Source: https://patents.google.com/patent/US8806715B2/en
Timestamp: 2018-08-20 17:11:09
Document Index: 365428099

Matched Legal Cases: ['Application No. 10', 'Application No. 10', 'art 43', '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 13', 'art 13', 'art 13']

US8806715B2 - Door closer comprising device for preventing a spring-back - Google Patents
Door closer comprising device for preventing a spring-back Download PDF
US8806715B2
US8806715B2 US13513468 US201013513468A US8806715B2 US 8806715 B2 US8806715 B2 US 8806715B2 US 13513468 US13513468 US 13513468 US 201013513468 A US201013513468 A US 201013513468A US 8806715 B2 US8806715 B2 US 8806715B2
US13513468
US20120240351A1 (en )
This is a U.S. national stage of application No. PCT/EP2010/007251, filed on 30 Nov. 2010. Priority is claimed on German Application No. 10 2009 056 265.6 filed 1 Dec. 2009 and German Application No. 10 2010 013 853.3 filed 1 Apr. 2010, the contents of which are incorporated here by reference.
The invention relates to a door closer that reduces or avoids a springback or rebound.
In the state of the art, a differentiation is made between door closers and door drives. In case of door closers, the door has to be opened manually by a person. During the opening process, energy is stored, e.g. in a closer spring, and the door closer is able to close the door using the stored energy. In contrast, the door drive is an assembly that automatically opens and closes the door by an additional auxiliary energy, e.g. by a motor or hydraulics. In particular when considering the hydraulic circuits in door drives and door closers, significant differences can be found. In electro-mechanic door drives, a motor and a pump are always provided, which apply the required hydraulic pressure. The respective pressure chambers are thereby actively charged with hydraulic pressure, such that the opening of the door is effected. Thus, in the door drive, the pressure is generated by the internal components, i.e. motor and pump. Contrary thereto, the pressure chambers in a door closer are filled by expansion of the chambers and by suctioning the hydraulic oil from other spaces of the door closer. Herein, the energy for the closer spring and for the pressure generation is supplied into the door closer by opening the door. Consequently, the force and moment characteristics as well as the occurring loads are mostly different for a door closer and a door drive. The door drive has to apply the energy for accelerating the door in an opening direction additionally, whereas, in case of the door closer, the door is accelerated in an opening direction by the user.
It is an object underlying the present invention to provide a door closer which has a very slender structure while being manufactured at low costs, and which is consequently also applicable as an integrated door closer, e.g. in a door frame or a door. In addition, the door closer is configured to include a locking function or a free-swing-function, and a rebound shall be avoided as far as possible.
In one embodiment, a hinge door closer includes a locking function or free-swing-function, comprising a door closer housing, an output shaft to be connected to a door, a piston assembly connected to the output shaft and guided in the door closer housing, a closer spring, a piston rod adapted to connect the piston assembly to the closer spring, and a hydraulic lock compartment adapted to lock the closer spring. Further, it is provided that a spring-loaded check valve is arranged between the lock compartment and a space becoming smaller during the opening process of the door. This space becoming smaller during the opening process is in particular the accommodating space for the closer spring.
Preferably, a free-swing-assembly is provided for embodying the free-swing-function, which is adapted to enable a translational motion of the piston assembly decoupled from the closer spring when the closer spring is locked. Within the alternative locking function, the closer spring is fixedly connected to the piston assembly, such that the piston assembly and therewith the door are arrested simultaneously by the locking of the closer spring.
Preferably, the door closer including a free-swing-function is used in facilities for handicapped persons, apartments for senior citizens, or nursery schools as well as for safeguarding fire protection doors. In combination with a fire alarm system, the closing of said doors is secured for avoiding a propagation of smoke and fire, without exposing the users of the door to a constant opening moment of prior art door closers. In particular in case of fire protection doors, very strong closer springs have to be used, such that a safe closing of the door can be guaranteed also in case of an air draft in the corridors. The tensioning of such closer springs whenever the door is opened cannot be expected from children, ill persons or senior citizens, in particular. In this case, the free-swing-function enables that the closer spring is biased only once and remains biased until a possible emergency case. The present door closer can be inserted invisibly into the door leaf or in the door frame due to its very slender overall width, such that no optical drawback occurs and it is protected against demolition by vandalism.
For the free-swing-function included in the door closer mechanism, the closer spring, also referred to as energy storing spring, must be retained in a biased position by the hydraulic lock compartment, in order to prevent an immediate closing of the door after the manual opening thereof. Since the effective direction of the closer spring is directed to the output shaft via the piston assembly, the additional closer spring tension piston is preferably used, which piston acts on the piston assembly via the piston rod. In combination with the piston rod and the separating wall, the hydraulic lock compartment for hydraulically arresting the closer spring is thus generated. The piston rod extends through the lock compartment, such that the lock compartment may also be referred to as ring space. Based on this structure of the inventive door closer, a decisive difference between the known door drives and the door closer proposed herein can be well explained. In the known door drive, an oil volume actively pressurized by a hydraulic pump is pumped into the pressure chambers, and therewith an energy saving spring is biased through a spring tension piston. In contrast, the proposed door closer provides that the oil volume corresponding to the stroke is displaced from other housing areas into the lock compartment during the manual opening process, and the discharge from the lock compartment is e.g. blocked by a solenoid valve. Thus, in the door closer proposed herein, the stored force of the closer spring is absorbed by the oil pressure and cannot introduce a torque to the output shaft via the piston assembly.
Preferably, the spring-loaded check valve locks toward the space becoming smaller. According to one embodiment of the invention, a hydraulic pressure is built up and maintained in the lock compartment to arrest the closer spring. For a pressure generation in the lock compartment, all elastic members contained therein, e.g. seals, residue air or also the hydraulic oil itself, are compressed accordingly. This results in an undesired loss of volume. The closer spring tension piston compensates for this loss of volume, however, performs a small subsequent stroke. This subsequent stroke is transmitted to the piston rod and consequently to the piston assembly, the output shaft and the door. This results in a turning back of the door by several degrees when using the locking function. In case the free-swing-function is used, the subsequent stroke has the effect that the door cannot be opened completely to the desired position. This undesired effect is referred to as rebound, which becomes noticeable in particular in case of restricted door opening angles determined by structural conditions. This effect is especially pronounced in case of door closers with cam technology due to the small rotary angle-stroke-ratio. The arrangement proposed herein, including the spring-loaded check valve, reduces said rebound by pumping the hydraulic oil, being actively pre-pressurized, from a pressure space becoming smaller in the opening direction through the third check valve into the lock compartment during the opening process. Therewith, a relative opening resistance, similar to a opening damping, is intentionally generated in order to bias the hydraulic oil and to obviate compression-set-characteristics. In pre-known arrangements, the hydraulic oil is only passively suctioned from the tank compartment into the pressure compartments during the opening process, which may partially even generate a slightly negative pressure. The elastic members therewith completely relax and require a relatively high compensation volume including a corresponding subsequent stroke in order to enable again a holding pressure sufficient for the spring force. In this case, a maximum pressure difference exists. In the case described herein, the compression-set-characteristics of the elastic members in the lock compartment therefore occur during a slight pressure difference, as a result of which the loss of volume and thus the subsequent stroke is smaller. Accordingly, the turning back or the rebound of the piston assembly from the intended position is considerably smaller.
Preferably, the spring-loaded check valve is arranged such that the hydraulic oil in the space becoming smaller is pre-pressurized by the opening process and is thus actively pumped through the check valve into the lock compartment.
Preferably, the check valve is arranged in a the closer spring tension piston.
This closing is in particular achieved by arranging a further, in particular spring-loaded, check valve between the space becoming smaller and the tank line, wherein the further check valve locks toward the tank line. Therewith, hydraulic oil e.g. present in the accommodating space of the closer spring is biased during the opening process and can be pumped into the lock compartment through the first-mentioned spring-loaded check valve in the closer spring tension piston.
FIG. 6 is a detailed view of the free-swing according to the first embodiment;
FIG. 12 is a hydraulic switching symbol for a solenoid control valve of an inventive door closer according to a fifth embodiment,
The door closer 41 extends along a longitudinal door closer axis 62. The door closer 41 comprises a door closer housing 42 which in turn consists of a first door closer housing part 43 and a second door closer housing part 44. In FIG. 1, the various hydraulic lines are shown to be outside the door closer housing 42. This illustration, however, is only given for facility of inspection. In practice, the hydraulic lines are integrated into the door closer housing 42. In the following, the structure of the door closer 41 along its longitudinal door closer axis 62 is explained from left to right. A first pressure spring 45 is supported against the door closer housing 42, in particular against a front face of the first door closer housing part 43. The first pressure spring 45 pushes a piston assembly 94. This piston assembly 94 is guided in the door closer housing 42, in particular in the first door closer housing part 43. Opposite to the first pressure spring 45, a second pressure spring 52 abuts against the piston assembly 94. Said second pressure spring 52 is supported against a separating wall 53, in particular a housing separating wall. The separating wall 53 is disposed at the sectional area between the first door closer housing part 43 and the second door closer housing part 44. The separating wall 53 forms a flange for connecting the two housing parts 43, 44 and simultaneously seals the two housing parts 43, 44 against each other. A piston rod 54 passes through the separating wall 53 along the longitudinal door closer axis 62. The piston rod 54 is sealingly guided in the separating wall 53, in particular by a slide ring seal. The piston rod 54 is fixedly connected to a closer spring tension piston 55. Said closer spring tension piston 55 is guided in the door closer housing 42, in particular in the second door closer housing part 44. The closer spring tension piston 55 is followed by a closer spring 56. The closer spring 56 is supported against the closer spring tension piston 55 on one side and against an adjusting unit 57 for the closer spring biasing on the other side. Adjacent to the adjusting unit 57 for the closer spring biasing, a 3/2-solenoid control valve 1, in the embodiment of a cartridge valve, is disposed and integrated into the door closer housing 42, in particular in the second door closer housing part 44.
The piston assembly 94 comprises, on a side thereof facing the first pressure spring 45, a damper piston 46, and an opening piston 47 on the side facing the piston rod 54. The damper piston 46 comprises a first cam roller 47 which is rotatably supported therein. The opening piston 51 comprises a second cam roller 50 supported rotatably therein. An output shaft 48, in the embodiment of a cam shaft, is arranged between the first cam roller 47 and the second cam roller 50. The output shaft 48 extends along an output axis 85 perpendicular to the longitudinal door closer axis 62. Said output shaft 48 transmits the force from the piston assembly 94 though an arrangement of levers or an arrangement with slide rails to the door as well as from the door to the piston assembly 94. For this purpose, the output shaft 48 comprises a cam-shaped rolling contour 49. The first cam roller 47 and the second cam roller 50 roll on this rolling contour 49. The rolling contour 49 is heart-shaped.
The damper piston 46, the opening piston 51 and the closer spring tension piston 55 are sealingly guided within the door closer housing 42 and, for this purpose, preferably comprise seals or sealing flanges at their circumference. Due to this sealed guiding of the pistons, different spaces or chambers are generated in the door closer housing 42, which are connected to each other via various hydraulic lines. Said chambers or spaces are, according to the structure shown in FIG. 1, again explained from left to right along the longitudinal door closer axis 62: A closure damping compartment 58 is formed, defined by the left end face of the door closer housing 42, in particular the first door closer housing part 43, and the damper piston 46. A piston assembly inner space 59 is disposed between the damper piston 46 and the opening piston 51. Same can also be referred to as cam shaft space. The piston assembly inner space 59 is on both sides sealed by the damper piston 46 and the opening piston 51 and is always maintained at a tank pressure level. An opening damping compartment 60 is disposed between the opening piston 51 and the separating wall 53. On the other side of the separating wall 53, the lock compartment 61 is arranged between the separating wall 53 and the closer spring tension piston 55. The lock compartment 61 is defined by the separating wall 53, the wall of the second door closer housing part 44 and the closer spring tension piston 55. In addition, the door closer 41 comprises a tank compartment 31. The tank compartment 31 is arranged between the closure spring tension piston 55 and the solenoid control valve 1 and accommodates the closer spring 56 and the adjusting unit 57. Based on FIGS. 11 to 18, the specific design of the solenoid control valve 1 is explained later on. In this context, also the specific constructive design of a preferred tank compartment 31 will be explained. In particular, a closer spring accommodating space 92 and/or the piston assembly inner space 59 can be used as a tank by unthrottled connections to the tank compartment 31.
The door closer 41 comprises a first hydraulic line, embodied as pressure line P, a second hydraulic line, embodied as operating line A, and a third hydraulic line, embodied as tank line T. The three hydraulic lines extend in parallel with the longitudinal door closer axis 62 in the door closer housing 42. The three hydraulic lines are connected to the various chambers or spaces in the door closer 41 through short channels which extend radially/vertically with respect to the longitudinal door closer axis 62. FIG. 1 shows the hydraulic lines only schematically. In practice, the hydraulic lines are integrated into the door closer housing 42. The pressure line P extends from the lock compartment 61 to the solenoid control valve 1 directly and without being throttled. The operating line A extends from the closure damper space 58 to the solenoid control valve 1 directly and without being throttled. The solenoid control valve 1 is further connected to the tank line T. The designation “direct and without being throttled” means that no separate throttles are provided in the lines. Nevertheless, the pressure can be slightly throttled by possible filters or dynamic pressure differences.
The closure damping compartment 58 is connected to the tank line T through a second throttled connection 75 arranged at the front face of the first door closer housing part 43. For this purpose, a second throttle valve 63 is used. In addition, a third throttled connection 76 is provided in the circumferential surface of the door closer housing 42 between the closure damping compartment 58 and the tank line T, including a third throttle valve 64. The piston assembly inner space 59 is connected to the tank line T in an unthrottled manner by at least one radial channel. A filter 31 is depicted in the tank line T. Herein, the position of the filter 31 is only exemplary. For example, the filter 31 can also be integrated into the solenoid valve 1. Preferably, further filters 31 can be arranged in the other hydraulic lines.
In the damper piston 46, a first check valve 66 is installed. This check valve locks toward the piston assembly inner space 59. A second check valve 67 is installed in the closer piston 51. Same also locks toward the piston assembly inner space 59. A third check valve 68 is provided in the closer spring tension piston 55. This check valve enables a hydraulic flow toward the lock compartment 61 and a locking toward the tank compartment 31 or the closer spring accommodating space 92, respectively. A forth check valve 69 is provided between the tank compartment 31 and the tank line T. Said check valve is spring-loaded and locks toward the tank line T. With the first, second and third check valves 66, 67 and 68, the closure damping compartment 58, the opening damping compartment 60 and the lock compartment 61 can always be filled with hydraulic oil from the tank volume upon expansion.
A free-swing assembly is formed between the piston rod 54 and the opening piston 51. The constructive design of this free-swing assembly is explained in more detail in FIG. 6. At first, however, the functions and motions of the door closer 41 are explained in more detail with reference to FIGS. 2 to 5. The functions and motions of the door closer 41 according to FIGS. 2 to 5 are applicable for all embodiments proposed herein. FIG. 2 shows the door closer 41 at an angle position of 0° with a released closer spring. FIG. 2 therewith shows the starting position of the door closer 41. FIG. 3 shows the door closer during opening at an angle position of 150° of the output shaft 48. The door is opened by a person. Due to this, the output shaft 48, which is connected to the door frame via an arrangement of levers, rotates. The force is transmitted through the rolling contour 49 to the cam rollers 47, 50. This results in a translational motion of the piston assembly 94 to the right. Together with the piston assembly 94, also the piston rod 54 and therewith the closer spring tension piston 55 are moved to the right. Consequently, the closer spring 56 is biased. During this opening process, the pressure line P is closed by means of the solenoid control valve 1. Hydraulic liquid is pushed through the third check valve 68 into the lock compartment 61. The opening process shown in FIG. 3 serves to tension the closer spring 56. After tensioning the closer spring 56 and by keeping the pressure line P closed, the free-swing-function of the door closer 41 is active. FIG. 4 shows the door closer 41 again in a closed position with a door angle of 0°. As is easily discernible, the closer spring 56 remains in the tensioned position, since the lock compartment 61 is still filled with hydraulic oil. Together with the closer spring tension piston 55, also the piston rod 54 remains unmovable. Due to the free-swing assembly, the piston assembly 94 lifts off the piston rod 54 through the backturn of the output shaft 48 upon a closing motion operated manually at the door. Herein, the piston assembly 94 can freely move together with the door. Merely a slight force is transmitted through the two pressure springs 45, 52 to the piston assembly 94. As shown in FIG. 5, the closer spring 56 remains in its tensioned and arrested position during the free-swing-function. Meanwhile, the door is freely movable without any torque.
Apart from the difference described in the following, the second embodiment corresponds to the first embodiment. In contrast to the first embodiment, an additional piston 95 is arranged between the separating wall 53 and the piston assembly 94, in particular the opening piston 51, in the second embodiment. The additional piston 95 is fixedly connected to the piston rod 54 for transmitting a translational motion. The first front face 74 is formed frontally at the additional piston 95. The additional piston 95 comprises a passage, such that the area between the additional piston 95 and the piston assembly 94 as well as the area between the additional piston 95 and the separating wall 53 form the opening damping compartment 60. A further difference between the first embodiment and the second embodiment is that, in the second embodiment, the piston rod 54 is connected pivotally to the additional piston 95 and the closer spring tension piston 55. The connection between the piston rod 54 and the additional piston 95 is pivotal about a first axis 79. The connection between the piston rod 54 and the closer spring tension piston 55 is pivotal about a second axis 80. Both axes 79, 80 are positioned vertically with respect to the longitudinal door closer axis 62. In addition, the first axis 79 is positioned vertically with respect to the second axis 80. Further, the axis 80 is positioned vertically with respect to the longitudinal door closer axis 62. Said pivotal connection of the piston rod 54 prevents a seizing of the assembly in case forces occur, which do not extend in parallel with the longitudinal door closer axis 62.
The piston assembly 94 proposed in FIGS. 9 and 10 replaces the piston assembly 94 of FIGS. 1 to 7, in particular the damper piston 46 including the first cam disc 47 and the opening piston 51 including the second cam disc 50. The output shaft 48 remains unchanged. Due to the use of the piston assembly 94 according to the third embodiment, the first pressure spring 45 and the second pressure spring 52 are not required, however, can be used in addition.
The four tie rods 81 to 84 are respectively connected to the opening piston 51 by screwings 87. At the other ends thereof, the four tie rods 81 to 84 protrude into through-holes of the damper piston 46. Here, the ends of the tie rods 81 to 84 are respectively screwed by a spring tension nut 88. The first tie rod 81 and the third tie rod 83 being arranged diagonally to the first tie rod 81 are respectively tensile-loaded by an integrated clearance compensation spring 86. The integrated clearance compensation springs 86 are fit on the first tie rod 81 and the third tie rod 83 and are located in the damper piston 46. A first end of the clearance compensation springs 86 facing away from the output shaft 48 is supported against the spring tension nut 88, which is screwed to the respective tie rods 81, 83. A second end of the respective clearance compensation springs 86 facing the output shaft 48 is supported against a shoulder 93 (see FIG. 10) which is formed in the damper piston 46. Due to this specific arrangement, the clearance compensation springs 86, which are embodied as pressure springs, may load the first and second tie rods 81, 83 with tension.
In addition, FIG. 9 shows a first sealing flange 89 at the damper piston 46, which seals the damper piston 46 with respect to the door closer housing 42, in particular with respect to the closure damping compartment 58. In a similar manner, the opening piston 51 is sealed with respect to the door closer housing 42 by a second sealing flange 90. These two sealing flanges 89, 90 are used in the piston assemblies 94 of all embodiments.
Further, the piston assembly 94 according to the third embodiment can also preferably be used together with the first pressure spring 45 and/or the second pressure spring 52. A specific application is e.g. given in case of very heavy fire protection doors. The closing force required in case of a fire requires very strong closer springs 56. For the everyday use of the door, it would be desirable that the closer spring 56 always remains biased and closes the door in case of a fire. Nevertheless, there exists the need for a smooth-running and automatically closing door, wherein said easy closing should occur after each use. Therefore, it is preferable that each of the door closers 41 proposed herein comprises the second pressure spring 52 as an “additional closer spring”, embodied e.g. according to EN1 or EN2, wherein said additional closer spring/second pressure spring 52 is much more weaker than the closer spring 56. The second pressure spring 52 in this embodiment therewith always loads the piston assembly 94, in particular the opening piston 51, in the closing direction, even when in free-swing-mode and upon a blocked closer spring 56, such that the door closes, at least if the resistance is not too large, automatically, also during the free-swing-mode. Nevertheless, the user does not have to tension the large closer spring 56 upon each opening process, but only the much smaller second pressure spring 52. In particular in this embodiment, the piston assembly 94 according to FIGS. 9 and 10 according to the third embodiment can be preferably combined with the second pressure spring 52.
The second part 13 of the valve spindle 5 comprises a first sealing surface, embodied as a convex surface 9 (see in particular FIG. 16) on a side thereof facing the valve seat bore 6. Said convex surface 9 is formed by a ball 10. The ball 10 in turn is embedded into a face side recess of the valve spindle 5, in particular of the second part 13. In addition, a shoulder is formed at the valve spindle 5, in particular at the second part 13.
A valve pressure spring 14 is supported on said shoulder. The convex surface 9 is arranged within said valve pressure spring 14. The valve pressure spring 14 is further supported at the front face of the first valve seat bore 6. Said front face can also be referred to as sealing surface or lateral surface of the first valve seat bore 6. Due to this arrangement of the valve pressure spring 14, the valve spindle 5 is loaded toward the solenoid 4. In a de-energized state, this results in an opening of the first valve seat bore 6.
The valve housing 2 comprises a base housing component 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-solenoid control valve 1 is structured and assembled as follows: An annular extension 29 is disposed at the solenoid 4. A part of the second valve chamber insert 28 is embedded into said extension 29. The second valve chamber insert 28 in turn accommodates the first valve chamber insert 27. The already mentioned sleeve 23 of the solenoid 4 extends to the second valve chamber insert 28 and is connected thereto. The complete unit consisting of solenoid 4, second valve chamber insert 28 and first valve chamber insert 27 is screwed into the base housing component 26. For this purpose, an internal thread is formed at the base housing component 26, and a corresponding external thread is formed at the extension 29 of the solenoid 4. The individual housing components are sealed against each other.
FIG. 16 shows a detail of FIG. 15. Based on this illustration, particularly the differential-area-ratio can be explained. It shall be noted that said differential-area-ratio is used upon a closed second valve seat bore 7 and thus in the de-energized valve position shown in FIG. 14. As shown in FIG. 16, the valve spindle 5 comprises a sealing diameter D1 at the groove ring seal 25. The second valve seat bore 7 has an inner diameter D2. In a region between the groove ring seal 25 and the second valve seat bore 7, the valve spindle 5 has a smallest diameter D3. When the second valve seat bore 7 is closed, the pressure in the operating line A acts on the following surfaces of the valve spindle 5: 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). Due to the fact that the first surface is smaller than the second surface, the operating pressure acts to the right in the shown illustration, when the second valve seat bore 7 is closed. Therewith, the valve pressure spring 14 is supported and the cone surface 11 is pulled into the second valve seat bore 7.
Based on the fifth embodiment, it was explained how a hydraulic 3/2-solenoid control valve 1, in particular with a cartridge design, can be formed for an operation free of leakage oil. In the de-energized switching position, shown in FIG. 14, the side of the valve spindle 5 formed as the cone surface 11 is pushed into the second valve seat bore 7 of the operating line by the pressure spring 14 and therewith blocks the connection of said line with respect to the tank in an oil-tight manner. On the magnet side, the valve spindle 5 is radially formed with a groove ring seal 25 with respect to the armature space 22. The sealing diameter D1 of the valve spindle 5 toward the armature space 22 is larger than the second valve seat bore 7. Therewith, there results a defined area ratio between the cone seat and the sealing diameter D1 of the armature space 22. If the operating line A is pressurized, a differential force is generated through the area ratio between the operating line and the sealed armature space 22, which force pulls the valve spindle 5 toward the solenoid 4 and acts in addition to the elastic force against the second valve seat bore 7. The sealing effect increases with increasing pressure in the operating line A. The solenoid 4 is preferably configured such that a switching against the elastic force plus differential force is prevented. In this position, the pressure line P and the tank line T are connected to each other.
In addition, the valve housing 2 in the solenoid valve 1 according to the sixth embodiment is designed somewhat simpler. The valve chamber 3 is no longer structured in two parts including a first valve chamber insert 27 and a second valve chamber insert 28. Rather, only one valve chamber insert 27 is used in this embodiment.
Further, it is advantageous that the free-swing assembly comprises a first front face arranged vertically with respect to the longitudinal door closer axis and being fixedly connected to the piston rod as well as a second front face in parallel with the first front face and fixedly connected to the piston assembly, wherein the second front face lifts off from the first front face and thus decouples when the closer spring is locked. By two abutting and lifting front faces, a very simple and efficient free-swing assembly can be realized as a sliding-coupling.
In a preferred embodiment of the piston assembly, it is provided that the piston assembly comprises a damper piston including a first cam roller and an opening piston including a second cam roller, wherein the output shaft is arranged between the damper piston and the opening piston. The cam rollers of the damper piston and of the opening piston have to be in constant contact with the rolling contour, and thus roll on the rolling contour when the output shaft is rotated. Therewith, a working stroke is generated for the damper piston and the opening piston. On the longer side of the door closer housing, the closer spring is biased through the opening piston and the piston rod. On the other side thereof, the hydraulically effective damper piston is displaced. By displacing the damper piston, the hydraulic volume is displaced, such that the door velocity during the closing process is controlled or braked by interposed throttle valves. In combination with the force of the closer spring, a resultant force is generated through the cam geometry of the rolling contour, which force generates the opening and closing moment by the corresponding internal lever arm. In order to design the proposed door closer as slender as possible, the opening piston and the damper piston are preferably arranged in a specific way: The damper piston is disposed on one side of the output shaft and the opening piston is disposed on the other side of the output shaft, such that the output shaft is arranged between these two pistons. Consequently, no direct contact is possible between the opening piston and the damper piston. Said very slender constructional design of the door closer provides that a combination of both functions, biasing the closer spring and dampening the closing process, is not directly possible within one component. The realization of the hydraulic auxiliary function “free-swing” therefore requires elaborate means on both housing sides, since the functional areas are arranged separately within the housing. For a comparison: In case of widely designed floor door closers, only one piston is generally provided on the spring side, which simultaneously realizes the closer spring biasing and the damping function. In this case, however, a so-called tab carriage is used, which surrounds the cam contour including the two rollers supported therein and secures a constant monitoring of the cam-roller-contact. Upon use of said plate-carriage, no further considerations are required for securing the clearance-free contact between the two pistons of the piston assembly and the rolling contour. However, such a plate-carriage cannot be used in integrated and very slender constructed door closers, as they are proposed herein. In addition, when using a cam technology, it has to be considered that small strokes and thus small volume displacements with simultaneous high tensile force requirements are present, which is a disadvantage compared to the common rack-and-pinion technologies. Cam door closers therefore require sustainable bearings and elaborate hydraulic component arrangements. In the following, two variants are disclosed, which enable that the two separated, pistons, the opening piston and the damper piston, always have a clearance-free contact with the rolling contour. A first variant uses tie rods and internal clearance compensation springs. The second variant uses pressure springs which engage outside at the opening piston and/or the damper piston.
Preferably, it is provided that the piston assembly comprises at least two integrated clearance compensation springs, wherein at least two tie rods being arranged diagonally to each other are tensile-loaded by means of the clearance compensation springs, in order to compensate for a clearance between the rolling contour and the cam rollers. These two tensile-loaded tie rods provide for a clearance compensation between the cam rollers of the two pistons and the rolling contour, and the other two diagonal rods serve to prevent twisting and therewith prevent tilting moments and related friction or seizing of the opening piston and the damper piston.
Preferably, the door closer comprises a solenoid control valve, in particular a 3/2-solenoid control valve, wherein a closure damping compartment is formed between the door closer housing and the piston assembly on a side of the piston assembly facing away from the piston rod, in particular on the side of a damper piston.
The solenoid control valve controls at least the pressures in the closure damping compartment and in the lock compartment. The solenoid control valve enables to hydraulically seal the lock compartment. Therewith, the closer spring, once biased, can no longer relax and the free-swing-function of the door closer is activated. By switching the solenoid control valve, the lock compartment is again pressure-released and the closer spring can dislocate the piston assembly and therewith close the door through the output shaft, in case of a fire.
In a preferred embodiment of the opening damping compartment, it is provided that a first unthrottled connection is arranged between the opening damping compartment and the tank compartment, wherein the first throttled connection is always open and the first unthrottled connection is either closed or opened by the piston assembly, depending on the position of the piston assembly. The first unthrottled connection preferably enters into the opening damping compartment between the first throttled connection and the output shaft. Therewith, the hydraulic oil can be discharged through the first unthrottled connection into the tank compartment at the beginning of the opening process of the door. Consequently, the door can be opened very easily and without any resistance at the beginning of the opening process. When a specific opening angle is reached, the piston assembly, in particular the opening piston, closes the first unthrottled connection. Consequently, the hydraulic oil can only be discharged through the first throttled connection into the tank compartment and the door is damped shortly before it reaches its final position during opening.
In a preferred embodiment, it is provided that the solenoid control valve connects the first line to the third line and blocks the second line in a first switching position; in a second switching position, the second line is connected to the third line and the first line is blocked. Therewith, the pressure line P and thus the lock compartment are connected to the tank line T in the first switching position. The operating line A and thus the closure damping compartment are blocked. In this switching position, the closer spring or the closer spring tension piston, respectively, are not locked and the free-swing-function is deactivated. By blocking the operating line A, the hydraulic oil can be discharged from the closure damping compartment into the tank compartment only through the further throttled connection and the closing process of the door is therewith always damped. In the second switching position, the pressure line P of the lock compartment is blocked and the operating line A of the closure damping compartment is connected to the tank line. Therewith, the closure spring is hydraulically arrested and the free-swing-function is activated. In this switching position, the closure spring cannot transmit any force to the piston assembly. Simultaneously, the closer dampening is deactivated and the piston assembly is freely movable and the door can be moved without a large effort. This embodiment of the hydraulic control is the preferred embodiment.
In a preferred embodiment, it is provided that the solenoid valve releases the closer spring when de-energized and enables the free-swing-function when energized. For a constant maintenance of the free-swing-function, the solenoid valve has to be constantly energized. With this deenergize-to-trip-principle, it is guaranteed that the door always securely closes by means of the energy stored in the closer spring in case of a power breakdown. This closing function always has a priority for an emergency case and is regulated by law or industrial standards.
Further, the invention preferably comprises a filter, in particular in the first line. Particularly preferred, the filter is arranged outside the valve chamber directly in front of the inlet into the first valve seat bore. The filter prevents pollution of the oil and in particular a pollution of the two valve seats. In a further preferred embodiment, the first valve seat bore is arranged directly opposite to the second valve seat bore. In a preferred embodiment, the solenoid comprises a coil, an armature, a pole core as well as a gap between the pole core and the armature. The pole core comprises a borehole along the longitudinal axis of the valve spindle and therefore provides an accommodation and a linear guidance for the valve spindle. Further preferably, the inventive solenoid valves comprise a control unit for the solenoid. By means of said control unit, the solenoid can be switched between energized and de-energized.
Further, it is preferred that the hydraulic cartridge solenoid control valve comprises a volume compensation unit including a tank compartment. This volume compensation unit including a tank compartment is integrated into the valve housing or connected to the valve housing by a flange. The tank compartment is preferably connected to the third line. The valve is preferably structured along the longitudinal axis of the valve spindle as follows. The valve chamber including the valve spindle is arranged in the center. On one side of the chamber, the volume compensation unit including the tank compartment is integrated or connected by a flange. On the other side of the valve chamber, the solenoid is mounted. Therewith, the hydraulic cartridge solenoid control valve can be inserted into a component with the volume compensation unit to the fore. The solenoid and in particular a plug at the solenoid preferably protrude from the component. In a preferred embodiment, the tank compartment of the volume compensation unit is slightly pressure-loaded by a volume compensation piston and a compensation spring/pressure spring.
In addition, the invention comprises a door closer, in particular a hinge door closer, including a free-swing-function, comprising one of the afore-described hydraulic solenoid valves or one of the hydraulic cartridge solenoid valves, wherein the valve adapter is formed in the door closer. The hydraulic solenoid valve or the cartridge solenoid valve is thus integrated into the housing of the door closer or connected thereto by a flange, and serves to control the hydraulic between the closure damping compartment, the lock compartment and the tank compartment or the tank line.
1. A door closer having at least one of a locking function and a free-swing function, comprising:
an output shaft configured to be connected to a door;
a hydraulic lock compartment adapted to lock the closer spring;
an sliding-coupling accommodating space for the closer spring that becomes smaller during an opening process of the door;
a spring-loaded check valve that locks toward the accommodating space becoming smaller and arranged between the hydraulic lock compartment and the accommodating space;
a closer spring tension piston guided in the door closer housing and abutting on the closer spring;
wherein the spring-loaded check valve is arranged such that hydraulic oil in the accommodating space is pre-pressurized by an opening process and is actively pumped through the spring-loaded check valve into the hydraulic lock compartment.
3. The door closer of claim 2, wherein the free-swing assembly is a sliding-coupling that exclusively transmits compressive force between the closer spring and the piston assembly.
4. The door closer of claim 1, further comprising:
a fluid-tight separating wall arranged in the door closer housing between the piston assembly and the closer spring,
wherein the piston rod passes through the separating wall in a fluid-tight manner.
5. The door closer of claim 4, wherein the hydraulic lock compartment is arranged between the separating wall and the closer spring tension piston.
6. The door closer of claim 1, wherein
the piston assembly comprises at least one cam roller abutting on the cam-shaped rolling contour.
7. The door closer of claim 1, wherein the spring-loaded check valve is arranged in the closer spring tension piston.
8. The door closer of claim 1, wherein the accommodating space is closed, except for the spring-loaded check valve, during the opening process.
9. The door closer of claim 8, wherein a further check valve is arranged between the accommodating space a tank line, wherein the further check valve is configured to lock toward the tank line.
10. The door closer of claim 9, wherein the further check valve is a spring-loaded check valve.
11. The door closer of claim 1, wherein the door closer is a hinge door closer.
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Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BIENEK, VOLKER;WIEMANN, SABINE;PABST, THOMAS;SIGNING DATES FROM 20120417 TO 20120418;REEL/FRAME:028502/0458