WO2024088631A1 - Ressort à lame - Google Patents

Ressort à lame Download PDF

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Publication number
WO2024088631A1
WO2024088631A1 PCT/EP2023/074490 EP2023074490W WO2024088631A1 WO 2024088631 A1 WO2024088631 A1 WO 2024088631A1 EP 2023074490 W EP2023074490 W EP 2023074490W WO 2024088631 A1 WO2024088631 A1 WO 2024088631A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
arms
disc spring
width
spring arms
Prior art date
Application number
PCT/EP2023/074490
Other languages
German (de)
English (en)
Inventor
Andreas Zimmer
Markus WEINÖHL
Christoph Bleesen
Original Assignee
Marquardt Gmbh
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 Marquardt Gmbh filed Critical Marquardt Gmbh
Publication of WO2024088631A1 publication Critical patent/WO2024088631A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/32—Belleville-type springs
    • F16F1/324—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs
    • F16F1/326—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs with a spiral-like appearance

Definitions

  • the invention relates to a leaf spring or disc spring with an optimized design, in particular a leaf spring or disc spring for applications in measuring devices or sensors in the automotive industry.
  • leaf springs A large number of different leaf springs are known from the state of the art. Disc springs or leaf springs are known especially for resetting membranes or other moving devices in measuring devices.
  • such measuring devices are known with a housing and with a membrane arranged in and/or on the housing. known.
  • the housing also contains an elastic element for resetting the membrane.
  • a signal generator is operatively connected to the membrane and/or the elastic element.
  • a signal sensor works together with the signal generator to generate the measurement signal. With these sensors, a certain hysteresis is observed when the pressure and/or temperature of the fluid to be measured changes, which in turn can lead to a falsification of the measurement signal.
  • DE 689 08 697 T2 describes a disc spring that serves as an elastic return element.
  • the disc spring has a spiral-like wave ring structure between its center and its edge.
  • a leaf spring for a measuring device with an elastic element is known from DE 10 2010 0022428 A1.
  • the elastic element has a structure for stiffening.
  • structures for stiffening the elastic element are introduced into certain areas of the geometry of the elastic element.
  • the leaf spring shown expediently has a circular shape.
  • a particularly high restoring force can be achieved with the elastic element if the leaf spring has a spring element that runs spirally from the center to the edge area of the leaf spring. This ensures a compact design with high spring force.
  • the leaf spring in addition to its circular shape, have a spring element running spirally from the center to the edge of the leaf spring to achieve a high restoring force. This ensures a compact design with high spring force. It has been shown that it is difficult to create a spring with a specific and optimized force-displacement characteristic curve within the available installation space and material parameters using the solutions known in the state of the art. The known solutions require a relatively large installation space and offer insufficient options for adaptation to the desired spring characteristics.
  • the invention is therefore based on the object of overcoming the aforementioned disadvantages and providing an optimized solution for a leaf spring or disc spring.
  • a disc spring (leaf spring) formed from a substantially circular, plate-shaped spring sheet is therefore proposed, wherein the spring sheet forms a plurality of spirally bent spring arms with a variable width B, which extend around a center (middle).
  • a preferred solution is one in which the curved spring arms extend over an arc angle a that is between 120° and 310°, preferably between 180° and 270°, more preferably between 200° and 240°.
  • the following properties in particular can be influenced: - Stress reduction in the component and thus increase in component efficiency (especially with a reduction in width of approx. 25% in the spring arm center)
  • the width B of one, several or preferably all spring arms increases and/or decreases along the arc angle a, at least in sections or over the entire length.
  • a concept has proven particularly advantageous in which the width B of one, several or all spring arms initially decreases in sections along its arc angle a and then increases again in sections and preferably has the same width B at the beginning and end. It is also advantageous if the respective spring arm has its minimum width B approximately in the middle between its two spring arm ends. Advantageous ratios of the widths are explained below in connection with the description of preferred embodiments.
  • the two ends of the respective spring arms are each connected integrally and in one piece to the spring plate.
  • the spring arms do not have a free end, but are attached or integrally connected to the spring plate at the end.
  • a correspondingly arcuate gap runs over the entire length of the bent spring arms between the respective spring arms when viewed in the radial direction R.
  • the spring arms extend at least partially or completely along an Archimedean spiral or a spiral with increasing radius R, so that the radius increases outwards when viewed in the circumferential direction.
  • a further advantageous solution is one in which the spring arms, viewed from the inside outwards in the radial direction R, each have an increasingly larger radius compared to the spiral-shaped spring arm located further inside.
  • An advantageous embodiment is one in which the spring arms are not mounted within the entire surface of the spring plate, but in the center of the plate spring there is an essentially (approximately) circular spring plate section on which the radially inner ends of the spring arms are arranged, preferably at an equidistant arc angle.
  • a design in which the inner ends of the (in this case three) spring arms are offset from each other at an arc angle of 120° has also proven to be advantageous. This means that the three spring arms are nested within each other, each offset by an angle of 120°.
  • the arched gap provided between the spring arms advantageously has an increasing width with a nose-like shape at its beginning and/or end.
  • This end shape can be designed as a nose shape, teardrop shape or pear shape.
  • the maximum width B of the spring arms is approximately 2 - 4% of the spring arm length, but may also deviate from these dimensions if certain properties of the spring plate are to be specifically modified.
  • the width B of the spring arms preferably varies in a range between 20 - 30%, preferably about 25%.
  • Fig. 1 is a plan view of a first example of a disc spring according to the invention
  • Fig. 2 is a plan view of an alternative embodiment of a disc spring according to the invention.
  • Fig. 3 is a graph showing the relationship between the width reduction of the spring arms and the stress reduction and component size.
  • Figures 1 and 2 show exemplary embodiments of a disc spring 1.
  • These disc springs 1 consist of a substantially circular, plate-shaped spring sheet 10.
  • the spring sheet 10 has three spirally bent spring arms 20.
  • the spring arms 20 have a first spring arm end 20a (inside) and a second spring arm end 20b (radially further out).
  • the width B of the spring arms 20 is not constant, but the width B of one initially decreases along the arc angle a (here from 0.8 mm) to a dimension of 0.6 mm and then increases again in sections to the dimension of 0.8 mm.
  • the respective spring arm 20 has its minimum width B (0.6 mm) approximately in the middle between its two spring arm ends 20a, 20b.
  • the two spring arm ends 20a, 20b of the respective spring arms 20 are integral and connected in one piece to the spring plate 10. This can be done by punching out the spring plate to create the gap 30.
  • the curved spring arms 20 extend over a total arc angle of approximately 270°.
  • the spring arms 20 extend along a spiral with increasing radius R, whereby this can be an Archimedean spiral.
  • the disc spring 1 has a substantially circular spring plate section 11 on which the radially inner ends 20a of the spring arms 20 are arranged at an equidistant arc angle of 120°.
  • the maximum width B of the spring arms 20 of approximately 0.8 mm is approximately 3% of the spring arm length of 26.74 mm. These dimensions are only examples and can also be selected differently.
  • the width B of the spring arms is varied from 0% to 50% in the middle, which means 0.8mm at each end and from 0.8 mm to 0.4 mm starting in the middle. It is easy to see that if the spring arm width is reduced by 25% towards the middle of the spring arm 20, the stress reduction is maximum at 8.9%. With this configuration, the outer radius can be reduced by 3.8%.
  • the invention is not limited in its implementation to the preferred embodiments given above. Rather, a number of variants are conceivable which make use of the solution presented even in fundamentally different embodiments.
  • the invention also relates to a measuring device having a disc spring according to the invention as described above.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)

Abstract

L'invention concerne un ressort à disque (1) constitué d'une tôle d'acier à ressort (10) sensiblement circulaire en forme de plaque, la tôle d'acier à ressort (10) formant d'un seul tenant une pluralité de bras de ressort courbés en spirale (20) de largeur (B) variable qui s'étendent autour d'un centre (Z).
PCT/EP2023/074490 2022-10-24 2023-09-06 Ressort à lame WO2024088631A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022128021.7 2022-10-24
DE102022128021.7A DE102022128021A1 (de) 2022-10-24 2022-10-24 Blattfeder

Publications (1)

Publication Number Publication Date
WO2024088631A1 true WO2024088631A1 (fr) 2024-05-02

Family

ID=88069018

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/074490 WO2024088631A1 (fr) 2022-10-24 2023-09-06 Ressort à lame

Country Status (2)

Country Link
DE (1) DE102022128021A1 (fr)
WO (1) WO2024088631A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0028144A1 (fr) * 1979-10-29 1981-05-06 Gordon Davey Système de support pour piston de compresseur à mouvement alternatif
DE68908697T2 (de) 1989-01-20 1993-12-09 Tatsuta Densen Kk Feder mit konischer platte.
US20040041315A1 (en) * 2001-06-06 2004-03-04 Mathieu Noe Vibration damping device
JP2007255539A (ja) * 2006-03-22 2007-10-04 Twinbird Corp バネ装置
DE102008025045A1 (de) 2007-06-02 2008-12-04 Marquardt Gmbh Sensor
US20090007560A1 (en) * 2004-08-02 2009-01-08 Ryoh Inoshiri Vibration suppression apparatus and stirling engine having the same
DE102010022428A1 (de) 2009-06-03 2010-12-09 Marquardt Mechatronik Gmbh Sensor
EP3014234B1 (fr) * 2013-06-27 2021-07-07 Marquardt Mechatronik GmbH Capteur

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2632791A (en) 1949-11-30 1953-03-24 Honeywell Regulator Co Vibratory condenser converter
US8047503B2 (en) 2008-02-26 2011-11-01 Eaton Corporation Conical spring bushing
US8176809B2 (en) 2008-12-10 2012-05-15 GM Global Technology Operations LLC Planar torsion spring
US9863670B2 (en) 2011-09-20 2018-01-09 Lockheed Martin Corporation Extended travel flexure bearing and micro check valve
US20160102724A1 (en) 2014-10-09 2016-04-14 Rethink Motion Inc. Concentric Arc Spline Rotational Spring

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0028144A1 (fr) * 1979-10-29 1981-05-06 Gordon Davey Système de support pour piston de compresseur à mouvement alternatif
DE68908697T2 (de) 1989-01-20 1993-12-09 Tatsuta Densen Kk Feder mit konischer platte.
US20040041315A1 (en) * 2001-06-06 2004-03-04 Mathieu Noe Vibration damping device
US20090007560A1 (en) * 2004-08-02 2009-01-08 Ryoh Inoshiri Vibration suppression apparatus and stirling engine having the same
JP2007255539A (ja) * 2006-03-22 2007-10-04 Twinbird Corp バネ装置
DE102008025045A1 (de) 2007-06-02 2008-12-04 Marquardt Gmbh Sensor
DE102010022428A1 (de) 2009-06-03 2010-12-09 Marquardt Mechatronik Gmbh Sensor
EP3014234B1 (fr) * 2013-06-27 2021-07-07 Marquardt Mechatronik GmbH Capteur

Also Published As

Publication number Publication date
DE102022128021A1 (de) 2024-04-25

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