Brake system

Abstract

The present invention relates to a braking device that can be mounted on a rotating shaft, the braking device comprising a guide support (1) including at least one transmission guide (2), a first casing (3), an axially movable first pusher element (13, 17, 18) and a lining disc (5) arranged between a first brake disc (6) and a second brake disc (7). The first casing (3) comprises a drive system configured, when activated, to move the first pusher element (13, 17, 18) axially towards the lining disc (5) and to push the first brake disc (6) towards the first lining (52), and when deactivated, to move the first pusher element (13, 17, 18) axially backwards in a direction opposite to the direction of pushing the first disc brake (6).

Description

[Technical Field]

[0001] The present invention comprises a braking device having a system that optimizes the braking capacity of a rotating means such as a shaft, based in particular on the retraction capacity of the brake disc, i.e., is specifically designed to reduce the "time to lock" (TTL), i.e., the time required to brake, by minimizing the brake disc to lining separation and allowing the shaft to rotate without residual friction. The invention can be applied in various industrial sectors, primarily the automotive industry, but also in all industries where braking systems operate, even non-automotive, such as turbines and motors used to generate electrical energy, but is particularly suitable for vehicles powered by electric motors. DISCLOSURE OF THE INVENTION [Problem to be solved by the invention]

[0002] Problems to be solved by the invention and background of the invention Many braking systems having different types of configurations are known in the art, particularly in the automotive field, where greater research and development has taken place in this field, resulting in different types of braking systems based on the needs of the vehicle.

[0003] The most well-known braking system in the automotive sector is De A disc brake system in which, when the brake pedal is operated, a hydraulic, pneumatic, or electrical system is activated, causing the brake pads to move against a disc that rotates with the vehicle's wheel, and the friction between the brake pads and the disc brakes the wheel and, therefore, the vehicle.

[0004] In this braking system, as already mentioned, the brake disc continuously rotates with the vehicle wheel while the pads remain in a fixed position relative to the wheel. The axial movement of the pads towards the brake disc, bringing them into contact with the disc and applying pressure to the disc, generates friction and brakes the disc and therefore the vehicle wheel, resulting in overheating between the contacting parts.

[0005] Since the brake disc is constantly rotating, the only cooling available is through natural convection. Similarly, the surface, material and shape of the brake pads make it very complicated to provide a cooling system to remove the heat generated.

[0006] In addition to overheating, known systems of the prior art limit the useful life of both the pads and brake discs due to uneven pad wear and pad offsets or eccentricities that affect braking.

[0007] Document ES2705358 describes a braking device that defines the axial displacement of a brake disc, the lining disc being attached to a shaft and therefore rotating with the shaft, and in the embodiment described therein, the brake disc can be cooled by a fluid flowing through an internal cavity, improving the operation of the device by reducing its heating capacity.

[0008] Document ES2705358 also describes a braking device that is specially adapted so that the brake discs, which are only movable in the axial direction, can be internally cooled by a fluid, while the lining discs transmit the rotation of the shaft. This document focuses on the method of axial displacement of the moving elements of the device, such as the brake discs and the lining discs.

[0009] This consists in a displacement of the brake disc relative to the lining disc sufficient to allow the latter to rotate without any friction, thus minimizing the distance required to move the brake disc axially in the braking direction until the required contact for braking is achieved.

[0010] In other words, none of the devices described in these documents includes technical features that make it possible to provide an approximation system that positions the brake disc at a minimum distance from the lining disc, without generating residual friction between them, and that increases the braking propagation speed throughout the entire wear stroke of the brake pad, making it possible to shorten the braking time as much as possible.

[0011] Similarly, the devices described in the above-mentioned documents require compression springs placed between the lining disc and the brake disc to separate the contact areas of said discs, which contain elements that are susceptible to damage and / or corrosion due to the stresses to which they are continuously subjected. [Means for solving the problem]

[0012] The present invention relates to a braking device that can be attached (or assembled) to a rotating shaft, i.e., a torque-transmitting shaft, which is assembled to the braking device directly or indirectly via a member such as a bushing. The braking system is specially adapted for vehicles with electric drive motors or hybrid drive systems, where the energy efficiency of all systems integrated into their architecture becomes more important in order to maximize the energy provided by the current battery, thereby reducing battery weight and increasing vehicle autonomy. On the other hand, electric and hybrid vehicles have energy recuperation systems capable of generating a braking torque of up to [0.2g-0.3g], which cooperate with the mechanical braking system to reach emergency deceleration braking of 1g, so that the mechanical system is operated by EHB (electro-hydraulic brake) or a 100% electric system. This braking device substantially improves braking, and thanks to the optimization achieved by this approximation system, there is no energy loss due to residual friction, there is less wear as with free rotation, and because it is closer, less energy is required for its application, all of which improves the autonomy of the vehicle.

[0013] Meanwhile, continuous improvement of active safety systems has become a priority for modern automobiles. Many of these electronic systems are associated with the braking system, such as ABS, ESP, torque vectoring, anti-roll, and traction control (TC). This braking system significantly improves TTL, which provides a more immediate response to vehicle dynamics, thereby improving the active safety of the vehicle. Thanks to the design of this mechanical device, it is lighter in weight and more robust, even when large axial forces are applied to generate large braking torques.

[0014] This device is - a guide support that can be rigidly mounted on a shaft, said guide support comprising at least one longitudinal transmission guide, preferably three guide shafts evenly distributed on the guide support, said transmission guides being arranged eccentrically with respect to the shaft and pointing in the same direction as the axial direction of the shaft when the guide support is assembled on the shaft; - a first fixed support casing that does not move or rotate with the shaft and allows the brake device to be rigidly fixed to an external frame of a vehicle or the like; - First Fixed Support a first pusher element axially movable relative to the casing; - lining discs, - a support disc coupled in a floating manner to at least one transmission guide of the guide support; a first lining assembled to a first surface of the support disc; - a second lining mounted on a second surface of the support disc; - First Fixed Support a first brake disc axially movable relative to the casing; - a second brake disc; Equipped with - a lining disc is disposed between the first brake disc and the second brake disc; The guide support is configured to transmit rotation of the shaft to the lining disc, and the lining disc is coupled to the guide support by at least one transmission guide and is therefore configured to rotate together with the shaft.

[0015] The support disc being coupled to the transmission guide or guide in a floating manner means that when the disc is attached to or coupled to a shaft, the disc rotates with the shaft, but may have, for example, a loose coupling so that the support disc can move in the axial direction of the shaft even if the shaft does not move.

[0016] The second brake disc may be mounted in the same manner as the first brake disc, i.e., it may move axially relative to the shaft, but does not require a loose connection and may remain stationary for the device to function.

[0017] The first pusher element and the first brake disc are fixed and form an axially displacing unit. To this end, the brake device may include a compression spring arranged between the brake discs, so that the first brake disc always contacts the first pusher element, regardless of the displacement of the first pusher element. In other embodiments, the elements may be fixed in another way, such as by mechanical elements like pins, or may be formed from a single casting.

[0018] 1st Fixed Support The casing includes a drive system configured to, when actuated, move the first pusher element axially toward the brake disc, pushing the first brake disc toward a first brake lining of the brake disc and generating a first friction, and in the displacement, when the first brake disc is pushed by the first pusher element, exert a pushing pressure on the first lining of the lining disc and move it axially toward the second brake disc.

[0019] In this way, the second brake disc acts as a stop against the axial displacement of the first pusher element and can remain stationary, so that the lining discs can contact each brake disc on both sides, compressing the linings and generating a braking torque that is transmitted from the brake disc to the shaft. In this way, the second brake disc does not have to move axially to brake the lining discs, but can move axially without the first Fixed Support It can be rigidly attached to the casing, but it is also preferable to fix it in a floating manner.

[0020] The drive system is configured, when activated, to move the brake disc in a pushing direction towards the second brake disc, and, when deactivated, to retract the first pusher element and move the first pusher element axially in a direction opposite to the direction in which it pushes the first brake disc.

[0021] In this way, the first brake disc is configured to move axially in a direction opposite to the direction in which it pushes the lining disc, together with said opposite retraction of the first pusher element.

[0022] This retraction is achieved by a small displacement of the first pusher element in the opposite direction to the pushing displacement, which is also carried out by the first brake disc by forming an axial displacement unit. This small displacement creates a small axial gap between the two brake discs where the lining discs are located.

[0023] The floating connection of the lining disc on the transmission guide and the rotation of the lining disc connected to the rotating shaft are configured so that when the first brake disc moves in the opposite direction, the lining disc is positioned between the two brake discs in the created axial gap in a self-positioning state. In other words, no spring is required between the support disc and the brake disc to separate them; the attachment of the lining disc to the transmission guide is sufficient.

[0024] In this way, the retraction only moves the first brake disc enough to allow the lining disc to rotate without leaving friction with the brake disc, and therefore the movement of the first brake disc during a new braking is also minimized, thereby minimizing the blocking time for a new braking.

[0025] Similarly, this configuration also allows the distance between the brake disc and the lining disc to be constantly adjusted as the lining wears. In other words, regardless of the lining wear, this configuration always positions the brake disc at a minimum distance from the lining, and this distance is determined depending on the elements constituting the drive system, thus solving the problems present in the devices described in the background.

[0026] In other words, the free rotation of the lining disc (not subjected to axial force by the brake disc via the spring) and its floating position relative to the guide support causes the lining disc to develop a very small lateral eccentricity, sufficient to move it apart on either side of the brake disc until inertia causes it to center itself. It is clear that the very small space created by the retraction of the pusher is sufficient to "self-adjust", freeing the lining from friction and releasing the rotating shaft from the residual brake.

[0027] In one embodiment, the brake device comprises: - a second fixed support casing arranged at an opposite end of the first support casing; a second pusher element axially movable relative to the second support casing; Equipped with The second pusher element and the second brake disc are fixed and form an axial displacement unit, and the second Fixed Support The casing includes a drive system configured, when actuated, to move the second pusher element axially toward the lining disc and push the second brake disc toward a second lining of the lining disc.

[0028] In other words, the second Fixed Support The operation of the device having a casing comprises a first Fixed Support This is the same as with the casing, but in this case the second brake disc can move axially towards the lining disc, thus allowing both brake discs to move towards the lining at the same time, resulting in faster braking.

[0029] In this embodiment, the second brake disc is configured to exert a pressing force on the second lining in the axial direction when pushed by the second pusher element, causing said brake disc to move towards the first brake disc.

[0030] As with the first pusher element, the second Fixed Support The drive system of the casing is configured to retract the second pusher element when not in operation, and the second pusher element is axially retracted to the second brake The disc moves in the opposite direction to the direction you push it.

[0031] For this reason, the second brake disc is configured to move axially in a direction opposite to the pushing direction of the lining disc in conjunction with the retraction of the second pusher element, and the lining disc is configured to self-position between the two brake discs when the first and second pusher elements retract, i.e., to be separated from both without generating residual friction.

[0032] These embodiments are the first Fixed Support Even if the device has a casing, the first and second Fixed Support Even those with a casing may have two or more brake discs and one or more lining discs interposed between the brake discs, and are not limited to having only two brake discs and one lining disc.

[0033] In one embodiment, the support disc of the lining disc comprises: - peripheral regions of the first and second faces of the support disc, to which the lining is fixed; - at least one sliding connection housing including an axial direction; Equipped with The sliding connection housing is preferably arranged at the outer peripheral portion of the central through-hole of the support disk and is coupled to at least one longitudinal transmission guide in a loosely adjusted mounting state.

[0034] In one embodiment, the brake device includes a resilient damping gasket disposed between each mating connection of each transmission guide and the sliding connection housing of the lining disc. The gasket allows for better damping of the connection between the components, avoiding vibrations and resonances that could damage the device components, as well as canceling vibrations that could generate frequencies in the human auditory spectrum. Preferably, the gasket is made of fluororesin rubber, has high chemical resistance, excellent abrasion and corrosion resistance, and can withstand continuous temperatures of 200° to 280° (peak 340°), making it suitable for the described application.

[0035] In one embodiment, the lining disk has a plurality of fins arranged around the periphery of the central through hole of the support disk to dissipate heat accumulated in the disk; - the plurality of fins are rigidly attached to a support disc by rigid connecting means; or The fins and the support disc are formed from a single casting.

[0036] In other words, they can be manufactured in one piece or multiple pieces can be attached together by mechanical means such as welding or screws.

[0037] When the lining disc rotates, these fins rotate at the same angular velocity due to their connection with the rotating shaft. As the fins rotate, they generate fluid flow, creating a flow from the inside to the outside. Depending on the inclination angle and surface area of ​​these fins, they can provide higher speeds and fluid flow rates at the same rotation speed.

[0038] In one embodiment, the lining disk comprises a plurality of first and second linings fixed to the outer regions of the first and second surfaces of the support disk, respectively, the linings being separated by radial groove-like gaps, and the linings having a blade shape.

[0039] These flow gaps are advantageous for discharging particles from the support disk, and filters capable of retaining particles can be placed in them to prevent the particles from affecting the operation of the device and reduce environmental pollution.

[0040] In one embodiment, the brake system includes a particle filtering structure concentrically disposed over the lining disc, the particle filtering structure configured to retain particles detached from the lining. In one embodiment, the structure is disposed between the first brake disc and the second brake disc.

[0041] In another embodiment, the filtering structure is a cylindrical framework that is arranged to cover the first and second brake discs, i.e., the areas where friction occurs and particles are expelled from the lining, and can be fixed to the casing or any element that does not move relative to the shaft.

[0042] In one embodiment, at least one brake disc has an annular shape with a central disc through-hole concentric with the shaft including the axial direction and a solid outer friction portion against the lining, in other words, the area of ​​the brake disc where friction occurs is solid so that it has a greater resistance to the stresses to which it is subjected.

[0043] In one embodiment, at least one brake disc has an annular shape with a central disc through-hole concentric with the shaft, i.e., including the axial direction, and an outer friction portion against a lining with at least one internal channel configured for the passage of a fluid. Preferably, the brake disc has a plurality of radially open internal passages through which a fluid, such as air, can pass to cool the brake disc, which is prone to heating.

[0044] In one embodiment, at least one brake disc comprises a plurality of heat dissipating brake fins, preferably said brake fins being located around the periphery of said brake disc and arranged radially.

[0045] As with brake discs, these heat dissipation fins can be part of the same casting, or they can be two or more rigidly attached separate bodies, with the advantage that the fins can be made of a material with better thermal conductivity (e.g., aluminum) to improve temperature distribution.

[0046] In one embodiment, the braking device comprises a bearing, preferably a roller bearing, which can be mounted on the shaft, to support the brake disc or casing, which does not rotate on the shaft, and to transmit the lateral stresses of said component to the shaft.

[0047] In one embodiment, the braking device comprises at least one compression spring disposed between the brake discs and configured to exert a separating pressure between the brake discs, the spring maintaining the brake discs constantly spaced apart by a distance determined by a pusher element of the drive device.

[0048] In one embodiment, the braking device comprises at least one guide element fixed to the first housing and oriented in the axial direction of the shaft, the first brake disc comprises a through hole loosely fitted in said guide element, the second brake disc comprises a through hole fitted in the guide element, in particular the braking device comprises a second Fixed Support When provided with a casing and a second pusher element, this through-hole may also be a loose fit.

[0049] In one embodiment, the brake device includes an elastic damping gasket disposed between each fitting of each guide element and each through-hole of the brake disc, the elastic gasket being the same as that disposed between the sliding connection housing of the lining disc and the transmission guide.

[0050] In one embodiment, the brake device comprises a plurality of guide elements, each consisting of a guide screw inserted into a through hole of the same plurality of through holes of each of the brake discs, the guide screws being configured to guide the displacement of the first brake disc in the axial direction of the shaft, the guide screws preferably being inserted into through holes arranged in the lugs of each brake disc.

[0051] In one embodiment, the brake device includes a plurality of compression springs each concentrically mounted on a respective guide screw, the compression springs being disposed between the first brake disc and the second brake disc, and the compression springs being configured to exert a spacing pressure between the brake discs.

[0052] The guide screw can be threaded into a nut that secures the brake device component, so in some embodiments, the first Fixed Support The distance between the casing and the second brake disc or between the two casings can be limited.

[0053] In one embodiment, the pusher element of the axial drive system comprises a piston configured to generate a pushing load on a lateral surface of the first brake disc, said surface being opposite a surface that generates friction with the first lining; The piston is a first Fixed Support The casing is configured to be accommodated and move longitudinally, i.e., axially, in a pressing direction and a retracting direction opposite to the pressing direction, within the cavity of the casing.

[0054] In one embodiment, the axial drive system of the first pusher element comprises at least one fluid access, such as a liquid or a gas, disposed within the casing; the access is configured to introduce and extract fluid into the cavity of the casing; At least one fluid access configured to introduce and extract fluid to axially move a piston, - the first Fixed Support a high-pressure gasket disposed within the cavity of the casing and configured to exert lateral pressure on a lateral surface of the piston; - an O-ring arranged in the cavity of the casing parallel to the high-pressure gasket to prevent pressure loss; The high-pressure gasket prevents the piston from moving toward the first piston when the axial drive device is deactivated. Fixed Support configured to retract into a cavity in the casing; The high-pressure gasket is configured to deform in lateral contact with the surface of the piston when the piston moves in the pushing direction, to undergo elastic deformation that allows for storage of deformation energy, and to perform retraction displacement when the actuation system is deactivated. In other words, the retraction directly depends on the properties and shape of the high-pressure gasket and its deformation.

[0055] Preferably, the high-pressure gasket is made from ethylene propylene diene rubber or EPDM, which is comprised of an elastomeric thermopolymer with high abrasion and wear resistance.

[0056] Preferably, the high pressure gasket is formed by two concentric gaskets facing each other within the cavity of the casing, each gasket more preferably having a U-shaped cross section.

[0057] Gaskets (high pressure gaskets and O-rings) ensure the tightness of the chamber created between the casing and the piston.

[0058] In this embodiment, the braking device may include a heat insulating element located between the piston and the first brake disc or on the part of the brake disc that is in contact with the piston, so that in the event of an increase in the temperature of the first brake disc, said heat insulating element can insulate the piston in contact with the fluid in the casing chamber, thereby avoiding the possible problem of boiling of said fluid, which can lead to braking failures, known as the "fading effect".

[0059] In one embodiment, the piston comprises a cylindrical ring shape and the compression spring comprises a conical shape, or the piston comprises a conical ring shape and the compression spring comprises a cylindrical shape.

[0060] Two equivalent solutions are estimated to achieve a proper force balance system so that the braking system is at maximum approximation between the friction elements throughout the entire stroke.

[0061] The first solution is a combination of a cylindrical ring-type piston and a conical compression spring. These elements have a constant resistance throughout the entire axial displacement stroke, resulting in a balanced system. The second solution is a combination of a conical piston and several cylindrical springs. These two elements have a resistance that increases linearly along their stroke length, resulting in a balanced system by equalizing the gradient of the resistance forces of each element. Both solutions ensure permanent contact between the pusher element and the first brake disc throughout the entire stroke.

[0062] In one embodiment, the axial drive system comprises an electric motor fixed to the casing and configured to rotate a toothed pinion coupled to a shaft of the motor and arranged on the pusher element; The piston has a ring shape with a thread on its outer cylindrical surface and teeth on its inner cylindrical surface that mesh with the pinion, the casing has an internal thread within the cavity that is threadedly engaged with the thread of the piston, the electric motor is configured to rotate the pinion and transmit the rotation to the piston, and the piston is configured to be screwed into or unscrewed from the casing as it rotates, and moves axially, causing the brake disc to move.

[0063] Depending on the torque applied by the electric motor, the axial force may be higher or lower, resulting in an increased or decreased braking torque.

[0064] In this configuration, the motor is rotated in the opposite direction to the push-in displacement by the amount necessary to leave sufficient clearance between the two brake discs so that the lining on the lining disc does not rub against either of the two brake discs, and the amount of retraction can be precisely adjusted based on the distance traveled by the first pusher element.

[0065] Similarly, this configuration can also incorporate an auxiliary (hand) brake, since by rotating the piston with the desired torque, an axial force can be generated that, thanks to the resistance between the piston threads and the casing cavity, keeps the mechanical load torque constant even without torque from the electric motor.

[0066] In one embodiment dependent from the above embodiment, the braking device comprises: an outer cover rigidly secured to the exterior of the casing and configured to seal the exterior of the casing; an inner cap rigidly fixed to the inside of the casing and configured to seal an inner portion of the piston; - an elastic dust cover to prevent particles from entering the gear system of the piston against the pinion.

[0067] In one embodiment, the axial drive system of the pusher element comprises two electric motors fixed to the casing; the pusher element comprises two pressing members, each connected to a shaft of the electric motor by a threaded attachment, configured to push the brake disc axially in a pushing direction, either directly or via a piston arranged between them; Upon operation of the electric motor, the threaded mounting of the pressure member converts rotation of the motor into axial displacement of the pressure member, causing the pressure member to move in said axial direction.

[0068] As with the embodiment with one motor, in this embodiment with two motors it is possible to adjust the setback to a minimum but sufficient distance so that the lining disc can rotate without residual friction.

[0069] In one embodiment, the brake device comprises a turbofan framework having a hollow cylindrical shape and a plurality of blades separated by cavities, the blades being disposed on lateral surfaces of the turbofan, the turbofan being disposed to concentrically surround the brake disc and the lining disc, connected to a rotating shaft and configured to rotate about itself relative to a first housing, and generating forced ventilation within the brake device.

[0070] This turbofan framework can provide ventilation to cool components that are prone to heat generation due to friction, and can therefore be used effectively in other braking systems that do not necessarily have all of the essential features of the system described above. [Brief explanation of the drawings]

[0071] [Figure 1A] FIG. 1 is a perspective view of a brake disc, which may be the first brake disc or the second brake disc, since both may be the same. [Figure 1B]FIG. 1 is a perspective view of a brake disc having an annular shape, the brake disc having a central disc through-hole including an axial direction, and an outer friction portion having a plurality of radially open internal channels configured to pass fluid inside the brake disc for cooling the brake disc. [Figure 1C] 1B is a perspective view of a brake disc as shown in FIG. 1A, with a plurality of heat-dissipating brake fins arranged radially around the periphery of the brake disc. [Figure 1D] 1C is a perspective view of a brake disc such as the disc shown in FIG. 1B having a plurality of fins such as the disc shown in FIG. 1C. [Figure 2] 1 is a perspective view of a brake disc shown with four linings on either side of a support disc connected to four guide screws, each mounted on a compression spring; FIG. [Figure 3A] FIG. 1 is a perspective view of a brake device with a filtering structure concentrically arranged over a lining disc, and an axial drive system with fluid access within the casing. [Figure 3B] 3B is a perspective view of a brake device with a filtering structure concentrically arranged over the lining disc, viewed from the opposite side to FIG. 3A, in which the axial drive system has fluid access within the casing. [Figure 4] FIG. 3C is an exploded perspective view of the brake device shown in FIGS. 3A-3B, showing the components of the device except for the piston and high-pressure gasket disposed in the cavity of the casing. [Figure 5A] 1 is a perspective view of a brake device including a filtering structure having a cylindrical frame arranged to cover first and second brake discs, and an axial drive system including two electric motors fixed to a first fixed support casing, each connected to a pressing member. [Figure 5B]FIG. 5B is a perspective view of a brake device having a filtering structure with a cylindrical framework arranged to cover the first and second brake discs, viewed from the opposite side to FIG. 5A, in which the axial drive system includes two electric motors fixed to the first fixed support casing, each connected to a pressing member. [Figure 6] FIG. 5C is an exploded perspective view of the braking device shown in FIGS. 5A-5B, showing the components of the device. [Figure 7A] FIG. 1 shows a perspective view of a brake device comprising a filtering structure covering a lining disc and a turbofan having a hollow cylindrical shape and covering the brake disc and the lining disc, and the axial drive system comprises an electric motor fixed to a first fixed support casing. [Figure 7B] 7B shows a perspective view of a brake device including a filtering structure covering the lining disc and a turbofan having a hollow cylindrical shape and covering the brake disc and the lining disc, as seen from the opposite side to FIG. 7A, and the axial drive system includes an electric motor fixed to the first casing. [Figure 8] FIG. 7C is an exploded perspective view of the brake device shown in FIGS. 7A-7B, showing the components of the device, such as the piston and casing, threaded together. [Figure 9] FIG. 1 is an exploded perspective view of the casing with the fluid drive system, showing the access for the fluid as well as the high-pressure gasket surrounding the piston. [Figure 10A] 1 is a schematic diagram showing displacement of a piston within a cavity in a casing by a drive system including access for fluid. FIG. [Figure 10B] 1 is a schematic diagram showing displacement of a piston within a cavity in a casing by a drive system including access for fluid. FIG. [Figure 10C] 1 is a schematic diagram showing displacement of a piston within a cavity in a casing by a drive system including access for fluid. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0072] Text description of the illustration image022.gif. In order to complete the description and to make the characteristics of the invention more readily comprehensible, this specification is accompanied by drawings which form an integral part thereof and which show, by way of example and not by way of limitation, the following:

[0073] The list of reference numbers used in the depicted figures is given below: (1) Guide support (2) Communication guide (3) First Fixed Support casing (4) O-ring (13, 17, 18) First pusher element (5) Lining disc (51) Support disk (52) First lining (53) Second lining (54) Slide connection housing (55) heat dissipation Lining fin (56) Groove-shaped gap (6) First brake disc (61) First brake disc outer friction portion (62) First brake disc inner channel (63) First brake disc braking fin (64) First brake disc through hole (7) Second brake disc (71) Second brake disc outer friction part (72) Second brake disc inner channel (73) Brake fin for second brake disc (74) Second brake disc through hole (8) Elastic damping gasket (9) Filtering Structure (10) Bearings (11) Compression spring (12) Guide element (13) Piston (14) Fluid Access (15) High-pressure gasket (16) Electric motor (17) Pinion (18) Pusher element (19) Turbofan framework (191) Turbofan Blade (20) Bush

[0074] As can be seen in the figures, and in particular in Figures 3, 5 and 7, as well as in the exploded views of Figures 4, 6 and 8, the invention consists in a braking device in which the element that rotates co-rotating with the shaft to be braked (to which it is adapted to be coupled) is a lining disc (5), while the first brake disc (6) and the second brake disc (7) located on either side of the lining disc (5) do not co-rotate with the shaft, as is common in many existing braking devices on the market, but instead have a floating connection to the shaft, allowing for axial displacement thereof.

[0075] 1A-1D show perspective views of different possible embodiments of the first brake disc (6) and the second brake disc (7), all of which depict the brake discs (6, 7) having an annular shape with an outer friction zone or section (61, 71) that can be solid, as shown in FIGS. 1A and 1C, or open and consisting of multiple radially arranged internal channels (62, 72), as shown in FIGS. 1B and 1D. Similarly, FIGS. 1C and 1D show that the brake discs (6, 7) can also include multiple fins, referred to as brake fins (63, 73) because of their placement on the brake discs (6, 7). These fins can be part of the same casting as the rest of the disc, or can be secured by mechanical means such as screws, pins, or welding. The brake discs (6, 7) also have four evenly spaced fixing lugs around their periphery, each with a first brake disc through-hole (64) and a second brake disc through-hole (74), which extend in the axial direction.

[0076] Figure 2 shows the connection between the first brake disc (6) and the lining disc (5). The lining disc (5) is placed between the two brake discs (6, 7) and, like these discs, has a circular through-hole in the center, in which a connectable shaft or bushing (20) can be placed.

[0077] The lining disc (5) shown in Figure 2 has a support disc (51) that forms an outer region, and four first linings (52) and four second linings (53) are evenly arranged on the first and second surfaces of the support disc (51), respectively, and the first four linings (52) are firmly fixed so as to contact the first brake disc (6).

[0078] In the center of the support disc (51), the lining disc (5) has three evenly distributed through-slide connection housings (54), which are configured to be tightly or loosely fitted with the three transmission guides (2) of the guide support (1), respectively, including in the axial direction. To ensure proper fitting and to avoid unwanted vibrations or frequencies in the operation of the brake device, elastic damping gaskets (8) are arranged between each fitting between the slide connection housings (54) and the transmission guides (2). In this way, the rotation of the shaft connected to the guide support (1) is shared by the lining discs (5), but the lining discs (5) can move in the axial direction of the shaft regardless of the shaft's displacement.

[0079] Since the support disc (51) may generate heat due to friction between the linings (52, 53) and the brake discs (6, 7), the lining disc (5) is provided with a plurality of heat-dissipating lining fins (55) arranged on the outer periphery of the central circular through-hole. heat dissipation The lining fins (55) not only dissipate accumulated heat, but also generate a forced flow that can ventilate the entire brake system when the lining disc (5) rotates and is connected to a shaft.

[0080] As can be seen in Figure 2, between each of the first (52) or second (53) linings there is a channel-like gap (56) which can be large or small depending on the size and number of linings included in the disc. The channel gap (56) is specially designed to direct particles generated by wear of the linings (52, 53) due to friction with the brake discs (6, 7) radially outward, and the filtering structure (9) can be positioned concentrically with the lining disc (5) between the first (6) and second (7) brake discs as shown in Figures 4 and 8, or covering both brake discs (6, 7) as shown in Figures 5A and 5B.

[0081] In addition to the above elements, the actuation of the braking device requires a first element that does not move relative to the shaft and can therefore be rigidly connected to the frame. Fixed Support A casing (3) is also required, and this first Fixed Support The casing (3) is disposed next to the first disc (6), on the opposite side to the side where the lining disc (5) is disposed. Fixed Support The casing (3), as well as the brake discs (6, 7), are supported on bearings (10) connectable to the shaft so as to be able to transmit lateral loads. Fixed Support A drive system arranged between the casing (3) and the first brake disc (6) drives the first Fixed Support It comprises a first pusher element (13, 17, 18) axially movable relative to the casing (3).

[0082] The drive system of the device is configured to move the first pusher element (13, 17, 18), which is always in contact with the first brake disc (6), in an axial direction in a direction pushing it towards the first lining (52), so that it moves in said direction and contacts the first lining (52) of the lining disc (5). This pushing force also generates an axial displacement in the lining disc (5), and the lining disc (5), which is connected to the transmission guide (2) in a floating manner, moves in the same direction until the second lining (53) contacts the second brake disc (7), and friction is generated by the clamping of the linings (52, 53) onto the brake discs (6, 7), braking the shaft.

[0083] The brake discs (6, 7) are connected to the shaft and the first brake disc (12) via through holes (64, 74) on the axially arranged guide element (12). Fixed Support It is connected to the casing (3) in a floating manner so as to be movable in the axial direction.

[0084] These guide elements (12) each comprise a guide screw threaded into a nut, which in addition to fixing the axial movement of the brake discs (6, 7) makes it possible to delimit the length of their displacement from the head of the screw to the screwed nut.

[0085] As can be seen in Figures 4 and 8, the joint between each guide element (12) and the through-holes (64, 74) is provided with an elastic damping gasket (8) which facilitates sliding, damps any vibrations that may occur, and prevents thermal expansion from affecting the operation of the device.

[0086] To ensure that the brake discs (6, 7) are sufficiently separated so that they do not come into contact with the linings (52, 53) except when pushed by the first pusher element (13, 17, 18), the braking device comprises a compression spring arranged on the guide element (12), which generates a controlled compressive stress aimed at separating the discs (6, 7) as far as is permitted by the screw, nut and pusher element.

[0087] One of the main novelties of the claimed braking device is that the drive system is configured so that, when it is desired to stop braking, the displacement of the brake discs (6, 7) in the direction opposite to the pushing displacement by the first pusher elements (13, 17, 18) is the minimum necessary and sufficient to allow the lining discs (5) to rotate together with the shaft without leaving any residual friction with the brake discs (6, 7). In this way, the distance that the brake discs (6, 7) must again move towards the brake linings (52, 53) to initiate a new braking operation is minimized. In other words, the braking time, known as the "time to lock" (TTL), is reduced, since the displacement opposite to the pushing displacement consists of the retraction of the first pusher elements (13, 17, 18).

[0088] This configuration allows for short braking times, so that even if the linings (52, 53) are worn, the travel distance of the brake discs (6, 7) is always minimal, since not only the brake discs (6, 7) but also the lining discs (5) are mounted in a floating manner.

[0089] The retraction of the first pusher element (13, 17, 18) generated by the drive system can be according to three embodiments shown in perspective views in FIGS.

[0090] In the embodiment of FIG. 4, as also shown in FIGS. 3A-3B, the first Fixed Support The casing (3) has a cylindrical ring-shaped cavity in which a piston (13) is located. When a fluid, either liquid or gas, is introduced into said cavity, an axial displacement (not visible in Figure 4) of the piston (13) occurs, which causes the first brake disc (6) to move towards the lining disc (5) and creates a first friction. This displacement continues until it moves the lining disc (5) against the second brake disc (7), creating a tight fit between the two linings (52, 53) and the two brake discs (6, 7).

[0091] When you want to stop braking, the fluid is no longer in the first Fixed Support It is not introduced into the cavity of the casing (3), and the high pressure gasket (15) displaces the drawing into the cavity.

[0092] This high pressure gasket (15) is shown in Figure 9 and preferably consists of two gaskets or rubber made of ethylene propylene diene or EPDM with a U-shaped cross section fixed on either side of an internal cavity arranged concentrically with the piston.

[0093] As can be seen in Figures 10A to 10C, when the gasket (15) elastically deforms in the pushing direction during axial displacement, deformation energy is stored, causing the piston (13) to retreat when it no longer exerts a pushing force. In this way, the retreating displacement is always the same and is always the minimum necessary to allow the lining disc (5) to rotate without friction with the brake discs (6, 7), which is particularly suitable for preventing energy from being extracted when braking is not desired. Similarly, wear of the linings (52, 53) prevents the braking time from increasing due to the longer stroke traveled by the pusher.

[0094] In the embodiment shown in Figures 5 to 8, the displacement of the first pusher element (13, 17, 18) in the axial direction is no longer hydraulic or pneumatic, but electrical.

[0095] Thus, in the embodiment shown in FIGS. 5A-5B and 6, the drive system includes a first Fixed Support The brake system comprises two electric motors (16) fixed to the casing (3), each of which is connected by a screw configured to convert rotation into longitudinal displacement to an axially movable pushing member (18) capable of directly pushing the first brake disc (6) or the piston (13) arranged between them.

[0096] In this way, these two electric motors (16) are diametrically opposite each other and cause the first brake disc (6) to move in an aligned manner towards the lining disc (5) in the same way as with a fluid. To perform reversal, it is sufficient for the electric motor (16) to rotate a minimum distance in the direction opposite to the pressing direction in order to create sufficient clearance between the brake discs (6, 7) and the lining disc (5) so that the lining disc (5) can rotate without residual friction.

[0097] In the embodiment shown in Figures 7A-7B and 8, the braking device consists of only one electric motor (16) which overcomes possible misalignment or eccentricity in the axial displacement of the first brake disc (6) with a gear system.

[0098] In this embodiment, a pinion (17) is connected to the shaft of the electric motor (16) and engages with the internal teeth of the piston (13). The piston (13) has a screw thread formed on its outer periphery. Fixed Support It is threadedly engaged with the threads in the internal cavity of the casing 3. In operation of this embodiment, the electric motor 16 rotates the pinion 17, which transfers the rotational motion to the piston 13, which converts the rotation into axial displacement.

[0099] Therefore, the electric motor (16) can move the piston (13) in either axial direction, and can perform a pushing motion that generates braking, or a retracting motion.

[0100] This embodiment also shows a turbofan skeleton (19) connectable to a shaft via a bushing (20), the turbofan skeleton (19) being rotatable about itself, and the turbofan skeleton A plurality of blades (191) arranged on the cylindrical surface of (19) generate a flow on the outside of the brake discs (6, 7) and lining disc (5), thereby utilizing the rotation of the shaft to cool down equipment components that may overheat.

Claims

1. 1. A braking device mountable on a rotating shaft, the braking device comprising: a guide support (1) that can be rigidly mounted on a shaft, and that includes at least one longitudinal transmission guide (2) that is arranged eccentrically with respect to the shaft and that is oriented in the same direction as the axial direction of the shaft when the guide support is assembled on the shaft; a first fixed support casing (3), a first pusher element (13, 17, 18) axially movable relative to the first fixed support casing (3); a support disk (51) connected in a floating manner to at least one transmission guide (2) of the guide support (1); a first lining (52) fixed to a first surface of the support disc (51); and A second lining (53) fixed to the second surface of the support disc (51). a lining disc (5) provided with a first brake disc (6) axially movable relative to the first fixed support casing (3); - a second brake disc (7), Equipped with A lining disc (5) is arranged between the first brake disc (6) and the second brake disc (7), The guide support (1) is configured to transmit the rotation of the shaft to the lining disc (5), and the lining disc (5) is configured to rotate together with the shaft; the first pusher element (13, 17, 18) and the first brake disc (6) are connected to form an axial displacement unit; the first fixed support casing (3) comprises a drive system configured, when activated, to move the first pusher element (13, 17, 18) axially towards the lining disc (5) and to push the first brake disc (6) towards the first lining (52) of the lining disc (5); the first brake disc (6) is configured to exert a pressing force on the first lining (52) in an axial direction when pushed by the first pusher element (13, 17, 18), generating friction and moving the lining disc (5) towards the second brake disc (7); the drive system is configured, when not in operation, to retract the first pusher element (13, 17, 18) in the axial direction and move it in a direction opposite to the direction in which it pushes the first brake disc (6); the first brake disc (6) is configured to move axially in a direction opposite to a direction in which the first pusher element (13, 17, 18) pushes the lining disc (5) as the first pusher element (13, 17, 18) retreats; A brake device, wherein the floating connection of the lining disc (5) on the transmission guide (2) is configured to separate the lining disc (5) from the two brake discs (6, 7) when the first brake disc (6) moves in the opposite direction as the lining disc (5) rotates.

2. a second fixed support casing arranged at the opposite end of the first fixed support casing (3); a second pusher element axially movable relative to the second casing; Equipped with The second pusher element and the second brake disc (7) are fixed to form an axial displacement unit; the second casing comprises a drive system configured, when actuated, to move the second pusher element axially towards the lining disc (5) and to push the second brake disc (7) towards the second lining (53) of the lining disc (5); the second brake disc (7) is configured to exert a pressing force on the second lining (53) in an axial direction when pushed by the second pusher element, causing the lining disc (53) to move towards the second brake disc (7); the drive system of the second casing is configured, when not in operation, to retract the second pusher element and move it in a direction opposite to the direction in which it pushes the second brake disc (7); the second brake disc (7) is configured to move axially in a direction opposite to the direction of pushing the lining disc (5) with the retraction of the second pusher element in the opposite direction; 2. The braking device according to claim 1, wherein the floating connection of the lining disc (5) on the transmission guide (2) is configured to separate the lining disc (5) from the two brake discs (6, 7) without generating residual friction when the first and second pusher elements (13, 17, 18) are retracted together with the rotation of the lining disc (5) on the shaft.

3. The support disc (51) of the lining disc (5) is - the peripheral area of ​​the first and second faces of the support disc (51) on which the linings (52, 53) are fixed; - at least one through-slide connection housing (54) including the axial direction; comprising; 2. The brake device according to claim 1, wherein the sliding connection housing (54) is coupled to the at least one longitudinal transmission guide (2) in a loosely mounted manner.

4. 4. A braking device according to claim 3, comprising an elastic damping gasket (8) arranged between each mating connection of each transmission guide (2) and the sliding connection housing (54) of the lining disc (5).

5. The lining disc (5) has a plurality of heat-dissipating lining fins (55) arranged on the outer periphery of the central through-hole of the support disc (51), A plurality of heat dissipating lining fins (55) are rigidly attached to the support disc (51) by rigid connecting means; or 2. The brake device according to claim 1, wherein the plurality of heat-dissipating lining fins (55) and the support disc (51) comprise a single case.

6. 2. A brake device according to claim 1, wherein the lining disc (5) comprises a plurality of first linings (52) and second linings (53) fixed to outer regions of the first and second surfaces of the support disc (51), respectively, the linings being separated by groove-like gaps (56) in the radial direction, and the linings (52, 53) having a blade shape.

7. 2. A braking device according to claim 1, comprising a particle filtering structure (9) arranged concentrically around the lining disc (5) and adapted to retain particles detached from the lining (52, 53).

8. 8. A braking device according to claim 7, wherein the filtering structure (9) is a cylindrical frame arranged to cover the first and second brake discs (6, 7).

9. 2. A braking device according to claim 1, wherein at least one brake disc (6, 7) has an annular shape with a central disc through-hole concentric with the shaft and with a hard outer friction portion (61, 71) against the lining (52, 53).

10. 2. A braking device according to claim 1, wherein at least one brake disc (6, 7) has an annular shape with a central disc through-hole concentric with the shaft, in the axial direction, and with an outer friction portion (61, 71) against the lining (52, 53), and with at least one internal channel (62, 72) configured for the passage of a fluid.

11. 2. The braking device according to claim 1, wherein at least one brake disc (6, 7) is provided with a plurality of heat-dissipating brake fins (63, 73), the brake fins (63, 73) being located on the outer periphery of the brake disc (6, 7) and arranged radially.

12. 2. A braking device according to claim 1, comprising a bearing (10) mountable on a shaft.

13. 2. A braking device according to claim 1, comprising at least one compression spring (11) arranged between the brake discs (6, 7) and adapted to exert a separating pressure between the brake discs (6, 7).

14. 2. A braking device according to claim 1, comprising at least one guide element (12) fixed to the first fixed support casing (3) and oriented in the axial direction of the shaft, the first brake disc (6) comprising a first disc through-hole (64) loosely fitted in the guide element (12), and the second brake disc (7) comprising a second disc through-hole (74) fitted in the guide element.

15. 15. A braking device according to claim 14, comprising a resilient damping gasket (8) arranged between each guide element (12) and each brake disc through-hole (64, 74).

16. 15. A brake device according to claim 14, comprising a plurality of guide elements (12), each of which has a guide screw inserted into the same plurality of brake disc through-holes (64, 74) of each brake disc (6, 7), the guide screws being configured to guide the displacement of the first brake disc (6) in the axial direction of the shaft, and fixed to a first fixed support casing (3) of the brake device.

17. 17. A braking device according to claim 16, comprising a plurality of compression springs (11) each concentrically mounted on a respective guide screw, the compression springs (11) being arranged between the first brake disc (6) and the second brake disc (7), the compression springs (11) being configured to exert a separating pressure between the brake discs (6, 7).

18. A pusher element (13, 17, 18) of the drive system comprises a piston (13) configured to generate a pressing load on a lateral surface of the first brake disc (6), 2. The brake device according to claim 1, wherein the piston (13) is accommodated in a cavity of the first fixed support casing (3) and is configured to move longitudinally in one pushing direction and a retracting direction opposite to the pushing direction.

19. A drive system comprising: at least one fluid access (14) arranged in the first fixed support casing (3), configured to introduce and extract fluid into the cavity of the first fixed support casing (3), the introduction and extraction of fluid being configured to move the piston (13) axially in a push direction and a return direction, respectively; a high-pressure gasket (15) arranged in a cavity of the first fixed support casing (3) and configured to exert a lateral pressure on the lateral surfaces of the piston (13); Equipped with 19. The braking device according to claim 18, wherein the high-pressure gasket (15) is configured to retract the piston (13) into the cavity of the first fixed support casing (3) when the drive system is in an inoperative state.

20. 14. A braking device according to claims 18 and 13, wherein the piston (13) has a cylindrical ring shape and the compression spring (11) has a conical shape, or the piston (13) has a conical ring shape and the compression spring (11) has a cylindrical shape.

21. The drive system comprises an electric motor (16) fixed to the first fixed support casing (3), the electric motor (16) being configured to rotate a toothed pinion (17) connected to a shaft of the motor (16); The piston (13) has a ring shape with a thread on its outer cylindrical surface and a tooth profile on its inner cylindrical surface that meshes with the pinion (17); 19. A braking device according to claim 18, wherein the first fixed support casing (3) has an internal thread within the cavity that screws into the thread of the piston, and the electric motor (16) is configured to rotate the pinion (17) and transmit the rotation to the piston (13), which, upon rotation, screws into or unscrews from the first fixed support casing (3) and moves axially to move the brake discs (6, 7).

22. The drive system comprises two electric motors (16) fixed to a first fixed support casing (3), the pusher elements (13, 17, 18) comprise two pressing members (18), each of which is connected to a shaft of the electric motor (16) by a threaded attachment, the pressing members (18) being configured to press the brake discs (6, 7) in an axial direction; 2. The brake device of claim 1, wherein, upon actuation of the electric motor, the threaded attachment of the pressing member converts rotation of the motor into axial displacement of the pressing member, causing the pressing member to move axially.

23. 2. The brake device according to claim 1, comprising: a turbofan framework (19) having a hollow cylindrical shape; and a plurality of turbofan blades (191) separated by cavities, the turbofan blades (191) being arranged on side surfaces of the turbofan framework (19), the turbofan framework (19) being arranged concentrically to surround the brake discs (6, 7) and the lining discs (5), the turbofan framework (19) being connected to a rotating shaft, and configured to rotate relative to the first fixed support casing (3), and generating forced ventilation within the brake device.

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