JP3371657B2 - Belt tensioner for automotive safety belt device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a belt tensioner for an automobile safety belt device.

[0002]

2. Description of the Related Art A belt tensioner comprises a holder firmly fixed to a chassis, a belt take-up reel for winding a safety belt held by the holder, and a safety belt so that the safety belt lightly tightens an occupant. Is provided between the belt take-up reel and the holder, the take-up spring device for urging the belt to continuously pull lightly in the take-up direction, and when the safety belt is rapidly pulled and / or an accident. Has a blocking device that prevents the safety belt from being pulled out when acceleration occurs, and an additional drive device that is connected to the belt take-up reel via a clutch.

This clutch is normally disengaged, so that the additional drive is normally separated from the belt take-up reel. During acceleration due to an accident, the clutch is engaged and the additional drive device is rapidly started. And before the occupant falls forward,
The additional drive device and the belt take-up reel are rotatably and firmly connected to each other via the engaged clutch, and the safety belt is wound to a length that tightly tightens the occupant.

The additional drive device is preferably triggered by an accident in response to an acceleration sensor and is ignited to cause a sudden high pressure in the pressure chamber, in particular a pyrotechnic pressure source.
A torque generator to which a voltage is applied by the pressure in the pressure chamber, and a drive shaft rotatably and rigidly coupled to the belt take-up reel via a clutch.

A torque generator for a belt tensioner is known from DE-A-2505626. The torque generator comprises a drive wall extending radially between the drive reel and the peripheral wall of the housing. In the space between the drive wall and the sealing wall extending radially inward from the housing, the drive pressure generated by the explosive ignition is applied. This drive pressure acts on the drive wall which is connected to the drive reel and thereby sets the rotation of the drive reel.

[0006]

In the above-mentioned conventional example, since the drive wall comes into contact with the ceiling wall after the rotation of the drive reel is slightly less than one rotation, the maximum angle at which the drive reel can be completely moved. Is somewhat less than 360 degrees. In addition, the drive wall must be radially removable so that it is expensive to produce and must cooperate with a drive shaft that has teeth around it. Therefore, the manufacture of known torque generators is complicated, expensive and not reliable in operation.

Each part is dimensioned so that a minimum tensioning length of the belt, typically 140 mm, is achieved. However, preferably some preliminary withdrawal is possible so that the belt is withdrawn by a belt tensioner, for example up to 205 mm or tensioned. This is not possible with known belt tensioners.

After tensioning, the pressure generated momentarily and suddenly by the explosive ignition then gradually drops, where the belt tension provided by the occupant who collapses into the belt triggers the blocking device and causes the tension An occupant is surely held by the hung belt.

It is an object of the present invention to provide a belt tensioner whose drive shaft or drive reel can rotate more than 360 degrees when the pressure source is activated as a result of acceleration of the vehicle caused by an accident.

A further object of the present invention is to provide a belt tensioner torque generator that is produced at a low cost and is very reliable during operation.

It is a further object of the present invention to provide a belt tensioner torque generator that allows the desired change in drive torque depending on the rotational angle of the drive shaft without changing the drive pressure.

[0012]

To achieve this object, the present invention provides a torque generator having at least one flexible tension band. The flexible tension band is preferably made of spring steel and is provided on or concentrically with the outer periphery of the drive shaft and is attached to the drive reel partially wound around the drive shaft or drive reel at a first attachment point. At one end, subdividing the band running chamber into two sub-chambers provided in the housing around the drive shaft or around the drive reel and sealed against the other, while the withdrawal band is the band running chamber It is fixed at the other end at a second attachment point to the peripheral wall of the band running chamber having a width corresponding to the width of the withdrawal band so as to extend through it. The partial chambers, which under pressure exert the withdrawal of the tension band from the rotary drive shaft or the drive reel, are connected to the pressure space, and in the other partial spaces are preferably perforated. Also, for pressure uncoupling of the partial chambers, at least one sealing wall extends from the housing to a drive shaft concentrically provided thereto or to the outer circumference of a flexible draw band wound on a drive reel. It is provided.

In this way, the total free hanging length of the draw band extending from the drive shaft of the drive reel to the peripheral wall is useful for the action of pressure and for the production of force. Proper selection of the diameter of the drive shaft or drive reel and the surrounding housing allows the reel or drive shaft to rotate at angles substantially greater than 360 ° in triggering the torque generator.

According to a first advantageous embodiment, the flexible withdrawal band reverses its direction of strain after being lifted off the drive shaft or drive reel and abuts the peripheral wall of the housing in this reversed direction of strain. It becomes possible.

However, it is particularly preferred if the flexible withdrawal band extends through the band running chamber to its peripheral wall in the same direction of strain as it has as a result of being wound on the drive shaft or drive reel.

The area of the flexible withdrawal band acted upon by the pressure from the pressure chamber is such that the burst pressure lifts the first band layer on the drive shaft or drive reel up to the sealing wall and thus acts on the withdrawal band to this point. So it is substantially expanded. This results in a substantially larger area of the withdrawal band being acted upon by the same burst pressure, and a correspondingly greater tension is transferred to the flexible withdrawal band. The wall expansion basically corresponds to the entire drive shaft or drive reel circumference in just one partial chamber pair and in some partial chamber pairs the drive shaft extending between adjacent sealing walls. Or it basically corresponds to a part of the outer circumference of the drive reel. Thus, in effect, the total band area rises from the flexible drawer band to the ceiling wall sealing lip. The present invention has already been successfully used with only a single flexible withdrawal band.

In a particularly preferred embodiment, one or more sealing walls have a sealing lip facing the outer surface of the wound draw band, and the pressure in the associated pressure chamber causes the draw band to be wound. Characterized in that it extends against the housing so as to press the sealing lip against the outer surface of the housing in a gas-tight manner and is arranged flexibly or hinged. In this way, the sealing wall and in particular the sealing lip is pressed by the pressure in the pressure chamber associated with the outer circumference of the withdrawal band wound on the drive shaft or drive reel and thus pressure-dependent, i.e. a particularly effective pressure. The action is generated. The higher the burst pressure, the better the seal.

In such a belt tensioner, between the additional drive and the belt take-up reel which is normally not engaged and which is engaged immediately before the additional drive is activated in the event of acceleration due to an accident. It is already known (EP 0 581 288 A1) that a clutch is arranged. A clutch of this kind is also represented by the radially displaceable drive wall of DE-A-2505626.

[0019] A further object of the present invention is to form a particularly effective design of one or especially torque generating device and coupled to this type of clutch used in the present invention have a more extraction bands.

To achieve this object, the present invention provides:
Clutch is engaged by the pressure generated by starting operation of the pressure source, the additional drive, which clutch is to be separated from the pressure source by a valve device to be engaged, the clutch The belt
The rotational force of the additional drive device 15 is transmitted to the winding reel.
Equipped with a clutch disc that
Is engaged with the guide disc on the end face of the take-up reel.
Is possible.

In this case, the clutch is the first clutch portion,
A clutch disk that is particularly additional driving device twice rolling capable firmly connected, the second clutch portion, in particular rotatable and firmly connected to the belt take-up reel, preferably by 1 end guide disk of the belt take-up reel It is particularly advantageous to have a counter disk formed. Preferably, the first coupling part is at least partly axially displaceable to enable it to engage the counter disk, the first clutch part being connected to the second clutch part by spring force. Engagement is possible and configured to be held against spring force before being triggered.

Particularly preferably, the first clutch portion is a clutch disc that is biased by a spring force toward the counter disc, and the clutch disc is preferably formed against the engagement of the cams against the spring force. It is held on its outer circumference. The engagement between the cams can be released by the relative rotation of the clutch housing and the clutch disc. In particular, the clutch disc is itself made of elastic spring steel sheet and is stressed under normal conditions between its center and its outer periphery in a basically conical shape so that the clutch is in the disengaged state. Has been. Also, when the stress is stopped, for example by releasing it, the clutch disc is returned to its normal position, in particular in the plane. This engages the clutch.

The clutch preferably has a slider that is movable by the pressure of the pressure source and that engages the clutch by the movement of the pressure of the pressure source.

The slider has a piston area which is started by the pressure of the pressure source and a starting rod which is preferably thin on the side remote from the pressure start. The starting rod, in front of the starting rod when pressure is applied to the piston area,
The reverse provided on the outer circumference of the clutch disc so that the clutch disc is rotated from the engaged blocking position to an angle such that the spring force is rotated to a position where it is engaged with the counter disc, in particular with the guide disc of the belt take-up reel. It is configured to cooperate with the receiving portion via the receiving portion projecting laterally above the receiving portion.

In the first stage of the rotational movement of the clutch disc by the slider, the cam on the outer periphery of the clutch disc and the cam of the clutch housing are separated from each other, and in the second stage of the rotational movement, the clutch disc has the through hole of the clutch disc as the counter disc. The cam is further rotated in a line in the axial direction until the through hole of the elastic clutch disc and the cam of the counter disc engage with each other.

With the appropriate guidance of the pressure gas that is availablely produced from the pressure source, the clutch is engaged and the additional drive is essentially started.

Rotation of the clutch disc on the drive shaft of the torque generator or for engagement of the clutch on the drive reel causes the clutch disc to rotate without transferring torque to the drive shaft or drive reel until the clutch is engaged. Appropriate clearances are available to allow.

In order to ensure this, according to the present invention, when the clutch disc rotates in the direction opposite to the belt winding direction, the clutch disc can further rotate until the through hole and the cam are fitted. Thus, a gap is formed between the drive shaft or drive reel and the clutch disc.

[0029]

DETAILED DESCRIPTION OF THE INVENTION Embodiments will be described below with reference to the drawings.

FIG. 1 shows a first example of the belt tensioner according to the embodiment.

FIG. 2 is an enlarged perspective view of the belt tensioner viewed from the opposite side to FIG.

FIG. 3 is a perspective view of the same belt tensioner as seen from the side of the additional drive device immediately after the ignition of the explosive, and the face cover and the winding spring device at one end of the band drive space are not shown.

FIG. 4 is an explanatory view of the belt pulling process.

9 to 16 are construction diagrams of the belt tensioner.

As shown in FIGS. 1 and 2, the belt tensioner has a holder 11 mounted, for example, on the chassis 40 in the floor area of the passenger compartment. Belt take-up reel 12
Is rotatably attached to the holder 11 with the central shaft 38 as the center of rotation, and the safety belt 13 is wound around the reel 12. The safety belt 13 is connected to a chassis 40 on the other side via a belt lock 39, a wire cable 13 ', etc., as shown simply by the broken line in FIG. Normally, the safety belt 13 is in contact with the body of the occupant. The safety belt 13 can also be a component of the three-point belt device, as shown by the chain line in the upper right of FIG.

On the end surface of the belt take-up reel 12, a usual take-up spring device 14 is provided. The winding spring device 1
The take-up spring in 4 applies a light belt take-up torque to the belt take-up reel 12 so that the safety belt 13 pulled out by the occupant and worn by the occupant can be wound up to a length such that the safety belt 13 comes in close contact with the body of the occupant. Add to 12.

An ordinary belt drawer blocking mechanism (not shown) is provided between the holder 11 and the belt take-up reel 12. This blocking mechanism is
The belt take-up reel is fixed so that the safety belt 13 is started when the safety belt is suddenly pulled out or decelerated due to an accident, and the safety belt 13 is prevented from being pulled out.

The winding spring device can also be provided on the end face of the belt winding reel 12 or on the holder 11 with the reference numeral 14 'in FIGS. For this reason, the inner shaft 41 of FIG. 1 must rotatably extend through the corresponding through holes of the additional drive 15 and the clutch 20, which will be described in more detail below. When the winding spring device is arranged at the position 14 ', there is an advantage that the normal driving device and the additional driving device for the belt winding reel 12 generate driving force from the same side.

As shown in FIGS. 1 and 2, the additional drive device 15 and the clutch 20 are preferably arranged between the winding spring device 14 ′ and the holder 11 or the belt winding reel 12. . The additional drive device 15 will be described in detail below with reference to FIGS.

As shown in FIGS. 1 and 3, the additional drive device 15
Has a drive shaft 19 concentric with the rotation shaft 38 of the belt take-up reel 12. On the drive shaft 19,
A rotatable drive reel 22 is concentrically and fixedly attached. In FIGS. 1 and 3, two pull-out bands 21 of spring steel plate of about 0.2 mm are each wound counterclockwise on a drive reel 22 and fixed firmly to the drive reel 22 at a mounting point 25 on its outer circumference. To be done.

In the initial state shown in FIGS. 1 and 3, each pull-out band 21 has a drive reel 22.
About 3 to 4 layers are wound around. Each of the pull-out bands 21 extends in a bow shape toward an attachment point 26 on a peripheral wall 30 surrounding the two band running chambers 23 surrounding the drive reel 22.

In the initial state, the arcuate portion of the pull-out band 21 extends along the sealing wall 29. The ceiling wall 29 is a drive reel 22.
It is in a state of being curved so as to have a substantially “U” shape in the radial direction of, and is formed integrally with the housing 24. The ceiling wall 29 extends from the peripheral wall 30 toward the reel 22. The ceiling wall 29
The tip of the centripetal direction toward the reel 22 is a tapered sealing lip 31 facing the outer circumference of the reel 22.

In the region of the sealing lip 31, a sealing element 32 is arranged between each sealing wall 29 and the pull-out band 21. The sealing element 32 is extended between the flat plate-shaped end walls 51 and 52 facing each other with the band traveling chamber 23 interposed therebetween. A belt take-up reel 12 having a central opening 67
The plate-shaped end wall 51 and the peripheral wall 30 which are arranged adjacent to each other form a fixed component of the housing 24 of the torque generator 18. On the other hand, the end wall 52 arranged on the opposite side in the axial direction of FIG. 1 can be provided on the opening side of the housing 24. A cover plate 53 is attached to the end wall 52. The lid plate 53 has a central opening 54 for the passage of the inner shaft 41 to the winding spring device 14 '.

The width of the pull-out band 21 is equal to the width of the end wall 5.
The pulling band 21 divides the band running chamber 23 into two partial chambers 23 ′ and 23 ″ which are sealed from each other and are sized so as to come into slidable contact with the first and the second parts 52 and 52. ing.

The branch lines 27 and 28 (FIG. 3), each extending from a common pressure chamber 17 into which pressure is introduced from the pressure source 16, have sealing walls 2 in the area of the root of the sealing wall 29 located on the peripheral wall 30.
It is open on the convex side of 9.

The pressure source 16 is connected via a control line 42 shown in broken lines in FIG. 3 to an acceleration sensor 43, which is also shown only in broken lines. The acceleration sensor 43 is
Pressure source 1 when sudden deceleration of a vehicle occurs due to an accident
6 is ignited, which causes rapid pressure in the pressure chamber 17. A vent hole 37 communicating with the outside air is provided on the concave side of the ceiling wall 29, and is configured to prevent an extremely large pressure from being applied to the chamber 23 ″ when the additional drive device 15 is started. .

The branch lines 27 and 28 communicate with the band running chamber 23. The pull-out band 21 is routed so as to cross the opening surfaces of the branch lines 27 and 28 to the chamber 23. Therefore, when gas is ejected from the branch lines 27 and 28 into the chamber 23, pressure can be rapidly applied to the extraction band 21. In addition, branch line 2
The opening surface of No. 7 is located on the outer peripheral surface of the chamber 23.

When the pressure source 16 of the torque generator 18 is started and gas is generated, the extraction band 21 is moved to the partial chamber 2
The drive shaft 19 having a hole for receiving the inner shaft 41 is rotationally driven in the belt winding direction by being pressed from 3'to 23 ".

As shown in FIGS. 1 and 9-16, the clutch 20 includes an additional drive 1 having a torque generator 18.
5 and the belt take-up reel 12. In normal times, the winding spring device 14 'and the belt winding reel 12 are not linked. When an acceleration of a predetermined value or more is generated due to a vehicle collision or the like, the clutch 20 operates so that the two are connected (engaged), the torque from the torque generator 18 is transmitted to the reel 12, and the tension is rapidly applied to the belt 13. Is added.

As shown in FIGS. 1, 9 and 10, the drive reel 22 is axially (FIG. 9) and radially (FIG. 1) on its side axially distant from the torque generator 18.
0) With a protruding nose or wedge cam 55.
The cam 55 has a constant gap in the outer peripheral direction.
The outer peripheral edge of the central opening 71 of the clutch disc 44 so that the drive reel 22 can overcome the gap and rotate the clutch disc 44. And engages with the complementary shaped outer peripheral slot (gap) 56 at.

On the outer peripheral portion of the clutch disc 44, as shown in FIGS. 1, 9 and 10, a retaining nose, that is, a retaining cam 50 protruding in the radial direction is provided in a protruding manner. As shown in FIGS. 10 and 12, the cam 50 engages a counter nose or cam 57. The clutch disc 44 is the receiving cavity 6 of the clutch housing 58.
It is located within 0.

The cam 57 is provided so as to protrude radially inward from the clutch housing 58 into the receiving cavity 60. The cam 57 is the clutch disk 4 which is pressed.
From the clutch housing 58 to the clutch disc 4 such that 4 travels toward the belt take-up reel 12 by the end face of the drive reel 22 (or an intermediate piece fixed thereto).
4 projects radially inward into the receiving cavity 60 for 4 and is initially retained radially outwardly against such an axial displacement. The clutch disc 44 made of elastic material, in particular spring steel, is thereby elastically deformed as shown in FIGS.

As shown in FIGS. 1, 9, 10, and 12, the clutch disc 44 has a plurality of through holes (hollow-shaped openings) 4.
5 are provided at regular intervals in the circumferential direction. A cam 46 is projectingly provided on the plate surface of the end guide disk 47 of the belt take-up reel 12 which faces the torque generator 18 in the axial direction. The cam 46 can face the opening 45. When the retaining cam 50 is engaged with the cam 57, the cam 46 is in a state of being disengaged from the through hole 45 (see, for example, FIG. 12).

The clutch disc 44 is normally in the disengaged state shown in FIG. In this non-engaged state, the belt take-up reel 12 can be freely rotated by the drive reel 22 without any hindrance, and the inner shaft 4 extending through the openings 67, 71 and 72 (not shown).
1 to cooperate with the winding spring device 14 '.

A slider 48 for engaging and actuating the clutch is slidably disposed in the groove 49 of the clutch housing 58. The groove 49 extends in the vertical direction in the drawing so as to be tangentially continuous with the peripheral edge of the circular receiving cavity 60 of the clutch housing 58. The slider 48 in the groove 49 is arranged so as to be vertically movable so as to slightly touch the clutch disc 44.

The slider 48 has a starting rod portion 48 "at its upper portion and a piston portion 48 'at its lower portion. Reference numeral 59 indicates a valve piece.

An ignition type pressure source 16 is provided below the lower end surface of the piston portion 48 '. As shown in FIG. 12, a pressure guiding path 61 is provided which connects the recess 49 and the pressure chamber 17. When the slider 48 is located at the initial position shown in FIGS.
8'blocks the communication between the ignition type pressure source 16 and the pressure guiding path 61.

9 to 11, the starting rod portion 48 "of the slider 48 is provided with a receiving portion 62 which projects toward the clutch disc 44 and engages with the reverse receiving portion 63. The reverse receiving portion is provided. Reference numeral 63 denotes a cam-shaped convex portion that projects outward from the outer peripheral surface of the clutch disc 44. When the slider 48 moves upward, the receiving portion 62 causes the reverse receiving portion 63.
And the clutch disc 44 is rotated clockwise.

A cylindrical ignition type pressure source 16 is shown in FIGS.
As shown in FIGS.
Placed on the side of. Note that, as shown in FIGS. 10 and 12, the pressure source 16 may be provided on an axial extension of the recess 49 below the clutch 20. Importantly, when the pyrotechnic pressure source 16 is activated, initially only the slider 48 is pressed by the gas to engage the clutch 20 and then the pressure is applied to the torque generator 18 via the pressure conduit 61. Is to be propagated.

The operation of the belt tensioner described above is as follows.

When the acceleration sensor 43 (FIG. 3) detects acceleration due to a vehicle accident, the ignition pressure source 16 is ignited via the control line 42. Thereafter, the pyrotechnic pressure source 16 initially does not exert pressure on the torque generator 18, as shown in FIGS. 3 and 4 (dots in areas filled with gas). The gas pressure from the pressure source 16 first pushes up the piston portion 48 'from the initial position of FIGS. 9 and 10 to the operating position of FIGS. The clutch disc 44 is rotated by the engagement between the receiving portion 62 and the reverse receiving portion 63.

The clutch disc 44 rotates until its retaining cam 50 is disengaged from the cam 57 as shown in FIGS. When the retaining disc 50, which was rotated by the clutch disc 44 and overlapped with the cam 57 (FIG. 12), is disengaged from the cam 57 as shown in FIG. 15, the clutch disc 44 is elastically restored toward the guide disc 47. Then, the cam 46 of the guide disc 74 is engaged with the through hole 45 of the clutch disc 44 immediately or after hitting the web 69 of the clutch disc 44.

The outer peripheral slot 56 provided at the edge of the opening 72 (FIG. 10) must allow the drive reel 22 and the cam 55 to rotate the clutch 44.

A plurality of through holes 4 arranged around the cam 46.
As a result of the above-described design of the clutch 20 with 5, the torque is transmitted by the clutch 20.

Specifically, the engagement of the clutch is performed as follows.

When the pressure source 16 is activated, first the slider 4
8 rises upward in the figure. As the slider 48 rises, the clutch disc 44 rotates and the clutch disc 44 engages with the guide disc 47. The rotation direction of the clutch disc 44 up to this engagement is opposite to the rotation direction when the clutch disc 47 is driven by the torque generator 18 to rotate after the engagement.

Thus, it is important to change the rotation direction before and after the engagement. That is, by doing so, the drive shaft 19 of the drive reel 22 does not rotate due to friction or foam fixed engagement even when the clutch 44 rotates. In the initial state before the ignition pressure source 16 is activated, the clutch disc 44 can freely rotate with respect to the drive reel 22.

In the present invention, the through hole 45 and the cam 46 must always be engaged during the engagement (torque transmission) of the clutch 20.

Therefore, the receiving portion 62 of the slider 48 and the reverse receiving portion 63 of the clutch disc 44 are designed to continue to be engaged until the clutch disc 44 snaps into the cam 46. That is, even after the holding cam 50 is disengaged from the cam 57 of the clutch housing 58 by the rotation of the clutch disc 44, the receiving portion 62 and the reverse receiving portion 63 are engaged with each other. When the holding cam 50 is disengaged from the cam 57 and the through-hole 45 of the clutch disc 44 does not face the cam 46 of the guide disc 47, the cam 46 moves the clutch disc 4
4 hits the web 65, but further rotation of the clutch disc 47 causes the cam 46 to enter and engage the through hole 45. The receiving portion 62 of the slider 48 rotates the clutch disc 44 while engaging with the reverse receiving portion 63 even when the cam 50 is disengaged from the cam 57 and the cam 46 contacts the web 69. In this way, the clutch disc 44 is rotated by the upward movement of the slider 48 until the through hole 45 snaps into the cam 46.

When the cam 46 enters the through hole 45 as shown in FIG. 15, the clutch disc 44 becomes flat as shown by the broken line in FIG. 13a, and the reverse receiving portion 63 moves toward the guide disc 47. It separates from the receiving part 62. As a result, the slider 48 and the clutch disc 44
Is disengaged, the slider 48 smoothly rises to the upper limit, and its valve piece 59 is positioned in front of the pressure guiding path 61. Then, the gas pressure from the pressure source 16 is applied to the valve piece 59, and as shown in FIG.
9 is pushed into the pressure guiding passage 61, and the gas pressure from the pressure source 16 is introduced into the pressure guiding passage 61.

In this way, the clutch disc 44 and the guide disc 47 approach each other, and both are securely engaged. Then, the clutch 20 is securely engaged before the pressure from the pressure source 16 is applied to the torque generator 18.

The particular advantage of the specification of the elastic clutch disc 44 formed of leaf springs requires very little axial construction space and yet allows positive engagement and disengagement of the clutch 20. That is.

Due to its unique spring trait, initially FIG.
Clutch disk 4 deformed conically as shown in FIG.
4 finally becomes the flat shape shown in FIGS. Then, the cam 46 and the through-hole 45 are engaged with each other, and the rotatably fixed connection between the drive reel 22 and the belt take-up reel 12 which may have some circumferential clearance if necessary. To create.

When the slider 48 moves upward as shown in FIGS. 11 and 12, the valve piece 59 is pressed immediately before entering the pressure guiding path 61.

When the slider 48 moves up to the upper limit and the lower edge 64 of the valve piece 59 is located slightly above the lower edge 65 of the inlet of the pressure guiding path 61, the explosive high gas pressure filled in the groove 49 is increased. As a result, the valve piece 59 is pushed into the pressure guiding path 61.

The explosive pressure from the ignition pressure source 16 is propagated to the pressure chamber 17 via the pressure guiding path 61 and from the pressure chamber 17 to the partial chamber 23 'through the branch lines 27 and 28. The area filled with this high-pressure gas is shown by dots in FIGS.

By introducing high-pressure gas into the branch lines 27 and 28, pressure is applied to the concave side of the pull-out band 21 and the drive reel 22 is rotated counterclockwise in FIG.

In this way, the drive reel 22 is
The unwound draw-out band 21 is the band running chamber 2
It rotates while making a more firm contact with the peripheral wall 30 of 3.

The free "through-hanging" or loop area of the withdrawal band 21 is initially relatively short, as in FIG. 3, so that the pressure transferred to the band is likewise initially relatively small.

When the band running chamber 23 becomes larger, the effective "through hanging" or loop surface of the draw band 21 is enlarged, as shown in FIG. 4, which causes the pressure exerted on it to increase correspondingly, The torque applied to the drive reel 22 also increases.

The draw-out band 21 is further pushed by the gas from the state shown in FIG. 4 toward the end region 66 of the peripheral wall 30 shown by the reference numeral 66 in FIG. As the free loop surface of the pull-out band 21 becomes smaller as it approaches the end region 66,
The torque applied to the drive reel 22 also gradually decreases.

Finally, the curved portion of the draw-out band 21 has a concave end region 66 of the band running chamber 23.
Will overlap. As a result, the moving time of the pull-out band 21 is used up. Drive reel 22 in the meantime
The rotation of the belt 13 causes the belt 13 to be wound up to a maximum of 205 mm, for example.

In the state of FIG. 4 during winding,
The safety belt 13 is wound around 140 mm.

When the pressure release from the ignition type pressure source 16 is completed and the pressure in the partial chamber 23 'is reduced, the pull-out band 2 wound around the drive reel 22 is drawn.
The winding of 1 is loose. Then, by the tension applied from the pull-out band 21 until then, the outer peripheral recess (recess) 3
The spring tongue 35 pushed into 6 pushes outwardly the winding layer 21 winding layer loosened by its own restoring force, and takes the releasing posture shown in FIG. In the state of FIG. 8, the cooperating relationship between the drive reel 22 and the end of the pull-out band 21 having the spring tongue 35 is eliminated.

When the clutch 20 is in the closed state, the drive reel 22 can rotate without any hindrance under the influence of the pulling-out and pulling-in operations of the safety belt 13. In this way, the usual function of the belt withdrawal and winding mechanism by the winding spring device 14 'is ensured as in the prior art.

When the withdrawal band 21 is withdrawn as shown in FIG. 4 or longer and the pressure of the pressure source 16 rises,
A blocking device (not shown) between the holder 11 and the belt take-up reel 12 blocks the reel 12 so as to prevent the belt 13 from being unwound, so that the occupant can take up the belt 13.
The belt 13 can be reliably prevented from being pulled out even if the user falls down.

The present invention thus provides a very compact belt tensioner which reliably engages the clutch and subsequently pulls the belt with the same single pyrotechnic pressure source.

The embodiment of FIGS. 5A and 6 shows that the two withdrawal bands 21 shown only in dashed lines are combined into a single continuous band, the band passage being provided outside the mounting point in the housing. It is distinguished from the embodiment of FIGS. 1 to 4 in that it is guided by 33.

For this reason, the force generated in the withdrawal band 21 in the region of the attachment point 26 in the pressure application of the torque generator 18 is transferred only to the housing to the extent that the passage for accommodating the band 21 is curved. The actual extraction force disappears in the region of the band 21 located in the chamber 23.

Incidentally, in FIG. 5 (A), the pull-out band 2
1 passes across the cylindrical pressure chamber 17 in the region of the attachment point 26 in the upper left of the figure, so that the region 21 of the withdrawal band 21 passing through this pressure chamber 17 has two partial spaces 17 ', Subdivided into 17 ".

The region 21 ′ of the withdrawal band 21 extending in the band passage 33 serves only to support the parts of the withdrawal band located in the chamber 23 against one another.

As shown in FIG. 5A, the groove 34 is provided on the convex curved surface of the sealing wall. This groove 34 is
It communicates with the partial chamber 23 ′ so that the gas pressure from the branch line 27 can be introduced into the groove 34. Therefore, immediately after the operation of the pressure source 16 is started, in the state where the drawing band 21 is in close contact with the sealing wall 29, the gas pressure enters the groove 34, and the gas pressure rapidly increases over the entire surface of the drawing band 21 facing the groove 34. Will be added to.

As shown in FIG. 5A, the front end side of the sealing wall 29 is separate from the base end side, and both are pivotally attached by a hinge 74. This hinge 74 is arranged on the convex curved surface side of the ceiling wall 29, and therefore the tip end side of the ceiling wall 29 is rotatable about the hinge 74 in the direction of the arrow θ in FIG.

Thus, following activation of the pressure source 16, the pivotable ceiling wall region
Pivoted so that automatic disengagement of the band end from the outer peripheral recess 36 in the drive reel 22 described with respect to FIGS. 7 and 8 also results in the sealing wall 2
Undisturbed in area 9

FIG. 5 (a) [FIG. 5a] shows another structural example of the ceiling wall 29 portion. This Figure 5
In the embodiment of (a), the ceiling wall 29 is held by the tension of the pull-out band 21 lying on them through the partition joint 75 having an appropriate shape and the receiving portion 24 'fixed to the housing. If so, this type of expanding spring may be eliminated. With such a configuration, by appropriately pre-pressing the drive reel 22 by the tensioned pull-out band 21, the sealing wall 29 is brought into a normal state with respect to the partition joint 75 and the receiving portion 24 '. Pressed.

In FIG. 5a, when the ignition pressure source is activated, the gas pressure in the partial chamber 23 'pushes the sealing wall 29 against the partition joint 75 and the receiving portion 24'. Further, this gas pressure causes the pull-out band 21 to be largely pulled out from the drive reel 22. Only when the pressure in the partial chamber 23 'drops again,
The loose layer of the pull-out band 21 wound around the drive reel 22 presses against the ceiling wall 29, and the arrow 7
It does not prevent the loosening of the layers of the pull-out band 21 wound around the drive reel 22 by sliding along the partition joint 75 and the receiving portion 24 ′ in the direction of 3. In this way, the ends of the withdrawal band 21, which are rotatably and securely hung on the outer periphery of the drive reel 22, are hooked when the hooks at the points are located directly facing the sealing lip 31 of the sealing wall 29. Automatically elastically release from the recess that is installed.

The inventive concept of this embodiment is clarified by the following facts. That is, since the ceiling wall 29 can be separated from the housing 24, the ceiling wall 29 is held at a desired position by the tension in the pull-out band 21 or the partial chamber 23 '. However, when the sealing wall 29 is prevented from coming into contact with the pull-out band 21 and the pressure is reduced, the ceiling wall 29 loosens the winding of the pull-out band 21 around the drive reel 22 and the housing 24 is closed. , 24 'automatically separates.

The mounting hole 70 shown in FIG. 5 is used for mounting the individual housings of the additional drive device 15, the clutch 20 and the winding spring device 14 ′, and for mounting the frame 11 of the belt winding reel 12.

In the present invention, when the ignition type pressure source is activated, the safety belt 13 is heated to 140% for about 10 mSec.
It is wound up to about 205 mm and tensioned.

In the initial state, the pull-out band 21 is wound around the drive reel 22 outside the drive shaft 19 three to four times. The diameter of the drive shaft 19 or the drive reel 22 and the number of windings of the pull-out band 21 wound around the drive shaft 19 or the drive reel 22 are determined according to the desired length to be pulled out during the tensioning.

Further, even after the band loop has completely run through the entire band running chamber 23, the drive shaft 19 and the drive reel 22 are further 1-2.
It is configured so that it can rotate about a degree of rotation. This allows
Automatic movement of the band edge from the peripheral recess (Fig. 7) does not occur early. The rotation of the drive shaft 19 and the drive reel 22 about 1 to 2 rotations means that the spring tongue 35 or another hanging in or fixing member drives the drive reel 22 in such a length that the tension exists in the pull-out band 21. It is necessary to ensure that it is pressed into the corresponding recess 36 of the shaft 19.

Therefore, one operating on one and similar drive shafts 19 or drive reels 22
Instead of two oppositely located withdrawal bands 21,
Several such arrangements provided on the outer circumference are basically used, and the use of four or more withdrawal bands 21 provided on the outer circumference with corresponding sealing walls 29 is not considered for structural reasons. In each case, the use of two oppositely arranged withdrawal bands 21 with corresponding sealing walls 29 is ideal. This is because the holding force of the drive shaft 19 or the drive reel 22 can be made sufficiently large only by providing two drawing bands 21.

In the embodiment shown in FIG. 17, the pull-out band 21 is
The drive reel 22 is curved and extends from the peripheral wall 30. This curving direction is the same as the curving direction of the portion of the pull-out band 21 wound around the outer peripheral surface of the drive reel 22. One end of the pull-out band 21 is
The branch line 27 is fixed to the housing 24 at a portion (reference numeral 26) near the opening facing the chamber 23.

A sealing wall 29 extends substantially parallel to the branch line 27 between the housing 24 and the draw band 21 of the drive reel 22 or wound around it. The sealing lip 29 ′ on the front end side of the sealing wall 29 is in air-tight contact with the wound pull-out band 21. The sealing lip 29 ′ extends along the outer peripheral surface of the drive reel 22 toward the branch line 27 side. In this way, the partial chambers 23 ', 2
The 3 "are separated from each other so that they do not communicate with each other.

A vent hole 37 and a vent passage 37 'for communicating the inside of the chamber 23 with the outside air are provided on the end side in the running direction of the pull-out band 21.

As shown in phantom and fine hatching in FIG. 17, the sealing wall 29 preferably has a projection 29 "towards the partial chamber 23 'and the sealing lip 29' is oriented in the direction of the pressure chamber 23 '. The protrusion 29 ″ is flexible and is hinged to the sealing wall 29 about a pivot axis parallel to the axis of the drive shaft 19. In this way, the sealing lip 29 ′ is pressed airtight against the outer surface of the pull-out band 21 wound on the drive reel 22 by the pressure in the partial chamber 23.

FIG. 18 shows still another embodiment.

In the embodiment shown in FIG. 18, the pull-out band 2
One end side of 1 is fixed to the peripheral wall 30 at a position of 26, and the other end side is wound around the drive reel 22. The pull-out band 21 is bent only on the same side as the bending direction of the portion wound around the reel 22, and does not have the opposite bending.

Also in this embodiment, the partial chamber 2
3 ″ communicates with the outside air through a vent hole 37 and a vent passage 37 ′.

An important advantage of the embodiment of FIGS. 17 and 18 is that the pressure in the partial chamber 23 'in which the gas pressure is introduced is exerted on the sealing lip 29' of the sealing wall 29. With such a configuration, the length of the portion of the pull-out band 21 that freely extends in the band running chamber 23 and receives the gas pressure to generate tension is longer than that in the embodiment of FIGS. Become. (It becomes longer by the diameter of the drive reel 22.) As a result,
Even when the same gas pressure is applied to the pull-out band 21, the force for driving the drive reel 22 becomes significantly stronger than that in the embodiment of FIGS.

In FIG. 18, the drawing band 21 immediately after the introduction of the gas pressure is shown by a solid line. As the gas pressure is further introduced, the withdrawal band 21 moves as shown by the broken line. Two stages in the middle of this movement are indicated by broken lines.

Particularly important is the ceiling wall 2
9 is basically only slightly in contact with the drive reel 22. Furthermore, the ceiling wall 29
Is also important in the present invention. That is, the sealing wall 29 is designed to be particularly elastic or is hinged to the housing 24 at 29 ''', for example. As a result, the sealing lip 29 'is driven by the drive reel 22 with a small spring force.
It is urged towards the flexible draw band 21 which is wrapped around.

In this manner, each pressure load on the surface of the sealing wall 29 facing the chamber 23 presses the sealing lip 29 ′ of the sealing wall 29 against the outer surface of the pull-out band 21 wound on the drive reel 22. It Then, as the pressure in the partial chamber 23 'rises, the sealing lip 29' and the drive reel 22 or the withdrawal band 2 wound around it.
A sufficient sealing effect is formed between the two.

Furthermore, the pull-out band 21 is pressed radially from the inside toward the outside against the sealing lip 29 'by the pressure in the partial space 23'.

FIG. 19 shows another structural example of the main part of the belt tensioner.

In FIG. 19, the belt tensioner has a withdrawal band 21 extending across the width of the band travel chamber 23 as a force transfer sealing means in the housing 24. One end of the pull-out band 21 is fixed to the drive reel 22 at a mounting point 25. The pull-out band 21 is partially wound around the drive reel 22 in such a direction that the drive reel rotates in the belt winding direction by pulling out the pull-out band 21. The pull-out band 21 extends from the drive reel 22 toward the peripheral wall 30, but in a portion between the reel 22 and the peripheral wall 30, the pull-out band 21 has a semicircular shape (180
Bow shape). The concave side of this semicircle is arranged to be the side receiving the gas pressure from the branch line 27. The other end side of the pull-out band 21 extends along the peripheral wall 30 and then at the attachment point 26, the housing 2
It is fixed at 4. The mounting point 26 is
It is located near the branch line 26.

In the housing 24, in the direction of rotation, a partial chamber 23 ′ under pressure is formed in front of the 180 ° arcuate portion, and a partial chamber 23 ″ with a hole is formed.
Drawer band 21 to be formed behind the 0 ° arcuate section
It has a flat end wall 51 and a flat cover 53, which are inwardly contacted by the edges of, and is formed similarly to the housing of the embodiment of FIG.

The clutch 20, which is shown only in broken lines and which is not normally engaged, but which is engaged in an unillustrated manner due to accidental acceleration, is rotatably and rigidly connected to the withdrawal band 21 and the belt reel. It should be considered as being present between the drive reel 22 and the drive shaft 19 projecting axially from the drive reel 22. However, the clutch is preferably provided between the drive shaft 19 and the belt reel 15.

In the embodiment shown in FIG. 20, a sealing cylinder 76 is provided along the 180 ° arcuate portion of the draw band 21. The flat end surface of the sealing cylinder 76 is in airtight and slidable contact with the wall 51 and the cover 53. In this way, the two parts in the band running chamber 23 are more airtightly separated.

In both of the above embodiments, the clutch should be designed so that the engagement relationship is released again after a suitable time following accidental tensioning. A preferable example of the clutch is as shown in FIGS.

The operation of the embodiment shown in FIGS. 19 and 20 will be described below.

In the initial state, the pull-out band 21 is
The maximum amount is wound around the drive reel 22, 180 °
Is positioned so as to face the branch line 27. In this state, the pull-out band 21, the ceiling wall 29, the peripheral wall 30, and the end wall 5
The volume of the partial chamber 23 ′ formed between the first and the third parts 53 is minimum.

Note that the pull-out band 21 may not be curved in an arcuate shape as described above, but the pull-out band 21 may be linearly arranged from the drive reel 22 to the attachment point 26 of the peripheral wall 30 (or in the vicinity thereof).

When acceleration due to an accident occurs, the pressure source is started, and the clutch 20 is engaged between the pull-out band 21 and a belt winding mechanism (not shown).

The high-pressure gas from the ignition pressure source is introduced into the partial chamber 23 'through the withdrawal band 21, and the 180 ° arcuate portion of the withdrawal band 21 forms the partial chamber 23 ".
It is strongly pressed to the side. As a result, a counterclockwise torque is applied to the drive reel 22, and the drive reel 22 rotates. The clutch 20 is engaged during the rotation of the drive reel 22, and the belt reel 1 (not shown)
2 is rotated in the belt winding direction via the clutch 20. At this time, the pull-out band 21 wound around the drive reel 22 is pulled out. Within the partially arcuate band travel chamber 23, the 180 ° arcuate portion of the withdrawal band runs counterclockwise.

FIGS. 19 and 20 show a state in which the arcuate portion at 180 ° is slightly moved from the small partial chamber 23 ′ in the band running chamber 23 immediately after the gas pressure is introduced. When the pull-out band 21 is linearly arranged from the drive reel 22 toward the peripheral wall 30 in the vicinity of the attachment point 26, the above-mentioned 180 ° arcuate portion is formed until the gas pressure is introduced. Then, the arcuate portion similarly moves within the band running chamber 23.

The sealing cylinder 76 shown in FIG.
While the 0 ° arcuate portion moves in the band running chamber 23, the band running chamber 23 is pushed while pushing the arcuate part.
Move in.

The length by which the pull-out band 21 is pulled out from the drive reel 22 basically corresponds to the product of the running angle (in radians) of the 180 ° arc-shaped apex and the diameter of the peripheral wall. The rotation range (rotation angle) of the drive reel 22 results from the index of this parameter and the diameter of the drive reel. Therefore, the rotation angle of the drive reel increases according to the ratio of the diameter of the peripheral wall to the diameter of the drive reel.

[Brief description of drawings]

FIG. 1 Patent application No. P443259 shown in enlarged perspective
The 1st Example of the belt tensioner which operates with the ignition possible ignition type pressure source concerning 4.0 is shown.

2 is an enlarged perspective view of a similar embodiment of the belt tensioner in the assembled state shown in a perspective view from the opposite side of FIG. 1. FIG.

FIG. 3 is a perspective view of a cross section of the same belt tensioner viewed from the side of the additional drive device, and is a cross sectional perspective view showing a state immediately after ignition of the ignition type pressure source.

4 is a cross-sectional perspective view showing the same cross section of the apparatus of FIGS. 1 to 3 as in FIG. 3, but showing a state in which the pull-out band 21 is pulled out more than in FIG. 3.

FIG. 5A is an end view of a further preferred embodiment of the housing of the belt tensioner including the band running space with the end cover removed, and FIG. 5A is a detachable mounting of the sealing wall to the housing. 6 is an enlarged end view of a sealing lip portion according to another embodiment of FIG.

6 is a sectional view taken along line VI-VI of FIG.

FIG. 7 is an enlarged end view of a cross section of the preferred embodiment of the drive reel of the belt tensioner according to the present invention within the withdrawal band attachment point.

8 is an enlarged cross-sectional view of an end portion of a pull-out band provided with a spring tongue for attaching to a recess on the outer peripheral surface of the drive reel of FIG. 7.

FIG. 9 is a perspective view of a belt tensioner of the present invention similar to that of FIGS. 3 and 4, but in addition to the take-up spring arrangement, an additional drive away from the drive shaft and drive reel is also shown, with the clutch generally FIG. 3 is a perspective view showing the non-engaged state of FIG.

FIG. 10 is a side view showing the internal structure (particularly, the clutch and the driving means) of the same device as that of FIG. 9 except that the arrangement of the pressure source is different.

11 is a perspective view showing a state where a clutch is engaged in the device of FIG.

12 is a partial vertical cross-sectional view showing a configuration including a belt take-up reel in the apparatus of FIG.

13A is an end view for explaining a state in which an additional drive device is removed in FIG. 12, and FIG. 13A is a sectional view taken along line XIIIa-XIIIa in FIG. 13A.

FIG. 14 is a perspective view illustrating a state where the clutch is completely engaged in the device of FIGS.

FIG. 15 is a partial vertical cross-sectional view showing a state where the clutch is completely engaged in FIG.

16 is an end view of the clutch of FIG.

FIG. 17 is a vertical cross-sectional view showing another embodiment in a state similar to that of FIG.

FIG. 18 is a sectional view of the same portion as FIG. 17 showing still another embodiment.

FIG. 19 is an exploded perspective view showing a torque generator for a belt tensioner according to the present invention.

FIG. 20 is a perspective view similar to that of FIG. 19 showing another embodiment of the torque generator.

[Explanation of symbols]

11 Holder 12 Belt Winding Reel 13 Safety Belt 13 'Wire Cable 14 Winding Spring Device 14' Winding Spring Device 15 Additional Drive Device 16 Pressure Source 17 Pressure Chamber 17 'Partial Chamber 17 "Partial Chamber 18 Torque Generator 19 Drive Shaft 20 Clutch 21 Draw-out band 21 'Band area 21 "Band area 22 Drive reel 23 Band running chamber 23' Partial chamber 23 'under pressure Partial chamber 24 without pressure Housing 24' Receiving part 25 In drive reel 22 Attachment point of the draw-out band 26 Attachment point of the draw-out band in the housing 24 27 Branch line 27 'Feed line 28 Branch line 29 Ceiling wall 29' Sealing lip 29 "Protrusion 30 Peripheral wall 31 Sealing lip 32 Seal Element 33 band passage 34 gas passage groove 35 spring tongue 36 outer peripheral recess (recess) 37 vent hole 37 'vent passage 38 shaft 39 belt lock 40 chassis 41 inner shaft 42 control line 43 acceleration sensor 44 clutch disc 45 through hole 46 cam 47 End guide disk 48 Slider 48 'Piston part 48 "Starting rod part 49 Displacement recess 50 Retaining cam 51, 52 End wall 53 Cover 54 Opening 55 Cam 56 Outer peripheral slot (gap) 57 Counter cam 58 Clutch housing 59 Valve piece 60 Receiving hollow Chamber 61 Pressure guide 62 Receiving part 63 Reverse receiving part 66 End region 67 Opening 68 Inlet 69 Web 70 Mounting holes 71, 72 Opening 74 Hinge 75 Partitioning position 76 Sealing cylinder

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Jürgen Mitsux Germany H-Ugen Day-89275, Futishiveg 3ev (72) Inventor Martin Wiffring Germany Graz-A-8020, Anne Strasse 12/606 (72) Inventor Robert Kopetsky Germany Ronsey 89173, Amnor 43/1 (72) Inventor George Banato Umendorf Day 88-444, Schbert Strasse 4 Germany (72) Inventor Andreas Wengart Heus Schlingen Day 73572, Nowe Mogringer Strasse 21 (72) Inventor Jürrich Die Pold Wermude-Germany-89081, Amrotenbach 5 (72) Inventor Thomas Kempfre, Bibel, Germany Talday-89346, Bägerm-Kempfler-Strasse 13 (72) Inventor Eric Emmaert Germany Weruemuday-89073, Cornig-Wilhelm-Strasse 27/1 (72) Inventor Hermann Stefan German Graz-A-8010, Copernicus Gasse 24 / 3 (56) References: Kaikaihei 2-100967 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) B60R 22/46 B60R 22/36

Claims (17)

(57) [Claims] 1. A belt take-up reel 12 for winding a safety belt 13, and a winding spring device for pulling the safety belt 13 continuously and lightly in the winding direction so that an occupant is lightly tightened by the safety belt 13. 14, 14 'and a blocking device to prevent the withdrawal of the safety belt 13 in case the safety belt is pulled rapidly and / or in the case of acceleration resulting from an accident; A belt tensioner for a safety belt device for an automobile having an additional drive device 15 for rotating the belt take-up reel 12 through a clutch 20 so that the safety belt 13 tightens the occupant before the vehicle falls down. , A rotary shaft 1 that is interlocked with the belt take-up reel 12 via the clutch 20 so that power can be transmitted.
9 or 22, and a belt running chamber 23 in which the rotating shaft is arranged.
A pull-out band 21 having one end wound around the rotary shaft and the other end attached to the peripheral wall 30 of the belt running chamber 23, and two parts separated by the pull-out band 21 in the chamber 23. The chambers 23 ', 23 "are operated in the event of an accident, and the high pressure gas is supplied to one of the partial chambers 2
3 ', and thereby pushes and moves the pull-out band 21 toward the other partial chamber 23 "side, and the pulling force of the moving pull-out band 21 rotates the rotary shaft in the safety belt winding direction. 16. A belt tensioner for a safety belt device for an automobile, comprising: 2. The withdrawal band 21 according to claim 1.
A belt tensioner having a width that airtightly separates the two partial chambers 23 ', 23 "from each other. 3. The belt tensioner according to claim 1, further comprising a vent passage for communicating the inside of the other partial chamber 23 ″ with the outside air. 4. The method of claim 1 to any one of 3, partial chamber 23 ', due to the pressure of the impact absorbing 23 ", at least one of the sealing wall 29 is provided in the band running chamber 23 A belt tensioner characterized by that. 5. The drawing wall 21 according to claim 4, wherein the ceiling wall 29 is a draw band 21 wound around the rotary shaft 19 or 22.
Has a sealing lip 29 ′ facing the outer surface of the pulling band 21 by means of gas pressure from the pressure source 16 introduced into the pressure chamber 23 ′.
9'is a belt tensioner characterized by being pressed airtightly. 6. A belt take-up reel 12 for winding up a safety belt 13, and a winding spring device for pulling the safety belt 13 continuously and lightly in the winding direction so as to lightly tighten an occupant with the safety belt 13. 14, 14 'and a blocking device to prevent the withdrawal of the safety belt 13 in case the safety belt is pulled rapidly and / or in the case of acceleration resulting from an accident; A belt tensioner for a safety belt device for an automobile having a safety belt 13 and an additional drive device 15 for rotating the belt take-up reel 12 via a clutch 20 so as to tighten the occupant before the vehicle falls down. Is engaged by a pressure source that is started at the time of generating high pressure gas ,
The clutch 20 is the same as the belt take-up reel 12 described above.
Clutch disk for transmitting the rotational force of the additional drive device 15
44, the clutch disc 44 is
Can be engaged with the guide disk 47 on the end surface of the take-up reel 12.
A belt tensioner for a safety belt device for automobiles, which is characterized by being said to be capable. 7. placed in any one of 請 Motomeko 1 to 5
Thus, the clutch 20 is started in the event of an accident and the high pressure
Must be engaged by a pressure source that generates
A belt tensioner for a safety belt device for automobiles , characterized by: 8. The clutch 20 according to claim 7,
Is a belt tensioner having a slider 48 that moves by the pressure of a pressure source to engage the clutch 20. 9. The clutch 20 according to claim 7 or 8, wherein the clutch 20 includes a clutch disc 44 that transmits the rotational force of the additional drive device 15 to the belt take-up reel 12. A belt tensioner which is engageable with a guide disk 47 on an end surface of the take-up reel 12. 10. The clutch disc 44 according to claim 9, which is made of a spring steel sheet having elasticity in itself, and is normally provided with a holding member on the outer periphery so as to maintain a conical shape so as to disengage the clutch 20. A belt tensioner characterized in that the cam 50 is locked, and when the lock of the cam 50 is released, the clutch disc 44 elastically restores and deforms into a flat shape, thereby engaging the clutch. 11. The clutch disk 44 according to claim 10, wherein a through hole 45 is provided, and the through hole 45 has a through hole 45.
The cam 4 axially protruding from the plate surface of the guide disk 47
A belt tensioner characterized in that 6 can be engaged. 12. The slider according to claim 8, wherein the slider 48 closes an inlet 68 of a pressure guiding path 61 from the pressure source 16 to the chamber 23 when the pressure source 16 is in a non-operating state, and the pressure source 16 operates. Then, the belt tensioner is pushed and moved by the gas pressure from the pressure source 16 to open the inlet 68 to connect the pressure source 16 and the pressure guiding path 61 to each other. 13. The slider 4 according to claim 12,
8 is provided with a valve piece 59, and the valve piece 59
Is moved to a position facing the inlet 68 when the slider 48 is moved to the limit of movement by the gas pressure from the pressure source 16, and then is released from the slider 48 by the pressure of the pressure source 16 or is pivotally moved. Belt tensioner characterized by being separated. 14. The slider according to claim 12, wherein the slider 48 is arranged in a groove 49 extending tangentially to the clutch disc 44 and is movable in the tangential direction. And belt tensioner. 15. The slider 48 according to claim 12, wherein the slider 48 has a piston portion 48 ′ that receives pressure from the pressure source 16 and a starter that extends in a direction away from a side that receives the pressure. A rod portion 48 ″, the starting rod portion 48 ″ has a receiving portion 62, and a reverse receiving portion 63 is provided on the outer periphery of the clutch disc 44 so as to project to the piston portion 48 ′. 27, the clutch disc 44 is rotated to a position where the receiving portion 62 contacts the reverse receiving portion 63 and engages with the guide disc 47 of the belt take-up reel 12 when is loaded. Belt tensioner. 16. The holding cam 50 on the outer periphery of the clutch disc 44 is the counter cam 57 of the clutch housing 58 in the first stage of the rotational movement of the clutch disc 44 by the slider 48 according to claim 15.
Away, in the second stage of the rotational movement, the clutch disc is further rotated until the through hole 45 of the clutch disc 44 is axially aligned with the engaging cam 46 of the guide disc 47, where the through hole 45 of the clutch disc 44 is made. A belt tensioner in which an engaging cam 46 is engaged with the belt tensioner. 17. The pressure source 16 according to claim 16.
When the slider is actuated, the slider 48 receives the clutch discs via the receiving portions 62 and 63 until the engagement between the cams 50 and 57 is released and the through hole 45 and the engaging cam 46 are aligned in the axial direction. A belt tensioner characterized in that the slider 48 is disengaged from the clutch disc 44 when it is rotated.