WO2011154026A1 - Dispositif amortisseur à cartouche à gaz - Google Patents

Dispositif amortisseur à cartouche à gaz Download PDF

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Publication number
WO2011154026A1
WO2011154026A1 PCT/EP2010/007365 EP2010007365W WO2011154026A1 WO 2011154026 A1 WO2011154026 A1 WO 2011154026A1 EP 2010007365 W EP2010007365 W EP 2010007365W WO 2011154026 A1 WO2011154026 A1 WO 2011154026A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
gas spring
spring damper
damper device
working
Prior art date
Application number
PCT/EP2010/007365
Other languages
German (de)
English (en)
Inventor
Oussama Ajala
Joachim Kieserling
Magnus Lahti
Christian Mosler
Andreas Opara
Karl-Josef Rieger
Markos Troulis
Original Assignee
Daimler 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 Daimler Ag filed Critical Daimler Ag
Publication of WO2011154026A1 publication Critical patent/WO2011154026A1/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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/061—Mono-tubular units
    • 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
    • B60G13/14—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers accumulating utilisable energy, e.g. compressing air
    • 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
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F16F9/5126—Piston, or piston-like valve elements
    • 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
    • B60G2202/10—Type of spring
    • B60G2202/15—Fluid spring
    • B60G2202/154—Fluid spring with an accumulator
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2300/00—Indexing codes relating to the type of vehicle
    • B60G2300/60—Vehicles using regenerative power

Definitions

  • the invention relates to a gas spring damper device with a working cylinder, a displaceably mounted within the working cylinder and the working cylinder in a filled or filled with a hydraulic medium first working space and a filled or filled with the hydraulic medium second working space working piston, one of the working piston permanently assigned and in the first Working space plunging piston rod, by means of hydraulic energy in the
  • Gas spring damper device can be introduced and removed, one of the first
  • Working space hydraulically associated first hydraulic energy storage by means of at least a subset of the hydraulic energy is convertible, a second working space hydraulically associated second hydraulic energy storage means of at least one further subset of the hydraulic energy is convertible, a two working spaces hydraulically associated hydraulic motor generator device by means of additional hydraulic energy in the gas spring damper device can be selectively introduced and removed, a first hydraulic damping device connected between the first working space and the first energy store and a second hydraulic damping device connected between the second working space and the second energy store and a device according to the device
  • Gas spring damper devices for motor vehicles are known. These can be activated, for example, by means of a hydraulic motor generator device. Furthermore, it is known that these have at least one hydraulic energy store for storing and dispensing hydraulic energy. In addition, these usually have a hydraulic damping device, by means of the energy of a body movement of a equipped with the gas spring damper device
  • control device by means of which in dependence on at least one an operating state of the electrical machine characterizing signal and / or in dependence on one by means of a
  • Detecting means detected and a relative position and / or a relative movement of the piston relative to the cylinder characterizing signal a damping force of the damping device can be determined.
  • the object of the invention is an improved gas spring damper device
  • the object is in a gas spring damper device with a working cylinder, a displaceably mounted within the working cylinder and the working cylinder in a filled with a hydraulic medium or fillable first working space and a filled or filled with the hydraulic medium second working space
  • Working piston a piston dedicated to the working piston and plunging into the first working space, by means of the hydraulic energy in the
  • Gas spring damper device can be introduced and removed, one of the first
  • Working space hydraulically associated first hydraulic energy storage by means of at least a subset of the hydraulic energy is convertible
  • a second working space hydraulically associated second hydraulic energy storage means of at least one further subset of the hydraulic energy is convertible
  • a two working spaces hydraulically associated hydraulic motor generator device by means of additional hydraulic energy in the gas spring damper device can be selectively introduced and removed, a switched between the first working space and the first energy storage first hydraulic damping device and connected between the second working space and the second energy storage second hydraulic damping device by at least one additional hydraulic transmission member with one of a movement dynamics of the
  • This dynamic motion can result from different road conditions of a roadway, which travels a motor vehicle equipped with the gas spring damper device.
  • the transmission behavior of the additional hydraulic transmission member can be designed so that comparatively small bumps in the road are swallowed particularly well, so not possible to be transferred to the rest of the motor vehicle. Such comparatively small road bumps correspond to one
  • the task is also in a gas spring damper device with a
  • Working cylinder a displaceably mounted within the working cylinder and the working cylinder in a filled or filled with a hydraulic fluid first working space and a filled or filled with the hydraulic medium second working space working piston, a working piston fixedly assigned and plunging into the first working chamber piston rod, by means of the hydraulic Energy in the gas spring damper device can be introduced and removed, a first working space hydraulically associated first hydraulic energy storage by means of at least a subset of the hydraulic energy is convertible, a second working space hydraulically associated second hydraulic energy storage means of at least one further subset of the hydraulic energy is convertible, a hydraulic motor generator device hydraulically assigned to both working spaces by means of the additional hydraulic energy in the gas spring damper optionally selectively engageable and removable, a switched between the first working space and the first energy storage first hydraulic damping device and a switched between the second working space and the second energy storage second hydraulic damping device by a switched between the working spaces additional hydraulic device with a bidirectional of a
  • the gas spring damper device is designed according to a so-called one-tube principle, wherein a damper work of the gas spring damper device takes place in each case with displacement of the volume of the respectively decreasing working space.
  • the respective displaced volume is via the respective downstream hydraulic
  • Damping device displaced in the respective downstream hydraulic energy storage. It can be introduced by means of the movement of the piston rod
  • a transition of the hydraulic medium between the working spaces is made possible by means of the additional hydraulic device connected between the work spaces, wherein this transition is bidirectional, ie during a dipping movement or in the opposite case during a rebound movement of the piston rod.
  • this transition is dependent on a speed of the piston rod and thus on a pressure difference between the work spaces.
  • Gas spring damper device equipped motor vehicle can be made dependent, in particular by means of a suitable control device. This can be done advantageously in cooperation with an activation by means of the hydraulic motor generator device.
  • the task is also in a gas spring damper device with a
  • Working cylinder a displaceably mounted within the working cylinder and the working cylinder in a filled or filled with a hydraulic fluid first working space and a filled or filled with the hydraulic medium second working space working piston, a working piston fixedly assigned and plunging into the first working chamber piston rod, by means of the hydraulic Energy in the gas spring damper device can be introduced and removed, a first working space hydraulically associated first hydraulic energy storage means of the at least a subset of the hydraulic energy is convertible, a second hydraulic energy accumulator hydraulically assigned to the second working space by means of the at least one further subset of the hydraulic energy is convertible, hydraulically assigned to two working spaces hydraulic motor generator device by means of additional hydraulic energy in the gas spring damper device is selectively introduced and removed, a connected between the first working space and the first energy storage first hydraulic damping device and a connected between the second working space and the second energy storage second hydraulic damping device solved by a switched between the energy storage additional controllable hydraulic actuator.
  • the energy storage can be short-circuited by means of the additional controllable hydraulic
  • the additional hydraulic transmission member is connected directly between the working spaces.
  • a pressure equalization between the work spaces can be done directly via the additional hydraulic transmission member.
  • the working piston has the additional hydraulic transmission member.
  • the additional hydraulic transmission member can be provided space-saving directly in the working piston.
  • amplitude-selective it can be understood, for example, that the additional hydraulic
  • Transmitter for low amplitudes has a low hydraulic resistance and for large amplitudes a greater hydraulic resistance.
  • excitations with a comparatively small amplitude can therefore be swallowed particularly well.
  • frequency selective temporarily permeable can be understood, for example, that for comparatively high frequencies, the additional hydraulic transmission member has a comparatively low hydraulic resistance and for comparatively low frequencies a comparatively high hydraulic resistance.
  • frequencies greater than 5 Hz, in particular between 5 and 30 Hz, in particular between 10 and 25 Hz, in particular of approximately 20 Hz can be understood.
  • Under comparatively low frequencies can be understood.
  • the additional hydraulic transmission member is connected between the energy storage.
  • the energy storage depending on the
  • Movement dynamics of the piston rod are more or less short-circuited.
  • the gas spring damper device comprises two of the hydraulic transmission members.
  • the effect described above can be achieved at different points of the gas spring damper device.
  • each of the damping devices each one of the additional hydraulic transmission elements is connected in parallel.
  • Transfer member are switched softer or harder depending on the dynamics of movement of the piston rod.
  • the damping characteristic of the gas spring damper device for a compression movement and for a rebound movement frequency dependent which advantageously high-frequency
  • the additional hydraulic device is a double-acting adjustment valve
  • the additional hydraulic device can be adjusted by means of the double-acting adjusting valve depending on a control signal.
  • the additional hydraulic device has a further controllable hydraulic actuator and this in series a double-acting passive throttle.
  • controllable actuator can be selectively opened or closed, wherein in the closed state no overflowing hydraulic medium between the workrooms can be done.
  • closed state In the open state, however, advantageously takes place a bidirectional passive throttling of an overflow of the
  • Actuator made a comfort improvement.
  • a bidirectional transmission behavior dependent on a flow direction can be used
  • the object is also achieved in a motor vehicle with a gas spring damper device described above. This results in the advantages described above.
  • Fig. 1 is a schematic functional view of a gas spring damper device with a hydraulic lots
  • Fig. 2 shows another gas spring damper device with a frequency-selective
  • Fig. 3 shows another gas spring damper device with one between two
  • Fig. 4 shows another gas spring damper device with a between the
  • Fig. 5 shows another gas spring damper device with two single-acting
  • Fig. 6 shows another gas spring damper device with two single-acting
  • Fig. 7 shows a further gas spring damper device with a between the
  • Fig. 8 shows another gas spring damper device with one between two
  • Fig. 9 shows a further gas spring damper device, wherein between the working spaces a double-acting check valve and a double-acting passive throttle are connected.
  • FIG. 1 shows a gas spring damper device 1 of a motor vehicle 3 shown only partially.
  • the gas spring damper device 1 has a working cylinder 5.
  • a working piston 7 is mounted longitudinally displaceable. Of the Working piston 7 separates the working cylinder 5 into a first working space 9 and a second working space 11.
  • the working spaces 9 and 11 are filled with a hydraulic medium, for example a hydraulic oil.
  • the working piston 7 is assigned a piston rod 15 fixed.
  • the piston rod 15 is immersed in the first working space 9 and is mounted along with the working piston 7 longitudinally displaceable relative to the working cylinder 5.
  • Piston rod 15 hydraulic energy can be introduced into the gas spring damper device 1 or these are removed.
  • the first working space 9 is followed by a first hydraulic damping device 17.
  • the first hydraulic damping device 17 is followed by a first hydraulic energy store 19.
  • the second working space 11 is followed by a second hydraulic damping device 21.
  • the second hydraulic damping device 21 is followed by a second hydraulic energy storage 23.
  • the hydraulic energy accumulators 19, 23 can be designed in any desired manner, for example as disk spring accumulator and / or air cushion accumulator. in the
  • the energy storage 19 and 23 provide a hydraulic
  • the hydraulic energy accumulators 19, 23 are at least partially filled with a compressible medium, for example air, wherein the hydraulic energy can be stored by means of the compressible medium.
  • a compressible medium for example air
  • Energy storage 19, 23 takes place.
  • the hydraulic energy storage 19, 23 are the same size.
  • the actual damper work of the gas spring damper device 1 is accomplished by means of the hydraulic damper device 17, 21, which convert in a known manner speed-dependent hydraulic energy into heat energy.
  • the hydraulic damping devices 17, 21 each have an adjustable throttle and this parallel connected to a check valve, wherein the
  • Each check valve is connected so that a filling of the respective hydraulic energy storage 19, 23 through the throttle and emptying occurs under low hydraulic resistance through the opening check valve. It is advantageously ensured that the gas spring damper device 1 according to the monotube principle, that is loaded on pressure works. Damper work is becoming smaller and smaller
  • the hydraulic motor generator device 25 has a bidirectional one
  • the hydraulic motor generator device as well as the adjustable hydraulic circuit
  • Damping devices 17,21 can by means of a non-illustrated
  • Control unit are controlled, for example, a tendency to roll of the
  • the working piston 7 has an additional hydraulic transmission member 27.
  • the transmission member 27 is between the first working space 9 and the second
  • the additional hydraulic transmission member 27 has a double-acting amplitude-selective throttled
  • Throttle symbol and a two-sided spring-loaded oscillating piston symbolizes.
  • the oscillating piston enters an upper or a lower stop, wherein no further pressure equalization or volume flow between the working spaces 9, 11 more can take place. It can be seen that advantageous for comparatively small movements of the piston rod 15, the damping devices 17 and 21 and these downstream, the hydraulic energy storage 19 and 23 can be bypassed, advantageously a comfort-enhancing soft damping characteristic of
  • Gas spring damper device 1 is given for small amplitudes of the piston rod 15.
  • Figure 2 shows a schematic view of another gas spring damper device 1 analogous to the gas spring damper device shown in Figure 1 1.
  • the temporary hydraulic passages each have a double oscillating piston which is spring-loaded on both sides.
  • An input side oscillating piston has a throttle and forms an inlet valve.
  • Another of the oscillating piston is fluid-tight longitudinally displaceable and associated with an outlet opening.
  • Reciprocating piston recoils while the inlet valve opens, leaving a
  • Hydraulic flow through the inlet valve and the hydraulic bypass between the work spaces 9 and 11 can be done.
  • a pressure equalization takes place through the throttle of the sealing oscillating piston, so that the inlet valve is closed again, so at low frequencies no compensation of the hydraulic medium between the working spaces 9 and 11 can take place.
  • FIG 3 shows another gas spring damper device 1 analogous to that shown in Figures 1 and 2.
  • the working piston 7 has no additional hydraulic transmission member 27.
  • the additional hydraulic transmission member 27 is connected between the energy storage 19 and 23.
  • the additional hydraulic transmission member 27 is analogous to the hydraulic transmission member 27 of Figure 1 as a double-acting amplitude-selective throttled hydraulic lots between the two energy storage 19 and 23 executed.
  • a stiffness of the energy storage 19 and 23 are bypassed for small amplitudes.
  • FIG. 4 shows a further gas spring damper device 1 similar to that shown in FIG.
  • the only difference between the hydraulic energy storage 19,23 connected additional hydraulic transmission member 27 is designed as a double-acting frequency-selective throttled temporary hydraulic passage, which corresponds to the passage shown in Figure 2.
  • a reduced dynamic stiffness results from a damped activation of the working spaces 9, 11 with one another. This is advantageously frequency-selective and essentially independent of a pressure difference between the energy storage 19 and 23 possible.
  • FIG. 5 shows another gas spring damper device 1 analogous to the gas spring damper devices shown in Figures 1 to 4.
  • the gas spring damper device 1 analogous to the gas spring damper devices shown in Figures 1 to 4.
  • Gas spring damper device 1 two of the additional hydraulic transmission members 27 on.
  • the additional hydraulic transmission members 27 are each connected in parallel to the hydraulic damping devices 17, 21 and each designed as a single-acting amplitude-selective hydraulic lots.
  • the additional transmission elements 27 low damping, so that for small amplitudes a comparatively low attenuation occurs.
  • FIG. 6 shows a further damping device 1 analogous to the damping device 1 shown in FIG. 5. The only difference is the two additional ones
  • hydraulic transmission members 27 each designed as a single-acting frequency-selective, throttled temporary hydraulic passages. The only difference is that they have a single action, with a pair of oscillating pistons being provided for each hydraulic damping device 17 and 21, their opening direction being connected counter to the blocking direction of the respectively parallel non-return valve of the respective hydraulic damping device 17, 21.
  • FIG 7 shows another gas spring damper device 1 analogous to the gas spring damper device 1 shown in Figures 3 and 4. The only difference is instead of the additional transfer member 27, an additional controllable hydraulic actuator 29 connected between the hydraulic energy storage 19 and 23.
  • the actuator 29 is present as a spring-return electrically actuated
  • Proportionalsperrventil 31 executed.
  • a short circuit or a bypass of the hydraulic energy accumulators 19, 23 take place in proportion to an electrical control signal.
  • this results in a reduced dynamic stiffness of the gas spring damper device by a damped activation of the working spaces 9, 11.
  • FIG. 8 shows another gas spring damper device analogous to the gas spring damper device 1 shown in FIGS. 1 and 2.
  • the only difference is provided by an additional hydraulic device 33 instead of the additional hydraulic transmission element 27.
  • the additional hydraulic device 33 is provided in the working piston 7 and has a bidirectionally dependent on a speed of the piston rod 15 transmission behavior. The speed of the piston rod 15 causes a pressure difference between the working spaces 9, 11, wherein the
  • Hydraulic device 33 is flowed through.
  • a reduced dynamic stiffness of the gas spring damper device 1 by a damped activation of the working spaces 9, 1 1 can be achieved.
  • FIG. 9 shows another gas spring damper device 1 analogous to the gas spring damper device 1 shown in FIG. 8.
  • the additional hydraulic device 33 is arranged outside the working cylinder 5, this being connected between the working chambers 9, 11 analogously to FIG.
  • the additional hydraulic device 33 according to FIG. 9 has a spring-returning, electrically actuatable further proportional shut-off valve 35 and, connected in series, a double-acting passive throttle 37.
  • the double-acting throttle 37 according to FIG. 9 is analogous to the double-acting or bidirectional throttle according to FIG. 8, but not adjustable in difference. So this one has two
  • the gas spring damper device 1 shown in Figures 1 to 9 operates on the principle of an active Einrohrdämpfers and has the
  • a reduction of the dynamic damper stiffness can take place, for example by about 80%.
  • This can advantageously be achieved in that, for example, in the case of an immersion movement, the displacement displaced by the piston rod 15 Hydraulic medium increases a working pressure of the gas spring damper device 1 in both hydraulic energy storage 19 and 23 evenly.
  • This can advantageously take place with comparatively little activation, that is to say preferably with a straight-ahead travel of the vehicle 3.
  • Hydraulic device 33 may be closed in the de-energized state.

Abstract

L'invention concerne un dispositif amortisseur à cartouche à gaz (1), en particulier pour un véhicule automobile (3), comprenant : - un cylindre de travail (5), - un piston de travail (7) monté de façon coulissante à l'intérieur du cylindre de travail (5) et divisant le cylindre de travail (5) en un premier espace de travail (9) rempli ou pouvant être rempli avec un fluide hydraulique (13) et un second espace de travail (11) rempli ou pouvant être rempli avec le fluide hydraulique (13), - une tige de piston (15) attribuée fixement au piston de travail (7) et plongeant dans le premier espace de travail (9), tige au moyen de laquelle de l'énergie hydraulique peut être introduite dans le dispositif amortisseur à cartouche à gaz (1) et prélevée, - un premier accumulateur d'énergie (19) attribué au plan hydraulique au premier espace de travail (9) au moyen duquel au moins une quantité partielle de l'énergie hydraulique peut être transformée, - un second accumulateur d'énergie hydraulique (23), attribué au plan hydraulique au second espace de travail (11), au moyen duquel au moins une autre quantité partielle de l'énergie hydraulique peut être transformée, - un dispositif générateur à moteur hydraulique (25) attribué au plan hydraulique aux deux espaces de travail (9, 11), au moyen duquel en supplément de l'énergie hydraulique peut être introduite facultativement dans le dispositif amortisseur à cartouche de gaz (1) et enlevée, - un premier dispositif d'amortissement hydraulique (17) monté entre le premier espace de travail (9) et le premier accumulateur d'énergie (19), - un second dispositif d'amortissement hydraulique (21) monté entre le second espace de travail (11) et le second accumulateur d'énergie (23). Afin de mettre à disposition un dispositif perfectionné d'amortisseur à cartouche à gaz (1), celui-ci présente au moins un élément de transmission (27) hydraulique supplémentaire présentant un comportement à la transmission dépendant d'une dynamique de déplacement de la tige de piston (15) plongeante.
PCT/EP2010/007365 2010-06-11 2010-12-03 Dispositif amortisseur à cartouche à gaz WO2011154026A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010023434.6 2010-06-11
DE201010023434 DE102010023434A1 (de) 2010-06-11 2010-06-11 Gasfederdämpfervorrichtung

Publications (1)

Publication Number Publication Date
WO2011154026A1 true WO2011154026A1 (fr) 2011-12-15

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WO (1) WO2011154026A1 (fr)

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WO2012149949A1 (fr) * 2011-05-03 2012-11-08 Daimler Ag Véhicule automobile terrestre de tourisme comportant un dispositif de découplage, ainsi que procédé de découplage de la carrosserie du véhicule automobile terrestre de tourisme
CN103722996A (zh) * 2014-01-10 2014-04-16 湖南大学 基于电储能元件的液压减振器能量回收系统及控制方法
WO2016096291A1 (fr) * 2014-12-15 2016-06-23 Zf Friedrichshafen Ag Amortisseur de vibrations et véhicule automobile
BE1024507B1 (nl) * 2017-01-31 2018-03-15 Shi Yan Frequentie afhankelijk actief ophangingsysteem
US20190047350A1 (en) * 2015-09-25 2019-02-14 Zf Friedrichshafen Ag Vibration Damper, Method For Operating A Vibration Damper, Control Device And Motor Vehicle
CN110273972A (zh) * 2019-07-08 2019-09-24 北京金风科创风电设备有限公司 阻尼器、风力发电机组的塔筒和风力发电机组
WO2019241650A1 (fr) 2018-06-14 2019-12-19 ClearMotion, Inc. Accumulateurs pour système de suspension active distribuée
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US11499535B2 (en) 2010-06-16 2022-11-15 ClearMotion, Inc. Integrated energy generating damper
US11635075B1 (en) 2014-06-25 2023-04-25 ClearMotion, Inc. Gerotor pump with bearing
US11745558B2 (en) 2013-03-15 2023-09-05 ClearMotion, Inc. Active vehicle suspension
US11760339B2 (en) 2014-04-02 2023-09-19 ClearMotion, Inc. Active safety suspension system
US11841035B2 (en) 2014-08-19 2023-12-12 ClearMotion, Inc. Apparatus and method for active vehicle suspension
US11892051B2 (en) 2018-02-27 2024-02-06 ClearMotion, Inc. Through tube active suspension actuator
US11919348B2 (en) 2008-04-17 2024-03-05 ClearMotion, Inc. Distributed active suspension system with an electrically driven pump and valve controlled hydraulic pump bypass flow path
US11964528B2 (en) 2019-01-03 2024-04-23 ClearMotion, Inc. Slip control via active suspension for optimization of braking and accelerating of a vehicle
US11965531B2 (en) 2017-02-12 2024-04-23 ClearMotion, Inc. Hydraulic actuator with a frequency dependent relative pressure ratio

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US8839920B2 (en) 2008-04-17 2014-09-23 Levant Power Corporation Hydraulic energy transfer
JP6396414B2 (ja) 2013-03-15 2018-09-26 クリアモーション，インコーポレイテッド 多経路流体ダイバータバルブ
US9702349B2 (en) 2013-03-15 2017-07-11 ClearMotion, Inc. Active vehicle suspension system
US9855814B2 (en) 2013-04-23 2018-01-02 ClearMotion, Inc. Active suspension with structural actuator
DE102014210701A1 (de) 2014-06-05 2015-12-17 Zf Friedrichshafen Ag Schwingungsdämpfer sowie Kraftfahrzeug
CN104455177A (zh) * 2014-10-20 2015-03-25 刁久新 汽车用主动自适应式减振器
EP3247577B1 (fr) 2015-01-23 2020-03-04 Clearmotion, Inc. Procédé et appareil de commande d'un actionneur
CN105134864B (zh) * 2015-09-30 2017-08-11 郑州比克新能源汽车有限公司 一种电动汽车电磁衬套
DE102016206434A1 (de) * 2016-04-15 2017-10-19 Zf Friedrichshafen Ag Schwingungsdämpfer sowie Kraftfahrzeug
CN117905837A (zh) * 2019-03-11 2024-04-19 动态清晰公司 压力补偿的主动悬架致动器系统

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