WO2002064933A1

WO2002064933A1 - Hydraulic drive for a turning sash

Info

Publication number: WO2002064933A1
Application number: PCT/EP2002/001415
Authority: WO
Inventors: Jürgen HOMBERG
Original assignee: Dorma Gmbh + Co. Kg
Priority date: 2001-02-13
Filing date: 2002-02-11
Publication date: 2002-08-22
Also published as: EP1409827B1; DE10107050C2; ATE432405T1; EP1409827A1; DE50213577D1; ES2327213T3; DE10107050A1; DK1409827T3

Abstract

The invention relates to a hydraulic drive for a turning sash, comprising a door-closing element (1) having an eccentrically positioned pinion (6) comprising a circular working curve. Said pinion intermeshes with a toothed rack (5) arranged on a piston (4), causing a particular embodiment of the working curve and the teeth (9) of the toothed rack (5), adapting to an involute toothing of the pinion (6). The invention aims to improve the closing delay in order to obtain an optimum movement sequence of the piston (4) in the housing (2) of the door-closing element (1).

Description

Title: Hydraulic swing door operator

description

The invention relates to a hydraulic rotary vane drive with a pump driven by an electric motor.

EP 0 662 185 B1 describes a swing door drive consisting of a drive unit and a door closer. The door closer has a closer shaft on which a pinion meshing with a rack of a piston is arranged in a rotationally fixed manner. The piston is supported on a closer spring. The drive unit consists of an electric motor, which drives a spindle via a gearbox, on which a carriage is linearly displaceable. When the electric motor is actuated, the carriage rotatably mounted on the spindle displaces the piston against the force of the closing spring and against the force of a return spring displacing the carriage when the electric motor is not energized. The electric motor thus only effects the opening process of the door, while the closing process is effected exclusively by the door closer, including a medium that hydraulically controls the closing process.

The swing door drive according to US Patent 409,961 uses a pneumatically operated cylinder, the piston rod of which acts on a rack with an S-shaped rolling curve when the door is opened, which meshes with a pinion arranged on the door, the axis of rotation of which runs coaxially with the axis of rotation of the door. The door is closed by a spring pushing back the piston of the cylinder in its initial position.

Furthermore, manually operable slide rail closers are known, in which a piston guided in the housing and supported against a closing spring is provided, a pinion arranged on the closer shaft meshing with a toothed rack of the piston.

The aforementioned slide rail closers, also known as pinion closers, have the advantage over conventional door closers that that they have no linkage that projects freely into the room, but only an actuating arm that lies flat against the door frame or door leaf. However, they suffer from the disadvantage that the actuating arm lying flat on the door frame or door leaf in conjunction with the conventional, symmetrical pinion mechanism leads to an unfavorable force curve on the door. There is therefore a desire for an optimal design of the pinion so that the pinion on the assigned rack and thus the piston in the piston housing runs as smoothly and smoothly as possible during the opening and closing process of the door.

In known door closers, centrally or eccentrically mounted pinions are used.

A door closer with an eccentrically mounted pinion has become known from EP 0 856 628 A1, the toothing of the toothed rack forming a linear rolling line running at an angle between 4.5 ° and 7.2 ° to the direction of movement of the piston. The choice of the angle depends on the size of the door closer or the force of the closing spring. An optimal, especially low-friction and shock-free run of the pinion teeth on the rack is not guaranteed due to the eccentric bearing of the pinion and the linear course of the rack.

A comparable solution using a toothed rack which runs linearly at an angle is described in US Pat. No. 633,682.

An eccentrically mounted pinion is also shown in DE 36 45 313 C2 and DE 36 45 314 C2 using a rolling curve arranged on the pinion with different lever arms to the axis of rotation. The pitch curve of the assigned rack is correspondingly curved.

In a door closer known from DE 82 17 72 C2 or French patent application 96 69 45, the closer shaft is connected to an eccentrically mounted elliptical gear that meshes with an oblique rack on the piston side. By means of the elliptical gearbox, due to the different long lever arms of the elliptical see gear reaches a gear ratio to a certain extent adapted to the desired torque curve.

The pneumatic door closer according to US 1,359,144 has a circular, eccentrically mounted pinion, which meshes with an odd toothed rack on the piston. The circular pinion is provided with a regular toothing on a circular Wälzkuπte, with the eccentric bearing different lever arms are effective.

Various configurations of a piston drive for door closers are described in DE 36 38 353 A1, EP 0 207 251 A2, DE 94 12 64 and US 2,933,755, in connection with eccentrically or centrally mounted pinions - possibly with the interposition of a translating pinion - the closing spring is acted upon directly by means of a crank mechanism.

Centrally mounted pinions are known from EP 0 056 256 A2 and from EP 0 350 568. EP 0 056 256 A2 is concerned with a door closer, the piston of which has two mirror-symmetrically opposite toothed racks, a centrally mounted pinion in the closed position with shortened teeth engaging in both toothed racks of the piston.

The door closer according to EP 0 350 568 has a centrally mounted pinion which has teeth with a progressively increasing tooth height which extend over the circumference and which engage between the rods of a correspondingly curved toothed rack.

DE 44 44 131 A1 and DE 44 44 133 A1 disclose essentially centrally mounted pinions of a drive for a door or a window, the pinion itself having toothing over approximately half its circumference, the teeth of which are arranged on and on lever arms of different lengths a correspondingly curved roller tooth of a rack. The object of the invention is, during the opening process of the door by a rotary leaf drive, the closing process of the connected door should not be effected by the rotary leaf drive, but by an energy storage (power transmission unit) z. B. a door closer should be realized to dispense with the mechanical action of a piston of a door closer used. The aim is to optimize the movement of the piston of the door closer during the opening and closing process within the door closer housing by means of a special design of the pinion and the toothed rack of a door closer that works independently with respect to the opening drive, ie in particular a jam-free and therefore low-friction process to ensure the pinion on the piston rack. By using a pinion with a suitable rolling curve, the manufacturing costs of the pinion are to be minimized, whereby a longer rack life and a higher efficiency should be achieved by a special design of the rack compared to known racks due to the desired low friction, which enables the use of a weaker closing spring. Furthermore, an improvement in the closing characteristics of the door closer is also to be achieved by an improvement in the oil exchange from the piston chamber to the spring chamber during the closing process. The aim is also to create a small, inexpensive swing door operator.

The invention solves this problem with the teaching of claims 1 to 3.

According to the invention, either a device is used which essentially consists of individual modules, such as a door closer, motor, pump or of an overall unit, which contains a motor-pump unit and a power transmission unit in one housing, the power transmission unit functioning as a Door closer can perform. In the case of the power transmission unit or the door closer, a toothed rack or its teeth are optimally adapted to the course of a toothing of a pinion, taking into account its eccentric bearing and its circular rolling curve, so that a smooth transition to the next tooth in each case when opening is guaranteed as well as during the closing process. This applies in particular to the area of the pinion which exceeds the rotation by 180 °.

If a separate door closer is used, it preferably has a one-sided axis exit, the axis exit being used to connect a lever which interacts with a slide rail via a slide. The motor-pump unit can be flanged to the door closer either directly or indirectly. Furthermore, it is conceivable to use a corresponding mounting plate here, which allows the individual modules, such as. B. Door closers, gearbox and motor pump, individually attachable to ensure flexible replacement in the event of a defect in individual modules.

In addition, it is also possible to accommodate the above-described individual modules, such as door closers, motors and pumps, in one overall block, in which case the internal structure of the door closer and that of the power transmission unit can look the same or have the same effect.

A hydraulic force is applied to the piston of a door closer used during the opening process. This means that a toothed rack in the piston interacts with a pinion on the output shaft of the door closer. The hydraulic force for moving the piston of the door closer is z. B. generated by a motor-pump unit, which initiates the opening process of the connected door based on a sensor signal. The individual components of the swing door drive, such as. B. Door closer, motor, pump, etc. can be delivered modular or as a unit.

It has proven to be advantageous to design the toothed rack in such a way that its flank angles on the opening side of the teeth rise substantially up to half the length of the toothed rack and are subsequently designed to be essentially constant or falling. The sloping course leads in particular to an improvement in the low-friction. The rotation of the pinion from the closed position to the maximum open position can be more or less than approximately 180 ° without adversely affecting the required efficiency. Here, however, it is essential that the closing-side tooth flanks arranged in the area adjacent to 180 °, the opening direction of which are angled or rounded off last teeth of the rack.

In principle, any tooth shapes can be used in an embodiment of the invention; d. H. the pinion and / or the rack can have teeth with straight, angled or convexly curved tooth flanks. However, it has proven to be advantageous - in particular also for manufacturing reasons - to assign the toothed rack essentially a straight toothing and the pinion an involute toothing.

In order to achieve an optimization of the closing characteristic, the invention also includes an improvement in the oil exchange between the piston spaces separated by the piston.

Depending on the area of application of the swing door operator, different closing phases can be assigned to the closing process of the connected door. This can e.g. B. two or four closing phases with different speeds of the door leaf. As very comfortable B. proved four closing phases.

The closing process then comprises four closing phases, each closing phase being assigned a closing angle in a manner known per se, including a certain tolerance. Through the longitudinal groove arranged in the piston skirt, both the first and the third closing phase can be controlled by means of a single valve, so that the achievable low-friction running of the pinion on the rack is supported by an advantageous configuration of the oil exchange from the piston chamber to the spring chamber during the closing process , whereby a valve usually required for the third closing phase can be dispensed with. Such a swing door operator is to be regarded as an opening aid, the closing process of the door z. B. is effected by the door closer described above. It should be noted that a door closer that is equipped with a cam disc can also be used.

The invention is explained in more detail below with the aid of a schematically illustrated possible exemplary embodiment.

Show it:

Figure 1: A schematic front view of a hydraulic rotary leaf drive.

Figure 2: A vertical section through a closer housing.

Figure 3: The section along the line A-A according to Figure 1.

Figure 4: A top view of the piston with two end positions of the

Pinion.

Figure 5 - 7: Three phases of a course of the pinion on a rack.

Figure 8-11: In a schematic representation four positions of the piston during the closing delay.

Figure 12: A second execution of a closing delay.

FIG. 1 shows the schematic illustration of a hydraulic swing door drive 100, the drive device being arranged on a door leaf 101 and a slide rail 102 on a door frame 103 in the exemplary embodiment shown. The drive device has an electric motor 104 and a pump 105. The hydraulic medium supplied by the pump 105 passes through a valve 106 into a pressure chamber 107 located in the image plane on the left next to a piston 4, not shown in FIG. 1, and displaces the piston 4 during the opening process of the door leaf 101 in the image plane against the force of a closing spring 3 to the right. At the same time, the liquid located in a spring chamber 18 flows back into a compensation line 108 a suction area 109 of the puncture 105. When the piston 4 is acted upon previously, a pinion 6, which is not shown in FIG Axis D of rotation of pinion 6 arm 111 mounted in a rotationally fixed manner. When the electric motor 104 is de-energized, the closing spring 3 returns the piston 4 to its starting position, the hydraulic fluid being compensated in turn via the compensating line 108.

According to FIGS. 2 to 7, the piston 4, on which the closing spring 3 acts, is guided in a housing 2 of a door closer 1. As can be seen from FIGS. 3 and 4, the piston 4 has a toothed rack 5 which meshes with a pinion 6 having a toothing 7. The pinion 6 is mounted eccentrically in the area of a central longitudinal axis designated 23 in the axis of rotation designated D, the center M of the pitch circle of the pinion 6 being offset in the direction of the rack 5 in the closed position of the pinion 6 shown in FIG In the open position shown in FIG. 4, the center M of the pitch circle of the pinion 6 is offset in opposite directions. The rolling curve of the pinion 6 is circular. The teeth of the toothed rack 5, generally designated 9, have tooth flanks on the opening side and tooth flanks on the closing side, the tooth flanks 8 on the closing side (see FIG. 4) of the last two teeth 9 being angled. The tooth flanks of the remaining teeth 9 have a straight course. The aforementioned measure ensures that when the piston 4 moves in the direction of the arrow X (opening direction) when the pinion 6 runs on the rack 5 also in the area in which the pinion 6 has slightly exceeded the rotation by 180 ° (see closed position of the pinion 6 in FIG. 4) there is a low-friction engagement of the involute toothing 7 in the teeth 9 of the rack 5. The pitch curve of the rack 5 is moreover adapted to the eccentric mounting of the pinion 6 and accordingly has a slight S-shaped course, with all teeth 9 of the rack 5 having different flank angles on the opening side and on the closing side. Positions 4 and 6 of the pinion 6 are shown separately in FIGS. 4 shows the closed position, ie with the door closed, namely the position of the piston 4 and the pinion 6. The pinion 6 is located in the right area of the recess of the piston 4. The axis of rotation D is located on the central longitudinal axis 23. If the piston 4 is now moved in the opening direction (arrow direction X), the pinion 6 rotates about the Axis of rotation D. Due to the eccentricity of the pinion 6, a position approximately in the central region, which corresponds to a specific door opening position, can be seen from FIG. Due to the running of the pinion 6 on the rack 5, the piston 4 has moved further in the opening direction.

An end position of the pinion 6, which corresponds to the maximum opening side of the door, which is not shown, is shown in FIG. 6. These three FIGS. 4 to 6 make the course of the eccentrically mounted pinion with involute toothing very clear, and at the same time the constant engagement of the teeth 7 of the pinion 6 in the rack 5 with its teeth 9 can be seen.

As shown in FIG. 2 and FIGS. 8 to 11 in particular, three regulating valves 11, 12 and 13 serving for the closing delay are arranged in the housing wall 10 of the door closer 1, the function of which is explained below with reference to FIGS. 8 to 11. For the sake of completeness, it should be pointed out that instead of the door closer 1, another device can also be used, e.g. B. a power transmission unit, which may have the same or equivalent internal structure as a door closer or slide rail door closer.

During the start of the closing process according to FIG. 8, the piston 4 passes over an oil drain line 14, which is connected via a line 19 to the regulating valve 11 and a line 20 to a piston chamber 24. The oil emerging from the piston chamber 24 can pass into the spring chamber 18 via a longitudinal groove 16 in a piston jacket 15 and a radial bore 17 in the piston 4. The lines 25, 21 and 22 assigned to the regulating valve 12 lie on a different plane.

BESTATIGUNGSKOPIE As shown in FIG. 7, the longitudinal groove 16 has passed over the line 14, so that oil can only pass from the piston chamber 24 to the spring chamber 18 due to the play between the piston 5 and the housing wall 10, which results in a strong delay in the closing speed (second phase of the closing delay) ,

In the third phase of the closing delay, the oil in turn passes from the piston chamber 24 via the line 20 and the same regulating valve 11 and the lines 19 and 14 into the region of an overflow edge of the piston 4, not shown, in the spring chamber 18. Since this is the same Valve 11 is acting, the closing speed is the same in the first and third deceleration phases.

In the fourth phase of the closing delay (beginning of the closing area), the line 20 of the valve 11 leading to the piston chamber 24 is closed; the oil from the piston chamber 24 passes through the line 25, the regulating valve 12, the line 21 and the line 22 via the abovementioned overflow edge into the spring chamber 18. The regulating valve designated 13 is usually closed during the closing delay; However, there is the possibility of reducing the delay period by correspondingly opening this valve during the second closing phase (in which an oil exchange only takes place via the leakage between the piston and the housing wall), the oil emerging from the piston chamber 24 being throttled via the line 26 the regulating valve 13, the line 27 and the line 28 is passed into the spring chamber 18.

FIG. 12 shows a variant with regard to the oil drain lines and the valves for controlling the closing process. In this variant, only two different closing phases are implemented, so that a modification compared to the four closing phases shown above is possible. Only valves 11 and 12 are required for this. The oil drain line 19 is continued and merges into an oil drain line 29, which ends behind the overflow edge of the piston 4 in the region of the toothed rack 5, which is not shown in any more detail. In addition to the two exemplary embodiments described above with regard to different closing phases of the connected doors, it is of course also possible in the course of the invention to implement a different number of closing phases with different closing speeds.

BESTATIGUNGSKOPIE LIST OF REFERENCE NUMBERS

1 slide rail closer

2 housing 3 closing spring

4 pistons

5 rack

6 sprockets

7 involute toothing 8 tooth flanks on the closing side

9 teeth of the rack

10 housing wall

11 regulating valve

12 regulating valve 13 regulating valve

14 Oil drain line

15 piston skirt

16 longitudinal groove

17 radial bore 18 spring chamber

19 Oil drain line

20 oil drain line

21 Oil drain line

22 Oil drain line 23 Central longitudinal axis

24 piston chamber

25 oil drain line

26 Oil drain line

27 Oil drain line 28 Oil drain line

29 Oil drain line 100 swing door operator

101 door leaf

102 slide rail

103 door frame

104 electric motor

105 pump

106 valve

107 pressure chamber

108 compensation line

109 suction area

110 slider

111 arm

M center of the \ N

D axis of rotation of the Ri

X direction of arrow in open

BESTATIGUNGSKOPIE

Claims

Patent claims

1. Hydraulic rotary door drive (100) with a pump (105) driven by an electric motor (104), which has a piston (4) guided in a housing (2) of a door closer (1) against the force of a piston (4) mounted in a spring chamber (18). Closing spring (3) is acted upon, with a compensating line (108) provided between the spring chamber (18) and the pump (105), with a pinion which is rotatably mounted eccentrically in the housing (2) of the door closer (1) and has a circular rolling curve ( 6), which meshes with a rack (5) of the piston (4), with a center point M of the rolling curve relative to an axis of rotation D of the pinion (6) in the closed position in the direction of the rack (5) and in the open position relative to the axis of rotation D is offset in opposite directions, characterized by the following features: the pinion (6) has teeth (7); the rack (5) is designed as a rack profile and the closing-side tooth flanks (8) of the last teeth (9) in the opening direction (arrow X) are angled; the teeth (9) of the rack (5) are arranged on an S-shaped rolling curve, with the rolling curve rising essentially up to half the length of the rack and then falling down, starting from the closed position, all teeth (9) of the rack (5) have different flank angles on the opening side and closing side, the opening-side flank angle of the teeth (9) increases essentially up to half the length of the rack (5) and then runs essentially the same; the closing-side flank angle of the teeth (9) drops essentially to about half the length of the rack (5) and then rises; the tooth tip width of the teeth (9) increases essentially up to half the length of the rack (5) and then descends, the rotation of the pinion (6) from the closed position to the maximum opening position is more than 180 °, the rotation of the pinion (6) exceeding 180 ° The closing-side tooth flanks (8) of the last teeth (9) assigned to the pinion (6) in the opening direction (arrow has a closing delay.

2. Hydraulic rotary vane drive (100) with a pump (105) driven by an electric motor (104), which has one in one

The piston (4) guided in the housing (2) of a door closer (1) is acted upon against the force of a closing spring (3) mounted in a spring chamber (18), with a compensation line (108) provided between the spring chamber (18) and the pump (105). , with a pinion (6) which is rotatably mounted eccentrically in the housing (2) of the door closer (1) and has a circular rolling curve and which meshes with a toothed rack (5) of the piston (4), with a center point M of the rolling curve opposite an axis of rotation D of the pinion (6) in the closed position in the direction of the rack (5) and in the open position is offset in opposite directions relative to the axis of rotation D, characterized by the following features, the rack (5) is designed as a rack profile and the closing-side tooth flanks (8) of The last teeth (9) are angled in the opening direction (arrow X), the teeth (9) of the rack (5) are arranged on an S-shaped rolling curve, the rolling curve e rising essentially up to half the length of the rack (5) and then falling down, starting from the closed position Teeth (9) of the rack (5) have different flank angles on the opening side and closing side, the opening-side flank angle of the teeth (9) increases essentially to about half the length of the rack (5) and then descends, the closing-side flank angle of the teeth ( 9) essentially drops to about half the length of the rack (5) and then increases, the tooth tip width of the teeth (9) increases essentially to about half the length of the rack (5) and then decreases, the rotation of the pinion ( 6) from the closing position to the maximum opening position is more than 180°, the closing side tooth flanks (8) assigned to the area of the pinion (6) exceeding 180°, the last teeth (9) of which are angled in the opening direction (arrow X) and the piston (4) in the housing (2) is guided with a closing delay by means of at least one regulating valve (11, 12, 13).

Hydraulic rotary door drive (100) with a pump (105) driven by an electric motor (104), which has a piston (4) guided in a housing (2) of a door closer (1) against the force of a closing spring mounted in a spring chamber (18).

(3), with a compensating line (108) provided between the spring chamber (18) and the pump (105), with a rotatably mounted eccentrically in the housing (2) of the door closer (1). geared, a circular rolling curve pinion (6), which meshes with a rack (5) of the piston (4), a center point M of the rolling curve opposite a rotation axis D of the pinion (6) in the closed position in the direction of the rack (5 ) and in the opening position is offset in opposite directions relative to the axis of rotation D, characterized by the following features, the rack (5) is designed as a rack profile, the closing side tooth flanks (8), the opening direction (arrow X) of which last teeth (9) are angled or convex are curved, the teeth (9) of the rack (5) are arranged on an S-shaped rolling curve, each starting from the closed position: the rolling curve essentially up to half the length of the

Rack (5) is designed to rise and then slope down, all teeth (9) of the rack (5) have different flank angles on the opening side and closing side, the opening-side flank angle of the teeth (9) essentially increases to approximately half the length of the rack (5) and The following is essentially the same, the closing-side flank angle of the teeth (9) drops essentially to about half the length of the rack (5) and then increases, the rotation of the pinion (6) from the closing position to the maximum opening position is less as approximately 180°, the closing side tooth flanks (8) assigned to the area of the pinion (6) approaching 180°, the opening direction (arrow the housing (2) is guided with a closing delay by means of at least one regulating valve (11, 12, 13).

4. Rotary wing drive according to one of claims 1 to 3, characterized in that the pinion (6) and / or the rack (5) have teeth with straight, angled or convexly curved tooth flanks.

5. Rotary vane drive according to one of claims 1 to 4, characterized in that the pinion (6) has involute toothing (7).

6. Rotary wing drive according to claims 1 to 3, characterized in that by different arrangement of oil drain lines (19, 20, 21, 22, 25, 26, 27, 28, 29) and the regulating valves (11, 12, 13) different closing characteristics can be realized.

7. Rotary wing drive according to claims 1 to 3, characterized in that the regulating valves (1 1, 12, 13) are arranged in a housing wall (10) of the housing (2), with at least one of the regulating valves (11, 12, 13) two closing phases are assigned.

8. Rotary wing drive according to claims 1 to 7, characterized in that the closing process comprises four phases of the closing delay, wherein using the regulating valves (11, 12), the first regulating valve (11) has both a first closing phase between approximately 180 ° and 100 ° as well as a third closing phase between approximately 70° and 20° with the same closing speed, while the second regulating valve (12) controls the fourth closing phase between approximately 20° and 0° and in the second closing phase between approximately 100° and 70° function of both

Control valves (11, 12) are canceled.

9. Rotary wing drive according to one or more of the preceding claims, characterized in that an oil drain line (14) of the first regulating valve (11) opens in the first phase of the closing delay into a longitudinal groove (16) arranged in a piston jacket (15), which via a spring chamber side

The longitudinal groove (16) delimiting the radial bore (17) of the piston (4) is connected to the spring chamber (18).

10. Rotary vane drive according to one or more of the preceding claims, characterized in that the oil drain line (14) opens into an oil drain line (19), which is connected via the regulating valve (11) to the oil drain line (20), which flows into a piston chamber (24 ) ends.

11. Rotary wing drive according to one or more of the preceding claims, characterized in that in the second phase of the closing delay, pressure equalization from the piston chamber (24) to the spring chamber (18) is possible due to a play between the piston (5) and the housing wall (10). is.

12. Rotary wing drive according to one or more of the preceding claims, characterized in that in the third closing phase the oil from the piston chamber (24) via the oil drain line (20), the regulating valve (1 1) and the oil drain lines (14, 19) and a The overflow edge of the piston (5) enters the spring chamber (18).

13. Rotary vane drive according to one or more of the preceding claims, characterized in that in a fourth phase of the closing process the oil drain line (20) is closed and the oil from the piston chamber (24) via the oil drain line (25), the regulating valve (12) and the oil drain lines (21 and 22) and via the overflow edge into the spring chamber (18).