Door operator

Abstract

A door operator includes a housing and at least one linearly guided piston in the housing. A roller carrier is disposed in the piston and includes a rotatably movable supported pressure roller. The piston is formed as a deep drawn structural component and includes a bottom and a circumferential walling. The support and the axial guiding of the roller carrier with a pressure roller within the piston can be realized in a simple and cost effective manner. Furthermore, an aperture is provided in the bottom of the piston, through which the pressure roller protrudes to the outside beyond the bottom of the piston.

Claims

1. A door operator comprising: a housing and at least one linearly guided piston disposed in the housing, a roller carrier disposed in the piston and including a rotatably movable supported pressure roller, wherein the piston is formed as a deep drawn structural component and includes a bottom and a circumferential walling, an aperture is provided in the bottom of the piston and the pressure roller projects outwardly beyond the bottom; and a spring extends into the piston and is configured to move the piston towards a cam which is attached to a pivoting axis for a door assembly.

2. The door operator according to claim 1, wherein the roller carrier is essentially configured as U-shaped.

3. The door operator according to claim 1, wherein the roller carrier is configured as a stamped bent part.

4. The door operator according to claim 2, wherein the roller carrier includes free branches that protrude beyond the bottom outwardly and are laterally fixed by means of the aperture.

5. The door operator according to claim 2, wherein the roller carrier includes free branches having lateral shoulders and serve for supporting the roller carrier at the interior side of the bottom.

6. The door operator according to claim 1, wherein a plurality of flangings, which serve for supporting the roller carrier, are disposed in the circumferential walling of the piston.

7. The door operator according to claim 1, wherein the pressure roller is supported via a bolt in the roller carrier and the bolt is supported in its axial direction at the aperture.

8. The door operator according to claim 1, wherein a carrying plate, which abuts against the roller carrier, is disposed in the piston.

9. The door operator according to claim 8, wherein the carrying plate is able to extend between a plurality of flangings disposed in the circumferential walling of the piston.

10. The door operator according to claim 8, wherein the carrying plate is configured as a stamped bent part.

11. The door operator according to claim 8, wherein the spring abuts against the carrying plate.

12. The door operator according to claim 8, wherein a non-return valve and/or a pressure control valve is disposed in the carrying plate.

13. The door operator according to claim 1, wherein depressions are provided adjacent the bottom and are configured for receiving bearing shells and/or other structural components.

14. The door operator according to claim 1, wherein the piston is configured as a reversed drawn structural component.

15. The door operator according to claim 1, wherein the piston is configured as a sheet metal part.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further details, features and advantages of the disclosure will become apparent from the following description, reference being made to the drawings. In the drawings:

(2) FIG. 1 shows a longitudinal section through an inventive door operator,

(3) FIG. 2 shows a perspective view of a piston guided in the door operator according to a first embodiment,

(4) FIG. 3 shows the piston of FIG. 2 in a partially broken view,

(5) FIG. 4 shows a longitudinal section through the piston according to FIG. 2,

(6) FIG. 5 shows a perspective view of the piston guided in the door operator according to a second embodiment,

(7) FIG. 6 shows the piston of FIG. 5 in a partially broken view,

(8) FIG. 7 shows a longitudinal section through the piston according to FIG. 5,

(9) FIG. 8 shows a longitudinal section through the inventive door operator, wherein the cam disc is disposed in a 0° position,

(10) FIG. 9 shows a longitudinal section through the inventive door operator, wherein the cam disc is disposed in a 30° position, and

(11) FIG. 10 shows a section of FIG. 9 in an enlarged scale.

DETAILED DESCRIPTION OF THE DRAWINGS

(12) In the following description, the door operator 1 illustrated in FIG. 1 will be explained only insofar as it is of interest in the present case.

(13) The door operator 1, which may be for example a door operator with cam technology, includes a housing 2, in which among others a piston 3 is longitudinally displaceable. In the exemplary embodiment illustrated in FIG. 1, two pistons 3 are provided, which however basically have the same configuration. The pistons 3 are charged by respectively one spring 4, which pushes them in the direction towards a cam disc 5, which is attached to a pivoting axis 6 for a door arm assembly.

(14) A first embodiment of the piston 3 is illustrated in detail in the FIGS. 2 to 4.

(15) The piston 3 comprises a deep drawn or a reversed drawn sheet metal part, which is configured bowl-shaped or pot-shaped and includes a bottom 3a and a circumferential walling 3b.

(16) A roller carrier 7, which carries a pressure roller 8, is disposed in the piston 3. Essentially, the roller carrier 7 is formed to be U-shaped with free branches 7a and is manufactured from a stamped bent part. The pressure roller 8 is rotatably supported at a bolt 9, which in turn is supported in the free branches 7a of the U-shaped roller carrier 7.

(17) An aperture 10, through which the pressure roller 8 via the bottom 3a of the piston protrudes to the outside, is disposed in the bottom 3a of the piston 3. The aperture 10 is provided with two opposing lateral protrusions 10a into which the free branches 7a of the U-shaped roller carriers 7 protrude in such a way that the free branches 7a are surrounded by the protrusions 10a on three sides. Thus, the roller carrier 7 is fixed in the aperture 10 in lateral direction.

(18) At its free branches 7a, the roller carrier 7 includes lateral protruding shoulders 7b, via which the roller carrier 7a is able to prop up at the interior side of the bottom 3a.

(19) As the protrusions 10a of the aperture 10 surround the free ends 7a on three sides, also the bolt 9 supporting the pressure roller 8 is supported and fixed by the protrusions 10a in its axial direction.

(20) A carrying plate 11, which may be formed as a stamped part and which abuts against the roller carrier 7, is disposed in the piston 3.

(21) A non-return valve and/or a pressure control valve may be disposed in the carrying plate 11, if it is a hydraulically operated door operator 1.

(22) Flangings 12, which serve for supporting the roller carrier 7 as well as the carrying plate 11, are provided in the circumferential walling 3b of the piston. Said flangings 12 may also assist in a torque-proof guiding of the roller carrier 7 and/or the carrying plate 11.

(23) For mounting the piston 3, the roller carrier 7 with the pressure roller 8 as well as the carrying plate 11 are inserted into the piston 3 from the open side. Then, the parts can be reliably maintained in their position by means of the flangings 12.

(24) In the completed mounted condition, the spring 4 extends into the piston 3 from the open side and abuts against the carrying plate 11. In this condition, the shoulders 7b of the roller carrier 7 are pressed against the interior side of the bottom 3a, while the free branches 7a are guided in the protrusions 10a in longitudinal direction and retained in transverse direction.

(25) A second embodiment of the piston 3 is illustrated in detail in the FIGS. 5 to 7.

(26) The piston 3 according to this embodiment essentially corresponds to the embodiment shown in the FIGS. 2 to 4. However additionally, in this second embodiment in addition to the aperture 10 depressions 13 are provided, which offer space for the reception of bearing shells and/or other structural components.

(27) On account of the rounding of the bottom 3a of the piston 3 caused in the production process, wear is minimized and better efficiency is achieved. Moreover, a relatively long configuration of the piston 3 allows for achieving a better guiding of the piston 3 in the housing 2.

(28) A longitudinal section of the door closer 2 is shown in the FIGS. 8 and 9 in two different positions of the cam disc 5 for illustrating a further advantage of the inventive door closer 1. In particular the force ratios in a door closer 1 with cam disc technology are illustrated in FIG. 9.

(29) The force resultant required for generating a torque M in the cam axis, which force resultant is introduced via the pressure roller 8, generates a force component F.sub.spring in the piston 3 acting in a direction of the spring 4 and a transverse acting normal force component F.sub.n, which causes a lateral support of the piston 3 at the housing 2.

(30) On account of the tilting effect of the piston 3 within the housing 2 caused by means of the normal force component F.sub.n, a punctual contact of the piston 3 in the housing 2 is the result and not a full contact. Depending on the distances L1 and L2 caused by construction, the normal force F.sub.n may be divided into the supporting loads A and B. Said bearing forces A and B—multiplied by the respective friction value μ—result in the frictional forces F.sub.r.

(31) The normal force F.sub.n and the friction forces F.sub.r resulting therefrom are essentially responsible for the efficiency of the door closer 1.

(32) The frictional forces F.sub.r, opposite to the respective direction of movement, reduce the spring energy stored in the spring 4, respectively increase the opening moment M required for compressing the spring 4.

(33) As the efficiency of the overall mechanical system results from the applied and the recovered energy, an optimization of the support of the piston 3 over the distances L1 and L2 as well as of the friction ratios result in a clear improvement of the efficiency. According to the principle “run the length”, larger contact areas are the result at the bearing points, whereby critical peak values with regard to the surface pressure can be avoided.

(34) Thereby, a lower tilting effect of the piston 3 reduces wear, whereby operational soiling of the hydraulic oil is likewise kept low.

(35) Furthermore, lower bearing forces A and B allow for selecting more advantageous materials for the housing 2, respectively for the piston 3. Surface treatments may be likewise reduced, or can be completely omitted.

(36) Thereby, considerable savings can be achieved when manufacturing the individual structural components.

(37) As revealed in particular in FIG. 10, the reduction of the bearing forces A and B allow for reducing scorings of the piston 3 into the walling of the housing 2 as a result of too large a tilting movement and material overloading. Conventionally manufactured pistons in a cutting process will score with their chamfer, which is generated during manufacturing, into the housing 2 as a result of the tilting of the piston, whereby soiling and contamination is produced.

(38) However, the inventive configuration of the piston 3, like in a “post on two beams” by means of longer distances L1 and L2 of the bearings and the thereby more centered introduction of force, stabilizes and relaxes the overall system. The normal force F.sub.n on the roller side at the piston radius is lower and the piston 3 runs straighter. The normal force F.sub.n is introduced at the point of the roller bolt center. The frictional force F.sub.r acts opposite to the direction of movement of the piston 3 and reduces the desired spring force of the spring 4.

(39) The preceding description according to the present disclosure serves for illustrative purposes only and is not intended to limit the disclosure. Various changes and modifications are possible within the framework of the disclosure without leaving the scope of the disclosure or the equivalents thereof.