EP1362157A1

EP1362157A1 - Electromechanical hinged wing drive

Info

Publication number: EP1362157A1
Application number: EP02704705A
Authority: EP
Inventors: Jürgen HOMBERG
Original assignee: Dorma Deutschland GmbH
Current assignee: Dorma Deutschland GmbH
Priority date: 2001-02-13
Filing date: 2002-02-11
Publication date: 2003-11-19
Also published as: PL362522A1; US20040064917A1; CA2434572A1; DE10107051A1; US7051403B2; JP2004518839A; WO2002064932A1; MXPA03002227A; CZ20031817A3; DE10107051C2; RU2287651C2; JP3987799B2; SK8442003A3; RU2003109433A

Abstract

The invention relates to an electromechanical hinged wing drive comprising a door closer (1) with an eccentric pinion (6) that has a circular pitch circle and that intermeshes with a toothed rack (5) that is mounted on the piston (4). The invention is further characterized in that the pitch circle and the teeth (9) of the toothed rack (5) are adapted to the teeth of the pinion (6). In order to obtain an optimum displacement of the piston (4) in the housing (2) of the door closer (1) the design of the closing delay is improved.

Description

Title: Electromechanical swing door operator

description

The invention relates to an electromechanical swing door drive with a door closer.

DE 41 24 282 C2 describes an electromechanical swing door drive in which an electric motor - possibly with the interposition of a clutch - drives a transmission which is connected directly or with the interposition of a gear train to a closer shaft of a door closer. The door closer can be designed as a slide rail door closer. Since the electric motor acts directly on the closer shaft of the door closer via a gear train or several gear trains, additional pulse generators, timers, detectors and limit switches controlling the electric motor are required to achieve the required opening and closing characteristics.

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 toothed pinion arranged on the closer shaft meshing with a toothed rack of the piston.

The above-mentioned slide rail closers, also known as pinion closers, have the advantage over conventional door closers that they have no linkage that projects freely into the room, but only an actuating arm lying flat against the door frame or door leaf, which interacts with a slide that can be moved in a slide rail , 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 associated rack and pinion runs as smoothly and smoothly as possible during the opening and closing process of the door to achieve the piston in the piston housing, which also corresponds to an ideal torque curve.

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, which leads to jumps in the curve of the moments.

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 pitch 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. Due to the different long lever arms of the elliptical gearwheel, a translation adapted to the desired torque curve to a certain extent is achieved by means of the elliptical gear.

The pneumatic door closer according to US Pat. No. 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 regular teeth on a circular pitch curve, where with different lever arms due to the eccentric bearing.

Various configurations of a piston drive in door closers are described in DE 36 38 353 A1, EP 0 207 251 A2, DE 94 12 64 and US 2,933,755, whereby in connection with eccentrically or centrally mounted pinions - optionally with the interposition of a translating pinion - by means of a Crank drive is a direct action on the closing spring.

Centrally mounted pinions are known from EP 0 056 256 A2 and from EP 0 350 568 A2. 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 A2 has a centrally mounted pinion, which has teeth with a progressively increasing tooth height that extend over the circumference and 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 pitch curve of a rack.

The object of the invention is to use a electromechanical drive for the opening process of the connected door, the closing process not to be realized by the electromechanical drive but by an energy store (power transmission unit) to create a small and inexpensive swing door drive which demanded opening and closing characteristics as guaranteed with a sliding arm door closer, ie the movement of the piston of the door closer during the opening and closing process within the To optimize the door closer housing, ie in particular to ensure a pinch-free and therefore low-friction running of the pinion on the rack of the piston. The use of a pinion with a suitable rolling curve is intended to minimize the manufacturing costs of the pinion, with a special design of the toothed rack compared to known toothed racks due to the desired low friction to achieve a longer service life and higher efficiency, which enables the use of a weaker closing spring , In an embodiment of the invention, an improvement in the closing characteristics of the slide rail closer is to be additionally achieved by an improvement in the oil exchange from the piston chamber to the spring chamber during the closing process.

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 of a door closer, transmission and motor or a whole which contains a motor, a transmission and a power transmission unit in a housing, the power transmission unit including the functions of a door closer. think. In the case of the power transmission unit or the door closer, a 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 during the opening and the closing process is guaranteed. 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 two-sided axle outlet, one axle outlet being used to connect a lever that interacts with a slide rail via a slide, and the opposite axle outlet is used with a power transmission element in a manner known per se with the transmission a corresponding motor is connected. The gearbox can be attached to the door closer either directly or indirectly. be flanged. Furthermore, it is conceivable to use a corresponding mounting plate here, which allows the individual modules, such as. B. Door closer gear and motor can be designed individually 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, gearboxes and motors, in one overall block, where the internal structure of the door closer and that of the power transmission unit can look the same or have the same effect. 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 falling 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. However, it is essential here that the closing-side tooth flanks arranged in the region adjacent to 180 °, the opening direction of which are the last teeth of the toothed rack, are angled or rounded.

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 sequence 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, 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 realized by the door closer described above. A door closer, which is equipped with a cam disc, can also be used, but much higher powers are required for the drive motor, which would inevitably lead to an increase in price and an increase in the rotary leaf drive.

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 an electromechanical 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. FIGS. 5-7: three phases of a running of the pinion on a toothed rack; FIGS. 8-11: a schematic representation of four positions of the piston during the closing delay.

Figure 12: A second possibility of delayed closing.

Figure 1 shows the schematic representation of an electromechanical swing door operator 100, wherein in the illustrated embodiment, a drive device on the door leaf 111 and a slide rail 109 are arranged on a door frame 110. The drive has an electric motor 102 acting on a gear 101. A transmission output shaft 103 is connected to an axis of rotation D of a pinion 6 not shown in FIG. 1 (see FIG. 4) via a gear train 104 designed as a chain, cable or toothed belt. According to FIGS. 2 to 4, the pinion 6 is guided in the piston 4, also not shown in FIG. 1, which is loaded by a closing spring 3 arranged in a spring chamber 18. On the axis of rotation D of the pinion 6, a free end 106 of an arm 105 engages in a rotationally fixed manner, the other free end 107 of which is guided in the slide rail 109 by means of a slide piece 108. It goes without saying that, given suitable spatial conditions, the slide rail 109 can be arranged on the door leaf 111 and the drive on the door handle 110.

According to FIGS. 2 to 7, the piston 4, on which a closing spring 3 acts, is guided in a housing 2 of a door closer 1. As can be seen in FIGS. 3 and 4, the piston 4 has a toothed rack 5 which meshes with the pinion 6 which has an involute toothing 7. The pinion 6 is mounted eccentrically in the region of a central longitudinal axis designated 23 in the axis of rotation designated D, wherein in the closed position of the pinion 6 shown in FIG. 3 the center M of the pitch circle of the pinion 6 is offset in the direction of the rack 5 and in the The center position M of the pitch circle of the pinion 6 shown in FIG. 4 is offset in the opposite direction. The rolling curve of the pinion 6 is circular. The teeth of the 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 last two teeth 9 are 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 °, A low-friction engagement of the involute toothing 7 in the teeth 9 of the rack 5 takes place. The rolling 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, i. H. with the door closed, namely the position of the piston 4 and the pinion 6 again. 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, the constant engagement of the teeth 7 of the pinion 6 in the rack 5 with its teeth 9 being recognizable at the same time.

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 noted that instead of the door closer 1 also another device can be used, e.g. B. a power transmission unit that has 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 a 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.

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 aforementioned 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 takes place only 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 regulation Lierventil 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 the valves 11 and 12 are necessary 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.

LIST OF REFERENCE NUMBERS

1 door 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 gearbox

102 electric motor

103 transmission output shaft

104 gear train

105 arm

106 free end

107 free end

108 slider

109 slide rail

110 door frame

111 door leaf

M center of the Wälzkre

D Pinion rotation axis

X arrow direction in opening;

Claims

claims

1. Electromechanical rotary leaf drive (100) with one over

Gear (101) driven by an electric motor (102), rotatably mounted eccentrically on a housing (2) of a door closer (1) or a suitable power transmission unit, having a circular rolling curve and having a toothed rack (5) in the housing (2) guided, against a closing spring (3) supported piston (4), whereby a center point (M) of the pitch curve with respect to an axis of rotation (D) of the

Pinion (6) is offset in the closed position in the direction of the rack (5) and in the open position with respect to the axis of rotation (D), characterized by the following features, the pinion (6) has a toothing (7); the rack (5) is designed as a rack profile and the closing 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 pitch 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 fall, all teeth (9) of the rack (5) have different flank angles on the opening and closing sides, the flank angle on the opening side of the teeth (9) rises substantially up to half the length of the rack (5) and follows essentially the same, the closing flank angle of the teeth (9) drops substantially up to half the length of the toothed rack (5) and subsequently increases, the tooth head width of the teeth (9) essentially up to half

The length of the rack (5) increases and then declines, the rotation of the pinion (6) from the closed position to the maximum open position is more than 180 °, the tooth flanks (8) of the closing teeth (8) of the last teeth (9) in the opening direction (arrow X) assigned to the area of the pinion (6) exceeding 180 ° are angled and the piston (4) is guided in the housing (2) by means of at least one regulating valve (1 1, 12, 13) with a closing delay.

2. Electromechanical rotary leaf drive (100) with a pinion (6) having a circular rolling curve and driven eccentrically on a housing (2) of a door closer (1) or a suitable power transmission unit via a gear (101) by an electric motor (102) which meshes with a toothed rack of a piston (4) which is guided in the housing (2) and is supported against a closing spring (3), with a center point (M) of the pitch curve in the direction of a closed axis relative to an axis of rotation (D) of the pinion (6) on the rack (5) and in the open position opposite to the axis of rotation (D), characterized by the following features, the pinion (6) has a toothing (7); the rack (5) is designed as a rack profile and the closing 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 pitch curve , where, starting from the closed position, the pitch curve is designed to rise up to half the length of the toothed rack (5) and then decreases, all teeth (9) of the toothed rack (5) have different flank angles on the opening side and on the closing side, the flank angle of the teeth (9) on the opening substantially increases approximately up to half the length of the toothed rack (5) and then falls off, the flank angle of the teeth (9) on the closing side essentially drops approximately up to half the length of the toothed rack (5) and then increases runs, the tooth head width of the teeth (9) increases substantially up to half the length of the rack (5) and then decreases, the rotation of the pinion (6) from the closed position to the maximum open position is more than 180 °, the The area of the pinion (6) assigned to the pinion (6) which exceeds 180 °, the opening direction (arrow X) of the last teeth (9) being angled and the piston (4) in the housing (2) by means of at least one regulating valve (11, 12, 13) is performed with a delay.

3. Electromechanical swing leaf drive (100) with one over

Gear (101) driven by an electric motor (102), rotatably mounted eccentrically on a housing (2) of a door closer (1) or a suitable power transmission unit, and having a circular rolling curve, which is connected to a rack and pinion in the housing ( 2) guided piston (4), supported against a closing spring (3), whereby a center point (M) of the pitch curve with respect to an axis of rotation (D) of the pinion (6) in the closed position in the direction of the rack (5) and is offset in the opening position opposite to the axis of rotation (D), characterized by the following features, the rack (5) is designed as a rack profile, the closing tooth flanks (8), the opening direction (Arrow X) last teeth (9) are angled or convexly curved, the teeth (9) of the rack (5) are arranged on an S-shaped pitch curve, each starting from the closed position: the pitch curve essentially up to is designed to rise to half the length of the rack (5) and then to decrease, all teeth (9) of the rack (5) have different flank angles on the opening and closing sides, the flank angle on the opening side of the teeth (9) essentially up to half the length of the rack ( 5) rises and then follows a substantially constant course, the closing flank angle of the teeth (9) drops substantially up to half the length of the toothed rack (5) and then rises, the rotation of the pinion (6) from the closed position to the maximum open position is less than about 180 °, with the closing-side tooth surfaces assigned to the region of the pinion (6) approximating 180 ° Anken (8), the opening direction (arrow X) last teeth (9) of the rack (5) are angled, and the piston (4) in the housing (2) by means of at least one

Control valve (11, 12, 13) is performed with a delay.

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

Have tooth flanks.

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

6. Rotary vane 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 locking characteristics can be realized.

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

8. Rotary leaf drive according to claims 1 to 7, characterized in that the closing process comprises four phases of the closing delay, using the regulating valves

(11, 12) the first regulating valve (1 1) controls both a first closing phase between approximately 180 ° and 100 ° and 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 controls between approximately 20 ° and 0 ° and in the second closing phase between approximately 100 ° and 70 ° the function of both regulating valves (1 1, 12) is canceled.

9. Rotary vane drive according to one or more of the preceding claims, characterized in that an oil drain line

(14) of the first regulating valve (11) in the first phase of the closing delay opens into a longitudinal groove (16) arranged in a piston jacket (15), which also has a radial bore (17) of the piston (4) delimiting the longitudinal groove (16) on the spring chamber side the spring chamber (18) is connected.

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 in a piston chamber (24) opens.

11. Rotary leaf drive according to one or more of the preceding claims, characterized in that in the second phase of the closing delay a pressure equalization from the piston chamber (24) to the spring chamber (18) due to a game between the

Piston (5) and the housing wall (10) is possible.

12. Rotary leaf 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 (11) and the oil drain lines (14, 19) and one Overflow edge of the piston (5) reaches 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 over the overflow edge into the spring chamber (18).