EP2112315A2 - Door closer with a hydraulic closing delayer - Google Patents

Abstract

The door closer (1) has a closer shaft (2) connected to a cam (4) in a housing (3) acting with a tapping element fitting in a hydraulic damping device with piston (5). The cam sector acting with the tapping element has an angled sector which causes an increased stroke of the hydraulic piston to increase oil expulsion to slow down the closing of the door panel.

Description

The present invention relates to a door closer with a hydraulic closing delay according to the closer defined in the Oberbergriff of claim 1 Art.

A generic door closer is from the patent DE 42 39 219 C2 known. This is designed as an automatic door closer for one-sided doors, which comprises a can be coupled to a door closer shaft, which is rotatable from a closed position in a rotational direction and within the housing with a Hubkurvenscheibe non-positively and positively connected. The Hubkurvenscheibe cooperates with a roller which is located in or on a longitudinally movable spring energy accumulator, which acts on a, forming a working pressure spring. The interior of the door closer housing has two pressure chambers separated by a hydraulic piston, which are connected to one another by channels for differently throttled outflow of the pressure medium from the pressure chamber, which is smaller when the door leaf closes, and by a non-return valve which also opens in an opening movement of the door leaf.

In or on the spring energy storage, a rotatably mounted roller is arranged, wherein further on the oil displacing hydraulic piston, a second roller is arranged, which roll over each section via the Hubkurvenscheibe. If the door is opened, then either directly or via a linkage the Hubkurvenscheibe is set in rotation. Due to the contour of the Hubkurvenscheibe the compression spring of the spring force accumulator is compressed, so that stored in the spring energy storage work.

This work is used to automatically close the door leaf after opening. For this, the compression spring presses against the working piston, wherein the standing in contact with the Hubkurvenscheibe role is rotatably mounted in the working piston. The hydraulic piston, however, serves to dampen the rotational movement of the door leaf, wherein the speed of the rotary movement, in particular the closing movement of the door leaf, can be adjusted via a throttle valve arrangement.

In such automatic door closers, the problem arises that in particular in room doors, such as hotels, an opening of about 90 °, and the door immediately after opening again performs the closing movement. However, this self-closing should be reversible for a short period, for example, to be able to pass through the room door with suitcases. For reasons of fire safety, it is not permissible for door leaves to be provided with a mechanical fixation that is not coupled to the fire protection system. Electromagnetic locking devices, however, are very expensive and require an additional smoke switch.

A delay in the closing movement of the door leaf after complete opening is therefore desirable, so that the door can be passed without having to actively hold the door.

Furthermore, door closers are known which can produce a closing delay with additional throttle valves. This closing delay can affect the entire or only partial sections of the opening angle of the door closer. A limited closing delay over an opening angle of z. B. only 70 ° - 90 ° is thus very difficult to achieve. Another disadvantage is the expensive and elaborate holes, so that the oil between the pressure chambers on the or the additional throttle valves can flow back and forth. Since these small throttle valves tend to clog relatively quickly, since smallest particles Deposited in the channels or valve seats, the reliability of this solution is very limited. If valve assemblies are provided with corresponding small control gaps to cause the closing delay over portions of the opening angle, they can pollute, so that the damping function is adversely affected. Thus, the longevity of such damping devices via control column does not provide a satisfactory solution.

It is therefore the object of the present invention to provide a door closer with a hydraulic closing delay, which has a simple design and allows a long and maintenance-free operating life.

This object is achieved on the basis of a door closer according to the preamble of claim 1 in conjunction with its characterizing features. Advantageous developments of the present invention are specified in the dependent claims.

The invention includes the technical teaching that cooperating with the tapping element contour portion of Hubkurvenscheibe has an angular portion which causes a relative to the angle of rotation of the Hubkurvenscheibe increased stroke of the hydraulic piston to increase the oil displacement to create a delay in the closing movement of the door leaf.

With the angle section according to the invention in the Hubkurvenscheibe is achieved that when sweeping the angle of rotation of the Hubkurvenscheibe by the Abgriffselement the hydraulic piston based on the rotation angle performs an increased stroke. In this case, the Hubkurvenscheibe with a first roller in operative connection, which rolls over the Hubkurvenscheibe and is reciprocally against a compression spring of a spring force accumulator in communication and received in a working piston is, wherein the tapping element is formed of a second roller, and wherein the first roller and the second roller with the associated piston are arranged opposite to the Hubkurvenscheibe opposite. Alternatively, the tapping element can also consist of a sliding tappet, which is in sliding contact over the contour of the Hubkunrenscfleibe.

The angle section is designed such that an increased increase of the angle α between H1 and H2 is introduced into the contour to increase the ratio of the stroke of the hydraulic piston relative to the angle of rotation of the door leaf. Only when the second roller is in contact with the remaining contour section of the lifting cam disk in front of the angle section H1 to H2 can the door leaf close at normal closing speed. This can be made possible without additional valve arrangement and thus without additional control column, since the stroke information of the hydraulic piston is stored with the increased stroke directly on the Hubkurvenscheibe and thus no clogging small control column on the valve assemblies by dirt, etc. can take place. Thus, the door closer according to the invention is cheaper and more reliable than the door closer with the same function according to the prior art, since expensive and pollution-prone valve arrangements can be dispensed with here.

According to an advantageous development of the cam disc, this has an active cam track and a passive cam track, wherein the active cam track is brought into operative connection with the first roller and the passive cam track with the second roller. The angle section H1 - H2 is formed as a contour section within the passive curved path. The active curved path forms the active portion of the Hubkurvenscheibe, which causes the closing force on the door leaf together with the spring energy storage. The portion of the passive curved path, however, is in operative connection with the hydraulic damping device, so that the second roller rolls over the passive curved path and causes the required stroke in the oil-displacing hydraulic piston. The design of the passive curved path can be done independently of the active curved path, since the shape of the passive curved path does not affect the torque curve of the door closer, but only the closing delay and thus the time course of the closing process.

According to the prior art, door closers have a flat, uniform stroke over the entire range of rotation of the door, with the result that the hydraulic control of the flow rates of the volume flow of the hydraulic oil via different throttle positions of several valves. So z. B. the closing delay in the angular range of 90 ° - 70 ° controlled by a separate valve. For the normal closing range of 70 ° -5 ° another valve is arranged and for the final impact range of 0 ° -5 ° again provided an additional valve. Each of these valves can be arranged in a separate hydraulic bore or be controlled by bypasses. According to the invention, it is possible to design a hydraulic end impact control by appropriate design of the passive curve in that is positioned in the rotation of the end stop by a concentric to the axis arranged circle segment with zero stroke. Thus, several door closing sections with different closing speed can be generated with only a single regulating valve without feedback to the torque curve (opening and closing).

An advantageous development of the invention is that the angle section H1 - H2 is introduced on such a portion in the passive curved path, which corresponds to an opening angle of the door leaf of 50 ° to 100 °, and preferably, however, from 70 ° to 90 °. Depending on the specific design of the door, the door can usually be opened up to 90 °, whereby larger opening angles are possible. For example, if the door leaf is open up to 70 ° or even 90 °, The second roller initially rolls over a conventionally formed contour of the cam disc in the area of the passive curved path. In the transition to the angle section H1 - H2, however, the lifting movement of the hydraulic piston experiences an acceleration even with a uniform rotational movement of the door leaf, since the radius of the Hubkurvenscheibe from hub H1 to Hub H2 decreases sharply. Thus, the oil-displacing hydraulic piston continues to approach the axis of rotation of the cam disc. If the door is open, for example, at 90 ° and is released by the user, then the second roller rolls back in the rearward direction over the angle section according to the invention from H2 to H1, where H2 describes the small radius and H1 the maximum radius of the cam disc. In this case, the hydraulic piston must displace a disproportionately increased stroke and consequently an increased amount of hydraulic fluid, which causes a slowing down or delaying the closing movement of the door leaf. If the opening angle of the door leaf reaches a value, for example of 70 °, the second roller has overcome the maximum stroke H1 and can roll over the uniformly formed remaining passive curved path up to the closed position H0.

It is further contemplated that the cam disc is rotatable about an axis of rotation and the passive cam track with respect to the axis of rotation comprises a maximum stroke radius (Rmax), which forms the transition of the passive cam track in the angular section H1 - H2 and is greater than the maximum stroke radius of the active curved track. The maximum stroke radius within the cam plate thus forms a cam geometry over which the second roller must roll, wherein the hydraulic piston performs the correspondingly increased stroke movement. Therefore, it is further provided that the angle section H1 - H2 has within the passive curved path to form a saddle contour in the direction of the axis of rotation facing concave contour. As a result, the movement behavior of the door leaf is influenced within the range of the closing delay, with increasing training of the saddle contour the Slowing down the closing movement of the door is not uniform and a maximum delay in the lower range, for example, at 70 °. Thus, the door closes from 90 ° to 70 ° with a slowdown, with the minimum closing speed being about 74 °. If the door has fallen below 70 °, then there is a uniform and non-delayed closing movement, as is known in conventional door closers.

Advantageously, the hydraulic piston adjoins a rear pressure chamber filled with hydraulic oil, which communicates fluidically with the front pressure chamber via a throttle valve. The cam disc is received in the front pressure chamber, which is separated only by the hydraulic piston of the rear pressure chamber. If the hydraulic piston moves in the direction of the rear pressure chamber, this is reduced in volume, whereas the front pressure chamber increases in volume equally. The displaced from the rear pressure chamber hydraulic oil flows through the throttle valve in the front pressure chamber, wherein the adjustment of the flow cross-section in the throttle valve causes the damping effect of the movement of the hydraulic piston. The throttle valve may be arranged in the housing of the door closer, wherein an arrangement within the hydraulic piston itself is possible.

According to an advantageous development of the door closer according to the invention, it is further provided that in the rear pressure chamber between the housing and the hydraulic piston there is an auxiliary pressure spring which presses the second roller against the passive cam track of the Hubkurvenscheibe. The auxiliary spring has no effect on the damping behavior of the hydraulic piston, since this is only stiff enough so that the spring pushes the hydraulic piston toward the front pressure chamber to fill the rear pressure chamber in the return movement of the hydraulic piston again with pressure oil.

According to possible embodiments of the door closer, it may be designed as a slide rail door closer, as a top door closer, as a floor door closer or as a frame door closer. The exact installation position of the door closer and the execution of the door closer with respect to the operative connection of the closer shaft with the door is therefore not a limitation of the present invention, so that the Hubkurvenscheibe can also be located directly on the axis of rotation of the door leaf, and the door closer without linkage with the door leaf connected is. The active curved path is designed in a conventional manner such that over the entire angle of rotation, over which the first roller is in contact with the curved path, a constant closing force can be generated.

A further advantageous embodiment can be achieved in that the door closer is arranged in a door frame or in a door leaf. This results in a solution that is invisible to the user, which can be incorporated into any design of a possible interior design, eg. B. in hotels, inserts.

According to an advantageous development, the closer shaft of the door closer z. B. via a slide rail linkage or a scissors linkage with a door frame or a door leaf are in operative connection. About the linkage type of closing torque curve of the cam gear as a function of the mounting, z. B. on the tape or Gegenbandseite be influenced.

Further, measures improving the invention are specified in the subclaims or will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS.

Figur 1:

eine schematische Querschnittsansicht des erfindungsgemäßen Türschließers,

Figur 2:

eine schematische Darstellung der Hubkurvenscheibe, welche im Bereich der passiven Kurvenbahn gezeigt ist,

Figur 3:

eine Draufsicht auf die Hubkurvenscheibe, wobei der Bereich der aktiven Kurvenbahn und der Bereich der passiven Kurvenbahn gekennzeichnet ist und

Figur 4:

ein Diagramm des Hubverlaufes des Hydraulikkolbens über dem Winkel der Türöffnung von der Schließstellung H0 bis über den Winkelabschnitt H1 - H2.

These show in:

FIG. 1:

a schematic cross-sectional view of the door closer according to the invention,

FIG. 2:

2 is a schematic representation of the cam disc shown in the region of the passive cam track.

FIG. 3:

a plan view of the Hubkurvenscheibe, wherein the area of the active cam track and the area of the passive cam track is characterized and

FIG. 4:

a diagram of the Hubverlaufes of the hydraulic piston over the angle of the door opening from the closed position H0 to over the angle section H1 - H2.

The in Fig. 1 schematically illustrated door closer 1 has a closer shaft 2, which is rotatably received in a housing 3. With the closer shaft 2 is a Hubkurvenscheibe 4 rotationally connected, wherein the closer shaft 2 in turn is rotationally connected to a door, which is damped by the door closer 1 in its closing movement. The housing 3 is filled with a damping medium, which is usually a hydraulic oil. In the housing 3, a first piston, which forms the working piston 8, are arranged within the area filled with oil. A second piston forms the hydraulic piston 5, wherein between the working piston 8 and the hydraulic piston 5 Hubkurvenscheibe 4 is arranged.

If the Hubkurvenscheibe 4 set in rotation by the door is opened and the closer shaft 2 performs a rotational movement, so is the contour of the co-rotating Hubkurvenscheibe 4 both the working piston 8 and the hydraulic piston 5 is set in stroke.

The working piston 8 is connected to a compression spring 7 in operative connection, so that it forms a spring energy store in conjunction with the compression spring 7. In the working piston 8, a first roller 6 is rotatably mounted, which is in contact with the outer contour of the Hubkurvenscheibe 4. The assumed direction of rotation about an axis of rotation 12 of the Hubkurvenscheibe 4 is shown by an arrow, so that when the Hubkurvenscheibe 4 is rotated in the direction of rotation, the first roller 6 rolls over a portion of Hubkurvenscheibe 4, which is characterized by the active curved path 10. The active curved path 10 is designed in such a way that the radius of the active curved path 10 increases continuously relative to the axis of rotation 12. Thus, the working piston 8 moves in the direction of the compression spring 7 and compresses them. Consequently, a work is stored in the compression spring 7, which can initiate the subsequent closing movement of the door leaf. Shown is the first roller 6 in a detent position, which is formed by a concave portion within the Hubkurvenscheibe 4.

If the lifting cam 4 rotates in the direction of the arrow, then a second roller 9, which is rotatably received within the hydraulic piston 5, can roll over the curved section of the lifting cam 4, which is formed by the passive curved track 11. In this case, the hydraulic piston 5 moves in the direction of the axis of rotation 12, since the radius of the passive curved path 11 is slightly reduced relative to the axis of rotation 12. Due to the inventive contour of the passive cam track 11, however, the lifting movement of the hydraulic piston 5 is not uniform based on the rotational movement of Hubkurvenschelbe 4. Thus, the hydraulic piston 5 at an opening movement of the door, and thus during a rotational movement of the Hubkurvenscheibe 4 in the illustrated direction of rotation a lifting movement carries out, an auxiliary compression spring 16 is provided within the rear pressure chamber 13, which is supported between the housing 3 of the door closer 1 and the hydraulic piston 5.

The hydraulic piston 5 is limited by a rear pressure chamber 13 and a front pressure chamber 15. During the opening movement, the hydraulic piston 5 moves in the direction of the axis of rotation 12 and opens the volume of the rear pressure chamber 13 so that it increases. At the same time, the volume of the front pressure chamber 15 decreases, so that the hydraulic oil, which is located both in the rear pressure chamber 13 and in the front pressure chamber 15, can flow over a hydraulic line 17. Within the hydraulic line 17, a throttle valve 14 is used, which forms a flow constriction in order to dampen the lifting movement of the hydraulic piston 5 accordingly. The throttle valve 14 may be formed as a one-way valve, so that the overflow of the hydraulic oil from the front pressure chamber 15 into the rear pressure chamber 13 is not or only slightly damped. However, if the door leaf executes a closing movement, then the hydraulic piston 5 again moves in the direction of the rear pressure chamber 13 and reduces the volume. In this case, the damping effect of the throttle valve 14 can be used, so that the return movement of the hydraulic piston 5 in the direction of the rear pressure chamber 13 is made more difficult. Depending on the formed contour of the passive cam track 11, the return movement of the hydraulic piston 5 can either be accelerated or slowed down. If the return movement accelerates, an increased resistance of the closing movement of the door leaf is the consequence, since the increased stroke of the hydraulic piston 5 emphasizes an increase in the oil displacement and thus uses the closing delay according to the invention.

In FIG. 2 a section of Hubkurvenscheibe 4 is shown, which forms the passive cam track 11. Within the passive curved path 11, an inventive angle section H1 - H2 is formed, which extends over the angle α.

The first part of the passive cam track 11 initially extends from the closed position H0 to the beginning of the angular section H1. Shown is also the second roller 9, which is in contact with the first part of the passive cam track 11. If the second roller 9 rolls over this section of the passive curved path 11, an enlarged stroke of the hydraulic piston, which runs uniformly with the rotational movement of the lifting cam 4, takes place. If the contact of the second roller 9 reaches the position H1, the radius profile of the passive curved path 11 changes such that the radius drops from a maximum radius Rmax to a minimum radius which lies at the end of the angular section H2. Thus, the hydraulic piston performs a significantly increased stroke movement for opening the rear pressure chamber, so that when the Hubkurvenscheibe 4 initiates the closing movement of the door, the displacement of the pressure oil is significantly increased by the hydraulic piston from section H2 to section H1. Thus, the closing delay according to the invention of the door leaf is achieved, this being achieved only via the specially designed contour of the passive curved path 11.

Fig. 3 shows the subdivision of Hubkurvenscheibe 4 in the passive cam 11 and the active cam track 10. The direction of rotation about the rotation axis 12 is not set directly for the Hubkurvenscheibe 4, according to the present embodiment, the Hubkurvenscheibe 4 invention is provided for door leaves, which has a one-sided opening from about 90 °.

Fig. 4 shows a schematic representation of the stroke H over the door opening angle TÖ in a diagram. The stroke H of the hydraulic piston starts at a stroke H0, which represents the closed position of the door leaf. The stroke from an opening angle, starting at 0 ° to about 70 °, is represented by the course of the stroke from H0 to H1. The significantly increased stroke of H1 - H2 becomes out of the curve clearly, with respect to the axis of rotation 12 (see Fig. 3 ) the stroke H2 is smaller than the stroke H1. The dashed further course of the stroke represents door opening angles greater than 90 °. The diagram shows that the ratio of the stroke over the angle section H1 - H2 is large compared to the stroke from H0 to H1. The stroke is proportional to the required transport of the pressure oil from the rear pressure chamber into the front pressure chamber, so that the effect of the closing delay from the diagram becomes clear.

The present invention is not limited in its execution to the above-mentioned preferred embodiment. Rather, a number of different embodiments of a door closer is possible, which may be designed as Gleitschienentürschließer, as upper door closer, as a floor door closer or as a frame door closer.

LIST OF REFERENCE NUMBERS

1

door closers

2

closer shaft

3

casing

4

cam disc

5

hydraulic pistons

6

first role

7

compression spring

8th

working piston

9

second role

10

active curved track

11

passive curved path

12

axis of rotation

13

rear pressure chamber

14

throttle valve

15

front pressure chamber

16

Auxiliary spring

17

hydraulic line

H0

closed position

H1 - H2

angle section

Rmax

maximum stroke radius

α

angle

TÖ

doorway

H

Stroke of the hydraulic piston

Claims (12)

Door closer (1) with a closer to a door can be coupled to the turntable shaft (2) which is rotatable from a closed position in at least one direction of rotation and connected to a housing (3) Hubkurvenscheibe (4), which cooperates with at least one tap element, which is in communication with a hydraulic damping device and is received in an oil-displacing hydraulic piston (5),
characterized,
in that the contour section of the cam disc (4) cooperating with the tapping element has an angular section (H1-H2) which, based on the angle of rotation of the cam disc (4), causes an enlarged stroke of the hydraulic piston (5) to increase the oil displacement, thereby delaying the closing movement of the door leaf above the angle section (H1-H2). Door closer (1) according to claim 1, characterized in that the Hubkurvenscheibe (4) with a first roller (6) is operatively connected, which rolls over the Hubkurvenscheibe (4) and against a compression spring (7) of a spring energy store in a liftable connection and is received in a working piston (8), wherein the tapping element is formed from a second roller (9), and the first roller (6) and the second roller (9) with the associated piston (5, 8) with respect to the Hubkurvenscheibe ( 4) are arranged opposite one another. Door closer (1) according to claim 1 or 2, characterized in that the Hubkurvenscheibe (4) one with the first roller (6) in operative connection active cam track (10) and one with the second Roller (9) operatively connected passive cam track (11), wherein the angle portion (H1-H2) forms a contour portion of the passive cam track (11). Door closer (1) according to one of claims 1 to 3, characterized in that the angle section (H1-H2) is introduced on a portion in the passive curved path (11), the opening angle of the door leaf of 50 ° to 100 °, preferably from 70 ° to 90 ° corresponds. Door closer (1) according to one of the preceding claims, characterized in that the Hubkurvenscheibe (4) about an axis of rotation (12) is rotatable, and the passive cam track (11) relative to the axis of rotation (12) comprises a maximum stroke radius (Rmax), which forms the transition of the passive curved path (11) into the angular section (H1-H2) and is greater than the maximum stroke radius of the active curved path (10). Door closer (1) according to one of the preceding claims, characterized in that the angle section (H1-H2) within the passive curved path to form a saddle contour has a concave contour pointing in the direction of the axis of rotation (12). Door closer (1) according to one of the preceding claims, characterized in that the hydraulic piston (5) adjoins a rear pressure chamber (13) filled with hydraulic oil, which is connected to the front cam chamber (15) receiving the cam disc (4) via a throttle valve (14) ) communicates fluidically. Door closer (1) according to one of the preceding claims, characterized in that in the rear pressure chamber (13) between the housing (3) and the hydraulic piston (5) a Hiffsdruckfeder (16) which presses the second roller (9) against the passive cam track (11) of the Hubkurvenscheibe (4). Door closer (1) according to one of the preceding claims, characterized in that the active curved path (10) is designed such that over the rotation angle (H0 to H2), a constant closing force can be generated. Door closer (1) according to one of the preceding claims, characterized in that the door closer (1) is designed as Gleitschienentürschließer, as overhead door closer, as a floor door closer or as a frame door closer. Door closer (1) according to one of the preceding claims, characterized in that the door closer (1) is arranged in a door frame or in a door leaf. Door closer (1) according to one of the preceding claims, characterized in that the closer shaft (2) of the door closer (1) via a slide rail linkage or a scissor linkage with a door frame or a door leaf is in operative connection.

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