• 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 differential with two output shafts (3, 4) and a lock, with one of the output shafts (4) rotatably connected to the basket or web (2) of the differential gear (1) is connectable, the lock a shift sleeve (9). having, which is rotatably connected to this output shaft (4) and mounted coaxially displaceable and has a final toothing (19) which is engageable with a by the basket or web (2), preferably complementarily formed, toothing (20) directly into engagement and wherein a hydraulic adjusting device (11, 12) for the shift sleeve (9) is provided, with which the shift sleeve (9) from a release position into an engagement position with the toothing (20) displaceable and while maintaining the contact pressure in the engaged position, the Actuating device (11, 12) to a pressure build-up unit (60) with a hydraulic low-pressure line (48) and to a pressure relief unit (62) with a hydraulic Ho chdruckleitung (49) is connectable, via the low pressure line (48) the shift sleeve (9) is adjustable from its release position to its engaged position and the pressure pressure of the shift sleeve (9) is maintained in its engaged position on the high pressure line (49), wherein a check valve (45) prevents backflow of pressurized fluid from the high-pressure line (49) into the low-pressure line (48) and when the high-pressure line (49) is depressurized, the sliding sleeve (9) can be returned to its release position.
    公开号:AT511442A4
    申请号:T14652011
    申请日:2011-10-10
    公开日:2012-12-15
    发明作者:Wilhelm Ing Oberaigner
    申请人:Wilhelm Ing Oberaigner；
    IPC主号:
    专利说明:

    1
    The invention relates to eirr * AdSgletetisgetriebe 'according to the preamble of claim 1.
    Such differential gear with locks are known for example from DE 102004020863 A1 or DE 10303984 A1 in principle known.
    Locks can be used as a transverse lock for the drive axles of vehicles. However, barriers can be used in the same way as longitudinal barriers, for example in a transfer case.
    The lock of differential can be operated by hydraulic cylinders. Such switching cylinders can be connected via a switching pin with a switching tube and act directly on the shift sleeve. Such systems can not afford a large holding or locking force due to their design. These known locking clutches, such as those shown schematically in Fig. 2, for example, have a flank angle of the teeth, which is about 0 ° or they have a negative flank angle or a deposit on the dog teeth, which are associated with considerable disadvantages. Such claw toothing, once engaged, is difficult to release and prone to significant wear. The production of such claw toothing is complex.
    If, however, a positive flank angle is used, as shown schematically in Fig. 3, then considerable forces are required to hold the lock under load in engagement. However, these forces are difficult to apply by an operating unit. In the case of a hydraulic actuation of the lock very large shift cylinder would be required to apply the holding forces, or smaller shift cylinder, which are subjected to very high pressures.
    Large shift cylinders require very large actuation volumes, so that a rapid switching on and off of the lock is difficult. If, on the other hand, a solution with a high switching cylinder pressure were realized, then this pressurization forces a high-pressure hydraulic system, in particular the pump must be able to build up very high pressures. Such a hydraulic system leads to high costs, unfavorable acoustic behavior and requires relatively high pump drive torques.
    The object of the invention is to provide a lock for a differential, which is technically simple and reliable locking and unlocking allows. The locking and unlocking should be done quickly in order to take into account changed driving conditions quickly.
    These objects are achieved in a differential gear according to the invention that the adjusting device to a pressure build-up unit with a hydraulic low-pressure line and to a pressure relief unit with a hydraulic 2
    High pressure line can be connected to the pressure line, the sliding sleeve is adjustable from its release position into its engaged position and maintained via the high pressure line, the contact pressure of the sliding sleeve in its engaged position and pressure relief of the high pressure line, the shift sleeve is traceable to its release position. Due to the positive flank angle of preferably 6 ° to 9 °, a rapid opening of the barrier is achieved, which occurs immediately in the construction of the cylinder pressure.
    In a preferred embodiment of the invention it is provided that the low-pressure line is guided by an oil reservoir via an oil pressure pump, a switching valve and a check valve to the adjusting device or the sliding sleeve, that the high-pressure line is guided by the adjusting device via a pressure relief unit back to the oil reservoir and that Control unit is provided, with which the switching valve, the pressure relief unit and optionally the oil pump are controlled.
    According to the invention, the actuation pressure of the shift cylinder to be applied by the pump is further selected to be low, which is sufficient for a rapid, single engagement of the lock. In order to avoid unwanted disengagement of the engaged, hydraulically pressed lock, a spring-loaded check valve is provided in the hydraulic circuit, which prevents the operating pressure from increasing to the cylinder pressure. The hydraulic system is thus advantageously divided into a high and a low pressure area. Leakage in the high-pressure area may, under certain circumstances, lead to a slow disengagement of the barriers. By a continuous application of the operating pressure can be counteracted. When the cylinder pressure falls below the operating pressure, for example, when no locking moments act, opens the check valve and thus enables the compensation of lost by leakage volumes.
    It is advantageous if the final toothing and the toothing represent the only rotationally locked connection between this output shaft and the differential. According to the invention, no further connections or locking units are required to lock the output shaft to be locked in rotation with the differential, resulting in a simple structure. The hydraulic pressure load in the locked system is sufficient to ensure a corresponding locking in all operating situations.
    It is advantageous if it is provided that the end toothing and the toothing each have a positive flank angle, that is to say an angle between the flanks of the teeth and the tooth base, which is 6 ° or more and is preferably between 6 ° and 9 ° , If this angle is selected, the cylinder pressure need not be too high to engage the end gear and spline. 3
    The hydraulic contact pressure, inking the edges between the teeth ends the overcoming of frictional forces and thus the rapid unlocking. This is further assisted if the final toothing and the toothing are made of steel and optionally lubricated with oil. It results in a robust and durable barrier.
    In a preferred embodiment it can be provided that the differential gear is designed as a bevel gear differential or planetary gear or that the output shaft via the shift sleeve with the input shaft, in particular basket, the differential gear is connectable. Furthermore, the lock according to the invention can also act between the two output shafts of the differential gear. In principle, the lock can also be used without a differential, for example as a clutch for shiftable four-wheel drives.
    A simple construction of the lock results when the slidably mounted on the output shaft shift sleeve axially with an annular piston of a, preferably annular cross-section possessing, hydraulic cylinder is adjustable, which is arranged fixed in position on the output shaft housing and / or differential housing.
    To compensate for the respective different speeds, it can be provided that for decoupling between the rotationally fixedly mounted annular piston and the shift sleeve, a rotary or compensating bearing is arranged, via which the annular piston of the hydraulic cylinder, the shift sleeve pressure-loaded. Thus, the annular piston remains drehinvariant, whereas the shift sleeve freely rotates with the output shaft.
    In order to assist the unlocking or to bring the shift sleeve quickly disengaged from the cooperating with her component of the differential gear, it can be provided that at least one of the shift sleeve loading and pushing into its release position spring unit is provided, the spring force to lock the final toothing with the teeth exerted pressure of the piston is directed opposite. It is structurally advantageous if the spring unit, preferably a helical compression spring, surrounds the output shaft and is supported on a supported by the output shaft disc.
    A rapid response under different operating conditions and an exact function of the differential gear is given when a pressure fluid reservoir is connected to the pressure fluid supply circuit of the hydraulic cylinder and / or when the pressure release of the shift sleeve for the opening of the lock and for a termination of the engagement between the final toothing and the Gearing a switchable pressure relief unit, eg a switchable 4 • Φ 4 »4 • · • · • ·
    Multi-way valve, in the DruckfluidVers6 * r £ jufi§sRf6te * ä & b hydraulic cylinder is turned on.
    A significant advantage is achieved when the control unit of a brake control system, in particular anti-lock braking system (ABS) is connected to the pressure relief unit and the pressure relief unit can be acted upon by the control unit in the event of braking to be assisted with ABS opening signals, Since in an ABS-assisted braking Differential locks are in principle turn off, the differential gear according to the invention is an advantage that can be unlocked very easily, so that an ABS braking can be initiated immediately due to the rapid unlocking of the lock.
    A particular embodiment of the differential gear provides that the end teeth on the end face of the, preferably cylindrical, sliding sleeve and the toothing on the basket or web surrounding the output shaft, each in the form of axially extending to the output shaft teeth are formed.
    Furthermore, the invention also relates to a vehicle with a differential gear with a lock for Querverrieglung one of the axles of the differential gear and / or longitudinal locking of a transfer case and / or Längsverrieglung the drive shaft of the vehicle engine closer or directly driven by the engine differential with the basket or Bridge this differential gear, In other types of differential gear, it is also possible in principle to connect the two output shafts together to achieve the blocking effect with the differential lock according to the invention.
    In the following the invention will be explained in more detail for example with reference to the drawing. Fig. 1 shows a lockable differential gear in a schematic sectional view. Fig. 2 and Fig. 3 show schematically locking teeth. Fig. 4a shows schematically an executable variant of the hydraulic system, with non-switched differential lock. Fig. 4b shows schematically an embodiment of the hydraulic system, with switched differential lock. Fig. 5 shows schematically the basic structure of the hydraulic system for the differential lock according to the invention.
    In Fig. 1, a differential or axle drive 1 is shown. Such a module can be used in a similar form both as a front axle module or as a rear axle module. In a comparable form, such a module can also be provided or designed as Durchtriebsachsmodul.
    In the present case, the differential gear 1 is designed as a bevel gear differential. In principle, the differential gear according to the invention could also be designed as a planetary differential. 5 • * * · I * · ··· «• ♦ · ♦ * I · * · I ·» • ♦ * * l * * * * «« «* * * ·«
    The non-illustrated, non-illustrated, manual or automatic transmission, which is output via an output shaft 33, is transmitted via a bevel pinion 34 to the ring gear 35 and from there to the differential carrier 2. About the balancing pin 39 which is rigidly connected to the basket 2, bevel gears 36 are driven, which are rotatably mounted on the balancing pin 39. Usually, two differential gears 36 are used; Advantageously, four differential gears are used for differential with locks.
    The Ausgteichsräder 36 apply the applied torque to the Achswellenräder 38 and thus directly on the two drive shafts 3 and 4 from. This is usually achieved by means of splines between the axle shaft gears 38 and the drive shafts 3 and 4.
    With such a differential or differential gear 1 a dynamic and safe cornering is achieved. However, it is sometimes necessary to turn off the compensation function achieved by the differential. In the event that e.g. the drive shaft 3 has no or only a poor traction would remain without lock the wheel with good traction on the drive shaft 4 and the power would be reduced via the wheel, which is located on the drive shaft 3. The vehicle itself would not move. These principles of a differential gear are known.
    By a mechanical transverse lock, the differential or differential can be overridden. This is done, as shown in FIG. 1 can be seen by the drive shaft 4 is connected directly to the differential carrier 2. In the same way, of course, the drive shaft 3 can be connected instead of the drive shaft 4 with the differential carrier 2.
    Such a connection between the drive shaft 4 and the differential carrier 2 is achieved via a shift sleeve 9, which is mounted axially displaceable but secured against rotation on the drive shaft 3 or on the drive shaft 4. This shift sleeve 9, for example, with a spline 37 on the drive shaft 4 rotationally fixed, that is rotatable with the drive shaft 4, be stored.
    If one pushes the shift sleeve 9 in the direction of the differential carrier 2, so locks a locking teeth or end teeth 19, which is advantageously carried by the end face of the shift sleeve 9, in a corresponding toothing 20 on the differential carrier 2 and thus, as in Fig. 2 and 3, the differential carrier 2 with the drive shaft 4 rotatably connected.
    The actuation of the shift sleeve 9 takes place via a ring cylinder 12 which is connected to a hydraulic pressure fluid supply line or high-pressure line 49, such as this one is shown in FIG. 4a, for example. 9Pressurized and adjusted. The pressure built up in the pressure fluid supply line 49 moves an annular piston 11, which is pressurized by the annular cylinder 12 and the shift sleeve 9 axially adjusted on the axle shaft 4 in the direction of the differential cage 2 and the toothing 20 located thereon. The annular piston 11 is only axially displaceable, but otherwise fixed to the housing, that is firmly connected to the housing 31 of the axle shaft 3 or 4 and / or the housing 32 of the differential. In order to achieve a rotational speed compensation between the stationary annular piston 11 and the rotating shift sleeve 9, a bearing element 10 is present or interposed between these components to decouple the shift sleeve 9, which rotates at input speed with respect to the fixed annular piston 11.
    Since liquids are incompressible, the annular piston 11 can no longer escape or retreat after pressurization and while maintaining the pressure in the high-pressure fluid circuit 40. Thus, the lock between the drive shaft 3 or 4 and the differential carrier 2 is switched on permanently and the applied to the engine output shaft 33 input torque for propulsion of the vehicle via both axle shafts 3 and 4.
    A disadvantage of the dog teeth according to FIG. 2 is that they do not switch off quickly and safely under load. Under pressure, the intermeshing teeth wedged and can not solve quickly even with a pressure reduction. In order to avoid this, it is provided, as shown in FIG. 3, that the end toothing and the toothing each have a positive flank angle, that is to say an angle between the flanks of the teeth and the tooth base, which is 6 ° or more, and preferably between 6 and 9 °.
    It may also be provided that at least one of the shift sleeve 9 loading and pushing into its release position spring unit 13 is provided, whose spring force is directed opposite to the pressure applied to the locking of the end teeth 19 with the teeth 20 pressure of the piston. This spring unit 13 pushes the shift sleeve 9 back to its initial position for rapid release of the lock. A simple construction results when the spring unit, preferably a helical compression spring, surrounds the output shaft 4 and is supported on a disc 14 supported by the output shaft 4. The required rapid shutdown, as required in novel braking systems, in particular ABS braking systems, is supported; important for this are the selected angle of the end teeth 19 and the toothing 20 and the hydraulic pressure load or the ability to terminate the hydraulic pressure load and the lock abruptly. 7 * · Μ * · * I · · · · · · ·········································
    In Fig. 5, the GrundstruktCir hydrate fifksystetrrs * is shown schematically. From an oil reservoir 41 oil is removed. A pressure buildup unit 60 is switched by an electronic control unit 23 and can apply a higher actuation pressure ρθ from an output pressure level Po. A spring-loaded check valve 45 establishes the connection from the low-pressure line 48 to the high-pressure line 49 and the hydraulic actuator 61 or the adjusting device 11, 12. The spring loaded check valve 45 prevents pressurized fluid from the actuator 61 from flowing back into the low pressure line 48. In this way, it is ensured that the cylinder pressure pz of the high-pressure line 49, which is dependent on the external load, can not lead to an increase in the actuating pressure pB in the low-pressure line. The check valve 45 restricts the high pressure to the high pressure part of the system. The pressure build-up in the high pressure part is done by an external load of the hydraulic cylinder and the control part 11, 12 in operation and can not be actively influenced. Without check valve 45 would flow according to the resulting pressure drop from the high pressure part of pressurized fluid in the low pressure part and raise the pressure there. By the spring-loaded check valve 45, however, a backflow of fluid and thus a pressure-related reaction to the low-pressure part is prevented. As a result, cost-effective, compact components can be used in the low-pressure part.
    The electronic control unit 23 further controls the pressure relief unit 62. The pressure relief unit 62 allows a rapid lowering of the cylinder pressure pz to the output pressure p0. The line 40 serves as a drain from the actuator 61. The expired fluid volume can flow into the oil reservoir 41 or be fed into the pressure build-up unit 60. A partial supply of the pressure buildup unit 60 from the conduit 40 has the advantage of reducing the likelihood that air will be drawn. FIGS. 4a and 4b schematically show an example of a concrete, executable hydraulic system, wherein the structure can be traced back to the main assemblies shown in FIG. FIGS. 4a and 4b differ in that in FIG. 4a the state of the hydraulic system is shown with the lock open, while FIG. 4b shows the state of the hydraulic system when the lock is switched on. The hydraulic system is supplied via a tank 41, via the inlet and outlet line 40 and a hydraulic pump 42 with hydraulic fluid. The drive of the hydraulic pump 42 can be effected in particular by an electric motor or by a mechanical coupling with gear elements, for example the differential carrier 2. A pressure relief valve 43 is used to limit the operating pressure to a defined level and represents a * Abstgftei'dng' against * any faults in the system.
    An oil filter 50 may be provided to filter the oil from dirt particles. The oil filter 50 may be provided with a differential pressure valve 51, which opens a filter bypass at excessive pressure drop. The oil filter 50 and the associated differential pressure valve 51 can be arranged both on the suction side and on the pressure side of the hydraulic pump 42.
    An intended pressure fluid reservoir 15 guarantees fast switching times that could not be realized by a hydraulic pump 42 alone. With the memory 15 fast pressure increases are achieved.
    The hydraulic pump 42 may be designed to be switched off in order to avoid the energy intake and sound radiation of the pump in normal ferry operation. In this operating state could lead to an undesirable loss of pressure in the pressure fluid reservoir 15. To avoid this loss, a spring-loaded check valve 46 may be provided which prevents backflow of pressurized fluid in the direction of the pump.
    A 2/2 way valve 44 and a 2/2 way valve 18 are used to connect and disconnect the differential lock, the switching of the 2 / 2Wegeventile 18.44 takes place either mechanically or via an electrical control unit 23. In principle, a hydraulic control of the 2/2. 2-way valves conceivable. It is advantageous that due to the return springs of the two 2 / 2Wegeventile 18, 44 in case of failure of the electrical control unit 23, the differential lock is automatically opened.
    In the state shown in Fig. 4a, the differential lock is not switched. The 2/2 way valve 44 is in blocking division, so that no pressure is built up via the low-pressure line 48. The spring-actuated check valve 45 connects the low-pressure line 48 to the high-pressure line 49. In the state shown in FIG. 4a, both the low-pressure line 48 and the high-pressure line 49 are depressurized or have the outlet pressure p0. The fluid in the high-pressure line 49 acts with its pressure on the hydraulic cylinder 12. The 2/2-way valve 18 is in the open position, so that fluid volume from the high-pressure line 49 can flow into the drain 40. As a result, a rapid return of the hydraulic cylinder 12 is ensured in its initial position. Another, optionally adjustable, pressure relief valve 47 is in the state shown in Fig. 4a with non-switched differential lock in each case inactive, since the high-pressure line 49 is depressurized or has only the output pressure po.
    In the state shown in Fig. 4b, the differential lock is switched. The 2/2 way valve 44 is in the open position, so that the low pressure line 48 is acted upon by the actuation pressure pB. The spring-operated check valve 45 9 connects the low-pressure line 48 of the up-hole 49. In the state shown in FIG. 4 b, the low-pressure line 48 has the actuation pressure p B. The high-pressure line 49 acts on the hydraulic cylinder 12. The high-pressure line 49 has the cylinder pressure pz which is greater than or equal to the actuation pressure pB, whereby any influences of the check valve 45 are neglected. About the spring-operated check valve 45 ensures that a pressure increase in the high pressure line 49 does not lead to a pressure increase in the low pressure line 48. An increase in pressure above the actuation pressure p0 can occur due to loads on the lock during operation. The 2 / 2Wegeventil 18 is in the blocking position, so that the fluid volume from the high pressure line 49 can not flow the drain 40. As a result, locking of the hydraulic cylinder 12 is ensured in its end position. About the spring-loaded check valve 45, the Nachfluss of pressurized fluid is made possible, if it has come in the high pressure area leaks. Of course, the check valve 45 also ensures a rapid filling of the hydraulic cylinder 12, if the differential lock is switched on. The pressure in the low-pressure line 48 and in the high-pressure line 49 can be monitored by the control unit 23.
    For overload protection another, optionally adjustable, pressure relief valve 47 is provided to correspond to extreme pressures that can occur during operation in special situations. When the cylinder pressure pz exceeds the operating pressure pB, there is substantially a proportionality between cylinder pressure pz and the torque transmitted from the differential lock. The limiting of the hydraulic pressure can be used advantageously to protect the drive train from overloading. Likewise, the pressures can be limited, so that the hydraulic components can be protected from impermissibly high pressures.
    Once the pressure relief unit 18 is in flow position, the pressure medium flows back into the container 41 and the spring unit 13 pushes the piston 11 in its initial position.
    It is particularly advantageous, as shown in Figs. 1,4a, 4b and 5, when connected to the pressure relief unit 18, the control unit of an ABS combustion system and the pressure relief unit 18 from the controller 23 in the case of assisted with ABS braking with Opening signals can be acted upon. With the control unit 23, a pressure drop in the pressure fluid circuit 39 can be achieved immediately and quickly and the piston 11 can be returned to its original position.
    Of particular advantage is the procedure according to the invention for the creation of differential gears for vehicles provided with permanent four-wheel drive.
    It is noted that with the blocking division of a directional valve throughout that switching position is to be understood, in which no flow is possible. 10
    It will be noted that in principle other shapes and embodiments of the hydraulic cylinder 12 and the piston 11 are possible. It could also be provided a plurality of along the circumference of the axle 3 or 4 distributed hydraulic adjusting devices or piston-cylinder units for the shift sleeve 9.
    Similarly, a plurality of spring units may be provided surrounding the axle shaft 3 or 4 for resetting the shift sleeve 9.
    The pressure fluid reservoir 15 is connected between the check valve 46 and the switching valve 44 to the low pressure line 48.
    权利要求:
    Claims (13)
    [1]
    11

    1. differential gear with two output shafts {3, 4) and a lock with which one of the output shafts (4) rotatably connected to the basket or web (2) of the differential gear (1) is connectable, the lock a shift sleeve (9) having, which is rotatably connected to this output shaft (4) and mounted coaxially displaceable and has a final toothing (19) which is directly engageable with a by the basket or web (2), preferably complementarily formed, toothing (20) and wherein a hydraulic adjusting device (11, 12) for the shift sleeve (9) is provided, with which the shift sleeve (9) from a release position into an engagement position with the toothing (20) displaceable and while maintaining the contact pressure in the engaged position durable. characterized in that the adjusting device (11, 12) to a pressure build-up unit (60) with a hydraulic low pressure line (48) and to a pressure relief unit (62) with a hydraulic high pressure line (49) can be connected, via the low pressure line (48) the shift sleeve (9) is adjustable from its release position into its engaged position and via the high pressure line (49) the contact pressure of the sliding sleeve (9) is maintained in its engaged position, wherein a check valve (45) backflow of pressurized fluid from the high pressure line (49) in the low pressure line (48) prevents and pressure relief of the high-pressure line (49), the shift sleeve (9) is traceable to its release position.
    [2]
    2. Differential according to claim 1, characterized in that the low-pressure line (48) from an oil reservoir (41) via an oil pressure pump (42), a switching valve (44) and the check valve (45) to the adjusting device (11, 12) is guided, the high-pressure line (49) is guided by the adjusting device (11, 12) back to the oil container (41) via a switching valve (18) and a control unit (23) is provided, with which the switching valve (44), the switching valve (18 ) and optionally the oil pump (42) are controlled.
    [3]
    Third differential gear according to claim 1 or 2, characterized in that the end toothing (19) and the toothing (20) represent the only rotationally locked connection between said output shaft (4) and the differential gear (1) and / or that the final toothing (19) and the teeth (20) each have a positive flank angle (w), that is, an angle between the flanks (21) of the teeth and the 12 1 1 t > (* * * Ι a *) * * * * tooth base (22), which lies vdfaucf & Wei ^ le ZWisCPibTi 8 * and 9 ° and / or that the final toothing (19) and the toothing (20) are made of steel and optionally oil lubricated.
    [4]
    4. Differential according to one of claims 1 to 3, characterized in that the differential (1) is designed as bevel gear or planetary gear with bevel gears and / or that the output shaft (4) via the sliding sleeve (9) with the basket (2) of the Differential (1) is connectable and / or that on the output shaft (4) slidably mounted shift sleeve (9) axially of at least one, preferably annular, piston (11) at least one, preferably annular cross-section possessing, hydraulic cylinder (12) is adjustable, which is arranged fixed in position on the output shaft housing (31) and / or differential housing (32).
    [5]
    5. Differential according to one of claims 1 to 4, characterized in that for decoupling between the rotatably mounted piston (11) and the sliding sleeve (9) a rotary or compensating bearing (10) is arranged, via which the piston (11) of the Hydraulic cylinder (12), the shift sleeve (9) pressure-loaded.
    [6]
    6. differential according to one of claims 1 to 5, characterized in that at least one the shift sleeve (9) loading and pushing into its release position spring unit (13) is provided whose spring force to lock the end teeth (19) with the toothing (20 ) exerted pressure of the piston (11) is directed opposite.
    [7]
    7. A differential according to claim 6, characterized in that the spring unit (13), preferably a helical compression spring, the output shaft (4) surrounds and is supported on one of the output shaft (4) carried disc (14).
    [8]
    8. Differential according to one of claims 1 to 7, characterized in that to the low pressure line (48) of the hydraulic cylinder (12), a pressure fluid reservoir (15) is connected.
    [9]
    9. Differential according to one of claims 1 to 8, characterized in that for pressure relief of the high-pressure line (49) or the sliding sleeve (9) for the opening of the lock and for a termination of the engagement between the 13 • * t * * * 4) of the final gearing (19) and of the differential pressure relief unit (62) a switchable multiway valve (18) in the high pressure line (49) is switched on.
    [10]
    10. A differential according to one of claims 1 to 9, characterized in that the control unit (23) for the pressure relief unit (18), the control unit of an ABS combustion system is connected and the pressure relief unit (18) from the control unit (23) in the case of ABS to be supported braking with opening signals can be acted upon.
    [11]
    11. Differential according to one of claims 1 to 10, characterized in that optionally adjustable overpressure valve (47) is provided to limit the hydraulic pressure in the high-pressure line (49) at the top and / or by the shift sleeve (9) transmitted torque to limit upward.
    [12]
    12. Differential according to one of claims 1 to 11, characterized in that the end toothing (19) on the end face of the, preferably tubular or cylindrical shaped, sliding sleeve (9) and the toothing (20) on the basket or web (2) Output shaft (4) surrounding each in the form of axially to the output shaft (4) extending teeth (25) are formed.
    [13]
    13. Vehicle with at least one driven by the vehicle engine differential gear according to one of claims 1 to 12, with a lock for Querverrieglung one of the axle shafts (3, 4) of the differential gear (1) or Langsverrieglung the drive shaft of the vehicle engine closer or directly from the engine driven differential gear with the basket or web (2) of this differential gear (1). Vienna, October 10, 2011
    类似技术:
    公开号 | 公开日 | 专利标题
    DE102012016235B4|2016-11-03|Actuator arrangement for a drive train
    DE102004033439B4|2006-11-23|Powertrain for a motor vehicle
    AT512581B1|2013-10-15|DRIVE ARRANGEMENT
    DE102009005410B4|2012-04-12|Actuating arrangement and method for connecting a drive axle in the drive train of a motor vehicle and drive arrangement
    DE112014001283T5|2015-11-26|Two-speed drive module
    DE10052259B4|2009-10-15|Emergency unlocking device for the parking brake of a motor vehicle
    AT8780U1|2006-12-15|FRICTION COUPLING WITH HYDRAULIC ACTUATOR AND DRIVE UNIT WITH AT LEAST ONE SUCH
    AT512343B1|2013-08-15|DRIVE ARRANGEMENT WITH HYDRAULIC ACTUATION
    DE102015116936A1|2016-04-21|Doppelkolbenaktuator
    DE102015214037A1|2017-01-26|Parking brake system
    EP3227587A2|2017-10-11|Parking lock device
    DE102016109553A1|2017-11-30|System for actuating a parking brake
    WO2010139558A1|2010-12-09|Arrangement comprising at least one dog clutch
    AT511442B1|2012-12-15|DIFFERENTIAL
    DE202013008955U1|2014-02-18|limited slip differential
    DE102007024736B3|2008-06-12|Locking cylinder with fluidic slide bearing has supporting body as supporting and bearing body with supporting and bearing surface and counter supporting and bearing surface of second axial bearing in form of fluidic slide bearing
    EP3084221B1|2018-02-14|Automotive vacuum pump with switchable coupling
    EP3084220B1|2019-10-09|Automotive propulsion unit with combustion engine and switchable vacuum pump
    DE202016107084U1|2018-03-19|Planetary gear and powershift transmission
    EP1902891B1|2009-01-07|System and method for driving tandem axles
    EP1077825A1|2001-02-28|Driving device
    DE102020004982A1|2022-01-20|Automatic transmission for a motor vehicle and motor vehicle
    DE102016002198A1|2016-09-01|Output transmission group for a drive train of a mobile machine
    DE102013223613A1|2015-05-21|Parking lock system for a motor vehicle transmission
    DE102019108944A1|2020-10-08|Transmission for a drive train of a motor vehicle and motor vehicle
    同族专利:
    公开号 | 公开日
    AT511442B1|2012-12-15|
    DE102012109336A1|2013-04-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPS59199331A|1983-04-26|1984-11-12|Honda Motor Co Ltd|Controller for differential lock apparatus|
    DE10303984A1|2003-02-01|2004-09-02|Daimlerchrysler Ag|Axle linkage for commercial vehicles has a differential lock for coupling a compensating linkage housing to an axle shaft with a positive fit and resistance to torque|
    AT7699U1|2003-04-28|2005-07-25|Engineering Ct Steyr Gmbh & Co|CLAW COUPLING AND DIFFERENTIAL LOCK WITH SUCH A|DE102016202625B3|2016-02-19|2017-05-04|Ibs Filtran Kunststoff-/ Metallerzeugnisse Gmbh|Pressure oil filter system for a motor vehicle transmission|
    RU2647109C1|2016-12-29|2018-03-13|Федеральное государственное бюджетное образовательное учреждение высшего образования "Оренбургский государственный университет"|Intermedular differential|
    DE102018210691A1|2018-06-29|2020-01-02|Zf Friedrichshafen Ag|Switch module, differential lock, transfer case and axle connection|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    AT14652011A|AT511442B1|2011-10-10|2011-10-10|DIFFERENTIAL|AT14652011A| AT511442B1|2011-10-10|2011-10-10|DIFFERENTIAL|
    DE201210109336| DE102012109336A1|2011-10-10|2012-10-01|Engine propelled differential gear for vehicle, has check valve for preventing return flow of pressure fluid from high pressure line into low pressure line when sliding sleeve is returned to release position|
    [返回顶部]