EP2585662A1

EP2585662A1 - Door closer

Info

Publication number: EP2585662A1
Application number: EP11727398.7A
Authority: EP
Inventors: Volker Bienek
Original assignee: Dorma Deutschland GmbH
Current assignee: Dormakaba Deutschland GmbH
Priority date: 2010-06-25
Filing date: 2011-06-14
Publication date: 2013-05-01
Also published as: DE102010017574A1; WO2011160785A1; CN102959168A; SG185779A1; CN102959168B; TW201202538A; DE102010017574B4

Abstract

The invention relates to a door closer, comprising a door closer housing, a drive unit which can be coupled to a door by means of a door closer shaft and a linkage and is disposed in the door closer housing, and a hydraulic damping unit, which has a damping piston which is guided in a damping cylinder of the door closer housing and is operatively connected to the drive unit. Said damping piston cooperates with a first oil discharge channel associated with a rapid door closing movement and a second oil discharge channel associated with a slow door closing movement, wherein the first and second discharge channels are disposed one after the other and wherein the first discharge channel, as seen looking in the direction of movement of the damping piston, is disposed downstream of the second discharge channel.

Description

Title: Door closer

description

The invention relates to a door closer according to the preamble of claim 1. For the controlled closure of door systems usually spring-operated door closer are used. During a manual opening process, the door closer axis is rotated via a linkage and, furthermore, a spring-loaded energy storage spring is biased via a drive device in the door closer. For the closing process, the energy storage spring relaxes again and presses on the drive device of the door closer and the linkage, the door back to its zero position without external energy.

So that this process does not happen abruptly and very quickly, the entire spring force of the energy storage in the door closer is almost completely absorbed by a hydraulic damping device. In the pressure fluid chamber of the damping device arises in dependence on the piston surface during the closing operation of the spring force corresponding hydraulic pressure, which keeps the power system approximately in balance. By means of a control valve is controlled a low oil return flow from the pressure chamber into a tank space of the door closer. This creates a slight imbalance in the force relationships, causing the door closes relatively slowly due to the spring forces.

With only one control valve for the entire door closing sequence from each door angle, only a constant closing speed can be achieved

CONFIRMATION COPY adjust the closed position of the door. To ensure that the door does not strike the seat in the door frame too much when it reaches the closed position, the entire closing sequence must be controlled.

Depending on the material of the door system, the construction and the sealing elements, the door will bounce off the frame again if it closes too quickly and will sometimes spring open again. So a vibration sequence can arise until the complete rest position of the door.

However, a slow set closing speed to avoid this effect has the disadvantage that unnecessarily much time is needed for the entire closing of larger door opening angles. For higher-traffic doors, this time requirement is very important, since often the door leaves no longer completely return to the zero position. In addition, at low outside temperatures, the long closing time due to higher heat energy losses has a negative effect. Especially with elevator systems, each additional closing time of the respective landing doors causes a longer waiting time for the users on all floors, since the elevator cage may only approach after the entire door system has been closed. A simple increase in the closing speed in this particular application is not possible for the following technical reasons: Since elevator doors are equipped with limit switches and automatic door locks for the closed position, a bouncing wing would interfere too fast closing speed, the control processes extremely and malfunction of the lead the entire system. The solution of this problem can only be achieved with a second closing brake area, where shortly before the zero position, the speed of the door is slowed down so that it can eventually close slowly. This second closing brake area can be equipped with its own control be adjusted valve. The first brake area can thus be set much faster, which significantly shortens the entire closing process.

In known door closers with a breakdown of the entire hydraulic closing sequence seen in two or more areas, the different speed ranges are realized by differently arranged drain holes in the cylinder bore of the damping or brake piston. Depending on the piston position, which corresponds to a respective door angle, drainage channels in the pressure chamber are opened or closed via the piston edges. The drainage channels are then provided in the course with differently adjusted control valves, whereby various door speeds are adjustable.

However, a disadvantage of such known door closers is that this very simple control method is only suitable for relatively large oil displacement quantities of the damping piston and thus only for larger door closer or drive arrangements. Very small designed door closer, especially with cam technology, have not enough displacement volume due to the very low working stroke and the small piston surfaces. For tolerance reasons, there is inevitably a greater or lesser gap between the housing cylinder and the damping piston, as a result of which leakage oil can flow off in an uncontrolled manner.

If, during the door closing operation, one of the discharge channels in the pressure chamber is closed by the damping piston during the working stroke or opened depending on the function, a certain amount of leakage oil nevertheless flows uncontrolled via the gap between the piston and the cylinder wall. The hydraulic oil tries to find a way to the lower-pressure tank space of the door closer. Leave through this leakage oil Thus, set no precise degrees for the beginning and end of a speed range or a hydraulic function.

For larger door closers with higher oil displacement per door angle, this effect has only a relatively small impact, but some hydraulic functions are not feasible in door closers in the smallest construction with very little oil volume due to the problems outlined.

Another disadvantage of this control method with Abiaufbohrungen in the cylinder wall is that usually no sealing ring can be used on the damping piston, as when passing over the drain holes of the sealing ring is destroyed very quickly. Only a few very elaborate seal designs allow running over Abiaufbohrungen. However, these special seals also require larger installation dimensions, which are not available for very small door closers.

Another known way to control door closing speeds is the use of one or more control valves located in the closure screw of the cylinder chamber of the door closer. Depending on the door angle and thus according to the stroke position of the damping piston, these control valves are opened by mechanical contact with the end face of the piston. In this case, a flow channel is released, which in turn controls the return flow of the hydraulic oil into the tank space of the door closer by a downstream, adjustable control valve. The control valves are kept closed by means of correspondingly strong springs or an electromagnetic unit against the oil pressure in the damping chamber. Only through the mechanical contact with the damping piston, the control valve is opened. The position of the damping piston and thus the switching point are each assigned to a specific door opening angle. The remaining stroke of the damping piston from the contact point to the zero position of the door must also drive the control valve and immerse it in the screw plug.

However, these door closing mechanisms have the disadvantage that the speed of the door can only be adjusted from a slow to a faster level. The fact that an Abiaufbohrung is additionally opened by the control valve, creates more throttle cross-section, which increases the closing speed. By immersing the control valve in the screw it must be made relatively wide according to the Kolbenresthubes. This increases the overall length of the entire door closer.

Furthermore, door closers are provided with a hollow tube for flow control of a hydraulic locking function. The hollow tube housing is firmly attached to one of the lateral locking screws and immersed to a defined breakpoint in a sealing bushing of the piston. Through the hollow tube, the hydraulic oil flows to a solenoid valve. When the solenoid valve is energized, no hydraulic oil can flow back into the tank space of the door closer, causing a locking function.

The immersion of the hollow tube in the sealing bush of the piston is depressurized during the opening process of the door. Only after completion of the opening process, the energy storage spring tries to relax again, creating a hydraulic pressure is built up. However, such door closers work with a relatively low working pressure and relatively high oil volume.

In summary, it should be noted that the known door closer with the described control options due to the high leakage losses or due to the low spring forces for safe locking of the control valves for very small door closer with high working pressure are not suitable. It is therefore an object of the present invention to provide a door closer specified in the preamble of claim 1, which makes even with small dimensions and high working pressures control the door closing movement of a fast initial closing to a slow controlled closing the door possible.

The solution of this object is achieved by the features of claim 1.

Since a closing door, depending on weight, door width and closing speed has a relatively high inertia, a large speed reduction must be achieved shortly before the closed position to reduce much door energy. In the pressure chamber of the damping device in this case arises a very high and abruptly increasing hydraulic pressure.

Small door closers work due to the small piston surfaces basically already at a very high pressure level in the damping cylinder. Furthermore, due to the low working strokes only very small displacement volumes are available.

It is therefore necessary that the transition to the second braking range is controlled very correctly without causing uncontrolled leakage losses. These functional requirements of the invention, the door closer to the full extent, since the provided for the first and faster braking area return channel can be accurately closed and absolutely tight, which ensures that the displaced by the damping piston hydraulic oil only through the second flow channel for the slow door closing movement in the tank space can flow back. This results in a sufficiently high damping pressure, whereby the door is delayed enough to prevent it from returning too quickly to the zero position.

The dependent claims have advantageous developments of the invention to the content. In particular, the arrangement of an extension or rod on the damping piston ensures that a door-angle-dependent or stroke-dependent switching point can be achieved.

The seal is completely leak-free at a defined position by the interaction of the extension with a sealing body. Thus, the arrangement is suitable for even the smallest door closer systems with low oil displacement (oil volume).

Due to the immediate and complete sealing of the faster valve area no caster or slippage occurs.

The complete freedom from leaks of the door closer according to the invention is for systems with very small oil displacement a main requirement for a rapid pressure build-up in the damping cylinder. This is preferably achieved with the door closer according to the invention, so that a strong deceleration of the door system near the zero position is made possible. In order to achieve a speed grading from fast to slow, the control valves are preferably arranged such that above the switching point of the speed ranges, ie at the faster closing speed, both control valves are opened in parallel. From the switching point, the hydraulic oil can thus flow out of the pressure chamber of the damping cylinder only via the slowly set valve. Further details, advantages and features of the invention will become apparent from the following description of an embodiment with reference to the drawings.

FIG. 1 shows a longitudinal section through a door closer according to the invention,

FIG. 2: an enlarged view corresponding to FIG

Area of the door closer, in which the damping device is arranged, wherein for ease of illustration, the door closing housing is not shown,

FIG. 3 shows a representation corresponding to FIG. 2 with the drainage channel closed for fast door closing and FIG

FIG. 4 shows a representation corresponding to FIG. 3 of a second one

Embodiment of the door closer according to the invention. FIG. 1 shows a door closer 1 according to the invention, which is provided with a housing 6. In the housing 6, a drive device 20 is arranged, which can be coupled via a door closer shaft 19 and a linkage 18 with a door not shown in the figures. The drive device 20 is preferably designed as a cam drive which has a cam disk 29 arranged rotationally fixed on the closer shaft 19 and two rollers 30 and 31 which rest on the cam disk 29. The roller 30 is in this case mounted on a damping piston 24, while the roller 31 is arranged on a drive piston 32 which is in operative connection with an energy storage spring 21 which is arranged in the housing 6. Furthermore, the door closer 1 has a hydraulic damping device 23. This has the damping piston 24 which is guided in a damping cylinder 5 arranged in the housing 6. The damping piston 24 is in operative connection with the drive device 20, as described above.

The damping device 23 also has a first oil drain channel 9 associated with a fast door closing movement and a second oil drain channel 14 associated with a slow door closer movement. According to the invention, the first discharge channel 9, seen in the direction of movement R of the damping piston 24, is arranged behind the second discharge channel 14.

In the embodiment of the door closer 1 shown in FIGS. 1 and 2, the damping piston 24 is provided with a lance-like extension 2 which extends in the closing direction R of the damping piston 24. In the illustrated embodiment, the extension 2 is realized by a special safety valve unit 3, which is integrated in the damping piston 24. However, the basic function and the basic structure of the extension 2 can also be achieved by a simple direct rod on or extension of the damping piston 24.

In the particularly preferred embodiment of Figures 1 and 2, the extension 2 is provided with a centering bevel 26.

In a hollow chamber 9 'of a screw plug 4 of the damping cylinder 5 and the door closer housing 6, a sealing body 7 is inserted with a sealing ring 8.

The sealing ring 8 can be constructed in various ways and from different materials and different profile designs his. In the illustrated embodiment, an O-ring is provided as a sealing ring 8. The hollow chamber 9 'is closed by a further smaller screw plug 16 oil-tight against the outside environment of the door closer 1. As can be seen from FIGS. 1 and 2, in the closure screw 4, following the sealing body 7, the drainage channel 9 for the hydraulic oil is provided, which opens into an annular channel 10. From the annular channel 10, a bore 11 leads to a control valve 12, which allows a fast closing of the door by appropriate adjustment. After the control valve 12, a return channel 13 in the door closer housing 6 leads back into a low-pressure tank space 17 of the door closer. 1

Directly from the pressure chamber of the damping cylinder 5, the flow channel 14 leads to a further control valve 15, which allows for slow closing of the door by appropriate adjustment. As the figures 1 to 3 further show, the sealing body 7 is constructed in the example of two cup-like halves 41, 42, which are connectable to each other. In the example case, the two halves 41 and 42 are screwed together and limit in the state shown in Figures 2 and 3, an inner receiving space 43. In the inner receiving space 43, a compression spring 22 is arranged, which is supported on a housing end 25 facing the end of the sealing body 7 , At the other end, the compression spring 22 is supported on a pressure plate 33, which is arranged in the receiving space 43 and which can be brought into operative connection with the extension 2. Around the sealing body 7 around a further compression spring 27 is arranged, which is supported at one end to the screw plug 4 and arranged in this smaller screw plug 16. With her other Ren end, the compression spring 27 is supported on a contact shoulder 44 of the sealing body 7 from.

The compression spring 22 has in the embodiment shown in Figures 1 to 3 a harder spring rate than the second compression spring 27. Between the sealing body 24 and the screw plug 4 is further arranged a third compression spring 34.

FIGS. 1 to 3 further illustrate that the oil drain, following the second control valve 15, takes place via the return duct 13 arranged in the door closer housing 6 into the tank space 17. The functional sequence of the door closer 1 described above will be explained below.

If the door is opened manually, a torque is introduced into the door closer shaft 19 via the linkage 18. With the help of the drive device 20 can be generated from the rotational movement, a lifting movement, whereby the energy storage spring 21 is biased.

At the same time, the sealing piston 24 moves with the extension 2 in the direction of the door closer shaft 19, whereby hydraulic oil can flow from the tank space 17 of the door closer 1 into the pressure space or damping cylinder 5 via a bore and a check valve in the damping piston. After the release of the door, the energy storage spring 21 tries to relax again and forwards via the drive device 20 of the door closer 1, the torque required for the closure in the door closer shaft 19 a. In order for this process does not abruptly, a hydraulic counter-pressure in the damping cylinder 5 is built on a further reversal of the rotational movement of the door closer shaft 19 in a lifting movement of the damping piston 24. Due to the convenient for a walk-through higher opening angle of the door of z. B. 75 °, the damping piston 24 is arranged after release of the door in a position close to the closer shaft 19. Thus, the extension 2 located on the damping piston 24 is completely lifted off the sealing body 7.

During the closing process, the damping piston 24 again approaches the closure screw 4 at the housing end 25. The position of the damping piston 24 corresponds to the contact point of the extension 2 with the sealing body 7. The sealing body 7 is still open. The hydraulic oil displaced by the damping piston 24 during the closing process can flow through an oblique bore 28 in the closure screw 4 into the hollow chamber 9 'of the closure screw 4.

The sealing body 7 is pressed before contact with the piston extension 2 of the compression spring 27 from the sealing seat of the smaller screw 16 and thus held in the open position.

The oil displaced from the pressure chamber 5 during the closing process by the damping piston 24 then flows unhindered from the hollow chamber 9 'through the further drainage holes 9, 10 and 11 into the housing 6 with the sealing seat open. Subsequently, the oil flows to the control valve 12 set at a faster rate Thereafter, the further oil drain takes place via the return bore 13 into the tank space 17 of the door closer 1. The door can thus close relatively quickly.

Depending on the design, the extension 2 located on the damping piston 24 is adapted in its length to the desired switching point or the desired door angle for the beginning of the second closing speed. Upon reaching this door angle, first presses the extension 2 on the pressure plate 33, which is arranged on the back of the sealing body 7. The pressure plate 33 is pressed even within the sealing body 7 of the compression spring 22, which has a harder spring rate than the outer spring 27, to a boundary of the sealing body 7.

Upon further closing stroke of the damping piston 24, due to the different spring rates, initially the outer spring 27, which is arranged around the sealing body 7, is initially compressed, whereby the entire sealing body 7 is pushed into the sealing seat 8 'of the inner locking screw 16. The sequence 9 to the control valve 12 set more quickly is thus closed abruptly and leak-free.

The hydraulic oil can thus proceed only via the additionally present in the damping cylinder 5 second flow channel 14 to the slower set control valve 15. Thus, a very high pressure build-up immediately builds up, which slows down the door and slows down to zero position.

Due to the pressure increase, the sealing body 7 is additionally pressed into the sealing seat 8 '. The sealing seat 8 'is for the sealing body 7 is a rigid position limitation. Therefore, the residual stroke of the damping piston 24 is compensated by the switching angle to the zero position of the door with the built-in sealing body 7 compression spring 22. The sealing seat 8 'remains closed continuously.

Due to the higher rate of the compression spring 22, a significant compression of the spring occurs only after reaching the sealing position. Thus, a sequential circuit is achieved, which only results in the closing of the sealing seat 8 'by the sealing body 7 and then only the length compensation of Piston residual stroke allows. The length compensation is thus completely integrated in the sealing body 7, which allows a very compact design.

Hereinafter, a second embodiment will be explained with reference to FIG. All matching with the figures 1 to 3 elements are provided with the same reference numerals. Accordingly, reference may be made in this regard to the foregoing discussion.

In the embodiment shown in Figure 4, the extension 2 is formed as a guide sleeve 35 which is connected to the damping piston 24. In the illustrated embodiment, the guide sleeve 35 is screwed to the damping piston 24.

In this embodiment, the sealing body 7 is arranged in an inner space 45 of the guide sleeve 35. The sealing body 7 is in this case biased by a compression spring 36 onto a stop 40 of the guide sleeve 35, which is arranged adjacent to the housing end 25. The sealing body 7 has an end-face planar sealing surface 46 which can be applied to a housing-side sealing surface 8 '. In the illustrated embodiment, the sealing surface 8 'is arranged on the smaller screw plug 16, which is screwed into the larger screw plug 4. The representation of Figure 4 also illustrates the arrangement of three sealing rings 37, 38 and 39 between the larger screw plug 4 and the housing 6 and the screw plug 16 and the screw plug 4th

Since the sealing body 7 is arranged in the closure screw 16 in this embodiment, the sealing body 7, together with length compensation, can in this case be arranged in the damping piston 24 or its guide sleeve 35. The sealing body 7 is in this case pressed by the additionally integrated in the guide sleeve 35 compression spring 36 against the stop 40 of the guide sleeve 35 and drives the entire stroke of the damping piston 24 with. The integrated compression spring 36 serves as a length compensation for the remaining stroke of the damping piston 24, which still arises from the switching point of the brake areas to the zero position of the door. In addition, the compression spring 36 ensures that the sealing seat 8 'remains constantly depressed to the zero position of the door. All previously explained embodiments have the common feature that at a defined switching point for the braking areas of the sealing body 7 always in a sealing screw located in the screw 4 and 16 8 'moves and closes a subsequent Abiaufbohrung or drainage channel to the valve 12 set faster. The sealing seat 8 'can in this case be arranged directly in the main locking screw 4 or in the further smaller locking screw 16 arranged in the latter.

When using the further inner or smaller locking screw 16, the sealing seat position and thus the switching point of the braking areas can be made adjustable.

After the closure of the sealing seat 8 ', a strong increase in pressure arises, which additionally presses the sealing body 7 into the sealing seat 8' and creates a freedom from leaks. For the further closing process, the hydraulic oil has to flow through the slower adjusted control valve 15 back into the tank space 17, which causes the door to close slowly. LIST OF REFERENCE NUMBERS

1 door closer

2 extension (rod)

3 safety valve unit

4 screw plug

5 damping cylinders

6 door closer housing

7 sealing bodies

8 sealing ring (O-ring)

8 'sealing seat

9 drainage channel for fast opening

9 'hollow chamber

10 ring channel

11 bore

12 control valve for fast opening

13 return channel

14 drainage channel for slow opening

15 slow opening control valve

16 second smaller screw plug

17 tank room

18 linkage

19 door closer shaft

20 drive device 21 energy storage spring

22 hard spring

23 damping device

24 damping pistons

25 housing end

26 chamfer

27 compression spring

28 oblique hole

29 cam or cam disc

30 rolls

31 rolls

32 drive piston

33 pressure plates

34 third compression spring between plug 4 and

Damping piston 24

35 guide sleeve

36 compression spring

37 sealing ring

38 sealing ring

39 sealing ring

40 stop

41 halves

42 halves

43 recording room contact shoulder

inner space

sealing surface

movement direction

Claims

Door closers (1)

- With a door closer housing (6);

- With a in the door closer housing (6) arranged drive means (20) which is coupled via a door closer shaft (19) and a linkage (18) with a door; and

- With a hydraulic damping device (23) having a in a damping cylinder (5) of the door closer housing (6) guided and with the drive means (20) in operative connection damping piston (24), which is associated with a fast door closing movement associated first oil drain passage (9) and a slow-closing door associated second oil drain passage (14) cooperates,

- Wherein the first and second flow channel (9 or 14), as seen in the direction of movement (R) of the damping piston (24) are arranged one behind the other, characterized

- That the first flow channel (9), seen in the direction of movement (R) of the damping piston (24) to the housing end (25), behind the second flow channel (14) is arranged.

Door closer according to claim 1, characterized in that the first outlet channel (9) is provided with a first control valve (12) for a fast door opening.

Door closer according to claim 1 or 2, characterized in that the second outlet channel (14) is provided with a second control valve (15) for a slow door closure.

4. Door closer according to one of claims 1 to 3, characterized in that the first outlet channel (9) and the second outlet channel (14) are connected to a return channel (13) which communicates with a tank space (17).

5. Door closer according to one of claims 1 to 4, characterized in that the damping piston (24) is provided with an extension (2) facing the adjacent housing end (25).

6. Door closer according to claim 5, characterized in that the extension (2) with a sealing body (7) cooperates, which in a hollow chamber (9 ') of a screw plug (4) is arranged in the housing end (25), the Damping piston (24) is adjacent, is inserted.

7. Door closer according to claim 6, characterized in that the sealing body (7) has an end-side sealing region which can be applied to a sealing seat (8 ') facing it.

8. Door closer according to claim 7, characterized in that the sealing region as a sealing ring (8), preferably in the form of an O-ring, is formed.

9. Door closer according to one of claims 6 to 8, characterized in that the sealing body (7) has two cup-like halves (41, 42) which are connectable to each other, preferably screwed, and in the connected state, an inner receiving space (43 ) limit.

10. Door closer according to claim 9, characterized in that in the receiving space (43) a compression spring (22) is arranged, which at one of the housing end (25) facing the end of the sealing body (7) and at the other end to a in the receiving space (43 ), Neten pressure plate (33) is supported, which can be brought into operative connection with the extension (2).

11. Door closer according to one of claims 6 to 10, characterized in that around the sealing body (7), a further compression spring (27) is arranged, which at one end to the screw plug

(4 or 16) and at the other end to a contact shoulder (44) of the sealing body (7) is supported.

12. Door closer according to claim 11, characterized in that the compression spring (22) in the receiving space (43) has a harder spring rate than the compression spring (27).

13. Door closer according to one of claims 1 to 12, characterized in that between the damping piston (24) and the closure screw (4), a third compression spring (34) is arranged.

14. Door closer according to claim 5, characterized in that the extension (2) as a guide sleeve (35) is formed, which with the

Damping piston (24) connectable, preferably screwed, is.

15. Door closer according to claim 14, characterized in that the sealing body (7) in the interior (43) of the guide sleeve (35) is arranged. 16. Door closer according to claim 15, characterized in that the sealing body (7) by means of a compression spring (36) on a stop (40) of the guide sleeve (35) which is adjacent to the housing end (25) is biased.

17. Door closer according to claim 16 or 17, characterized in that the sealing body (7) has an end-face planar sealing surface (46) which on a housing-side, preferably on the End screw (4 or 16) arranged sealing surface (8 ') can be applied.