• 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:
    2.1 Such a switchable clutch or brake with a first clutch or brake part and with a second clutch or brake part which is rotatably disposed relative to the first clutch or brake part about a clutch or brake rotation axis, with . at least one through a fluid. movable pressure piston, as well as with at least one coupling or brake disc which is axially displaceable relative to the coupling or brake rotation axis, so that the first and the second coupling or brake part rotate with each other when the pressure piston is set into motion to link, as well as: with ten. least one. roller bearing which is placed between the first and the second coupling or brake part is known. 2.2 According to the invention, the roller bearing is provided with a fluid-driven auxiliary piston which exerts an axial load on the roller bearing when the fluid is set in motion and which is set in motion depending on the pressure piston set in motion by the fluid. can be through the fluid. 2.3 Use as a hydraulic switchable coupling.
    公开号:NL2018447A
    申请号:NL2018447
    申请日:2017-03-01
    公开日:2017-09-26
    发明作者:Kister Marcel；Datema Hendrik；Glomm Matthias
    申请人:Gkn Stromag Ag；
    IPC主号:
    专利说明:

    NLP201061A
    Fluid-driven switchable clutch or brake
    The invention relates to a fluid-driven switchable clutch or brake with a first clutch or brake part and with a second clutch or brake part that is rotatably disposed relative to the first clutch or brake part about a clutch or brake rotation axis with at least one pressure piston movable by a fluid, as well as with at least one coupling or brake disk axially displaceable relative to the coupling or brake rotation axis, the first and the second are moved when the pressure piston is set into motion. coupling coupling or brake part rotatably with each other, as well as with at least one roller bearing, which is placed between the first and the second coupling or brake part.
    A fluid driven switchable coupling is generally known. The known switchable coupling is driven by hydraulic oil and comprises two coupling parts which can be rotated relative to each other and which can be coupled to each other via a slat package in the form of a plurality of slat discs for the transmission of a torque. A hydraulically movable pressure piston is provided for this purpose, which is displaceable axially relative to the lamella discs and compresses the lamella discs when loaded with pressure. A torque transfer between the first and the second coupling part is hereby automatically obtained. In order to ensure relative rotational mobility of the two coupling parts, at least one roller bearing is provided which is biased with respect to the coupling rotation axis via spring elements in the axial direction.
    It is an object of the invention to provide a fluid driven switchable clutch or brake of the aforementioned type, which allows lower maintenance costs.
    This object is achieved in that the roller bearing is provided with a fluid-driven auxiliary piston which exerts an axial load on the roller bearing when the fluid is set in motion and which can be set in motion depending on the pressure piston set in motion by the fluid. by the fluid. The solution according to the invention achieves an axial bias of the at least one roller bearing only during a switching operation of the switchable clutch or brake, that is to say when the pressure piston is set in motion by the fluid. In an aerated state of the pressure piston, the auxiliary piston is also not set in motion by means of the fluid. The solution according to the invention makes it possible to significantly increase the service life of the at least one roller bearing. This is because axial loading of the at least one roller bearing only takes place during a switching operation and a corresponding switched state of the switchable clutch or brake. In the aerated state of the switchable clutch or brake, on the other hand, the at least one roller bearing is not set in motion by the auxiliary piston. According to the invention, the switchable clutch or brake comprises at least one axially displaceable clutch or brake disc. Preferably, a plurality of clutch or brake slides are provided in the form of lamella discs, which are alternatively assigned to one or the other coupling part for transmission, and which define a plurality of friction surfaces which are pressed against each other under axial pressure by the pressure piston about the torque transfer. The solution according to the invention is provided in the same way for a coupling as for a brake. The invention preferably relates to a hydraulic switchable clutch or brake, which uses hydraulic oil as fluid and therefore as pressure medium.
    In an embodiment of the invention, the auxiliary piston is provided with a branch line derived from a main line for supplying fluid to the pressure piston, which branch line can be supplied with fluid and can be aerated together with the main line. The branch line advantageously comprises a plurality of axially extending fluid channels arranged over a coupling or brake circumference. Alternatively or additionally, the branch line may have an annular space coaxial with respect to the clutch or brake rotation axis.
    In a further embodiment of the invention, the main line extends substantially radially and the branch line extends at least partially axially within the first coupling part. The first coupling part is preferably placed radially inwards with respect to the second coupling part.
    In a further embodiment of the invention, the auxiliary piston is axially connected to a roller bearing ring of the roller bearing. The auxiliary piston is advantageously connected to a roller bearing ring of the roller bearing which is located radially inside the roller bearing relative to the clutch or brake rotation shaft, so as to act axially on the roller bearing ring.
    In a further embodiment of the invention, the branch line is formed by at least one axially extending fluid channel that leads to the auxiliary piston. The at least one fluid channel opens into a piston chamber, which is arranged annularly coaxially with respect to the coupling or brake axis of rotation and is delimited by a preferably also annular auxiliary piston. The auxiliary piston lies axially against the corresponding rolling bearing ring of the rolling bearing. The piston chamber connects axially opposite the roller bearing ring of the roller bearing to the auxiliary piston.
    In a further embodiment of the invention, the at least one roller bearing is permanently pre-stressed axially by a mechanical spring device. The mechanical spring device causes a permanent axial force on a roller bearing ring of the roller bearing in the same axial direction as the additional axial tension exerted by the auxiliary piston. The axial biasing force exerted by the mechanical spring device is considerably smaller than the axial force exerted by the fluid or the roller bearing by pressing the auxiliary piston. In the case of a clutch or brake that is not being operated, no fluid is active and therefore no additional axial force acts on the roller bearing. Instead, the rolling bearing is axially biased exclusively by the mechanical spring device. The rolling bearing is advantageously designed as a ball bearing.
    In a further embodiment of the invention the mechanical spring device is designed such that the spring device exerts a permanent axial bias on the auxiliary piston in the direction of the roller bearing of the roller bearing. As a spring device, at least one corrugated ring, at least one plate spring, or a plurality of axially extending helical compression springs arranged uniformly over the circumference of the coupling or brake can be arranged.
    In a further embodiment of the invention the spring device is designed as a plate spring acting on the auxiliary piston. The disc spring extends annularly coaxially to the clutch or brake rotation shaft. The annular plate spring may have a flat or a corrugated contact surface on the roller bearing ring of the roller bearing.
    Further advantages and features of the invention follow from the claims and from the preferred embodiment of the invention described below, which is explained with reference to the drawings.
    FIG. 1 shows a cross-sectional view of an upper half of an embodiment of a switchable coupling, which is substantially symmetrical in rotation, and
    FIG. 2 is an enlarged view of a portion II of the coupling of FIG. 1.
    A hydraulically switchable coupling 1 according to figures 1 and 2 comprises a first coupling part 2 in the form of a coupling housing and a second coupling part 3 in the form of an inner body arranged within the coupling housing. Both coupling parts 2 and 3 are rotatably mounted with respect to a coupling rotation shaft D. In a manner not further shown, a feed shaft is axially inserted in a coaxial coupling passage with respect to the coupling rotation axis D, which axis comprises hydraulic supply connections, in order to effect a hydraulic supply of the switchable coupling 1 in a manner described below . In the assembled state, the feed shaft is rotationally connected to the inner body of the coupling and thus forms, together with the inner body of the coupling, the inner, second coupling part 3.
    The inner coupling part 3 carries an annular pressure piston 4 which is axially displaceable with respect to the axis of rotation D of the coupling. The piston 4 is connected to a pressure chamber 7 which is hydraulically pressurized in a manner described below. The pressure piston 4 is held in its aerating position shown in Fig. 1 via a plurality of helical compression springs 6, which are uniformly distributed over the circumference of the coupling. During hydraulic pressurization, the pressure piston 4 is axially displaced in the direction of a plurality of coupling discs 5, which are formed by inner and outer slats. The inner slats are rotatably connected to the inner coupling part 3, while the outer slats are rotatably connected to the coupling part 2 formed as a coupling housing. The coupling discs 5 form a slat package of eight inner slats and seven outer slats, each of which has a writing ring shape and define opposing friction surfaces. On an opposite side of the pressure piston 4 axially to the lamella package formed by the coupling discs 5, an axial displaceability of the coupling discs 5 is limited by an end disc which is not further specified. The end disc is ring-shaped and attached to the inner body of the coupling via a screw connection. The end disc is hereby part of the inner coupling part 3. The outer coupling part 2 is rotatably arranged with the aid of two rolling bearings relative to the inner coupling part 3, wherein only the left-hand rolling bearing 8 in Fig. 1 is described in more detail below. The rolling bearing 8 comprises a radial inner rolling bearing ring 9, as well as a radial outer rolling bearing ring 10, between which a row of bearing balls are arranged. The inner roller bearing ring 9 is placed on an outer casing of the feed shaft of the inner coupling part 3, while the outer roller bearing ring 10 is axially retained on an inner circumference of an end wall of the coupling housing serving as the outer coupling part 2.
    In order to be able to provide the pressure piston 4 hydraulically with pressure, the pressure chamber 7 is hydraulically connected via a main line 13 to hydraulic supply lines of the supply shaft. The main line 13 is formed by a plurality of main channels arranged uniformly over the coupling circumference and extending radially in the inner body of the coupling. The main line 13 is furthermore provided with an annular chamber 13a, from which a branch line 14 is branched axially towards the roller bearing 8, which branch line is formed by a plurality of fluid channels arranged parallel to each other and uniformly distributed over the coupling circumference. The fluid channels of the branch line 14 are provided with a substantially reduced cross-sectional area relative to the radially extending flow channels of the main line 13, as can be seen in particular from FIG. 2. The fluid channels of the branch line 14 open into a fluid chamber 17, which is designed to be coaxial with respect to the coupling axis of rotation D. The fluid chamber 17 is on the one hand axially bounded by the inner body of the coupling. On the other hand, the fluid chamber 17 is bounded axially as well as radially outwards by an annular auxiliary piston 11, which axially abuts the radially inner roller bearing ring 9. For the auxiliary piston 11, the fluid chamber 17 forms a piston chamber in which the auxiliary piston 11 is axially slidable. The auxiliary piston 11 can be provided with hydraulic pressure in axially opposite direction to the pressure piston 4. The auxiliary piston 11 is positioned axially movably with respect to the inner coupling part 3.
    The auxiliary piston 11 is kept axially under pressure by a mechanical spring device 12 in the direction of the inner roller bearing ring 9. In the embodiment according to Figs. 1 and 2, the mechanical spring device 12 is formed by an annular plate spring which is placed in the fluid chamber 17. The disc spring 12 is supported, on the one hand, on the end wall of the inner body of the coupling and, on the other hand, on a corresponding piston surface of the auxiliary piston 11, as can be easily seen from Fig. 2. The disc spring of the mechanical spring device 12 is built into the fluid chamber 17 under permanent bias, so that the auxiliary piston 11 undergoes a permanent axial force through the spring device 12 in the direction of the inner roller bearing ring 9. As a result, the inner roller bearing ring 9 is permanently slightly axially shifted relative to the outer roller bearing ring 10, so that the roller balls of the roller bearing 8 are radially as well as axially free of play between the outer roller bearing ring 10 and the inner roller bearing ring 9. detained. The outer roller bearing ring 10, as can be clearly seen from Fig. 2, is axially retained without play between an axial stop and an axial locking ring, which are not further specified.
    The non-switched aeration state of the switchable coupling 1 is shown with reference to Figs. 1 and 2. In order to switch the switchable coupling 1 and thereby connect the inner coupling part 3 to the outer coupling part 2 for transmitting a torque, the main line 13 is hydraulically supplied over the supply shaft, whereby the pressure piston 4 is axially driven in the direction of the slat package is shifted, which is formed by the coupling discs 5. As a result, the coupling discs 5 are pressed against each other as well as against the closing disc, whereby torques are automatically transmitted via the different friction surfaces between the inner coupling part 3 and the outer coupling part 2. With the hydraulic pressure of the main pipe 13, the annular chamber 13a also becomes automatic hydraulically pressurized. Because the branch line 14 to the annular chamber 13a and also to the fluid chamber 17 is open, the auxiliary piston 11 is also automatically pressurized hydraulically axially in the opposite direction to which the pressure piston 4 is pressurized. As a result, the auxiliary piston 11 is additionally axially pressed against the inner roller bearing ring 9 in the direction of the pre-tensioning of the spring device 12, so that a freedom of play of the roller balls between the inner roller bearing ring 9 and the outer roller bearing ring 10 is improved. As soon as the hydraulic pressure in the pressure chamber 7 is reduced again in order to aerate the switchable coupling, the helical compression springs 6 push the pressure piston 4 back into its aerated starting position according to Fig. 1. The reduction of the hydraulic pressure is based on the branch line 14 communicating by means of fluid flow also continues into the fluid chamber 17, as a result of which the auxiliary piston 11 is additionally brought under hydraulic pressure. In the aerated state of the switchable coupling 1, therefore, only the axial biasing force of the spring device 12 acts on the auxiliary piston 11 and therefore on the inner roller bearing ring 9.
    权利要求:
    Claims (8)
    [1]
    A fluid-driven switchable clutch or brake with a first clutch or brake part (2) and with a second clutch or brake part (3) which relative to the first clutch or brake part (2) around a clutch or brake brake rotation shaft (D) is rotatably mounted, with at least one pressure piston (4) movable by a fluid, as well as with at least one coupling or brake disk (axially displaceable relative to the coupling or brake rotation shaft (D)) 5), when the pressure piston (4) is set into motion, to rotate the first and the second coupling or brake part (2, 3) in a rotationally fixed manner with each other, and also with at least one roller bearing (8), which between the first and the second clutch or brake part (2, 3) are arranged, characterized in that the roller bearing (8) is provided with a fluid driven auxiliary piston (11) which, when set in motion by the fluid, has an axial load on the rolling bearing (8), and which depending on a movement of the pressure piston (4) through the fluid can be set in motion by the fluid.
    [2]
    Fluid-driven switchable clutch or brake according to claim 1, characterized in that the auxiliary piston (11) is provided with a branch line (14) derived from a main line (13) for supplying fluid to the pressure piston (4), which together with the main line (13) can be supplied with fluid and can be aerated.
    [3]
    Fluid-driven switchable clutch or brake according to claim 2, characterized in that the main line (13) extends substantially radially and the branch line (14) extends at least partially axially within the first coupling part (3).
    [4]
    The fluid-driven switchable clutch or brake according to claim 1, characterized in that the auxiliary piston (11) is axially connected to a roller bearing ring (9) of the roller bearing (8).
    [5]
    Fluid-driven switchable clutch or brake according to one of the preceding claims, characterized in that the branch line (14) is formed by at least one fluid channel axially extending in the first coupling part (3), which channel to the auxiliary piston (11) performs.
    [6]
    Fluid-driven switchable clutch or brake according to one of the preceding claims, characterized in that the at least one roller bearing (8) is permanently biased axially by a mechanical spring device (12).
    [7]
    Fluid-driven switchable clutch or brake according to claim 6, characterized in that the mechanical spring device (12) is designed such that the spring device (12) on the auxiliary piston (11) has a permanent axial bias in the direction of the roller bearing -ring (9).
    [8]
    Fluid-driven switchable clutch or brake according to claim 7, characterized in that the spring device (12) is designed as a plate spring acting on the auxiliary piston (11).
    类似技术:
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    同族专利:
    公开号 | 公开日
    DE102016204454B3|2017-05-24|
    NL2018447B1|2018-06-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2014050315A1|2012-09-26|2014-04-03|ジヤトコ株式会社|Friction clutch|
    EP2905496A1|2012-10-04|2015-08-12|Jatco Ltd|Lubricating structure for friction engagement element of automatic transmission|
    WO2014097841A1|2012-12-21|2014-06-26|ジヤトコ株式会社|Clutch control device for automatic transmission|
    WO2014168038A1|2013-04-11|2014-10-16|日産自動車株式会社|Clutch piston structure|
    WO2015072912A1|2013-11-18|2015-05-21|Scania Cv Ab|Clutch device for a retarder|
    DE202010017006U1|2010-12-21|2011-03-03|Stromag Ag|Fluid-operated clutch or brake|
    法律状态:
    2020-11-04| MM| Lapsed because of non-payment of the annual fee|Effective date: 20200401 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102016204454.0A|DE102016204454B3|2016-03-17|2016-03-17|Fluid operated clutch or brake|
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