EP4101592B1 - Dispositif de presse et système de presse - Google Patents

Dispositif de presse et système de presse Download PDF

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Publication number
EP4101592B1
EP4101592B1 EP21179007.6A EP21179007A EP4101592B1 EP 4101592 B1 EP4101592 B1 EP 4101592B1 EP 21179007 A EP21179007 A EP 21179007A EP 4101592 B1 EP4101592 B1 EP 4101592B1
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EP
European Patent Office
Prior art keywords
spindle
wheel
pressing
drive wheel
drive
Prior art date
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Active
Application number
EP21179007.6A
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German (de)
English (en)
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EP4101592A1 (fr
Inventor
Valentin STALDER
Roger Dejakum
Albert Loichinger
Peter Eichenberger
Raphael JUD
Rudolf Kamber
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Geberit International AG
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Geberit International AG
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Publication date
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Priority to EP21179007.6A priority Critical patent/EP4101592B1/fr
Publication of EP4101592A1 publication Critical patent/EP4101592A1/fr
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Publication of EP4101592B1 publication Critical patent/EP4101592B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses

Definitions

  • the present invention relates to a pressing device according to claim 1 and a pressing system according to claim 14.
  • press fittings When connecting drinking water pipes, press fittings are often used, which are pressed using a pressing tool.
  • Such pressing tools include a pressing device and a pressing tool, such as a pressing jaw or a pressing loop, which is interchangeably attached to the pressing device.
  • a pressing force can be applied to the pressing jaws and the press fitting is pressed with the pressing jaws.
  • a piston in the pressing device is extended with high force and acts on the pressing jaws.
  • such pressing devices are designed to be electro-hydraulic, with an oil pressure being built up using a pump, which then causes a force on the piston, which in turn acts on the pressing jaws.
  • the hydraulic mode of operation has various disadvantages. Very precise tolerances are required in terms of manufacturing technology, which makes production expensive. Handling the oil during initial filling and also during maintenance work is complex. The oil continues to diffuse over time, which leads to a loss of pressing force.
  • the DE 203 05 473 U1 proposes a hydraulic oil-free pressing device, with a planetary gear being provided between a pressing ram and a drive.
  • the use of such planetary gears is disadvantageous because the planetary gears are very complex and therefore prone to failure.
  • planetary gears are usually very voluminous, which makes them difficult to use in tight spaces.
  • a pressing device according to the preamble of claim 1 is out US 6,240,626 B1 known.
  • the invention is based on the object of providing a pressing device which overcomes the disadvantages of the prior art.
  • a pressing device comprises an electric motor with an output shaft, a gear driven by the output shaft, a spindle driven by the gear, which defines a central axis, a press piston driven by the spindle, and a tool holder for receiving a pressing tool.
  • the gear has a first gear part acting on the spindle and a second gear part acting on the spindle.
  • the first gear part has a first drive wheel and spindle wheel, the spindle being mounted in the spindle wheel in a rotationally fixed and longitudinally displaceable manner.
  • the spindle wheel is rotatable with respect to a rotation about the central axis and fixed with respect to a movement along the central axis, i.e. stored immovably.
  • the second gear part has a second drive wheel and a spindle nut driven by the second drive wheel.
  • the spindle nut is rotatable with respect to a rotation about the central axis and fixed with respect to a movement along the central axis, i.e. stored immovably.
  • the spindle wheel and the spindle nut are set in rotation, such that the spindle experiences an axial feed with respect to the spindle wheel and with respect to the spindle nut, with this axial feed of the spindle of the press piston experiencing a feed movement in the direction of the tool holder, so that a pressing movement can be carried out by the pressing piston.
  • the spindle is moved in the axial direction relative to the spindle wheel and the spindle nut as well as to the two drive wheels.
  • the spindle is moved forward from a starting position in the direction of the central axis moved to an end position.
  • the movement from the end position to the starting position is carried out by driving the electric motor in reverse.
  • a freewheel which is arranged so that only the spindle nut rotates relative to the spindle or the spindle rotates relative to the spindle nut.
  • the outer diameter of the spindle essentially defines the buckling resistance of the spindle.
  • the outside diameter of the spindle has only a very small influence on the compactness of the pressing device.
  • a pressing device can therefore be specified which can apply large forces as long as it is compact.
  • the first drive wheel and the second drive wheel are arranged on a common drive shaft. This has the advantage of a simple design because only one drive shaft has to be driven by the output shaft of the electric motor.
  • the output shaft of the electric motor acts indirectly on the drive shaft via a drive gear.
  • a translation or reduction stage can be provided in the drive housing.
  • the output shaft of the electric motor acts directly on the drive shaft, which can simplify the mechanical design.
  • the drive shaft can also be provided by the output shaft from the electric motor.
  • the first drive wheel and the spindle wheel each have teeth, with the teeth of the first drive wheel engaging in the teeth of the spindle wheel.
  • the second drive wheel and the spindle wheel each have teeth, with the teeth of the second drive wheel engaging in the teeth of the spindle wheel.
  • Designing the elements mentioned as gear wheels has the advantage that large forces can be transmitted efficiently.
  • the teeth are preferably external teeth.
  • the teeth can be of any design, especially with regard to the number and shape of the teeth.
  • the distance between the first drive wheel and the second drive wheel is fixed.
  • the distance between the spindle wheel and the spindle nut is also fixed.
  • the spindle wheel and the spindle nut are set in rotation.
  • the translations between the first drive wheel and the spindle wheel and between the second drive wheel and the spindle nut are such that the spindle nut rotates at a lower speed than the spindle, so that said propulsion can be provided, and that preferably a larger torque is provided via the spindle nut can be provided on the spindle than via the spindle wheel.
  • the transmission ratio between the first drive wheel and the spindle wheel is smaller than the transmission ratio between the second drive wheel and the spindle nut.
  • the gear ratio between the first drive wheel and the spindle wheel is between 1:2 and 1:10, in particular 1:5.13.
  • the gear ratio between the second drive wheel and the spindle nut is between 1% and 50%, in particular 9%, higher than between the first drive wheel and the spindle wheel.
  • the overall gear ratio of the gearbox is preferably between 1:20 and 1:200, especially at 1:65.
  • the speed of the drive shaft and thus of the first drive wheel and the second drive wheel is in the range from 500 revolutions per minute to 15,000 revolutions per minute, in particular in the range from 1,500 revolutions per minute to 5,000 revolutions per minute.
  • the difference in speed between the spindle and the spindle nut is preferably in the range from 60 to 3,000 revolutions per minute.
  • the spindle and the spindle nut preferably rotate in the same direction of rotation.
  • the pressing device further has a support structure, wherein the first drive wheel and the spindle wheel are rotatably mounted at one bearing point of the support structure, and the second drive wheel and the spindle nut are rotatably mounted at another bearing point in the support structure.
  • the two bearing points are at a fixed distance from one another and are preferably firmly connected to one another.
  • the drive wheels, the spindle wheel and the spindle nut are mounted on the bearing point via roller bearings, the bearing point having correspondingly designed receptacles.
  • the electric motor and/or the drive shaft of the drive gear is also mounted on the support structure.
  • the tool holder is preferably also mounted on the support structure.
  • the rotationally fixed and longitudinally displaceable connection between the spindle wheel and the spindle is provided by a splined shaft connection, in particular by a multi-splined shaft connection.
  • a mechanically simple storage can be provided, which can well fulfill the two functions of being rotationally fixed and longitudinally displaceable.
  • the spindle is preferably connected to the press piston via an axial bearing.
  • the pressing piston is mounted in a longitudinal guide in the direction of the central axis of the spindle, but is mounted on the tool holder in a rotationally fixed manner.
  • the first drive wheel and the second drive wheel are axially offset from the central axis of the spindle.
  • the elements of the two gear parts are therefore located next to the spindle.
  • the pitch of the spindle is in the range from 1.5 to 10, in particular from 5 to 7, millimeters and / or that the spindle and the spindle nut are designed as a ball screw.
  • the diameter of the spindle is in the range from 10 to 30 millimeters, in particular from 18 to 22 millimeters.
  • the spindle can also be designed as a spindle with a metric thread or as a spindle with a trapezoidal thread.
  • the pitch of the metric thread or the trapezoidal thread is in the range of 1.5 to 10 millimeters.
  • the power of the motor is in the range of 200 to 1500 watts.
  • the motor's torque is in the range of 0.5 to 4.5 Newton meters.
  • the pressing piston preferably has a pair of rollers on the front, which can be moved against a pressing tool fastened in the tool holder.
  • the pressing force provided by the pressing piston is applied to the pressing tool via the pair of rollers.
  • the information given here regarding the parameters can also be made larger or smaller when scaling the pressing device.
  • a pressing system includes a pressing device as described above and a pressing tool inserted into the tool holder, such as a pressing jaw or a pressing loop.
  • the pressing device 1 comprises an electric motor 2 with an output shaft 3, a gear 4 driven by the output shaft 3, a spindle 5 driven by the gear 4, which defines a central axis M, a press piston 6 driven by the spindle 5, and a tool holder 7 Recording a pressing tool.
  • the pressing device further comprises a drive gear 11, which is arranged between the output shaft 3 and the gear 4.
  • the pressing tool is, for example, a pressing jaw or pressing tongs, a pressing sling or another pressing tool. A fitting of a pipe connection can be pressed using the pressing tool.
  • the pressing device 1 and the pressing tool not shown in the figures, form a pressing system.
  • the electric motor 2 acts on the transmission 4 with its output shaft 3.
  • the drive gear mentioned is arranged between the gear 4.
  • a gear 11a of the drive gear 11 is arranged on the output shaft 3 of the electric motor 2.
  • the gear 11a acts on a gear 10a of a drive shaft 10 of the transmission 4.
  • the output shaft 3 is connected to the rotor shaft of the electric motor via a shaft coupling 25.
  • the output shaft 3 can also be provided directly by the rotor shaft.
  • the tool holder 7 has a mouth-like receiving section 16 and a bearing opening 17 in which the press piston 6 is mounted.
  • the pressing tool is stored in the mouth-like receiving section 16.
  • Various pressing tools can be used in the receiving section 16.
  • the transmission 4 has a first transmission part 8 and a second transmission part 9. Both the first gear part 8 and the second gear part 9 act on the spindle.
  • the first gear part 8 has a first drive wheel 8a and a spindle wheel 8b.
  • the second gear part 9 has a second drive wheel 9a and a spindle nut 9b.
  • the two drive wheels 8a, 9a are mounted on the drive shaft 10, which, as described above, is driven directly or indirectly by the electric motor 2 via the drive gear 11.
  • a support structure 12 is present in which the individual parts are stored.
  • the support structure 12 according to the present embodiment essentially comprises a first bearing point 13 and a second bearing point 14.
  • the two bearing points 13, 14 are firmly connected to one another. For example, via a housing or a similar structure.
  • the first bearing point 13 provides storage for the drive gear 11 and the electric motor 2.
  • the first bearing point also provides storage for the drive shaft 10 and the spindle wheel 8b.
  • the first storage point 13 has corresponding storage openings for storing the elements mentioned, in which the elements mentioned are stored.
  • the spindle wheel 8b is rotatable, but axially immovable, mounted in the corresponding bearing opening.
  • the second bearing point 14 provides storage for the drive shaft 10 and the spindle nut 9b.
  • the drive shaft 10 is mounted on the first bearing point 13 and the second bearing point 14.
  • the second storage point 14 has corresponding storage openings for storing the elements mentioned, in which the elements mentioned are stored.
  • the spindle nut 9b is rotatable, but axially immovable, stored in the corresponding bearing opening.
  • the tool holder 7 is also firmly connected to the support structure.
  • the spindle 5 is mounted with a spindle end 18 in a rotationally fixed and longitudinally displaceable manner in the spindle wheel 8b.
  • the storage is such that a rotational movement acting on the spindle wheel 8b can be transferred to the spindle 5, the spindle 5 being set in rotation, and that the spindle 5 is displaceable in the directions of its central axis M relative to the spindle wheel 8b. This shift is the result of the action of the second Gear part 9, as will be described below.
  • the spindle 5 is connected to the spindle wheel 8b via a splined shaft connection 19.
  • Other types of connection are also conceivable.
  • the spindle nut 9b engages in the external thread 20 on the spindle 5.
  • the spindle nut has an internal thread 21.
  • the spindle nut 9b is rotated about the central axis M of the spindle 5 via the second drive wheel 9a.
  • the speed of the spindle nut 9b is smaller than the speed of the spindle wheel 8b. This means that the spindle 5 rotates faster than the spindle nut 9b.
  • This provides spindle propulsion and this spindle propulsion can also be used to apply the pressure force to the press block 6.
  • the spindle nut 9b is rotatable with respect to rotation about the central axis M and fixed with respect to movement along the central axis M.
  • the spindle nut 9b is firmly mounted with respect to axial movement.
  • the two drive wheels 8a, 9a rotate.
  • the drive wheel 8a drives the spindle wheel 8b and the drive wheel 9a drives the spindle nut 9b.
  • the translations between the first drive wheel 8a and the spindle wheel 8b and between the second drive wheel 9a and the spindle nut 9b are such that the spindle nut 9b rotates at a lower speed than the spindle 5, so that said propulsion can be provided, and that via the Spindle nut 9b a greater torque can be provided to the spindle 5 than via the spindle wheel 8b.
  • the speed difference between the spindle wheel 8b and the spindle nut 9b forms the speed relevant for the spindle feed. In other words, the spindle wheel 8b rotates at a higher speed than the spindle nut 9b.
  • the transmission ratio between the first drive wheel 8a and the spindle wheel 8b is between 1:2 and 1:10, in particular at 1:5.13, and the transmission ratio between the second drive wheel 9a and the spindle nut 9b is between 1% and 50%, in particular around 9%, higher than between the first drive wheel and the spindle wheel.
  • the overall transmission ratio of the gearbox 4 is preferably between 1:20 and 1:200, in particular 1:65.
  • the Figure 4a shows a sectional view through the section line BB Figure 3 .
  • the output shaft 3 of the electric motor 2 engages in the gear 10a of the drive shaft 10.
  • the Figure 4b shows a sectional view through the section line CC Figure 3 .
  • the first drive wheel 8a engages with the spindle wheel 8b.
  • the Figure 4c shows a sectional view through the section line DD of the Figure 3 .
  • the second drive wheel 9a engages in the spindle nut 9b.
  • the first drive wheel 8a and the spindle wheel 8b each have teeth, the teeth of the first drive wheel 8a engaging in the teeth of the spindle wheel 8b.
  • the second drive wheel 9a and the spindle nut 9b each have teeth, the teeth of the second drive wheel 9a engaging in the teeth of the spindle wheel 9b.
  • the toothing is an integral part of the spindle wheel 8b.
  • the teeth are designed separately from the actual nut and are connected to the nut with a wedge connection 26. Integral training would also be conceivable.
  • an axial bearing 15 is arranged, which acts on the press piston 6.
  • the spindle 5 has a shoulder-shaped receptacle 22 on which the axial bearing 15 rests.
  • the press piston also has a receptacle 23, which also serves to accommodate the axial bearing.
  • the pressing piston 6 here also has a pair of rollers 24, which acts on the pressing tool.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Claims (15)

  1. Dispositif de sertissage (1) comprenant
    un moteur électrique (2) avec un arbre d'entraînement (3),
    un engrenage (4) entraînée par l'arbre d'entraînement (3),
    une broche (5) entraînée par l'engrenage (4), la broche (5) définissant un axe central (M),
    un piston de sertissage (6) entraîné par la broche (5), et
    un porte-outil (7) pour contenir un outil de sertissage,
    l'engrenage (4) comportant une première pièce d'engrenage (8) agissant sur la broche (5),
    la première pièce d'engrenage (8) comportant une première roue motrice (8a) et une roue de broche (8b), la broche (5) étant montée de manière à être solidaire en rotation et déplaçable longitudinalement dans la roue de broche (8b), la roue de broche (8b) étant rotative par rapport à une rotation autour de l'axe central (M) et fixée par rapport à un mouvement le long de l'axe central (M),
    caractérisé en ce que l'engrenage (4) comporte une deuxième pièce d'engrenage (9) agissant sur la broche (5),
    la deuxième partie de l'engrenage (9) comportant une deuxième roue motrice (9a) et un écrou de broche (9b) entraîné par la deuxième roue motrice (9a), l'écrou de broche (9b) étant rotatif par rapport à une rotation autour de l'axe central (M) et fixé par rapport à un mouvement le long de l'axe central (M), et
    lorsque les deux roues motrices (8a, 9a) tournent, la roue de broche (8b) et l'écrou de broche (9b) sont mis en mouvement de rotation de telle sorte que la broche (5) subisse une avance axiale par rapport à la roue de broche (8b) et par rapport à l'écrou de broche (9b), le piston de sertissage (6) subissant un mouvement d'avance dans en direction du porte-outil (7) lors de cette avance axiale de la broche (5).
  2. Dispositif de sertissage (1) selon la revendication 1, caractérisé en ce que la première roue motrice (8a) et la seconde roue motrice (9a) sont disposées sur un arbre d'entraînement commun (10).
  3. Dispositif de sertissage (1) selon la revendication 2, caractérisé en ce que l'arbre de sortie (3) du moteur électrique (2) agit indirectement sur l'arbre d'entraînement (10) via un engrenage d'entraînement (11) ; ou que l'arbre d'entraînement (3) du moteur électrique (2) agit directement sur l'arbre d'entraînement (10).
  4. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la première roue motrice (8a) et la roue de broche (8b) ont chacune une denture, la denture de la première roue motrice (8a) s'engrenant dans la denture de la roue de broche (8b); et/ou en ce que la deuxième roue motrice (9a) et la roue de broche (9b) ont chacune une denture, la denture de la deuxième roue motrice (9a) s'engrenant dans la denture de la roue de broche.
  5. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les rapports de transmission entre la première roue motrice (8a) et la roue de broche (8b) et entre la deuxième roue motrice (9a) et l'écrou de broche (9b) sont tels :
    que l'écrou de broche (9b) tourne à une vitesse inférieure à celle de la broche (5) de manière à assurer ladite avance,
    et qu'un moment plus grand peut être fourni à la broche (5) par l'intermédiaire de l'écrou de broche (9b) que par la roue de broche (8b).
  6. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le rapport de transmission entre la première roue motrice (8a) et la roue de broche (8b) est inférieur au rapport de transmission entre la deuxième roue motrice (8b) et l'écrou de broche (9b).
  7. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le rapport de transmission entre la première roue motrice (8a) et la roue de broche (8b) est compris entre 1:2 et 1:10, en particulier est de 1:5.13, et que le rapport de transmission entre la deuxième roue motrice (9a) et l'écrou de broche (9b) est supérieur de 1 % à 50 %, en particulier de 9 %, à celui entre la première roue motrice et la roue de broche.
  8. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de sertissage (1) comporte une structure de support (12), dans laquelle à un endroit de palier (13) de la structure de support (12), la première roue motrice (8a) et la roue de broche (8b) sont montées de manière rotative, et dans laquelle à un autre endroit de palier (14) dans la structure de support (12) la deuxième roue motrice (9a) et l'écrou de broche (9b) sont montés de manière rotative.
  9. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la connexion solidaire en rotation et déplaçable longitudinalement entre la roue de broche (8b) et la broche (5) est assurée par une connexion d'arbre cannelé, en particulier par une connexion d'arbre multi-cannelures, ou par une connexion d'arbre polygonal.
  10. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la broche (5) est reliée au piston de sertissage (6) par un palier de butée (15).
  11. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la première roue motrice (8a) et la seconde roue motrice (9a) sont décalées axialement par rapport à l'axe central (M) de la broche (5).
  12. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le pas de la broche est compris entre 1.5 et 10, en particulier entre 5 et 7, millimètres et/ou que la broche et l'écrou de broche sont conçus comme des vis à billes.
  13. Dispositif de sertissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le piston de sertissage (6) comporte à l'avant une paire de rouleaux (16), qui peut être déplacé contre un outil de sertissage fixé au porte-outil (7).
  14. Système de sertissage comprenant un dispositif de sertissage (1) selon l'une quelconque des revendications précédentes et un outil de sertissage inséré dans le porte-outil (7).
  15. Système de sertissage selon la revendication 14, caractérisé en ce que l'outil de sertissage est une mâchoire de sertissage ou une chaîne de sertissage.
EP21179007.6A 2021-06-11 2021-06-11 Dispositif de presse et système de presse Active EP4101592B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21179007.6A EP4101592B1 (fr) 2021-06-11 2021-06-11 Dispositif de presse et système de presse

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Application Number Priority Date Filing Date Title
EP21179007.6A EP4101592B1 (fr) 2021-06-11 2021-06-11 Dispositif de presse et système de presse

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EP4101592A1 EP4101592A1 (fr) 2022-12-14
EP4101592B1 true EP4101592B1 (fr) 2023-11-29

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Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6240626B1 (en) * 1997-02-21 2001-06-05 Novopress Gmbh Pressen Und Presswerkzauge & Co. Kg Pressing device
DE29919604U1 (de) * 1999-11-09 2000-01-05 Forschungszentrum Karlsruhe GmbH, 76133 Karlsruhe Vorschubgetriebe zum gleichzeitigen Antrieb und Vorschub einer Spindel
DE20305473U1 (de) 2003-04-03 2003-06-12 Novopress GmbH Pressen und Presswerkzeuge & Co. KG, 41460 Neuss Handgeführtes Preßgerät

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