EP0956415B1 - Door closer for generating a speed-increasing leap during the closure phase - Google Patents

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

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

A door closer has become known from SE 469 342 B. a closing torque characteristic adapted to the door angle is achieved by opening one that first acts on the door piston first spring and then in series one acting on the pressure piston second spring is tensioned. When closing, there are those on the door piston first acting spring its energy, the second spring in tension Position persists until one is centered in both pistons Slide fluidically through a channel system that stops the pressure piston Relieved pressure chamber, so that now the second spring Can give energy to the output shaft.

This door closer is capable of different moments depending on the door opening on the door, however, requires an extraordinary high manufacturing costs.

In particular, extremely precise and therefore expensive production is required of the door piston engaging in the pressure piston with its attachment as well as the pressure piston itself. To make matters worse, the Pressure piston in addition to the fit assigned to the door piston two more Has fits that have corresponding housing fits are assigned in alignment. This also makes the production considerably more expensive.

Finally, the known door closer has a switching valve that Centrally arranged slide on, both in the door piston as well as axially displaceable, hydraulically sealed.

This means that diameter tolerances add up to what is involved in production of such a door closer demands the highest precision provides.

A further disadvantage is the fact that there are numerous seals to be sealed against one another Pressure rooms are required by means of a complicated Channel system fluidly communicate with each other and thus the desired Closing torque characteristics depending on temperature - especially in cold weather - is severely impaired. The well-known also Door closers place high demands on the assembly personnel, as they are fluid effective, interlocking cylinder surfaces when mating of the door piston and the pressure piston as well as the one that penetrates both Slider can easily be damaged.

Another door closer is known from DE 195 49 373 A1. This Door closer has a door piston acting on an output shaft one shoulder, one pressure piston and one acting on it Lift mechanism on. The pistons are axially displaceable in a housing guided. Furthermore, this known door closer has a first pressure chamber and a second pressure chamber connected to an overflow line and the door piston are assigned, as well as an average pressure chamber on, which is assigned to the approach and the pressure piston. Moreover at least one further pressure chamber is provided, which is the pressure piston assigned. The overflow line can have a throttle and the pistons and the housing each have the pressure chambers connecting channels. The door piston lies by means of the offset shoulder in the opening direction on the pressure piston and is in Closing direction - hydraulically decoupled from the pressure piston - first hydraulic and then mechanically in operative connection.

The object of the invention is therefore to provide a particularly economical simple door closer to provide the different Can realize moment profiles.

This object is solved by the features of claim 1.

In a door closer according to the invention are interlocking Avoided pistons. Furthermore, only a single pressure accumulator is required. The effort for manufacturing and assembly is significantly reduced. The related fits of the housing or the Pistons can be manufactured in one setup, which improves the running accuracy the corresponding cylinder or piston surfaces without additional Effort significantly improved and on the other hand the number of Machining cycles is reduced. This is also the channel system greatly simplified, so that no elongated channels are required and therefore the ventilation is very simplified during assembly. This will leakage almost impossible.

Here, the middle pressure chamber and a further pressure chamber connecting channel and check valve depending on the design conditions be arranged in the pressure piston or housing.

It can also be used to control the closing speed of a door closer according to the invention the space of a pressure space in a first Part and a second part can be divided, both rooms being fluid connected to each other via a flow cross section acting as a throttle are.

It is advantageous if the mutually facing piston surfaces of the two Pistons are designed so that sticking together by adhesion is avoided.

In particular, the requirement for a modular design can be achieved according to the invention thereby be met if the two pistons are 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 are coupled by means of a radial screw connection. hereby all that is required is a standard type of piston receiving the piston Housing, with the different, the required Housing adapted to the clamping forces can easily be screwed on. there Complicated assembly steps, as in the state of the art in Factory are required.

For this purpose, a force storage device associated with the energy store can advantageously be externally accessible adjustment means can be provided, whereby the Closing force is continuously adjustable in a wider range.

According to the invention, it is also advantageous if the actuatable Check valve a mechanically, hydraulically, pneumatically or electrically operated 2/2-way valve, wherein the first pressure chamber means for pressure-dependent control of the check valve are assigned.

According to the invention, it is necessary to implement overload protection then only one parallel to the throttle in the flow direction overpressure valve blocking the first pressure chamber.

Further advantageous configurations result from the remaining subclaims.

Furthermore, the invention is more or less based on the figures schematically illustrated embodiments described in more detail.

Figur 1a:

Eine Strukturdarstellung eines Türschließers nach der Erfindung,

Figur 1b:

eine Einzelheit einer alternativen Ausgestaltung eines erfindungsgemäßen Türschließers,

Figur 2:

ein erstes Ausführungsbeispiel eines Türschließers nach der Erfindung,

Figur 3:

ein zweites Ausführungsbeispiel der Erfindung in den Stellungen:

Figur 3a:

Tür geschlossen,

Figur 3b:

Öffnungsbeginn,

Figur 3c:

Tür offen,

Figur 3d:

Umkehrung des Übersetzungsverhältnisses während des Schließvorganges und

Figur 4:

den Graph des Übersetzungsverhältnisses des Türschließers in Abhängigkeit des Drehwinkels der Tür.

It shows:

Figure 1a:

A structural representation of a door closer according to the invention,

Figure 1b:

a detail of an alternative embodiment of a door closer according to the invention,

Figure 2:

a first embodiment of a door closer according to the invention,

Figure 3:

a second embodiment of the invention in the positions:

Figure 3a:

Door closed,

Figure 3b:

Start of opening,

Figure 3c:

Door open,

Figure 3d:

Reversal of the gear ratio during 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, based on 1 shows the basic structure and the function explained in more detail become.

A door piston 100 shown acts on the left with a piston surface 101 a pressure chamber D1 and on the right with a piston surface 102 on one Pressure chamber D2, the two pressure chambers D1 and D2 with an overflow line 12 and 13 are fluidly connected. Both the overflow line 12 and the overflow line 13 are each pre-settable Throttle 121 and 131 assigned. Furthermore, the overflow line 12 a closing in the flow direction from the pressure chamber D1 to the pressure chamber D2, Check valve RV1 connected in parallel to throttle 121. to Overload protection is a safety check valve parallel to throttle 121 RV2 provided.

The pressure space D2 is on the opposite side of the piston surface 102 Side with a line 14 having a check valve RV3 the overflow line 12, wherein the direction of action of the check valve RV3 - seen in the direction of flow - to the overflow line 12 is directed.

The door piston 100 has a lug with a smaller diameter on the right 110, which passes through the pressure chamber D2 and its effective piston surface 111 acts on a medium pressure space D3. Right of the middle Pressure chamber D3 is located on it with its left piston surface 201 acting pressure piston 200 arranged. This pressure piston 200 is on the right another pressure chamber D4 is assigned to which the pressure piston 200 acts with its right piston surface 202 and on which one a pressure plate 31 stationary pressure spring 30 presses.

The pressure chamber D4 and the middle pressure chamber D3 are by means of a line 15 fluidly connected, this one - in the direction of flow to the Pressure chamber D4 seen - closing check valve RV4 has. There is also a fluidically effective connection to the pressure chamber D4 via a line 16 to the overflow line 12.

The pressure chamber D1 acts on a fluid by means of a control line 41 2/2-way valve formed check valve 40, which is in its starting position the pressure chamber D2 with the further pressure chamber D4 via a line 42 combines.

The door piston 100 has a toothing 103 by means of which the rotary movement a pinion that meshes with the toothing 51 of the output shaft 50 converted into an axial movement of the door piston 100 becomes. The part of the piston 100 which has the toothing 103 is filled with fluid. The piston 100 also faces the piston surface 102 facing side a radial seal 104. That way the space of the toothing 103 is fluidly assigned indirectly to the pressure space D1, whereby the fluid the toothing 103 and the pinion 51st lubricates at the same time.

In addition, the projection 110 has an outlet in the piston surface 111 Bore 17, in which a transverse to 110 approach to the hole 17 reaching cross hole 18 opens. The cross bore 18 is in one Distance x from the piston surface 111 is arranged. This distance x determines the location regarding the angle of rotation ϕ of the door, when a change the gear ratio should occur, is therefore control engineering the specified point y at which a strong closing force is desired is. The pistons and its surfaces are each interrupted in FIG Line shown.

As can be seen from Figure 1b and Figure 2, the line 15 and the check valve RV4 can also be assigned to the pressure piston 200. Furthermore, the pressure piston 200 can move the pressure chamber D4 into a pressure chamber D4 (first parts) and a pressure chamber D4 * accommodating the spring 30 Divide (second part), dividing D4 and D4 * between the two rooms Flow cross section 19 is provided, which also have a throttle function can. The abutment on the housing is for fine adjustment of the spring force the spring 30 is formed as an axially adjustable pressure plate 31.

As FIG. 2 and FIG. 3c show, the piston surface 201 of the pressure piston has 200 a projection 203 with a smaller diameter, so that no lifting of the door piston between the piston surfaces 111 and 201 100 preventive adhesive forces can occur. This can one or both of the piston surfaces 111 and / or 201 also a crowned Have shape or a projection 203 can also approach 110 be assigned.

The diameter of the piston should be chosen so that the diameter of the approach 110 is smaller than that of the door piston 100, but the diameter of the pressure piston 200 larger than that of the approach 110, however is again smaller than that of the door piston 100.

That resulting from the pressure rooms and channels or lines Volume is filled with hydraulic oil and vented.

In the starting position, as shown in Figures 2 and 3a, the Door piston 100 together with attachment 110 in its initial position, that of the closed door corresponds. Due to the piston surface 111 of the Approach 110 positively acting piston surface 201 of the pressure piston This initial position is maintained under force in 200.

If - as shown in Figure 3b - the door is opened, the door begins Door piston 100 and the pressure piston 200 with positive locking accordingly that of the output shaft 50 and the pinion 51 onto the rack 103 transmitted opening movement of the door to move to the right. in this connection fluid flows from the pressure chamber D2 via the line 13 and the overflow line 12 in the pressure chamber D1. Line 14 is from the check valve RV3 closed. That by the one immersed in the pressure chamber D4 Pressure piston 200 displaced fluid volume overflows proportionately the line 16 and the overflow line 12 in the pressure chamber D1, wherein the check valve RV1 is open. The time-dependent opening behavior is adjustable by the throttle 121 and the throttle 131. Fluid flows into the line 15 contained in the pressure piston 200 increasing increasing mean pressure space D3. This connection - i.e. a gear ratio of i = 1 - remains until it is reached the end position corresponding to the maximum open position of the door pistons 100 and 200 are obtained, as can be seen from FIG is.

If no external force is exerted on the door in opening direction 4, the spring acting on the pressure piston 200 30 of the pressure piston 200 moves in the closing direction 5, at the same time the check valve RV4 an escape of fluid from the middle Pressure chamber D3 prevented and by the pressure increase in the pressure chamber D1, the shut-off valve 40 designed as a 2/2-way valve by means of the control line 41 transferred to its locked position and the line 42 interrupted becomes. As a result, only more fluid flows over from the pressure chamber D1 the overflow line 12 and only throttled via line 14 through the throttle 121 into the pressure chamber D2.

For each displacement travel unit of the pressure piston 200 there is one of these certain volume column displaced. According to the smaller diameter The approach 110 of the door piston 100 results in this - since the middle Pressure chamber D3 is fluid-tight - a transmission ratio with i> 1. The door piston 100 consequently lifts off the pressure piston 200.

The translation i> 1 remains until - as shown in Figure 4 - the Approach 110 penetrating, corresponding to the desired location y Cross bore 18 of the centrally arranged bore 19 is a fluid Connection of the pressure chamber D3 with the pressure chamber D2 creates. In this At the moment the gear ratio jumps to a gear ratio i < 1 - that is, a reduction - until the end face 201 of the pressure piston 200 rests on the pressure surface 111 associated with the attachment and then the gear ratio assumes 1: 1 again.

Damage to the door closer is caused by the pressure relief valve RV2 prevented by external force on the door.

FIG. 2 also shows that the pistons are assigned to a housing 1 are and the spring 30 in one by means of a screw 3 the housing 1 connected further housing 2 is housed. On this way, the demand for different can be particularly simple strong closing springs are met. Because of the wider housing assigned, externally accessible setting means in the form of a the pressure plate 31 pressing the spring, the spring can in particular simply be both preloaded and fine-tuned.

References list

1

casing

2

casing

3

screw

4

opening direction

5

closing direction

12

overflow

13

Überstömleitung

14

management

15

management

16

management

17

drilling

18

cross hole

19

flow area

30

compression spring

31

printing plates

40

Check valve (2/2-way valve)

41

control line

42

management

50

output shaft

51

pinion

100

door piston

101

piston area

102

piston area

103

gearing

104

radial seal

110

approach

111

piston area

121

throttle

131

throttle

200

pressure piston

201

piston area

202

piston area

203

Andre Hung

x

distance

y

predetermined position

D1

pressure chamber

D2

pressure chamber

D3

pressure chamber

D4

Pressure room (first part)

D4 *

Pressure chamber (second part)

RV1

check valve

RV2

Security check valve

RV3

check valve

RV4

check valve

φ

angle of rotation

Claims (12)

1. A door closer comprising a door piston (100) with an attachment (110) operating on an output shaft (50); a pressure piston (200) and an energy accumulator (30) acting thereon, wherein the pistons (100, 200) are movably guided in axial direction in a housing (1) and are connected with a first pressure chamber (D1) and a second pressure chamber (D2), which are connected to an overflow line (12) and associated with the door piston (100); a central pressure chamber (D3) associated with the attachment (110) and with the pressure piston (200); as well as at least one additional pressure chamber (D4, D4*) associated with the pressure piston (200), wherein the overflow line (12) may present a throttle and the pistons respectively the housing are provided with ducts connecting the pressure chambers and wherein the door piston (100), via the reduced diameter attachment (110), in the opening direction (4) is positively adjoining the pressure piston (200) and in the closing direction (5), adapted to be hydraulically uncoupled from the pressure piston, is first hydraulically and then mechanically in operative connection, characterised in that the central pressure chamber (D3) is in fluid connection, on the one hand with the second pressure chamber (D2) via a. duct (transversal bore 18, bore 17) associated with the attachment (110) on the door piston (100) and adapted to be closed or opened in dependence on the distance travelled by the door piston (100), and on the other hand with the additional pressure chamber (D4) via a duct (15) presenting a non-return valve (RV4), operative from the central pressure chamber (D3), and in that the second pressure chamber (D2) is in fluid connection with the additional pressure chamber (D4) associated with the pressure piston (200) via a duct (14, 16) presenting a non-return valve (RV3) as well as with the overflow line (12) and with a duct (42) associated with a stop valve (40), which is switched to be open in the position of rest and which is moved into its closed position when the pressure rises in the first pressure chamber (D1).
2. A door closer according to claim 1, characterised in that the duct (15) connecting the central pressure chamber (D3) and the additional pressure chamber (D4) including the non-return valve (RV4) are arranged inside the pressure piston (200) or in the housing (1).
3. A door closer according to claim 1, characterised in that the additional pressure chamber (D4) is divided into a first compartment (D4) and a second compartment (D4*), the two compartments (D4, D4*) being in fluid connection via a flow cross-section (19), which can be executed to act as a throttle.
4. A door closer according to any of claims 1 to 3, characterised in that the facing piston surfaces (111, 201) of the two pistons (100, 200) are executed in a way as to prevent sticking together by adhesion.
5. A door closer according to any of claims 1 to 4, characterised in that the side of the door piston (100) having the piston surface (102) presents a radial seal (104).
6. A door closer according to any of claims 1 to 5, characterised in that the two pistons (100, 200) are associated with a housing (1) and the energy accumulator (30) is associated with an additional housing (2).
7. A door closer according to claim 6, characterised in that the housing (1) and the additional housing (2) are coupled via a radial screw connection (3).
8. A door closer according to any of claims 6 or 7, characterised in that the additional housing (2) presents an adjusting means (pressure plate 31) accessible from the outside and associated with the energy accumulator (30).
9. A door closer according to any of claims 1 to 8, characterised in that the energy accumulator (30) is executed as a mechanical, hydraulic, pneumatic or electric energy accumulator and can present a linear or a progressive characteristic.
10. A door closer according to any of claims 1 to 9, characterised in that the actuatable stop valve (40) is a 2/2-way valve that can be actuated mechanically, hydraulically, pneumatically or electrically, the first pressure chamber (D1) being associated with means (control line 41) for controlling the stop valve (40) depending on pressure.
11. A door closer according to any of the preceding claims, characterised in that the overflow line (12), in the area of the throttle (121), is associated with a non-return valve (RV1) parallel to the throttle and closing in the direction of flow from the first pressure chamber (D1) to the second pressure chamber (D2).
12. A door closer according to any of the preceding claims, characterised in that the overflow line (12), in the area of the throttle (121), is provided with a relief valve (RV2) parallel thereto and closing in the direction of flow to the first pressure chamber (D1).

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