• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a hydropneumatic element (1) for vehicles, in particular tracked vehicles, having a housing (2) which has a hydraulic damping device (3) - a hydraulic cylinder - and one with the damping device (3) via a rest position in a fully spring-loaded »position displaceable first separating piston (4) in operatively connected gas spring (5) contains. In order to avoid a complex temperature compensation when heating the gas of the gas spring (5), without causing a change in the equilibrium position of the vehicle, the invention proposes to build the hydraulic element (1) mechanically such that a temperature compensation by the use of a graded passive gas spring characteristic results, wherein the Hydrop element (1) is designed such that the Kennylienstufe in the range of the static position (equilibrium state between wheel load and Hydrop) results. The power level is now realized with only one gas volume.
    公开号:CH705371B1
    申请号:CH02728/12
    申请日:2011-05-31
    公开日:2016-01-29
    发明作者:Detlev Eckhoff
    申请人:Rheinmetall Landsysteme Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a hydropneumatic element for vehicles, in particular tracked vehicles.
    Hydropneumatic spring-damper elements, which are usually referred to briefly as hydrop elements, are known from DE 10 2008 026 680 A1. They serve, for example, for vibration damping of heavy all-terrain vehicles (for example, tracked vehicles) and consist essentially of a gas volume acting as a spring and an oil damper cooperating with the gas volume. For this purpose, a separating piston can be provided in a common cylindrical housing, which separates the gas volume from the oil-filled hydraulic volume, so that a dependent of the position of the separating piston spring action of the gas filling takes place. In the hydraulic volume is a connected to a piston rod load-bearing piston, which usually contains throttle holes, so that when driving the corresponding vehicle over bumps the oil compressed by the piston is forced through the throttle holes in a low pressure region of the hydraulic volume and results in a speed-dependent damping force.
    In particular, in the use of Hydrop-elements in military caterpillars relatively high heat generated by the high-frequency movements in these damper elements. The resulting increase in the gas temperature leads to a change in the pressure and force ratios of the gas spring and thus to a change in the static position (equilibrium position of wheel load and Hydrop element) of the piston rod of the vehicle. This then has, inter alia, an undesirable increase in the chain tension and possibly changes in the static position (vehicle height) result.
    For temperature compensation of the heat generated in the damper elements is therefore proposed in the aforementioned DE 10 2008 026 680 A1, to cool the heating hydraulic oil by means of corresponding cooling elements.
    DE 10 2008 025 482 A1 discloses a motion-dependent damping by means of set Tothübe or the suspension of damping. During compression, a back pressure arises in front of the diaphragm of a damping piston, so that the damping is suspended. If the spring travel is greater than the set dead stroke, the damping piston moves against a fixed stop, so that the oil volume to be displaced must be pressed exclusively through the orifice plate and thus generates the damping.
    In known dampers, such as the company Hemscheidt chassis technology GmbH and Co., two separate gas volume (primary and secondary gas volume) are used for temperature compensation of the spring characteristic, so as to realize the passive compensation within the damper.
    The invention has for its object to provide a hydrop-element of the type mentioned, in which a simple temperature compensation is possible.
    This object is achieved by the features of claim 1. Further, particularly advantageous embodiments of the invention disclose the dependent claims.
    The invention is based essentially on the idea of mechanical construction of the Hydrop element that results in a temperature compensation by the use of a stepped gas spring characteristic, wherein the Hydrop element is designed such that the corresponding force level when reaching the static position the piston rod occurs. For this purpose, a stepped piston and a cylinder and a high-pressure gas line are incorporated in a known hydrop-element, so this additionally integrated into this.
    The hydrop-element now comprises a hydraulic cylinder as a hydraulic damping device with a load-bearing piston which is connected to a hollow piston rod, wherein the oil-filled piston rod in a cylindrical first housing part of a fully rebound on a static in a fully Sprung position is arranged axially displaceable.
    The first housing part contains the fixed at the bottom end and extending coaxially into the first housing part auxiliary cylinder, wherein there is an annular space between the inner surface of the first housing part and the outer surface of the additional cylinder, along which the piston rod is displaceable, such in that an oil channel remains between the piston rod and the outer surface of the additional cylinder. In the auxiliary cylinder, an axially displaceable from an initial to an end position second separating piston is arranged, which separates a gas-filled first subspace of the inner cylinder of a filled with the hydraulic fluid second subspace of the auxiliary cylinder, the second subspace via a first throttle valve with the Interior of the piston rod is connected.
    The pneumatic gas spring comprises a second piston-containing second cylindrical housing part, which is separated by the first separating piston in a bottom-side third subspace and an axially located fourth subspace, wherein the third subspace via a second throttle valve and a first pipe with the Annulus of the first housing part and the fourth subspace are connected via a second pipe to the first subspace of the auxiliary cylinder.
    The first throttle valve, the dimensions of the second separating piston and the auxiliary cylinder and the gas pressure in the second housing part are chosen such that upon displacement of the piston rod from its fully rebound position into its static position of the second separating piston from its initial position to its final position is moved without causing a shift of the first separating piston from its rest position out and that further displacement of the piston rod after reaching the static position is only possible if the first separating piston - due to the bias of the gas of the gas spring - after reaching the maximum value of predetermined jumped force curve from its rest position is displaced.
    Preferably, in the auxiliary cylinder, a coaxially extending from the bottom end of the auxiliary cylinder into a portion of the inner space extending inner cylinder is arranged, which is connected on the bottom side with the second pipe. In addition, the second separating piston is a stepped piston, which is guided with its front narrower piston part through the side walls of the inner cylinder and with its rear-side wider piston part through the side walls of the additional cylinder region located in front of the inner cylinder. Due to the power transmission on the stepped piston is ensured in a simple manner that the separating piston is not moved until reaching the static position of the piston rod.
    In order to obtain the most space-saving design of the hydrop-element, the first and the second cylindrical housing part are arranged parallel to each other in a preferred embodiment of the invention, wherein the first and second pipes are integrated in a connecting the two housing parts third housing part.
    With the above variant, a robust temperature compensation without the use of sensors and additional assemblies for hydropneumatic suspension and damping elements is realized using only one gas piston. Especially this concept of a hydrops with stepped piston and only one gas volume realizes a simpler construction. The hydrops with stepped piston and two gas volumes are technically much more complex.
    With regard to operational safety, there are the advantages that gas loss can be seen from the outside, with an incorrect operation in the gas filling limited only to the filling of a gas volume, since only a gas spring must be filled. This filling can be done via a central filling interface on the vehicle. But then the hydrops no longer need to be expanded or completely relieved. A better access of the filling connections is guaranteed. In addition, an optimization of the rebound characteristic is possible, it can be covered a higher temperature range. The main piston rod guide can also be carried out in one stage, a telescoping is no longer a requirement.
    Further details and advantages of the invention will become apparent from the following, explained with reference to figures embodiments. Show it:<Tb> FIG. 1 <SEP> is a longitudinal section through a schematic representation of a hydropneumatic element according to the invention, in which the piston rod is in its «fully rebounded» position;<Tb> FIG. FIG. 2 shows the hydrop element shown in FIG. 1, in which the piston rod is in its static position; FIG.<Tb> FIG. FIG. 3 shows the hydrop-element shown in FIG. 1, with the piston rod in its "fully spring-loaded" position; FIG.<Tb> FIG. 4 <SEP> Diagrams showing the spring characteristic of the hydrop element according to the invention.
    In Fig. 1, 1 denotes a hydrop-element, for example, for a non-illustrated tracked vehicle. The hydrop-element 1 comprises a housing 2 for a hydraulic damping device - a hydraulic cylinder 3 - and for a (for example pneumatic) gas spring 5 which is in operative connection with the damping device via a first separating piston 4.
    The hydraulic cylinder 3 in turn comprises a load-bearing piston 6 which is connected to a hollow piston rod 7. The filled with a hydraulic fluid (oil) piston rod 7 is arranged axially displaceable in a cylindrical first housing part 8 of a "fully rebounded" via a static position in a "fully Sprung" position.
    The first housing part 8 also includes a fixed at the bottom end and extending coaxially in the first housing part 8 additional cylinder 9, wherein between the inner surface 10 of the first housing part 8 and the outer surface 11 of the auxiliary cylinder 9 results in an annular space 12, along which the piston rod 7 is displaceable, in such a way that between the piston rod 7 and the outer surface 11 of the auxiliary cylinder 9, an oil passage 13 remains.
    In the auxiliary cylinder 9, a coaxially extending from the bottom end into a portion of the inner space inner cylinder 14 is arranged. In addition, in the auxiliary cylinder 9 designed as a stepped piston 15 second separating piston is arranged axially displaceable from an initial to an end position. The stepped piston 15 is guided with its front narrow piston part 16 through the side walls of the inner cylinder 14 and with its rear wide piston member 17 through the side walls of the cylinder located in front of the inner cylinder 14 auxiliary cylinder region and therefore separates the gas filled with the first compartment 18 of the inner cylinder 14 of a with Oil as hydraulic fluid filled second subspace 19 of the auxiliary cylinder 9. The second subspace 19 is connected via a first throttle valve 20 with the oil-filled interior 21 of the hollow piston rod 7.
    The gas spring 5 comprises a first separating piston 4 containing cylindrical second housing part 22 which is connected via a third housing part 23 with the first housing part 8 and arranged parallel thereto.
    The second housing part 22 is separated by the first separating piston 4 in an oil-containing, bottom-side third sub-space 24 and an axially located, fourth subspace 25 containing gas. In this case, the third subspace 24 via a second throttle valve 26 and extending in the third housing part 23 first pipe 27 to the annular space 12 of the first housing part 8 and the fourth subspace 25 via a likewise extending in the third housing part 23 second pipe 28 to the first subspace 18th connected.
    The first throttle valve 20, the dimensions of the stepped piston 15 and the auxiliary cylinder 9 and the gas pressure in the second housing part 22 are chosen such that upon displacement of the piston rod 7 from its "fully rebounded" position in its static position (Fig. 2) of the stepped piston 15 is moved from its initial position to its end position, without causing a displacement of the first separating piston 4 from its rest position out.
    Hereinafter, starting from Fig. 1, the sequence of movement of the inventive hydrop-element will be described in more detail. In this case, the piston rod 7 is "fully rebounded", the stepped piston 15 is in its initial position, and the first separating piston 4 is in its rest position, in which it is located on a mechanical stop on its hydraulic fluid (oil) limiting side. In addition, the gas is biased according to the static wheel load and the oil-containing sub-areas completely filled (bubble-free).
    The piston rod 7 then moves from the position "fully rebounded" (Fig. 1) in their illustrated in Fig. 2 static position (equilibrium state of wheel load and Hydrop element). The oil volume to be displaced in accordance with the piston rod cross section and the piston stroke displaces the stepped piston 15 axially from its starting position into its end position. Both oil volumes are coordinated.
    The stepped piston 15 pushes the gas from the first compartment 18 through the pipe 28 into the fourth compartment 25 and compresses the already biased gas according to the displaced compression volume. Due to the power transmission on the stepped piston 15 ensures that the first separating piston 4 does not move until reaching the static position of the piston rod 7.
    Now moves the piston rod 7 of the static position in the position "fully rebounded" (Fig. 3), for example, in an off-road vehicle, so shifts the first separating piston 4, as soon as the pressure on the oil side is higher than on the gas side. The path of the first separating piston 4 is determined by the displaced oil volume from the piston rod, and the force curve above the static position is dependent on the bias of the gas volume.
    The mode of action of the hydropod element according to the invention with regard to the temperature compensation when assuming its static position will be explained in more detail below with the aid of the spring characteristics shown in FIG. In this case, the force exerted on the piston 6 in kN is shown as a function of the displacement of the piston 6 in mm in the diagram.
    As can be seen from the spring characteristic of the inventive hydropneumatic element designated I, takes in the movement of the piston 6 and thus also the piston rod 7 of the "fully rebounded" position (Fig. 1) in the static position (Fig. 2) the force due to the movement of the stepped piston 15 and the associated additional compression of the gas in the subspace 25 to. Due to the high pressure in the fourth sub-chamber 25 is carried out at increasing the force on the piston 6 initially no displacement of the first separating piston 4. Only after exceeding a pressure difference of about 75 kN, the pressure on the acted upon by the oil side of the first separating piston 4 is higher as on the gas-facing side, and the piston 6 and the piston rod 7 can be moved (with simultaneous displacement of the separating piston 4) to its "fully Sprung" position.
    Due to the sudden increase in the force in the static position of the piston rod 7 results in the desired temperature compensation. For if the temperature of the gas increases in the subspace 25 due to the increase in the oil temperature in the interior 21 of the piston rod 7, although the gas pressure in the fourth subspace 25 increases, but only the first separating piston 4 is held in its rest position.
    The spring characteristic of the known from DE 10 2008 026 680 A1 Hydrop element is shown by the reference numeral II in Fig. 4. An erratic increase in force in the region of the static position comparable to spring characteristic I is missing in this characteristic curve.
    LIST OF REFERENCE NUMBERS
    [0034]<Tb> 1 <September> hydropneumatic element<Tb> 2 <September> Housing<Tb> 3 <September> attenuator<tb> 4 <SEP> first separating piston<Tb> 5 <September> gas spring<Tb> 6 <September> Piston<Tb> 7 <September> piston rod<tb> 8 <SEP> (first) housing part<Tb> 9 <September> Auxiliary cylinder<tb> 10 <SEP> inner surface<tb> 11 <SEP> outer surface<Tb> 12 <September> annulus<Tb> 13 <September> oil passage<Tb> 14 <September> inner cylinder<tb> 15 <SEP> second separating piston, stepped piston<tb> 16 <SEP> narrow piston part<tb> 17 <SEP> wide piston part<tb> 18 <SEP> first subspace (inner cylinder)<tb> 19 <SEP> second subspace (additional cylinder)<tb> 20 <SEP> first throttle valve<Tb> 21 <September> Interior<tb> 22 <SEP> (second) housing part<tb> 23 <SEP> third housing part<tb> 24 <SEP> third subspace<tb> 25 <SEP> fourth subspace<tb> 26 <SEP> second throttle valve<tb> 27 <SEP> first pipeline<tb> 28 <SEP> second pipe
    权利要求:
    Claims (5)
    [1]
    1. Hydrop-element for vehicles, in particular tracked vehicles, with a filled with a hydraulic fluid hydraulic cylinder (3) having a first housing part (8) and a displaceably mounted in the same between a «fully rebound» position and a fully «sprung» position piston rod (7) and with a gas spring (5) with a second housing part (23) and a displaceable in the same first separating piston (4) having a with an interior (21) of the hydraulic cylinder (3) connected third subspace (24) of a with Gas-filled fourth subspace (25) separates, characterized in that in the hydraulic cylinder (3) an additional cylinder (9) is arranged, with a displaceable between an initial position and an end position stage piston (15) which between one with the fourth subspace (25) the gas spring (5) connected to the first subspace (18) of the additional cylinder (9) and one with an interior (21) of the hydraulic cylinder (3) composite a narrow piston part (16) of the stepped piston (15) in the first part space (18) and a wider piston part (17) in the second part space (19) is displaceable.
    [2]
    2. Hydrop-element according to claim 1, characterized in that in the connection between the second subspace (19) with the interior (21) of the hydraulic cylinder (3), a first throttle valve (20) is arranged.
    [3]
    3. Hydrop-element according to one of claims 1 or 2, characterized in that in the connection between the interior (21) of the hydraulic cylinder (3) and the third sub-space (24), a second throttle valve (26) is arranged.
    [4]
    4. Hydrop-element according to one of claims 1 to 3, characterized in that the piston rod (7) is formed as a hollow cylinder and the auxiliary cylinder (9) is coaxially surrounded by the first housing part (8), such that between an inner surface (10 ) of the first housing part (8) and an outer surface (11) of the additional cylinder (9) is an annular space (12) in which the piston rod (7) is displaceable.
    [5]
    5. Hydrop-element according to one of claims 1 to 4, characterized in that within the auxiliary cylinder (9) an inner cylinder (14) is arranged, which surrounds the first subspace (18) and the narrow piston part (16), the first subspace (18) limiting, in the inner cylinder (14) is guided while the broad piston part (17), the second part space (19) delimiting, in the auxiliary cylinder (9) is guided.
    类似技术:
    公开号 | 公开日 | 专利标题
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    同族专利:
    公开号 | 公开日
    DE102011009079B4|2021-10-07|
    AT514781A5|2015-03-15|
    WO2011154107A1|2011-12-15|
    DE102011009079A1|2011-12-15|
    AT514781B1|2015-06-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2287627B1|1974-10-11|1979-02-09|Sirven Jacques|
    DE3044016A1|1980-11-22|1982-06-24|Fichtel & Sachs Ag, 8720 Schweinfurt|Temp. corrected hydropneumatic damper - has limited flow connection to high pressure reservoir|
    SU1059318A1|1982-08-04|1983-12-07|Волгоградский Ордена Трудового Красного Знамени Политехнический Институт|Pneumatic hydraulic spring|
    DE3427902C2|1984-07-28|1988-01-14|Franz Dr.-Ing. 7530 Pforzheim De Tuczek|
    DE19724015A1|1997-06-06|1998-12-10|Hydac Technology Gmbh|Suspension system|
    DE19849222B4|1998-10-26|2004-02-12|Zf Sachs Ag|Self-pumping hydropneumatic shock absorber with internal level control|
    JP2001191778A|2000-01-11|2001-07-17|Yamaha Motor Co Ltd|Suspension device for four-wheel car|
    AT390304T|2004-01-30|2008-04-15|Curtiss Wright Antriebstechnik|HYDROPNEUMATIC SUSPENSION DEVICE AND METHOD FOR CONTROLLING THE SAME|
    DE602006005365D1|2006-09-13|2009-04-09|Horstman Defence Systems Ltd|suspension device|
    EP2052889B1|2007-10-26|2016-06-15|Strömsholmen AB|Hydropneumatic spring-damping device and method of operation of a hydropneumatic spring-damping device|
    DE102008025482A1|2008-05-27|2009-12-03|Rheinmetall Landsysteme Gmbh|Motion-dependent damping|
    DE102008026680A1|2008-06-04|2009-12-17|Rheinmetall Landsysteme Gmbh|Hydropneumatic damper device|DE102013011288A1|2013-07-08|2015-01-08|Rheinmetall Landsysteme Gmbh|Adaptive Hydrop drive for tracked vehicles|
    法律状态:
    2014-03-14| NV| New agent|Representative=s name: WAGNER PATENT AG, CH |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102010023238|2010-06-09|
    DE102011009079.7A|DE102011009079B4|2010-06-09|2011-01-21|Hydropic element|
    PCT/EP2011/002680|WO2011154107A1|2010-06-09|2011-05-31|Hydrop element|
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