DE4002747A1 - Electro hydraulic door-drive - has overflow passage connecting ram working chamber to other side on shutting - Google Patents

Abstract

The electro-hydraulic drive is for the leaf of a door, having a ram whose piston is coupled to the leaf and spring-loaded into the shut position. The working chamber of the piston is on the side of the latter to which it moves under spring action. It can be connected to the outlet side of an electrically-driven pump (3). The other side of the piston, to which it moves on opening the door, is connected to the hydraulic reservoir or the pump suction side. With the piston (2) in the shut or nearly-shut position, the working chamber (8) is connected by an overflow passage (42,42') to the other chamber (12'), the reservoir (6) or the suction side of the pump. When the door is opened by the pump a plug shuts the overflow passage off at least partly. ADVANTAGE - Ensures door is fully shut.

Description

The invention is based on an electrohydraulic Drive unit for wings of doors or the like, with the Features of the preamble of claim 1.

Such a drive unit is from DE-OS 32 02 966 known. Disadvantages arise when closing the door, because a final blow is missing. The drive can often close fall or do not overcome the seal when closing, so that the door does not close completely.  

A hydraulic end stop, like that of door closers is known, e.g. B. in the overhead door closer GEZE TS 4000, in the area of the end stroke of the piston work space short-circuited with the unpressurized cylinder space is not reali with the drive mentioned at the beginning be siert, because the short-circuit channel would with the opening a disruptive bypass when the door is opened via the hydraulic pump would arise and an opening from the closed position would be via the Pump is then no longer possible.

The invention is based, at the beginning mentioned drive unit to a hydraulic end stop realize.

The invention solves this in that the piston working space with piston positions in the range of small closing angles with the other cylinder chamber or the hydraulic reservoir or connected to the suction side of the pump via an overflow channel is the one the overflow channel in which the hydraulic pump at least partially lock the door rendes closure member. Via the overflow channel follows when the door closes shortly before the closing is reached an accelerated oil flow from the piston work space in the other cylinder chamber or in the hydraulic reservoir or to the suction side of the pump. This oil flow when closing can controlled by the piston, preferably switched on who the. A disruptive bypass when opening is by Ver final link prevented. For versions in which the Overflow channel opens into the other cylinder chamber, the Overflow channel preferably arranged so that when closing first run over its mouth from the piston and there when locked by the piston and in the area of the end stroke released by the piston.  

With the release of the mouth, the hydraulic end stop that is, increased closing speed, preferably in a closing angle range of 4 to 0 degrees. The angular range is determined by the position of the mouth relative to the closing angle dependent piston position.

In versions in which the overflow line with the Hy draulic reservoir or the suction side of the pump is connected, the increased oil flow when closing can also through the Pistons are switched, for. B. over one of the piston Ren switch in the cylinder wall, preferably reed switch. The switch can be the closure member in the overflow line, the Z. B. can be designed as a solenoid valve, control d. H. switch on / off.

In the case of particularly simple designs, this is Closure member as a throttle, for. B. as an adjustable throttle valve trained. Of course, the over flow channel through appropriate cross-sectional training itself act as a throttle.

In other versions, the closure member can also be used as Differential piston be formed, preferably two interconnected, in particular intersecting holes having. The differential piston can be a three-way valve act til by z. B. interlocking channels points, of which a first mouth when opening and closing the door to the piston work area is open and a second one Mouth only when opening the door to the pressure side of the pump is open and a third mouth only when the door is closed towards the overflow channel is at least partially open.  

In particularly preferred versions, the differential is piston as a closure member in the overflow channel arranged check valve.

A structurally simple and technically special favorable arrangement is obtained when the overflow channel with a channel leading to the pressure side of the hydraulic pump is connected, preferably by a section of the over flow channel through a section of the hydraulic pump leading channel is formed, the latter Ab cut opens directly into the piston working space.

Preferred embodiments of the He invention explained with reference to the figures. 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 setting the end stop in a first embodiment, for example, when closing the door during the end stop.

Fig. 3 is a sectional view corresponding to FIG. 2 of another embodiment, but when the door is opened.

The drive shown is a swing door drive with a hydraulic piston-cylinder unit 1 . The piston 2 is acted upon by an electrically driven hydraulic pump 3 for opening the door and a closing spring 4 for closing the door.

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. A provided with the invention additional ches throttle valve 22 a is for adjusting the speed of closing just before reaching the closed position, that is, for setting the hydraulic end stop.

The hydraulic pump 3, which can be driven by an electric motor 5, 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 flow line 9 , which is controlled by means of a solenoid valve 10 which is open in the de-energized state but closed in the energized state.

The piston 2 of the piston-cylinder unit 1 is slidably arranged in the cylinder and works with the closing spring 4 . The closing spring 4 acts on the piston ben 2 in the direction of the illustrated end position, in which the non-illustrated, drive-coupled wing of a door or the like assumes its closed position by means of a drive shaft 11 with the piston 2 . To drive coupling of the output shaft 11 to the piston 2 Ver teeth on the piston 2 and the drive shaft 11th When opening the door leaf, the piston 2 is shifted to the right in the illustration in FIG. 1, to the left when closing.

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

The operator works as follows to open the door.  

If the pump 3 is put into operation when the solenoid valve 10 is closed, that is to say under voltage, the hydraulic medium forced from the pump via the line 41 , 42 into the piston working chamber 8 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 connection 14 in the direction of movement in the direction of movement and thus blocks, the hydraulic medium can only reach the connecting line 13 and the reservoir 6 via the throttled connection 15 , so that the speed of the speed increases 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.

The operator works as follows to close the door.

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 displaced to the left via the closing spring 14 while the wing closes at a comparatively high speed, the hydraulic medium from the piston working chamber 8 via two selector valves 16 and 16 with the Dros 17 a throttled connections 16 and 17 into the return line 9 and thus the reservoir 6 is pushed ver.

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

At the end of the closing movement, e.g. B. acts in an angular range of 4-0 degrees, the hydraulic end stroke, the strength of which can be adjusted 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 mouth 22 b of the channel 22 or by the distance of the mouth 22 b from the closing end position of the piston. As can be seen from the figures, the mouth 22 b is in the direction of closing direction of the piston 2 in front of the mouth 17 b and thus also in front of the mouth 16 b. When closing, the piston 2 first runs over the mouth 22 b and releases it at the end of the closing movement. In this position of the piston, the outflow of the hydraulic oil from the working space 8 into the unpressurized cylinder chamber 12 'and 12 via the channels 42 , 42 ', 22 is possible, with the throttle valve 22 a, the oil flow is throttled depending on the valve position. The channel sections 42 , 42 ', 22 thus form an overflow channel, which opens at 42 b in the Kol benarbeitsraum 8 and at 22 b in the cylinder chamber. The section 42 is formed by an oil supply channel connected to the pressure side of the pump 3 , specifically by a section opening into the working space 8 after the check valve 7 .

Pressure relief valves 18 , 18 'arranged in the piston only have safety functions and are closed during normal operation. Furthermore, check valves 19 , 19 'are provided in the piston as intake valves 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 a suction valve between the unpressurized Zy cylinder spaces 12 ' and 12 , with a line 20 'belonging to the cylinder space 12 ' annular space 21 is connected to the reservoir 6 , so that this way and then via the check valve 19th '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 sections, in which the above-described device for adjusting the hydraulic end stop is structurally particularly simple. The throttle valve 22 a and the check valve 7 are arranged in the cylinder housing in the longitudinal direction next to each other and connected via the channels 42 , 42 'and 22 , which form the overflow channel during hy draulic end stroke. The oil supply line 41 connected to the pressure side of the pump 3 leads into the 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 next to each other in the cylinder housing parallel to the aforementioned valves 7 and 22 a. The leadership of the channels speaks the representation in Fig. 1, the mouths 16 b, 42 b of the channels 16 and 42 each at the closing end of the loading path of the piston at the same height, but transversely ver sets into the piston working space 8 .

The check valve 7 in Fig. 2 has a closure element 7 a, the valve seat in the valve 7 in the valve 7 to the channel 41 or to the pump 3 closes 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 channel 41 and thus valve 7 opens. In each position of the Ven tilelements 7 a, the channel 42 is connected to the channel 42 ', so that during the closing process, as soon as the piston 2 releases the mouth 22 b, and with a corresponding setting of the throttle valve 22 a, the hydraulic medium from the working space is over Ar the channels 42 , 42 'and 22 can flow into the unpressurized cylinder space. The further the throttle valve 22 a is open, the faster the closing speed in this area and thus the stronger the end impact.

As already mentioned, flows during the opening process the Hydrau likmedium via the check valve 7 is pressurized by the pump in the reverse direction through the channel 42 in the piston work chamber 8 and thus displaces the piston 2 in Fig. 2 to the left. If the valve is wide open to a 22, when starting from the closed position leads to a disturbing bypass via the overflow. When the valves 22 a are completely 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 slightly turn the valve 22 a.

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 differential piston 70 a, which prevents a troublesome bypass when the door is opened automatically, 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 space 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 ver. The oil flows exclusively through the longitudinal bore 71 . The transverse bore 72 or the annular groove 73 are sen ruled out via the channel wall adjoining the valve seat. This means that in this position of the differential piston an annoying 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 conventional valve body 70 in addition to the differential piston, the a is upstream of the differential piston 70 and cooperates exclusively with the mouth of the passage 41. It opens the mouth of the channel 41 during the opening process.

During the closing process, the differential piston 70 a and the valve body 70 b are displaced or pressed into the valve seat in a manner corresponding to the exemplary embodiment in FIG. 2 under the action of the hydraulic medium of the chamber 8 , and thus the valve 70 is closed towards the pump. In this in Fig. 3 shifted down position of the differential piston opens the transverse bore 72 with the annular groove 73 in the channel 42 ', so that in the relevant closing angle range of the hydraulic end stroke by the oil flow from the working space 8 in the unpressurized cylinder space on the Overflow 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, the differential piston 70 a can also be formed in one piece with the valve body 70 b or serve itself as the valve body of the check valve 70 .

In modified, not shown embodiments, the overflow line runs differently from the execution examples 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, a solenoid valve or the like is arranged as a closure member according to the invention, which is 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 acting be the door open position. The switch opens the solenoid valve when it is released by piston 2 when closing 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 solenoid valve, which is closed when opening and controlled by the piston.

The solenoid valve is switched so that it opens when the Door is closed, that means does not open even if the piston passes the switch when the door is opened.

Claims (11)

1. Electrohydraulic drive unit for the wing of doors or the like with a cylinder-piston unit, the piston of which couples antriebsge with the wing and can be acted upon by a closing spring in a position of the wing, preferably in the closed position, and whose piston working space on the side of the piston to which the piston seeks to escape under the spring pressure, can be connected to the pressure side of an electric hydraulic pump and, via a preferably electrically controllable solenoid valve, to a hydraulic reservoir or the pressure side of the hydraulic pump, and the other cylinder space, into which the piston tries to evade when the door is opened , is connected to the hydraulic reservoir or the suction side of the hydraulic pump, characterized in 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 valve likreservoir ( 6 ) or the suction The side of the pump ( 3 ) is connected via an overflow channel ( 42 , 42 ', 22 ), which is an overflow channel ( 42 , 42 ', 22 ) when the door is opened via the hydraulic pump ( 3 ) at least partially blocking closure member ( 22nd a, 70 a) has. 2. Electro-hydraulic drive unit according to claim 1, characterized in that the United closure member as a throttle, for. B. is designed as an adjustable throttle valve ( 22 a). 3. Electro-hydraulic drive unit according to claim 1 or 2, characterized in that the closure member is designed as a differential piston ( 70 a), which preferably has two interconnected, in particular intersecting bores ( 71 , 72 ). 4. Electro-hydraulic drive unit according to claim 3, characterized in that the differential piston ( 70 ) has mutually opening channels ( 71 , 72 , 73 ), of which a first mouth ( 71 , 75 ) when opening and closing the door to the piston working space ( 8th ) is open, a second mouth ( 71 , 76 ) is only open when opening the door to the pressure side of the pump ( 3 ) and a third mouth ( 72 , 73 ) is only open when the door is closed to the overflow channel ( 42 ') is at least partially open. 5. Electro-hydraulic drive unit according to claim 3 or 4, characterized in that the one bore is designed as a longitudinal bore ( 71 ) and the other bore as a transverse bore ( 72 ) or vice versa. 6. Electro-hydraulic drive unit according to claim 5, characterized in that the transverse bore ( 72 ) in an outer annular groove ( 73 ) in the differential piston ( 70 a) opens. 7. 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 of a check valve ( 70 ) arranged in the overflow channel ( 42 , 42 ', 22 ). 8. Electro-hydraulic drive unit according to one of the preceding claims, characterized in that the overflow channel ( 42 , 42 ', 22 ) is connected to a channel ( 42 , 41 ) leading to the pressure side of the hydraulic pump ( 3 ), 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 ), where the latter section ( 42 ) opens directly into the piston working chamber ( 8 ) . 9. Electro-hydraulic drive unit according to one of the preceding claims, characterized in that the overflow line connects the piston working space ( 8 ) and the reservoir ( 6 ) or the suction side of the pump ( 3 ) and the closure member with one with the piston ( 1 ) cooperating switch is connected. 10. Electro-hydraulic drive unit according to claim 9, characterized in that the switch is designed as a reed switch or the like, wherein part of the switch in the piston ( 2 ) and another part of the switch is arranged in the cylinder wall. 11. Electro-hydraulic drive unit according to one of the above aspiring claims, in particular according to claim 9 or 10, characterized in that the closure member is designed as a solenoid valve, which is preferably controlled by the piston.