EP3664999B1 - Presse actionnée à la main - Google Patents

Presse actionnée à la main Download PDF

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Publication number
EP3664999B1
EP3664999B1 EP19779456.3A EP19779456A EP3664999B1 EP 3664999 B1 EP3664999 B1 EP 3664999B1 EP 19779456 A EP19779456 A EP 19779456A EP 3664999 B1 EP3664999 B1 EP 3664999B1
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EP
European Patent Office
Prior art keywords
shaft
press
spring
counterweight
actuating lever
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
EP19779456.3A
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German (de)
English (en)
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EP3664999A1 (fr
EP3664999C0 (fr
Inventor
Andreas Leo Meyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gebrueder Schmidt Fabrik fuer Feinmechanik GmbH and Co KG
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Gebrueder Schmidt Fabrik fuer Feinmechanik GmbH and Co KG
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Publication of EP3664999A1 publication Critical patent/EP3664999A1/fr
Application granted granted Critical
Publication of EP3664999B1 publication Critical patent/EP3664999B1/fr
Publication of EP3664999C0 publication Critical patent/EP3664999C0/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/24—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by rack-and-pinion means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements

Definitions

  • the present invention relates to a hand-operated press with an actuating member coupled to a shaft, the actuation of which is converted into a lifting movement of a press ram coupled to the shaft and thus also into a change in a relative position of the press ram, the press also having a reset mechanism for resetting the actuating member which counteracts the actuation of the actuating member and causes a restoring movement of the press ram that is opposite to the lifting movement.
  • Such hand-operated presses which are also referred to as hand lever presses, are used in large numbers for manual assembly processes. These can be designed as toggle presses or rack presses.
  • toggle presses the press ram is moved by means of a toggle lever mechanism, which is driven by an actuating element that is usually designed as an actuating lever.
  • the press ram experiences a sinuous movement.
  • the adjustment angle of the actuating lever (actuating element) increases, the press ram travels a smaller distance.
  • the toggle lever mechanism is in the so-called "extended position"
  • the stroke of the press ram is fully extended. Shortly before the toggle lever reaches the extended position, a large force can be exerted on the press ram due to the toggle lever mechanism.
  • Hand-operated presses with a toggle lever mechanism are therefore particularly suitable for pressing processes in which high force is required over a short distance.
  • the press ram is driven by a spur gear shaft that engages with a rack or a set of teeth incorporated into the press ram.
  • the spur gear shaft is usually firmly connected to the actuating element (e.g. actuating lever).
  • the spur gear shaft can be made in one piece or in several pieces (shaft, shaft-hub connection, spur gear).
  • the press ram can be designed as a round ram or as a square ram. At the end of the press ram there is a tool holder for holding customer-specific pressing tools.
  • An anti-twist device usually prevents the press ram from rotating over the entire stroke.
  • the ram stroke is determined by the length of the rack attached to the ram or the length of the teeth integrated in the ram and by the adjustment angle of the actuating lever. If the force on the actuating lever remains the same, the same pressing force is theoretically exerted over the entire ram stroke.
  • Hand lever presses with a rack are therefore particularly suitable for pressing processes in which continuous force is required over long distances.
  • Hand-operated presses regardless of whether they are designed as toggle presses or rack-and-pinion presses, are usually equipped with a reset mechanism that has the task of moving the press ram and thus also the actuating element back to its basic position after the pressing process.
  • a reset mechanism For example, a return spring can be used, which is designed as a conventional tension spring.
  • tension springs have to be designed to be relatively large, particularly with a large plunger stroke.
  • Another disadvantage when using such conventional tension springs is the force difference that arises between the starting position and the maximum plunger stroke.
  • a torsion spring designed as a helical torsion spring can be used in the return mechanism.
  • Such torsion springs can be arranged in a rack and pinion press, for example between the spur gear shaft or the spur gear and the slide housing in which the press ram is guided longitudinally.
  • the torsion spring can be accommodated in the slide housing to save space due to the small number of turns.
  • torsion springs For hand-operated presses with a large ram stroke, torsion springs with a large number of turns would have to be used. However, due to the installation length of the torsion spring, this large number of turns of the torsion spring prevents it from being installed in slide housings of typical size. Furthermore, at large angles of rotation there is a risk that the torsion spring will “buck” due to the torsional tension. This leads to premature “breaking” of the torsion spring and thus to total failure of the return mechanism. Torsion springs are therefore poorly suited for use in return mechanisms for hand-operated presses with large ram strokes.
  • the US 3,251,250 A shows a column drilling machine which discloses the features of the preamble of claim 1, and in which the return mechanism for the operating lever for displacing the drill head has a spiral spring.
  • Another device with a counterweight attached to a hand lever is from the JP S62 155990 U known.
  • From the US 2,006,746 A a spindle mechanism for extending and retracting a rotatable tool is known.
  • the DE 25 04 872 A1 also shows a work stand for an electric DIY machine.
  • the return mechanism has a spiral spring, which is designed as a spirally wound leaf spring, and has a first tab at its radially inner end, which is designed as a curved section is integrally connected to the coil spring, wherein the first tab is curved in the direction of a curvature of the coil spring, wherein the coil spring has at its radially outer end a second tab which is designed as a curved section which is integrally connected to the coil spring, wherein the second tab is curved in the opposite direction to the curvature of the spiral spring, and wherein the shaft has a web which is aligned parallel to a longitudinal axis of the shaft, a cavity being arranged between the web and an outside of the shaft pointing towards the web, into which the first tab engages.
  • spiral spring unlike a helical torsion spring or torsion spring, has a spiral or helical shape in the mathematical sense, whereas a helical torsion spring or torsion spring typically has a helical or helical shape.
  • a spiral spring is designed as a spirally wound leaf spring, in which the spring leaf has an increasing distance from the axis as the angle of rotation around the axis of the spiral spring increases.
  • the usually flat spring leaf of such spiral springs is, unlike the helically wound wire of a torsion spring, not subjected to torsion when loaded, but rather to tension.
  • Such spiral springs are often referred to as “mainsprings”.
  • the main advantage of using a spiral spring in the present case of a reset mechanism of a hand-operated press is that such spiral springs produce a relatively constant force curve when loaded, which is almost independent of their angle of rotation.
  • a spiral spring in the return mechanism of a hand-operated press there is only a minimal difference in force for the press operator between the starting position and the maximum position of the actuating element (for example the actuating lever). For the operator, this is expressed in a very pleasant and continuous actuation of the actuating element without increased or changing effort.
  • the restoring movement caused by the restoring mechanism takes place relatively continuously as soon as the operator visibly reduces the force exerted on the actuating element or even completely releases the actuating element.
  • spiral springs with a relatively small spring constant can be used due to the mechanical properties of such spiral springs. Even with large expected angles of rotation, spiral springs can be designed to be relatively space-saving and can be easily accommodated in the slide housing of the hand-operated press.
  • the spiral spring has a first tab at the radially inner end and a second tab at the radially outer end.
  • the first tab is preferably used to attach the spiral spring to the shaft.
  • the second tab is preferably used to attach the spiral spring to the spring housing. If no extra spring housing is provided, the second tab of the spiral spring can also be connected directly to the slide housing.
  • the first and second tabs are designed as curved sections which are integrally connected to the coil spring, the first tab being curved in the direction of a curvature of the coil spring and the second tab being curved in the opposite direction to the curvature of the coil spring.
  • the two tabs are preferably not completely closed tabs, but rather merely bent, essentially U-shaped ends of the spring leaf, which are more curved than the remaining parts of the spiral spring located between the ends of the spring leaf. This creates a kind of hook that can easily be hooked onto the shaft or the spring housing or the slide housing (if there is no spring housing).
  • the second tab which is curved in the opposite direction to the curvature of the spiral spring, is hooked onto the spring housing or the slide housing. This is preferably done when installing the spiral spring in the spring housing, i.e. before inserting the spring housing together with the spiral spring into the slide housing of the press.
  • the first tab which is curved in the direction of the curvature of the spiral spring, is attached to the shaft after the spring housing has been inserted into the slide housing. This fastening process can be done relatively easily.
  • the shaft has a web which is aligned parallel to a longitudinal axis of the shaft, a cavity into which the first tab engages is arranged between the web and an outside of the shaft facing the web.
  • This bar enables a simple but nevertheless secure connection of the spiral spring to the shaft.
  • the web can be designed, for example, as a cylindrical or heavy-duty tension pin.
  • the simple connection of the first tab provided on the spiral spring with the web makes it extremely easy to install the spiral spring pre-tensioned in the spring housing into the slide housing.
  • the spring housing and the spiral spring are first inserted into the slide housing.
  • the shaft only has to make one revolution in order to hook the first tab into the web arranged on the shaft.
  • the reset mechanism can therefore be used directly.
  • the installation dimension of the spiral spring which is specified by the spring housing, does not change.
  • the shaft is rotatably mounted in a slide housing in which the press ram is guided longitudinally, the spiral spring being arranged in a spring housing which is mounted in the slide housing.
  • the spiral spring is therefore arranged in an extra housing, the spring housing, and can be mounted together with the spring housing in the slide housing.
  • the spiral spring can therefore be pretensioned before it is installed in the slide housing.
  • the spiral spring which has a very high potential energy when pre-tensioned, therefore poses no danger during assembly. It can be inserted into the slide housing together with the spring housing relatively easily and without danger, even when pre-tensioned.
  • the spiral spring would have to be inserted directly into the slide housing of the press. Since the spiral spring typically has to be pre-tensioned to ensure sufficient restoring force, the pre-tensioned spring in such a case would result in a very high risk potential during assembly, as the pre-tensioned spiral spring tries to expand with high energy in order to return to its original state (untensioned state ) to get. However, this can be avoided by placing the spiral spring in a spring housing.
  • the spiral spring can also be inserted into the spring housing in the spring housing in an unstressed or only slightly prestressed manner according to the above-mentioned embodiment and only prestressed after it has been installed in the slide housing of the press, without any danger for the operator or fitter.
  • the spring housing is preferably constructed in two parts and has a cup-shaped or basket-shaped housing part and a cover part which is attached to the cup-shaped or basket-shaped housing part.
  • the spring housing can be removed relatively easily from the slide housing and then the spiral spring can be removed from the spring housing by loosening the cover part from the housing part.
  • the spiral spring is preferably coupled to the shaft at its radially inner end and coupled to the spring housing at its radially outer end.
  • the shaft has a flat surface on the outside facing the web.
  • an upper side of the web facing away from the shaft is aligned flush with an outer peripheral surface of the shaft.
  • the actuating member has an actuating lever which is coupled to the shaft and runs transversely to it, with a counterweight being arranged on a side of the shaft opposite the actuating lever, which is coupled to the actuating lever and / or the shaft and as Torque compensation is used during actuation of the operating lever, with the counterweight having a larger mass than the operating lever and a center of gravity of the counterweight having a shorter distance from the shaft than a center of gravity of the operating lever.
  • both the lifting movement or the actuation of the operating lever as well as the restoring movement, which is caused by the restoring mechanism, can be designed more uniformly.
  • the position of the operating lever has no effect on the restoring force of the return mechanism.
  • the counterweight is preferably dimensioned such that the counterweight acts as a preferably complete torque compensation for the operating lever during the actuation of the actuating lever and during the return movement.
  • This torque compensation allows the actuating lever to be moved very evenly with a constant amount of force exerted on it, regardless of its current (angular) position. This even applies in the event that a press operator releases the operating lever after the pressing process. Even then, the return movement of the actuating lever takes place at a constant speed over the entire angular range of the movement.
  • the influence of the operating lever's own weight on the restoring force of the restoring mechanism would have a direct effect on the speed of the press ram.
  • the operating lever is in a horizontal position Position and points towards the operator, the force exerted on the shaft by the operating lever's own weight acts against the restoring force of the restoring mechanism.
  • the force exerted on the shaft by the operating lever's own weight increases the restoring force of the restoring mechanism. This would result in a very uneven movement of the operating lever.
  • the restoring mechanism can be designed more simply or a spring used in the restoring mechanism (here the spiral spring) can be made smaller. Without such a counterweight, the spiral spring or the return mechanism would have to be larger. This in turn would require a larger installation space for the reset mechanism, which on the one hand would require extra adjustments to the press and on the other hand would lead to undesirably large components.
  • a larger-sized return mechanism or a larger-sized spiral spring would also have a higher potential energy when tensioned. If the operator's hand were to slip on the operating lever, this would result in the operating lever being set in rotation very quickly due to the reset mechanism. This in turn would pose a significant risk to the operator.
  • the counterweight has a greater mass than the operating lever. This makes it possible to make the counterweight relatively compact, so that the counterweight hardly increases the installation space of the press.
  • the focus of the The counterweight therefore has a shorter distance from the shaft than the center of gravity of the operating lever.
  • the actuating lever preferably runs transversely to the shaft.
  • transverse does not necessarily mean orthogonal, but rather any orientation that is not parallel.
  • the actuating lever can, for example, also be aligned at an acute angle relative to the shaft or its longitudinal axis.
  • the actuating lever is preferably designed to be straight or straight. However, this does not necessarily have to be the case.
  • the actuating lever can also be curved or angled without departing from the scope of the present invention.
  • the actuating member further has a handle lever which is mounted on the actuating lever transversely to the actuating lever, a mass of the counterweight being dimensioned such that the counterweight acts as a torque compensation for the actuating lever and the Handle lever is used.
  • the handle lever is particularly advantageous in hand-operated presses with a long ram stroke, in which a rotary movement must be carried out with the actuating lever over a large angular range, for example > 360°.
  • the ergonomics for the operator can be improved many times over by providing such a handle lever, which is mounted on the operating lever transversely to the operating lever. A laborious "repositioning" of the operator's operating hand is no longer necessary when operating using the handle lever.
  • the dead weight of the handle lever can also be compensated for in addition to the dead weight of the actuating lever for the aforementioned torque compensation.
  • the handle lever is mounted on the actuating lever so that it can rotate about its longitudinal axis.
  • the handle lever is aligned transversely, preferably orthogonally, to the operating lever.
  • transverse is also to be interpreted generally in the above sense.
  • the counterweight has a first counterweight and a second counterweight, wherein a mass of the first counterweight is dimensioned such that the first counterweight serves as a torque compensation for the operating lever during the actuation of the actuating lever, and wherein a mass of the second counterweight is such is dimensioned so that the counterweight serves as a torque compensation for the handle lever during operation of the operating lever.
  • first and second counterweights are each releasably coupled to the operating lever and/or the shaft, and that the handle lever is releasably mounted on the operating lever.
  • both counterweights can be coupled to the operating lever and/or the shaft for torque compensation.
  • one of the two counterweights can be omitted or removed from the operating lever and/or the shaft. Regardless of whether one or more counterweights are used, they can be mounted directly on the operating lever or alternatively or additionally connected to the shaft. This has no influence on the torque compensation effect described above.
  • the shaft is designed as a spur gear shaft, with the press ram or a component coupled to it having teeth into which the spur gear shaft engages.
  • the press according to the invention is designed as a so-called rack and pinion press.
  • the spur gear shaft can be designed in one piece (toothed shaft) or in several pieces as a shaft with a shaft-hub connection and a spur gear arranged thereon.
  • the plunger can be designed as a round plunger or a square plunger.
  • the toothing is either arranged directly on the press ram. Alternatively, it can also be arranged on a component coupled to the press ram, for example on a rack running parallel to the press ram, which at the same time serves as an anti-rotation device for the press ram.
  • the press according to the invention can also be designed as a toggle press.
  • the shaft is then designed as a regular shaft, i.e. not as a spur gear shaft.
  • the Fig. 1 to 4 show a first embodiment of a hand-operated press according to the present invention.
  • the press is designated as a whole by reference number 10.
  • the press 10 has a base part 12, which is typically referred to as a press stand.
  • the press stand 12 forms the basic structure of the press 10 and essentially serves as a support for the remaining components of the press 10.
  • the press stand 12 is usually placed on a surface, for example a workbench.
  • a so-called slider 14 is mounted on the press stand 12, which in the exemplary embodiment shown here is adjustable on the press stand 12 along the height direction, which is indicated by the double arrow 16. This adjustability allows the slider 14 to be adjusted accordingly depending on the workpiece size and the desired stroke along the height direction 16.
  • An actuating member 18 is attached to the side of the slide 14, which is designed as an elongated actuating lever 20 in the exemplary embodiment shown here.
  • This actuator 18 is used to operate the press 10 by hand.
  • a wheel or another handle can in principle also be used to operate the press 10 by hand.
  • the press 10 is designed as a rack and pinion press.
  • a press ram 24 is guided longitudinally in the housing of the slide 14, which is referred to as the slide housing 22.
  • a shaft 26 is arranged in the slide housing 22, which is in 8 and 9 is shown in detail.
  • the shaft 26 is rotatably mounted in the slide housing 22.
  • the shaft is designed as a spur gear shaft (see 8 and 9 ).
  • the spur gear shaft 26 can either be designed in one piece, with the spur gear 28 being integrally connected to the shaft 26, or in several parts, with the spur gear 28 being inserted in a corresponding shaft-hub connection on the shaft 26.
  • the shaft 26 is coupled to the press ram 24. More precisely, the spur gear 28 engages in a toothing 30 provided on the rear side of the press ram 24 (see Fig. 3 ).
  • the actuating member 18 or the actuating lever 20 is coupled to the press ram 24 via the shaft 26 rotatably mounted in the slide housing 22.
  • the axis 36 is therefore also referred to as an anti-twist device.
  • the toothing 30 does not necessarily have to be arranged on the press ram 24 itself. In principle, this could also be attached to the axle or anti-rotation device 36.
  • a tool holder 38 for holding customer-specific pressing tools.
  • a wide variety of pressing tools can be attached to this tool holder 38 relatively easily using a fastener, for example using a screw.
  • the ram stroke is determined by the length of the toothing 30 arranged on the press ram 24 and the adjustment angle of the actuating lever 20.
  • the press 10 also has a reset mechanism 40, which is at least partially in Fig. 4-7 is shown.
  • This reset mechanism serves to reset the press ram 24 and thus also the actuating lever 20.
  • the reset mechanism 40 causes a restoring movement of the press ram 24 or the actuating lever 20, which is opposite to the lifting movement of the press ram 24 or the actuating movement of the actuating lever 20.
  • This return movement causes the press ram 24 to move along the in Fig. 3 schematically indicated arrow 42 moves upwards and the actuating lever 20 along the in Fig. 3 schematically indicated arrow 44 brought back to its starting position.
  • This starting position in which the press ram 24 is in its upper stop, is in Fig. 3 shown.
  • the force of the return mechanism 40 is generated by a spiral spring 46, which is shown in detail in Fig. 5 is shown.
  • the spiral spring 46 has a band-shaped spring leaf 48 or spring plate which is wound in a spiral shape. Unlike a coil torsion spring or torsion spring, such a spiral spring 46 is subjected to tension when loaded. Due to the load, the spirally wound spring leaf 48 is contracted or wound up. This shortens the distance between the radially outer windings and the radially inner windings of the spring leaf 48.
  • Such a spiral spring 46 is also referred to as a driving spring.
  • the spiral spring 46 is arranged on the shaft 26 or around the shaft 26.
  • the radially inner end 50 of the spring leaf 48 is preferably connected directly to the shaft 26.
  • An inner housing wall can be provided at the radially inner end of the spiral spring 46 in order to prevent direct contact of the radially inner turns of the spring leaf 48 with the shaft 26.
  • this is only an optional possibility and in the in Fig. 5 shown embodiment is not the case.
  • a significant advantage of using such a spiral spring 46 is that the restoring force only increases slightly, even with several revolutions of the shaft 26, compared to a helical torsion spring or torsion spring. This results in only a minimal difference in force for the operator between the starting position and the maximum position of the actuating lever 20. The restoring movement also occurs in a very uniform manner.
  • spiral spring 46 does not expand under load, in contrast to a helical torsion spring or torsion spring, so that it can be accommodated in the slide housing 22 in a very space-saving manner.
  • the spiral spring 46 In comparison to a helical torsion spring or torsion spring, the spiral spring 46 also ensures the possibility of generating a relatively large restoring force despite comparatively fewer turns.
  • the spiral spring 46 is preferably arranged in an extra housing 52, which is referred to as a spring housing.
  • a spring housing 52 Accommodating the spiral spring 46 in such a spring housing 52 offers the advantage that the spiral spring 46 can be pre-tensioned in advance, i.e. before it is installed in the slide housing 22, and is then inserted into the slide housing 22 together with the spring housing 52. This is particularly advantageous from a safety perspective, since the spiral spring 46 poses no danger to the fitter. In addition, this significantly simplifies the assembly of the spiral spring 46.
  • the spring housing 52 which in Figs. 6 and 7 is shown has a two-part structure.
  • the spring housing 52 has a cup-shaped or basket-shaped housing part 54 and a cover part 56, which can preferably be releasably connected to the housing part 54.
  • the mechanical connection of the pot-shaped or basket-shaped housing part 54 and the cover part 56 takes place by caulking several metal tabs 58.
  • various other types of connection of the two parts 54, 56 of the spring housing 52 are conceivable, for example by screwing , a bayonet lock etc.
  • the spiral spring 46 is preferably wetted with a lubricant before it is installed in the spring housing 52.
  • the spiral spring 46 has a first tab 60 at its radially inner end for attachment to the shaft 26. At its radially outer end 62, the spiral spring 46 has a second tab 64 for attachment to the spring housing 52.
  • the two tabs 60, 64 are preferably integrally connected to the spring leaf 48 of the spiral spring 46.
  • the two tabs are particularly preferably designed as curved sections, which are produced by bending the ends 50, 62. Both tabs 60, 64 are preferably more strongly curved than the spring leaf 48 or the remaining parts of the spring leaf 48 of the spiral spring 46.
  • the first tab 60 is curved in the direction of the curvature of the spiral spring 46.
  • the second tab 64 is curved in the opposite direction to the curvature of the coil spring 46.
  • the spiral spring 46 can be attached relatively easily by hanging it on the shaft 26 or the spring housing 52.
  • a web 66 is provided on the shaft 26 as a counterpart to the first tab 60 (see 8 and 9 ). This web 66 runs parallel to the longitudinal axis 68 of the shaft 26. Below the web 66 there is a cavity 70 into which the first tab 60 of the spiral spring 46 engages. The cavity 70 results between an outside of the shaft that faces the web 66 and is set back from the outer circumference of the shaft 26.
  • the shaft 26 preferably has a flat surface 72 on this outside. This flat surface 72 or the cavity resulting between the flat surface 72 and the web 66 simplifies the insertion of the first tab 60 of the spiral spring 46.
  • the top 74 of the web 66 facing away from the shaft 26 is arranged flush with an outer peripheral surface 76 of the shaft 26.
  • the second tab 64 arranged on the radially outer end 62 of the spiral spring 46 is suspended on a web 78 of the spring housing 52 (see Fig. 6 ).
  • This type of connection between the spiral spring 46 and the shaft 26 or the spring housing 52 using the tabs 60, 64 has the particular advantage that, on the one hand, the assembly is relatively simple and, on the other hand, the spiral spring or the spring leaf 48 is supported by the Tabs 60, 64 are not weakened.
  • the spiral spring 46 is inserted into a recess provided in the slide housing 22 after its assembly in the spring housing 52 in an already pre-tensioned state and then mounted with a cover 80, which is fastened to the slide housing 22, for example with the aid of two screws 82 (please refer Fig. 4 ).
  • the shaft 26 only has to make one revolution in order to hook the first tab 60 of the spiral spring 46 into the web 66 or the cavity 70. This is done more or less automatically by rotating the shaft 26.
  • the actuating lever 20 By further moving the actuating lever 20 in the actuating direction 32, the inner exposed turns of the spiral spring 46 rest on the shaft 26 or on the turns already wound on the shaft 26.
  • the installation dimension of the spiral spring 46 which is specified by the spring housing 52, does not change. All that changes is the ratio of the external to internal windings of the spring leaf 48.
  • the actuating lever 20 is preferably detachably attached to the shaft 26 in order to be able to adjust it accordingly during the setup of the press 10 in the direction of the arrow 32 or in the direction of the arrow 44 and then to fix it again on the shaft 26.
  • the press 10 ' according to the second exemplary embodiment differs essentially in the design of the actuating member 18.
  • the actuating member 18 has an actuating lever 20 and a handle lever 84 which is mounted on the actuating lever 20 transversely to the actuating lever 20.
  • a handle lever 84 is often also referred to as an ergo handle.
  • the handle lever 84 is particularly advantageous in pressing processes with a long ram stroke, since the actuating lever 20 must exert a rotational movement > 360 °. With such a large rotational movement, the handle lever 84 prevents an annoying gripping of the actuating lever 20, which is neither ergonomically nor safety-related advantage, since the operator's hand can slip off the actuating lever 20 relatively easily during such a gripping.
  • the handle lever 84 can be mounted on the actuating lever 20 so that it can rotate about its longitudinal axis. In this way, the operator can very easily apply force to the handle lever 84 or the operating lever 20 without having to change the orientation of his hand during operation.
  • the handle lever 84 is an optional feature, since the press can basically be operated using the actuating lever 20 alone without the handle lever 84.
  • the handle lever 84 is therefore preferably releasably mounted on the operating lever 20 so that the handle lever 84 can be used or omitted as desired.
  • a counterweight 86 is also mounted on the actuator 18. This counterweight 86 serves to compensate for the own weight of the operating lever 20 and the handle lever 84, if this is used.
  • the counterweight 86 effects a torque compensation, through which the actuating member 18 can be moved more continuously, regardless of its angular position. This enables a type of actuation that is more pleasant for the operator of the press without changing force or moment conditions during the actuation of the actuating element 18. In addition, this takes place Due to the counterweight 86, the restoring movement of the actuating member 18 also occurs in a continuous manner.
  • the return mechanism 40 can also be made smaller. This in turn results in a less strong acceleration of the actuator 18 by the return mechanism 40 during the return movement. This significantly minimizes the potential danger for the press operator.
  • the counterweight 86 Due to its very space-saving arrangement, the counterweight 86 hardly represents an obstacle for the operator. It preferably has a larger mass than the actuating lever 20. If the actuating lever 20 is used together with the handle lever 84, the mass of the counterweight 86 is also larger than the sum of the masses of the actuating lever 20 and the handle lever 84. For this reason, the counterweight 86 can be designed to be relatively small. The center of gravity of the counterweight 86 is at a shorter distance from the shaft 26 than the center of gravity of the actuating lever 20 or the handle lever 84.
  • the counterweight 86 can be mounted on the shaft 26 and/or the operating lever 20.
  • the counterweight 86 has a first counterweight 88 and a second counterweight 90.
  • the first counterweight 88 serves as a weight or torque compensation for the operating lever 20.
  • the second counterweight 90 serves as a weight or torque compensation for the handle lever 84.
  • Both counterweights 88, 90 are preferably releasably coupled to the operating lever 20 and/or the shaft 26. If the press is operated only with the operating lever 20, only the first counterweight 88 is used and the second counterweight 90 is removed from the press. However, if the actuating lever 20 is used together with the handle lever 84, both counterweights 88, 90 are used. This means that regardless of whether the operating lever 20 is with or without a handle lever 84 is used, a linear restoring force of the restoring mechanism 40 can be generated.

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  • Mechanical Engineering (AREA)
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  • Press Drives And Press Lines (AREA)

Claims (12)

  1. Presse (10, 10') actionnée à la main avec un organe d'actionnement (18) relié à un arbre (26), dont l'actionnement est transformé en un mouvement de levage d'un poinçon de presse (24) relié à l'arbre (26), et donc également en un changement d'une position relative du poinçon de presse (24), la presse (10, 10') présentant en outre un mécanisme de rappel (40) pour le rappel de l'organe d'actionnement (18), qui s'oppose à l'actionnement de l'organe d'actionnement (18) et qui provoque un mouvement de rappel du poinçon de presse (24) opposé au mouvement de levage, le mécanisme de rappel (40) présentant un ressort en spirale (46) qui est conçu sous la forme d'un ressort à lame enroulé en spirale et qui présente à son extrémité (50) située radialement à l'intérieur une première patte (60), qui est configurée comme une partie incurvée formant corps avec le ressort en spirale (46), la première patte (60) étant incurvée dans la direction d'une courbure du ressort en spirale (46), caractérisé en ce que le ressort en spirale (46) comporte, à son extrémité (62) située radialement à l'extérieur, une deuxième patte (64) qui est configurée sous la forme d'une partie incurvée formant corps avec le ressort en spirale (46), la deuxième patte (64) étant courbée en sens inverse de la courbure du ressort en spirale (46), et en ce que l'arbre (26) présente une nervure (66) qui est orientée parallèlement à un axe longitudinal (68) de l'arbre (26), un espace creux (70) dans lequel s'engage la première patte (60) étant aménagé entre la nervure (66) et un côté extérieur de l'arbre (26) tourné vers la nervure (66).
  2. Presse actionnée à la main selon la revendication 1, dans laquelle l'arbre (26) est monté à rotation dans un boîtier de coulisse (22) dans lequel le poinçon de presse (24) est guidé longitudinalement, et dans laquelle le ressort en spirale (46) est agencé dans un boîtier de ressort (52) qui est monté dans le boîtier de poinçon (22).
  3. Presse actionnée à la main selon la revendication 2, dans laquelle le boîtier de ressort (52) comprend une partie de boîtier (54) en forme de pot ou de panier ainsi qu'une partie de couvercle (56) qui est fixée à la partie de boîtier (54) en forme de pot ou de panier.
  4. Presse manuelle selon la revendication 2 ou 3, dans laquelle le ressort en spirale (46) est relié à l'arbre (26) à son extrémité (50) située radialement à l'intérieur et est relié au boîtier de ressort (52) à son extrémité (62) située radialement à l'extérieur.
  5. Presse actionnée à la main selon l'une quelconque des revendications 1 à 4, dans laquelle l'arbre (26) présente une surface plane (72) sur la face extérieure tournée vers la nervure (66).
  6. Presse actionnée à la main selon l'une quelconque des revendications 1 à 5, dans laquelle une face supérieure (74) de la nervure (66), opposée à l'arbre (26), est en affleurement d'une surface périphérique extérieure (76) de l'arbre (26).
  7. Presse actionnée à la main selon l'une quelconque des revendications 1 à 6, dans laquelle l'organe d'actionnement (18) comprend un levier d'actionnement (20) relié à l'arbre (26) et s'étendant transversalement à celui-ci, un contrepoids (86) étant disposé sur une face de l'arbre (26) opposée au levier d'actionnement (20), qui est relié au levier d'actionnement (20) et/ou à l'arbre (26) et qui sert d'équilibrage de couple pendant l'actionnement du levier d'actionnement (20), le contrepoids (86) ayant une masse supérieure à celle du levier d'actionnement (20) et un centre de gravité du contrepoids (86) étant à une distance plus courte de l'arbre (26) qu'un centre de gravité du levier d'actionnement (20).
  8. Presse actionnée à la main selon la revendication 7, dans laquelle l'organe d'actionnement (18) comprend en outre un levier de préhension (84) monté sur le levier d'actionnement (20) transversalement au levier d'actionnement (20), et dans laquelle une masse du contrepoids (86) est dimensionnée de telle sorte que le contrepoids (86) sert d'équilibrage de couple pour le levier d'actionnement (20) et le levier de préhension (84) pendant l'actionnement du levier d'actionnement (20).
  9. Presse actionnée à la main selon la revendication 8, dans laquelle le levier de préhension (84) est monté sur le levier d'actionnement (20) de manière à pouvoir tourner autour de son axe longitudinal.
  10. Presse actionnée à la main selon la revendication 8 ou 9, dans laquelle le contrepoids (86) comprend un premier contrepoids (88) et un deuxième contrepoids (90), une masse du premier contrepoids (88) étant dimensionnée de telle sorte que le premier contrepoids (88) sert de compensation de couple pour le levier d'actionnement (20) pendant l'actionnement du levier d'actionnement (20), et dans lequel une masse du deuxième contrepoids (90) est dimensionnée de telle sorte que le deuxième contrepoids (90) serve d'équilibrage de couple pour le levier de préhension (84) pendant l'actionnement du levier d'actionnement (20).
  11. Presse actionnée à la main selon la revendication 10, dans laquelle le premier et le deuxième contrepoids (88, 90) sont respectivement reliés de manière amovible au levier d'actionnement (20) et/ou à l'arbre (26), et dans laquelle le levier de préhension (84) est monté de manière amovible sur le levier d'actionnement (20).
  12. Presse actionnée à la main selon l'une des revendications 1 à 11, dans laquelle l'arbre (26) est conçu sous la forme d'un arbre à engrenages cylindriques et le poinçon de presse (24) ou un composant (36) relié à celui-ci présente une denture (30) avec laquelle l'arbre à engrenages cylindriques est en engagement.
EP19779456.3A 2018-10-05 2019-09-26 Presse actionnée à la main Active EP3664999B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018124596.3A DE102018124596B4 (de) 2018-10-05 2018-10-05 Handbetätigte Presse
PCT/EP2019/076050 WO2020069968A1 (fr) 2018-10-05 2019-09-26 Presse actionnée à la main

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EP3664999A1 EP3664999A1 (fr) 2020-06-17
EP3664999B1 true EP3664999B1 (fr) 2023-09-20
EP3664999C0 EP3664999C0 (fr) 2023-09-20

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US (1) US11911988B2 (fr)
EP (1) EP3664999B1 (fr)
CN (1) CN112805147A (fr)
DE (1) DE102018124596B4 (fr)
WO (1) WO2020069968A1 (fr)

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DE102022111888B4 (de) * 2022-05-12 2024-03-28 Gebr. Schmidt Fabrik für Feinmechanik GmbH & Co. KG Handbetätigte Presse
CN115320150B (zh) * 2022-10-12 2023-03-24 博格达智能装备(南通)有限公司 一种用于玻璃纤维隔板生产的压力机

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Also Published As

Publication number Publication date
US11911988B2 (en) 2024-02-27
EP3664999A1 (fr) 2020-06-17
CN112805147A (zh) 2021-05-14
EP3664999C0 (fr) 2023-09-20
US20210213698A1 (en) 2021-07-15
DE102018124596B4 (de) 2021-01-14
DE102018124596A1 (de) 2020-04-09
WO2020069968A1 (fr) 2020-04-09

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