EP0715675A1

EP0715675A1 - Revolving door drive

Info

Publication number: EP0715675A1
Application number: EP94924733A
Authority: EP
Inventors: Lothar Singer
Original assignee: Geze GmbH
Current assignee: Geze GmbH
Priority date: 1993-07-10
Filing date: 1994-07-10
Publication date: 1996-06-12
Anticipated expiration: 2014-07-10
Also published as: DE4323150B4; WO1995002107A1; ATE154665T1; ES2104409T3; EP0715675B1; US5687451A; DE59403198D1; DE4323150A1

Abstract

An automatic revolving door drive with a hydraulic piston-cylinder unit (7, 8), a closing spring (10) and an opening motor consists of an electromotor (5) and a hydraulic pump (4). The invention deals with a so-called servo-closer that opens a door in a mechanical and assisted manner and automatically closes the door in an hydraulically dampened manner by means of the closing spring. In order to be able to use low-power opening motors and to implement a relatively small design, the pressure of the hydraulic medium is regulated when the door is mechanically opened so as to be adapted to the momentary force of the closing spring (10). For that purpose, the closing spring (10) which co-operates with the piston (7) is supported at one end on the piston (7) and at the other end on a hydraulic pressure pad (25). The same hydraulic pressure is set in the pressure chamber (12) and in the hydraulic pressure pad (25) by a special pressure-regulating valve (20).

Description

Swing door drive

Description:

The invention relates to a swing door drive with a hydraulic closer device with a hydraulic piston-cylinder unit and closer spring and with a motorized opener device with hydraulic pump and electric motor.

Such a swing door drive is such. B. from DE-OS 32 02 966 known. There, a so-called electrohydraulic door closer is described, which has a compression spring as an energy store for closing and opening a hydraulic pump with an electric motor. The door is opened fully automatically by the piston being moved hydraulically with the aid of the hydraulic pump with compression of the closer spring, and the closing process then takes place purely mechanically, as in the case of a conventional hydraulic door closer, under the action of the closer spring. A disadvantage of the known such swing door drives with a fully automatic opening motor is the relatively large design. It essentially results from the powerful unit consisting of hydraulic pump and electric motor required for fully automatic opening. In practice, however, it is often not necessary to open the door fully automatically by motor. A so-called servo closer, which has an opener motor, which is only used to support manual opening, would often be sufficient.

ERSATZBLÄTΓ REGE From DE-OS 32 34 319 a so-called automatic door closer is known, in which the closer spring can be hydraulically pretensioned by means of a hydraulic pump via a hydraulic support member arranged between the piston and the closer spring, so that the walker the door does not have to use any force to pretension the closer spring. The construction is relatively complicated.

The invention is based on the object of further developing a rotary door drive mentioned at the outset in such a way that it can be used as a servo door closer and is of simple construction with a relatively small construction.

The invention solves this problem by regulating the pressure of the hydraulic medium in a manner adapted to the instantaneous force of the closer spring during the motorized opening process. This takes into account the fact that depending on the respective door opening angle and depending on the spring preload, different pump pressures are required in order to manually open the door preferably over the entire range of rotation without additional effort.

In preferred embodiments of the swing door drive, the piston is guided displaceably in the hydraulic cylinder, forming a pressure chamber and a pressure-free chamber. To regulate the pump pressure it can be provided that the closer spring cooperating with the piston or a spring adapted to it is supported at one end on the piston and at the other end on a hydraulic pressure cushion, in the pressure chamber and in the hydraulic pressure cushion the same hydraulic pressure is adjusted • regulated. The pressure chamber and the hydraulic pressure cushion are preferably hydraulically connected to the pressure side of the hydraulic pump, and a pressure equilibrium in the pressure chamber and in the pressure cushion can be set in different opening positions of the door. Depending on the ratio of the pressure-absorbing effective areas of the piston in the pressure chamber and the valve member in the pressure cushion, the piston is shifted under the effect of the pump pressure (automatic opening) or kept floating (servo drive) when the pressure balance is set. In preferred embodiments, the quotient of the effective areas can be set optionally. In the stationary pressure equilibrium in servo operation, the piston is kept floating via the pump pressure, the pressure cushion is connected on the one hand to the pressure chamber and on the other hand to the suction side of the pump. The pump delivers in the short circuit from the pressure side into the pressure pad to the suction side.

In particularly advantageous designs, it is provided that a regulated pressure regulating valve is provided in the hydraulic circuit of the swing door drive. The pressure regulating valve can be regulated in various ways. The control is preferably carried out via the closer spring and / or via a separate spring, preferably a spring matched to the closer spring. When controlling via the closer spring, the piston travel and the spring preload are taken into account. Alternatively, an exclusively travel-dependent control of the valve can be used, in which the piston travel or the axis rotation angle, e.g. B. the output / closer shaft or the position of the door is detected. In principle, the regulation can also take place electronically. The control can alternatively or additionally be carried out with the aid of a stored program.

In particularly preferred embodiments it is provided that the pressure regulating valve has a regulated valve pressure space. A preferably piston-shaped valve member can be arranged in the valve pressure chamber, which cooperates with the spring regulating the pressure regulating valve. A particularly compact arrangement is obtained if the spring regulating the pressure regulating valve is supported with one end on the piston of the piston-cylinder unit and with the other end on the valve member. The spring can advantageously be formed by the closer spring. Exemplary embodiments are shown in the following figures.

Show

Figure 1 is a schematic sectional view of a servo closer according to the invention;

Figure 2 is a circuit diagram of the servo closer in Figure 1;

Figure 3 is an enlarged view in area III in Figure 1 with a modified pressure regulating valve;

Figure 4 is a circuit diagram of another modified

Embodiment of the servo closer,

FIG. 5 first switching position of the switching valve 26 in FIG. 2,

6 shows the second switching position of the switching valve 26 in FIG. 2.

The servo closers shown in the figures are each a hydraulic swing door drive with which the door is opened with motor or motor support and closed hydraulically damped under the action of a closer spring. It is constructed as a hydraulically damped door closer with closer spring 10, combined with an electro-hydraulic opener drive, with electric motor 5 and pump 4. The door closer and the opener drive are integrated in one unit in a housing 1.

The housing 1 can be mounted on the door leaf or the door frame as in the conventional overhead door closer. Corresponding to a conventional closer shaft, the output shaft 2 is mounted in the housing 1 and can be coupled in a rotationally fixed manner to a force-transmitting linkage (not shown). As with a conventional overhead door closer, the linkage is supported on the door frame or on the door leaf. If the linkage is designed as a sliding arm, the slider arranged at its free end is guided in a sliding rail arranged on the door frame or on the door leaf. If the linkage is designed as a scissor arm, the free end is stored in a fixed pivot bearing on the door frame or on the door leaf.

In the drive shown in the figures, the closing mechanism 3, the hydraulic pump 4 and the electric motor 5 are arranged side by side in the housing 1 from left to right. An electronic control unit 6 is mounted on the front, adjacent to the closer mechanism.

The closer mechanism 3 consists of a hydraulic piston 7 guided in a hydraulic cylinder 8. The piston 7 is designed as a hollow piston and has in its interior a rack-shaped toothing 7a which meshes with a pinion 9 which is connected to the output shaft 2 in a rotationally fixed manner. The piston 7 interacts with the closer spring 10, which in the exemplary embodiment is arranged in a pressure-free space 11 in the hydraulic cylinder to the right of the piston 7. A pressure chamber 12 is formed in the hydraulic cylinder 8 to the left of the piston. The hydraulic rooms 11 and 12 are hydraulically connected to one another via hydraulic channels.

The sealing surface or sealing edge of the piston 7 is at the left end of the piston z. B. formed as an annular surface with sealing ring 7a.

The closer spring 10 is designed as a helical compression spring. It is supported with its left end on the right end of the piston 7 and with its right end on a spring plate 13. As known from DE-OS 32 24 300, the spring plate 13 can be adjusted in its axial position in the unpressurized space 11 by means of an adjusting spindle 13a, the position of the spring plate 13 and thus the setting of the spring force via a magnetic indicator 13b is displayed on the outer surface of the housing 1. The adjusting spindle 13a engages with its end facing away from the spring plate 13 in a valve member 21 and is mounted therein. The valve member 21 is part of a pressure regulating valve 20 arranged in the cylinder chamber 8. The closer spring 10 is supported on the valve member 21. The valve member 21 is movably mounted in the hydraulic cylinder 8 and delimits the pressure-free space 11, which therefore extends from the right-hand side of the piston 7 to the valve member 21.

The pressure regulating valve 20 can be designed differently, e.g. B. as a seat valve, as shown in FIGS. 1, 2 and 3, two variants, or as a slide valve, as shown in FIG. 4.

In the case of the seat valves 20 shown in FIGS. 2 and 3, the valve member 21 has one or more annular sealing edges 21a, 21b which cooperate with a valve seat 23 fixed to the housing by sitting there when the valve 20 is closed. Between the effective valve surface 22 on the valve member 21 and the valve seat 23, a narrowly limited minimum valve pressure chamber 25 is formed.

The valve pressure chamber 25 is connected via a channel 14 to the pressure side and via a channel 31 to the suction side of the pump 4 (see FIGS. 2 and 3). When the pump is switched on, the valve member 21 is shifted to the left, forming a pressure cushion in the valve pressure chamber 25. The hydraulic medium can then flow into the pressure-free chamber 11 and via the channel 31 to the suction side of the pump 4. A line 30 is provided as a hydraulic connection of the pressure chamber 12 to the valve pressure chamber 25, which branches off from the supply channel 14 and opens into the pressure chamber 12.

The pressure side of the pump 4 is therefore connected on the one hand via the channels 14 and 30 to the pressure chamber 12 and on the other hand via the channel 14 to the valve pressure chamber 25. Depending on the position which the valve member 21 assumes under the action of the pressure cushion, the valve pressure chamber 25 can also be connected directly to the suction side of the pump 4 and to the pressure-free chamber 11, specifically via line 31.

L 26 It is essential in all the illustrated embodiments of the pressure valve 20 that both the pressure chamber 12 of the piston 7 and the valve pressure chamber 25 are acted upon by the closer spring 10. Due to the hydraulic connection of the pressure chambers described above, when the pump 4 is switched on, the same hydraulic pressure is set in the pressure chamber 12 and in the pressure cushion in the valve pressure chamber 25. This pressure is dependent on the compression of the closer spring 10, that is to say on the bias of the spring 10 and on its further compression determined by the position of the piston 7. This means that the higher the preload or the strength of the spring 10 and the larger the door opening angle, the greater the hydraulic pressure which is established in the pressure chambers 12 and 25.

Depending on the ratio of the effective area of the piston 7 to the effective valve area 22 - under the effect of the same hydraulic pressure applied on both sides to the piston 7 and the closer spring 10 - forces act on the piston 7 that force the piston 7 (automatic opening) or only keep floating (pure servo function). In the latter case, the valve member 21 is held so lifted from the valve seat 23 via the pressure cushion in the valve chamber 25 that the pump is short-circuited, that is. That is, the pressure side of the pump is connected to the suction side via the pressure cushion in the valve pressure chamber 25 and via the line 31 and the pump delivers in this short circuit.

With the pressure regulating valve 20, the pressure equilibrium in the pressure chambers 12 and 25 is established in each opening position of the door, with the pressure side of the pump finally via channel 14, valve pressure chamber 25 and channel 31 with the suction side, at least when the piston is at rest the pump is connected. The valve member 21 is slightly raised from the valve seat 23 in this stationary position, to the left in FIGS. 2 and 3.

The design of the valve pressure chamber 25 and the size of the effective valve surface 22 depend on the shape of the valve member 21 and the valve seat 23 and on the position of the sealing edges 21 a, 21 b. The valve member in Figures 2 and 3 is substantially plate-shaped.

ERSAΪZBLAπ (RULE 26) In the embodiment in Figure 3, only one sealing edge 21 a is provided, specifically on the outer edge of the plate-shaped valve member. The surface facing the valve seat 23 between this annular sealing edge 21 a is the effective valve surface 22, which is in relation to the effective surface of the piston 7, which determines whether the drive opens automatically with the help of the pump, such as an automatic drive or when opening only acts as a support.

In the valve 20 used in FIGS. 1 and 2, in contrast to FIG. 3, an optional size adjustment of the effective valve surface 22 is possible. For this purpose, a switching valve 26 is mounted fixed to the housing in the feed channel 14 directly in the valve seat 23. It has a valve body 28 which can be switched by means of a rotary switch 27 and which, in its different positions, has valve channels which are differently effective and which are assigned to the different effective valve surfaces 22a, 22b (FIG. 2), ie. that is, an associated large valve area is effective in one valve position of the switching valve 26 and an associated small valve area 22 is effective in another position of the valve 26.

The valve member 21 has an inner and an outer sealing edge 21 a, 21 b. Inside the inner sealing edge 21b is a first valve surface 22b with a first valve pressure chamber 25b and between the inner and outer sealing edge 21b or 21a is a second valve surface 22a with a second valve pressure chamber 25a. In the one switching position of the switching valve 26, only the first valve pressure chamber 25a is flowed through and therefore only the valve surface 22a is effective. In the second switching position of the switching valve 26, the two valve pressure spaces 25a and 25b are flowed through and thus the valve surface 22a and 22b, that is to say a larger valve surface, is effective.

The two switching positions of the switching valve 26 are shown in FIGS. 5 or 6. In the switch position in FIG. 5, as is also present in FIG. 2, the right channel 14 is connected to the left channel 14 and the right channel 32 to the left channel 32. In the other switching position in FIG. 6, the right channel 14 is connected to the left channel 14 and the left channel 32. The right channel 32 ends dead.

REPLACEMENT BLAΓΓ The effective area of the piston 7 in the pressure chamber 22 is unchangeably constant. With the optional setting of the effective valve surface 22 by means of the rotary switch 27, the quotient of the effective surfaces of the valve pressure chamber 25 can thus be selected. If the quotient of these areas is greater than 1, the pressure applied via the hydraulic pump causes the piston to move in the opening direction, ie to the right in the figures. In this case the drive acts as an automatic opener drive. If the quotient of the areas is 1, the piston is kept floating. This means that the closer spring 10 is compensated in each piston position by the hydraulic pressure acting on the closer spring on both sides. The door can thus be opened like a door without a door closer. In this case the drive acts as a pure opening servo drive.

The hydraulic pump 4, which is arranged directly adjacent to the switching valve 26, can be designed as a conventional gear pump. The electric motor 5 coupled to the hydraulic pump 4 is also constructed conventionally.

The hydraulic pump 4 is switched on and off via one or more sensors. For example, external motion detectors, switches on the door leaf or on the handle or motion detectors in the closer housing and / or a rotary encoder on the closer shaft can be provided for this purpose.

The switch-on process is initiated by a person who wants to pass the door, depending on the design and arrangement of the sensor, either automatically when the person approaches or by actuating a switch. The pump then remains switched on until the person has passed the door, which can be detected by the corresponding sensor or by a timer.

The pump is then switched off or throttled and one or more shut-off valves in return flow lines leading out of the pressure chamber 12 and the valve pressure chamber 25 preferably open automatically or automatically, so that the hydraulic medium from the pressure chambers 12 and 25 into the pressure-free chamber 11 and / or can flow to the suction side of the pump 4.

- ^ ^p - ^{E EL 2δ)} The piston 7 is shifted to the left while releasing the closer spring 10 in the figures, as a result of which the pinion coupled to the piston-side toothing is rotated together with the closer shaft 2 in a clockwise direction, ie closing direction.

The pressure regulating valve 20, which is regulated via the closer spring 10, has two functions in the exemplary embodiment shown in FIGS. 1, 2 and 3. Its first function is to implement the control of the pump pressure which is dependent on the door opening angle or on the respective closing force, as described above.

The additional second function of the pressure regulating valve 20 is that in the event of an overload, i. i.e., if the door is blocked when opening or is forced shut when closing, it acts as a safety pressure relief valve. The briefly built up overpressure in the pressure chambers 12 and 25 in this case is automatically reduced - by moving the valve member 21 to the left while compressing the closer spring 10 - via the return flow line 31 to the pressure-less side of the hydraulic pump or to the pressure-less chamber 11. Since this control valve 20, which functions as a safety pressure relief valve, is controlled via the closer spring 10, the triggering force acting on the valve increases with the compression of the closer spring 10, so that a constant opening or closing torque is obtained. A constant response sensitivity of the pressure relief valve is thus obtained, regardless of the open position of the door, thereby reducing the risk of injury when walking on.

This function as a safety pressure relief valve is guaranteed in any case given the selected area ratio of the effective valve area 22 and the effective area of the piston 7. The circuit diagram in FIG. 2 shows the hydraulic circuit of the servo closer in FIG. 1. The main functional parts of the servo closer are shown schematically, as are the hydraulic channels already mentioned: feed channel 14, connecting channel 30 and return flow channel 31, furthermore return flow channels between the pressure chamber 12 and the pressure-free chamber 11 with throttle valves for setting the backflow speed when closing. These are the channels 44, 45, 46 and 47 with the throttle valves 45a, 46a and 47a for setting the end stop, the closing speed and the closing delay.

As a shut-off valve, which prevents the hydraulic medium from flowing back out of the pressure chamber 12 when it is opened, the circuit diagram in FIG. 2 provides a hydraulically controlled shut-off valve 40, which is closed when the door is opened and is opened when the door is closed. The check valve 40 is arranged in the return flow channel 44 and is controlled via the hydraulic pressure in the channel 30. It replaces the solenoid valve used in conventional electrohydraulic drives. The versions shown do not use a solenoid valve.

The check valve 40 is a slide valve. It blocks or opens the return flow channel 44, which connects the pressure chamber 12 to the pressure-free chamber 11. The slide 41 is piston-shaped and is sealingly displaceably guided in a cylindrical valve chamber 42. The slide 41 is acted upon on one end side by a valve spring 43 arranged in the valve chamber 42 and on the other end side by the hydraulic pressure of the pressure side of the hydraulic pump 4 via the channel 30. When the door 4 is opened with the pump 4 switched on, as shown in FIG. 3 with a solid line, the slide 41 is held in the blocking position under the action of the hydraulic pressure, in which the hydraulic supply line is opened by connecting the channels 30 and 44, but the return flow channel 44 is closed 44c is locked.

ERSÄΓZBLÄΓT (RULE 26) If the hydraulic pressure in the channel 30 is reduced, as in the closing process when the pump 4 is switched over or switched off or throttled, the slide 41 is displaced to the left into the dashed position in the figure in the illustration under the action of the valve spring 43 and thereby the blocking of the Reverse flow channel 44 is canceled by connecting 44b and 44c and the connection of channels 30 and 44 is interrupted.

Instead of or in addition to controlling the closing speed via the throttle valves, the closing operation, ie. that is, the closing speed can also be regulated via the pump. A reversible pump is used for this. During the closing process, the hydraulic medium is pushed back by the pump. The pump then acts as a hydraulic motor and the electric motor as a generator. The closing speed is controlled electronically.

The power supply for this is provided by the generator itself. In order to control additional closer functions, such as end stop, opening damping and closing delay, microswitches can be fixedly attached to the closer housing. For this purpose, switches at 10 degrees and 80 degrees can be arranged. The closing speed can be controlled separately via the switch at 10 degrees. The closing delay can also be initiated via a timer. The opening damping can be controlled via the switch at 80 degrees.

The circuit diagram in FIG. 4 describes a servo closer which has essentially the same structure as the exemplary embodiments described above. However, the pressure regulating valve 20 is designed as a slide valve and the hydraulic circuit is somewhat modified. The valve member 21 of the valve 22 is designed as a piston-shaped slide which is tightly guided in the cylinder space. The valve pressure chamber 25 is formed in the cylinder chamber on the side of the slide 21 facing away from the closer spring 10.

ERSAT2BLATΪ (RULE 26) At the end of the valve pressure chamber 25, the supply channel 14 opens and the outlet openings of the connecting channel 30, which connects the valve pressure chamber 25 to the pressure chamber 12, and the outlet opening of the return flow channel 54, which can be blocked by a hydraulically controlled shut-off valve 50, are located . The return flow channel 31, which is connected to the suction side of the pump 4, opens at a distance from the end face of the valve pressure chamber 25 and determines the expansion of the valve pressure chamber 25. The slide valve 20 serves in the same way as the seat valves in FIGS. 2 and 3 as a pressure regulating valve, which controls the hydraulic pressure, depending on the instantaneous closing force, with the same pressure in the valve pressure chamber 25 and in the pressure chamber 12, and as a safety pressure valve.

When opening, the piston-shaped slide 21 is moved under the action of the pump pressure into the position shown in dashed lines on the left. The same pressure prevails in the pressure chambers 25 and 12, which are connected to the check valve 30b via the line 30. In the left position of the slide valve 21, the pump 4 feeds the hydraulic fluid via the channel 14 into the pressure chamber 25. The return flow to the suction side takes place from the pressure chamber 25 via the channel 31.

When starting up, when the pump is switched on, or when opening quickly, the piston-shaped slide 21 is in a further right position, in which it closes the outlet opening of the channel 31.

When the door is closed, when the pump is switched off, the slide 21 is in its right end position. The valve 40 controlled by the pump pressure is now open and the return flow channel 44 is therefore no longer blocked. The piston 7 now moves under the action of the closer spring 10 to the left. The oil flows through the channel 44 through the filter 45 and flow valve 44a and valve 40 into the unpressurized space 11. At the same time, there is backflow into the now depressurized valve chamber 20 and finally to the suction side of the pump. This backflow from the pressure chamber also takes place via the filter 45 and a flow valve 30a. If pressure surges occur during opening or closing, these are immediately reduced via the valve 20, since the slide 21 deflects to the left under compression of the closer spring 10 and the hydraulic medium can be discharged via the outlet channel 31 or 54.

A further function of the valve 20 in the embodiment in FIG. 4 is that it forms a special device for pre-storing the energy required for opening. For this purpose, the pump is switched on before the door is moved and the slide 21 is moved to the left into the position shown in broken lines under the action of the hydraulic medium. The piston 7 is not moved. As a result, the closer spring 10 is biased. The energy from the pretension is then available when the opening process is initiated and supports opening in the initial phase. The slide 21 can be moved more or less far from its dashed position to the right, especially when opening quickly, while the piston 7 is also moved to the right when the door is opened. When the door is opened, less force is required at least in the initial phase. The energy stored in the preload of the closer spring can be used as an opening aid in this way.

Even when the door is opened further, a power reserve or buffering is obtained by biasing the closer spring 10 by moving the slide 21 via the hydraulic pump, which supports the servo effect of the drive when opening and also allows fast, forceless opening for a limited further opening angle .

ERSAΓZBLAΓT (RULE 26)

Claims

1. Revolving door drive with a hydraulic closer device with hydraulic piston-cylinder unit and closer spring and with a motorized closer device with hydraulic pump and electric motor, characterized thereby,

that during the motorized opening process the pressure of the hydraulic medium is adjusted to the instantaneous force of the closer spring (10).

2. Revolving door according to claim 1, wherein the piston in the hydraulic cylinder is guided displaceably to form a pressure chamber and a pressure-free chamber, characterized in that the closer spring (10) cooperating with the piston (7) or a spring matched to this one end is supported on the piston (7) and the other end is supported on a hydraulic pressure cushion (25), the same hydraulic pressure being regulated in the pressure chamber (12) and in the hydraulic pressure cushion (25).

3. Revolving door drive according to claim 2, characterized in that the pressure chamber (12) and the hydraulic pressure pad (25) with the pressure side of the hydraulic pump (4) are hydraulically connected and in ver¬ different opening positions of the door at least almost equal pressure im Pressure chamber (12) and in the pressure cushion (25) can be set, the hydraulic pump (4) running without further shifting work and / or being short-circuited and holding the piston (7) floating or wherein the hydraulic pump (4) does the shifting work and the piston (7 ) emotional.

4. Revolving door drive according to one of the preceding claims, characterized ge ken nze ic h net that a regulated pressure regulating valve (20) is provided in the hydraulic circuit of the revolving door drive.

REPLACEMENT SHEET (REÜLL 26)

5. Revolving door drive according to claim 4, characterized in that the pressure regulating valve (20) is regulated via the closer spring (10) and / or via a separate spring, preferably a spring which is tuned to the closer spring (10).

6. Swing door drive according to claim 3 or 4 or 5, characterized in that the pressure regulating valve (20) has a regulated valve pressure chamber (25).

7. Swing door drive according to claim 5 or 6 in conjunction with claim 2, da¬ by ge ke n nze ic h net that the pressure pad (25) is connected to the pressure regulating valve (20), preferably as a regulated valve pressure chamber (25) of the pressure regulating valve (20) is formed.

8. Swing door drive according to claim 6 to 7, characterized in that the valve pressure chamber (25) has a controllable outlet channel (31) which is preferably connected to the suction side of the hydraulic pump (4).

9. swing door drive according to one of claims 6 to 8, characterized ge ke nn¬ ze ic hn et that in the valve pressure chamber (25) a valve member (21) is arranged an¬ which with the pressure regulating valve (20) regulating spring (10 ) interacts.

10. Swing door drive according to claim 9, characterized ge ke n nze ichn et that the pressure regulating valve (20) regulating spring (10) is supported with one end on the piston (7) of the piston-cylinder unit and with its other end on the valve member (21) .

11. Swing door drive according to claim 9 or 10, characterized ge ke nnze ic h¬ n et that the valve member (21) acts on the outlet channel (31).

12. Swing door drive according to one of claims 9 to 11, characterized in that the size of the effective valve surface (22) of the valve member (21) is optionally adjustable.

13. Swing door drive according to one of claims 9 to 12, characterized in that the ratio of the effective valve area (22) of the valve member (21) and the effective area of the piston (7) of the piston-cylinder unit is selectively adjustable.

14. Swing door drive according to claim 12 or 13, characterized ge ke n nze ichnet that a preferably switchable by means of a hand switch valve (26) is provided for optional adjustment, which cooperates with the effective valve surface (22) of the pressure regulating valve (20) or this determines.

15. Swing door drive according to one of claims 4 to 14, characterized in that the pressure regulating valve is designed as a slide valve with a sealingly displaceable piston-shaped valve member or as a seat valve with a seat valve member which can be lifted / lifted off tightly.