Abstract:
A valve drive for activation of gas exchange valves of internal combustion engines, with which valve stroke switching is accomplished with little effort, a low construction height, and at low switching forces. Incorrect switching and damage to the camshaft during valve stroke switching are avoided, even at high engine speeds of rotation. An adjustment shaft that is rotatable by the camshaft and parallel to the camshaft has two adjustment devices rotatably disposed on it, along with two tappets between the adjustment devices. The tappets are connected with a shift gate for valve switching between two different cam profiles of a cam package that is axially displaceable on the camshaft. The tappets each have a contour that contacts the adjustment devices via a guide pin. A gear wheel engages with a gear segment on the camshaft, via a drive on the adjustment shaft, to rotate the adjustment shaft.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     Applicant claims priority under 35 U.S.C. 119 of German Application No. 10 2008 061 440.8 filed Dec. 10, 2008. 
     BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The invention relates to a valve drive for activation of gas exchange valves of internal combustion engines. 
     2. The Prior Art 
     It is known to operate gas exchange valves of an internal combustion engine variably with different opening and closing time points, as well as with different valve opening strokes. Such a valve control is described in German Patent Application No. DE 42 30 877 A1. In this connection, a camshaft block having two different cam contours is disposed on a camshaft so as to rotate with it, but in an axially displaceable manner. Depending on the axial position of the cam block, a cam contour stands in a functional connection with the stroke valve, by way of an intermediate element (transfer lever). The axial displacement of the cam block for changing the valve parameters takes place during the base circle phase, counter to the effect of a reset spring, by means of a pressure ring. 
     German Patent Application No. DE 35 20 859 A1 describes an internal combustion engine having at least one camshaft driven by a crankshaft, for activation of inlet and outlet valves. Two cams having different structures, in terms of their cam contour, and placed directly next to one another are disposed on the camshaft; these cams determine the opening and closing time point and the opening stroke in accordance with their configuration, taking the valve play into account. During passage through the cam base circle, which has the same shape in both cams, an adjustable intermediate piece is displaced, by way of a shift rod and a lever, in such a manner that optionally, one of the two cams can be brought into a functional connection with the valve. 
     German Patent Application No. DE 195 19 048 A1 describes a variable valve drive for an internal combustion engine, in which again, two cams having different structures, in terms of their cam contour, and placed directly next to one another are disposed on the camshaft. The change in cam engagement takes place by axial displacement of the camshaft with the cam situated on it. 
     Furthermore, a valve drive of an internal combustion engine is described in German Patent Application No. DE 195 20 117 C2, in which an axially displaceable cam block having at least two different cam paths is disposed on the camshaft, so as to rotate with it. The adjustment of the cam block takes place by way of an adjustment organ that is guided in the interior of the camshaft. The adjustment organ is displaced in the interior of the camshaft by a dual-action hydraulic or pneumatic piston/cylinder unit disposed on the face side of the camshaft. The adjustment organ is connected with an entrainment piece that penetrates an oblong hole disposed axially in the camshaft, and ends in a bore of the cam block. 
     German Patent Application No. DE 100 54 623 A1 describes a device for switching over a cam package on a camshaft, to activate gas exchange valves, in which the cam package is guided on the camshaft in an axially displaceable manner. The gas exchange valve is in a functional connection with different cam contours, in accordance with the position of the cam package. The adjustment of the cam package takes place by way of a setting element in interaction with a gate track. The setting element is a pin that can be displaced radially to the outside, which interacts, in the moved-out state, with at least two gate tracks formed in a guide part disposed around the cam package by approximately 180°. 
     A disadvantage of the cited prior art is the great need for construction space that is required to adjust the cam block. These solutions can therefore be used only in the case of relatively large cylinder distances, so that the corresponding components can be accommodated. Another disadvantage is the great mass forces that occur during the setting process, which are required for displacing the cam blocks or the adjustment organs. Switching to a corresponding cam contour can generally take place only cylinder-selectively with the solutions named in the prior art. Valve-selective switching is not possible. 
     A significant disadvantage of DE 100 54 623 A1 is that in order to switch to a different cam contour, the pin has to be moved out of the camshaft and tracked into an axially displaceable shift gate. After the switching process, the pin has to be moved back in again. This design is very parts-intensive and production-intensive, and there is the risk of damage to the camshaft, resulting from incorrect shifting of the pin. A further disadvantage is that the engine speed of rotation is limited because of the required adjustment time of the pin. Furthermore, the adjustment is dependent on the oil pressure that is present. 
     German Patent Application No. DE 10 2004 033 798 A1 describes a valve stroke switching mechanism for gas exchange valves in an internal combustion engine, between two different cam contours, by means of a shift gate disposed on the housing of the internal combustion engine so as not to rotate, but in an axially displaceable manner. The shift gate partly surrounds the camshaft and is provided with a gate groove that widens opposite to the direction of rotation of the camshaft, the side walls of which groove each form a gate flank that can be brought reciprocally into a functional connection with a contact surface disposed on an axially displaceable second cam contour, on both sides, laterally, in order to switch the valve stroke. During valve stroke switching, the axially displaceable second cam contour is either pushed over the cam contour of the cam that is firmly connected with the camshaft, by means of the shift gate, or pushed away from the cam contour, so that optionally, two different cam contours can be brought into a functional connection with the gas exchange valve. 
     SUMMARY OF THE INVENTION 
     It is therefore an object of the invention to create a valve drive of the type stated, for activation of gas exchange valves of internal combustion engines, with which valve stroke switching is carried out with little technical effort, a low construction height, and at low switching forces to be applied, whereby incorrect switching and damage to the camshaft during valve stroke switching are avoided even at high engine speeds of rotation. 
     According to the invention, this task is accomplished by a valve drive for activation of gas exchange valves of internal combustion engines, having at least one camshaft driven by the crankshaft of the internal combustion engine, axially displaceable cams disposed on the camshaft, which stand in a functional connection, directly or by way of intermediate elements, with the gas exchange valve, and a shift gate disposed on the housing of the internal combustion engine; in an axially displaceable manner. The gate is provided with a gate groove that widens counter to the direction of rotation of the camshaft, and which can be brought into a functional connection with contact surfaces of a displaceable cam contour, for valve stroke switching between at least two different cam profiles. 
     For activation of the valve stroke switching, an adjustment shaft that can be rotated by the camshaft is disposed parallel to the camshaft, and two adjustment devices are disposed on this shaft so as to rotate with it, along with two tappets that are axially displaceable on the adjustment shaft, between the adjustment devices. The tappets are firmly connected with the axially displaceable shift gate for valve switching between at least two different cam profiles of a cam package that is axially displaceable on the camshaft. The face sides of the tappets that are disposed between the adjustment devices are each provided with a contour, which contours stand in a functional connection with one another by way of a guide pin or a counter contour that is attached to the adjustment device, in each instance. In this connection, the contours of the two tappets are disposed offset by 180°. By rotating the adjustment shaft, the tappets are axially displaced on the adjustment shaft by the guide pins or counter contours that slide on the contour. 
     The adjustment shaft is driven by the camshaft. Camshaft can be brought into engagement with the adjustment shaft by a shiftable gear mechanism. The gear mechanism is adapted to drive the adjustment shaft a defined angle by each rotation of the camshaft. Shifting of the gear mechanism is designed to allow a temporarily engagement of the gear mechanism so that gear mechanism can be brought into or out of engagement during each rotation of the camshaft. The engagement of the cam mechanism can so be limited to a single rotation of the cam shaft to drive the adjustment shaft a defined angle range for example 90° or 180°. 
     A first embodiment of the gear mechanism has a gear wheel on the adjustment shaft. The gear wheel is disposed so as to rotate with the shaft, but in axially displaceable manner, which gear wheel is brought into engagement with a gear segment disposed on the camshaft, by a drive disposed on the adjustment shaft, in order to rotate the adjustment shaft. 
     An alternative embodiment of the gear mechanism has a shift cam and a lever system. The lever system which is disposed on the adjustment shaft so as to rotate with it has at least two lever arms. The shift cam is in an axially displaceable manner disposed on the camshaft so as to rotate with it. The shift cam can be brought into engagement with the lever system to drive the adjustment shaft. 
     The advantage of the solution according to the invention consists in that reliable valve stroke switching between different cam contours takes place with little effort and little required construction space. Because of the controlled rotation of the adjustment shaft by way of the camshaft, and thus the compulsorily controlled displacement of the shift gate, incorrect switching positions during valve stroke switching are avoided. 
     In a preferred embodiment, a cam package can be disposed on the camshaft so as to rotate with it. The cam package is firmly connected with a pin in an axially displaceable manner. The pin can be brought into engagement with the insides of the gate groove of the shift gate, which groove widens counter to the direction of rotation of the camshaft. 
     In another embodiment, the gear segment disposed on the camshaft is disposed in such a manner that an axial displacement of the shift gate by means of the pin only takes place during engagement of the base circle profile of the camshaft with the gas exchange valve. 
     A spring can be disposed on the gear wheel, the spring force of which is directed counter to the displacement direction of the drive. The adjustment device can be provided with a locking device consisting of a spring and a ball. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Other objects and features of the present invention will become apparent from the following detailed description considered in connection with the accompanying drawings. It is to be understood, however, that the drawings are designed as an illustration only and not as a definition of the limits of the invention. 
       In the drawings, wherein similar reference characters denote similar elements throughout the several views: 
         FIG. 1  shows a perspective representation of one embodiment of the invention, in which a large cam contour is active; 
         FIG. 2  shows a side view from the right according to  FIG. 1 ; 
         FIG. 3  shows a side view from the left according to  FIG. 1 ; 
         FIG. 4  shows a detail view of the camshaft with the displaceable cam segment in a switching position in which the small cam contour stands in a functional connection with a gas exchange valve; 
         FIG. 5  shows a detail view of the camshaft with the displaceable cam segment in a switching position in which the large cam contour stands in a functional connection with a gas exchange valve; 
         FIG. 6  shows a perspective representation of the solution according to the invention, during an activated switch between the cam profiles; 
         FIG. 7  shows a perspective representation of the solution according to the invention, in an intermediate position during a switch between the cam profiles; 
         FIG. 8  shows a front view according to  FIG. 6 ; 
         FIG. 9  shows a view from above according to  FIG. 6 ; 
         FIG. 10  shows a perspective representation of an alternative embodiment of the invention having an alternative gear mechanism to drive the adjustment shaft; 
         FIG. 11  shows a front view according to  FIG. 10 ; and 
         FIG. 12  shows a perspective representation of the alternative embodiment of the invention during an activated switch between the cam profiles. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring now in detail to the drawings, the valve drive according to one embodiment of the invention is shown in  FIG. 1 , for activation of gas exchange valves, and consists of a camshaft  1  driven by a crankshaft of the internal combustion engine, with an adjustment shaft  12  for activating valve stroke switching between two different cam profiles  15 ,  16  disposed parallel to it. In this embodiment, adjustment of two valves of a cylinder takes place. An application of the invention can also be used for multiple cylinders. A cam package  2  is mounted in an axially displaceable manner in camshaft  1 , so as to rotate with it. Cam package  2  consists of four cams, of which each set of two adjacent cams have a large cam profile  15  and a small cam profile  16 . Cam package  2 , as shown in  FIGS. 4 and 5 , can be structured to be divided in the axial direction, whereby the cam part that consists of base circle profiles  14  is firmly connected with camshaft  1 , and the cam part provided with the cam parts having cam profiles  15 ,  16  is displaceable relative to the firmly disposed base circle profiles  14 .  FIG. 4  shows a switching position in which each small cam profile  16  stands in a functional connection with the gas exchange valves. In this switching position, small cam profile  16  is above base circle profile  14 .  FIG. 5  shows a switching position in which the gas exchange valves are activated by large cam profiles  15 . In order for a precise end switching position to be achieved, a catch element, which is known but not shown, is disposed between the displaceable cam part and camshaft  1 . 
     It is also possible to configure cam package  2  as a component that is connected with camshaft  1  so as to rotate with it, but in an axially displaceable manner on it. In this configuration, it is necessary for each of large cam profile  15  and small cam profile  16  to be provided with a uniform base circle profile  14 . 
     A pin  4  is firmly disposed on axially displaceable cam package  2 , which pin can be brought into engagement with the inside surface of a widening gate groove  20  of an axially displaceable shift gate  3  for displacing cam package  2 . Shift gate  3  partly surrounds camshaft  1  and is provided with a gate groove  20  that widens counter to the direction of rotation of camshaft  1 . Pin  4  passes through gate groove  20  of shift gate  3  during every revolution of camshaft  1 . In this connection, pin  4  is disposed on cam package  2  in such a manner that the axis of pin  4  is disposed in accordance with a switching position that is appropriate for the phase of the base circle  14 , as shown in  FIGS. 4 and 5 . 
     A tappet  5 ,  23  is firmly connected on both sides of the circumference of shift gate  3 . Tappets  5 ,  23  are mounted to be axially displaceable on adjustment shaft  12 . A contour  21  is disposed on the face side of tappet  5  that lies on the outside, and a contour  22  is disposed on the face side of tappet  23  that lies on the outside. The two tappets  5 ,  23  are disposed on adjustment shaft  12 , between two adjustment devices  10 ,  17  that are disposed on adjustment shaft  12  so as to rotate with it. A guide pin  18  is firmly disposed on adjustment device  10 , which pin connects with contour  21  of tappet  5 . A guide pin  24  is firmly disposed on the adjustment device  17 , which pin connects with contour  22  of tappet  23 . The engagement of guide pin  18  of adjustment device  10  on contour  21  of tappet  5  is disposed offset by 180° relative to the engagement of guide pin  24  of adjustment device  17  on contour  22  of tappet  23 . In this connection, either the axes of guide pins  18 ,  24  can lie in one axis direction and contours  21 ,  22  are offset by 180° relative to one another, or contours  21 ,  22  are disposed identically and guide pins  18 ,  24  are offset by 180° relative to one another. 
     A gear wheel  7  is mounted on adjustment shaft  12  so as to rotate with it, but in an axially displaceable manner. In order to displace gear wheel  7  on adjustment shaft  12  counter to the spring pressure of a spring  9 , gear wheel  7  is connected with a drive  6  that moves an adjustment bolt  19  out when activated. After activation of drive  6 , the axially displaceable gear wheel  7  engages into a gear segment  8  that is situated on camshaft  1 . This gear segment  8  extends on camshaft  1  over an angle range of 180° if two gas exchange valves are activated, and is disposed in such a manner that a displacement of tappets  5 ,  23  takes place only if pin  4  is situated outside of gate groove  20 . If multiple gas exchange valves of additional cylinders, for example two, are activated by a cam star, gear segment  8  would extend only over an angle range of 90°. 
     Adjustment of cam package  2  for valve stroke switching between two different cam profiles  15 ,  16  takes place as follows:  FIG. 6  shows a valve drive in which the switching process of engagement of small cam profile  16  with the gas exchange valves to large cam profile  15  was activated by starting up drive  6 . Cam package  2  is in the position shown in  FIG. 4  before the switching process is initiated. During the adjustment process, gear wheel  7  is displaced on adjustment shaft  12  by adjustment bolt  19 , so that it engages gear segment  8  situated on camshaft  1 . Displacement of gear wheel  7  only occurs if it has been assured that no engagement of the gear wheel  7  with gear segment  8  can take place during the actual displacement process. Before gear wheel  7  engages gear segment  8 , pin  4  runs through gate groove  20  in shift gate  3 , without touching the inside walls of gate groove  20  while doing so. With the engagement of gear wheel  7  into gear segment  8 , rotation of adjustment shaft  12  by camshaft  1  takes place.  FIG. 6  shows the direction of rotation of adjustment shaft  12  and of camshaft  1  and the displacement direction of cam package  2  for this example. 
       FIG. 7  shows an intermediate position of the valve stroke switching by adjustment shaft  12 . Because of the rotation of adjustment shaft  12 , at the same time, adjustment devices  10 ,  17  disposed on adjustment shaft  12  so as to rotate with it are rotated, and thus guide pins  18 ,  24  firmly disposed on these devices are rotated. Since guide pins  18 ,  24  are connected with contours  21 ,  22  of tappets  5 ,  23  that are each disposed offset by 180°, axial displacement of the two tappets  5 ,  23  on adjustment shaft  12 , in the direction of adjustment device  17 , takes place. At the same time, axial displacement of shift gate  3  by tappets  5 ,  23  takes place.  FIG. 8  shows a side view according to  FIG. 7 , and  FIG. 9  shows the related top view. In  FIG. 8 , the interaction of guide pins  18 ,  24  with contour  21 ,  22  of the tappets  5 ,  23 , respectively, can be clearly seen. In this connection, contours  21 ,  22  of tappets  5 ,  23  are disposed in such a manner that switching of switch gate  3  in accordance with the phase takes place. 
     After engagement of gear wheel  7  with gear segment  8  has taken its course, adjustment devices  10 ,  17  have been rotated so far that guide pin  18  lies against the highest point of contour  21 , and guide pin  24  lies against the lowest point of contour  22 . The displacement of tappets  5 ,  23  has been concluded. In order to prevent adjustment shaft  12  from being turned further, a locking device is disposed on adjustment device  10  or  17 . The locking device consists of a spring  11  and a ball  13 , which engages into a corresponding depression disposed in adjustment device  10  or  17 . In  FIG. 2 , balls  13  engaged into the depression of adjustment device  10  can be seen. At the same time, drive  6  is deactivated, and gear wheel  7  is moved out of the engagement region of gear segment  8  by the spring force of spring  9  that acts counter to the adjustment direction of drive  6 . In  FIG. 1 , this position is shown with gear wheel  7  already pushed back. 
     During displacement of shift gate  3  by tappets  5 ,  23 , the pin  4  that is firmly disposed on cam package  2  is situated outside of the region of gate groove  20  that widens counter to the direction of rotation of camshaft  1 , as shown in  FIG. 7 . By further rotation of camshaft  1 , pin  4  meets the left inside surface of gate groove  20  at its widest point. As a result of the rotational movement of camshaft  1 , pin  4  migrates along the left inside of gate groove  20 . Because gate groove  20  narrows in the direction of rotation of camshaft  1 , pin  4  and thus the axially displaceable cam package  2  are displaced to the right, until large cam profile  15  lies above the corresponding base circle profile  14 , as shown in  FIG. 5 . By means of a locking device disposed between camshaft  1  and the displaceable cam package, cam package  2  is locked in place in the newly achieved switching position. Because of the placement of shift gate  3  and pin  4 , a displacement of cam package  2  and thus valve stroke switching only take place if base circle profile  14  of camshaft  1  is connected to a gas exchange valve. 
     Reverse adjustment takes place analogous to the above description, whereby tappets  5 ,  23  are displaced in the direction of adjustment device  10  by guide pins  18 ,  24  that connect with contours  21 ,  22 . 
       FIGS. 10 ,  11  and  12  show a second embodiment of the invention, wherein similar reference characters denote similar elements throughout the several embodiments. 
     Cam package  2  consists of three different cam profiles, the small cam profile  16 , the large cam profile  15  and a middle-sized cam profile  25  which is located between the large  15  and the small cam profile  16 . A valve stroke switching between three different valve strokes caused by the different cam profiles  15 ,  16 ,  25  can be realized. 
     A tappet  5 ,  23  is firmly connected to both sides of the circumference of shift gate  3 . Tappets  5 ,  23  are mounted on adjustment shaft  12  and adapted to be axially displaceable on adjustment shaft  12 . Tappets  5 ,  23  can be designed integrally as shown in  FIG. 10  or can be separate tappets  5 ,  23  as shown in  FIG. 11 . 
     The tappets  5 ,  23  are disposed on adjustment shaft  12 , between two adjustment devices  10 ,  17 . Differing from the first embodiment, where guide pins connecting adjustment devices  10 ,  17  and tappets, are counter contours  26 ,  27  disposed on the face side of the adjustment devices  10 ,  17  so as to rotate with them. Counter contour  26  is disposed on the face side of adjustment device  10  opposite of contour  21  disposed on the face side of tappet  5 . Adjustment device  10  and tappet  5  are mechanically linked by contour  21  and counter contour  26 . Analogous to adjustment device  10  is a counter contour  27  disposed on the face side of adjustment device  17  opposite of contour contour  22 , disposed on the face side of tappet  23 . It is a preferred embodiment to link adjustment devices  10 ,  17  with tappets  5 ,  23  via contours  22 ,  23  and counter contours  26 ,  27 . An alternative embodiment has a link via guide pins  18 ,  24  disposed on adjustment devices  10 ,  17 , as described in  FIGS. 6 and 7 . Another—not shown—alternative embodiment has guide pins  18 ,  24  disposed on tappets  5 , 23  and linked with adjustment devices  10 ,  17  where counter contours  26 ,  27  are disposed on their face sides. 
     Adjustment shaft  12  is driven by camshaft  1  which can be shiftable linked with the adjustment shaft  12  by a gear mechanism. The gear mechanism consists of a lever system  28  which is disposed on the adjustment shaft  12  so as to rotate with it and a shift cam  29 . The shift cam  29  is in an axially displaceable manner disposed on the camshaft  1  so as to rotate with it. The shift cam  29  can, depending on its axial position on the cam shaft  1 , be linked mechanically with the lever system  28  to drive the adjustment shaft  12 . In another—not shown—embodiment is the lever system  28  axially displaceable disposed on the adjustment shaft  12  and shift cam  29  has a fixed axial position on cam shaft  1 . 
       FIGS. 10 and 11  show the gear mechanism in its inactive state where shift cam  29  and lever system  28  are unengaged. In this inactive state is the adjustment shaft  12  not driven by camshaft  1  in standstill. Tappets  5  and  23  keep their position without rotation of the adjustment devices  10 , 17 . 
     Shift cam  29  can be actuated by actuator  30  which can axially displace the shift cam  29  on camshaft  1 . 
     The possible axial displacement of shift cam  29  is illustrated by a double arrow in  FIG. 11 . The axial displacement towards its engaged position with the lever system  28  is caused by actuator  30  whereby the reverse movement into its inactive state is supported by spring  32 . 
     The lever system  28 —shown in  FIGS. 10 ,  11  and  12 —consists in this embodiment of a system of four interconnected levers arranged around a central hub, whereby each lever supports a pivotably mounted roller  31  supported on the end of each lever. In another embodiment are, instead of the rollers  31 , slide faces (not shown) supposed on the end of each lever. 
     The shift cam  29  is mounted on cam shaft  1  so as to rotate with it, but in an axially displaceable manner. In order to displace shift cam  29  on cam shaft  1 , counter to the spring pressure of spring  32 , shift cam  29  is driven by actuator  30  that drives shift cam  29  axially on camshaft  1 . After activation of actuator  30 , the axially displaceable shift cam  29  engages into a lever of the lever system  28  that is firmly disposed on adjustment shaft  12 . 
     Adjustment of cam package  2  for valve stroke switching between the different cam profiles  16 ,  25  and  15  takes place as follows:  FIG. 12  shows a valve drive in which the switching process of engagement of medium sized cam profile  25  with the gas exchange valves to large cam profile  15  was activated by starting up actuator  30 . Cam package  2  is in the position before the switching process is initiated. During the adjustment process, shift cam  29  is displaced on adjustment shaft  12  by actuator  30 , so that it engages lever system  28  situated on adjustment shaft  12 . Before shift cam  29  engages lever system  28 , pin  4  runs through gate groove  20  in shift gate  3 , without touching the inside walls of gate groove  20  while doing so. With the engagement of shift cam  29  into lever system  28 , rotation of adjustment shaft  12  by camshaft  1  takes place. Shift gate  3  is positioned by displacement devices  10 , 17  where counter contours  26 ,  27  face the contours  21 ,  22  of tappets  5 ,  23  as described in detail above. The profile of contours  21 ,  22 , counter contours  26 ,  27  and their position to each other define the axial position of tappets  5 ,  23 . 
     The lever system  28  has four lever arms equally spaced around the central hub. The lever system  28  is adapted to rotate adjustment shaft 90° by each rotation of the cam shaft preferably for shifting three different cam profiles. An alternative embodiment of the lever system  28  has two lever arms equally spaced to rotate adjustment shaft 180° by each rotation of the shift cam  29 . 
     The design of the shift element as a shift cam  29  is a preferred embodiment. The shape of the shift element can vary. It has to be adapted to drive the lever system to rotate adjustment shaft. 
     Accordingly, while only a few embodiments of the present invention have been shown and described, it is obvious that many changes and modifications may be made thereunto without departing from the spirit and scope of the invention.
       1  camshaft     2  cam package     3  shift gate     4  pin     5  tappet     6  drive     7  gear wheel     8  gear segment     9  spring     10  adjustment device     11  spring     12  adjustment shaft     13  ball     14  base circle profile     15  large cam profile     16  small cam profile     17  adjustment device     18  guide pin     19  adjustment bolt     20  gate groove     21  contour     22  contour     23  tappet     24  guide pin     25  medium-sized cam profile     26  first counter-contour     27  second counter-contour     28  lever system     29  switch cam     30  actuator     31  roller     32  spring