EP2276375B1 - Acceleration apparatus with two energy stores - Google Patents

Description

The invention relates to an acceleration device with a guided in a housing entrainment element, which is funded by an energy from an initial energy value to a residual energy value from a force and / or positively secured parking position in an end position, wherein the accelerator device is a guide device with a second energy storage includes, which is loaded at location of the driving element in the parking position to an initial energy value, wherein the first energy storage is a mechanical energy storage and wherein the second energy storage comprises a compression or a tension spring and a combined deceleration and acceleration device with such an accelerator device.

From the DE 20 2004 005 322 U1 An acceleration device is known. To change the bias of a tension spring, the position of a spring pulley can be changed. With this measure, the used working range of the linear spring characteristic can be moved.

The WO 2008/034626 A2 discloses an accelerator having a spring deflected by a spring-loaded disc. As soon as the deflected spring is more taut, the disc is moved under load of its support spring. This allows short-term force and voltage changes the preloaded deflected spring are received.

The present invention is based on the problem of developing an acceleration device and a combined deceleration and acceleration device with an energy store, wherein at least the dynamic properties of the acceleration device can be influenced.

This problem is solved with the features of the main claim. For this purpose, the guide device comprises a guide element for positive guidance of the first-mentioned energy store. After the triggering element has been released from the parking position, the energy change rate of the first-mentioned energy store can be controlled by the second energy store discharging from the initial energy value to a residual energy value by means of the guide element at least in a subinterval of the discharge time interval of the first-mentioned energy store. The first energy store comprises a tension spring, which has at least two areas of different spring stiffness. An area of higher spring stiffness is applied to a deflecting device and wraps around it at least in some areas. In addition, the spring stiffness of the accelerator device is smaller than the minimum allowable spring stiffness of a single spring, which allows the stroke of the driving element with the same forces.

Figur 1:

Kombinierte Verzögerungs- und Beschleunigungsvorrichtung mit einem Mitnahmeelement in der Parkposition;

Figur 2:

Vorrichtung aus Figur 1 mit dem Mitnahmeelement in der Endposition;

Figur 3:

Energie-Zeit-Diagramm des ersten Energiespeichers;

Figur 4:

Teilquerschnitt einer Beschleunigungsvorrichtung mit einem verstellbaren Anschlag und einem Rastelement;

Figur 5:

Kombinierte Verzögerungs- und Beschleunigungsvorrichtung mit einer den ersten Energiespeicher endseitig führenden Führungsvorrichtung in der Parkposition;

Figur 6:

Fig. 5 mit dem Mitnahmeelement in der Endposition.

Further details of the invention will become apparent from the dependent claims and the following description of schematically illustrated embodiments.

FIG. 1:

Combined deceleration and acceleration device with a driving element in the parking position;

FIG. 2:

Device off FIG. 1 with the entrainment element in the end position;

FIG. 3:

Energy-time diagram of the first energy store;

FIG. 4:

Partial cross-section of an acceleration device with an adjustable stop and a latching element;

FIG. 5:

Combined deceleration and acceleration device with a first energy storage end leading guide device in the parking position;

FIG. 6:

Fig. 5 with the entrainment element in the end position.

The Figures 1 and 2 each show in a longitudinal section a combined deceleration and acceleration device (10) with a housing (11) and a carrier element (40) guided therein. The driving element (40) is of a force and / or positive parking position (1) shown in the figure 1 in one in the FIG. 2 shown end position (2) and back conveyed.

Such a deceleration and acceleration device (10) is used, for example, as part of a guidance system, e.g. a drawer guide or a sliding door assembly used to slow down, for example, a movable furniture part against a fixed furniture part controlled and move to an end position. This end position can e.g. be an open or closed end position of the furniture part. Here, the deceleration and acceleration device (10) is attached to one of the two relatively movable furniture parts. At the respective other furniture part a not shown here actuator is arranged. The housing (11) - of the two e.g. to each other mirror-symmetrical housing parts, only one housing part is shown in the figures - for example, has two through holes (12) in which it by means of fastening means, for. can be attached to the piece of furniture.

For example, when closing a drawer contacted in an adjacent to the closed end position of the drawer partial stroke, the actuator, the driving element (40), it releases from the parking position (1) and performs it in the Einfahrhubrichtung (5) along a guide device (21) in the end position (2), cf. FIG. 2 ,

As soon as the actuating element has released the entraining element (40) from the parking position (1), the movement of the drawer is braked by means of the retarding device (30). For example, at the same time the accelerating device (50) is activated, which moves the drawer against the action of the delay device (30) in the e.g. Closed end position pulls. The entrainment element (40) remains in engagement with the actuating element until it reaches the drawer end position.

When the drawer is opened, the actuating element pulls the carrier element (40) from the end position (2) into the parking position (1). There, the actuator releases from the driving element (40).

The retarding device (30) comprises a cylinder-piston unit (32) from which in the Figures 1 and 2 only the cylinder (33) and the piston rod (34) are shown. The cylinder-piston unit (32) can be actuated pneumatically or hydraulically. The displacement chamber is in this embodiment between the piston and the cylinder head (35), the compensation space is limited by means of the piston and the cylinder bottom (36).

The stroke of the piston and the piston rod (34) is for example 110 millimeters. On the piston rod head (37) the driving element (40) is pivotally mounted. The pivot axis lies in the representation of Figures 1 and 2 normal to the drawing plane.

The acceleration device (50) comprises an energy store (52) fastened to the carrier element (40) and to the housing (11) in a respective U-shaped recess (47, 13) and to a guide device (60) guided in the housing (11).

The energy store (52) is eg a mechanical energy store (52) and in this embodiment comprises a tension spring (53). This has, for example, two regions (56, 57) of different diameters, of which the region (56) of smaller diameter bears against a deflection device (70) and wraps it around in regions. The wrap angle is for example in position of the driving element (40) in the parking position (1) 183 degrees, see. FIG. 1 ,

The tension spring (53) can have a constant diameter. Also it can, e.g. be designed with a long housing, without deflection. It is also conceivable, instead of a tension spring (53) to arrange a compression spring, a spiral spring, etc. between the housing (11) and the driving element (40). Here, a transmission element, e.g. a rope, between the spring and the driving element (40) may be arranged. The entrainment element (40) may also be provided by means of a transmission, e.g. a lever mechanism to be connected to the energy storage (52).

The in the Figures 1 and 2 shown tension spring (53) has a nominal length - this is the length of the unstressed spring between the plant thickenings (54, 55) - of, for example, 170 millimeters. Their total stroke is for example 116 millimeters, which is about 68% of the nominal length. In the presentation of the FIG. 2 is the tension spring (53) relaxed to a residual stroke of 76 millimeters and in the FIG. 1 lengthened by the total lift. The used stroke of the tension spring (53) is for example 31% of the stroke of the driving element (40). It is thus less than 80% of the stroke of the driving element (40). In the charged state causes the initial energy value of the tension spring (53), for example, a tensile force of 20 Newton. In the discharged state of the FIG. 2 causes the residual energy value the tension spring (53) has a tensile force of eg 11 Newtons.

The one-piece tension spring (53) in this embodiment has a constant wire diameter of e.g. 0.85 millimeters. The first area (56) adjoining the catch receiving area of the spring (53) has, for example, an outer diameter of 4.7 millimeters. Its length in the untensioned state is e.g. 55% of the nominal length of the tension spring (53). At this area (56) adjoins with a transition region (58) of the housing-side second portion (57) of the tension spring (53), for example, has an outer diameter of 7.1 millimeters. Its unstressed length is in the embodiment about 44% of the nominal length of the spring (53). The diameter of the second region (57) is greater than 1.5 times the diameter of the first region (56).

The spring stiffness of the first region (56) in the exemplary embodiment is 0.16 Newton per millimeter. The spring stiffness of the second region (57) is e.g. 0.1 Newton per millimeter. The reciprocal of the total stiffness of the tension spring (53) in this series connection of the spring portions (56, 57) is the sum of the reciprocals of the individual spring stiffnesses. The tension spring (53) can also have more than two regions of different spring stiffnesses. In an embodiment of the tension spring with a constant outer diameter and a constant wire thickness, the spring stiffness over the length of the spring (53) is constant.

The energy stored in the tension spring (53), measured in joules, results from the integral of the spring force along the spring stroke. In the exemplary embodiment, the first energy store (52) is maximally charged in the parking position (1). This energy value is referred to below as the initial energy value of the first Energy storage (52) called. The residual energy value of the first energy store (52) is the energy value that the tension spring (53) has in the end position (2). The energy change rate of the first energy store (52) results from the differentiation of the energy function over time.

The guide device (60) comprises a guide element (61) and an energy store (62), which is referred to below as a second energy store (62).

The guide member (61) is e.g. a cuboid guide carriage (61), which is forcibly guided on both sides in a respective guide groove (14) in the housing (11). The guide grooves (14) are straight and, e.g. arranged parallel to the guide means (21) of the driving element (40). They may be narrower than the guide carriage (61). The guide carriage (61) then has e.g. a in the housing groove (14) projecting guide rail. At its two end faces, the guide grooves (14) by means of stop strips (15, 16) are limited. These stop strips (15, 16) can be switched on or adjustable in order to shorten or lengthen the length of the guide grooves (14) or to change the position of the guide grooves (14) in the housing (11). Optionally, the setting on only one guide groove (14) is sufficient.

On its end face facing away from the tension spring (53), the guide carriage (61) bears e.g. a guide pin (64). This guide pin (64) protrudes into the second energy store (62) and is guided by this. The second energy store (62) comprises, for example, a compression spring (63), which is supported on the guide carriage (61) and in the housing (11).

The compression spring (63) has, for example, an outer diameter of 8.5 millimeters and a wire thickness of 0.7 millimeters. The in the FIG. 2 shown partially relaxed compression spring (63) has a length of 85 millimeters and a residual force of 11 Newton. In the tensioned state, cf. FIG. 1 , the spring length is 42.5 millimeters and the force is 19.8 Newton. The stroke of the compression spring (63) is thus about 39% of the stroke of the driving element (40). It is less than 70% of the stroke of the driving element (40) in this embodiment.

Instead of a compression spring (63), the second energy store (62) may be designed as a tension spring. This tension spring is then e.g. outside of the first energy storage (52) surrounded space (19) between the housing (11) and the guide carriage (61).

When operating alone, the second energy storage device (63) has, for example, a constant energy change rate relative to its discharge or charging time interval. The stroke of this compression spring (63) is limited by the stroke limits of the guide carriage (61). The unloading time interval in the exemplary embodiment is the time interval that the guide carriage (61) for traversing the path from the right stop (15), cf. FIG. 1 , to the left stop (16) needed.

Optionally, in the housing (11) may be arranged, for example, a spring-loaded locking lug, which locks the guide carriage (61) in the parking position (1). When the cogging force is exceeded, the guide carriage (61) is then released. It is also conceivable to load the guide carriage (61) in a direction normal to one of the guide grooves (14), for example by means of a spring. The guide carriage (61) is then released only when the feed force of the second energy store (62) exceeds the increased friction due to the additional spring.

At the second energy storage (63) facing away from the guide carriage (61), the deflection device (70) is arranged in the embodiment. This includes e.g. a deflection roller (71) mounted rotatably on an axle (74) and having a running surface which is delimited on both sides by means of guide discs (73). The axis (74) is for example in a fork-shaped receptacle (75) of the guide carriage (61). Instead of a rotatable deflection roller (71) also a relative to the guide carriage (61) fixed deflection segment can be used.

In an embodiment of the deceleration and acceleration device (10) with a deflecting device (70) which is rotatably mounted or mounted directly in the housing (11), the guiding device (60) can act on the first energy store (52) at a different location.

The entrainment element (40) is in the embodiment of Figures 1 and 2 For example, by means of two guide pins (42, 43) in the guide device (21) out. The latter comprises two guide grooves (22) arranged opposite one another in the housing (11), of which only one is shown in longitudinal section. The entrainment element (40) projects out of the housing (11) with two abutment shoulders (44, 45) of different heights. In this case, the abutment shoulder (44) facing away from the cylinder (33) is higher than the abutment shoulder (45) facing the cylinder (33). These two abutment shoulders (44, 45) delimit a driving recess (46).

The two guide grooves (22) each comprise a straight (23) and a bent portion (24) adjoining them in the direction of the cylinder (33). The latter is in the representations of Figures 1 and 2 bent upwards. The imaginary center lines of the guide rails (22) tension one Level on, in which the center line of the piston rod (34) is located. On its side facing away from the driving recess (46), the driving element (40) has a spring receptacle (47).

After mounting the combined deceleration and acceleration device (10) in a guide system, for example, in an open drawer, the entrainment element (40) in the in the FIG. 1 illustrated parking position (1). The piston rod (34) of the cylinder-piston unit (32) is retracted. The first (52) and the second energy store (62) are loaded. The guide device (60) is located on the right stop (15). The tensioned tension spring (53) is arranged so that the elongate area (57) of low spring stiffness does not touch the deflection roller (71).

If, for example, the drawer is closed, the actuating element contacts the carrier element (40) on the contact shoulder (44) and pulls it out of the parking position (1). The driving element (40) is tilted in such a way that the abutment shoulders (44, 45) engage around the actuating element. In the further relative movement of the two furniture parts to each other, the actuating element pulls the driving element (40) along the guide device (21) in the direction of the end position (2). The piston rod (34) of the cylinder-piston unit (32) is pulled out. In the retarding device (30), the piston of the cylinder-piston unit (32) compresses the displacement space. Here, the compressed in the displacement chamber pneumatic or hydraulic medium can be throttled displaced into the expansion chamber. Optionally, for example, in a hydraulic cylinder-piston unit (32), additionally supplied hydraulic fluid from an external expansion tank in the expansion chamber. The throttling can be done along the For example, remove piston stroke movement. The movement of the driving element (40) - and thus the drawer - is slowed down.

With the beginning of the lifting movement of the driving element (40), the acceleration device (50) acts on the entrainment element (40). The tension spring (53) contracts and pulls the entrainment element (40) in the direction of the end position (2). The first energy store (52) is discharged.

In the FIG. 3 the stored energy of the first energy store is plotted as the ordinate value over the discharge time interval in a highly simplified manner as the abscissa value. The unit of unloading time interval is seconds. Due to the low energy and time intervals considered here, the energy function is shown in straight line sections. At the time of the coordinate origin, the actuator contacts the entrainment member (40). The energy stored in the tension spring (53) decreases from the initial energy value with, for example, a constant rate of energy discharge up to a first point in time (81).

As soon as the force of the tension spring (53) on the deflection device (70) is smaller than the threshold force value of the pressure spring (63) caused by the initial energy value and any latching or adhesive force, the pressure spring (63) pushes the guide carriage (61) with the deflection device (70) in the presentation of FIG. 1 to the left. In this case, the second energy store (62) emits energy. The guide carriage (61) with the deflection device (70) is moved along the housing guide (14). The first energy store (52) which adjoins the deflection device (70) is thus forcibly guided by means of the guide device (60).

The energy output of the second energy store (62) causes, for example, a reduction in the energy output per unit time of the first energy store (52). The amount of energy change rate of the first energy storage (52) becomes smaller. In the diagram of FIG. 3 this is shown in the second time interval (84) between times (81) and (82). The change of the stored energy of the first energy store (52) takes place along a flatter straight line than in the first mentioned time interval.

Once the guide device (60) is set in motion, the quotient of the feed force on the driving element (40) and the stroke of the driving element changes. This quotient is a measure of the spring stiffness of the overall system. The amount of this quotient is, for example, less than the amount of the corresponding quotient of the first energy store (52). This amount may be less than the minimum required amount of spring stiffness of a single spring (53) for the force difference and the stroke of the driving element (40). The minimum required spring stiffness of this single spring is u.a. from the maximum spring diameter, the minimum wire thickness and the material-dependent maximum permissible shear stress.

As soon as the guide carriage (61) has reached the left stop (16), the second energy store (62) presses against the stop (16) and the first energy store (52) with the residual force caused by its residual energy value. During the further stroke of the entraining element (40), the first energy store (52) is no longer controlled by means of the second energy store (62).

In the diagram of FIG. 3 beats the guide carriage (61) at the second time (82) on the left stop (16). Which now adjusting energy change rate of the first energy storage (52) corresponds to the rate of energy change during the first time interval (83).

The spring stiffness of the overall system now again corresponds to the spring stiffness of the tension spring (53).

As soon as the carrier element (40) has reached the end position (2), the first energy store (52) remains with a residual energy value. With the residual force caused thereby, the tension spring (53) holds the driving element (40) in the end position (2).

By means of the accelerator device described, the drawer is accelerated against the action of the deceleration device (30) and slowly fed into its e.g. closed end position out. Here she stays without jerking. By means of this device, the dynamic behavior of the acceleration device (50) is thus influenced.

The discharge time interval of the second energy store (62) may also be at the beginning or at the end of the discharge time interval of the first energy store (52). Also, the discharge time interval of the second energy store (62) may overlap one or both endpoints of the discharge time interval of the first energy store (52). It is also conceivable to carry out the two discharge time intervals identically.

For example, if the end point of the discharge time interval of the second energy store (62) to be advanced in time, for example, the stop (16) in the FIG. 4 offset to the right. This can be done eg by means of repositioning and locking. Also, an adjustment of the stop (16) by means of screws is conceivable. This increases the residual energy value of the second energy store (62). For example, can hereby the time interval of the amount of the low discharge rate of the first energy store (52) can be shortened.

In order to shift the end point of the discharge time interval of the second energy store (62) backwards in time, for example, the stop (16) in the FIG. 4 shifted to the left.

In order to influence the energy discharge rate of the first energy store (52) earlier in time, for example, the right stop (15) for the guide device (60) can be offset to the right.

If the energy discharge rate of the first energy store (52) to be influenced later in time, for example, the spring-loaded latching stopper (91) as shown in the FIG. 4 be formed represented. The charged second energy store (62) presses the latching stop downwards by means of the guide carriage (61) and passes over it as soon as the load on the deflection device (70) has fallen below a threshold value.

The deceleration and acceleration device (10) can be designed so that the energy change per unit time is largely constant. For the operator, this results in a uniform movement of the drawer.

When the drawer is opened, the actuating element pushes the entraining element (40) from the end position (2) into the parking position (1). The piston rod (34) with the piston is retracted, for example, almost without resistance. The tension spring (53) is tensioned, wherein the elongation of the area (57) of low spring stiffness is higher than the elongation of the area (56) of high spring stiffness. At the same time, the compression spring (63) compressed as soon as the force on the deflection device (70) exceeds the pressure force of the compression spring (63). During further movement of the driving element (40), for example, the guide carriage (61) strikes against the right stop (16). The second energy store (62) is now loaded to its initial energy value.

During the further movement of the carrier element (40), only the first energy store (52) is charged further. As soon as the carrier element (40) has reached the parking position (1), the actuating element releases from the combined deceleration and acceleration device (10). Both energy stores (52, 62) are charged to their respective initial energy values. The drawer can now be fully opened.

The time intervals of charging the first energy store (52) and charging the second energy store (62) may differ from the discharge time intervals. The charging rate of the two energy storage devices can be largely constant over the entire charging time interval. The operator can thus supply a largely constant energy per unit time of this entire interval of the device.

In the FIGS. 5 and 6 a delay and acceleration device (10) is shown, in which the second energy store (62) leads the housing-side end (59) of the first energy store (52). In this embodiment, both energy accumulators (52, 62) comprise tension springs (53, 66), the spring ends (59, 67) of which facing each other are accommodated in a spring receptacle (68, 69) fastened to the guide carriage (61). The guide carriage (61), for example, between two housing-side, eg adjustable stops (15, 16) in a housing guide (14) movable. A rest stop (91) holds the guide carriage (61) with the second energy store (62) until it exceeds a force threshold in the starting position.

The housing (11), the delay device (30), the entrainment element (40), the first energy store (52), the guide carriage (61), the stops (15, 16) and the detent element (91) are for example of similar construction as in FIG Connection with the embodiment of the Figures 1 and 2 described. The deflection device (70) is fastened, for example, in the housing (11).

As soon as the actuating element triggers the carrier element (40), the charged first energy store (52) pulls the carrier element (40) out of the parking position (1) in the direction of the end position (2). After releasing the guide carriage (61), both energy stores (52, 62) release kinetic energy. The energy change rate of the first energy store (52) decreases. The movement of the carrier element (40) is accelerated until the second energy store (62) has reached its residual energy value. For example, in this time interval, the reciprocal of the spring stiffness of the acceleration device (50) corresponds to the sum of the reciprocals of the individual spring stiffnesses of the two tension springs (53, 66). As soon as the second energy store (62) has reached its residual energy value, the entrainment element (40) is driven only by means of the first energy store (52). The energy change rate of this energy store (52) now returns to the initial value.

In this embodiment, the stroke of the first tension spring (53), for example, 80% of the stroke of the driving element (40).

This acceleration device (50) can also be set so that the energy output over time is largely constant. It is also conceivable to design the device so that the spring stiffness achieved is lower than the minimum allowable spring stiffness of a single spring, which allows the stroke of the driving element (40) with the same forces.

The energy change of the first (52) and / or the second energy store (62) may be progressive, degressive, intermittent or nonlinear. Combinations of the embodiments described above are conceivable.

LIST OF REFERENCE NUMBERS

1

parking position

2

end position

5

Einfahrhubrichtung

10

Combined deceleration and acceleration device

11

casing

12

Through holes

13

Spring retainer, U-shaped recess

14

Straight guide, guide groove, housing groove, housing guide

15

Stop bar, stop

16

Stop bar, stop

19

surrounded space

21

guide means

22

guide

23

straight section of (22)

24

curved section of (22)

30

delay means

32

Cylinder-piston unit

33

cylinder

34

piston rod

35

cylinder head

36

cylinder base

37

Piston rod head

40

driving element

42

guide pins

43

guide pins

44

contact shoulder

45

contact shoulder

46

driving recess

47

Spring retainer, U-shaped recess

50

Accelerating device, pulling device

52

Energy storage, first energy storage, the former energy storage

53

mainspring

54

conditioning thickening

55

conditioning thickening

56

first range of (53), high spring stiffness region, small diameter region

57

second area of (53), low spring stiffness area

58

Transition area

59

End of (53)

60

guiding device

61

Guide element, guide carriage

62

second energy store

63

compression spring

64

spigot

66

mainspring

67

End of (66)

68

spring mount

69

spring mount

70

deflecting

71

idler pulley

73

guide discs

74

axis of rotation

75

bifurcated recording

81

first time

82

second time

83

first time interval

84

second time interval

85

third time interval

91

latching stop

W

energy

t

Time

Claims (9)

1. Acceleration device (50) with an entrainment element (40) guided in a housing (11) and adapted to be moved from a parked position (1) secured by force-locked and/or form-locked means to an end position (2) by energy storage means (52) discharging from an initial energy level to a residual energy level, the acceleration device (50) comprising a guiding device (60) with a second energy storage (62) loaded to an initial energy level when entrainment element (40) is in its parked position (1), the first energy storage (52) being a mechanical energy storage (52) and second energy storage (62) comprising a compression spring (63) or a tension spring (66),

   - the guiding device (60) comprising a guiding element (61) for the forced guidance of first-mentioned energy storage (52),

   - the rate of change of the energy level of first-mentioned energy storage (52) being adapted to be controlled by guiding element (61) in at least a portion of the discharge period of first-mentioned energy storage (52) as second energy storage (62) discharges from its initial energy level to a residual energy level upon release of entrainment element (40) from its parked position (1),

   - the first energy storage (52) comprising a tension spring (53) having at least two ranges (56, 57) of different spring stiffness,

   - a range (56) of higher spring stiffness engaging and being at least partly wrapped around a deflecting device (70) and

   - the spring stiffness of acceleration device (50) being lower than the minimum of permissible spring stiffness of a single spring enabling the stroke of entrainment element (40) to be obtained with the same forces.
2. Acceleration device (50) as claimed in claim 1, characterized by guiding device (60) being guided in housing (11) in rectilinear guiding means (14).
3. Acceleration device (50) as claimed in claim 2, characterized by the stroke of guiding device (60) being limited by at least one stop element (15; 16).
4. Acceleration device (50) as claimed in claim 3, characterized by that stop element (15; 16) being adjustable.
5. Acceleration device (50) as claimed in claim 1, characterized by the discharge period of first-mentioned energy storage (52) being greater than or equal to the discharge period of second energy storage (62).
6. Acceleration device (50) as claimed in claim 1 or 5, characterized by the discharge periods of first and second energy storage (52, 62) terminating at the same point in time.
7. Acceleration device (50) as claimed in claim 1, characterized by at least first-mentioned energy storage (52) comprising a tension spring (53).
8. Acceleration device (50) as claimed in claim 7, characterized by tension spring (53) being at least partly wrapped around diflecing device (70).
9. Combined retarding and acceleration device (10) comprising an acceleration device (50) as claimed in claim 1.

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