EP0058323A1 - Pressure medium operated torque actuator - Google Patents

Abstract

1. A pressure-actuated swing motor (10), more particularly for driving a swing door which is connected by swing arms to a rotating column, having a cylinder (12), an axially displaceable piston (56) therein and a drive shaft (16) which is axially fixed and mounted in a rotatable manner at the front of the cylinder and has at least two curved paths (60, 66) running in a screw-shaped line on a section of the cylinder housing, into which the guide projections (64, 68) connected to the piston engage, characterised in that the bearing (40, 18) of the drive shaft (16, 46) of the swing motor (10) for the mounting of the swing motor (10) and the rotating column (154) consisting of one part which is connected in a rigid manner to the drive shaft (16, 46) and the swing door (160) are positioned such that the lower face (112) of the swing motor housing (12, 34) has fixing holes arranged symetrically to the axis of rotation for introducing one of the intermediate parts (42) connecting the swing motor (10) to the bodywork (162) of the vehicle in at least four different adjustable positions and that spill valves (118) which are selectively interchangeable for standard compressed air supply devices are arranged on the housing (112), whose supply devices (126) are positioned in a mirror-inverted fashion on facing sides.

Description

The invention relates to a pressure-actuated swivel motor, in particular for driving a swivel door wing connected via swivel arms to a rotating column, with a cylinder, an axially displaceable piston therein and with an axially fixed output shaft which is rotatably mounted on the end face in the cylinder and which has at least two helical elements on a cylinder jacket section has running cam tracks, in which guide projections connected to the piston engage.

Such a swivel motor is already known (DE-OS 25 38 529). In this swivel motor, self-locking is provided by appropriately designing the cam tracks in at least one end position of the piston. Therefore, the piston cannot be moved out of its end position when the pressure medium supply is interrupted.

In this swivel motor, self-locking is generated by cam tracks, the ends of which run parallel to the piston axis. It is therefore not necessary to continuously supply pressure medium to the swivel motor in the end position characterized by self-locking. If the swing motor is used, for example, as a door drive in vehicles, the doors remain closed even when driving fast, in which a force is exerted on the doors in the direction of the open position by the resulting negative pressure. The doors can only be opened again if the swivel motor is moved from its position characterized by self-locking by the supply of the pressure medium.

The invention has for its object to further develop a swing motor of the type mentioned in such a way that it can be used universally for swing door leaves arranged on different sides of the vehicle and having different directions of rotation, generates a large torque with small radial dimensions and is simple to the rotating column in the Can attach axis direction.

The object is achieved in that the bearings of the output shaft of the swivel motor for the mounting of the swivel motor including the rigidly connected to the output shaft, made of one piece rotating column and the swing door leaf are designed such that the lower end face of the swivel motor housing is arranged symmetrically to the axis of rotation mounting holes for the attachment of an intermediate piece connecting the swivel motor to the vehicle bodywork in at least four differently adjustable positions and that optionally exchangeable overflow valves are arranged on the housing for compressed air standard connections, the pressure connections of which are mirror images of one another on mutually facing sides.

In this configuration, the swivel motor can be connected to the rotary column to form an integral unit. The swivel motor forms the continuation of the rotating column. This unit is very stable. The lower bearing of this unit is taken over by the bearings of the shaft of the swivel motor. This saves a bearing for the rotating column. In contrast to the bearings previously arranged at the lower end of the respective rotating column, the bearings inside the swivel motor are not exposed to dirt. The bearings can be maintenance-free. The unit can be quickly and easily removed for maintenance or repair purposes. The time for installing new seals is therefore short. Furthermore, the unit can be manufactured inexpensively. The unit requires little space. The installation of other parts near the rotating column is therefore possible. For example, lights, cable ducts, etc. can be installed close to the rotating column or installed in their vicinity. The identical construction of the unit for swing door wings attached to vehicles on different sides results in larger quantities during manufacture. This makes it possible to reduce the cost.

In a preferred embodiment, the intermediate piece consists of two support plates running at right angles to one another, each of which is connected to one another at an edge and has fastening holes. The screwing points are easily accessible in this embodiment. No special tools are required to attach the swivel motor to the body. It is also advantageous that the space required for the upper bearing of the rotating column is small. Furthermore, the upper bearing can be easily attached to the body using conventional tools. The unit consisting of the swivel motor and the rotating column can therefore be assembled inexpensively.

An expedient embodiment consists in that a shaft section provided with the helical cam tracks has a slightly larger diameter than the output shaft of the swivel motor. This measure results in a swivel motor with small radial dimensions.

The cam tracks preferably run with different pitches in the axial direction of the shaft section in order to generate different torques and rotational speeds of the rotary column. A desired movement of the swing door leaf can be optimally predetermined by the attachment of such curved tracks with different gradients, in which a smooth transition is achieved by gradual transitions. The swing door leaf can be actuated with a short delay via a corresponding curve, then strong acceleration and then a movement with reach a relatively high speed until a strong deceleration and a slow transition to the end position are triggered shortly before the end position.

In another preferred embodiment it is provided that an increased closing force of the swing door wing can be generated by the different course of the slopes of the cam tracks.

The rotary column rigidly connected to the output shaft preferably consists of a piece of pipe.

A further preferred embodiment consists in that a shaft section of the output shaft is surrounded by a housing part on which a locking cylinder housing is radially attached, in which a pressure-actuated piston is displaceable, which carries a bolt held in the blocking position for the shaft section by spring force, the bolt can be unlocked both by pressurizing the piston and by a Bowden cable. The swing door leaf is held in the closed position by the compressed air being applied to the swing motor. If the compressed air supply fails, the swing door leaf must not open for safety reasons. For the same reasons, pressing the swing door against the force generated by the compressed air must be excluded. In addition, however, there must still be a possibility that the swing door wing can be opened in an emergency. With the arrangement explained above, these requirements can be met in a relatively simple manner.

In an expedient embodiment, the Bowden cable is non-positively connected to the emergency valve of a vehicle. When the emergency valve is switched on, not only is the swivel motor depressurized, but also the swing door leaf is released for opening. The swing door leaf can therefore be pushed open by hand.

In a favorable embodiment is in a swivel motor, the cam tracks in at least one end position of the piston when the supply of pressure medium is interrupted and when via the output shaft; forces acting back on the piston cause self-locking, provided that an axial force for movement can be exerted at least from its self-locking position or the exercise can be initiated by a drive arranged on the side of the cylinder. With this arrangement, the self-locking position can be overcome if necessary without the supply of pressure medium.

In an emergency, the piston and the parts driven by it can therefore be moved out of their position without pressure medium. This is particularly important for objects such as vehicle doors that are to remain locked without the supply of external energy, but which must also be opened without energy in an emergency. The measures explained above open up new application possibilities for swing motors.

A preferred embodiment is designed such that the drive has a pinion which can be rotated by hand about an axis and pivoted about a further axis from rest positions into a fixed position in which the teeth of the pinion are in engagement with teeth which are in a the course of the cam tracks are arranged on the piston or on a carrier fixedly connected to the piston. If the piston moves under the influence of the pressure medium, there is no engagement between the pinion and teeth. This has several advantages. On the one hand, no energy is required to overcome the friction between the pinion and teeth and to accelerate or decelerate the pinion when the speed of the piston changes, and on the other hand, the parts of the projection of the pinion which are accessible by hand are in the rest position during the movement of the piston , so that no additional protection against touch is required. In addition, this arrangement is characterized by a structurally simple structure and can therefore be manufactured inexpensively.

In an advantageous embodiment it is provided that the pinion is mounted eccentrically on a rotatable disc, on the edge of which a projection is arranged which, when the teeth of the pinion and piston engage, is pressed against a stop in the direction opposite to the direction of rotation of the pinion. With this arrangement, the fixed position of the pinion can be achieved during the engagement with the teeth on the piston without great effort. If the teeth of the pinion and the piston are brought into engagement with one another in the course of the pivoting of the pinion about the further axis, the projection against the stop lies during the subsequent rotation of the pinion about its axis during the movement of the piston. After the rotation of the pinion has ended, the contact force between the projection and the stop disappears. The pinion can therefore be pivoted back into its rest position with a simple movement.

A stop pin is preferably provided as the projection, which projects from one of the circular end faces of the disk and can be pressed against a ball on the stop, which is under a spring preload and can be moved against it in a spherical cap. With this arrangement, the teeth of the pinion can be gently latched into the teeth of the piston.

A useful embodiment is that the axis of rotation of the pinion and the axis of rotation of the disc with the longitudinal axis of the stop pin lie in or approximately in a plane which is perpendicular to the piston center axis when the pinion engages in the teeth of the piston. This measure enables the teeth of the pinion and piston to be brought into engagement quickly.

In a favorable embodiment, the distance between the axes of rotation of the pinion and the disk is approximately as large as half the radius of the disk, while the radii of the pinion and disk correspond approximately in size. Result in this arrangement small dimensions in the radial direction. The radius of the pinion depends on the desired size of the force to be applied by hand, with which both the piston and the parts driven by the piston are to be set in motion. The space requirement of the drive is mainly determined by the dimensions of the pinion, while the above-described design of the disk requires only a little additional space.

In another preferred embodiment it is provided that the cam tracks are arranged as grooves on the outside of a section of the output shaft and of the piston with inclinations running in diverging directions with respect to the piston center axis, that rollers running on the cylinder or on the piston run in the grooves, that the teeth are on the outside of the hollow piston and that the pinion is arranged in a housing attached to the cylinder at a distance from the cylinder end, in which the teeth of the pinion with the teeth arranged in one end position of the hollow piston close to the piston end face in Intervention can be brought. The swivel motor with the laterally projecting housing for the drive can be designed as a compact, space-saving unit with such a construction. If necessary, this unit can also be replaced by a layperson. The cylinder end from which the output shaft projects outwards is expediently provided with a flange which has a series of bores. In this case, the swivel motor can be attached to or detached from a carrier in a few simple steps. In the case of a door drive, this type of fastening has the advantage that the entire door unit or the door axis with the levers does not have to be removed in the event of a possible repair of the swivel motor. The slopes of the grooves determine the opening and closing speed of the swing motor adopted by the _t rubbed parts. Appropriate incline zones can therefore be used to open and shoot quickly in the middle swing area of the parts, for example the vehicle doors, can be reached, while creep speeds are caused by a change in the slope just before the end positions of the parts.

Preferably, at least one end projection of the pinion protrudes from the housing with its end, the end being designed as an engagement point for a tool. The pinion can therefore neither be pivoted nor rotated without an appropriate tool. An unintentional actuation is avoided. The tool can e.g. be arranged in vehicles in an easily accessible location.

In a further expedient embodiment, the end of the projection of the pinion is designed as a square head.

Another preferred embodiment consists in that a second disk is arranged on the other side of the pinion next to the disk and that the disks of the same design are rotatably mounted in bores in the side walls of the housing. The force exerted on the piston by springs is absorbed by the shaft in the event of pressure medium failure or pressure medium shutdown. Forces that act on the piston from the parts driven by the swivel motor are not converted into axial forces because of the self-locking.

Further details, features and advantages of the invention result from the following description of several exemplary embodiments shown in the drawings.

• Fig. 1 einen Schwenkmotor im Längsschnitt,
• Fig. 2 einen Querschnitt längs der Linien I - I der in Fig. 1 dargestellten Vorrichtung,
• Fig. 3 eine Ansicht eines in Fig. 1 dargestellten Antriebs am Schwenkmotor,
• Fig. 4 eine Seitenansicht des Gehäuseteils für den in Fig. 3 im einzelnen dargestellten Antrieb,
• Fig. 5 den in Fig. 3 dargestellten Antrieb in einer anderen Stellung,
• Fig. 6 eine Seitenansicht des Gehäuseteils mit dem Antrieb in der in Fig. 5 dargestellten Stellung,
• Fig. 7 einen Längsschnitt durch eine andere Ausführungsform eines Schwenkmotors,
• Fig. 8 eine schematische Ansicht eines mit einer Drehsäule, einem Türflügel und einer Fahrzeugkarrosserie verbundenen Schwenkmotors,
• Fig. 9 ein Überströmventil im Querschnitt und
• Fig. 10 ein Norm-Anschlußglied im Querschnitt.

Show it:

• 1 is a swivel motor in longitudinal section,
• 2 shows a cross section along the lines I - I of the device shown in FIG. 1,
• 3 is a view of a drive shown in FIG. 1 on the swivel motor,
• 4 shows a side view of the housing part for the drive shown in detail in FIG. 3,
• 5 shows the drive shown in FIG. 3 in a different position,
• 6 is a side view of the housing part with the drive in the position shown in Fig. 5,
• 7 shows a longitudinal section through another embodiment of a swivel motor,
• 8 shows a schematic view of a swivel motor connected to a rotating column, a door wing and a vehicle body,
• Fig. 9 is an overflow valve in cross section and
• Fig. 10 is a standard connector in cross section.

A swivel motor contains a cylinder tube 12 as the housing, which is closed on one end face 14 except for a bore for the passage of a shaft 16. The shaft 16 is rotatably supported in a roller bearing 18 which is fixed in the axial direction by a locking ring 20. To remove the interior 22 of the cylinder tube 12. seal, the shaft 16 is surrounded on the end face 14 by a seal 24. The cylinder tube 12 is provided near the upper and lower ends with a connection 26, 28 for the application of compressed air.

The shaft 16 merges in the interior 22 into a shaft section 30, the diameter of which is only slightly larger than that of the shaft 16. Following the shaft section 30 is a shaft section 32, which is surrounded by a housing part I 34, into which a locking cylinder housing 36 is integrated. The shaft section 32 is followed by a further shaft section 38, which serves as a seat for a roller bearing 40, the outer ring (not specified in more detail) of which is arranged in recesses in the housing part 34 and an intermediate piece 42, while the inner ring of the roller bearing 40 is located between the shoulder of the shaft sections 32 and 38 and an unspecified circlip. The intermediate piece 42 is attached to the lower end face of the swivel motor 10. A seal 44 is located between the shaft section 32 and the inside of the housing part 34. The shaft section 38 continues in a shaft end 46 which has a groove with a feather key 48.

A flange 92 is located at the level of the cover 38 at the end of the cylinder barrel.

A hollow piston 50 is movably mounted between the shaft section 30 and the inner wall of the cylinder tube 12. The hollow piston 50 surrounds the shaft section 30 on the cylinder face side and on the end face facing away from the shaft section 32 and does not have one designated bore through which the shaft 16 protrudes. A bearing bush 52 is inserted into this bore, which enables the hollow piston 50 to be guided easily in the axial direction of the shaft 16. A shaft seal 54 is also inserted into the bore. A guide ring 56 is inserted in the cylindrical outer wall of the end of the hollow cylinder 50 adjacent to the roller bearing 34. A piston seal 58 is located next to the guide ring 56. Two diametrically opposite, helically extending grooves 60 are arranged in the cylindrical outer wall of the hollow piston 50. These grooves 60 form curved tracks.

A support roller 62 engages in one of the grooves 60. The support rollers 62 are mounted on shafts 64 which are firmly connected to the cylinder tube 12. The distance of the support rollers 62 arranged along the same central axis from the roller bearing 34, which forms an end of the cylinder interior, is slightly smaller than the axial length of the hollow piston 50. The central axis of the support rollers 62 intersects the longitudinal axis of the hollow piston 50 at a right angle. The cylindrical outer surfaces of the support rollers 62 face the side walls of the grooves 60.

Grooves 66 are arranged in the cylindrical outside of the shaft section 30, which also have a helical course. The grooves 66 are located at diametrically opposite locations. The slopes of the two types of grooves 60 and 66 are different. If the grooves 60 have a right-handed course, the course of the grooves 66 is left-handed. Support rollers 68, which are rotatably mounted on bolts 70, project into the grooves 66. The support rollers 68 are arranged along the same central axis which intersects the longitudinal axis of the hollow piston 50 at a right angle. The bolts 70 are rigidly connected to the hollow piston 50 and project radially into the interior of the grooves 66. The hollow piston 50 carries the bolts 70 together with support rollers 68 close to one end thereof, which faces the roller bearing 34.

When compressed air enters the cylinder tube 12 via the connection 28, the hollow piston 50 moves along the shaft section 30 and along the shaft 16 against the end face 14. Because of the helical grooves 60 and the support rollers 62 projecting into them, the hollow piston 50 leads during its axial direction Movement at the same time a rotary movement. This rotary movement is transmitted to the shaft section 30 by the support rollers 68. During the axial displacement of the hollow piston 50, the support rollers 68 run in the grooves 66 and thereby intensify the rotary movement of the shaft section 30, via which the shaft 16, the sections 32 and 36 and the end 46 are also set in rotation. The parts 16, 30, 32, 36, 46, which are made from one piece, are therefore referred to as drive shaft.

The rotational movement of the output shaft is ended when the hollow piston 50 has reached its end position at the front end 14. When the interior of the cylinder is vented via the port 28 and the port 26 is pressurized with compressed air, both the movement of the hollow piston 50 and the output shaft are reversed.

It is assumed that a swing door leaf is to be driven by the swing motor 10. The door leaf is connected to pivot bearings via swing arms. The shaft end 46 engages at least one swing arm via a coupling (not shown).

The desired opening and closing speed of the door leaf is achieved by means of corresponding slopes of the grooves 60 and 66. The slopes are selected so that the door leaf is accelerated to a maximum speed when it is opened and then slowly changes to its open position. When closing, a phase of rapid increase in speed up to a maximum value is followed by a phase of slow transition to the closed position. The slow transition to the opening and closing position is achieved with grooves 60 and 66, the ends of which are on both sides more and more parallel to the axial direction of the cylinder tube 12 approach. In the two end positions of the hollow piston 50, one of which is assigned to the open and the other to the closed position of the door leaf, self-locking occurs as a result of the grooves 60, 66 running parallel to the axis of the cylinder 12, that is to say persists in the event of failure or shutdown of the compressed air the hollow piston 50 also in its end position when a torque acts on it from the outside via the shaft end 46 and the shaft sections 36, 32 and 30. The self-locking feature prevents the door leaf from closing or opening if the compressed air fails or is switched off. This is particularly important in the case of a closed door leaf. During the journey, pressure differences between the interior and the outside environment occur predominantly at higher speeds, as a result of which a force is exerted on the door wing in the direction of the open position. The self-locking prevents the door leaf from opening despite this force.

In order to be able to open the door leaf via the swivel motor in an emergency even without compressed air, for example after the vehicle has stopped, a manually actuable drive 72 is attached to the side of the cylinder tube 12, with which an axial force can be exerted on the hollow piston 50. Under the influence of the axial force, the hollow piston 50 moves at least out of its end position characterized by self-locking. However, it is also possible to move the hollow piston 50 from one end position to the other by longer actuation of the drive, the connected door leaf, for example, opening completely.

The drive 72 is composed of a pinion 74 and a disk 76 connected to it. The pinion 74 is rotatably mounted on the disk 76 about an eccentric axis 78. The disk 76 can be pivoted about a further axis 80 within an angular range that is less than one revolution. Pinion 74 and Disc 76 are located in a housing 82 arranged laterally on the cylinder tube 12, which is closed by a cover 84 on its side facing away from the cylinder tube 12.

The pinion 74 and the disk 76 can be brought from rest positions by swiveling into a fixed end position in which the teeth of the pinion 74 engage teeth 86 on the hollow piston 50. The teeth 86 are arranged in a row along a curved path, the course of which corresponds to the curvature of the helical grooves 60.

The disk 76 is provided at its edge with a projection designed as a stop pin 88. The stop pin 88 projects vertically outwards from an end face of the disk 76. When the disk 76 and the pinion 74 are pivoted, the stop pin 88 can be pressed against a stop 90 arranged in the interior of the housing 82 close to the cover 84. The stop 90 contains a ball, not shown, which is under spring preload and can be pressed into a spherical cap, not shown, by pressing the stop bolt 88 against the spring force.

Pinion 74, disk 76 and stop pin 88 are arranged so that the axes of rotation 78, 80 of pinion 74 and disk 76 lie with the longitudinal axis of the stop pin 88 in a plane which, when the teeth of pinion 74 engage the teeth 86 of the hollow piston 50 is perpendicular to its central axis. In this position of the plane, the stop pin 88 is pressed against the stop 90. The distance between the axes of rotation 78, 80 of the pinion 74 and the disk 76 is approximately as large as half the radius of the disk 76, while the radii of the pinion 74 and disk 76 coincide approximately. As a result, the space requirement of the drive 72 in the radial direction of the disk 76 and the pinion 74 is small. The distance of the drive 72 from the flange 92 on the housing part 34 is chosen so that in one End position of the hollow piston 50, in the end face of which rests on the roller bearing 34, the teeth of the pinion 74 can be brought into engagement with the teeth 86 of the hollow piston 50, which are close to the edge of the hollow piston end face facing away from the roller bearing 34.

The pinion 74 contains an end projection 94, the end of which protrudes from the housing 82. The end of the projection 94 is designed as a square head. In addition to the disk 76, a disk 96 of the same design can be fastened on the other end face of the pinion 74. The two disks 76 and 96 are rotatably mounted in bores 98 of the side walls 100 of the housing 82.

A rest position of the drive 72, in which there is no contact between the pinion 74 and the piston 50, is shown in FIGS ^. 5 and 6. In this rest position of the drive 72, the hollow piston 50 can be moved back and forth in the cylinder 12 by means of compressed air. If the hollow piston 50 is to be removed from its end position characterized by self-locking in the event of a compressed air failure, then a square key must be placed on the projection 94. When the square key is rotated in the direction designated by 102 in FIG. 6, the teeth of the pinion 74 come into engagement with the teeth 86 of the hollow piston 50. The stop pin 88 is pressed against the arrangement of the ball on the stop 90 explained above. The spring preload of the ball ensures that the engagement, ie the phase between the first contact of the teeth of the pinion 74 and the hollow piston 50, is carried out with an approximately continuous application of force until the precise engagement is produced.

In the position of the pinion 74 and the disks 76, 96 shown in FIGS. 1, 3 and 4, the teeth of the pinion 74 and the hollow piston 50 are in the most favorable position for the transmission of the axial force. By rotating the square key about the axis 78, the pinion 74 executes the rotary movement designated 104 in FIG. 3. The hollow piston is designated 106 in FIG. 3 Direction shifted. At the same time, a force is transmitted to the disk 76, which acts in the direction designated 108 in FIG. 3 and presses the pin 88 against the stop 90. The pinion 74 and the disks 76, 96 are hereby fixed in position until the rotation of the pinion 74 has ended. The pinion 74 can be rotated until the hollow piston 50 has been removed from its end position characterized by self-locking or has reached its other end position.

The engagement between the teeth of the pinion 74 and the teeth 86 of the hollow piston 50 can be released by rotating the pinion 74 against the direction 104 using the square key in the position shown in FIGS. 3 and 4. The pinion 74 moves along with the disks 76 and 96 somewhat in the direction of the rest position shown in FIGS. 5 and 6. By subsequently pivoting the pinion 74 and the disks 76 and 96 about the axis 80, these can be brought into the rest position.

The swivel motor 10 shown in FIGS. 1 to 6 can be constructed on the basis of the described configuration as a compact, slim unit which can generate larger torques in a small space. This unit can also be easily replaced by laypersons for repair or maintenance purposes. To release the swivel motor 10 from the support, only the screws in the bores 48 have to be removed and the coupling at the shaft end 46 has to be separated. It is not necessary to replace the entire door wing or parts of the door wing.

The pinion 74 and the disks 76 and 96 can be arranged in two positions in the housing 82. In the first position, the protrusion 94 protrudes outward from the wall 100. In the other position, the pinion 74 and the disks 76 and 96 are 180 ° mounted rotated in the housing 82, the projection 94 protruding outward on the opposite housing wall. This makes it possible to achieve the desired accessibility from one side or the other with only a single drive type 72. This means simplifying warehousing.

It is also possible to provide a separate manual operation for the disks 76 and 96. This can be done by a part of the disk 76 or 96 protruding beyond the side walls of the housing 82, the circumference of which is knurled. The disks 76 and 96 together with pinion 74 can be brought into the engagement position between pinion 74 and hollow piston 50 by means of the knurled part.

As already explained above, the diameter of the shaft section 30 is somewhat larger than the diameter of the shaft 16. This results in a construction of the swivel motor 10 which has a small outside diameter. This makes it easier to arrange swing motors in a row with the rotating columns of swing doors.

The roller bearing 40 is dimensioned so that it withstands the stresses emanating from the respective rotating column and the door leaf.

The intermediate piece 42 consists of two support plates 108, 110 running at a right angle to one another. The support plate 108 is fastened to the end face 112 of the housing part 34, while the support plate 110 can be connected to a support element of the respective vehicle. There are slots 114 in the support plate 110, into which fastening screws are inserted. The support plates 108, 110 are each square. The housing part 34 merges at its end facing the intermediate piece 48 into a square flange 92 which has four bores which are arranged symmetrically to the longitudinal axis of the shaft 16 and the shaft sections 32, 38 and 46 and which are not shown in any more detail. Screws 116 are inserted into these bores, which are in threaded bores the support plate 108 are screwed. The bores and the screws 116 are located close to the corners of the flange 92. Because of the symmetrical arrangement of the bores in the flange 92, the intermediate piece 48 can be screwed onto the flange 92 in four different positions. The support plate 110 occupies a different position. The four selectively adjustable positions of the support plate 110 correspond to the sides of a square, the edge length of which corresponds to the length of the support plate 108.

The support plate 108 is slightly longer on one side than the flange 92. It is the side from which the support plate 110 is angled downward. Therefore, the outside of the support plate 110 is located a little away from the edge of the flange 92, which forms the outer boundary of the swivel motor 10 on three sides. On the fourth side, the flange 92 projects horizontally beyond the locking cylinder housing 36. If necessary, the support plate 108 can be made so long that the outside of the support plate 110 is also in front of the outer end of the locking cylinder housing 36 on the fourth side.

Due to the alignment of the intermediate piece 42 with the corresponding stop device of the vehicle, the swivel motor 10 can be used for swivel doors with rotating columns arranged to the left or right of the door opening. In addition, depending on the stop surface on the vehicle, the outside of the support plate 110 can be attached parallel to the door entry or perpendicular to it.

Overflow valves 118, the response pressure of which can be set, are connected to the connections 26, 28. To set the response pressure, 118 screws 120 are provided on the overflow valves. The overflow valves 118 are essentially cuboid in shape. They are each screwed on a flat side to a projection 122 surrounding the connection openings 26, 28. Furthermore, the overflow valves 118 are each provided with throttle screws 124. The overflow valves are used to dampen the swivel doors.

This additional end position damping is required if the fastest opening and / or closing times are required. Conventionally known dampings can no longer fulfill this task because the damping volume which is built up from normal atmospheric pressure is insufficient. However, air with excess pressure can be used with the overflow valves. The amount of overpressure volume required for an optimal damping process can be selected with the spring. The adjustable throttle screws ensure fine adjustment shortly before the doors stop.

FIG. 9 shows in cross section an overflow valve 118, the connection opening 126 of which opens into a narrow side. The screws 120 for adjusting the contact pressure are located next to the connection opening 126. The screws 120 have an unspecified cylindrical cavity in which a spring 128 is arranged, which is supported on a piston 130 which is in a cylinder. is movable. Under the influence of the spring preload, the piston 130 presses a seal 132 against a channel 134 which is connected to a cylinder 136 in which the throttle screw 125 is located. The throttle screw 125 includes a tapered end 136 whose position in an opening 140 forms the air passage cross section between the channel 142 connected to the connection opening 26 or 28 and the channel 144 running to the connection opening 126.

The overflow valves 118 are attached to the connections 26, 28 in such a way that their connection openings face one another. Since the overflow valves have their greatest extension parallel to the axis of the cylinder tube, they take up little additional space in the radial direction. The compact design of the swivel motor 10 therefore remains in connection with the overflow valves 118.

Depending on the use of the swivel motor 10 in a swivel door wing with a rotating column on the left or right of the door opening, it may be necessary to interchange the connecting lines to the overflow valves 118. This is easily possible due to the facing connection openings 126.

Damping of the swing door leaf is not necessary in all cases. With the end position damping, the kinetic energy of the swing door leaf is to be reduced shortly before it strikes the door frame in order to prevent high loads on the door frame and swing door leaf when the swing door leaf is braked. A damping of the swing door leaves can also be achieved by an elastic seal that is attached to the door frame. If the overflow valves 118 are omitted, standard connecting members 146 are screwed onto the connections 26 and 28, one of which is shown in FIG. 10. The standard connecting members, like the overflow valves 118, have two bores 148 which are used in screws 150 for fastening to the cylinder 12.

The upper end of the shaft 16 is attached to the lower end 152 of a rotating column 154. The rotating column 154 is a tube into which the shaft 16 is inserted in order to produce a rigid connection. A pivot arm 156 is attached to the upper end of the rotary column 154. A door leaf 160 is suspended from the upper swivel arm 156 and from a lower swivel arm 158. The lower swivel arm 158 is connected to the shaft end 46, as can be seen in FIG. 8. The swivel motor 10 is connected to the body 162 of a vehicle, not shown, via the intermediate piece 48. The support plate is screwed to a wall section of the body 13 with screws, not shown. Compressed air lines 164 run to the overflow valves 118 and are connected to a compressed air generator arranged in the interior of the body 13.

The swing door leaf 160 is kept closed by the constantly applied compressed air of the cylinder 12. For safety reasons, the swing door leaf must remain closed in the event of a compressed air failure. For this purpose, self-locking is provided by a corresponding design of the grooves 60, 66. Even if there is no self-locking over a groove course intended for this purpose, the swing door leaf 160 must not be able to be opened in the event of compressed air failure or by being pressed against the force of the compressed air. However, it must be ensured that the swing door leaf 160 can still be opened in an emergency. These conditions are met by the door lock arranged in the locking cylinder housing 36.

In the cylinder housing 36, a piston 166 is slidably mounted, which at one end merges into a locking pin 168. The bolt 168 protrudes into a recess 170 in the shaft section 32 and is sealed against the inside of the cylinder by an O-ring 172. Compressed air is applied to the pressure chamber in the cylinder via a nipple 174, the pressure chamber being delimited by a seal 176 attached to the piston 166. The end of piston 166 is one Fixed Bowden cable 178, which is inserted into a cylinder end wall 180. Under the force of a spring 182, the bolt 168 is pressed into the recess 170 so that the shaft 16 cannot rotate. The swing door leaf 160 therefore remains closed.

When compressed air is supplied to the cylinder via the nipple 174, the piston 166 moves into its right end position. The bolt 168 releases the recess so that the shaft 16 is unlocked. Since the cylinder is immediately pressurized with compressed air, the piston 166 is advanced, so that the shaft 16 is unlocked before jamming can occur due to a displacement of the hollow piston 50.

The Bowden cable 182 is connected to the emergency valve, not shown, of the vehicle. When the emergency valve is turned over, the cylinder 12 is depressurized. At the same time, the piston 166 is withdrawn and the shaft 16 or the shaft section 32 is released. The swing door leaf 160 can therefore be pushed open by hand in the event of compressed air failure. Since the bolt 168 projects into the recess 170 in the closed position, it is prevented that the swing door leaf can be opened against this force generated by the compressed air.

The compressed air is fed to the piston 166 via a line 184 which is connected to a control valve (not shown) in the interior of the body 13.

The recess 170 runs out on one side like a secant. Therefore, locking occurs only in one direction of rotation.

In the swivel motor 210 shown in FIG. 7, a hollow piston 214 is mounted in a cylinder tube 212 so as to be displaceable in the axial direction. On the hollow piston 214, as in that in FIGS. 1 to 6 Embodiment shown attached to shafts rotatably mounted support rollers which engage in helically wound grooves 216 of a shaft section 218, which merges into further shaft sections 220 and 222 at its two ends. The shaft section 222 continues in a shaft end 224, which protrudes from the cylinder tube 212 and is intended for connection of a coupling, not shown. The shaft section 222 serves as the seat of a roller bearing 225, the outer ring of which is fitted into the cylinder tube 212. In front of the side of the roller bearing 225 facing the shaft end 224 there is a cover 226 which is held in its axial position by a ring 228. The parts 218, 220, 222 and 224 form an output shaft. An annular seal 229 is arranged between the shaft section 222 and the cover 226. Another seal 230 is inserted between the cover 226 and the cylinder inner wall and roller bearing 225.

A connecting piece 232 is welded to the cylinder 212 for the attachment of a compressed air line. The connection piece 232 contains a channel 234, which continues in the wall of the cylinder tube 212 and opens below the roller bearing 225 into the interior of the cylinder tube 212. When compressed air is supplied via the channel 234, the annular end face 236 of the hollow piston 214 is acted upon by compressed air. In the end face 236 there are at least two bores 238 running inward in the axial direction, into which springs 240 are inserted, which are supported on the bottom of the bores 238 and on the roller bearing 225.

The second, annular end face 242 of the hollow piston 214 is also provided with axially inwardly extending bores 244, into which further springs 246 are inserted. The ends of the springs 246 are each supported on the bottom of the bores 244 and on an axial ball bearing 248 which is arranged in the interior of the cylinder tube 212 close to the second end.

A second connection piece 250 is welded onto the outside of the cylinder tube 212 and contains a connection 252 for a further compressed air line, which is not shown in detail. A channel 254 leads from the connection 252 to a hollow cylinder 256, in which a while 258 is displaceably mounted with the piston 260. The two ends 262 and 264 of the shaft 258 protrude from the cylinder 256. The end 264 carries an unspecified handle to touch. The other end 262 runs in a bore 266 in the wall of the cylinder 212. Seals (not designated in more detail) are arranged both in the cylindrical outer surface of the piston 260 and in the wall of the bore 266. A spring 268 is arranged between the one flat surface of the piston 260 and the wall of the cylinder 256 adjacent the end 264. When compressed air is supplied to port 252, piston 260 moves against the force of spring 268 toward the inner cylinder wall facing end 264. As a result, the tip of the end 262, which otherwise projects into the interior of the cylinder 212, is drawn back into the bore 266. In this case, the hollow piston 214 can move freely in the axial direction of the cylinder tube 212.

The hollow piston 214 shifts in one direction due to the application of compressed air which is supplied to the connection 232. A second connection 269 for a compressed air line is welded close to the second end of the cylinder tube 212. When the interior of the cylinder 212 is vented via the port 232 and the port 269 is supplied with compressed air, the hollow piston 214 moves in the other direction. The hollow piston 214 can be guided on the outside of the hollow cylinder 50 by grooves (not shown). However, it is also possible to force an axial movement on the hollow piston 214 by appropriate guide means. In this case, the bearings which allow the springs 240 and 246 to rotate following the hollow piston 214 can omitted. When the hollow piston 214 is displaced, a rotary movement is transmitted to the shaft section 218 and the shaft sections 222, 224, 220 connected to it. The curvature of the grooves 216 and the further grooves (not shown) running on the outside of the hollow piston 214 are based on the considerations already discussed in detail above in connection with the arrangement shown in FIGS. 1 to 6.

The embodiment of a swivel motor 210 shown in FIG. 7 contains only a connecting piece 250 with the parts enclosed therein, it being assumed that the parts to be moved by the output shaft should only remain in one end position if the compressed air fails until manual intervention occurs. If this is also desired for the other end position, a second connection piece 250 with the associated elements 252, 254, 256, 258, 260, 262, 264 and 268 must be provided on the cylinder 212, since otherwise the springs 246 remove the hollow piston 214 from it Move end position in which the grooves 216 and the other grooves, not shown, have a self-locking course.

If the hollow piston 214 is in the end position shown in FIG. 7, the tip of the shaft end 262 is moved into the displacement path of the hollow piston 214 when the compressed air fails or is switched off. This takes place under the influence of the spring 268. The tip of the shaft end therefore absorbs the forces transmitted from the springs 240 to the hollow piston 214. The hollow piston can therefore not move. In this case, a door leaf connected to the swivel motor 210 would remain in the closed position, for example.

Now, when the shaft 258 is moved by pulling the button of the end 264 against the force of the spring 268, the tip of the shaft end 262 clears the way for the hollow piston 214, which through the Springs 240 is displaced from its position characterized by self-locking. This allows the connected door leaf to be opened in an emergency, for example. The elements 250, 252, 254, 256, 258, 260, 262, 264 and 268 thus form a drive for releasing the axial force acting on the hollow piston 214.

For safety reasons, it is favorable to arrange the connection 252 in front of the reversing valve for the two connections 232 and 268.

Two connecting pieces 250 with the corresponding parts can also be arranged at diametrically opposite locations of the cylinder tube 212. As a result, the piston 214 can be supported on two ends 262.

Claims (14)

1. Pressure-actuated swivel motor, in particular for driving a swivel door wing connected to a rotating column via swivel arms, with a cylinder, a piston axially displaceable therein and with an axially fixed output shaft which is rotatably mounted on the end face of the cylinder and which has at least two helical cam tracks on a cylinder jacket section. engage in the guide projections connected to the piston,
characterized,
that the bearing (40, 18) of the output shaft (16, 46) of the swivel motor (10) for holding the swivel motor (10) including the rigidly connected to the output shaft (16, 46), one-piece rotary column (154) and of the swing door leaf (160) are designed so that the lower end face (112) of the swing motor housing (12, 34) is arranged symmetrically to the axis of rotation mounting holes for the attachment of a connecting the swing motor (10) to the vehicle body (162) in at least four differently adjustable positions Intermediate piece (48) and that optionally interchangeable overflow valves (118) are arranged on the housing (12) with compressed air standard connections, the pressure connections (126) of which are mirror images of one another on mutually facing sides. 2. swing motor according to claim 1,
characterized,
that the intermediate piece (48) consists of two support plates (108, 110) which run at right angles to one another and are connected to one another at each edge and have fastening holes, or is an angle piece. 3. Swing motor according to claim 1 or one of the following claims, characterized in that
that a shaft section (30) provided with the helical cam tracks (66) has a slightly larger diameter than the output shaft (16) of the swivel motor (10). 4. Swing motor according to claim 1 or one of the following claims, characterized in
that the cam tracks (66) for generating different torques and speeds of rotation of the rotary column (154) in the axial direction of the shaft section (30) run with different slopes. 5. Swing motor according to claim 1 or one of the following claims, characterized in
that a shaft section (32) of the output shaft is surrounded by a housing part (34), to which a locking cylinder housing (36) is radially attached, in which a pressure-actuated piston (166) is displaceable, one of which by spring force in the blocking position for the shaft section (32 ) held bolt (168), the bolt (168) being unlockable both by pressurizing the piston and by a Bowden cable (182) which is preferably non-positively connected to the emergency valve of a vehicle. 6. swivel motor according to claim 5,
characterized,
that the bolt (168) engages in a radial recess (170) of the shaft section (32) and that the recess runs flat in one direction of rotation along a secant. 7. swivel motor with cam tracks, the course of which in at least one end position of the piston when the pressure medium supply is interrupted and when the forces acting on the piston via the output shaft cause self-locking according to claim 1 or one of the following claims,
characterized,
that by means of a drive (72; 150 to 164, 166) arranged on the side of the cylinder (12; 112), an axial force can be exerted on the piston (50, 114) for movement, at least from its self-locking position, or the exercise can be initiated, the drive ( 72) has a pinion (74) which can be rotated by hand about an axis (78) and can be pivoted about a further axis (80) from rest positions into a fixed position in which the teeth of the pinion (74) with teeth (86) are in engagement, which are arranged in a row corresponding to the course of the curved tracks (60) on the piston (50) or on a carrier fixedly connected to the piston. 8. swivel motor according to claim 7,
characterized,
that the pinion (74) is mounted eccentrically on a rotatable disc (76), on the edge of which a projection (88) is arranged which, when the teeth of the pinion (74) and piston (50) engage, in the direction of rotation of the pinion (74 ) is pressed in the opposite direction against a stop (90), a stop pin (88) is preferably provided as a projection, which projects from one of the circular end faces of the disk (76) and can be pressed against a ball on the stop (90), which is under is a spring tension and against this can be moved into a spherical cap. 9. Swing motor according to claim 7 and / or claim 8, characterized in
that the axis of rotation (78) of the pinion (74) and the axis of rotation (80) of the disc (76) with the longitudinal axis of the stop pin lie in or approximately in a plane which upon engagement of the pinion (74) in the teeth (86) of the Piston (50) is perpendicular to the piston center axis. 10. Swing motor according to claim 7 or one of the following, characterized in that
that the distance between the axes of rotation (78, 80) of the pinion (74) and the disc (76) is approximately as large as half the radius of the disc (76), while the radii of the pinion (74) and disc (76) are approximately match in size. 11. Swing motor according to claim 7 or one of the following, characterized in that
that the cam tracks are arranged as grooves (60, 66) on the outside of a section (30) of the output shaft and the piston (50) with inclinations extending in diverging directions with respect to the piston center axis, that in the grooves (60, 66) each on Cylinder (12) or rollers (62, 68) attached to the piston (50) run so that the teeth (86) lie on the outside of the hollow piston (50) and that the pinion (74) is attached to the cylinder (12) Housing (82) is arranged at a distance from the cylinder end at which the teeth of the pinion (74) can be brought into engagement with the teeth (86) arranged in the one end position of the hollow piston (50) close to the piston end face. 12. Swing motor according to claim 7 or one of the following, characterized in
that at least one end projection (94) of the pinion (74) protrudes from the housing (82) with its end, the end being designed as a point of engagement for a tool and preferably being a square head. 13. Swing motor according to claim 7 or one of the following, characterized in
that in addition to the disc (76), a second disc (96) is arranged on the other side of the pinion (74) and that the identically designed discs (76, 96) are rotatably mounted in bores (98) of the side walls of the housing (82) . 14. swing motor according to claim 7,
characterized,
that the drive is designed as a shaft (258) displaceable in the path of the piston (214) under spring preload in the event of pressure medium failure, at one end (264) of which a tensile force can be exerted by hand, through which the other end (262) is off the track of the piston (214), which is under a spring preload, the shaft (258) preferably being connected to a piston (260) which is movably arranged in a cylinder of a housing (250) and can be displaced into an end position by supplying pressure medium in which the end (262) of the shaft (250) is removed from the path of the piston (214).

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