EP4084932B1 - Compresseur de ressort - Google Patents

Compresseur de ressort Download PDF

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Publication number
EP4084932B1
EP4084932B1 EP21765832.7A EP21765832A EP4084932B1 EP 4084932 B1 EP4084932 B1 EP 4084932B1 EP 21765832 A EP21765832 A EP 21765832A EP 4084932 B1 EP4084932 B1 EP 4084932B1
Authority
EP
European Patent Office
Prior art keywords
contact surface
projections
dome
pockets
shaped contact
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
EP21765832.7A
Other languages
German (de)
English (en)
Other versions
EP4084932A1 (fr
Inventor
Martin Stark
Thomas BRAKHAGE
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.)
Hazet Werk Hermann Zerver GmbH and Co KG
Original Assignee
Hazet Werk Hermann Zerver GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hazet Werk Hermann Zerver GmbH and Co KG filed Critical Hazet Werk Hermann Zerver GmbH and Co KG
Publication of EP4084932A1 publication Critical patent/EP4084932A1/fr
Application granted granted Critical
Publication of EP4084932B1 publication Critical patent/EP4084932B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25B27/14—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for assembling objects other than by press fit or detaching same
    • B25B27/30—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for assembling objects other than by press fit or detaching same positioning or withdrawing springs, e.g. coil or leaf springs
    • B25B27/302—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for assembling objects other than by press fit or detaching same positioning or withdrawing springs, e.g. coil or leaf springs coil springs other than torsion coil springs
    • B25B27/304—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for assembling objects other than by press fit or detaching same positioning or withdrawing springs, e.g. coil or leaf springs coil springs other than torsion coil springs by compressing coil springs

Definitions

  • the invention relates to a spring tensioner according to the features of patent claim 1.
  • the EP 1 591 207 B1 discloses an internal tensioner for tensioning a helical compression spring according to the preamble of claim 1, which has a tensioning drive with a threaded spindle and two clamping plates which are inserted between the turns of the helical compression spring to be tensioned.
  • the clamping plates have contact surfaces adapted to the helical compression spring.
  • One of the two clamping plates has an opening on the edge so that the threaded spindle can reach into the clamping plate from the side.
  • the other clamping plate has a central opening with a contact surface for a pressure piece.
  • the pressure piece has a spherical cap-shaped surface, so that a certain angle between the pressure piece and the clamping plate is possible.
  • helical compression springs In the installed position with a fully sprung chassis, helical compression springs generally do not have a straight course, but are slightly curved. As a result, the coils of the springs do not run parallel to one another, with the result that the clamping plates are not initially parallel to one another when clamping.
  • the spherical cap shape ensures a certain level of balance in the area of the two clamping plates.
  • the EP 1 905 545 B1 also discloses a spring tensioner for helical compression springs, with a spherical section-shaped receptacle for a pressure piece on an outside of a clamping plate.
  • the clamping plate has a ring of depressions and projections.
  • Two radially projecting abutment bodies are provided on the pressure piece to engage in the recesses.
  • the anti-twist device requires additional axial and radial installation space.
  • the invention is based on the object of providing a spring tensioner which allows a limited pivoting of the clamping plate relative to the internally arranged clamping device and at the same time allows the use of a pressure piece that is as compact as possible and has a short length.
  • the spring tensioner comprises a tensioning device which can be inserted axially into a coil spring to be tensioned.
  • the spring compressor includes a first and a second clamping plate.
  • the clamping plates can be coupled to the clamping device at a distance from each other.
  • the clamping device has a drive end, with the second clamping plate being arranged adjacent to the drive end.
  • the second clamping plate has an opening to accommodate the clamping device.
  • the clamping device also has a pressure piece which can be moved along the clamping device under the influence of an actuator in order to adjust the distance between the clamping plates.
  • the pressure piece presses axially on the second clamping plate. The force is transmitted via a dome-shaped contact surface between the pressure piece and the clamping plate.
  • the anti-twist device has projections and pockets to accommodate the projections.
  • the projections and the pockets are located in the dome-shaped contact surface itself and interrupt it in the circumferential direction, so that the dome-shaped contact surface is composed of several separate dome-shaped contact surface areas.
  • the dome-shaped contact surface areas are overall larger in the circumferential direction than the circumferential area in which the projections and the pockets are arranged.
  • the axial length of the pressure piece can be reduced. Only a very limited range of lengths is required to fulfill multiple functions at the same time.
  • the first function is the transmission of force from the pressure piece to the second clamping plate via the dome-shaped contact surface areas. There is no force transmission via the pockets and projections, but only via the dome-shaped contact surface areas or, in total, the only dome-shaped contact surface.
  • the second function is anti-twist protection.
  • the pockets are arranged either in the pressure piece or in the second clamping plate. Both the pockets and the projections are so large that the dome-shaped contact surface areas are completely separated from one another.
  • the axial length of the dome-shaped contact surface is fully used to prevent rotation, in that the projections and pockets not only adjoin the dome-colored contact surface areas in the axial direction, but completely penetrate them in the axial direction.
  • the anti-twist device can have relatively small dimensions because no compressive forces are transmitted in the axial direction via the anti-twist device.
  • dome-shaped contact surface areas are not individual line contacts, but that the dome-shaped contact surface areas are circumferential areas that extend over several degrees within a single axial plane, so that the contact between the The pressure piece and the clamping plate are as full-surface as possible, which in turn contributes to uniform force transmission and the avoidance of stress peaks in the components.
  • the third function that is fulfilled in the area of the contact surfaces is the compensation function of the angular positions between the pressure piece and the clamping plate.
  • the clamping plates are preferably forged components, while the pressure piece is manufactured as a turned or milled component. Depressions distributed over the circumference of the pressure piece are easier to introduce than projections, since this would require a larger amount of material to be removed adjacent to the projections.
  • the pockets are deeper than the projections are high.
  • the projections reach into the pockets.
  • the corresponding information on depth and height should be understood to mean that when the pressure piece and the second clamping plate are axially aligned, a gap remains between the surfaces of the pockets and the projections.
  • the gap between the pockets and the projections is significantly larger than is required for pure mountability.
  • the play also exists laterally, i.e. radially, so that a radial pivoting of the pressure piece relative to the clamping plate is possible.
  • the play resulting from the gap also exists in the axial direction of the clamping device, so that the clamping plate can be angled to a limited extent relative to the pressure piece by moving along the dome-shaped contact surface without contact between the projections and pockets. Angling is only possible to a limited extent.
  • the opening in the second clamping plate has a diameter that increases with increasing distance from the dome-shaped contact surface.
  • the diameter is in particular conically expanded, for example with an opening angle of 10°-15°. This means that the clamping plate can be pivoted by 5°-7.5° in any direction. So that there is no contact between a spindle of the clamping device and the clamping plate when the clamping plate is pivoted, the pressure piece can have a shaft which passes through the opening over its entire length. The shaft encloses the spindle of the clamping device.
  • the size and shape of a gap between the shaft and the opening determines how far the clamping plate can be angled.
  • the first clamping plate at the other end of the clamping device can also be coupled to the clamping device in an axially pivotable manner.
  • An abutment with a spherical cap-shaped contact surface can be arranged on the spindle or spherical cap-shaped contact surface areas can be formed, combined with an anti-twist device to prevent the clamping plate from rotating relative to the spindle.
  • the individual contact surface areas on the pressure piece and on the second clamping plate are part of the one and only spherical cap-shaped contact surface. So they are not different, especially smaller spherical cap-shaped areas, with each spherical cap-shaped contact surface having a different center in the sense of different bowl-shaped depressions.
  • the spherical cap-shaped contact surfaces preferably extend over an angular range of at least 15° each.
  • the angular range refers to the circumferential direction around the longitudinal axis of the clamping device.
  • the individual contact surface areas extend over 20°-40° with 6 contact surface areas.
  • the number of contact surface areas, or pockets and depressions, is preferably between 2 and 12, in particular between 4 and 12, particularly preferably 6 pockets are provided.
  • the spherical cap-shaped contact areas between the projections do not necessarily have to be identical in size to the spherical cap-shaped contact surfaces between the pockets.
  • the spherical cap-shaped contact surface areas between the projections are larger than the spherical cap-shaped contact surface areas between the pockets.
  • the pockets are slightly wider than the projections, which is at the expense of the spherical cap-shaped contact surface areas. In total, however, they are Contact surface areas larger than the areas not designed as contact surfaces that are occupied by the pockets and projections.
  • the spherical cap-shaped contact surface areas can be of the same length in the axial direction or to extend over an equally large angular range in the axial direction of the clamping device or the pressure body.
  • the contact surface area on the clamping plate can have a shorter axial length than the contact surface area on the pressure body.
  • the pressure body acts as an inner part (sphere) and the clamping plate acts as an outer part (spherical shell).
  • the clamping plate slides on the inner pressure body, so that the inner pressure body is in contact with the clamping plate in different axial sections, depending on the angular position.
  • the pressure body as a smaller component and as a rotating component is easier to process in terms of surfaces. Larger spherical cap-shaped contact surface areas can be produced more easily here.
  • the spring tensioner according to the invention has a multifunctional area on the pressure piece, whereby the pressure piece can be significantly shorter, more compact and also simpler. It is also more cost-effective to manufacture and fulfills the same functions as more complex designs that have separate functional areas.
  • the Figures 1 and 2 show a side view and a longitudinal section of a spring tensioner 1 which is inserted into a helical compression spring 2.
  • the spring tensioner 1 comprises a tensioning device 3 and a first and second tensioning plates 4, 5.
  • the first tensioning plate 4 has an opening 6 that is open to the circumferential side for the engagement of the tensioning device 3.
  • the lower tensioning plate 5 has a central opening 7 into which the tensioning device 3 is used.
  • the clamping plates 4, 5 each have mutually facing contact surfaces 8, 9 for the turns of the helical compression spring 2.
  • On the outer surfaces of the clamping plates 4, 5 opposite the contact surfaces 8, 9, the tensioning device 3 has devices to exert pressure on the clamping plates 4, 5, to tension the helical compression spring 2.
  • a pressure piece 10 is used for this purpose, which is in Figure 3 is shown in cross section in an enlarged view.
  • the pressure piece 10 can be moved in the longitudinal direction on a threaded spindle 11 of the clamping device 3.
  • a clamping nut 12 as an actuator is in engagement with the threaded spindle 11.
  • the pressure piece 10 is supported on the clamping nut 12 via an axial bearing 13 on the clamping nut 12.
  • the pressure piece 10 is displaced axially.
  • the pressure piece 10 does not rotate. It is guided via a backdrop guide 14.
  • the shaft 17 passes through the opening 7 over its entire axial length.
  • the pressure piece 10 is held captively on the threaded spindle 11 via a stop 18 in the groove 15.
  • the Figures 4 to 7 show the pressure piece 10 in different representations and Figures 8 to 12 the second clamping plates 5.
  • the pressure piece 10 serves to transmit a compressive force to the second clamping plate 5.
  • the compressive force is transmitted via a spherical cap-shaped contact surface 19, the geometric position of which is in Figure 11 is shown.
  • the Figure 11 shows a section through the second clamping plate 5 along the line XI-XI in Figure 10 .
  • the Figure 11 shows the section plane in the image plane on the left and detail A in an enlarged view in the image plane on the right.
  • the spherical cap-shaped contact surface 19 in the area of the second clamping plate 5 borders on the funnel-shaped opening 7.
  • the Figure 11 shows that the diameter D1 of the opening 7 in the second clamping plate 5 increases continuously in the direction of the contact surface 9.
  • the contact surface 19 is completely interrupted several times. There are a total of six projections 20, evenly distributed over the circumference, in the contact surface 19, which rise radially inwards beyond the spherical cap-shaped contact surface 19. As a result, the contact surface 19 is divided into individual, equal-sized contact surface areas 21.
  • the Figure 10 shows the size ratio of the contact surface areas 21 to the projections 20.
  • the projections 20 are significantly narrower or extend over a smaller circumferential area than the contact surface areas 21. Overall, the remaining contact area 19 is therefore larger than the area occupied by the projections 20.
  • the arrangement of the projections 20 corresponds to pockets 22 in the pressure piece 10.
  • the Figures 4 to 7 show the pressure piece 10 with the said pockets 22.
  • the pressure piece 10 also has a spherical cap-shaped contact surface 23, which is connected to the contact surface 21 of the Figure 11 corresponds.
  • the in Figure 11 The circle 25 shown defines the position of the spherical cap-shaped contact surface 19. If the pressure piece 10 and the second clamping plate 5 are exactly axially aligned, the in Figure 11
  • the center 26 of the circle 25 shown is also in the center of the contact surface 23 of a pressure piece 10 arranged there.
  • the circle 25 is of course only the cross section through the spherical cap-shaped surface.
  • the Figure 4 shows that the contact surface 23 is divided by the pockets 22 into separately arranged contact surface areas 24. Unlike the contact surface areas 21 in the clamping plate 5, the contact surface areas 24 in the pressure piece 10 are somewhat shorter when viewed in the circumferential direction ( Figure 7 ). The contact surface areas 24 are slightly longer in the axial direction of the pressure piece 10 than the contact surface areas 21 of the clamping plate 5. The contact surface areas 24 border in the axial direction on the shaft 17, which has a reduced diameter. An opening 27 for receiving the sliding block 16 is arranged in the shaft 17. It is a radial bore.
  • the contact surface areas 24 and the pockets 22 are located on or in a circumferential collar in the transition to a substantially cylindrical base body 28 which is larger than the shaft 17.
  • the compressive force is transmitted from the clamping nut 12 into the contact surface areas 24 via the base body 28.
  • the base body 28 accommodates a shaft section of the clamping nut 12 ( Figure 3 ). As a result, the pressure body 10 is guided.
  • the Figure 7 shows in an axial view from the direction of the shaft 17, which has a slimmer diameter, that the pockets 22 take up approximately half of the entire circumferential area, while the remaining circumferential area is accounted for by the contact surface areas 24.
  • the pockets 22 are wider than the projections 19 so that the lower clamping plate 5 can move relative to the pressure piece 10 without tensions building up in the axial direction in the area of the pockets 22 or in the area of the projections 20 due to mutual contact.
  • the Figure 3 shows the mutual engagement of projections 20 in the pockets 22. It can be seen that in the axial alignment shown, there is no contact between the projections 20 and the pockets 22.
  • the contact surface areas of both components are located outside the cutting plane Figures 2 and 3 , but they touch each other there.
  • the pockets 22 not only have sufficient depth but also sufficient length.
  • the clamping plate 5 were in the image plane Figure 3 clockwise to the right, the projection 20 on the left in the image plane would be able to move freely upwards within the pocket 22, while in the same way the projection 20 on the right in the image plane would be displaced downwards within the other pocket 22. The movement comes to an end when the conical inner wall 29 of the opening 7 comes into contact with the outside 30 of the shaft 17.
  • the spring tensioner 1 and the second clamping plate 5 are in the Figure 13 exactly axially aligned with respect to the longitudinal axis LA1 of the clamping device 3.
  • the contact surfaces 19, 23 of the second clamping plate 5 and the pressure piece 10 lie against one another. The projections and grooves are not visible in this section plane.
  • the Figure 14 shows a situation in which the longitudinal axis LA1 of the clamping device 3 deviates by an angle of 5 ° compared to the longitudinal axis LA2 of the opening 7 in the second clamping plate 5.
  • the shaft 17 is shifted to the left in the image plane and abuts the inner wall 29 of the opening 7 on the left side in the image plane Gap 31 in opening 7 becomes asymmetrical.
  • the end of the pivoting movement has been reached. In this position there is no contact between the pockets and the projections.
  • the pressure piece 10 functions for pressure transmission and as angle compensation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Clamps And Clips (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Compressor (AREA)

Claims (9)

  1. Compresseur de ressort (1) avec un appareil de serrage (3), qui peut être introduit axialement dans un ressort hélicoïdal (2) à tendre, ainsi qu'avec une première et une seconde plaque de serrage (5), qui peuvent être couplées à distance l'une de l'autre avec l'appareil de serrage (3), dans lequel la seconde plaque de serrage (5) présente une ouverture (7) pour recevoir l'appareil de serrage (3), dans lequel une pièce de pression (10) peut être déplacée le long de l'appareil de serrage (3) sous l'action d'un actionneur, pour régler l'écartement des plaques de serrage (4, 5), dans lequel une surface de contact (19) en forme de calotte est formée entre la pièce de pression (10) et la seconde plaque de serrage (5) pour la transmission de force ainsi qu'une sécurité antirotation pour empêcher une rotation de la pièce de pression (10) par rapport à la plaque de serrage (5), dans lequel la sécurité antirotation présente des saillies (20) et des poches (22) pour les saillies (20), caractérisé en ce que les saillies (20) et les poches (22) interrompent la surface de contact (19) en forme de calotte en direction circonférentielle et la subdivisent en zones de surface de contact (21, 24) séparées les unes des autres, dans lequel les zones de surface de contact (21) en forme de calotte sont globalement plus grandes en direction circonférentielle que la zone circonférentielle dans laquelle les saillies (20) et les poches (22) sont disposées.
  2. Compresseur de ressort selon la revendication 1, caractérisé en ce que des poches (22) sont formées dans la pièce de pression (10) et les saillies (20) dans la plaque de serrage (5).
  3. Compresseur de ressort selon la revendication 1 ou 2, caractérisé en ce que les poches (22) sont plus profondes que les saillies (22) ne sont hautes, de sorte que la plaque de serrage (5) peut être pliée de manière limitée par rapport à la pièce de pression (10) par l'intermédiaire d'un mouvement le long de la surface de contact en forme de calotte (23) sans contact entre les saillies (20) et les poches (22).
  4. Compresseur de ressort selon l'une quelconque des revendications 1 à 3, caractérisé en ce qu'une ouverture (7) est disposée dans la seconde plaque de serrage (5) pour recevoir l'appareil de serrage (3), dans lequel l'ouverture (7) présente un diamètre (D1) qui devient plus grand à mesure que la distance jusqu'à la surface de contact en forme de calotte (19) augmente.
  5. Compresseur de ressort selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la première plaque de serrage (4) peut être couplée à l'appareil de serrage (3) de manière pivotante axialement par rapport à l'appareil de serrage (3).
  6. Compresseur de ressort selon quelconque l'une des revendications 1 à 5, caractérisé en ce que les zones de surface de contact (21, 24) sont des parties de la seule et unique surface de contact (23) en forme de calotte sphérique.
  7. Compresseur de ressort selon l'une quelconque des revendications 1 à 6, caractérisé en ce que chacune des zones de surface de contact en forme de calotte sphérique (21, 24) s'étend sur une plage angulaire d'au moins 15° par rapport à l'axe longitudinal (LA1) de l'appareil de serrage (3).
  8. Compresseur de ressort selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les zones de surface de contact en forme de calotte sphérique (21) entre les saillies (20) sont plus grandes que les zones de surface de contact en forme de calotte sphérique (24) entre les poches (22).
  9. Compresseur de ressort selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les zones de surface de contact en forme de calotte sphérique (24) sur le corps de pression (10) s'étendent, par rapport à un axe transversal de l'appareil de serrage (3), sur une plage angulaire plus grande que les zones de surface de contact en forme de calotte sphérique (21) sur la plaque de serrage (5).
EP21765832.7A 2020-10-21 2021-08-12 Compresseur de ressort Active EP4084932B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202020106011.2U DE202020106011U1 (de) 2020-10-21 2020-10-21 Federspanner
PCT/DE2021/100689 WO2022083815A1 (fr) 2020-10-21 2021-08-12 Compresseur de ressort

Publications (2)

Publication Number Publication Date
EP4084932A1 EP4084932A1 (fr) 2022-11-09
EP4084932B1 true EP4084932B1 (fr) 2024-01-31

Family

ID=73460302

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21765832.7A Active EP4084932B1 (fr) 2020-10-21 2021-08-12 Compresseur de ressort

Country Status (5)

Country Link
EP (1) EP4084932B1 (fr)
CN (1) CN115135453B (fr)
DE (1) DE202020106011U1 (fr)
ES (1) ES2978943T3 (fr)
WO (1) WO2022083815A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202021104272U1 (de) 2021-08-09 2021-08-17 GEDORE Holding GmbH Federspanner
DE102021120678A1 (de) 2021-08-09 2023-02-09 GEDORE Holding GmbH Federspanner

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202021104272U1 (de) * 2021-08-09 2021-08-17 GEDORE Holding GmbH Federspanner

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3733723A1 (de) * 1986-10-10 1988-04-21 Kleinbongartz & Kaiser Werkzeu Federnspanner
DE20101841U1 (de) * 2001-02-03 2001-05-31 Hazet-Werk Hermann Zerver GmbH & Co. KG, 42857 Remscheid Spannvorrichtung für Schraubenfedern
DE10361597B3 (de) * 2003-12-24 2005-06-30 Klann-Spezial-Werkzeugbau-Gmbh System zum Spannen einer Schraubenfeder
DE202004006807U1 (de) 2004-04-28 2004-07-15 Hazet-Werk Hermann Zerver Gmbh & Co. Kg Innenspanner zum Spannen einer Schraubendruckfeder
DE102006017287B4 (de) * 2006-04-12 2021-03-25 Litens Automotive Gmbh Spanner für einen Endlostrieb
DE202006014999U1 (de) 2006-09-28 2006-11-23 Hazet-Werk Hermann Zerver Gmbh & Co. Kg Federspanner für Schraubenfedern

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202021104272U1 (de) * 2021-08-09 2021-08-17 GEDORE Holding GmbH Federspanner

Also Published As

Publication number Publication date
CN115135453A (zh) 2022-09-30
CN115135453B (zh) 2023-08-04
WO2022083815A1 (fr) 2022-04-28
EP4084932A1 (fr) 2022-11-09
ES2978943T3 (es) 2024-09-23
DE202020106011U1 (de) 2020-10-30

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