EP1289817A1 - Brake servo unit comprising a bushing adjustable by deformation, and assembly for adjusting the bushing - Google Patents
Brake servo unit comprising a bushing adjustable by deformation, and assembly for adjusting the bushingInfo
- Publication number
- EP1289817A1 EP1289817A1 EP01955302A EP01955302A EP1289817A1 EP 1289817 A1 EP1289817 A1 EP 1289817A1 EP 01955302 A EP01955302 A EP 01955302A EP 01955302 A EP01955302 A EP 01955302A EP 1289817 A1 EP1289817 A1 EP 1289817A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- sleeve
- control rod
- face
- transverse
- section
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
- B60T13/46—Vacuum systems
- B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
- B60T13/569—Vacuum systems indirect, i.e. vacuum booster units characterised by piston details, e.g. construction, mounting of diaphragm
Definitions
- the invention relates to a pneumatic brake booster for a motor vehicle.
- the invention relates more particularly to a pneumatic brake booster for a motor vehicle, of the type which comprises a rigid envelope inside which is movable a transverse partition sealingly delimiting a front chamber, subjected to a first pressure of engine depression, and a rear chamber subjected to a second pressure varying between engine depression and atmospheric pressure, of the type which comprises a movable piston secured to the movable partition moving with the movable partition and a control rod moving in the piston selectively as a function of an axial input force exerted towards the front against a return force exerted on the rod by a return spring, of the type in which the rod is movable in an intermediate actuation position or an extreme actuation position obtained when the input force is applied at a determined high speed, from the type which comprises a plunger which is arranged at the front of the control rod in the piston and a three-way valve which comprises at least one annular rear seat of the plunger and which
- a conventional servomotor has neither a probe nor a one-way clutch device for the probe.
- the plunger is likely to come to directly solicit the reaction disc secured to the rear face of the mobile piston.
- the actuation of the control rod causes the actuation of the plunger also forming a feeler, which causes the maximum opening of the valve at three tracks so that the rear chamber is brought to atmospheric pressure. There follows a displacement towards the front of the movable partition and the end of the plunger comes into contact with the reaction disc secured to the rear face of the movable piston.
- the force exerted on the mobile piston when the control rod is at the end of the race results from the assistance force which is caused by the pressure difference on each side of the mobile wall and from the force exerted by the plunger forming a probe on said movable piston.
- the driver of the vehicle also feels the braking reaction force, which is transmitted from the movable piston to the plunger via the reaction disc.
- the plunger can come into contact with the reaction disc and transmit to the driver a feeling of maximum braking even before the difference in pressure is maximum between the front and rear pressure chambers, which can lead the driver to relax his effort, even if he should be maintained to benefit from the maximum braking effort.
- a servomotor such as that of the type described above overcomes this drawback by blocking the probe in contact with the reaction disc by immobilizing the sleeve and therefore maintaining maximum force on the rear face of the movable piston even if the driver would have partially relaxed his effort.
- a unidirectional clutch device for such a servomotor is moreover of a substantially reduced manufacturing cost since it comprises a feeler integrated into the socket.
- the booster of the type described above has the drawback of requiring compliance with precise manufacturing dimensions for the socket.
- the sleeve comprising the probe is mounted so that a determined clearance is established between the probe and the reaction disc in the rest position.
- the value of this play determines the assistance force supplied by the mobile piston for which a reaction force is transmitted, via the reaction disk, from the mobile piston to the control rod.
- the value of this assistance effort is commonly called the "jump" of the servomotor, and it is therefore dependent on the dimensions of the probe, in particular the thickness of the probe.
- the axial position of the blocking element of the bush determines the speed for which the one-way clutch device may trip.
- This speed is commonly known as the "tripping speed”, and it is therefore dependent on dimensions of the sleeve, in particular on the axial distance separating the front end of the plunger from the blocking element of the sleeve.
- the blocking element of the sleeve is produced in the form of a transverse shoulder face, which makes it possible to obtain a sleeve capable of being suitable for the correct operation of the servomotor by producing it by a machining process. , including filming. The dimensional dimensions are then obtained by the turning process.
- the invention provides a socket, the dimensions of which can be adjusted simply by a plastic deformation process.
- the invention provides a servomotor of the type described above, characterized in that the socket has a first adjustment part, arranged between the front and rear faces of the probe, and a second adjustment part, arranged between the rear face. of the feeler and the locking element, which are plastically deformable, at least in the axial direction, so as to allow the actuator to be adjusted before it is assembled.
- the locking element is formed by a substantially annular key which loosely surrounds the socket and which is capable, when the input force is applied at the determined speed, of being driven by the movable piston to tilt around a generally transverse axis so that a lug of the key comes into abutment against a rear transverse face of the socket forming the blocking element,
- the bushing comprises a tubular front cylindrical section, the end of which forms the feeler and a tubular rear cylindrical section, of a diameter substantially greater than the diameter of the front section which comprises a radial groove, a transverse front face of shoulder of which forms the rear transverse blocking face,
- the front section includes an inner annular flange which extends rearwardly, projecting from the rear face of the probe, and which is capable of being deformed axially before assembly to constitute the first adjustment part making it possible to adjust the position, or jump of the servomotor, in which the probe requests the reaction disc, - the front section and the rear section of the sleeve are separated by an intermediate section of reduced thickness which is capable of being deformed axially to constitute the second adjustment part making it possible to adjust the trigger position according to which the lug of the key is received in abutment against the rear transverse locking face,
- the groove has a substantially frustoconical profile behind the front transverse shoulder face
- the lug has the shape of a concave frustoconical angular sector which is complementary to the frustoconical profile of the groove of the sleeve,
- the key has, in section through an axial plane, the shape of a "T" whose vertical branch of substantially radial orientation is crossed by the sleeve and whose horizontal branch, of substantially axial orientation is received without axial play Between two opposite walls of a recess which crosses the piston perpendicularly to its axis to allow only a tilting of the key in the recess.
- the front horizontal half-branch of the T-shaped wrench has a face facing radially towards the bushing from which the lug protrudes
- the T-key is elastically recalled against the rear transverse wall of the recess by two compression springs arranged between the front transverse wall of the recess and blind holes for centering the T-key which are arranged on the side and other side of the socket in the vertical branch of the T,
- the sleeve is made of a material having a reduced elastic limit and a high toughness.
- the invention also provides an assembly for the plastic deformation of a tubular sleeve of a pneumatic brake booster of the type described above which comprises, from front to back, a cylindrical front tubular section with a determined external diameter. , which is closed at its end by a front transverse wall from which extends towards the inside of the bushing a deformable annular coaxial flange forming a first adjustment part, a deformable intermediate section of the same outside diameter as the front section forming a second adjustment part, and a rear cylindrical section of a determined diameter greater than the diameter of the front section comprising at least one rear transverse shoulder face.
- the invention provides an assembly of the type described above, characterized in that it comprises a male matrix and a coaxial tubular female matrix between which the sleeve is interposed to be deformed during a single deformation operation by axial compression by pressing the dies axially against each other to obtain simultaneously determined dimensions of the first and second setting part.
- the internal diameter of the tubular female matrix is greater than the external diameter of the rear section of the sleeve, and the female matrix has a rear transverse wall from which extends a cylindrical bearing on which the sleeve is threaded forwards. so that a front end of the cylindrical seat bears against the annular collar of the sleeve,
- the male matrix has a bore with a diameter corresponding to the outside diameter of the front section of the bushing, a front transverse bottom of which is intended to allow the front transverse wall of the front section of the bushing to be supported,
- the male matrix comprises a convex cylindrical bearing surface which projects rearwards and which is intended to receive a first tubular shim of determined length adjustment arranged in the extension of the female tubular matrix
- the assembly comprises a tubular spacer before d support intended to be threaded on the sleeve in axial contact with the transverse shoulder face of the sleeve and a second rear tubular shim of fixed length adjustment which are intended to be placed in the female matrix between the cylindrical seat of the female matrix and its internal cylindrical wall prior to the deformation operation by axial compression
- the male matrix is fixed, and the female matrix is slidably mounted axially to be pressed towards the male matrix with a compression force of determined intensity.
- FIG. 1 is an overall view of a booster produced in accordance with the state of the art
- FIG. 2 is a view in axial section of detail of a pneumatic brake booster according to the invention shown in the inactive position of the one-way clutch,
- FIG. 3 is a view in axial section of detail of a pneumatic brake booster according to the invention shown in the active position of the one-way clutch,
- FIG. 4 is a view in axial section of a socket for a one-way clutch according to FIGS. 1 or 2, and,
- FIG. 5 is an axial sectional view of an assembly for the plastic deformation of a sleeve according to Figure 3.
- identical reference numerals denote identical parts or having similar functions.
- front By convention, the terms “front”, “rear”, upper “,” lower “respectively designate elements or positions oriented respectively to the left, the right, the top, or the bottom of FIGS. 1 to 5.
- FIG. 1 shows a set of a pneumatic brake booster 1 0 for a motor vehicle.
- the pneumatic servomotor 10 comprises a rigid casing 12 inside which is mounted a movable transverse partition 14 which delimitably a front chamber 16, subjected to a first pressure "Pi” whose value is equal to the value of the depression of the vehicle engine, and a rear chamber 18 subjected to a second pressure "P 2 ".
- the second pressure "P 2 " is likely, as will be described later, to vary between the value of engine vacuum “Pi” and the value of atmospheric pressure "P a ".
- the front chamber 16 is supplied with pressure "Pt" via a vacuum conduit 20 which is connected to a source of vacuum in the vehicle, for example a vacuum prevailing in an intake manifold (not shown) of a vehicle engine.
- the pneumatic booster 10 comprises a movable piston 22 which is integral with the movable partition 14. Inside the casing 12, the movable partition 14 is biased elastically towards the rear by a return spring 24 which bears on the envelope 12 and on a front face 26 of the movable piston 22.
- the front face 26 of the movable piston 22 carries a reaction cup 30 inside which is arranged, as will be seen below, a reaction disc 32 in elastomeric material.
- a front face 34 of the reaction cup 30 is integral with an actuating rod 28, which is consequently integral with the displacements of the movable piston 22, and which allows the actuation of a hydraulic master cylinder 36 for braking the vehicle.
- a control rod 38 which is for example connected to a brake pedal of the vehicle by means of a coupling sleeve 41 which is arranged at its rear free end 43, is capable of moving in the movable piston 22 , selectively as a function of an axial input force exerted forward on the control rod 38.
- the actuating force is exerted against a return force which is exerted on the rod 38 by a return spring 40 which is interposed between the movable piston 22 and the control rod 38.
- the other front end of the control rod 38 is shaped as a ball joint 42 and is received in a complementary housing 44 of a substantially cylindrical plunger 46 which is slidably mounted in the movable piston 22.
- a rear annular seat 48 of the plunger 46 is part of a three-way valve 50 which is capable of varying the second pressure "P 2 " prevailing in the rear chamber 18, in particular by connecting the front chamber 16 and the rear chamber 18 when the control rod 38 is in the rest position, or by gradually bringing the rear chamber 18 into communication with the atmospheric pressure "P a " when the control rod 38 is activated.
- a feeler 52 is formed at the front end of a socket 58 which is slidably mounted on the front end of the plunger 46 which is opposite to the housing 44.
- the front end of the socket 58 forming the feeler 52 is also slidably mounted inside a bore 54 of the movable piston
- the servomotor 10 comprises a one-way clutch device 56 which comprises on the one hand a locking element forming part of the coaxial socket 58 and which on the other hand comprises a movable locking element which is formed of a substantially annular key 60 surrounding the bush 58 with radial clearance.
- the coaxial sleeve is slidably mounted on the plunger 46 and is resiliently returned by the intermediary of a spring 57, interposed between the piston 22 and the sleeve 58, in contact with a front transverse face 59 of the plunger 46 .
- the socket 58 passes through a circular lumen 61 of the key 60.
- the key 60 is disposed in a recess 62 which crosses the piston 22 perpendicular to its axis "A".
- the key 60 is resiliently biased against a rear wall 66 of the recess 62.
- a lower part 70 of the key 60 is, in the rest position shown in FIG. 2, supported on a support 72 which is linked to the casing 12 of the booster 10.
- a transverse pin 71 which crosses transversely the socket 58 and the plunger 46, is, in the rest position of the rod 38, bearing on a front face of the key 60 to define the rest position of the plunger 46.
- the plunger 46 drives the sleeve 58 at a speed which is higher than that of the movable piston 22.
- An upper part 64 of the key 60 is then driven by the control piston 22 while its lower part 70 leaves its support on the support 72.
- the key 60 does not being more supported on the socket 58, it rocks around a generally transverse axis and counterclockwise to cooperate with a blocking element of the periphery of the socket 58, in particular a rear transverse face 76 of the socket .
- the unidirectional clutch device 56 has been shown in the figures as comprising a locking element consisting of the key 60 previously described, but it will be understood that it may also include a movable locking element of another type, which is capable of immobilizing axially precisely the rear transverse face 76 of the socket 58.
- the servomotor 10 which is the subject of the invention, which will now be described more specifically with reference to FIGS. 2 and 3, comprises a one-way clutch 56 whose key 60 includes a lug 78 which is intended, in the active position of the clutch , to come into abutment against the rear transverse face 76 of the socket 58 forming the blocking element for blocking the socket 58 according to a precise axial position.
- the socket 58 comprises a tubular front cylindrical section 79, the end of which forms the feeler 52, and a tubular rear cylindrical section 83, with a diameter substantially greater than the diameter of the front section, which has a radial groove 80, a front transverse shoulder face forms the rear transverse face 76 for locking.
- the radial groove 80 delimits in the rear section 83 a front cylindrical surface 81 and a rear cylindrical surface 85.
- the groove 80 has a substantially frustoconical profile behind the front transverse face 76 of the shoulder. In this way, the end of the groove 80 which is opposite the face front transverse shoulder 76 progressively joins the cylindrical periphery of the rear section 83 of the socket 58.
- the frustoconical profile of the groove 80 of the socket 58 is particularly advantageous because it allows, during the tilting of the key 60, to guide the lug 78 of the key, which has the shape of a concave frustoconical angular sector complementary to the profile frustoconical of the groove 80, to its stop position against the front shoulder face 76 of the socket 58.
- the circular opening 61 of the key 60 which surrounds the socket 58, does not participate in blocking the socket 58. The latter is entirely ensured by the lug 78.
- the key 60 has, in section through an axial plane, the general shape of a "T" whose vertical branch 82 of substantially radial orientation includes the lumen 61 which is crossed by the socket 58.
- the key 60 in "T” has a horizontal branch 84, which is of substantially axial orientation perpendicular to the main branch 82, and which is received without axial play between the front walls 68 and rear 66 of the recess 62 which crosses the piston 22 perpendicularly to its axis "A".
- This configuration has the advantage of allowing only a tilting movement of the key 60 in the recess 62.
- the key 60 is not capable of moving axially relative to the recess 62, but can see its branch 82 tilt in the recess 62, in accordance with FIG. 3.
- the lug 78 is arranged under the horizontal branch 84 of the key 60 in "T". More particularly, the horizontal horizontal half-branch 86 of the T-shaped key has a face facing radially towards the socket 58 from which the lug 78 projects.
- the key 60 in "T” is resiliently returned to meet the transverse wall 66 of the recess by two compression springs 94 and 95 which are arranged between the transverse wall before 68 of the recess 62 and the blind 96 holes for centering the key 60 in T which are arranged on either side of the sleeve in the vertical branch 82 of the T.
- the mobile piston 22 moves substantially at the same speed as the plunger 46, because the establishment of the pressure atmospheric "P a " takes place as the three-way valve 50 opens.
- the horizontal branch 84 being maintained between the front 68 and rear 66 walls of the recess 62 without the possibility of axial displacement, the key 60 switches as soon as the vertical branch 82 of the key leaves its lower support on the support 72 integral with the casing 12.
- the lug 68 then comes into contact with the socket 58 on the front surface 81 of the rear section 83, but does not instantaneously enter the frustoconical groove 80 since the socket 58 and the movable piston 22 move at roughly the same speed.
- the key 60 does not block the socket 58 and does not oppose the return from front to back of the movable piston 22.
- the plunger 46 advances faster than the movable piston 22 can do, due to the delay linked to the balancing of the pressure in the rear chamber 18.
- the lug 78 leaves the front bearing 81, falls into the groove 80, and slides into abutment up to the face 76 shoulder to precisely lock the bush 58 axially.
- the key 60 blocks the socket 58 and therefore the probe 52, thus opposing the return of the movable piston 22 from front to back, regardless of the position of the plunger 46. This position maintains maximum braking force on piston 22.
- the socket 58 comprising the feeler 52 is mounted so that a determined clearance "J 1", shown in FIG. 2, is established in the rest position, between the feeler 52 and the reaction disc 32.
- this clearance "J 1" determines the assistance force supplied by the mobile piston 22 for which a reaction force is transmitted, via the reaction disk 32, from the mobile piston 22 to the control rod 38.
- the value of this assistance effort is called “jump" of the servomotor 10, and it depends on the dimensions of the probe 52, in particular on the axial thickness "H 1" of the probe 5 shown in FIG. 4.
- the axial position of the rear transverse face 76 forming the locking element of the socket 58 conditions the speed at which the clutch device unidirectional 58 is likely to trip. Indeed, as long as the lug 78 of the key 60 is capable of being retained by the front bearing 81 of the rear section 83, it does not fall into the groove 80, and the one-way clutch device 56 remains inactive.
- This speed is commonly known under the name of "tripping speed”, and is therefore dependent, as shown in FIG. 4, on the dimensions of the sleeve, in particular on the axial distance "H2" which separates a rear face 100 of the probe, which is arranged at the bottom of the bore 102 of the socket 58 and on which the front transverse end 59 of the plunger 46 is in support during its movement from back to front, of the transverse shoulder face 76 of the socket 58.
- the socket 58 is obtained by a turning process in order to produce precisely the dimensional dimensions H 1 and H2 capable of being suitable for the correct operation of the servomotor 10.
- This design has the drawback of considerably increasing the cost price of the socket because it requires respecting precise dimensions during the manufacture of the socket 58, and requires a unitary check of the socket 58.
- the invention provides a socket 58, the dimensions of which can be adjusted simply by a plastic deformation process.
- the socket 58 comprises a first adjustment part, arranged between the front and rear faces of the probe 52, and a second adjustment part, arranged between the rear face 100 of the probe 52 and the rear transverse face 76, which are plastically deformable at least in the axial direction so as to allow the actuator 10 to be adjusted before it is assembled.
- the front section 79 includes an inner annular flange 104 which extends rearwardly, projecting from the rear face 100 of the probe 52, and which is capable of being deformed axially before assembly to constitute the first adjustment part making it possible to adjust the position, or jump of the servomotor 10, in which the probe 46 urges the reaction disc 32.
- the front section 79 and the rear section 83 of the socket 58 are separated by an intermediate section 106 of reduced thickness "e" which is capable of being deformed axially to constitute the second adjustment part making it possible to adjust the release position according to which the lug 78 of the key 60 is received in abutment against the rear transverse blocking face 76.
- the sleeve 58 is in particular made of a material comprising a reduced elastic limit and of great toughness, and it is deformed in a deformation assembly 108, represented in FIG. 5, which is specially intended for the deformation of the socket 58.
- the assembly 108 comprises a male matrix 1 10 and a female tubular matrix 1 12 coaxial between which the sleeve 58 is interposed to be deformed during a single deformation operation by axial compression by pressing the dies 1 10 and 1 12 axially l 'one against the other to simultaneously obtain the determined dimensions "H 1" and H2 "of the first and second adjustment parts.
- the internal diameter D h i 2 of the tubular female matrix 1 12 is greater than the external diameter D e83 of the rear section 83 of the socket 58, so as to allow reception of the socket 58 in the female matrix 1 12.
- female matrix 1 12 has a rear transverse wall 1 14 from which extends a cylindrical seat 1 16 forwardly on which the sleeve 58 is threaded so that a front end 1 18 of the cylindrical seat 1 16 takes pressing against the annular flange 104 of the socket 58.
- the male die 1 10 has a bore 120 with a diameter corresponding to the outside diameter D e 79 of the section front 79 of the socket 58.
- a front transverse bottom 122 of the bore 120 is intended to allow the support of the front transverse wall 59 of the front section 79 of the socket 58.
- the male die 1 10 has a convex cylindrical surface 124 which projects rearward and which is intended to receive a first tubular shim 126 for adjusting the length
- the assembly 108 comprises a tubular spacer 128 before support which is intended to be threaded on the sleeve 58 in axial contact with the transverse shoulder face 76 of the sleeve 58 a second rear tubular wedge 130 for adjusting the length "L ⁇ 30 "determined which are intended to be placed in the female matrix 1 12 between the cylindrical surface 1 16 of the female matrix and its inner cylindrical wall 1 32 prior to the deformation operation by axial compression.
- tubular shims 126 and 130 can be replaced, from one type of servomotor to another, to obtain values different from the dimensions "H 1" and "H2".
- Ln 0 / ⁇ denotes the dimension of the matrix 1 10 which separates its front transverse bottom 122 from a shoulder 132 on which the first tubular wedge 126 comes to bear
- Ln 2/1 denotes the dimension of the matrix 1 12 which separates its front end 1 34 on which the first tubular shim 126 comes to bear on the front end 1 18 of the cylindrical seat 1 16.
- H2 Li 12/2 _ L-130 - Ll 28 (R2)
- Ln 2/2 denotes the dimension of the matrix 1 12 which separates the front end 1 18 from its cylindrical seat 1 16 from the rear transverse wall 1 14, and in which L- ⁇ 2 8 denotes the length of the spacer.
- H2 directly depend on the lengths of tubular shims 126 and 130. Typically, during the deformation operation, each of the initial dimensions H 1 or H2 is reduced from 0 to 0.5 mm.
- the male die 1 10 is fixed, and the female die 1 12 is slidably mounted axially to be pressed towards the male die with a force F of determined intensity.
- the orientation of the compressive force F and its point of application are shown in FIG. 5.
- the invention therefore advantageously makes it possible to benefit from a booster 10 of a reduced cost making it possible to benefit from maximum braking force in emergency braking situations, whatever the behavior of the driver after violent braking.
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Braking Systems And Boosters (AREA)
- Braking Arrangements (AREA)
- Actuator (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Forging (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0006601 | 2000-05-22 | ||
FR0006601A FR2809067B1 (en) | 2000-05-22 | 2000-05-22 | SERVOMOTOR WITH A BUSH ADJUSTABLE BY DEFORMATION, AND MOUNTING TO ADJUST THE BUSH |
PCT/EP2001/006459 WO2001089901A1 (en) | 2000-05-22 | 2001-05-18 | Brake servo unit comprising a bushing adjustable by deformation, and assembly for adjusting the bushing |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1289817A1 true EP1289817A1 (en) | 2003-03-12 |
Family
ID=8850542
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01955302A Withdrawn EP1289817A1 (en) | 2000-05-22 | 2001-05-18 | Brake servo unit comprising a bushing adjustable by deformation, and assembly for adjusting the bushing |
Country Status (11)
Country | Link |
---|---|
EP (1) | EP1289817A1 (en) |
JP (1) | JP2003534198A (en) |
KR (1) | KR20030010630A (en) |
CN (1) | CN1438952A (en) |
AU (1) | AU774150B2 (en) |
BR (1) | BR0111337A (en) |
FR (1) | FR2809067B1 (en) |
MX (1) | MXPA02012187A (en) |
PL (1) | PL359000A1 (en) |
RU (1) | RU2002134472A (en) |
WO (1) | WO2001089901A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2825058B1 (en) * | 2001-05-25 | 2003-09-19 | Bosch Sist De Frenado Sl | FIXED AND VARIABLE TWO-DIFFERENTIAL JUMP SERVO MOTOR |
FR2825057B1 (en) * | 2001-05-25 | 2003-09-19 | Bosch Sist De Frenado Sl | AIR VARIABLE JUMP HEIGHT BRAKE ASSIST MOTOR |
FR2825056B1 (en) * | 2001-05-25 | 2003-09-19 | Bosch Sist De Frenado Sl | AIR VARIABLE JUMP HEIGHT BRAKE ASSIST MOTOR |
FR2825059B1 (en) * | 2001-05-25 | 2003-09-19 | Bosch Sist De Frenado Sl | DIFFERENTIATED JUMP SERVOMOTOR |
FR2844495B1 (en) * | 2002-09-12 | 2005-06-10 | Bosch Sist De Frenado Sl | BRAKE ASSIST SERVOMOTOR COMPRISING AN EMERGENCY BRAKE DEVICE, METHOD OF ADJUSTING A THRESHOLD OF ACTIVATION THRESHOLD OF THE DEVICE, AND DEVICE FOR CARRYING OUT SAID METHOD |
FR2855135B1 (en) * | 2003-05-22 | 2005-07-15 | Bosch Gmbh Robert | PNEUMATIC BRAKE ASSIST SERVOMOTOR |
FR2922174B1 (en) * | 2007-10-12 | 2009-12-04 | Bosch Gmbh Robert | EMERGENCY BRAKE SYSTEM FOR MOTOR VEHICLE. |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2074270B (en) * | 1980-04-16 | 1984-03-14 | Lucas Industries Ltd | Servo valves for brake boosters |
DE3205268A1 (en) * | 1982-02-15 | 1983-08-25 | Alfred Teves Gmbh, 6000 Frankfurt | Brake servo unit with adjustable fastening of a spring plate |
-
2000
- 2000-05-22 FR FR0006601A patent/FR2809067B1/en not_active Expired - Fee Related
-
2001
- 2001-05-18 EP EP01955302A patent/EP1289817A1/en not_active Withdrawn
- 2001-05-18 CN CN01811915A patent/CN1438952A/en active Pending
- 2001-05-18 BR BR0111337-2A patent/BR0111337A/en not_active IP Right Cessation
- 2001-05-18 WO PCT/EP2001/006459 patent/WO2001089901A1/en not_active Application Discontinuation
- 2001-05-18 PL PL01359000A patent/PL359000A1/en unknown
- 2001-05-18 AU AU77504/01A patent/AU774150B2/en not_active Ceased
- 2001-05-18 KR KR1020027015780A patent/KR20030010630A/en not_active Application Discontinuation
- 2001-05-18 RU RU2002134472/11A patent/RU2002134472A/en not_active Application Discontinuation
- 2001-05-18 JP JP2001586107A patent/JP2003534198A/en not_active Withdrawn
- 2001-05-18 MX MXPA02012187A patent/MXPA02012187A/en unknown
Non-Patent Citations (1)
Title |
---|
See references of WO0189901A1 * |
Also Published As
Publication number | Publication date |
---|---|
FR2809067A1 (en) | 2001-11-23 |
KR20030010630A (en) | 2003-02-05 |
JP2003534198A (en) | 2003-11-18 |
MXPA02012187A (en) | 2004-08-19 |
PL359000A1 (en) | 2004-08-23 |
BR0111337A (en) | 2003-06-17 |
AU7750401A (en) | 2001-12-03 |
RU2002134472A (en) | 2004-05-27 |
AU774150B2 (en) | 2004-06-17 |
CN1438952A (en) | 2003-08-27 |
WO2001089901A1 (en) | 2001-11-29 |
FR2809067B1 (en) | 2002-08-09 |
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