DE2309439A1 - MACHINE FOR PRESSING TEETH AND THE LIKE INTO A WORKPIECE - Google Patents

Description

506 IU: .- Francs /. ·

2309A39

Anderson-Cook Inc. Millers, Michigan, USA

"Machine for pressing teeth and the like into a workpiece"

The invention relates to a machine for pressing gear teeth, Serrations and the like in metal workpieces, and it relates in particular to machines in one embodiment which sits the workpiece between two stroke-movable pressing tools during a pressing process.

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It is known to deform metal workpieces between two opposing, stroke-movable tools. With the stroke movement of the tools against each other, they exert pressure on the workpiece and shape the workpiece. One of the problems that arise when working with machines of this type is to transfer energy from a drive to the pressing tools , in order to bring about a stroke movement of the tools and, at the same time, to bring about a synchronous movement of the tools with one another. In the manufacture of gear teeth and serration teeth, it is particularly important that the stroke-movable tools constantly run synchronously with one another in order to properly produce the teeth on the rotating workpiece between the stroke-movable tools. For example, a high degree of accuracy is required to produce involute gear teeth or splines on an axle or shaft that is non-rotatably intended for engagement with another part. Slipping between the reciprocating tools during the manufacture of the teeth is simply not acceptable. In several known devices of this type, a syn chronization in the movement of the stroke-movable tools is caused by idle gears which mesh with rack teeth which are provided on the oppositely arranged stroke-movable tools.

Examples of machines of this general type are for example from US Patents 408 529, 458 685,

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2,995,964, 3,183,697 and 3,303,682 known.

Another problem that one comes across when doing this type of work is to control the deflection between the stroke-movable tools during a pressing operation. In order to maintain the accuracy during the pressing, it is very important that the stroke-movable tools do not move separate from each other while they are in engagement with a workpiece, beyond an amount that is necessary is to maintain the design tolerances on the teeth that are molded onto the workpiece. The measure of the Pressure tending to move the tools away from each other can change depending on the characteristics of the Material of the workpiece.

In known machines of this type, the problem also arises that the correct setting between the stroke-movable Pressing tools is maintained because of the wear and tear on the guides on which the tools slide. Frequent setting of the tools by setting counter wedges is necessary. That will be with a well-known Machine of this type made particularly difficult by the fact that a synchronizing gear on the tool holding spindle sits and is in direct contact with both sliding parts that carry the tool. The size of the spindle and therefore the Size of the workpiece that can be carried by the spindle,

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is limited, and that makes the adjustment of the sliding parts extremely difficult when the honors wear out because that Synchronization gear sits between the sliding parts and directly on. attacks both sliding parts. The distance between the sliding parts is so limited that with the wear of the guides an adjustment of the toothed racks can only be achieved by adjusting the counter wedges.

In the known machines of this type, the stroke-movable press tools are generally stroke-movable working cylinders driven what a large reservoir of hydraulic fluid makes necessary. In the known machines of this general type, it is not possible to use a hydrostatic Provide drive source to drive the pressing tools.

The invention is therefore based on the object of providing a machine for pressing gear teeth and the like create., in which selectively adjustable means for determining the deflection are provided, so that the degree of deflection the pressing tools can be set selectively in order to take into account the various forces on which one can during a respective pressing process.

Furthermore, a machine for pressing gear teeth and the like is to be created, in which a power transmission

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is provided that is powered by hydrostatic motors can be in order to reduce the required capacity for the hydraulic reservoir.

Next is a machine for pressing gear teeth and the like created in workpieces by stroke-movable tools The machine has an improved drive transmission to control the movement of the tooth-forming tools to synchronize and to get a better mechanical drive of the tools.

Next is a machine for forming gear teeth, serration teeth and the like on workpieces are created by the workpiece between stroke-movable tooth-forming tools, is rotated, the machine having a drive gear which cooperates with the lifting-movable tools such that automatically the movement of the tools against each other is synchronized, whereby the tools with the required Speed are driven relative to each other and the tools are only connected to each other by the drive.

Furthermore, a machine for the production of gear teeth or serration teeth or the like on a workpiece is to be created, by placing the workpiece between two opposite ones. Movable tools is rotated, whereby the machine an

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has drive gear that drives the tools and the movement of the tools are synchronized relative to one another, with the components of the drive gear for maintenance and repair and can be easily installed and removed for replacement.

According to the invention, a machine for the production of Gear and serration teeth and the like on a workpiece can be created by rotating the workpiece between two opposing tooth-forming tools, wherein the machine has a drive gear to lift the tools in opposite directions relative to each other to move, apart from the output connections for the tools, all components of the drive gear are separated from the tools, and the drive gear is provided with a synchronizing transmission to cause the tools to be synchronized with one another move while being driven in opposite directions.

According to the invention, a machine of this type is characterized by two tool holders for holding the tooth-forming tools. The tool holders are spaced apart on the machine bed for rectilinear movement in essentially parallel paths to each other mounted transversely to the axis of rotation of a workpiece on opposite sides of the same, the between

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the tool holder is held by a workpiece support. The workpiece support can take the form of spaced apart Have tips, which are provided for rotatably supporting an axis, a shaft or a similar workpiece. to the Gear or serration teeth are to be produced. To drive the tools when pressing, the machine includes a gear for simultaneous driving of the tool holders in opposite directions with respect to one another along their respective ones Guides. The transmission includes two drive racks that are each attached to one of the tool holders and are arranged parallel to the path of movement of the tool holder in question are two spaced, rotatable, substantially parallel drive shafts extending transversely to the drive racks extend and which are each in driving engagement with one of the drive racks, a rectilinear movement of the relevant tool holder along its guide in response to the rotation of the shaft to effect, and a reduction gear (or a similar drive connection such as a chain and sprockets) that connects to the shafts is related to a synchronous, simultaneous rotation of the shafts "and a corresponding movement of the relevant To effect tool holder in opposite directions.

The drive racks for the tool holder in the illustrated embodiment sit on the upper or lower Side of the oppositely arranged tool holder, see above

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2309A39

that the drive shafts engaged with the respective drive racks rotate in the same direction to cause rectilinear movement in opposite directions with respect to each other. The countershaft meshed with the drive shafts in 'connection, comprising a gear which is fixed to each of the drive shafts, further comprising a synchronizing gear which mil two gears of the drive shafts i: ¹ connection is to slippage to prevent between the drive rollers . In the exemplary embodiment shown, the synchronizing gear is mounted for free rotation around the axis of the workpiece.

The drive for driving the shafts includes in the illustrated. Embodiment a hydraulic rotary motor that with is coupled to both drive shafts. The gears of the countershaft including the synchronizing gear are along the axes, the drive shafts at a distance from the tool holders arranged so that the tool holders are connected to the drive only by the connections that between the Drive shaft and the drive racks on the tool holders exist.

The tooth-forming tools are mounted on the machine bed for straight movement, one lower part and one comprises upper part, with a slot between .vorvors

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which extends transversely to the axis of rotation of a workpiece that is held by the workpiece support. Means of control of the bend extend between the upper and lower sections across the slot by the amount of the bend to determine between the stroke-movable tools. In the illustrated embodiment, the means for controlling the deflection comprise two rods which are located between the lower and upper part extend on opposite sides of the workpiece. One end of each of the poles stands in engagement with an internally threaded adjusting member which is rotatably mounted on one of the bed sections. That other end of the rods is mounted on the other bed section, so that a rotation of the adjustment members to one Changing the tension on the rods leads to a preload of the rods to allow the deflection to be accurate is controlled.

The invention is explained in more detail below using an exemplary embodiment with reference to the drawings. In the drawings are:

Fig. 1 is a diagram of a machine according to the invention,

FIG. 2 is a diagram of the transmission and tooth-making tools in FIG

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in. Pig. 1 shown and

Pig. 3 a section through the machine used in. Pig. 1 is shown, the drive and its assignment to the surrounding construction of the machine is shown.

The machine instructs. Bed 2 and includes a lower part of the bed 4 and an upper bed section 6 which extends from an upright connecting section 8 to the front. The connecting part 8 extends upwards from the rear part of the lower bed section 4 and carries the upper bed section 6 in Distance to the lower part of the bed 4. A space 10 is between the lower and upper bed part 4 and 6, respectively, and two rods 7 extend between the lower and the upper bed section over the price space 10.

As shown in Pig. 3, the connecting part 8 consists of two spaced apart bed parts, to which a rear bed part 14, which forms the rear wall of the bed 2, and an intermediate bed part 12, which forms the front wall of the connecting part 8, with the intermediate bed part 1 2 at a distance seated in front of the rear bed part 14. In camps 9 and I7 in. Den . Bed parts I4 and 12, a spindle 16 is mounted, which has a tip 18, which at its front and right linden tree

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as shown in Pig. 3 sicjvt. The tip 18 acts with a tip 22 on a tailstock 20 together, which is adjustable sits on a tailstock support arm 19, which extends from the upper part of the bed 6 to the front. The spindle 16 and tailstock 20 together with the tips 18 and 22 form a workpiece support for the rotatable mounting of a workpiece V /, which is shown in dashed lines in FIG. 3. Of the Tailstock 20 can be adjusted in a conventional manner in the longitudinal direction of tailstock support arm 19 in order to accommodate different workpieces Record lengths. The spindle 16 can also be adjustable to adjust the position of the tip 18 in the direction of it To change the axis of rotation in the direction of the intermediate bed part 12 or away from it.

In Figs. 2 and 3, reference numbers 25 and 26 designate a lower and an upper tool holder, respectively, which is mounted on the lower "or upper" bed section. The lower tool holder comprises two parallel guides 28 and 30 for a slide part 32. The slide part is intended to move in a straight line along the honors 28 and 30. Elongated support members 34 and 36 with flanges overlying the sides of the slide 32 are attached to the lower part of the bed. holding part 38 fixed, forming gear to a tool 40 to _ha: -th the lower tool holding member 38 and the sliding member.

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32 are thus for rectilinear movement in the free space 10 stored along the guides 28 and 30. The upper tool holder is essentially identical to the lower tool holder and comprises two guides 42 and 44, one upper slide part 46, elongate retaining parts 48 and 50, which at. attached to the upper part of the bed, and an upper one Tool holding part 52 for holding a tooth-forming tool 54, which is identical in construction to the tooth-forming tool 40. The upper tool holder 52 and the upper one Sliding parts 46 are thus for rectilinear movement in the free space 10 along the guides. 42 and 44 stored.

Referring particularly to Figures 1 and 2, the lower and upper are. Tool holder 38 and 52 for rectilinear Movement in parallel paths at a distance from one another transversely to the axis of rotation of the workpiece V / on opposite sides of the same, when stored, the workpiece W from the workpiece support 16, 18 and 20, 22 is held. The tools 40 and 54 are in the illustrated embodiment with teeth on their working surfaces designed to press teeth against the workpiece W one after the other. The working surfaces of the tools 40 and 54 are arranged at a distance from one another which is smaller than the diameter of the part of the workpiece W on which the teeth are to be made. When the tools 40 and 54 are in a reciprocating motion relative to each other in opposite directions Directions are offset from the position shown in Fig. 1,

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the teeth of the tools 40 and 54 mesh with the workpiece W. and form serration teeth or gear teeth in the workpiece W in a pressing operation, while the workpiece W by the relative movement of the tools 40 and 54 is set in. Rotation.

According to the invention a transmission is provided. To simultaneously the tool shells 38 and 52 in opposite directions drive along their respective tracks. The transmission includes two drive racks 56 and 58 attached to the lower or upper. Side of the slide 32 and 46 are arranged (Fig. 3) · In the schematic representation shown in Fig. 2 the sliding members are omitted and there the drive racks 56 and 58 are in communication with the respective ones Tool holding parts 38 and 52 are shown. The drive racks extend in the longitudinal direction of the sliding parts and sit, that is, parallel to the path of movement of the relevant tool holding parts 38 and 52. The transmission also includes two spaced apart arranged rotatable shafts 60 and 62, both of which extend transversely to the drive racks 56 and 58. the Shaft 60 is in engagement with a gear or a plurality of gears 64 with the drive rack 56, wherein the gear or the gears are rotatably connected to the shaft 60. Correspondingly, the shaft 62 is in engagement with the drive rack 58 via one or more gearwheels 66, the are rotatably connected to the shaft 62. The wave 60 is with

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Serrations 68 (Pig. 3) are provided to the gear or gears 64 to be connected to the shaft 60 in a rotationally fixed manner. Correspondingly, the shaft 62 is provided with Kerbzähn.en 70 to the gear or to connect the gears 66 to the shaft 62 in a rotationally fixed manner. As shown in. Pig. 3 sit, two gears 64 on the serration of the shaft 60, and a. Longitudinal slot in the drive rack 56 accommodates a wedge 56a or the like, the lower edge of which sits in a groove between the two Gears 64 is formed. This wedge 56a, which is between the drive rack 56 (or several racks, if the Longitudinal slot is viewed as a separation of the rack 56 into multiple racks) and engages gears 64, assists in maintaining part alignment and rectilinear movement of the drive racks during one Pr e s avorgange a.

The transmission further comprises means 72 for effecting a synchronous, simultaneous rotation of the shafts 60 and 62 and thus a corresponding synchronous movement of the tool holding parts 38 and 52 with the. respective tools 40 and 54 in opposite directions Directions. The means 72 in the illustrated embodiment are in the form of a back gear with a gear 74 which is non-rotatably connected to the shaft 60, with a gear 76, which is rotatably connected to the gear 62, and with a synchronizing gear 78 which is rotatable

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on the spindle 16 between the spaced. Bed parts 12 and 14 sits and meshes with the gears 74 and 76. The gears 74, 76 and 78 that form the back gear 72 are located each at a distance from the sliding parts 46 and 32 along the axis of the rotating workpiece W.

The shafts 60 and 62 are driven by a drive in the form of rotary hydraulic motors 80 and 82 of conventional construction driven. The hydraulic motor 80 is with its shaft

83 rotatably with the shaft 60 by a conventional coupling

84 coupled. The shaft 85 of the hydraulic rotation motor is corresponding 82 rotatably coupled to the shaft 62 by a conventional coupling 86.

Two axially spaced apart upper bearing sleeves 87 and 89 sit in the upper part of the bed and two axially spaced arranged lower bearing sleeves 88 and 90 sit in the lower. Part of the bed (Pig. 3). The shafts 60 and 62 are in the. Bearing sleeves 88, 90 and 87, 89 mounted. The shaft 62 is supported by conventional bearings 91 and 93 in the sleeve 87, and it is in the bearing sleeve 89 by a conventional bearing 95 stored. The bearing 95 is in the intended position. Location on The end of the shaft 62 is secured by a retaining cap 96 which is fastened to the shaft 62 with screws 97. The sleeve 89 is on the front wall of the upper part of the bed by screws 98 attached, which extends through an outward, extending.

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Extending paddling, which is formed on the sleeve 09. the Sleeve 87 is provided by a holder 99 in the. Position held by screws 100 on the upper part of the bed is attached. The shaft 60 is supported in the sleeves 88 and 90 in a manner corresponding to that of the shaft 62 in FIGS Sleeves 87 and 89. The sleeves 88 and 90 are accordingly on the lower part of the bed essentially in the same way as the sleeves 87 and 89 secured in the upper part of the bed.

Rods 7 extend between the lower bed section 4 and the upper part of the bed 6 on opposite sides of the The axis of rotation of the workpiece W as shown in FIG. 1. The rods 7 are with the bed parts in such a way connected that adjustable means for controlling the deflection are created to the deflection of the tools and 54 to be determined during a pressing operation. The upper ends of the rods 7 sit in internally threaded ones Adjusting members 92, which in turn are freely rotatably mounted on the upper bed section 6 via the elements 50. the lower ends of the rods 7 are screwed into the lower bed section 4 and provided by a lock nut 94 in the Secure location. Thus, by rotating the adjusting member 92 in one direction, the rods 7 can be prestressed the tension being measured by strain gauges attached to the rods 7. Consequently, the tension on the rods 7 according to the foreseen degree of

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bending of the tools 40 and 54 away from each other during a pressing process. a workpiece W can be set, the has known mechanical properties.

When the machine is in operation, the workpiece W is inserted into the free space 10 between the tips 18 and 22. The tips. 18 and 22 are set so that they rotatably support the workpiece W with the portion to be provided with teeth between the Tools 40 and 54 is located. The rotary hydraulic motors 80 and 82 are then energized to operate the tools 40 and 54 in the directions indicated by the arrows in FIG. 2. The transmission gear 72 ensures that the tools 40 and 54 move at the same speed move in opposite directions, in relation to each other and stay in sync with each other. Because the distance between the working surfaces of the tools 40 and 54 is smaller than the diameter of the part of the workpiece to be machined, the tools 40 and 54 displace material on the workpiece, in order to press teeth into the workpiece, the counterparts to the Teeth on the working surfaces of the tools 40 and 54 are while the workpiece W is lifted by the stroke movement of the tools 40 and 54 is set in rotation. The tools can be in their Movement can be stopped by turning off the rotary motors when the rear ends of the tools 40 and 54 run over the workpiece W. The workpiece is then removed and the tools are returned to their original position.

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performed like they did in Pig. 1 is shown to show the insertion of a to wait for further workpiece.

The hydraulic rotary motors along with the gearbox with the waves. 60, 62 and the intermediate gear 72 create an improved, coordinated drive for tools 40 and and create better control for starting, and Stop the tools 40 and 54 during a pressing process. The hydraulic rotary motors 80 and 82 can in one embodiment be provided in a hydrostatic or closed. Hydraulic circuit can be used so that the only oil you need in the reservoir, oil to compensate for leaks.

A large bearing surface is provided for the spindle 16, and the arrangement of the reduction gear 72 with the synchronizing Gear 78, which is mounted on the spindle 16, allows some adjustment to be made to compensate for the Wear on guides 28, 30 and 42, 44 through replacement, of gear 78 by a different size gear, if necessary. A synchronization in the movement of the teeth forming the teeth Tools 40 and 54 is not adversely affected by wear on the guides, since the synchronizing Gear 78 is not directly connected to the tool holders 25 and 25.

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Claims (1)

Claims (1.) Machine for pressing teeth and the like into a ι Workpiece, with a workpiece support for rotating holding * * of a workpiece, two toolholders that are used for rectilinear Movement in substantially parallel paths at a distance to each other in the transverse direction to the axis of rotation and on opposite sides Sides of the axis of rotation of a workpiece are supported, which is held by the V / ckstücksupport, and a gear for simultaneously driving the tool holders in opposite directions during a pressing process along their respective paths, characterized by two drive racks (56, 58), one of which is connected to one of the tool holders (25, 26) and arranged parallel to the path of movement of the same is and of which the other with the other of Tool holder (25, 26) connected and parallel to the path of movement the same is arranged, two spaced-apart, rotatable, substantially parallel shafts (60, 62), which is essentially in the transverse direction of the drive racks (56, 58) extend and one of which in the driving Engagement with one of the racks (56, 58) is such that a rectilinear movement of the associated tool holder along its path of movement in response to rotation of the one shaft and of which the other shaft in driving engagement with the other of the - 20 309842 / 03AQ Rack is such that a rectilinear movement of the associated tool holder along its path of movement is caused in response to a rotation of the other shaft, and a gear part (78) which is in engagement between the shafts (60, 62), such that a synchronous simultaneous rotation of the shafts (60, 62) and a corresponding movement of the tool holder (25, 26) is caused in opposite directions. 2. Machine according to claim 1, characterized that the transmission part is a gear reduction is. 3 · Machine according to claim 2, characterized in that the countershaft has two gear wheels (74, 76) which are each fastened to one of the shafts (60, 62) at a point that is separated from the connection between the shaft (60, 62) and is remote from the associated drive rack (56, 58) and includes a rotatable synchronizing gear (78) meshing with the two gears (74, 76). 4. Machine according to claim 3, characterized by a drive (80, 82) for driving the shafts (60, 62). - 21 - 309042/03 4 0 5. Machine according to claim 4, characterized that the drive is two hydraulic motors (80, 82) which are each drivingly coupled to one of the shafts (60, 62). 6. Machine according to claim 1, characterized by selectively adjustable means (7) for determination the deflection of the tool holders (25, 26) in relation to one another during a pressing process. 7 · Machine according to claim 6, characterized through a. Bed with a lower bed section (4) and an upper Eettpartie (6), between which a free space (10) is formed, which extends transversely to the axis of rotation of a workpiece W extends from the 'workpiece support (16, 18, 2 0, 22), and by two tool holders (25, 26) with an upper tool holder attached to the upper Bed part (6) is mounted, and with a lower tool holder which is mounted on the lower bed part (4), wherein the tool holders (25, 26) for supporting two pressure forming tools (40, 54) for movement along the space (10) are set up and a workpiece W sits therebetween, which is from the workpiece support during a pressing process (16, 18, 20, 22), the means (7) for determining the deflection being between the upper (6) - 22 - 309842/0340 and the lower part of the bed (4) extend over the free space (10) . 8. Machine according to claim 7, characterized in that the means (7) for determining the deflection comprise at least one rod extending between the upper one. (6) and the lower bed part (4) extends over the free space (10), furthermore an internally threaded adjusting member (92) which is rotatably mounted on one of the bed parts (4, 6) and in which one end of the rod (7 ) engages, while the other end of the rod (7) with the other of the bed portions (4, 6) is connected such that rotation of the adjustment member (92) leads in a direction to increase the tension on the rod (7) , while rotation of the adjusting member (92) in the opposite direction leads to a reduction in the tension in the rod (7). 9. Machine according to claim 7, characterized in that the means for determining the off bend comprise two rods (7) extending between the upper (6) and the lower bed section (4) on opposite sides of the axis of rotation of a workpiece W. extend, which is held in the workpiece support (16, 18, 20, 22), wherein two internally threaded adjusting members (92) are rotatably mounted on one of the bed parts (4, 6) and - 23 309842/0340 - 23 - 2309A39 each of the rods (7) has one end in threaded engagement with one of the adjustment members (92) while the other End of the same with the other of the bed parts (4, 6) in connection, so that a rotation of the adjustment members (92) in one direction leads to an increase in the tension in the associated rod (7) and a rotation of the Adjusting members (92) in the opposite direction to a reduction in tension in the associated stand (7) leads. 10. Machine according to claim 1, characterized through a bed (2) with a lower bed section (4), an upper bed section (6) and an upright connecting section (8) that connects the upper bed section (6) to the lower one Holds the bed section (4) at a distance from it in such a way that a free space (10) is created between the bed sections (4, 6, 8), wherein the price space (10) extends in the transverse direction of the axis of rotation of a workpiece V / extends in the workpiece support (16, 18, 20, 22), the one tool holder (26) and the drive rack (58) on the upper bed part (6) and the other tool holder (25) and the drive rack (56) are mounted on the lower bed part (4) and the workpiece support (16, 18, 20, 22) comprises a spindle (16), which is rotatably mounted in the connecting part (8). - 24 309842/0340 1. Machine according to claim 10, characterized that the connecting part (8) comprises two spaced apart bed parts (12, 14) in which the Spindle (16) is rotatably mounted, and that the drive a synchronizing gear (78) mounted on the spindle (16) between the spaced apart bed parts (12, H) sits. 12. Machine according to claim 11, characterized in that that one shaft (62) is rotatably mounted in the upper bed part (6), while the other Shaft (60) in. The lower bed part (4) is rotatably mounted, and that the drive is a gear (76) which is attached to the one Shaft (62) is fixed and meshes with the synchronizing gear (78) and comprises a gear (74), which is connected to the other shaft (60) and meshes with the synchronizing gear (78). 13. Machine according to claim 12, characterized by two in the axial. Spaced upper bearing sleeves, which are in. The upper. Arranged bed section (6) are, two axially spaced lower bearing sleeves, which are arranged in the lower bed part (4), and at least one. Bearing arranged in each of the sleeves is, the one shaft (62) in the upper sleeves - 25 309842/0340 sits and is rotatably mounted in the bearing wick while the other shaft (60) received in the lower sleeves and is rotatably mounted in the bearing wick. H. Machine according to claim I3, characterized that the waves, in engagement with the. relevant drive racks (56, 58) in the space between, the respective sleeves. 3098A2 / 03i0