EP0841452B1 - Door closer with an energy storage device for closing the door wing - Google Patents

Abstract

The mechanism comprises a straight or curved spring bar (51) which is subjected to compression, tension and-or torsional load. The bar is mounted between two supporting components (5a,5b). There can be several roughly parallel bars, preferably inclined to a common central axis, and so arranged that the sum of the radial forces in relation to this axis acting on the supporting components is minimal and preferably zero. The bars can be mounted symmetrically in relation to the axis. They can be inclined to each other, and of different thicknesses and-or lengths. They can be at different radii from the component centres.

Description

The invention relates to a door closer with an energy store according to the Preamble of claim 1.

DE 195 42 050 A1 describes a door closer for a door with a door leaf known, with a single energy storage device for closing the door leaf, is designed softer than a closer spring, with the energy store at Opening movement of the door leaf at least partially loaded and when Closing is at least partially discharged, and wherein a device for Setting the closing and / or opening speed is provided, for. B. a hydraulic or pneumatic damping device with piston-cylinder unit. The energy store can be on torsion or axially on train or Be stressed and has a non-linear characteristic when opening and / or when closing.

It could be disadvantageous that the characteristic curve is not so easy to adapt.

Door closers with a closer spring as an energy store are also known, e.g. hydraulic door closers, in which the closer spring with a piston-cylinder unit interacts. The piston-cylinder unit is via a gearbox connected to the closer spring, which directly or via a power transmission linkage is connected to the door. Such door closers are e.g. described in DE-OS 36 38 353. In practice with such Closer springs used in door closers have conventional linear Spring characteristics, i.e. the spring force increases proportionally over the spring stroke. In Usually helical compression springs are used.

In order to obtain a suitable torque characteristic on the door, one with increasing door opening angle, decreasing moment is a special one power transmission linkage between the closer shaft and the door required. When using a sliding arm linkage between the closer shaft and the closer spring a power transmission switched, which varies over the door opening angle Gear ratio, e.g. a cam gear or a Pinion gear with non-round pinion. The resulting torque characteristic on the Door is due to the geometry and size of the linkage, or the dimensions of the transmission in connection with the structural conditions of the Door closer housing limited.

Closer springs are also known which are designed as torsion springs, e.g. as a coil spring in DE-OS 41 00 335, as a spiral spring in DE-OS 32 02 930, or as a torsion bar spring in DE-OS 44 26 274.

Also known is a spring with a non-linear spring characteristic, the one Combination of several different partial springs, the fixed interconnected partial springs are each at an angle to each other. This Spring is complex to manufacture and each has one of the partial springs dependent torque characteristic.

The object of the invention is to provide a door closer of the type mentioned create that is simple and compact and also has a good moment history supplies.

The object is achieved in that the energy storage for Closing the door leaf supported at least one between two support elements Has spring body, the spring body being linear or curved is rod-shaped. The spring body is subjected to axial pressure or tension and / or axially subjected to pressure or tension and torsion.

In special embodiments, several spring bodies of the same length are parallel, or arranged almost parallel to one another, preferably opposite one another common central axis inclined and arranged symmetrically around this.

When loading or unloading the energy store, the support elements in be moved against each other in the axial direction and / or rotated against each other. The energy store has a non-linear characteristic.

In addition, the spring bodies become elastic as a result of the charging or discharging process bent and / or twisted. The bending direction and the maximum bending of the Spring body can be specified by a guide device. Farther it is possible to unload the spring body to influence the characteristic Preload the state of the energy storage.

One of the two support elements can be rotatably mounted. When loading the Energy storage is counter to the force by rotating the support element a return spring reaches an additional total stroke, the loading process here, too, takes place solely by a pure lifting movement. For further Increasing the stroke, several energy storage devices are cascaded in a row arranged.

In a special embodiment, the energy store replaces the closer spring of a conventional hydraulic door closer. He can do this through a Stroke movement of the piston can be compressed and loaded.

In a further embodiment, the energy store is replaced by a pure one Rotational movement of the support elements loaded at a constant distance. This embodiment is also suitable for use in door hinges.

Further features of the invention are listed in subclaims 5 to 37.

Figur 1

eine schematische Darstellung eines hydraulischen Türschließers mit hydraulischer Kolben-Zylinder-Einheit, wobei der Kolben mit einem erfindungsgemäßen Energiespeicher zusammenwirkt;

Figur 2

eine perspektivische Darstellung des Energiespeichers in Figur 1 im entladenen, spannungslosen Zustand;

Figur 3

eine schematische Darstellung eines hydraulischen Türschließers gemäß Figur 1, jedoch im geladenen Zustand des Energiespeichers;

Figur 4

ein Kraft-Weg-Diagramm des Energiespeichers in Figur 2;

Figur 5

eine alternative Ausführung des Energiespeichers in Figur 2 mit einer Führungsvorrichtung;

Figur 6

eine weitere Ausführungsform des Energiespeichers in Figur 2 mit einem drehbar gelagerten Stützelement;

Figur 7

eine schematische Darstellung mehrerer hintereinander angeordneter Energiespeicher;

Figur 8

eine alternative Ausführungsform eines Energiespeichers, welcher durch eine reine Drehbewegung der Stützelemente geladen wird;

Figur 9

eine Momentenkennlinie des Energiespeichers in Figur 8;

Figur 10

eine schematische Darstellung einer Dämpfungseinrichtung für einen Energiespeicher gemäß Figur 8;

Figur 11

eine schematische Darstellung eines mit einer herkömmlichen Schließerfeder gekoppelten Energiespeichers.

The invention is explained in more detail in the figures. It shows:

Figure 1

a schematic representation of a hydraulic door closer with hydraulic piston-cylinder unit, the piston cooperating with an energy store according to the invention;

Figure 2

a perspective view of the energy store in Figure 1 in the discharged, de-energized state;

Figure 3

a schematic representation of a hydraulic door closer according to Figure 1, but in the charged state of the energy store;

Figure 4

a force-displacement diagram of the energy store in Figure 2;

Figure 5

an alternative embodiment of the energy store in Figure 2 with a guide device;

Figure 6

a further embodiment of the energy store in Figure 2 with a rotatably mounted support element;

Figure 7

a schematic representation of a plurality of energy stores arranged one behind the other;

Figure 8

an alternative embodiment of an energy store, which is charged by a pure rotary movement of the support elements;

Figure 9

a torque characteristic of the energy storage in Figure 8;

Figure 10

a schematic representation of a damping device for an energy store according to Figure 8;

Figure 11

is a schematic representation of an energy store coupled to a conventional closer spring.

The exemplary embodiment shown in FIG. 1 is a hydraulic rack and pinion door closer, as it is in its basic structure in DE-OS 36 38 353 is described. In the closer housing, not shown is a hydraulic piston-cylinder unit with a guided in the cylinder 2 Piston 3 arranged. The subspace to the left of the piston 3 is Unpressurized space 2a and the partial space to the right of the piston are referred to as pressure space 2b. The piston 3 is a hollow piston with an internal rack 3a executed, which meshes with a pinion 4. The pinion 4 is rotatably with the closer shaft 1 aligned in the pinion axis.

When the door is opened, the closer shaft 1 rotates clockwise with the pinion 4, whereby the piston 3 in Figure 1 according to the direction of the arrow to the left is moved. During this movement, the piston 3 adjacent to the Unpressurized space 2a of the cylinder 2 compresses energy storage 5 and thus loaded. Conversely, the energy store 5 discharges when the Door and exerts a corresponding torque on the closer shaft via the pinion 4 1 off. The hydraulic oil located in the pressure chamber 2b of the cylinder applied with the piston pressure. Due to the adjustable flow rate of the hydraulic oil flowing into the pressure-free chamber 2a becomes a hydraulic damping of the closing movement realized.

In Figure 2, the energy storage 5 shown in Figure 1 is a perspective See view. Between two disc-shaped support elements 5a and 5b there are three linear, preferably metallic spring bodies 51 with a circular cross-sectional area and the same length in each case. Each of the support elements 5a, 5b has three on its side facing the spring bodies 51 Receiving holes 52 on. The spring bodies are in these receiving bores 52 51 introduced with their respective ends and stationary there, but not necessarily non-rotating, fixed. The support elements 5a and 5b are arranged so that the Receiving bores 52 are aligned with one another in the axial direction, thereby creating a parallel position of the spring body 51 is reached. In addition, the arrangement of the Spring body 51 symmetrically with respect to the central axis shown in dashed lines of the energy store 5

Figure 3 again shows a schematic representation of the hydraulic door closer 1, but in the charged state of the energy store 5. By the rotation of the closer shaft 1 and the resulting lifting movement the piston 3, the energy storage 5 was compressed. In the case of FIG indicated by arrows stroke movement h with their ends in the Support elements 5a and 5b bent spring body 51 bent. The Energy store 5 has the non-linear characteristic shown in FIG Spring force F over the spring stroke h. The characteristic curve results from that the rod-shaped spring body 51 is not in the relaxed initial state have it compressed immediately. This corresponds to a very high spring force minimal stroke. With the bending of the spring body 51 also increases Stroke, whereby the force to be applied is lower, the stronger the spring body 51 are bent.

However, the invention is not limited to the exemplary embodiment shown. Not only circular support elements 5a and 5b are conceivable, but e.g. elliptical, square or rectangular cross sections are also possible. The Support elements 5a, 5b also do not have to match the cross-sectional shape of the cylinder 2 be identical. They are only in their size by the dimensions of the Cylinder 2 limited.

It also applies to the spring body 51 that any cross-sectional shape and diameter possible are. In particular, the cross-sectional shape and the diameter of a spring body 51 also vary over its axial length.

Other design options relate to the number, arrangement and length the spring body 51. There are versions with four, five or more spring bodies 51 just as possible as applications with two or only one spring body 51. The spring body 51 can on the support element 5a, 5b in any Order, e.g. concentric, star-shaped, linear, etc. An arrangement symmetrical to the central axis of the energy store 5 is for minimizing the sum of the radial forces acting on the support element 5a, 5b an advantage, but not a prerequisite for the function of the energy storage 5. Likewise, the use of spring bodies of different lengths or Thickness possible.

The exemplary embodiment shown in FIG. 5 has an additional guide device 53 for the spring body 51 compared to the energy store 5 in FIG. For this purpose, a guide disk 5c is arranged centrally between the two support elements 5a and 5b, which has guide slots 54 for the spring bodies 51. The three slots 54 start together in the center of the guide disc 5c and run symmetrically radially outwards. One of the spring bodies 51 is passed through each of the slots 54, with each of the spring bodies 51 being located at the outer end of the corresponding slot 54 in the closed position of the door. The choice of the slot length allows the spring bodies 51 to be pre-bent when the door is closed. For this purpose, the slot length of the guide disc 5c is chosen to be shorter than the radial distance of the receiving bores 52 from the center of the support elements 5a and 5b. The pre-bending reduces the initial force F _A required when charging the energy store 5. In FIG. 4, this corresponds to driving through the spring characteristic from a point A further to the right of the original zero position.

The guide device 53 is used when charging the energy store 5 Bending direction and maximum bending predetermined for each of the spring bodies 51. With increasing bend, the spring body 51 inevitably migrate along the Slits 54 inwards until they meet in the center in the bent state. A further bend is then no longer possible, which means at the same time the maximum stroke of the piston 3 is limited and overextension of the spring bodies 51 is avoided. In alternative designs of the guide device 53 can the guide slots 54 are also arranged in a different manner, for example spirally his.

In the gear transmissions shown in Figures 1 and 3 are both versions with round as well as with non-round pinion 4 possible. With door closers With a conventional closer spring, the transmission is predominantly used a suitable torque ratio when opening and closing the door responsible. When using the energy store 5 according to the invention simpler gears are used, since the energy store 5 is already on has a characteristic curve that leads to favorable torque ratios. Due to the shape of the characteristic curve shown, it has a high initial force and only a small one Stroke is instead of a gear transmission with rack 31 and pinion 4 Use of a cam disk drive advantageous. The power transmission takes place while rolling over cam discs with one of the spring characteristic adapted geometry.

Another embodiment of the energy store 5 is shown in FIG. 6. In this example, too, there are three rod-shaped spring bodies 51 between two support elements 5a and 5b clamped. One of the two support elements 5a, in the Figure 5 is the left, is rotatably mounted in a rotary bearing 55, the Axis of rotation preferably with the central axis of the energy store 5 and the Axis of symmetry of the spring body 51 coincides. For how it works irrelevant which of the two support elements 5a, 5b is rotatably mounted. The energy store 5 reacts to a stroke caused by the piston 3 not only with a bend of the spring body 51, but also with one Rotational movement of the support element 5a in the bearing 55. The rotary bearing 55 works against the force of a return spring, not shown, for example a spiral spring which, when the energy store 5 is discharged, the rotary bearing 55 moved back to the starting position. Compared to the embodiment in Figure 5 can be a larger by using the additional pivot bearing 55 Achieve stroke.

A further increase in the total stroke while maintaining the spring force can be by the cascading shown in Figure 7. To do this, several Energy storage 5 in the cylinder 2 arranged one behind the other, with each Support elements 5a, 5b of the individual energy stores 5 lie against one another.

All previously shown embodiments of the invention work when loading the Energy storage 5 with an axial compression movement by the stroke of the Piston 3. In the embodiment shown in Figure 8, the energy storage 5, however, by a pure rotary movement w of the support elements 5b loaded, where D denotes the axis of rotation, which here preferably with the The central axis of the energy store 5 is identical. For example, the closer shaft 1 via a bevel gear with the support element to be rotated 5b couple. The distance s of the two support elements 5a, 5b remains at Charging and discharging the energy storage 5 constant.

In contrast to the previous exemplary embodiments, the receiving bores in FIG. 8 are 52 not aligned, i.e. the radial distance r one Spring body 51 from the center of the respective support element 5a, 5b is for the first support element 5a larger than for the second 5b. From the resulting Inclination of the spring body 51 results in that when charging the energy store 5 tangential forces and therefore also a torque on the support elements 5a, 5b act. In addition, the spring body 51 in the closed state Door an axial preload, which to reduce the distance s between leads the support elements 5a, 5b. With a set screw, with which the distance between the support elements 5a and 5b can be adjusted, the Characteristic curve can be influenced on site.

In a variant not shown, the spring body 51 is inclined in the closed state of the door by axially preloading the energy store 5 in combination with a rotation of the support elements 5a, 5b. The receiving bores 52 can certainly be aligned with one another.

1) der radiale Abstand r der Aufnahmebohrung 52 von der Mittelachse des Energiespeichers 5,

2) der Durchmesser d der Federkörper 51 und

3) der Neigungswinkel β der Federkörper 51, wobei der erste Schenkel des Winkels in der Längsachse des Federkörpers 51 liegt und der zweite Schenkel tangential zu einem um die Drehachse D konzentrischen Kreis durch den Abstützpunkt des Federkörpers 51 auf dem Stützelement 5a.

FIG. 9 shows the torque M over the angle of rotation w of the energy store 5 described in FIG. 8. This embodiment is characterized by a high initial torque at a small angle of rotation w and a non-linear characteristic. The characteristic curve can advantageously be set in the desired form by varying individual parameters. Influencing factors are:

1) the radial distance r of the receiving bore 52 from the central axis of the energy store 5,

2) the diameter d of the spring body 51 and

3) the angle of inclination β of the spring body 51, the first leg of the angle lying in the longitudinal axis of the spring body 51 and the second leg tangential to a circle concentric about the axis of rotation D through the support point of the spring body 51 on the support element 5a.

In particular, the angle of inclination β can be determined using the clamping distance s Support elements 5a, 5b influence. By reducing the distance s Forced bending of the spring body 51 also reduces the angle of inclination β, which results in a flatter characteristic curve with a lower starting torque.

A damping device 6, which is particularly in combination with the Energy storage 5 shown in Figure 8, also for use in door hinges is shown in Figure 10. The axis of rotation of the door is with the axis of rotation D of the energy store 5 identical. The damping device 6 has a stationary outer 61a and a slightly smaller rotatable one inner damping cylinder 61b. Between the two cylinders 61a, 61b there is a gap space 63 which is filled with hydraulic oil. The inner damping cylinder 61b also forms the jacket for the internal energy store 5. Through two sealing devices 62a, 62b, one of which has 62a the outer cylinder 61a and the other 62b with the inner cylinder 61b is connected, the flow of hydraulic oil is prevented. When loading the Energy storage 5 by a rotary movement of the closer shaft, not shown at the same time, the inner cylinder 61a becomes opposite to the outer cylinder 61b twisted. In a partial area 63a between the cylinder walls 61a, 61b thus the hydraulic oil compresses and flows through one or more overflow channels 64 in the opposite pressure-free partial area 63b. By A suitable arrangement of an overflow valve can thus ensure an undisturbed overflow of the hydraulic oil reached during the charging process of the energy store 5 and a damping during its unloading process.

FIG. 11 finally shows an application example with one on a conventional one Closer spring 11 supported energy store 5. The energy store 5 is arranged between the piston 3 and the closer spring 11. Such an arrangement allows force-displacement characteristics to be within one wide range vary by the characteristics of the two sub-components, the closer spring 11 and the energy store 5 are superimposed on one another. For this purpose, the closer spring 11 is advantageously in the closed state The door is biased in such a way that the door opening process initially takes a moment has, which of the non-linear characteristic of the energy storage 5th is dominated. Preferably leads over the entire opening and closing process seen the door, the closer spring 11 from a larger stroke than that Energy storage 5.

List of reference characters

1

closer shaft

11

closer spring

2

cylinder

2a

Drucklosraum

2 B

pressure chamber

3

piston

3a

rack

4

pinion

5

energy storage

5a, 5b

support element

5c

guide disc

51

spring body

52

location hole

53

guiding device

54

guide slot

55

pivot bearing

6

damping device

61 a, 61 b

outer and inner damping cylinder

62a, 62b

poetry

63a

pressure chamber

63b

Drucklosraum

64

overflow

d

thickness

H

stroke

r

radial distance

s

axial distance

w

angle of rotation

β

tilt angle

D

axis of rotation

F

force

M

torque

Claims (34)

1. Door closer for a door with a door leaf, having an energy store (5) for closing the door leaf, having at least one spring body (51) which is supported between two supporting elements (5a, 5b), the energy store (5) being at least partially charged during the opening movement of the door leaf and being at least partially discharged during its closing, the spring body (51) being of rod-shaped design in a linear or curved manner and being axially under compression or tension or axially under compression or tension and under torsion, characterized in that a plurality of spring bodies (51) are arranged parallel or virtually parallel to one another, and in that, when the energy store (5) is charged or discharged, the distance between the supporting elements (5a, 5b) is changed and/or the supporting elements (5a, 5b) are moved with respect to each other in the axial direction.
2. Device according to Claim 1, characterized in that the spring bodies (51) are arranged about an axis in such a manner that the sum of the radial forces acting on the supporting elements (5a, 5b) is minimized with respect to this axis.
3. Device according to Claim 2, characterized in that the spring bodies (51) are arranged symmetrically about an axis.
4. Device according to Claim 1, characterized in that the spring bodies (51) are arranged at an angle to one another.
5. Device according to Claim 1, characterized in that the spring bodies (51) differ in thickness (d).
6. Device according to Claim 1, characterized in that the spring bodies (51) differ in length.
7. Device according to Claim 1, characterized in that the spring bodies (51) are at a different radial distance (r) from the centre of the supporting element (5a, 5b).
8. Device according to Claim 1, characterized in that the cross-sectional geometry and/or the thickness of the spring body or spring bodies (51) varies along the axial length thereof.
9. Device according to Claim 1, characterized in that, during charging or discharging of the energy store (5), the supporting elements (5a, 5b) are rotated relative to each other.
10. Device according to Claim 9, characterized in that the relative rotation takes place about an axis which is perpendicular to a supporting surface of the supporting element (5a, 5b), or takes place about a connecting axis of these two supporting elements (5a, 5b) or about a rotational or central axis (D) of the energy store (5) or about an axis of symmetry of the spring bodies (51).
11. Device according to Claim 9 or 10, characterized in that the angle of inclination (β) of the spring body or spring bodies (51) changes during charging or discharging of the energy store (5), the first leg of the angle lying in the longitudinal axis of the spring body (51), and the second leg lying tangentially to a concentric circle about the rotation axis of the supporting element (5a) through the supporting point of the spring body (51).
12. Device according to Claim 11, characterized in that the angle of inclination (β) of the spring bodies (51) is at a minimum in the closed state of the door and is at a maximum in the open state of the door, or vice versa.
13. Device according to Claim 11, characterized in that the angle of inclination (β) of the spring bodies (51) in the closed state of the door and in the open state of the door takes up a value between its minimum and its maximum.
14. Device according to Claim 1, characterized in that the spring body or spring bodies (51) have a rigid rod which is mounted resiliently, provision being made for the spring bodies (51) to be designed as a rigid linkage rotating, with the distance between the supporting elements (5a, 5b) changing, under pressurization of a supporting spring.
15. Device according to Claim 1, characterized in that the spring body or spring bodies (51) have a rod-shaped body which is bent elastically or remains rigid during charging or discharging of the energy store (5).
16. Device according to Claim 15, characterized in that, during charging or discharging of the energy store (5), torsion and bending of the spring body or spring bodies (51) are combined with each other.
17. Device according to Claim 1, characterized in that the energy store (5) has a guide device (53) for the spring body or spring bodies (51).
18. Device according to Claim 17, characterized in that the guide device (53) has guide slots (54) for forcing the bending direction and/or for limiting the maximum bending of the spring body or spring bodies (51), the guide slots (54) being of radial or spiral-shaped design.
19. Device according to Claim 1, characterized in that, in the closed position of the door, the spring body or spring bodies (51) are deformed under prestress, in particular are axially prestressed and/or prestressed by torsion.
20. Device according to Claim 1, characterized in that a number of groups of spring bodies (51) are arranged one behind another.
21. Device according to Claim 1, characterized in that one of the supporting elements (5a) is mounted rotatably and/or has a rotary bearing in which the spring body or spring bodies (51) are held.
22. Device according to Claim 21, characterized in that the rotational axis of the supporting element (5a) or of the rotary bearing coincides with an axis of the energy store (5).
23. Device according to Claim 22, characterized in that the supporting element (5a) or the rotary bearing is rotated counter to the force of a restoring spring during charging of the energy store (5) and is returned into the starting position under the action of the storing spring during discharging of the energy store (5).
24. Device according to Claim 22, characterized in that the rotational axis (D) of the energy store (5) is identical with the rotational axis of the door.
25. Device according to Claim 1, characterized in that the spring body or spring bodies (51) are held in a positionally fixed manner and/or rotationally fixed manner in the supporting elements (5a, 5b) of the device.
26. Device according to Claim 1, characterized in that both a conventional closer spring (11) and an energy store (5) are charged during opening of the door and discharged during closing of the door.
27. Device according to Claim 26, characterized in that the energy store (5) is supported on a conventional closer spring (11).
28. Device according to Claim 26, characterized in that the energy store (5) is arranged between the piston (3) and the closer spring (11).
29. Device according to Claim 26, characterized in that the energy store (5) is arranged between the closer spring (11) and the end side of the cylinder (2).
30. Device according to Claim 26, characterized in that the closer spring (11) executes a greater stroke than the energy store (5) during opening and during closing of the door.
31. Device according to Claim 26, characterized in that the closer spring (11) is prestressed in the closed state of the door.
32. Device according to Claim 26, characterized in that the torque profile during opening and during closing of the door corresponds to a combining of the characteristic curves of the closer spring (11) and of the energy store (5).
33. Device according to Claim 1, characterized in that the stroke of the energy store (5) is restricted.
34. Device according to Claim 1, characterized in that the energy store (5) is connected to a damping device (6) in order to damp the closing speed.

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