WO2016096291A1 - Amortisseur de vibrations et véhicule automobile - Google Patents

Amortisseur de vibrations et véhicule automobile Download PDF

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Publication number
WO2016096291A1
WO2016096291A1 PCT/EP2015/076897 EP2015076897W WO2016096291A1 WO 2016096291 A1 WO2016096291 A1 WO 2016096291A1 EP 2015076897 W EP2015076897 W EP 2015076897W WO 2016096291 A1 WO2016096291 A1 WO 2016096291A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration damper
pressure compensation
compensation mechanism
hydraulic device
damper according
Prior art date
Application number
PCT/EP2015/076897
Other languages
German (de)
English (en)
Inventor
Sven Philip KRÜGER
Sven Greger
Stefan Rappelt
Jens Seiler
Holger Kirchner
Hendrik Marquar
Alexander Schwarz
Thomas Manger
Steffen Heyn
Andreas Förster
Achim Thomae
Christian Maurischat
Michael Triebel
Helmut Baalmann
Norbert Ackermann
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2016096291A1 publication Critical patent/WO2016096291A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B60G17/08—Characteristics of fluid dampers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
    • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
    • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B60G2202/41—Fluid actuator
    • B60G2202/416—Fluid actuator using a pump, e.g. in the line connecting the lower chamber to the upper chamber of the actuator
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall

Definitions

  • the invention relates to a vibration damper for a motor vehicle comprising a cylinder in which a piston is guided axially movably on a piston rod, wherein the piston divides the cylinder into a first and a second working space, and wherein a hydraulic device is provided in fluid communication with the cylinder and Furthermore, at least one pressure compensation mechanism between the first and the second working space is present.
  • Vibration damper for motor vehicles are known in many configurations, including as a mono-tube damper, two rohrdämpf he and two rohrdämpf he with partition or three-tube damper.
  • dampers can be used for wheel control by providing variable damping forces.
  • the damping force can be variably adjusted by, for example, a controllable proportional valve is present, which varies the flow cross section for the hydraulic medium and, accordingly, the
  • a body control by means of a vibration damper.
  • the vehicle body in the broadest sense so the body to stabilize or compensate for that, for example, sloping surfaces such as slopes or bumps or bends the effects on the structure can be reduced. This includes, for example, the rolling or nodding of the motor vehicle, which are to be controlled or reduced.
  • Vibration damper which has a gerotor, so a device which is operable both as a motor and as a generator, which is coupled to a pump. With this device, both energy can be recuperated, as well as a body control and a wheel control are performed. Wheel control, body control and recuperation are thus effected by the same device.
  • a vibration damper with the same operating principle continues to come from the US 2009/0260935 A1 .
  • DE 10 2009 022 328 A1 discloses a vibration damper in which the wheel control takes place by means of a pressure regulating valve and the body control by means of a motor-pump unit.
  • the body control and the wheel control are thus realized by independent units, which are accordingly separately optimized.
  • a structure similar to this is evident from WO 2014/066469 A1.
  • the adjustable damping forces are generated by controllable valves, one for the tension and one for the pressure direction, and the body control via a motor-pump unit.
  • the passage is also called a constant passage or bypass, but the passage does not have to be open all the time.
  • the passage has the task of providing for a comparatively small volume flow and a certain pressure equalization between the first working space and the second working space, so that no sudden pressure equalization takes place when opening one of the pressure relief valves.
  • the passage is dimensioned so that only marginal volume flows are passed through it.
  • the passage can also be closed by a valve, furthermore, there may also be a passage for the drawing and a passage for the printing direction.
  • valves At much lower pressures than the pressure relief valves of the passages, which valves have, if present, these valves merely function to provide a minimum threshold.
  • the passage (s) are thus in addition to the existing in the piston pressure limiting valves provided openings that should provide for the pressure equalization between the first working space and the second working space before opening the pressure equalization valves, with only a minimum flow rate flows.
  • the pressure compensation mechanism is arranged outside the cylinder. While in the prior art, the passage and thus the pressure compensation mechanism is arranged on the piston, it is now provided that the pressure compensation mechanism is provided outside the cylinder and thus of course also outside the piston. This is possible because the hydraulic device is connected to the cylinder and thereby has a flow path to both the first and the second working space. As a result, a further possibility has been created to connect the first working space and the second working space, wherein this connection point is no longer in the cylinder. Rather, it is placed in the flow path outside the cylinder.
  • the piston can have pressure relief valves, but it does not have to.
  • the pressure compensation mechanism may be arranged in or at the hydraulic device.
  • the pressure compensation mechanism may be arranged in or at the hydraulic device.
  • the pressure compensation mechanism may be arranged in the entire flow path outside the cylinder.
  • the flow path between cylinder and hydraulic device is anyway relatively narrow, so that the provision of the pressure compensation mechanism is the simplest and least expensive to realize in or in the hydraulic device.
  • the pressure compensation mechanism is shown as a through hole.
  • the pressure compensation mechanism is therefore a kind of bypass around the hydraulic device or at the hydraulic likvorraum or a groove in the wall of the flow path, which is formed continuously.
  • the pressure compensation mechanism can be switched. This means that the pressure compensation mechanism can be opened and closed. Although such a pressure compensation mechanism is not a constant passage, it can be considered as a switchable bypass.
  • the pressure compensation mechanism can be opened or closed depending on an operating state of the hydraulic device or an associated device, in particular an electrical device. It is particularly preferably provided that the pressure compensation mechanism is closed during operation of the hydraulic device or a device connected to the hydraulic device. Accordingly, the pressure compensation mechanism is closed during operation of the hydraulic device, so that it can work without leaks.
  • the hydraulic device may comprise a pump. If the pressure compensation mechanism is closed during operation of the pump, its efficiency can be increased. Especially in this combination, it is particularly advantageous to provide the pressure compensation mechanism not on the piston but on the pump or its environment, since the control of the pump and the pressure compensation mechanism can then be done simultaneously and with the same control device.
  • the pressure compensation mechanism as a function of the hydraulic device, in particular as a pump function may be formed.
  • the pressure compensation mechanism is no longer provided as an opening for equalizing pressures between the first working space and the second working space, but via the pump.
  • a pump movement of a pressure distribution between the first and the second working space as well as a hydraulic medium distribution can be achieved. It is then not the Pump movement determined solely in dependence on the body control, but additionally a Naturallass bin into it.
  • the vibration damper may comprise a motor which is connected to the hydraulic device.
  • the hydraulic device and the motor may in particular represent a motor-pump unit, which are arranged in a housing on the vibration damper. This arrangement can also be referred to as a hydraulic motor.
  • the hydraulic device can have a shaft and an arrangement can be present on the shaft with which the pressure compensation mechanism is closed when the shaft is stationary and at least partially open when the shaft rotates.
  • the switchability of the pressure compensation mechanism can be realized in several ways.
  • One possibility is an arrangement on the shaft, which preferably works dependent on centrifugal force. Parts of the arrangement are then pushed outward on rotation, accordingly, the pressure compensation mechanism is at a distance from the shaft.
  • the arrangement does not obscure the pressure compensation mechanism when the shaft is stationary, but with the pushing outwards it moves over the pressure compensation mechanism and closes it in this way.
  • the pressure compensation mechanism can be opened or closed by means of a switchable valve.
  • the advantage is that the circuit of the valve can be carried out in response to the energization of the motor or the hydraulic device, and so creates a simple way of coupling between the opening and closing of the pressure compensation mechanism as well as the operation of the hydraulic device.
  • the or an additional pressure compensation mechanism may be arranged in or at a controllable valve.
  • the controllable valve particularly preferably sets the damping force of the vibration damper.
  • the damping force of a vibration damper is controlled by adjustable valves.
  • the pressure compensation mechanism can be arranged. Also there it is possible to use the already existing control currents of the valve in addition to switching the pressure compensation mechanism.
  • the invention relates to a motor vehicle with at least one vibration damper.
  • This is characterized by the fact that the vibration damper is designed as described.
  • the motor vehicle may be a car, a truck or even a motorcycle.
  • FIG. 1 shows a vibration damper in a first embodiment (prior art)
  • FIG. 2 shows a characteristic curve of the vibration damper according to FIG. 1 (prior art)
  • FIG. 4 shows characteristic curves of the vibration damper according to FIG. 3 (prior art)
  • FIG. 5 shows a vibration damper in a third embodiment
  • FIG. 6 shows characteristic curves of the vibration damper according to FIG. 5.
  • Figure 1 shows a vibration damper 1 of the prior art. This is designed as a tubular damping it and has a working cylinder 2, in which a piston 3 is guided axially movable. Furthermore, a piston rod 4 and a compensation chamber 5 are present. The piston 3 separates the working cylinder 2 in a first working space 5 and a second working space 6. In the piston 3, two pressure relief valves 7 and 8 and a passage 9 are arranged. Since the passage 9 is not switchable is in this case a constant passage.
  • FIG. 2 shows the characteristic curve 10 that can be generated with the vibration damper 1 according to FIG. 1.
  • the piston speed is plotted against the axis 12 and the pressure against the axis 14.
  • the passage 9 for the curve is authoritative. This is accordingly parabolic.
  • the pressure relief valve 8 opens, so that the flow resistance drops on the piston and accordingly follows a linear curve.
  • the pressure relief valve 7 which is why in the opposite direction after a certain time a linear curve is present. Only in the central area around the O-point around the characteristic is dominated by the passage 9.
  • Figure 3 shows a further known alternative of a vibration damper 1, in which two controllable valves 22 and 24 are provided, wherein one of the valves 22 or 24 are used for the printing direction and the other for the pulling direction.
  • the valves 22 and 24 are arranged outside of the working cylinder 2, but they can also be arranged within the cylinder 2.
  • the resulting characteristic curves 26 are shown in FIG. 4. They essentially correspond to the characteristic curve 10; depending on the setting of the valves 22 and 24, they superimpose the parabolic section of the passage 9 earlier or later.
  • Each of the characteristic curves 26 is thus a characteristic curve for a certain predetermined damping force.
  • FIG. 5 shows a vibration damper 1 in which the passage 9 is arranged outside the working cylinder 2.
  • the passage 9 is not integrated in the piston 3.
  • the passage 9 is located in the hydraulic device 28.
  • the hydraulic device 28 is preferably designed as a pump and connected to a motor 30, in particular an electric motor.
  • the passage 9 can be switchable, it can also be closed via a centrifugal force-dependent arrangement on the shaft between the hydraulic device 28 and motor 30.
  • an additional passage 32 may be provided with switchable controllable valves 23 and 24. It is thus possible to realize a plurality of passages 9 and 32 on the vibration damper 1.
  • the vibration damper 1 according to Figure 5 is in particular a wheel control by means of valves 22 and 24 as well as a body control by means of the motor-pump assembly with hydraulic device 28 and motor 30 is possible.
  • the resulting damping characteristic of the vibration damper 1 according to FIG. 5 is shown in FIG.
  • the region of the second and fourth quadrants is now also accessible.
  • it requires the realization of the passage 9 as a pump function, so that tensile forces and tensile forces can be exerted in the direction of compression.

Abstract

L'invention concerne un amortisseur de vibrations (1) pour un véhicule automobile, comprenant un cylindre (2) dans lequel un piston (3) est guidé en mobilité axiale sur une bielle (4). Le piston (3) divise le cylindre (2) en une première (5) et une deuxième (6) chambre de travail et un dispositif hydraulique (28) se trouve en liaison fluidique avec le cylindre (2). Il existe au moins un passage (9) destiné à relier la première (5) et la deuxième (6) chambre de travail, et le passage (9) est disposé à l'extérieur du cylindre (2).
PCT/EP2015/076897 2014-12-15 2015-11-18 Amortisseur de vibrations et véhicule automobile WO2016096291A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014225930.4A DE102014225930A1 (de) 2014-12-15 2014-12-15 Schwingungsdämpfer sowie Kraftfahrzeug
DE102014225930.4 2014-12-15

Publications (1)

Publication Number Publication Date
WO2016096291A1 true WO2016096291A1 (fr) 2016-06-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/076897 WO2016096291A1 (fr) 2014-12-15 2015-11-18 Amortisseur de vibrations et véhicule automobile

Country Status (2)

Country Link
DE (1) DE102014225930A1 (fr)
WO (1) WO2016096291A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017050563A1 (fr) * 2015-09-25 2017-03-30 Zf Friedrichshafen Ag Amortisseur de vibrations, procédé pour faire fonctionner un amortisseur de vibrations, dispositif de commande ainsi que véhicule à moteur

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017216919A1 (de) 2017-09-25 2019-03-28 Zf Friedrichshafen Ag Verstellbarer Schwingungsdämpfer
DE102017216922A1 (de) 2017-09-25 2019-03-28 Zf Friedrichshafen Ag Verstellbarer Schwingungsdämpfer
DE102018215054A1 (de) * 2018-09-05 2020-03-05 Zf Friedrichshafen Ag Schwingungsdämpferanordnung
DE102020202384A1 (de) 2020-02-25 2021-08-26 Zf Friedrichshafen Ag Verstellbarer Schwingungsdämpfer

Citations (8)

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Publication number Priority date Publication date Assignee Title
FR2562844A1 (fr) * 1984-04-14 1985-10-18 Bosch Gmbh Robert Dispositif de commande de la durete de la suspension d'un vehicule
JPS60213512A (ja) * 1984-04-05 1985-10-25 Nissan Motor Co Ltd 液圧制御サスペンシヨン
EP1306574A2 (fr) * 2001-10-26 2003-05-02 Sachs Race Engineering GmbH Amortisseur de vibrations avec force d'amortissement réglable
DE102009022328A1 (de) * 2008-12-10 2010-06-17 Daimler Ag Dämpfereinrichtung
DE102009056874A1 (de) * 2009-12-03 2010-07-22 Daimler Ag Federdämpfervorrichtung für ein Fahrzeug
WO2011154026A1 (fr) * 2010-06-11 2011-12-15 Daimler Ag Dispositif amortisseur à cartouche à gaz
DE102011100307A1 (de) * 2011-05-03 2012-11-08 Daimler Ag Landgebundenes Personenkraftfahrzeug mit einer Entkopplungsvorrichtung sowie Verfahren zum Entkoppeln einer Karosserie des landgebundenen Personenkraftfahrzeugs
US20130104534A1 (en) * 2011-11-01 2013-05-02 Tenneco Automotive Operating Company Inc. Energy harvesting passive and active suspension

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AT213722B (de) * 1958-02-14 1961-02-27 E H Friedrich Dr Ing Nallinger Flüssigkeitsstoßdämpfer für Fahrzeuge, insbesondere Kraftfahrzeuge
DE3709447A1 (de) * 1987-03-23 1988-10-13 Bilstein August Gmbh Co Kg Regelbarer stossdaempfer, insbesondere fuer kraftfahrzeuge
US8376100B2 (en) 2008-04-17 2013-02-19 Levant Power Corporation Regenerative shock absorber
EP4289640A3 (fr) 2010-06-16 2024-02-28 ClearMotion, Inc. Amortisseur de génération d'énergie intégré
US8820064B2 (en) 2012-10-25 2014-09-02 Tenneco Automotive Operating Company Inc. Recuperating passive and active suspension
US9481221B2 (en) * 2013-01-08 2016-11-01 Tenneco Automotive Operating Company Inc. Passive and active suspension with optimization of energy usage
US9550404B2 (en) 2013-03-15 2017-01-24 Levant Power Corporation Active suspension with on-demand energy flow

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60213512A (ja) * 1984-04-05 1985-10-25 Nissan Motor Co Ltd 液圧制御サスペンシヨン
FR2562844A1 (fr) * 1984-04-14 1985-10-18 Bosch Gmbh Robert Dispositif de commande de la durete de la suspension d'un vehicule
EP1306574A2 (fr) * 2001-10-26 2003-05-02 Sachs Race Engineering GmbH Amortisseur de vibrations avec force d'amortissement réglable
DE102009022328A1 (de) * 2008-12-10 2010-06-17 Daimler Ag Dämpfereinrichtung
DE102009056874A1 (de) * 2009-12-03 2010-07-22 Daimler Ag Federdämpfervorrichtung für ein Fahrzeug
WO2011154026A1 (fr) * 2010-06-11 2011-12-15 Daimler Ag Dispositif amortisseur à cartouche à gaz
DE102011100307A1 (de) * 2011-05-03 2012-11-08 Daimler Ag Landgebundenes Personenkraftfahrzeug mit einer Entkopplungsvorrichtung sowie Verfahren zum Entkoppeln einer Karosserie des landgebundenen Personenkraftfahrzeugs
US20130104534A1 (en) * 2011-11-01 2013-05-02 Tenneco Automotive Operating Company Inc. Energy harvesting passive and active suspension

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017050563A1 (fr) * 2015-09-25 2017-03-30 Zf Friedrichshafen Ag Amortisseur de vibrations, procédé pour faire fonctionner un amortisseur de vibrations, dispositif de commande ainsi que véhicule à moteur

Also Published As

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