JPH0574732B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a disc brake with an automatic adjustment device for a motor vehicle.

The invention particularly relates to a disc brake of the type having a sliding caliper with a brake actuator that can be actuated separately either by fluid pressure or by a mechanical control device. When the brake actuator is actuated, the first friction member is directly frictionally engaged with the first surface of the rotary disk, and the second friction member is brought into direct frictional engagement with the first surface of the rotary disk by a reaction force via the sliding caliper. frictionally engages the second surface of the disc. The caliper slides against a fixed support that directly or indirectly receives the torque generated by the friction member. In this type of brake, taking into account the initial thickness of the friction member, an automatic adjustment device must be installed in the control device so that the stroke of the mechanical control device does not change as the friction member wears. is necessary. Various measures have been proposed to solve this problem. These automatic adjustment devices generally have the disadvantage that they adjust regardless of the cause of their operation. That is, this type of automatic adjustment device not only compensates for the wear of the friction member as usual, but also
It also operates to compensate for elastic distortion of the caliper due to high fluid control pressures. It is necessary for this type of automatic adjustment device to have a dead stroke which prevents self-adjustment from occurring, and this dead stroke is relatively large and corresponds to the distortion that occurs in the caliper during operation.

In order to solve this problem, the applicant
French patent application no. 2538486 published
No. 82-21683, when the control pressure reaches a predetermined value, the automatic adjustment device is disabled by blocking rotation of the nut by means of a control piston via a bushing fixed in the direction of rotation relative to the nut. A disc brake of the above type is proposed, in which the control piston is annular and is arranged between the body of the brake actuator and the cylindrical part of the screw.

Although this solution is quite satisfactory,
The brake must be pre-designed to accept this regulating device, and a predetermined pressure value is set by a hole in the brake actuator body provided to accommodate an annular control piston. Therefore, there is a drawback that this pressure value cannot be changed after machining.

The object of the invention is to provide a disc brake of the above type, which maintains the above-mentioned advantages of the automatic adjustment device, while eliminating the above-mentioned disadvantages. To achieve this object, the present invention includes a caliper and a brake actuator that acts directly on the first friction member and acts on the second friction member by a reaction force via the caliper, the brake actuator , a mechanical control device acting on the fluid control piston through an automatic adjustment device, the automatic adjustment device comprising a screw having a reversible pitch actuated by the fluid control piston when the piston exceeds a predetermined stroke; a nut device; an annular nut device axially slidably and non-rotatably connected to the nut and configured to cooperate with the control piston to prevent rotation when fluid pressure acting on the fluid control piston reaches a predetermined value; The fluid control piston and the control piston are coaxially fitted so that one is located inside the other, and cooperate in a sealed and slidable manner to control the fluid control piston and the control piston. The piston receives the fluid pressure at one end and the atmospheric pressure at the other end, and when the fluid pressure reaches a predetermined value, engages the annular member and pushes the annular member against the wall of the fluid control piston. The present invention proposes a disc brake with an automatic adjustment device, which is characterized in that the rotation and axial movement of the annular member are prevented by holding the annular member.

With this configuration, the control piston is housed within the fluid control piston, or vice versa, and the brake actuator, particularly its body, does not have to be modified to accommodate the control piston, so the fluid control piston can be accommodated. By replacing it, the predetermined pressure value can be easily changed. This configuration allows brakes with conventional self-adjusting devices with reversible pitch screw and nut devices to accept fluid control pistons with control pistons without modification to the brakes;
Existing brakes could benefit greatly from a device that prevents overadjustment and significantly reduces dead travel.

These and other features and advantages of the invention will become apparent from the following description of an embodiment, made with reference to the accompanying drawings.

The disc brake shown in FIG.
It is equipped with a sliding caliper indicated by 0. Calipa 1
0 comprises a brake actuator, generally designated 12, which acts directly on the first friction member 14 and indirectly, via the sliding caliper 10, on the second friction member 16. Both friction members can be frictionally engaged with the rotating disk 18. The brake actuator 12 includes a fluid control device and a mechanical control device, as will be described later. Conventionally, the fluid control device is comprised of a fluid control piston 20 slidably fitted within a bore 22 formed in the brake actuator 12. A seal 24 provides a seal between the piston 20 and the bore 22, and the piston is protected by a piston protection cap 26. piston 20
The bottom wall 28 of the bore 22 defines a chamber 30 that is connected to a pressure source (not shown), such as a vehicle master cylinder.

A mechanical control device, generally designated 32, is constituted by a lever 34 connected to a cable or equivalent device (not shown) fixed to a shaft 36;
A groove 38 is formed within the shaft 36 in which a link 40 is accommodated. The shaft 36 is the brake actuator 1
lever 3.
It is fixed longitudinally to the actuator by a shoulder formed at 4 and a retaining ring or equivalent device. The shaft 36 and link 40 are housed in a blind bore 42 formed in the brake actuator 12, the opening of the blind bore is provided with a plug, and the assembly is protected by a flexible cap 44. Ru. The blind bore 42 also receives a screw 46 and the enlarged portion 4 of the screw.
8 is provided with a groove 50 cooperating with the link 40.
A return spring 52 is disposed between the bottom of blind hole 42 and enlarged portion 48 . The screw 46 has a grooved cylindrical portion that cooperates with the seal 54 . The seal 54 and the cylindrical portion of the screw 46 are slidable against a hole 56 formed in the brake actuator body. The screw 46 is connected to the chamber 30 by a threaded portion 58 having a reversible pitch.
A nut 60 is attached to the threaded portion. The fluid control piston 20 is the control piston 64
A control piston 64 is sealed within this hole 62 by a seal 66. The fluid control piston 20 has a second hole 68 of a diameter larger than the diameter of the hole 62, the step between these forming a wall 70 facing the chamber 30. A collar 74 is disposed between this wall 70 and a collar 72 formed on the end of the control piston 64, the collar 74 being formed on a bushing 76 constituting an annular member coaxial with the control piston 64. . The end of the bushing 76 on the same side as the chamber 30 is provided with a number of fingers 78 that project into a groove 80 formed in a collar 82 on the nut 60. These fingers 7
8 and the groove 80, the bush 76 and the nut 60 are rotationally fixed relative to each other, while
It is possible to move relative to each other in the axial direction. A third hole 84 having a larger diameter than the hole 68 slidably accommodates an annular member 86, and the annular member 86 is held in contact with a step formed by the two holes 68 and 84 by a spring 88. The spring 88 abuts a retaining ring or equivalent member 90 fixed to the piston 20 in proximity to the chamber 30 . A ball thrust race is disposed between the annular member 86 and the collar 82 such that the annular member 86 and the collar 82 form a rolling track. A one-way clutch 92 is disposed between the control piston 64 and the nut 60, and in the illustrated embodiment is formed by a spring clutch fitted into a cylindrical portion of the nut 60, with one end of the spring clutch being connected to the control piston. 64 into the hole formed therein.

The brake described above with reference to FIG. 1 operates in the following manner.

In the rest state, a number of components of the brake are in the positions shown. If the brake is actuated by a mechanical control, the lever 34 and shaft 36
pushes the link 40 in the direction of arrow A. Link 4
0 forces the enlarged portion 48 of the screw 46 through the groove 50 against the spring 52. The cylindrical portion of the screw 46 can slide against the hole 56 formed in the brake actuator, so that the screw 46 also follows the arrow A.
move in the direction. This movement of the screw 46 is transmitted to the nut 60 by the threaded portion 58, and the nut 60
is prevented from rotating by the one-way clutch 92, so that the nut 60 abuts the control piston 64, and the control piston is forced by the collar 72 through the collar 74 and wall 70 of the bushing 76 to the fluid control piston 20. Push. In this way,
The force of the link 40 is transmitted to the friction member 14, and the reaction of this friction member 14 against the disc 18 causes a reaction force in the opposite direction to act on the shaft 36 in the direction of arrow A.
The caliper 10 is slid in the opposite direction to bring the friction member 16 into contact with the disk 18. Upon release of the mechanical control, numerous components of the brake return to the positions shown.

When the brake is actuated by a hydraulic control device, fluid pressure is supplied to the chamber 30 and the piston 2
0 to the left in FIG. If the amount of movement of piston 20 relative to nut 60 does not exceed the operating play between the ball thrust race, annular member 86 and collar 82, no self-adjustment will occur due to movement of piston 20. If the amount of movement of the piston 20 is greater than the predetermined operating play, the nut 60 is connected to the ball thrust race, the annular member 86
and is driven to the left by the piston 20 via a spring 88 driven by a retaining ring 90 fixed to the piston. The screw 46 is axially immobilized by the spring 52, and the nut 60, due to its reversible pitch,
can be rotated relative to screw 46 to follow the movement of the nut, and one-way clutch 92 allows this rotation. During this phase of operation, the control piston 64 engages the collar 7 of the bushing 76 as described below.
4 is not brought into contact with the wall 70, but the button 7
6 can freely rotate together with the nut 60. Thereafter, when the fluid pressure is released, the seal 24 retracts the piston 20 slightly in the normal manner and the one-way clutch 92 prevents rotation of the nut 60. As the nut 60 rotates and moves to the left during braking, the automatic adjuster assumes a new position offset to the left and prevents the piston 20 from returning to its initial position.

However, if the brake application is not immediately released, the pressure within the chamber 30 will continue to rise and the effect of this pressure and the force generated by the piston 20 will cause the caliper 10 to deflect. It is therefore necessary to prevent the adjustment operation before mechanical distortion of the caliper begins.

When the pressure in the chamber 30 reaches a level set by the cross-sectional area of the control piston 64 and the resistance to movement of this piston created by the seal 66, the control piston 64 will move to the left under the influence of this pressure. The button 76 moves through the collar 72.
retains the collar 74 of the piston 20 against the wall 70 of the piston 20. Therefore, the bush 76 is connected to the control piston 6
rotationally and axially immobilized by 4;
Rotation of nut 60 is prevented by fingers 78 and grooves 80. Nut 60 compresses spring 88 through ball thrust race and annular member 86. The piston 20 moves to the left under the influence of the pressure flowing into the chamber 30, and the resulting force causes a distortion in the caliper 10, which is caused by the collar 72 of the control piston 64 in the collar 74 of the bushing 76. Since the restraining force exerted is greater than the force of spring 88, the automatic adjustment device will not be activated. When the fluid pressure is released, in a first step, spring 88 expands to force annular member 86 against the shoulder located between holes 84 and 68, and nut 60 is moved along the axis carried by the ball thrust race. It is no longer subject to directional forces, but remains free of operating play. In the second stage,
The seal 24 moves the piston 20 to the right in FIG. 1 in the normal manner, creating operating play between the nut 60 and the ball thrust race. In the third stage, the pressure continues to drop and the seal 66, like the seal 24, pushes the control piston 64 to the right, releasing the collar 74 of the bushing 76, which causes the nut 60 to rotate in the direction of rotation. If pushed, it can freely rotate again with the nut.

FIG. 2 shows a modification of FIG. 1, in which only the end of the fluid control piston 20 is shown. In this variant, a spring 94 formed by an elastic washer is attached to a shoulder 9 formed on the control piston 64.
6 and a retaining ring 98 fixed to the piston 20. A second retaining ring 100 located at the end of the control piston 64 restricts relative movement between the piston 20 and the control piston 64 due to the action of the spring 94.

This brake operation is similar to the configuration of the first embodiment, except that the spring 94 assists the force of the seal 66 to ensure that the piston 64 moves to the right when the pressure in the chamber 30 decreases. The operation is identical to that described. Also, the predetermined pressure value that prevents the automatic adjustment device from operating can be easily changed.

FIG. 3 shows a second embodiment of the invention. The disc brake shown in FIG. 3 is generally designated 110 and is glued to a fixed support or member (not shown) that is fixed to a fixed part (not shown) of the vehicle.
It is equipped with a sliding caliper as shown. Calipa 11
0 comprises a brake actuator, generally designated 112, which actuator acts directly on the first friction member 114 and on the sliding caliper 1.
10 can act indirectly on the second friction member 116 to bring both friction members into frictional engagement with the rotary disk 118. The brake actuator 112 includes a fluid control device and a mechanical control device as described below.

The fluid control device includes an annular control piston 164.
The control piston 164 itself is comprised of a fluid control piston 120 slidably fitted into a hole 162 formed in the brake actuator 11.
It is slidably fitted into the hole 122 formed in 2. Seal 166 connects piston 120 to bore 16
2, while the seal 124 provides a seal between the control piston 164 and the brake actuator 1.
12 and the hole 122 of the main body is sealed. Pistons 120 and 164 are connected to piston protection cap 12
Protected by 6. Pistons 120 and 164
The bottom wall 128 of the bore 122 defines a chamber 130 that is connected to a pressure source (not shown), such as a vehicle master cylinder.

The mechanical control device, generally designated 132, includes:
It is constituted by a lever 134 coupled to a cable or equivalent device (not shown) fixed to a shaft 136, in which a groove 138 is formed to accommodate a ring 140. The shaft 136 is received within two holes formed in the brake actuator 112 and is fixed longitudinally thereto by a shoulder formed in the lever 134 and a retaining ring or equivalent device. Shaft 136 and link 140
are housed in a blind hole 142 formed in the brake actuator 112, the opening of the blind hole is provided with a plug, and these assemblies are attached to the flexible cap 1.
Protected by 44. Blind hole 142 also has screw 1
46 and the enlarged portion 148 of the screw is connected to link 1
A groove 150 cooperating with 40 is provided. Blind hole 14
A return spring 152 is disposed between the bottom of 2 and the enlarged portion 148. Screw 146 includes a cylindrical portion with a groove formed therein that cooperates with seal 154 . The seal 154 and the cylindrical portion of the screw 146 are slidable against a hole 156 formed in the brake actuator body. The screw 146 is extended into the chamber 130 by a threaded portion 158 having a reversible pitch, into which a nut 160 is mounted. Fluid control piston 120
is the hole 1 extended by the larger diameter second hole 184.
68 and the hole 184 is located on the same side as the chamber 130. The annular member 186 is provided with a ring 190 disposed within a groove formed in the hole 184.
It is held in contact with a step formed by two holes 168 and 184. Annular member 186 and nut 16
A ball thrust race is disposed between the collar 182 formed at 0, and the annular member 186 and the collar 182 form a rolling track. One-way clutch 192 connects fluid control piston 120 and nut 1
60, and in the illustrated embodiment is formed by a spring clutch fitted into the cylindrical portion of the nut 160, with one end of the spring clutch extending into a hole formed in the fluid control piston 120. There is. The nut 160 is the annular member 1
It is extended in the direction of chamber 130 by an extension 202 passing through 86 . The extension 202 has a finger 180 at the end on the same side as the chamber 130 that engages a finger 178 formed on the annular member 176 . Fingers 178 and 180 are axially slidable relative to each other while nut 160 and annular member 17
6 is fixed in the rotational direction. The annular member 176 does not reach the bore 162 of the control piston 164 but is connected to the chamber 1.
30 and extends radially outwardly so as to face the end wall 170 of the piston 120 on the same side as the piston 30 . The control piston 164 has a collar 17 at the end on the same side as the chamber 130.
2, and a collar 172 extends radially inwardly to surround the annular member 176 between the collar and the wall 170 of the piston 120. color 17
2 and the annular member 176 so that the annular member 176 is not constrained. The control piston 164 is connected to the chamber 13
A front face 1 located opposite a front face 198 formed in the fluid control piston 120 at the end remote from 0;
96, and the distance between front surfaces 196 and 198 is greater than the play between collar 172 and annular member 176. The piston 120 has a shoulder 2 which allows the annular portion or rim 194 of the cap 126 to be mounted.
04, the annular portion extending from the shoulder 204 to the front surface 196 of the control piston 164.

In this second embodiment, a resilient ring 200 is fitted within a groove 206 formed in the fluid control piston 120 and faces the groove 206 and extends into a groove formed in the control piston 164. 120 and control piston 164 to prevent accidental separation of fingers 178 and 180. It will be appreciated that other devices may be used to restrict this relative movement. This elastic ring 20
0 is the fluid control piston 120 and the control piston 16
4 can be left as a unit.

The brake described above with reference to FIG. 3 operates in the following manner.

In the rest state, a number of components of the brake are in the positions shown. When the brake is actuated by a mechanical control device, the lever 134 and the shaft 1
36 pushes the link 140 in the direction of arrow _F1 .
Link 140 forces enlarged portion 148 of screw 146 through groove 150 against spring 152 . The cylindrical portion of the screw 146 is slidable relative to the hole 156 formed in the brake actuator, so that the screw 146 also moves in the direction of arrow _F1 . This movement of screw 146 is transmitted by threaded portion 158 to nut 160, and rotation of nut 160 is prevented by one-way clutch 192 so that nut 160 abuts fluid control piston 120. In this way, the force of link 140 is transferred to friction member 114 and disk 118
This reaction of the friction member 114 against the friction member 114 causes a reaction force in the opposite direction to act on the shaft 136, causing the caliper 110 to slide in a direction opposite to the direction of arrow _F1 , and bringing the friction member 116 into contact with the disk 118. Upon release of the mechanical control, numerous components of the brake return to the positions shown.

When the brake is actuated by a hydraulic control, fluid pressure is supplied to chamber 130 to force piston 120 to the left in FIG. Natsuto 160
If the amount of movement of the piston 120 relative to the ring does not exceed the operating play between the ball thrust race, the annular member 186, and the collar 182, no self-adjustment will occur due to the movement of the piston 120. If the amount of movement of piston 120 is greater than the predetermined operating play, nut 160 is driven to the left by piston 120 through the ball thrust race and an annular member 186 secured to the piston. The screw 146 is axially immobilized by a spring 152, and the nut 160, because of its reversible pitch, can rotate relative to the screw 146 to follow the movement of the piston 120, creating a one-way clutch. 192 allows rotation of this nut. During this phase of operation, control piston 164
As will be described later, the annular member 176 is not brought into contact with the wall 170, and the annular member 176 is attached to the nut 1.
It can be rotated freely with 60. Thereafter, when fluid pressure is released, seal 166 retracts piston 120 slightly in the normal manner and one-way clutch 192 prevents rotation of nut 160. Since the nut 160 rotated and moved to the left during braking, the automatic adjuster assumes a new position offset to the left and prevents the piston 120 from returning to its initial position.

However, if the brake application is not immediately released, the pressure within the chamber 130 will continue to rise and the effect of this pressure and the force generated by the piston 120 will cause the caliper 110 to deflect. It is therefore necessary to prevent the adjustment operation before mechanical distortion of the caliper begins.

When the pressure in the chamber 130 reaches a level set by the cross-sectional area of the control piston 164, the resistance to movement of this piston produced by the seal 124, and the force deforming the annular portion 194 of the cap 126, the control piston 164 moves to the left under the effect of this pressure, arresting the annular member 176 against the wall 170 of the piston 120 through the collar 172. Thus, the annular member 176 is rotationally immobilized by the control piston 164 and rotation of the nut 160 is prevented by the fingers 178 and 180. The nut 160, which has become unable to rotate,
The screw 146 is moved through the threaded portion with a reversible pitch to compress the spring 152. The pistons 120 and 164 move to the left due to the pressure flowing into the chamber 130, and the resulting force causes distortion of the caliper 110.
The restraining force generated on the annular member 176 by the collar 172 of the control piston 164 is exerted by the spring 15
Since the force is greater than 2, the automatic adjustment device will not be activated. When fluid pressure is released, the first
At this step, spring 152 expands to move screw 146 to its initial position and nut 160
is no longer subject to the axial force transmitted by the screw 146, but no operating play is maintained. In the second stage, the seal 166 retracts the piston 120 to the right in FIG. 3 in a normal manner, creating operating play between the nut 160 and the ball thrust race. In the third stage, the pressure continues to decrease and the seal 124, like the seal 166, pushes the control piston 164 back to the right to release the annular member 176, assisted by the annular portion 194 of the protective cap 126; The annular member 176 can freely rotate with the nut 160 when it is pushed in the rotational direction.

As can be seen from the description of this second embodiment, the device according to the invention is self-adjusting depending on the predetermined pressure set by the cross-sectional area of the control piston 164 and the stiffness of the annular part 194 of the protective cap 126. The blocking operation can be controlled. When a predetermined pressure is generated, the control piston 164 is moved to the piston 1 by the collar 172 via the annular member 176.
The force acting on the friction member generated by the pressure axially abutting 20 and thus flowing into chamber 130 is obtained when piston 120 is extended to bore 122 in the brake actuator body. It becomes the same as the power that is applied. This solution does not change the brake operating characteristics and does not require machining of the caliper or self-adjuster screws.
The device according to the invention can be installed in existing brakes.

This advantage is the same in the first embodiment described above.

It is also apparent that the fluid control piston, control piston, annular member and nut form an assembly that can be removed as a unit from the brake actuator and screw.

Although the invention has been described with reference to the illustrated embodiment, the invention is not limited thereto, and many modifications can be made without departing from the scope of the invention. For example, the mechanical control device may be operated in other ways to generate an axial force on the screw in the direction of arrow A in FIG. 1; similarly, one-way clutch 92 may be other than a spring clutch. Further, the piston 20
and 64 may be provided with an anti-rotation device.

[Brief explanation of the drawing]

FIG. 1 shows the first disc brake according to the present invention.
FIG. 2 is a partial sectional view showing a modification of FIG. 1, and FIG. 3 is a sectional view showing a second embodiment of the present invention. 10,110...Sliding caliper, 12,112...
Brake actuator, 14,114...first friction member, 16,116...second friction member, 20,1
20...Fluid control piston, 22, 62, 122,
162...hole, 24,66,124,166...seal, 26,126...piston protection cap, 3
2,132...Mechanical control device, 46,146...Screw, 60,160...Nut, 64,164...Control piston, 70,170...Wall, 72,74,17
2... Collar, 76, 176... Bush or annular member, 94... Spring, 194... Annular portion, 19
6,198...Front.

Claims (1)

[Claims] 1 Caliper 10, 110 and first friction member 1
4,114 and the caliper 10,
The reaction force via 110 causes the second friction member 16,1 to
Brake actuator 12,1 acting on 16
12, the brake actuator 1
2,112 is a mechanical control device 3 acting on the fluid control piston 20,120 via an automatic adjustment device
2,132, the automatic adjustment device includes a screw and nut device 46-60, 146-16 having a reversible pitch actuated by the fluid control piston 20, 120 when the piston exceeds a predetermined stroke.
0 and is axially slidably and non-rotatably connected to the nuts 60, 160, and cooperates with the control pistons 64, 164 when the fluid pressure acting on the fluid control pistons 20, 120 reaches a predetermined value. and an annular member 76, 176 whose rotation is prevented by rotating the fluid control piston 2.
0, 120 and the control pistons 64, 164 are coaxially fitted so that one is located inside the other and cooperate in a sealing and slidable manner, with the control pistons 64, 164 having one end. receives the fluid pressure at the end and atmospheric pressure at the other end, and when the fluid pressure reaches a predetermined value, the annular member engages with the annular member 76, 176 and pushes the annular member against the wall of the fluid control piston 20, 120. 70,
170. A disc brake with an automatic adjustment device, characterized in that the annular member is restrained against rotation and axial movement of the annular member. 2 Elastic members 66, 94, 1 between the control pistons 64, 164 and the fluid control pistons 20, 120
66-194 are arranged to control the control piston 6.
4,164 as the fluid control piston 20,120
The disc brake according to claim 1, wherein the disc brake is spaced apart from the walls 70, 170 in the axial direction. 3. The disc brake according to claim 1 or 2, wherein the control piston 64 is hermetically and slidably housed in a hole 62 formed in the fluid control piston 20. . 4 The elastic member connects the control piston 64 and the hole 6.
3. The disc brake according to claim 3, wherein the disc brake is a seal 66 disposed between the disc brake and the disc brake. 5. A fluid control piston 120 is hermetically and slidably housed within a bore 162 formed in the control piston 164, and a control piston 164 is hermetically and slidably housed within a bore 122 formed in the brake actuator 112. 3. The disc brake according to claim 1 or 2, wherein the disc brake is freely stored. 6 the control piston 164 is connected to the annular member 176;
6. The disc brake according to claim 5, characterized in that the piston is an annular piston having a collar 172 at one end thereof which can be brought into contact with a wall 170 of the fluid control piston 120. 7. The control piston 164 has a front surface 196 at the other end, and the front surface 196 is capable of pressing against the elastic member 194 disposed between this surface and a front surface 198 formed on the fluid control piston 120. A disc brake according to claim 6. 8 The above elastic member is the brake actuator 12
annular part 1 fixed to a protective cap 126 of 2;
Claim 7 characterized in that: 94
Disc brake as described in section. 9. Claims 1 to 9, characterized in that the fluid control piston 20, 120, the control piston 64, 164, the annular member 76, 176 and the nut 60, 160 form an assembly that can be removed as a unit. The disc brake according to any one of item 8.