EP3849749B1 - Pressing tool - Google Patents

Description

field of technology

The invention relates to a pressing tool for carrying out a pressing process for the press connection of parts, for example a sleeve with an electrical conductor, wherein a part, for example the sleeve, can have different external dimensions within a predetermined range, wherein the pressing tool further comprises a tool part for acting on the part, for example the sleeve, and the tool part is part of a pivoting jaw, wherein the pivoting jaw further comprises an action surface and is pivotable about a pivot axis from an initial position with a largest opening width to a pressing position with a smaller opening width, wherein the pressing tool further comprises a hydraulic piston movable in a hydraulic cylinder, which exerts a piston force depending on a hydraulic pressure in the hydraulic cylinder, wherein with each movement of the hydraulic piston, an automatic termination of the pressing process occurs upon reaching a same maximum piston force, wherein the hydraulic piston further comprises a cooperation surface formed by a roller connected to the hydraulic piston for a force-transmitting cooperation of the hydraulic piston with the action surface, wherein due to a geometry of the action surface, the piston force can be converted into a different pressing force is feasible.

State of the art

Known pressing tools are preferably used for pressing, especially for a pressing process referred to as "crimping," of parts, for example a sleeve, or further, for example, a cable lug with an inserted electrical conductor. Such parts, for example sleeves Cable lugs, or cable lugs, are available within a given range in different external dimensions, in particular with different cross-sectional areas, in particular with a receiving opening for accommodating another part, for example the conductor(s). For example, sleeves or cable lugs with 4, 10, 16, 50, 70, or even 120 ^mm² are known.

There is a need to be able to press parts such as sleeves or cable lugs with different external dimensions, preferably without changing the tool, and more preferably without further adjustments to the pressing tool, using only one - the same - pressing tool. Such a pressing tool is known, for example, from WO 2014/108361 A1 ( US 2015/0364889 A1 ). This pressing tool is electro-hydraulically operated and has a piston and a hydraulic cylinder, with a piston rod supporting the tool part being moved linearly via the piston. The part, or a pressed part, such as a sleeve or cable lug, is pressed with the part(s) received in a receiving opening, such as a conductor, between the tool part and a fixed jaw.

From the DE 103 18 508 A1 A pressing tool with, in the exemplary embodiment, two pivoting jaws, although only one may be provided, is known, wherein the pivoting jaw is pivotable about a pivot axis oriented transversely to a piston displacement direction. The pivoting jaw can be designed to support a tool part, for example, for carrying out a pressing process. Furthermore, such a pressing tool is known, for example, from WO 03/022480 A1 .

In addition, it is known that with each movement of the piston, the pressing process automatically stops when the same maximum Piston force is applied. This can, as is known, be achieved by an automatic valve opening when the maximum pressure is reached, after which, according to a further known embodiment, an automatic return displacement of the piston and the tool part controlled by it can be initiated. In this context, reference is made, for example, to the WO 99/19987 A1 ( US 6 276 186 B1 ).
From the US 2016/0363510 A1 A pressing tool according to the preamble of claim 1 is known, in which the piston force measured in the hydraulic piston is measured over time. The piston force correlates with the piston travel and the opening state of the swivel jaws. The highest piston force is reached at the end of the travel, when the swivel jaws are closed.

Summary of the invention

Based on the state of the art according to WO 03/022480 A1 The object of the invention is to provide a pressing tool which is advantageously designed with regard to carrying out a pressing process for parts with external dimensions which differ within a predetermined range.

This object is achieved in the subject matter of claim 1, in which the action surface is designed in such a way that a higher pressing force is effective in association with a larger opening width of the pivoting jaw when the maximum piston force is reached, and a lower pressing force is effective in association with each smaller opening width of the pivoting jaw when the maximum piston force is reached compared to the larger opening width.

According to the solution according to the invention, the maximum piston force, upon reaching which the pressing process is automatically terminated, This is achieved preferably in every (proper) pressing process when the required pressing force is achieved, regardless of the size of the part to be crimped or pressed, here for example the sleeve or the cable lug. The effective pressing force with an opening width of the swivel jaw that is smaller than the opening width associated with the highest pressing force is correspondingly always smaller than the highest pressing force. Thus, parts of different sizes, such as sleeves or cable lugs, with parts preferably arranged therein, such as electrical conductors, can be crimped using the same swivel jaw. Accordingly, different pressing forces can be applied to carry out the press connection without changing the pressing tool.

Adjusting the pressing force associated with the opening width of the swivel jaw can be easily achieved by a corresponding geometric design of the impact surface of the swivel jaw. The relevant relationships for this are described, for example, in the aforementioned WO 03/022480 A1 described.

Thus, the different pressing force is achieved by appropriately designing the impact surface, through which the piston acts on the pivoting jaw, preferably using a roller connected to the piston. According to the invention, the impact surface is designed as a curved path with reference to a plan view in which the axis of rotation of the roller acting on the impact surface is represented as a point. This curved path, upon linear movement of the piston and the roller connected to it, causes a degressive force transmission to the pivoting jaw and, via this, to the tool part.

The pressing force that can be exerted at a given opening width of the swivel jaw is directly dependent on the external dimensions of the part to be pressed, for example the sleeve or the cable lug.

The tool part can be designed as a mandrel oriented tangentially with respect to a pivoting circle, through whose center the pivot axis runs. Such a mandrel can pivot accordingly and can interact with the part to be pressed in a stamp-like manner. A fixed jaw can serve as the counter jaw, which is therefore not pivotable.

The mandrel is preferably designed so that it can be used to suitably crimp parts, particularly sleeves or cable lugs, with different external dimensions, taking into account the resulting different crimping forces. Thus, in a cross-section in which the pivoting circle is represented as a line, the mandrel can, for example, have a tapered geometry with a conical tip directed in the crimping direction.

In a further embodiment, the mandrel can be designed as a stepped mandrel and can thus have an outer contour that widens radially outwards in a step-like manner - relative to the pivoting circle - in accordance with the above-mentioned cross-section, starting from the conical tip of a stepped cone.

Furthermore, according to a possible embodiment, the mandrel can be circular in shape with reference to a floor plan in which the pivoting circle is represented as a point at least in the projected floor plan area of the mandrel, or alternatively polygonal, for example square, hexagonal or octagonal.

In a further embodiment, two pivoting jaws can be provided. These two pivoting jaws can be arranged to rotate about a common pivot axis, and more preferably, can be moved uniformly toward each other during the pressing process.

Each pivoting jaw can, as is also preferred, have an action surface via which the piston acts on the pivoting jaws in a pivoting manner using a roller with a cooperation surface.

In an arrangement of two swivel jaws, according to a preferred embodiment, only one swivel jaw can support the tool part, while the other swivel jaw has a receptacle, for example, a bowl-like receptacle for inserting the part to be pressed, thus forming a counter-support with respect to the swivel jaw provided with the tool part. The receptacle of one swivel jaw can, as preferred, be suitable for accommodating parts of different external dimensions within a predetermined range.

Each swivel jaw can also have a tool part. In such a configuration, both tool parts can be moved toward each other along the swivel circle during the pressing process, with the part to be pressed interposed. In this case, the tool part can be an integral component of the swivel jaw, as is generally possible, but alternatively, it can also be a part that can be assigned to the swivel jaw and attached to it, for example, a replacement part.

A tool part, in particular each of the tool parts when a tool part is arranged on each pivoting jaw, can have a plurality of ribs arranged one behind the other in the direction of the pivot axis. These ribs can be spaced apart from one another in the direction of the pivot axis. This can create spaces between two ribs into which the ribs of the other tool part can move during pressing. Accordingly, this creates a pair of tool parts whose ribs can move into each other like a comb during pressing.

This initially allows for favorable guidance of the tool parts to one another during the pressing process. Furthermore, the ribs, as is also preferred, can be used directly for pressing the part, for example, the sleeve or the cable lug, particularly the edges of the ribs pointing in the pivoting direction during the pressing process. This results in a corresponding pressing geometry of the part to be pressed.

The ribs of a tool part can be divided into first and second ribs, which are offset from one another in the direction of the pivot axis. The first and second ribs can be designed differently, particularly with respect to the front edge pointing in the pivot direction during the pressing process. These first and second ribs can also be designed essentially mirror-symmetrically to the pivot circle or to a tangential line to the pivot circle.

According to a preferred embodiment, first and second ribs alternate regularly one behind the other in the direction of the pivot axis.

The first ribs can form a first, essentially rectilinear edge of the press opening relative to a press opening remaining between the tool parts and appearing essentially rectangular in the direction of the pivot axis, and the second ribs can form a second edge extending essentially perpendicular to the first edge. With respect to a projection along the pivot axis into a plane perpendicular to the pivot axis, the course of the first and second edge edges of the two tool parts thus results in a press opening appearing rectangular, with edge edges of equal length in the region of the press opening. which edge length depends on the outer dimension of the pressed part.

The first and second edge edges can, as also preferred, each extend at an acute angle to the pivot circle or a tangent of the pivot circle, so that the press opening appears substantially diamond-shaped.

In one possible embodiment, both tool parts are designed identically, in particular with regard to the design and number of first and second ribs.

The tool part can also be movably mounted on the swivel jaw. This mobility can be limited to pivoting, with a pivot axis running parallel to the pivot axis of the swivel jaw. Alternatively or in combination with the pivoting capability, the tool part can also be rotatable about a rotation axis running perpendicular to the orientation of the pivot axis.

When two tool parts are arranged, both tool parts can be arranged to be movable, in particular pivotable, or alternatively only one of the tool parts.

The ranges or value ranges or multiple ranges specified above and below also include, with regard to the disclosure, all intermediate values, in particular in 1/10 steps of the respective dimension, and may therefore also be dimensionless. For example, the specification 28 to 35 kN also includes the disclosure of 28.1 to 35 kN, 28 to 34.9 kN, 28.1 to 34.9 kN, etc., the disclosure of 8 to 12 mm also includes the disclosure of 8.1 to 12 mm, 8 to 11.9 mm, 8.1 to 11.9 mm, etc. This disclosure can serve, on the one hand, to delimit a specified range limit from below and/or above, but alternatively or additionally to reveal one or more singular values from the respective specified range.

Short description of the drawings

.Fig. 1

ein Presswerkzeug in perspektivischer Darstellung, betreffend eine erste Ausführungsform, hierbei im Wesentlichen aufweisend ein Antriebsgeräteteil und einen Arbeitskopf mit Schwenkbacken;

Fig. 2

den Arbeitskopf gemäß Figur 1 in einer Einzeldarstellung;

Fig. 3

die Stirnansicht gegen den Arbeitskopf;

Fig. 4

die Seitenansicht gegen den Arbeitskopf, betreffend eine Grundstellung des Werkzeuges mit einer größten Öffnungsweite zwischen den Schwenkbacken;

Fig. 5

Presswerkzeug gemäß Figur 1 in einer Längsschnittdarstellung, jedoch eine Zwischenstellung im Zuge eines Verpressvorganges betreffend, bei einer Verpressung einer Hülse mit einer größeren Außenabmessung;

Fig. 6

eine Folgedarstellung zu Figur 5, die Stellung zum Ende des Verpressvorganges betreffend, bei Erreichen einer maximalen Kolbenkraft;

Fig. 7

eine im Wesentlichen der Figur 4 entsprechende Darstellung, bei einer bezüglich der Außenabmessung kleineren zu verpressenden Hülse;

Fig. 8

die Pressendstellung der Situation gemäß Figur 7;

Fig. 9

den Schnitt gemäß der Linie IX-IX in Figur 8;

Fig. 10

das Werkzeugteil der ersten Ausführungsform in einer perspektivischen Einzeldarstellung;

Fig. 11

den Schnitt gemäß der Linie XI-XI in Figur 10;

Fig. 12

den schematischen Kraftverlauf der Presskraft bei Erreichen der maximalen Kolbenkraft in Abhängigkeit zu einer Öffnungsweite der Schwenkbacken;

Fig. 13

eine der Figur 2 entsprechende perspektivische Darstellung des Arbeitskopfes, betreffend eine zweite Ausführungsform mit zwei kammartig ineinandergreifenden Werkzeugteilen;

Fig. 14

die Stirnansicht hierzu;

Fig. 15

den Arbeitskopf der zweiten Ausführungsform in Seitenansicht, betreffend eine Grundstellung mit größerer Öffnungsweite zwischen den Schwenkbacken;

Fig. 16

eine der Figur 15 entsprechende Darstellung, jedoch die Verpressstellung einer Hülse mit größerer Außenabmessung;

Fig. 17

eine der Figur 16 entsprechende Darstellung, jedoch bei einer Hülse mit kleinerer Außenabmessung;

Fig. 18

eine Längsschnittdarstellung durch den Arbeitskopf in einer Situation gemäß Figur 17;

Fig. 19

die Werkzeugteile der zweiten Ausführungsform in perspektivischer Einzeldarstellung;

Fig. 20

die Werkzeugteile in stirnseitiger Einzeldarstellung;

Fig. 21

den Schnitt gemäß der Linie XXI-XXI in Figur 20 durch die Werkzeugteile.

The invention is explained below with reference to the accompanying drawings, which, however, only represent exemplary embodiments. A part that is explained only with reference to one of the exemplary embodiments and is not replaced by another part in another embodiment due to the special feature highlighted therein is thus also described for this further embodiment as a possible part present at any rate. The drawing shows:

Fig. 1

a pressing tool in perspective view, relating to a first embodiment, essentially comprising a drive device part and a working head with pivoting jaws;

Fig. 2

the working head according to Figure 1 in a single representation;

Fig. 3

the frontal view against the working head;

Fig. 4

the side view towards the working head, concerning a basic position of the tool with the largest opening width between the swivel jaws;

Fig. 5

Press tool according to Figure 1 in a longitudinal section, but an intermediate position during a pressing process concerning the pressing of a sleeve with a larger external dimension;

Fig. 6

a follow-up to Figure 5 , concerning the position at the end of the pressing process, when a maximum piston force is reached;

Fig. 7

one essentially of the Figure 4 corresponding representation, for a sleeve to be pressed that is smaller in terms of external dimensions;

Fig. 8

the pressing position of the situation according to Figure 7 ;

Fig. 9

the section along the line IX-IX in Figure 8 ;

Fig. 10

the tool part of the first embodiment in a perspective individual view;

Fig. 11

the section along the line XI-XI in Figure 10 ;

Fig. 12

the schematic force curve of the pressing force when the maximum piston force is reached as a function of the opening width of the swivel jaws;

Fig. 13

one of the Figure 2 corresponding perspective view of the working head, relating to a second embodiment with two comb-like interlocking tool parts;

Fig. 14

the front view of this;

Fig. 15

the working head of the second embodiment in side view, relating to a basic position with a larger opening width between the swivel jaws;

Fig. 16

one of the Figure 15 corresponding representation, but the pressing position of a sleeve with larger outer dimensions;

Fig. 17

one of the Figure 16 corresponding representation, but with a sleeve with smaller outer dimensions;

Fig. 18

a longitudinal section through the working head in a situation according to Figure 17 ;

Fig. 19

the tool parts of the second embodiment in individual perspective view;

Fig. 20

the tool parts in individual frontal view;

Fig. 21

the section along the line XXI-XXI in Figure 20 through the tool parts.

Description of the embodiments

Shown and described is, firstly with reference to the representation in Figure 1 , an electro-hydraulically actuated pressing tool 1 in a rod-like design.

The pressing tool 1 initially and essentially comprises a drive unit part 2, which can simultaneously form a handle area 3. Such a drive unit part 2 is known, for example, from WO 2003/084719 A2 ( US 7 254 982 B2 ). The content of this WO document or US document is hereby incorporated in its entirety into the disclosure of the present invention, also for the purpose of incorporating features of this WO document or US document into the claims of the present invention.

A working head 4 is connected to the drive unit part 2 at a free end of the working device. This can be mounted replaceably on the pressing tool 1, preferably by a separation in the area of a hydraulic cylinder. Furthermore, as is also preferred, the working head 4 can be mounted so that it can rotate freely about a working head longitudinal axis x relative to the drive unit part 2 or the corresponding receptacle for the working head 4.

With reference, for example, to the representation in Figure 4 is the connection with the mentioned WO 2003/084719 A2 ( US 7 254 982 B2 ) can be seen, for example, with regard to a return valve 5, a tank 6, and a pump tappet 7. In this context, it can also be seen that a hydraulic pump 8 and an electric motor 9 for the hydraulic pump 8 can be provided in series. The electrical supply, in particular to the electric motor 9, but also to a control unit (not shown) and other electrical components in the pressing tool 1, is provided by the arrangement of an accumulator 10.

The grip area 3 is designed for the usual gripping of the pressing tool housing with one hand. For ergonomic reasons, an actuation button 11 is provided associated with the grip area 3.

In particular, the above-mentioned components return valve 5, tank 6, hydraulic pump 8 with pump tappet 7, electric motor 9, the control unit and other electrical components, as well as the actuation button 11, are preferably all parts of the drive unit part 2.

The working head 4 is provided with two pivoting jaws 12 and 13 that can pivot toward or away from each other. These jaws can pivot about a common geometric pivot axis y, which is transverse to the working head's longitudinal axis x.

The two pivoting jaws 12 and 13 form, on the one hand, the pressing jaw area 15 and 16 of a bearing eye 14 and, on the other hand, an action surface 18 in the form of a curved path 18 of the bearing eye 14 on a jaw leg 17.

The action surfaces 18 of both swivel jaws 12 and 13 are arranged facing each other.

The bearing lugs 14 of both swivel jaws 12 and 13 are aligned coaxially with each other and, in the assembled state, are penetrated by a bolt 19, for example, a locking bolt. This bolt 19 is held on both sides of the swivel jaws 12, 13 in receiving holes of a drive-head-side receiving neck 20.

The receiving neck 20 is fork-shaped in the usual way and has a bolt receptacle, preferably in the form of a through-hole, extending transversely to a longitudinal extension of the receiving neck 20 through the fork leg 21. The bolt 19 is held in this bolt receptacle.

The action surfaces 18 of the pivoting jaws 12 and 13 protrude into the area between the fork legs 21 of the receiving neck 20 and are acted upon during a pressing process by rollers 22 of the drive unit part 2, which rollers can preferably be displaced hydraulically in the direction of the action surfaces 18, which causes the pivoting jaws 12, 13 to spread in the area of the curved path 18 and, as a result, the pressing mouth 23 formed by the pressing jaw areas 15 and 16 to close.

A hydraulic piston 24 is provided in the working head 4 for pivoting the swivel jaws 12 and 13 in a press jaw closing direction. This piston can be displaced along the x-axis in a hydraulic cylinder 25 against the force of a return spring 26. The circumferential surface of each roller 22 forms a contact surface through which the piston 24 indirectly acts on the contact surfaces 18.

During operation of the pressing tool 1, upon corresponding actuation of the actuating button 11, hydraulic fluid is pumped via the pump tappet 7 via a hydraulic line 27 into the hydraulic cylinder 25 for the corresponding actuation of the piston end face facing the hydraulic fluid.

The hydraulic piston 24, which is displaced due to the hydraulic medium being applied against the force of the return spring 26, moves a carrier for the rollers 22, which is acted upon by the piston rod 28, linearly along the longitudinal axis x, whereby with increasing displacement path of the rollers 22, starting from a basic position according to Figure 4 the pressing mouth 23 is reduced in the direction of a closed position due to the force-transmitting interaction of rollers 22 and the curved action surfaces 18 of the pivoting jaws 12 and 13.

Upon reaching a preferably identical maximum piston force of, for example, approximately 25 to 35 kN, further, for example, approximately 32 kN, the pressing process is automatically terminated, preferably as a result of the return valve 5 being opened. Upon termination, if necessary the return valve 5 being opened, the hydraulic piston 24 and, via this, the rollers 22 can be returned to their basic position according to Figure 4 The swivel jaws 12 and 13 also swivel back to their home position, for example, through the arrangement of a corresponding return spring.

The pivoting jaws 12 and 13 are designed for pressing or crimping parts, here represented by a sleeve 30 in the form of a cable lug with ends of an electrical conductor 31 held in a receiving opening 49 of the sleeve 30.

For this purpose, one pivoting jaw 13 has a receptacle 32 in the pressing jaw area 16 in the form of a bowl-like recess, into which receptacle 32 the part to be pressed, here the sleeve 30, is inserted. The sleeve 30 can be fully or partially inserted into this receptacle 32, depending on the respective external dimensions, in particular depending on the initial diameter of the sleeve 30.

In the representations of the Figures 4 to 6 is a sleeve 30 with, compared to the embodiment in the Figures 7 to 9 larger initial diameter d shown lying in the press mouth 23.

The receptacle 32 is arranged in such a way that its longitudinal section according to Figure 4 The resulting lowest point lies on the swivel circle S, through whose center the swivel axis y runs.

Also on the swivel circle S, with reference to the longitudinal section, in the area of the other swivel jaw 12, the tip or tip section of a tool part 33 is located, assigned to the pressing jaw area 15 of the other swivel jaw. The tool part 33 is in the Figures 1 to 11 illustrated first embodiment is formed as a pointed cone-shaped mandrel 34, the longitudinal axis z of which runs substantially tangentially to the pivot circle S with reference to the longitudinal sectional view.

The mandrel 34 has the pointed conical tool head 35, which has a preferably round outline with respect to a plane transverse to the longitudinal axis z. A pin-like mounting projection 36 extends from a conical base along the longitudinal axis z. The tool part 33 is held in the pivoting jaw 12 by this projection, and can be replaced if necessary.

The tool head 35 projects into the area of the press jaw 23, further directed towards the holder 32.

In addition, the mandrel 34, in particular the tool head 35, is preferably designed as a stepped mandrel in the form of a stepped cone. As can be seen in particular from the illustrations in the Figures 10 and 11 As can be seen, with reference to a longitudinal section according to Figure 11 starting from the mandrel base, a gradual reduction of the tool head diameter down to the tool head tip 37.

During the crimping process of the sleeve 30, the tool part 33 and the receptacle 32 deform the sleeve 30 by adapting the sleeve wall to the contour created by the tool part 33 and the receptacle 32. The conductor ends held in the sleeve 33 are crimped to the sleeve wall.

As can be seen from the illustrations in the Figures 6 and 8 As can be seen, the pressing results in approximately L-shaped compacts with a convex surface facing the receptacle 32 and a concave surface facing the mandrel 34.

With increasing and, in the embodiments shown, uniform pivoting of both pivoting jaws 12, 13 in the direction of a pressing jaw closing direction, there is a reduction in the (relevant) opening width a between the pressing jaw areas 15 and 16 or along the pivoting circle S between the tool tip 37 and the base of the receptacle 32.

Due to the lever arm-like force transmission between the hydraulic piston 24 and the swivel jaws 12, 13, a high pressing force can occur in the pressing area between the tool part 33 and the holder 32, particularly at the moment of maximum piston force.

For sleeves 30 with a larger diameter, a larger opening width a is usually present at the moment of maximum piston force than for sleeves 33 with a smaller diameter (cf. Figures 6 and 8 ). Accordingly, larger sleeves 30 result in a smaller piston displacement path along the x-axis than smaller sleeves 30. The rollers 22 thus interact with the curved action surfaces 18 over different distances. The lever arm h between the pivot axis y and the contact point P of the interaction surface of the roller 22 on the action surface 18, which continuously shortens in this case, leads to a reduction in the force transmission.

As also from the Figure 12 shown curve of the pressing force F when the maximum piston force is reached and depending on the opening width a, when the maximum piston force is reached, a higher pressing force F results for larger opening widths a than for any smaller opening width a compared to this larger opening width a, at which a smaller pressing force F always acts on the compact compared to the higher pressing force F.

For example, with a (circular) initial cross-sectional dimension of the sleeve 33 of, for example, 120 mm ^2, at the moment of maximum piston force of, for example, approximately 28 to 35 kN, further, for example, approximately 32 kN, an opening width a of, for example, approximately 20 to 30 mm, further, for example, approximately 25 mm and a pressing force of, for example, approximately 55 to 65 kN, further, for example, approximately 60 kN can be set; with, for example, 50 mm ² , an opening width a of, for example, approximately 8 to 12 mm, further, for example, approximately 10 mm and a pressing force of, for example, approximately 36 to 40 kN, further, for example, approximately 38 kN and with, for example, 10 mm ² , an opening width a of, for example, approximately 3 to 4 mm, further, for example, approximately 3.5 mm and an associated pressing force F of, for example, approximately 38 to 35 kN, further, for example, approximately 32 kN can be set.

The above-described interaction of opening widths a and pressing force F also occurs in the Figures 13 to 21 shown second embodiment.

The pressing tool 1 in question is, first and foremost, identical to the first embodiment with regard to the drive and the basic arrangement and design of the pivoting jaws 12, 13, particularly in the area of their impact surfaces 18. In contrast to this first embodiment, each pivoting jaw 12 and 13 is assigned a tool part 33 and 38. These act as the pivoting jaws 12 and 13 move towards each other. Swivel jaws 12 and 13 together for pressing parts, for example a sleeve 30 and a conductor 31.

The tool parts 33 and 38 are essentially identical in shape, preferably each pivotably mounted in the pressing jaw area 15 and 16, respectively, about an axis u. This axis u extends parallel to the pivot axis y of the pivot jaws 12 and 13.

Each of the tool parts 33 and 38 of the second embodiment has a plurality of individually arranged first and second ribs 39, 40, which are provided in a successive arrangement in the direction of the pivot axis y or in the direction of the tool part-side pivot axis u.

The first and second ribs 39 and 40 of a tool part 33 and 38, respectively, are arranged alternately, whereby in this alternating arrangement they can directly abut on one or both sides of the ribs adjacent in the axial direction.

As shown in detail in the illustration in the Figures 19 to 21 As can be seen, when viewed in a plane transverse to the pivot axis u, the ribs 39 and 40 each have a triangular shape. As can be seen particularly from the sectional view in Figure 21 As can be seen, the ground plan design of a rib 39, 40 can be given as an isosceles-right-angled triangle, wherein the hypotenuse of a first rib 39 of this triangle can form a first edge 41 running at an acute angle to the pivot circle S or at an angle of approximately 45 degrees to a tangent T on the pivot circle S.

The relevant second edge 42 of the second rib 40 is shown with reference to a plan view or a sectional view according to Figure 21 opposite direction the first edge 41, accordingly runs in a projection along the axis u at least approximately at an angle of 90 degrees to the first edge 41.

The first and second ribs 39 and 40 are fastened on a common base 43, which base 43 receives a receiving bore 44 running in the axial direction for a pivot pin 45 held on the jaw side.

Viewed in the direction of movement of the tool parts 38 and 33, a guide projection 46 can be provided laterally on each tool part 33, 38, which guide projection 46 moves into a correspondingly adapted guide receptacle 47 of the other tool part 38, 33, whereby a secure guidance of the two tool parts 33 and 38 to one another is provided during a pressing process.

The first and second ribs 39 and 40 of both tool parts 33 and 38 move into each other like a comb, such that in one possible embodiment both in a completely open basic position as shown in Figure 15 as well as in any pressing-closed position according to the illustrations in the Figures 16 and 17 a press opening 48 is formed which appears essentially rectangular in the direction of the axis u or the pivot axis y. This opening is circumferentially limited by the first and second edge edges 41 and 42 of the first and second ribs 39 and 40 of the tool parts 33 and 38.

Due to the given pivoting mobility of the tool parts 33 and 38 about the axis u, a linear movement is also possible by pivoting the pressing jaw areas 15, 16 of the swivel jaws 12, 13 towards each other. The tool parts 33 and 38 or their first and second ribs 39 and 40 move into each other.

Also in this embodiment of the tool parts 33 and 38, in particular due to the given transmission ratio between the hydraulic piston 24 - via the rollers 22 - and the action surfaces 18 of the swivel jaws 12, 13, when the maximum piston force is reached at a larger opening width a - due to the pressing of a pressed part, such as a sleeve 30, with a larger outer dimension - a higher pressing force F acting on the pressed part or on the sleeve 30 is given (compare Figure 16 ), whereas for any opening width a smaller than this opening width a, as for example in Figure 17 As shown, due to a smaller external dimension of the compact or sleeve 30, when the maximum piston force is reached, a lower pressing force F is effective compared to the previously described higher pressing force F.

Claims (11)

1. A pressing tool (1) for performing a pressing operation for the press-fitting of parts, for example a sleeve (30) to an electrical conductor (31), wherein one part, for example the sleeve (30), can have different outer dimensions within a specified range, wherein the pressing tool (1) further has a tool part (33, 38) for acting on the part, for example the sleeve (30), and the tool part (33, 38) is part of a pivoting jaw (12, 13), wherein the pivoting jaw (12, 13) further has an action surface (18) and can be pivoted around a pivot axis (y) from a starting position having a greatest opening width (a) into a pressing position having a smaller opening width (a), wherein the pressing tool (1) further has a hydraulic piston (24) movable in a hydraulic cylinder (25), which applies a piston force depending on a hydraulic pressure in the hydraulic cylinder (25), wherein each time the hydraulic piston (24) is moved, the pressing operation automatically ends once a same maximum piston force has been reached, wherein the hydraulic piston (24) further has an interactive surface formed by a roller (22) connected with the hydraulic piston (24) for a force-transmitting interaction of the hydraulic piston (24) with the action surface (18), wherein the piston force can be converted into a deviating pressing force (F) due to a geometry of the action surface (18), characterized in that the action surface (18) is designed in such a way that a higher pressing force (F) is active as allocated to a larger opening width a of the pivoting jaw (12, 13) once the maximum piston force has been reached, and that a smaller pressing force (F) by comparison to the higher pressing force (F) is active as allocated to each smaller opening width (a) of the pivoting jaw (12, 13) by comparison to the larger opening width once the maximum piston force has been reached.
2. The pressing tool according to claim 1, characterized in that the tool part (33) is designed as a mandrel (34) directed tangentially relative to a pivot circle (S), through whose midpoint the pivot axis (y) runs.
3. The pressing tool according to claim 2, characterized in that the mandrel (34) is designed as a stepped mandrel.
4. The pressing tool according to one of the preceding claims, characterized in that two pivoting jaws (12, 13) are provided.
5. The pressing tool according to one of the preceding claims, characterized in that a receptacle (32) is formed on a pivoting jaw (13).
6. The pressing tool according to one of claims 4 or 5, characterized in that each pivoting jaw (12, 13) has a tool part (33, 38).
7. The pressing tool according to one of the preceding claims, characterized in that each of the tool parts (33, 38) has a plurality of ribs (39, 40) arranged one after the other in the direction of the pivot axis (y), and the ribs (39, 40) of the tool parts (33, 38) mesh into each other during a pressing operation.
8. The pressing tool according to claim 7, characterized in that the ribs (39, 40) of a tool part (33, 38) are divided into first (41) and second (42) ribs, which are staggered relative to each other in the direction of the pivot axis (y).
9. The pressing tool according to claim 8, characterized in that, in relation to a press opening (48) that remains between the tool parts (33, 38) and has an essentially rectangular appearance in the direction of the pivot axis (y), the first ribs (39) form a first, essentially straight peripheral edge (41) of the press opening (48), and the second ribs (40) form a second peripheral edge (42) running essentially perpendicular to the first peripheral edge (41).
10. The pressing tool according to one of the preceding claims, characterized in that the tool part (33, 38) is movably arranged on the pivoting jaw (12, 13).
11. The pressing tool according to claim 10, characterized in that the tool part (33, 38) is pivotably arranged on the pivoting jaw (12, 13).