US20040145284A1

US20040145284A1 - Braking and damping device

Info

Publication number: US20040145284A1
Application number: US10/755,688
Authority: US
Inventors: Remo Egger
Original assignee: Individual
Current assignee: Grass GmbH Deutschland
Priority date: 2003-01-16
Filing date: 2004-01-12
Publication date: 2004-07-29
Also published as: ATE348936T1; DE502004002340D1; DE10301418A1; EP1441099A1; EP1441099B1

Abstract

The invention concerns a braking and damping device for movable masses—in particular, for movable cabinet components, with a casing, a first adjustable braking element that is located partially in the casing and is coupled with the movable cabinet component and a second adjustable braking element that is located in the casing; whereby, the braking elements form operating surfaces that are inter-related, so that a shifting of the braking elements relative to one another produce a braking force. The invention shows that the braking elements that are coupled together by a transferring element that provides and removes force in such a manner that in a first movement phase, the braking elements implement a synchronous movement with which the relative velocity between the operating surfaces is smaller or less than the speed of the first braking element that is coupled with the cabinet component. In the second movement phase the braking elements implement opposite movement with which the relative velocity between the operating surfaces is greater than the speed of the first, with the braking element coupled with the cabinet component and in the third movement phase, the first two movement phases are opposite movement phases, the second braking element essentially stands still. The relative velocity between the operating surfaces corresponds essentially to the speed of the first braking element (7) coupled to the cabinet component.

Description

The invention concerns a braking and damping device for movable masses, in particular for movable cabinet components, such as, e.g. drawers, cabinet doors and lifter doors, according to the characterizing clause of the

patent claim

1.

Braking and damping devices that are based on friction principles are well known.

Document 101 21 977 A1 describes a braking and damping device for cabinet hardware fitting, here, in particular, used in a cabinet hinge. This device damps/absorbs the hinge rotating motion and prevents a fast, noisy and potential slamming of a cabinet door, lifter door or similar cabinet component on the cabinet. The braking and damping action is caused by at least one linear movable slide, which has at least one gliding surface, which moves along a corresponding stationary gliding surface of the cabinet hardware fitting. There is a highly viscous liquid medium between the sliding surfaces that cause the braking/damping effect. The movable part of the cabinet hardware fitting (as for example, a hinge arm) couples with the slider only within the range of a closing angle, so that the braking/damping action only takes place within this closing angle. The slider must overcome the opening movement and the entire braking force by the opening angle range, until the hinge arm disengages and can be brought slack into the open position.

It is the task of the invention to create a braking and damping device, in particular for movable cabinet components, which effectively brakes and dampens the movement of the cabinet components. Their braking and damping function differs in the direction of movement substantially from the braking and damping function in the other direction.

The task is solved, according to the invention, by the characteristics indicated in

patent claim

1.

The basis of the invention consists of braking elements that are coupled together by a transferring element that gives and removes force/energy in such a way that in the first movement phase of the braking element, the braking elements implement a synchronous movement with which the relative velocity between the operating surfaces is less than the speed of the first braking element that is coupled with the cabinet component. In the second movement phase, the braking elements implement movement in the opposite direction with which the relative velocity between the operating surfaces is greater than the speed of the first, with the cabinet component's coupled braking element. In the third movement phase, the first two movement phases are opposite movement phases, the second braking element essentially stands still and the relative speed between the operating surfaces corresponds essentially to the speed of the first braking element ( 7) that is coupled to the cabinet component.

The first two movement phases, preferably, go through when the movable cabinet components are braking; that is, during the first movement direction of the movable cabinet component. Because of the differing speeds of the operating surfaces relative to one another during the first two movement phases, different braking strengths/forces are also reached. Preferably, the braking force in the first movement phase (at the beginning of the deceleration process) is smaller than the braking strength/force in the second movement phase at the end of the deceleration process.

The third movement phase corresponds to the movement direction, which will go through a resetting or opening of the movable cabinet components. Here, the braking force is substantially less or smaller than in the second movement phase, because the relative speed between the operating surfaces of both braking elements is less or smaller.

Preferred embodiments and designs of the invention are given in the sub-claims.

In a preferred embodiment of the invention, the transferring element that gives and removes force is a pinion, whose rotational axle is held axially and longitudinally movable in the elongated slots of the casing, which are parallel to the movement direction of the braking element. Furthermore, each braking element is provided with a toothed rack, so that both toothed racks work together with the pinion and allow a transfer or removal of force between the braking elements.

According to the advantageous embodiment of the invention, the peripheral speed of the pinion during the first movement phase is less (advantageously, substantially less) than the speed with the cabinet component's coupled braking elements, so that the rotational axle of the pinion moves along the elongated slots in the same direction as this braking element. Thus, the relative speed between the operating surfaces is only half as much as the speed of the first braking element that is coupled with the cabinet component.

During the second movement phase, the peripheral speed of the pinion corresponds fundamentally to the speed of the braking element coupled with the cabinet component; whereby, the rotational axle of the pinion does not change its position. In this phase the relative velocity between the operating surfaces doubles in comparison to the first, with the braking element coupled to the cabinet component. The braking force increases greatly. This high braking and damping effect remains until the complete pushed-in position of the movable cabinet components.

During the third movement phase the peripheral speed of the pinion corresponds fundamentally to the speed of the braking element that is coupled with the cabinet component, so that the rotational axle of the pinion moves in the elongated slot in the same direction as this braking element. Thus, a small relative velocity between the operating surfaces of the braking elements results and with it, a smaller braking action.

According to the invention, it can be favorably accomplished that the first movement phase corresponds to the first braking force, the second movement phase corresponds to the second braking force and the third movement phase corresponds to the third braking force. By dimensioning the effective length and surface of the working surfaces and adjusting the length of the elongated slots, these varying braking forces can be adjusted in their strength and in their mutual relationships. The invention also makes it possible in a simple way, to choose longer damper ranges.

Increasing the braking action and maintaining a homogeneous braking operation can, advantageously, be achieved by putting a highly viscous liquid between the operating surfaces.

The operating surfaces of the respective braking elements are designed, preferably, as comb-groove areas. The effective friction strength and, with it, the braking force can be changed by varying the number of combs and slots.

The length of the braking range can also be determined by the effective length of the comb-groove area of the first braking element and the effective length of the comb-groove area of the second braking element, which differs from each other.

Naturally it is understood that the three movement phases can go through the reverse order; that is, the actual braking and damping process extends over the third movement phase, while the resetting movement of the device goes through the second and the first movement phases, one after the other.

The invention is more closely described in the following on the basis of the designs. Further characteristics, advantages and application possibilities of the invention are shown in the drawings and their descriptions. [0019]
FIG. 1 shows the braking and damping device in a fully extended pulled-out position (that is, at the beginning of its braking/damping action); [0020]
FIG. 2 shows the braking and damping device in a position in which the connecting push and draw rod is partially inserted; [0021]
FIG. 3 shows the braking and damping device in a position in which the connecting push and draw rod is inserted even more; [0022]
FIG. 4 shows the braking and damping device in a position in which the connecting push and draw rod is inserted almost completely; [0023]
FIG. 5 shows the braking and damping device with its connecting push and draw rod at the end of the operating range; [0024]
FIG. 6 shows the braking and damping device in a position in which the connecting push and draw rod is partially pulled out; [0025]
FIG. 7 shows the braking and damping device in a position in which the connecting push and draw rod is pulled out almost maximally; [0026]
FIG. 8 shows the braking and damping device in a position in which the connecting push and draw rod are pulled out maximally; [0027]
FIG. 9 shows the individual parts of the braking and damping device in an exploded representation;[0028]
FIG. 1 shows the braking and damping device ([0029] 1) in a fully pulled-out extended position (that is, at the beginning of its braking/damping action), for example, when closing a drawer. As is evident in connection to FIG. 9, two sliders—a lower slider (7) and an upper slider (12) are located in a casing. (2) that is formed, preferably, as a tube with a square or right-angled cross section. The sliders (7, 12) are guided lengthwise into the casing (2) and can be moved back and forth in arrow direction (19 and/or 20) (FIG. 5). There is a cover (5) at the end of the casing (2), which can, preferably, also be designed as the device's fastener. A vent bore hole (6) can, preferably, be found in this cover (5). The opposite end of the casing (2) is open; only a stop (18) is located at this end (see FIG. 9 also).
The lower slider ([0030] 7) includes a connection push and draw rod (8) with a coupling head, which projects out of the open end of the casing (2). The coupling head is connected to the movable cabinet component (not shown) that is to be braked. The connecting push and draw rod (8) follows a toothed rack component (9) and a comb-groove area (10). The comb-groove area (10) forms the actual operating surface (11), which produces a braking force. The horizontal surface of the sliders (7, 12) and the parallel side surfaces are adjustable longitudinally with the slide fit in the casing (2).
The upper slider ([0031] 12) is designed with a connecting push and draw rod and is therefore shorter and has a somewhat similar length toothed rack component (13) as the lower slider, but has a shorter comb-groove area (14). This comb-groove area (14) also forms an operating surface (15) for producing a braking force. The slider (12) is likewise held lengthwise adjustable with the slide fit in the casing (2). Both sliders (7, 12) are guided in relation to each other, so that the comb-groove area (10, 14) can likewise engage to one another with the slide fit. Both toothed rack areas (9, 13) are arranged against each other so that the pinion (16) forms a torque-transferring pinion gear between them. The pinion (16) has a continuous axle (17), which is held axially movable and lengthwise movable on both sides in the elongated slots (3, 4) of the casing (2).
Preferably, there is a highly viscous liquid between the comb and grooves (that engage into one another) of both sliders ([0032] 7, 12) and/or between the operating surfaces (11, 15).
FIG. 1 shows the lower slider ([0033] 7) in its fully extended (pulled-out) position and the upper slider that is located a small distance from the stop (18). The connecting push and draw rod is now moved in arrow direction (19) by the cabinet component that is to be braked.
FIG. 2 shows the connecting push and draw rod ([0034] 8) of the slider (7) that is pushed partially into the casing (2). During this movement the pinion (16) goes in a clockwise direction and its axle (17) is carried at the same time along the elongated slots (3, 4) in direction (19). The peripheral speed of the pinion (16) is therefore smaller than the speed of the lower slider (7). In the position shown the pinion (16) and the upper slider (12) are about halfway on its sliding distance. Because of the smaller peripheral speed of the pinion (16), the upper slider (12) goes only about ¼ of the sliding distance of the lower slider (7) and in the same direction (arrow direction 19). The relative velocity between the operating surfaces (11, 15) of the comb and groove areas (10, 14) is therefore only about half as much as the draw-pull speed of the connecting push and draw rod (8)—that is, the speed of the cabinet component to be braked. The damping action is, therefore, relatively small in this first movement phase.
In FIG. 3 the axle ([0035] 7) of the pinion (16) is at the end of the elongated slots (3, 4) while the connecting push and draw rod (8) continues the draw-pull movement with the lower slider (7) and the toothed rack (9). The pinion (16) turns in the clockwise direction with the same speed as the speed of the lower slider on the spot at the rear end of the elongated slots (3, 4). The upper slider (12) moves, therefore, with the same longitudinal speed as the lower slider (7) in the direction of the stop (18)—that is, towards the arrow direction (19). The sliders (7, 12) move to each other in opposite directions, so that the relative speed between the comb and groove areas (10, 14) doubles in relation to the respective speed of the slider (7, 12). Thus, the braking and damping action increases greatly in this second movement phase. This high braking and damping effect stays until the complete pushed-in position of the lower slider (7). FIG. 4 shows the position of the slide system in which the operating surfaces (11, 15) of the comb and groove areas (10, 14) still move with double relative speed to each other.
FIG. 5 shows the lower slider ([0036] 7) at the end of it operation. The upper slider (12) likewise has its operation distance and stands a short distance before its stop (18).
FIG. 6 shows the beginning of the third movement phase of the braking and damping device ([0037] 1). In this movement phase both sliders (7, 12) are brought back into their initial position. The connecting push and draw rod (8) of the lower slider (7) is already pulled out partially in arrow direction (20) from the casing (2). The pinion (16) turns counterclockwise and has already unreeled on the toothed rack (13) of the upper slider (12) and the slider presses completely on the stop (18). The upper slider (12) remains like this for the remainder of the third movement phase. The lower slider (7) and the pinion (16) maintain its opening/pull-out movement, so that the pinion is forced to move in arrow direction (20) along the elongated slots (3, 4). The comb and groove area (10, 14) and/or the operating surfaces (11, 15) move to each other with a speed that corresponds to the opening pull-out speed of the lower slider (7). The braking action is not as strong and lies between the braking strengths of the first two movement phases. The braking force remains essentially the same during the entire third movement phase. This movement is kept in addition to the position according to FIG. 7.
At the end of the third movement phase (that is, at the end of the pull-out movement) as shown in FIG. 8, the axle ([0038] 17) of the pinion (16) stops at the beginning of the elongated slots (3, 4) and presses the upper slider (12) away from the stop (18). The connecting push and draw rod (8) (that is, the upper slider [7]) reaches the pull-out end. The positions of the sliders (7, 12) correspond to the initial ‘beginning’ positions represented in FIG. 1.

Drawing Legend

[0039] 1. Braking and damping device
[0040] 2. Casing
[0041] 3. Elongated slot
[0042] 4. Elongated slot
[0043] 5. Cover
[0044] 6. Vent bore hole
[0045] 7. Slider (first)
[0046] 8. Connecting push-draw rod
[0047] 9. Toothed rack
[0048] 10. Comb-groove area
[0049] 11. Operating surface
[0050] 12. Slider (second)
[0051] 13. Toothed rack
[0052] 14. Comb-groove area
[0053] 15. Operating surface
[0054] 16. Pinion
[0055] 17. Axle
[0056] 18. Stop
[0057] 19. Arrow direction
[0058] 20. Arrow direction

Claims

1. Braking and damping device for movable masses, in particular for movable cabinet components, with a casing (2), a first adjustable braking element (7) that is located partially in the casing and is coupled with the movable cabinet component and a second adjustable braking element (12) that is located in the casing; whereby, the braking elements form operating surfaces (11, 15) that are related to one another, so that a shifting of the braking elements relative to one another produce the braking force, is characterized by the braking elements (7, 12) that are coupled together by a transferring element (16) that provides and removes force in such a manner that in a first movement phase the braking elements (7, 12) implement a synchronous movement with which the relative velocity between the operating surfaces (11, 15) is smaller or less than the speed of the first braking element (7) that is coupled with the cabinet component. In the second movement phase the braking elements (7, 12) implement opposite movement with which the relative velocity between the operating surfaces (11, 15) is greater than the speed of the first, with the braking element (7) coupled with the cabinet component and in the third movement phase, the first two movement phases are opposite movement phases, the second braking element (12) essentially stands still. The relative velocity between the operating surfaces (11, 15) corresponds essentially to the speed of the first braking element (7) coupled to the cabinet component.

2. Braking and damping device, according to claim 1, is characterized by the transference element that gives and removes force that is a pinion (16), which rotational axle (17) is held axially movable and longitudinally movable in the elongated slots (3, 4) of the casing (2), are parallel to the movement direction of the braking elements (7, 12).

3. Braking and damping device, according to one of the claims 1 or 2, is characterized by each braking element (7, 12) has a toothed rack (8, 13) and both toothed racks work together with the pinion (16).

4. Braking and damping device, according to one of the claims 1 to 3, is characterized by the peripheral speed of the pinion (16) that is less in the first movement phase than the speed of the braking element (7) that is coupled with the cabinet component; whereby, the rotational axle (17) of the pinion moves along the elongated slot (3, 4) in the same direction (19) as this braking element (7).

5. Braking and damping device, according to one of the claims 1 to 4, is characterized by the peripheral speed of the pinion (16) during the second movement phase corresponds essentially to the speed of the braking element (7) that is coupled to the cabinet component; whereby, the rotational axle (17) of the pinion does not change its position.

6. Braking and damping device, according to one of the claims 1 to 5, is characterized by the peripheral speed of the pinion (16) during the third movement phase that corresponds essentially to the speed of the braking element (7) that is coupled to the cabinet component; whereby, the rotational axle (17) of the pinion moves along the elongated slots (3, 4) in the same direction (20) as this braking element (7).

7. Braking and damping device, according to one of the claims 1 to 6, is characterized by the highly viscous liquid that is put in between the operating surfaces (11, 15).

8. Braking and damping device, according to one of the claims 1 to 7, is characterized by the fact that each braking element (7, 12) has a comb-groove area (10, 14) that forms the operating surfaces (11, 15), which produce the braking action.

9. Braking and damping device, according to one of the claims 1 to 8, is characterized by the fact that the effective length of the comb-groove area (10) of the first braking element (7) differs from the effective length of the comb-groove area (14) of the second braking element (12).

10. Braking and damping device, according to one of the claims 1 to 9, is characterized by the fact that the first movement phase corresponds to a first braking strength/force, the second movement phase corresponds to a second braking strength/force, and the third movement phase corresponds to a third braking strength/force.

11. Braking and damping device, according to one of the claims 1 to 10, is characterized by the three movement phases that will go in reverse order.