EP1648660B8

EP1648660B8 - Incremental gear for bar clamp

Info

Publication number: EP1648660B8
Application number: EP04763710A
Authority: EP
Inventors: Manfred Geier; Ralf Strauss; Phil Reed
Original assignee: Irwin Industrial Tools GmbH
Current assignee: Irwin Industrial Tools GmbH
Priority date: 2003-08-01
Filing date: 2004-08-02
Publication date: 2011-09-14
Anticipated expiration: 2024-08-02
Also published as: US20080048374A1; US8016276B2; EP1648660A2; EP2338641B1; WO2005011918A8; AU2010241391A1; WO2005011918A3; EP2353785A1; EP2359984A1; AU2004260731A1; EP2359984B1; WO2005011918A2; EP2338641A1; EP1648660B1; EP2347859A1; ATE483554T1

Abstract

The stepping drive (21) has an actuator arm (31) and a driver part (41), which are connected via a coupling part for stationary power transmission. This part is rigid or elastic, and is pref. a bar (59), esp. a pressure bar or spring , esp. helical spring. The bar is positioned parallel to a connecting rod (11), and is moved in longitudinal direction of that bar when the actuator arm is operated. The coupling bar is connected articulated to arm and driver part, esp. via a hinge joint mechanism, and esp. forms a two-plate link chain. The stepping drive is part of a clamp clip. This has a connecting rod, a stationary jaw (5) connected to it, and a carrier (3) fastened to the jaw, on which the rod is held moveable, and a moveable jaw (13) fastened to the rod.

Description

Irwin Industrial Tools GmbH

The invention relates to a tool for generating a clamping force and / or a spreading force with a push or pull rod, a fixed jaw, a carrier fixedly connected to the fixed jaw, on which the pull or push rod is movably mounted, and one the pushrod fixed jaw.

Such a tool, called a quick release clamp, is disclosed in DE 39 17 473. This quick release clamp has a step mechanism for a gradual shifting of the push or pull rod including the movable jaw relative to the fixed jaw. The step mechanism is realized in that an actuating arm comes into engagement with a driver that can be tilted on the push or pull rod at a certain lever ratio. The driver can be moved against a return spring. If the operating lever is pivoted, the driver on the push rod tilts and pushes the push rod relative to the fixed jaw in a normal push direction. A push-back lock prevents the push rod from sliding back. The backstop is tilted relative to the push or pull rod in such a way that moving the push or pull rod in the opposite direction to the normal push is avoided. If an object is clamped between the two jaws, a closed force-locking circuit is created from the fixed jaw via the non-return lock into the push rod and the movable jaw. This quick release clamp suffers from the disadvantage that the step size is on the one hand very small, so that the clamping process requires several actuation strokes. On the other hand, high actuation forces have to be applied in order to generate a high clamping force between the jaws.

EP 0 997 233 discloses a tensioning tool in which the lever ratios of the actuating arm can be changed towards smaller ner bearing paths with increasing tensioning force, in that the actuating arm has a bearing opening designed as an elongated hole, which is penetrated by a carrier-fixed bearing journal. With such a clamping tool, only small increments or only insignificant increases higher increase in clamping force can be achieved. In addition, a spring preload must be overcome in order to achieve the smaller lever ratios, so that although the lever ratios are reduced in favor of simple actuation, the energy saving is at least partially offset by the spring preload. When changing the lever ratios towards a shorter active lever, i.e. smaller feed paths, on the one hand you have to work against a position retaining spring that pushes the pivot bearing point towards the lever configuration with large increments, and on the other hand, during this lever configuration change phase, an increase in the clamping forces between the jaws cannot be reached. In this respect, the known step mechanism cannot change the lever configurations without ensuring a continuous increase in the clamping forces on the jaws in the course of the actuating lever path.

It is an object of the invention to overcome the disadvantages of the prior art, in particular to provide a stepper gear for a clamping and / or spreading tool which can realize large and small feed paths, with force and path losses for the lever configuration change taking into account a simple stepping gear structure if possible are to be suppressed.

This object is solved by claims 1 and 5.

With two fixed lever configurations that can be controlled separately and can be switched on directly, loss of power and displacement due to continuous changes in the operating lever and the associated disadvantages are eliminated. In addition, 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 quick closing process of the clamping jaws and small with regard to the generation of large clamping forces, the same actuation paths having to be overcome for both operating situations ,

In a preferred development of the invention, a travel lever configuration with a large step size is provided with a travel action lever which, for example, depends on the distance of the pivot bearing of the actuating arm from the power transmission point to one with the thrust or Drawbar interacting driver is determined, and a power lever configuration is provided with a small step size with a power lever, which can be determined, for example, in the same way as the travel lever, the corresponding other power transmission point is considered. With the stepping gear according to the invention, gear ratios from travel-active lever to power-active lever of greater than or equal to approximately 1.5, between 1.5 and 2, for greater than or equal to approximately 2, for greater than or equal to approximately 2.2, between 2 and 5, greater than 5, between 5 and 5.5 or greater or equal to approximately 5.5 are generated.

In a preferred embodiment of the invention, the stepper transmission can be operated with two alternately active lever configurations, which in particular are mutually exclusive. In a first operating state, therefore, a travel lever configuration acts and in a subsequent or second operating state, a power lever configuration acts. Other operating states are not excluded by the invention, especially since in a preferred embodiment of the invention two different lever configurations are actuated at the same time, one being designed with priority over the other.

In a first alternative embodiment of the invention, the at least two lever configurations are formed by an actuating arm with a permanent pivot bearing point. In a second alternative embodiment of the invention, the two lever configurations are implemented by at least two actuating arms, of which at least one, preferably both, have a permanent pivot bearing point.

An independent aspect of the invention relates to a step mechanism which is designed for step-by-step displacement of the push or pull rod together with the movable jaw relative to the fixed jaw in a feed direction with at least two different step sizes and has at least one actuating arm which can be actuated with at least two lever configurations. According to the invention, a device for switching from a first lever configuration to a second lever configuration is provided, the switching device according to the invention being designed such that when it is activated, in particular in a Predeterminable operating state, the activated lever configuration immediately, seamlessly engages. In this way, a gear change of the stepper transmission according to the invention can be achieved without actuating the intermediate stroke and without interrupting the feed.

In a preferred embodiment of the invention, at least one, preferably exactly one, pivotably mounted actuating arm is provided for the at least two lever configurations and has two active levers. The two active levers are seamless, can be switched on directly. The at least two active levers can preferably be brought into engagement with at least one, preferably at least two, drivers which can be displaced against a return spring in accordance with the lever force.

As explained above, in known step gears with two step sizes, the lever configuration change can only be realized by shifting the pivot bearing arm on the actuating arm. The operator has to put up with a partial actuation stroke without increasing the force on the jaws. This loss of actuation path and loss of force is eliminated by the measure according to the invention.

In a preferred development of the invention, the device for switching from one lever configuration to another lever configuration is carried out automatically with the aid of the operator at a predetermined tensioning or actuating force. In this case, a viewing window can be provided on the tool holder, which visualizes the operation of the respective lever configuration for the operator.

In a preferred further development, the switching device is formed by a mechanism for separating a coupling structure, which can be designed in accordance with the coupling component mentioned above. The mechanism for separating the coupling structure, that is to say 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. direction designed, which is designed in particular as a spring-loaded force or locking mechanism.

In a special embodiment of the invention, when the decoupling device is activated, a lever configuration, in particular the travel lever configuration, is released in favor of another lever configuration, in particular the power lever configuration. Since the power lever configuration is always held in an activatable position during operation of the stepping gear, the stepping gear does not experience any loss of actuation during the switching process.

In a special embodiment of the invention, the decoupling device has a force release threshold, when it is exceeded, the decoupling device separates a driver from the actuating arm. The force release threshold is preferably greater than a return spring force which acts on the driver. This ensures that the return drive force of a return spring does not operate the release or activation of the decoupling device. The decoupling device can also be provided with an overload release threshold, which is particularly relevant in power mode and, when exceeded, the lever configuration is deactivated or switched off in small increments, so that damage to the stepper gearbox due to excessive actuating forces applied by the operator is excluded.

In a preferred development of the invention, a coupling device is provided for restoring a separate coupling between a driver and the actuating arm. The coupling device should preferably be positioned such that it is not necessary to reach around on the clamping or spreading tool. The coupling device can preferably be actuated via a lock, which is usually provided to prevent displacement of the push rod or pull rod against the feed direction after actuation of the actuating arm. This means that both the release of the lock and the start-up of the coupling between the driver and the actuating arm can be provided simultaneously, ie with one hand. The actuating arm with at least two lever configurations with different operating levers can be brought into engagement with the push or pull rod on the at least two different operating levers via at least two drivers that can be displaced against at least one return spring. The provision of at least two drivers, each of which is responsible for one increment, provides separate force interventions on the push or pull rod when using one and the same actuating arm. In order to implement different lever configurations, at least two force transmission points must be provided on the actuating arm, which determine the corresponding lever configuration of the stepping gear. This aspect has in particular the ergonomic advantage that a multi-speed step transmission is provided which can only be operated with an actuating arm, each step size in the gear can be adapted exactly to the respective operating requirements. For a specific power operation in which high clamping forces are to be generated on the jaws, a force transmission point to be determined in advance on the actuating arm is selected accordingly, with which short lever ratios are formed and which is to be connected to one of the drivers. A corresponding power transmission point must be defined for the travel mode, which forms the desired lever configuration for a large increment and is to be connected to one of the drivers.

In the preferred embodiment of the invention, at least two return springs are provided for the at least two drivers. On the one hand, each of the return springs causes the drivers and thus also the actuating arm to be moved back separately.

In a preferred development of the invention, at least one driver in the unactuated operating state of the actuating arm is to be forced into a position tilted on the push or pull rod. In a preferred embodiment of the invention, a return spring can be provided as such a means of restraint. The measure according to the invention achieves an increase in the step width displaceable by an actuation stroke by more than 15% compared to the step mechanism of the known clamping clamps. In addition, a spring force does not have to be overcome with each actuation stroke in order to force the driver into the tilting position engaging with the push or pull rod. Rather, the release of the cant should be functionally individualized in an operating state be carried out when the push or pull rod is actually to be pulled through the carrier unhindered.

In a preferred embodiment of the invention, a return spring is to act on a driver in such a way that the driver is canting against the push or pull rod, so that the driver in the unactuated operating state of the actuating arm acts immediately, without delay, on the push or pull rod when the Actuating arm is operated.

In a preferred embodiment of the invention, the return spring and the driver are assigned to one another in such a way that the driver is kept in constant contact with the actuating arm. This measure opens up the possibility of multi-speed step transmissions, in particular of multi-speed step transmissions, which make a gear change seamless, i. H. without intermediate stroke and interruption of feed, d. H. without the actuating arm experiencing a partial actuation stroke without increasing the force on the jaws.

In a preferred further development of the invention, the actuating arm has a stop against which the driver can hit under the influence of the return spring. The stop is arranged on the driver with respect to the location of the force of the return spring in such a way that the driver is informed of a pivoting force about the stop. It is the pivoting force that holds the driver in the position tilted in relation to the push or pull rod.

In a preferred embodiment of the invention, the return spring has a spring constant which, in the compressed or stretched state, can always at least support the unactuated actuating arm in its actuating starting position.

In a further development of the invention, at least one driver, preferably at least two drivers, is connected to the actuating arm via a coupling component such that the force transmission points on the actuating arm and on the driver are always stationary remain, whereby essentially constant operating levers are formed during the entire operation. The coupling component can be rigid, for example as a compression rod, or elastic as a spring, in particular as a spiral spring. The coupling component is preferably intended to bring the driver into an inclined position relative to the push or pull rod normal even when the actuating arm is in the unactuated operating state.

In a preferred development of the invention, an elastic, flexible or rigid coupling component is provided for coupling one of the at least two drivers to the actuating arm, said coupling component being articulated in particular on the actuating arm and also on the driver. The coupling component preferably forms a multi-link chain, in particular a two-link chain. The coupling component effects fixed power transmission points on the actuating arm and on the driver.

In a preferred development of the invention, a driver is connected to the actuating arm via the coupling component to form a travel lever configuration for a travel operation of large increments of the stepping gear. Another driver is connected to the actuating arm in a sliding or rolling contact to form a substantially constant power lever configuration for a power step operation of small increments of the step gear.

In a preferred embodiment of the invention, one of the lever configurations, in particular for a shift with a small increment, can be continuously activated, and a further lever configuration, in particular for a shift with a large increment, can be operated with priority over the activatable lever configuration with a small increment. When the decoupling device is deactivated, the primary lever configuration actually acts on the push rod or pull rod and shifts the latter in particular with a large increment. When the decoupling device is activated, the lever configuration with a small increment takes over the functional operation of the stepper transmission without delay and without interruption and is effectively engaged with the push or pull rod. Another independent aspect of the invention relates to a stepping gear for the gradual shifting of the push or pull rod in a feed direction with two separately operable operating arms. The at least two actuating arms bring about a displacement of the push rod or pull rod in the same feed direction. With this independent measure according to the invention of two actuating arms for the same feed direction, a multi-step gear, preferably a two-step gear, can be formed in a simple manner.

In contrast to the conventional stepper gears, in which clamping forces in a range from 600 to 1,500 Newtons can be achieved, six times as high clamping forces can be generated with the stepper gears according to the invention. This increase in force 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.

In a preferred development of the invention, the at least two lever configurations are formed by two actuating arms pivotably articulated on the carrier, each of which has its own operating lever, which can be brought into engagement with the push or pull rod in accordance with the lever force via a driver that can be displaced via a return spring. In particular, the individual operating lever of the respective actuating arm is essentially constant during operation.

In a preferred development of the invention, the at least two actuating arms are articulated to the carrier in the manner of a pair of scissors so that separate pivot bearings are provided in particular for the actuating arms at different locations on the carrier.

In a development of the invention, two actuating arms are pivotably articulated on the carrier and have opposite actuation directions. The at least two actuating arms can preferably be articulated in a scissor arrangement on the carrier. In a further development of the invention, the at least two actuating arms each have a pivot bearing which is arranged at different points on the carrier. A pivot bearing is preferably positioned on one side of the push or pull rod, in particular on the actuation side, and at least one pivot bearing is positioned on the opposite side, preferably the tensioning side, of the push or pull rod.

In a development of the invention, a travel actuating arm with a large step size is provided, which is articulated on an actuating side of the push or pull rod by means of a driver that can be displaced against a return spring, and whose travel active lever is articulated on a tensioning side of the push rod. or pull rod attacks on the driver.

In a further development of the invention, a displacement actuating arm for a large step size and a force actuating arm for a small step size are provided. The displacement actuating arm preferably has a first section which extends substantially perpendicular to the push or pull rod in the region of the point of engagement with the driver and a second section, the first and second section partially surrounding the driver. Alternatively, the second section of the actuating arm can extend substantially in an axial extension to the first section.

In a further development of the invention, in the unactuated operating state of the travel actuating arm, its pivot bearing is offset against the feed direction with respect to a perpendicular to the push or pull rod at the level of the driver. With this positional condition of the swivel bearing, very good lever configurations can be achieved for a stepping gear ratio with large displacement paths.

In a preferred development of the invention, a force actuating arm with a small step size is pivotably articulated on an actuating side of the push or pull rod, the force actuating arm being engageable with a driver on the actuating side of the push or pull rod, via the at least two actuating arms can cooperate operationally with the push or pull rod. In a preferred embodiment of the invention, a displacement actuating arm with a large step size and a force actuating arm with a small step size are coordinated with one another such that when the one actuating arm is actuated, the other actuating arm acts as a support or abutment arm.

In a preferred embodiment of the invention, a return spring is integrated in the stepping gear, which, after releasing an operating force of the operator, brings the at least two operating arms back out of their operating end position into a starting point. In the starting position, the at least two actuating arms are ready for a complete actuation stroke.

A further development of the invention relates to permanent canting of the driver. In order to avoid loss of path in the actuating stroke of the actuating arm, the permanent canting of the driver ensures that an input of force into the push or pull rod takes place immediately when the actuating arm is actuated.

In a preferred development of the invention, a device is provided for releasing the permanent canting of the driver. This is intended to enable the push rod or pull rod to be moved outside of the company in order to open a clamping zone between the jaws and in the direction of advance without obstruction. The device for releasing the permanent canting is preferably actuated by releasing a lock which prevents the push or pull rod from being displaced counter to the direction of advance of the stepping gear.

In a preferred development of the invention, in a one-way operation of the stepping mechanism, a way actuating arm can be pivoted in large increments using a force actuating arm which is determined against the direction of actuation of the way actuating arm as an abutment, and the push or pull rod can be displaced in large increments. In a power operation, a power actuating arm can be pivoted as a counter arm using the travel actuating arm, which is determined in particular because of the lever ratios against the actuating direction of the power actuating arm, as a result of which the pushing or Pull rod in small increments for applying clamping and / or spreading forces is displaceable.

In the known clamping tool according to EP 0 997 233, it is disadvantageous that the actuation direction does not correspond to the direction of advance of the push or pull rod including the movable jaw, which often leads to incorrect positioning of the clamping tool by an inexperienced operator. Furthermore, the lever configuration for a small step size, that is to say for high clamping forces on the jaws, has an unfavorable force profile from the actuating lever via the pivot bearing region into the active lever. The actuating force must be redirected to the active lever in the area of a kink at the pivot bearing point, as a result of which the structure is particularly susceptible to fatigue at the pivot bearing. In addition, with a power lever configuration with a small step size, only slightly larger clamping forces can be generated, which is due to the small shortening of the lever arm and the compression spring on the elongated hole.

Proceeding from this, it is a further object of the invention to overcome the disadvantages of the prior art, in particular to provide a stepping gear for a clamping and / or spreading tool, in particular a clamping clamp, with which large clamping forces can be produced between the jaws and under Consideration of a favorable force curve should be easy to use ergonomically.

This object is solved by the features of claim 9.

Thereafter, a stepper gear is provided with an actuating arm, the pivot bearing of which is positioned on a clamping side of the push or pull rod, that is to say on the side where the clamping jaws are located. Furthermore, according to the invention, the force transmission point of the actuating arm is to be fixed on a driver that can be displaced against a return spring on the same side as the pivot bearing. The pivot bearing and the point of engagement should lie in such a way that the direction of actuation is essentially the same as the feed direction of the push or pull rod. With the measure according to the invention, the smallest feed paths can be determined in a simple constructive manner. with which very high clamping forces can be applied with the same actuation paths.

In contrast to the conventional step mechanisms, in which clamping forces in a range from 600 to 1,500 Newtons can be achieved, six times as high clamping forces can be generated with the step mechanism according to the invention. This increase in force shows its advantage not only quantitatively but also in the fact that such clamping tools are now accessible to a larger area of application by requiring clamping forces of 5,000 to 6,000 Newtons.

In a preferred development of the invention, the force transmission point of the actuating arm lies on the driver between the pivot bearing and the push or pull rod. In this way, a favorable force profile can be created from the actuation intervention by the operator to the intervention site. The pivot bearing is preferably arranged substantially at the level of the driver in the course of a longitudinal direction of the push or pull rod, with which short effective levers which are required for small feed paths can be realized. In addition, this measure ensures that space-consuming actuating force redirection structures can be avoided.

In a further preferred embodiment of the invention, the pivot bearing in the unactuated state is offset 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 level of the driver against the feed direction of the stepping gear.

In a preferred further development of the invention, the actuating arm is provided with a permanently fixed pivot bearing point. In this way, power losses are avoided which result from displaceable mounting points which are known to be used for changing lever ratios. In a preferred embodiment of the invention, the swivel bearing and the point of engagement of the actuating arm on the driver are arranged essentially on a plane to which the push or pull rod lies as a plane normal.

The actuating arm preferably has a first section with an active lever and a second section, on which an operator can actuate the actuating arm, an obtuse angle lying between the first and second section being greater than approximately 135 degrees, preferably approximately 150 degrees, in particular in is essentially 180 degrees.

In order to enable the actuating arm to be brought back into the starting point at the end of an actuating stroke, a return spring is provided in a further development according to the invention.

In a further preferred embodiment, the driver is brought into a constantly tilted position with respect to the push or pull rod. For this purpose, a return spring can preferably be provided, which acts continuously on the driver during operation and presses the driver against a stop, which is formed on the actuating arm, even in the unactuated operating state. The actuating arm is tilted and tilted relative to the push or pull rod via the stop.

In a preferred development of the invention, a device is provided with which the permanent canting of the driver can be solved. Thus, a displacement of the push rod or pull rod should also be possible against the feed direction in the unactuated state of the actuating arm. Preferably, the device for releasing the canting can be operated by means of a non-return lock which prevents the push or pull rod from being displaced counter to the direction of advance of the stepping gear.

In a special development of the invention, the actuating arm with a small step size is to serve as a counter arm for a second actuating arm, in particular with a large step size, in a certain operating position. When the actuating arm is released, small further it is the return spring that pushes the actuating arm back into its starting position.

In order for the stepping gear according to the invention to be able to generate six times the clamping forces between the jaws compared to conventional stepping gears, an overload protection device is provided in a preferred embodiment, which releases the generated clamping force when a force release threshold is exceeded and derives it from the stepping gear. The overload protection device is preferably designed as a decoupling device which disconnects the connection between the driver and the actuating arm as soon as the force release threshold is reached or exceeded.

In the known, proven clamping tool according to DE 39 17 473, it is disadvantageous that with fully open jaws and small objects to be clamped in, several actuation strokes must be carried out on the actuating arm in order to enable the object to be gripped with the jaws.

The known stepping gear provides a lever configuration in which a stepping gear ratio of active lever length to an actuating lever length of at most 0.3 can be achieved, the actuating lever being the distance of the pivot bearing from an actuation area on the actuating arm that is usually used by the operator, at most by means of the pivot bearing opposite free end of the actuating arm, is definable.

It is a further object of the invention to provide a stepping gear for a clamping and / or spreading tool, in particular a clamp, with which large feed paths of the push or pull rod can be realized with an actuating stroke of the actuating arm while maintaining a small actuating space requirement.

This object is solved by the features of claim 11. A swivel bearing of the actuating arm is then to be arranged on an actuating side of the push or pull rod. The actuating 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 handle. Furthermore, the actuating arm is to be positioned according to the invention in such a way that a force entry point in the driver is to be provided on a side of the push or pull rod opposite to the actuating side, namely on a tensioning side. The clamping side is to be understood as the side of the push or pull rod on which the jaws of the clamping and / or spreading tool lie. The stepper transmission according to the invention provides a lever configuration with which much larger displacement paths can be realized with an actuation stroke than is possible with the stepper drives of known clamping and / or expanding tools. The lever configuration created by the stepper transmission according to the invention provides a much larger active lever, which is responsible for the large displacement paths. Thus, with a clamping and / or spreading tool provided with the stepping gear according to the invention, even small objects to be clamped in with widely spaced clamping jaws can preferably be gripped with only one actuation stroke or at least far fewer actuation strokes than can be realized with the stepping drives of the known clamping and / or spreading tools is.

In a further development of the invention, specific 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 actuation lever is a quantity that can be defined from the distance of the pivot bearing from the actuation point on the actuation arm used by the operator. The maximum operating lever lengths are specified below, which are defined from the distance of the pivot bearing from the opposite free end of the operating arm. The step mechanism according to the invention can, in particular with a usual length of the actuating lever of approximately 5 to 20 cm, a lever length ratio of greater than or equal to approximately 0.4; greater than or equal to approximately 0.5; greater than or equal to approximately 0.6; greater than or equal to 0.7; greater than or equal to approximately 0.8; be greater than or equal to approximately 0.9 or greater than or equal to approximately 1. In a further development of the invention, the actuating arm has a first section which extends essentially perpendicular to the push or pull rod from a force input point at which the actuating arm comes into engagement with the driver. A second section adjoins the first section at a non-negligible angle of preferably greater than or equal to approximately 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 the second section of the actuating arm preferably partially surround the driver.

Alternatively, the second section of the actuating arm can extend substantially axially to the first section.

In a further preferred embodiment of the invention, the pivot bearing is arranged offset with respect to a perpendicular to the push or pull rod at the level of the driver against the direction of advance of the stepping gear. With this positional condition of the pivot bearing, very good lever configurations can be achieved for a stepper gear ratio with large displacement paths.

In a further preferred measure for providing favorable lever configurations for a stepping gear ratio with large displacement paths, the pivot bearing and the force input point are to be arranged in a plane which penetrates the push or pull rod as a plane normal.

It is a further object of the invention to provide an improved stepper gear for a tensioning and / or spreading tool, in particular a clamping clamp, with which a drive or actuation force can be transmitted to the push or pull rod with the greatest possible optimization and without loss of force or loss of travel Actuation path-feed path ratio is guaranteed.

This object is solved by the features of claim 12. The actuating arm is then connected to the driver via a coupling component which secures a fixed power transmission. The coupling component always ensures a power transmission at the same point on the driver or actuating arm, so that active lever displacements are excluded. In addition, friction effects on the contact surfaces are switched off, which makes the clamping and / or spreading tool easier to operate. The coupling component also has structural advantages because it opens up degrees of freedom in the design of the stepping gear.

In the invention, a decoupling mechanism is provided on the driver and / or on the actuating arm, for example in order to release the tilted driver from its tilted position forced by the coupling component.

Furthermore, the decoupling mechanism can be designed to serve as a protective device against overloads applied by the operator. If too much force is applied to the actuating arm, the decoupling device releases the coupling between the driver and the actuating arm. For this purpose, the decoupling device can be designed as a load-dependent release device. The load-dependent release device is preferably implemented by a spring-loaded force mechanism.

In a preferred development of the invention, the coupling component is rigid or flexible or elastic, in particular as a rod, preferably as a compression rod, or as a spring, preferably as a helical spring. The coupling component is preferably essentially parallel to the push or pull rod. In particular, in the course of the actuation of the actuating arm, the coupling component is displaced along its axial direction or in the longitudinal direction of the push or pull rod.

In a preferred development of the invention, the coupling component is connected in an articulated manner both to the actuating arm and to the driver. Pivotal movements between the coupling component and the driver and the actuating arm and the coupling component can thus be realized. In a preferred embodiment, a hinge joint mechanism for connecting the coupling component to the loading low in activity and provided for the driver. In a preferred development of the invention, the coupling component forms a multi-link chain, in particular a two-link chain.

In order to avoid loss paths when actuating the actuating arm, the coupling component according to the invention is preferably dimensioned such that the driver is tilted with respect to the push rod or pull rod even when the actuating arm is not actuated, so that the edges of a passage formed on the driver canting on the push rod. or pull rod.

In a preferred further development of the invention, a return spring acts on the driver in such a way 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 selected so strongly that an independent assumption of the starting position by the actuating arm can be realized. However, the return spring should only be designed so strong that the force acting on the driver on the load-dependent release device does not cause the decoupling device to be activated unintentionally.

In a preferred development of the invention, a coupling device is provided for restoring a separate coupling between the driver and the actuating arm. The coupling device should preferably be positioned in such a way that it is not necessary to reach around the clamping and / or spreading tool. The coupling device can preferably be actuated via a lock, which is usually provided to prevent displacement of the push rod or pull rod against the feed direction after actuation of the actuating arm. This enables the lock to be released and the coupling between the driver and the actuating arm to be started up at the same time.

In the known, proven stepper transmission according to DE 39 174 473, a driving slide from a plate with an essentially central passage is provided, which the push or pull rod penetrates in a clearance fit. In an unactuated operating state of the actuating arm, the driving slide is biased by a return spring, which is supported against a carrier section, against a flat surface of the actuating arm. The passage edges are not in engagement with the push or pull rod in the unactuated operating state. With a first actuation of the handle (first actuation phase), the driving slide is tilted towards the push rod or pull rod to make it ready for operation and tilted with the latter, so that during a second actuation phase, with the formation of clamping forces, the push rod or pull rod is displaced in the feed direction against the return spring can. When the actuating arm is released, the tensioned return spring releases the cant. A disadvantage of the stepper gearbox is that part of the actuation path, namely the first actuation phase for moving the driving slide into the tilted engagement position, is lost for the advance of the push or pull rod. In addition to the loss of the actuation path, a part of the actuation force for the deformation of the return spring for tilting the driving slide on the push or pull rod must also be used to overcome the unused actuation path.

It is a further object of the invention to overcome the disadvantages of the prior art, in particular to provide an improved stepping gear of the type specified above for a tensioning and / or expanding tool, in particular a clamp, in which the available drive or actuation paths are optimally used and the drive or actuation force applied by the operator is to be implemented with a high degree of efficiency.

This object is solved by claim 14. Afterwards, the driver should be pushed into a position jammed on the push or pull rod in the unactuated operating state. In a preferred embodiment of the invention, a return spring can be provided as such a means of restraint. The measure according to the invention achieves an increase in the step width displaceable by an actuation stroke by more than 15% compared to the step mechanism of the known clamping clamps. In addition, a spring force does not have to be overcome with each actuation stroke in order to move the driver into the or to bring the tie rod into the canting position. Rather, the tilting should be carried out in a function-customized manner for an operating state if the push or pull rod is actually to be pulled through the carrier unimpeded.

In order to also be able to move the push or pull rod in an unactuated operating state of the clamping tool against the feed direction, a device for releasing the permanent canting of the driver is provided in particular if the constraining means tilting the driver is also designed to form clamping forces on the driver ,

In a preferred embodiment of the invention, the constraining means is set such that the driver is informed of a clamping force acting on the push or pull rod in the unactuated operating state of the actuating arm. The return spring, which is preferably responsible for this, is supported on the carrier.

In a preferred embodiment of the invention, the return spring and the driver are arranged relative to one another in such a way that the driver is kept in constant contact with the actuating arm. This measure opens up the possibility of multi-speed step transmissions, in particular multi-speed step transmissions, which make a gear change seamless, i.e. can realize without intermediate stroke and interruption of the feed.

In a preferred embodiment of the invention, the driver is connected to the actuating arm via a coupling component such that the force transmission points on the actuator low supply and always remain stationary on the driver, whereby essentially constant operating levers are formed throughout the operation. The coupling component can be designed rigidly, for example as a compression rod, or elastically as a spring, in particular a spiral spring. The coupling component is preferably intended for canting the driver by the coupling in the unactuated operating state of the actuating arm on the push or pull rod.

In a preferred embodiment of the invention, this release device can be actuated via a lock, which prevents the push or pull rod from being moved back during the operation of the clamping tool against the displacement effect. The release of the lock and the release of the canting of the driver can preferably be done by simultaneously actuating the lock. For this purpose, a structural coupling of the lock with the driver must be provided.

In a further preferred embodiment of the invention, the release device is designed as a decoupling device, which is used in the alternative embodiment of a coupling component. The decoupling device causes the actuating arm to be separated from the driver so that the latter no longer remains in its tilted forced position. The decoupling device is preferably a load-dependent release device, in particular a spring-loaded latching mechanism.

In a preferred further development of the invention, the release device is equipped with a minimum load threshold, which is set such that the return spring acting on the driver cannot activate the release device, so that an unwanted release or disconnection of the coupling between driver and actuating arm is excluded during operation , Furthermore, an overload threshold can be provided, which is set to protect the stepping gear and the tool from excessive actuation forces.

The invention relates to a tool for generating a clamping and / or spreading force, in particular a clamp, with a push or pull rod, a fixed jaw, one with the fixed jaw firmly connected carrier on which the push or pull rod is movably mounted, a movable jaw fixed to the push or pull rod and a step mechanism according to the invention.

For example, a stepper transmission can be designed with at least two drivers and a switching device, or a stepper transmission can have a two-actuating arm arrangement and a device for switching from one lever configuration to another lever configuration.

Further advantages, features and properties of the invention will become clear from the following description of two preferred embodiments of the invention with reference to the accompanying drawings, in which:

Figure 1 is a side view of a tool in the configuration as a clamp with a 2-speed step gear, which is shown in a rest position.

FIG. 2 shows a side view of the tool according to FIG. 1, the end of an actuation stroke of the travel gear being shown in large increments;

FIG. 3 shows a side view of the tool according to FIG. 1, the power transmission gear having a small increment being activated;

FIG. 4 shows a side view of the tool according to FIG. 1, in which the stroke end of the power transmission gear is shown;

FIG. 5 shows a side view of the tool according to FIG. 1, in which the travel gear is restored;

FIG. 6 is a schematic, but realistic, lever view showing a side view of a tool in the configuration of a clamp, in which a 2-speed step transmission is in a rest position; FIG. FIG. 7 shows a side view of the tool according to FIG. 6, in which a power actuating arm is brought into an abutment position;

FIG. 8 shows a side view of the tool according to the invention according to FIG. 6, in which a dotted control arm is shown in an actuated operating state;

FIG. 9 shows a side view of the tool according to the invention according to FIG. 6, in which a frictional connection between the fixed and the movable jaw is shown;

FIG. 10 shows a side view of the tool according to the invention according to FIG. 6, in which the power actuating arm is shown in an actuated operating state; and

11 is a side view of the tool according to the invention according to FIG. 6, in which the clamping of the jaws is released by actuating a release lever.

1 to 5 comprises a carrier 3, which has a fixed jaw 5, a housing 7 and a handle 9, and a push rod 11 movably mounted on the carrier 3, at one end of which a movable jaw 13 is fixed for example by means of

Rivets or detachable with a quick locking mechanism, is attached. The jaws 5 and 13 can be arranged facing one another (clamping tool) or pointing away from one another (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 delimits a free space 19 which is dimensioned for at least partially accommodating organs of a 2-speed step transmission 21 with two different step sizes. In Fig. 1 the jaws 5 and 13 are shown in an open position to each other, wherein a clamping zone 23 is defined between the jaws 5, 13. An object (not shown) can be clamped in this clamping zone 23.

For easy manufacture of the clamping clamp, the clamping jaw 5 and the housing 7 and the handle 9 are made from one piece, in particular injection molded from a plastic piece.

The push rod 11 and the jaw 13 are defined as movable in that they can be moved relative to the carrier 3. The push rod 11 is mounted on the support on two radial bearing areas 25, 27 so as to be axially displaceable, which can introduce radially acting bearing forces from the push rod 11 into the support 3 or from the support 3 into the push rod 11.

The step mechanism 21 is designed to gradually move the movable push rod 11 together with the movable jaw 13 in a feed direction V. The stepping gear 21 according to the invention comprises, as a drive, an actuating arm 31 which is pivotably articulated on the carrier 3 via a pivot bearing 33.

In an unactuated state of the actuating arm 31 (FIG. 1), a portion of the side of the actuating arm 31 facing away from the handle 9 bears against a stop formed by an actuating side section 35 of the carrier 3.

The operating arm 31 has a hand grip insert 37 which is made of a material with a high coefficient of friction, such as rubber. When the clamping clamp 1 is operated, an operator (not shown) grips the handle 9 in such a way that the insert 37 is gripped by at least the middle and / or index finger while the palm of the counter is nestled around the handle 9.

The step transmission according to the invention has a force-driving slide 39 and a displacement-driving slide 41. Both driving slides (39 and 41) have a passage 43 and 45, the respective dimensions of which are dimensioned with respect to the constant cross-section of the push rod 11 such that the push rod 11 in a vertical position the driving slide (39, 41) is pushed through to the longitudinal axis of the push rod 11 in a clearance fit.

A return spring 49 acts against the travel driving slide 41, which is located as a helical spring around the push rod 11 and is supported on the one hand on the inside of the push rod bearing 25 and on the other hand preloads the travel driving slide 41 against a feed direction V. Even in the actuation-free position of the step mechanism 21 shown in FIG. 1, the return spring 49 acts in a prestressing manner on the travel slider 41.

In a substantially parallel orientation to the return spring 49, a return spring 51 is arranged on the tensioning side (15), which is supported on the one hand in a blind hole seat inserted in the carrier 3 and on the other hand acts on the force-taking slide 39 in a prestressed manner.

In the unactuated operating state of the step mechanism 21 shown in FIG. 1, the return spring 51 presses against a tension-side (15) section of the force-driving slide 39. The force-driving slide 39 is formed by two plates of the same dimension; a plate engages the return spring 51; the other plate cooperates with the operating arm 31 operationally, which is explained in detail below.

The travel slider 41 has an extension on the actuating side (17) on which a load-dependent decoupling device 53 is accommodated. The decoupling device 53 serves to permit a scissor-like movement between the actuating arm 31 and the displacement slider 41 when a predetermined actuation force threshold, that is to say a load threshold acting on the decoupling device 53, is exceeded. The extension of the travel slider 41 has a receptacle in which a preload holding spring 55 is inserted in a prestressed manner. The preload holding spring 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 region of the coupling rod 59 is provided with a shell-like receptacle, in which the deactivated stood (Fig. 1) of the decoupling device 53 is a pin 61 biasing over the biasing spring 55. The predeterminable load threshold or force release threshold can be predetermined by the spring constant of the preload holding spring 55 and the dimensions of the pin 61 and the shell-like end region of the coupling rod 59. The operating state of the step mechanism 21, the decoupling device 53 is activated so that a scissor-like movement between the actuating arm 37 and the travel slider 41 is possible, will be described in detail later.

In the deactivated state (FIG. 1) of the decoupling device 53, the coupling rod 59 prevents a relative movement between the travel slider 41 and the actuating arm 31. Due to a hinge-like pin-shell 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 to the displacement slider, whereby stationary power transmission points (65) are formed.

The hinge joint 63 defines a permanent travel-active lever ww, which is effective when the decoupling device 53 is deactivated, i. H. the actuating arm 31 is coupled to the travel slider 41. The length of the active lever w, which is relevant for a step-by-step operation of the step mechanism 21, is determined from the distance between the pivot bearing 33 of the actuating arm 31 and the hinge joint 63.

The second operating state (FIGS. 3 and 4) of the two-speed step mechanism 21 is defined by a force-action lever W _K , the length of which is determined by the distance of the pivot bearing 33 from a force transmission point on the actuating arm 31, which force transmission point 65 is determined by a system bolt attached to the actuation arm 65 is formed.

An operating lever b _max is the same for both operating states, distance operating state and force operating state, whereby for a better understanding of the description of the figures, reference is only made to the longest operating lever by corresponding operation, which is due to the distance of the pivot bearing 33 of the operating arm 31 to free actuation-side end 67 of the actuating arm 31 is defined. On the side of the housing 7 facing the clamping zone 23, a lock 71 is provided, which prevents the push rod 11 from moving against the feed direction V. The lock 71 has an actuating section 73 and a bearing part 75 which is pivotably mounted in a C-shaped recess formed in the carrier 3. A prestressed locking spring 77 presses the lock 71 into the position shown in FIGS. 1 to 4 obliquely to the longitudinal axis of the push rod 11, which penetrates the lock 71 through a passage, not shown in more detail, which has a clearance fit for the dimension of the push rod 11.

In the inclined position shown in FIGS. 1 to 4, the lock 71 with its lateral edges (not shown in more detail) canted with the push rod 11 in such a way that the clamping forces generated on the tilted areas by means of the locking spring 77 push the push rod 11 back against the feed direction V. prevent and thus maintain the clamping forces generated on the jaws 5 and 13.

A coupling device 81 is provided on the actuating side 17 of the push rod 11 and is slidably mounted as an elongate component in a bearing receptacle in the carrier section 35. The locking spring 77 forces the elongated 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.

Individual, in particular independent aspects of the invention are described below, which relate in particular to a functional connection of the individual components of the inventive step mechanism 21 and the tool according to the invention.

Stepping gear away operation 21st

As indicated above, the stepper transmission according to the invention has two gear step widths or two different feed paths with a complete actuation stroke of the Actuating arm 31. The operating state is explained below, in which large feed paths are achieved with an actuating stroke which is defined by the angle α between the handle 9 and the actuating arm 31.

In the way operation for moving the push rod 11 together with the movable jaw 13, the active lever ww is effective. No forces occur on the jaw 5, whereby the actuation of the arm 31 is already possible with a small force, which, however, is not sufficient to activate the decoupling device 53, i. H. to push the pin 61 out of the shell-like receptacle of the coupling rod 59 by compressing the preload holding spring 55.

When the actuating arm 31 is pivoted, the push rod 11 is displaced in the feed direction V by the increment of the travel operation against the return spring 49 via the travel driving slide 41 tilted with the push rod 11. The return spring 49 may only be dimensioned so strong that it does not transmit a force to the travel slider 41 in any of its compressed positions, which force is stronger than a trigger force threshold required to activate the decoupling device 53.

When the complete actuation stroke (see FIG. 2) is complete, the actuation arm 31 rests on the handle 9 and the return spring 49 is brought into its maximally compressed position. If the actuating arm is released by the operator, the return spring 49 presses the actuating arm 31 into the rest position shown in FIG. 1 in the rest position shown in FIG. 1, in which it rests against a stop on the carrier region 35.

1 and 2, in which the rest position and the end position of the actuating arm in the travel mode of the stepping gear 21 is shown, it can be seen that even during the travel mode large incremental engagement of the power transmission point (at 65) of the actuating arm 31 with the force-driving slide 39, and thus also in the away operation of the stepping gear 21, the force-driving slide 39 corresponding to the actuation stroke of the actuating arm 31 and the force-active lever WK in the feed direction V is moved. The feed of the force-driving slide 39 in the feed direction V does not effectively determine the displacement of the push rod 11 when the stepping mechanism 21 is in the off mode, because the feed rate of the push rod 11 during the off mode is substantially higher than the feed rate due to the way lever configuration. which could have been caused by the displacement of the force driving slide 39 according to the force lever configuration. If the actuating arm 31 is operated while the stepping mechanism is in the travel mode, both the travel driving slide 41 and the power driving slide 39 are moved in the feed direction V, the push rod 11 being immovable relative to the travel driving slide 41 during the travel operation, however, the push rod 11 is displaced relative to the force-driving slide 39.

As a result, the lever configuration (active lever W _K ) responsible for the power operation of the step transmission 21 also functions during the travel operation, but without acting on the push rod 11 in accordance with the lever force transmission. The distance shown in FIG. 2 between the force-driving slide 39 and the travel-driving slide 41 therefore does not represent the actual displacement increment of the stepping gear in the way operation, because the force-driving slide 39 is also approximately the product of the active lever W. _K and the sine of the angle α has shifted. The actual step size of the step mechanism 21 in the travel mode can approximately be determined by the product of the travel lever ww and the sine of the angle α.

Power operation of the step gear 21

In the power operation of the stepping gear 21, the push rod 11 is only displaced in small increments in the feed direction V, which makes it easier to generate increases in tension between the jaws 5 and 13.

The active lever W _{K of} the actuating arm 31 is effective in the power mode. As can be seen in FIG. 3, the decoupling device 53 is shown in its activated state. The pin 61 is pressed out of the shell-like mounting, so that the travel slider 41st can be pushed freely from the return spring 49 against the feed direction V to the force-driving slide 33 insofar as the travel-driving slide 41 is no longer forced into a tilted position by the rigid coupling by means of the coupling rod 59.

The decoupling device 53 is activated when a force is transmitted to the actuating arm 31 by the operator which is greater than the trigger force threshold set in advance by the decoupling device. This actuating force is only applied during operation when a clamping force is to be generated between the jaws 5 and 13, namely when an object to be clamped is to experience clamping forces. This scenario is indicated in FIG. 3 by the contact of the jaws 5, 13.

By decoupling the coupling rod 59 from the displacement slider 41, the displacement lever wψ of the actuating arm 31 is no longer effective.

As explained above, the actuating arm 31 is always at the point 65 (force-active lever W _K ) on the force-driving slide 39 during the entire operation of the stepping gear, which is brought about by the return spring 51. Thus, the power lever configuration is effective immediately, and a continuous advancement of the push rod 11 without interruption due to the switching process by the decoupling is achieved when the actuating arm is continued to be actuated.

Due to the small power lever WK it can be seen that when the actuating arm 31 is actuated by an actuating stroke (α), a significantly smaller step size is achieved than is achieved in the above-described way operation with the way lever Wirk.

After actuation of the actuating arm 31 in power operation by an actuation stroke (α), this lies on the handle 9, which is shown in FIG. 4. When the actuating arm 31 is released, the latter is brought back into the rest position of the actuating arm 31 due to the return spring 51, as shown in FIG. 3. Since the return spring 49 is out of order When the travel slider 41 is pushed against the force slider 39, the pin 61 cannot snap back into the shell-like end region of the coupling rod 59. A renewed actuation stroke with the power lever configuration is thus possible without delay.

Release the clamping force and clutch

If the clamping force acting between the jaws 5 and 13 is to be released, the lock 71 must be actuated on its actuation-side section 73 in the feed direction V, so that the actuation section 73 is pivoted on the swivel part 75 (FIG. 5) and the canting with the push rod 11 is solved, which is responsible for maintaining the clamping force between the jaws 5 and 13 due to the closed force profile from one jaw via the lock 71 into the push rod 11 and further into the other jaw 13.

When the lock 71 is actuated, the coupling device 81 is actuated simultaneously, as indicated in FIG. 5. The elongated component of the coupling device 81 is pressed against the bias of the locking spring 77 in the feed direction V.

In the rest position of the actuating arm 31 in the power operation of the stepping gear 21 (see FIG. 3), the travel driving slide 41 rests against the free end of the elongated component, so that when the lock 71 is actuated, the travel driving slide 41 acts directly becomes. The return spring 49, when the lock 71 is actuated, causes the displacement slider 41 to pivot around an engagement area of the return spring 49 on the displacement slider 41, so that the pin 61 can reach the shell-like end region of the coupling rod 59, which is shown in FIG. 5 is.

As can be seen in FIG. 5, a driver 85 causes the force catch slide 39, which is always tilted, to be released. By releasing the lock 71 and the tilt of the force catch slide 39, the rail can be displaced counter to the feed direction V by the jaws 5 and 13 to separate from each other in order to establish a new clamping zone 23. Always tilted slide valve 39

As explained above, the force-driving slide 39 is held in a constantly tilted position relative to the push rod 11, so that force operation is possible at any point along the push rod 11.

The tilted position of the driving slide 39 enables a switch from the gear with a large step size to the gear with small step size of the stepping mechanism 21, even during an actuation stroke of the actuating arm, without loss of actuation path.

The travel slider 41 is also brought by the coupling component 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.

6 to 11, a tool or a step gear is shown. The tool is shown in the configuration of a clamp 101, which has a carrier 103, which has a fixed jaw 105 and a housing 107, a movable push rod 111, at one end of which a movable clamp 113 is fixedly attached. The fixed jaw and the housing 107 can be made from one piece, in particular can be injection molded from a plastic piece. The jaws 105, 113 are located on a clamping side 115 of the push rod 111, the opposite side of the push rod 111 being called the actuating side 117.

The housing 107 delimits an interior 119, in which the organs of a two-speed step transmission 121 are at least partially accommodated, which provide two operating states, namely one-way operation, which is characterized by long displacement paths of the push rod 111, and one power operation, which is formed by small displacement paths to build up high clamping forces between the jaws 105 and 113. 6, the jaws 105 and 113 are shown separated from one another, wherein a clamping zone 123 can be defined between the jaws, in which a contrast can be inserted.

The stepping gear 121 with two step sizes comprises a dotted indicated actuation arm 125 which can be pivoted about a bearing 127. The pivot bearing 127 is arranged on the actuation side 117 on the carrier 103.

The travel actuating arm 125 has a recessed gripping insert 129 which has a high coefficient of friction. In addition, the travel actuating arm 125 has a first section 131 with the gripping insert 129 and a second section 132, which two sections 131, 132 are arranged at an angle of approximately 125 degrees.

The travel actuating arm 125 has an invariable permanent lever configuration defined by the active lever w _\ y. The length of the active lever is determined by the distance of the pivot bearing 127 from a power transmission point 128.

Furthermore, the step transmission 121 according to the invention comprises a force actuating arm 137 which can be pivoted about a pivot bearing 139 which is arranged on the tension side (115) on the carrier 103. The power actuating arm 137 comprises a hand grip insert 141, which lies on the side of the power actuating arm 137 facing away from the travel actuating arm 125. As can be seen from the arrangement of the gripping inserts 141, 129, the clamping clamp 101 can be gripped either by the force actuating arm 137 or by the displacement actuating arm 125.

The power actuating lever 137 has a first arm section 143 and a second arm section 145, which arm sections 143, 145 lie at an angle of approximately 160 ° to one another. The lever configuration of the power actuator arm 137 is determined by the power The active lever WK is defined, the length of which can be defined by the distance between the pivot bearing 139 of the force actuating arm 137 and the force transmission point 135, which is designed as a bolt fastened to the force actuating lever 137.

The step transmission according to the invention comprises a single driving slide 151, which is formed by two parallel plates. The driving slide 151 comprises a passage (not shown in detail) through which the push rod 111 can penetrate in a clearance fit. In the actuating arms 125 and 137, a driving slide 151 engages on one clamping side (115).

A return spring 153, which surrounds the push rod 111 as a helical spring, is supported on the one hand on the inside of the radial bearing area of the carrier 103 and, on the other hand, biases the driving slide 151 against a feed direction V.

6 shows the rest position of the power actuating arm 137, in which the power actuating arm 137 comes to a stop (not shown in detail) of the housing 107 on the actuating side 117. As a result, the force actuating arm, like the force transmission point 135, cannot be pivoted against the feed direction V. By means of the return spring 153, the driving slide 151 is brought into abutment against the feed direction V with the force transmission point 135 and into a tilted position in which the driving slide 151 is tilted with the push rod 111. In this way, a position of the driving slide 151 that is tilted in the unactuated state of the force actuating arm 137 is provided.

On a side of the housing 107 facing the clamping zone 123, a lock 155 is provided which has an actuating section 157. A pivoting section 159 engages with a recess which is attached to the housing 107 on the tensioning side in such a way that the lock 155 is held on the housing 107 and can be pivoted about the pivoting section 159. The lock 155 has a passage that the push rod 111 can penetrate in a clearance fit. A locking spring 161 forces the lock into a position that is always tilted relative to the push rod 111, so that the lock 155 cant relative to the push rod 111, thereby preventing the push rod 111 from being displaced in the opposite direction of advance V.

The transmission according to the invention also has a device 163 for releasing the tilted position, which is arranged on the actuation side on the carrier 107. The device 163 is formed as an elongate component, which is slidably mounted on the actuation-side housing section and is biased by the locking spring 161 against the feed direction V.

Stepper gear 121 operation away

6 to 8 show three operating positions of the travel operation of the stepping gear, with an unactuated position being shown in FIG. 6, an intermediate position in FIG. 7 and an actuating end position in FIG. 8.

In the starting position shown in FIG. 6, the clamping clamp 101 is gripped such that the palm rests on the travel actuating arm 125 and at least the middle and / or index finger can grip the power actuating arm 137.

Due to the always tilted position of the driving slide 151, one of the actuating arms 125 or 137 causes a displacement of the push rod 111 during the smallest actuation stroke.

Before the travel actuating arm 125 takes effect, the power actuation arm 137 is pivoted by a first pivoting range β in order to bring the power actuation arm into its counter or abutment position, in which the power actuation arm 137 with its the travel actuation arm 125 facing side on the pivot bearing 127 of the travel actuating arm 125, which is shown in Fig. 7. In the abutment position, the power actuating arm 137 can no longer be pivoted toward the travel actuating arm 125 become. Already during this first actuation phase of the power actuating arm 137, the driving slide 151 has been displaced in the feed direction V according to the power lever configuration in accordance with the active lever W _K. It should be noted that this displacement corresponds to the step size of the power operation.

If the force actuating arm has reached the abutment position shown in FIG. 7, the shifting of the large step width can be carried out in accordance with the travel operation of the step gear 121. As can be seen in FIG. 8, the travel actuating arm 125 is pivoted towards the fixed power actuating arm 137 in accordance with the travel lever configuration in which the travel active lever ww acts.

With a full actuation stroke of the travel actuation arm 125, the return spring 153 is compressed (FIG. 8). If the actuating force is released from the travel actuating arm 125 (FIG. 9), the return spring 153 presses the driver slide 151 out of its tilted position and moves it back towards the force actuating arm 137, in particular toward the force transmission point 135. The driving slide 151 is pushed back in constant contact with the force transmission point 128 of the travel actuating arm 125 at its tension-side end.

If the object to be clamped (not shown) has not yet been gripped (see FIG. 7), the travel actuating arm 125 can be actuated again after reaching the position shown in FIG. 7 until the jaws 105 and 113 hold the object to be clamped (not shown) ) have taken

Power operation of the step gear 121

The force operation with a small step size of the stepping gear is described in particular with reference to FIGS. 8 to 10. Power operation is used in particular when high clamping forces have to be applied to the jaws 105 and 113. This is to be indicated in FIGS. 8 to 10 in that the jaws 105, 113 are in direct contact. After the two jaws 105, 113 have made contact, further actuation of the travel actuating arm 125 can no longer be carried out insofar as the large travel active lever ww requires enormous forces in order to realize a displacement of a travel increment. In this respect, the travel actuating arm 125 is to be regarded as a counter or abutment arm in the power operation of the stepping gear mechanism, against which a pivoting movement of the power actuation arm 137 is made possible.

Before the power actuation stroke can be carried out, the power actuation arm 137 must be brought from its end position shown in FIG. 7 into the starting position shown in FIGS. 6 and 9. For this purpose, the force actuating arm 137 must be released so that the return spring 153 can initiate the necessary pivoting movement about the pivot bearing 139 into the starting position via the driving slide 151 and the force transmission point 135.

In the power operation of the step gear 121, the travel actuating arm 125 is used as a counter or abutment arm. The power actuating arm 137 is pivotable until the side of the power 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. 10. The power lever configuration produces small increments with a constant actuation stroke, so that the desired clamping forces can be induced on the jaws 105 and 113.

This process can be repeated by releasing the power actuator arm 137 from the operator's fingers (not shown), whereby the return spring 153 returns the actuator arm to the starting position for a new power actuation stroke, as shown in FIG. 9. Loosen the tension and tilt

In order to release the clamping force between the clamping jaws 105, 113, which is maintained by the lock 155, the actuating section 157 of the lock 155 must be actuated. The device 163 for releasing the canting of the driving slide is actuated simultaneously. When the lock 155 is actuated, the elongate component of the device 163 presses on the actuation-side section of the driving slide 151, as a result of which it is pivoted about the force transmission point 135 of the force actuating arm 137 and thus loses its tilted position relative to the push rod 111.

When the lock 155 is deactivated and the device 163 is activated, the push rod 111 together with the movable jaw 113 can be moved against the feed direction V.

The features of the invention disclosed in the above description, in the drawing and in the claims can be essential both individually and in any combination for realizing the invention in its various embodiments.

Irwin Industrial Tools GmbH

List of reference symbols

1 clamp 59 coupling rod

3 supports 63 hinge joint

5 jaw 65 system bolts

7 housing 71 lock

9 Handle 73 ^{^} operating section

11 Push rod 75 bearing part / swivel part

13 jaw 77 locking spring

15 clamping side 81 coupling device

17 Actuating side 101 clamp

19 Clearance 103 beams

21 2-speed step gear 105 jaw

23 clamping zone 107 housing

25 Storage area 111 push rod

27 Storage area 113 clamping jaw

31 operating arm 119 interior

33 pivot bearing 121 stepper gear

35 actuation side section 123 clamping zone

37 Hand grip insert 125 travel actuating arm

39 Power take-away slide 127 swivel bearing

41 travel slider 128 power transmission point

43 passage 129 gripping system

45 passage 132 second section

49 Return spring 135 power transmission point

51 Return spring 137 Power actuator arm

53 Decoupling device 139 swivel bearing

55 preload retaining spring 141 hand grip insert

57 ball 143 arm section 145 arm section

151 slider

153 return spring

155 lock

157 Actuating section

159 swivel section

161 locking spring

163 Device for releasing the cant

235 force entry point

V Feed direction W _K Power lever w Travel lever

Claims

Irwin Industrial Tools GmbH patent claims

1. Stepper gear for a clamping and or spreading tool, which has a fixed jaw and a fixedly connected to the fixed jaw carrier (3), on which a push or pull rod with a fixedly attached movable jaw (13) is movably supported, wherein the step mechanism is designed for step-by-step displacement of the push rod or pull rod together with the movable jaw relative to the fixed jaw in a feed direction with at least two different increment lengths and has at least one actuating arm (31) which can be actuated with at least two lever configurations, characterized in that a device is provided for switching from a first lever configuration to a second lever configuration, wherein when the switching device is activated, in particular in a predeterminable operating state, the activated lever configuration comes into direct, seamless engagement.

2. Stepper transmission according to claim 1, characterized in that the switching device is formed by a mechanism for separating a coupling structure between the actuating arm (31) and a driver, via which the actuating arm (31) can be brought into engagement with the push or pull rod, wherein in particular the decoupling mechanism is designed as a load-dependent release device.

3. Stepper transmission according to claim 1 or 2, characterized in that a coupling device (81) for restoring a separate coupling between the driver and the actuating arm (31) is provided, in particular the Einkupplimgseinrichtung (81) via a lock (71) to prevent displacement the push or pull rod can be actuated counter to the feed direction V.

4. Stepper transmission according to one of claims 1 to 3, characterized in that a continuously activatable lever configuration is provided, in particular for a displacement with a small increment, in particular when the decoupling mechanism is deactivated, a priority lever configuration, in particular for a displacement with a large increment, the operation of the stepping transmission ( 21) and, in particular when the decoupling mechanism (53) is activated, the lever configuration of large increments is deactivated and the lever configuration of small increments is activated.

5. Stepping gear, in particular according to one of claims 1 to 4, for a clamping and / or spreading tool, which clamping and / or spreading tool has a fixed jaw (105) and a carrier (103) firmly connected to the fixed jaw (105) on which a push or pull rod with a fixedly attached movable jaw (113) can be movably supported, the stepping gear being designed for step-by-step shifting of the push or pull rod in a feed direction and two separately operable actuating arms are provided which are actuated cause a displacement of the push or pull rod in the same feed direction (V).

6. Stepper transmission according to claim 5, in which the at least two lever configurations are operable alternately, in particular mutually exclusive, are effective.

7. Stepper transmission according to one of claims 5 or 6, in which the two actuating arms are pivotably articulated on the carrier (103) in such a way that they have opposite actuation directions.

8. Stepper transmission according to one of claims 5 to 7, in which a force-actuating arm (137) is pivotably articulated on an actuating side (117) of the push or pull rod and on the actuating side (117) of the push or pull rod with a Driver can be brought into engagement, via which the force actuating arm (137) interacts operationally with the push or pull rod, in particular a displacement actuating arm (125) with a large step size and a force actuating arm (137) with a small step size being matched to one another in this way that when you press the one operating arm the other operating arm acts as a support or abutment.

9. Stepping gear, in particular according to one of the claims 1 to 8, for a clamping and / or spreading tool, in particular for a clamp, the clamping and / or spreading tool having a fixed jaw and a carrier (3 , 103) on which a push or pull rod with a movable jaw firmly attached to it can be movably supported, the stepping gear being designed for step-by-step shifting of the push or pull rod in a feed direction and having an operating arm to be operated in one operating direction, which can be brought into engagement with the push or pull rod in accordance with the lever force transmission by means of a driver which can be displaced against a return spring, characterized in that the actuating arm is pivotably articulated on a tensioning side (15, 115) of the push or pull rod and the actuating arm on the tensioning side ( 15, 115) of the push or pull rod engages with the driver Is ngbar, so that the direction of actuation is substantially the same as the feed direction of the push or pull rod.

10. Stepper transmission according to claim 9 with an overload protection device which is designed to release a coupling of the driver to the actuating arm at a force release threshold.

11. Stepping gear, in particular according to one of the claims 1 to 10, for a clamping and / or spreading tool, in particular for a clamping clamp (101), the clamping and / or spreading tool having a fixed jaw (105) and one with the fixed one Bak (105) has fixedly connected carrier (103) on which a push or pull rod with a movable jaw (13, 113) fixedly attached to it can be movably supported, the stepping mechanism (121) being used to gradually shift the push or pull rod is designed in a feed direction and has at least one actuating arm pivotably articulated on the carrier (103), which can be brought into engagement with the push rod or pull rod in accordance with the force of the lever by means of a force that can be displaced against a return spring (153), characterized in that a pivot bearing (127) of the actuating arm is arranged on an actuating side (117) of the push or pull rod and the actuating arm has a force entry point (128) in the driver on a tensioning side (115) of the push or pull rod opposite the actuating side (117) ,

12. Stepping gear, in particular according to one of claims 1 to 11, for a clamping and / or spreading tool, in particular for a clamp, the clamping and / or spreading tool having a fixed jaw and a carrier (3) firmly connected to the fixed jaw. has, on which a push or pull rod with a fixedly attached, movable jaw can be movably supported, the stepping gear being designed for step-by-step displacement of the push or pull rod in a feed direction and having an actuating arm (31) and a driver via which the actuating arm (31) can be brought into engagement with the push or pull rod in accordance with lever force transmission, the actuating arm (31) being connected to the driver via a coupling component securing a stationary force transmission, characterized by a decoupling device for separating the coupling between the driver and the actuating arm ,

13. Stepper transmission according to claim 12, characterized in that a coupling device (81) is provided for restoring a separate coupling between the driver and the actuating arm (31).

14. Stepping gear, in particular according to one of claims 1 to 13, for a clamping and / or expanding tool, in particular for a clamp, the clamping and / or expanding tool having a fixed jaw (5, 105) and one with the fixed jaw (5, 105) has firmly connected carrier (3, 103) on which a push or pull rod (11, 111) with a fixedly attached, movable jaw (13, 113) can be movably supported, the stepping mechanism (21, 121) being designed for gradual displacement of the push or pull rod in a feed direction and an actuating arm (31, 125, 137) and a driver, by means of which the actuating arm (31, 21, 125) can be brought into engagement with the push or pull rod (11, 111), characterized by an urging means which at least in the holds the unactuated operating state of the actuating arm canting on the push or pull rod and keeps it in constant contact with the actuating arm, and a device (81, 163) for releasing the canting of the driver.

15. Stepper gearbox according to claim 14, characterized in that the release device (81, 163) can be actuated via a lock (71, 155) which counteracts the feed direction V by displacing the push or pull rod (11, 111).

16. Tool for generating a clamping and / or spreading force, in particular a clamp, with: - a push or pull rod (11, 111), - a fixed jaw (5, 105), - one with the fixed jaw (5, 105) firmly connected carrier (3, 103) on which the push and pull rod (11, 111) is movably mounted, one on the push or pull rod (11, 111) fixedly arranged movable jaw (13, 113) and one after of claims 1 to 15 trained stepper gears (21, 121).