patents

Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement Download PDF

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Publication number
EP2359984B1
EP2359984B1 EP10012910.5A EP10012910A EP2359984B1 EP 2359984 B1 EP2359984 B1 EP 2359984B1 EP 10012910 A EP10012910 A EP 10012910A EP 2359984 B1 EP2359984 B1 EP 2359984B1
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EP
European Patent Office
Prior art keywords
push
driver
pull rod
lever
actuating arm
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.)
Active
Application number
EP10012910.5A
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German (de)
English (en)
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EP2359984A1 (fr
Inventor
Manfred Geier
Ralf Strauss
Phil Reed
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Irwin Industrial Tool Co
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Irwin Industrial Tool Co
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Filing date
Publication date
Priority claimed from DE2003135352 external-priority patent/DE10335352B4/de
Priority claimed from DE2003135351 external-priority patent/DE10335351B4/de
Priority claimed from DE2003135354 external-priority patent/DE10335354B4/de
Priority claimed from DE2003135353 external-priority patent/DE10335353B4/de
Priority claimed from DE2003135365 external-priority patent/DE10335365A1/de
Application filed by Irwin Industrial Tool Co filed Critical Irwin Industrial Tool Co
Publication of EP2359984A1 publication Critical patent/EP2359984A1/fr
Application granted granted Critical
Publication of EP2359984B1 publication Critical patent/EP2359984B1/fr
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    • 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
    • B25B5/068—Arrangements for positively actuating jaws with at least one jaw sliding along a bar

Definitions

  • the invention relates to a tool for generating a clamping force and / or a spreading force with a push or pull rod, a stationary jaw, one fixed to the stationary Bakke carrier on which the pull or push rod is movably mounted, and one on the push rod fixed cheek.
  • Such a tool referred to as a quick-release clamp
  • This quick release clamp has a step gear for a gradual displacement of the push or pull rod together with the movable jaw relative to the fixed jaw.
  • the indexing gear is realized in that an actuating arm engages with a catchable on the push or pull rod driver at a certain lever ratio.
  • the driver is displaceable against a return spring. If the operating lever is pivoted, the driver canted on the push rod and pushes the push rod relative to the fixed jaw in a feed direction.
  • a reverse lock prevents the push rod from sliding back. The reverse lock is tilted relative to the push or pull rod that movement of the push or pull rod opposite to the feed direction is avoided.
  • the EP 0 997 233 discloses a clamping tool in which the lever ratios of the actuating arm with increasing clamping force can be changed towards smaller displacement paths by the actuating arm has a trained as a slot bearing opening, which is penetrated by a carrier-fixed bearing pin. With such a clamping tool only minor incremental increases or only slightly higher clamping force increase can be achieved. In addition, a spring preload must be overcome to achieve the smaller lever ratios, so that although the leverage ratios are reduced in favor of a simple operation, which Kraftersparnis is at least partially canceled by the spring preload.
  • a clamping tool according to the preamble of claim 1 is known from US 6,386,530 B1 known.
  • the measure according to the invention makes it possible to provide feed paths for the clamping and / or spreading tool, which are large for a fast closing operation of the clamping jaws and small with respect to the generation of large clamping forces, with equal operating distances to be overcome for both operating situations.
  • a path-lever configuration of large increment with a path-effective lever for example, by the distance of the pivot bearing of the actuating arm of the power transfer to one with the push or Towbar cooperating carrier is determined, and provided a force lever configuration small increment with a force-action lever, which can be determined, for example, in the same way as the travel lever, the corresponding other power transfer is considered.
  • gear ratios of path-effective lever to force-effective lever of greater than or equal to about 1.5, between 1.5 and 2, at greater than or equal to about 2, at greater than or equal to about 2.2, between 2 and 5, greater than 5, between 5 and 5.5 or greater or equal to about 5.5 are generated.
  • the indexing gear can be operated with two alternately active lever configurations, which in particular are mutually exclusive. In a first operating state, therefore, a path lever configuration is effective, and in a subsequent or second operating state, a force lever configuration is effective.
  • Other operating states are not excluded by the invention, especially since in a preferred embodiment of the invention, two different lever configurations are operated simultaneously, with one being designed primarily with respect to the other.
  • the at least two lever configurations are formed by an actuating arm with a permanent pivot bearing point.
  • the two lever configurations are realized by at least two actuating arms, of which at least one, preferably both, have a permanent pivot bearing point.
  • a step transmission which is designed for the stepwise displacement of push or pull rod together with movable jaw relative to the fixed jaw in a feed direction with at least two different pitches and having an actuating arm which is operable with at least two lever configurations.
  • a device is provided for switching from a first lever configuration to a second lever configuration, wherein according to the invention the switching device is designed in such a way that during its activation, in particular in one predeterminable operating state, the switched lever configuration immediately, seamlessly engages. In this way, a gear change of the step transmission according to the invention without embhubbetuschist and without interrupting the feed can be achieved.
  • At least one, preferably exactly one, pivotally mounted actuating arm is provided for the at least two lever configurations, which has two active levers.
  • the two active levers are seamless, directly connectable.
  • the at least two active levers are preferably engageable with at least one, preferably at least two, displaceable against a return spring driver leverage.
  • the means for switching from one lever configuration to another lever configuration without the assistance of the operator is automatically performed at a predetermined tightening or operating force.
  • a viewing window can be provided on the support of the tool, which visualizes the operation of the respective lever configuration to the operator.
  • the switching device is formed by a mechanism for separating a coupling structure, which may be formed according to the above-mentioned coupling component.
  • the mechanism for separating the coupling structure ie the decoupling mechanism, is preferably designed to be arranged between the actuating arm and a driver.
  • the decoupling mechanism or the decoupling device is preferably a load-dependent release device designed, which is designed in particular as a spring-loaded force or locking mechanism.
  • a lever configuration in particular the travel lever configuration, is released in favor of another lever configuration, in particular the force / lever configuration. Since the power lever configuration is always maintained in an activatable position during the operation of the step transmission, the step transmission undergoes no actuation path loss during the switching operation.
  • the decoupling device to a power release threshold when exceeded, the decoupling separates a driver of the actuating arm.
  • the force release threshold is greater than a return spring force acting on the driver. This ensures that not the remindbringtriebkraft a return spring operates releasing or activating the decoupling device.
  • the decoupling device may also be provided with an overload release threshold, which is particularly relevant in power operation and the lever configuration is disabled small step size or turned off, so that damage to the indexer are excluded by excessive applied operating forces by the operator.
  • a Einkupplungs worn is provided for restoring a separate coupling between a driver and the actuating arm.
  • the coupling device should preferably be positioned in such a way that gripping on the clamping or spreading tool is not necessary.
  • the Einkupplungs noticed is actuated via a lock, which is usually provided for preventing a displacement of the push or pull rod against the feed direction after actuation of the actuating arm.
  • a lock which is usually provided for preventing a displacement of the push or pull rod against the feed direction after actuation of the actuating arm.
  • the actuating arm with at least two lever configurations with different active levers can be brought into engagement with the push or pull rod on the at least two different action levers via at least two entrainable against at least one return spring driver.
  • the provision of at least two drivers, each responsible for one stepover, provides separate force engagements on the push or pull rod when using one and the same actuator arm.
  • at least two force transfer points are to be provided on the actuating arm, which determine the corresponding lever configuration of the step transmission.
  • this aspect has the ergonomic advantage of providing a multi-speed stepgear which is operable with only one operating arm, with each step in the passage being able to be adapted precisely to the particular operating needs.
  • a pre-determined force transfer point is accordingly selected on the actuating arm, are formed with the short lever ratios and which is to be connected to one of the drivers.
  • a corresponding force transfer point has to be defined, which forms the desired lever configuration for a large increment and is to be connected to one of the drivers.
  • At least two return springs are provided for the at least two drivers.
  • Each of the return springs causes the one hand, the separate rearward displacement of the driver and thus also the actuating arm.
  • At least one driver in the unactuated operating state of the actuating arm is to be urged into a tilted position on the push or pull rod.
  • a coercive means may be provided in a preferred embodiment of the invention, a return spring. This measure achieves an increase in the displacement which can be displaced by an actuating stroke by more than 15% relative to the indexing mechanism of the known tensioning clamps.
  • a spring force need not be overcome at each actuation stroke to force the driver in the engaging with the push or pull rod Verkant ein. The release of the tilt should rather be function-individualized in an operating state be made when in fact the push or pull rod should be pulled through the support unhindered.
  • a return spring to act on a driver so that the driver is tilted against the push or pull rod, so that the driver in the unactuated operating state of the actuating arm immediately, without delay sliding on the push or pull rod acts when the Actuating arm is actuated.
  • the return spring and the driver are associated with each other such that the driver is kept in constant contact with the actuating arm.
  • the actuating arm has a stop against which the driver can come under the influence of the return spring.
  • the stop is arranged with respect to the force application point of the return spring on the driver so that the driver is communicated to a pivotal force about the stop. It is the pivoting force that holds the driver in the opposite of the push or pull rod tilted position.
  • the return spring has a spring constant, which can always spend the unactuated actuating arm at least supportive in its actuation starting position in the compressed or stretched state.
  • At least one driver preferably at least two drivers, connected to the actuating arm via a coupling member such that the power transfer points on the operating arm and the driver always stationary remain, which are formed during the entire operation substantially constant active lever.
  • the coupling component can be designed to be rigid, for example as a compression rod, or elastically as a spring, in particular as a spiral spring.
  • the coupling member is intended to spend the driver by the coupling in the unactuated operating state of the actuating arm in a relation to the push or Buchstangennormalen inclined position.
  • an elastic, flexible or rigid coupling component is provided for coupling one of the at least two drivers on the actuating arm, which is connected in particular articulated on the actuating arm and on the driver.
  • the coupling member forms a multi-link chain, in particular a two-link chain.
  • the coupling component causes stationary crane transfer points on the actuating arm and the driver.
  • a driver is connected to the actuating arm via the coupling component to form a travel-lever configuration for a distance operation of large step size of the step transmission.
  • Another driver is connected to the actuating arm in a grinding or rolling contact to provide a substantially constant power lever configuration for a small incremental force step action of the stepper.
  • one of the lever configurations in particular for a displacement with a small increment, can be activated continuously, and a further lever configuration, in particular for a displacement with a large increment, can be operated with priority over the activatable lever configuration of small increment.
  • the priority lever configuration actually acts on the push or pull rod and displaces the latter, in particular with a large increment.
  • the lever configuration with a small increment takes up the functional operation of the stepping gear without delay and without transition and is in effective engagement with the push or pull rod.
  • step gears in which clamping forces can be achieved in a range of 600 to 1500 Newton
  • step gears according to the invention six times as high clamping forces can be generated.
  • This increase in power shows its advantage not only quantitatively but also in a wider range of applications, in which clamping forces of 5,000 to 6,000 Newtons are required.
  • a return spring is integrated in the indexing gear, which spends the actuating arm from its Betreliriensend ein back to an exit point after releasing an operating force of the operator. In the starting position, the actuating arm is ready for a complete operating stroke.
  • a further development of the invention relates to a permanent locking of the driver.
  • the disguiseverlantung the driver ensures that an application of force takes place in the push or pull rod immediately upon actuation of the actuating arm.
  • a device for releasing the Treasureverkantung of the driver is provided. This is an off-site displacement of the push or pull rod for opening a clamping zone between the jaws contrary and can be performed without hindrance in the feed direction.
  • the means for releasing the Treasureverkantung is actuated by releasing a lock which prevents the displacement of the push or pull rod against the feed direction of the indexer.
  • a further object of the invention is to overcome the disadvantages of the prior art, in particular to provide a step transmission for a clamping and / or spreading tool, in particular a tension clamp, can be caused with the large clamping forces between the jaws and the under Attention to a favorable force curve should be ergonomically easy to use.
  • a step transmission is provided with an actuating arm, the pivot bearing is positioned on a clamping side of the push or pull rod, ie on the side where the jaws are located. Furthermore, according to the invention, the force transfer point of the actuating arm to be fixed on a displaceable against a return spring driver on the same side as the pivot bearing.
  • the pivot bearing and the intervention. place to each other so that the actuating direction is rectified substantially with the feed direction of the push or pull rod.
  • the force transfer point of the actuating arm is located on the driver between the pivot bearing and the push or pull rod.
  • the pivot bearing is arranged in the course of a longitudinal direction of the push or pull rod substantially at the level of the driver, with which short active lever can be realized, which are required for small feed paths. In addition, this measure achieves that space-consuming actuating force diverting structures can be avoided.
  • the pivot bearing is arranged offset in the unactuated state in the course of a longitudinal direction of the push or pull rod with respect to a perpendicular to the push or pull rod at the height of the driver counter to the feed direction of the indexer.
  • the actuating arm is provided with a permanently stationary pivot bearing point. This power losses are avoided, resulting in displaceable storage points that are known to be used to change leverages.
  • the pivot bearing and the point of engagement of the actuating arm on the driver is arranged substantially on a plane to which the push or pull rod lies as a plane normal.
  • the actuating arm has a first portion with a knuckle and a second portion on which an operator can actuate the actuating arm, wherein an obtuse angle lying between the first and second portion greater than about 135 degrees, preferably about 150 degrees, in particular is essential 180 degrees.
  • the driver is placed in a constantly tilted position with respect to the push or pull rod.
  • a return spring may be provided, which acts on the driver operationally constantly and pushes the driver in the unactuated operating state against a stop which is formed on the actuating arm. About the stop the operating arm is tilted and tilted with respect to the push or pull rod.
  • a device is provided with which the Treasureverkantung the driver can be solved.
  • the device for releasing the tilting can be operated via a non-return lock, which prevents a displacement of the push or pull rod against the feed direction of the indexer.
  • the step mechanism according to the invention can be caused six times of clamping forces between the jaws compared to conventional step gears, a overload protection device is provided in a preferred embodiment, which releases the generated clamping force when exceeding a force triggering threshold and derived from the step gear away.
  • the overload protection device is designed as a decoupling device which separates the connection between the driver and the actuating arm as soon as the force triggering threshold is reached or exceeded.
  • the known step transmission provides a lever configuration in which a step gear ratio of operating lever length can be achieved to an operating lever length of 0.3 maximum, the operating lever, the distance of the pivot bearing of a commonly used by the operator operating range on the actuating arm, maximum by the pivot bearing opposite free end of the actuating arm, is definable.
  • a pivot bearing of the actuating arm is to be arranged on an actuating side of the push or pull rod.
  • the operating side is to be understood as the side of the push or pull rod on which an operator operates the actuating arm in order to be able to pivot the latter, in particular relative to an abutment grip.
  • the actuating arm is to be positioned such that a force application point in the driver on a side opposite the operating side of the push or pull rod, namely on a clamping side, is provided.
  • clamping side is the side of the push or pull rod to understand the jaws of the clamping and / or spreading tool.
  • the indexable gear provides a lever configuration with which substantially larger displacement paths can be realized in the case of an actuating stroke than is possible with the stepwise drives of known clamping and / or spreading tools.
  • the lever configuration created by the stepper provides a much larger effective lever responsible for the large displacement paths.
  • lever length ratios are specified which are intended to indicate the relationship of the active lever length to an actuating lever length, which ratios can be achieved by the measures according to the invention.
  • the operating lever is a size which can be defined from the distance of the pivot bearing from the operating point used by the operator on the actuating arm.
  • the maximum operating lever lengths are given, which are defined by the distance of the pivot bearing from the opposite free end of the actuating arm.
  • the step transmission according to the invention can, in particular with a usual length of the actuating lever of about 5 to 20 cm, a lever length ratio of greater than or equal to about 0.4; greater than or equal to about 0.5; greater than or equal to about 0.6; greater than or equal to 0.7; greater than or equal to about 0.8; greater than or equal to about 0.9 or greater, or equal to about 1.
  • the actuating arm on a first portion which extends substantially perpendicular to the push or pull rod of a force application point at which the actuating arm comes into engagement with the driver.
  • a second section includes at a non-negligible angle of preferably greater than or equal to about 20 degrees, preferably greater than or equal to 30 degrees, preferably not greater than 45 degrees, extending obliquely to the push or pull rod.
  • the first and second portions of the actuator arm partially surround the follower.
  • the second portion of the actuating arm may extend substantially in an axial extension to the first portion.
  • the pivot bearing is arranged offset in relation to a perpendicular to the push or pull rod at the height of the driver counter to the feed direction of the indexer.
  • the actuating arm is connected to the driver via a stationary power transmission locking coupling member.
  • the coupling member ensures a force transfer always at the same point of the driver or actuator arm, so that Wirkhebelverschiebungen are excluded.
  • friction effects are switched off at the contact surfaces, which causes easier operation of the clamping and / or spreading tool.
  • the coupling component also has constructive advantages, because it opens up degrees of freedom in the design of the step transmission.
  • a decoupling mechanism may be provided on the driver and / or on the actuating arm, for example, to release the tilted driver from its forced by the coupling member canting position.
  • the decoupling mechanism may be configured to serve as a protection against overloads applied by the operator. If the actuating arm is subjected to an excessive force, the decoupling device releases the coupling between the driver and the actuating arm.
  • the decoupling device can be designed as a load-dependent release device.
  • the load-dependent release device is realized by a spring-loaded force mechanism.
  • the coupling component is rigid or flexible or elastic, in particular as a rod, preferably as a push rod, or as a spring, preferably as a helical spring.
  • the coupling member is substantially parallel to the push or pull rod.
  • the coupling component is displaced along its axial direction or in the longitudinal direction of the push or pull rod.
  • the coupling member is pivotally connected both with the actuating arm and with the driver. This pivoting movements between the coupling member and the driver and the actuating arm and the coupling member can be realized.
  • a hinge joint mechanism is for connecting the coupling member to the actuator arm and the driver provided.
  • the coupling component forms a multi-link chain, in particular a two-link chain.
  • the coupling member is preferably dimensioned such that the driver is tilted in the unactuated operating state of the actuating arm with respect to the push or pull rod, so that the edges of a trained on the driver passage tilting on the push or Pull rod lie.
  • a return spring acts on the driver so that it can be moved back relative to the push or pull rod when the actuating arm is to be returned from its actuated position to the starting position.
  • the return spring is to be chosen so strong that an independent assumption of the starting position by the actuating arm can be realized.
  • the return spring is interpreted only so strong that the force acting on the load-dependent release device via the driver force does not cause unintentional activation of the decoupling device.
  • a Einkupplungs worn is provided for restoring a separate coupling between the driver and the actuating arm.
  • the Einkupplungs should preferably be positioned so that a gripping the clamping and / or spreading tool is not necessary.
  • the Einkupplungs is actuated via a lock, which is usually provided for preventing a displacement of the push or pull rod against the feed direction after actuation of the actuating arm.
  • a release of the lock and a commissioning of the coupling between driver and actuator arm can be provided simultaneously.
  • a driving slide is provided from a plate with a substantially central passage, which penetrates the push or pull rod in a clearance fit.
  • actuating arm of the driving slide In an unactuated operating state of the actuating arm of the driving slide is biased by a return spring which rests against a support portion, on a flat surface of the actuating arm.
  • the passage edges are not engaged with the push or pull rod in the unactuated operating condition.
  • a coercive means may be provided in a preferred embodiment of the invention, a return spring.
  • the measure according to the invention achieves an increase in the displacement which can be displaced by an actuating stroke by more than 15% compared with the indexing gear of the known clamping clamps.
  • a spring force must not be overcome at each operating stroke to the driver in the with the thrust or Drawbar to bring in engaging tilt position. The release of the tilt should rather be made functionally individualized to an operating state, if in fact the push or pull rod should be pulled through the support unhindered.
  • a device for releasing the permanent tilting of the driver is particularly provided when the driver tilting the positive means is also designed to form clamping forces on the driver ,
  • the coercive means is adjusted so that the driver is informed in the unactuated operating state of the actuating arm acting on the push or pull rod clamping force.
  • the preferably responsible for this return spring is supported on the carrier.
  • the return spring and the driver is arranged to each other such that the driver is kept in constant contact with the actuating arm.
  • the actuating arm has a stop against which the driver can come under the influence of the return spring.
  • the stop is arranged with respect to the force application location of the return spring on the driver such that the driver is communicated to a pivoting force about the stop. It is the pivoting force that holds the driver in the opposite of the push or pull rod tilted position.
  • the driver is connected to the actuating arm via a coupling member such that the power transmission points on the actuating arm and always remain stationary on the driver, which are formed throughout the operation substantially constant active lever.
  • the coupling component may be rigid, for example.
  • a push rod or elastically as a spring, in particular coil spring, be designed.
  • the coupling member is intended to apply the driver by the coupling in the unactuated operating state of the actuating arm tilting on the push or pull rod.
  • this release device is actuated via a lock, which prevents a return displacement of the push or pull rod during operation of the clamping tool against the displacement effect.
  • the release of the lock and the release of the tilt of the driver can be done by simultaneous operation of the lock.
  • the release device is designed as a decoupling device, which comes into play in the alternative embodiment of a coupling component.
  • the decoupling causes the separation of the actuating arm of the driver, so that it no longer remains in its tilting forced position.
  • the decoupling device is a load-dependent release device, in particular a spring-loaded latching mechanism.
  • the release device is equipped with a minimum load threshold, which is set such that the return spring acting on the driver can not activate the release device, so that accidental release or disconnection of the coupling between the driver and the actuating arm is excluded during operation , Furthermore, an overload threshold can be provided, which is set to protect the step gear and the tool before the large operating forces.
  • the invention relates to a tool for generating a clamping and / or spreading force as defined in claim 1.
  • the in the Fig. 1 to 5 illustrated clamp 1 comprises a carrier 3, which has a fixed jaw 5, a housing 7 and a handle 9, and a movably mounted on the carrier 3 push rod 11, at one end a movable jaw 13 fixed, for example by means of rivets or releasably with a snap-action mechanism , is appropriate.
  • the jaws 5 and 13 may be arranged facing each other (clamping tool) or facing away from each other (spreading tool).
  • the jaws 5 and 13 are arranged on a clamping side 15 of a longitudinal axis of the push rod 11.
  • the handle 9 is arranged on an actuating side 17 of the longitudinal axis of the push rod 11.
  • the housing 7 defines a free space 19, which is dimensioned for the at least partial accommodation of organs of a 2-speed step transmission 21 with two different pitches.
  • Fig. 1 the jaws 5 and 13 are shown in an open position to each other, wherein between the jaws 5, 13, a clamping zone 23 is defined. In this clamping zone 23, an object (not shown) can be clamped.
  • the clamping jaw 5 and the housing 7 and the handle 9 are made of one piece, in particular molded from a plastic piece.
  • the push rod 11 and the jaw 13 are defined as movable insofar as they can be moved relative to the carrier 3.
  • the push rod 11 is slidably mounted on the carrier at two radial bearing portions 25, 27 in the axial direction, which can initiate radially acting bearing forces of the push rod 11 in the carrier 3 or of the carrier 3 in the push rod 11.
  • the step gear 21 is designed to shift the movable push rod 11 together with the movable jaw 13 in a feed direction V gradually.
  • the stepper gear 21 according to the invention comprises as drive an actuating arm 31 which is pivotally connected via a pivot bearing 33 on the carrier 3.
  • a portion of the side facing away from the handle 9 of the actuating arm 31 is located on a stop formed by an actuating side portion 35 of the carrier 3.
  • the operating arm 31 has a hand gripper insert 37 formed of a material having a high friction coefficient, such as rubber.
  • a hand gripper insert 37 formed of a material having a high friction coefficient, such as rubber.
  • the step transmission according to the invention has a power take-off slider 39 and a Weg-driving slide 41.
  • Both driving slide (39 or 41) have a passage 43 and 45, whose respective dimension with respect to the constant cross section of the push rod 11 is dimensioned such that the push rod 11 in a vertical position the driving slide (39, 41) is penetrated to the longitudinal axis of the push rod 11 in a clearance fit.
  • a return spring 49 which is located around the push rod 11 as a helical spring and on the one hand on the inside of the push rod bearing 25 is supported and on the other hand biased the way-driving slide 41 against a feed direction V. Also in the in Fig. 1 illustrated actuation-free position of the step gear 21, the return spring 49 biasing acts on the path-driving slider 41 a.
  • a return spring 51 is disposed on the tension side (15), which on the one hand is supported in a blind hole seat introduced in the carrier 3 and, on the other hand, acts on the force take-off slider 39 in a pressure-biased manner.
  • the path-driving slide 41 has on the actuation side (17) an extension, on which a load-dependent decoupling device 53 is housed.
  • the decoupling device 53 serves to allow a scissor-like movement between the actuating arm 31 and the path-driving slider 41 when a predetermined operating force threshold, ie a load threshold acting on the decoupling device 53, is exceeded.
  • the extension of the path-driving slider 41 has a receptacle in which a biasing spring 55 is inserted biased.
  • the Vorspannhaltefeder 55 acts on a ball 57, which in the deactivated state ( Fig. 1 ) of the decoupling device 53 presses on a shell-like end region of a coupling rod 59.
  • the end portion of the coupling rod 59 is provided with a cup-like receptacle in the deactivated state ( Fig. 1 ) of the decoupling device 53 is a pin 61 biasing over the Vorspannhaltefeder 55.
  • the predeterminable load threshold or force release threshold can be predetermined by the spring constant of the Vorspannhaltefeder 55 and the dimensions of the pin 61 and the cup-like end portion of the coupling rod 59.
  • the decoupling device 53 is activated so that a scissor-like movement between the actuating arm 37 and the path-driving slider 41 is possible, will be described in detail later.
  • the coupling rod 59 prevents in the deactivated state ( Fig. 1 ) of the decoupling device 53 relative movement between the path-driving slider 41 and the actuating arm 31. Due to a hinge-like pin-tray arrangement on the one hand and a hinge joint 63 on the other hand, the coupling rod 59 forms a two-hinge joint chain for coupling the actuating arm 31 with the Weg-driving slide, wherein stationary power transmission points (65) are formed.
  • the hinge joint 63 defines a permanent way-active lever w w , which is effective when the decoupling device 53 is deactivated, that is, the actuating arm 31 is coupled to the path-driving slider 41.
  • the length of the action lever w w which is relevant for a long-distance travel operation of the step transmission 21, is determined by the distance of the pivot bearing 33 of the actuating arm 31 and the hinge joint 63.
  • the second operating state ( Fig. 3 and 4 ) of the double-action step drive 21 is defined by a force-effective lever w K whose length is determined by the distance between the pivot bearing 33 to a power transfer point on the actuating arm 31, which force transfer point 65 is formed by a contact pin 65 attached to the actuating arm.
  • An actuating lever b max is the same for both operating states, path operating state and force operating state, wherein for the better understanding of the description of the figures reference is made only to the longest operating lever by appropriate operation, which by the distance of the pivot bearing 33 of the actuating arm 31 for free operation side end 67 of the actuating arm 31 is defined.
  • a lock 71 is provided which prevents displacement of the push rod 11 against the feed direction V.
  • the lock 71 has an actuating portion 73 and a bearing part 75 which is pivotally mounted in a C-shaped recess formed in the carrier 3.
  • a biased locking spring 77 pushes the lock 71 in the in Fig. 1 to 4 illustrated position obliquely to the longitudinal axis of the push rod 11, which penetrates the lock 71 through a passage, not shown, having a clearance fit to the dimension of the push rod 11.
  • an engaging device 81 On the operating side 17 of the push rod 11, an engaging device 81 is provided, which is slidably mounted as an elongated member in a bearing receptacle in the support portion 35, the locking spring 77 forces the elongate member to come into contact with the operating portion 73 of the lock 71.
  • the detailed functional description of the coupling device 81 follows below.
  • the step transmission according to the invention has two passage increments or two different feed paths in a complete actuation stroke of Actuating arm 31.
  • the operation state is explained in which large feed paths are achieved in an operating stroke, which is defined by the angle ⁇ between the handle 9 and the actuating arm 31.
  • the active lever w w is effective. At the jaw 5 no forces occur, whereby the operation of the arm 31 is already possible with a small force, which is not sufficient to activate the decoupler 53, ie push out the pin 61 from the cup-like receptacle of the coupling rod 59 by the Preload holding spring 55 is compressed.
  • the push rod 11 is displaced via the tilted with the push rod 11 way-driving slide 41 in the feed direction V by the step size of the path operation against the return spring 49.
  • the return spring 49 may only be dimensioned so strong that it communicates in any of its compressed positions a force the way-driving slider 41, which is stronger than, a necessary for the activation of the decoupling device 53 triggering force threshold.
  • the lever configuration (active lever w K ) responsible for the power operation of the step transmission 21 also operates during the travel operation, without, however, acting on the push rod 11 in accordance with lever force transfer.
  • the in Fig. 2 shown distance between the power take-off slider 39 and the path-driving slider 41 so does not represent the actual displacement step size of the stepper in the way-operation, because also the force-driving slider 39 by about the product of the active lever w K and the sine of the Angle ⁇ has shifted.
  • the actual step size of the step transmission 21 in the path operation can be approximately determined by the product of the path-effective lever w w and the sine of the angle ⁇ .
  • the push rod 11 is displaced only in small increments in the feed direction V, which can be easier to generate voltage increases between the jaws 5 and 13.
  • the active lever w K of the actuating arm 31 is effective.
  • the decoupling device 53 is shown in its activated state.
  • the pin 61 is pushed out of the cup-like storage, so that the Weg-driving slide 41st of the return spring 49 unhindered against the feed direction V to the power take-off slide 33 can be pushed insofar as the path-driving slider 41 is forced by the rigid coupling means of the coupling rod 59 is no longer in a tilted position.
  • the decoupling device 53 is activated when a force is transmitted to the actuation arm 31 by the operator that is greater than the release force threshold preset by the decoupling device.
  • This operating force is applied according to the operation only when a clamping force between the jaws 5 and 13 is to be generated, namely, when an item to be clamped is to experience clamping forces.
  • This scenario is in Fig. 3 , indicated by the contact of the jaws 5, 13.
  • the actuating arm 31 is always located at the point 65 (force action lever w K ) on the power take-off slider 39 throughout the operation of the step gear, which is effected by the return spring 51.
  • the force-lever configuration becomes effective immediately, and a continuous feed of the push rod 11 without interruption due to the switching operation by the decoupling is achieved by continuing the operation of the operating arm.
  • the lock 71 is to be actuated on its actuation-side section 73 in the feed direction V, so that the actuation section 73 is pivoted on the pivoting part 75 ( Fig. 5 ) and the canting with the push rod 11 is released, which is responsible for maintaining the clamping force between the jaws 5 and 13 due to the closed force curve of a jaw on the lock 71 in the push rod 11 and further into the other jaw 13.
  • the engaging device 81 Upon actuation of the lock 71, the engaging device 81 is operated simultaneously, as in FIG Fig. 5 is indicated. In this case, the elongated component of the Einkupplungs adopted 81 is pressed against the bias of the locking spring 77 in the feed direction V.
  • a driver 85 causes a release of the always tilted force-driving slider 39.
  • the rail can be moved against the feed direction V to separate the jaws 5 and 13 from each other to schedule a new clamping zone 23.
  • the power take-off slider 39 is held in an always tilted position relative to the push rod 11, so that the power operation at any point along the push rod 11 is possible.
  • the tilted position of the follower slide 39 allows that switching from the high stepping gear to the small stepping step of the stepping gear 21 can be realized even during an operating stroke of the actuating arm without Betchanistswegppe.
  • the path driving slider 41 is spent by the coupling member 59 in cooperation with the return spring 49 in an always tilted or tilted position to the push rod 11 when the decoupling device 53 is deactivated.
  • a tool or a step gear shown is illustrated in the configuration of a clamp 101 comprising a support 103 having a fixed jaw 105 and a housing 107, a movable push rod 111 at one end of which a movable jaw 113 is fixedly mounted.
  • the fixed jaw and housing 107 can be made of one piece, in particular be injection molded from a plastic piece.
  • the jaws 105, 113 are located on a clamping side 115 of the push rod 111, wherein the opposite side of the push rod 111 actuating side 117 is called.
  • the housing 107 defines an interior space 119 in which the organs of a two-speed step-action gear 121 are at least partially accommodated, which provides two operating conditions, namely a travel operation, which is characterized by high displacement paths of the push rod. 111, and a power operation formed by small displacement paths for building high clamping forces between the jaws 105 and 113.
  • Fig. 6 the jaws 105 and 113 are shown separated from each other, wherein between the jaws a clamping zone 123 can be defined, in which a contrast to be clamped can be used.
  • the stepper gear 121 with two increments includes a dotted indicated path-actuating arm 125 which is pivotable about a bearing 127.
  • the pivot bearing 127 is arranged on the actuating side 117 on the carrier 103.
  • the Weg-actuating arm 125 has a recessed gripping insert 129 which has a high coefficient of friction.
  • the travel actuating arm 125 has a first section 131 with the gripping insert 129 and a second section 132, which are arranged at an angle of approximately 125 degrees to both sections 131, 132.
  • the travel actuator arm 125 has a fixed permanent lever configuration defined by the active lever w w .
  • the length of the action lever is determined by the distance of the pivot bearing 127 from a force transfer point 128.
  • the step gear 121 comprises a force-actuating arm 137, which is pivotable about a pivot bearing 139, the tension side (115) is arranged on the carrier 103.
  • the force-actuating arm 137 includes a handgrip insert 141 which lies on the side of the force-actuating arm 137 facing away from the travel-actuating arm 125.
  • the clamp 101 can be grasped either by the force-actuating arm 137 or by the travel-actuating arm 125.
  • the force-actuating lever 137 has a first arm portion 143 and a second arm portion 145, which arm portions 143, 145 are at an angle of approximately 160 ° to each other.
  • the lever configuration of the force actuation arm 137 is determined by the force action lever w K whose length is defined by the distance of the pivot bearing 139 of the force-actuating arm 137 to the transfer point 135, which is designed as a force-actuating lever 137 attached to the bolt.
  • the indexer includes a single follower 151 formed by two parallel plates.
  • the driving slider 151 includes a passage (not shown in detail), which can pass through the push rod 111 in a clearance fit. In the actuating arms 125 and 137 come on a tension side (115) with a driving slider 151 into engagement.
  • a return spring 153 which surrounds the push rod 111 as a helical spring, is braced, on the one hand, against the inside of the radial bearing region of the carrier 103 and, on the other hand, biases the drive slide 151 against a feed direction V.
  • Fig. 6 the rest position of the force-actuating arm 137 is shown, in which the force-actuating arm 137 at a stop (not shown in detail) of the housing 107 on the actuating side 117 comes.
  • the force-actuating arm, as well as the power transfer point 135, are not pivoted counter to the feed direction V.
  • the return spring 153 of the driving slide 151 is brought against the feed direction V into abutment with the power transfer point 135 and in a tilted position in which the driving slide 151 is tilted to the push rod 111. In this way, a tilted in the unactuated state of the force-actuating arm 137 position of the driving slider 151 is provided.
  • a lock 155 is pivotally provided which has an actuating portion 157.
  • a pivot portion 159 engages with a recess which is mounted on the tension side of the housing 107, such a way that the lock 155 is held on the housing 107 and pivotable about the pivot portion 159.
  • the lock 155 has a passage which the push rod 111 can penetrate in a clearance fit.
  • a locking spring 161 forces the lock in a tilted always to the push rod 111 position, so that the lock 155 against the push rod 111 tilted, whereby a displacement of the push rod 111 against the feed direction V is prevented.
  • the transmission also has a device 163 for releasing the tilted position, which is arranged on the carrier 107 on the actuation side.
  • the device 163 is formed as an elongated component, which is mounted displaceably on the actuating-side housing section and is biased by the locking spring 161 counter to the feed direction V.
  • FIG. 6 to 8 are shown three operating positions of the path operation of the step transmission, wherein in Fig. 6 an unconfirmed position, in Fig. 7 an intermediate position and in Fig. 8 an operating end position are shown.
  • the clamp 101 is gripped so that the palm rests against the path-actuating arm 125 and at least the middle and / or index finger can grip the force-actuating arm 137.
  • the force actuation arm 137 is pivoted about a first pivot range ⁇ in order to place the force actuation arm in its counter or abutment position, in which the force actuation arm 137 moves with its travel path.
  • Actuating arm 125 facing side abuts the pivot bearing 127 of the Weg-actuating arm 125, which is in Fig. 7 is shown.
  • the driving slide 151 has been displaced in the direction of advance V according to the force lever configuration corresponding to the active lever w K. It should be noted that this displacement width corresponds to the step size of the power operation.
  • the return spring 153 Upon a full actuation stroke of the travel actuating arm 125, the return spring 153 is compressed ( Fig. 8 ). When the operating force is released from the travel operating arm 125 ( Fig. 9 ), so the return spring 153 pushes the driving slide 151 out of its tilted position and moves it back to the force-actuating arm 137, in particular to the power transfer point 135 to. The pushing back of the driving slide 151 is done in constant contact with the power transmission point 128 of the path-actuating arm 125 at the clamping end.
  • the power operation with small step size of the step transmission is in particular on the basis of Fig. 8 to 10 described.
  • the power operation is used in particular when high clamping forces are to be applied to the jaws 105 and 113. This should be in the Fig. 8 to 10 be indicated that the jaws 105, 113 are in direct contact.
  • the travel actuating arm 125 is to be regarded in the force operation of the stepping gear as a counter or abutment arm, against which a pivoting movement of the force-actuating arm 137 is made possible.
  • the force-actuating arm 137 Before the force-actuating stroke is enforceable, the force-actuating arm 137 must be out of his in Fig. 7 shown end position in the in Fig. 6 and 9 be brought home position shown. For this purpose, the force-actuating arm 137 is let go, so that the return spring 153 can cause the necessary pivoting movement about the pivot bearing 139 into the starting position via the driving slide 151 and the force transfer point 135.
  • the force-actuating arm 137 is pivotable until the side of the force-actuating arm 135 facing the travel-actuating arm 125 comes into engagement with the pivot-bearing 127 of the travel-actuating arm, which is shown in FIG Fig. 10 is shown.
  • the force-lever configuration small increments are caused at the same actuating stroke, so that the desired clamping forces on the jaws 105 and 113 can be induced.
  • This process can be repeated by releasing the force actuating arm 137 from the operator's fingers (not shown), whereby the return spring 153 returns the actuating arm to the initial force actuating stroke starting position, which is shown in Figs Fig. 9 is shown.
  • the actuating portion 157 of the lock 155 is to be actuated.
  • the device 163 is simultaneously actuated for releasing the tilting of the driving slide.
  • the elongate member of the device 163 presses on actuation of the lock 155 on the actuation side portion of the driving slide 151, whereby it is pivoted about the power transfer point 135 of the force-actuating arm 137 and thus loses its tilted position to the push rod 111.
  • the push rod 111 together with the movable jaw 113 can be displaced counter to the feed direction V.

Claims (10)

  1. Outil pour produire une force de serrage et/ou d'écartement, en particulier pince de serrage, comprenant :
    une barre de poussée ou de traction (11),
    une mâchoire fixe (5),
    un support (3) relié fixement à la mâchoire fixe (5) sur lequel la barre de poussée ou de traction (11) est disposée mobile,
    une mâchoire mobile (13) disposée fixement sur la barre de poussée ou de traction (11) et
    un engrenage pas-à-pas qui est conçu pour le déplacement pas-à-pas de la barre de poussée ou de traction avec la mâchoire mobile par rapport à la mâchoire fixe dans un sens d'avancée avec deux longueurs de pas de progression différentes, et un bras d'actionnement (31) qui peut être actionné avec deux configurations de levier, sachant qu'un dispositif pour basculer d'une première configuration de levier à une seconde configuration de levier est prévu, sachant qu'à l'activation du dispositif de basculement, la configuration de levier basculée se met en prise directement et sans transition, caractérisé en ce que le dispositif de basculement est ainsi conçu que le basculement de la première configuration de levier à la seconde configuration de levier s'effectue automatiquement à une force de serrage ou d'actionnement prédéterminée.
  2. Outil selon la revendication 1, caractérisé en ce que le dispositif de basculement est formé par un mécanisme de séparation d'une structure de couplage entre le bras d'actionnement (31) et un entraîneur, par lequel le bras d'actionnement (31) peut être mis en prise avec la barre de poussée ou de traction, sachant qu'en particulier le dispositif de découplage est conçu en tant que dispositif de déclenchement en fonction de la charge.
  3. Outil selon la revendication 1 ou 2, caractérisé en ce qu'un dispositif de couplage (81) est prévu pour rétablir un couplage séparé entre l'entraîneur et le bras d'actionnement (31), sachant qu'en particulier le dispositif de couplage (81) peut être actionné par un verrou (71) pour empêcher un déplacement de la barre de poussée ou de traction contre le sens d'avancée V.
  4. Outil selon l'une des revendications 1 à 3, caractérisé en ce qu'une configuration de levier pouvant être activée en permanence, en particulier pour un déplacement avec une progression de pas inférieure est prévue, sachant qu'en particulier, lorsque le dispositif de découplage est désactivé, une configuration de levier prioritaire, en particulier pour un déplacement avec une progression de pas plus importante détermine le fonctionnement de l'engrenage pas-à-pas (21) et en particulier lorsque le mécanisme de découplage (53) est activé, la configuration de levier à progression de pas supérieure est désactivée et la configuration de levier à progression de pas inférieure est activée.
  5. Outil selon l'une des revendications 1 à 4, dans lequel l'engrenage pas-à-pas présente un bras d'actionnement à utiliser dans un sens d'actionnement, qui peut être mis en prise en transmission de force de levier sur la barre de poussée ou de traction par un entraîneur mobile contre un ressort de rappel, caractérisé en ce que le bras d'actionnement est articulé pivotant sur un côté de serrage (15) de la barre de poussée ou de traction et le bras d'actionnement sur le côté de serrage (15) de la barre de poussée ou de traction peut être mis en prise avec l'entraîneur, de sorte que le dispositif d'actionnement est essentiellement orienté dans la même direction que le sens d'avancée de la barre de direction ou de traction.
  6. Outil selon la direction 5, comprenant un dispositif de protection contre les surcharges qui est conçu pour séparer un couplage de l'entraîneur avec le bras d'actionnement à un seuil de déclenchement de force.
  7. Outil selon l'une des revendications 1 à 6, dans lequel l'engrenage pas-à-pas présente un entraîneur par lequel le bras d'actionnement (31) peut être mis en prise en transmission de force de levier avec la barre de poussée ou de traction, sachant que le bras d'actionnement (31) est relié à l'entraîneur par une pièce de couplage assurant une transmission de force fixe, caractérisé par un dispositif de découplage pour séparer le couplage entre l'entraîneur et le bras d'actionnement.
  8. Outil selon la direction 7, caractérisé en ce qu'un dispositif de couplage (81) est prévu pour rétablir un couplage séparé entre l'entraîneur et le bras d'actionnement (31).
  9. Outil selon l'une des revendications 1 à 8, dans lequel l'engrenage pas-à-pas (21) présente un entraîneur par lequel le bras d'actionnement (31) peut être mis en prise avec la barre de poussée ou de traction (11), caractérisé par un moyen de forçage qui maintient l'entraîneur en calage sur la barre de poussée ou de traction (11) au moins dans l'état de service non actionné du bras d'actionnement et en contact permanent avec le bras d'actionnement, et un dispositif (81) pour défaire le calage de l'entraîneur.
  10. Outil selon la revendication 9, caractérisé en ce que le dispositif de séparation (81) peut être actionné par un verrou (71) agissant contre un déplacement de la barre de poussée ou de traction (11) contre le sens d'avancée V.
EP10012910.5A 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement Active EP2359984B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE2003135352 DE10335352B4 (de) 2003-08-01 2003-08-01 Schrittgetriebe mit einem Mitnehmer und Werkzeug
DE2003135351 DE10335351B4 (de) 2003-08-01 2003-08-01 Schrittgetriebe mit einem Mitnehmer und Werkzeug, insbesondere Spannzwinge
DE2003135354 DE10335354B4 (de) 2003-08-01 2003-08-01 Schrittgetriebe
DE2003135353 DE10335353B4 (de) 2003-08-01 2003-08-01 Schrittgetriebe mit großer Schrittweite
DE2003135365 DE10335365A1 (de) 2003-08-01 2003-08-01 Schrittgetriebe mit kleiner Schrittweite
EP04763710A EP1648660B8 (fr) 2003-08-01 2004-08-02 Mecanisme pas a pas pour outil de serrage a barre

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP04763710.3 Division 2004-08-02
EP04763710A Division EP1648660B8 (fr) 2003-08-01 2004-08-02 Mecanisme pas a pas pour outil de serrage a barre

Publications (2)

Publication Number Publication Date
EP2359984A1 EP2359984A1 (fr) 2011-08-24
EP2359984B1 true EP2359984B1 (fr) 2015-07-29

Family

ID=34120060

Family Applications (5)

Application Number Title Priority Date Filing Date
EP10012911.3A Not-in-force EP2338641B1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP10012912A Withdrawn EP2347859A1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP10012913A Withdrawn EP2353785A1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP10012910.5A Active EP2359984B1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP04763710A Not-in-force EP1648660B8 (fr) 2003-08-01 2004-08-02 Mecanisme pas a pas pour outil de serrage a barre

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP10012911.3A Not-in-force EP2338641B1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP10012912A Withdrawn EP2347859A1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement
EP10012913A Withdrawn EP2353785A1 (fr) 2003-08-01 2004-08-02 Mécanisme pas à pas pour un outil de serrage et/ou d'écartement et outil de serrage et/ou d'écartement

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP04763710A Not-in-force EP1648660B8 (fr) 2003-08-01 2004-08-02 Mecanisme pas a pas pour outil de serrage a barre

Country Status (5)

Country Link
US (1) US8016276B2 (fr)
EP (5) EP2338641B1 (fr)
AT (1) ATE483554T1 (fr)
AU (2) AU2004260731A1 (fr)
WO (1) WO2005011918A2 (fr)

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JP2003521387A (ja) 2000-02-02 2003-07-15 ベッセイ ウント ゾーン ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー 締付装置
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Also Published As

Publication number Publication date
EP2338641A1 (fr) 2011-06-29
EP2347859A1 (fr) 2011-07-27
WO2005011918A3 (fr) 2005-05-12
EP1648660A2 (fr) 2006-04-26
EP2353785A1 (fr) 2011-08-10
EP2359984A1 (fr) 2011-08-24
EP2338641B1 (fr) 2015-06-17
AU2004260731A1 (en) 2005-02-10
EP1648660B8 (fr) 2011-09-14
US8016276B2 (en) 2011-09-13
AU2010241391A1 (en) 2011-03-10
WO2005011918A8 (fr) 2011-05-05
ATE483554T1 (de) 2010-10-15
US20080048374A1 (en) 2008-02-28
EP1648660B1 (fr) 2010-10-06
WO2005011918A2 (fr) 2005-02-10

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