EP3334954A1 - Federaggregat, federspeicher und aktor - Google Patents
Federaggregat, federspeicher und aktorInfo
- Publication number
- EP3334954A1 EP3334954A1 EP16777640.0A EP16777640A EP3334954A1 EP 3334954 A1 EP3334954 A1 EP 3334954A1 EP 16777640 A EP16777640 A EP 16777640A EP 3334954 A1 EP3334954 A1 EP 3334954A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spring
- force
- contour
- jaws
- accumulator
- 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.)
- Pending
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
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
- F03G1/00—Spring motors
- F03G1/06—Other parts or details
- F03G1/10—Other parts or details for producing output movement other than rotary, e.g. vibratory
-
- 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/063—Negative stiffness
-
- 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
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
- F16F2230/0064—Physically guiding or influencing using a cam
Definitions
- Spring assembly Spring accumulator and actuator
- the invention relates to a spring assembly, a spring accumulator and an actuator.
- actuators have spring elements as above be ⁇ wrote.
- Such actuators, and therefore also the Federele ⁇ elements are typically deflected, wherein the spring elements are often part of the spring brake, either explicitly (as additional components with memory function) or implicit (as components such as piezoelectric stacks or Dichtungselemen ⁇ te like bellows with the appropriate Stiffness).
- the characteristic of the actuator eg force curve and Ge ⁇ schwindtechniksverlauf
- the spring force of the spring elements is dependent on the strength of the deflection. This results in a high dependence on the deflection for many applications.
- the spring assembly according to the invention comprises at least one Fe ⁇ derelement with a deflectable against a spring force part and a compensation device.
- the compensation device is, at least along a portion along which the part is deflectable, designed to counteract more strongly deflected part of the spring force than at a weaker deflected part.
- the section expediently comprises the case of vanishing deflection.
- the section expediently comprises all paths which can be described by the part with its deflection below a maximum path or distance.
- Under a deflectable part of a spring element according to the present invention is about a free end of a compression or tension spring or a freely movable Saltend- or non-edge region of a spring element, such as the center of a disc plate spring to understand.
- the compensation device counteracts From ⁇ dependence of the spring force of the deflection of the deflectable member.
- a spring assembly and in particular a spring accumulator with such a spring aggregate and in particular an actuator with a significantly reduced Auslenkungspinkeit the force are formed on the free part of the spring element.
- the significant reduction in this dependence of the force effect opens up new fields of application for spring accumulators and actuators, which were previously unavailable due to dependency.
- the compensation device preferably comprises a body deflectable with the part along a path and one or more clamping jaws which clamp or clamp the body in the direction transverse to the path.
- the body has a convex contour viewed in the direction of the clamping jaw . In this way, a force acting against the spring force can be exerted on the body by means of a clamping.
- the contour preferably has a tangent parallel to the path when the part is not deflected on the jaw or jaws.
- the jaws behave neutral on the undeflected part.
- the contour at more deflected part on the jaw or on a path oblique to the path is preferably a shape of the spring assembly according to the invention.
- an increasing force acting against the spring force can unfold on the part.
- the contour in the case of the spring assembly, is an outer contour.
- the contour is an inner contour.
- the body is elastic.
- the spring accumulator according to the invention has a spring unit as described above.
- the compensation device itself is formed with a spring accumulator.
- a spring accumulator preferably elastic see body between the jaws as such further energy storage, ie, the entire spring accumulator including compensation device acts in this development as energy storage.
- the actuator according to the invention comprises a spring unit as described before ⁇ standing and / or a spring accumulator as described above.
- the functionality of the actuator can be significantly improved since, according to the invention, the force-displacement characteristic of such an actuator is not influenced by spring elements, such as those formed by metal bellows or diaphragm bellows. This is particularly important for smaller actuators, such as microactuators, important because here the power-path reserves are usually low and even small Fe ⁇ dersteiftechniken can have great negative impact.
- Fig. La a spring accumulator according to the invention with a spring assembly according to the invention of an actuator according to the invention with two spring elements with a deflectable part in a non-deflected position schematically in longitudinal section
- Fig. Lb the spring accumulator according to the invention.
- Fig. 2a a further embodiment of an OF INVENTION ⁇ to the invention the spring accumulator schematically in longitudinal section as well as a third embodiment of an OF INVENTION to the invention the spring accumulator schematically in Longitudinal section.
- the spring accumulator shown in Fig. La, lb and lc comprises two compression springs 5, 10 with spring constant k, which can each deflect along an axis A.
- the compression springs 5, 10 extend from two mutually facing and mutually immovable sides 13, 17 of an actuator not shown in detail opposite each other.
- the compression springs 5, 10 with their deflection directions to each other (and with the axis A) are aligned.
- the two compression springs 5, 10 are connected to each other on opposite sides of a clamping body 20 of a compensation device for compensating the deflection of the dependent spring force F k of the compression springs 5, 10 with each other.
- the clamping body 20 has a longitudinal section which is constant in different sections parallel to the plane of the drawing, ie, the clamping body 20 forms a general mathematical see cylinder whose generatrix is perpendicular to the plane of the drawing.
- the outer contour 25 of the longitudinal section of Klemmkör ⁇ pers 20 has a - viewed in the direction perpendicular to the axis A outwardly - convex curved course.
- the clamping body 20 is in the direction perpendicular to the axis A to two jaws 30, 35, which are oriented as roller bearings with rolling ⁇ axes perpendicular to the plane and fixed to the sides 13, 17 of the actuator.
- the jaws may be formed as a sliding bearing.
- the clamping body 20 is flexible and is clamped by the jaws 30, 35 and thereby compressed in the direction perpendicular to the axis A and within the plane of the drawing.
- the tangent at the location 40, 45 of the clamping jaws 30, 35 extends parallel to the axis A to the outer contour of the clamping body 20.
- Da ⁇ forth results by the jaws 30, 35 on the clamping body 20 no force, which is oriented along the axis A. is.
- Fy perpendicular to the axis force component
- each jaw 30, 35 which are opposite to each other oriented.
- no spring force F k acts, acting in total no force on the clamping body 20th
- the clamping body 20 With increasing deflection (FIG. 1 b), the clamping body 20, on the one hand, experiences an increasing spring force as a result of the greater deflection of the compression springs 5, 10. In addition, however, the clamping body changes in relation to the clamping jaws 30, 35 compared with the arrangement described above. Because of the deflection of the clamping body 20 namely the tangent to the outer contour of the clamping body 20 at the location 40, 45 of the jaws 30, 35 is no longer parallel to the axis A but is slightly inclined to each of these. In this case, these tangents open to the outer contour of the clamping body 20 with each other an open angle in the direction of the deflection.
- the clamping jaws 30, 35 are due to the - in the direction perpendicular to the axis A outwardly - convex outer contour of the clamping body 20 at such a point that the tangents to the outer contour at the location of the jaws 30, 35 with the axis A according to the position gem.
- Fig. 1 b include larger angle. Accordingly, the force component increases
- the contour of the clamping body 20 has in the illustrated embodiment on such a course that the force acting in total on the clamping body 20 along the axis A na ⁇ hey constant, ie is almost independent of the deflection of the clamping body 20.
- the outer contour of the clamping body 20 can be selected such that the mediated by the jaws 30, 35 force F x on the clamping body 20, the spring force F k always repeals.
- the clamping ⁇ body 20 remains free of force at each deflection. Consequently, in such embodiments, the clamp body 20 will remain in any deflected position.
- the jaws 30, 35 need not necessarily attack the clamping body 20 as shown above on the outer contour.
- clamping body 20 a has corresponding inner contour on which the Klemmba ⁇ bridges 30, 35 attack as shown in Fig. 2a:
- the clamping body 50 shown there has the shape of a hollow general mathematical cylinder, ie, the base of the cylinder is two times together and has the topology of a circular ring, which in the present case ge ⁇ is deformed deformed:
- the clamping body 50 has in planes pa ⁇ rallel to the plane an inner contour, which on each of an inner jaw 30, 35 adjacent part of the clamp body 50 on the jaw 30, 35 to be ⁇ considered convex shape.
- the spring force is suitably compensated, in relation to the deflection
- the clamp body does not necessarily have the shape of a general mathematical cylinder. Rather, the clamping body can also as shown in Figure 2b have rotationally symmetrical shape ⁇ . The shown in Figure 2b.
- Clamping body 70 has the same longitudinal section as the clamping body 20 shown in FIGS. 1a to 1c. In contrast to the clamping body 20, however, the clamping body 70 protrudes about the axis A by rotation of the longitudinal section.
- the jaws 90 are ball bearings in this case.
- clamp body 50 is shown by rotation of the longitudinal section of the clamp body 50. Also in this case are the
- Jaws (not specifically shown) realized with ball bearings reali ⁇ .
- the spring elements do not satisfy the Hook's law. Rather, in many cases occurring in practice, the spring constant is not an actual constant, but even of the deflection s dependent.
- the clamping body 20 may be formed from ⁇ to compensate for the spring force, which follows from this non-linear characteristic, or compensate for their increase / decrease with increasing deflection or attenuate.
- the shape of the clamp body is modified with respect to the drawing. If, for example, k (s) increases with deflection s, the curvature of the clamping body must be lower in its undeflected position and higher at the edge than shown in Fig. 1 and Fig. 2. Smaller k (s) with the displacement s from the Krüm ⁇ tion the clamping body is higher in the middle and at the edge thereof correspondingly lower.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Springs (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015218851.5A DE102015218851A1 (de) | 2015-09-30 | 2015-09-30 | Federaggregat, Federspeicher und Aktor |
PCT/EP2016/073135 WO2017055363A1 (de) | 2015-09-30 | 2016-09-28 | Federaggregat, federspeicher und aktor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3334954A1 true EP3334954A1 (de) | 2018-06-20 |
Family
ID=57083286
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16777640.0A Pending EP3334954A1 (de) | 2015-09-30 | 2016-09-28 | Federaggregat, federspeicher und aktor |
Country Status (7)
Country | Link |
---|---|
US (1) | US20180283363A1 (de) |
EP (1) | EP3334954A1 (de) |
JP (1) | JP6671467B2 (de) |
KR (1) | KR102145490B1 (de) |
CN (1) | CN108138896B (de) |
DE (1) | DE102015218851A1 (de) |
WO (1) | WO2017055363A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10457108B2 (en) * | 2017-10-23 | 2019-10-29 | GM Global Technology Operations LLC | Non-linear stiffness actuator for vehicle suspension |
KR102090336B1 (ko) * | 2019-03-20 | 2020-03-17 | 양동호 | 고유진동수 가변형 동흡진기 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1250451B (de) | 1967-09-21 | Maschinenfabrik Winkler, Fallert a Co. A.G., Bern | Einrichtung an Farbwerken von Druckmaschinen zum Einstellen sowie An- und Abstellen der Verreib- und Auftragwalzen | |
CS155075B1 (de) * | 1968-02-08 | 1974-05-30 | ||
FR2265599B1 (de) | 1974-04-01 | 1978-05-26 | Bennes Marrel | |
US4257495A (en) * | 1978-05-10 | 1981-03-24 | National Research Development Corporation | Damping device |
US5024111A (en) * | 1989-10-30 | 1991-06-18 | Aec-Able Engineering Co., Inc. | Adjustment of zero spring rate suspensions |
JPH03277837A (ja) * | 1990-03-27 | 1991-12-09 | Yamaha Motor Co Ltd | バネ系機構 |
US5558191A (en) * | 1994-04-18 | 1996-09-24 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
US6966535B2 (en) * | 2002-05-07 | 2005-11-22 | Newport Corporation | Snubber for pneumatically isolated platforms |
DE102006062195B3 (de) * | 2006-12-22 | 2008-04-30 | Lisega Ag | Konstantträger |
ATE475039T1 (de) * | 2007-03-14 | 2010-08-15 | Gm Global Tech Operations Inc | Gangschaltvorrichtung |
KR20130042290A (ko) * | 2011-10-18 | 2013-04-26 | 숭실대학교산학협력단 | 짝수차 다항식 형상의 캠-스프링 방식 준영강성 제진기 |
TWI604111B (zh) * | 2013-09-13 | 2017-11-01 | Institute Of Unclear Energy Res Rocaec | Three-dimensional direction shock absorber |
DE112014004415T5 (de) * | 2013-09-27 | 2016-06-16 | Firestone Industrial Products Company, Llc | Vibrationsisolator und einen solchen enthaltende Systeme |
US10457108B2 (en) * | 2017-10-23 | 2019-10-29 | GM Global Technology Operations LLC | Non-linear stiffness actuator for vehicle suspension |
-
2015
- 2015-09-30 DE DE102015218851.5A patent/DE102015218851A1/de active Pending
-
2016
- 2016-09-28 WO PCT/EP2016/073135 patent/WO2017055363A1/de active Application Filing
- 2016-09-28 US US15/764,874 patent/US20180283363A1/en not_active Abandoned
- 2016-09-28 JP JP2018516153A patent/JP6671467B2/ja active Active
- 2016-09-28 EP EP16777640.0A patent/EP3334954A1/de active Pending
- 2016-09-28 KR KR1020187012203A patent/KR102145490B1/ko active IP Right Grant
- 2016-09-28 CN CN201680057333.5A patent/CN108138896B/zh active Active
Also Published As
Publication number | Publication date |
---|---|
CN108138896B (zh) | 2020-01-03 |
JP6671467B2 (ja) | 2020-03-25 |
KR102145490B1 (ko) | 2020-08-18 |
KR20180063209A (ko) | 2018-06-11 |
WO2017055363A1 (de) | 2017-04-06 |
US20180283363A1 (en) | 2018-10-04 |
DE102015218851A1 (de) | 2017-03-30 |
CN108138896A (zh) | 2018-06-08 |
JP2018531348A (ja) | 2018-10-25 |
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DAV | Request for validation of the european patent (deleted) | ||
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Owner name: METISMOTION GMBH |
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Effective date: 20211105 |