Combined cylinder with force transfer mechanism that features variable transfer ratio

FIELD: transport.

SUBSTANCE: invention relates to machine building, particularly, to combine brake cylinders. Combined brake cylinder comprises cylinder of working braking mechanism, an active working brake, driven by working fluid displaced by piston and braking mechanism cylinder with spring energy accumulator, a passive parking brake. Piston of aforesaid braking mechanism cylinder with spring energy accumulator and rod of cylinder of working braking mechanism piston are aligned. In case piston stroke in aforesaid braking mechanism cylinder with spring energy accumulator increases power transfer ratio increases as well. Rail mounted vehicle disc type braking mechanism support unit incorporates said combined braking cylinder.

EFFECT: compact design, maximised force of braking.

25 cl, 15 dwg

 

The present invention relates to the combined brake cylinder containing the working cylinder of the brake mechanism as a working brake, at least one is driven by the working fluid by the piston of the working cylinder of the brake mechanism, through which the piston rod of the working cylinder of the brake mechanism actuates the brake mechanism and the cylinder of the brake mechanism with spring energoakkumulyatorami as a passive Parking brake actuated by the working fluid against at least one spring energoakkumulyator the piston cylinder of the brake mechanism with spring energoakkumulyatorami, the piston cylinder of the brake mechanism with spring energoakkumulyatorami in the case of Parking brake transmits the force, at least one spring energoakkumulyator through a transmission mechanism to the piston rod of the working cylinder of the brake mechanism, in accordance with the restrictive part of paragraph 1 of the claims.

In modern rail vehicles the ratio of the internal length of the body to the base in the swivel trucks cars is very limited. In particular, the swivel trucks high-speed trains on the axis should be up to four drives of hormonogenesis. Constructive space for the brake system is also often limited due to the placement of drive units or tie rods magnetic rail brakes. These problems occur especially when the so-called combined brake cylinder, which is driven by the working fluid to the working cylinder of the brake mechanism as the working and the brake cylinder of the brake mechanism with spring energoakkumulyatorami as a passive Parking brake attached to each other by means of flanges, are used as brake swivel trolley cars, such as combined brake cylinders require a relatively large structural space and have large structural dimensions than the working cylinder brake without brake cylinder mechanism with spring energoakkumulyatorami. Under active brake mechanism is generally understood brake mechanism when applying pressure on it is clamped, and when the pressure is released. In most cases, it is the working of the brake mechanism. In the case of passive brake mechanism, such as a brake mechanism with a spring energoakkumulyatorami as a Parking brake, the braking force is generated on the contrary, due to the pru is affine energoakkumulyator, moreover, when applying pressure to the brake cylinder mechanism with spring energoakkumulyatorami it, against the action of spring energoakkumulyator, pressed in the release position of the brake mechanism, and at lower pressure due to the action of the spring energoakkumulyator transferred to the position of the clip.

The required number of Parking brakes in turning the truck of the car depends on the available efforts cylinder of the brake mechanism with spring energoakkumulyatorami and thereby from the stress of the spring power. Great efforts Parking brake however, require the presence of relatively large dimensions of the springs, which is in contradiction with the task of creating the most small size of the combined brake cylinder. Such combined brake cylinders for use in rail vehicles in most cases are built further as element of the brake mechanism in the disc brake calipers, with a relatively small gear ratio. In addition, there is a problem in that on the basis of the characteristic curve, which describes the dependence of the elasticity of the spring energoakkumulyator the length of stroke of the brake mechanism with spring energoakkumulyator the Ohm, the elasticity decreases with increasing stroke length of the piston of the brake mechanism with spring energoakkumulyatorami and, thus, the position of the clamp on the brake disc has only a relatively small component of the effort of the spring energoakkumulyator. This situation is clearly shown by the characteristic curve in Fig.6, which, among other things, demonstrates the dependence of the elasticity of the spring energoakkumulyator from the stroke length s of the piston of the brake mechanism with spring energoakkumulyatorami.

Combined brake cylinder in accordance with the original version known from EP 0553450 B1. This is enshrined in the caliper disk brake of a rail vehicle of a combined brake cylinder of the brake mechanism with spring energoakkumulyatorami positioned vertically and transmits the force of the spring energoakkumulyator by means of a Cam mechanism in the form of wedge-shaped parts on the piston rod of the working cylinder of the brake mechanism, which, in contrast, is horizontal or orthogonal. The running-in phase is wedge-shaped parts, which rolls connected with the piston rod of the working cylinder brake pressure slider made linear, so that the gear ratio continuously and then AFL is stvie decreasing elasticity due to the stroke length of the piston cylinder of the brake mechanism with spring energoakkumulyatorami transferred the force of the Parking brake with spring energoakkumulyatorami decreases. The vertical position of the cylinder of the brake mechanism with spring energoakkumulyatorami requires more compared with the working cylinder of the brake mechanism, a relatively large structural space as a combined brake cylinder is located in two directions.

Thus the task of the proposed invention consists in the improvement of the combined brake cylinder previously specified type so that it was more compact and small design space provided as large a force of the Parking brake.

This problem is solved by the present invention is characterized by signs of paragraph 1 of the formula.

According to the invention the transmission mechanism is formed in such a way that movement of the piston cylinder of the brake mechanism with spring energoakkumulyatorami and piston rod of the working cylinder of the brake mechanism coaxially and gear ratio with increasing stroke length of the piston cylinder of the brake mechanism with spring energoakkumulyatorami increases. On the basis of the first event is reduced footprint of the combined brake cylinder space vertically, because the working cylinder of the brake mechanism and the cylinder of the brake mechanism with spring energy is accumulation can be coaxially connected to each other by means of a flange. This is beneficial in that, in particular, constructive space in the vertical direction in the swivel trucks cars is very limited, and even less room there is in the horizontal direction.

The second event causes the buildup of efforts to increase the stroke length of the piston cylinder of the brake mechanism with spring energoakkumulyatorami, resulting in the preferred embodiment, to the considerable efforts of the Parking brake in the end position of the piston of the cylinder of the brake mechanism with spring energoakkumulyatorami and thus the clamping of the brake mechanism with spring energoakkumulyatorami. Then decreasing due to the stroke length of the piston cylinder of the brake mechanism with spring energoakkumulyatorami force of the spring energoakkumulyator compensated by increasing the reduction ratio of the gear mechanism. With proper execution of the transfer mechanism can be implemented practically unchanged, and a considerable force of the spring energoakkumulyator on the piston rod of the working cylinder of the brake mechanism through a total stroke length of the piston cylinder of the brake mechanism with spring energoakkumulyatorami.

By given in the dependent claims can be made is tweenie preferred options for the improvement of the invention, presented in the independent claims.

Particularly preferred is the ability to provide fixed against rotation, is arranged to actuate coaxially with the Central axis of the combined brake cylinder compression rings which, through the axial forces acts on the spindle, one of which is fixed from rotation, and the other part of which is mounted for rotation coaxially with the Central axis, the rotational movement is performed with the rotating part of the spindle drive for the transmission of axial forces between fixed from rotation part and rotating part may be blocked, and to stop transmission of the axial force can be released by means of demountable swivel lock. Thread in the preferred embodiment, is not self-locking thread, and folding device of the rotary latch is in the emergency leave for the implementation of the emergency dispensing cylinder of the brake mechanism with spring energoakkumulyatorami. Further provides for the transmission of axial forces between the drive spindle and the piston rod of the working cylinder of the brake mechanism.

Under emergency release means of the mechanical leave the brake mechanism is a spring energoakkumulyatorami, if the compressed air supply has been violated and, consequently, the piston cylinder of the brake mechanism with spring energoakkumulyatorami can no longer by actuation with fluid to move into the release position.

In accordance with a variant of execution of the combined brake cylinder in accordance with the invention according to paragraph 7 of the formula control ring and fixed to the rotation part of the spindle drive joint and the rotary latch is located between the pressure ring and the rotating part of the spindle drive.

In accordance with the improvement of this variant implementation of the invention on the compression ring is made of at least one located perpendicular to the Central axis of the combined brake cylinder anchor pin, which can be rotated is selected, at least one bell crank, which is one of its shoulder articulated to the piston cylinder of the brake mechanism with spring energoakkumulyatorami, and her other shoulder rests on a fixed support surface of the combined brake cylinder so that upon actuation of the piston cylinder of the brake mechanism with spring energoakkumulyatorami if the Parking brake is initiated by the rotation support is shrink crank lever around the pivot axle, and thus unidirectional actuation of the adjusting ring. This bell crank forms in this case a lever transmission, and the corresponding gear ratio is detected based on the position of the crank arm or shoulder crank lever in a given time.

Developed by the cylinder piston of the brake mechanism with spring energoakkumulyatorami in the case of the Parking brake force of the Parking brake is put on through the crank arm as the transmission mechanism in the control ring and thereby enhanced. From the pressure ring is multiplied force through made with the possibility of locking the thread is transferred to the spindle drive, and from there through the thrust bearing on the pipe of the piston of the working cylinder of the brake mechanism and bracket spindle, a move which eventually enters this multiplied force to the brake mechanism, preferably in the caliper disk brake of a rail vehicle.

If there are two installed on passing outward perpendicular to the Central axis of the combined brake cylinder supporting pins of the adjusting ring with the possibility of rotation of a cranked lever, which in relation to having the Central axis of the combined brake cylinder-plane are rotated relative to each other (i.e. the position of one of the cranked lever identify aetsa on the basis of the rotation of the other crank arm by 180 degrees. around the Central axis, symmetric positional location), the reactive moments that occur from acting as a lever clearance from the crank arm to the Central axis compensated, so that in the preferred embodiment, on the control ring or the piston cylinder of the brake mechanism with spring energoakkumulyatorami no torque acts about an axis perpendicular to the Central axis (the tipping point).

In a preferred embodiment of, respectively, one shoulder crank lever by means of double-jointed tongue is connected with the piston of the cylinder of the brake mechanism with spring energoakkumulyatorami, and the other shoulder of the cranked lever is supported through made with the possibility of running at a fixed supporting surface of the support roller, so that the wear is minimized.

In order to hold the control ring in the combined brake cylinder is definitely without a possibility of rotation, but with the possibility of axial displacement at the ends of the support pins of the adjusting ring are movable body that is without a possibility of rotation conducted in located in the direction of the Central axis of the combined brake cylinder wings.

A support surface for made with the possibility of spinning rollers other is on the shoulder of the cranked lever is made in the preferred embodiment, the partition between the cylinder of the brake mechanism with spring energoakkumulyatorami and the working cylinder of the brake mechanism, which is already available, so no need for additional structural elements. Since this partition simultaneously forms a support surface for the at least one spring energoakkumulyator cylinder of the brake mechanism with spring energoakkumulyatorami.

In a particularly preferred embodiment of the device of the rotary latch contains made with the possibility of introducing into the external toothing of the spindle, which is driven manually, the release latch, which can be rotated installed on the compression ring.

According to the second variant implementation of the combined brake cylinder in accordance with the invention according to paragraph 16 of the claims through a piston cylinder of the brake mechanism with spring energoakkumulyatorami parallel to the Central axis of the combined brake cylinder may operate at least one V-path, along which can be conducted by the lever arm, at least one installed rotatably on the combined brake cylinder lever, the other lever arm of which rests on the control ring, and one lever along clinovia circuit initiates pivotal movement of the lever around the axis of rotation of the lever and the sama is acting through another shoulder the lever on the control ring, unidirectional relative movement of the piston of the brake mechanism with spring energoakkumulyatorami, the axial force. Thus, for example, the axis of rotation of the lever is perpendicular to the Central axis of the combined brake cylinder.

In accordance with a variant of execution of this event are provided preferably two in the direction of the axis of rotation of the lever at least partially embrace the control ring V-path, which interact with two symmetrical relative to the Central axis of the combined brake cylinder and combined into two shoulders of the lever arms. Due to the presence of two levers revealed improved load distribution. On the other hand, the load is distributed symmetrically.

The control ring is preferably transmits the axial force through the thrust bearing on the forming is performed with a rotating part of the spindle drive gear wheel, the teeth of which may include configured to actuate the manually latch device of the rotary latch, and a gear wheel mounted for rotation on a fixed rotating part of the spindle drive through the thread, which transmits the axial force on the piston rod of the working cylinder of the brake mechanism.

If then iLink brake mechanism with spring energoakkumulyatorami if the Parking brake is moved in the direction of the clamp, both V-path is moved together with him, resulting in some shoulders rotating lever is moved along the wedge contours and thereby initiate the rotary motion of the rotating arm, resulting in other shoulders rotating lever to move the control ring unidirectional relative axial movement of the cylinder piston of the brake mechanism with spring energoakkumulyatorami. Set in the combined brake cylinder fixed from rotation of the control ring passes then affecting the axial force through the thrust bearing on the rotating part of the spindle drive, the rotation of which, however, in the normal operation mode is locked relative to the fixed rotating part of the spindle drive through the device of the rotary latch. When fixed to the rotation part of the spindle drive axial force is transmitted to the piston rod of the working cylinder of the brake mechanism.

If the emergency leave Parking brake device of the rotary latch is actuated so that the rotatably part of the drive spindle can rotate freely relative to the fixed from rotation by desmoteplase thread, made with the possibility of rotation of the part is screwed to tirovannoj from the rotating part of the spindle drive as long while both parts will not cease to exert a force impact on each other. In this case, piston cylinder of the brake mechanism with spring energoakkumulyatorami moves until it touches the bottom of the cylinder of the brake mechanism with spring energoakkumulyatorami.

According to the third variant of execution of the combined brake cylinder in accordance with the invention according to paragraph 20 of the claims the rocker mechanism is provided as a transmission mechanism containing at least one articulated with pressure ring roller earring, with at least one sliding guide, which held at least one rocker arm, which on the one hand articulated with the body of the combined brake cylinder, and on the other hand, at least one articulated to the piston of the brake mechanism with spring energoakkumulyatorami tongue.

When this roller earring preferably at its pointing from the pressure ring end fitted made with the possibility of rotation of the roller, which is made with the possibility of running across the surface of the scenes rocker arm. Compression rings are installed, for example, by at least one mobile guide, fixed against rotation in the case of a combined brake cylinder.

<> If there are two roller earrings with rocker rails, two conducted in the rocker guide rocker arm, and the two tabs that are located relative to the plane with the Central axis of the combined brake cylinder, rotated relative to each other, derived from the actuation of the transfer mechanism, the tilting moments are offset.

If then the piston of the brake mechanism with spring energoakkumulyatorami if the Parking brake is moved in the direction of the clamp, the elasticity of the spring energoakkumulyator through both pull-tab rocker arm and roller earrings supported pressure ring. It passes then the force on the piston rod of the working cylinder of the brake mechanism and thereby to the brake mechanism. In virtue of this kinematics roller ring, respectively, is automatically configured depending on the stroke length of the piston of the brake mechanism with spring energoakkumulyatorami the angular position of the attached rocker arm, as she accepts a position at which the line of action of force roller earrings perpendicular to a tangent to the surface of the scenes at the touch point support roller. Due to the kinematically driven negotiation position roller earrings depending on the stroke length of the piston of the brake is of echanism spring energoakkumulyatorami increased gear ratio formed by means of this transmission mechanism.

As in other versions of the invention, due to a kinematic transmission mechanism cylinder of the brake mechanism with spring energoakkumulyatorami and the working cylinder of the brake mechanism can be located coaxially with the Central axis of the combined brake cylinder, and movement of the working cylinder of the brake mechanism and cylinder of the brake mechanism with spring energoakkumulyatorami in the case of the clip, and if you leave the brakes are unidirectional.

The invention relates also to the block caliper disk brake of a rail vehicle containing the above combined brake cylinder.

More precisely, the invention is explained in the following description of examples of implementation.

Examples of execution of the invention represented in the drawings and explained in more detail in the subsequent description.

The drawings show the following:

figure 1 is a top view of the block caliper disk brake of a rail vehicle with a combined brake cylinder in accordance with the invention;

figure 2 is a vertical longitudinal section of the combined brake cylinder of figure 1 with the combined brake cylinder in accordance with the first variant of execution in the release position;

figure 3 is a view in per spective, the e of the combined brake cylinder of figure 2 with slits;

4 is a longitudinal section of the combined brake cylinder of figure 2 with the combined brake cylinder in the position of the clamp;

5 is a Central vertical longitudinal section of the combined brake cylinder of figure 2 in the release position;

6 is a diagram showing the dependence of the elastic force, the gear ratio i of the transmission mechanism of the combined brake cylinder and the force in the cylinder depending on the stroke length s of the piston cylinder of the brake mechanism with spring energoakkumulyatorami combined brake cylinder in accordance with the invention;

7 is a horizontal Central longitudinal section of the combined brake cylinder in accordance with the following variant of execution of the invention in the release position;

Fig - perspective image of the combined brake cylinder 7 with cuts;

figure 9 is a horizontal longitudinal section of the combined brake cylinder in Fig.7. in the braking position;

figure 10 is a vertical Central longitudinal section of the combined brake cylinder in Fig.7;

11 is a cross-section of the combined brake cylinder in Fig.7;

Fig is a vertical longitudinal section of the combined brake cylinder in accordance with the following option implemented the program of the invention in the release position;

Fig - perspective image of the combined brake cylinder on Fig with cuts;

Fig is a vertical longitudinal section of the combined brake cylinder on Fig in the braking position;

Fig - horizontal Central longitudinal section of the combined brake cylinder on Fig in the release position.

Presented in figure 1 caliper 1 disk brake of a rail vehicle has two passing is basically parallel to each other lever 2, 4 caliper disk brake mechanism. Both levers 2, 4 caliper disk brake mechanism in the Central area of its longitudinal length articulated with each other by thrust 6. The levers 2, 4 caliper disk brake, thrust 6 arranged in the plane or parallel to the plane of the caliper disk brake mechanism, parallel to the plane of the drawing.

On some ends of the levers 2, 4 caliper disk brake mechanism are articulated by means of bolts brake pads 8, with which a friction closure can engage with the disk 10 of the brake mechanism. Between the other ends of the levers 2, 4 caliper disk brake mechanism is combined brake cylinder 12, a housing 14 which is on the same lever 4 when Porta disk brake mechanism and the piston of the working cylinder of the brake mechanism through which the piston rod of the working cylinder of the brake mechanism and the bracket 16 of the spindle disk brake mechanism articulated with another lever 2 caliper disk brake mechanism.

Figure 1 shows that the caliper 1, the disc brake mechanism is in accordance with the ratio of the lever arms 2, 4 caliper disk brake mechanism, only a small gear ratio, the contact pressure of the brake pads 8, thus only a small transmission coefficient higher than that carried out a combined brake cylinder 12 Rethimno force to the levers 2, 4 caliper disk brake mechanism.

Therefore, in figure 2 in the release position presents the combined brake cylinder 12, through which is possible to achieve an increased braking force in the case of the Parking brake. Combined brake cylinder 12 includes a cylinder 18 of the working brake active brake actuated by working fluid, the piston 20 of the working cylinder of the brake mechanism, through which the rod 22 of the piston of the working cylinder of the brake mechanism and the bracket 16 of the spindle disk brake mechanism actuates the lever 2 caliper disk brake mechanism, and applying pressure to the piston 20 of the operating brake mechanism or the discharge pressure is carried out through the submission and, accordingly, removal of air from the working chamber 24 of the brake mechanism. The locking of the rotation is Oia, for example, by withholding the combined brake cylinder 12 and is held axially in the piston 20 working brake bolt 26 secures the fact that the piston 20 of the working cylinder of the brake mechanism without rotation is performed in the cylinder 18 of the operating brake mechanism. Return spring 28 is pre-pressed plunger 20 of the working cylinder of the brake mechanism presented in figure 2 in this case the right side of the release position.

The cylinder 18 of the operating brake mechanism by means of a flange attached to the cylinder 30 of the brake mechanism with spring energoakkumulyatorami as a passive Parking brake coaxially relative to the Central axis 32 of the combined brake cylinder 12, which is held actuated by the working fluid against the impact of preferably several located in each other spring accumulators 34 and the piston 36 of the cylinder of the brake mechanism with a spring accumulator. Spring battery 34 is placed in the spring chamber 38 of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami and are based on one hand on the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, and on the other side of the partition 40 between the cylinder 30 brake fur the mechanism with spring energoakkumulyatorami and the cylinder 18 of the operating brake mechanism. Due to the supply pressure is made on the other side of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami chamber 42 of the brake mechanism with spring energoakkumulyatorami the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami against the action of spring accumulators 34 enters presented in figure 2 on the right side of the release position.

The piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami in the case of the Parking brake transmits the spring force accumulator 34 via the power transmission mechanism 44 on the rod 22 of the piston of the working cylinder of the brake mechanism or attached to the piston 20 of the working cylinder of the brake mechanism. From rod 22 of the piston of the working cylinder brake force is transmitted to the bracket 16 of the spindle disk brake mechanism, and thence to the corresponding lever 2 caliper disk brake mechanism for initiation of the clamping movement of the caliper 1 disk brake mechanism when the brake pads 8 with friction closure engages with the disk 10 of the brake mechanism.

The transfer device 44 made this so that movement of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami and piston 20 of the working cylinder brake the EIT mechanism coaxially and power gear ratio i gear device 44 with increasing stroke length s of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami increases, what, in particular, illustrates the characteristic curve of figure 6.

As follows from figure 5, the spindle 46 protrudes through the through hole of the partition wall 40 in the direction of the piston 20 of the working cylinder of the brake mechanism from which the piston rod 22 of the piston of the working cylinder of the brake mechanism in the form of a pipe of the piston of the working cylinder of the brake mechanism is held in the inner space of the spindle 46 so that the spindle 46 is located on the pipe 22 of the piston of the working cylinder of the brake mechanism with the possibility of rotation, for example, by mounting the bearings. On the radially outer shoulder of the pipe 22 of the piston of the working cylinder of the brake mechanism are thrust bearings 48, through which the compression force can be transmitted from the spindle 46 on the pipe 22 of the piston of the working cylinder of the brake mechanism. Thus the spindle 46 and the pipe 22 of the piston of the working cylinder of the brake mechanism or the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami and the piston 20 of the working cylinder of the brake mechanism are arranged coaxially to each other and, in particular, with respect to the Central axis 32 of the combined brake cylinder 12.

For the implementation of the power transmission through the gear mechanism 44, as shown embodiment of the combined brake cylinder 12 on Fig, on the compression ring 50, in which by means of desmoteplase thread 52 may be mounted on an intact pipe 22 of the piston of the working cylinder of the brake mechanism with the possibility of rotation of the spindle 46 (see figure 5), with the possibility of rotation around the axis perpendicular to the Central axis 32 of the combined brake cylinder 12, has at least one crank arm 54, which one of its end articulated to the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, and the other end rests on a fixed support surface 56 of the combined brake cylinder 12 (figure 2).

In the preferred embodiment, there are two crank lever 54 mounted for rotation on a perpendicular to the Central axis 32 of the combined brake cylinder 12 from the pressure rings 50 outside the support pins 58, which in relation to having a Central axis 32 of the plane are rotated relative to each other, i.e. the ends of the crank levers 54 are in opposite directions (see figure 3).

Figure 2 shows that in the preferred embodiment, respectively one end of the shoulder 60 of the cranked lever 54 by means of double-articulated latch 64 is connected to the piston 36 of the cylinder of the brake mechanism with spring energy is ccumulation, and the other end of the other shoulder 62 of the crank arm 54 is supported through made with the possibility of running at a fixed supporting surface 56 of the support roller 66, which is rotatably mounted on the other shoulder 62 of the crank arm 54. Support surface 56 to made with the possibility of spinning rollers 66 crank levers 54 are preferably formed on the partition 40 between the cylinder 30 of the brake mechanism with spring energoakkumulyatorami and the cylinder 18 of the operating brake mechanism and facing the spring chamber 38, in which is placed a spring-loaded accumulators 34.

In order to hold the control ring 50 in the combined brake cylinder 12 without the possibility of rotation, but with the possibility of axial displacement, at the end of the support pins 58 of the pressure rings 50 are movable body 68, which is held in passing in the direction of the Central axis 32 of the combined brake cylinder 12, preferably made in the piston cylinder 36 of the brake mechanism with spring energoakkumulyatorami wings 70 (figure 3). The piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, in turn, through at least one parallel to the Central axis 32 of the combined brake cylinder 12, is firmly connected to any is held in the partition 40 guide bolt 72 in the cylinder 30 of the brake mechanism with spring energoakkumulyatorami guaranteed from the scroll, so that the control ring 50 is fixed there with fixation of the rotation.

In the control ring 50 by means of blocking or deblokiruyuschee using demountable swivel lock 74 desmoteplase thread 52 can be screwed spindle 46 (figure 5). Collapsible rotary latch 74 is part of the unit 76 emergency leave intended for emergency dispensing cylinder 30 of the brake mechanism with spring energoakkumulyatorami. Under emergency release means of the mechanical leave the brake mechanism with spring energoakkumulyatorami if there is interference with the provision of compressed air and as a consequence, the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami could not be more moved to the release position by actuation by means of the working fluid.

The crank levers 54 form then gear 44, and the corresponding gear ratio i is detected on the basis of the provisions in this time crank lever 54 or shoulders 60, 62 crank levers 54. Thus in the position of the handbrake, when from the chamber 42 of the brake mechanism with spring energoakkumulyatorami removes the air and as a consequence, the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami due to the action of the spring Energoatom is atarov 34 is moved from the shown in figure 2, the provisions of vacation in figure 4 presents the position of the clamp, there is a transfer of force from the piston cylinder 36 of the brake mechanism with spring energoakkumulyatorami in articulated with him the tabs 64, which, for its part, articulated with one shoulder 60 crank lever 54, through both crank lever 54 in the control ring 50, and the crank levers 54 as a consequence, on the one hand addicted in motion, and with the other hand turn, and they create support for the forces of reaction at the fixed support surface 56. Depending on the rotary position of the cranked levers 54 shoulders 60, 62 crank levers 54 are other valid length a and b respectively with respect to the Central axes of the support pins 58 of the pressure ring 50, which is clearly demonstrated by comparing figure 2 (release position) with figure 4 (clamping).

In other words, valid for the torque of length a and b respectively of the levers on the shoulders 60, 62 crank levers 54 are changed depending on the respective rotary position of the cranked levers 54, which, in turn, depends on the stroke length of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami. Thus the gear ratio i is formed by means of the cranked levers 54 of the gear mechanism 44, depending on the stroke length of the piston 36 of the cylinder of the brake mechanism with spring is energoakkumulyatorami in this case, changes, however, in such a way that the force transmission ratio i increases, that is, a relatively large stroke of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami at a relatively low elasticity of the spring brake 34 is translated into a slight movement of the bracket 16 of the spindle disk brake mechanism with a relatively large expansion force of the caliper 1, the brake mechanism. The specialist selects the geometric parameters, in particular the length of the shoulders 60, 62 of the cranked levers, so that the power transmission ratio of i due to the presence of a bent lever 54 with increasing rotation angle or increasing the stroke length of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami increases, which shows the characteristic curve of figure 6.

Thus, if the cylinder 30 of the brake mechanism with spring energoakkumulyatorami for the implementation of the clip Parking brake is removed, the air, the elasticity of the spring power 34 through the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami and the tabs 64 based, respectively, on one shoulder 60 both crank levers 54. Installed on the compression ring 50 to rotate the crank levers 54 are guided in this by the support roller 66 are appropriate to estwenno other shoulder 62 of the lever on the bearing surface 56 of the septum 40. The sum of FDforces Ffederelasticity and effort FRwhen running in the axial direction is transmitted on the control ring 50, the spindle 46 and the pipe 22 of the piston of the working cylinder of the brake system, the bracket 16 of the spindle disk brake mechanism.

With increasing stroke of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami and thereby the rotation of the cranked levers 54 increases the effective gear ratio i cranked levers 54. With proper selection of the lengths of the shoulders 60, 62 of the levers or angles between the shoulders 60, 62 of the levers or lengths of the tongues 64 and/or the provisions of their articulated joints on the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami decrease the elasticity of the spring power 34 due to the stroke length of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami compensated by increasing gear ratio i, so that the detected sample characteristics acting on the bracket 16 of the spindle of the disc brake mechanism of the braking force in accordance with 6, which is due to the stroke length s of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami is almost constant.

Through both acting at an angle to the piston 36 of the cylinder of the brake mechanism with spring energy the battery reeds 64 as the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, and the control ring 50 is injected torque around the Central axis 32 of the combined brake cylinder 12. This torque is supported by held in the wings 70 mobile housings 68 of the pressure rings 50 in the piston 36 of the brake mechanism with spring energoakkumulyatorami, which, in turn, by means of guide bolts 72 without the possibility of rotation is retained in the cylinder 30 of the brake mechanism with spring energoakkumulyatorami (figure 2).

Created by the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami force of the Parking brake is transmitted through the crank arm 54 as the transmitting mechanism 44 on the control ring 50 and consequently enhanced. From the pressure ring 50 is multiplied force through is arranged to lock the thread 52 is inserted into the spindle 46, and thence through the thrust bearing 48 in the pipe 22 of the piston of the working cylinder of the brake mechanism and the bracket 16 of the spindle of the disc brake mechanism whose movement and so oriented in figure 2 or figure 4 left in the end converts this force into a rotary movement of the levers 2, 4 caliper disk brake mechanism.

If you have to leave the Parking brake there is no compressed air, for example, due to a defect or leak in the system is e compressed air, that is the release of the Parking brake can be achieved by actuating the device manual 76 emergency leave. To do this, by pressing the set in the combined brake cylinder 12 preferably vertically with the possibility of displacement of the push pin 78 is configured to turn on the compression ring 50 around the axis parallel to the Central axis 32 of the combined brake cylinder 12, the latch 80 is removed from the external gear 82 of the spindle 46, whereupon rotary latch between the spindle 46 and the pressure ring 50 is raised (figure 3). As the thread 52 between these parts is not self-locking, the spindle 46 is screwed into the control ring 50 until until both parts will not cease to exert an axial force and the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami is in contact with the bottom of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami. The piston 20 of the operating brake mechanism actuated from recoil, can also together with the spindle 46 to accept the release position.

The latch 80 is held in the raised position due to the introduction of a retaining pin 84 (Fig 3). Only when the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami by submitting press the deposits in the chamber 42 of the brake mechanism with spring energoakkumulyatorami will be moved to the release position and pull the control ring 50, the locking pin 84 will rise due to the contact with the wall 40, whereupon the latch 80 can again enter into the external toothing 82 of the spindle 46 and the result can again be formed rotary latch between him and the pressure ring 50.

Inside the pipe 22 of the piston of the working cylinder of the brake mechanism placed the knob of wear, which is formed, for example, by acting unilaterally acting Governor. When working braking into the chamber 24 of the operating brake mechanism is air, so that the piston 20 of the working cylinder of the brake mechanism through the rod 22 of the piston of the working cylinder of the brake mechanism actuates the bracket 16 of the spindle disk brake mechanism, and thus the caliper 1, the disc brake mechanism.

In the second embodiment according to Fig.7-11 are the same, compared with the previous version, and likewise items marked with the same reference position. In contrast, by means of the piston cylinder 36 of the brake mechanism with spring energoakkumulyatorami parallel to the Central axis 32 of the combined brake cylinder 12 may operate at least one wedge circuit 86, along which may be a shoulder 88 of the lever, at least one set is and the combined brake cylinder 12 to rotate lever 90, the other shoulder 92 which rests on the control ring 50, and the longitudinal one shoulder 88 of the lever 90 clinovia circuit 86 causes the rotary movement of the lever 90 about the axis 94 of rotation of the lever and thereby acting through the other shoulder 92 of the lever on the control ring, identically oriented with respect to the movement of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, axial force that best demonstrates Fig. When this axis 94 of rotation of the lever 90 is located, for example, perpendicular to the Central axis 32 of the combined brake cylinder 12 and held, for example, in the cover 96 of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami.

In the preferred embodiment, there are two symmetric about the Central axis 32 of wedge contour on the two wedge plates 86, which at least partially wrapping around the control ring 50 and which interact with two symmetrical relative to the Central axis 32 of the combined brake cylinder 12 and, respectively, are combined in two shoulders of the lever arm 90. This two shoulders lever 90 includes further the upper arm 90A and the lower lever 90b, respectively, with one conducted at the appropriate clinovia circuit 86 shoulder 88 of the lever and with one held on the supporting surface the displacement of the adjusting ring 50 by a shoulder 92 of the lever (Fig).

In this embodiment, the control ring 50 transmits the axial force, for example, through the thrust bearing 98 is made with the rotating part of the spindle drive in the shape of a gear 100, which is made to rotate on a fixed rotation portion 102 of the drive spindle by means of desmoteplase thread around 52 coaxially with the Central axis 32 axis (figure 10). The external toothing 82 gears 100, in turn, may include a latch 80 rotary clamp device 74 76 emergency leave, which is rotatably mounted in the cover 96 of the cylinder (11). Fixed from rotation portion 102 of the drive spindle may then transmit the axial force on the rod 22 of the piston of the working cylinder of the brake mechanism.

How, in particular, of 11, the latch 80 is formed as made with the possibility of rotation around the axis 104 of rotation parallel to the Central axis 32 of the rocker lever, which on one hand can log into the external toothing 82 gears 100 and which on the other hand can be fed under pre-tension of the spring controlled manually, several protruding through the through hole of the housing 14 push the pin 78 so that depending on the position of the pressure pin 78 without the possibility of rotational d is to achieve to connect the gear wheel 100 with the housing 14 of the combined brake cylinder 12 or to release this connection to rotate the gear wheel 100 fixed on the rotation of the part 102 of the spindle drive.

If the next cylinder 30 of the brake mechanism with spring energoakkumulyatorami moves in Fig.7. the provisions of vacation if Parking brake is presented in figure 9, the position of the clamp, both gate circuit 86 move along with it, resulting in some shoulders two shoulders 88 of the lever 90 is moved along the wedge circuits 86 and thereby initiate rotational movement of the two shoulders of the lever 90, resulting in other shoulders 92 of the lever to move the control ring 50 in unidirectional with respect to the movement of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami axial direction that best demonstrates Fig. At the ends of the other shoulders two shoulders 92 of the lever 90 is supplied, for example, rollers 104 to enable break-on wedge contours 86 or pressure ring 50.

Gear ratio i is detected on the basis of the lengths a and b of the shoulders 88, 92 of the rotating lever 90 and dependent on the stroke length of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami angle α of the wedge gate circuits 86 in the corresponding point of tangency of the rollers 104 (see Fig.7 and Fig.9):

Set in the combined brake cylinder 12 fixed from rotation of the control ring 50 passes then acting on it, the axial force through the UE is RNA bearing 98 on the gear wheel 100, the rotation which is relatively fixed from rotation of the part 102 in normal operation is blocked, however, by turning the latch 74. From fixed from rotation portion 102 of the drive spindle axial force is transmitted to the rod 22 of the piston of the working cylinder of the brake mechanism.

In normal operation, push the pin 78 of the rotary latch 74 by means of spring-loaded in an outward direction so that the latch 80 includes an external toothing 82 gears 100 and prevents its rotation (11). If the emergency leave Parking brake push pin 78 of the rotary latch 74 then is actuated by pressing the latch 80 is folded around the axis of rotation, causing it to one end comes out of the external gear 82 gears 100. This contributes to the fact that the gear wheel 100 can rotate freely relative to the fixed rotation portion 102 of the drive spindle by means of desmoteplase thread 52 to until both parts will not cease to exert a force impact on each other. In this case, piston cylinder 36 of the brake mechanism with spring energoakkumulyatorami moves until it touches the bottom of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami, and the piston 20 of the working cylinder of the brake mechanism, here is the action of a return spring 28, may together with the spindle 46 to move in presented on Fig.7. the release position.

In the third embodiment, in accordance with Fig-15 the same compared to the previous versions and works in a similar way the items marked with the same reference position.

As in other versions of the invention, the cylinder 30 of the brake mechanism with spring energoakkumulyatorami and the cylinder 18 of the operating brake mechanism are arranged coaxially. As spring energoakkumulyator 34 is provided, for example, a conical coil spring, which is clamped an annular piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami.

Between the piston 36 and cylinder of the brake mechanism with spring energoakkumulyatorami and the rod 22 of the piston of the working cylinder of the brake mechanism position symmetrically or in relation to containing the Central axis 32 of the combined brake cylinder 12 plane rotated relative to each other are two rocker mechanism 106, which transmit the force of the spring energoakkumulyator 34 on the rod 22 of the piston cylinder 18 of the operating brake mechanism. The rocker mechanism 106 is composed mainly of the rocker arm 108, one end of which is rotatably installed on the housing 14 of the cylinder and the other end of the village is edstam latch 110 articulated to the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, and roller earrings 112, which at one end rotatably installed on the compression ring 50 and at the other end has a support roller 114 which engages with the surface 116 of the scenes rocker arm 108.

If the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami performs the move, the rocker arm 108 is rotated around its fulcrum at the front 118 of the bearing in the housing of the cylinder. Due to the rotation of the rocker arm 108 changing the angle between the roller ring 112 and the surface 116 of the slide, which is typically configured at 90 degrees. Roller earring 112 independently rotated after that until, until the line of action of force again will not be perpendicular to the tangent to the surface 116 of the scenes at the touch point support roller 114. Due to this change the actual arms of the levers, and hence the gear ratio.

By an appropriate choice of the geometry of the wings, the location of the support points and the lengths of the levers and reeds can be obtained increases due to the stroke of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami gear ratio, whereby reducing the effort of the spring energoakkumulyator 34 is compensated or at least reduced by the stroke length.

As in the other embodiments, is made the I invention, the housing 14 of the combined brake cylinder 1 sostoi mainly of three parts, which in the preferred embodiment, swiney with each other. The cylinder 18 of the operating brake mechanism is placed in the left half of the cylinder (Fig), the cylinder 30 of the brake mechanism with spring energoakkumulyatorami is located in the right half and is closed by a cover 96 of the cylinder. Through the use of cover 96 of the cylinder allows the Assembly of the cylinder 30 of the brake mechanism with spring energoakkumulyatorami.

The annular piston 20 of the working cylinder of the brake mechanism is rigidly connected to the pipe 22 of the piston of the working cylinder of the brake mechanism, for example, by means of a sealed press the nozzle and the outside diameter is sealed by press-fitting cuffs, and the inner diameter by a radial seal between the plate cylinder and the pipe 22 of the piston of the working cylinder of the brake mechanism. The piston 20 of the working cylinder of the brake mechanism through at least one guide bolt is locked against rotation relative to the body.

The pipe 22 of the piston of the working cylinder of the brake mechanism carried out, first, in the cylinder 18 of the operating brake mechanism, and secondly, in the partition 40. The cylinder 30 of the brake mechanism with spring energoakkumulyatorami contains external TP the positive surface of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, made in the form of an annular piston, and has a guide surface for the movable housings 68 of the adjusting ring 50, which, for its part, held at the ends of the two protruding perpendicular to the Central axis 32 of the support pins 58 of the pressure rings 50 (Fig). In the partition 40 is formed not visible in the context of connecting elements supply air to the chamber 42 of the brake mechanism with spring energoakkumulyatorami and the working chamber 24 of the brake mechanism. The piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami provided with a seal on the inner and outer diameter. With the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, for example, swiney pivot pin for pivotally jointed with them reeds 110, with their axes of rotation are perpendicular to the Central axis 32 of the combined brake cylinder 1. Spring energoakkumulyator 34, which in this case is made in the form of a conical coil spring, is supported on one side on the housing 14 of the cylinder, and on the other side of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami.

The rocker arms 108 on the one hand through the reeds 110 articulated to the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami, and on the other hand, with the possibility in the stop firmly established in vincenne with the body 14 of the cylinder rack 118 bearings. Mounted on the support pins 58 of the pressure ring 50 around the axis perpendicular to the Central axis 32 of the combined brake cylinder 12 roller earrings 112 have their pointing in the direction from the reference pins 58 the ends of the support rollers 114, which ultimately transfer the force from the rocker arms 108 on the control ring 50.

On the compression ring 50 is installed latch 80 rotary clamp device 74 76 emergency leave (Fig). The device 76 emergency vacation contains desmoteplase thread 52 to mechanically reduce braking effort when Parking, if the spring clip of the battery 34 there is no compressed air, and is also made with the possibility of screwing through desmoteplase thread 52 fixed on the rotation of the part 102 of the spindle drive gears 100, through which, for example, two bearings 120 roller rotatably installed in the compression ring 50, fixed to the rotation part 102 of the spindle drive, which by means of two clamps engages in the slot of the tube 22 of the piston of the working cylinder of the brake mechanism and thereby first , installed it with fixation against rotation, and secondly, in the direction of clamping of the brake mechanism can transmit axial forces on the pipe 22 of the piston of the working cylinder is th brake mechanism, from latch 80 installed in the compression ring 50 and is made with the possibility of introducing into engagement with the toothed wheel 100. It supports emerging in desmoteplase thread 52 torque and holds it on the control ring 50, which through movable housings 68 is supported in the wings of the housing 14 of the cylinder. As in other versions of the invention the control unit emergency release latch 80 is manually removed from the external gear 82 gears 100.

For pneumatic dispensing cylinder 30 of the brake mechanism with spring energoakkumulyatorami (Fig) into the chamber 42 of the brake mechanism with spring energoakkumulyatorami is pressure, so that the spring accumulator 34 is pre-tightened the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami.

For clamping of the brake mechanism with spring energoakkumulyatorami (Fig) from the chamber 42 of the brake mechanism with spring energoakkumulyatorami removes the air, so that the elasticity of the spring energoakkumulyator 34 through both tabs 110, rocker lever 108 and roller earrings 112 supported pressure ring 50. It holds the force through the device 76 emergency vacation to the pipe 22 of the piston of the working cylinder of the brake mechanism, and thence to the bracket 16 of the spindle disk brake mechanism. About the e roller earrings 112 are automatically configured depending on the stroke length of the piston angular position of the rocker arms 108. They occupy a position in which the line of action of force roller earrings 112 is perpendicular to the tangent to the surfaces 116 the scenes at the corresponding point touch support rollers 114. In other words, in this case, the fulcrum roller earrings 112, the center of the support roller 114 or the touch point support roller 114 with the surface 116 of the scenes are arranged on one straight line.

In the present embodiment, the surface 116 of the slide, on which rolls the support roller 114 is flat. Depending on the desired gear ratio may, however, also the presence of, for example, concave or convex surface 116 of the scenes. In the case of a convex surface, the radius of curvature should not be, however, less than the length of the roller earrings 112 so that you can adjust the sound balance.

Depending on the stroke length of the piston 36 of the cylinder of the brake mechanism with spring energoakkumulyatorami gear ratio i can be calculated on the basis of the lengths of a and b real of the lever arms and the angles α and β (Fig and Fig):

i=acosβbcosα

Force FStacting on the control ring 50 or the bracket 16 of the spindle discover the brake mechanism is detected, thus, through:

FSt=i·FF

If for a vacation in the clamping of the brake mechanism with spring energoakkumulyatorami not available compressed air, for example, due to leaks, the brake mechanism with a spring energoakkumulyatorami may be released by actuation of the manual device 76 emergency leave. To do this, by pressing on the control unit emergency leave installed in the compression ring 50, the latch 80 is withdrawn from engagement 82 gears, resulting in eliminating the locking of the possibility of rotation between the executed without the possibility of rotation of the part 102 of the drive spindle and the drive gear 100. As the thread 52 between the two parts is desmoteplase, the gear wheel is screwed on without the possibility of rotation of the part 102 to until both parts will not cease to give each other power. In this case, piston cylinder 36 of the brake mechanism with spring energoakkumulyatorami goes into the release position, and the piston 20 of the working cylinder of the brake mechanism, driven by a return spring, together with executed without the possibility of rotation of the part 102, for its part, accepts the release position.

1. Combined brake the second cylinder (12), containing the cylinder (18) of operating brake mechanism as an active brake, at least one is driven by a working fluid, a piston (20) of the working cylinder of the brake mechanism, which is designed to actuate the brake mechanism (1) via the shaft (22) of the piston of the working cylinder of the brake mechanism, and the cylinder (30) of the brake mechanism with spring energoakkumulyatorami as a passive Parking brake, actuated by the working fluid, the opposite effect, at least one spring energoakkumulyator (34), the piston (36) cylinder of the brake mechanism with spring energoakkumulyatorami, the piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami if the Parking brake is configured to transfer forces to at least one spring energoakkumulyator (34) through a transmission mechanism (44) on the rod (22) of the piston of the working cylinder of the brake mechanism, characterized in that the gear mechanism (44) of the piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami and rod (22) of the piston of the working cylinder of the brake mechanism coaxially, and the power ratio with increasing stroke length of the piston (36) cylinder of the brake mechanism with proii the NYM energoakkumulyatorami increases.

2. Brake cylinder according to claim 1, characterized in that it contains a fixed from rotation and is arranged to actuate coaxially with the Central axis (32) of the combined brake cylinder (12) control ring (50), through which the axial forces acts on the actuator (46, 50; 100, 102) of the spindle, one part (50; 102) which is fixed from rotation, and the other part (46; 100) which is arranged to rotate coaxially with the Central axis (32), the rotational movement is performed with the rotating part (46; 100) of the actuator (46, 50; 100, 102) of the spindle for transmitting axial forces between fixed from rotation part (50; 102) and the rotating part (46; 100) is blocked, and to stop transmission of the axial force is released through the demountable swivel lock (74).

3. Brake cylinder according to claim 2, characterized in that thread (52) is not self-locking thread.

4. Brake cylinder according to claim 2 or 3, characterized in that the collapsible rotary latch (74) is made with the possibility of introducing into the device (76) emergency leave emergency leave Parking brake.

5. Brake cylinder according to claim 2 or 3, characterized in that the transmission of axial forces between the actuator (46, 50; 100, 102) of the spindle and the rod (22) of the piston of the working cylinder of the brake mechanism.

6. Brake the second cylinder according to claim 2 or 3, characterized in that on the compression ring (50) has two eccentric relative to the Central axis (32) of the gear mechanism (44) to compensate for the torque around the axis perpendicular to the Central axis (32).

7. Brake cylinder according to claim 2 or 3, characterized in that the control ring (50) and fixed from rotation part of the actuator (46, 50) spindle combined and rotary latch (74) is located between the pressure ring (50) and is made with the rotating part (46) of the actuator (46, 50) of the spindle.

8. Brake cylinder according to claim 7, characterized in that on the compression ring (50) is made of at least one located perpendicular to the Central axis (32) of the combined brake cylinder (12) anchor pin (58), which can be rotated is selected, at least one crank (54), which by its end articulated to the piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami, and the other end rests on a fixed support surface (56) of the combined brake cylinder (12) so that when the actuation piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami if the Parking brake is initiated by the turn supported by a cranked lever (54) around the anchor pin (58), as well as unidirectional given the s in the action of the pressure ring (50).

9. Brake cylinder according to claim 8, characterized in that on passing from the outside, perpendicular to the Central axis (32) of the combined brake cylinder (12) supporting the pins (58) of the adjusting ring (50) is installed with the possibility of rotation of a cranked levers (54), which in relation to containing the Central axis (32) of the combined brake cylinder (12) plane are rotated to each other.

10. Brake cylinder according to claim 9, characterized in that the shoulder (60) of the cranked lever (54) by means of double-articulated latch (64) is connected with the piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami.

11. Brake cylinder according to claim 9 or 10, characterized in that the other shoulder (62) crank arm (54) is supported by made with the possibility of running on a fixed support surface (56) of the support roller (66).

12. Brake cylinder according to claim 11, characterized in that at the ends of the support pins (58) of the adjusting ring (50) are movable body (68), which without the possibility of rotation conducted in located in the direction of the Central axis (32) of the combined brake cylinder (1) wings.

13. Brake cylinder according to item 12, characterized in that the bearing surface (56) for the cranked lever (54) is performed on the partition (40) between the cylinder (30) of the brake mechanism with a spring e is electomotion and the cylinder (18) of operating brake mechanism.

14. Brake cylinder according to item 13, wherein the retainer (40) forms a support surface for at least one spring energoakkumulyator (34) of the cylinder (30) of the brake mechanism with spring energoakkumulyatorami.

15. Brake cylinder according to claim 2 or 3, characterized in that the rotary latch (74) contains all executed with a possibility of introducing external gearing (82) is made with the rotating part (100) of the actuator (100, 102) spindle driven manually latch (80), which is installed with the possibility of turning on the compression ring (50).

16. Brake cylinder according to claim 2 or 3, characterized in that the piston (36) of the cylinder of the brake mechanism with spring energoakkumulyatorami parallel to the Central axis (32) of the combined brake cylinder (12) is actuated, at least one V-contour (86), along which held the shoulder (88) of the lever, at least one installed rotatably on the combined brake cylinder (12) of the lever (90), and the other shoulder (92) of the arm (90) is based on the control ring (50), and one shoulder (88) of the lever (90) along clinovia circuit (86) initiates pivotal movement of the lever (90) around the axis (94) of rotation of the lever and unidirectional relative movement of the piston (36) of the brake mechanism with spring Energoatom what system axial force on the control ring (50).

17. Brake cylinder according to item 16, characterized in that the axis (94) of rotation of the arm (90) is perpendicular to the Central axis (32) of the combined brake cylinder (12).

18. Brake cylinder according to item 16, characterized in that it contains two in the direction of the axis (94) of rotation of the lever (90), at least partially embrace the control ring (50), V-contour (86), which interact with two symmetric with respect to the Central axis (32) of the combined brake cylinder (12) and combined into two shoulders lever (90), leverage.

19. Brake cylinder according to item 16, characterized in that the control ring (50) is designed to transfer axial force through the thrust bearing (98) performed with the rotating part of the actuator (100, 102) of the spindle forming a gear wheel (100), gearing (82) which is arranged to actuate the manually latch (80) rotary latch (74), and a gear wheel (100) mounted for rotation on a fixed rotation part (102) of the actuator (100, 102) spindle through-thread 52), which transmits the axial force on the rod (22) of the piston of the working cylinder of the brake mechanism.

20. Brake cylinder according to claim 2 or 3, characterized in that it contains the rocker mechanism with at least one articulated with pressure ring (50) railwaycars (112), at least one sliding guide, which held at least one rocker arm (108), which, on the one hand, articulated with the body (14) of the combined brake cylinder (12)and, on the other hand, at least one articulated to the piston (36) of the brake mechanism with spring energoakkumulyatorami tongue (110).

21. Brake cylinder according to claim 20, characterized in that the roller earring (112) on your remote from the adjusting ring (50) end fitted made with the possibility of rotation of the supporting roller (114), which is made with the possibility of running across the surface (116) scenes rocker arm (108).

22. Brake cylinder according to claim 20, characterized in that the control ring (50) is installed through at least one mobile guide (68), with fixation against rotation in the housing (14) of the combined brake cylinder (1).

23. Brake cylinder according to claim 20, characterized in that it contains two roller earrings (112) with rocker rails, two conducted in the rocker guide rocker arm (108)and two latch (110), which are located relative to the plane containing the Central axis (32) of the combined brake cylinder, rotated to each other.

24. Brake cylinder according to item 23, wherein the control ring (50) has two spaced perpendicular to the Central the axis (32) of the supporting axle (58), which contain one support roller earrings (112).

25. Block (1) caliper disk brake of a rail vehicle containing at least one combined brake cylinder (12) according to any one of claims 1 to 24.



 

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6 cl, 3 dwg

FIELD: transport.

SUBSTANCE: proposed disk brake block comprises two flanges with appropriate friction linings to allow friction against disk. Said flanges are articulated on ends of two levers driven by brake force source that comprises first piston displacing along first axis A. Brake block comprises also assembly to automatically control the gap between friction linings and said disk. First piston transmits braking force to pusher arranged inside aforesaid source to increase and transmit said force via said assembly and, along second axis B perpendicular to said first axis A, to ends of said levers perpendicular to those where said flanges are articulated with.

EFFECT: higher operating performances.

12 cl, 7 dwg

Vehicle clamp brake // 2429393

FIELD: transport.

SUBSTANCE: brake clamp comprises first braking lever arranged opposite vehicle wheel first friction surface and second braking lever arranged opposite second friction surface. Moving brake shoe is mounted on first braking lever to apply brake force to first friction surface. Brake clamp houses pistons to move moving brake shoe in response to membrane extension and guide frame to guide pistons in direction perpendicular to first friction surface. Moving brake shoe applies uniform brake force to vehicle wheel together with brake shoe secured to second braking lever.

EFFECT: uniform pressure on revolving wheel surface.

13 cl, 12 dwg

FIELD: machine building.

SUBSTANCE: drive mechanism of disk brake of vehicle includes bracket consisting of case and cover, brake drive shaft and screw gear installed in bracket, and also lever mounted on external side of bracket on brake drive shaft. A mechanism of automatic control of the brake including a driving link is installed inside the lever. The driving link of automatic control of the brake is arranged coaxially to the brake drive shaft and is kinematically coupled with the bracket. A movable in circumferential direction packing is positioned between the bracket and a controller of the drive lever so, that internal cavities of the bracket and the lever form a common cavity sealed from the side opposite to the bracket.

EFFECT: simplification of design, raised maintainability and service life of mechanism of vehicle dick brake drive.

1 dwg

Modular disk brake // 2298712

FIELD: mechanical engineering, namely, disk brakes, having floating or sliding support.

SUBSTANCE: disk brake contains body for positioning braking mechanism on it and support, detachably connected to body. Disk brake is formed of various modules. Body acts as supporting means for fastening other modules. One of modules is formed by support together with at least three guiding fingers. Lid of braking mechanism is strongly connected to body. Seal is positioned and compressed during assembly between lid and body.

EFFECT: increased technical characteristics of disk brake.

18 cl, 7 dwg

Brake mechanism // 2292497

FIELD: mechanical engineering.

SUBSTANCE: brake mechanism comprises two pivotally interconnected levers and two opposite brake blocks secured to the levers for permitting periodical interaction with the rotating disk. The brake mechanism is provided with air-operated cylinder mounted at one of the ends of the lever so that its housing is secured to one of the levers and the rod is secured to the other lever. The brake blocks are mounted at the second end of the levers whose pivot joint is interposed between brake blocks and air-operated cylinder. One of the brake blocks is made of a current-carrying bus spring-loaded with respect to the lever for permitting connection with a power source. The levers are spring-loaded one with respect to the other by means of an extension springs interposed between the pivot joint of levers and air-operated cylinder. The rotating disk is made of two members whose bases are rigidly interconnected. One of the members is mounted for permitting contact with the current-carrying bus, is made of a conducting material, and is provided with a member for releasing voltage .

EFFECT: expanded functional capabilities.

2 dwg

Disk brake // 2265144

FIELD: transport mechanical engineering.

SUBSTANCE: disk brake comprises braking disk, active and reactive braking blocks, support, and mechanism for releasing braking blocks. The mechanism is the cam-roller type. The drive of the reactive block is made of a floating frame composed of active and reactive beams interconnected through the ties.

EFFECT: enhanced reliability.

3 dwg

The invention relates to a disc brake device for a vehicle

FIELD: transport.

SUBSTANCE: invention relates to automotive industry, particularly, to brake systems. Proposed method consists in perforating brake cylinder bottom. Note here that perforations feature diameter smaller than that of mounting screw thread. Then, perforations are reamed by set tool to produce beads to alloy mounting screws to pass there through. Thereafter force is applied to mounting screws to strain the beads so that the latter enter the groove or mounting screws are grooved to be locked in groove. Brake cylinder is producing using the above described method.

EFFECT: higher reliability and safety.

7 cl, 14 dwg

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