Annular disc brake, and method for increasing gripping force of brake shoe

FIELD: machine building.

SUBSTANCE: annular disc brake includes a rotating disc and at least one disc shoe installed on each side of the rotating disc. Brake shoe or shoes on one side are connected to an axially guided load-carrying element of the brake shoe. The brake has a force transfer mechanism creating enhancement of increase in force between the axially driven element and load-carrying element. The method for increasing gripping force of brake shoe in annular disc brake consists in the fact that the first force is generated synchronously with the brake drive; at that, the first force has the direction that is parallel to rotation axis of the rotating disc. Also, rotating torque is generated using the first force; at that, rotating torque has the rotation centre that coincides with rotation axis of the rotating disc. Besides, the second force is generated using rotating torque; at that, the second force has the direction that is essentially identical to the direction of the first force and is higher than the first force. The second force is used for gripping of brake shoes on opposite sides of the rotating disc.

EFFECT: increasing brake compactness and providing uniform distribution of braking force in a circumferential direction of the rotating disc.

20 cl, 12 dwg

 

The technical field

The present invention relates to a circular disc brakes and to a method of increasing the effort of setting the brake pads in a circular disc brakes.

The level of technology

Ring disc brakes sometimes previously called full contact ring disc brakes. The annular disk brake includes at least one rotating disk, which is axially movable relative to the stationary component. The rotating disk is connected, transmitting the torque from the rotating element, such as, for example, a wheel of the vehicle. The rotating disk is placed axially between the one or more brake pads on one side and one or more movable brake pads on the opposite side of the rotating disk. A set of movable brake shoes axially pressed against the corresponding side of a rotating disk with a drive, for example, pneumatic, hydraulic or electric drive. When the stationary and movable brake pads are grasping the connection with the sides of the rotor disk, there is a friction braking and heat is generated.

In the design of the ring disc brakes there are many difficult moments. One of them is not bodymist create sufficient grasping efforts using the actuator, which can fit in the space provided for brake space. Ring disc brakes are often installed in vehicles, and they are usually installed inside the vehicle wheels or very close to it. Thus, the available space is relatively limited, even in large vehicles. In addition, vehicle manufacturers are constantly looking for brakes, more and more compact, to reduce this space. When designing circular disc brakes, designed for connection to the pneumatic system used as the primary energy source for these brakes, some requirements may be particularly difficult to perform. When designing the annular disk brakes there is always room for improvements.

Brief description of the invention

According to one object serves a disc brake having a Central axis and characterized in that it contains: main bearing, located coaxially relative to the Central axis (R); a rotating disc located coaxially relative to the Central axis and which interact with each slide and transfer torque from the main support, the rotary disk has opposite first and storystory; the housing is attached to the main bearing for rotation around a Central axis; at least one first brake Shoe having a surface directed towards the first side of the rotating disc, and at least one first brake pad is connected inside the housing; at least one second brake pad having a surface directed towards the second side of the rotating disk; essentially axially directed bearing element brake pads, located coaxially relative to the Central axis, while the bearing element brake pads has mutually opposite first and second sides; and at least one second brake pad connected to the first side bearing element brake pads; a drive unit coupled to the housing and containing an axially driven element, and mechanism of force transmission containing the first Cam interface between the axially driven element and the intermediate element located axially between the driven element and the second side support member, brake pads, and an intermediate element located coaxially relative to the Central axis and rotates in a radial plane; thus, the mechanism further comprises a second Cam interface between the intermediate e is a COP and the second side bearing element brake pads, moreover, when the intermediate element is turned, the bearing element brake pads makes axial movement, so that this mechanism generates the gain increases efforts axially between the driven element and the second side bearing element brake pads.

According to another object offers a way to increase the effort of setting the brake pads in the annular disk brake including an actuator and a rotary disk having an axis of rotation, and the method is characterized in that it contains the following simultaneous steps: creating a first force by the drive of the brake, and the first force has a direction that is parallel to the axis of rotation of the rotary disc; create torque by using the first power, the moment of rotation is the center of rotation, which essentially coincides with the axis of rotation of the rotating disk; a second power using torque, and the second force has a direction that is essentially identical to the direction the first force is the value greater than the first force; and using a second force for grasping the brake pads on opposite sides of a rotating disk.

Presents various aspects of the improvements will be apparent after reading the following detailed description presented along the attached drawings.

Brief description of drawings

Fig. 1 is an isometric view showing the appearance of an example of a ring disc brakes with an example of an improved configuration;

Fig. 2 is an isometric view showing the inner part of the brake of Fig. 1;

Fig. 3 is an enlarged isometric view of the brake of Fig. 1 with the neck;

Fig. 4 is a view similar to Fig. 1, with some components shown removed from the rest of the brakes;

Fig. 5 is an isometric view showing the rear part of the two parts, external body parts brakes with Fig. 1, and their respective brake pads, separated from them;

Fig. 6 is an isometric view showing the main caliper, the caliper of the disc and connecting elements of a rotating disk used in the brake of Fig. 1;

Fig. 7 is an isometric view showing the various components shown in Fig. 6, which are collected together;

Fig. 8 is an isometric view with the division of parts of the brake of Fig. 1;

Fig. 9 is an isometric view of the rear part of the bearing brake pads, and the inner sleeve inner hull installed in the brake of Fig. 1;

Fig. 10 is an isometric view, showing some of the components located at the rear of the brake of Fig. 1;

Fig. 11 is a view showing the sub-node with the components according to Fig. 10 another is glam;

Fig. 12 is a view showing the sub-node with the components according to Fig. 8 different angle.

Detailed description of the invention

Fig. 1 and 2 show an example of the assembled annular disk brake 10 with the example of an improved configuration. Shows the brake 10 is designed for use in the right front wheel (not shown) of a large vehicle such as a truck or bus. Fig. 1 is a view of the outer part, and Fig. 2 is a view of the inner part of the brake 10. The terms "external" and "internal" in this context, refers to the relative position with respect to the longitudinal axis through the center of the vehicle. The wheel of the vehicle rotates in the direction of rotation-clockwise for an observer looking at the outer part shown in Fig. 1, when the vehicle moves forward. The arrow labeled "FORWARD" shown in Fig. 1, as well as some other illustrations to indicate the direction of rotation of the rotating components of the brake 10, when the vehicle moves forward. This corresponds to the main direction of rotation of the brake 10.

It should be noted that the brake is similar to the brake 10, which is designed for use with the front left side of the vehicle, should be a mirror reflection of the fact that p is shown in this illustration. The brake 10, as shown, may be modified for use on many different types of vehicles, including vehicles that are not designed to move on the road, such as airplanes. In addition, you can also use brake 10 on machines that are not vehicles. Such machines may have, for example, pulleys or other rotating element, which is connected to the brake 10. The use of the term "vehicle" or its equivalents in this text applies only to the illustrated example and does not necessarily exclude the use of the brake 10 in other environments.

Illustrated brake 10 includes a main support 12 to which is attached a wheel rolling machine. Bearing 12 is installed with the internal rotation around the Central shaft 14, which is located coaxially relative to the Central axis R of the brake 10 (see Fig. 3). The axis of rotation of the wheel coincides with the Central axis R of the brake 10.

Support 12 has a lot of axisymmetric locating pins 16 protruding outward from the annular section 12A of support 12. In the illustrative example shows the ten mounting screws 16. This configuration is common for large trucks. It should be noted that the threaded mounting bolts 16 are not shown.

Illustrated bearing 12 has inner and the cavity 18 of the bearing. The cavity 18 of the bearing shown open from the outside. On the outer side opening of the cavity 18 of the bearing can be hermetically closed by a cap (not shown), which is attached to the circular flange 12b, which is located around the outside of the hole. This cover can be useful to prevent the ingress into the cavity 18 of the bearing dirt or other contaminants from the outside. It is also possible other configurations.

Inside many of the components illustrated brake 10. This case contains the outer part 20 of the casing and the inner part 22 of the housing. In the illustrative example, the outer portion 20 of the housing shown divided circumferentially into two halves 20A and 20b. These two halves 20A and 20b are fastened together by means of two bolts 24. In addition, in the illustrative example, the shaft 14 is connected with the interior of the housing 22, as is more fully explained hereinafter, thereby forming a single whole with it.

The outer part 20 of the housing attached to the inner part 22 of the housing using a variety of bolts 26. The outer part 20 of the housing has multiple flanges, distributed around the circumference, which are held in the axial direction towards the inner part 22 of the housing and which provide attachment points for the respective bolts 26. The flanges 28 of the outer part 20 of the housing are separated from each other and have inner and corresponding holes 30. This open configuration favors the circulation of air within the brake 10. It is also possible options.

The outer part 20 and the interior of the housing 22 are parts that do not rotate together with the support 12 when the mobile device is in motion. However, in this illustrative example, they are connected with the frame or body of the vehicle by means of trunnion 32. Swivel pin 32 is turned down very low bolted to the rear side of the inner part 22 of the housing. In Fig. 2 shows the swivel pin 32 and some of the bolts 34 installed for mounting trunnion 32 to the interior of the housing 22. Swivel pin 32 is used because the brake 10 in this illustrative example, is designed for the front wheel. There are also other options. For example, if the brake 10 is used in a "non-environment", for example, on apolorazepam wheel such as the wheel, installed in the rear of most vehicles, the outer portion 20 of the housing and the interior of the housing 22 can be directly connected with such items as yoke or arm. After that, the inner part 22 of the case can be directly connected to the axle. Depending on requirements, it is also possible to develop other configurations.

In this ill the administrative example, the node 40 of the actuator, in General, has an annular configuration and is connected to the outer housing, more precisely, to the rear side of the inner part 22 of the housing with bolts 36. The inner part 22 of the housing, thus placed between the outer part 20 of the casing and hub 40 of the actuator. The node 40 of the drive can also be connected to the housing in any other way. As you can see, setting the node 40 of the actuator on the inner side of the inner part 22 of the body can increase the compactness of the brake 10, as compared with constructions in which the drive unit is located inside the case.

Fig. 2 also shows the inlet opening 42 near pressurized fluid medium for node 40 of the actuator. In the case of a pneumatic drive unit inlet 42 may be pneumatic connector receiving pressurized gas, pressurized air, which is the brake control 10. The force generated by the node 40 to the drive, then controlled by the input pressure node 40 of the actuator. You can also drive brake 10 with the use of pressurized fluids, such as pressurized oil, or using an electric drive. However, in the case when any vehicle, e.g. a truck, uses a pneumatic actuator drive, the brake 10 can be is designed with a mode of protection against malfunction, so, if the input of the inlet there is no pressure or the pressure at the inlet opening is insufficient, the brake 10 is automatically set to a full or almost full braking. Likewise directly inside the node 40 of the actuator can set the valve or other elements for controlling pressurized fluid medium. In this case, the inlet could only receive the fluid under a relatively constant pressure, and control enable brake 10 was produced in the brake remote commands. Remote control command can be electrical, mechanical or even a team that uses a circuit (not shown) other pressurized fluid connected to the brake 10 through another inlet.

Fig. 3 is an enlarged view of the brake 10 according to Fig. 1, the brake 10 is shown with a cutout. This drawing shows the support 12, and also shows how in this illustrative example, the bearing 12 mounted to rotate around the shaft 14. As shown in the drawing, the support 12 includes passing back hollow section 12C, coupled with its annular section 12A. Within the cavity 18 of the bearing supports 12 are two spaced apart bearing 50, 52. The inner ring needle bearing is nicks 50, 52 seated on the shaft 14 and the outer ring are planted inside the ring section 12A and the hollow section 12C supports 12, respectively. The bearings 50, 52 coaxial with the Central axis R of the brake 10.

In addition, in Fig. 3, the shaft 14 is connected with radially located by a flange 54, which, in turn, is connected to or made as a single unit with the other components of the inner part 22 of the housing. Shows the flange 54 has a lot of holes 56 through which the bolts 34 securing the housing to the stub axle 32.

It must be said that it is shown in this illustrative example of a specific configuration of the bearings 50, 52, is only one of many possible configurations. For example, in some configurations it may be necessary that the cavity 18 of the bearing was located on the outer side relative to the annular section 12A of support 12. In this configuration, the shaft is longer than shown on the drawing. It is also possible many other configurations.

In Fig. 3 shows that the inner part 22 of the housing illustrated brake 10 has an internal circular flange 22A having a number of holes, which are exposed position relative to the holes 56 of the flange 54, which is connected to the shaft 14. Some of the other components shown in Fig. 3, are explained next.

Fig. 4 is isometrica the cue type, similar to the Fig. 1. It shows two separated one from the other halves 20A, 20b of the outer part 20 of the housing, thereby opening the rotating disk 60 of the brake 10. However, it should be noted that in Fig. 4 shows the rotating disk 60 without his support. This bearing will be described later. The rotating disk 60 is coaxial relative to the Central axis R (see Fig. 3). Therefore, the rotating disk 60 is the rotating part of the brake 10, and the axis of rotation of the rotating disc 60 is coincident with the Central axis R of the brake 10.

Fig. 4 optionally further shows that on the rear side of the two halves 20A, 20b of the outer part 20 of the body are the brake pads 62. These brake pads 62 best shown in Fig. 5, which is an isometric view showing the rear part of the two halves 20A, 20b, and their respective brake pads 62. Each brake pad 62 is attached to the corresponding half 20A, 20b or made in one piece with it. Although the illustrative example shows two polukrasnye brake pads 62, one on each of the halves 20A, 20b, it is possible to use a single circular brake pad (not shown)that provides a contact in 360 rotating disk 60, or to use more than two polukrasnye brake pads. The outer part 20 of the housing can also be made in the form of a single block is a, not divided into two halves.

The brake pads 62 can be connected inside the housing using screws or other demountable fasteners, or can be tightly attached to the halves 20A, 20b. For example, a metal rear brake pads 62 may be welded or narashima attached to respective of the halves 20A, 20b. Thus, when the brake pads 62 will wear out the brake pads 62 will be impossible to detach from the halves 20A, 20b to replace them. Installing a new set of halves 20A, 20b of the hull is carried out along with them the brake pads 62 simplifies maintenance and, in addition, the brake pads 62 will always be in the correct position inside the halves 20A, 20b.

In this illustrative example, the brake pads 62 connected with the halves 20A, 20b have respective surface a, which interacts with the outer surface 60A of the rotating disc 60. The inner surface 60b of the rotating disc 60 communicates with another set of brake pads 64 and the brake pads 64 are shown separated from the rest of the brake 10 in Fig. 4. Surfaces 60A, 60b of the rotating disc 60 can be processed in such a way as to have the maximum level of concentric, with due form and surface treatment. Ka which will be explained hereinafter, the second set of brake pads 64 is mounted on an axially directed bearing element 66 brake pads.

When appropriate surfaces 64A of the inner brake pad 64 interact with the inner surface 60b of the rotating disc 60, the rotating disk 60 tightened closer to the brake pads 62 located on the outer side. Because they are attached to the outer part 20 of the housing, the brake pads 62 on the outer side is fixed in a suitable position. In the end, the rotating disk 60 "concatenated" the brake pads 62, 64 on both sides. Increase the force with which the brake pads 64 interact with the outer surface 60b of the rotating disk, increases the force of the "seizure" of the brakes, and thus, the friction from the brake pads 62, 64 on both sides of the rotating disc 60. The kinetic energy resulting from movement of the vehicle or due to the vehicle's engine, then the brake 10 is converted into heat to a complete stop the vehicle or to the implementation efforts of "gripping" brake pads. The heat from the brakes 10, eventually dissipates in the atmosphere.

Fig. 6 is an isometric view with the division of parts, showing the rotating disk 60 in cross section, and bearing 70 of the rotating disk, the use of which has been created in this illustrative example, to install a rotating disk 60 on the support 12. As mentioned earlier, the support 70 of the rotating disk of Fig. 4 is not shown. Fig. 7 shows the components of Fig. 6 after Assembly. It should be noted that in Fig. 6 and 7 illustrates only half of the rotary disc 60.

The rotating disk 60 illustrative example was made using two parallel walls forming mutually opposite outer surfaces 60A, 60b. These walls are connected together through a set of asymmetric edges 60C, passing in the radial direction and forming air channels, as shown for example in Fig. 6. The heated air tends to enter radially outward and cooler air flows in a radially inner portion of the rotary disc 60. The inner part attached to this form, which corresponds to the support 70 of the rotating disk. Different parts of a rotating disk 60 can be made integrally with each other. Other options are also possible.

As mentioned above, the rotating disk 60 is rotating and the adhesion to the support 12, and the bearing 70 of the rotating disc allows the rotating disk 60 to move in the axial direction relative to the support 12. This axial displacement has a value that compensates for the wear of the outer pads. In addition, it should be sufficient for departing from the brake pads 62 installed on the outer part 20 cor the USA with the disappearance of the braking effort. Accordingly, when the brake 10 is in an idle state, the rotating disk 60 should not be too hard to interact with the brake pads 62, in order to minimize friction.

Bearing 70 of the rotating disk of this illustrative example is, in General, a ring element which is coaxial to the Central axis R of the brake 10 (see Fig. 3). Bearing 70 of the rotating disk has a cylindrical inside, covered with material with low friction, and coupled around the circumference of the hollow section 12C supports 12. Circumferential portion 70 of the rotating disk equipped with a plurality of axially protruding fingers 72 that are located on it asymmetrically. The fingers 72 have outer side 72A, freely included in the corresponding sleeve 74 that is integrally made with the rear sides of the ring section 12A of support 12. In the illustrative example, made five speakers fingers 72. However, you can use a different number of fingers and, in addition, you can also change the relative position of the fingers 72 and bushing 74.

As better shown in Fig. 6 and 7, the sleeve 74 of the illustrative example are located between the heads of two mounting bolts 16. Two bushings 74 are separated by the heads of the two installation bolts 16. Sleeve 74 are interconnected by an annular reinforcing wall 76. At least one of the speakers of the fingers 72 and one and the bushings 74 are mutually mating surface from a material with low friction, either in the form of a coating or in the form of a sleeve. Thus, the mutual axial displacement of the rotating disk 60 and the seat 12 can be relatively easy. In addition, the fingers 72 illustrative example have something like a Central area 72s, which has a larger diameter than the diameter of the bushings 74. These Central areas 72s act as stops.

As shown in Fig. 7, the rotating disk 60 is associated with his arm 70 by set screws or bolts 78 that is inserted into the threaded holes in the inner side 72b of the fingers 72. As shown in the drawing, the fingers 72 are connected with the rest of the support 70 of the rotating disk using a radially protruding brackets 80, 82. In addition, Fig. 7 shows that between the support 70 of the rotating disk and the inner part of the rotary disc 60 can be made large holes that facilitate air circulation. It is also possible options.

It should be noted that the outer diameter of the fingers 72 on the outer side 72A not necessarily the same as on the inner side 72b.

During operation, when the wheel, which is connected with a support 12 rotates, when the brake 10 embracing the force applied brake pads 62, 64 to each side of the rotating disc 60, tends to slow the rotation of this rotating disk 60, thereby creating a braking torque in the direction of the AI, opposite direction of rotation. This braking torque by means of the axially protruding fingers 72 is transmitted from the rotating disk 60 to the wheel. Therefore, these fingers 72 perceive themselves essentially all of the braking torque of the brake 10.

There are many other ways that can be devised to create rotational interaction between the support 12 and the rotating disk 60. However, it is shown bearing 70 of the rotating disc has a good semicentenary capacity and can hold the rotating disk 60 in a radial plane. The hysteresis brake 10 can also be very low.

Fig. 8 is an isometric view with distributed components of the brake shown in Fig. 1-3. It should be noted that the inner part shows the rotating disc 60 is somewhat different from that shown in Fig. 6 and 7. In Fig. 8 components which rotate with the wheel, are bearing 12 and the rotating disk 60. Of course, the support 70 of the rotating disk (Fig. 8 not shown) also rotates together with the wheel. As already mentioned, the outer portion 20 of the housing and the inner part 22 of the housing does not rotate together with the support 12. In the illustrative example, they can be connected with the stub axle 32, as shown in Fig. 1-3, by means of bolts 34. In Fig. 8 shows only some of the bolts 34. Node 40 PR is water connected to the rear part of the inner part 22 of the housing, as described later.

As already mentioned, the brake pads 64 connected to one side of the axially directed bearing member 66 brake pads. Bearing element 66 brake pads illustrative example includes two concentric annular element 66A, 66b (see Fig. 9), which are connected together using four axisymmetric roller support assemblies 68. This detachable connection simplifies maintenance, since the brake pads 64, when worn, can be replaced without having to remove the brake 10 bearing element 66 brake pads. Thus, as shown in Fig. 4, the brake 10 allows maintenance of the inner side of the simple removal of two brake pads 64 of the bearing member 66 brake pads. This can be done, for example, by moving the locking mechanism or bolts (not shown).

As for the brake pads 62 on the outer side, instead of two polugruppovykh brake pads 64 you can use the same circular brake pad or use more than two semi-circular brake pads 64. In addition, in some configurations, the brake pads 64 may be made in one piece with the bearing element 66 brake pads or tightly associated with him in any other way.

Bearing element 66 of the brake pads is llustrative example is directed in the axial direction using a variety of grooves 90, performed on the inner ring 92 of the inner part 22 of the housing. In Fig. 9 shows the rear part of the bearing member 66 brake pads, and the inner ring 92. It should be noted that other components of the inner part 22 of the housing omitted. The inner ring 92 may be made in one piece with the other components of the inner part 22 of the housing or connected with them in another way, as well as mobile or stationary connected to the stub axle, shaft or with the beam axis.

On the host element 66 brake pads illustrative example, there are two different sets of rollers. The first set of rollers includes rollers 94. Each roller 94 is mounted for rotation around the axis 96, which runs in the radial direction relative to the Central axis R (see Fig. 3). The rollers 94 are inside of the bearing member 66 brake pads. They freely enter into the grooves 90 of the inner ring 92. After that, the rollers 94 can easily move along the grooves 90.

It should be noted that the rollers 94 can be replaced by servo elements of another type, for example, fingers sliding or otherwise moving element with low friction, depending on the whole structure.

As shown in Fig. 8, the grooves 90 of the illustrative example are slightly oblique relative to the direction that is parallel to the Central OS is R (see Fig. 3). The slots 90 are displaced in the direction of rotation of the wheel, when the vehicle moves forward. As mentioned earlier, after the brake 10 is assembled, the rollers 94 on the inner side of the bearing member 66 brake pads engaging corresponding grooves 90 of the inner ring 92. This provides axial direction of the bearing member 66 brake pads, when it gets close to the rotating disk 60 or removed from it. Braking torque that may occur on the host element 66 brake pads when you activate the brake is transmitted to the inner part 22 of the housing.

Since, as shown in Fig. 8, the grooves 90 are beveled in the direction of rotation of the wheel, the braking torque transmitted to the bearing element 66 brake pads, can generate reactive axial force, increasing the braking ability. This extra braking power so to a certain extent proportional to the intensity of braking. The bevel angle of the slots 90 can be adjusted in accordance with the specific needs and avoid releasing the braking effort out of control. For example, the average angle may be less than 20, such as from 10 to 20. There may be other values. The grooves 90 may also be curved to change more braking effort when the bearing element 66 brake pads approaching the rotating disk 60 or removed from it. In addition, you can use the slots 90 with non-parallel opposite walls. This can be useful to prevent the opposite effect when braking the vehicle during its movement in the opposite direction or if the vehicle is stopped on a steep hill, rising up.

Fig. 8 also shows that between the bearing element 66 of the brake pads and the inner part 22 of the housing shown brake 10 is an intermediate element 100. The intermediate element 100 shown in Fig. 10-12. This intermediate element 100 is axisymmetric and sloping in the axial direction of the inclined surface 102. The intermediate element 100 is located coaxially relative to the Central axis R (see Fig. 3). He turned in a radial plane within the inner part 22 of the casing and around its inner ring 92. In the illustrative example, to facilitate rotation of the intermediate element 100 between the rear surface of the intermediate element 100 and the surface 105 at the bottom of the inner part 22 of the housing bearings 103 or other elements with low friction. The intermediate element 100 in the axial direction is not moved.

The inclined surface 102 shown intermediate element 100 is directed toward the rear part of the bearing member 66 brake pads. These culac the new surface interact with the respective rollers 104, mounted on the roller support nodes 68 of the bearing member 66 brake pads. The rollers 104 are shown, for example, in Fig. 9. They can be installed on the same axis as the rollers 92. There may be other options.

Fig. 10 is an isometric view showing the inner part 22 of the housing, as well as some of the associated components. Fig. 11 is a view similar to the view of Fig. 10, showing the same in the rear part from a different angle. Fig. 12 is an isometric view of all these parts. Fig. 11 shows the housing 44 of the node 40 of the actuator. Fig. 10 and 12 show the housing 44 of the node 40 of the actuator and the inner part 22 of the housing partially cut.

According Fig. 8, the node 40 of the actuator illustrative example has a ring configuration. It contains a pneumatic inflatable annular actuator 46, which is inserted into the housing 44 of the node 40 of the actuator. The node 40 of the actuator also includes an axially driven element 48, which is adjacent to the inflatable annular actuator 46. Axially driven element 48 is coaxial relative to the Central axis R (see Fig. 3). The diameter of the inflatable annular actuator 46 may be larger than the diameter of the inflatable ring, which could be inserted, for example, in the inner part 22 of the housing.

Axially driven element 48 includes four axelrodichthys Cam 49 with inclined surfaces 49A of the Cam, located axially symmetric manner around the circumference of the axially driven element 48. The Cams 49 axially of the driven element 48 interact with the corresponding servo element, for example, with roller 108, is made around the circumference of the intermediate element 100. These rollers 108 are axis 110, which is oriented in the radial direction relative to the Central axis R. As best shown in Fig. 12, the circumference of the back wall shows the inner part 22 of the case is made arcuate apertures 112, and through a corresponding one of the openings 112 are the Cams 49 axially of the driven element 48, which engages with the outer rollers 108.

Since the Cams 49 are in engagement with the rollers 108 intermediate element 100, and since the axially driven element 48 is moved only in the axial direction, the movement of this element 48 causes rotation of the intermediate element 100 around the Central axis R. This rotary movement moves the rollers 104 of the bearing member 66 brake pads farther up inclined surfaces 102. This leads to axial displacement of the bearing member 66 brake pads in the direction of the rotating disk 60. The main purpose is shown in Fig. 10-12 drive mechanism is to reduce the axial displacement of the inflatable ring on the coeff is consistent with a person of the bearing member 66 brake pads and at the same time, the increase reflecting the efforts of the bearing member 66, the brake pads on the equivalent ratio of the power drive mechanism inflatable rings. Therefore, the magnitude of the gain of the generated force may be set to about 5, which is then "adjusted" the change of the attitude angle drive inclined Cam surfaces 49 and the intermediate angle of the inclined surfaces 102. In addition, due to the special configuration of the illustrative example, the axial displacement of the bearing member 66 of the brake pads causes a small rotary movement of the bearing member 66 brake pads in the same direction as the rotation of the wheels of the vehicle traveling ahead.

There is also a recoil mechanism, which is used, for example, as part of the node 40 of the actuator, for removal of the bearing member 66 of the brake pads against the rotating disc 60, when the brake force is reduced or disappears. The recoil mechanism may include one or more springs. One spring is conventionally shown in Fig. 8 under the reference position 120. The spring or springs 120 may be installed between the bearing element 66 of the brake pads and the inner part 22 of the housing. The spring or springs 120 can also be configured and arranged differently, and to move the bearing member 66 brake pads back in its original position can be designed many different schemas.

During operation, the pressurization of the inflatable annular element knots is 40 actuator pushes axially driven element 48 in the direction of the outside. However, the configuration shown brake 10 generates an increasing axial force between the driven element 48 and the bearing element 66 brake pads. This increase in effort increases the braking force in the brake 10. The mechanism of the power transmission shown brake 10 includes a first Cam interface that is formed between the axially driven element 48 and the intermediate element 100, and the second Cam interface that is formed between the intermediate element 100 and the supporting member 66 brake pads. When the brake 10, as in the case where the vehicle driver presses the brake pedal to slow down a moving vehicle, the actuator 46 of the node 40 of the actuator creates a first force. The first force acts in a direction that is parallel to the axis of rotation of the rotary disc 60. At the same time creates a time by using the first power, at the same time has a center of rotation, which essentially coincides with the axis of rotation of the rotating disc 60. Simultaneously, the second force arises from the use of this time, the second force acts in a direction that is essentially identical to the direction of the first force, and has a greater value than the first power. The second power is used as the braking force for grasping the brake pads 62, 64 against the opposite sides 60A, 60b of the rotating disc 60.

As you can see, the design of the brakes, like the brake 10 can be made more compact than ever before. In addition, the brake 10 can be configured to provide sustainable self-increasing stopping power during braking. Generally speaking, installing axially movable set of brake pads on directed support element brake pads, which is pressed by the intermediate element to the rotating disk, as shown here, you can improve many aspects of the design of the disk brake. This configuration may, for example, to increase the compactness of the brake. In addition, uniform distribution of braking force to the circumference of a rotating disk 60 increases the service life of the brake pads 62, 64.

If necessary, there may be a mechanism (not shown) compensation for temporary wear of the brake pads 62, 64. Such a system, for example, can move to the lowest point on the intermediate element 100, which can reach the rollers 104 on the rear side of the bearing member 66 of the brake pads with the loss of braking effort. While other configurations are possible.

It should be noted that in the design presented here brakes 10 and method can be made many changes. For example, in the ring of the MD disc brake can be installed more than one rotating disk. In this case, two rotating disk would be axially movable relative to each other. Both the rotating disk can be in rotational engagement with the main support of brakes. Between two rotating disks can be installed an additional bearing element brake pads (not shown). This intermediate bearing element brake pads in this case would be two-way and freely in the axial direction, although, ideally, he also may be in rotational engagement with a fixed structure, such as parts 20, 22 of the housing shown brake 10. If necessary, the rotating disk may be solid rotating disk without internal cooling channels, such channels illustrative example. In addition, the opposite surface of the rotating disk with channels or without internal cooling channels can be fasovannymi or with holes to further enhance cooling. If you use a pneumatic actuator, a pneumatic actuator may be a circular shape, and, for example, square shape with rounded corners, in order to increase the surface area where it is needed, and to make the drive as compact as possible. As already mentioned, the drive unit shown and described may be replaced by a drive to each the type, who can use hydraulic fluid environment or even an electric mechanism. It is also possible many other options.

1. The annular disk brake (10)having a Central axis (R), characterized in that it contains:
main bearing (12)located coaxially relative to the Central axis (R);
the rotating disk (60)located coaxially relative to the Central axis (R) and the interacting sliding and transferring torque from the main support (12), rotating disk (60) has opposite first and second sides (60A, 60b);
the housing (20, 22), attached to the main bearing (12) for rotation around the Central axis (R);
at least one first brake pad (62)having a surface (a)directed towards the first side (60) of a rotating disk (60)with at least one first brake pad (62) is attached inside the housing (20, 22); at least one second brake pad (64)having a surface (64A)which is directed towards the second side (60b) of the rotating disk (60);
essentially axially directed bearing element (66) brake pads, located coaxially relative to the Central axis (R), with the bearing element (66) brake pads has opposite first and second sides, and at least one second deceleration is the main block (64) is connected to the first side support member (66) brake pads;
the node (40) of the actuator coupled to the housing (20, 22) and containing an axially driven element (48); and
the mechanism is transmitted, containing the first Cam interface between the axially driven element (48) and the intermediate element (100)is located axially between the driven element (48) and the second side support member (66) brake pads, and an intermediate element (100) is located coaxially relative to the Central axis (R) and rotates in a radial plane; thus, the mechanism further comprises a second Cam interface between the intermediate element (100) and the second side support member (66) brake pads, and when the intermediate element (100) is turned, the bearing element (66) brake pads makes axial movement, so that the mechanism generates the gain increases efforts axially between the driven element (48) and the second side support member (66) brake pads.

2. Brake (10) according to claim 1, characterized in that the gain increases effort has a coefficient of 1 to 5.

3. Brake (10) according to claim 1 or 2, characterized in that the first Cam interface contains axisymmetric axially projecting Cams (49)having a Cam surface that interacts with the corresponding servo elements (108), and one of the Cams (49) and tracking elements (108) nah what are axially on the driven element (48), and the other of the Cams (49) and tracking elements (108) located on the intermediate element (100).

4. Brake (10) according to claim 3, characterized in that the servo elements (108) are rollers arranged circumferentially on the periphery of the intermediate element (100) or axially of the driven element (48), and rollers (108) mounted for rotation around respective axes radially arranged (110).

5. Brake (10) according to claim 3, characterized in that the intermediate element (100) is mounted to rotate inside the housing (20, 22).

6. Brake (10) according to any one of claims 1, 2, 4, or claim 5, characterized in that the second Cam interface contains axisymmetric and axially angled slanted surface (102)associated with the corresponding servo elements (104), and one of the inclined surfaces (102) and tracking elements (104) are located on the first side support member (66) brake pads, and the other of the inclined surfaces (102) and tracking elements (104) are located on the intermediate element (100).

7. Brake (10) according to claim 6, characterized in that the intermediate element (100) is rotated in the direction of rotation corresponding to the direction of rotation of the support (12), when the intermediate element (100) moves the element (66) brake pads closer to the rotating disk (60).

8. Brake (10) according to claim 6, characterized in that witness e the cops (104), interacting with inclined surfaces (102), are rollers.

9. Brake (10) according to any one of claims 1, 2, 4, 5, 7 or claim 8, characterized in that the carrier element (66) brake pads axially directed using multiple grooves (90), made on the inner ring (92), United with the inner side of the housing (20, 22)and inner ring (92) is located coaxially relative to the Central axis (R)and grooves (90) coupled with the corresponding servo elements (94)connected to a bearing element (66) brake pads.

10. Brake (10) according to claim 9, characterized in that the grooves (90) have angular location relative to a direction which is parallel to the Central axis (R), and grooves (90) create a rotational movement of the bearing member (66) brake pads in the same direction of rotation as the direction of rotation of the rotating disk (60), when the bearing element (66) brake pads moving in the direction of the rotating disk (60).

11. Brake (10) according to claim 10, characterized in that the grooves (90) have an average angle of from 10 to 20 relative to the direction that is parallel to the Central axis (R).

12. Brake (10) according to any one of claims 1 to, 2, 4, 5, 7, 8, 10 or claim 11, characterized in that the rotating disk (60) includes a holder (70)is mounted around the circumference of the hollow section (12C), passing from the support (12)and the holder (70) I which is axially guided in the support (12).

13. Brake (10) according to any one of claims 1 to, 2, 4, 5, 7, 8, 10 or claim 11, characterized in that the bearing (12) contains many passing through the axis of the bolt, to which may be attached to the vehicle's wheel.

14. Brake (10) according to any one of claims 1 to, 2, 4, 5, 7, 8, 10 or claim 11, characterized in that the node (40) of the actuator includes a pneumatic actuator (46).

15. Brake (10) according to 14, characterized in that the pneumatic actuator has an essentially circular configuration, with pneumatic actuator (46) is located coaxially relative to the Central axis (R).

16. Brake (10) according to any one of claims 1 to, 2, 4, 5, 7, 8, 10, 11 or 15, characterized in that the housing (20, 22) includes two axially spaced parts connected with the possibility of separation.

17. Brake (10) according to item 16, wherein the at least one first brake pad (62) consists of two blocks, and one of the two housing parts (20, 22) is divided into two circumferential halves (20a, 20b), inside of which are connected respectively one of the first two brake pads (62).

18. The way to increase the effort of setting the brake pads in the annular disk brake (10)includes an actuator (46) and the rotating disk (60)having an axis of rotation, wherein the synchronized:
generate the first force of the actuator (46) brake (10), and the first force has a direction that parallel is but the axis of rotation of the rotating disk (60);
generate a torque by using the first power, the moment of rotation is the center of rotation, which essentially coincides with the axis of rotation of the rotating disk (60);
generate a second force using torque, and the second force has a direction that is essentially identical to the direction of the first force and is the value greater than the first force; and
use a second force for grasping the brake pads (62, 64) on opposite sides (60A, 60b) of a rotating disk (60).

19. The method according to p, characterized in that the second force is greater in magnitude compared to the first force by a factor equal to from 1 to 5.

20. The method according to p or 19, characterized in that for generating the second power type axial reactive force to further increase the second force, and axial reactive force generate brake torque at the time of setting the brake pads on a rotating disk (60).



 

Same patents:

FIELD: mechanical engineering.

SUBSTANCE: modular brake mechanism mounted in the support provided with the port at least in its front side comprises braking lever, front rack that is connected with the braking lever when the brake operates, and at least one stop plate which is mounted on the transverse rack and overlaps the plate for closing the port in the front side of the support. The transverse rack moves by the lever in the plane virtually perpendicular to the plane of the brake disk. The brake mechanism is modular and comprises two or more units. At least one of the units has at least two members. Each of the units can be dismounted through the port in the support.

EFFECT: facilitated dismounting of out-worn units.

6 cl, 7 dwg

FIELD: mechanical engineering; disk brakes.

SUBSTANCE: proposed disk brake contains caliper enclosing brake disk and provided with cavity for mounting brake mechanism. Brake mechanism has support bracket installed inside in port in caliper wall furthest from brake disk. Brake mechanism is provided with adjuster, adjusting shaft and shaft for restoring initial position. Device is used to transmit motion between shafts to adjust and restore initial position. Adjuster is set into operation by pin of lever arranged on brake mechanism lever and is installed in support bracket at assembling.

EFFECT: improved synchronization of adjusting motion between two thrust units of brake mechanism, provision of compactness, facilitated servicing of brake mechanism.

10 cl, 8 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed disk brake comprises caliper, holder secured to vehicle, friction appliances arranged on both sides of disk brake, detachable unit to secure friction appliances, and spring secured to friction appliance to joint first and second wings of caliper. Said caliper has extending part to embrace disk brake on both sides and is furnished with hydraulic cylinder with piston. Note here that caliper is arranged to move on the holder, while disk brake can rotate between said extending part and caliper piston. Holder represents a half passing on only one side of disk brake plane, while guide pins are arranged above disk brake perpendicular to its plane. Detachable unit is arranged partially in the first recess arranged in friction appliance one support and, partially, in second recess made in extending part of caliper and/or holder.

EFFECT: improved braking qualities of caliper and reduced weight.

19 cl, 8 dwg

Disk brake // 2363869

FIELD: automotive industry.

SUBSTANCE: invention relates to automotive industry, particularly, to disk brakes. Proposed disk brake consists of brake caliper and brake throw-in mechanism. The latter is encapsulated into brake caliper and incorporates booster to transmit braking force to push rod arranged to slide in the said brake caliper. It is furnished with pressure plate, fitted on its end on the brake disk side, to transmit braking force to brake disk with the help of brake shoe lining holder and brake shoe lining. Aforesaid pressure plate is jointed to the brake shoe lining holder so that, in applying and releasing the brake, aforesaid push rod shifts from the axis and moves in the brake caliper with the help of aforesaid holder. The latter can move radially and tangentially in the said caliper or said holder. There are appliances to joint the disk brake throw-in mechanism with the push rod pressure plate, on the side opposite the brake shoe lining.

EFFECT: reduces weight, simplified assembly and mounting.

16 cl, 10 dwg

Rear disc brake car // 2193126
The invention relates to transport machinery, namely to the braking system of the vehicle, in particular to the rear brake, and can be used in the Parking brake rear disc brake

Disc brake vehicles // 2113368
The invention relates to disc brakes of vehicles and in particular to the host disk brakes, which contains the friction element and the spring

Disc brake // 2093725
The invention relates to the field of engineering, particularly to disc brakes for vehicles

Disk brake // 2363869

FIELD: automotive industry.

SUBSTANCE: invention relates to automotive industry, particularly, to disk brakes. Proposed disk brake consists of brake caliper and brake throw-in mechanism. The latter is encapsulated into brake caliper and incorporates booster to transmit braking force to push rod arranged to slide in the said brake caliper. It is furnished with pressure plate, fitted on its end on the brake disk side, to transmit braking force to brake disk with the help of brake shoe lining holder and brake shoe lining. Aforesaid pressure plate is jointed to the brake shoe lining holder so that, in applying and releasing the brake, aforesaid push rod shifts from the axis and moves in the brake caliper with the help of aforesaid holder. The latter can move radially and tangentially in the said caliper or said holder. There are appliances to joint the disk brake throw-in mechanism with the push rod pressure plate, on the side opposite the brake shoe lining.

EFFECT: reduces weight, simplified assembly and mounting.

16 cl, 10 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed disk brake comprises caliper, holder secured to vehicle, friction appliances arranged on both sides of disk brake, detachable unit to secure friction appliances, and spring secured to friction appliance to joint first and second wings of caliper. Said caliper has extending part to embrace disk brake on both sides and is furnished with hydraulic cylinder with piston. Note here that caliper is arranged to move on the holder, while disk brake can rotate between said extending part and caliper piston. Holder represents a half passing on only one side of disk brake plane, while guide pins are arranged above disk brake perpendicular to its plane. Detachable unit is arranged partially in the first recess arranged in friction appliance one support and, partially, in second recess made in extending part of caliper and/or holder.

EFFECT: improved braking qualities of caliper and reduced weight.

19 cl, 8 dwg

FIELD: machine building.

SUBSTANCE: annular disc brake includes a rotating disc and at least one disc shoe installed on each side of the rotating disc. Brake shoe or shoes on one side are connected to an axially guided load-carrying element of the brake shoe. The brake has a force transfer mechanism creating enhancement of increase in force between the axially driven element and load-carrying element. The method for increasing gripping force of brake shoe in annular disc brake consists in the fact that the first force is generated synchronously with the brake drive; at that, the first force has the direction that is parallel to rotation axis of the rotating disc. Also, rotating torque is generated using the first force; at that, rotating torque has the rotation centre that coincides with rotation axis of the rotating disc. Besides, the second force is generated using rotating torque; at that, the second force has the direction that is essentially identical to the direction of the first force and is higher than the first force. The second force is used for gripping of brake shoes on opposite sides of the rotating disc.

EFFECT: increasing brake compactness and providing uniform distribution of braking force in a circumferential direction of the rotating disc.

20 cl, 12 dwg

Portable container // 2514443

FIELD: transport.

SUBSTANCE: container comprises control element arranged at separate bed or at container vessel and connected via transfer assembly with container cover, and wheels. Besides, this container comprises the brake composed of a rod arranged in guides elastically connected with control element or transfer assembly to fir in toothed rim at wheel or wheels.

EFFECT: ease of use.

3 cl, 1 dwg

FIELD: transport.

SUBSTANCE: disc brake comprises floating clamp, brake piston driven by motion converter cartridge rear part of the latter being thrust against the bottom of seat made in said clamp for cartridge and including control shaft extending through seat bottom. Cartridge is locked by yoke resiliently pressed against sear wall. Cartridge pusher has lengthwise ledges composed of rods fitted in seat lengthwise slots. Anti-strain device is arranged between pusher rods and clamp seat slots. This device comprises ring with lugs distributed in circle in compliance with arrangement of rods. Said lugs have cylindrical tabs bent as said lengthwise ledges to lock the pusher and to allow its translation.

EFFECT: simplified production of brake clamp.

8 cl, 10 dwg

FIELD: transport.

SUBSTANCE: invention relates to the automotive industry, particularly, to disk brakes of vehicles. The disc brake comprises a floating clamp, a brake piston driven by a motion converter cartridge, the rear part of the latter being thrust against the bottom of a seat made in the said clamp for the cartridge and including a control shaft extending through the seat bottom. The front part of the cartridge rests against the brake piston. The named part of the cartridge includes a pusher fitted with a disk interacting with a control shaft disk by means of balls located between disks with a possibility of rolling along the paths designed as inclined surfaces for the conversion of the rotary motion of one disk with reference to another into the translational movement of the pusher. The cartridge is locked in its seat by a yoke resiliently pressed against the seat wall. The pusher disk has longitudinal grooves interacting with lock cores and thus holding the pusher from rollover with ensuring freedom of its translational movement.

EFFECT: simplification of fabrication of the brake bracket due to minimising of the quantity of parts of the movement conversion cartridge is achieved.

7 cl, 12 dwg

FIELD: transport.

SUBSTANCE: invention relates to automotive industry, particularly, to brake systems. Disc brake comprises floating clamp, brake piston driven by cartridge converting motion, cartridge rear part resting on the bottom of seat made in said clamp, and includes control shaft extending through seat bottom. Cartridge front part thrusts against brake piston. Cartridge incorporates the disc to interact with control shaft disc via balls arranged the disc to roll in paths made as inclined surfaces for conversion of rotation of one disc relative to another one into translation of pusher. Cartridge is locked by yoke resiliently pressed against sear wall. Said pusher has lengthwise ledges extending to enter said lengthwise grooves made in seat walls to retain said pusher and to allow its translation.

EFFECT: simplified production of brake clamp.

6 cl, 6 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building, namely, to disc brakes. Disc brake comprises support, clamp, retainer to accommodate the latter for it to displace on said support, seal secured at the recess in retainer and device to pre-stretch said seal in said recess. Said device is actuated at fitting the retainer in place.

EFFECT: simplified production.

14 cl, 5 dwg

FIELD: process engineering.

SUBSTANCE: set of inventions relates to machine building, particularly, to disc brake piston jackets. Claimed piston protection jacket is arranged between the caliper and piston. Said jacket has a bulged fillet made at its inner section to fit in the piston groove and an insert fitted in the jacket at its moulding. Said insert is secured in a circular recess made in the caliper. The jacket can be folded for said insert, mid sections and extreme section to overlap each other. The jacket has lengthwise ribs arranged at the inner section surface to support this section, that is, to facilitate the stiffness and to allow the air to leak outside from said bulged fillet fitted in the piston groove. Claimed brake comprises the piston with protective jacket.

EFFECT: better disc brake piston tightness.

9 cl, 3 dwg

FIELD: machine building.

SUBSTANCE: invention relates to disc brakes. Disc brake for commercial vehicle comprises a brake caliper, a clamping device, at least one adjustable spindle and an adjusting device. Brake caliper extends over a brake disk. Clamping device presses the brake pads against the brake disc. Adjusting spindle rotates by is rotatably mounted in a bridge by means of a corresponding thread, the clamping device engages the bridge.

EFFECT: to increase the reliability.

9 cl, 2 dwg

FIELD: mechanical engineering; disk brakes.

SUBSTANCE: proposed disk brake contains caliper enclosing brake disk and provided with cavity for mounting brake mechanism. Brake mechanism has support bracket installed inside in port in caliper wall furthest from brake disk. Brake mechanism is provided with adjuster, adjusting shaft and shaft for restoring initial position. Device is used to transmit motion between shafts to adjust and restore initial position. Adjuster is set into operation by pin of lever arranged on brake mechanism lever and is installed in support bracket at assembling.

EFFECT: improved synchronization of adjusting motion between two thrust units of brake mechanism, provision of compactness, facilitated servicing of brake mechanism.

10 cl, 8 dwg

FIELD: mechanical engineering.

SUBSTANCE: modular brake mechanism mounted in the support provided with the port at least in its front side comprises braking lever, front rack that is connected with the braking lever when the brake operates, and at least one stop plate which is mounted on the transverse rack and overlaps the plate for closing the port in the front side of the support. The transverse rack moves by the lever in the plane virtually perpendicular to the plane of the brake disk. The brake mechanism is modular and comprises two or more units. At least one of the units has at least two members. Each of the units can be dismounted through the port in the support.

EFFECT: facilitated dismounting of out-worn units.

6 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: annular disc brake includes a rotating disc and at least one disc shoe installed on each side of the rotating disc. Brake shoe or shoes on one side are connected to an axially guided load-carrying element of the brake shoe. The brake has a force transfer mechanism creating enhancement of increase in force between the axially driven element and load-carrying element. The method for increasing gripping force of brake shoe in annular disc brake consists in the fact that the first force is generated synchronously with the brake drive; at that, the first force has the direction that is parallel to rotation axis of the rotating disc. Also, rotating torque is generated using the first force; at that, rotating torque has the rotation centre that coincides with rotation axis of the rotating disc. Besides, the second force is generated using rotating torque; at that, the second force has the direction that is essentially identical to the direction of the first force and is higher than the first force. The second force is used for gripping of brake shoes on opposite sides of the rotating disc.

EFFECT: increasing brake compactness and providing uniform distribution of braking force in a circumferential direction of the rotating disc.

20 cl, 12 dwg

Up!