WO1999002810A1

WO1999002810A1 - Door closer for generating a speed-increasing leap during the closure phase

Info

Publication number: WO1999002810A1
Application number: PCT/DE1997/001449
Authority: WO
Inventors: Thomas Salutzki
Original assignee: Dorma Gmbh + Co. Kg
Priority date: 1997-07-09
Filing date: 1997-07-09
Publication date: 1999-01-21
Also published as: EP0956415A1; EP0956415B1; ATE235639T1; DE59709648D1

Abstract

The invention relates to a door closer comprising a shoulder(110)-type piston (100) acting upon a driven shaft, a pressure build-up piston (200) and an energy accumulator (30), the pistons (100, 200) being axially guided inside a housing (1). The door closer is also fitted with a first (D1) and a second (D2) pressure chambers connected to an overflow hose and combined with the door piston (100), with a middle pressure chamber (D3) combined with both the shoulder (110) and the pressure build-up piston (200), and at least with one additional pressure chamber (D4, D4*) possibly presenting a choke, while the pistons, or the housing, all have channels for interconnecting the pressure chambers, and while the door piston (100), which is not only interlocking with the door piston due to the offset shoulder (110) in the hand of door (4), but also operatively linked with it- first hydraulically, then mechanically - in the direction of closure, leaves the possibility of hydraulic decoupling from the pressure build-up piston.

Description

Title: Door closer to create a translation jump during the closing phase

description

The invention relates to a door closer according to claim 1.

A door closer has become known from SE 469 342 B, in which a closing torque characteristic adapted to the door angle is achieved by first opening a first spring acting on the door piston and then tensioning a second spring acting in series on the pressure piston when closing the spring acting on the door piston first releases its energy, the second spring remaining in a tensioned position until a slide mounted centrally in both pistons fluidically relieves a pressure chamber holding the pressure piston through a channel system, so that the second spring now exerts its energy on the Abtπebswelle can deliver

Although this door closer can exert different moments depending on the door opening on the door, it requires an extraordinarily high manufacturing effort

In particular, high-precision and thus expensive manufacture is required both for the door piston engaging with the attachment in the pressure piston and for the pressure piston itself. To make matters worse, the pressure piston has two further fits in addition to the fit associated with the turk piston, to which corresponding housing fits are assigned in alignment makes the production considerably more expensive

Finally, the known door closer has a switch valve. Centrally arranged slide on which is axially displaceable, hydraulically sealed both in the door piston and in the pressure piston. This adds up to diameter tolerances, which is what of such a door closer places the highest demands on precision.

A further disadvantage is that numerous pressure chambers to be sealed off from one another are required, which communicate fluidly with one another by means of a complicated duct system, and the desired closing torque characteristic is severely impaired as a function of temperature, particularly in cold weather. The known door closer also places high demands on the assembly personnel, since the fluidically effective, interlocking cylinder surfaces can easily be damaged when the door piston and the pressure piston, as well as the slide which passes through, are joined together.

The object of the invention is therefore to provide a particularly economically producible, simple door closer which can implement different torque profiles.

This object is solved by the features of claim 1.

In a door closer according to the invention, engaging pistons are avoided. Furthermore, only a single pressure accumulator is required. The effort for manufacturing and assembly is significantly reduced. The corresponding fits of the housing or the pistons can be manufactured in one clamping, which significantly improves the running accuracy of the corresponding cylinders or piston surfaces without additional effort and, on the other hand, reduces the number of machining cycles. This also greatly simplifies the duct system, so that it does not require elongated ducts and therefore the ventilation is very simplified during assembly. In this way, leakage is almost completely excluded.

A particularly advantageous embodiment of the door closer according to the invention is given when a medium pressure chamber is fluidly connected: on the one hand with a second pressure chamber by means of a channel which is assigned to the attachment of the turkish piston and can be closed or opened depending on the displacement path of the turkish piston,

and on the other hand with a further pressure chamber by means of a channel which has a check valve effective from the middle pressure chamber,

and the second pressure chamber is fluidly connected to the further pressure chamber assigned to the pressure piston via a channel having a check valve, as well as to the overflow line and to a channel to which a shut-off valve, which is switched continuously in the rest position, is assigned and which, when the pressure rises in the first Pressure room is transferred to its locked position

Here, the channel connecting the middle pressure chamber and a further pressure chamber, along with a check valve, can be arranged in the pressure piston or housing, depending on the structural circumstances

Furthermore, in order to control the closing speed of a door closer according to the invention, the space of a pressure space can be divided into a first part and a second part, the two spaces being fluidly connected to one another via a flow cross section acting as a throttle

It is advantageous if the piston faces of the two pistons facing each other are designed in such a way that sticking together by adhesion is avoided

According to the invention, the requirement for a modular design can be met if the two pistons are assigned to a housing and the energy accumulator is assigned to a further housing, the housing of the door closer and that of the energy accumulator preferably being coupled by means of a radial screw connection. due to only a standard type of the piston-receiving housing is required, the housing adapted to the different, the required clamping forces being easily screwed on. This eliminates the complicated assembly steps that are required in the prior art in the factory

For this purpose, an adjustment means, which is assigned to the energy accumulator and is accessible from the outside, can advantageously be provided in the housing, as a result of which the closing force can be adjusted continuously in a further range

According to the invention, it is also advantageous if the actuatable shut-off valve is a mechanically hydraulic, pneumatic or electrically actuable 2/2-way valve, wherein means for pressure-dependent actuation of the shut-off valve are assigned to the first pressure chamber

In order to implement overload protection, according to the invention, all that is required is an assignment, parallel to the throttle, of an overpressure valve blocking the flow to the first pressure chamber

Further advantageous configurations result from the other subclaims

Furthermore, the invention is described in more detail with reference to exemplary embodiments shown more or less schematically in the figures

It shows

Figure 1a is a structural view of a door closer according to the

invention

Figure 1 b shows a detail of an alternative embodiment of a door closer according to the invention

FIG. 2 shows a first exemplary embodiment of a door closer according to the invention, Figure 3: a second embodiment of the invention in the

Positions:

Figure 3a: door closed,

FIG. 3b: start of opening,

Figure 3c: door open,

Figure 3d: reversal of the i of the closing process and

Figure 4: the graph of the gear ratio of the door closer as a function of the angle of rotation of the door

The same parts have the same reference numerals. First, the basic structure and the function will be explained in more detail with reference to FIG. 1.

A door piston 100 shown acts on the left with a piston surface 101 on a pressure chamber D1 and on the right with a piston surface 102 on a pressure chamber D2, the two pressure chambers D1 and D2 being fluidly connected to an overflow line 12 and 13. Both the overflow line 12 and the overflow line 13 are each assigned a presettable throttle 121 and 131. Furthermore, the overflow line 12 has a check valve RV1, which closes in the flow direction from the pressure chamber 1 to the pressure chamber 2 and is connected in parallel with the throttle 121. A safety check valve RV2 is provided in parallel to the throttle 121 for overload protection.

The pressure chamber D2 is connected to the overflow line 12 on the side opposite the piston surface 102 by a line 14 having a check valve RV3, the direction of action of the check valve RV3 - viewed in the flow direction - being directed towards the overflow line 12. The Turkolben 100 on the right has a smaller diameter extension 110 which passes through the pressure chamber D2 and its effective piston ^¬ surface 111 to an intermediate pressure chamber D3 affects the right of the middle pressure chamber D3 located is a pressure acting on it with his left Kolbenfiäche 201 plunger 200 is disposed A further pressure chamber D4 is assigned to this pressure piston 200 on the right, on which the pressure piston 200 acts with its right piston surface 202 and on which a pressure spring 30 which is fixedly supported on a pressure plate 31 is pressed

The pressure chamber D4 and the middle pressure chamber D3 are fluidically connected via a conduit 15, wherein this one - viewed in the direction of flow to the pressure chamber D4 - closing check valve RV4 having Further, there is a fluidically effective connection of the pressure space D4 _ü via a line 16 to the Overflow line 12

The pressure chamber D1 acts fluidly by means of a control line 41 on a check valve 40 designed as a 2/2-way valve, which connects the pressure chamber D2 with the further pressure chamber D4 via a line 42 in its outlet line

The Turkolben 100 includes a toothing 103 by means of which the rotational ^¬ movement one with the toothing walzend engaged stationary pinion 51 of the output shaft 50 in an axial movement of the Turkolbens set to ^¬ 100 is of the teeth 103 comprising part of the piston 100 with fluid filled The piston 100 also has a radial seal 104 on the side facing the piston surface 102. In this way, the space of the toothing 103 is fluidly assigned indirectly to the pressure chamber D1, as a result of which the fluid lubricates the toothing 103 and the pinion 51 simultaneously

Furthermore, the extension 110 has a bore 17 emerging in the piston surface 111 _, into which a transverse bore 18, which extends transversely in the extension 110 and extends as far as the bore 17, merges. The transverse bore 18 is in one Distance x from the piston surface 111 This distance x determines the location with respect to the angle of rotation φ of the door, when a change in the gear ratio is to occur, so that, in terms of control technology, that predetermined point y at which a strong closing force is desired. The pistons and their surfaces are each shown with a broken line in FIG.

As can be seen from FIGS. 1 b and 2, the line 15 and the check valve RV4 can also be assigned to the pressure piston 200. Furthermore, the pressure piston 200 can separate the pressure chamber D4 into a pressure chamber D4 (first parts) and a pressure chamber D4 ^* ( part two), a flow cross-section 19 being provided between the two spaces D4 and D4 ^* , which can also have a throttling function. For fine adjustment of the spring force, the abutment of the spring 30 on the housing side is designed as an axially adjustable pressure plate 31

As shown in FIGS. 2 and 3c, the piston surface 201 of the pressure piston 200 has a recess 203 with a smaller diameter, so that between the piston surfaces 111 and 201 no adhesive forces preventing the door piston 100 from lifting off can occur. One or both of the piston surfaces can do this 111 and / or 201 also have a spherical shape, or a turn 203 can also be assigned to the projection 110.

The diameters of the pistons are to be selected such that the diameter of the shoulder 110 is smaller than that of the door piston 100, but the diameter of the pressure piston 200 is larger than that of the shoulder 110, but again smaller than that of the door piston 100.

The volume resulting from the pressure spaces and channels or lines is filled with hydraulic oil and vented

In the starting position, as shown in FIGS. 2 and 3a, the door piston 100 together with attachment 110 is in its starting position, which is the Closed door corresponds to this starting position is maintained under force when the piston surface 201 of the pressure piston 200 acts positively on the piston surface 111 of the shoulder 110

If the door is now opened, as shown in FIG. 3b, the turk piston 100 and the pressure piston 200 begin to move to the right with positive locking in accordance with the opening movement of the door transmitted from the output shaft 50 and the pinion 51 to the rack 103. This flows from the Pressure chamber D2 fluid via line 42 and the opened 2/2 way shut-off valve into pressure chamber D4 Line 14 is closed by check valve RV3.The fluid volume displaced by pressure piston 200 immersed in pressure chamber D4 flows proportionally via line 16 and overflow line 12 into the pressure chamber D1, the non-return valve RV1 being open. Fluid flows through the line 15 contained in the pressure piston 200 into the increasingly increasing central pressure chamber D3. This relationship - that is to say a transmission ratio of ι = 1 - remains until the maximum open position is reached Obtain the corresponding end position of the pistons 100 and 200, w ie this can be seen from FIG. 4

If no more force is exerted on the door from the outside in the opening 4, the force of the spring 30 acting on the pressure piston 200 moves the pressure piston 200 in the closing direction 5, with the check valve RV4 simultaneously causing fluid to escape from the middle pressure chamber D3 prevents and, due to the pressure increase in the pressure chamber D1, the check valve 40, which is designed as a 2/2-way valve, is transferred into its blocked position by means of the control line 41 and thus the line 42 is interrupted. As a result, only fluid flows from the pressure chamber D1 via the overflow line 12 and only throttled via line 14 through throttle 121 proportionally into pressure spaces D2 and D4

For each displacement travel unit of the pressure piston 200, a certain volume column is displaced by it, in accordance with the smaller diameter. Knife of the approach 110 of the door piston 100 this results - since the middle ^¬ pressure space D3 is fluid-tight - a transmission ratio with i> 1. The door piston 100 thus lifts from the pressure piston 200.

The translation i remains until - as shown in FIG. 4 - the transverse bore 18 of the centrally arranged bore 19 passing through the shoulder 110 and corresponding to the desired location y creates a fluidic connection between the pressure chamber D3 and the pressure chamber D2. At this moment, the gear ratio jumps to a gear ratio i <1 - that is, a reduction ratio - until the end face 201 of the pressure piston 200 again lies on the pressure face 111 associated with the attachment and then the gear ratio again assumes 1: 1.

The RV2 pressure relief valve prevents damage to the door closer when the door is subjected to external force.

In Fig _. 2 also shows that the pistons are assigned to a housing 1 and the spring 30 is accommodated in a further housing 2 connected to the housing 1 by means of a screw connection 3. In this way, the demand for differently strong closing springs can be met in a particularly simple manner. By assigned to the further _housing, externally accessible adjustment means in the form of a spring pressing on the pressing plate 31, the spring is particularly easy as well ^¬ biased also be finely adjusted as.

Reference number list

1 housing

2 housings

3 screw connection 4 opening direction

5 closing direction

12 overflow line

13 overflow line

14 line 15 line

16 line

17 hole

18 cross hole

19 River cross section 30 compression spring

31 pressure plates

40 check valve (2/2-way valve)

41 control line

42 Line 50 output width

51 sprockets

100 flasks

101 piston surface

102 piston surface 103 toothing

104 radial seal

110 approach

111 piston surface

121 throttle 131 throttle

200 pressure pistons 201 piston area

202 piston area

203 start-up

X distance y predetermined position

D1 pressure room

D2 pressure room

D3 pressure room

D4 pressure chamber (first part)

D4 ^* pressure chamber (second part)

RV1 check valve

RV2 safety check valve

RV3 check valve

RV4 check valve φ angle of rotation

Claims

Patent claims

1 door closer with a door piston (100) acting on an output shaft (50) with a shoulder (1 10), a pressure piston (200) and an energy accumulator (30) acting on it, the pistons (100, 200) in one Housing (1) are guided in an axially displaceable manner, and with a first pressure chamber (D1) and a second pressure chamber (D2), which are connected to an overflow line (12) and assigned to the Turk piston (100), a middle pressure chamber (D3), which is assigned to the approach (1 10) and the pressure piston (200) and at least one further pressure chamber (D4,

D4 ^* ), which is assigned to the pressure piston (200), whereby the overflow line (12) can have a throttle and the pistons or the housing each have channels connecting the pressure chambers, and the Turk piston (100) by means of the offset approach (1 10) in the opening direction (4) in a form-fitting manner

Pressure piston (200) resting and in the closing direction (5) - hydraulically decoupled from the pressure piston - is first hydraulically and then mechanically in operative connection

Door closer according to claim 1, characterized in that the middle pressure chamber (D3) is fluidly connected on the one hand to the second pressure chamber (D2) by means of an extension assigned to the shoulder (110) of the door piston (100), depending on the displacement path of the door piston (100). closable or openable channel (transverse bore 18, bore 17) and on the other hand with the further pressure chamber (D4) by means of one from the middle pressure chamber

(D3) effective check valve (RV4) having channel (15), and that the second pressure chamber

(D2) is fluidly connected to the further pressure chamber (D4) assigned to the pressure piston (200) via a channel (14 16) having a check valve (RV3), as well as to the overflow line (12) and to a Channel (42), which is assigned a check valve (40) which is continuously switched in the rest position and which is transferred to its blocking position when the pressure in the first pressure chamber (D1) increases.

3. Door closer according to claim 2, characterized in that the channel (15) connecting the middle pressure chamber (D3) and another pressure chamber (D4) together with the check valve (RV4) is arranged in the pressure piston (200) or housing (1).

4. Door closer according to claim 2, characterized in that the pressure chamber (D4) is divided into a first part (D4) and a second part (D4 ^* ), the rooms (D4, D4 ^* ) having one

Flow cross section (19) are fluidly connected to one another, which can be designed to act as a throttle.

5. Door closer according to one of claims 1 to 4, characterized in that the mutually facing piston surfaces (1 1 1, 201) of the two pistons (100, 200) are designed such that sticking together through adhesion is avoided.

6. Door closer according to one of claims 1 to 5, characterized in that the side of the door piston (100) having the piston surface (102) has a radial seal (104).

7. Door closer according to one of claims 1 to 6, characterized in that the two pistons (100, 200) are assigned to a housing (1) and the energy accumulator (30) is assigned to a further housing (2).

8. Door closer according to claim 7, characterized in that the housing (1) and the housing (2) are coupled by means of a radial screw connection (3).

9. Door closer according to one of claims 7 or 8, characterized in that the housing (2) is in the energy storage (30). assigned, externally accessible adjustment means (pressure plate 31).

Door closer according to one of claims 1 to 9, characterized in that the energy accumulator (30) is designed as a mechanical, hydraulic, pneumatic or electrical energy accumulator, whereby it can have a linear or progressive characteristic curve

Door closer according to one of claims 2 to 10, characterized in that the actuatable check valve (40) is a mechanically, hydraulically, pneumatically or electrically actuated 2/2-way valve.

Directional valve is, with the first pressure chamber (D1) being assigned means for pressure-dependent control (control line 41) of the check valve (40).

Door closer according to one of the preceding claims, characterized in that instead of the throttle (121), the overflow line (12) is assigned a check valve (RV3) which closes parallel to it in the direction of flow from the first pressure chamber (D1) to the second pressure chamber (D2).

Door closer according to one of the preceding claims, characterized in that the overflow line (12) at the location of

Throttle (121) is provided parallel to this, a pressure relief valve (RV2) which blocks in the flow direction to the first pressure chamber (D1).