EP3863473B1 - Self-retracting device with deflected spring energy accumulator - Google Patents

Description

The invention relates to a self-closing device with a housing (21) and a carriage (81), with a driver element that can be moved in the housing between a parking position secured by a non-positive and/or positive fit and an end position and back, with a first element that connects the driver element and the housing Spring energy store and with at least one second spring energy store, both of which are charged when the driver element is in the parking position and are discharged to a residual energy value when the driver element is in the end position, the first spring energy store being guided around a deflection disk which is rotatably mounted relative to the carriage and wherein the carriage is loaded relative to the housing in the direction of the first spring energy storage device, which wraps around the deflection disk, by means of the second spring energy storage device, and the deflection disk has a circumferential guide groove.

From the DE 10 2008 021 458 A1 such a self-closing device is known.

The present invention is based on the problem of reducing the installation space required for such a self-closing device and simplifying assembly.

This problem is solved with the features of the main claim. For this purpose, the deflection pulley is supported on the carriage by means of two external bearing journals which are rotatably mounted in the carriage. At least one plane tangential to the lateral surface of the deflection pulley intersects both bearing journals. In addition, the deflection pulley is guided during a rotary movement by means of the carriage or by means of the bearing journal.

The deflection sheave of the self-closing device is supported in the longitudinal direction and in the height direction by means of several rolling contact zones. This can be a point, surface or line contact. Here, the deflection disk is pressed against two bearing journals by means of the first spring energy store that wraps around it. This pressing force is increased by means of the second spring energy accumulator, which presses a carriage carrying the bearing journals against the deflection disk. This determines the position of the deflection pulley in the longitudinal direction and in the vertical direction. In the transverse direction oriented transversely to the longitudinal direction and transversely to the vertical direction, the movement of the deflection disk is limited either by means of the carriage or by means of the bearing pins.

Figur 1:

Selbsteinzugsvorrichtung in der Parkposition;

Figur 2:

Selbsteinzugsvorrichtung in der Endposition;

Figur 3:

Schlitten;

Figur 4:

Umlenkscheibe;

Figur 5:

Lagerzapfen;

Figur 6:

Ansicht der Selbsteinzugsvorrichtung von der Rückwand;

Figur 6:

Schnitt der Schlittenbaugruppe;

Figur 8:

Variante der Schlittenbaugruppe.

Further details of the invention result from the subclaims and the following description of embodiments shown schematically.

Figure 1:

self-closing device in the parking position;

Figure 2:

self-closing device in the final position;

Figure 3:

Sleds;

Figure 4:

deflection pulley;

Figure 5:

bearing journal;

Figure 6:

View of the self-closing device from the rear wall;

Figure 6:

section of carriage assembly;

Figure 8:

Variant of slide assembly.

the Figures 1 and 2 show a self-closing device (10). Such self-closing devices (10) are used to move moving furniture parts, such as drawers or sliding doors, relative to a fixed furniture part, such as a furniture body, in a controlled manner into a closed or open end position. In this case, the self-closing device is fastened to one piece of furniture and a driver is fastened to the piece of furniture that is moved relative thereto. Before reaching the closed or the open end position, the driver contacts a driver element (41) of the self-closing device (10) and releases it from a parking position (11). The drawer or the sliding door is now conveyed to the end position by the self-closing device (10). In the end position of the sliding door or the drawer, the driver element (41) is in an end position (12), cf. figure 2 .

The self-closing device (10) has a housing (21) consisting of a lower housing shell (22) and an upper housing shell (35), cf. figure 6 , consists. On the upper side (23), the housing (21) has a longitudinal slot (24) through which the driver element (41) protrudes into the environment (1). The driver element (41) is guided in the housing (21) by means of a pair of guide pins (42) arranged on both sides and by means of a piston rod head (52) along a guide track (25) on the housing side. This track (25) in the longitudinal direction (5) oriented straight section (26) and in the representations of Figures 1 and 2 downwardly curved parking section (27). In the parking position (11), the driver element (41) with the pair of guide pins (42) is in the parking section (27). The piston rod head (52) is in the straight section (26). In the in the figure 2 shown end position (12) are both the pair of guide pins (42) and the piston rod head (52) in the straight section (26). A driver recess (43) of the driver element (41) points upwards. The driver element (41) can also be designed in several parts. For example, a pull pin (44) delimiting the driving recess (43) can be folded down. The bottom of the housing (21) and areas of the front wall (31) and the rear wall (28) are open in the embodiment. But they can also be closed.

In the exemplary embodiment, a hydraulic cylinder-piston unit (51), for example, is also mounted in the housing (21). The cylinder-piston unit (51) has a cylinder (53) in which a piston that can be displaced by means of a piston rod (54) is guided. For example, when the piston rod (54) is retracted, oil is throttled from a displacement space located between the piston and the cylinder base (55) into a compensation space located between the piston and the cylinder head (56). repressed. The piston rod (54) carries the piston rod head (52) which is pivotably mounted in the driver element (41). The self-closing unit (10) can also be designed without a cylinder-piston unit (51).

It is also conceivable not to connect the piston rod (54) of the cylinder-piston unit (10) to the driver element (41). The driver element (41) then has, for example, two pairs of guide pins (42). In this case, for example, a restoring spring is arranged in the displacement chamber and loads the piston rod (54) with the piston rod head (52) in the direction of the driver element (41). For example, if the driver element (41) is moved quickly in the direction of the parking position (11), the piston rod head (52) can become detached from the driver element (41) in such an embodiment.

The cylinder-piston unit (51) can be arranged in the housing (21) in such a way that the piston rod (54) points towards the rear wall (28) of the housing (21) and the cylinder base (55) is oriented towards the driver element (41). For example, the cylinder (53) is then slidably mounted in the housing (21). The cylinder base (55) can be connected to the driver element (41) or rest against it.

A first spring energy store (61) is held on the driver element (41) and in the housing (21). This first spring energy store (61) is suspended in a spring holder (36) in the housing (21). This first spring energy store (61) is a tension spring (61) in the exemplary embodiment. Its length, relaxed to a residual energy value, is, for example, 1.35 times the length of the housing (21) measured in the longitudinal direction (5). The Indian figure 1 shown charged first spring energy store (61) is 50% longer than the housing (21).

The first spring energy store (21) is guided around a deflection disk (71) of a carriage assembly (70). The angle of wrap of the spring energy store (61) around the deflection disk (71) is 181 degrees in the exemplary embodiment.

The carriage assembly (70) comprises a carriage (81), the deflection disk (71), two bearing journals (91) and a second spring energy store (101). The carriage (81) with the deflection disk (71) and the bearing journal (91) is loaded relative to the housing (21) by means of the second spring energy store (101) in the direction of the rear wall (28). For this purpose, the second spring energy store (101) is attached to the housing (21) and to the carriage (81). In the exemplary embodiment, the carriage assembly (70) is guided in the longitudinal direction (5) by means of the deflection disk (71) engaging in a housing groove (29) by means of a guide bolt (74). The carriage assembly (70) can also be designed without a guide on the housing side.

In the figure 3 the carriage (81) of the carriage assembly (70) is shown. The carriage (81) has a cuboid enveloping contour. For example, it has a transverse opening (82) with a rectangular cross-section approximately in the middle. This transverse opening (82) is surrounded on all sides by connecting webs (83). These connecting webs (83) connect two parallel guide plates (84). The guide plates (84) delimit the carriage (81) in the transverse direction (6). You can be flush with the connecting webs (83) in the height direction (7). At its end pointing towards the end wall (31) of the housing (21), the carriage (81) has a spring bushing (85) opening into the transverse opening (82). This spring bushing (85) is oriented, for example, in the longitudinal direction (89) of the slide.

At the end facing away from the spring bushing (85), the carriage (81) has two bearing pin receptacles (86). These trunnion mounts (86) are oriented in the transverse direction (6). In the exemplary embodiment, the bearing journal receptacles (86) are arranged symmetrically to a central transverse plane of the carriage (81) oriented in the longitudinal direction (89) of the carriage. The individual bearing pin receptacle (86) has an insertion recess (87) on each guide plate (84) which opens into a receptacle (88) in the shape of a section of a cylinder. Here, the guide plates (84) protrude like a fork from the connecting webs (83). The distance between the guide plates (84) is 78% of the overall width of the carriage (81). The width of the carriage (81) is, for example, 95% of the inside width of the housing (21).

the figure 4 shows the deflection disk (71). In the exemplary embodiment, the deflection disk (71) has a hollow hub (73) in which, for example, the guide pin (74) is inserted when the deflection disk (71) is installed. For example, the deflection disk (71) can be guided in the housing groove (29) by means of the guide pin (74). Concentrically to the hollow hub (73), the deflection disk (71) has two congruent disk horns (75). Both disc horns (75) have cylindrical lateral surfaces (76). These disc horns (75) delimit a circumferential guide groove (77). The guide groove (77) has a central U-shaped channel section (78) which is delimited towards the outside on both sides by a concave outer channel section (79). The radius of curvature of the outer channel section (79) is, for example, three times the radius of the channel section (78). In the exemplary embodiment, the width of the deflection disk (71) over the disk horns (75) is 99% of the distance between the two guide plates (84) in the region of the bearing pin receptacles (86). The deflection disk (71) can also be designed without a hub. In this In this case, the two disc horns (75) can be circular discs.

In the figure 5 a bearing pin (91) is shown. Both bearing journals (91) are of identical design in the exemplary embodiment. The individual bearing journal (91) is made up of, for example, five mutually coaxial sections (92-94). In the exemplary embodiment, its length corresponds to the width of the carriage (81) in the transverse direction (6). The individual bearing journal (91) is constructed symmetrically in relation to its central plane oriented normal to the transverse direction (6). A cylindrical bearing section (92) adjoins each of the end faces (95). Its diameter is, for example, 96% of the diameter of a bearing journal receptacle (86). A likewise cylindrical collar section (93) adjoins the respective bearing section (92). Its diameter is slightly larger than the diameter of the receptacle (88).

Furthermore, the bearing pin (91) has a central guide section (94). This is designed as a peripheral guide collar (94). In the exemplary embodiment, its length in the transverse direction (6) is a quarter of the length of the bearing journal (91). In the embodiment, this length can be up to 56% of the length of the bearing journal (91). Its diameter is 25% larger than the diameter of the bearing section (92). The guide collar (94) is rounded in the transverse direction (6). The bearing pin (91) can also be designed without a guide collar (94) or with more than one guide collar (94).

When assembling the self-closing device (10), for example, the driver element (41) with the cylinder-piston unit (51) is first inserted into the lower housing shell (22). Then the carriage (81) with the inserted therein Bearing pin (91) inserted in the lower housing shell (22). Here, the carriage (81) with the transverse opening (82) is placed over the housing-side spring mount (32). Now, for example, the second spring energy store (101), designed as a tension spring, can be hung in the spring receptacle (32) on the housing and in the spring bushing (85) of the carriage (81). For example, the carriage (81) is now in the figure 2 shown position. The deflection disk (71) with the inserted guide bolt (74) can now be inserted in such a way that the guide bolt (74) engages in the housing groove (29) and the lateral surfaces (76) of the deflection disk (71) on the collar sections (93) of the bearing journals (91). Finally, the first spring energy store (61) can be hung in the driver element (41) and in the housing (21) and guided around the deflection disk (71). Finally, the housing upper shell (35) can be put on and the housing (21) can be joined. For example, it is screwed or welded. A different order of assembly is also conceivable.

The space required for the self-closing device (10) is determined by the external dimensions of the housing (21). the figure 6 shows a view of the rear wall (28) of the self-closing device (10). The required width of the housing (21) in the upper area (33) results from the cylinder-piston unit (51). In the lower area (34), the carriage (81) determines the width of the housing (21). For example, the width of the lower area (34) is 75% of the width of the upper area (33) of the housing (21). The housing (21) is shown in the illustration figure 6 used with the lower area (34), for example, in a carrier profile (15).

After assembly, the self-closing device (10) is, for example, in the figure 2 illustrated end position (12). The piston rod (54) of the cylinder-piston unit (51) is retracted. The first spring energy store (61) is discharged to a residual energy value. The tension spring (61) is stretched, for example, by 30% compared to its fully unloaded nominal length. It loads the deflection disk (71) against the bearing journal (91). The bearing journals (91) are arranged, for example, symmetrically to the bisecting line of the angle of wrap. For example, the radials intersecting the center axis (72) of the deflection disk (71) enclose an angle of 54 degrees through the center lines (96) of the bearing journals (91). At least one plane tangent to the deflection disk (71) intersects both bearing journals (91). The two bearing journals (91) are thus offset from one another on the side of the deflection disk (71) facing the carriage (81). In the exemplary embodiment, a tangential plane oriented normal to the longitudinal direction (89) of the carriage divides 27% of the volume of both bearing journals (91) from the deflection disk (71).

A tangential plane on both bearing journals (91) facing the deflection disk (71) has a smaller distance to the central axis (72) of the deflection disk (71) than each tangent to the first spring energy store (61) parallel to this tangential plane. The latter tangential plane is oriented, for example, normal to the bisecting line of the angle of wrap. This bisector is oriented, for example, in the longitudinal direction (89) of the slide. In the exemplary embodiment, this tangential plane lies against the guide sections (94) of the bearing journals (91).

The second spring energy store (101) is also at a residual energy value when the driver element (41) is in the end position (12). relieved. For example, this tension spring (101) is 20% longer than its unloaded nominal length. The second spring energy store (101) loads the slide (81) in the direction of the first spring energy store (61). The forces of both spring energy stores (61, 101) act together on the contact points (111) between the deflection disk (71) and the bearing journal (91). The force vectors caused by the two spring energy stores (61, 101) point to contact points (111) from opposite directions. The contact between the deflection disc (71) and the bearing journal (91) is thus additionally secured. A movement of the deflection disk (71) in the longitudinal direction (5) as well as in the vertical direction (7) is thus prevented.

In the exemplary embodiment, the carriage (81) encompasses the first spring energy store (61) both in the upper run (62) and in the lower run (63). The first spring energy store (61) is thus guided by means of the carriage (81). The projecting guide plates (84) of the carriage (81) lie on both sides of the deflection disk (71).

the figure 7 shows a sectional view of the deflection disk (71), a bearing journal (91) and the carriage (81). The sectional plane of this view is spanned by the central axis (72) of the deflection disk (71) and a radial line connecting this to the central line (96) of a bearing journal (91). The first spring energy store (61) and the housing (21) are not shown in this view.

In the representation of figure 7 the carriage (21) with its two guide plates (84) overlaps the deflection disk (71) in some areas. The carriage thus limits a movement of the deflection pulley (71) in the transverse direction (6). With that he leads Carriage (81) in this embodiment, the deflection disc (71) in a rotary movement.

The bearing pins (91) are rotatably mounted in the carriage (81). The bearings of the bearing sections (92) in the receptacles (88) are designed as plain bearings in the exemplary embodiment. The respective collar sections (93) prevent the bearing journals (91) from moving in the transverse direction (6). The deflection disk (71) rests with its disk horns (75) on the collar sections (93). The contact points (111) are contact lines oriented in the transverse direction (6). The guide sections (94) of the bearing pins (91) are immersed in the guide groove (77). In the embodiment, they have no contact with the guide groove (77).

For example, when you open the sliding door or the drawer, the driver pulls from the in the figure 2 shown end position (12), the driver element (41) relative to the housing (21) in the opening direction (13). The first spring energy store (61) is loaded. In doing so, it loads the deflection disk (71) in the opening direction (13). The deflection disk (71) also pushes the carriage (81) in the opening direction (13). At the same time, the deflection disk (71) is rotated about its central axis (72). It rolls off on both bearing journals (91), which are rotated in the process. The second spring energy store (101) is charged. The expansion of the first spring energy store (61) is less than the stroke of the driver element (41) in the longitudinal direction (5). The spring-loaded deflection shortens the stroke. When the driver element (41) moves in the opening direction (13), the piston rod (54) is pulled out relative to the cylinder (53).

As the carrier element (41) moves further, it reaches the parking position (11), cf. figure 1 . The first spring energy store (61) and the second spring energy store (101) are charged to their respective maximum operating values. The driver element (41) is secured in the housing (21) in a non-positive and/or positive manner. The carrier is released. The sliding door or drawer can now be opened further.

When the sliding door or the drawer is closed, the driver contacts the driver element (41) in a partial stroke adjacent to the closed end position, for example. The driver element (41) is released from the parking position (11). Its guide pin pair (42) pivots into the straight section (26) of the guide track (25). The driver element (41) moving in the closing direction (14) loads the piston rod (54). This is pushed into the cylinder (53). Here, e.g. oil is displaced from the displacement chamber into the compensation chamber. The movement of the driver element (41) is delayed. At the same time, the first spring energy store (61) pulls the driver element (41) in the direction of the end position (12).

The shortening first spring energy store (61) rotates the deflection disc (71) in the illustrations Figures 1 and 2 clockwise. In these views, the deflection disk (71) rotates the bearing journals (91) mounted in the carriage counterclockwise. As the contact pressure of the first spring energy store (61) decreases, the load on the second spring energy store (101) is relieved. The carriage (81) is moved in the closing direction (14). For example, the forces of both spring energy stores (61, 101) are superimposed. In the exemplary embodiment, the two spring energy accumulators (61, 101)) together with a low spring rigidity have an accelerating effect on the driver element (41). This acceleration force counteracts the deceleration force of the cylinder-piston unit (51). The resultant of these forces slowly pulls the sliding door or drawer into the closed end position, for example. Here the door or the drawer remains without hitting.

For example, in the event of rapid closing, the first spring energy store (61) can lift off the deflection disk (71). The deflection pulley (71) is relieved abruptly, for example. Migration of the deflection disk (71) is prevented by means of the guide collars (94), the carriage (81) and the position of the bearing journals (91) relative to the deflection disk (71). Due to the deflection, an elongation of the first spring energy store (61) only allows a maximum of half the amount of this elongation as a displacement of the deflection disk (71). At the same time, when the deflection disk (71) is relieved, the carriage (81) is displaced in the closing direction (14) by means of the second spring energy store (101). The first spring energy store (61) is again accommodated in the guide groove (77).

The carriage assembly (70) can also have two second spring energy stores (101). These are then arranged parallel to one another, for example, and each is held on the carriage (81) and on the housing (21). In this case, a second spring seat (32) is provided in the housing (21).

In the figure 8 a variant of the carriage assembly (70) is provided. The sectional plane of this representation corresponds to the sectional plane of the figure 7 .

The width of the carriage (81) corresponds to the width of the deflection pulley (71). In this variant, the bearing journals (91) with their bearing sections (92) are also in the carriage (81). pivoted. For example, the guide section (94) directly adjoins the bearing sections (92). Its outer diameter corresponds to the outer diameter of the bearing pin (91) shown in FIG.

In this exemplary embodiment, the deflection disk (71) is designed without a hub. The disc horns (75) delimit the deflection disc (71) in the transverse direction (6). The cross section of the guide groove (77) of the deflection disc (71) corresponds to the cross section in the figure 4 shown guide groove (77).

The deflection disk (71) touches the individual bearing journal (91) in two rolling contact zones (111). On the side of the individual bearing journal (91), these rolling contact zones (111) lie in the outer radii (97) of the guide sections (94). The rolling contact zones (111) are located in the outer channel sections (79) on the deflection disk (71). Depending on the load, these rolling contact zones (111) can be points or small areas. In this exemplary embodiment, the lateral surfaces (76) of the disk horns (75) are not in contact with the bearing journals (91).

The width in the transverse direction (6) of the in the figure 8 shown variant of the carriage assembly (70) is, for example, 20% less than the width in the figure 7 illustrated embodiment.

The function of a self-closing device (10) with the in the figure 8 illustrated carriage assembly (70) corresponds to the function of the self-closing device (10) described in connection with the first embodiment. The carriage assembly (70) is prevented from tipping due to the prestressing of the first spring energy store (61) and the second spring energy store (101). If necessary an additional guide for the carriage (81) or the deflection disk (71) can be provided in the housing (21).

In this exemplary embodiment, the bearing journals (91) are held in the transverse direction (6) by means of the guide sections (94). By means of the guide sections (94), they guide the deflection disk (71) during its rotary movement. The guidance of the deflection disk (71) in the longitudinal direction (5) and in the vertical direction (7) corresponds to the guidance mentioned in connection with the first exemplary embodiment.

Combinations of the individual exemplary embodiments are also conceivable within the scope of the invention defined by the claims.

Reference list:

1

vicinity

5

longitudinal direction

6

transverse direction

7

height direction

10

self-closing device

11

parking position

12

final position

13

opening direction

14

closing direction

15

support profile

21

Housing

22

housing bottom shell

23

top

24

longitudinal slit

25

guideway

26

straight section

27

park section

28

back panel

29

housing groove

31

bulkhead

32

Spring retainer for (101)

33

top of (21)

34

bottom of (21)

35

housing upper shell

36

Spring mount for (61)

41

take away element

42

guide pin pair

43

take away exception

44

trunnion

51

Cylinder-piston unit

52

piston rod head

53

cylinder

54

piston rod

55

cylinder bottom

56

cylinder head

61

first spring energy store, tension spring

62

upper run

63

return run

70

carriage assembly

71

deflection pulley

72

Central axis of (71)

73

hollow hub

74

guide pin

75

disc horns

76

lateral surfaces of (75)

77

guide groove

78

u-shaped gutter section

79

outer gutter section

81

Sleds

82

transverse breakthrough

83

connecting bars

84

guide plates

85

spring bushing

86

Pivot mounts

87

insertion depression

88

recording

89

slide longitudinal direction

91

bearing journal

92

Section of (91), camp section

93

Section of (91), fret section

94

Section of (91), guide section, guide collar

95

end faces

96

center lines

97

outer radii

101

second spring energy store, tension spring

111

Contact points between (71) and (91), rolling contact zones

Claims (8)

1. Automatic feed-in apparatus (10) with a housing (21) and a carriage (81), comprising an entrainment element (41) that can be moved in the housing (21) between a parking position (11) secured in a non-positive and/or positive-locking manner and an end position (12) and back, comprising a first spring energy store (61) connecting the entrainment element (41) and the housing (21) and comprising at least one second spring energy store (101), both of which are charged when the entrainment element (41) is positioned in the parking position (11) and are discharged to a residual energy value when the entrainment element (41) is positioned in the end position (12), wherein the first spring energy store (61) is guided around a deflection disc (71) rotatably mounted relative to the carriage (81) and wherein the carriage (81) is biased relative to the housing (21) in the direction of the first spring energy store (61) wrapping around the deflection disc (71) by means of the second spring energy store (101) and wherein the deflection disc (71) comprises a circumferential guide groove (77), characterized in that

   - the deflection disc (71) on the carriage (81) is supported by means of two outer bearing pins (91) rotatably mounted within the carriage (81),

   - at least one tangential plane on the shell surface (76) of the deflection disc (71) intersects both bearing pins (91) and

   - the deflection disc (71) is guided during a rotary movement by means of the carriage (81) or by means of the bearing pins (91).
2. Automatic feed-in apparatus (10) according to Claim 1, characterized in that it comprises a cylinder-piston unit (51), which mounted in the within the housing (21) and can be biased by means of the entrainment element (41).
3. Automatic feed-in apparatus (10) according to Claim 1, characterized in that the bearing pins (91) comprise a central guide section (94).
4. Automatic feed-in apparatus (10) according to Claim 3, characterized in that the guide section (94) is formed at least partially complementary to the guide groove (77).
5. Automatic feed-in apparatus (10) according to Claim 1, characterized in that the bearing pins (91) are symmetrically arranged to bisect the wrap angle of the first spring energy store (61).
6. Automatic feed-in apparatus (10) according to Claim 1, characterized in that a tangential plane facing the deflection disc (71) on both bearing pins (91) has a smaller distance to a centre axis (72) of the deflection disc (71) than any parallel tangent on the first spring energy store (61).
7. Automatic feed-in apparatus (10) according to Claim 1, characterized in that the deflection disc (71) is without a nave.
8. Automatic feed-in apparatus (10) according to Claim 1, characterized in that the carriage (81) or the deflection disc (71) is guided within the housing (21).

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