EP0419599A1 - Frein a disque pour vehicules automobiles - Google Patents

Frein a disque pour vehicules automobiles

Info

Publication number
EP0419599A1
EP0419599A1 EP90903155A EP90903155A EP0419599A1 EP 0419599 A1 EP0419599 A1 EP 0419599A1 EP 90903155 A EP90903155 A EP 90903155A EP 90903155 A EP90903155 A EP 90903155A EP 0419599 A1 EP0419599 A1 EP 0419599A1
Authority
EP
European Patent Office
Prior art keywords
housing
brake
disc
disc brake
holder
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Withdrawn
Application number
EP90903155A
Other languages
German (de)
English (en)
Inventor
Rudolf Thiel
Ulrich Klimt
Hans Bungert
Ludwig Dreilich
Helmut Kast
Hinrich Hornbostel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ITT Automotive Europe GmbH
Original Assignee
ITT Automotive Europe GmbH
Alfred Teves GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19893906713 external-priority patent/DE3906713A1/de
Priority claimed from DE19904002955 external-priority patent/DE4002955A1/de
Application filed by ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Publication of EP0419599A1 publication Critical patent/EP0419599A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/22655—Constructional details of guide pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0975—Springs made from wire
    • F16D65/0976—Springs made from wire acting on one pad only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/002—Brake calipers assembled from a plurality of parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/005—Brakes straddling an annular brake disc radially internally
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/026—Braking members; Mounting thereof characterised by a particular outline shape of the braking member, e.g. footprint of friction lining

Definitions

  • the invention relates to a disc brake for motor vehicles, consisting of a movable brake housing (housing) encompassing the brake disc with a saddle shape, with a hydraulic actuation unit for the brake pads, and a holding element (holder) for the housing, the holder with a part the suspension is connected.
  • a disc brake housing includes a brake carrier and a brake housing.
  • the spring bracket is mounted with its one end section in the brake carrier, which has two brake carrier arms which are connected to one another via a connecting web. After the brake pad has been pushed in, the spring clip is folded down so that it comes to rest on the brake pad with a partial section. The other end section of the spring clip is then inserted under the connecting web. For assembly, the spring clip must therefore be pressed down at least as far in the direction of the brake pad, since the other free end is inserted under the connecting web who can. In some cases, considerable assembly forces have to be brought up.
  • This type of disc brake which is used in particular in modern high-performance passenger cars, has the advantage of increasing the effective radius and reducing the thermal load.
  • German Offenlegungsschrift 35 08 039 already provides an internally encompassing disc brake, in particular for motor vehicles, with a brake disc which is supported on its outer edge, a stationary brake carrier, a brake housing which is axially displaceably mounted on the brake carrier by means of a bolt guide can be actuated by means of an actuating device which encompasses the inner edge of the brake disc, with two radially extending legs and a substantially axially extending bridge section connecting them, a first brake lining which is arranged on one side of the brake disc in the brake carrier and is supported and can be acted upon directly by the actuating device, and a second brake lining, which is arranged and supported on the other side of the brake disc on the brake housing and can be acted upon by the relevant leg of the housing.
  • the pin guide has a support pin designed as a fixed bearing, which absorbs all essential circumferential forces which are transmitted from the second brake pad via the brake housing to the guide and which is fixed to the brake carrier or the brake housing is connected and engages in a guide bore in the brake housing or in the brake carrier, and in that the support pin in the area of the radial extension of the Brake disc is arranged.
  • the invention is based on the following objects:
  • a space-saving solution for the brake is to be found.
  • the installation space specified by the vehicle manufacturer should be used consistently.
  • the radially outer connecting web, which is designated by the reference number 50 in the aforementioned publication, is to be omitted. It is also a task to increase the effective radius of the brake even more than in the prior art and to reduce the thermal load on the brake to an even greater extent than in the prior art.
  • the brake is said to be more compact overall.
  • the tendency to rub and noise should be reduced.
  • the entire concept should become more service-friendly. It should be possible to carry out a simple lining removal and a simple brake disc change without dismantling the caliper.
  • the piston-side, that is, the inner lining is to be a drawn lining, which creates favorable conditions for the transmission of the high tangential forces that occur during braking.
  • a partial-pad disc brake is to be specified in which the inner brake pad can be mounted and sprung more easily.
  • the claw should be full and not in the form of fingers.
  • a fully designed claw has the advantage of noise reduction because of the material accumulation.
  • the holder should be easier to edit than before.
  • the invention is intended to create better conditions for casting the housing.
  • conditions are to be created in such a way that complex milling operations for the production of the lining support are superfluous.
  • the pane assembly should be simplified. Specifically, this means that the outlet-side lining support on the holder should be eliminated, so that the disk can be threaded better during assembly. At the same time it is achieved that the use of thicker covering materials is possible.
  • support and guide elements are provided which support and guide the housing on the one hand and on the other directly on a part of the wheel suspension, such as steering knuckles, swivel bearings, bypassing the holder.
  • support and / or guide elements between the housing comprising the floating caliper and a piston-cylinder unit on the one hand and the holder on the other hand and between the housing on the one hand and an un indirect part of the wheel suspension are provided on the other hand.
  • the housing is connected to the holder, in particular on the inlet side of the brake, by means of a support bearing and is preferably connected directly to part of the wheel suspension by means of a floating bearing in the region of the outlet side of the brake.
  • the housing is pivotally connected to the holder by the support bearing and that the floating bearing is designed as a support member between the housing and part of the wheel suspension and prevents the pivoting movements of the housing.
  • a special embodiment of the invention is that the wheel suspension has a guide part, in particular a bolt or a sleeve, on which the housing is guided and / or supported in the form of a floating bearing.
  • the wheel suspension has a guide bore in which the housing is guided and / or supported in the form of a bearing, in particular by a bolt-shaped or sleeve-shaped one.
  • the floating bearing have an elastic bushing, in particular a rubber bushing, which is arranged as a damping element between the housing and the wheel suspension.
  • a direct dissipation of the tangential force, which is applied to the inner lining during braking, is achieved in that the inner lining is provided directly next to the support bearing with a supporting surface for the peripheral force and is supported on the holder.
  • the lining back plate of the inner lining which is subjected to tensile forces during braking, is designed with an L-shaped hammer head which engages in a corresponding recess in the holder.
  • a support surface is provided on the housing, which prevents the inner lining from pivoting radially inward, and is preferably located in the area of the brake outlet.
  • the outer covering be provided with a covering back plate which has two support stops arranged on the side of the claw of the fist.
  • the housing be made in two parts, that the separating surface be arranged parallel to the friction surfaces of the brake disc and in the region of the open side of the cup-shaped cylinder of the piston-cylinder unit is.
  • the special division of the housing ensures that no separate component has to be used as the cylinder bottom, as is the case with the subject of the above. German OS, see there Fig. 2, is necessary.
  • the installation of a floor as a separate component is very expensive.
  • the claw can be made full and thus noise-damping in the subject matter of the invention. This was made possible by dividing the housing. So far, the claw consisted of two fingers. The recess between the fingers was required in the prior art in order to be able to produce the piston bore. The full claw also gives the housing greater rigidity. Further details of the invention can be found in the following description of an exemplary embodiment of the invention.
  • the spring clip is mounted in the housing at two points, which are adjacent but have a predetermined distance from one another.
  • the end sections of this spring clip move around different pivot points and are braced against one another.
  • the spring now tries to compensate for this tension by moving into a rest position. There are two stable resting positions, namely one above the dead center level and another below the dead center level. If the spring clip is pivoted away from the brake pad, it assumes a stable mounting position when it is pivoted beyond the dead center plane. In this position, the brake pad can be installed and removed unhindered by the spring clip. After installing or reinstalling the brake pad, the spring clip only has to be pivoted towards the brake pad up to just above the dead center plane.
  • the dead center As soon as the dead center has been exceeded, ie as soon as the spring clip has been pivoted through the dead center plane, it tries to compensate for the tension again and to assume a stable position again. It comes to rest with a predetermined area on the brake pad and secures it against falling out and keeps it rattle-free.
  • the assembly of the brake pad is considerably simplified by the springing according to the invention.
  • the spring clip does not have to be dismantled when the brake pads are changed, but only folded over. This requires relatively little effort.
  • the spring clip does not have to be replaced when changing the pad.
  • the spring clip positions itself when swiveling into the holding position, ie when it is folded down, so that incorrect assembly after a brake pad change is not possible. Finally, the process of releasing the spring clip from the brake pad only takes a short time, which also speeds up the assembly.
  • the dead center plane advantageously encloses a predetermined angle with the central axis of the brake pad.
  • the two fastening points are arranged horizontally and vertically offset from one another, if one assumes that the central axis of the brake lining lies in the horizontal or vertical. This can be ensured in a simple manner that sufficient spring force always acts on the brake pad.
  • the ends of the end sections run essentially perpendicular to the longitudinal extension of the spring clip and are inserted into housing bores. No additional brackets are required because the The spring clip is adequately fastened by the pretension in the housing bores. To mount the spring clip, the end sections can simply be inserted into the housing bores.
  • housing bores perpendicular to the brake disc i.e. run parallel to the axial direction of the brake disc.
  • the housing bores have no special requirements with regard to machining or tolerance. They lie in the main machining direction, which greatly simplifies the manufacture of the disc brake.
  • the ends of the end sections are advantageously introduced into the housing from opposite sides, part of one end engaging over the housing.
  • the housing must of course not exceed a certain thickness in order not to make the spring too large.
  • the spring can, however, be arranged in the connecting web between the brake carrier arms. This special arrangement further increases security against accidental loss of the spring clip.
  • the axial movement, i.e. the movement of the spring clip in the direction of the brake disc or away from it is limited so much by this arrangement that the two ends are reliably held in the housing bores.
  • the part of the end that crosses the housing forms a stop for the spring clip lifted off the brake lining and limits the pivoting movement to a predetermined angle.
  • the sum of the lengths of the ends which are introduced into the housing should be more than 80% of the thickness of the housing at this point.
  • the spring clip must then be deformed relatively strongly in order to remove the ends from the housing.
  • the end of the end section spanning the housing can be made shorter than the other end because the other end has no direct securing means and can therefore be removed more easily.
  • the end sections are advantageously offset from one another perpendicular to the brake disc. This prevents the end sections from blocking each other when the spring clip is pivoted, thereby making movement of the spring clip more difficult.
  • the end sections in the area of the spring clip tip, at which they are connected to one another are bent in a direction that is essentially perpendicular to the brake disc. This ensures that the spring clip holds the brake pad securely even when the Brake pad is permanently positioned closer to the brake disc after heavy wear.
  • the fastening points are advantageously arranged in a housing casting. There is a little more space available here to mount the spring clip.
  • FIG. 1 shows a floating caliper disc brake which grips the brake disc radially from the inside outwards in a view radially from the outside inwards
  • FIG. 2 is a sectional view along the section line II-II of FIG. 1,
  • FIG. 3 shows the brake according to FIG. 1 in an axial view from the center of the vehicle to the outside
  • Fig. 4 is a sectional view corresponding to the cutting line
  • Fig. 7 is a disc brake.
  • FIG. 10 shows a section X-X according to FIG. 9.
  • the dash-dotted line 1 in FIG. 1 represents the axis of an element belonging to the wheel suspension. It is shown as point 1 in FIGS. 2 and 3.
  • the element of the wheel suspension can be, for example, the part of a screw bolt connection.
  • the dash-dotted line 2 of FIG. 1 also represents the axis of a part of the wheel suspension. It is shown as point 2 in FIGS. 2 and 3.
  • This part of the wheel suspension can, as shown in FIGS. 5 and 6, be designed as a bolt 3 or as a sleeve 4 which belongs to a floating bearing.
  • An axis perpendicular to the plane of the drawing is represented by a point 5 in FIGS. 2 and 3. It deals around the axis of a part belonging to the wheel suspension, for example a screw connection.
  • the parts arranged in positions 1 and 5, for example screw bolt connections, serve to fasten the brake holder 6 to parts of the wheel suspension which are not shown. It can be knuckle elements or the elements of a pivot bearing.
  • the dash-dotted line 2 of FIGS. 1 and 4, or their punctiform illustration in FIGS. 2 and 3, represents the axis of the floating bearing 7.
  • the physical configuration of the floating bearing is in FIGS. 5 and 6, which are described in more detail below.
  • the brake housing is designated, which, as can be seen in particular from FIG. 4, is fist-shaped.
  • the fist is open in the radially outward direction and includes the brake disk 9.
  • the fully formed claw of the fist which lies outside in relation to the center of the vehicle, is designated by 10.
  • 11 denotes the inner bridge of the housing.
  • the cylinder of the housing is designated by 12.
  • the hydraulically actuated piston 13 is located within the cylinder. When the pressure chamber 14 is pressurized, the piston moves to the left in the direction of the arrow 15 and displaces the brake lining 16 against the brake disk 9.
  • the lining 16 is thus pressed against the brake disk 9 by the direct action of the piston, while the lining 19 arranged on the left is shifted to the right and pressed against the rotating disk 9 by the reaction force described above via the displacement of the housing to the right becomes, which leads to deceleration.
  • the inner covering arranged on the right consists of covering material 20 and the back plate 21.
  • the outer covering arranged on the left consists of the back plate 22 and the covering material 23.
  • the brake disc is designed as a ventilated brake disc. It has a cast body which is provided with channels, one of which is visible in FIG. 4 and designated by 24. When the disc rotates, an air flow is generated radially outward through the channels, which is used for heat dissipation.
  • the brake disc 9, which is normally made of cast iron, is connected to a steel body 25.
  • the Stahl ⁇ body is attached to the wheel in a known manner. The wheel is schematically indicated by the rim base 26.
  • the housing is made in two parts: a bridge and Claw part 27 and a cylinder part 28. With 29 the interface of the two parts of the housing is designated.
  • the two housing halves are connected to one another by the screw bolts 30, 31, 32, 33.
  • the holder is firmly connected to the wheel suspension, such as the steering knuckle or the pivot bearing, by the screw bolts in positions 1 and 5.
  • the housing 8 is pivotally connected to the holder 6 by a support bearing 34.
  • the axis of the support bearing is designated 35.
  • the support bearing can consist of a bolt which is fixed in the housing by means of an interference fit and which can move axially in the holder (sliding fit).
  • the arrangement can also consist of an interference fit in the holder and a sliding seat in the housing.
  • the tendency of the housing to pivot relative to the holder occurs when the brake pads are pressed against the brake disc and a force occurs in the tangential direction.
  • the position of the imaginary central point of application of the tangential forces on the linings and the position of the axis of the support bearing are selected so that the housing has a pivoting tendency counterclockwise in the direction of arrow 37.
  • FIGS. 5 and 6 Two exemplary embodiments for the floating bearing are shown in FIGS. 5 and 6.
  • the bolt 3 is screwed into a part 38 of the wheel suspension.
  • a housing eye 39 is provided on the housing 8.
  • Bolt 3 and housing eye 39 form the floating bearing.
  • An elastic bushing 40 is attached between the housing eye and the bolt.
  • the eye 39, or the housing, is arranged axially sliding on the bolt 3.
  • Fig. 6 is an alternative to Fig. 5.
  • a sleeve 4 is fixedly connected to a part 42 of the wheel suspension.
  • the elastic bushing 44 is located between the eye 43 of the housing and the sleeve 4.
  • the eye 43, or the housing, is arranged on the sleeve 4 in an axially sliding manner.
  • Axial displacement of the housing on the support bearing 34 is also possible.
  • a bellows 45 is provided to seal the support bearing 34, in particular when the housing moves axially on the holder.
  • the housing is thus slidably arranged on parts of the holder and directly on parts of the wheel suspension.
  • the floating bearing prevents the housing from rotating about the axis of the support bearing.
  • the floating bearing also compensates for manufacturing tolerances.
  • the braking force of the inner lining is absorbed directly by the holder.
  • the braking force of the outer lining is conducted via the housing to the support bearing on the inlet side.
  • the connecting web which was necessary in the prior art, see OS 35 08 039 and bears the reference number 50 there, is omitted in the present invention.
  • the brake according to the invention offers good conditions for simple and quick installation in the vehicle.
  • the guidance and support of the piston-side, that is to say the inner lining is carried out by an L-shaped hammer head.
  • the hammer head bears the reference number 46.
  • the inner lining 16 is advantageously a drawn lining, that is to say the high forces occurring during braking are transmitted directly from the hammer head to the holder, specifically in the area of the disc brake inlet directly next to the support bearing , or carrying bolt.
  • the radial lining support of the inner lining is carried out by a stop 47 provided in the brake outlet on the housing bridge 11.
  • the outer covering 19 is supported by two support lugs 48, 49 attached to the back plate 22 of the covering. - 19 -
  • Protrusions are provided for the radial fixation of the outer covering, one of which is denoted by 50 in FIG. 2. These projections protrude into recesses 41 in the claw 10. Furthermore, a pad holding device 51 with a spring is provided, which presses the outer pad radially inward and thus secures the pad.
  • the R "ückenplatte 21 of the inner pad includes a tab 52 which is bent in the Topf syndromem the cup-shaped piston 13 in. With 53 the level of the end surface of the nose is designated, which projects into the Topf Hurm, and is greater than the clearance In this way, the nose 52 serves to secure the inner lining against loss in the event that the spring 54 breaks.
  • the spring 54 serves as a holding and depressing member for the inner lining 16.
  • the spring 54 see FIG. 2, presses on the lining in the direction of the arrow 55 and thus keeps it rattling free on its support surface.
  • the positions of the pivot axes 56, 57 of the retaining spring and their configuration are selected such that a pretension is generated in the direction of arrow 55.
  • the outer covering is supported tangentially via two support lugs 48, 49 located on the side of the fist or claw.
  • the force applied to the outer covering in the tangential direction is thus transmitted to the housing.
  • the force is transferred from the housing to the support bearing and from there to the holder.
  • the holder is firmly connected to the wheel suspension.
  • the power is transferred from the holder to the wheel suspension.
  • a disc brake 201 has a housing, which includes, among other things, a brake housing 202 and a brake carrier 203.
  • the disc brake 201 also has a brake disc 2o4 against which the brake linings 205, 206 can be moved with the aid of an actuating device 207.
  • the direction of movement of the brake linings 205, 206 in the direction of the brake disk 204 is referred to below as the axial direction.
  • the brake carrier 203 has two brake carrier arms 208, 209 which are connected to one another via a connecting web 210, so that the brake carrier 203 as a whole has a has a genetic shape.
  • the brake carrier 203 can be connected to a steering knuckle (not shown) of a vehicle via three bores 211, 212, 213.
  • the brake lining 205 is received in a shaft 214 which is delimited in the circumferential direction by support surfaces 215, 216.
  • the brake lining 205 has shoulders or shoulders 229 which rest on corresponding support surfaces 230 of the brake carrier.
  • the movement of the brake pad 205 in the radial direction away from the support surface 230 is limited by a spring clip 217 which has two end sections 218, 219 which are connected to one another at a tip 220. While the end sections 218, 219 of the spring clip run essentially parallel to the brake disk 204, the tip 220 of the spring clip 217, to which the end sections 218, 219 are connected to one another, is bent in the axial direction. The tip lies on a projection 231 of the brake lining 205. The tip 220 of the spring clip 217 extends over a predetermined length, so that even when the brake pad 205 moves in the axial direction as a result of pad wear, the brake pad 205 is always covered by the spring clip 217.
  • the end sections 218, 219 each have temple ends 221, 222.
  • the bow end 221 of the end section 218 is simply bent over in the axial direction.
  • Section 219 of the spring clip 217 is first bent upward in a plane parallel to the brake disk 204, then bent into a section 223 overlapping the connecting web 210 in the axial direction and finally bent through 180 °, so that the end of the clip end 222 also Axial direction is aligned.
  • the two end faces of the spring clip are thus practically opposite to each other.
  • two bores 224, 225 are provided in the connecting web, into which the two clip ends 221, 222 are inserted from opposite sides.
  • the temple ends 221, 222 are so long that the sum of their lengths, which are located in the holes 224, 225, is greater than 80% of the housing thickness, i.e. the thickness of the connecting bar 210 at this point. This ensures that the spring clip 217 cannot be accidentally removed from the housing.
  • the bracket end 222 is shorter than the bracket end 221. This is possible because the end section 219 overlaps the connecting web 210 and is thus already secured.
  • the two bores 224, 225 are arranged in the axial direction. They are offset in the horizontal and vertical directions with respect to a central axis 227 of the brake pad 205.
  • the two bores 224, 225 lie in a dead center plane 26, which forms an angle 228 with the central axis 227.
  • the section overlapping the connecting web 210 secures the spring clip 217 against folding too far.
  • the spring clip 217 positions itself when it is closed, ie when pivoting in the direction of the brake pad itself, so that neither incorrect assembly after changing the pad nor loss of the Spring clip 217 is possible.
  • the pretensioning of the spring clip 217 also causes the clip ends 221, 222 to be braced in the bores 224, 225, so that the spring clip is reliably fastened in the bores 224, 225.
  • the end sections 218, 219 of the spring clip 217 are offset from one another in the axial direction. This ensures that they do not interfere with each other when the spring clip 217 is pivoted in the direction of the arrow 232. Rather, they can be guided past one another.
  • FIGS. 7 and 8 show a further embodiment of the disk brake, in which parts which correspond to those in FIGS. 7 and 8 are provided with reference numerals reduced by 100.
  • the spring clip 217 is no longer fastened directly in the connecting web 210, but in a sprue 234 which is arranged on the connecting web 110 in the radial direction on the outside. This results in greater freedom in the design of the fastening of the spring clip.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

Frein à disque pour véhicules automobiles, dont le disque de frein est enveloppé radialement du côté intérieur par un boîtier de frein en forme de poing. Les éléments d'appui et de guidage du boîtier consistent en un palier de support (34) et un palier libre (7). Le palier de support (34) relie le boîtier (8) avec l'élément de fixation (6). Le boîtier pivote autour du palier de support. Le boîtier s'appuie sur le palier libre, qui consiste en une tige (3) qui est directement et fermement reliée avec la suspension de la roue (38). Grâce à cette invention et à l'idée astucieuse d'agencer le palier libre directement sur la suspension de la roue et de supporter la garniture tangentiellement dans la zone d'entrée, on obtient une utilisation optimale de l'espace disponible, en particulier dans le sens radial, on augmente le rayon effectif et on réduit la contrainte thermique qui s'exerce sur le frein.
EP90903155A 1989-03-03 1990-02-16 Frein a disque pour vehicules automobiles Withdrawn EP0419599A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19893906713 DE3906713A1 (de) 1989-03-03 1989-03-03 Scheibenbremse fuer kraftfahrzeuge
DE3906713 1989-03-03
DE19904002955 DE4002955A1 (de) 1990-02-01 1990-02-01 Teilbelag-scheibenbremse
DE4002955 1990-02-01

Publications (1)

Publication Number Publication Date
EP0419599A1 true EP0419599A1 (fr) 1991-04-03

Family

ID=25878381

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90903155A Withdrawn EP0419599A1 (fr) 1989-03-03 1990-02-16 Frein a disque pour vehicules automobiles

Country Status (5)

Country Link
US (1) US5193652A (fr)
EP (1) EP0419599A1 (fr)
JP (1) JPH03504410A (fr)
KR (1) KR920700362A (fr)
WO (1) WO1990010162A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19653029A1 (de) * 1996-12-19 1998-06-25 Teves Gmbh Alfred Bolzenführung für eine Schwimmsattel-Teilbelagscheibenbremse
US7299903B2 (en) * 2006-01-25 2007-11-27 Kelsey-Hayes Company Symmetric brake clip
DE102006050647A1 (de) * 2006-10-24 2008-04-30 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse, insbesondere für ein Nutzfahrzeug
DE102011118736B4 (de) * 2011-11-17 2015-02-05 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug sowie Bremsbelag für eine Scheibenbremse
EP4257839A1 (fr) * 2022-04-06 2023-10-11 ZF CV Systems Europe BV Dispositif de frein et véhicule, en particulier véhicule utilitaire

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
US3424277A (en) * 1967-05-03 1969-01-28 Ford Motor Co Inside caliper disc brake
DE1928991C3 (de) * 1969-06-07 1981-06-25 Alfred Teves Gmbh, 6000 Frankfurt Bremsbackenhalterung für Scheibenbremsen
FR2174383A5 (fr) * 1972-03-02 1973-10-12 Dba
FR2245227A5 (fr) * 1973-04-19 1975-04-18 Dba
DE2802006C3 (de) * 1978-01-18 1981-02-12 Filterwerk Mann & Hummel Gmbh, 7140 Ludwigsburg Kniehebelverschluß für Ansaugluftfilter von Brennkraftmaschinen, Kompressoren und sonstigen luftansaugenden Maschinen
JPS55132532U (fr) * 1979-03-13 1980-09-19
JPS5740128A (en) * 1980-08-20 1982-03-05 Tokico Ltd Disc brake
US4352414A (en) * 1980-12-01 1982-10-05 Rockwell International Corporation Friction pad and support for a disc brake
JPS5863593A (ja) * 1981-09-26 1983-04-15 曽　俊雄 スクリ−ンパイプ効果式プロペラノ−ズル
DE3149883A1 (de) * 1981-12-16 1983-06-23 Alfred Teves Gmbh, 6000 Frankfurt Schwimmsattel-teilbelagscheibenbremse
DE3515418A1 (de) * 1985-04-29 1986-10-30 Alfred Teves Gmbh, 6000 Frankfurt Innen umgreifende scheibenbremse, insbesondere fuer kraftfahrzeuge
DE3539602A1 (de) * 1985-11-08 1987-05-14 Teves Gmbh Alfred Innenumgreifende scheibenbremse, insbesondere fuer kraftfahrzeuge
DE3906713A1 (de) * 1989-03-03 1990-09-06 Teves Gmbh Alfred Scheibenbremse fuer kraftfahrzeuge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9010162A1 *

Also Published As

Publication number Publication date
US5193652A (en) 1993-03-16
JPH03504410A (ja) 1991-09-26
KR920700362A (ko) 1992-02-19
WO1990010162A1 (fr) 1990-09-07

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