• 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 gearbox (2) for vehicles, comprising a planetary gear (14) with a ring gear (22), a sun gear (18) and a planet gear holder (20), on which at least one planet wheel (24) is rotatably mounted, which ring gear (22) and sun gear (18) engages at least one planet gear (24) by means of teeth (32); and a first axially displaceable coupling sleeve (40), which in a first gear position is arranged to disconnect a shaft (16) included in the gearbox (2) from the planet gear holder (20) and in a second gear position is arranged to connect the input the shaft (16) with the planetary gear holder (20). A second axially displaceable coupling sleeve (42) is arranged in the first gear position to connect a gearbox housing (12) surrounding the planetary gear (14) to the ring gear (22) and in the second gear position to disengage the gearbox housing (12) from the ring gear (22). ). The invention also relates to a vehicle (1), which comprises such a gearbox (2). (Fig. 2)
    公开号:SE1450627A1
    申请号:SE1450627
    申请日:2014-05-27
    公开日:2015-11-28
    发明作者:Dieter Slapak
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    The direction depends on the direction in which the gears in the planetary gear are skewed.
    Thus, the reaction forces can act backwards or forwards in the extent of the axis of rotation.
    In a known range gearbox, low and high gears are obtained by displacing the ring gear axially between the low range position, in which the ring gear is rotationally locked relative to the gearbox housing, and the high gear position, in which the ring gear is rotatable relative to the gearbox housing and where the ring gear and planet gear rotates as a coherent unit. The planetary gear comprises two coupling rings arranged on each side of the ring wheel and two synchronizing rings, which are arranged on each side of the ring wheel. The task of the synchronizing rings is to effect a synchronous change.
    In order to obtain a good synchronizing function in this type of gearbox, the surface of the teeth of the synchronizing ring, which faces the ring gear and which is intended to receive the teeth of the ring wheel during synchronization, must be provided with an angle, so-called ratchet angle, in relation to the axis of rotation of the synchronizing ring, which ratchet angle must be balanced against the firing moment which the synchronizing ring transmits on the ring gear in order to achieve synchronous speed. This means that said locking angle must be designed so that the teeth of the synchronizing ring abut on the part of the ring gear teeth which is provided with the locking angle and act sufficiently on the ring wheel so that synchronous speed can be obtained and then detached from the part of the ring wheel teeth provided with the locking angle and when the ring gear is to engage in the current clutch ring when synchronous speed has been obtained. To ensure that synchronous speed is reached before the ring gear passes the synchronizing ring in the axial direction, the teeth of the synchronizing ring must not release the ring gear teeth too easily.
    When the teeth of the synchronizing ring are detached from the teeth of the ring gear when synchronous speed is obtained between ring gear and clutch ring, the ring wheel will be displaced axially, so that the synchronizing ring is moved inwardly in the ring wheel and remains in an axial position relative to the ring wheel. abuts the planet gears of the planetary gear. 10 15 20 25 30 The freedom of movement of the ring gear in the axial direction is limited by the geometric design of the teeth of the ring wheel and the clutch ring. At the axial end positions of the ring wheel, end surfaces at the tooth tips of the ring wheel meet and abut a circumferential end surface of the respective coupling ring, which means that the ring wheel can no longer be displaced in the axial direction.
    Document WO0155620 discloses a synchronizing device at a planetary gear where the planetary gear comprises a sun gear, a planet gear holder and a ring gear. The sun gear is rotatably connected to the input shaft and a number of planet gears engage with the sun gear, which planet wheels are rotatably mounted on a planet gear holder rotatably connected to an output shaft. An axially displaceable ring gear encloses and engages the planet gears. The low and high gears of the gearbox are obtained by displacing the ring gear axially between the low-range position and the high-range position.
    However, these synchronizing devices are subject to wear and tear and involve large repair costs. If the range gearbox is to transmit large torques, synchronization devices will have considerable dimensions, which entails increased weight, increased space requirements and increased inertia torque. When the high-range position is engaged, torque will be transmitted from the sole wheel to the planet gears, which means that facets can form on the sun gear's gear anchor, which creates noise in the gearbox and accelerates wear of the planet gear's gears.
    There are gearboxes in which the synchronizing devices have been replaced with boomed coupling sleeves. By controlling the transmission so that synchronous speed occurs between the two components to be interconnected, an axial displacement of the coupling sleeve along the two components is made possible in order to connect and interconnect them. When the components are to be disconnected from each other, the transmission is controlled so that a torque balance arises between the components, whereby the coupling sleeve does not transmit torque. It then becomes possible to displace the coupling sleeve along the components in order to disengage them from each other. Torque balance refers to a state when a torque acts on a ring gear arranged at the planetary gear, corresponding to the product of the torque acting on the planetary gear holder of the planetary gear and the planetary gear ratio while a torque acts on the sun gear of the planetary gear, corresponding to the torque product on the planetary gear carrier and (1-planetary gear ratio). In the event that two of the constituent parts of the planetary gearbox, the sun gear, ring gear or planetary gear holder, are connected by means of a coupling unit, this coupling unit does not transmit torque between the parts of the planetary gearbox when the torque balance prevails. Thus, the coupling unit can be easily displaced and the constituent parts of the planetary gear can be disengaged.
    Document US6199644 discloses a planetary gear comprising a sun gear, a planet gear holder with planet gears and a ring gear. The sun gear can be rotatably connected to the input shaft in a low-rank position by means of a coupling sleeve and disengaged from the input shaft in a high-rank position. In the high-rank position, the input shaft is connected to the planetary gear holder by means of the same coupling sleeve. The ring gear is permanently connected to a gearbox. The known planetary gear is arranged in an auxiliary gearbox, which has only two gear positions.
    The known gearboxes often require a complete disassembly when replacing a component, which means that a lot of time is required and that it becomes costly to repair the gearbox.
    SUMMARY OF THE INVENTION Despite known solutions, there is a need to further develop a gearbox where the shift times are short, where the reliability and reliability of the transmission are high, and where all components of the transmission are used efficiently so that low energy is required when shifting. There is also a need to further develop a gearbox which has small dimensions in relation to possible torque transmission and a gearbox with low axial forces which act on the axial bearing of the main shaft main gearbox.
    There is also an effort to reduce the fuel consumption of a vehicle, which includes the gearbox and to reduce noise from the gearbox, and a need to further develop a gearbox that is easy to repair.
    The object of the present invention is to provide a gearbox which entails short gearing times. Yet another object of the present invention is to provide a gearbox which provides high reliability and reliability of the gearbox.
    A further object of the invention is to provide a gearbox which utilizes all the components included in the transmission efficiently.
    A further object of the invention is to provide a gearbox which has small dimensions in relation to possible torque transmission.
    A further object of the invention is to provide a gearbox which reduces the fuel consumption of a vehicle which comprises the gearbox.
    A further object of the present invention is to provide a gearbox which requires low energy when shifting.
    A further object of the invention is to provide a gearbox which has a low noise level.
    A further object of the invention is to provide a gearbox which is easy to repair.
    A further object of the invention is to provide a gearbox, with low axial forces, which acts on the axial bearing of the gearbox.
    These objects are achieved with a gearbox of the kind mentioned in the introduction, which is characterized by the features stated in claim 1. These objects are also achieved with a vehicle which comprises a gearbox of the kind mentioned in the introduction, which is characterized by the features set forth in claim 12.
    By the first axially displaceable coupling sleeve transmitting torque from the input shaft to the planet gear holder and further to the output shaft in the second gear position and the second axially displaceable coupling sleeve locks the ring gear with the gear housing, so that torque is transmitted from the input shaft and ring gear the mesh holder for the output shaft in the first gear position provides an efficient gearbox with high efficiency and low losses. The gearbox will show a reduced need for lubrication while minimizing facet damage to the gear members.
    The axial stroke of each coupling sleeve is shorter compared to the stroke of the ring gear of a traditional range gearbox, which means that it is possible to quickly switch between different gear positions.
    The first and the second coupling sleeve can each be made with a limited length extension, which means that the mass of the respective coupling sleeve becomes low. The low mass of each coupling sleeve means that it is possible to quickly switch between different gear positions.
    According to an embodiment of the invention, the gearbox comprises an axial stop mounted on the planet wheel holder, which abuts against and is connected to the ring wheel, which axial stop prevents the ring wheel from being displaced axially. Thus, the axial position of the ring gear will be fixed and the gear of the planetary gear can be provided with either a straight tooth or an inclined tooth.
    According to an embodiment of the invention, the second axially displaceable coupling sleeve in the second gear position is only connected to the gear housing. The second coupling sleeve will thus not give rise to mass inertia forces in the gearbox. According to an embodiment of the invention, the input shaft is connected to the sun gear, and the planetary gear holder is connected to a shaft output from the gearbox. Thus, the gearbox has a simple construction, with a few components.
    According to an embodiment of the invention, the input shaft is connected to the sun gear with a spline joint, which has an axial extension which allows an angular displacement between the input shaft and the shaft of the sun wheel. During operation, the main shaft of the main gearbox will bend during certain operating conditions. Due to the permissible angular displacement in the spline joint, the sun gear will not be affected by the bending of the main shaft, which reduces the stresses of the sun gear teeth.
    According to an embodiment of the invention, the spline joint is designed so that the planetary gear can be mounted and disassembled in one piece on the input shaft. Thus, the repair costs can be reduced, as the time required for the repair is reduced.
    According to an embodiment of the invention, the first axially displaceable coupling sleeve on an inner surface is provided with first booms, which are arranged to co-operate with corresponding first booms arranged on the input shaft and the planet wheel holder. A simple and efficient connection and disconnection of the input shaft and the planetary gear holder is thus obtained.
    According to an embodiment of the invention, the second axially displaceable coupling sleeve on an inner surface is provided with second booms, which are arranged to cooperate with corresponding other booms arranged on the ring wheel and on the gear housing. A simple and efficient connection and disconnection of the ring wheel and the gearbox is thus obtained.
    According to an embodiment of the invention, the number of booms on the first sleeve differs from the number of teeth on the ring gear. This obtains a large number of fixed locked positions between the second coupling sleeve and the ring gear, which minimizes facet formation by allowing a large number of facets to be formed on the gear anchors of the gears. However, the facets will lie close together, so that together they will be perceived as a substantially even surface of the cog Anks. The optimum number of barriers can be calculated to obtain as many facets as possible. According to the invention, however, the gear anchors of the planet gears will not be subjected to great stresses in the second gear position. This minimizes the risk of the formation of facets.
    According to an embodiment of the invention, the teeth of the ring wheel, the sun wheel and the at least one planet wheel are designed as oblique teeth and extend at an angle in relation to the center axis of each wheel. This results in a gearbox with high torque transmission and low noise level.
    Additional advantages of the invention will become apparent from the following detailed description.
    BRIEF DESCRIPTION OF THE DRAWINGS In the following, as an example, preferred embodiments of the invention are described with reference to the accompanying drawings, in which: Fig. 1 shows a vehicle in a side view with a gearbox according to the present invention, Fig. 2 shows a schematic sectional view of the gearbox according to the invention in a low-spruce position, and Fig. 3 shows a schematic sectional view of the gearbox according to the invention in a high-spruce position.
    DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION Fig. 1 shows a side view of a vehicle 1, for example a truck, which comprises a gearbox 2 according to the present invention. The gearbox 2 is included in a transmission 3, which comprises an internal combustion engine 4, a main gearbox 6 and a propeller shaft 10. The internal combustion engine 4 is connected to the main gearbox 6, which in turn is connected to the gearbox 10 15 20 25 30 30 according to the present invention. The gearbox 2 is further coupled to the drive wheel 8 of the vehicle 1 via the PTO shaft 10. The gearbox 2 according to the present invention is also called a range gearbox, and has the purpose of doubling the number of gear possibilities. The gearbox 2 is surrounded by a gearbox housing 12.
    Fig. 2 shows a schematic sectional view of a gearbox 2 according to the present invention.
    The gearbox 2 comprises a planetary gear 14, which has a low and high gear, respectively, with which the shifting possibilities of the main gearbox 6 can be divided into a low-rank position and a high-rank position. In a first gear position, which corresponds to the low-range position, a downshift takes place through the planetary gear 14. In the high-range position the gear ratio is 1: 1 in the planetary gear 14. Fig. 2 shows the gearbox 2 in the first gear position, corresponding to the low gear or low-range position.
    The gearbox 2 is housed in the gearbox housing 12 and comprises an input shaft 16, which may be constituted by a main shaft 26 of the main gearbox 6. The planetary gearbox 14 comprises three main components which are rotatably arranged relative to each other, namely a sun gear 18, a planet gear holder 20 and a ring gear. 22. On the planet gear holder 20, a number of stored planet wheels 24 are arranged. Arranged on the planetary gear holder 20 is also the output shaft 28 of the gearbox 2, which is connected to the propeller shaft 10 of the vehicle 1. With knowledge of the number of teeth 32 of the sun gear 18 and the ring gear 22, the mutual speeds of the three components can be determined during operation. The sun gear 18 is rotatably connected to the input shaft 16 and the planet gears 24 engage in said sun gear 18. The ring gear 22 encloses and engages the planet gears 24. The teeth 32 of the sun gear 18, the planet gear 24 and the ring gear 22 may be inclined, i.e. they has an angle with respect to a axis of rotation 30 common to the sun gear 18, the planet gear holder 20 and the ring gear 22. By cutting the teeth 32 obliquely, a reaction force is obtained from the gears 18, 22, 24 of the rotation shaft 30 in the planetary gear 14. . The direction of the reaction force depends on the direction in which the teeth 32 in the planetary gear 14 are inclined. Thus, the reaction forces can act backwards or forwards in the extension of the axis of rotation 30.
    The input shaft 16 is preferably connected to the sole wheel 18 by a spline joint 34, which has an axial extension which allows an angular displacement between the input shaft 16 and the shaft 38 of the sun gear 18. During operation, the main gearbox 6 comes main shaft 26 due to its elasticity and resilient properties to bend under certain operating conditions and high stress. As the load on the main shaft 26 decreases, the main shaft 26 will return to its original shape. The input shaft 16 is provided at its end with a sleeve 36 which internally cooperates with the circumference of a portion of the shaft 38 of the sun gear 18 by means of the spline joint 34. Due to the permissible angular displacement in the spline joint 34, the sun wheel 18 will not be affected by the curvature of the main shaft 26 which reduces the stresses of the teeth 32 of the sun gear 18. The spline joint 34 is preferably designed so that the planetary gear 14 can be mounted and disassembled in one piece on the input shaft 16. Thus, the repair costs can be reduced, as the time required for the repair is reduced.
    A first axially displaceable coupling sleeve 40 is arranged in the first gear position to disengage a shaft 16 included in the gearbox 2 from the planet gear holder 20 and is arranged in the second gear position to connect the input shaft 16 to the planet gear holder 20. A second axially displaceable coupling sleeve 42, is in the first gear position arranged to couple the gearbox housing 12 surrounding the planetary gear 14 with the ring gear 22 and in the second gear position arranged to disconnect the gearbox housing 12 from the ring gear 22.
    The first axially displaceable coupling sleeve 40 is provided on an inner surface with first booms 44, which are arranged to cooperate with the corresponding first booms 44 arranged on the input shaft 16 and the planetary gear holder 20. Corresponding first booms 44 arranged on the input shaft 16 are formed on the periphery of a first ring 46, which is rotatably mounted on the input shaft 16. Corresponding first booms arranged on the planet gear holder 20 are formed on the periphery of a second ring 48, which is rotatably mounted on the planet wheel holder 20.
    The number of first bars 44 on the first axially displaceable coupling sleeve 40 and on the input shaft 16 preferably exceeds the number of teeth 32 on the ring gear 22.
    This obtains a large number of fixed locked positions between the ring gear 22 and the first coupling sleeve 40, which minimizes the occurrence of facets and means that a large number of facets can be formed on the gears 18, 22, 24 teeth 32. However, the facets will to lie close to each other, so that together they will be perceived as a substantially smooth surface of the teeth 32. The facets therefore do not affect the function of the gearbox 2 and have no appreciable effect on the service life of the gears 18, 22, 24.
    The second axially displaceable coupling sleeve 42 is provided on an inner surface with second booms 50, which are arranged to cooperate with corresponding second booms 50 arranged on the periphery of the ring wheel 22 and on a projection 52, which is fixedly connected to the gearbox housing 12.
    An axial stop 54 mounted on the planet gear holder 20 is arranged to abut against the ring wheel 22, which axial stop 54 prevents the ring wheel 22 from being displaced axially. The axial stop 54 can be constituted by a disc-shaped plate, which by means of a first axial bearing 56 is mounted on the planet wheel holder 20. The axial stop 54 is rotatable relative to the planet wheel holder 20 and the input shaft 16, and follows the rotation of the ring wheel 22. The axial stop 54 means partly that the ring gear 22 is fixed axially, and partly that the axial bearing of the gearbox 2 of the input shaft 16 is subjected to less stresses when the gears 18, 22, 24 are provided with an obliquely cut tooth. A second axial bearing 57 can be arranged between the shaft 38 of the sun gear 18 and the planet gear holder 20 to absorb axial forces which arise in the sun wheel 18.
    The low gear of the gearbox 2 is obtained by displacing the first clutch sleeve 40 axially to disengage the planetary gear holder 20 from the input shaft 16 simultaneously, or in close proximity to the second clutch sleeve 42 being displaced, so that the ring wheel 22 is coupled to the gearbox housing 12. The axial displacement the first and second coupling sleeves 40, 42 are provided with a first and second shift forks 58, 60, which are arranged in a circumferential groove 62 on the outside of the first and second coupling sleeves 40, 42. The first shift fork 58 is actuated by a first force means 64 and the second shift fork 60 is actuated by a second force means 66. The first and second force means 64, 66 may be constituted by a pneumatic or hydraulic cylinder. The first and second gear bodies 58, 60 and the first and second power members 64, 66 are schematically drawn in FIG. 2.
    Preferably, the respective coupling sleeve 40, 42 has a small mass, which means that low energy and force are required to move the respective coupling sleeve 40, 42 when changing.
    Thus, a quick changeover can be performed for a short period of time between the different gear positions in the gearbox 2.
    Fig. 3 shows a sectional view of the gearbox 2 according to the invention in the second gear position or the high-rank position, in which the first coupling sleeve 40 has been displaced to the left in Fig. 3 to connect the input shaft 16 to the planet gear holder 20. The second coupling sleeve 42 has been displaced to the left in Fig. 3 to disengage the ring gear 22 from the gearbox housing 12. The second clutch sleeve 42 will thus only be connected to the gearbox housing 12, which means that the second clutch sleeve 42 becomes stationary and will not affect mass inertia forces in the main gearbox 6 upon rotation of the ring gear 22. The torque transfer from the input shaft 16 to the output shaft 28 thus takes place via the input shaft 16 and the planet gear holder 20 and further to the output shaft 28, whereby the gear ratio through the planetary gear 14 becomes 1: 1.
    The gearbox 2 according to the invention indicates the following when switching from the first to the second gear position, i.e. from the low range position to the high range position and will be described in connection with Figures 2 and 3. In Fig. 2, the gearbox 2 has been shifted to the low range position, which causes the first clutch sleeve 40 to be moved to a position which disengages the input shaft 16 from the planet gear holder 20. The first clutch sleeve 40 will not affect mass inertia forces in the main gearbox 6 during the rotation of the input shaft 16. The second clutch sleeve 42 has is thus moved to a position which connects the ring gear 22 to the gearbox housing 12. Thus, the gearbox 2 operates in the low gear position, whereby a downshift takes place through the planetary gear 14. The shifting process from the low gear position to the high gear position occurs by disconnecting the second clutch sleeve 42 from the first ring gear 22 the gearbox housing 12 ceases, which is accomplished by disconnecting a combustion engine 4 from the main gearbox 6 through a coupling 6 arranged therebetween. Alternatively, the internal combustion engine 4 is controlled so that the torque balance between the ring gear 22 and the gearbox housing 12 is generated. When the second clutch sleeve 42 no longer transmits any torque, the axial displacement of the second clutch sleeve 42 is enabled. Simultaneously or after a predetermined period of time, the first clutch sleeve 40 shall be displaced by the first shift fork 58 to engage the planetary gear holder shaft 20 with the input shaft 16. This is accomplished by controlling the internal combustion engine 4 so that the input shaft 16 rotates at a speed which is adapted to the speed of the planetary gear holder 20. When the input shaft 16 and the planetary gear holder 20 rotate at the same speed, the first coupling sleeve 40 can engage with the first bars 44 formed on the input shaft 16. Thus, the gearbox 2 operates in the high-rank position.
    To shift to the low-range position, the first clutch sleeve 40 should be displaced by the first shift fork 58 to the right in G. 3 to disengage the planetary gear holder 20 from the input shaft 16. This is made possible by terminating the torque transmission between the input shaft 16 and the planetary gear carrier 20, which is accomplished by disconnecting the internal combustion engine 4 from the main gearbox 6 through the clutch 68.
    Alternatively, the internal combustion engine 4 is controlled so that torque balance between the input shaft 16 and the planet gear holder 20 is generated. When the first clutch sleeve 40 no longer transmits any torque, the axial displacement of the first clutch sleeve 40 is enabled. Simultaneously or after a predetermined period of time, the second clutch sleeve 42 shall be displaced by the second shift fork 60 in the direction of the ring wheel 22 so as to engage the ring gear 22 with the gearbox housing 12. Since the second clutch sleeve 42 is stationary, the ring wheel 22 must be brought to a stationary position before the coupling takes place between the second clutch sleeve 42 and the ring wheel 22.
    This is accomplished by controlling the internal combustion engine 4 so that the input shaft 16 rotates at a speed adapted to the planet gear holder 20 and the speed of the planet gears 24, which causes the ring gear 22 to stand still. When the ring gear 22 is stationary, the second clutch sleeve 42 can engage with the second bars 50 formed on the ring wheel 22. Thus, the gearbox 2 operates in the low-range position, in which a downshift takes place through the gearbox 2. An electronic control unit 70 is connected to the gearbox 2, the main gearbox 6, the internal combustion engine 4 and the clutch 68 to perform the gear steps above. Preferably, a number of speed sensors (not shown) in the gearbox 2, the main gearbox 6, the internal combustion engine 4 can be connected to the control unit. Another computer 72 may also be connected to the control unit 70. The control unit 70 may be a computer with suitable software for this purpose. The control unit 70 and / or the computer 72 comprises a computer program P, which may comprise routines for controlling the gearbox 2 according to the present invention. The program P can be stored in an executable manner or in a compressed manner in a memory M and / or in a read / write memory. Preferably, a computer program product is provided, which comprises a program code stored on a computer readable medium for performing the above steps, when said program code is run on the control unit 70 or another computer 72 connected to the control unit 70. Said program code may be inadvertently stored on said computer readable medium.
    The gearbox 2 described above is advantageous from a manufacturing and assembly point of view, as the required machining of the components is simple and also the number of components is small. The design is further such that the need for space in both axial and radial joints is small. The described gearbox 2 can also be used in other contexts than those described above. Thus it is e.g. It is possible to use it with hydraulic automatic gearboxes where a plurality of gearboxes with planetary gears are connected to each other.
    According to an embodiment of the invention, it is possible to arrange a first coupling ring (not shown) and at least a first synchronizing ring (not shown) between the first coupling sleeve 40 and the planet gear holder 20, which first coupling sleeve 40 is arranged to be coupled to the first coupling ring in the first gear position.
    Thus, a mechanical synchronization between the input shaft 16 and the plant wheel holder 20 can be achieved. Correspondingly, a second coupling ring (not shown) and at least one second synchronizing ring (not shown) can be arranged between the second coupling sleeve 42 and the ring wheel 22, which second coupling sleeve 42 is arranged to be coupled to the first coupling ring (not shown) in the first gear position. .
    Thus, a mechanical synchronization between the ring wheel 22 and the gearbox housing 12 can be achieved. The function of the gearbox 2 according to this embodiment works in the same way as with the coupling sleeves 40, 42 without synchronization, but instead of generating torque balance with the internal combustion engine 4 and ceasing torque transmission by disengaging the internal combustion engine 4, the coupling rings and synchronizing rings will ensure and disconnection of input shaft 16 and planetary gear carrier 20 and ring gear 22 and gearbox housing 12, respectively, is made possible.
    The stated components and features stated above can be combined within the scope of the invention between different specified embodiments.
    权利要求:
    Claims (12)
    [1]
    A gearbox for vehicles, comprising a planetary gear (14) with a ring gear (22), a sun gear (18) and a planet gear holder (20), on which at least one planet wheel (24) is rotatably mounted, which ring gear (22) and sun gear (18) engages the at least one planet wheel (24) by means of teeth (32); and a first axially displaceable coupling sleeve (40), which in a first gear position is arranged to disconnect a shaft (16) included in the gearbox (2) from the planet gear holder (20) and in a second gear position is arranged to couple the input shaft (16) with the planetary gear holder (20), characterized by a second axially displaceable coupling sleeve (42), which in the first gear position is arranged to couple a gearbox housing (12) surrounding the planetary gear (14) to the ring gear (22) and in the second gear position is arranged to disconnect the gearbox housing (12) from the ring gear (22).
    [2]
    Gearbox according to claim 1, characterized in that an axial stop (54) mounted on the planet gear holder (20) abuts and is connected to the ring wheel (22), which axial stop (54) prevents the ring wheel (22) from displacing axially.
    [3]
    Gearbox according to one of Claims 1 to 2, characterized in that the second axially displaceable coupling sleeve (42) in the second gear position is only connected to the gearbox housing (12).
    [4]
    Gearbox according to one of the preceding claims, characterized in that the input shaft (16) is connected to the sun gear (18), and that the planetary gear holder (20) is connected to a shaft (28) emanating from the gearbox (2).
    [5]
    Gearbox according to one of the preceding claims, characterized in that the input shaft (16) is connected to the sun gear (18) by a spline joint (34), which has an axial extension which allows an angular displacement between the input shaft (16) and the shaft (38) of the sun gear (18). 10 15 20 25 30 17
    [6]
    Gearbox according to claim 5, characterized in that the spline joint (34) is designed such that the planetary gear (14) can be mounted and disassembled in one piece on the input shaft (16).
    [7]
    Gearbox according to one of the preceding claims, characterized in that the first axially displaceable coupling sleeve (40) on an inner surface is provided with first booms (44), which are arranged to cooperate with corresponding first booms (44) arranged on the input shaft ( 16) and the planetary gear holder (20).
    [8]
    Gearbox according to one of the preceding claims, characterized in that the second axially displaceable coupling sleeve (42) on an inner surface is provided with second booms (50), which are arranged to cooperate with corresponding second booms (50) arranged on the ring wheel (22). and on the gearbox housing (12).
    [9]
    Gearbox according to Claim 8, characterized in that the number of first bars (44) on the first axially displaceable coupling sleeve (40) and on the input shaft (16) exceeds the number of teeth (32) on the ring gear (22).
    [10]
    Gearbox according to one of the preceding claims, characterized in that the teeth (32) of the ring gear (22), the sun gear (18) and the at least one planet wheel (24) are designed as inclined teeth (32) and extend at an angle in in relation to the axis of rotation (30) of the planetary gear (14).
    [11]
    Gearbox according to one of the preceding claims, characterized in that the gearbox (2) is a range gearbox and that the input shaft (16) is connected to a main gearbox (6) -
    [12]
    Vehicle (1), characterized in that it comprises a gearbox (2) according to any one of claims 1-11.
    类似技术:
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    同族专利:
    公开号 | 公开日
    EP3149359B1|2020-06-24|
    KR20170010319A|2017-01-26|
    KR101904368B1|2018-10-05|
    WO2015183154A1|2015-12-03|
    EP3149359A1|2017-04-05|
    US20170023105A1|2017-01-26|
    EP3149359A4|2018-02-21|
    SE539659C2|2017-10-24|
    US10072734B2|2018-09-11|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1450627A|SE539659C2|2014-05-27|2014-05-27|Transmission for vehicles and vehicles which include such a gearbox|SE1450627A| SE539659C2|2014-05-27|2014-05-27|Transmission for vehicles and vehicles which include such a gearbox|
    EP15799287.6A| EP3149359B1|2014-05-27|2015-05-12|Gearbox for vehicles and vehicle, comprising such a gearbox|
    PCT/SE2015/050527| WO2015183154A1|2014-05-27|2015-05-12|Gearbox for vehicles and vehicle, comprising such a gearbox|
    US15/302,430| US10072734B2|2014-05-27|2015-05-12|Gearbox for vehicles and vehicle, comprising such a gearbox|
    KR1020167035366A| KR101904368B1|2014-05-27|2015-05-12|Gearbox for vehicles and vehicle, comprising such a gearbox|
    KR1020167035365A| KR101898903B1|2014-05-27|2015-05-25|Gearbox for vehicles and vehicles comprising such a gearbox|
    BR112016025058A| BR112016025058A2|2014-05-27|2015-05-25|gearbox for vehicles and vehicles comprising such gearbox|
    SE1550665A| SE540417C2|2014-05-27|2015-05-25|Gearbox for vehicles and vehicles comprising such a gearbox|
    US15/310,953| US10018259B2|2014-05-27|2015-05-25|Gearbox for vehicles and vehicles comprising such a gearbox|
    PCT/SE2015/050596| WO2015183159A1|2014-05-27|2015-05-25|Gearbox for vehicles and vehicles comprising such a gearbox|
    EP15799107.6A| EP3152464B1|2014-05-27|2015-05-25|Gearbox for vehicles and vehicles comprising such a gearbox|
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