TW201531636A - Shifting device for a planetary gearbox - Google Patents

Abstract

The invention relates to a shifting device for a gearbox, in particular a two-stage planetary gearbox, comprising a rotatable shifting sleeve which, for shifting the gearbox, is able to be displaced along its axis of rotation into at least one shift position, wherein the shifting sleeve has a connection region in which said shifting sleeve can be connected to a drive shaft of the gearbox in such a way that a rotational movement of the drive shaft can be transmitted to the shifting sleeve, and comprising at least one stationary shifting element which, when actuated to displace the shifting sleeve axially into the shift position, can be coupled to said shifting sleeve in a form-fitting manner. According to the invention, the shifting sleeve has in the circumferential direction a stop, against which the actuated shifting element can butt so that a rotational movement of the shifting sleeve is stopped relative to a rotational movement of the drive shaft.

Description

Planetary gear set switching mechanism

The present invention relates to planetary gear sets, and more particularly to a planetary gear set having a switching mechanism.

Press, the planetary gear set switching mechanism is widely used in various machine tools, turning, milling and machining centers, and it is driven by a DC/AC spindle motor, which can improve the performance of the spindle motor for processing different materials or Different cutting forces can increase the flexibility of the machine tool through a large torque or speed. The two-stage planetary gear set currently used by the machine tool is provided with a two-stage transmission shaft.

A switching mechanism for a two-stage planetary gear set is known, which comprises at least one outer sliding sleeve which is non-rotatable but axially displaceably arranged on a gear set shaft, as described in German Patent No. DE 10 2009 054 942 A1. A pulley is disposed adjacent to each other on at least one side of the outer sliding sleeve, and is rotatably disposed on the gear set shaft, and the outer sliding sleeve can be axially transmitted through the actuator of the associated actuator Moving from a neutral position to a switching position in the direction of the respective pulleys, and when reaching the switching position, the respective pulleys are meshed with the gear set shaft, and the associated actuator positions are fixedly disposed, and Engaging into at least one switching groove, the switching groove is disposed on a diameter outside the outer sliding sleeve, the switching groove includes a shape that is curved in the axial direction, and thus, the shaft of the gear set rotates At the same time, the axial movement of the outer sliding sleeve is caused corresponding to the shape of the switching groove.

A first object of the present invention is a planetary gear set switching mechanism that includes a switching sleeve that is rotatable along a rotational axis to at least one switching position to enable switching of the gear set switching mechanism. a first switching state of the gear set can be generated, wherein the drive shaft of the gear set has no transmission, under drive and/or high speed transmission (over Driven with the driven shaft, the switching sleeve further includes a first connecting zone, the switching sleeve being connectable with the driving shaft of the gear set switching mechanism, so that after the driving shaft is rotated, The drive shaft can be moved to the position of the switching sleeve; at least one switching element, the switching element being a switching lever disposed in the region of the outer side surface of the switching sleeve and/or with the switching sleeve Radially spaced apart, the switching element can form a form of latching engagement with the switching sleeve when actuated to move the switching sleeve axially into the switching position, in particular the switching The rod is moved from a radially outer first position to a radially inner second position in the radial direction to engage or be coupled to the switching sleeve. The switching mechanism is characterized in that: the switching sleeve is provided with a first blocking piece in the circumferential direction, and the switching element can be fixed on the first blocking piece, so that the switching sleeve can stop the rotating movement, that is, The switching element is in contact with the blocking piece of the switching sleeve in a state in which the switching element has been actuated, thus further preventing further rotational movement of the switching sleeve.

In the solution of the prior art, the axial movement of the switching sleeve is achieved via a spiral groove, so that the switching sleeve is not stopped but is additionally tightly engaged with the drive shaft for rotation. In the prior art, the present invention can design a switching mechanism which is advantageous in manufacturing cost by the flap, and further, the force acting on the switching element can be reduced by the flap. Therefore, in order to actuate the switching element, a greatly reduced force consumption is also required. Moreover, the switching element advantageously has a load only during the switching process, and a smaller electromagnet is sufficient to actuate the switching element. The utility model relates to an electromagnet-actuated switching lever. Here, the operation of the switching rod between the first position in the radially outer portion and the second position in the radially inner portion is achieved by an electromagnet, and can also be driven by an electric motor or a hydraulic pressure. Alternatively, pneumatically or in any other manner, the switching mechanism can be formed by the switching force and the holding force acting on the switching mechanism. A baffle is formed in the region of the outer side surface and/or the inner side surface of the switching sleeve by means of projections and recesses extending in the radial direction, so that the switching sleeve is also advantageously manufactured advantageously. The system can be disposed on the outer side surface or the inner side surface of the switching sleeve in the form of a groove (a notch or a track (bulge)).

In order to ensure that the switching sleeve can be completely stopped for a further rotational drive shaft, it is advantageous when the flap extends substantially parallel to the axis of rotation. However, another way is that the blocking piece can also be disposed to be inclined to the rotating shaft, so that the switching sleeve can move in the axial direction. Rotate easily. In principle, the flap must be formed in order to create a difference in the number of revolutions between the drive shaft and the shifting sleeve in the actuating switching element, the switching sleeve being rotated more slowly than the drive shaft.

A second object of the invention is for the first flap to extend parallel to the axis of rotation.

A third object of the present invention is to provide a lead-in area at one end of the first flap to enable introduction of the switching element and/or a lead-out area at the other end of the flap to enable the switching element to be derived. In this way, a reliable stop and re-drive of the switching sleeve can be ensured, in order to move the switching sleeve, the activated switching element must therefore be brought into contact with the blocking piece via the lead-in area as long as the switching element is positioned On the blocking piece, the switching sleeve has to be moved axially in the direction of the switching position along its axis of rotation, such that the blocking piece moves axially on the positionally fixed switching element as long as the When the switching sleeve has reached the switching position, the device contact area between the switching element and the flap can be eliminated by the lead-out area, so that the switching sleeve starts to rotate again together with the drive shaft.

A fourth object of the present invention is that the switching sleeve further includes a second blocking piece, the second blocking piece is in the switching sleeve when the rotation direction of the driving shaft is reversed and/or in the switching position, the switching The component can collide with the second flap so that the switching sleeve can be moved back by its switching position, and the second flap can also be formed in an area of the outer side surface and/or the inner side surface of the switching sleeve. A projection and/or a recess extending in the radial direction.

A fifth object of the present invention is that the first baffle and/or the second baffle respectively form a lead-in area and/or a lead-out area, and an vacant area is recessed on the outer side surface of the switch sleeve. The vacant zone is in communication with the lead-in zone and/or the lead-out zone such that the first flap and/or the second flap are respectively located at corresponding side edges of the vacant zone.

A sixth object of the present invention is to ensure that the switching element can be independently introduced into or derived from the vacant area, the radial depth of each vacant area being in a lead-in area and/or a lead-out area The first flap and/or the second flap are reduced in the circumferential direction to a level outside the diameter of the switching sleeve.

A seventh object of the present invention is to enable the gear set to achieve different switching states, the switching sleeve further comprising at least one first emptying area, the first emptying area enabling the switching sleeve Moving between a first and second switching position, the switching sleeve further includes at least one second emptying area, the second emptying area enabling the switching sleeve to be between a neutral position and each of the switching positions mobile.

An eighth object of the present invention is that the connecting portion enables the switching sleeve that has been stopped to move or be moved away from the driving shaft in the axial direction according to the rotation direction of the driving shaft, thus, The shifting element can be disengaged by the axial force required to move the shifting sleeve, since the axial force is substantially completely absorbed by the first connecting region, which is therefore only loaded during the switching process.

According to a ninth aspect of the present invention, the switch sleeve further includes a thread, the thread being an internal thread and/or a fine thread for axial movement along a rotation axis in the first connection region, The first connection zone can be formed to absorb the axial force.

According to a tenth aspect of the present invention, the switching mechanism further includes an engaging member movable in an axial direction and fasteningly connecting at least two parts of the gear set switching mechanism, the switching sleeve being The space can be formed in a space-saving manner. The gear set switching mechanism is connected to the switching sleeve in a second connecting zone by means of form locking and/or force locking. The at least two parts of the gear set are meshed. The force generated by the engagement element is thus absorbed by the engagement element, so that the switching sleeve only takes over the task of switching, so that the gear set is formed in a space-saving manner.

According to an eleventh object of the present invention, it is advantageous for the engaging element to be latched in the axial direction and/or to be connected to the switching sleeve in a circumferentially circumferentially force-locking manner, so that advantageously Simultaneously moving the engaging element to a corresponding switching position and/or a neutral position while the switching sleeve is axially moved, and further, formed between the engaging element and the switching sleeve in a circumferential direction A force-locking connection prevents inadvertent axial movement of the switching sleeve when the drive shaft is stopped and/or accelerated.

A twelfth object of the present invention is to prevent "the relative rotation of the switching sleeve relative to the drive shaft in the first connection region" when the drive shaft is accelerated and/or stopped. It is advantageous when the engagement element forms a frictional force between the engagement element and the switching sleeve in the circumferentially directed force that is greater than the maximum moment of inertia generated by the switching sleeve in the first connection zone.

A thirteenth object of the present invention is to provide a switchable planetary gear set for use in a machine tool, the planetary gear set including a drive shaft, a driven shaft, and a planetary And a central shaft, wherein the central shaft is axially movable, the central shaft is moved between a first and a second switching position by a planetary gear set switching mechanism, wherein the central shaft, the drive shaft The planetary arrangement and/or the driven shaft can be intermeshing in different manners in each of the switching positions, wherein the switching mechanism is in accordance with the foregoing implementation, and the features can be individually or in any combination.

For your convenience, the review committee can make a further understanding and understanding of the purpose, technical features and effects of the present invention. The embodiments are combined with the drawings, and the details are as follows:

[study] no

〔this invention〕

1‧‧‧ drive shaft

2‧‧‧ driven shaft

3‧‧‧Central axis

4‧‧‧ Planetary configuration

5‧‧‧Switching mechanism

6‧‧‧First connection area

7‧‧‧Second connection area

8‧‧‧First switching element

9‧‧‧ outside surface

10‧‧‧Switching sleeve

10A, 10B‧‧‧ spring elements

11‧‧‧First vacated area

12, 14‧‧ ‧ thread

13‧‧‧Second switching element

15‧‧‧ Engagement components

16‧‧‧ rolling bearings

17‧‧‧ driven shaft gear

18‧‧‧Center shaft gear

19‧‧‧ Planetary bracket

20‧‧‧ Planetary Gears

21‧‧‧Connecting components

22‧‧‧Second vacated area

23‧‧‧ring gear

24‧‧‧ planetary gear

25‧‧‧Gear rod

26‧‧‧ Planet Sun

27‧‧‧Rotary axis

28‧‧‧Shell

29‧‧‧ Bearing

30‧‧‧First bite teeth

31‧‧‧Second bite

32‧‧‧First baffle

33‧‧‧second baffle

34‧‧‧ lead-in area

35‧‧‧Exporting area

1 to 1a are schematic views of a switchable planetary gear set having a switching mechanism in a first switching state; FIG. 2 is a perspective view of a switching sleeve of the switching mechanism; FIGS. 3a-3d are a switching process sequentially performed when the planetary gear set is switched from the first switching state shown in FIG. 1 to the second switching state; FIG. 4 is a perspective view of the switching sleeve having the second and third emptying regions Moving the switching sleeve to a neutral position; FIG. 5 is a view showing the planetary gear set having a switching element engaged in the second vacant area to switch the gear set to a neutral state; and FIG. 6 is a view Planetary gear set in neutral position.

Referring to Figure 1, there is shown a schematic diagram of a switchable planetary gear set that is preferably used in a machine tool, such as a mandrel for driving the machine tool, the planetary gear set governing a machine tool A drive shaft 1 (eg, an electric motor) is shown that is rotatably positioned in a housing 28 via a corresponding bearing 29, and in addition, the planetary gear set dictates a rotatable, preferably, and driven The shaft 1 extends together with the driven shaft 2, whereby the planetary gear set can be coupled to a part to be driven (tool mandrel, which is not currently shown), through which the rotational movement of the drive can be The moving shaft 2 is transferred to the part to be driven.

The displacement of the rotational movement described above is achieved by means of a rotatable central shaft 3 which is fastened to engage the drive shaft 1 on the one hand and can be different in different ways as will be detailed below. Being led to form an active connection with the driven shaft 2 so that Achieving at least a first of the planetary gear set (see FIG. 1) and a second switching state (see FIG. 3d), wherein the drive shaft 1 and the driven shaft 2 are rotated The number is not the same.

Referring to FIG. 1, a first switching state of the planetary gear set, wherein the rotational movement of the drive shaft 1 is displaced to the driven shaft 2 via a center-switched planetary configuration 4, the planetary configuration 4 preferably dictating A planet sun 26 rotatable about a rotational axis 27 is surrounded by a plurality of the planetary gears 24 having an outer engaging tooth and rotatably positioned on a planet carrier 19 by means of a gear bar 25 The planet carrier 19 surrounds the central shaft 3 in an annular manner. Finally, the planetary arrangement 4 includes a ring gear 23 provided with internal snap teeth and fixedly coupled to the housing 28, and a planet with corresponding external snap teeth. The gear 24 is in contact with the ring gear 23 in a comb-like manner.

Referring to FIG. 1 , the planetary sun 26 of the planetary arrangement 4 includes a first engaging tooth 30 formed as an external engaging tooth, and in the first switching state, the central shaft 3 is formed as an internal engaging tooth. The second engaging teeth 31 are tightly engaged, such that the rotational movement of the central shaft 3 is transmitted to the planetary sun 26 and transmitted to the planetary carrier 19 via the planetary gear 24 guided in the outer ring gear 23 The planet carrier 19 includes a planetary gear provided with internal snap teeth, whereby the planet carrier 19 meshes with a driven shaft gear 17 of the driven shaft 2 via a connecting element 21, the connecting element 21 via a rolling bearing 16 is positioned on the central shaft 3 and is axially movable together with the central shaft 3, which is in particular an externally engaged sleeve or a connecting gear.

Referring to FIG. 1, in the first switching state, the rotational movement caused by the driving is first transmitted to the central shaft 3 firmly connected to the drive shaft 1, from which it continues. The first and second engaging teeth 30, 31 are transmitted to the planetary sun 26, the rotation of which causes the planetary gear 24 to move, and thus the rotational movement of the planetary carrier 19, the rotation of the planetary carrier 19 ultimately by means of the planetary carrier gear 20 is transmitted to the connecting member 21, and is transmitted thereto to the driven shaft gear 17, thereby ensuring the driving of the gear reduction of the driven shaft 2, and the planetary carrier 19 and the planetary carrier gear 20 can form a common Parts to replace the two separate parts shown in Figure 1.

The planetary gear set or the planetary configuration 4 can now be the first cut shown in Figure 1 The switching state is switched to the second switching state shown in FIG. 3d. Thus, the gear set has a switching mechanism 5 that dictates a switching sleeve 10 that is rotatably formed around the rotating shaft 27, In order to switch to the gear set, the switching sleeve 10 has to be formed to be axially movable along its axis of rotation 27, the switching sleeve 10 comprising first and second connection zones 6, 7, the first connection zone When the rotation of the switching sleeve 10 is stopped, the switching sleeve 10 is moved in the axial direction toward the drive shaft 1 or moved away from the drive shaft 1 according to the rotation direction of the drive shaft 1 The switching sleeve 10 includes a thread 12 in the first connecting portion 6, the thread 12 is formed on an inner thread on the inner surface of the switching sleeve 10, and the thread 12 of the switching sleeve 10 is in the first connection In the region 6, the corresponding thread 14 of the drive shaft 1 is screwed, and the thread 14 of the drive shaft 1 is formed as an external thread in the present embodiment and is disposed at the end of the drive shaft 1 facing the switching sleeve 10. on.

Referring to Figure 1, the switching mechanism 5 includes an engaging member 15 whereby the central shaft 3 is securely coupled to the planet via the first and second engaging teeth 30, 31, as previously described. The sun 26 is engaged, the engaging element 15 is fixedly coupled to the central shaft 3 in the axial direction and in the circumferential direction. The rotational movement of the central shaft 3 and the axial movement of the central shaft 3 are displaceable to the meshing. Element 15, that is, the engagement element 15 follows the movement of the central shaft 3 or the engagement element 15 can also be an assembly of the central shaft 3.

Referring to FIG. 1 , the switching sleeve 10 is connected to the engaging element 15 in its second connecting region 7 , and the connection between the switching sleeve 10 and the engaging element 15 can be form-locked and/or force. a locking manner is formed, so that the switching sleeve 10 and the engaging element 15 are in a form-locking connection in the axial direction, so that the engaging element 10 can also be coupled to the switching sleeve when the switching sleeve 10 is moved in the axial direction. The cartridge 10 moves together, the central shaft 3, the engagement element 15 and the switching sleeve 10 thus forming a unit movable in the axial direction of the planetary gear set, the second connection zone 7 being circumferentially axially locked in a force-locking manner Forming, the frictional force of the circumferentially formed force blocking between the engaging element 15 and the switching sleeve 10 is greater in the second connecting region 7 than the maximum moment of inertia generated by the switching sleeve 10 in the first connecting region 6 . Thus, it is possible to prevent a helical movement between the drive shaft 1 and the switching sleeve 10 in the first connection region 6 when the drive shaft 1 is accelerated or stopped. The axial movement of the switching sleeve 10 is thus only achieved by the first shifting element 8 when an effective stop or stop occurs.

Referring to FIG. 1 , the first switching element 8 is a component of the switching mechanism 5 , and the first switching element 8 is fixedly disposed in the housing in a circumferential direction and an axial direction of the switching sleeve 10 . 28, the first switching element 8 can be operated in a radial direction from the first switching position of the radially outer portion shown in FIG. 1 to a second switching position inside the radial direction (please refer to FIG. 3a) to The switching sleeve 10 forms a form of latching engagement or connection. In the embodiment shown, the first shifting element 8 is formed, for example, as a shifting lever, the first shifting element 8 corresponding to the first free area 11 of the switching sleeve 10 , the first free area 11 being formed in the The outer side surface 9 of the sleeve 10 is switched, and the first free area 11 is formed in the form of a groove. Alternatively, the first free area 11 may be formed as a track and correspondingly protruded by the outer side surface 9, and an exemplary form of the first free area 11 on the outer side surface 9 of the switching sleeve 10 is shown in broken lines. In the area of the central axis 3 in Figures 1, 3, 5 and 6.

Please refer to FIG. 1a for an enlarged view of the area indicated by A in FIG. 1. The force-locking connection in the circumferential direction between the switching sleeve 10 and the engaging element 15 is based on FIG. 1a by two This is achieved by prestressed spring elements 10A and 10B. The spring elements 10A and 10B produce a determined amount of friction between the engaging element 15 and the switching sleeve 10, thus providing a form of sliding engagement as long as a stopping force applied to the switching sleeve 10 exceeds the engaging element 15 The frictional momentum between the switching sleeve 10 and the sliding engagement of the form when the engaging element 2 is rotationally moved allows the switching sleeve 10 to be stopped relative to the engaging element 15, since the spring element 10A, The higher hardness of 10B makes it possible to create a quasi-type latching connection between the switching sleeve 10 and the engagement element 15 in the axial direction. Furthermore, the switching sleeve 10 and the engagement element 15 are The elastically engaged engagement shown in the axial direction helps to relieve the possible tooth-to-tooth-position between the snap-in teeth 30, 31, thus each suitable spring object, for example one or more dish shapes Springs, spiral springs or wave springs can be used as the spring elements 10A, 10B. In another embodiment of the invention, one or two spring elements 10A, 10B can also be omitted. In the latter case, a force-locking can additionally be caused in the circumferential direction between the engagement element 15 and the switching sleeve 10.

Referring to FIG. 2, the switching sleeve 10 and the first vacant area 11 include a first blocking piece 32, and the first blocking piece 32 is parallel to the rotating axis. 27 extending, and the first switching element 8 can be fixed on the first blocking piece 32, so that the switching sleeve The cylinder 10 is axially moved to stop the rotational movement of the switching sleeve 10 relative to the rotating drive shaft 1. Further, one end of the first flap 32 is provided with a lead-in area 34 for being able to be introduced into the first A switching element 8 is disposed on the other end of the first flap 32 to define the actuated first shifting element 8 which also includes a thread 12 (see Figure 1). Not shown in FIG. 2, the thread 12 is an internal thread and/or a fine thread for axial movement along the axis of rotation 27 in the first connection zone 6.

In order to switch the planetary gear set from the first switching state shown in FIG. 1 to the second switching state shown in FIG. 3d, the first switching element 8 should first be actuated according to FIG. 3a. Therefore, the first switching element 8 is moved from the radially outer position (see FIG. 1) to the radially inner position as shown in FIG. 3a, so that the first switching element 8 can be functionally connected to the first free area 11. Due to the first and/or the second connecting regions 6, 7, the switching sleeve 10 is rotatable together with the driving shaft 1, the central shaft 3 and the engaging element 15, and the switching sleeve 10 is driven by a force The latching or the frictional momentum between the switching sleeve 10 and the engaging element 15 is dragged in the second connecting zone 7 together with the rotational movement of the central shaft 3, by the rotational movement of the switching sleeve 10, Then, the first switching element 8 reaches the first vacant area 11 via the lead-in area 34 when activated, so that the first switching element 8 can be fixed on the first blocking piece 32, so that the switching The rotational movement of the sleeve 10 is stopped or abruptly stopped, and conversely, the drive shaft 1, the central shaft 3 and the joint The coupling element 15 continues to rotate due to the sliding of the force-locking connection zone provided in the second connection zone 7, so that relative rotation is now effected between the switching sleeve 10 and the engagement element 15. The frictional momentum existing between the switching sleeve 10 and the engagement element 15 is supported on the housing 28 by the first switching element 8. Since the drive shaft 1 is now rotated and the switching sleeve 10 is upright, the switching sleeve 10 is screwed to a fixed drive shaft in the axial direction based on the threads 12, 14 that engage with one another in the first connecting region 6. 1 , here, the engagement element 15 moves together with the switching sleeve 10 in the direction of the drive shaft 1 , because in the second connection region 7 the engagement element 15 is axially locked in a form-locking manner. The switching sleeve 10 is engaged.

In this movement, the first switching element 8 slides on the first flap 32 along the axial direction of the gear set according to FIG. 3b until the switching sleeve 10 reaches its first according to the 3c figure. At the position of the switching position, the activated first switching element 8 is not in contact with the first flap 32 and is slid out of the first free area 11 via the lead-out area 35, the first free area The radial depth of 11 is initiated by the first flap 32 in the lead-in zone 34 and/or the lead-out zone 35 and is reduced to the level of the outer diameter of the switching sleeve 10 in the circumferential direction, then the first switching element 8 The pressure is applied outwardly in the radial direction, causing it to be pressed back to its original, unactuated position.

Referring to FIG. 3d, the planetary gear set is now in its second switching position, in order to maintain the switching mechanism 5 or the switching sleeve 10 in the position, the first and the The second switching element 8 , 13 holds the switching sleeve 10 in this position only by the first connecting region 6 between the switching sleeve 10 and the drive shaft 1 (in particular with a bolted connection, ie The threads 12, 14) that engage each other can be achieved. Therefore, the first switching element 8 has to absorb only the force to stop the rotational movement of the switching sleeve 10. The axial movement of the switching sleeve 10 is achieved only in the first connection region 6 by a threaded connection between the switching sleeve 10 and the drive shaft 1.

Referring to FIG. 3d, the connection between the first and second engaging teeth 30, 31 causes the planetary sun 26 to be in the first switching position (see FIG. 1). In combination of 3, this connection is released by the axial movement of the central shaft 3, so that the central shaft 3 and the planetary sun 26 are now disengaged. Similarly, the connecting member 21 is also moved together with the central shaft 3 in the direction of the drive shaft 1 so that the engagement between the planetary carrier gear 20 and the drive shaft gear 17 is also eliminated. As a result, the driven shaft is eliminated. 2, the planetary arrangement 4 is disengaged. In contrast, according to the 3d figure, the central shaft 3 and the driven shaft 2 are now directly meshed by the axial movement of the central shaft 3 to its second switching position, at which time the drive The shaft gear 17 is led to engage with the center shaft gear 18 in a comb-like manner. Now, the rotational movement of the drive shaft 1 is transmitted to the driven shaft 2 in this switching state without being added to the planetary arrangement 4. The inevitable friction losses are thus minimized in this switching state.

In order to re-steer the gear set from the second switching state shown in FIG. 3d to the first switching state shown in FIG. 1, the direction of rotation of the drive shaft 1 has to be reversed, and then the first switching is performed by re-actuating. The element 8 is configured to move the switching sleeve 10 in the opposite axial direction to move the switching sleeve 10 back to the first switching position by the drive shaft 1, such that the activated first switching element 8 is in accordance with the second The drawing reaches the first empty area 11 via a lead-in area 34. Now, the lead-in area 34 becomes the lead-out area 35 of the first flap 32 due to the opposite direction of rotation, and the first empty area 11 further includes The second blocking piece 33, as described above, stops the switching sleeve 10 on the second blocking piece 33 by means of the blocking piece of the first switching element 8 in a similar manner, so that the first connecting portion 6 can be The threaded connection causes the switching sleeve 10 to move axially back to the first switching position, and as soon as the first switching position is reached, the activated first switching element 8 loses effective contact with the second flap 33 and via A lead-out area 35 (which corresponds to the lead-in area 34 of the first flap 32) is re-guided by the first free-out area 11 because the switching sleeve 10 is latched by the force of the engaging element 15. Connect and start rotating again. The lead-out area of the second flap 33 corresponds to the lead-in area 34 of the first flap 32, which is currently formed as a Z-shaped switching groove.

In addition to the first and second switching positions, the planetary gear set can be additionally switched to a neutral position (see Figure 6), so as shown in Figure 4, the switching sleeve 10 still includes a second An vacant area 22 in which a second switching element 13 can be engaged, which second switching element 13 can be biased and/or offset relative to the switching sleeve 10 in the axial direction for the first switching element 8 There is a greater axial extent than the first shifting element 8 , which is for example enlarged via a diameter that is enlarged relative to the first shifting element 8 . Thus, it can be prevented that the second switching element 13 is in a state of being combined with the first free area 11, for example, the second switching element 13 is introduced into the first empty area 11 at this time. Then, in particular, the size of the second switching element 13 and the first free area 11 must be selected to prevent the second switching element 13 from snapping into the first free area 11. The second free area 22 must be configured and oriented such that the switching sleeve 10 can be moved from the second switching position to the central neutral position. An exemplary form of the second vacant area 22 on the outer side surface 9 of the switching sleeve 10 is shown in dashed lines in the region of the central axis 3 in Figures 1, 3, 5 and 6.

Referring to FIG. 4, the switching sleeve 10 further includes a third vacant area (not shown in FIG. 4) in which the second switching element 13 can be engaged. The second vacated area 22 and the third vacated area are formed on different ends of the switching sleeve 10, and the third vacant area must be disposed and oriented to engage the second switching element 13 in the neutral position. The switching sleeve 10 can be moved from its first switching position to a neutral position (i.e., similar to the second vacant area 22, which must be configured and oriented such that the switching occurs when the second switching element 13 is snapped into the neutral position The sleeve 10 can be moved to a neutral position by its second switching position, and the second empty area 22 and the third empty area include a lead-in area 34 and a second block in comparison with the first empty area 11 The working area of the piece 33 and the lead-out area 35, the second vacant area 22 and the third vacant area correspond to the first vacant area 11, the first vacant area 11 and the second vacant area 22 It is also possible that the third vacant area is also preferably disposed around the switching sleeve 10. Wherein the second vacated area 22 and the third vacated area or the first And the second vacant areas 11, 22 may also be disposed on opposite sides of the switching sleeve 10, that is, positioned 180° apart from each other in the circumferential direction of the switching sleeve 10, the first empty In particular, the exit zone 11 can also be arranged offset by 90° from the second free zone 22 or the third free zone in the circumferential direction.

Referring to FIG. 6, the planetary gear set is in a neutral position, wherein the central shaft 3 occupies a position when viewed in the axial direction, the position being located between the first and second switching positions of the central shaft 3, And the central shaft 3 has been disengaged from the drive shaft 1 and the driven shaft 2 in the position, wherein the axial fixation in the position is the same as in the first and the second switching position. The connecting zone 6 and the second connecting zone 7 are achieved, so that in the circumferential direction, the frictional locking connection between the switching sleeve 10 and the engaging element 15 is prevented when the drive shaft 1 is stopped or accelerated. The switching sleeve 10 is screwed in or out with respect to the drive shaft 1, and in addition, a bolted connection between the switching sleeve 10 and the drive shaft 1 is maintained to maintain the switching sleeve 10 in a proper neutral position.

The invention is not limited to the described embodiments shown. Variations in the scope of the patent claims are also possible, for example, when some features have been shown and described in different embodiments, combinations of these features are possible. In particular, the individual or all of the internal or external threads (for example, 14 or 31) shown in the drawings may be formed as external or external threads, in which case the respective external teeth or external portions are respectively corresponding. The thread (for example 12 or 30) is configured as an internal snap or internal thread. The respective internal and external snap teeth (eg, 12 and 14) can also be replaced by frontal snap teeth (eg, claw-shaped snap teeth).

The above is only the preferred embodiment of the present invention, but the scope of the claims of the present invention is not limited thereto, and according to those skilled in the art, according to the technical content disclosed in the present invention, Equivalent changes that are easily considered are within the scope of protection of the invention.

1‧‧‧ drive shaft

2‧‧‧ driven shaft

3‧‧‧Central axis

4‧‧‧ Planetary configuration

5‧‧‧Switching mechanism

6‧‧‧First connection area

7‧‧‧Second connection area

8‧‧‧First switching element

9‧‧‧ outside surface

10‧‧‧Switching sleeve

11‧‧‧First vacated area

12, 14‧‧ ‧ thread

13‧‧‧Second switching element

15‧‧‧ Engagement components

16‧‧‧ rolling bearings

17‧‧‧ driven shaft gear

18‧‧‧Center shaft gear

19‧‧‧ Planetary bracket

20‧‧‧ Planetary Gears

21‧‧‧Connecting components

22‧‧‧Second vacated area

23‧‧‧ring gear

24‧‧‧ planetary gear

25‧‧‧Gear rod

26‧‧‧ Planet Sun

27‧‧‧Rotary axis

28‧‧‧Shell

29‧‧‧ Bearing

30‧‧‧First bite teeth

31‧‧‧Second bite

Claims (13)

A planetary gear set switching mechanism is a two-stage planetary gear set. The switching mechanism includes: a switching sleeve that is rotatable along a rotating shaft to at least one switching position to switch the gear set switching mechanism The switching sleeve further includes a first connecting zone, and the switching sleeve is connectable with the driving shaft of the gear set switching mechanism, so that the driving shaft can move to the switching sleeve after the rotating movement And a position of the at least one first switching element that, when actuated, forms a form of latching engagement with the switching sleeve to axially move the switching sleeve into the switching position. The switching mechanism is characterized in that the switching sleeve is provided with a first blocking piece in the circumferential direction, and the first switching element can be fixed on the first blocking piece so that the switching sleeve can stop the rotating movement. The switching mechanism of claim 1, wherein the first flap is extendable parallel to the axis of rotation. The switching mechanism of claim 1 or 2, wherein one of the first flaps is provided with a lead-in area at the end to enable introduction of the first switching element and/or an export at the other end of the first flap Zone to enable the first switching element to be derived. The switching mechanism of claim 1, wherein the switching sleeve further comprises a second flap, when the rotation direction of the drive shaft is reversed and/or In the switching sleeve of the switching position, the switching element can collide with the second flap so that the switching sleeve can be moved back by its switching position. The switching mechanism of claim 4, wherein the first flap and/or the second flap respectively form a lead-in area and/or a lead-out area, and an outer surface of the switch sleeve is recessed with a vacancy The vacant zone is in communication with the lead-in zone and/or the lead-out zone. The switching mechanism of claim 5, wherein the radial depth of each of the vacated areas is in a lead-in area and/or a lead-out area, and the first flap and/or the second flap are circumferentially oriented. Reduce the level to the outside diameter of the switching sleeve. The switching mechanism of claim 1, wherein the switching sleeve further comprises at least one first empty area, the first empty area enabling the switching sleeve to move between the first and second switching positions / or the switching sleeve further includes at least one second vacant zone that enables the switching sleeve to move between a neutral position and each of the switching positions. The switching mechanism of claim 1, wherein the connection zone enables the switched sleeve to be moved toward or away from the drive shaft in the axial direction depending on the direction of rotation of the drive shaft. The switching mechanism of claim 1, wherein the switching sleeve further comprises a thread, the thread being an internal thread and/or a fine thread for axially along the axis of rotation in the first connection zone mobile. The switching mechanism of claim 1, wherein the gear set switching mechanism further includes an engaging member movable in an axial direction and fasteningly connecting at least two parts of the gear set switching mechanism, The gear set is cut The changing mechanism is connected to the switching sleeve in a second connection zone in a form-locking and/or force-locking manner. A switching mechanism as claimed in claim 10, wherein the engaging element is latched in the axial direction and/or is connected in a circumferentially force-locking manner to the switching sleeve. The switching mechanism of claim 10 or 11, wherein a frictional force formed between the engaging element of the second connecting region and the switching sleeve formed by a circumferentially directed force is greater than a first connecting region of the switching sleeve The maximum moment of inertia generated. A switchable planetary gear set for use in a machine tool, the planetary gear set including a drive shaft, a driven shaft, a planetary configuration and a central shaft, wherein the central shaft can move axially, The central shaft is moved between a first and a second switching position by a gear set switching mechanism, wherein the central shaft, the drive shaft, the planetary configuration and/or the driven shaft are capable of switching between The positions are intermeshing in different ways, and the planetary gear set is characterized in that the switching mechanism is set according to one of the items 1 to 12 previously described.