EP1362155A1

EP1362155A1 - Sliding rail door-closing device

Info

Publication number: EP1362155A1
Application number: EP02719797A
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
Anticipated expiration: 2022-02-11
Also published as: US20040074145A1; ATE295928T1; RU2288334C2; MXPA03002228A; PL362555A1; AU2002250913B2; DE10107046C2; WO2002064926A1; US7024725B2; CA2434577A1; EP1362155B1; DE50203139D1; ES2242849T3; DE10107046A1; JP2004518838A; CZ20031796A3; SK8392003A3

Abstract

This invention relates to an overhead door closer with slide arm assembly having a toothed pinion that is eccentrically supported and presents a circular rolling curve, which pinion meshes with a toothed rack arranged at a piston. The invention concentrates on a particular embodiment of the rolling curve and of the teeth of the toothed rack in adaptation to a toothing of the pinion. Furthermore, the invention concentrates on an improved embodiment of the delayed closing operation in order to achieve an optimized movement pattern of the piston within the housing of the overhead door closer with slide arm assembly.

Description

Title: Slide rail door closer

description

The invention relates to a slide rail door closer with a guided in a housing, supported against a closing spring piston, with an eccentrically rotatably mounted on the housing, meshing with a rack of the piston toothed pinion, which has a circular pitch curve, the center of which relative to the axis of rotation of the pinion in the Closing position in the direction of the rack and in the opening position opposite to the axis of rotation is offset.

The above-described slide rail door closers, also referred to as pinion closers, have the advantage over conventional door closers that they do not have a linkage that projects freely into the room, but rather only an actuating arm that lies flat against the door frame or door leaf. However, they have 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 in order to achieve the least possible frictionless and shock-free running of the pinion on the associated rack and thus of the piston in the piston housing during the opening and closing process of the door.

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

A door closer of the type mentioned at the beginning with an eccentrically mounted pinion has become known from EP 0 856 628 A1, the toothing of the toothed rack being a linear rolling line running at an angle between 4.5 ° and 7.2 ° to the direction of movement of the piston forms. 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 running of the teeth of the pinion on the rack is due to the eccentric bearing of the pinion and the linear course of the rack is not guaranteed, there are jumps in the course of the curves 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 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 gearwheel which meshes with an oblique rack on the piston side. Due to the different long lever arms of the elliptical gearwheel, a translation adapted to a certain extent to the desired torque curve 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 toothing on a circular pitch curve, whereby different lever arms are effective 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 racks that are diametrically opposed in mirror image, one centrally mounted Pinion in the closed position with shortened teeth engages in both 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 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 pitch curve of a rack.

The object of the invention is to optimize the movement of the piston of the slide rail door closer during the opening and closing process within the door closer housing, d. H. 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, 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 , In an embodiment of the invention, an improvement in the closing characteristic of the slide rail door 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 according to claims 1, 3 and 4.

According to the invention, 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 pitch curve, so that a smooth transition to the next one in each case Tooth is guaranteed during both the opening and the closing process. This applies in particular to the area of the pinion which exceeds the rotation by 180 °. It has proven to be advantageous to design the opening-side flank angle of the teeth, the toothed rack to rise essentially up to half the length of the toothed rack and then to follow a substantially constant or decreasing course, the falling course contributing 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 negatively affecting the required efficiency. It is essential that the closing tooth flanks arranged in the area adjacent to 180 °, the last teeth of the rack in the opening direction, are angled or rounded.

Further features of the invention are characterized by the subclaims.

In principle, any tooth shape 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.

Furthermore, the invention includes an improvement in the closing characteristics by an improvement in the oil exchange.

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. Due to 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 low-friction running of the pinion on the rack that can be achieved with the features a) - d) is achieved by an advantageous configuration of the oil exchange is supported from the piston chamber to the spring chamber during the closing process, it being possible to dispense with a valve which is usually required for the third closing phase.

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

Show it:

Figure 1: A vertical section through a door closer housing.

Figure 2: The section along the line A-A according to Figure 1.

Figure 3: A top view of the piston with two end positions of the pinion.

Figure 4-6: Three phases of the course of the pinion on a rack.

Figures 7-10: In a schematic representation four positions of the piston during the closing delay.

Figure 11: A second execution of the closing delay.

According to Figures 1 to 6, a piston 4 is guided in a housing 2 of a slide rail door closer 1, on which a closing spring 3 acts. As can be seen in FIGS. 2 and 3, the piston 4 has a toothed rack 5 which meshes with a 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. 2, a center point M of the pitch circle of the pinion 6 is offset in the direction of the rack 5 and In the open position shown in FIG. 3, the center M of the pitch circle of the pinion 6 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 (see FIG. 3) of the last two teeth 9 being of angled design. The tooth flanks of the remaining teeth 9 have zen 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 toothed 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. 3) 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 otherwise 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, as can be seen from FIGS is that show the course of the pinion on the rack in three phases.

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.

As shown in FIG. 1 and FIGS. 7 to 10 in particular, three regulating valves 11, 12 and 13 serving to delay the closing are arranged in the housing wall 10 of the slide rail door closer 1, the function of which is explained below with reference to FIGS. 7 to 10.

During the start of the closing process according to FIG. 7, 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 through a longitudinal groove 16 in the piston skirt 15 and a radial bore 17 in the piston 4 pass into the spring chamber 18. The lines 25, 21 and 22 assigned to the regulating valve 12 lie on a different plane.

As shown in FIG. 8, 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 delayed).

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 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 regulating valve 13, the line 27 and the line 28 are passed into the spring chamber 18.

FIG. 11 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 goes into an oil drain line 29, which ends behind the not specified overflow edge of the piston 4 in the region of the rack 5.

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 to implement a different number of closing phases with different closing speeds.

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 M center of the pitch circle of the pinion

D Pinion rotation axis

X Direction of arrow in opening direction

Claims

claims

1. Slide rail door closer (1) with a piston (4) guided in a housing (2), supported against a closing spring (3), with an eccentrically rotatably mounted on the housing (2), with a

Rack (5) of the piston (4) meshing, toothed pinion (6), which has a circular Wälzkuπ / e, the center (M) relative to the axis of rotation (D) of the pinion (6) in the closed position in the direction of the rack ( 5) and in the open position opposite to the axis of rotation (D), characterized by the following features:

a) the toothed rack (5) is designed as a toothed rack profile, its tooth flanks (8) on the closing side of the last teeth (9) in the opening direction (arrow X) being angled or convexly curved; b) the teeth (9) of the rack (5) are arranged on an S-shaped Wälzkun e, each starting from the closed position: the rolling curve substantially up to half

Length of the rack (5) is increasing and then decreasing; 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 essentially remains the same; the flank angle of the teeth (9) on the closing side essentially drops to approximately half the length of the toothed rack (5) and then increases in the course; the tooth head width of the teeth (9) increases essentially up to half the length of the toothed rack (5) and then decreases; c) the rotation of the pinion (6) from the closed position to the maximum open position is more than 180 °, the tooth flanks (8) on the closing side which are assigned to the area of the pinion (6) exceeding 180 ° being the last in the opening direction (arrow X) Teeth (9) of the rack (5) are angled; d) that the piston (4) is guided in the housing (2) by means of at least one regulating valve (11, 12, 13) with a closing delay.

2. Sliding rail door closer (1) with a piston (4) guided in a housing (2) and supported against a closing spring (3), with an eccentrically rotatably mounted on the housing (2), with a rack (5) of the piston (4) combing, toothed pinion

(6), which has a circular rolling point, the center (M) of which is offset relative to the axis of rotation (D) of the pinion (6) 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:

a) the rack (5) is designed as a rack profile, the closing tooth flanks (8) in the opening direction (arrow X) last teeth (9) are angled or convexly curved; b) the teeth (9) of the rack (5) are arranged on an S-shaped Wälzkuπ e, each starting from the closed position: the Wälzkun / e essentially rising to about half the length of the rack (5) and then falling is; 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 side

Rises substantially 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 drops essentially up to half the length of the toothed rack (5) and then increases in the course; the width of the tooth head of the teeth (9) increases substantially up to half the length of the toothed rack (5) and then falls off; c) 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 in the opening direction (arrow X) assigned to the area of the pinion (6) exceeding 180 ° (9) the rack (5) are angled; d) that the piston (4) is guided in the housing (2) by means of at least one regulating valve (11, 12, 13) with a closing delay.

3. Slide rail door closer (1) with a piston (4) guided in a housing (2) and supported against a closing spring (3), with a piston which is rotatably mounted eccentrically on the housing (2) Rack (5) of the piston (4) meshing, toothed pinion (6), which has a circular pitch curve, the center (M) of which is opposite the axis of rotation (D) of the pinion (6) in the closed position in the direction of the rack (5) and is offset in the open position opposite to the axis of rotation (D), characterized by the following features:

a) the toothed rack (5) is designed as a toothed rack profile, its tooth flanks (8) on the closing side of the last teeth (9) in the opening direction (arrow X) being angled or convexly curved; b) the teeth (9) of the toothed rack (5) are arranged on an S-shaped rolling curve, starting from the closed position: the rolling curve essentially up to about half

Length of the rack (5) is increasing and then decreasing; 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 essentially increases somewhat up to half the length of the toothed rack (5) and then essentially remains the same; the flank angle of the teeth (9) on the closing side

Essentially drops to about half the length of the rack (5) and then rises; c) the rotation of the pinion (6) from the closed position to the maximum open position is less than about 180 °, the tooth flanks (8) of the closing side assigned to the 180 ° approximated area of the pinion (6) of the teeth direction (arrow X) last teeth (9) of the rack (5) are angled; d) that the piston (4) is guided in the housing (2) by means of at least one regulating valve (11, 12, 13) with a closing delay.

4. Slide rail door closer 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. Slide rail door closer according to one of claims 1 to 4, characterized in that the pinion (6) has an involute toothing (7).

6. Slide rail door closer 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), at least one of the regulating valves (1 1, 12, 13 ) two closing phases are assigned.

7. Slide rail door closer according to one or more of the preceding claims, characterized in that the closing process comprises four phases of a shooting delay, the first using two regulating valves (11, 12)

Regulating valve (11) 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 between approximately 20 ° and 0 ° and in the second closing phase between - solve

between about 100 ° and 70 ° the function of both regulating valves (11, 12) is canceled.

8. Slide rail door closer 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 skirt (15), which Is connected to the spring chamber (18) via a radial bore (17) of the piston (14) delimiting the longitudinal groove (16) on the spring chamber side.

9. Slide rail door closer 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 is in a piston chamber (24 ) flows out.

10. Slide rail door closer according to one or more of the preceding claims, characterized in that in the second phase of the closing delay, a pressure equalization of the

Piston chamber (24) to the spring chamber (18) is possible due to play between the piston (5) and the housing wall (10).

11. Slide rail door closer according to one or more of the preceding claims, characterized in that in the third

Closing phase the oil from the piston chamber (24) passes through the oil drain line (20), the regulating valve (11) and the oil drain lines (14, 19) and an overflow edge of the piston (5) into the spring chamber (18).

2. Slide rail door closer 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), through the regulating valve (12 ) and the oil drain lines (21) and (22) and over the overflow edge into the spring chamber (18).