Source: https://patents.google.com/patent/WO2011066947A1/en
Timestamp: 2018-04-26 13:44:12
Document Index: 112558014

Matched Legal Cases: ['art 44', 'art 43', 'art 43', 'art 43', 'art 44', 'arts 43', 'arts 43', 'art 44', 'art 44', 'art 43', 'art 44', 'art 43', 'art 43', 'art 12', 'art 12', 'art 12', 'art 13', 'art 12', 'art 13', 'art 13', 'art 13', 'art 13', 'art 12', 'art 12', 'art 26', 'art 26', 'art 26', 'art 26', 'art 26', 'art 26', 'art 44', 'art\n14', 'art\n27', 'art\n44', 'art\n45']

WO2011066947A1 - Door closer with free-swing function - Google Patents
WO2011066947A1
WO2011066947A1 PCT/EP2010/007255 EP2010007255W WO2011066947A1 WO 2011066947 A1 WO2011066947 A1 WO 2011066947A1 EP 2010007255 W EP2010007255 W EP 2010007255W WO 2011066947 A1 WO2011066947 A1 WO 2011066947A1
PCT/EP2010/007255
The invention relates to a door closer, in particular a pivoting door closer, with a free-swing function, comprising a door closer housing, an output shaft that can be connected to a door, a piston assembly which is connected to the output shaft and which is guided in the door closer housing, a closing spring, a piston rod arranged for connecting the piston assembly to the closing spring, a free-swing arrangement which is designed to enable a translational movement of the piston assembly in a decoupled manner from the closing spring when the closing spring is blocked and which is designed as a displacement coupling that transmits pressure forces exclusively between the closing spring and the piston assembly. The door closer also comprises a hydraulic blocking chamber designed to block the closing spring.
The invention relates to a door closer with a freewheeling function
The prior art distinguishes between door closers and door operators. The closer the door of a person must be opened manually. During the opening process is energy, for example, stored in a closing spring and door closer can close the door automatically by the stored energy. In contrast, the door drive is an arrangement which by means of additional auxiliary energy, for example by means of electric motor and linkage, the door automatically opens and closes again. Especially when considering the hydraulic circuits in door drives and door closers one realizes significant differences. For electromechanical door drives a motor and a pump are always present, which apply the necessary hydraulic pressure. The respective pressure chambers are then actively supplied with hydraulic pressure, thereby opening the door is effected. The pressure is thus generated in the door drive by the internal components, motor and pump. In contrast, pressure chambers fill in a door closer by expansion of the chambers and by sucking the hydraulic oil from other areas of the door closer. Here is introduced by opening the door, the energy for the closing spring and the pressure build-up in the door closer. The forces and moments as well as the loads occurring as a result are usually different for a door closer and a door drive. The door operator must also have the energy for accelerating the door in the opening direction while the door the door closer in the opening direction is accelerated by the user. It is an object of the present invention to provide a door closer, which is constructed very narrow in cost-effective production, and thus is also used as a door closer integrable in for example a frame or a door. In addition, the door closer is to have a one-way function.
The object is solved by the features of the independent claims. The dependent claims relate to advantageous developments of the invention to the object.
Thus, the object is achieved by a door closer, in particular rotary door closer with a freewheeling function, comprising a door closer housing, a connectable to a door output shaft connected to said driven shaft and guided in the door closer housing piston assembly, a closing spring, an arranged to connect the piston assembly with the closing spring piston rod, a freewheel arrangement which is adapted to a translational movement of the piston assembly is uncoupled from the closing spring with blocked closing spring to allow a trained and for blocking the closing spring hydraulic lock space. Further, the freewheeling arrangement is designed as a sliding coupling, which only transmits compressive forces between the closer spring and of the piston assembly.
no fixed connection between the closer spring and piston assembly must exist for the one-way function. Therefore, a pushing compound is used according to the invention, which only transmits pressure forces.
Preferably, the door closer comes with freewheeling function in facilities for the physically disabled, senior housing and kindergartens and to hedge on fire doors used. In combination with a fire alarm system to close these doors will be secured to prevent smoke and fire spread without having to expect the door users a permanent opening moment conventional door closers. Especially with fire doors normally very strong springs must be used, so that a safe closing of the door can be ensured even with a breeze in corridors. The margins of these normally springs at each opening of the door in particular children, sick people and the elderly can not be expected. The freewheeling function allows here that the closing spring is biased only once and remains until the eventual fire biased. The presented door closer can be used due to the very narrow width invisibly in the door leaf or in the frame, which brings no visual impairment with and protects against damage from vandalism.
Preferably, the door closer comprising a door closer arranged in the housing between the piston assembly and the closing spring fluid-tight partition wall, wherein the piston rod fluid-tightly passes through the partition wall. The partition is fixed and sealed to the door closer housing. Between the piston rod and the partition wall, a mechanical seal is preferably used. There are usually combines several seals to achieve nearly 100% tightness. With only one seal comprises a groove ring seal is used as an alternative. Further comprising the door closer advantageously one out in the door closer housing and bearing against the closing spring closing spring tension piston. The piston rod thus transmits the force from the piston assembly to the closer spring tension piston. On closer spring tension piston, the closing spring is on.
Advantageously, the locking space is formed between the partition and the closing spring tensioning piston. On one side of the partition, the piston assembly is thus with the output shaft. The piston rod transmits the forces through the partition to the other side. There, the barrier chamber, the closing spring tensioning piston and the closing spring are arranged. For the included door closer mechanism freewheel function, the closing spring must, also known as energy storage spring, are held by the hydraulic lock space in prestressed able to prevent the immediate closure of the door after the manual opening operation. Since the direction of action of the closing spring is directed through the piston assembly to the output shaft, the additional closing spring tensioning piston is preferably used, which acts via the piston rod to the piston assembly. In connection with the piston rod and the partition wall of the hydraulic barrier chamber for the hydraulic locking of the closing spring thus produced. The piston rod extends through the lock chamber, whereby the barrier chamber is also to be designated as an annular space. On this construction of the door slider invention a crucial difference between previously known door drives and the presented door closer must be explained well. When previously known door drive active set from a hydraulic pump pressurized oil volume is pumped into the pressure chambers and thus biased, an energy storage spring with a spring tensioning piston. In contrast, the displaced featured door closer the corresponding to the stroke volume of oil during the manual opening operation from other housing areas in the lock chamber and the outflow from the neutral zone, for example, blocked by a solenoid valve. Thus, in the presented here door closer, the stored force of the closing spring is received via the oil pressure and can not initiate to the output shaft via the piston assembly torque. Advantageously, the free-running arrangement between the piston rod and the piston assembly is disposed. Alternatively, preferably, the free-wheel assembly is in the piston rod or between the piston rod and the closing spring, in particular between the piston rod and the closing spring tensioning piston.
Further advantageous is that the freewheel arrangement, a normal to a door closer the longitudinal axis of stationary and fixedly connected with the piston rod first end face, and comprising a connected parallel to the first face and secured to the piston assembly second end face, wherein the second end face first with blocked closing spring of the apart end surface, and therefore decoupled. By two abutting end faces and contrasting a very simple and effective freewheel arrangement can be implemented as a sliding coupling.
Advantageously, in the piston assembly, a pocket is formed, wherein the piston rod is movably guided in the pocket. Alternatively, the bag may for example be carried out in the spring tension piston. In a further alternative, the piston rod is designed in two parts, in which case having a portion of a piston rod in the direction of the longitudinal axis of the door closer open bag and the other part of the piston rod is seated in the pocket movable in translation.
Advantageously, the door closer comprises a door closer housing between the piston assembly and the piston rod out, is firmly connected with the piston rod auxiliary piston, wherein the first end face is formed on the auxiliary piston. Piston rod and auxiliary piston are firmly connected to each other, that is, they move along the longitudinal axis of the door closer always together.
In an advantageous embodiment the auxiliary piston is provided, that the connection between the piston rod and auxiliary piston about a first axis is perpendicular to the running door closer longitudinal axis pivotable. Through these adjustable versions are any forces which could not extend linearly with the door closer longitudinal axis and thus lead to deadlock avoided.
In addition, it is advantageously provided that the connection between the piston rod and closing spring tensioning piston is made about a second axis perpendicular to the door closer longitudinal axis and perpendicular to the first axis of swivel. Also through this pivotal connection between the piston rod and closing spring tension piston a possible jamming is avoided.
For non-locked state of the lock space, the closing spring can act by its biasing force on the piston rod in direct pressure contact within the overrunning clutch to the piston assembly and acting in the opposite direction the piston assembly on the piston rod. In this operating state is a normal door closer operation, in which the closing spring is tensioned manually and the door is moved back to release the door, the closing spring on the piston assembly and the output shaft again in the zero position. If, however, the closing spring hydraulically locked, for example by supplying current to a solenoid valve, the hydraulic oil can not flow out of the barrier chamber. Consequently, the spring force can not act on the piston assembly after one manually loading the closing spring. For manual operation of the door from the open position to the closing direction, the piston rod within the freewheeling arrangement raises, starting especially within the shift clutch of the piston assembly. The piston assembly itself moves driven by the door and the output shaft, and performs a small stroke from. Within the freewheeling arrangement, a current corresponding to the stroke distance of the first end face has formed on the second end face. The return movement of the piston assembly by re-opening the door is performed without force, which corresponds to a one-way function. Further manual opening and closing movements of the door take place at well blocked neutral zone as often and without force in freewheel mode. Only after releasing the lock chamber, the closing spring can move back into a relaxed state. In this case, in the freewheeling arrangement, the first end face is brought into contact again with the second end face and transmit the force of the closing spring on the piston assembly and the output shaft on the door. So that the door is securely closed by the stored energy without additional manual intervention. In a preferred embodiment it is provided that the output shaft comprises a cam-shaped Abwälzkontur, in particular a cam disc, and the piston assembly comprises at least one abutting on the cam roller Abwälzkontur. Door closers with Gleitschienengestänge have prevailed for optical reasons in recent years more and more. In order to simultaneously achieve a comfortable ease of use, that is, a decreasing with increasing door angle opening resistance or decreasing opening torque is used for the inventive door closer preferably within the door closer mechanism, the cam technology to transmit the force between the piston assembly and the output shaft.
In the following the invention with reference to the accompanying drawing will be explained in more detail. In which: Figure 1 shows a door closer according to the invention according to a first.
Fig. 2 shows a door closer according to the invention in the closed
Door position at 0 ° angle with inactive freewheel for all embodiments,
Fig. 3 shows a door closer according to the invention with the door open position at 150 ° opening angle with an inactive free-running for all embodiments
Fig. 4 shows a door closer according to the invention in the closed
Door position at 0 ° opening angle with activated free wheel for all of the embodiments, Fig. 5 a door closer according to the invention during the
Opening operation different with activated free wheel for all embodiments, a detailed view of the freewheel according to the first embodiment, a door closer according to the invention according to a second embodiment with an inactive free-running, the door closer according to the invention according to the second embodiment with activated free wheel, a piston assembly of a door closer according to the invention according to a third embodiment, sectional views of the piston assembly of the third embodiment, a hydraulic circuit symbol of a magnetic directional control valve of a door closer according to the invention according to a fourth embodiment, a hydraulic circuit symbol of a magnetic directional control valve of a door closer according to the invention according to a fifth embodiment of a hydraulic circuit symbol for a magnetic directional control valve of a door closer according to the invention according to a sixth embodiment, the hydraulic 3/2-Magne twegeventil of the door closer according to the fifth embodiment in a de-energized position, the hydraulic 3/2 Magentwegeventil of the door closer according to the fifth embodiment in energized position, Fig. 16 shows a detail from Fig. 15,
Fig. 17, the hydraulic 3/2-directional solenoid valve of the door closer according to the sixth embodiment in a de-energized position, a detail from FIG. 17, and
Fig. 19 shows a door closer according to the invention according to a seventh
In the following, with reference to FIG., The basic structure as well as the hydraulic control and operation of a door closer 41 according to the first embodiment explained. 1 The door closer 41 extends along a longitudinal axis 62. A door closer, the door closer 41 comprises a door closer housing 42, which in turn 43 and a second door closer housing part 44 is composed of a first door closer housing part. In Fig. 1, the various hydraulic lines outside the door closer housing 42 are illustrated. However, this is only for clarity. In actual practice, the hydraulic lines are integrated in the door closer housing 42nd Next, the structure of the door closer 41 along its longitudinal axis 62 door closer is presented from left to right. A first compression spring 45 supported against the door closer housing 42, in particular against a face of the first door closer housing part 43. The first compression spring 45 loaded a piston assembly 94 to pressure. This piston assembly 94 is in the door closer housing 42, in particular in the first door closer housing part 43 out. Opposite the first compression spring 45 engages a second compression spring 52 against the piston assembly 94th This second compression spring 52 abuts against a partition wall 53, in particular housing bulkhead. The partition wall 53 is located at the interface between the first door closer housing part 43 and the second door closer housing part 44. The partition wall 53 is a flange for connecting the two housing parts 43, 44 represents and simultaneously seals the two housing parts 43, 44 from each other. Through the partition wall 53 through a piston rod 54 extends along the longitudinal axis 62. The door closer piston rod 54 is sealed, in particular by means of a mechanical seal, made in the partition wall 53rd The piston rod 54 is fixedly connected to a closing spring tensioning piston 55th This closing spring tensioning piston 55 is in the door closer housing 42, in particular in the second door closer housing part 44 out. At the closing spring tension piston 55, a closing spring 56 connects. The closing spring 56 is supported on one side against the closing spring tensioning piston 55 and on the other side against a setting unit 57 for the Schließerfedervorspannung. Following the setting unit 57 for the Schließerfedervorspannung a 3/2-directional solenoid valve 1 is formed as a cartridge valve, integrated in the door closer housing is 42, in particular in the second door closer housing part 44th
The piston assembly 94 includes, on its first compression spring 45 side facing a damping piston 46 and its piston rod facing 54 side of an opening piston 51. The damping piston 46 includes a rotatably mounted in it first cam roller 47. The opening piston 51 includes a rotatably mounted in it second cam roller 50. between the first cam roller 47 and the second cam roller 50 is a driven shaft 48 formed as a camshaft arranged. The output shaft 48 extends along an output axis 85 perpendicular to the door closer the longitudinal axis 62. This output shaft 48 transmits the force from the piston assembly 94 via a lever linkage or Gleitschienengestänge to the door and on the door on the piston assembly 94. To this end, the output shaft 48 includes a cam-shaped Abwälzkontur 49. the first cam follower 47 and second cam rollers 50 roll on this Abwälzkontur 49th The Abwälzkontur 49 is heart shaped. The damping piston 46, the opening piston 51 and the closing spring tensioning piston 55 are sealingly guided within the door closer housing 42 and comprise for this purpose preferably at their periphery seals or sealing flanges. By this tight guidance of the pistons 42 different spaces or chambers which are connected to each other through various hydraulic lines are formed in the door closer housing. These chambers or spaces are in turn presented in accordance with that shown in Figure 1 structure from left to right along the door closer longitudinal axis. 62: Defined by the left end face of the door closer housing 42, in particular of the first door closer housing part 43, and the damping piston 46, a closure damping chamber 58 is formed , Between the damping piston 46 and the opening piston 51 is a piston assemblies interior 59. This can also be called a camshaft chamber. The piston assemblies inner space 59 is on both sides by the damping piston 46 and sealed the opening piston 51 and is always on the tank pressure level. Between the opening piston 51 and the partition 53 is an opening damping chamber 60. On the other side of the partition 53 is located between the partition wall 53 and the closing spring tensioning piston 55 of the locking space 61. The locking space 61 is defined by the partition wall 53, the wall of the second door closer housing part 44 and the closing spring tensioning piston 55 further includes the door closer 41 comprises a tank space 31. the tank space 31 is located between the closing spring tensioning piston 55 and the solenoid directional control valve 1 and takes the closer spring 56 and the setting unit 57 on. Referring to Figs. 11 to 18 is a precise configuration of the magnetic directional control valve 1 is shown later. In this case, the specific structural design of a preferred tank space 31 is described. In particular, a closing spring receiving space 92 and / or the piston assemblies interior 59 may be co-used by means of unrestricted connections to the tank chamber 31 as a tank.
The door closer 41 further comprising a first hydraulic line, formed as a pressure line P, a second hydraulic line, designed as a working line A, and a third hydraulic line, formed as a tank line T. The three hydraulic lines run parallel to the door closer longitudinal axis 62 in the door closer housing 42nd short, radially or perpendicularly to the door closer longitudinal axis 62 extending channels the three hydraulic lines with the various chambers or spaces in the door closer 41 are connected. Fig. 1 shows the hydraulic lines only schematically. In fact, the hydraulic lines in the door closer housing 42 are integrated. The pressure line P leading from the locking space 61 directly and unthrottled to the solenoid directional control valve 1. The working line A leads from the closed damping chamber 58 directly and unthrottled to the solenoid directional control valve 1. The solenoid directional control valve 1 is further connected to the tank line T. The description as directly and unthrottled means that no separate chokes are provided in the lines. Nevertheless, the pressure may be reduced slightly over any filters and dynamic pressure differences.
The orifice damping chamber 60 is connected via a first throttled connection 78 to the tank line T. To this end, a first throttle valve 65 is used. In addition, between the opening of the damping chamber 60 and the tank line T, a first unrestricted connection 77. The opening of the opening damping chamber 60 in the first unrestricted connection 77 is located closer to the output shaft 48 than the opening of opening the damping chamber 60 into the first throttled connection 78 can thereby the unthrottled connection be closed by the piston opening 51 77 for a particular door opening angle.
The closed damping chamber 58 is connected through a second throttled connection 75, which starts at the end face of the first door closer housing part 43 with the tank conduit T. To this end, a second throttle valve 63 is used. Also located in the outer surface of the door closer housing 42 a third throttled connection 76 between the closure damping chamber 58 and the tank line T with a third throttle valve 64. The piston assemblies inner space 59 is connected via at least unthrottled connected a radial passage with the tank conduit T. In the tank line T, a filter 31 is located. The position of the filter 31 is purely by way of example here. Thus, the filter can, for example, 31 integrated in the solenoid valve. 1 It can also preferred more filters 31 are in the other hydraulic lines. In the damping piston 46, a first check valve 66 is installed. This locks in the direction of the piston assemblies inner space 59. In the normally open piston 51 a second check valve 67 is installed. This also locks in the direction of the piston assemblies inner space 59. In the closing spring tensioning piston 55 a third check valve 68 is provided. This allows hydraulic flow in the direction of the locking chamber 61, and a blocking in the direction of the tank space 31 between the tank space 31 and the tank line T is a fourth check valve provided 69th This check valve is spring-loaded and blocks in the direction of the tank line T. By the first, second and third non-return valve 66, 67 and 68 of the closure damping chamber 58, the Offnungsdämpfungsraum 60 and the locking space 61 can always fill the tank volume when expanded with hydraulic oil. Between the piston rod 54 and the opening piston 51, a freewheel arrangement is formed. The structural configuration of this free-running arrangement will be explained in Fig. 6 in more detail. First, however, 2 to 5 of the function and movement of the door closer 41 is explained in more detail with reference to FIGS.. The function and movement of the door closer 41 according to FIGS. 2 to 5 is applicable to all embodiments presented here. Fig. 2 shows the door closer 41 at 0 ° angular position with relaxed closing spring. Fig. 2 thus the initial position of the door closer is 41. Fig. 3 shows the door closer during the opening operation at an angular position of 150 ° of the drive shaft 48. The door is thereby opened by a person. 48. As a result, rotates the output shaft connected via a linkage to the door frame via the Abwälzkontur 49 the force is transferred to the cam rollers 47, 50. This causes a translational movement of the piston assembly 94 to the right. With the piston assembly 94 and the piston rod 54 and thus the closer spring tension piston 55 is moved to the right. Thus, the closer spring to biases 56th During this opening operation, the pressure line P is closed by means of the solenoid directional control valve. 1 Via the third check valve 68 hydraulic fluid is forced into the barrier chamber 61st The opening process illustrated in Fig. 3 is used for tensioning the closing spring 56. After the tensioning of the closing spring 56 and while maintaining the sealed pressure line P, the freewheel function of the door closer 41 is active. Fig. 4 shows the door closer 41 again in a closed position during a door angle of 0 °. How good to see here, the closer spring 56 remains in the cocked position, as the. Blocking space 61 remains filled with hydraulic oil. Together with the closing spring tensioning piston 55 and the piston rod 54 remains stationary. The piston assembly 94 takes off, thanks to the freewheeling arrangement with a manually made at the door closing movement on the reverse rotation of the drive shaft 42 of the piston rod 54th The piston assembly 94 is free to move here with the door. Only over the two compression springs 45, 52 a slight force is transmitted to the piston assembly 94 so that a steady and play-free contact of the piston assembly 94 to the drive shaft 48 and the cam contour is ensured 49 via the cam rollers 47 and 50th As shown in FIG. 5, remains during the freewheeling function, the closing spring 56 in its cocked and locked position. The door is free to move during which no torque.
Fig. 6 shows a detailed view of the freewheel according to the first embodiment. The freewheeling arrangement is embodied as a sliding clutch. The two essential components of these freewheel arrangement, the first face 74 and second face 72. The first face 74 is parallel to the second face 72. Both faces 74, 72 are perpendicular to the door closer the longitudinal axis 62. The first face 74 is an end face of the piston rod 54th the second end surface 72 is located on the piston assembly 94, particularly at the opening piston 71. in the embodiment shown in Fig. 6 embodiment in the opening piston 51 a pocket 71 is incorporated. In this bag 71, a part of the piston rod 54 engages and is guided therein along the piston guide 73rd The second end face 72 is formed as a bottom of the pocket 71st The two end surfaces 74, 72 thus stand opposite each other in the pocket 71 and, in the case of the free wheel stand out from each other. FIGS. 7 and 8 show a door closer 41 according to a second embodiment. Identical or functionally identical components are provided in all the embodiments with the same reference numerals. Fig. 7 shows a door closer 41 while biasing the closing spring 56. In Fig. 8, the locking space 61 is blocked hydraulically via the pressure line P. This leaves the closing spring tensioning piston 55 and the closing spring 56 in the cocked position. The piston assembly 94 and the door can be moved in freewheeling. The second embodiment corresponds to the first embodiment except as described in the following differences: Unlike the first embodiment, in the second embodiment, an auxiliary piston 95 between the partition 53 and the piston assembly 94, in particular the opening piston 51 are disposed. The auxiliary piston 95 is firmly connected to the transfer of translational movement with the piston rod 54th The first end face 74 is formed frontally on additional piston 95th The auxiliary piston 95 includes a passage, so that both the space between the auxiliary piston 95 and piston assembly 94, and the space between the auxiliary piston 95 and partition wall 53 forming the opening damping space 60th Another difference between the first and second embodiments is that in the second embodiment, the piston rod 54 is pivotally connected to the auxiliary piston 95 and the closing spring tensioning piston 55th The connection between the piston rod 54 and the auxiliary piston 95 is pivotable about a first axis 79th The connection between the piston rod 54 and the closing spring tensioning piston 55 is pivotable about a second axis 80th The two axes 79, 80 are both perpendicular to the door closer the longitudinal axis 62. In addition, is the first axis 79 perpendicular to the second axis 80. Further, the axis 80 is perpendicular to the door closer the longitudinal axis 62. This pivotal connection of the piston rod 54 prevents the occurrence of forces that are not extend parallel to the longitudinal axis door closer 62, a jamming of the assembly. FIGS. 9 and 10 show a piston assembly 94 of the door closer 41 according to a third embodiment. Identical or functionally identical components are provided in all the embodiments with the same reference numerals. The piston assembly 94 of the third embodiment can be preferably used in the door closer 41 according to all embodiments presented here.
The presented in FIGS. 9 and 10, piston assembly 94 replaces the piston assembly 94 in FIGS. 1 to 7, in particular the damping piston 46 with the first cam 47 and the opening piston 51 with the second cam plate 50. The output shaft 48 remains unchanged. By using the piston assembly 94 according to the third embodiment, the first compression spring 45 and the second compression spring 52 are no longer necessary, but nevertheless can be used in addition.
Fig. 9 shows the piston assembly 94, wherein the damping piston 46 and the opening piston 51 by a first tie rod 81, a second tie rod 82, a third tie rod 83 and a fourth tie-rod 84 are interconnected. The four tie rods 81-84 are arranged parallel to the longitudinal axis door closer 62nd In addition, the four rods 81-84 at four corners of a purely for purposes of explanation vorzustellenden rectangle. The output shaft 85 of the output shaft 48 passes through the intersection of the diagonals of this rectangle. This special arrangement of the four tie rods 81-84 the full height of can 91 (see Fig. 10) of the Abwälzkontur 49 arranged at the top between the two tie rods 81, 82 and the two tie rods 83 arranged at the bottom, are 84 are arranged. The height 91 of the 49 Abwälzkontur defines itself in the direction of the output shaft 85. The Abwälzkontur 49 requires no recesses for the tie rods 81-84 and thus can be optimally loaded.
The four tie rods 81-84 are each fixedly connected via screw 87 to the opening piston 51st At its other end, the four rods 81-84 respectively project in through bores of the damping piston 46. Here, the ends of the tie rods 81-84 each screwed with a spring clamping nut 88th The first tension rod 81 and the diagonally disposed to the first tie rod 81 third tie rod 83 are each loaded with a built-in play compensating spring 86 to train. The integrated play compensation springs 86 stuck on the first tie rod 81 and the third tie rod 83 and are located in the damping piston 46. A first, the output shaft 48 remote from the end of the play compensation springs 86 bears against the spring retaining nut 88 which is screwed to the corresponding tie-rod 81, 83 , A second of the output shaft 48 facing the end of each play compensating spring 86 bears against a shoulder 93 (see Fig. 10) formed in the damping piston 46. Due to this special arrangement, the play compensation springs 86, which are designed as compression springs, the first and third pull rod 81, 83 weigh on train. In addition, Fig. 9 shows a first sealing flange 89 on the damping piston 46, which 46 against the door closer housing 42, particularly against the closed damping chamber 58, seals the damping piston. Similarly, the opening piston 51 is sealed by a second sealing flange 90 against the door closer housing 42nd The second sealing flange 90 is formed as a support collar for a piston seal. The opening piston 51 is made in one piece with the second sealing flange 90th These two Abdichtungsflansche 89, 90 are used in the piston assemblies 94 of all embodiments. The integrated play compensation springs 86 are located within a piston of the damping piston, preferably arranged 46th The integrated play compensation springs 86 ensure, in conjunction with their associated tie rods that the smallest greatest possible distance between the two cam followers is maintained 47 and 50 which are spaced by the Abwälzkontur 49, wherein the cam rollers 47 and 50 without play bear against the Abwälzkontur 49th
The integrated play compensation springs 86 are interpreted such that the friction of the components within the piston assembly 94 and the friction of the Abdichtungsflansche is 89 and 90 overcome with respect to the portion of the first door closer housing part 43 because otherwise lifting movement of the assembly 94 in the freewheel mode, the cam rollers 47 and 50 of the Abwälzkontur would stand 49th
By this arrangement, the integrated clearance compensation springs 86 no abutment arises with respect to components of the door closer outside the piston assembly 94, thus no forces to the Abwälzkontur 49 and thus no unwanted torque transmitted to the output shaft 48th
Fig. 10 shows three cross-sectional views of the piston assembly 94 according to the third embodiment. In section BB can be seen that turn the bag 71 is formed in the opening piston 51 here. At the bottom of this pocket is the second end face 72. In this bag 71, the piston rod 54 engages, so that the freewheel function is ensured.
The previously presented embodiments show two basic ways to play compensation between the cam rollers 47, 50 and the Abwälzkontur 49. In the first two embodiments of the damping piston 46 is slightly pressure-loaded by the first compression spring 45 in the direction of the output shaft 48th The opening piston 51 is pressure-loaded by the second compression spring 52 slightly toward the output shaft 48th This ensures a constant contact between the cam rollers 47, 50 and 49. An alternative to this Abwälzkontur shows the third embodiment. Here the lash adjuster is integrated into the piston assembly 94th By tie rods 81-84 and the integrated clearance compensation springs 89 of the damping piston 46 and the opening piston 51 are always slightly contracted, so that the two cam rollers 47, 50 always bear against the Abwälzkontur 49th It is particularly advantageous here that no moment acts on the output shaft 48 and thus remains in the free-wheeling the door in any position. The symmetrical and diagonal arrangement of the four tie rods 81 to 84 is used for absolutely even power transmission, thus preventing any tilting. Therefore, the two clearance compensation springs 46 used on two mutually diagonal connecting rods 81, 83 are arranged. Alternatively, a play compensation spring could be provided 86 also on each of the rods 81-84. Of course, the play compensation springs 86 can be preferably all or in part, in the opening piston 51 are disposed. In addition, the tie rods prevent another 81 -84 rotation of the damping piston 46 and piston opening 51st
Further, the piston assembly 94 can be preferably used according to the third embodiment together with the first compression spring 45 and / or the second compression spring 52nd A specific application of results, for example with very heavy fire doors. The closing force required for the fire caused very strong closers springs 56. Thus, it is desirable for everyday committing the door that the closer spring 56 always remains biased and closes the door, for example in case of fire. Nevertheless, there is a need for a smooth-running and self-closing door, this slight closing should take place after each inspection. Therefore, it is preferable that in each of the presented door closer 41, the second compression spring as "additional closing spring" designed 52, for example after EN1 or EN2, executes said additional closing spring or second compression spring 52 is much weaker than the closing spring 56 . the second compression spring 52 in this embodiment thus loaded even in the freewheel and with blocked closing spring 56, the piston assembly 94, in particular the opening piston 51, always in the closing direction, so that the door even when freewheeling, at least when not so great resistance, automatically closes. the walkers through but does not clamp at each opening operation, the large closing spring 56, but only the very easily performed second compression spring 52, despite everything. in particular, in this embodiment, the piston assembly 94 may preferably as shown in FIGS. 9 and 10 combined to the third embodiment with the second pressure spring 52 become.
Figs. 11, 12, and 13 show a fourth, fifth and sixth exemplary embodiment of a door closer 41, being shown in each case the circuit symbol for the solenoid directional control valve 1 here. Fig. 12 to the fifth output example shows the preferred embodiment here.
The fourth embodiment according to FIG. 11 shows the working line A is saved for closing the damping chamber 58 in such a door closer 41 has a very simple design. The solenoid control valve 1 controls here only one connection of the pressure line P from the locking space 61 to the tank line T. The pressure line P can be open or closed, alternatively, so that the freewheel is selectively disabled or enabled.
Fig. 12 shows the circuit symbol for the fifth embodiment. Here, the pressure line P is connected to the tank line T in a left Pictured energized state of the solenoid directional control valve. 1 The working line A is blocked. The switching position shown on the right shows the energized state of the solenoid directional control valve 1. Here are blocked, the pressure line P and thus the blocking space 61 and consequently the closer spring 56th The closed damping chamber 58 is on the working line A to the tank shorted (see. Fig. 1). Fig. 13 shows the circuit symbol for the sixth embodiment. According to the left-hand illustration the pressure line P is connected to the working line A in the non-energized state. In the energized state according to the right-hand representation the pressure line P, and thus the barrier chamber 61 are blocked. The working line A and consequently the closing damping chamber 58 is shorted to the tank line T.
Figs. 14 to 16 now show the structural design of the solenoid directional control valve 1 according to the door closer 41 according to the fifth output example. Then is presented with reference to FIGS. 17 and 18, a structural design of the solenoid directional control valve 1 for a door closer 41 according to the sixth embodiment. the switching position shown in FIG. 12 is shown on the left side with reference to Fig. 14. FIGS. 15 and 16 show the switching position according to the illustrated right Symbol in Fig. 12. Fig. 14 shows a section through the hydraulic 3/2-directional solenoid valve in the non-energized state. The hydraulic 3/2-directional solenoid valve 1 comprises a valve housing 2, an integrated into the valve housing 2 valve chamber 3, an electromagnet 4 and a valve stem 5. The valve stem 5 moves in longitudinal direction along a valve axis 38th
The valve chamber 3 includes a first valve seat bore 6 as the connection of the pressure line P to the valve chamber 3 and a second valve seat bore 7 as the connection of the working line A 3 to the valve chamber Further, at the valve chamber 3 a free opening 8 to the tank line T formed. The first valve seat bore 6 is the second valve hole 7 directly opposite. The free opening 8 is also executed as a bore, the bore of the free opening 8 is perpendicular to the first valve bore 6 and the second valve bore. 7 In addition, a diameter of the first valve seat bore 6 is substantially made smaller than a diameter of the second valve seat bore. 7
The valve stem 5 is constructed in two parts and comprises a first part 12 and a screwed, and in the first part 12 is thus connected to the first part 12 second part fixed to 13. The second part 13 extends from the interior of the valve chamber 3 through the second valve seat bore 7 through in the direction of the electromagnet 4. the first part 12 is completely outside the valve chamber. 3
The second part 13 of the valve stem 5 comprises on its seat of the first valve bore 6 facing side a first sealing surface, formed as a convex surface 9 (see in particular Fig. 16). This convex surface 9 is formed by a ball 10. The ball 10 in turn is in an end-side recess of the valve plunger 5, in particular the second part 13, embedded. Further, formed on the valve plunger 5, in particular the second part 13, a paragraph. In this paragraph, a valve spring is supported on the 14th The convex surface 9 is located within said valve spring 14. The valve spring 14 is supported further on the end face of the first valve seat bore 6 from. This end face may be referred to as a sealing surface or side surface of the first valve seat bore. 6 By this arrangement, the valve compression spring 14 of the valve stem is loaded in the direction of the electromagnet 4. 5 In the energized state, this leads to an opening of the first valve seat bore. 6
At the second valve seat bore 7 of the valve stem 5, in particular the second part 13 within the valve chamber 3, a second sealing surface, formed as a conical annular surface 11. This conical annular surface 11 is formed around the entire circumference of the valve stem 5 comprises. In the currentless state of the electromagnet 4, this conical annular surface 11 is pressed onto the second valve seat bore 7 and thus seals the working line A relative to the valve chamber 3 from.
The electromagnet 4 comprises a coil 16, an armature 17 and a pole core 18. The coil 16 is wound around the armature 17 and the pole core to the eighteenth The armature 17 and the pole core 18 are arranged along the longitudinal valve axis 38 in a row. In the pole core 18 there is a bore along the valve longitudinal axis 38. This bore forms a linear guide 19 for at least a portion of the valve stem 5, in particular a portion of the first part 12 of the valve stem 5. Between the pole core 18 and the armature 17 is in the energized state on a small gap 20. In the non-energized state, the gap 20 is larger. The electromagnet 4 comprises further a connecting line or power supply 21 for connection to a control / regulation of the hydraulic 3/2-directional solenoid valve 1. The armature 17 and the pole core 18 are embedded in a sleeve 23rd Further, there is an insulation 24 between the sleeve 23 and the coil sixteenth
The pole core 18 and the armature 17 are located in a so-called armature chamber 22. This armature chamber 22 is located within the sleeve 23. The working line A is compared to this armature chamber 22 by a special seal, in particular groove ring seal 25 is sealed. This groove ring seal 25 is located between the valve plunger 5, in particular the first part 12, and the pole core 18 within the valve stem 5, a connecting channel runs 15. This connecting passage 15 connects the armature space 22 with the valve chamber 3. As the valve chamber 3 is always free with the tank line T is connected, thus the armature space 22 is always depressurized. The connecting channel 15 is formed by a longitudinal bore along the longitudinal valve axis 38 in the valve stem 5 and by bores perpendicular to the longitudinal valve axis 38 from the surface of the valve stem 5 to the longitudinal bore. In particular, by the two-piece design of the valve stem 5, the longitudinal bore along the longitudinal valve axis 38 in the interior of the valve stem 5 can be manufactured.
The valve housing 2 comprises a base housing part 26, a first valve chamber insert 27 and a second valve chamber insert 28. The first valve chamber insert 27 and the second valve chamber insert 28 together form the valve chamber 3. The hydraulic 3/2-directional solenoid valve 1 is constructed as follows and as mounted follows: At the electromagnet 4 is an annular projection 29. In this extension 29 a portion of the second valve chamber insert 28 is embedded. The second valve chamber insert 28, in turn, makes the first valve chamber insert 27 into itself. The above-mentioned sleeve 23 of the electromagnet 4 extends up to the second valve chamber insert 28 and is connected thereto. The complete unit consisting of the solenoid 4, the second valve chamber insert 28 and the first valve chamber insert 27 is screwed into the base housing part 26th For this purpose, the base housing section 26 and an inner thread on the extension 29 of the electromagnet 4 is formed a corresponding male thread. The individual housing components are sealed against each other. Furthermore, the housing 2 is a cap 30. This cap 30 encloses the electromagnet 4 and sits on the base housing part 26th Within the first valve chamber insert 27 a drilled insert 35 is introduced. In this drilled insert 35, the first valve seat bore 6 is formed. The insert 35 and the valve chamber insert 27 are preferably used together as a single piece carried out. Moreover, seated in the first valve chamber insert 27, a filter 36. This filter 36 is located outside the valve chamber 3 and in the pressure line P.
Furthermore, it is integrated within the base housing part 26 has a volume compensation unit 37 with tank space 31st This volume compensation unit 37 with tank chamber 31 includes a volume compensating piston 32, a counterbalance spring or length compensation spring
33 and a bearing 35 for the compensating spring 33. The tank chamber 31 is connected to the tank line T. The volume compensating piston 32 defines a wall of the tank space 31 of the piston 32 is slightly spring loaded by the balancing spring 33rd The compensating spring 33 is supported on one side against the volume compensating piston 32 and on the other side against the spring bearing
34.. The spring bearing 34 is frontally screwed into the base housing part 26th The hydraulic 3/2-directional solenoid valve 1 is largely rotationally symmetrical with respect to the longitudinal valve axis 38 is formed. course of this rotational symmetry soft pressure lines P, working lines A and tank lines T from. The pressure line P and the working line A open at at least one point in each case on the outer surface of the base housing part 26. There, annular channels 39 are executed. These annular channels 39 are sealed with O-ring seals 40 when the cartridge-type performed in 3/2-directional solenoid valve 1 is inserted into a corresponding receptacle.
Fig. 15 shows the hydraulic 3/2-directional solenoid valve 1 according to the embodiment in the energized state. Here is good to see that the valve stem is moved 5 compared with the representation in FIG. 14 to the left. Characterized the working line A is connected via the second valve seat hole 7 directly to the valve chamber 3 and thus to the tank line T and the tank space 31st The pressure line P is blocked by the seating of the ball 10 in the first valve bore 6 and thus not connected to the valve chamber. 3
Fig. 16 shows a detail from Fig. 15. At this representation can be illustrated in particular, the difference in area ratio. It should be noted that this differential area ratio is used with a closed second valve seat bore 7 and thus in the embodiment shown in Fig. 14 non-energized valve position. As the, FIG. 16, 5, the valve tappet on the groove ring seal 25 to a sealing diameter D1. The second valve seat bore 7 is formed with an inner diameter D2. The valve stem 5 has a smallest diameter D3 in the region between the groove ring seal 25 and the second valve seat bore. 7 In the closed second valve seat bore 7, the pressure in the working line A in the following areas of the valve stem 5 now acts: The first surface is calculated by (D2 2/4 * π) - (D3 2/4 * π). The second surface is calculated by (D1 2/4 * π) - (D3 2/4 * π). Characterized in that the first surface is smaller than the second surface, the working pressure in the illustration shown, acts in the closed state of the second valve seat bore 7 to the right. Thereby, the valve spring 14 is supported, and the tapered surface 1 1 is drawn into the second valve seat bore. 7
Based on the fifth embodiment has been shown as a hydraulic 3/2-directional solenoid valve 1, in particular in cartridge design, can be carried out for a leak-free operation. In the non-energized switching position, shown in Fig. 14, the valve stem 5 is pushed by the compression spring 14 with the designed as a conical surface 1 1 page in the second valve seat bore 7 of the work line and thus blocks the connection of this line in relation to the tank oil-tight manner. The valve stem 5 is executed on the agnetseite to the armature chamber 22 radially with a groove ring seal 25th The sealing diameter D1 of the valve stem 5 to the armature chamber 22 is made larger than the second valve seat bore 7. This results in a defined area ratio between the conical seat and the sealing diameters D1 of the armature chamber 22. If now the working line A is pressurized, the result is a differential force on the area ratio between the working line and the sealed armature chamber 22, which pulls the valve stem 5 in the direction of the electromagnet 4 and in addition to the spring force against the second valve seat bore 7 acts. With increasing pressure in the working line A, the sealing action increases. The electromagnet 4 is preferably designed such that a shift against the spring force plus differential force is prevented. The pressure line P and the tank line T are connected to each other in this position. In the energized switching position as shown in FIG. 15, the working line A is depressurized, said valve tappet 5 against the spring force with its ball 10, the pressure line P oil-tight seals. A connected via the pressure line P consumers such. As the locking space 61, can now be effectively sealed to the designed operating pressure. This operating pressure is dependent on the magnetic force. In this switching position the working line A is not under pressure connected to the tank line T. Thus, no pressure or only a low back pressure can build up in the working line A.
The embodiments of the proposed 3/2-directional solenoid valve are independent of the cartridge construction and regardless of the number of lines and / or switching positions, according to the invention applicable to other valve types. In particular, the combination of the ball seat and the conical seat in a valve, in particular a ram and / or the differential area ratio according to the invention are applicable to other valves.
Referring to Figs. 17 and 18, the structural design of the solenoid directional control valve 1 of the door closer according to the sixth embodiment will now be explained in detail. Both figures show here the currentless switching position with an open pressure line P, as shown symbolically in Fig. 13 on the left side. Identical or functionally identical components are provided in all the embodiments with the same reference numerals. In particular, the solenoid directional control valve 1, as used in the sixth embodiment, the magnetic-way valve 1, as used in the fifth embodiment is the same, except for the differences described below.
17 and 18 show how the Fig., The tank line T, and the working line A are reversed in the sixth embodiment from the fifth embodiment. This means that the working line is always connected through the free opening 8 with the valve chamber. 3 The connection between the valve chamber 3 and the tank line T is controlled by the second valve seat bore 7 and on the conical annular surface. 11 Furthermore, the valve lifter 5 is executed in the sixth embodiment as one piece. In addition, the path for the pressure equalization between the armature chamber 22 and the tank line T in the solenoid valve 1 according to the sixth embodiment is shorter. Here, the connection 15 is designed as a simple, planar surface between the armature chamber 22 and the tank conduit T. It does not require holes in the valve stem 5. The connection 15 is designed as a planar surface on the valve plunger 5 or by forming the valve stem 5 as a polygon.
Furthermore, the valve housing 2 in the solenoid valve 1 is constructed somewhat easier according to the embodiment. 6 The valve chamber 3 is here no longer in two parts with a first valve chamber insert 27 and a second valve chamber insert 28 constructed. Rather, only one valve chamber insert 27 is installed.
The solenoid valves according to the fourth, fifth and sixth embodiment of the door closer 41 can be used in all 41 preferably presented here, embodiments of the door closer.
Fig. 19 shows a door closer according to a seventh embodiment. Identical or functionally identical components are provided in all the embodiments with the same reference numerals. The presented as part of the seventh embodiment of assembly in order to avoid a so-called spring-back of the closing spring tensioning piston 55 can be applied in all the embodiments presented here, of the door closer 41 is preferred. Fig. 19 shows a configuration of the third check valve 68 in the closing spring tensioning piston 55 as the spring-loaded check valve. The space inside the door closer housing 42, in particular within the second door closer housing part 44, in which the closing spring 56 is positioned is referred to herein as the closing spring receiving space 92nd This closer spring housing space 92 is a space which decreases during the opening process of the door, because the closer spring tension piston 55 moves to the right. In addition, Fig. 19 shows the fourth check valve 69 is also a spring-loaded check valve. The third check valve blocks the hydraulic flow from the lock chamber 61 in the closing spring receiving chamber 92. The fourth check valve blocks the hydraulic flow from the normally open spring receiving space 92 in the tank conduit T. The closing spring receiving space 92 and the tank space 31 are here a space with hydraulic composite. The support disk shown in the setting unit 57 for the spring 56 is no hydraulic partition wall.
In the pressure build-up in the lock chamber 61 all the elastic members contained therein, such as seals, residual air or the hydraulic fluid itself be compressed accordingly, which draws a volume of unwanted degradation. The spring tension piston 55 compensates for this loss of volume, but makes up a small Folgehub. Ultimately, the closer spring tension piston 55 locks are not exactly at the desired location. The arrangement shown in FIG. 19 reduces this resilience by pumped into the lock chamber 61 during the opening operation of the closing spring receiving space 92 active set under pre-pressure hydraulic fluid via the third check valve 68. It is thus aware of a relative resistance to opening similar to a Backcheck generated to bias the hydraulic oil and thus prefetch setting behavior. Thanks to the fourth check valve 69, the hydraulic oil from the closing spring receiving space 92 can not escape in the direction of the tank conduit T. The hydraulic oil is thus brought under pretension by the closing spring tensioning piston 55 during the opening operation in the closing spring receiving space 92, and flows with a certain inlet pressure in the lock chamber 61. As a result, the undesirable spring back is significantly reduced. Further, according to the invention the following items and preferred characteristics are provided:
In a preferred embodiment of the piston assembly is provided that the piston assembly includes a damping piston with a first cam roller and an opening piston having a second cam roller, wherein the output shaft between the damping piston and the opening piston is arranged. The cam roller of the damping piston and of the opening piston must be in constant contact with the Abwälzkontur, and roll around so upon rotation of the output shaft on the Abwälzkontur from. This creates a working stroke of the damping piston and the piston opening. On the longer side of the door closer housing, the closing spring is biased over the opening piston and the piston rod. On the other side of the hydraulically acting damping piston is moved. Due to the displacement of the damping piston is displaced hydraulic volume, whereby it can be controlled by means of throttle valves connected between the door speed in the closing operation or braked. In conjunction with the force of the closing spring is formed on the cam geometry of the Abwälzkontur a resultant force which generates the appropriate internal lever arm of the opening or closing moment. To construct the presented door closer as narrow as possible by building, the opening piston and the damping piston are preferably arranged in a certain way: The damping piston is located on one side of the output shaft and the opening piston on the other side of the output shaft, so that the output shaft between the two pistons arranged is. As a result, no direct contact of the opening piston and the damping piston is possible. This very narrow construction of the door closer thus requires that a summary of the two functions, biasing the closing spring and damping of the closing operation, in a component is not directly possible. The realization of the auxiliary hydraulic function "freewheeling" thus requires elaborate measures on both sides of the housing, as the functional areas are separated within the housing for comparison. In the case of wide-building floor door closer is usually only one piston on the spring side provided which simultaneously performs the Schließerfedervorspannung and the damping function. However, a so-called cam plate is used, which comprises the cam contour with two mounted therein rolling and ensures a continuous monitoring of the cam roller contact. using this tab carriage so it requires no further considerations to ensure the backlash-free contact between the two pistons of the piston assembly and the Abwälzkontur. However, such a cam plate with integrated employed and thus very slimline door closers, as presented here, is not possible. Furthermore, when using the cam technology to be eighth, that there be a disadvantage compared to traditional rack technologies slight lift and volume displacements combined with high spring force requirements. Cam door closer thus require viable overlays and elaborate hydraulic component arrangements. Two different variants are presented below, which make it possible that the two separate flask, the opening piston and the damping piston, always play-free contact with the Abwälzkontur have. A first variant used rods and internal clearance compensation springs. The second variant uses compression springs which engage the outside of the opening piston and / or damping piston. Preferably, it is provided that the damping piston and the opening piston are interconnected via tie rods. Since the opening piston and the damping piston are disposed on both sides of the output shaft, there is no direct contact between the two is possible. The tie rods allow here a simple assembly and production-friendly connection of the two pistons. Furthermore, the use of several rods causes an effective protection against rotation of the two pistons to the door closer longitudinal axis. Furthermore advantageous is the use of exactly four tie rods. The four tie rods can be distributed uniformly over the cross section, so that a uniform force transmission is possible. In a particularly preferred embodiment it is provided that any two of the four tie bars are arranged symmetrically to the longitudinal axis of door closers. This means that in each case two diagonally opposite rods have the same distance to the output shaft. In particular, the four tie bars are disposed at the corners of only model presented square or rectangle. The output shaft passes through the intersection point of the diagonal of this square or rectangle. By this arrangement, absolutely uniform, directed parallel to the door closer longitudinal axis power transmission between the opening piston and the damping piston is possible and a jamming of the piston assembly is thus largely avoided.
In a particularly preferred embodiment it is provided that two pull rods above the Abwälzkontur and on both sides of the output shaft are arranged, and two other connecting rods below the Abwälzkontur and the output shaft are arranged on both sides, so that the Abwälzkontur with its complete height between the two upper tie rods and the two bottom tie rods is arranged. Due to the above and below the cam portion or the underlying rods Abwälzkontur the full carrying capacity of the Abwälzkontur can be maintained. Preferably, it is provided that the piston assembly comprises at least two built-in play-compensation springs, wherein at least two diagonally arranged tension rods are loaded in train by means of the play compensation springs to compensate a clearance between the Abwälzkontur and the cam rollers. This two-loaded tie rods are used to train lash adjustment between the cam rollers of the two pistons and the Abwälzkontur and the other two diagonal bars serve to prevent rotation, thus avoiding tilting moments and associated friction and jamming of the opening piston and the damping piston. the play compensation springs in the damping piston and / or piston disposed in the opening are preferred. There are therefore to play compensation between the cam rollers and the Abwälzkontur no outside acting on the piston assembly springs necessary. The piston assembly thus must not rest against stationary parts of the door closer and can be taken by the internal arrangement of rods and anti-rattle springs on its own to ensure the compensation of play.
Preferably, the tie rods extend through the clearance compensation springs therethrough, wherein the play compensation springs are designed as compression springs and press against the ends of the tie rods, so that the tie rods are loaded on the train. The other ends of the lash adjuster springs rest against the opening piston or the damping piston. The non-spring-loaded ends of the tie rods are firmly screwed in the other pistons.
Alternatively, or in addition to the use of tie-rods and anti-rattle springs is preferably provided that a first pressure spring is arranged between the damping piston and the door closer housing, wherein the first compression spring is designed for compensation of play between the Abwälzkontur and the first cam roller of the damping piston. This first spring acts upon the damping piston slightly toward the output shaft. Further, it is preferably provided that a second compression spring is arranged between the opening piston and the piston rod or between the opening piston and the additional piston or between the opening piston and the partition wall, wherein the second compression spring is adapted for compensation of play between the Abwälzkontur and the second cam roller. This second compression spring is used, similar to the first compression spring for compensation of play between cam roller and Abwälzkontur. Preferably, the first compression spring and / or the second compression spring are such weak run to transmit to the user no appreciable moment on the door, but only provide for the compensation of play in the cam mechanism.
In a preferred embodiment it is provided that an additional closing spring is disposed between the piston assembly and the piston rod or between the piston assembly and the auxiliary piston or between the piston assembly and the partition wall in order to easily load the piston assembly in the free-running in the closing direction, wherein the additional closing spring is weaker than the closing spring. The closing spring, which is the fire protection function fulfilled and extremely strong designed is preferably blocked once and then stretched to, for example, for the case of fire on the barrier chamber. During everyday use of the door but it is also often desirable that the door closes again after committing, although not with the force of a powerful closing spring for an emergency. For this serves the additional easily be put closer spring. In particular, this additional closing spring is designed in accordance with EN1 or EN2 according to DIN EN 1154. a so-called second compression spring has already been described for compensation of play between the cam roller of the opening piston and the Abwälzkontur. This second compression spring is preferably replaced by the additional closing spring. Alternatively, the use of piston assemblies internal tie rods and springs with play compensation of the additional closing spring can be combined.
Preferably, the door closer comprises a solenoid-operated directional valve, in particular a 3/2-directional solenoid valve, facing away from one of the piston rod side of the piston assembly, particularly on the side of the damping piston, there is formed a closed damping chamber between the door closer housing and the piston assembly. The solenoid valve controls at least the pressures in the closed damping chamber and in the neutral zone. This solenoid control valve allows to seal the lock chamber hydraulically. Thus, the once pre-tensioned closing spring can not relax and the free-wheeling function of the door closer is enabled. By switching the solenoid directional control valve of the lock chamber is depressurized again and the closing spring can, for example, in case of fire, move the piston assembly and thus close the door on the output shaft.
In a preferred embodiment it is provided that the barrier chamber, a first hydraulic line, in particular a pressure line P, leading to the solenoid-operated directional valve from the closed damping chamber a second hydraulic line, in particular a working line A, leads to the solenoid-operated directional valve, and the solenoid-operated directional valve, a third hydraulic line, in particular tank line T leads to a tank space. The hydraulic lines preferably extend substantially parallel to the longitudinal axis of door closers and are integrated into the housing of the door closer.
In an advantageous embodiment, an opening damping chamber between the piston assembly and the partition wall and / or between the piston assembly and the auxiliary piston is formed. In this case, there is a first throttled connection between the damping chamber and opening the tank space. The auxiliary piston may be pierced or not must be tightly guided in the door closer housing so that the opening damping chamber extends to the spaces between the piston assembly and auxiliary piston and piston and between the additional partition wall. When opening the door the piston assembly oil from the hydraulic damping chamber opening displaced. The hydraulic oil flows through the first throttled connection, and in particular the third conduit into the tank space. In a preferred embodiment of the opening damping chamber is provided that a first unrestricted connection between the opening damping chamber and the tank space is disposed, wherein the first throttled connection is always open and the first unrestricted connection closed or depending on the position of the piston assembly through the piston assembly is open. The first unrestricted connection occurs preferably a throttled connection between the first and the output shaft in the opening of the damping chamber. This can flow at the beginning of opening the door on the first unrestricted connection to the tank room, the hydraulic oil. As a result, the door at the beginning of the opening process is very easy and no resistance to open. At a certain opening angle, the piston assembly, particularly the opening piston, the first unrestricted connection closes. As a result, the hydraulic oil can flow only through the first throttled connection to the tank room and the door is damped shortly before reaching its final position at the opening.
Preferably, the door closer further comprises a throttled connection, which is arranged between the closure damping chamber and the tank chamber, in particular in the third conduit. This further throttled connection serves to dampen the door in the closing direction.
In a preferred embodiment it is provided that the solenoid directional control valve connecting in a first switch position the first line to the third line and the second line is blocked, in a second switching position the second line is connected to the third line and blocking the first conduit. Characterized the pressure line P, and thus the barrier chamber to the tank line T in the first switching position is connected. The working line A and thus the closed damping chamber are blocked. In this switching position, the closing spring and the closing spring tension piston is not blocked and the freewheeling function disabled. By blocking the working line A hydraulic oil can flow from the closing damping space only on the further throttled connection to the tank room and closing the door is thus always muted. In the second switching position, the pressure line P of the lock chamber is blocked and the working line A of the closure damping chamber connected to the tank line. Thus, the closing spring is hydraulically locked and the free-wheeling function is activated. The closing spring can transmit in this switching position, no force on the piston assembly. At the same time normally open damper is deactivated and the piston assembly is thus became movable and the door can be moved without much effort. This embodiment of the hydraulic control is the preferred embodiment. In an alternative hydraulic control system is provided, that the solenoid valve in a first switching position connects the first conduit to the second conduit, and in a second switching position connects the second line to the third line and the first conduit blocked. In the first switching position, the pressure line P of the lock chamber is thus connected to the working line A of the closure damping chamber. In this switching position, the closer spring relaxes and forces the hydraulic oil from the neutral zone. Through the first switching position of the barrier chamber is set to the same pressure level as the closed damping chamber. This addition of the displaced volume of oil a very functionally reliable adjustment of closing speed is achieved. The oil of both spaces of the blocking space and the closure damping chamber flows into the tank space together on the further throttled connection of the closure damping chamber. In the second switching position, the pressure line P of the lock chamber is blocked, whereby the free wheel function is activated again. The operating line A of the closure damping chamber is connected to the tank line, whereby the closing damper is deactivated in the freewheel.
In an advantageous embodiment it is provided that the solenoid valve in the non-energized state frees the closer spring and in the energized state allows the freewheel. For a permanent retention of the free I a uff unction must always remain the solenoid valve is energized. By this closed circuit principle ensures that the door using the data stored in the closing spring energy always closes safely during power failure. The closing function has always been a priority for emergencies and is required by law or standards.
Advantageously, it is provided that a spring-loaded non-return valve between the lock chamber and a contracting during the opening operation of the door space is arranged. This is miniaturizing during opening space is particularly the receiving space for the closing spring. The spring-loaded check valve blocks in the direction of the decreasing space. In the neutral zone, hydraulic pressure is inventively constructed and maintained so as to lock the closing spring. For building up pressure in the barrier chamber, to be compressed in accordance with all the elements contained, elastic, such as seals, residual air or the hydraulic oil itself. This entails an undesirable volume loss by itself. The closer spring tension piston compensates for this loss of volume from, but makes up a small Folgehub. This Folgehub is transmitted to the piston rod and thus the piston assembly, the output shaft and the door. This leads to a reverse rotation of the door by a few degrees. The door can not be fully opened to the desired position while the freewheel characterized. This undesirable effect is called resilience, which is particularly noticeable with limited opening angle, determined by structural factors, noticeable. This effect is particularly pronounced in door closers with cam technology due to the small rotation angle lifting ratio. The presented arrangement with the spring-loaded check valve reduces this resilience by active set pre-pressurizing the hydraulic oil is pumped via the non-return valve in the lock chamber during the opening process of a contracting in the opening direction pressure chamber. It has deliberately been a relative resistance to opening similar to a Backcheck generated to bias the hydraulic oil and prefetch setting behavior. In prior art arrangements, the hydraulic oil is only passively drawn from a tank space in pressure chambers during the opening process, which partially can even cause slight vacuum. The elastic members so relax completely and require again a relatively high compensation volume with appropriate Folgehub to allow sufficient for the spring force holding pressure. Here, there is a maximum pressure differential. In the case described here, the setting behavior of the elastic members in the barrier chamber is therefore carried out under a low pressure difference, whereby the loss of volume and thus the Folgehub lower. Accordingly, the reverse rotation or the resilience of the piston assembly from the intended position is significantly lower. Preferably, the check valve is arranged so that hydraulic oil in the decreasing space is set by the opening process under the supply pressure and is thus actively pumped through the check valve and into the barrier chamber.
Advantageously, the check valve in the closing spring tensioning piston is arranged.
It is also advantageous that which miniaturizing room is locked during the opening process, with the exception of the check valve.
In particular, this sealing is achieved in that a further check valve between the decreasing space and the tank line is located, said further non-return valve closes in the direction of the tank line. Thereby, for example, in the shooting space of the closing spring, hydraulic oil is biased during the opening operation and can be circulated via the spring-loaded check valve in the closing spring tensioning piston in the barrier chamber. The invention further comprises a hydraulic solenoid directional control valve, in particular a hydraulic 3/2-way solenoid valve comprising a valve housing, an electromagnet and a valve lifter. In the housing a valve chamber is integrated. This valve chamber includes a first valve seat bore as a connection to a first line, in particular a pressure line, a second valve seat bore as a connection to a second line, in particular working line, and a free opening to a third line, in particular tank line. The opening is referred to as "free" as it connects in each switching position of the valve, the valve chamber to the third conduit. The valve stem is at least partially disposed within the valve chamber and is linearly moved by the electromagnet. Further comprising the valve stem within the valve chamber, a first valve seat bore facing first sealing surface and a second valve seat bore facing second sealing surface, so that either the first valve seat bore or the second valve seat bore is closable. Furthermore, the valve stem extends from the valve chamber out through the second valve seat bore and through the second conduit through the electromagnet. Characterized in that the valve stem from the valve chamber also extends, the valve tappet can be connected with the electromagnet or be partially integrated in the electromagnet. In the closed second valve seat hole is pulled over a difference area ratio of the valve stem by the pressure of the second line, in particular working line, in the second valve seat bore. This arrangement with differential area ratio favors the leak-free seal of the second valve seat bore.
This differential area ratio is achieved in particular that a sealing diameter of the valve stem is greater outside the valve chamber as a diameter of the second valve seat bore. The sealing diameter is defined on a seal between the valve plunger and an electromagnet.
the differential area ratio is preferably achieved by increasing the diameter of the valve stem out of the valve chamber is made larger than the bore diameter of the second valve seat bore. This allows the pressure of the second line upstream of the valve chamber to support the force of the compression spring with a closed second valve seat hole and tighten the second sealing surface in the second valve seat bore.
In a further preferred embodiment, the valve tappet is formed at least in two parts. To this end, the valve stem comprises a first part and a second part, said first part being linearly movably guided in the electromagnet and the second part is screwed into the first part. Characterized the second part is fixedly connected to the first part and linearly movable together with the first part. Particularly for the differential area ratio this two-part design of the valve stem is particularly easy to install. Thereby, the sealing diameter may in particular be made larger than the bore diameter of the second valve seat bore. Furthermore, it is preferably provided that is arranged between the valve stem and an armature space of the electromagnet, a seal, in particular a groove ring seal. This seal is located on the already discussed sealing diameter of the valve stem electromagnet. More preferably, the armature space via a through extending through the valve stem connecting channel is always freely connected to the third line, in particular tank line. This pressure build-up in the armature space is avoided in case of possible leaks of this groove ring seal. The connecting passage within the valve tappet extends from the armature chamber through the valve stem and into the valve chamber. As already described, the valve chamber is always free connected to the third line, in particular tank line.
Alternatively to the first described hydraulic solenoid valve, the invention comprises a hydraulic solenoid valve, in particular hydraulic 3 / 2- solenoid valve, comprising a valve housing, an integrated into the valve housing valve chamber having a first valve seat bore as a connection to a first line, in particular pressure pipe, a free opening to a second line, in particular working line, and a second valve seat bore as a connection to a third line, in particular tank line. Further, this hydraulic solenoid control valve comprises an electromagnet and a movable by the electromagnet and partly arranged in the valve chamber valve tappet. The valve stem comprises here within the valve chamber, a first valve seat bore facing first sealing surface and a second valve seat bore facing second sealing surface, so that either the first valve seat bore or the second valve seat bore is closable. Furthermore, the valve stem from the valve chamber also extends through the second valve seat bore therethrough to the electromagnet.
In a preferred embodiment of the alternative hydraulic Magnetwegventils is provided that a compound of the third line consists of an armature space of the electromagnet on the valve stem or along the valve stem so that a pressure build-up is avoided in the armature space. In particular, this connection is realized in that a flat surface is formed on the valve tappet, or that the valve tappet is produced as a polygonal, in particular hexagonal.
In the following advantageous features of the two hydraulic solenoid valves according to the invention are described:
In a preferred embodiment it is provided that a diameter of the first valve seat hole is smaller than a diameter of the second valve seat bore.
In a preferred embodiment a compression spring is arranged between the first valve bore and the valve stem. The valve according to the invention may thus be referred to in the variant with a spring-loaded ball spherical-conical valve seat.
In a further advantageous refinement, it is provided that in the currentless state of the electromagnet, the second sealing surface, in particular conical surface, the second valve seat bore to seal, and that in the energized state of the electromagnet seals the first sealing surface, in particular convex surface, the first valve seat bore. The preferably provided compression spring serves to ensure that in the currentless state, the second sealing surface of the valve lifter is pushed into the second valve seat bore. Preferably, the first sealing surface comprises a convex surface, in particular a ball. Further preferably, the second sealing surface comprises a conical surface, in particular a conical annular surface. the first valve seat hole is selectively closed by the convex surface or the second valve seat bore with the tapered surface by linearly moving or moving the valve stem. Jamming or snagging in the switching position under pressure is effectively prevented by the ball valve design with the convex surface. Further, preferably, the invention comprises a filter, in particular in the first conduit. the filter outside of the valve chamber is particularly preferably arranged directly upstream of the inlet into the first valve seat bore. The filter prevents contamination of the oil and in particular contamination of the two valve seats. In a further preferred embodiment, the first valve seat bore lies directly opposite the second valve seat bore. In a preferred embodiment, the electromagnet includes a coil, an armature, a pole core, and a gap between pole core and the armature. The pole core includes a bore along the longitudinal axis of the valve stem and thus provides a receptacle and a linear guide for the valve stem. Furthermore, preferably magnetic valves of the invention comprise a control / regulation of the electromagnet. With this control / regulation of the electromagnet can be switched energized and de-energized. Furthermore, the invention comprises a hydraulic cartridge solenoid-operated directional valve, in particular hydraulic cartridge 3/2-directional solenoid valve comprising any of the recently introduced hydraulic solenoid valves, wherein the housing is configured for at least partial insertion into a valve receptacle. This valve receptacle is in a component which receives the cartridge 3/2-directional solenoid valve integrally. the first line, in particular the pressure line and the second line, in particular working line are particularly preferred, carried out with respect to the longitudinal axis of the valve stem radially or perpendicularly outward. Furthermore, there is preferably O-ring seals at the side for the external first and second lines on the surface of the valve housing, so that these lines can be connected pressure-tight manner by inserting the Cartridge housing. More preferably, the valve housing includes this circumferentially extending annular channels. Of these ring channels from a plurality of radially oriented channels for the first line and / or more radially directed channels for the second line may preferably result in the valve chamber.
Further, it is preferred that the hydraulic cartridge solenoid-operated directional valve comprises a volume equalization unit with tank space. This volume control unit with tank space is integrated into the valve housing or is flanged to the valve body. The tank chamber is preferably connected to the third conduit. The valve is built up preferably along the longitudinal axis of the valve tappet as follows: The valve chamber with a valve tappet is centrally arranged. On one side of the chamber, the volume control unit is integrated with tank room or flanged. On the other side of the valve chamber of the solenoid is mounted. Thereby, the hydraulic cartridge solenoid directional valve with the volume compensation unit preceding be inserted into a component. The electromagnet and in particular a plug on the electromagnet extend preferably out of the component. In a preferred embodiment of the tank space of the volume compensation unit by means of a volume compensating piston, and a counterbalance spring or pressure spring is slightly pressure-loaded. Furthermore, the invention comprises a door closer, in particular a rotary door closers, with a freewheeling function, comprising a hydraulic solenoid valves just described or one of the hydraulic cartridge solenoid valves, wherein the valve seat is formed in the door closer. The hydraulic solenoid valve or cartridge solenoid valve is thus integrated into the housing of the door closer or flanged and is used to control the hydraulic damping chamber between the closing, the blocking chamber and the tank space and the tank line.
The door closer with the hydraulic solenoid control valve preferably further comprises a door closer housing, a connectable to a door output shaft connected to said driven shaft and guided in the door closer housing piston assembly, a closing spring, an arranged to connect the piston assembly with the closing spring piston rod, a free-wheeling arrangement which to is formed, a translational movement of the piston assemblies uncoupled from the closing spring with blocked closing spring to allow a trained and for blocking the closing spring hydraulic lock space. The advantageous embodiments of the door closer according to the invention previously described are appropriate advantageous application to the door closer to the hydraulic solenoid directional control valve and the hydraulic cartridge solenoid directional valve.
1 3/2-directional solenoid valve
3 valve chamber
5 valve tappet
6, 7 the valve seat holes
8 free opening
9 convex surface
11 conical annular surface
12, first portion
13, second part
14 valve spring
18 pole core
21 connecting cable
22 armature space
25 groove ring seal
26 base housing part
27 first Ventiikammereinsatz
28 second Ventiikammereinsatz
31 tank room
32 volume balance piston
33 balancing spring 34 spring bearing
35 drilled using
37 volume compensation unit
38 valve axis
39 annular channels
40 O-ring seals
41 door closer
42 door closer housing
43 first door closer housing part
44 second door closer housing part
45 first compression spring
46 damping piston
47 first cam roller
48 output shaft, constructed as a camshaft
49 Abwälzkontur
50 second cam roller
51 opening piston
52 second compression spring
53 housing partition
54 piston rod
55 closer spring tension piston
56 closer spring
57 setting for 58 Schließerfedervorspannung closure damping chamber
59 piston assemblies interior, esp. Camshaft chamber
60 Backcheck room
61 barrier chamber
62 door closers axis
63 second throttle valve
64 third throttle valve
65 first throttle valve
66 first check valve 67 second check valve
68 third check valve
69 fourth check valve
70 Mechanical seal
72 second end face, esp. The pocket base
73 piston guide
74 first end face
75 second throttled connection 76 third throttled connection
77 first unrestricted connection
78 first throttled connection
79 first axis
80 second axis
81 first drawbar
82 second pull rod
83 third pull rod
84 fourth pull rod
85 output shaft
86 integrated clearance compensation springs
88 spring clamping nuts
89 first sealing flange
90 second sealing flange
91 level of Abwälzkontur
92 closer spring housing space
94 piston assembly
95 additional piston
P first line, esp. Pressure line
A second line, esp. Working line
T third line, esp. Tank line
1. A door closer (41), in particular rotary door closer comprising freewheeling function
a door closer housing (42),
a connectable with a door drive shaft (48),
one with the output shaft (48) connected and in the door closer housing (42) guided piston assembly (94)
a closing spring (56),
a connection to the piston assembly (94) with the closing spring (56) arranged piston rod (54),
a freewheel arrangement which is adapted to a translatory
Movement of the piston assembly (94) uncoupled from the closing spring
(56) to allow for blocked closer spring (56), and which is designed as a sliding coupling, which only transmits compressive forces between the closer spring (56) and the piston assembly (94), and
one for blocking the closing spring (94) formed hydraulic barrier chamber (61).
2. A door closer according to claim 1, characterized by a door closer housing (42) between the piston assembly (94) and the closing spring (56) is arranged fluid-tight partition (53), wherein the piston rod (54) fluid-tightly by the partition wall (53) extends.
3. Door closer according to one of the preceding claims, characterized by a door closer housing (42) guided and the closer spring (56) abutting closing spring tensioning piston (55).
4. A door closer according to claims 2 and 3, characterized in that between the partition wall (53) and the closing spring tensioning piston (55) is formed of the barrier chamber (61).
5. A door closer according to one of the preceding claims, characterized in that the freewheel arrangement between the piston rod (54) and the piston assembly (94) is arranged.
6. A door closer according to one of the preceding claims, characterized in that the freewheel arrangement standing a perpendicular to a door closer the longitudinal axis (62) and fixed to the piston rod (54) connected to the first end face (74) and parallel to the first end face (74) and fixed includes with the piston assembly (94) connected to the second end face (72), with blocked closer spring (56) lifts off the second end face (72) of the first end face (74) and thus decoupled.
7. A door closer according to one of the preceding claims, characterized in that in the piston assembly (94) is formed a pocket (71), wherein the piston rod (54) movable in the pocket (71) is guided.
8. A door closer according to one of claims 1 to 6, characterized by a door closer housing (42) between the piston assembly (94) and the piston rod (54) guided, secured to the piston rod (54) auxiliary piston connected (95), wherein the first end face (74) is formed on the auxiliary piston (95).
9. A door closer according to claim 8, characterized in that the connection between the piston rod (54) and auxiliary piston (95) about a first axis (79) is carried out perpendicular to the longitudinal axis door closer (62) is pivotally mounted.
10. A door closer according to claim 9, characterized in that the connection between the piston rod (54) and closing spring tensioning piston (55) about a second axis (80) is carried out perpendicular to the door closer the longitudinal axis (62) and perpendicular to the first axis (79) is pivotally mounted.
1 1. A door closer according to any one of the preceding claims, characterized in that the output shaft (48) has a cam-shaped Abwälzkontur (49), in particular the cam disc comprises, and the piston assembly (94) has at least one on the Abwälzkontur (49) adjacent cam roller (47, 50).
12. A door closer according to any one of the preceding claims, characterized by an opening damping space (60) between the piston assembly (94) and the partition (53) or between the piston assembly (94) and the auxiliary piston (95), and a first throttled connection (78) between the opening damping chamber (60) and a tank chamber (31).
13. A door closer according to claim 12, characterized by a first unrestricted connection (77) between the opening damping chamber (60) and the tank space (31), wherein the first throttled connection (78) is always open and the first unrestricted connection (77), depending on closed position of the piston assembly (94) or open.
PCT/EP2010/007255 2009-12-01 2010-11-30 Door closer with free-swing function WO2011066947A1 (en)
EP20100784995 EP2507456B1 (en) 2009-12-01 2010-11-30 Door closer with free-swing function
JP2012541352A JP2013512368A (en) 2009-12-01 2010-11-30 Door closer with a floating function
CN 201080054415 CN102803639B (en) 2009-12-01 2010-11-30 Door closer with free-swing function
US13513172 US8819895B2 (en) 2009-12-01 2010-11-30 Door closer with free-swing function
WO2011066947A1 true true WO2011066947A1 (en) 2011-06-09
PCT/EP2010/007252 WO2011066945A3 (en) 2009-12-01 2010-11-30 Door closer
PCT/EP2010/007249 WO2011066942A4 (en) 2009-12-01 2010-11-30 Hydraulic directional solenoid valve and door closer having a hydraulic directional solenoid valve
PCT/EP2010/007255 WO2011066947A1 (en) 2009-12-01 2010-11-30 Door closer with free-swing function
PCT/EP2010/007248 WO2011066941A1 (en) 2009-12-01 2010-11-30 Door closer comprising cam drive
PCT/EP2010/007253 WO2011066946A1 (en) 2009-12-01 2010-11-30 Door closer comprising additional closing spring
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