US20030121736A1 - Master cylinder lever for a hydraulic disc brake having a backpack reservoir - Google Patents
Master cylinder lever for a hydraulic disc brake having a backpack reservoir Download PDFInfo
- Publication number
- US20030121736A1 US20030121736A1 US10/316,452 US31645202A US2003121736A1 US 20030121736 A1 US20030121736 A1 US 20030121736A1 US 31645202 A US31645202 A US 31645202A US 2003121736 A1 US2003121736 A1 US 2003121736A1
- Authority
- US
- United States
- Prior art keywords
- reservoir
- cylinder
- port
- master cylinder
- lever
- 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.)
- Abandoned
Links
Images
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
- B60T7/00—Brake-action initiating means
- B60T7/02—Brake-action initiating means for personal initiation
- B60T7/08—Brake-action initiating means for personal initiation hand actuated
- B60T7/10—Disposition of hand control
- B60T7/102—Disposition of hand control by means of a tilting lever
-
- 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
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/22—Master control, e.g. master cylinders characterised by being integral with reservoir
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
- B62L3/00—Brake-actuating mechanisms; Arrangements thereof
- B62L3/02—Brake-actuating mechanisms; Arrangements thereof for control by a hand lever
- B62L3/023—Brake-actuating mechanisms; Arrangements thereof for control by a hand lever acting on fluid pressure systems
Definitions
- the present invention is directed toward an improved master cylinder lever for a hydraulic disc brake, and more particularly to a reservoir configuration preventing air from entering timing or compensating ports of the master cylinder.
- Known master cylinder levers for hydraulic disc brakes are designed for mounting on either a right handlebar or a left handlebar, but not both.
- Right and left specific master cylinder levers requires manufacturers to have two sets of tooling, which increases manufacturing costs and the complexity of the manufacturing process.
- bicycle manufacturers and lever suppliers must order sufficient right and left master cylinder levers to meet their needs and must maintain inventories of both right and left specific levers which increases stocking requirements over what would be required if a single lever could be deployed on the right or left handlebar.
- Buckley U.S. Pat. No. 6,003,639.
- Buckley teaches an inner cylindrical body within which a piston is axially aligned. A sidewall of the cylindrical body is surrounded by a bladder to define a fluid reservoir surrounding the cylindrical body. This structure substantially prevents air from entering the timing port or the compensating port regardless of the orientation of the master cylinder assembly, however, the structure shown in Buckley is expensive and difficult to manufacture.
- the present invention is intended to overcome one or more of the problems discussed above.
- a first aspect of the present invention is a master cylinder for a bicycle hydraulic disc brake.
- the master cylinder includes a cylinder wall defining a cylinder interior and a cylinder exterior.
- a piston is received within the cylinder interior.
- a port resides between the cylinder wall and a reservoir for providing fluid communication between the reservoir and the cylinder interior.
- a structure is provided within the reservoir for preventing any air bubbles within the hydraulic fluid from entering the port regardless of the orientation of the master cylinder.
- the reservoir may be defined in part by a portion of the cylinder exterior.
- the structure for preventing air from entering the port is preferably a protrusion extending into the reservoir, with the port being located on the protrusion.
- the port is preferably located on an apex of the protrusion.
- the reservoir may be defined in part by an elastomeric diaphragm. Extensions may be provided adjacent the port to prevent the elastomeric diaphragm from blocking the port.
- the portion of the cylinder exterior defining part of the reservoir is preferably a convex surface and the port is preferably located at an apex of the convex surface.
- a second aspect of the present invention is a hydraulic fluid reservoir for use with a master cylinder.
- the master cylinder includes a cylinder in fluid communication with the reservoir.
- the reservoir consists of a first wall and a sidewall extending from the first wall.
- An elastomeric diaphragm forming a flexible wall is attached to the sidewall opposite the first wall, with the first wall, the sidewall and the flexible wall cooperating to define an interior of the reservoir.
- a port provides fluid communication between the reservoir interior and the cylinder.
- the port has a reservoir opening in the reservoir interior located in one of the first wall and the sidewall, with the one of the first wall and the sidewall being configured to extend into the reservoir interior, thereby locating the reservoir opening at a position in the reservoir interior preventing an air bubble within the hydraulic fluid in the reservoir from entering the reservoir port, regardless of the orientation of the reservoir.
- the master cylinder lever of the present invention provides a unique “backpack” reservoir which prevents air from entering the cylinder of the master cylinder regardless of the orientation of the master cylinder. Thus, it eliminates the risk of air entering the cylinder and inhibiting brake performance in the event of storing the bicycle in an unintended orientation or an accidental tipping or tumble of the bicycle.
- the backpack reservoir facilitates construction of a symmetric lever which may be disposed on either the right or left handlebar of a bicycle without concern for enabling air to enter the cylinder. This has the further advantages of simplifying manufacturing and limiting the stocking requirements of both bicycle manufacturers and wholesale and retail distributors of master cylinder levers.
- FIG. 1 is a perspective view of a first embodiment of a master cylinder lever for a hydraulic disc brake in accordance with the present invention
- FIG. 2 is an exploded view of the backpack reservoir of the master cylinder lever of FIG. 1;
- FIG. 3 is a cross-section of the master cylinder lever of FIG. 1 taken along line 3 - 3 of FIG. 1;
- FIG. 4 is an exploded view of the piston train of the master cylinder lever of FIG. 1;
- FIG. 5 is an exploded perspective view of a socket receptacle spaced from a lever handle of the master cylinder lever of FIG. 1;
- FIG. 6 is an exploded view of the lever handle attachment assembly of the master cylinder lever of FIG. 1;
- FIG. 7 is a side elevation view of the master cylinder lever of FIG. 1;
- FIG. 8 is a cross-section of the master cylinder lever of FIG. 1 taken along line 8 - 8 of FIG. 7, illustrating an adjustable lever pivot assembly
- FIG. 9 is an alternate embodiment of the adjustable lever pivot assembly of FIG. 8;
- FIG. 10 is a perspective view of a second embodiment of a master cylinder lever for a hydraulic disc brake in accordance with the present invention.
- FIG. 11 is an exploded view of the backpack reservoir of the master cylinder lever of FIG. 10;
- FIG. 12 is a cross-section of the master cylinder of FIG. 1 taken along line 12 - 12 of FIG. 1;
- FIG. 13 is an exploded view of the piston train of the master cylinder lever of FIG. 1;
- FIG. 14 is a perspective view of the push rod and threaded insert of the master cylinder lever of FIG. 10;
- FIG. 15 is a side elevation view of the master cylinder lever of FIG. 10;
- FIG. 16 is a schematic representation of the geometry of the lever of the present invention.
- FIG. 17A is a schematic representation of the geometry of a Brand B lever
- FIG. 17B is a schematic representation of the geometry of a Brand A lever
- FIG. 18 is a schematic representation of the geometry of a Brand C lever
- FIG. 19 is a schematic representation of the geometry of a Brand D lever
- FIG. 20 is a graph of additional force required from a user's finger (%) versus lever travel from an engagement point for several brands of hydraulic levers as compared to the lever of the present invention
- FIG. 21 is a graph of a percentage of power to a lever versus lever travel for the lever of the present invention versus several known levers;
- FIG. 22 is a plot of lever travel versus degrees deviation from perpendicular of finger force
- FIG. 23 is a cross-section of an alternate embodiment of the lever of FIG. 12;
- FIG. 24 is an exploded view of the lever of FIG. 23.
- FIG. 25 is a cross-section taken along line 24 - 24 of FIG. 23.
- a first embodiment of master cylinder lever assembly 10 is illustrated in a perspective view in FIG. 1.
- the master cylinder lever assembly consists generally of a cylinder housing 12 having a bar clamp 14 at one end and a lever handle 16 pivotably attached at an opposite end.
- a reservoir cover 18 which covers a “backpack” reservoir which will be described in greater detail below.
- a contact point adjustment knob 20 which is also described in greater detail below.
- the master cylinder housing 12 is hydraulically connected to a slave cylinder which operates a hydraulic caliper (not shown) by hydraulic line 22 .
- FIG. 2 is an exploded view of the “backpack” reservoir of the master cylinder lever of FIG. 1.
- the backpack reservoir consists of a reservoir chamber 28 defined in a rear facing portion of the master cylinder housing 12 .
- a cylinder wall 30 defining in part the cylinder of the master cylinder housing 12 extends into the reservoir chamber 28 and defines in part a first wall 31 .
- Extending through the cylinder wall between the reservoir chamber 28 and the master cylinder is a timing port 32 and a compensating port 34 .
- a pair of bosses 36 extend axially of the cylinder wall 30 on opposite sides of the timing and compensating port 32 , 34 .
- a side wall 37 extends from the first wall.
- a diaphragm 38 made of an elastomeric material such as silicon rubber is made to overlay the side wall 37 and cover the reservoir chamber 28 .
- the diaphragm 38 has an expansion protrusion 40 extending therefrom opposite the reservoir chamber.
- a reservoir frame 42 is configured to receive the periphery of the diaphragm 38 to maintain a tight seal between the diaphragm 38 and the reservoir chamber 28 . This seal is promoted and the assembled relationship maintained by four screws 44 received in corner holes of the reservoir frame 42 and diaphragm 38 and threadably engaged with corresponding holes in the master cylinder housing 12 .
- a vanity cover 46 snap fits over the diaphragm and frame to both provide an aesthetic appearance and to protect the diaphragm 38 .
- Locating the timing and compensating ports 32 , 34 on the cylinder wall 30 as illustrated in FIG. 2 essentially eliminates the possibility of air entering either of the timing or compensating ports regardless of the position of the master cylinder. As should be apparent to one skilled in the art, this is because air will always rise and the curved surface of the cylinder wall always cause air bubbles to be deflected away from the timing and compensating ports regardless of the position of the master cylinder.
- the cylinder wall 30 is truly cylindrical, it could also have other configurations such as a triangular configuration with the ports located at the apex of the triangle which would have the same affect of preventing air bubbles from collecting in the vicinity of the timing or compensating ports. Any other profile of the cylinder wall or location of the ports on the cylinder wall which prevents collecting of air bubbles in the vicinity of the timing and compensating ports is considered to be within the scope of the invention.
- the bosses 36 are provided to prevent the diaphragm 38 from covering and inadvertently sealing the compensation or timing ports as hydraulic fluid is drawn into the compensating and timing ports.
- bosses 36 could be replaced with similarly positioned posts or the like or-other extensions to perform the same function of keeping the diaphragm spaced from the ports and such other configurations may have an additional advantage of minimizing the potential of air bubbles collecting in the vicinity of the ports.
- This structure facilitates a single lever being used on either a right or left portion of a handle bar without risk of bubbles entering the hydraulic fluid line.
- FIG. 3 a cross-section of the master cylinder, illustrates the piston train 49 operatively associated with the cylinder 50 of the master cylinder housing 12 .
- the cylinder 50 has a first end 51 and a second end 52 .
- FIG. 4 illustrates the piston train 49 in an exploded view and the same reference numbers will be used to identify like elements in FIG. 3 and FIG. 4.
- the piston train consists of a piston 54 received in the cylinder 50 having an annular cup or umbrella seal 56 abutting an internal portion of the piston 54 .
- a compression spring 60 biases the piston 54 toward the first or open end of the cylinder 51 .
- An “O” ring 62 forms a lower seal on the piston and is received within an annular recess in the piston.
- a hex spacer 64 has leading protrusion 66 with an annular detent that is snap fit into a corresponding female receptacle 68 in a trailing end of the piston 54 . This snap fit allows for relative rotational movement between the piston and the hex spacer 64 .
- the hex spacer 64 is in turn received in a hex hole 70 of contact point adjustment knob 20 .
- the knob 20 also has a leading externally threaded extension 72 which threadably engages a countersink 74 concentric with and external of the cylinder 50 .
- a male pushrod 76 having an externally threaded shaft 78 at its first end and a ball head 80 at its second end with posts 82 extending in opposite directions therefrom is snap fit received in a slotted socket 84 on an end opposite the protrusion 66 of the hex spacer 64 with the post 82 received in the slots 86 , as best seen in FIG. 3.
- the male pushrod 76 in turn is threadably engaged with a female pushrod 86 having an internally threaded cylinder 88 , again best viewed in FIG. 3.
- the female pushrod also includes a ball head 90 having oppositely extending posts 92 .
- a socket insert 94 has a leading ball socket 96 with opposite slots 98 for snap fit receiving the ball head 90 with the posts 92 received in the corresponding slots 98 .
- the socket insert 94 also includes locking posts 100 . Referring to FIG. 5, these locking posts are received within a keyed orifice 102 in the lever handle 16 and then rotated 90° to lock the posts 100 in the annular slot 104 .
- a dust cover 106 which is preferably elastomeric, is engaged in an annular slot 108 of the knob 20 with a nipple end receiving the female pushrod 86 as shown.
- the distance between the cup seal 56 and the timing port 32 is referred to as the “dead-band.”
- the cup seal is between the timing port 32 and the first end of the cylinder
- fluid in the reservoir between the seal and the timing port returns to the reservoir chamber 30 , perhaps causing expansion of the expansion protrusion 40 of the diaphragm 38 .
- the second end of the cylinder cannot be pressurized. It is highly desirable to be able to adjust the length of the dead-band in accordance with user preferences. Rotation of the contact point adjustment knob 20 in a first direction allows for the dead-band to be taken up and reduced and rotation in a second direction increases the dead-band. In FIG.
- a maximum dead-band is shown because the knob is almost fully threaded from the countersink 74 . Threading the knob into the countersink causes the piston to move upward, thus reducing the dead-band.
- the hex engagement between the hex spacer 64 and the knob 20 causes the hex spacer to rotate with the knob.
- the snap fit between the protrusion 66 and the female receptacle 68 of the piston prevents the piston from rotating relative to the knob, minimizing impairment of the seals.
- One highly advantageous aspect of this design is that as the knob is screwed inward in the first direction, the male pushrod rotates axially because of engagement between the posts 82 and the hex spacer.
- the threads between the male pushrod 76 and the female pushrod 86 are configured to cause the male pushrod to extend further from the female pushrod as a result of this axial rotation in the first direction.
- the respective threads of the knob and the pushrods are designed such that the net result is that the lever handle does not move relative to the housing as the knob is turned. This feature has the important advantage of maintaining a preselected start position of the lever resulting reach between the lever and the handlebar as the dead-band of the master cylinder is adjusted.
- FIG. 6 is an exploded view of the lever pivot assembly 110 of the first embodiment of the master cylinder lever of FIG. 1.
- the lever pivot assembly 110 consists of an axial bore 112 about which the lever handle 16 pivots.
- a threaded hole 114 perpendicularly intersects the bore 112 .
- a slotted bushing 116 (preferably made of plastic) which is part of a bushing plate 118 extends into each end of the bore 112 .
- a female bolt 120 is received through one slotted bushing while a male bolt 122 is received through the other slotted bushing so that they threadably engage within the bore 112 .
- the slotted bushings 116 each have annular camming tapers 124 between smaller and larger diameter portions of the bushing.
- a head of the female bolt 120 similarly has a camming taper which mates with the camming taper 124 of the bushing.
- the male bolt has a cammed surface which mates with a corresponding cammed surface of its corresponding bushing.
- a lock screw 130 is threadably received in the threaded hole 114 and, as illustrated in FIG. 8, can be threadably inserted in the hole to lock the male and female bolts in their select position. As the pivot wears the lock screw 130 can be backed off and the female and male bolts more tightly threadably engaged to pickup any slop.
- FIG. 9 is an alternate embodiment of the adjustable lever pivot assembly 110 ′.
- This embodiment differs in that the male bolt has a portion having an outer diameter equivalent to the outer diameter of the female bolt illustrated at 132 and the female bolt does not extend as far axially as the embodiment illustrated in FIG. 8.
- a gap 134 is provided between this enlarged diameter 132 of the male bolt 122 ′ and the female bolt 120 ′.
- the lock screw 130 directly engages each of the male bolt 122 and the female bolt 120 which may provide more secure locking although it may not provide as much axial adjustment from either end of the lever.
- FIG. 10 is a second embodiment of a master cylinder lever for a bicycle hydraulic disc brake 200 of the present invention.
- the second embodiment of the master cylinder lever assembly 200 consists of a cylinder housing 202 having a bar clamp 204 at one end and lever handle 206 pivotably attached to the housing at an opposite end.
- a reservoir housing 208 covers a hydraulic fluid reservoir 210 which will be discussed in greater detail below.
- a worm knob 212 used to adjust the lever dead-band in a manner that will be discussed in greater detail below.
- the master cylinder housing 202 is hydraulically connected to a slave cylinder which operates a hydraulic caliper (not shown) by hydraulic line 214 .
- FIG. 11 is an exploded view of a “backpack” reservoir of the master cylinder lever of FIG. 10.
- the backpack reservoir of FIG. 11 is identical in its configuration to the backpack reservoir of FIG. 2 except it is oriented substantially horizontally within the lever housing whereas the backpack reservoir of the first embodiment of the master cylinder lever of FIG. 1 is oriented vertically.
- the same reference numbers are used to describe like elements and the detailed description of these elements is provided above with reference to FIG. 2.
- FIG. 12 is a cross-section the master cylinder lever assembly of FIG. 10 taken along line 12 - 12 of FIG. 10.
- FIG. 12 illustrates a piston train 220 received within a cylinder 222 defined within the hydraulic cylinder housing 202 .
- the cylinder 222 has a first end 224 and a second end 226 .
- a threaded countersink 225 in the housing 202 abuts the second end 226 of the cylinder 222 , coaxial with a longitudinal axis of the cylinder.
- FIG. 13 illustrates the piston train 220 in an exploded view and the same reference numbers will be used to identify like elements in FIGS. 12 and 13.
- the piston train 220 consists of a piston 228 within the cylinder 222 .
- the piston 228 has a first annular cup or umbrella seal 230 near a leading end and a second annular cup or umbrella seal 232 near a trailing end.
- a push rod 234 has a threaded portion 236 at a first end and a head 238 at a leading second end. A leading portion of the head 238 defines a ball surface which is received in a corresponding cup surface 240 in a trailing end of the piston 220 .
- the threaded portion 236 of the push rod 234 is threadably engaged with the lever handle 206 in a manner that will be discussed in greater detail below.
- a hex orifice 241 is defined in the second end of the push rod and sized to fit an appropriate Allen wrench.
- a plurality of radial ribs 242 extend axially from a rear surface of the head 238 opposite the ball surface (see FIG. 14).
- An externally threaded insert 244 has an externally threaded leading axial portion 246 and a trailing axial portion 248 having radially inclined gear teeth which are best viewed in FIGS. 13 and 14.
- the threaded insert 244 further has an axial bore 250 having conical side walls.
- the bore 250 opens at the first end to an annular pocket 252 having axially extending teeth 254 configured to mate with the radial ribs 242 which extend axially from the rear surface of the head 238 (See FIG. 14).
- Externally threaded insert 424 further includes a rearward facing pocket 256 receiving an elastomeric annular wipe seal 257 having a nipple which forms a seal with the push rod 234
- a worm 258 is received in the housing along an axis transverse an axis of the cylinder.
- the worm 258 has a threaded shaft 259 and a worm knob 212 .
- the threads 259 of the threaded shaft threadably engage the radially inclined teeth 248 of the externally threaded insert 244 .
- a C-clamp (not shown) or the like secures the worm 258 within the transverse bore in the housing by engaging an annular groove 261 in the distal end of the threaded shaft 259 .
- a coil spring 262 resides between a second end 226 of the cylinder and a leading end of the piston 228 to bias the piston toward the first end 224 .
- the coil spring also compresses the radial ribs 242 of the push rod head 238 into mated engagement with the axially extending teeth 254 of the threaded insert 244 so the push rod 234 rotates axially as the threaded insert is rotated.
- the lever handle 206 may be pivotably attached to the housing by lever pivot assembly described above with reference to FIGS. 6 and 8. Alternatively, a conventional pivot coupling may be used. Spaced from the lever pivot assembly 110 , is a bore 264 in the lever along an axis parallel to the axis of the lever pivot assembly and transverse the axis of the cylinder 222 . A cross dowel 266 is received in the bore 264 . The cross dowel 266 includes a threaded bore 268 transverse the dowel axis. Referring to FIG. 12, this threaded bore 268 threadably receives the threaded portion 236 at the first end of the push rod 234 .
- the basic operation of the master cylinder lever 200 of FIG. 12 is similar to that of the first embodiment of the master cylinder lever 10 discussed above with reference to FIG. 3.
- the lever handle 206 is shown at a rest position in FIG. 12. As the lever is pivoted upward toward the bar clamp 204 and toward a fully actuated position, the push rod 234 is driven forward which in turn causes the piston 228 to move toward the second end 226 of the cylinder 222 .
- the leading cup or umbrella seal 230 covers the timing port 34 which prevents flow of fluid from the cylinder into the reservoir and causes build up of pressure in the second end of the hydraulic fluid cylinder which in turn pressurizes fluid within the hydraulic fluid line 22 and which in turn actuates a slave cylinder within a hydraulically coupled brake caliper (not shown).
- the compressing spring 262 biases the piston 228 toward the first end 224 of the cylinder to reassume the position shown in FIG. 12. Pivoting of the push rod 234 about the head 238 by pivoting of the lever handle 206 is accommodated by the conical side walls of the axial base 250 .
- the distance between the cup seal 230 and the timing port 32 is referred to as the dead-band.
- the dead-band As described above with reference to FIG. 3, during the part of lever actuation where the cup seal is between the timing port 32 and the first end of the cylinder, fluid in the reservoir between the seal and the timing port returns to the reservoir 30 .
- the second end of the cylinder cannot be pressurized.
- the piston can be advanced in the cylinder by rotating the knob 264 in a first direction which in turn causes rotation of the threaded insert to threadably advance the threaded insert within the threaded countersink 225 along the cylinder axis, thereby advancing the piston toward the second end of the cylinder.
- knob 212 in a second direction reverses the direction of the threaded insert to increase the dead-band.
- the ball and socket connection between the cup 240 at the trailing end of the piston and the ball at the leading end of the head 238 of the push rod 234 prevents the piston from rotating relative to the threaded insert which helps maintain the integrity of the seals.
- the second embodiment of the hydraulic cylinder lever of FIG. 12 also includes a structure for compensating for movement of the push rod during dead-band adjustment to maintain the lever 206 in a select rest position.
- the threads between the threaded portion 236 of the push rod and the threaded bore 268 of the cross dowel 266 are configured to counteract pivoting of the handle that would otherwise occur about the lever pivot assembly 110 when the push rod 234 is moved by movement of the threaded insert 244 .
- the threaded insert 244 is relatively fixed against rotation, turning of the push rod 234 causes disengagement between the radially extending ribs 242 of the head 238 and the complimentary axially extending teeth 254 in the externally threaded insert against the bias of the spring 262 and allows for pivotal movement of the lever handle 206 up or down in accordance with user preferences to provide a select reach.
- the teeth 254 and ribs 242 preferably have inclined, mating surfaces which define ramps facilitating this disengagement against the force of the bias of the spring 262 . Disengagement can be aided by pushing axially on the Allen wrench against the spring bias as the push rod 234 is rotated.
- the axis of the threaded bore in the cross dowel is provided to not intersect with the cross dowel axis. This has the effect of locking the push rod in place relative to the cross dowel when a load is placed on the lever handle 206 so as to prevent relative rotation between the push rod 234 and the cross dowel 236 . This feature thereby prevents inadvertent variation of the lever reach during lever actuation. An off-set of between 0.01-0.04 inches between the axes has been found to be sufficient.
- FIG. 15 is a side elevation view of a master cylinder lever of FIG. 10. This figure is used to illustrate an embodiment of a lever geometry which has been found to provide significant advantages in lever operation.
- the bar clamp 204 is designed to receive a handle bar 280 along a clamp axis 282 .
- the lever handle 206 is pivotably connected by lever pivot assembly 110 about a pivot axis 284 . In a highly preferred embodiment, the pivot axis is 39 mm from the clamp axis.
- the lever handle 206 defines a finger receptacle 286 configured to receive at least one finger of a user. In the embodiment illustrated in FIG.
- the finger receptacle 286 is configured to receive two fingers of a user and effective finger force point 288 is defined by approximately the center of a typical user's two fingers.
- effective finger force point 288 is defined by approximately the center of a typical user's two fingers.
- the location of the finger force point is deemed to be 30.0 mm from the end of the lever when based on an estimate of an average user's finger size.
- a select finger actuation path is defined by arrow 290 , and extends from the effective finger force point 288 at an “engagement point” of the lever.
- the “engagement point” means a point along the arc of lever actuation where the pads of a caliper operatively associated with the master cylinder lever begin compressing a disc therebetween.
- the select ideal finger actuation path 290 is a design criteria intended to estimate a typical finger path of a user of the brake in typical operating conditions. Based upon observations of users, the select ideal finger actuation path is at an angle ⁇ 90° or greater. In FIG. 15 the angle ⁇ is 96°, a best estimate of a typical average finger path. Actual finger paths may range from 90°-108°, or even greater than 108°.
- An arc 292 is defined by movement of the effective force point 288 as a lever is actuated between the engagement point position shown in FIG. 15 and a fully actuated position with the effective force point 288 at point 288 ′ in FIG. 15.
- the pivot axis 284 is preferably spaced from the clamp axis 282 a distance such that a chord between the points 288 and 288 ′ of the arc 292 substantially corresponds to the select ideal finger actuation path 290 .
- a user experiences a mechanical advantage resulting from handle actuation that does not substantially decrease as the handle is pivoted between the at rest position and the fully actuated position.
- the angle of the chord between the point 288 and 288 ′ could actually be slightly less than the angle ⁇ , but should be no less than 6° less than the angle ⁇ so as to prevent an unacceptable loss of mechanical advantage.
- the desired chord defined by the arc between the rest position and the fully actuated position of the effective finger force point is able to meet the criteria of substantially corresponding to an ideal finger actuation path in the range of greater than 96° if the pivot axis 284 can be brought close enough to the clamp axis 282 .
- this geometry is facilitated by locating the reservoir 208 and the cylinder 222 of the master cylinder lever housing generally to the clamp axis 282 , and the pivot 39 mm from the clamp axis. Where the master cylinder is aligned vertically as with the first embodiment illustrated in FIGS.
- FIGS. 16 - 19 illustrate the geometry of a highly preferred embodiment of the present invention as compared to representative hydraulic master cylinder levers on the market in 2002 .
- FIG. 17A is a Brand B lever geometry.
- FIG. 17B is a Brand A lever geometry.
- FIG. 18 is a Brand C lever geometry.
- FIG. 19 is a lever geometry of a Brand D hydraulic brake lever.
- the pivot axis 284 is 39 mm from the clamp axis 282 .
- the engagement point is 50 mm from the clamp axis 282 , and is illustrated by the line 300 .
- the application of braking force from the engagement point to the conclusion of the lever movement is assumed to be 10 mm and is represented by the full actuation line 302 .
- the assumed ideal finger actuation pad 290 is an angle ⁇ 96° from the clamp axis.
- the effective finger force point 288 is 30 mm from the bar end.
- the arc 304 represents the effective finger force point travel as the lever is actuated.
- a chord drawn between the engagement line where the effective finger force point is located at the beginning of brake actuation and the point that the full actuation line 302 intersects the arc 304 is at 96°, equal to the ideal finger path angle ⁇ . This provides for a minimal loss of mechanical advantage as the lever is actuated.
- the Brand B lever has a pivot axis 284 53 mm from the clamp axis 282 .
- the arc 304 of travel of the effective finger force point 208 deviates inwardly from the ideal finger path 290 .
- FIG. 17B where the Brand A lever pivot axis is 50 mm from the clamp axis 282 . As will be illustrated in the figures discussed below, this results in an increasing loss of mechanical advantage over the lever stroke.
- FIGS. 18 and 19 represent the geometry of the Brand C and Brand D hydraulic brake levers respectively. Like numbers are used to identify like elements of these figures. Brand C, with the pivot axis located 63 mm from the clamp axis has a more pronounced deviation of the arc 304 from the ideal finger path 209 and thus, as will be illustrated below, has even a greater loss of mechanical advantage than the Brand B lever. Finally, the Brand D levers, with a pivot point 65 mm from the clamp axis, produces an even greater loss of mechanical advantage.
- FIGS. 20 and 21 illustrate the respective mechanical advantage of the lever geometry of the present invention, designated as Avid, and the Brands A-D illustrated schematically above.
- Avid the geometry of Brands A-D levers each will result in applying an additional amount of force to the lever along the ideal finger path over the course of the lever actuation.
- Avid lever of the present invention it can be seen that the geometry actually produces an increasing mechanical advantage over the first 5 mm of lever travel and then a slight decrease of mechanical advantage (less than 1%) over the final 5 mm of lever travel. Over the full range of lever travel, a net loss of mechanical advantage is zero.
- FIG. 21 is essentially the inverse of FIG. 20. It illustrates that the geometries of the Brand A-D levers result in a loss of power over the actuation stroke. Again, the Avid lever of the present invention actually provides improved power through the first 5 mm with slightly decreasing power over the final 5 mm of travel and no change in the net amount of power applied to the lever between the engagement point and full actuation of the lever.
- FIG. 22 illustrates where the loss of power comes from by comparing how far from perpendicular to the clamp axis the finger force is over the lever actuation stroke.
- the force begins 5 mm off, goes to perpendicular at about the center of the stroke and then returns to 5 mm off at the conclusion of the stroke.
- Brands A-D a significant deviation from perpendicular is present at the beginning of the stoke and increases from there.
- the Avid lever geometry provides an increasing range of mechanical advantage over at least a portion of the lever actuation.
- the present invention can be characterized as the selection of a lever geometry having a pivot axis of 50 mm or less that is always equal to or closer to the clamp axis than the engagement point.
- This geometry produces a lever having an increasing mechanical advantage over at least a portion of the actuation stroke but does not encompass the geometry of the Brand A lever which is believed to be the lever having the pivot axis the closest to the clamp axis known in the art.
- FIG. 23 is a cross-section of an alternate embodiment of the drive train of a master cylinder.
- the piston and cylinder of the embodiment of FIG. 23 is essentially identical to that of the embodiment of FIG. 12, and like reference numbers followed by a prime (′) are used for like elements and described above in detail with respect to FIG. 12.
- the primary difference in the structures begins to the right of the surface 240 ′ in the trailing end of the piston 220 , which in FIG. 23 is flat as opposed to a cup surface.
- FIG. 23 has push rod 400 having a threaded portion 402 at a first end and head 404 at a second end.
- the head 404 has a bore receiving a pin 406 transverse the axis of the pushrod 400 .
- the head 404 is received in a socket 408 within a piston coupling 410 having a leading flat surface 412 abutting the cup 240 ′.
- the piston coupling 410 has axial slots 414 which receive the pins 406 to allow axial movement of the head 404 within the piston coupling 410 , but prevent axial rotation of the push rod 400 relative to the piston coupling 410 .
- the threaded portion 402 of the pushrod is threadably engaged with the lever handle 206 ′ in the same manner discussed above with respect to the embodiment of FIG. 12, including the off-center coupling with the cross-dowel.
- the piston coupling 410 has an annular flange 416 with sinusoidal florets 418 extending radially therefrom.
- An externally threaded insert 430 has an externally threaded leading axial portion 432 and a trailing axial portion 434 having radially inclined gear teeth which are best viewed in FIG. 24.
- Threaded insert 430 further has an axial bore 436 having sinusoidal florets 438 configured to mate with the sinusoidal florets 418 of the piston coupling 410 .
- An elastometric annular wipe seal 440 having a nipple 442 received in an annular groove 444 of the push rod 400 abuts the threaded insert 430 .
- the lever of FIG. 23 also includes a worm 258 ′ essentially identical to that of the embodiment discuss above with respect to FIG. 12 and which will not be re-described here.
- the pivot assembly 446 is similar to that described with reference to FIG. 12.
- the basic operation of the master cylinder of FIG. 23 is identical to that of the master cylinder lever 200 of FIG. 12 and this description will not be repeated.
- the embodiment of FIG. 23 shares the features of independent reach adjustment and a dead-band adjustment that compensates for and prevents change of the reach adjustment during dead-band adjustment and is not re-described here.
- the reach adjustment differs slightly from the embodiment discussed above with respect to FIG. 12.
- insertion of an Allen wrench into a hex socket 448 allows for reach adjustment.
- Axial rotation of the push rod by an Allen wrench will cause indexed axial rotation of the piston coupling 410 relative to the threaded insert 430 .
- the threaded insert 430 is prevented from axial rotation by the worm 258 ′.
- each indexed rotation of the push rod causes a uniform movement of the lever end relative to the clamp axis (e.g., 1 mm).
- the mating florets are illustrated in FIG. 25 in a cross-section taken along line 25 - 25 of FIG. 23.
- the embodiment of FIG. 23 also includes a feature to protect the piston train in the event of an accident causing movement of the lever handle 206 away from the clamp axis.
- the head 404 of the push rod can axially disengage from the socket 408 of the piston coupling in a direction to the right. Once a user recovers from such a mishap, the lever can be simply returned to its normal rest position which will cause the head 404 to pop back into the socket 408 .
Abstract
A master cylinder for a bicycle hydraulic disc brake includes a cylinder wall defining a cylinder interior and a cylinder exterior. A piston is received within the cylinder interior. A reservoir for hydraulic fluid is defined in part by a portion of the cylinder exterior, the portion of the cylinder exterior protruding into the reservoir. A port through the portion of the cylinder exterior which protrudes into the reservoir provides fluid communication between the reservoir and the cylinder interior. The port is located on the portion of the cylinder exterior which protrudes into the reservoir at a position which prevents air bubbles within the reservoir from entering the port.
Description
- This application claims priority from U.S. Provisional Patent Application Serial Nos. 60/344,450, filed Dec. 28, 2001; 60/416,130, filed Oct. 4, 2002; and 60/416,698, filed Oct. 7, 2002, each entitled “Master Cylinder Lever for Hydraulic Disc Brake”
- The present invention is directed toward an improved master cylinder lever for a hydraulic disc brake, and more particularly to a reservoir configuration preventing air from entering timing or compensating ports of the master cylinder.
- Known master cylinder levers for hydraulic disc brakes are designed for mounting on either a right handlebar or a left handlebar, but not both. Right and left specific master cylinder levers requires manufacturers to have two sets of tooling, which increases manufacturing costs and the complexity of the manufacturing process. In addition, bicycle manufacturers and lever suppliers must order sufficient right and left master cylinder levers to meet their needs and must maintain inventories of both right and left specific levers which increases stocking requirements over what would be required if a single lever could be deployed on the right or left handlebar.
- An additional problem with most prior art master cylinder levers is the reservoir for hydraulic fluid can allow bubbles within the reservoir to enter the timing or compensation ports if the master cylinder and associated reservoir attain some undesired orientation. One known solution to the problem of air entering the timing or compensation ports is shown in Buckley, U.S. Pat. No. 6,003,639. Buckley teaches an inner cylindrical body within which a piston is axially aligned. A sidewall of the cylindrical body is surrounded by a bladder to define a fluid reservoir surrounding the cylindrical body. This structure substantially prevents air from entering the timing port or the compensating port regardless of the orientation of the master cylinder assembly, however, the structure shown in Buckley is expensive and difficult to manufacture.
- The present invention is intended to overcome one or more of the problems discussed above.
- A first aspect of the present invention is a master cylinder for a bicycle hydraulic disc brake. The master cylinder includes a cylinder wall defining a cylinder interior and a cylinder exterior. A piston is received within the cylinder interior. A port resides between the cylinder wall and a reservoir for providing fluid communication between the reservoir and the cylinder interior. A structure is provided within the reservoir for preventing any air bubbles within the hydraulic fluid from entering the port regardless of the orientation of the master cylinder. The reservoir may be defined in part by a portion of the cylinder exterior. The structure for preventing air from entering the port is preferably a protrusion extending into the reservoir, with the port being located on the protrusion. The port is preferably located on an apex of the protrusion. The reservoir may be defined in part by an elastomeric diaphragm. Extensions may be provided adjacent the port to prevent the elastomeric diaphragm from blocking the port. The portion of the cylinder exterior defining part of the reservoir is preferably a convex surface and the port is preferably located at an apex of the convex surface.
- A second aspect of the present invention is a hydraulic fluid reservoir for use with a master cylinder. The master cylinder includes a cylinder in fluid communication with the reservoir. The reservoir consists of a first wall and a sidewall extending from the first wall. An elastomeric diaphragm forming a flexible wall is attached to the sidewall opposite the first wall, with the first wall, the sidewall and the flexible wall cooperating to define an interior of the reservoir. A port provides fluid communication between the reservoir interior and the cylinder. The port has a reservoir opening in the reservoir interior located in one of the first wall and the sidewall, with the one of the first wall and the sidewall being configured to extend into the reservoir interior, thereby locating the reservoir opening at a position in the reservoir interior preventing an air bubble within the hydraulic fluid in the reservoir from entering the reservoir port, regardless of the orientation of the reservoir.
- The master cylinder lever of the present invention provides a unique “backpack” reservoir which prevents air from entering the cylinder of the master cylinder regardless of the orientation of the master cylinder. Thus, it eliminates the risk of air entering the cylinder and inhibiting brake performance in the event of storing the bicycle in an unintended orientation or an accidental tipping or tumble of the bicycle. In addition, the backpack reservoir facilitates construction of a symmetric lever which may be disposed on either the right or left handlebar of a bicycle without concern for enabling air to enter the cylinder. This has the further advantages of simplifying manufacturing and limiting the stocking requirements of both bicycle manufacturers and wholesale and retail distributors of master cylinder levers.
- FIG. 1 is a perspective view of a first embodiment of a master cylinder lever for a hydraulic disc brake in accordance with the present invention;
- FIG. 2 is an exploded view of the backpack reservoir of the master cylinder lever of FIG. 1;
- FIG. 3 is a cross-section of the master cylinder lever of FIG. 1 taken along line3-3 of FIG. 1;
- FIG. 4 is an exploded view of the piston train of the master cylinder lever of FIG. 1;
- FIG. 5 is an exploded perspective view of a socket receptacle spaced from a lever handle of the master cylinder lever of FIG. 1;
- FIG. 6 is an exploded view of the lever handle attachment assembly of the master cylinder lever of FIG. 1;
- FIG. 7 is a side elevation view of the master cylinder lever of FIG. 1;
- FIG. 8 is a cross-section of the master cylinder lever of FIG. 1 taken along line8-8 of FIG. 7, illustrating an adjustable lever pivot assembly;
- FIG. 9 is an alternate embodiment of the adjustable lever pivot assembly of FIG. 8;
- FIG. 10 is a perspective view of a second embodiment of a master cylinder lever for a hydraulic disc brake in accordance with the present invention;
- FIG. 11 is an exploded view of the backpack reservoir of the master cylinder lever of FIG. 10;
- FIG. 12 is a cross-section of the master cylinder of FIG. 1 taken along line12-12 of FIG. 1;
- FIG. 13 is an exploded view of the piston train of the master cylinder lever of FIG. 1;
- FIG. 14 is a perspective view of the push rod and threaded insert of the master cylinder lever of FIG. 10;
- FIG. 15 is a side elevation view of the master cylinder lever of FIG. 10;
- FIG. 16 is a schematic representation of the geometry of the lever of the present invention;
- FIG. 17A is a schematic representation of the geometry of a Brand B lever;
- FIG. 17B is a schematic representation of the geometry of a Brand A lever;
- FIG. 18 is a schematic representation of the geometry of a Brand C lever;
- FIG. 19 is a schematic representation of the geometry of a Brand D lever;
- FIG. 20 is a graph of additional force required from a user's finger (%) versus lever travel from an engagement point for several brands of hydraulic levers as compared to the lever of the present invention;
- FIG. 21 is a graph of a percentage of power to a lever versus lever travel for the lever of the present invention versus several known levers;
- FIG. 22 is a plot of lever travel versus degrees deviation from perpendicular of finger force;
- FIG. 23 is a cross-section of an alternate embodiment of the lever of FIG. 12;
- FIG. 24 is an exploded view of the lever of FIG. 23; and
- FIG. 25 is a cross-section taken along line24-24 of FIG. 23.
- A first embodiment of master
cylinder lever assembly 10 is illustrated in a perspective view in FIG. 1. The master cylinder lever assembly consists generally of acylinder housing 12 having abar clamp 14 at one end and alever handle 16 pivotably attached at an opposite end. Also seen in FIG. 1 is areservoir cover 18 which covers a “backpack” reservoir which will be described in greater detail below. Also visible in FIG. 1 is a contactpoint adjustment knob 20 which is also described in greater detail below. Themaster cylinder housing 12 is hydraulically connected to a slave cylinder which operates a hydraulic caliper (not shown) byhydraulic line 22. - FIG. 2 is an exploded view of the “backpack” reservoir of the master cylinder lever of FIG. 1. The backpack reservoir consists of a
reservoir chamber 28 defined in a rear facing portion of themaster cylinder housing 12. Acylinder wall 30 defining in part the cylinder of themaster cylinder housing 12 extends into thereservoir chamber 28 and defines in part afirst wall 31. Extending through the cylinder wall between thereservoir chamber 28 and the master cylinder is atiming port 32 and a compensatingport 34. A pair ofbosses 36 extend axially of thecylinder wall 30 on opposite sides of the timing and compensatingport side wall 37 extends from the first wall. Adiaphragm 38 made of an elastomeric material such as silicon rubber is made to overlay theside wall 37 and cover thereservoir chamber 28. Thus, thefirst wall 31, theside wall 37 and thediaphragm 38 define thereservoir chamber 28. Thediaphragm 38 has anexpansion protrusion 40 extending therefrom opposite the reservoir chamber. Areservoir frame 42 is configured to receive the periphery of thediaphragm 38 to maintain a tight seal between thediaphragm 38 and thereservoir chamber 28. This seal is promoted and the assembled relationship maintained by fourscrews 44 received in corner holes of thereservoir frame 42 anddiaphragm 38 and threadably engaged with corresponding holes in themaster cylinder housing 12. Avanity cover 46 snap fits over the diaphragm and frame to both provide an aesthetic appearance and to protect thediaphragm 38. Locating the timing and compensatingports cylinder wall 30 as illustrated in FIG. 2 essentially eliminates the possibility of air entering either of the timing or compensating ports regardless of the position of the master cylinder. As should be apparent to one skilled in the art, this is because air will always rise and the curved surface of the cylinder wall always cause air bubbles to be deflected away from the timing and compensating ports regardless of the position of the master cylinder. While in the preferred embodiment illustrated herein, thecylinder wall 30 is truly cylindrical, it could also have other configurations such as a triangular configuration with the ports located at the apex of the triangle which would have the same affect of preventing air bubbles from collecting in the vicinity of the timing or compensating ports. Any other profile of the cylinder wall or location of the ports on the cylinder wall which prevents collecting of air bubbles in the vicinity of the timing and compensating ports is considered to be within the scope of the invention. Thebosses 36 are provided to prevent thediaphragm 38 from covering and inadvertently sealing the compensation or timing ports as hydraulic fluid is drawn into the compensating and timing ports. As would be apparent to those skilled in the art, thebosses 36 could be replaced with similarly positioned posts or the like or-other extensions to perform the same function of keeping the diaphragm spaced from the ports and such other configurations may have an additional advantage of minimizing the potential of air bubbles collecting in the vicinity of the ports. This structure facilitates a single lever being used on either a right or left portion of a handle bar without risk of bubbles entering the hydraulic fluid line. - FIG. 3, a cross-section of the master cylinder, illustrates the
piston train 49 operatively associated with thecylinder 50 of themaster cylinder housing 12. Thecylinder 50 has afirst end 51 and asecond end 52. FIG. 4 illustrates thepiston train 49 in an exploded view and the same reference numbers will be used to identify like elements in FIG. 3 and FIG. 4. - The piston train consists of a
piston 54 received in thecylinder 50 having an annular cup orumbrella seal 56 abutting an internal portion of thepiston 54. Acompression spring 60 biases thepiston 54 toward the first or open end of thecylinder 51. An “O”ring 62 forms a lower seal on the piston and is received within an annular recess in the piston. Ahex spacer 64 has leadingprotrusion 66 with an annular detent that is snap fit into a correspondingfemale receptacle 68 in a trailing end of thepiston 54. This snap fit allows for relative rotational movement between the piston and thehex spacer 64. Thehex spacer 64 is in turn received in ahex hole 70 of contactpoint adjustment knob 20. Theknob 20 also has a leading externally threadedextension 72 which threadably engages acountersink 74 concentric with and external of thecylinder 50. Amale pushrod 76 having an externally threadedshaft 78 at its first end and aball head 80 at its second end withposts 82 extending in opposite directions therefrom is snap fit received in a slottedsocket 84 on an end opposite theprotrusion 66 of thehex spacer 64 with thepost 82 received in theslots 86, as best seen in FIG. 3. Themale pushrod 76 in turn is threadably engaged with afemale pushrod 86 having an internally threadedcylinder 88, again best viewed in FIG. 3. The female pushrod also includes aball head 90 having oppositely extending posts 92. Asocket insert 94 has a leadingball socket 96 withopposite slots 98 for snap fit receiving theball head 90 with theposts 92 received in the correspondingslots 98. Thesocket insert 94 also includes locking posts 100. Referring to FIG. 5, these locking posts are received within akeyed orifice 102 in thelever handle 16 and then rotated 90° to lock theposts 100 in theannular slot 104. Referring back to FIG. 3, adust cover 106, which is preferably elastomeric, is engaged in anannular slot 108 of theknob 20 with a nipple end receiving thefemale pushrod 86 as shown. - The basic operation of the master cylinder is well understood by those skilled in the art. Referring to FIG. 3, pivoting the lever handle16 upward from a rest position toward the cylinder housing causes the
piston train 50 to drive the piston upward within the cylinder. As the piston moves upward in the cylinder the cup orumbrella seal 56 covers thetiming port 32 which pressurizes the fluid within thehydraulic line 22 at the second end of the cylinder and which in turn actuates a slave cylinder within a hydraulically coupled brake caliper (not shown). When the lever handle 16 is released, thecompression spring 60 biases the piston toward the first end of the cylinder to reassume the position shown in FIG. 3. The distance between thecup seal 56 and thetiming port 32 is referred to as the “dead-band.” During the part of lever actuation where the cup seal is between the timingport 32 and the first end of the cylinder, fluid in the reservoir between the seal and the timing port returns to thereservoir chamber 30, perhaps causing expansion of theexpansion protrusion 40 of thediaphragm 38. During this part of lever actuation, the second end of the cylinder cannot be pressurized. It is highly desirable to be able to adjust the length of the dead-band in accordance with user preferences. Rotation of the contactpoint adjustment knob 20 in a first direction allows for the dead-band to be taken up and reduced and rotation in a second direction increases the dead-band. In FIG. 3 a maximum dead-band is shown because the knob is almost fully threaded from thecountersink 74. Threading the knob into the countersink causes the piston to move upward, thus reducing the dead-band. Obviously, the hex engagement between thehex spacer 64 and theknob 20 causes the hex spacer to rotate with the knob. However, the snap fit between theprotrusion 66 and thefemale receptacle 68 of the piston prevents the piston from rotating relative to the knob, minimizing impairment of the seals. - One highly advantageous aspect of this design is that as the knob is screwed inward in the first direction, the male pushrod rotates axially because of engagement between the
posts 82 and the hex spacer. The threads between themale pushrod 76 and thefemale pushrod 86 are configured to cause the male pushrod to extend further from the female pushrod as a result of this axial rotation in the first direction. The respective threads of the knob and the pushrods are designed such that the net result is that the lever handle does not move relative to the housing as the knob is turned. This feature has the important advantage of maintaining a preselected start position of the lever resulting reach between the lever and the handlebar as the dead-band of the master cylinder is adjusted. - In the event a user wishes to adjust the reach of the lever (that is, the distance between a handle bar and the lever at the rest position), this can be done independently of the dead-band adjustment by pivoting the handle away from the caliper housing to disengage the snap fit between the
ball head 90 and theball socket 96 of thesocket insert 94. Once disengaged, thefemale pushrod 86 maybe rotated about its axis to extend or retract the female pushrod relative to the male pushrod to adjust the reach as desired. While the current embodiment may allow adjustment in 180° increments, other configurations allowing smaller increments of variation or perhaps event infinite variation of the lever reach are within the possession of those skilled in the art and within the scope of the invention. - FIG. 6 is an exploded view of the
lever pivot assembly 110 of the first embodiment of the master cylinder lever of FIG. 1. Thelever pivot assembly 110 consists of anaxial bore 112 about which the lever handle 16 pivots. A threadedhole 114 perpendicularly intersects thebore 112. A slotted bushing 116 (preferably made of plastic) which is part of abushing plate 118 extends into each end of thebore 112. Afemale bolt 120 is received through one slotted bushing while amale bolt 122 is received through the other slotted bushing so that they threadably engage within thebore 112. As perhaps best seen in FIG. 8, the slottedbushings 116 each have annular camming tapers 124 between smaller and larger diameter portions of the bushing. A head of thefemale bolt 120 similarly has a camming taper which mates with thecamming taper 124 of the bushing. Likewise, the male bolt has a cammed surface which mates with a corresponding cammed surface of its corresponding bushing. Referring to FIG. 8, as should be apparent to one skilled in the art, as the male bolt is threaded into the female bolt in the assembled configuration, the cam relationship causes the bushings to expand radially as the bolts are drawn axially together. This causes any “slop” in the pivotal connection between the lever handle and the caliper housing to be taken up. Alock screw 130 is threadably received in the threadedhole 114 and, as illustrated in FIG. 8, can be threadably inserted in the hole to lock the male and female bolts in their select position. As the pivot wears thelock screw 130 can be backed off and the female and male bolts more tightly threadably engaged to pickup any slop. - FIG. 9 is an alternate embodiment of the adjustable
lever pivot assembly 110′. This embodiment differs in that the male bolt has a portion having an outer diameter equivalent to the outer diameter of the female bolt illustrated at 132 and the female bolt does not extend as far axially as the embodiment illustrated in FIG. 8. Agap 134 is provided between thisenlarged diameter 132 of themale bolt 122′ and thefemale bolt 120′. In this embodiment, thelock screw 130 directly engages each of themale bolt 122 and thefemale bolt 120 which may provide more secure locking although it may not provide as much axial adjustment from either end of the lever. - FIG. 10 is a second embodiment of a master cylinder lever for a bicycle
hydraulic disc brake 200 of the present invention. The second embodiment of the mastercylinder lever assembly 200 consists of acylinder housing 202 having abar clamp 204 at one end and lever handle 206 pivotably attached to the housing at an opposite end. Areservoir housing 208 covers ahydraulic fluid reservoir 210 which will be discussed in greater detail below. Also visible in FIG. 10 is aworm knob 212 used to adjust the lever dead-band in a manner that will be discussed in greater detail below. Themaster cylinder housing 202 is hydraulically connected to a slave cylinder which operates a hydraulic caliper (not shown) byhydraulic line 214. - FIG. 11 is an exploded view of a “backpack” reservoir of the master cylinder lever of FIG. 10. The backpack reservoir of FIG. 11 is identical in its configuration to the backpack reservoir of FIG. 2 except it is oriented substantially horizontally within the lever housing whereas the backpack reservoir of the first embodiment of the master cylinder lever of FIG. 1 is oriented vertically. The same reference numbers are used to describe like elements and the detailed description of these elements is provided above with reference to FIG. 2.
- FIG. 12 is a cross-section the master cylinder lever assembly of FIG. 10 taken along line12-12 of FIG. 10. FIG. 12 illustrates a
piston train 220 received within acylinder 222 defined within thehydraulic cylinder housing 202. Thecylinder 222 has afirst end 224 and asecond end 226. A threadedcountersink 225 in thehousing 202 abuts thesecond end 226 of thecylinder 222, coaxial with a longitudinal axis of the cylinder. FIG. 13 illustrates thepiston train 220 in an exploded view and the same reference numbers will be used to identify like elements in FIGS. 12 and 13. - The
piston train 220 consists of apiston 228 within thecylinder 222. Thepiston 228 has a first annular cup orumbrella seal 230 near a leading end and a second annular cup orumbrella seal 232 near a trailing end. Apush rod 234 has a threadedportion 236 at a first end and ahead 238 at a leading second end. A leading portion of thehead 238 defines a ball surface which is received in acorresponding cup surface 240 in a trailing end of thepiston 220. The threadedportion 236 of thepush rod 234 is threadably engaged with thelever handle 206 in a manner that will be discussed in greater detail below. Ahex orifice 241 is defined in the second end of the push rod and sized to fit an appropriate Allen wrench. A plurality ofradial ribs 242 extend axially from a rear surface of thehead 238 opposite the ball surface (see FIG. 14). An externally threadedinsert 244 has an externally threaded leadingaxial portion 246 and a trailingaxial portion 248 having radially inclined gear teeth which are best viewed in FIGS. 13 and 14. The threadedinsert 244 further has an axial bore 250 having conical side walls. The bore 250 opens at the first end to anannular pocket 252 having axially extendingteeth 254 configured to mate with theradial ribs 242 which extend axially from the rear surface of the head 238 (See FIG. 14). Externally threaded insert 424 further includes a rearward facingpocket 256 receiving an elastomeric annular wipeseal 257 having a nipple which forms a seal with thepush rod 234. - A
worm 258 is received in the housing along an axis transverse an axis of the cylinder. Theworm 258 has a threadedshaft 259 and aworm knob 212. Thethreads 259 of the threaded shaft threadably engage the radially inclinedteeth 248 of the externally threadedinsert 244. A C-clamp (not shown) or the like secures theworm 258 within the transverse bore in the housing by engaging anannular groove 261 in the distal end of the threadedshaft 259. - A
coil spring 262 resides between asecond end 226 of the cylinder and a leading end of thepiston 228 to bias the piston toward thefirst end 224. The coil spring also compresses theradial ribs 242 of thepush rod head 238 into mated engagement with theaxially extending teeth 254 of the threadedinsert 244 so thepush rod 234 rotates axially as the threaded insert is rotated. - The lever handle206 may be pivotably attached to the housing by lever pivot assembly described above with reference to FIGS. 6 and 8. Alternatively, a conventional pivot coupling may be used. Spaced from the
lever pivot assembly 110, is abore 264 in the lever along an axis parallel to the axis of the lever pivot assembly and transverse the axis of thecylinder 222. Across dowel 266 is received in thebore 264. Thecross dowel 266 includes a threadedbore 268 transverse the dowel axis. Referring to FIG. 12, this threaded bore 268 threadably receives the threadedportion 236 at the first end of thepush rod 234. - The basic operation of the
master cylinder lever 200 of FIG. 12 is similar to that of the first embodiment of themaster cylinder lever 10 discussed above with reference to FIG. 3. The lever handle 206 is shown at a rest position in FIG. 12. As the lever is pivoted upward toward thebar clamp 204 and toward a fully actuated position, thepush rod 234 is driven forward which in turn causes thepiston 228 to move toward thesecond end 226 of thecylinder 222. As thepiston 228 moves toward thesecond end 226 of thecylinder 222 the leading cup orumbrella seal 230 covers thetiming port 34 which prevents flow of fluid from the cylinder into the reservoir and causes build up of pressure in the second end of the hydraulic fluid cylinder which in turn pressurizes fluid within thehydraulic fluid line 22 and which in turn actuates a slave cylinder within a hydraulically coupled brake caliper (not shown). When the lever handle 16 is released, the compressingspring 262 biases thepiston 228 toward thefirst end 224 of the cylinder to reassume the position shown in FIG. 12. Pivoting of thepush rod 234 about thehead 238 by pivoting of thelever handle 206 is accommodated by the conical side walls of the axial base 250. - The distance between the
cup seal 230 and thetiming port 32 is referred to as the dead-band. As described above with reference to FIG. 3, during the part of lever actuation where the cup seal is between the timingport 32 and the first end of the cylinder, fluid in the reservoir between the seal and the timing port returns to thereservoir 30. During this part of lever actuation, the second end of the cylinder cannot be pressurized. To adjust the length of dead-band, the piston can be advanced in the cylinder by rotating theknob 264 in a first direction which in turn causes rotation of the threaded insert to threadably advance the threaded insert within the threadedcountersink 225 along the cylinder axis, thereby advancing the piston toward the second end of the cylinder. Turning of theknob 212 in a second direction reverses the direction of the threaded insert to increase the dead-band. The ball and socket connection between thecup 240 at the trailing end of the piston and the ball at the leading end of thehead 238 of thepush rod 234 prevents the piston from rotating relative to the threaded insert which helps maintain the integrity of the seals. - The second embodiment of the hydraulic cylinder lever of FIG. 12 also includes a structure for compensating for movement of the push rod during dead-band adjustment to maintain the
lever 206 in a select rest position. The threads between the threadedportion 236 of the push rod and the threaded bore 268 of thecross dowel 266 are configured to counteract pivoting of the handle that would otherwise occur about thelever pivot assembly 110 when thepush rod 234 is moved by movement of the threadedinsert 244. In other words, as the threadedinsert 244 is advanced toward the second end of the cylinder, which necessarily causes the advancement of thepush rod 234 toward the second end of the cylinder and which would normally cause the lever handle 206 to pivot upward, the threaded engagement between the second end of the push rod and the cross dowel tends to move the lever handle 206 downward in an amount that corresponds to what would be the upward movement so as to maintain the lever handle 206 at a select start position. - In the event a user wishes to adjust the reach of the lever, this can be done independently of the dead-band adjustment. Insertion of an Allen wrench into the
hex orifice 242 allows for axial rotation of thepush rod 234. However, the worm connection between the threadedinsert 244 and theworm 258 prevents rotation of the threadedinsert 244 by thepush rod 234. Because the threadedinsert 244 is relatively fixed against rotation, turning of thepush rod 234 causes disengagement between theradially extending ribs 242 of thehead 238 and the complimentary axially extendingteeth 254 in the externally threaded insert against the bias of thespring 262 and allows for pivotal movement of the lever handle 206 up or down in accordance with user preferences to provide a select reach. Theteeth 254 andribs 242 preferably have inclined, mating surfaces which define ramps facilitating this disengagement against the force of the bias of thespring 262. Disengagement can be aided by pushing axially on the Allen wrench against the spring bias as thepush rod 234 is rotated. - In a highly preferred embodiment, the axis of the threaded bore in the cross dowel is provided to not intersect with the cross dowel axis. This has the effect of locking the push rod in place relative to the cross dowel when a load is placed on the lever handle206 so as to prevent relative rotation between the
push rod 234 and thecross dowel 236. This feature thereby prevents inadvertent variation of the lever reach during lever actuation. An off-set of between 0.01-0.04 inches between the axes has been found to be sufficient. - FIG. 15 is a side elevation view of a master cylinder lever of FIG. 10. This figure is used to illustrate an embodiment of a lever geometry which has been found to provide significant advantages in lever operation. The
bar clamp 204 is designed to receive ahandle bar 280 along aclamp axis 282. The lever handle 206 is pivotably connected bylever pivot assembly 110 about apivot axis 284. In a highly preferred embodiment, the pivot axis is 39 mm from the clamp axis. The lever handle 206 defines afinger receptacle 286 configured to receive at least one finger of a user. In the embodiment illustrated in FIG. 15, thefinger receptacle 286 is configured to receive two fingers of a user and effectivefinger force point 288 is defined by approximately the center of a typical user's two fingers. For the purpose of this application and the charts and calculations herein, the location of the finger force point is deemed to be 30.0 mm from the end of the lever when based on an estimate of an average user's finger size. A select finger actuation path is defined byarrow 290, and extends from the effectivefinger force point 288 at an “engagement point” of the lever. As used herein, the “engagement point” means a point along the arc of lever actuation where the pads of a caliper operatively associated with the master cylinder lever begin compressing a disc therebetween. In other words, a point where the lever handle drives the piston train against operative fluid resistance. The select idealfinger actuation path 290 is a design criteria intended to estimate a typical finger path of a user of the brake in typical operating conditions. Based upon observations of users, the select ideal finger actuation path is at an angle θ 90° or greater. In FIG. 15 the angle θ is 96°, a best estimate of a typical average finger path. Actual finger paths may range from 90°-108°, or even greater than 108°. Anarc 292 is defined by movement of theeffective force point 288 as a lever is actuated between the engagement point position shown in FIG. 15 and a fully actuated position with theeffective force point 288 atpoint 288′ in FIG. 15. - In one embodiment of the invention illustrated in FIG. 15, the
pivot axis 284 is preferably spaced from the clamp axis 282 a distance such that a chord between thepoints arc 292 substantially corresponds to the select idealfinger actuation path 290. In this manner, a user experiences a mechanical advantage resulting from handle actuation that does not substantially decrease as the handle is pivoted between the at rest position and the fully actuated position. The angle of the chord between thepoint - The desired chord defined by the arc between the rest position and the fully actuated position of the effective finger force point is able to meet the criteria of substantially corresponding to an ideal finger actuation path in the range of greater than 96° if the
pivot axis 284 can be brought close enough to theclamp axis 282. In the embodiment illustrated in FIG. 15, this geometry is facilitated by locating thereservoir 208 and thecylinder 222 of the master cylinder lever housing generally to theclamp axis 282, and the pivot 39 mm from the clamp axis. Where the master cylinder is aligned vertically as with the first embodiment illustrated in FIGS. 1-5, it would be very difficult to meet these design criteria because the cylinder and reservoir reside between thepivot axis 284 and theclamp axis 282. This is illustrated in FIG. 7. Here, thearc 292′ defined by pivotal movement of the effectivefinger force point 288 from the engagement point to the fully actuatedposition 288′ defines a chord 294′ that forms an angle less than 90° from theclamp axis 282. However, the angle θ of the select ideal finger actuation path is greater than 90°, again preferably greater than 96°. As a result, a user would sustain a significant loss of mechanical advantage when trying to actuate the lever handle 206 along the select idealfinger actuation path 290′. - FIGS.16-19 illustrate the geometry of a highly preferred embodiment of the present invention as compared to representative hydraulic master cylinder levers on the market in 2002. FIG. 17A is a Brand B lever geometry. FIG. 17B is a Brand A lever geometry. FIG. 18 is a Brand C lever geometry. FIG. 19 is a lever geometry of a Brand D hydraulic brake lever.
- Beginning with FIG. 16, in a highly preferred embodiment of the present invention, the
pivot axis 284 is 39 mm from theclamp axis 282. For the purpose of this analysis, it is assumed that the engagement point is 50 mm from theclamp axis 282, and is illustrated by theline 300. The application of braking force from the engagement point to the conclusion of the lever movement is assumed to be 10 mm and is represented by thefull actuation line 302. Finally, for the purpose of this analysis, the assumed idealfinger actuation pad 290 is an angle θ 96° from the clamp axis. The effectivefinger force point 288 is 30 mm from the bar end. Thearc 304 represents the effective finger force point travel as the lever is actuated. A chord drawn between the engagement line where the effective finger force point is located at the beginning of brake actuation and the point that thefull actuation line 302 intersects thearc 304 is at 96°, equal to the ideal finger path angle θ. This provides for a minimal loss of mechanical advantage as the lever is actuated. - In FIG. 17A the Brand B lever has a
pivot axis 284 53 mm from theclamp axis 282. Again, assuming anengagement point 300 beginning 50 mm from the clamp axis and afull actuation line arc 304 of travel of the effectivefinger force point 208 deviates inwardly from theideal finger path 290. The same is true in FIG. 17B, where the Brand A lever pivot axis is 50 mm from theclamp axis 282. As will be illustrated in the figures discussed below, this results in an increasing loss of mechanical advantage over the lever stroke. - FIGS. 18 and 19 represent the geometry of the Brand C and Brand D hydraulic brake levers respectively. Like numbers are used to identify like elements of these figures. Brand C, with the pivot axis located 63 mm from the clamp axis has a more pronounced deviation of the
arc 304 from the ideal finger path 209 and thus, as will be illustrated below, has even a greater loss of mechanical advantage than the Brand B lever. Finally, the Brand D levers, with a pivot point 65 mm from the clamp axis, produces an even greater loss of mechanical advantage. - FIGS. 20 and 21 illustrate the respective mechanical advantage of the lever geometry of the present invention, designated as Avid, and the Brands A-D illustrated schematically above. Referring first to FIG. 20, the geometry of Brands A-D levers each will result in applying an additional amount of force to the lever along the ideal finger path over the course of the lever actuation. With respect to the Avid lever of the present invention, it can be seen that the geometry actually produces an increasing mechanical advantage over the first 5 mm of lever travel and then a slight decrease of mechanical advantage (less than 1%) over the final 5 mm of lever travel. Over the full range of lever travel, a net loss of mechanical advantage is zero.
- FIG. 21 is essentially the inverse of FIG. 20. It illustrates that the geometries of the Brand A-D levers result in a loss of power over the actuation stroke. Again, the Avid lever of the present invention actually provides improved power through the first 5 mm with slightly decreasing power over the final 5 mm of travel and no change in the net amount of power applied to the lever between the engagement point and full actuation of the lever.
- FIG. 22 illustrates where the loss of power comes from by comparing how far from perpendicular to the clamp axis the finger force is over the lever actuation stroke. For the geometry of the present invention (the Avid lever), the force begins 5 mm off, goes to perpendicular at about the center of the stroke and then returns to 5 mm off at the conclusion of the stroke. For Brands A-D, a significant deviation from perpendicular is present at the beginning of the stoke and increases from there.
- As is apparent, the Avid lever geometry provides an increasing range of mechanical advantage over at least a portion of the lever actuation. In its broadest sense, the present invention can be characterized as the selection of a lever geometry having a pivot axis of 50 mm or less that is always equal to or closer to the clamp axis than the engagement point. This geometry produces a lever having an increasing mechanical advantage over at least a portion of the actuation stroke but does not encompass the geometry of the Brand A lever which is believed to be the lever having the pivot axis the closest to the clamp axis known in the art.
- FIG. 23 is a cross-section of an alternate embodiment of the drive train of a master cylinder. The piston and cylinder of the embodiment of FIG. 23 is essentially identical to that of the embodiment of FIG. 12, and like reference numbers followed by a prime (′) are used for like elements and described above in detail with respect to FIG. 12. The primary difference in the structures begins to the right of the
surface 240′ in the trailing end of thepiston 220, which in FIG. 23 is flat as opposed to a cup surface. - The embodiment of FIG. 23 has
push rod 400 having a threadedportion 402 at a first end andhead 404 at a second end. Thehead 404 has a bore receiving apin 406 transverse the axis of thepushrod 400. Thehead 404 is received in asocket 408 within apiston coupling 410 having a leadingflat surface 412 abutting thecup 240′. Referring to FIG. 24, thepiston coupling 410 hasaxial slots 414 which receive thepins 406 to allow axial movement of thehead 404 within thepiston coupling 410, but prevent axial rotation of thepush rod 400 relative to thepiston coupling 410. The threadedportion 402 of the pushrod is threadably engaged with the lever handle 206′ in the same manner discussed above with respect to the embodiment of FIG. 12, including the off-center coupling with the cross-dowel. Thepiston coupling 410 has anannular flange 416 withsinusoidal florets 418 extending radially therefrom. An externally threadedinsert 430 has an externally threaded leadingaxial portion 432 and a trailingaxial portion 434 having radially inclined gear teeth which are best viewed in FIG. 24. Threadedinsert 430 further has an axial bore 436 havingsinusoidal florets 438 configured to mate with thesinusoidal florets 418 of thepiston coupling 410. An elastometric annular wipeseal 440 having anipple 442 received in anannular groove 444 of thepush rod 400 abuts the threadedinsert 430. - The lever of FIG. 23 also includes a
worm 258′ essentially identical to that of the embodiment discuss above with respect to FIG. 12 and which will not be re-described here. Likewise, thepivot assembly 446 is similar to that described with reference to FIG. 12. - The basic operation of the master cylinder of FIG. 23 is identical to that of the
master cylinder lever 200 of FIG. 12 and this description will not be repeated. The embodiment of FIG. 23 shares the features of independent reach adjustment and a dead-band adjustment that compensates for and prevents change of the reach adjustment during dead-band adjustment and is not re-described here. The reach adjustment differs slightly from the embodiment discussed above with respect to FIG. 12. In the embodiment of FIG. 23, insertion of an Allen wrench into ahex socket 448 allows for reach adjustment. Axial rotation of the push rod by an Allen wrench will cause indexed axial rotation of thepiston coupling 410 relative to the threadedinsert 430. The threadedinsert 430 is prevented from axial rotation by theworm 258′. Theaxial slots 414 allow disengagement and relative movement of the florets and axial rotation of thepiston coupling 410 relative to thepush rod 400 is prevented by thepins 406 received in theslots 414. In a preferred embodiment, each indexed rotation of the push rod causes a uniform movement of the lever end relative to the clamp axis (e.g., 1 mm). The mating florets are illustrated in FIG. 25 in a cross-section taken along line 25-25 of FIG. 23. - The embodiment of FIG. 23 also includes a feature to protect the piston train in the event of an accident causing movement of the lever handle206 away from the clamp axis. In such an event, the
head 404 of the push rod can axially disengage from thesocket 408 of the piston coupling in a direction to the right. Once a user recovers from such a mishap, the lever can be simply returned to its normal rest position which will cause thehead 404 to pop back into thesocket 408.
Claims (12)
1. A hydraulic fluid reservoir for use with a master cylinder, the master cylinder including a cylinder in fluid communication with the reservoir, the reservoir comprising:
a first wall;
a side wall extending from the first wall;
an elastomeric diaphragm forming a flexible wall attached to the side wall opposite the first wall, the first wall, the side wall and the flexible wall cooperating to define a reservoir interior;
a port providing fluid communication between the reservoir interior and the cylinder, the port having a reservoir opening in the reservoir interior, the reservoir opening being located in one of the first wall and side wall, with the one of the first wall and the side wall being configured to extend into the reservoir interior, thereby locating the reservoir opening at a position in the reservoir interior preventing an air bubble within hydraulic fluid in the reservoir from entering the reservoir port, regardless of the orientation of the master cylinder.
2. A master cylinder for a bicycle hydraulic disc brake comprising:
a cylinder wall defining a cylinder interior and a cylinder exterior;
a piston received within the cylinder interior;
a reservoir for hydraulic fluid;
a port between the reservoir and the cylinder wall providing fluid communication between the reservoir and the cylinder interior; and
means within the reservoir for preventing any air bubbles within the hydraulic fluid from entering the port regardless of the orientation of the master cylinder.
3. The master cylinder for a bicycle hydraulic disc brake of claim 2 further comprising the reservoir being defined in part by a portion of the cylinder exterior.
4. The master cylinder for a bicycle hydraulic disc brake of claim 2 where in the means for preventing air from entering the port comprises a protrusion extending into the reservoir, the port being located on the protrusion.
5. The master cylinder for a bicycle hydraulic disc brake of claim 4 wherein the port is located at an apex of the protrusion.
6. The master cylinder for a bicycle hydraulic disc brake of claim 2 wherein the reservoir comprises an elastomeric diaphragm, the master cylinder further comprising means within the reservoir for preventing the elastomeric diaphragm from blocking the port.
7. The master cylinder for a bicycle hydraulic disc brake of claim 4 wherein the reservoir comprises an elastomeric diaphragm, the master cylinder further comprising an extension adjacent the port configured to prevent the elastomeric diaphragm from blocking the port.
8. The master cylinder for a bicycle hydraulic disc brake of claim 3 wherein the means for preventing air from entering the port comprises the portion of the cylinder exterior defining part of the reservoir extending into the reservoir and the port being located on the portion of the cylinder exterior defining part of the reservoir.
9. The master cylinder for a bicycle hydraulic disc brake of claim 8 wherein the portion of the cylinder exterior defining part of the reservoir is a convex surface and the port is located at an apex of the convex surface.
10. A master cylinder for a bicycle hydraulic disc brake comprising:
a cylinder wall defining a cylinder interior and a cylinder exterior;
a piston received within the cylinder interior;
a reservoir for hydraulic fluid defined in part by a portion of the cylinder exterior, the portion of the cylinder exterior protruding into the reservoir; and
a port through the portion of the cylinder exterior which protrudes into the reservoir providing fluid communication between the reservoir and the cylinder interior, the port being located on the portion of the cylinder exterior which protrudes into the reservoir at a position to prevent air bubbles within the reservoir from entering the port.
11. The master cylinder for a bicycle hydraulic disc brake of claim 10 further comprising an elastomeric diaphragm defining in part the reservoir and an extension adjacent the port configured to prevent the diaphragm from blocking the port.
12. The master cylinder for a bicycle hydraulic disc brake of claim 10 wherein the portion of the cylinder exterior which protrudes into the reservoir is a convex surface and the port is located at an apex of the convex surface.
Priority Applications (15)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/316,452 US20030121736A1 (en) | 2001-12-28 | 2002-12-10 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
EP20020080490 EP1325863B1 (en) | 2001-12-28 | 2002-12-24 | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment |
DE2002605573 DE60205573T2 (en) | 2001-12-28 | 2002-12-24 | Hydraulic disc brake master cylinder with adjustment device actuatable during travel |
EP04077893.8A EP1498347B1 (en) | 2001-12-28 | 2002-12-24 | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment |
EP05076712.8A EP1595782B1 (en) | 2001-12-28 | 2002-12-24 | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment |
EP05076711.0A EP1595781B1 (en) | 2001-12-28 | 2002-12-24 | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment |
CA 2415101 CA2415101A1 (en) | 2001-12-28 | 2002-12-24 | Master cylinder lever for a hydraulic disc brake |
US10/966,737 US7178646B2 (en) | 2001-12-28 | 2004-10-15 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
US11/552,458 US7575105B2 (en) | 2001-12-28 | 2006-10-24 | Master cylinder lever with independently variable rest position and engagement point |
US11/737,509 US7559414B2 (en) | 2001-12-28 | 2007-04-19 | Symmetric master cylinder lever for a hydraulic disc brake |
US12/022,919 US20080116025A1 (en) | 2001-12-28 | 2008-01-30 | Symmetric Master Cylinder Lever for a Hydraulic Disc Brake II |
US12/147,272 US7617913B2 (en) | 2001-12-28 | 2008-06-26 | Method of varying a rest position and a length of an actuation arc of a lever in a hydraulic disc brake system |
US12/147,259 US8074774B2 (en) | 2001-12-28 | 2008-06-26 | Master cylinder lever with variable dead band and variable reach adjustment independent of the dead band adjustment |
US12/147,267 US7530435B2 (en) | 2001-12-28 | 2008-06-26 | Method and apparatus for adjusting a lever actuated hydraulic disc brake master cylinder |
US13/324,868 US8464845B2 (en) | 2001-12-28 | 2011-12-13 | Master cylinder lever for a bicycle hydraulic disc brake |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US34445001P | 2001-12-28 | 2001-12-28 | |
US41613002P | 2002-10-04 | 2002-10-04 | |
US41669802P | 2002-10-07 | 2002-10-07 | |
US10/316,452 US20030121736A1 (en) | 2001-12-28 | 2002-12-10 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/966,737 Continuation US7178646B2 (en) | 2001-12-28 | 2004-10-15 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
Publications (1)
Publication Number | Publication Date |
---|---|
US20030121736A1 true US20030121736A1 (en) | 2003-07-03 |
Family
ID=27502119
Family Applications (9)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/316,452 Abandoned US20030121736A1 (en) | 2001-12-28 | 2002-12-10 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
US10/966,737 Expired - Lifetime US7178646B2 (en) | 2001-12-28 | 2004-10-15 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
US11/552,458 Expired - Lifetime US7575105B2 (en) | 2001-12-28 | 2006-10-24 | Master cylinder lever with independently variable rest position and engagement point |
US11/737,509 Expired - Fee Related US7559414B2 (en) | 2001-12-28 | 2007-04-19 | Symmetric master cylinder lever for a hydraulic disc brake |
US12/022,919 Abandoned US20080116025A1 (en) | 2001-12-28 | 2008-01-30 | Symmetric Master Cylinder Lever for a Hydraulic Disc Brake II |
US12/147,259 Expired - Fee Related US8074774B2 (en) | 2001-12-28 | 2008-06-26 | Master cylinder lever with variable dead band and variable reach adjustment independent of the dead band adjustment |
US12/147,272 Expired - Fee Related US7617913B2 (en) | 2001-12-28 | 2008-06-26 | Method of varying a rest position and a length of an actuation arc of a lever in a hydraulic disc brake system |
US12/147,267 Expired - Fee Related US7530435B2 (en) | 2001-12-28 | 2008-06-26 | Method and apparatus for adjusting a lever actuated hydraulic disc brake master cylinder |
US13/324,868 Expired - Fee Related US8464845B2 (en) | 2001-12-28 | 2011-12-13 | Master cylinder lever for a bicycle hydraulic disc brake |
Family Applications After (8)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/966,737 Expired - Lifetime US7178646B2 (en) | 2001-12-28 | 2004-10-15 | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
US11/552,458 Expired - Lifetime US7575105B2 (en) | 2001-12-28 | 2006-10-24 | Master cylinder lever with independently variable rest position and engagement point |
US11/737,509 Expired - Fee Related US7559414B2 (en) | 2001-12-28 | 2007-04-19 | Symmetric master cylinder lever for a hydraulic disc brake |
US12/022,919 Abandoned US20080116025A1 (en) | 2001-12-28 | 2008-01-30 | Symmetric Master Cylinder Lever for a Hydraulic Disc Brake II |
US12/147,259 Expired - Fee Related US8074774B2 (en) | 2001-12-28 | 2008-06-26 | Master cylinder lever with variable dead band and variable reach adjustment independent of the dead band adjustment |
US12/147,272 Expired - Fee Related US7617913B2 (en) | 2001-12-28 | 2008-06-26 | Method of varying a rest position and a length of an actuation arc of a lever in a hydraulic disc brake system |
US12/147,267 Expired - Fee Related US7530435B2 (en) | 2001-12-28 | 2008-06-26 | Method and apparatus for adjusting a lever actuated hydraulic disc brake master cylinder |
US13/324,868 Expired - Fee Related US8464845B2 (en) | 2001-12-28 | 2011-12-13 | Master cylinder lever for a bicycle hydraulic disc brake |
Country Status (1)
Country | Link |
---|---|
US (9) | US20030121736A1 (en) |
Cited By (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050199450A1 (en) * | 2004-03-09 | 2005-09-15 | Campbell Darren J. | Lever assembly and master cylinder |
US20060185943A1 (en) * | 2005-02-18 | 2006-08-24 | Shimano, Inc. | Hydraulic disc brake lever assembly |
US20060185360A1 (en) * | 2005-02-18 | 2006-08-24 | Shimano Inc. | Hydraulic disc brake lever assembly |
US20070215416A1 (en) * | 2006-03-14 | 2007-09-20 | Jui-Pin Chen | Bicycle brake lever |
US20080155982A1 (en) * | 2006-12-28 | 2008-07-03 | Jones Christopher S | Hydraulic Brake Master Cylinder |
US20080245632A1 (en) * | 2007-04-03 | 2008-10-09 | Shimano Inc. | Bicycle hydraulic brake device |
US20090229927A1 (en) * | 2008-02-29 | 2009-09-17 | Cesare Brioschi | Breaking device |
US20100064838A1 (en) * | 2008-09-18 | 2010-03-18 | Shimano Components (Malaysia) Sdn Bhd | Reservoir tank for hydraulic brake lever assembly |
US8464845B2 (en) | 2001-12-28 | 2013-06-18 | Sram, Llc | Master cylinder lever for a bicycle hydraulic disc brake |
US20130255239A1 (en) * | 2012-03-30 | 2013-10-03 | Shimano Inc. | Bicycle hydraulic component operating device |
ITPD20120323A1 (en) * | 2012-10-31 | 2014-05-01 | Freni Brembo Spa | LEVER OPERATING DEVICE FOR BRAKES AND / OR CLUTCHES, IN PARTICULAR FOR MOTORCYCLES |
CN103895801A (en) * | 2012-12-26 | 2014-07-02 | 株式会社岛野 | Bicycle Control Device |
US20150266540A1 (en) * | 2014-03-24 | 2015-09-24 | Sram, Llc | Variable rate assembly for a brake system for bicycle |
US20150321725A1 (en) * | 2014-05-09 | 2015-11-12 | Shimano Inc. | Hydraulic operating device |
US20160200392A1 (en) * | 2015-01-12 | 2016-07-14 | Sram, Llc | Hydraulic Bicycle System |
US20160264213A1 (en) * | 2015-03-12 | 2016-09-15 | Sram, Llc | Bicycle Control Device |
CN106132792A (en) * | 2014-04-28 | 2016-11-16 | 日立汽车系统株式会社 | Master cylinder for vehicle |
CN107117247A (en) * | 2016-02-24 | 2017-09-01 | 株式会社岛野 | Bicycle hydraulic operation device |
US9937978B2 (en) | 2016-06-15 | 2018-04-10 | Shimano Inc. | Bicycle hydraulic operating device |
US20180274562A1 (en) * | 2017-03-27 | 2018-09-27 | Sram, Llc | Hydraulic bicycle component control device |
US10189539B2 (en) | 2013-01-18 | 2019-01-29 | Gustav Magenwirth Gmbh & Co. Kg | Master cylinder device for a hydraulic disk brake |
US20190039685A1 (en) * | 2017-08-03 | 2019-02-07 | Shimano Inc. | Hydraulic operating device |
US10232905B2 (en) | 2016-06-15 | 2019-03-19 | Shimano Inc. | Bicycle hydraulic operating device |
US10442495B2 (en) * | 2014-06-20 | 2019-10-15 | Shimano Inc. | Bicycle hydraulic operating system |
US10668907B2 (en) | 2016-06-16 | 2020-06-02 | Shimano Inc. | Bicycle hydraulic operating device |
CN113682413A (en) * | 2020-05-19 | 2021-11-23 | 株式会社岛野 | Piston assembly for a human powered vehicle |
Families Citing this family (55)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7412829B2 (en) * | 2005-12-13 | 2008-08-19 | Shimano, Inc. | Hydraulic apparatus for a bicycle brake lever device |
US7500545B2 (en) * | 2005-12-13 | 2009-03-10 | Shimano, Inc. | Reservoir apparatus for a bicycle brake lever device |
US8336308B2 (en) * | 2006-11-06 | 2012-12-25 | Freni Brembo S.P.A. | Lever device for operating a hydraulic actuator, particularly for motorcycles |
ITFI20070018A1 (en) * | 2007-01-31 | 2008-08-01 | Formula Srl | HYDRAULIC PUMP. |
US20090120750A1 (en) * | 2007-11-09 | 2009-05-14 | Hsin-Tech (Shen Zhen) Co., Ltd | Hydraulic brake lever |
TWM342334U (en) * | 2007-11-12 | 2008-10-11 | Lee Chi Entpr Co Ltd | Hydraulic type brake lever |
US20090152063A1 (en) * | 2007-12-13 | 2009-06-18 | Szu-Fang Tsai | Pumping device for a hydraulic brake of a bicycle |
US20090152061A1 (en) * | 2007-12-13 | 2009-06-18 | Szu-Fang Tsai | Adjustable pumping device for a hydraulic brake device of a bicycle |
US8267227B2 (en) * | 2008-07-22 | 2012-09-18 | Akebono Brake Corporation | Lever assembly featuring blind cable assembly |
US7832531B2 (en) * | 2009-03-06 | 2010-11-16 | Shimano Inc. | Bicycle component fixing band |
US8177078B2 (en) * | 2009-06-03 | 2012-05-15 | Michael Pezzati | Eyeglasses retainer for handle bars |
DE102009039620A1 (en) * | 2009-09-01 | 2011-03-03 | Gustav Magenwirth Gmbh & Co. Kg | Encoder device for a closed hydraulic system of handlebar-guided vehicles |
US20110100772A1 (en) * | 2009-11-05 | 2011-05-05 | Akebono Corporation (North America) | Cable end retention clip assembly and method |
US9150275B2 (en) * | 2009-12-17 | 2015-10-06 | Shimano Inc. | Hydraulic connector arrangement |
US8201670B2 (en) * | 2009-12-17 | 2012-06-19 | Shimano Inc. | Bicycle hydraulic brake actuation device |
TW201122267A (en) * | 2009-12-30 | 2011-07-01 | Elite Sewing Machine Mfg Co Ltd | Hydraulic brake arrester. |
TWM390914U (en) * | 2010-02-12 | 2010-10-21 | ||
US20110290601A1 (en) * | 2010-05-27 | 2011-12-01 | Chang Hui Lin | Hydraulic Brake |
US20130192941A1 (en) * | 2010-05-27 | 2013-08-01 | Chang Hui Lin | Hydraulic brake |
IT1402543B1 (en) * | 2010-10-29 | 2013-09-13 | Freni Brembo Spa | TOGETHER WITH LIGHT SOURCE FOR A MOTORCYCLE |
TW201219251A (en) * | 2010-11-12 | 2012-05-16 | Heng Tong Machinery Co Ltd | to achieve the purpose of conveniently adjusting brake sensitivity through a simple operation of changing the degree of an adjustment screw extending into an oil return hole |
USD641670S1 (en) | 2010-11-24 | 2011-07-19 | Hb Performance Systems, Inc. | Brake pad |
US8943924B2 (en) | 2010-11-24 | 2015-02-03 | Hb Performance Systems, Inc. | System and method for an adjustable lever assembly |
US8893859B2 (en) * | 2010-12-10 | 2014-11-25 | Heng Tong Machinery Co., Ltd. | Hydraulic brake controller |
US20120240715A1 (en) * | 2011-03-24 | 2012-09-27 | Tektro Technology Corporation | Braking device with hidden hydraulic cylinder |
US8967347B2 (en) * | 2011-08-26 | 2015-03-03 | Ashima Ltd. | Adjustment device for a hydraulic brake system |
US9096288B2 (en) * | 2012-01-05 | 2015-08-04 | Shimano, Inc. | Dual hydraulic controller for bicycle components |
US8714322B2 (en) | 2012-01-16 | 2014-05-06 | Sram, Llc | Hydraulic brake mechanism |
US8851249B2 (en) * | 2012-08-30 | 2014-10-07 | Tien Hsin Industries Co., Ltd. | Hydraulic brake master cylinder |
US8888066B2 (en) * | 2012-12-18 | 2014-11-18 | Ashima Ltd. | Adjustable holder of a hydraulic brake device for a bicycle |
US9415831B2 (en) * | 2013-06-28 | 2016-08-16 | Shimano Inc. | Bicycle hydraulic operating device |
EP3038893B1 (en) * | 2013-08-27 | 2019-11-20 | Gustav Magenwirth GmbH & Co. KG | Master cylinder fitting |
US20150143991A1 (en) * | 2013-11-27 | 2015-05-28 | Hb Performance Systems, Inc. | Master cylinder with recessed piston-rod interface |
US10550858B2 (en) * | 2014-08-25 | 2020-02-04 | Shimano Inc. | Bicycle control device |
US10625813B2 (en) | 2014-11-13 | 2020-04-21 | Robert L. Barnett | Motorcycle front brake master cylinder assembly |
US9932086B2 (en) | 2014-11-13 | 2018-04-03 | Robert L. Barnett | Motorcycle front brake master cylinder assembly |
USD770346S1 (en) * | 2015-06-16 | 2016-11-01 | Haldex Brake Products Ab | Brake adjuster |
USD770344S1 (en) * | 2015-06-16 | 2016-11-01 | Haldex Brake Products Ab | Brake adjuster |
USD770345S1 (en) * | 2015-06-16 | 2016-11-01 | Haldex Brake Products Ab | Brake adjuster |
USD770343S1 (en) * | 2015-06-16 | 2016-11-01 | Haldex Brake Products Ab | Brake adjuster |
US11319017B2 (en) | 2015-10-19 | 2022-05-03 | Sram, Llc | Hydraulic brake control device with staggered timing ports |
US10343744B2 (en) * | 2016-05-23 | 2019-07-09 | Shimano Inc. | Bicycle operating device |
DE102016209955A1 (en) * | 2016-06-07 | 2017-12-07 | Shimano Inc. | A bicycle hydraulic device having a container |
US10183721B2 (en) * | 2016-08-10 | 2019-01-22 | Shimano Components (Malaysia) Sdn. Bhd. | Bicycle control device |
IT201700065297A1 (en) | 2017-06-13 | 2018-12-13 | Campagnolo Srl | Hydraulic seal body for bicycle brake systems and hydraulic hose assembly for bicycle brake systems |
US10259523B2 (en) * | 2017-07-26 | 2019-04-16 | Shimano Inc. | Hydraulic operating system |
US10526038B2 (en) * | 2017-08-03 | 2020-01-07 | Shimano Inc. | Operating device |
US10300983B2 (en) | 2017-08-03 | 2019-05-28 | Shimano Inc. | Operating assembly |
US10358183B2 (en) * | 2017-08-24 | 2019-07-23 | Shimano Inc. | Hydraulic operating apparatus |
TWI637871B (en) * | 2017-09-05 | 2018-10-11 | 顏伶恩 | Hydraulic braking system and control device thereof |
US10494053B2 (en) | 2018-01-21 | 2019-12-03 | Shimano Inc. | Operating device |
CN108528611B (en) * | 2018-03-15 | 2020-09-01 | 浙江星联电动自行车零件有限公司 | Magnetic induction type hydraulic disc brake |
TWI737501B (en) * | 2020-09-25 | 2021-08-21 | 彥豪金屬工業股份有限公司 | Bicycle braking and parking device |
US20220332388A1 (en) * | 2021-04-14 | 2022-10-20 | Ox-Motorcycle Products, LLC | Adjustable hydraulic motorcycle brake system and device |
IT202100028463A1 (en) * | 2021-11-09 | 2023-05-09 | Sunstar Eng Europe Gmbh | HYDRAULIC DRIVE PUMP FOR A CYCLE OR MOTORCYCLE. |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2213947A (en) * | 1937-09-27 | 1940-09-10 | Hydraulic Brake Co | Fluid pressure braking system |
US2952128A (en) * | 1957-05-09 | 1960-09-13 | Highland Olaf | Sealed pressure-equalizing hydraulic brake reservoir |
US2958198A (en) * | 1959-10-28 | 1960-11-01 | Gen Motors Corp | Hydraulic actuating system |
US3348377A (en) * | 1958-12-04 | 1967-10-24 | Wagner Electric Corp | Pressure generating means |
US4004707A (en) * | 1976-04-05 | 1977-01-25 | General Motors Corporation | Fluid baffle in master cylinder reservoir |
US4560049A (en) * | 1982-09-28 | 1985-12-24 | Honda Giken Kogyo Kabushiki Kaisha | Operation device for clutch master cylinder with means to adjust the play stroke of the clutch lever |
US4635442A (en) * | 1984-08-29 | 1987-01-13 | Automotive Products Plc | Hydraulic master cylinder assembly |
US4788821A (en) * | 1983-11-28 | 1988-12-06 | Automotive Products, Plc | Hydraulic shift for motor vehicle transmission |
US6457378B2 (en) * | 1999-12-16 | 2002-10-01 | Nissin Kogyo Co., Ltd. | Control lever equipment for bar handle vehicle |
US6658844B1 (en) * | 2002-04-10 | 2003-12-09 | Dethmers Manufacturing Company | Plastic master cylinder for hydraulic brake system |
Family Cites Families (75)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE857901C (en) * | 1951-04-08 | 1952-12-04 | Teves Kg Alfred | Hydraulic transmitter for motor vehicle brakes, in particular for motorcycles, scooters or the like. |
US3802200A (en) | 1972-03-27 | 1974-04-09 | Kelsey Hayes Co | Plastic master cylinder |
GB1536353A (en) | 1976-06-26 | 1978-12-20 | Automotive Prod Co Ltd | Hydraulic brake actuator |
JPS6042436B2 (en) | 1978-03-09 | 1985-09-21 | 株式会社東芝 | Reactor |
DE2922399B1 (en) | 1979-06-01 | 1980-12-18 | Magenwirth Gmbh Co Gustav | Brake cylinder housing for attachment to the handlebars of a motorized two-wheeler |
US4388944A (en) * | 1979-08-30 | 1983-06-21 | Keizo Honma | Device for capturing air bubbles from fluids in piping |
US4418534A (en) * | 1980-03-18 | 1983-12-06 | Lucas Industries Limited | Hydraulic pressure master cylinder |
US4391353A (en) * | 1981-01-23 | 1983-07-05 | Mathauser William R | Hand operated hydraulic bicycle brake |
GB2111148B (en) * | 1981-06-09 | 1985-09-18 | Nisshin Kogyo Kk | Diaphragm assembly |
JPS5849549A (en) * | 1981-09-19 | 1983-03-23 | Honda Motor Co Ltd | Hydraulic master cylinder device of motorcycle and the like |
DE3216885C2 (en) | 1982-05-06 | 1986-03-13 | Gustav Magenwirth Gmbh & Co, 7432 Urach | Brake cylinder housing for a closed hydraulic system to be attached to the handlebars of a two-wheeled vehicle |
US4615415A (en) * | 1983-03-23 | 1986-10-07 | Mathauser William R | Hand operated hydraulic bicycle brake |
US4626045A (en) * | 1984-06-07 | 1986-12-02 | Honda Giken Kogyo Kabushiki Kaisha | Control unit for antilock brake systems |
US4568131A (en) * | 1984-10-30 | 1986-02-04 | Blomberg Folke Ivar | Modulator for hydraulic brakes |
JPS621834A (en) | 1985-06-27 | 1987-01-07 | Kobe Steel Ltd | Manufacture of al-b alloy |
JPH0777877B2 (en) * | 1985-12-06 | 1995-08-23 | 本田技研工業株式会社 | Adjustable operating lever for vehicle |
US4785629A (en) * | 1987-06-04 | 1988-11-22 | Ennis Iii James F | Syringe-dispensed brake fluid for filling and purging master cylinder circuit from slave |
KR900008424B1 (en) | 1987-06-05 | 1990-11-20 | 닛신 고오교오 가부시끼가이샤 | Lever system for vehicles |
US4878346A (en) * | 1987-07-24 | 1989-11-07 | Hayes Industrial Brake, Inc. | Tab-aligned replaceable cartridge for master cylinder |
IT218037Z2 (en) | 1988-12-12 | 1992-03-30 | Brembo Spa | POSITION REGULATOR FOR MANUAL CONTROL LEVERS, APPLIED TO HANDLEBARS |
US4921081A (en) | 1988-12-22 | 1990-05-01 | Autra-Bike Co., Inc. | Hydraulic brake apparatus for bicycles |
JPH0331054A (en) | 1989-06-27 | 1991-02-08 | Nissin Kogyo Kk | Operational lever for fluid pressure master cylinder for vehicle |
JPH041034Y2 (en) | 1989-09-13 | 1992-01-14 | Nissin Kogyo Kk | |
US5287765A (en) | 1990-01-04 | 1994-02-22 | Brian Scura | Hand actuated cable displacement system |
US5207108A (en) * | 1991-06-07 | 1993-05-04 | Tassic William P | Transducer for sensing tension loading of a conveyor chain |
US5205153A (en) * | 1992-01-23 | 1993-04-27 | Cobe Laboratories, Inc. | Method and apparatus for detection of air bubbles in tubing |
GB9305838D0 (en) * | 1993-03-20 | 1993-05-05 | Automotive Products Plc | An operating mechanism for a hydraulic master cylinder |
IT232629Y1 (en) * | 1993-04-09 | 2000-01-18 | Brembo Spa | ADJUSTMENT DEVICE FOR CONTROL PUMPS OPERATING LEVERS |
US5620575A (en) * | 1993-12-27 | 1997-04-15 | Honda Giken Kogyo Kabushiki Kaisha | Composite plating apparatus and apparatus for dispersing air bubbles within a composite plating solution |
KR0130390Y1 (en) * | 1995-05-09 | 1999-02-18 | 문정환 | Apparatus for injecting rigid-liquid |
US5632362A (en) * | 1995-08-15 | 1997-05-27 | Rockshox, Inc. | Bicycle disc brake |
US5660082A (en) | 1995-10-19 | 1997-08-26 | Hsieh; Wen Cheng | Adjustable brake control for a bicycle |
EP0876557B1 (en) | 1996-01-26 | 2003-08-06 | Sram Corporation | Brake actuating system |
GB9604170D0 (en) | 1996-02-28 | 1996-05-01 | Weatherhill Ian | Hydraulic brakes |
JPH09249180A (en) | 1996-03-18 | 1997-09-22 | Akebono Brake Ind Co Ltd | Operation lever for vehicle with adjuster mechanism |
US5813501A (en) * | 1996-10-18 | 1998-09-29 | Terry, Sr.; Maurice C. | Hand operated hydraulic vehicle brake |
DE19718612A1 (en) | 1997-05-02 | 1998-11-05 | Magenwirth Gmbh Co Gustav | Operating unit for hydraulic brakes of two=wheelers and suchlike |
IT237821Y1 (en) | 1997-07-23 | 2000-09-29 | Crc Ct Ricerche Cagiva S A | PUMP ASSEMBLY, FRONT BRAKE SYSTEM LIQUID TANK AND BRAKE OR CLUTCH LEVER FOR A MOTORCYCLE |
US5950772A (en) * | 1997-08-29 | 1999-09-14 | Hayes Brake, Inc. | Bicycle brake system having a flexible disk |
US6318514B1 (en) * | 1997-08-29 | 2001-11-20 | Hayes Brake, Inc. | Disc brake system with spring clip pad holders |
US6082509A (en) * | 1998-02-10 | 2000-07-04 | Hayes Brake, Inc. | Fluid pressurization system |
JPH11324891A (en) * | 1998-05-11 | 1999-11-26 | Kazuaki Murata | Rotation driving device using bubble |
US6516682B2 (en) | 1998-10-01 | 2003-02-11 | Jay Brake Enterprises | Adjustable control lever |
WO2000034114A1 (en) * | 1998-12-09 | 2000-06-15 | Gustav Magenwirth Gmbh & Co. | Brake cylinder for rim brake |
JP3433912B2 (en) | 1999-07-19 | 2003-08-04 | 本田技研工業株式会社 | Control lever adjustment device |
JP4357660B2 (en) | 1999-08-27 | 2009-11-04 | 本田技研工業株式会社 | Master cylinder device for vehicle |
US6336960B1 (en) * | 1999-09-28 | 2002-01-08 | Advanced Micro Devices, Inc. | System and method for purging air bubbles from filters |
US6502675B1 (en) | 2000-01-11 | 2003-01-07 | Frank G. Andrus | Integrated handlebar and master cylinder having piston and hydraulic line coaxially aligned with major central axis of handlebar |
US6334514B1 (en) | 2000-02-02 | 2002-01-01 | Shimano Inc. | Bicycle disc brake |
US6349800B1 (en) | 2000-02-07 | 2002-02-26 | Shimano Inc. | Bicycle disc brake assembly |
EP1160152B1 (en) | 2000-06-02 | 2005-12-07 | Freni Brembo S.p.A. | Device for adjusting the position of the operating lever of a hydraulic actuator |
US6401882B1 (en) | 2000-06-30 | 2002-06-11 | Shimano Inc. | Heat insulator for disc brake |
US6347689B1 (en) | 2000-06-30 | 2002-02-19 | Shimano Inc. | Roll back seal for disc brake |
WO2002018037A2 (en) | 2000-08-31 | 2002-03-07 | Millipore Corporation | Gas vent filter construction incorporating a hollow fiber membrane assembly |
JP4374127B2 (en) | 2000-08-31 | 2009-12-02 | 日信工業株式会社 | Bar handle vehicle control lever |
US6321784B1 (en) * | 2000-09-28 | 2001-11-27 | Tony Leng | Oil-storing device for a bike saucer-brake |
US6922994B1 (en) * | 2000-09-29 | 2005-08-02 | Freni Brembo S.P.A. | Hydraulic pump for vehicles controllable by handlebars |
DE20018705U1 (en) | 2000-11-02 | 2000-12-28 | Magenwirth Gmbh Co Gustav | Control valve for actuating the brake or clutch of a vehicle with a handlebar |
US6370877B1 (en) * | 2001-01-30 | 2002-04-16 | Chang Hui Lin | Brake handle device for hydraulic brake assembly |
US6527303B2 (en) | 2001-06-04 | 2003-03-04 | Shimano Inc. | Hydraulic hose assembly for bicycle |
US20030121736A1 (en) * | 2001-12-28 | 2003-07-03 | Avid, L.L.C. | Master cylinder lever for a hydraulic disc brake having a backpack reservoir |
US6804961B2 (en) * | 2001-12-28 | 2004-10-19 | Sram Corporation | Master cylinder lever for a hydraulic disk brake having on the fly dead-band adjustment |
US7204350B2 (en) * | 2001-12-28 | 2007-04-17 | Sram Corporation | Master cylinder lever for a hydraulic disc brake having favorable handle pivot geometry |
ITFI20030044A1 (en) * | 2003-02-20 | 2004-08-21 | Formula Srl | DEVICE FOR THE CONTROL OF BRAKES IN CYCLES AND SIMILAR |
ITFI20030241A1 (en) * | 2003-09-15 | 2005-03-16 | Formula Srl | DEVICE FOR THE CONTROL OF HYDRAULIC BRAKES IN CYCLES, |
ITFI20030242A1 (en) * | 2003-09-15 | 2005-03-16 | Formula Srl | DEVICE FOR THE CONTROL OF HYDRAULIC BRAKES IN CYCLES, |
US6883647B1 (en) * | 2003-09-16 | 2005-04-26 | Chun Te Wen | Hydraulic brake lever for a bicycle |
US20060070483A1 (en) * | 2004-10-05 | 2006-04-06 | Dimsey James J | Brake and clutch lever height adjusters |
US7308791B2 (en) * | 2005-02-18 | 2007-12-18 | Shimano Inc. | Hydraulic disc brake lever assembly |
DE202005003033U1 (en) * | 2005-02-23 | 2005-04-28 | Fte Automotive Gmbh & Co. Kg | Hand lever fitting for handlebar-controlled vehicles, especially motorcycles |
USD522422S1 (en) | 2005-03-07 | 2006-06-06 | Hayes Disc Brake, Llc | Master cylinder |
US7487638B2 (en) * | 2006-06-09 | 2009-02-10 | Shimano Inc. | Bicycle hydraulic brake accentuate device |
US7757821B2 (en) * | 2006-06-09 | 2010-07-20 | Shimano Inc. | Bicycle hydraulic brake actuation device |
USD570272S1 (en) * | 2006-12-27 | 2008-06-03 | Hayes Bicycle Group, Inc. | Master cylinder |
US7942250B2 (en) * | 2007-04-03 | 2011-05-17 | Shimano Inc. | Bicycle hydraulic brake device |
-
2002
- 2002-12-10 US US10/316,452 patent/US20030121736A1/en not_active Abandoned
-
2004
- 2004-10-15 US US10/966,737 patent/US7178646B2/en not_active Expired - Lifetime
-
2006
- 2006-10-24 US US11/552,458 patent/US7575105B2/en not_active Expired - Lifetime
-
2007
- 2007-04-19 US US11/737,509 patent/US7559414B2/en not_active Expired - Fee Related
-
2008
- 2008-01-30 US US12/022,919 patent/US20080116025A1/en not_active Abandoned
- 2008-06-26 US US12/147,259 patent/US8074774B2/en not_active Expired - Fee Related
- 2008-06-26 US US12/147,272 patent/US7617913B2/en not_active Expired - Fee Related
- 2008-06-26 US US12/147,267 patent/US7530435B2/en not_active Expired - Fee Related
-
2011
- 2011-12-13 US US13/324,868 patent/US8464845B2/en not_active Expired - Fee Related
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2213947A (en) * | 1937-09-27 | 1940-09-10 | Hydraulic Brake Co | Fluid pressure braking system |
US2952128A (en) * | 1957-05-09 | 1960-09-13 | Highland Olaf | Sealed pressure-equalizing hydraulic brake reservoir |
US3348377A (en) * | 1958-12-04 | 1967-10-24 | Wagner Electric Corp | Pressure generating means |
US2958198A (en) * | 1959-10-28 | 1960-11-01 | Gen Motors Corp | Hydraulic actuating system |
US4004707A (en) * | 1976-04-05 | 1977-01-25 | General Motors Corporation | Fluid baffle in master cylinder reservoir |
US4560049A (en) * | 1982-09-28 | 1985-12-24 | Honda Giken Kogyo Kabushiki Kaisha | Operation device for clutch master cylinder with means to adjust the play stroke of the clutch lever |
US4788821A (en) * | 1983-11-28 | 1988-12-06 | Automotive Products, Plc | Hydraulic shift for motor vehicle transmission |
US4635442A (en) * | 1984-08-29 | 1987-01-13 | Automotive Products Plc | Hydraulic master cylinder assembly |
US6457378B2 (en) * | 1999-12-16 | 2002-10-01 | Nissin Kogyo Co., Ltd. | Control lever equipment for bar handle vehicle |
US6658844B1 (en) * | 2002-04-10 | 2003-12-09 | Dethmers Manufacturing Company | Plastic master cylinder for hydraulic brake system |
Cited By (67)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8464845B2 (en) | 2001-12-28 | 2013-06-18 | Sram, Llc | Master cylinder lever for a bicycle hydraulic disc brake |
US20050199450A1 (en) * | 2004-03-09 | 2005-09-15 | Campbell Darren J. | Lever assembly and master cylinder |
US7546909B2 (en) * | 2004-03-09 | 2009-06-16 | Hayes Bicycle Group, Inc. | Lever assembly and master cylinder |
US20080011566A1 (en) * | 2004-03-09 | 2008-01-17 | Campbell Darren J | Method of bleeding a braking system |
US20060185943A1 (en) * | 2005-02-18 | 2006-08-24 | Shimano, Inc. | Hydraulic disc brake lever assembly |
US20060185360A1 (en) * | 2005-02-18 | 2006-08-24 | Shimano Inc. | Hydraulic disc brake lever assembly |
US20060185941A1 (en) * | 2005-02-18 | 2006-08-24 | Shimano Inc. | Hydraulic disc brake lever assembly |
US7654366B2 (en) | 2005-02-18 | 2010-02-02 | Shimano Inc. | Hydraulic disc brake lever assembly |
US20070209360A1 (en) * | 2005-02-18 | 2007-09-13 | Shimano Inc. | Hydraulic disc brake lever assembly |
US7308791B2 (en) | 2005-02-18 | 2007-12-18 | Shimano Inc. | Hydraulic disc brake lever assembly |
US7377367B2 (en) | 2005-02-18 | 2008-05-27 | Shimano Inc. | Hydraulic disc brake lever assembly |
US7389642B2 (en) | 2005-02-18 | 2008-06-24 | Shimano Inc. | Hydraulic disc brake lever assembly |
EP1733959A3 (en) * | 2005-06-17 | 2007-06-13 | Shimano Inc. | Hydraulic brake lever assembly |
EP1870328A3 (en) * | 2005-06-17 | 2008-07-09 | Shimano Inc. | Hydraulic disc brake lever assembly |
EP1870327A3 (en) * | 2005-06-17 | 2008-07-16 | Shimano Inc. | Hydraulic disc brake lever assembly |
EP1870326A3 (en) * | 2005-06-17 | 2008-09-03 | Shimano Inc. | Hydraulic disc brake lever assembly |
EP1733959A2 (en) | 2005-06-17 | 2006-12-20 | Shimano Inc. | Hydraulic brake lever assembly |
US7497309B2 (en) * | 2006-03-14 | 2009-03-03 | Jui-Pin Chen | Bicycle brake lever |
US20070215416A1 (en) * | 2006-03-14 | 2007-09-20 | Jui-Pin Chen | Bicycle brake lever |
US20080155982A1 (en) * | 2006-12-28 | 2008-07-03 | Jones Christopher S | Hydraulic Brake Master Cylinder |
US20080245632A1 (en) * | 2007-04-03 | 2008-10-09 | Shimano Inc. | Bicycle hydraulic brake device |
US7942250B2 (en) | 2007-04-03 | 2011-05-17 | Shimano Inc. | Bicycle hydraulic brake device |
EP2096025A3 (en) * | 2008-02-29 | 2010-04-14 | Sunstar Engineering Pte. Ltd | Braking device |
US8281903B2 (en) | 2008-02-29 | 2012-10-09 | Sunstar Engineering Pte. Ltd. | Breaking device |
US20090229927A1 (en) * | 2008-02-29 | 2009-09-17 | Cesare Brioschi | Breaking device |
US20100064838A1 (en) * | 2008-09-18 | 2010-03-18 | Shimano Components (Malaysia) Sdn Bhd | Reservoir tank for hydraulic brake lever assembly |
US8146716B2 (en) | 2008-09-18 | 2012-04-03 | Shimano Inc. | Reservoir tank for hydraulic brake lever assembly |
US20130255239A1 (en) * | 2012-03-30 | 2013-10-03 | Shimano Inc. | Bicycle hydraulic component operating device |
CN103359246A (en) * | 2012-03-30 | 2013-10-23 | 株式会社岛野 | Bicycle hydraulic component operating device |
US9321505B2 (en) * | 2012-03-30 | 2016-04-26 | Shimano Inc. | Bicycle hydraulic component operating device |
ITPD20120323A1 (en) * | 2012-10-31 | 2014-05-01 | Freni Brembo Spa | LEVER OPERATING DEVICE FOR BRAKES AND / OR CLUTCHES, IN PARTICULAR FOR MOTORCYCLES |
WO2014068518A1 (en) * | 2012-10-31 | 2014-05-08 | Freni Brembo S.P.A. | Actuation device for a hydraulic actuator |
EP2749485A1 (en) * | 2012-12-26 | 2014-07-02 | Shimano Inc. | Bicycle control device |
US9873483B2 (en) | 2012-12-26 | 2018-01-23 | Shimano Inc. | Bicycle control device |
CN103895801B (en) * | 2012-12-26 | 2020-09-15 | 株式会社岛野 | Bicycle control device |
CN103895801A (en) * | 2012-12-26 | 2014-07-02 | 株式会社岛野 | Bicycle Control Device |
US10189539B2 (en) | 2013-01-18 | 2019-01-29 | Gustav Magenwirth Gmbh & Co. Kg | Master cylinder device for a hydraulic disk brake |
TWI582005B (en) * | 2014-03-24 | 2017-05-11 | 速聯有限責任公司 | Variable rate assembly for a brake system for bicycle |
US9290232B2 (en) * | 2014-03-24 | 2016-03-22 | Sram, Llc | Variable rate assembly for a brake system for bicycle |
US20150266540A1 (en) * | 2014-03-24 | 2015-09-24 | Sram, Llc | Variable rate assembly for a brake system for bicycle |
CN106132792A (en) * | 2014-04-28 | 2016-11-16 | 日立汽车系统株式会社 | Master cylinder for vehicle |
US9643682B2 (en) * | 2014-05-09 | 2017-05-09 | Shimano Inc. | Hydraulic operating device |
US20150321725A1 (en) * | 2014-05-09 | 2015-11-12 | Shimano Inc. | Hydraulic operating device |
CN105083452A (en) * | 2014-05-09 | 2015-11-25 | 株式会社岛野 | Hydraulic operating device |
TWI613119B (en) * | 2014-05-09 | 2018-02-01 | 島野股份有限公司 | Hydraulic operating device |
US10940913B2 (en) | 2014-06-20 | 2021-03-09 | Shimano Inc. | Bicycle hydraulic operating system |
US10442495B2 (en) * | 2014-06-20 | 2019-10-15 | Shimano Inc. | Bicycle hydraulic operating system |
US20160200392A1 (en) * | 2015-01-12 | 2016-07-14 | Sram, Llc | Hydraulic Bicycle System |
US9827968B2 (en) * | 2015-01-12 | 2017-11-28 | Sram, Llc | Hydraulic bicycle system |
US10407043B2 (en) | 2015-01-12 | 2019-09-10 | Sram, Llc | Hydraulic bicycle system |
TWI687336B (en) * | 2015-03-12 | 2020-03-11 | 美商速聯有限責任公司 | Bicycle control device |
US10946928B2 (en) * | 2015-03-12 | 2021-03-16 | Sram, Llc | Bicycle control device |
US20190106177A1 (en) * | 2015-03-12 | 2019-04-11 | Sram, Llc | Bicycle control device |
US10183723B2 (en) * | 2015-03-12 | 2019-01-22 | Sram, Llc | Bicycle control device |
US20160264213A1 (en) * | 2015-03-12 | 2016-09-15 | Sram, Llc | Bicycle Control Device |
CN107117247A (en) * | 2016-02-24 | 2017-09-01 | 株式会社岛野 | Bicycle hydraulic operation device |
US10232905B2 (en) | 2016-06-15 | 2019-03-19 | Shimano Inc. | Bicycle hydraulic operating device |
US9937978B2 (en) | 2016-06-15 | 2018-04-10 | Shimano Inc. | Bicycle hydraulic operating device |
US10668907B2 (en) | 2016-06-16 | 2020-06-02 | Shimano Inc. | Bicycle hydraulic operating device |
CN108657326A (en) * | 2017-03-27 | 2018-10-16 | 什拉姆有限责任公司 | hydraulic bicycle component control device |
CN111137381A (en) * | 2017-03-27 | 2020-05-12 | 什拉姆有限责任公司 | Hydraulic bicycle component control device |
US10611433B2 (en) * | 2017-03-27 | 2020-04-07 | Sram, Llc | Hydraulic bicycle component control device |
TWI687340B (en) * | 2017-03-27 | 2020-03-11 | 美商速聯有限責任公司 | Hydraulic bicycle component control device |
US20180274562A1 (en) * | 2017-03-27 | 2018-09-27 | Sram, Llc | Hydraulic bicycle component control device |
US20190039685A1 (en) * | 2017-08-03 | 2019-02-07 | Shimano Inc. | Hydraulic operating device |
US10967932B2 (en) * | 2017-08-03 | 2021-04-06 | Shimano Inc. | Hydraulic operating device |
CN113682413A (en) * | 2020-05-19 | 2021-11-23 | 株式会社岛野 | Piston assembly for a human powered vehicle |
Also Published As
Publication number | Publication date |
---|---|
US20120096851A1 (en) | 2012-04-26 |
US20090000878A1 (en) | 2009-01-01 |
US20070187191A1 (en) | 2007-08-16 |
US7559414B2 (en) | 2009-07-14 |
US8074774B2 (en) | 2011-12-13 |
US8464845B2 (en) | 2013-06-18 |
US7617913B2 (en) | 2009-11-17 |
US20080271446A1 (en) | 2008-11-06 |
US7575105B2 (en) | 2009-08-18 |
US20050061590A1 (en) | 2005-03-24 |
US20080116025A1 (en) | 2008-05-22 |
US7178646B2 (en) | 2007-02-20 |
US20070051575A1 (en) | 2007-03-08 |
US7530435B2 (en) | 2009-05-12 |
US20080257658A1 (en) | 2008-10-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7559414B2 (en) | Symmetric master cylinder lever for a hydraulic disc brake | |
US6804961B2 (en) | Master cylinder lever for a hydraulic disk brake having on the fly dead-band adjustment | |
US7204350B2 (en) | Master cylinder lever for a hydraulic disc brake having favorable handle pivot geometry | |
EP1325863B1 (en) | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment | |
TWI295253B (en) | Hydraulic disc brake lever assembly | |
EP1498347B1 (en) | Master cylinder lever for a hydraulic disc brake having on the fly dead-band adjustment | |
JP3590855B2 (en) | Adjustment device for manual operation lever for control pump | |
JP2001050319A (en) | Cylinder device of brake | |
US4919018A (en) | Hydraulic power wrench | |
JP2565339Y2 (en) | Sliding shower hook | |
JPH0437010Y2 (en) | ||
JP2565340Y2 (en) | Sliding shower hook | |
JPS6325400Y2 (en) | ||
JPH0210835Y2 (en) | ||
JPH0939868A (en) | Operation lever of hydraulic master cylinder device for bar handle vehicle | |
JPH0356665Y2 (en) | ||
JPH0355514Y2 (en) | ||
JPS5821033A (en) | Brake cylinder device for vehicle | |
JP2002021896A (en) | Brake adjuster assembly for drum brake | |
JPH0428924B2 (en) | ||
JP2000146017A (en) | Detent mechanism of control valve | |
JPH07112691A (en) | Hydraulic master cylinder for bar handle vehicle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: AVID, L.L.C., COLORADO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LUMPKIN, WAYNE R.;REEL/FRAME:013569/0921 Effective date: 20021203 |
|
AS | Assignment |
Owner name: SRAM CORPORATION, ILLINOIS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:AVID L.L.C.;REEL/FRAME:014491/0358 Effective date: 20040308 |
|
STCB | Information on status: application discontinuation |
Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION |