Abstract:
A switchable device for supplying at least one consumer of an internal combustion engine with pressure. The device includes the following: a cavity formed inside a camshaft; a displacement element arranged in the cavity, which element can be displaced between a first end position and a second end position, the displacement element having a pressure surface which at least partially delimits a fluid connectible accumulator chamber together with the wall of the cavity, the accumulator chamber being connectible to a pressure source in a fluid-conducting manner; an energy accumulator interacts with the displacement element, the displacement element being displaceable against the force of the energy accumulator from the first end position into the second end position under the effect of pressure applied to the accumulator chamber; a locking mechanism by which the displacement element can be locked in the second end position; a switching mechanism which can be actuated by an actuator, has a switch element that can be brought into at least two switching positions and interacts with the locking mechanism in such a manner that the locked state of the displacement element is maintained in a first switching position and is released in a second switching position.

Description:
FIELD OF THE INVENTION 
     The invention lies in the technical field of internal combustion engines and relates to a switchable device integrated in a cavity of a camshaft for a pressure supply to loads of an internal combustion engine. 
     BACKGROUND 
     From Patent No. EP 1197641 A2, a pressure accumulator for supporting a hydraulically adjustable camshaft is known in which the flow of hydraulic fluid into or out of the pressure accumulator is controlled by the use of different solenoid valves. 
     A pressure accumulator with a separate housing is further known from the German Laid Open Patent Application DE 102007056684 A1 of the applicant. 
     SUMMARY 
     Accordingly, the objective of the present invention relates to refining conventional pressure accumulators for supplying pressure to loads in internal combustion engines in an advantageous manner. 
     This and other objects are met according to the proposal of the invention by a switchable device for supplying pressure with the features of the main claim. Advantageous constructions of the invention are specified by the features of the subordinate claims. 
     According to the invention, a switchable device for a pressure supply (switchable pressure accumulator) to at least one load of an internal combustion engine is shown. The load can involve, in particular, a hydraulic camshaft adjuster for adjusting the phase position between the crankshaft and camshaft. It is also conceivable, however, that the device is used, for example, in an electrohydraulic valve actuation device of an internal combustion engine. 
     The device for supplying pressure comprises a cavity formed within a camshaft of the internal combustion engine and a displacement element that is arranged in the cavity and can be displaced between a first end position and a second end position. The displacement element has a pressure surface that at least partially bounds, together with a wall of the cavity, a storage space that can be connected or is connected in a fluid-conducting manner to the load. The storage space can be connected or is connected to a pressure source or pressurized medium source in a fluid-conducting manner. For example, the storage space is connected to the lubricating oil circuit of the internal combustion engine, wherein an oil pump is used as the pressure source and oil of the lubricating oil circuit is used as the pressurized medium. The displacement element can be constructed, for example, in the form of a piston with an end-side pressure surface. 
     The device according to the invention further comprises a force accumulator that interacts with the displacement element so that the displacement element can be displaced by pressurization of the storage space against the force of the force accumulator from the first end position into the second end position. The force accumulator is constructed, for example, as a spring element, in particular, in the form of a compression spring, wherein any other suitable spring type could also be used. 
     The device according to the invention further comprises a locking mechanism through which the displacement element can be locked detachably in the second end position in which the force accumulator is clamped. 
     In addition, the device according to the invention comprises a switching mechanism with a switch element, wherein this switching mechanism is actuated by an actuator and can be brought into at least two switch positions, wherein the switch element interacts with the locking mechanism so that the locking of the displacement element is maintained in a first switch position and is released in a second switch position. Advantageously, the switching element can be displaced between the two switch positions by an actuator rotationally decoupled from the camshaft. 
     For relatively low installation space requirements, the device according to the invention allows a more reliable and more secure supply of pressure to the loads of an internal combustion engine that is provided independent of the pressure in the lubricating circuit of the internal combustion engine. 
     In one advantageous construction of the device according to the invention, the storage space can be connected or is connected in a fluid-conducting manner to the pressure source and to the load with at least one leakage prevention device provided in-between. The leakage prevention device is constructed so that it allows the through flow of pressurized medium, while it blocks the through flow of non-pressurized medium merely at the hydrostatic pressure. Thus, the leakage prevention device can prevent leakage from the storage space if insufficient pressure is supplied by the pressure source, for example, in the case of insufficient output from the oil pump. The leakage prevention device can be used as a limit for the storage space and can form, in particular, a stop for the locking element in the second switch position. 
     In another advantageous construction of the device according to the invention, it comprises a ball carrier that is connected rigidly to the camshaft and surrounds the switch element. The ball carrier has a plurality of openings in each of which a ball is held so that it can move freely in the radial direction. Here, the balls are supported in the radial direction by a support surface formed by the switch element. 
     In this construction of the device, the device further comprises a locking element that is connected rigidly to the displacement element and is provided with a locking section that is led into engagement with the balls in the second end position of the displacement element, for example, in that it engages behind these balls, in order to lock the displacement element on the camshaft. On the other side, the locking element is not led into engagement with the balls in the first end position of the displacement body, so that the displacement element is not locked. 
     In this construction of the device, a first non-return element is also provided that is arranged so that the switch element can be displaced by the actuator relative to the ball carrier against the force of the first non-return element from the first switch position into the second switch position. The first non-return element is constructed, for example, as a spring element, in particular, in the form of a compression spring, wherein any other suitable spring type could also be used. 
     In this construction of the device, the support surface of the switch element is provided with at least one recess that is allocated to the balls and is constructed and arranged so that the balls can be held at least partially in the recess in the second switch position of the switch element, so that the locking section is led out of engagement with the balls and the locking of the displacement element is released. On the other side, the balls are not held by the recess of the support surface in the first switch position of the switch element, so that the locking of the displacement element is maintained. 
     These measures allow a technically especially simple realization of the locking and switch mechanism, wherein the device for supplying pressure is distinguished by an especially good response behavior. 
     In the above construction of the invention, it can also be advantageous if a sliding element is provided that can be displaced by the displacement element against the force of a second restoring element, wherein the sliding element is constructed so that it slides around the balls for securing them in their radial position in the first end position of the displacement element and releases these balls in the second end position. Thus the sliding element forms a captive securing device for the balls when these are not in engagement with the locking section of the locking element. The second restoring element is constructed, for example, as a spring element, in particular, in the form of a compression spring, wherein any other suitable type of spring could also be used. 
     In another advantageous construction of the device according to the invention for supplying pressure, this is provided with a sealing element that seals the camshaft to the outside and on which the force accumulator of the displacement element is supported. The sealing element can be used here especially for securing the position of the force accumulator. 
     In another advantageous construction of the device according to the invention, the pressure source can be connected or is connected in a fluid-conducting manner via a non-return valve that forms a block in the direction toward the pressure source to the load and to the storage space. 
     The invention further extends to an internal combustion engine that is equipped with at least one device that can be switched as described above for supplying pressure to at least one load. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention will now be explained in more detail with reference to an embodiment, wherein reference is made to the accompanying drawings. Elements that are identical or have identical actions are designated in the drawings with the same reference symbols. Shown are: 
         FIG. 1  is a schematic axial section diagram of an embodiment of the device according to the invention for supplying pressure, 
         FIG. 2  is a schematic overview diagram, with reference to which the connection of the device for supplying pressure from  FIG. 1  to the lubricating oil circuit of an internal combustion engine is illustrated, 
         FIG. 3  is an enlarged section from  FIG. 1  with locked switching element of the device for supplying pressure, 
         FIG. 4  is an enlarged section from  FIG. 1  with released switching element of the device for supplying pressure. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       FIG. 1  and  FIG. 2  will be considered first, wherein an embodiment of the device according to the invention for a pressure supply for loads of an internal combustion engine, as well as the connection of the device to the lubricating oil circuit of an internal combustion engine, are shown. The device designated overall with the reference number  1  comprises a hollow space  3  that is shaped within a camshaft  2  and in which a displacement element constructed in the shape of a hollow piston  4  is held. The built-up camshaft  2  as an example here can be rotated about a central rotational axis  7 . The same would also be conceivable, however, if the camshaft  2  was produced in the foundry process. 
     Into the hollow space  3  of the camshaft  2 , a sealing body  5  is pressed that is constructed in the shape of a stepped cylinder and extends from one end of the camshaft  2  into the hollow space  3 . It can be divided into a terminal first section  8  with larger diameter and an adjacent second section  9  with smaller diameter, wherein a ring stage  10  of the sealing body  5  is produced. A force accumulator spring (helical compression spring)  11  used as a force accumulator is supported with one of its ends on the ring stage  10  of the sealing body  5 . With its other end, this force accumulator contacts the piston  4 . 
     The sealing body  5  connected rigidly to the camshaft  2  is provided with a central axial bore  6  in which a switch rod  12  is held so that it can be displaced in the axial direction. The switch rod  12  can be actuated by an electromagnetic actuator  17  that is arranged on one end of the camshaft  2 , wherein a tappet  19  engages an end-side contact surface  18  of the switch rod  12  for this purpose. The switch rod  12  is part of a switch mechanism for releasing a locking mechanism for the piston  4  that will be explained in more detail farther below in connection with  FIG. 3  and  FIG. 4 . 
     The piston  4  has an end-side pressure surface  13  that defines a storage space  15  for compressed oil  28  together with an inner wall  14  of the hollow space  3  of the camshaft  2  and a leakage prevention device  16 . 
     Opposite the actuator  17 , a hydraulic camshaft adjuster  21  is attached, for example, by a (not shown) central screw to the end side of the camshaft  2 . As usual, the hydraulic camshaft adjuster  21  comprises a drive part in drive connection with the crankshaft via a drive wheel and a camshaft-fixed driven part, as well as a hydraulic actuating drive that is switched between a drive part and a driven part and transfers the torque from the drive part to the driven part and allows an adjustment and fixing of the rotational position between these parts. The hydraulic actuating drive is provided with at least one pressure chamber pair that act against each other and can be selectively pressurized with pressurized oil, in order to generate a change in the rotational position between the drive part and driven part by generating a pressure drop across the two pressure chambers. Hydraulic camshaft adjusters as such are well known to someone skilled in the art and described in detail, for example, in publications DE 202005008264 U1, EP 1596040 A2, DE 102005013141 A1, DE 19908934 A1, and WO 2006/039966 of the applicant, so that more exact details do not need to be discussed here. 
     As can be taken from  FIG. 2 , the hydraulic camshaft adjuster  21  and the storage space  15  are connected in a fluid-conducting manner via a common pressure line  24  with a pressure source or pressurized medium source constructed in the form of an oil pump  22 . The oil pump  22  can feed pressurized oil  28  from an oil tank  23  to the camshaft adjuster  21  and storage space  15 . A non-return valve  25  that is arranged in the pressure line  24  and forms a block in the direction toward the oil pump  22  prevents a return flow of pressurized oil in the case of reduced or insufficient output from the oil pump  22 . 
     In the central screw for fastening the camshaft adjuster  21  to the camshaft  2 , a control valve not shown in more detail is arranged for controlling the oil flows. This control valve can connect the pressure chambers of the camshaft adjuster  21  in a fluid-conducting manner via oil paths  26  selectively with the oil pump  22  or via a (not shown) oil line with the oil tank  23 . Such control valves are well known as such to someone skilled in the art and described in detail, for example, in the German Patent DE 19727180 C2, the German Patent DE 19616973 C2, the European Patent Application EP 1 596 041 A2, and the German Laid Open Patent Application DE 102 39 207 A1 of the applicant, so that more exact details do not have to be discussed here. 
     The storage space  15  is connected in a fluid-conducting manner via a connection space  67  to the control valve of the camshaft adjuster  21 . The oil paths  26  are connected in a fluid-conducting manner via corresponding pressure channels  68  to the pressure line  24 . 
     In the internal combustion engine, additional loads  27  are connected to the lubricating oil circuit, such as support elements and a camshaft bearing that must be supplied with pressurized oil  28 . 
     The piston  4  can be pushed against the spring force of the force accumulator spring  11  by pressurization of the storage space  15 , as shown in  FIG. 2  by the arrows. Here, pressurized oil  28  is fed by the oil pump  22  via the pressure line  24  into the storage space  15 , wherein the pressurized oil  28  passes through the leakage prevention device  16  that is transmissible for pressurized oil  28 . Here, the piston  4  is pushed from a first end position into a second end position in which the force accumulator spring  11  is tensioned or is more strongly tensioned in the event of a biasing tension. Through a plurality of ring seals  29 , the storage space  15  is sealed oil-tight from the outside. 
     In the second end position, the piston  4  can be locked by a locking mechanism. The locking mechanism will now be explained in more detail with reference to  FIG. 3 , which is an enlarged axial section view of the device  1  with locked piston  4 . The locking mechanism thus comprises a sleeve-shaped ball carrier  31  that is pressed into a sleeve-shaped end section  30  of the sealing body  5  and has a plurality of radial bores  32  arranged distributed in the peripheral direction. A ball  33  is held in each of these bores. Here, the bores  32  each have a larger diameter than the balls  33 , so that these are freely moveable in the radial direction in the bores  32 . The ball carrier  31  is provided with an end surface  58  on its side facing away from the sealing body  5 . 
     Furthermore, a sleeve body  36  is pressed into a hollow space  35  of the ball carrier  31 , wherein this sleeve body contacts a shoulder  39  of the sealing body  5  with a first end surface  59  facing away from the piston  4 , and wherein oil tightness is ensured by an intermediary ring seal  29 . An opposite second end surface  60  of the sleeve body  36  forms an end stop for a switch pin  37  connected rigidly to the switch rod  12 . 
     An outer lateral surface  41  of the switch pin  37  is provided with a ring groove  38  whose axial section has a ball-shell shape and is allocated to the balls  33 . On its end facing away from the sleeve body  36 , the switch pin  37  is provided with a sleeve-shaped end section  42  in which a restoring spring  43  is held. The restoring spring  43  is supported with its one end on a ring stage  46  shaped by the switch pin  37  and is supported with its other end on a plunger  44 . In the locking position of the piston  4  shown in  FIG. 3 , the plunger  44  contacts an inner surface  34  of the piston  4 . The plunger  44  is secured by a snap ring  45  against falling out from the end section  42  of the switch pin  37 . 
     Furthermore, on an outer lateral surface  40  of the ball carrier  31 , an at least approximately sleeve-shaped sliding body  47  is arranged so that it can move in the axial direction relative to the ball carrier  31 . The sliding body  47  is loaded by a sliding spring  49  that is constructed here, for example, as a compression spring. For this purpose, the sliding spring  49  is supported with one end on an end surface  62  of the sealing body  5  and with its other end on a ring stage  48  of the sliding body  47 , so that the sliding body  47  is loaded by the spring force of the sliding spring  49  in the direction of the switch pin  37 . The sliding body  47  made, for example, from sheet steel is provided with a sliding section  50  that slides into the locking position shown in  FIG. 3  over the balls  33  and thus acts as a captive securing device. In the non-locked position of the piston  4  shown in  FIG. 4 , the sliding section  50  releases the balls  33 . 
     The piston  4  is connected to a sleeve-shaped locking body  53 . The locking body  53  is provided with a radially projecting collar  54  that is provided for this purpose and is pressed by the force accumulator  11  against a shoulder  52  of the piston  4 , so that the locking body  53  is connected by a non-positive fit to the piston  4 . The locking body  53  has a locking section  55  with a radially inward directed ring bead  56  that forms a recess  57 . 
     Now if the storage space  15  is loaded with pressurized oil starting from the non-locked position shown in  FIG. 1 , the piston  4  is displaced by its pressure surface  13  against the spring force of the force accumulator  11 . Here, an end surface  61  of the locking body  53  comes into contact with a first end surface  63  of the sliding body  47  and displaces this body against the spring force of the sliding spring  49  up to the balls  33  in the region of the recess  57 . In addition, the inner surface  34  comes into contact with an end surface  65  of the plunger  44 , wherein the switch pin  37  is displaced in the same direction as the piston  4  loaded by the restoring spring  43 . Here, the balls  33  are pressed out from the ring groove  38  of the switch pin  37  into the recess  57 . This movement of the balls  33  is supported by centrifugal force of the rotating camshaft  2 . The balls  33  then contact the outer lateral surface  41  of the switch pin  37 , wherein the ring bead  56  engages behind the balls  33 . An end surface  66  of the switch pin  37  facing away from the plunger  44  is here led into contact with the second end surface  60  of the sleeve body  36  that thus acts as a stop for the switch pin  37 . By means of the switch pin  37 , the switch rod  12  is displaced in the central axial bore  6  of the sealing piece  5 . Finally, the inner surface  34  of the piston  4  is led into contact with the end surface  58  of the ball carrier  31  that thus acts as a stop for the piston  4 . The locked end position of the piston  4  reached in this way is shown in  FIG. 3  (called a second end position in the introduction to the description). The storage space  15  has a maximum volume, i.e., is filled to a maximum degree with pressurized oil  28  in the second end position of the piston  4 . 
     Through a switching mechanism to be explained below, the locked piston  4  can be released. In  FIG. 4 , an unlocked position of the piston  4  is shown. For this purpose, the switch rod  12  can be moved by the tappet  19  contacting the contact surface  18  against the force of the restoring spring  43 . Here, the tappet  19  acts on the end contact surface  18  of the switch rod  12 , wherein the tappet  19  is attached rigidly to a magnetic armature of an electromagnet  20  of the actuator  17  and can be displaced in the axial direction by energizing the magnetic armature. If the magnetic armature is not energized, the switch rod  12  is restored by the spring force of the restoring spring  43 . For releasing the lock, the switch rod  12  and the switch pin  37  that contacts the switch rod  12  is displaced by the action of the tappet  19  until the ring groove is aligned with the bores  32  of the ball carrier  31 . This has the result that the balls  33  enter into the ring groove  38 , so that the ring bead  56  no longer engages behind the balls  33  or the balls  33  come out from the recess  57 . The locking section  53  of the locking element  53  thus loses its engagement with the balls  33 , wherein the locking of the piston  4  is released. 
     As shown in  FIG. 4  by the arrow, the piston  4  is then displaced by the spring force of the force accumulator spring  11 , so that the volume of the storage space  15  is reduced and the pressurized oil  28  contained therein is discharged to the camshaft adjuster  2  and the other loads  27 . The non-return valve  25  prevents pressurized oil  28  from reaching the oil pump  22 . Simultaneously, the sliding body  47  is displaced by the spring force of the sliding spring  49 , wherein the sliding section  50  slides over the balls  33 . When the piston  4  is displaced by the force accumulator spring  11 , the leakage prevention device  16  forms a stop for the piston  4 . (The end position reached in this way is designated the first end position in the introduction to the description.) The pressurized oil  28  pressurized by the piston  4  can pass the leakage prevention device  16 . The leakage prevention device  16  comprises, for example, three disks that are locked in rotation with each other and are each provided with a bore, wherein the three bores are each offset by 120° relative to each other. This measure allows pressurized oil  28  to pass the leakage prevention device  16  and blocks the passage of pressurized oil  28  at merely atmospheric or hydrostatic pressure. 
     Additional features of the invention are given from the following description: 
     In the device according to the invention, a piston integrated in the camshaft is biased by the pressure of the oil pump when the internal combustion engine is running against a spring element up to a defined stroke. In this position, the piston engages in a holding mechanism (ball lock). When the internal combustion engine is turned off, the oil pressure in the oil galleries drops to ambient pressure, just like the pressure in the pressure accumulator. The energy remains stored in the spring element. Through a leakage prevention device (e.g., plate-labyrinth securing device), the lubricating oil cannot return from the oil storage space back into the oil galleries or via the camshaft bearing points into the cylinder head. This pressure accumulator has no pressure loss due to leakage. Complicated high-pressure seals are eliminated. In this way, the system friction is reduced and more usable energy is stored in the spring element. A radially decoupled actuator that is mounted outside the camshaft can release the holding mechanism through brief actuation. By means of the biased spring, the oil is forced from the oil storage space back into the oil circuit of the cylinder head and the camshaft adjuster, assuming that the supply oil pressure in the oil galleries is less than the pressure that can be reached with the pressure accumulator (spring element force multiplied with the piston pressure surface). To prevent a return flow of the oil in the direction of the oil pump when discharging, a non-return valve that forms a block in the direction of the oil pump is provided between the oil pump and the loads to be pressurized with the oil pressure from the pressure accumulator. 
     In the device according to the invention, the piston is guided in the axial direction in the camshaft and supported by a spring element (e.g., tensile or compression spring) on the sealing body that is pressed into the camshaft. The locking body is pressed into the piston. In the sealing body, the ball carrier is pressed. This has eight radial bores that are arranged distributed, for example, around the periphery and into which balls are guided. The sleeve pressed into the ball carrier is used as an end stop for the switch pin. The restoring spring of the switch pin is supported on the piston by means of the plunger and presses the switch pin against the sleeve. The plunger is secured against falling out by a snap ring. The switch rod is connected rigidly to the switch pin and is supported so that it can be displaced in the axial direction in the sealing body. The actuator is screwed into the cylinder head and presses on the switch rod against the restoring spring in the energized state. The attachment to the switch rod/camshaft is realized by a radial decoupling device. The sliding spring biases the axially displaceable sliding plate. A plate-labyrinth leakage prevention device formed of three plates each with a bore in the axial direction on the outer diameter is used, for example, as the leakage prevention device of the cylinder for “pressure-free” oil. The plates are rotated relative to each other by 120°. An advantage in terms of installation space is produced by the arrangement in the hollow space of the camshaft in comparison with pressure accumulators arranged outside of the camshaft. 
     The filling/locking process: when the internal combustion engine is running, oil flows via the camshaft bearing point into the camshaft in the direction of the camshaft adjuster and through the labyrinth-plate leakage prevention device against the piston of the pressure accumulator. Starting at a limit pressure that is given by the force of the force accumulator spring, the piston moves against the spring force in the direction of the locking mechanism. The locking body pushes the sliding plate against the sliding spring in the direction of the sealing body. At the same time, the piston presses against the switch pin via the plunger and the restoring spring. As soon as the contours of the locking body releases the bores in the ball carrier, the balls are pressed outward and thus the piston is locked rigidly. The movement of the balls is supported by centrifugal force generated by the rotating camshaft. Then the switch pin is pressed by the restoring spring against the sleeve and therefore the balls are held in the current position. 
     The unloading/unlocking process: when the actuator is energized, the switch rod and the switch pin are displaced against the restoring spring in the direction of the piston. As soon as the groove in the switch pin is over the radial bores in the ball carrier, the force accumulator spring presses the balls inward by means of the contours in the locking element against the switch pin until the cross section is free. The piston is now pressed forward, wherein the oil is pressed from the storage space into the oil galleries and in parallel into the control valve of the camshaft adjuster. A non-return valve in the oil supply gallery prevents oil from flowing back from the cylinder head. The plate-labyrinth leakage prevention device simultaneously acts as an end stop for the piston. 
     The device according to the invention thus allows a reliable supply of pressure to loads of an internal combustion engine, wherein, through the pressure accumulator integrated in the camshaft, pressurized oil is made available independent of the engine oil supply (lubricating oil circuit) of the internal combustion engine. Thus, loads can also be supplied with pressurized oil when the engine-side oil supply is not adequate, for example, when the engine is started and in the case of very hot pressurized oil in connection with a low output of the oil pump. In particular, immediately after the internal combustion engine is started, the camshaft adjuster can be adjusted into a base position (retarded, middle, advanced position), which is especially suitable in connection with start/stop systems. In addition, the adjustment rate of the camshaft adjuster can be improved, especially for the case of hot idling of the internal combustion engine. 
     LIST OF REFERENCE SYMBOLS 
     
         
           1  Device 
           2  Camshaft 
           3  Cavity of the camshaft 
           4  Piston 
           5  Sealing body 
           6  Axial bore 
           7  Rotational axis 
           8  First section 
           9  Second section 
           10  Ring step of the sealing body 
           11  Force accumulator spring 
           12  Switching rod 
           13  Pressure surface 
           14  Wall 
           15  Storage room 
           16  Leakage prevention device 
           17  Actuator 
           18  Contact surface 
           19  Tappet 
           20  Electromagnet 
           21  Camshaft adjuster 
           22  Oil pump 
           23  Oil tank 
           24  Pressure line 
           25  Non-return valve 
           26  Oil path 
           27  Load 
           28  Pressurized oil 
           29  Ring seal 
           30  End section of the sealing body 
           31  Ball carrier 
           32  Bore 
           33  Ball 
           34  Inner surface 
           35  Cavity of the ball carrier 
           36  Sleeve body 
           37  Switch pin 
           38  Ring groove 
           39  Shoulder of the sealing body 
           40  Outer lateral surface of the ball carrier 
           41  Outer lateral surface of the switch pin 
           42  End section of the switch pin 
           43  Restoring spring 
           44  Plunger 
           45  Snap ring 
           46  Ring step of the switch pin 
           47  Sliding body 
           48  Ring step of the sliding body 
           49  Sliding spring 
           50  Sliding section 
           51  Disk 
           52  Shoulder of the piston 
           53  Locking body 
           54  Collar 
           55  Locking section 
           56  Ring bead 
           57  Recess 
           58  End surface of the ball carrier 
           59  First end surface of the sleeve body 
           60  Second end surface of the sleeve body 
           61  End surface of the locking body 
           62  End surface of the sealing body 
           63  First end surface of the sliding body 
           64  Second end surface of the sliding body 
           65  End surface of the plunger 
           66  End surface of the switch pin 
           67  Connecting space 
           68  Pressure channel