DE4002747C3 - Electro-hydraulic drive unit - Google Patents

Description

The invention is based on an electro-hydraulic drive unit for sashes of doors or the same, with the features of the generic term of the An saying 1.

Such a drive unit is from the DE 32 02 966 A1 known, here when closing the door is missing a stop. Often the drive can The latch or the seal does not close overcome so that the door does not close completely.

A hydraulic end stop like that of door closers is known per se, e.g. B. at the overhead door lock GEZE TS 4000 by in the area of the end stroke the piston working space with the unpressurized cylinder room is short-circuited, at the beginning ge named drive can not be realized, because the Short circuit channel would open the door over the Hydraulic pump a disruptive bypass arise and opening from the closed position would be via the pump then no longer possible.

The invention is based, in which drive unit mentioned a hydraulic to realize the final blow.

The invention solves this problem with the counter state of claim 1. Advantageous Ausgestaltun gene of the invention are set out in the dependent claims ben.

When closing, the overflow channel takes place Door accelerates shortly before reaching the closed position ter oil flow from the piston work space in the other Cylinder chamber or in the hydraulic reservoir or Suction side of the pump. This oil flow when closing can be controlled by the piston, preferably turned on be switched. A disruptive bypass when opening prevented by the closure member. For versions, where the overflow channel in the other cylinder overflow channel is preferred so arranged that its coin when closing first run over the piston and thereby the Piston is locked and in the area of the end stroke released by the piston.

With the release of the mouth, the hydraulic End stroke, that means increased closing speed one, preferably in a closing angle range of 4 to 0 degrees. The angular range is determined by the position the mouth relative to the closing angle dependent Kol appointment determined.

If the overflow line with the hydraulic reserve voir or the suction side of the pump is connected the increased oil flow when closing the pistons are switched, e.g. B. on one of Piston run switch in the cylinder wall, preferably reed switches. The switch can ver final link in the overflow line, the z. B. as Ma solenoid valve can be formed, control, d. H. Expand / a turn.

A structurally simple and manufacturing technology be particularly favorable arrangement is obtained when the Overflow channel with one to the pressure side of the hydrau likpump leading channel is connected, preferably by passing a section of the overflow channel through a Section of the channel leading to the hydraulic pump is formed, this latter section immediately opens into the piston working space.

Preferred embodiments are as follows games of the invention explained with reference to the drawing.

Show

Figure 1 is a schematic representation of the electro-hydraulic system of the drive unit.

Figure 2 is a sectional view in the area of the inventive throttle valve for adjusting the end stroke in a first embodiment, when closing the door during the end stroke.

Fig. 3 is a sectional view corresponding to Fig. 2 egg nes another embodiment, but when opening the door.

The drive shown is egg N swing door drive with a hydraulic Kol ben-cylinder unit 1st The piston 2 is operated to open the door with an electrically driven hydraulic lik pump 3 and to close the door with a closing spring 4 .

Throttle valves are provided to regulate the oil flow when opening and closing. The throttle valves 14 a and 15 a are used to adjust the opening speed, the throttle valves 16 a and 17 a to adjust the closing speed. An additional throttle valve 22 a provided with the invention is provided for adjusting the closing speed shortly before reaching the closed position, that is, for adjusting the hydraulic end stop.

The driven by an electric motor 5 Hy draulic pump 3 is connected on the suction side to a reservoir 6 of the hydraulic medium and on the pressure side with the interposition of a check valve 7 via lines 41 , 42 with the piston working chamber 8 of the piston-cylinder unit 1 . The piston working chamber 8 can be emptied into the reservoir 6 via a return line 9 , which is controlled by means of a solenoid valve 10 which is open in the de-energized state but is closed in the current-carrying state.

The piston 2 of the piston-cylinder unit 1 is arranged displaceably in the cylinder and works together with the closing spring 4 . The closing spring 4 strikes the piston 2 in the direction of the illustrated end position, in which the not shown, by means of a drive shaft 11 with the piston 2 drive-coupled wing of a door or the like occupies its closing position. To drive coupling from the drive shaft 11 to the piston 2 teeth on the piston 2 and the drive shaft 11th When opening the door wing NEN, the piston 2 is pushed to the right in the illustration in FIG .

The piston-cylinder unit 1 is filled on both sides of the piston 2 with hydraulic medium, the space 12 communicating with the reservoir 6 on the side of the piston 2 opposite the piston working space 8 via a connecting line 13 .

The operator works like this to open the door follows.

If the pump 3 is in operation with the solenoid valve 10 closed, that is to say under voltage, the hydraulic medium forced into the piston working chamber 8 by the pump via line 41 , 42 moves the piston 2 out of the position shown at a relatively high speed right, the space 12 via two with the valves 14 a and 15 a throttled connections 14 and 15 of the connecting line 13 is emptied into the reservoir.

As soon as the piston 2 overruns the closer to 14 in the direction of movement and thus locks, the hydraulic likmedium can only get through the throttled connection 15 in the connecting line 13 and thus the reservoir 6 , so that the speed of the piston 9 slows down due to increased throttle resistance and the opening movement of the wing, not shown, coupled to the drive shaft 11 is damped.

To close the door, the operator works like follows.

When the pump 3 is shut off and the solenoid valve 10 is deenergized, i.e. the solenoid valve 10 is open, the piston 2 is pushed to the left at a comparatively high speed by closing the wing 14 with the wing closed, the hydraulic medium from the piston working chamber 8 via two with the throttle valves 16 a and 17 a throttled connections 16 and 17 in the return flow line 9 and thus the reservoir 6 is displaced.

As soon as the piston 2 passes over the connection 17 in this direction of movement or its mouth 17 b and thus blocks it, the hydraulic medium can leave the piston working chamber 8 only via the throttled th connection 16 with the mouth 16 b, so that due to the increased throttle resistance Movement speed of the piston 9 is slowed while simultaneously damping the closing movement of the driven wing.

At the end of the closing movement, e.g. B. in a win kel range of 4-0 degrees acts the hydraulic end blow, the strength of which can be set via the throttle valve 22 a. The final blow results from the oil flow from the piston working chamber 8 into the cylinder chamber 12 'via the overflow channel 42 , 42 ', 22nd

The angular range is determined by the position of the opening 226 of the channel 22 or by the distance of the mouth 22 b from the closing end position of the piston festge. As can be seen from the figures, the Mün is 22 b in the closing direction of movement of the piston 2 before the mouth 17 b and thus also before the mouth 16 b. During the closing operation of the piston 2 passes over to next the mouth 22 b and outputs it at the end of the closing movement free. In this position of the piston the outflow of hydraulic oil from the working chamber 8 into the non-pressurized cylinder chamber 12 ', and 12 via the channels are collected 42, 42', it is possible, with throttled 22 via the throttle valve 22 a of the oil flow depending on the valve position. The channel sections 42 , 42 ', 22 thus form an overflow channel, which opens into the piston working chamber 8 at 42 b and into the cylinder chamber at 22 b. The section 42 is formed by an oil supply channel connected to the pressure side of the pump 3 , namely by a section opening into the working space 8 after the check valve 7 .

Pressure relief valves 18 , 18 'arranged in the piston have only safety functions and are closed during normal operation. Furthermore, check valves 19 , 19 'are provided as intake valves in the piston when opening or closing.

Valve 19 serves to suck the hydraulic medium into the piston working space 8 when opening by hand. Valve 19 'acts when closing as an intake valve between the unpressurized cylinder spaces 12 ' and 12 , with a line 20 belonging to the cylinder space 12 'of the annular space 21 connected to the reservoir 6 , so that this way and then the Check valve 19 'the hydraulic medium is sucked in and the cylinder spaces 12 ' and 12 are filled when the piston 9 moves to the left.

In Fig. 2, an embodiment is shown in detail, in which the above-described device according to the Invention for adjusting the hydraulic end stroke is structurally particularly simple. The throttle valve 22 a and the check valve 7 are arranged in the cylinder housing alongside one another in the longitudinal direction and are connected to one another via the channels 42 , 42 'and 22 , which form the overflow channel during the hydraulic end stroke. The oil supply line 41 connected to the pressure side of the pump 3 leads into the return check valve 7 in FIG. 2 from below. The throttle valves 16 a and 17 a not shown in FIG. 2 with the channels 16 , 17 and 9 are also arranged side by side in the cylinder housing parallel to the aforementioned valves 7 and 22 a. The guidance of the channels corresponds to the illustration in FIG. 1, the orifices 16 b, 42 b of the channels 16 and 42 respectively opening into the piston working space 8 at the same height but transversely offset at the closing end of the movement path of the piston.

The check valve 7 in Fig. 2 has a Verscholzenele element 7 a, the valve seat in the valve 7 in the valve 7 to the channel 41 or to the pump 3 closes ver under the hydraulic pressure of the medium in the channel 42 , as shown in Fig. 2 , and during the opening process from the valve seat under the effect of the hydraulic pressure in the duct 41 and thus the valve 7 opens. In each position of the valve element 7 a of the Ka is nal connected 42 with the channel 42 ', so that during the closing operation, when the piston 2 opens the orifice 22 b and space with the appropriate setting of the Dros selventils 22 a, the hydraulic medium from the working on the Channels 42 , 42 'and 22 can flow into the unpressurized cylinder space. The further the throttle valve 22 a is opened, the faster the closing speed in this area and thus the stronger the final stroke.

As already mentioned flows during the opening operation, the hydraulic medium via the check valve 7 is pressurized by the pump in reverse Rich processing via the channel 42 in the piston work chamber 8 and thus displaces the piston 2 in Fig. 2 to the left. If the valve 22 a is opened too far, a disruptive bypass occurs over the overflow channel when starting from the closed position. When the valves 22 a are fully open, the bypass means that the piston 2 can no longer be moved to the right solely by the hydraulic pressure and thus the door can no longer be opened automatically from the closed position. To ensure the opening function, it is therefore necessary to close the valve 22 a slightly.

In the modified exemplary embodiment in FIG. 3, the only difference compared to the exemplary embodiment in FIG. 2 is a special check valve 70 . It has as a closure element a Dif ferentialkolben 70 a, which prevents a troublesome bypass when automatically opening the door even when the throttle valve 22 a is fully open.

The differential piston 70 a has a continuous central longitudinal bore 71 and a transverse bore 72 opening into this, which opens into an outer annular groove 73 .

In accordance with the previous embodiment, the check valve 70 is opened during the opening process so that the oil can flow into the piston working chamber 8 via the channels 41 , 42 . The differential piston 70 a lies on the stop 43 at a distance from the valve seat, as shown.

The channel 42 'is closed by the differential piston ben. The oil flows exclusively through the longitudinal bore 71 . The transverse bore 72 and the ring groove 73 are closed via the valve wall adjoining the valve seat. This means that in this position of the differential piston, a troublesome bypass during the opening process does not occur even when the throttle valve 22 a is fully open.

As indicated in Fig. 3, is provided b 70 a still a preferably spherical valve body 70 in addition conventional tialkolben for differentiation, the a is upstream of the differential piston 70 and exclu Lich with the mouth of the channel 41 cooperates. It opens the mouth of the channel 41 during the opening process.

When closing, the differential piston 70 a and the valve body 70 b are moved in the same way as in the exemplary embodiment in FIG. 2 under the action of the hydraulic medium of the chamber 8 or pressed into the valve seat and thus the valve 70 is closed towards the pump. In this in Fig. 3 pushed down ver position of the differential piston, the transverse bore 72 opens with the annular groove 73 in the channel 42 ', so that in the closing angle range in question the hy draulic end stroke by the oil flow from the working space 8 in the unpressurized cylinder space the flow channel 42 , 42 ', 22 takes place. The oil in the differential piston flows through the longitudinal bore 71 and the transverse bore 72 and finally the annular groove 73 .

In modified versions of the differential piston 70 a can also be integrally formed with the valve body 70 b or even serve as a valve body of the check valve 70 .

In modified, not shown execution examples, the overflow line runs differently from the embodiments in the figures from the piston working chamber 8 to the reservoir 6 or to the suction side of the pump 3 . In the overflow channel is arranged as a closure member according to the invention, a solenoid valve or the like arranged by the piston 2 via a switch arranged in the cylinder wall, for. B. Reed switch is controlled. This solenoid valve is therefore provided in addition to the solenoid valve 10 which effects the door open position. The switch opens the solenoid valve when it is released by piston 2 when it is closed after being run over. The position of the switch determines in a manner corresponding to the position of the channel mouth 22 b in the figures the angular range of the end stroke and is therefore arranged at a corresponding point in the cylinder.

A disruptive bypass when opening, that is, oil flow over the overflow channel from the working space 8 into the reservoir 6 or to the suction side of the pump 3 is prevented by the closed solenoid valve when opened, controlled via the piston.

The solenoid valve is switched so that when opening the door is closed, that does not mean then opens when the piston opens the scarf when the door is opened ter runs over.

Claims (5)

1.Electro-hydraulic drive unit for the wing of doors or the like with a cylinder / piston unit, the piston of which is drive-coupled to the wing and can be acted upon by a closing spring in the closed position of the wing, the piston working space on the side of the piston to which the Attempt to avoid pistons under the spring pressure, with the pressure side of an electric hydraulic pump and via an electrically controllable magnetic valve, which is closed when the door is opened and opened when the door is closed, can be connected to a hydraulic reservoir or the suction side of the hydraulic pump, and the other cylinder space, into which the piston tries to escape when the door is opened, is connected to the hydraulic reservoir or the suction side of the hydraulic pump, characterized in that
that the piston working chamber ( 8 ) at piston positions ( 2 ) in the range of small closing angles up to the closed position with the other cylinder chamber ( 12 , 12 ', 21 ) or the hydraulic reservoir ( 6 ) or the suction side of the pump ( 3 ) via an overflow channel ( 42 , 42 ', 22 ) is connected and an accelerated oil flow from the piston working chamber into the other cylinder chamber or into the hydraulic reservoir or to the suction side of the pump takes place via the overflow channel when the door is closed shortly before reaching the closed position, that the overflow channel is a the overflow channel ( 42 , 42 ', 22 ) when the door is opened by means of the hydraulic pump ( 3 ) at least partially blocking closure member ( 22 a, 70 a), which prevents an interfering bypass when opening, and that the closure member as a differential piston ( 70 a) is formed,
wherein the differential piston ( 70 ) has mutually opening channels ( 71 , 72 , 73 ), of which a first opening ( 71 , 75 ) when opening and closing the door to the piston working space ( 8 ) is open, a second opening ( 71 , 76 ) is only open when opening the door to the pressure side of the pump ( 3 ) and a third mouth ( 72 , 73 ) is at least partially open only when the door to the overflow channel ( 42 ') is closed. 2. Electro-hydraulic drive unit according to claim 1, characterized in that the one bore as a longitudinal bore ( 71 ) and the other Boh tion is designed as a transverse bore ( 72 ) or vice versa. 3. Electro-hydraulic drive unit according to claim 5, characterized in that the transverse bore ( 72 ) opens into an outer annular groove ( 73 ) in the differential piston ( 70 a). 4. Electro-hydraulic drive unit according to one of claims 3-6, characterized in that the differential piston ( 70 a) is designed as a closure member egg nes in the overflow channel ( 42 , 42 ', 22 ) arranged check valve ( 70 ). 5. Electro-hydraulic drive unit according to one of the preceding claims, characterized in that the overflow channel ( 42 , 42 ', 22 ) with a pressure side of the hydraulic pump ( 3 ) leading channel ( 42 , 41 ) is connected, preferably by a section ( 42 ) of the overflow channel ( 42 , 42 ', 22 ) is formed by a section ( 42 ) of the hydraulic pump ( 3 ) leading channel ( 42 , 41 ), the latter section ( 42 ) opening directly into the piston working chamber ( 8 ) ,