(19)
(11)EP 3 279 499 B1

(12)EUROPEAN PATENT SPECIFICATION

(45)Mention of the grant of the patent:
26.06.2019 Bulletin 2019/26

(21)Application number: 17001331.2

(22)Date of filing:  03.08.2017
(51)International Patent Classification (IPC): 
B60G 17/08(2006.01)
F16J 1/09(2006.01)
F16F 9/34(2006.01)
F16F 9/53(2006.01)
F16J 1/08(2006.01)
F16F 9/32(2006.01)
F16F 9/512(2006.01)

(54)

HYDRAULIC DAMPER HAVING SELF-ADJUSTING WEAR BAND

HYDRAULISCHER DÄMPFER MIT SELBSTEINSTELLENDEM VERSCHLEISSBAND

AMORTISSEUR HYDRAULIQUE DOTÉ D'UNE BANDE D'USURE AUTORÉGLABLE


(84)Designated Contracting States:
AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

(30)Priority: 05.08.2016 US 201662371254 P
15.06.2017 US 201715623859

(43)Date of publication of application:
07.02.2018 Bulletin 2018/06

(73)Proprietor: BeijingWest Industries Co. Ltd.
Beijing, (CN)

(72)Inventors:
  • Proeschel, Andrew Kegan
    Beavercreek, OH 45440 (US)
  • Tessier, Guy
    94120 Fontenay sous Bois (FR)

(74)Representative: Lukaszyk, Szymon 
Kancelaria Patentowa Lukaszyk Ul. Glowackiego 8/
40-052 Katowice
40-052 Katowice (PL)


(56)References cited: : 
WO-A1-2006/029421
US-A- 3 155 015
DE-A1- 4 342 755
US-B1- 6 386 343
  
      
    Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention).


    Description

    TECHNICAL FIELD



    [0001] A hydraulic damper assembly for a vehicle suspension system.

    BACKGROUND OF THE INVENTION



    [0002] Hydraulic damper/strut assemblies are commonly used in vehicle suspension systems for bearing a load and damping vibrations between a body and wheel assembly of the vehicle. An example of a hydraulic damper assembly is disclosed in U.S. Patent No. 3,155,015 to Orville Derdnand Genz which includes a housing that extends about and along an axis and defines an interior wall and a chamber for holding a fluid. A piston assembly that has a core is disposed in the chamber and is axially moveable in the chamber for providing a damping effect during movement of the piston assembly. A wear band is disposed about the core for engaging the interior wall of the housing during movement of the piston assembly to allow the strut to take on side load forces.

    [0003] An issue with such hydraulic damper assemblies is that the wear band and/or interior wall of the housing may erode over time, which may undesirably change the damping characteristics of the damper assembly. Accordingly there remains a need for improvements to hydraulic damper assemblies.

    [0004] Document DE 342755 A1 discloses a shock absorber. The separating piston which divides the inside of the work cylinder into two pressure chambers contains at least one additional flow path which connects these two chambers together. This additional flow path runs past the piston seal which projects at least partially into this additional flow path and in order to open and close same is designed as a sliding part displaceable in the separating piston. The piston seal is set displaceable in a ring-shaped outwardly open circumferential groove of the separating piston whose axial longitudinal extension is greater than that of the piston seal.

    SUMMARY OF THE INVENTION



    [0005] According to an aspect of the disclosure, a hydraulic damper assembly is provided. The hydraulic damper assembly includes a housing that extends about and along an axis and defines an interior wall and a chamber for holding a fluid. A piston assembly is disposed in the chamber and is axially moveable therein. The piston assembly includes a core. A wear band is disposed about the core and has an inside surface and an outside surface. The inside surface of the wear band defines at least one groove that is in fluid communication with the chamber for allowing the fluid to bias the wear band toward the interior wall of the housing during the passage of the fluid through the at least one groove during movement of the piston assembly, wherein said at least one groove is defined by a pair of spaced edge walls and a bottom surface disposed between said spaced edge walls, and said wear band defines at least one gap extending between first and second ends of said wear band and defining a pair of edges in spaced relationship with one another, and wherein said at least one groove is spaced from said at least one gap.

    [0006] According to another aspect of the disclosure, a hydraulic damper assembly is provided that includes a tubular housing that extends about and along an axis and defines an interior wall and a chamber. A piston assembly is disposed in the chamber and is axially moveable therein. The piston assembly includes a core that has a side surface. A piston ring is disposed about the core and presents an outer surface and an inner surface. At least one passage is defined between the side surface of the core and the inner surface of the piston ring. A wear band is disposed about the piston ring and has an inside surface and an outside surface and extends axially between a first end and a second end. The inside surface of the wear band defines at least one groove that is in fluid communication with the chamber for allowing the fluid to bias the wear band toward the interior wall of the housing during the passage of the fluid through the groove during axial movement of the piston assembly.

    [0007] The invention in its broadest aspect therefore provides a self-adjusting wear band that doesn't modify the damping characteristics of the damper assembly as the wear band or interior wall of the housing erode over time. More specifically, during movement of the piston assembly, the at least one groove on the inside surface of the wear band allows fluid to pass into the area between the piston core and the wear band, which biases the wear band against the interior wall of the tubular housing. This allows the wear band to automatically adjust for component wear.

    BRIEF DESCRIPTION OF THE DRAWINGS



    [0008] Other advantages of the present invention will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

    Fig. 1 is a perspective view of an embodiment of a piston assembly including a wear band disposed about a piston ring;

    Fig. 2 is a front cutaway view of an embodiment of a piston assembly and housing;

    Fig. 2A is a magnified view of a wear band in Fig. 2;

    Fig. 3 is a left side perspective view of an embodiment of a wear band;

    Fig. 4 is a right side perspective view of the wear band of Fig. 3;

    Fig. 5 is a front view of an embodiment of a wear band;

    Fig. 6 is a perspective cutaway view of the wear band of Fig. 5;

    Fig. 7 is a top view of the wear band of Fig. 5 in an open position to define a gap;

    Fig. 7A is a magnified view of an edge of the wear band of Fig. 7;

    Fig. 8 is a front cutaway view of the wear band of Fig. 5;

    Fig. 8A is a magnified view of a second end of the wear band of Fig. 8;

    Fig. 9 is a top view of the wear band of Fig. 5 in a closed position;

    Fig. 9A is a magnified view of a second end of the wear band of Fig. 9;

    Fig. 10 is a graph presenting durability data for a damper assembly including a wear band without a groove; and

    Fig. 11 is a graph presenting durability data for a damper assembly including a wear band with a groove.


    DESCRIPTION OF THE ENABLING EMBODIMENT



    [0009] Referring to the Figures, wherein like numerals indicate corresponding parts throughout the several views, a hydraulic damper assembly 20 is generally shown for use in a suspension system of a vehicle. It should be appreciated that the subject hydraulic damper assembly 20 could be utilized on various vehicles including, but not limited to, automobiles, motorcycles and all-terrain vehicles.

    [0010] As best illustrated in Fig. 2, the damper assembly 20 includes a tubular housing 22 that extends about and along a center axis A and defines an interior wall 24 and a chamber 26, 28. The housing 22 may be connected to a first component of the vehicle, such as a wheel assembly. A damping fluid, such as an MR fluid is contained in the chamber 26, 28. It should be appreciated that in certain embodiments, the interior wall 24 of the housing 22 may be chrome plated.

    [0011] As best illustrated in Figs. 1-2, a piston assembly 30 is disposed in the chamber 26, 28 and divides the chamber 26, 28 into a compression section 26 and a rebound section 28. The piston assembly 30 is axially moveable relative to the housing 22 and may be connected to a second component of the vehicle, such a body.

    [0012] The piston assembly 30 includes a core 32 that has a generally cylindrical shape and extends axially between a top surface 34 and a bottom surface 36 along a side surface 38. The top surface 34 of the core 32 defines a depression 40 along the axis A.

    [0013] A generally disc-shaped upper plate 42 abuts the top surface 34 of the core 32. The upper plate 42 defines an opening 44 that extends therethrough along the axis A. A rod 46 is received by the opening 44 of the upper plate 42 and the depression 40 of the core 32. The rod 46 is secured to the upper plate 42 and core 32 in the opening 44 and depression 40. A first seal 48 is disposed between the rod 46 and the core 32, and a second seal 50 is disposed between the rod 46, core 32 and upper plate 42. The seals 48, 50 inhibit fluid from passing between the piston and the core 32 / upper plate 42. The upper plate 42 further defines a plurality of circumferentially-spaced upper plate apertures 52 that each extend axially therethrough.

    [0014] A cushion seat 58 is disposed against the upper plate 42. Furthermore, a cushioning element 60 is disposed against the spring seat for cushioning the deceleration of the piston assembly 30.

    [0015] A generally disc-shaped lower plate 54 is disposed against the bottom surface 36 of the core 32. The lower plate 54 defines a plurality of lower plate apertures 56 that extend axially therethrough and are circumferentially spaced from one another, each in alignment with one of the upper plate apertures 52.

    [0016] A generally tube-shaped piston ring 62 is disposed radially about the core 32, upper plate 42 and lower plate 54. The piston ring 62 presents an outer surface 64 and an inner surface 66. A plurality of passages 68 are defined between the side surface 38 of the core 32 and the inner surface 66 of the piston ring 62, each in axial alignment with one of the upper plate apertures 52 and one of the lower plate apertures 56. The passages 68 allow the hydraulic fluid to pass therethrough during axial movement of the piston assembly 30 to provide the damping effect. It should be appreciated that one or more electromagnetic coils 69 (schematically shown in Fig. 2) may be integrated into the core 32 for providing a magnetic field across the passage 68 to change the viscosity of MR fluid contained therein to modify the damping characteristics of the damper assembly 20.

    [0017] The outer surface 64 of the piston ring 62 defines a recess 70 that extends annularly about the piston ring 62. A wear band 72 is received by the recess 70 of the piston ring 62. The wear band 72 extends axially between a first end 74 and a second end 76, and as illustrated in Figs. 2-3 and 7-9A, has an outside surface 78 and an inside surface 80. As shown in Figs. 8-9A, the wear band 72 tapers radially inwardly adjacent the first and second ends 74, 76. Referring to Figs. 1, 5, 7 and 8, the wear band 72 defines at least one gap 82 that extends between the first and second ends 74, 76 of the wear band 72 to present a pair of edges 83 in spaced relationship with one another. The gap 82 of the wear band 72 extends at an angle relative to the axis A. It should be appreciated that the angle of the gap 82 ensures that radial loads are carried by the outer surface 78 of the wear band 72.

    [0018] As best illustrated in Figs. 3, 4, 6, 7A and 8, the inside surface 80 of the wear band 72 defines at least one groove 84 that is in fluid communication with the chamber 26, 28. As best illustrated in Fig. 2A, the groove 84 allows fluid to pass into the area between the outer surface 64 of the piston ring 62 and inside surface 80 of the wear band 72 in the groove 84 during axial movement of the piston assembly 30, which therefore biases the wear band 72 toward the interior wall 24 of the housing 22. It should be appreciated that in embodiments of the hydraulic assembly in which no piston ring 62 is present, the fluid would pass directly between the side surface 38 of the core 32 and the inside surface 80 of the wear band 72 in the groove 84.

    [0019] In the example embodiment, the groove 84 extends between the first and second ends 74, 76 of the wear band 72. It should be appreciated that the groove could alternatively extend from only one of the first and second ends 74, 76 along a predetermined distance toward the other of the first and second ends 74, 76.

    [0020] It should be appreciated that any number of grooves 84 could be utilized, and the grooves 84 may be arranged in circumferentially and evenly spaced relationship with one another. In the example embodiment, each groove 84 extends axially along its entire length, but could alternatively extend at other angles or in other shapes. Furthermore, as best illustrated in Fig. 3, in the example embodiment the grooves 84 each are defined by a pair of spaced edge walls 87 and have a bottom surface 85 between the edge walls. It should be appreciated that the grooves 84 could have various cross-sectional shapes, e.g., an arc shape.

    [0021] It should be appreciated that biasing the wear band 72 against the interior wall 24 of the housing 22 allows the wear band 72 to automatically adjust for component wear. More specifically, biasing the wear band 72 radially outwardly ensures that the wear band 72 engages the interior wall 24 of the housing 22 even after the wear band 72 and/or interior wall 24 of the housing 22 have worn. As such, correct dimensional tolerancing of the piston ring 62, wear band 72, grooves 84 and interior wall 24 of the housing 22 provide improved durability lifespan of the damper assembly 20.

    [0022] Figs. 10 and 11 present durability performance characteristics between a an embodiment of an MR damper assembly 20 that is configured with a wear band 72 that does not include grooves 84, and an MR damper assembly 20 that is configured with a wear band 72 that includes grooves 84, respectively. More specifically, as illustrated in Fig. 10, the knee point of an on-state force velocity curve begins to shift as components of the damper assembly 20 experience wear. This is due to an additional area bypass from component wear, thus causing the MR damper assembly to lose low velocity on-state damping force at a high rate. On the other hand, as illustrated in Fig. 11, with a groove 84, the knee point shift of an on-state damping force as the wear occurs through the life of the damper assembly 20 is eliminated. In other words, Figs. 10 and 11 demonstrate that the groove 84 provides reduced on-state damping force loss (knee point shift) of the MR damper assembly 20 as wear occurs through the life of the MR damper / strut assembly 20.


    Claims

    1. A hydraulic damper assembly (20) comprising:

    a housing (22) extending about and along an axis and defining an interior wall (24) and a chamber (26, 28) for holding a fluid;

    a piston assembly disposed in said chamber (26, 28) and axially moveable therein;

    said piston assembly (20) including a core (32);

    a wear band (72) disposed about said core (32) and having an inside surface (80) and an outside surface (78);

    characterized in that said inside surface (80) of said wear band (72) defines at least one groove (84) in fluid communication with said chamber (26, 28) for allowing the fluid to bias said wear band (72) toward said interior wall (24) of said housing (22) during the passage of the fluid through said at least one groove (84) during the movement of said piston assembly (20),

    wherein said at least one groove (84) is defined by a pair of spaced edge walls (87) and a bottom surface (85) disposed between said spaced edge walls (87), and said wear band (72) defines at least one gap (82) extending between first and second ends (74, 76) of said wear band (72) and defining a pair of edges (83) in spaced relationship with one another, and wherein said at least one groove (84) is spaced from said at least one gap (82).


     
    2. The hydraulic damper assembly (20) as set forth in Claim 1 wherein said wear band (72) extends axially between a first end (74) and a second end (76), and said groove (84) extends from one of said first and second ends of said wear band (72) toward the other of said first and second ends (74, 76).
     
    3. The hydraulic damper assembly (20) as set forth in Claim 2 wherein said at least one groove (84) extends between said first and second ends (74, 76) of said wear band (72).
     
    4. The hydraulic damper assembly (20) as set forth in any one of Claims 1 to 3 wherein said at least one groove (84) extends axially along its entire length.
     
    5. The hydraulic damper assembly (20) as set forth in any one of Claims 1 to 4 wherein said at least one groove (84) includes a plurality of said grooves (84).
     
    6. The hydraulic damper assembly (20) as set forth in Claim 5 wherein said plurality of grooves (84) are spaced evenly from one another circumferentially about said inside surface (80) of said wear band (72).
     
    7. The hydraulic damper assembly (20) as set forth in Claim 6 wherein said plurality of grooves (84) each extend axially.
     
    8. The hydraulic damper assembly (20) as set forth in any one of Claims 1 to 7 further including a piston ring (62) disposed about said core (32) and presenting an outer surface (64) and an inner surface (66);
    said core (32) having a side surface (38);
    at least one passage (68) defined between said side surface (38) of said core (32) and said inner surface (66) of said piston ring (62); and
    said wear band (72) disposed about said piston ring (62) such that said fluid passes between said groove (84) and said outer surface (64) of said piston ring (62) during said movement of said piston assembly (20).
     
    9. The hydraulic damper assembly (20) as set forth in Claim 8 wherein said outer surface (64) of said piston ring (62) defines an annular recess (70) extending annularly about said axis, and said wear band (72) is disposed in said annular recess (70).
     
    10. The hydraulic damper assembly (20) as set forth in Claim 8 or 9 further including at least one magnetorheological coil (69) connected to said core (32) for selectively changing a viscosity of fluid passing through said passage (68) defined between said side surface (38) of said core (32) and said inner surface (66) of said piston ring (62).
     
    11. The hydraulic damper assembly (20) as set forth in any one of Claims 1 to 7 comprising:

    said housing (22) having a tubular form;

    said piston assembly (20) including a core (32) having a side surface (38);

    a piston ring (62) disposed about said core (32) and presenting an outer surface (64) and an inner surface (66);

    at least one passage (68) defined between said side surface (38) of said core (32) and said inner surface (66) of said piston ring (62);

    said wear band (72) disposed about said piston ring (62) and having said inside surface (80) and said outside surface (78) and extending axially between a first end (74) and a second end (76); and

    said inside surface (80) of said wear band (72) defining at least one groove (84) in fluid communication with said chamber (26, 28) for allowing the fluid to bias said wear band (72) toward said interior wall (24) of said housing (22) during the passage of the fluid through said groove (84) during the axial movement of said piston assembly (20).


     
    12. The hydraulic damper assembly (20) as set forth in Claim 11 wherein said at least one groove (84) extends from one of said first and second ends (74, 76) of said wear band (72) toward the other of said first and second ends (74, 76) of said wear band (72), said at least one groove (84) extends axially along its entire length, said at least one groove (84) includes a plurality of said grooves (84), said plurality of grooves (84) are spaced evenly from one another circumferentially about said inside surface (80) of said wear band (72), and said plurality of grooves (84) each extend axially.
     
    13. The hydraulic damper assembly (20) as set forth in Claim 11 or 12 further including at least one magnetorheological coil (69) embedded in said core (32) for selectively changing a viscosity of fluid passing through said passage (68) defined between said side surface (38) of said core (32) and said inner surface (66) of said piston ring (62).
     


    Ansprüche

    1. Eine hydraulische Dämpferbaugruppe (20), umfassend:

    ein Gehäuse (22), das sich herum und entlang einer Achse erschreckt sowie auch eine Innenwand (24) und Kammer (26, 28) zur Aufnahme der Flüssigkeit definiert;

    eine Kolbenbaugruppe, die in besagter Kammer (26, 28) angeordnet und darin axial beweglich ist;

    besagte Kolbenbaugruppe (20), mit einem Kern (32);

    ein Verschleißband (72), herum besagten Kernes (32) angeordnet und mit einer Innenfläche (80) sowie eine Außenfläche (78) verseht;

    dadurch gekennzeichnet, dass besagte Innenfläche (80) besagtes Verschleißbandes (72) mindestens eine Nut (84) in Flüssigkeitsübertragung mit besagter Kammer (26, 28) definiert, um die Flüssigkeit zu erlauben besagtes Verschleißbandes (72) gegen besagte Innenwand (24) besagter Gehäuse (22) zu beeinflussen während des Übergangs der Flüssigkeit durch besagten mindestens einen Nut (84) während einer Bewegung besagter Kolbenbaugruppe (20),

    worin besagte mindestens eine Nut (84) von ein Paar von beabstandeten Randwände (87) definiert wird und eine Bodenfläche (85), angeordnete zwischen den beabstandeten Randwände (87) und besagtem Verschleißband (72) definiert mindestens einen Spalt (82), der sich zwischen dem ersten und zweiten Ende (74, 76) besagtes Verschleißbandes (72) erschreckt und ein Paar von Ränder (83) definiert in einer beabstandeten Beziehung miteinander und worin besagte mindestens eine Nut (84) von besagter mindestens einer Nut (82) beabstandet wird.


     
    2. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 1, worin besagtes Verschleißband (72) sich axial zwischen einem ersten Ende (74) und einem zweiten Ende (76) erschreckt und besagte Nut (84) sich von einem der besagten ersten und zweiten Ende besagtes Verschleißbandes (72) gegen das andere von besagten ersten und zweiten Ende (74, 76) erschreckt.
     
    3. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 2, worin besagte mindestens eine Nute (84) sich zwischen besagtem erstem und zweitem Ende (74, 76) besagtes Verschleißbandes (72) erschreckt.
     
    4. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 1 zu 3, worin besagte mindestens eine Nut (84) sich axial entlang ihrer gesamten Länge erstreckt.
     
    5. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 1 zu 4, worin besagte mindestens eine Nut (84) besagte mehrere Nuten (84) enthält.
     
    6. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 5, worin besagte mehrere Nuten (84) gleichmäßig gegeneinander umfangsmäßig herum besagte Innenfläche (80) besagtes Verschleißbandes (72) beabstandet sind.
     
    7. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 6, worin jede der besagten mehrere Nuten (84) sich axial erschreckt.
     
    8. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 1 zu 7, ferner ein Kolbenring (62) umfassende, herum besagten Kern (32) angeordnet und eine Außenfläche (64) sowie eine Innenfläche (66) umfassende;
    besagter Kern (32), der mit einer Seitenfläche (38) verseht ist;
    mindestens ein Übergang (68), definiert zwischen besagter Seitenfläche (38) besagten Kernes (32) und besagter Innenfläche (66) besagten Kolbenringes (62); und
    besagtes Verschleißband (72), angeordnet um besagten Kolbenring (62), so dass besagte Flüssigkeit zwischen besagter Nut (84) und besagter Außenfläche (64) besagten Kolbenringes (62) während besagter Bewegung besagter hydraulischer Dämpferbaugruppe (20) strömt.
     
    9. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 8, worin besagte Außenfläche (64) besagtes Kolbenrings (62) eine ringförmige Vertiefung (70) definiert, die sich ringförmig herum besagte Achse erschreckt, und besagtes Verschleißband (72) in besagte ringförmige Vertiefung (70) angeordnet ist.
     
    10. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 8 oder 9, die ferner mindestens eine magnetorheologische Spule (69) umfasst, mit besagtem Kern (32) verbindet, um eine Viskosität der Flüssigkeit wahlweise zu ändern, die durch besagte Übergang (68) strömt, die zwischen besagter Seitenfläche (38) besagtes Kerns (32) und besagter Innenfläche (66) besagtes Kolbenrings (62) definiert wird.
     
    11. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 1 zu 7, umfassend:

    besagte Gehäuse (22) die rohrförmig ist;

    besagte Kolbenbaugruppe (20), einschließlich eines Kernes (32), der mit einer Seitenfläche (38) verseht ist;

    ein Kolbenring (62), das um besagten Kern (32) angeordnet und mit einer Außenfläche (64) sowie einer Innenfläche (66) verseht ist;

    mindestens ein Übergang (68), definiert zwischen besagter Seitenfläche (38) besagten Kernes (32) und besagter Innenfläche (66) besagten Kolbenringes (62);

    besagtes Verschleißband (72), das um besagten Kolbenring (62) angeordnet und mit besagter Innenfläche (80) sowie besagter Außenfläche (78) verseht ist, und sich axial zwischen erstem Ende (74) und zweitem Ende (76) erschreckt; und

    besagte Innenfläche (80) besagtes Verschleißbandes (72), die mindestens eine Nut (84) in Flüssigkeitsübertragung mit besagter Kammer (26, 28) definiert, um die Flüssigkeit zu erlauben besagtes Verschleißbandes (72) gegen besagte Innenwand (24) besagter Gehäuse (22) zu beeinflussen während des Übergangs der Flüssigkeit durch besagte Nut (84) während der axialen Bewegung besagter Kolbenbaugruppe (20).


     
    12. Die hydraulische Dämpferbaugruppe (20) nach Anspruch 11, worin besagte mindestens eine Nut (84) sich von einer der besagten ersten und zweiten Enden (74, 76) besagtes Verschleißbandes (72) gegen die andere der besagten ersten und zweiten Enden (74, 76) besagtes Verschleißbandes (72) erschreckt, besagte mindestens eine Nut (84) sich axial entlang ihrer gesamten Länge erschreckt, besagte mindestens eine Nut (84) umfasst besagte mehrere Nuten (84), besagte mehrere Nuten (84) gleichmäßig gegeneinander umfangsmäßig herum besagte Innenfläche (80) besagtes Verschleißbandes (72) beabstandet sind und jede der besagten mehrere Nuten (84) sich axial erschreckt.
     
    13. Die hydraulische Dämpferbaugruppe (20) nach einem der Ansprüche 11 oder 12, die ferner mindestens eine magnetorheologische Spule (69) umfasst, in besagtem Kern (32) eingebettet, um wahlweise eine Viskosität der Flüssigkeit, die durch besagte Übergang (68) strömt, die zwischen besagter Seitenfläche (38) besagtes Kerns (32) und besagter Innenfläche (66) besagtes Kolbenrings (62) definiert wird.
     


    Revendications

    1. Un ensemble amortisseur hydraulique (20) comprenant:

    un boîtier (22) s'étendant autour d'un axe et le long de celui-ci et définissant une paroi intérieure (24) et une chambre (26, 28) pour contenir un fluide;

    un ensemble à piston disposé dans ladite chambre (26, 28) et pouvant être déplacé axialement à l'intérieur de celle-ci;

    ledit ensemble à piston (20) comprenant un noyau (32);

    une bande d'usure (72) disposée autour dudit noyau (32) et ayant une surface interne (80) et une surface externe (78);

    caractérisé en ce que ladite surface interne (80) de ladite bande d'usure (72) définit au moins une rainure (84) en communication fluidique avec ladite chambre (26, 28) pour permettre au fluide de solliciter ladite bande d'usure (72) vers ladite paroi intérieure (24) dudit boîtier (22) pendant le passage du fluide à travers ladite au moins une rainure (84) pendant le déplacement dudit ensemble à piston (20),

    dans lequel ladite au moins une rainure (84) est définie par une paire de parois de bord espacées (87) et une surface inférieure (85) disposée entre lesdites parois de bord espacées (87), et ladite bande d'usure (72) définit au moins un espace (82) s'étendant entre la première et la seconde extrémité (74, 76) de ladite bande d'usure (72) et définissant une paire de bords (83) espacés l'un de l'autre, et dans lequel ladite au moins une rainure (84) est espacée dudit au moins un espace (82).


     
    2. Ensemble amortisseur hydraulique (20) selon la revendication 1, dans lequel ladite bande d'usure (72) s'étend axialement entre une première extrémité (74) et une seconde extrémité (76), et ladite rainure (84) s'étend depuis l'une desdites première et seconde extrémités de ladite bande d'usure (72) vers l'autre desdites première et seconde extrémités (74, 76).
     
    3. Ensemble amortisseur hydraulique (20) selon la revendication 2, dans lequel ladite au moins une rainure (84) s'étend entre lesdites première et seconde extrémités (74, 76) de ladite bande d'usure (72).
     
    4. Ensemble amortisseur hydraulique (20) selon l'une quelconque des revendications 1 à 3, dans lequel ladite au moins une rainure (84) s'étend axialement sur toute sa longueur.
     
    5. Ensemble amortisseur hydraulique (20) selon l'une quelconque des revendications 1 à 4, dans lequel ladite au moins une rainure (84) comprend une pluralité desdites rainures (84).
     
    6. Ensemble amortisseur hydraulique (20) selon la revendication 5, dans lequel ladite pluralité de rainures (84) sont espacées régulièrement les unes des autres de manière circonférentielle autour de ladite surface interne (80) de ladite bande d'usure (72).
     
    7. Ensemble amortisseur hydraulique (20) selon la revendication 6, dans lequel ladite pluralité de rainures (84) s'étendent chacune axialement.
     
    8. Ensemble amortisseur hydraulique (20) selon l'une quelconque des revendications 1 à 7, comprenant en outre un segment de piston (62) disposé autour dudit noyau (32) et présentant une surface extérieure (64) et une surface intérieure (66);
    ledit noyau (32) ayant une surface latérale (38);
    au moins un passage (68) défini entre ladite surface latérale (38) dudit noyau (32) et ladite surface intérieure (66) dudit segment de piston (62); et
    ladite bande d'usure (72) disposée autour dudit segment de piston (62) de telle sorte que ledit fluide passe entre ladite rainure (84) et ladite surface extérieure (64) dudit segment de piston (62) pendant ledit mouvement dudit ensemble à piston (20).
     
    9. Ensemble amortisseur hydraulique (20) selon la revendication 8, dans lequel ladite surface extérieure (64) dudit segment de piston (62) définit un évidement annulaire (70) s'étendant de manière annulaire autour dudit axe et dans lequel ladite bande d'usure (72) est disposée dans ledit évidement annulaire (70).
     
    10. Ensemble amortisseur hydraulique (20) selon les revendications 8 ou 9, comprenant en outre au moins un serpentin magnétorhéologique (69) connecté audit noyau (32) pour modifier sélectivement la viscosité du fluide passant à travers ledit passage (68) défini entre ladite surface latérale (38) dudit noyau (32) et ladite surface intérieure (66) dudit segment de piston (62).
     
    11. Ensemble amortisseur hydraulique (20) selon l'une quelconque des revendications 1 à 7, comprenant:

    ledit boîtier (22) ayant une forme tubulaire;

    ledit ensemble de piston (20) comprenant un noyau (32) ayant une surface latérale (38);

    un segment de piston (62) disposé autour dudit noyau (32) et présentant une surface extérieure (64) et une surface intérieure (66);

    au moins un passage (68) défini entre ladite surface latérale (38) dudit noyau (32) et

    ladite surface intérieure (66) dudit segment de piston (62);

    ladite bande d'usure (72) disposée autour dudit segment de piston (62) et ayant ladite surface interne (80) et ladite surface externe (78) et s'étendant axialement entre une première extrémité (74) et une seconde extrémité (76); et

    ladite surface interne (80) de ladite bande d'usure (72) définissant au moins une rainure (84) en communication fluidique avec ladite chambre (26, 28) pour permettre au fluide de solliciter ladite bande d'usure (72) vers ladite paroi intérieure (24) dudit boîtier (22) lors du passage du fluide à travers ladite rainure (84) lors du mouvement axial dudit ensemble à piston (20).


     
    12. Ensemble amortisseur hydraulique (20) selon la revendication 11, dans lequel ladite au moins une rainure (84) s'étend de l'une desdites première et seconde extrémités (74, 76) de ladite bande d'usure (72) vers l'autre desdites première et seconde extrémités (74, 76) de ladite bande d'usure (72), ladite au moins une rainure (84) s'étend axialement sur toute sa longueur, ladite au moins une rainure (84) comprend une pluralité desdites rainures (84), ladite pluralité de rainures (84) sont espacées régulièrement les unes des autres de manière circonférentielle autour de ladite surface interne (80) de ladite bande d'usure (72), et ladite pluralité de rainures (84) s'étendent chacune axialement.
     
    13. Ensemble amortisseur hydraulique (20) selon les revendications 11 ou 12, comprenant en outre au moins un serpentin magnétorhéologique (69) incorporé dans ledit noyau (32) pour modifier sélectivement la viscosité du fluide passant à travers ledit passage (68) défini entre ladite surface latérale (38) dudit noyau (32) et ladite surface intérieure (66) dudit segment de piston (62).
     




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    Cited references

    REFERENCES CITED IN THE DESCRIPTION



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    Patent documents cited in the description