DE102010017574B4 - door closers - Google Patents

Abstract

Door closer (1) - with a door closer housing (6) - with a drive device (20) arranged in the door closer housing (6), which can be coupled to a door via a door closer shaft (19) and a linkage (18); and - with a hydraulic damping device (23) having a damping piston (24) guided in a damping cylinder (5) of the door closer housing (6) and in operative connection with the drive device (20), which is equipped with a first oil valve associated with a rapid door closing movement. Run-out channel (9) and a slow door closing movement associated second oil drain passage (14), - wherein the first and second flow channel (9 or 14), as seen in the direction of movement (R) of the damping piston (24), arranged one behind the other are -, wherein the first flow channel (9), in the direction of movement (R) of the damping piston (24) to the housing end (25) seen behind the second flow channel (14) is arranged, - wherein the damping piston (24) with an extension (2 ), which points to the adjacent housing end (25), - wherein the extension (2) with a sealing body (7) cooperates in a hollow chamber (9 ') of a screw plug (4) which is inserted into the housing end (25) which is adjacent to the damping piston (24), - wherein the sealing body (7) has two cup-like halves (41, 42) which can be connected to one another, preferably screwed , Are and in the connected state an internal receiving space (43) limit, - wherein in the receiving space (43) a compression spring (22) is arranged at one of the housing end (25) facing end of the sealing body (7) and at the other end a pressure plate (33) arranged in the receiving space (43), which can be brought into operative connection with the extension (2), and wherein a further compression spring (27) is arranged around the sealing body (7), which adjoins one end on the Closing screw (4 or 16) and at the other end to a contact shoulder (44) of the sealing body (7) is supported.

Description

The invention relates to a door closer according to the preamble of claim 1.

For the controlled closing of door systems usually spring-operated door closers 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 set to 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 may partially pop up 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 just in this 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 rebounding wing would extremely disrupt the control processes due to fast closing speed and malfunction of the entire system to lead.

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 locking brake area can be adjusted with its own control valve. The first brake area can thus be set much faster, which significantly shortens the entire closing process.

In known door closers with a division of the entire hydraulic closing sequence 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.

A disadvantage of such known door closers, however, is that this very simple control method is only suitable for relatively large oil displacement amounts 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. Inevitably, there is a more or less large gap between the housing cylinder and the damping piston for tolerance reasons, whereby leakage oil can flow out uncontrollably.

If, during the door closing operation, one of the drainage channels in the pressure chamber is closed by the damping piston during the working stroke or opened depending on the function, one still flows certain amount of oil leakage over the gap between the piston and cylinder wall uncontrolled from. The hydraulic oil tries to find a way to the lower-pressure tank space of the door closer. By means of this leakage oil, therefore, it is not possible to determine precise degrees of angle for the beginning and the 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, however, with door closers in the smallest construction with very little oil volume some hydraulic functions due to the problems explained are not feasible.

Another disadvantage of this control method with drain holes in the cylinder wall is that usually no sealing ring can be used on the damping piston, since when passing over the drain holes of the sealing ring is destroyed very quickly. Only a few very elaborate seal designs allow running over drain holes. 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 residual stroke of the damping piston from the contact point to the zero position of the door must also be accompanied by the control valve and dipped into the screw plug accordingly.

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 a drain hole 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 be controlled very correctly without 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. Thus, a sufficiently high damping pressure results, thereby ensuring that the door is decelerated sufficiently to prevent it from returning to the zero position too quickly.

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 also suitable for 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.

• 1: Einen Längsschnitt durch einen erfindungsgemäßen Türschließer,
• 2: eine der 1 entsprechende vergrößerte Darstellung des Bereiches des Türschließers, in dem die Dämpfungseinrichtung angeordnet ist, wobei zur Vereinfachung der Darstellung das Türschließgehäuse nicht gezeigt ist,
• 3: eine der 2 entsprechende Darstellung bei geschlossenem Ablaufkanal für die schnelle Türschließung und
• 4: eine der 3 entsprechende Darstellung eines beispielhaften Türschließers.

Show it:

• 1 : A longitudinal section through a door closer according to the invention,
• 2 : one of the 1 corresponding enlarged view of the area of the door closer, in which the damping device is arranged, wherein the door closing housing is not shown for the sake of simplicity of illustration,
• 3 : one of the 2 corresponding representation with closed drainage channel for fast door closure and
• 4 : one of the 3 corresponding representation of an exemplary door closer.

In 1 is a door closer according to the invention 1 shown with a housing 6 is provided. In the case 6 is a drive device 20 arranged over a door closer shaft 19 and a linkage 18 can be coupled with a door not shown in the figures. Preferably, the drive device 20 designed as a cam drive, the one on the closer shaft 19 rotationally arranged cam 29 and two roles 30 and 31 that is on the cam plate 29 rest. The role 30 is here on a damping piston 24 stored while the roll 31 on a drive piston 32 is arranged, with an energy storage spring 21 is in operative connection, in the housing 6 is arranged.

Furthermore, the door closer 1 a hydraulic damping device 23 on. This has the damping piston 24 in one in the case 6 arranged damping cylinder 5 is guided. The damping piston 24 stands with the drive device 20 , as described above, in operative connection.

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

In the in the 1 and 2 illustrated embodiment of the door closer 1 is the damping piston 24 with a lance-like extension 2 that is in the closing direction R of the damping piston 24 extends, provided. In the illustrated embodiment, the extension becomes 2 through a special safety valve unit 3 realized in the damping piston 24 is integrated. However, the basic function and the basic construction of the extension is 2 also by a simple direct rod on or the extension of the damping piston 24 reachable.

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

In a hollow chamber 9 ' a locking screw 4 of the damping cylinder 5 or the door closer housing 6 is a sealing body 7 with a sealing ring 8th used.

The sealing ring 8th can be constructed in different ways and from different materials as well as different profile designs. In the illustrated embodiment is as a sealing ring 8th an o-ring is provided. The hollow chamber 9 ' is through another smaller screw plug 16 Oil-tight against the outside environment of the door closer 1 locked.

Like from the 1 and 2 is apparent in the screw plug 4 following the sealing body 7 the drainage channel 9 provided for the hydraulic oil, in an annular channel 10 empties. From the ring channel 10 leads a hole 11 to a control valve 12 , which allows a fast closure of the door by appropriate adjustment.

After the control valve 12 leads a return channel 13 in the door closer housing 6 back to a low-pressure tank room 17 of the door closer 1 ,

Directly from the pressure chamber of the damping cylinder 5 leads the drainage channel 14 to another control valve 15 , which allows a slow closure of the door by appropriate adjustment.

As the 1 to 3 further show is the sealing body 7 in the example of two cup-like halves 41 . 42 constructed, which are connected to each other. In the example case, the two halves 41 and 42 screwed together and limit in the in the 2 and 3 state shown an inner receiving space 43 ,

In the inner reception room 43 is a compression spring 22 arranged at one end of the housing 25 assigning end on the sealing body 7 supported. At the other end, the compression spring is supported 22 on a pressure plate 33 off in the recording room 43 is arranged and with the extension 2 can be brought into operative connection.

To the sealing body 7 around is another spring 27 arranged at one end to the screw plug 4 or arranged in this smaller screw plug 16 supported. At its other end, the compression spring is supported 27 on a contact shoulder 44 of the sealing body 7 from.

The compression spring 22 points at in the 1 to 3 illustrated embodiment, a harder spring rate than the second compression spring 27 ,

Between the sealing body 24 and the screw plug 4 is also a third compression spring 34 arranged.

The 1 to 3 further clarify that the oil drain following the second control valve 15 over in the door closer housing 6 arranged return channel 13 in the tank room 17 he follows.

The functional sequence of the previously described door closer will be described below 1 explained.

When manually opening the door is over the linkage 18 a torque in the door closer shaft 19 initiated. 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 moves 24 with the extension 2 in the direction of the door closer shaft 19 , Hydraulic oil from the tank space through a bore and a check valve in the damping piston 17 of the door closer 1 in the pressure chamber or damping cylinder 5 can flow.

After releasing the door, the energy storage spring tries 21 to relax again and passes over the drive device 20 of the door closer 1 the torque required for closing in the door closer shaft 19 on. So that this process does not run abruptly, is a further deflection of the rotational movement of the door closer shaft 19 in a stroke movement of the damping piston 24 a hydraulic back pressure in the damping cylinder 5 built up.

Due to the convenient for a walk-through higher opening angle of the door of z. B. 75 ° is the damping piston 24 after F clearance of the door in a position close to the closer shaft 19 arranged. This is the damping piston 24 extension 2 completely from the sealing body 7 lifted.

During the closing process, the damping piston approaches 24 again the screw plug 4 at the end of the housing 25 on. 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.

That of the damping piston 24 During the closing process displaced hydraulic oil can through an oblique bore 28 in the Screw 4 in the hollow chamber 9 ' the screw plug 4 flow.

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

The closing process of the damping piston 24 from the pressure room 5 displaced oil then flows out of the hollow chamber 9 ' with the seal seat open, unhindered over the other drainage holes 9 . 10 and 11 in the case 6 , Subsequently, the oil flows to the faster adjusted control valve 12 , Thereafter, the further oil drain via the return hole 13 in the tank room 17 of the door closer 1 , The door can thus close relatively quickly.

Depending on the design, this is the damping piston 24 extension 2 adjusted in length to the desired switching point or the desired door angle for the beginning of the second closing speed.

When this door angle is reached, the extension first presses 2 on the pressure plate 33 attached to the back of the sealing body 7 is arranged. The pressure plate 33 becomes even inside the sealing body 7 from the compression spring 22 that has a harder spring rate than the outer spring 27 has, to a limit of the sealing body 7 pressed.

On further closing stroke of the damping piston 24 due to the different spring rates, initially the outer, to the sealing body 7 arranged around spring 27 compressed, causing the entire sealing body 7 in the seal seat 8th' the inner screw plug 16 is pushed. The sequence 9 to the faster adjusted control valve 12 is thus closed abruptly and leak-free.

The hydraulic oil can thus only on the additional in the damping cylinder 5 existing second drain channel 14 to the slower adjusted control valve 15 expire. 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 additionally in the sealing seat 8th' pressed. The seal seat 8th' represents for the sealing body 7 a rigid position limitation.

Therefore, the residual stroke of the damping piston 24 from the switching angle to the zero position of the door with the in the sealing body 7 integrated pressure spring 22 balanced. The seal seat 8th' remains closed continuously.

Due to the higher rate of compression spring 22 A significant compression of the spring occurs only after reaching the sealing position. Thus, a sequential circuit is achieved, the first closing the sealing seat 8th' through the sealing body 7 yields and then only the length compensation of Kolbenresthubes permits. The length compensation is thus complete in the sealing body 7 integrated, which allows a very compact design.

Below is an unclaimed example based on the 4 explained. All with the 1 to 3 matching elements are provided with the same reference numerals. Accordingly, reference may be made in this regard to the foregoing discussion.

When in the 4 illustrated embodiment is the extension 2 as a guide sleeve 35 formed with the damping piston 24 connected is. In the illustrated embodiment, the guide sleeve 35 with the damping piston 24 screwed.

In this embodiment, the sealing body 7 in an interior 45 the guide sleeve 35 arranged. The sealing body 7 is here by means of a compression spring 36 to a stop 40 the guide sleeve 35 biased adjacent to the housing end 25 is arranged.

The sealing body 7 has an end-face planar sealing surface 46 on, on a housing-side sealing surface 8th' can be applied. In the illustrated embodiment, the sealing surface 8th' on the smaller screw plug 16 arranged in the larger screw plug 4 is screwed.

The presentation of the 4 further clarifies the arrangement of three sealing rings 37 . 38 and 39 between the larger screw plug 4 and the housing 6 or the screw plug 16 and the screw plug 4 ,

As the sealing body 7 in this embodiment in the locking screw 16 is arranged, the sealing body can 7 along with length compensation in this case in the damping piston 24 or its guide sleeve 35 be arranged.

The sealing body 7 This is due to the additional in the guide sleeve 35 integrated pressure spring 36 against the attack 40 the guide sleeve 35 pressed and drives the entire working 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 braking areas to the zero position of the door. In addition, the compression spring ensures 36 that the sealing seat 8th' constantly remains pushed 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 one in the screw plug 4 respectively. 16 located sealing seat 8th' moves and a subsequent drain hole or drain channel to the faster set valve 12 closes.

The seal seat 8th' This can be done directly in the main screw plug 4 or in the further arranged in this smaller screw plug 16 be arranged.

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

After closing the sealing seat 8th' There is a strong increase in pressure, which is the sealing body 7 additionally in the sealing seat 8th' presses and creates a freedom from leaks. For the further closing process, the hydraulic oil must be replaced by the slower adjusted control valve 15 back to the tank room 17 flow, which makes the door slowly close.

LIST OF REFERENCE NUMBERS

1

door closers

2

Extension (rod)

3

Safety valve unit

4

Screw

5

damping cylinder

6

Door closer housing

7

sealing body

8th

Sealing ring (O-ring)

8th'

sealing seat

9

Drain channel for fast opening

9 '

hollow

10

annular channel

11

drilling

12

Control valve for fast opening

13

Return channel

14

Drain channel for slow opening

15

Control valve for slow opening

16

second smaller screw plug

17

tankage

18

linkage

19

Door closer shaft

20

driving means

21

Energy storage spring

22

hard spring

23

attenuator

24

damping piston

25

housing end

26

chamfer

27

compression spring

28

oblique bore

29

Cam or cam disc

30

roll

31

roll

32

drive piston

33

printing plates

34

third compression spring between screw plug 4 and damping piston 24

35

guide sleeve

36

compression spring

37

seal

38

seal

39

seal

40

attack

41

halves

42

halves

43

accommodation space

44

contact shoulder

45

inner space

46

sealing surface

R

movement direction

Claims (8)

Door closer (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) which has a damping piston (24) which is guided in a damping cylinder (5) of the door closer housing (6) and is in operative connection with the drive device (20), which is equipped with a first oil drain valve assigned to a fast door closing movement. channel (9) and a slow door closing movement associated second oil drain passage (14), - 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, - Wherein the first flow channel (9), in the direction of movement (R) of the damping piston (24) to the housing end (25) seen behind the second flow channel (14) is arranged, - wherein the damping piston (24) provided with an extension (2) which points to the adjacent housing end (25), - wherein the extension (2) with a sealing body (7) cooperates in a hollow chamber (9 ') of a locking screw ( 4), which is in the housing end (25) which is the damping piston (24) adjacent, is inserted, - wherein the sealing body (7) has two cup-like halves (41, 42) which can be connected together, preferably screwed, are in the connected state an internal receiving space (43) limit, - wherein 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) arranged pressure plate (33) which can be brought into operative connection with the extension (2), and - wherein 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. Door closer to Claim 1 , characterized in that the first drainage channel (9) is provided with a first control valve (12) for a fast door opening. Door closer to Claim 1 or 2 , characterized in that the second drainage channel (14) is provided with a second control valve (15) for slow door closing. Door closer to one of the 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). Door closer according to one of the preceding claims, characterized in that the sealing body (7) has an end-side sealing region which can be applied to a sealing seat (8 ') facing it. Door closer to Claim 5 , characterized in that the sealing region as a sealing ring (8), preferably in the form of an O-ring is formed. Door closer according to one of the preceding claims, characterized in that the compression spring (22) in the receiving space (43) has a harder spring rate than the further compression spring (27). Door closer according to one of the preceding claims, characterized in that a third compression spring (34) is arranged between the damping piston (24) and the closure screw (4).

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