Brake assembly for a rail vehicle

Abstract

A rail vehicle brake assembly (100) acts on a rotating member (110) via first and second friction members (121; 122) movable between a respective engaged position (PENG) in which the friction members (121; 122) contact the rotating member (110), and a respective disengaged position (PDIS) in which the friction members (121; 122) are at an idle distance (dIDL) from the rotating member (110). An actuator (120) obtains a control signal (CS) and in response thereto controls the friction members (121; 122) to attain the respective engaged position (PENG). An adjuster mechanism (130) controls the friction members (121; 122) such that they in the disengaged position (PDIS) are positioned within a joint margin range (dm) from the idle distance (d IDL) notwithstanding any wear (w). The adjuster mechanism (130) has a probing arrangement (131) controlling the friction members (121; 122) such that an acti-15 vated distance (da) separating them from one another in the engaged position (PENG) decreases according to a monotonic function as the first and second friction members (121; 122) are worn (w). The probing arrangement (131) sets the activated distance (da) by an interaction between a slidable member (133) and a fixed-position member (135) that interact with one another along a contact profile containing an angled segment (T).

Description

[0001] Brake Assembly for a Rail Vehicle

[0002] TECHNICAL FIELD

[0003] The present invention relates generally to retardation arrangements for rail vehicles. Especially, the invention relates to a brake assembly according to the preamble of claim 1.

[0004] BACKGROUND

[0005] In operation of a rail vehicle, the onboard motors or engines may be engaged as engine brakes to decelerate the rail vehicle. For example, in an electrically powered rail vehicle, the electric engines may be employed as generators to reduce the speed. However, for efficiency and safety reasons, one cannot rely solely on this type of braking strategy. In particular, a dedicated brake function will always be needed to ensure emergency braking functionality and that the rail vehicle remains stationary after that it has been brought to a stop. In many cases, the same brake units are used for different types of braking functionality, such as service braking, emergency braking and parking braking.

[0006] Typically, the brake unit includes a rotating member mechanically linked to a wheel axle of the rail vehicle plus one or more friction members arranged to be pressed against the rotating member to decelerate the rail vehicle. Specifically, it is the contact between the friction material, i.e. the lining in the brake pads or shoes that creates frictional contact with the rotating member, e.g. a disc or a drum, and causes the desired amount of braking torque to slow down the rail vehicle. Repeated braking operations progressively wear away friction material, which results in a progressively thinner brake lining. As the friction material wears, the distance between the brake lining and the rotating member increases. The increase in distance increases the amount of mechanical travel required to engage the brake. This, in turn, translates into an ex- tended delay before the friction members make contact with the rotating member. In other words, the rail vehicle will travel a longer distance before deceleration begins. Of course, this is an undesired effect.

[0007] Various prior solutions are known to adjust and accommodate for the wearing of the brake lining, such that the friction members maintain a desired idle distance from the rotating member.

[0008] US 6,896, 106 shows a method of accommodating wear in an electrically operated brake assembly that includes setting a home position when a brake shoe engages a brake drum. A stepper motor drives the brake shoes into engagement with the drum. Upon engagement of the brake shoes with the drum, the stepper motor slips. Slipping of a stepper motor indicates that a home position has been reached. Upon release of the brake, the brake shoe is moved away from the drum a fixed distance. The fixed distance is an optimal distance between the friction member and the rotating member such that regardless of wear, the distance relationship between the brake shoe and drum is maintained. Although this strategy may be useful, as such, it is exclusively usable for electrically operated brakes and therefore has a limited field of application.

[0009] EP 3 683 468 shows a wear adjuster of a compact brake caliper unit, in particular for rail vehicles, that has an adjuster housing, an adjuster yoke, a threaded drive with a spindle and a pressure nut that can be screwed onto the spindle. The wear adjuster is designed as a pneumatic wear adjuster and has a control device of an adjustment cylinder of the wear adjuster, wherein the control device comprises a valve device. The valve device contains an inlet valve and a controlled outlet valve, which control the adjustment cylinder with the pressure medium of the brake cylinder as a drive of the wear adjuster. This design is only applicable to pneumatically operated brakes and relies on a relatively complex interaction of various pneumatic components. SUMMARY

[0010] The object of the present invention is to offer an uncomplicated and generically applicable solution for wear adjustment of rail vehicle brakes, such that a rail vehicle may experience a consistent and reliable braking behavior regardless of the wear of the friction members.

[0011] According to the invention, the object is achieved by a brake assembly for a rail vehicle, which brake assembly contains: a rotating member, first and second friction members, an actuator and an adjuster mechanism. The rotating member is mechanically linked to a wheel axle of the rail vehicle. Thus, the rotating member may for example be represented by a brake disc or the wheel itself. The first and second friction members are movable between a respective engaged position in which they contact the rotating member from opposing first and second sides respectively, and a respective disengaged position in which they are positioned at an idle distance from the rotating member. The actuator is arranged to obtain a control signal and in response thereto control the first and second friction members to attain the respective engaged position. The adjuster mechanism is configured to control the first and second friction members such that in the disengaged position the friction members are positioned within a joint margin range from the idle distance notwithstanding any wear of the first and second friction members. The adjuster mechanism contains a probing arrangement mechanically linked to the first and second friction members. The probing arrangement is arranged to control the friction members such that an activated distance by which the first and second friction members are separated from one another in the respective engaged position decreases according to a monotonic function as the friction members are worn. Specifically, the probing arrangement is configured to set the activated distance by an interaction between a slidable member and a fixed-position member arranged to interact with one another along a contact profile that comprises at least one angled segment. The above-described brake assembly is advantageous because it is fully self-adjusting. For instance, this means that it is not even necessary to set an initial idle distance for the friction members after replacement thereof. Namely, provided that the friction members are not mounted too close to the rotating member the friction members will automatically be positioned at the set idle distance after a few braking procedures.

[0012] According to one embodiment of the invention, the adjuster mechanism contains a ratcheted control screw that is mechanically linked to the first and second friction members. The ratcheted control screw is arranged to be rotated by the interaction between the slidable member and the fixed-position member so as to gradually reduce the activated distance in response to the first and second friction members being worn. As a result, the wear adjustment may be effected automatically without the involvement of any complex control mechanisms.

[0013] According to one embodiment of the invention, the first friction member is attached to a first arm that is rotatably attached to a first joint which, in turn, is eccentrically mounted on a rotatable member rotatably attached to a primary joint that is fixedly mounted in the brake assembly, and the second arm is rotatably attached to a second joint that is fixedly mounted in the brake assembly. This asymmetric attachment of the arms, or calipers, in the brake assembly results in a somewhat uncommon behavior of the arms, which enables various advantages that will be discussed below.

[0014] For example, according to one embodiment of the invention, the adjuster mechanism contains the rotatable member. Here, the slidable member is rotatably attached to the first joint, such that a movement of the first arm by rotation of the a rotatable member around the primary joint causes the slidable member to move together with the first arm. In this movement, both ends of the first arm translates in a direction being essentially parallel to one another. After that the first friction member has been brought into contact with the rotatable member the second arm will start to move the second friction member towards the rotatable member, and when also the second friction member contacts the rotatable member full brake force is applicable.

[0015] According to another embodiment of the invention, the fixed-position member includes a contact element, and the slidable member contains the at least one angled segment of the contact profile plus a straight-line segment of the contact profile. Here, each of the straight-line segment and the at least one angled segment is arranged to interact with the contact element during operation of the brake assembly. The straight-line segment is further arranged to interact with the contact element such that the first and second friction members are movable between the respective engaged and disengaged positions without causing an adjustment of the ratcheted control screw, if, in the respective disengaged position, the first and second friction members are positioned within the joint margin range from the idle distance. The at least one angled segment is arranged to interact with the contact element, such that the activated distance is reduced to an extent that depends on how long a distance the at least one angled segment of the contact profile slides against the fixed-position member during the braking procedure. Hence, the at least one angled segment controls the wear adjustment in a very straightforward manner.

[0016] According to yet another embodiment of the invention, the slidable member instead includes the contact element and the fixed- position member contains the at least one angled segment of the contact profile plus a straight-line segment of the contact profile. Analogous to the above, each of the straight-line segment and the at least one angled segment is arranged to interact with the contact element, and the straight-line segment is arranged such that the first and second friction members are movable between the respective engaged and disengaged positions without causing an adjustment of the ratcheted control screw, if, in the respective disengaged position, the first and second friction members are positioned within the joint margin range from the idle distance. Also here, the at least one angled segment is arranged to interact with the contact element, such that the activated distance is reduced to an extent that depends on how long a distance the contact element slides against the at least one angled segment. Thus, the at least one angled segment controls the wear adjustment in a very straightforward manner.

[0017] According to still another embodiment of the invention, the at least one angled segment includes a set of teeth and the contact element contains a rotatable gear-toothed member arranged to engage into the set of teeth of the at least one angled segment so as to in response to said engagement cause the adjustment of the ratcheted control screw. This is beneficial because the gear engagement renders the coupling between the contact element of the at least one angled segment mechanically efficient. For the same reasons the straight-line segment should preferably also include a set of teeth.

[0018] According to a another embodiment the invention, the adjuster mechanism further contains a shaft member connecting the probing arrangement to the ratcheted control screw. The shaft member is arranged to cause a rotation of the ratcheted control screw in response to the interaction between the slidable member and the fixed-position member along the at least one angled segment of the contact profile.

[0019] Preferably, the slidable member and the fixed-position member are configured such that when each of the first and second friction members is positioned in the respective disengaged position the slidable member and the fixed-position member contact one another at a point on the straight-line segment of the contact profile. If, when the first and second friction members are positioned in the respective engaged positions, the activated distance exceeds an adjustment threshold, the slidable member and the fixed- position member contact one another at a point on the straight- line segment of the contact profile. As a result, no wear adjustment will be made. However, if, when the first and second friction mem- bers are positioned in the respective engaged positions, the activated distance is equal to or subceeds the adjustment threshold, the slidable member and the fixed-position member contact one another at a point on the angled segment of the contact profile, thus causing a translational movement of the shaft member along its symmetry axis such that the ratcheted control screw is rotated, and thus wear adjustment is performed. This mechanism ensures that the set idle distance is maintained regardless of how the friction members are worn down.

[0020] According to a further embodiment of the invention, the ratcheted control screw is arranged between first and second pivot joints, where the first pivot joint is rotatably attached to the first arm and the second pivot joint is rotatably attached to the second arm. Additionally, the ratcheted control screw is arranged such that rotation thereof, for example so that the ratcheted control screw expands, causes the first and second pivot joints to be separated from one another, the second arm to rotate around the second joint and the first and second friction members to approach one another. Hence, the ratcheted control screw directly influences the operation of the first and second arms, such that the first and second friction members are always positioned at the idle distance in the disengaged position notwithstanding any wear of the friction members.

[0021] According to one embodiment of the invention, the angled segment has a convex, straight or concave shape directed towards the symmetry axis of the shaft member in such a way that the longer the slidable member slides along the fixed-position member over the angled segment the further the shaft member is caused to move away from the fixed-position member along its symmetry axis thus causing the ratcheted control screw to rotate around its axis in a first direction.

[0022] According to an alternative embodiment of the invention, the angled segment has a concave, straight or convex shape directed towards the symmetry axis of the shaft member in such a way that the longer the slidable member slides along the fixed-position member over the angled segment the further the shaft member is instead caused to move towards the fixed-position member along its symmetry axis thus causing the ratcheted control screw to rotate around its axis in a second direction, which may be opposite the first direction. However, preferably in both these alternative embodiments, the ratcheted control screw is designed so that said respective rotation results in that the ratcheted control screw expands.

[0023] In the latter of the two above embodiments, the brake assembly preferably contains a compressible member arranged to push the slidable member towards the fixed-position member while allowing the slidable member to slide along the fixed-position member. Namely, this ensures that slidable member remains in contact with the fixed-position member throughout the entire brake procedure.

[0024] Alternatively, the fixed-position member may include a guide track configured to lead the slidable member in the fixed-position member throughout a braking procedure, wherein the first and second friction members are moved between the respective engaged and disengaged positions. Here, the guide track contains first and second straight-line segments and first and second angled segments that are arranged to lead the slidable member in the guide track, such that the slidable member is in contact with at least one of said segments at each point in time during the braking procedure. Thus the slidable member remains in contact with the fixed-position member throughout the entire brake procedure.

[0025] According to still another embodiment of the invention, the ratcheted control screw is configured to reduce the activated distance between the first and second friction members continuously.

[0026] Alternatively, the ratcheted control screw may instead be configured to reduce the activated distance between the first and second friction members according to a stepwise procedure. Preferably, two consecutive steps in the stepwise procedure are here separa- ted from one another by an increment equivalent to less than or equal to the joint margin range. Namely, this ensures that the idle distance lies within an acceptable range.

[0027] According to yet other embodiments of the invention, the actuator is configured to be operated pneumatically or hydraulically in response to receiving the control signal as a variation in a fluid pressure level, or the actuator is configured to be operated electrome- chanically in response to receiving the control signal on an electrical format. In other words, the brake assembly is useful together with any existing technology for controlling rail vehicle brakes.

[0028] Further advantages, beneficial features and applications of the present invention will be apparent from the following description and the dependent claims.

[0029] BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The invention is now to be explained more closely by means of preferred embodiments, which are disclosed as examples, and with reference to the attached drawings.

[0031] Figures 1 a-b schematically illustrate a rail vehicle brake assembly according to a first embodiment of the invention when the friction members are disengaged and engaged respectively;

[0032] Figure 1 c schematically illustrates the brake assembly of Figures 1 a and 1 b when being adjusted for wear of the friction members;

[0033] Figures 2 - 4 show different embodiments of a proposed probing mechanism wherein a fixed-position member contains at least one angled segment of a contact profile, and a slidable member interacting therewith causes a shaft member to act on a ratcheted control screw in a first direction;

[0034] Figure 5 shows a free-wheel arrangement for manipulating a ratcheted control screw according to a first embo- diment of the invention;

[0035] Figure 6 schematically illustrates a rail vehicle brake accor- ding to a second embodiment of the invention;

[0036] Figures 7 - 9 show different embodiments of a proposed probing mechanism wherein the fixed-position member contains at least one angled segment of a contact profile, and a slidable member interacting therewith causes a shaft member to act on a ratcheted control screw in second direction;

[0037] Figure 10 shows a free-wheel arrangement for manipulating the ratcheted control screw according to a second embodiment of the invention;

[0038] Figure 1 1 illustrates how an activated distance between the friction members may be adjusted for wear according to a stepwise procedure;

[0039] Figure 12 illustrates how the activated distance between the friction members may be adjusted for wear according to a continuous procedure; and

[0040] Figure 13 schematically illustrates a rail vehicle brake according to a third embodiment of the invention.

[0041] DETAILED DESCRIPTION

[0042] In Figures 1 a and 1 b, we see a schematic illustration of a brake assembly 100 for rail vehicle brake according to a first embodiment of the invention. Specifically, Figure 1 a shows the brake assembly 100 when the first and second friction members 121 and 122 respectively are positioned in a disengaged position PDIS .

[0043] The brake assembly 100 includes a rotating member 110, first and second friction members 121 and 122 respectively, an actuator 120 and an adjuster mechanism 130.

[0044] The rotating member 110 is mechanically linked to a wheel axle of the rail vehicle. This means that the rotating member 110 may be a brake disc, which is arranged to rotate together with the wheel axle and the wheels thereon, or the rotating member 110 may be constituted by a wheel itself, as shown in Figures 1 a and 1 b. In such a case, the brake disc functionality is preferably integrated into the wheel, such that the first and second friction members 121 and 122 make contact with parts of the wheel side surfaces where the integrated brake disc is arranged.

[0045] The first and second friction members 121 and 122 are movable between a respective engaged position P EN G and the respective disengaged position P DIS . In the engaged position P E NG both the friction members 121 and 122 contact the rotating member 110, namely from opposing first and second sides respectively. In the disengaged position P DI S the friction members 121 and 122 are positioned at an idle distance diDL from the rotating member 110. In the present disclosure, the idle distance diDL is defined as a joint distance between both the friction members and the rotating member 110. This means that the entire idle distance diDL may be present between one of the friction members and the rotating member 110 whereas the other friction member has a zero distance to the rotating member 110. Due to the way in which the first and second friction members 121 are 122 are attached to the brake assembly 100 this is unproblematic according to the invention.

[0046] The actuator 120 is arranged to obtain a control signal CS and in response thereto control the first and second friction members 121 and 122 to attain the respective engaged position P EN G .

[0047] According to one embodiment of the invention, the actuator 120 is configured to be operated pneumatically or hydraulically. In such a case, the control signal CS may be represented by a variation in a fluid pressure level.

[0048] According to another embodiment of the invention, the actuator 120 is instead configured to be operated electromechanically in response to receiving the control signal CS on an electrical format. In such a case, the electric control signal may cause an electric motor to operate a gear arrangement such that the first and second friction members 121 and 122 attain the respective engaged position P E NG .

[0049] The adjuster mechanism 130 is configured to control the first and second friction members 121 and 122, such that in the disengaged position P DI S the friction members 121 and 122 are positioned within a joint margin range dmfrom the idle distance diDL notwithstanding any wear of the first and second friction members 121 and 122. Analogous to the above, the joint margin range dmis defined such that the entire range may be accommodated on one of the sides of the rotating member 110.

[0050] The adjuster mechanism 130 includes a probing arrangement 131 that is mechanically linked to the first and second friction members 121 and 122. The probing arrangement 131 is arranged to control the first and second friction members 121 and 122 such that an activated distance daby which the friction members are separated from one another in the respective engaged position P E NG decreases according to a monotonic function as the friction members are worn. Figures 11 and 12 exemplify to such monotonic functions, where the respective horizontal axis shows a wear w of the friction members 121 and 122 and the respective vertical axis indicates the activated distance da.

[0051] According to the invention, the probing arrangement 131 is configured to set the activated distance daby an interaction between a slidable member 133 and a fixed-position member 135 that are arranged to interact with one another along a contact profile, which comprises at least one angled segment T. According to embodiments of the invention, the contact profile preferably also includes a straight-line segment S. The fixed-position member 135 may be represented by a gear-toothed wheel as illustrated schematically in Figure 1 a, and the slidable member 133 may include a set of teeth adapted to engage into the gear-toothed wheel 135. According to one embodiment of the invention, the adjuster mechanism 130 further includes a ratcheted control screw 139 that is mechanically linked to the first and second friction members 121 and 122. for example via a respective arm 123 and 124 and at least one interconnecting member 151 and 152 as illustrated in Figure 1 a. The ratcheted control screw 139 is arranged to be rotated by the interaction between the slidable member 133 and the fixed-position member 135 so as to gradually reduce the activated distance dain response to the first and second friction members 121 and 122 are worn w.

[0052] According to one embodiment of the invention, the first friction member 121 is attached to a primary end of a first arm 123 that is rotatably attached to a first joint P1 somewhere between the primary end and a secondary end of the first arm 123. The first joint P1 , in turn, is eccentrically mounted on a rotatable member 132, which is rotatably attached to a primary joint P PFIX that is fixedly mounted in the brake assembly 100. As will be discussed further below with reference to Figures 1 b and 1 c, this attachment of the first arm 123 has the effect that a rotation of the rotatable member 132 around the primary joint P PFIX causes the primary and secondary ends of the first arm 123 to translate essentially parallel to one another towards the rotating member 110 when a brake force is to be applied thereto by the first friction member 121.

[0053] Analogously, the second arm 124 has primary and secondary ends, where the second friction member 122 is mounted in the primary end. The second arm 124 is rotatably attached to a second joint P2FIX somewhere between the primary and secondary ends, which second joint P2FIX is fixedly mounted in the brake assembly 100.

[0054] According to one embodiment of the invention, the adjuster mechanism 130 contains the rotatable member 132. Moreover, the slidable member 133 is rotatably attached to the first joint P1 such that a movement of the first arm 123 by rotation of the a rotatable member 132 around the primary joint P PFIX causes the slidable member 133 to move together with the first arm 123. When moving the first friction member 121 to the engaged position P EN G the slidable member 133 is pushed towards the second joint P 2 FIX as illustrated in Figure 1 b.

[0055] In Figure 1 b, all reference signs and labels that also appear in Figure 1 a designate the same components / units as described above with reference to Figure 1 a.

[0056] According to the embodiment of the invention shown in Figures 1 a and 1 b, the fixed-position member 135 includes a contact element in the form of a gear-tooth wheel. The slidable member 133 here contains the at least one angled segment T of the contact profile plus a straight-line segment S of the contact profile.

[0057] Each of the straight-line segment S and the at least one angled segment T is arranged to interact with the contact element during operation of the brake assembly 100. Specifically, this means that when the first arm 123 moves towards the rotating member 110 in connection with applying a brake force and moves away from the rotating member 110 in connection with releasing the brake force, the slidable member 133 slides with its contact profile along the fixed-position member 135 in first and second directions respectively, where the second direction is opposite to the first direction.

[0058] According to one embodiment of the invention, a first connection member 151 is connected to the secondary end of the first arm 123 via a first joint PC1 , a second connection member 152 is connected to the secondary end of the second arm 124 via a second joint PC2 and the first and second connection members 151 and 152 respectively are interconnected via the ratcheted control screw 139. When a brake force is applied, the above-described translational movement of the first arm 123 where its primary and secondary ends move in parallel with one another also causes the second joint PC2 and the secondary end of the second arm 124 to be pushed in a direction that is essentially parallel to the translational movement of the first arm 123. As a further result, the second arm 124 rotates around the second joint P2 FIX, which, in turn, pushes the second friction member towards the rotating member 110. Consequently, a brake force is applied to the rotating member 110. In this process, the first friction member 121 makes contact with the rotating member 1 10 somewhat before the second friction member 122 does so. In practice, however, this has no detrimental effect on the braking efficiency.

[0059] The straight-line segment S of the contact profile is arranged to interact with the contact element 135 such that the first and second friction members 121 and 122 are movable between the engaged and disengaged positions P EN G and P DI S respectively without causing an adjustment of the ratcheted control screw 139 if, in the disengaged position P DI S , the friction members 121 and 122 are positioned within the joint margin range dmfrom the idle distance diDL.

[0060] The at least one angled segment T, which in Figures 1 a and 1 b is represented by a convex shape, is arranged to interact with the contact element 135 such that the activated distance dais reduced to an extent that depends on how long a distance the at least one angled segment T of the contact profile slides against the fixed- position member 135.

[0061] According to one embodiment of the invention, the adjuster mechanism 130 further comprises a shaft member 137 that connects the probing arrangement 131 to the ratcheted control screw 139. The shaft member 137 is arranged to cause a rotation of the ratcheted control screw 139 in response to the interaction between the slidable member 133 and the fixed-position member 135 along the at least one angled segment T of the contact profile. Referring now to Figure 1 c, more precisely, this interaction means that when the first friction member 121 is moved towards the engaged position P E NG the slidable member 133 is pushed in a general direction towards the second joint P2 FIX.

[0062] The slidable member 133 and the fixed-position member 135 are configured such that when each of the first and second friction members 121 and 122 is positioned in the respective disengaged position PDIS, the slidable member 133 and the fixed-position member 135 contact one another at a point on the straight-line segment S of the contact profile.

[0063] If, when the friction members 121 and 122 are positioned in the respective engaged positions P ENG , the activated distance dabetween them exceeds an adjustment threshold, the slidable member 133 and the fixed-position member 135 likewise contact one another at a point on the straight-line segment S of the contact profile.

[0064] However, if, when the friction members 121 and 122 are positioned in the respective engaged positions P ENG , the activated distance dais equal to or subceeds the adjustment threshold, the slidable member 133 and the fixed-position member 135 contact one another at a point on the angled segment T of the contact profile. This causes a translational movement M of the shaft member 137 along its symmetry axis such that the shaft member 137 pushes the ratcheted control screw 139 to be rotated in a first direction D1 , for example as illustrated in Figure 5. Here, the ratcheted control screw 139 is comprised in a housing 138 in which the shaft member 137 is arranged to act on a lever 538 via an actuator 537 that has a slack to the lever 538, such that the actuator 537 only acts on the lever 538 when the translational movement M has consumed the slack. The actuator 537, in turn, is preferably arranged to rotate the ratcheted control screw 139 via a free-wheel 539 in such a way that the translational movement M of the actuator 537 in one direction results in a rotation of the ratcheted control screw 139 in the first direction D1 , whereas the translational movement M of the actuator 537 in a direction opposite to said one direction exclusively results in that the freewheel rotates around the ratcheted control screw 139.

[0065] As mentioned above, according to one embodiment of the invention, the ratcheted control screw 139 is arranged between the first and second pivot joints PC1 and PC2 via the first connection member 151 to the first pivot joint PC1 and the second connection member 152 to the second pivot joint PC2. Here, the ratcheted control screw 139 is arranged such that a rotation thereof causes the screw 139 to expand and thus separate the first and second pivot joints PC1 and PC2 from one another. This further causes the second arm 124 to rotate R around the second joint P2 FIX and the first and second friction members 121 and 122 to approach one another, and consequently apply a brake force to the rotating member 110 as described above. The ratcheted control screw 139 here not only accomplishes compensation for the wear of the friction members 121 and 122, the ratcheted control screw 139 also ensures that a desired brake force may be applied to the rotating member 110.

[0066] Referring now to Figure 2, according to one embodiment of the invention, a slidable member 233 is mounted on an elongated member 255 that is connected to the first joint P1 .

[0067] In this embodiment, the slidable member 233 also contains the contact element and the fixed-position member 235 includes the at least one angled segment T of the contact profile plus a straight-line segment S of the contact profile. Hence, the roles described above with reference to Figures 1 a to 1 c are basically reversed in Figure 2. In Figure 2, however, each of the straight- line segment S and the at least one angled segment T is arranged to interact with the contact element and the straight-line segment S is arranged such that the friction members 121 and 122 are movable between the engaged and disengaged positions P EN G and P DI S respectively without causing an adjustment of the ratcheted control screw 139, if, in the respective disengaged position P DI S , the friction members 121 and 122 are positioned within the joint margin range dmfrom the idle distance diDL. Further, the at least one angled segment T is arranged to interact with the contact element such that the activated distance dais reduced to an extent that depends on how long a distance the contact element slides against the at least one angled segment T, which shows a general convex surface towards the slidable member 233.

[0068] Analogous the previously described embodiments of the invention the ratcheted control screw 139 is mechanically linked to the friction members 121 and 122, and the ratcheted control screw 139 is arranged to be rotated by the interaction between the slidable member 233 and the fixed-position member 235 so as to gradually reduce the activated distance dain response to the friction members 121 and 122 being worn w.

[0069] Figure 3 shows one embodiment of the invention that is similar to that of Figure 2, however in Figure 3, a fixed-position member 335 includes the at least one angled segment T of the contact profile plus a straight-line segment S of the contact profile, where the at least one angled segment T shows a surface towards the slidable member 233 that is straight and directed towards the symmetry axis of the shaft member 137 in such a way that the longer the slidable member 233 slides along the fixed-position member 335 over the angled segment T the further the shaft member 137 is caused to move M away from the fixed-position member along its symmetry axis thus causing the ratcheted control screw 139 to rotate around its axis in a first direction D1.

[0070] Figure 4 shows yet another embodiment of the invention that is similar to that of Figures 2 and 3, however in Figure 4, a fixed- position member 435 includes the at least one angled segment T of the contact profile plus a straight-line segment S of the contact profile, where the at least one angled segment T shows a surface towards the slidable member 233 that is concave and directed towards the symmetry axis of the shaft member 137 in such a way that the longer the slidable member 233 slides along the fixed- position member 435 over the angled segment T the further the shaft member 137 is caused to move M away from the fixed-position member along its symmetry axis thus causing the ratcheted control screw 139 to rotate around its axis in a first direction D1.

[0071] Figure 6 schematically illustrates a brake assembly 100 for a rail vehicle brake according to a second embodiment of the invention. In Figure 6, all reference signs and labels that also appear in Figures 1 a to 1 c designate the same components / units as described above with reference to Figures 1 a to 1 c.

[0072] The main difference between the embodiment of Figure 1 and the one illustrated in Figure 6 is that in the latter the angled segment T has a concave shape directed towards the symmetry axis of the shaft member 137 in such a way that the longer a slidable member 633 slides along a fixed-position member 635 over the angled segment T the further the shaft member 137 is caused to move M towards the fixed-position member along its symmetry axis - in stead of away from the same - and thus causes the ratcheted control screw 139 to rotate around its axis in a second direction D2, which, depending on the design of the ratcheted control screw 139, may or may not be opposite to the first direction D1.

[0073] To ensure that the slidable member 633 remains in contact with the fixed-position member 635 throughout the entire braking procedure, a compressible member 655 is preferably arranged to push the slidable member 633 towards the fixed-position member 635 while allowing the slidable member 633 to slide along the fixed-position member 635. The compressible member may be represented by a compression spring mounted between a fixed piece 654 in the brake assembly 100 and the slidable member 633, for example as illustrated in Figure 6.

[0074] Figure 13 shows one embodiment of the invention that represents an alternative to the embodiment discussed above with reference to Figures 6 to 9. In Figure 13, all reference signs and labels that also appear in Figures 6 to 9 designate the same components / units as described above with reference to Figures 6 to 9.

[0075] Here, the fixed-position member 1335 contains a guide track G that is configured to lead the slidable member 233 in the fixed- position member 1335 throughout a braking procedure wherein the first and second friction members 121 and 122 are moved bet- ween the respective engaged and disengaged positions PENG and PDIS. The guide track G, in turn, has first and second straight-line segments S1 and S2 respectively and first and second angled segments T1 and T2 respectively, which are arranged to lead the slidable member 233 such that the slidable member 233 is in contact with at least one of the segments S1 , S2, T1 and / or T2 at each point in time during the braking procedure. For example, the guide track G may be designed as shown in Figure 13, i.e. , where the first straight-line segments S1 and the first angled segment T1 are arranged on a first side of the slidable member 233, the second straight-line segments S2 and the second angled segment T2 are arranged on a second side of the slidable member 233, and the first and second angled segments T1 and T2 are angled in such a way that the longer the slidable member 233 slides along the guide track G the further the shaft member 137 is caused to move in a consistent direction in relation to the fixed-position member 1335, e.g., leftwards Figure 13. It should be noted that the shaft member 137 may equally well be caused to move in any other consistent direction different from an orientation of the straight-line segments S1 and S2, such as rightwards.

[0076] Figure 10 shows a housing 638 that contains the ratcheted control screw 639, which housing 638 is configured to receive the shaft member 137 such that the shaft member 137 may act on the lever 538 via the actuator 537 via a slack to the lever 538, such that the actuator 537 only acts on the lever 538 when the translational movement M has consumed the slack. The actuator 537, in turn, is preferably arranged to rotate the ratcheted control screw 639 via a free-wheel 539 in such a way that the translational movement M of the actuator 537 in one direction results in a rotation of the ratcheted control screw 639 in the second direction D2, whereas the translational movement M of the actuator 537 in a direction opposite to said one direction exclusively results in a rotation of the free-wheel around the ratcheted control screw 639.

[0077] Figures 7 to 9 show different embodiments of the proposed probing mechanism 131 wherein different types of fixed-position members contain at least one angled segment T of the contact profile, and a slidable member is arranged to interact with the contact profile to cause the shaft member 137 to act on the ratcheted control screw 639 in a direction being opposite to the movement M illustrated in Figure 1 c.

[0078] Figure 7 shows one embodiment of the invention, where, analogous to Figure 6, the angled segment T has a concave shape. In Figure 7, however, the contact profile is included in a fixed-position member 735 and a slidable member 733 is mounted on an elongated member 755 that is connected to the first joint P1 . The concave shape of the angled segment T is directed towards the symmetry axis of the shaft member 137 in such a way that the longer the slidable member 733 slides along the fixed-position member 735 over the angled segment T the further the shaft member 137 is caused to move towards the fixed-position member 735 along its symmetry axis thus causing the ratcheted control screw 639 to rotate around its axis in the second direction D2.

[0079] Figure 8 shows one embodiment of the invention, where the angled segment T has a straight shape and a slidable member 833 is mounted on an elongated member 855 that is connected to the first joint P1 . The straight shape of the angled segment T is directed towards the symmetry axis of the shaft member 137 in such a way that the longer the slidable member 833 slides along the fixed-position member 835 over the angled segment T the further the shaft member 137 is caused to move towards the fixed-position member 835 along its symmetry axis thus causing the ratcheted control screw 639 to rotate around its axis in the second direction D2.

[0080] Figure 9 shows one embodiment of the invention, where the angled segment T has a convex shape and a slidable member 933 is mounted on an elongated member 955 that is connected to the first joint P1 . The convex shape of the angled segment T is directed towards the symmetry axis of the shaft member 137 in such a way that the longer the slidable member 933 slides along the fixed-position member 935 over the angled segment T the further the shaft member 137 is caused to move towards the fixed-position member 935 along its symmetry axis thus causing the ratcheted control screw 639 to rotate around its axis in the second direction D2.

[0081] Analogous to the above, according to embodiments of the invention, the at least one angled segment T may contain a set of teeth and the contact element may include a rotatable gear-toothed member, e.g., 233 or 733, which is arranged to engage into the set of teeth of the at least one angled segment T so as to in response to said engagement cause the adjustment of the ratcheted control screw 139 or 639 respectively.

[0082] In Figures 1 a - 1 c, 2 - 4 and 6 - 9, the specific distance that the shaft member 137 is caused to move M when the slidable member 233 slides along the fixed-position member 435 over the angled segment T depends on the specific dimensions of the components involved, inter alia the dimensions of the slidable members 133, 233, the elongated member 255, and the fixed-position members 135, 235, 335, 435, 735, 835 and 935 respectively. Hence, a desired gear ratio may be attained by choosing said dimensions.

[0083] Figure 1 1 shows a diagram that exemplifies how the activated distance dabetween the friction members 121 and 122 may be adjusted for wear w of the friction members according to a stepwise procedure. The diagram shows the wear w along the horizontal axis and indicates activated distance daalong the vertical axis.

[0084] Preferably, the ratcheted control screw 139 and 639 respectively is configured to reduce the activated distance dabetween the friction members 121 and 122 according to a stepwise procedure, where two consecutive steps in the stepwise procedure are separated from one another by an increment equivalent to less than or equal to the joint margin range dm. Namely, thereby it can be guaranteed that the idle distance diDL remains within joint margin range dm. Figure 12 shows a diagram illustrating how the activated distance dabetween the friction members 121 and 122 may be adjusted for wear w according to a continuous procedure. The diagram shows the wear w along the horizontal axis and indicates activated distance daalong the vertical axis. A continuous adjustment procedure may be attained if the ratcheted control screw 139 and 639 respectively is configured to reduce the activated distance dabetween the friction members 121 and 122 continuously.

[0085] The term “comprises / comprising” when used in this specification is taken to specify the presence of stated features, integers, steps or components. The term does not preclude the presence or addition of one or more additional elements, features, integers, steps or components or groups thereof. The indefinite article "a" or "an" does not exclude a plurality. In the claims, the word “or” is not to be interpreted as an exclusive or (sometimes referred to as “XOR”). On the contrary, expressions such as “A or B” covers all the cases “A and not B”, “B and not A” and “A and B”, unless otherwise indicated. The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measures cannot be used to advantage. Any reference signs in the claims should not be construed as limiting the scope.

[0086] It is also to be noted that features from the various embodiments described herein may freely be combined, unless it is explicitly stated that such a combination would be unsuitable.

[0087] Variations to the disclosed embodiments can be understood and effected by those skilled in the art in practicing the claimed invention, from a study of the drawings, the disclosure, and the appended claims.

[0088] The invention is not restricted to the described embodiments in the figures, but may be varied freely within the scope of the claims.

Claims

24Claims1. A brake assembly (100) for a rail vehicle, which brake assembly (100) comprises: a rotating member (110) mechanically linked to a wheel axle of the rail vehicle, first and second friction members (121 ; 122) movable between a respective engaged position (PENG) in which the first and second friction members (121 ; 122) contact the rotating member (110) from opposing first and second sides respectively, and a respective disengaged position (PDIS) in which the first and second friction members (121 ; 122) are positioned at an idle distance (diDi) from the rotating member (110), an actuator (120) arranged to obtain a control signal (CS) and in response thereto control the first and second friction members (121 ; 122) to attain the respective engaged position (P ENG) , and an adjuster mechanism (130) configured to control the first and second friction members (121 ; 122) such that in the disengaged position (PDI S) the first and second friction members (121 ; 122) are positioned within a joint margin range (dm) from the idle distance (diDi) notwithstanding any wear (w) of the first and second friction members (121 ; 122), characterized in that the adjuster mechanism (130) comprises a probing arrangement (131 ) mechanically linked to the first and second friction members (121 ; 122), which probing arrangement (131 ) is arranged to control the first and second friction members (121 ; 122) such that an activated distance (da) by which the first and second friction members (121 ; 122) are separated from one another in the respective engaged position (PENG) decreases according to a monotonic function as the first and second friction members (121 ; 122) are worn (w), and which probing arrangement (131 ) is configured to set the activated distance (da) by an interaction between a slidable member (133, 233, 633, 733) and a fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) arranged to interact with one another along a contact profile that comprises at least one angled segment (T, T1 , T2).

2. The brake assembly (100) according to claim 1 , wherein the adjuster mechanism (130) comprises: a ratcheted control screw (139, 639) that is mechanically linked to the first and second friction members (121 ; 122), which ratcheted control screw (139, 639) is arranged to be rotated by the interaction between the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) so as to gradually reduce the activated distance (da) in response to the first and second friction members (121 ; 122) being worn (w).

3. The brake assembly (100) according to claim 2, wherein: the first friction member (121 ) is attached to a first arm (123) that is rotatably attached to a first joint (P1) which, in turn, is eccentrically mounted on a rotatable member (132) rotatably attached to a primary joint (PPFIX) that is fixedly mounted in the brake assembly (100), and the second arm (124) is rotatably attached to a second joint (P2FIX) that is fixedly mounted in the brake assembly (100).

4. The brake assembly (100) according to claim 3, wherein: the adjuster mechanism (130) comprises the rotatable member (132), and the slidable member (133, 233, 633, 733) is rotatably attached to the first joint (P1 ) such that a movement of the first arm (123) by rotation of the a rotatable member (132) around the primary joint (PPFIX) causes the slidable member (133, 233, 633, 733) to move together with the first arm (123).

5. The brake assembly (100) according to any one of claims 3 or 4, wherein: the fixed-position member (135) comprises a contact element, and the slidable member (133, 633) comprises the at least one angled segment (T, T1 , T2) of the contact profile plus a straight- line segment (S, S1 , S2) of the contact profile, wherein each ofthe straight-line segment (S, S1 , S2) and the at least one angled segment (T, T1 , T2) is arranged to interact with the contact element during operation of the brake assembly (100), the straight- line segment (S, S1 , S2) being arranged to interact with the contact element such that the first and second friction members (121 ; 122) are movable between the respective engaged and disengaged positions (PENG ; PDIS) without causing an adjustment of the ratcheted control screw (139, 639), if, in the respective disengaged position (PDIS) , the first and second friction members (121 ; 122) are positioned within the joint margin range (dm) from the idle distance (diDi), and the at least one angled segment (T, T1 , T2) is arranged to interact with the contact element such that the activated distance (da) is reduced to an extent that depends on how long a distance the at least one angled segment (T, T1 , T2) of the contact profile slides against the fixed-position member (135).

6. The brake assembly (100) according to any one of claims 3 or 4, wherein: the slidable member (233, 733) comprises a contact element, and the fixed-position member (235, 335, 435, 635, 735, 835, 935, 1335) comprises the at least one angled segment (T, T1 , T2) of the contact profile plus a straight-line segment (S, S1 , S2) of the contact profile, wherein each of the straight-line segment (S, S1 , S2) and the at least one angled segment (T, T1 , T2) is arranged to interact with the contact element, and the straight-line segment (S, S1 , S2) is arranged such that the first and second friction members (121 ; 122) are movable between the respective engaged and disengaged positions (PENG; PDIS) without causing an adjustment of the ratcheted control screw (139, 639), if, in the respective disengaged position (PDIS) , the first and second friction members (121 ; 122) are positioned within the joint margin range (dm) from the idle distance (diDi), and the at least one angled segment (T, T1 , T2) is arranged to interact with the contact element such that the activated distance (da) is reduced to an extent27 that depends on how long a distance the contact element slides against the at least one angled segment (T, T1 , T2).

7. The brake assembly (100) according to any one of claims 5 or 6, wherein the at least one angled segment (T) comprises a set of teeth and the contact element comprises a rotatable gear-toothed member (233, 733) arranged to engage into the set of teeth of the at least one angled segment (T) so as to in response to said engagement cause the adjustment of the ratcheted control screw (139, 639).

8. The brake assembly (100) according to any one of claims 3 to 7, wherein the adjuster mechanism (130) further comprises a shaft member (137) connecting the probing arrangement (131 ) to the ratcheted control screw (139, 639), which shaft member (137) is arranged to cause a rotation of the ratcheted control screw (139, 639) in response to the interaction between the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) along the at least one angled segment (T) of the contact profile.

9. The brake assembly (100) according to claim 8, wherein the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935) are configured such that: when each of the first and second friction members (121 ; 122) is positioned in the respective disengaged position (PDIS), the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) contact one another at a point on the straight-line segment (S, S1 , S2) of the contact profile; if, when the first and second friction members (121 ; 122) are positioned in the respective engaged positions (PENG) , the activated distance (da) exceeds an adjustment threshold, the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) contact one another at28 a point on the straight-line segment (S, S1 , S2) of the contact profile; and if, when the first and second friction members (121 ; 122) are positioned in the respective engaged positions (PENG), the activated distance (da) is equal to or subceeds the adjustment threshold, the slidable member (133, 233, 633, 733) and the fixed-position member (135, 235, 335, 435, 635, 735, 835, 935, 1335) contact one another at a point on the angled segment (T, T1 , T2) of the contact profile, thus causing a translational movement (M) of the shaft member (137) along its symmetry axis such that the ratcheted control screw (139, 639) is rotated.

10. The brake assembly (100) according to claim 9, wherein the ratcheted control screw (139, 639) is arranged between first and second pivot joints (PC1 ; PC2), which first pivot joint (PC1 ) is rotatably attached to the first arm (123) and which second pivot joint (PC2) is rotatably attached to the second arm (124), and the ratcheted control screw (139, 639) is arranged such that rotation thereof causes: the first and second pivot joints (PC1 ; PC2) to be separated from one another, the second arm (124) to rotate (R) around the second joint (P2FIX) and the first and second friction members (121 ; 122) to approach one another.

11. The brake assembly (100) according to claim 10, wherein the angled segment (T) has a convex, straight or concave shape directed towards the symmetry axis of the shaft member (137) in such a way that the longer the slidable member (133, 233) slides along the fixed-position member (135, 235, 335, 435) over the angled segment (T) the further the shaft member (137) is caused to move (M) away from the fixed-position member along its symmetry axis thus causing the ratcheted control screw (139) to rotate around its axis in a first direction (D1 ).2912. The brake assembly (100) according to claim 10, wherein the angled segment (T, T1 , T2) has a concave, straight or convex shape directed towards the symmetry axis of the shaft member (137) in such a way that the longer the slidable member (633, 733) slides along the fixed-position member (635, 735, 835, 935, 1335) over the angled segment (T, T1 , T2) the further the shaft member (137) is caused to move (M) towards the fixed-position member along its symmetry axis thus causing the ratcheted control screw (139) to rotate around its axis in a second direction (D2).

13. The brake assembly (100) according to claim 12, comprising a compressible member arranged to push the slidable member (633, 733) towards the fixed-position member (635, 735, 835, 935) while allowing the slidable member (633, 733) to slide along the fixed-position member (635, 735, 835, 935).

14. The brake assembly (100) according to claim 12, wherein the fixed-position member (1335) comprises a guide track (G) configured to lead the slidable member (233) in the fixed-position member (1335) throughout a braking procedure wherein the first and second friction members (121 ; 122) are moved between the respective engaged and disengaged positions (PENG; PDIS), which guide track (G) comprises first and second straight-line segments (S1 ; S2) and first and second angled segments (T1 ; T2) that are arranged to lead the slidable member (233) such that the slidable member (233) is in contact with at least one of said segments (S1 , S2, T1 , T2) at each point in time during the braking procedure.

15. The brake assembly (100) according to any one of claims 2 to 14, wherein the ratcheted control screw (139, 639) is configured to reduce the activated distance (da) between the first and second friction members (121 ; 122) continuously.

16. The brake assembly (100) according to any one of claims 2 to 14, wherein the ratcheted control screw (139, 639) is configured to reduce the activated distance (da) between the first and second30 friction members (121 ; 122) according to a stepwise procedure.

17. The brake assembly (100) according to claim 16, wherein two consecutive steps in the stepwise procedure are separated from one another by an increment equivalent to less than or equal to the joint margin range (dm).

18. The brake assembly (100) according to any one of the preceding claims, wherein the actuator (120) is configured to be operated pneumatically or hydraulically in response to receiving the control signal (CS) as a variation in a fluid pressure level.

19. The brake assembly (100) according to any one of claims 1 to 17, wherein the actuator (120) is configured to be operated electromechanically in response to receiving the control signal (CS) on an electrical format.

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