Combined type pressing disc assembly and design method

Abstract

The invention discloses a combined type pressing disc assembly and a design method, and belongs to the field of aviation airplane wheel brake devices. The combined type pressing disc assembly comprises a pressing disc, a plurality of installation groove holes are evenly distributed in the same circumference, concentric with the axis of the pressing disc, of the pressing disc, a pressure bearing cup is installed in each installation groove hole in an embedded mode, and the pressure bearing cups are used for bearing thrust of the hydraulic actuator cylinder and transmitting the thrust to the pressing disc. The positions of the multiple installation groove holes coaxially correspond to the multiple hydraulic actuating cylinders, one side face of the pressure-bearing cup faces the hydraulic actuating cylinders, the other side of the pressure-bearing cup makes contact with the step faces in the installation groove holes, and the diameter of the pressure-bearing cup is larger than that of the hydraulic actuating cylinders. The pressing disc mechanism is improved, the pressure-bearing cup is installed on the pressing disc, the pressure-bearing cup is connected with the thrust applied to the pressing disc by the hydraulic actuator cylinder, the hydraulic actuator cylinder is prevented from making direct contact with the pressing disc, and the problem that an existing pressing disc deforms due to compression is solved.

Description

Technical Field

[0001] The present invention relates to the field of aircraft wheel brake devices, and particularly to a composite pressing disc assembly and a design method thereof. Background Art

[0002] Aircraft wheel brakes are used to generate braking torque when the aircraft lands, so as to brake, decelerate or stop the aircraft. Aircraft wheel brakes mainly include components such as hydraulic actuating cylinders, heat reservoirs, and housings. When the aircraft lands and brakes, the hydraulic actuating cylinder extends to press the heat reservoir assembly, and the heat reservoir assembly generates braking torque by friction. The heat reservoir assembly is mainly composed of a moving disc, a static disc, a pressure-bearing disc, and a pressing disc assembly, and generally uses carbon fiber composite materials. Among them, the pressing disc is in direct contact with the hydraulic actuating cylinder, bears the axial hydraulic thrust, and transmits the thrust to other brake discs. Under the action of the thrust, the static disc and the moving disc rub against each other to generate braking torque.

[0003] Hydraulic actuating cylinders generally use aluminum alloy or steel materials, while the stiffness and hardness of the pressing disc made of carbon fiber composite materials are lower than those of the hydraulic actuating cylinder. In addition, due to the limited diameter of the hydraulic actuating cylinder, the thrust of the hydraulic actuating cylinder can only act on a part of the pressing disc, causing local concentrated loading. Therefore, during long-term use of the pressing disc, the contact part with the hydraulic actuating cylinder will deform, and then the edge of the pressing disc will warp. The deformation of the pressing disc will cause the following problems: 1. It causes uneven contact between the pressing disc and other brake discs, resulting in uneven transmission of thrust, and further causing abnormal braking torque generated by the aircraft wheel brake. 2. When the thrust of the hydraulic actuating cylinder acts on the deformed pressing disc, the supporting force of the pressing disc is skewed from the thrust of the hydraulic actuating cylinder, and the hydraulic actuating cylinder cannot work in alignment, easily damaging the sealing ring of the hydraulic actuating cylinder and the working surface of the hydraulic actuating cylinder, and may cause the hydraulic actuating cylinder to leak oil. 3. Since the pressing disc is made of fiber braiding and carburizing, after the pressing disc is deformed, the internal fibers of the pressing disc are deformed and broken, which will also reduce the structural strength of the pressing disc.

[0004] Therefore, it is necessary to provide a pressing disc that can effectively prevent deformation to solve the above problems. Summary of the Invention

[0005] Technical Problems to be Solved In order to avoid the deficiencies of the prior art, the present invention provides a composite pressing disc assembly and a design method thereof. By improving the structure of the existing pressing disc, a pressure-bearing cup is designed on the pressing disc to transfer the thrust applied by the hydraulic actuating cylinder to the pressing disc, avoiding direct contact between the hydraulic actuating cylinder and the pressing disc, so as to solve the problem of deformation of the existing pressing disc under pressure.

[0006] The technical solution of the present invention is as follows: A composite pressing disc assembly, comprising: a pressing disc, on which a plurality of mounting slot holes are evenly distributed on the same circumference concentric with its axis; further comprising: a pressure-bearing cup, which is embedded and installed in the mounting slot holes of the pressing disc, and is used to receive the thrust of the hydraulic actuator and transmit the thrust to the pressing disc; Wherein, the positions of the plurality of mounting slot holes correspond coaxially to the plurality of hydraulic actuators. One side of the pressure-bearing cup faces the hydraulic actuator, and the other side contacts the inner step surface of the mounting slot hole. The diameter of the pressure-bearing cup is larger than the diameter of the hydraulic actuator.

[0007] A further technical solution of the present invention is: The mounting slot hole is a stepped through hole, which sequentially includes a large-diameter section, a small-diameter section, and a medium-diameter section. The pressure-bearing cup is installed in the large-diameter section. The axial depth of the large-diameter section is the same as the thickness of the pressure-bearing cup, and the inner step surface of the large-diameter section contacts the inner end surface of the pressure-bearing cup; the small-diameter section and the medium-diameter section are used to pass through the fasteners connecting the pressure-bearing cup and the pressing disc.

[0008] A further technical solution of the present invention is: A ring-shaped step groove is provided at one end of the outer diameter wall surface of the pressure-bearing cup facing the pressing disc. A matching one is provided in the large-diameter section. The outer diameter of the ring-shaped step groove of the pressure-bearing cup is in interference fit with the inner diameter of the ring-shaped inner boss of the large-diameter section.

[0009] A further technical solution of the present invention is: The fastener includes a rivet. A through rivet hole is provided axially at the center position of the pressure-bearing cup for riveting and fixing with the pressing disc through the rivet; the rivet hole is a stepped hole, and the inner step surface is used to contact the rivet head for axial limit.

[0010] A further technical solution of the present invention is: The fastener further includes a spacer ring. The rivet sequentially passes through the rivet hole of the pressure-bearing cup, the small-diameter section of the mounting slot hole, and the spacer ring located in the medium-diameter section to rivet and fix the pressure-bearing cup and the pressing disc.

[0011] A further technical solution of the present invention is: The composite pressing disc assembly further includes an indicating rod, which is installed on the pressing disc through an indicating rod seat and is used to indicate the wear condition of the heat reservoir assembly.

[0012] A design method for a composite pressing disc assembly, comprising: Design of the pressure-bearing cup: Calculate the thrust of the hydraulic actuator borne by a single pressure-bearing cup according to the brake pressure and the piston rod diameter of the hydraulic actuator; based on the contact stress between the pressure-bearing cup and the pressing disc contact surface under the action of the thrust being less than or equal to the allowable compressive stress of the pressing disc material, and combined with the rivet hole diameter of the pressure-bearing cup, determine the diameter of the pressure-bearing cup; based on the bending stress borne by the pressure-bearing cup under the action of the thrust being less than or equal to the allowable bending stress of the material, determine the diameter and thickness of the annular stepped groove, and select the distance from the inner stepped surface of the annular stepped groove to the other end surface of the pressure-bearing cup to calculate the thickness of the pressure-bearing cup. Design of the installation slot hole of the pressing disc: Determine the installation slot hole size according to the design data of the pressure-bearing cup. And rivet design: Calculate the rivet length according to the axial thickness at the internal step of the rivet hole of the pressure-bearing cup, the axial thickness of the small-diameter section of the pressing disc, the axial effective thickness of the inner hole of the spacer ring, the rivet diameter, and the empirical coefficient. Complete the design of the composite pressing disc assembly based on the determined diameter and thickness of the pressure-bearing cup, the diameter and thickness of the annular stepped groove, the installation slot hole size of the pressing disc, and the rivet length.

[0013] A further technical solution of the present invention is: Determine the rivet hole diameter of the pressure-bearing cup according to the rivet diameter, wherein the rivet diameter is selected according to the connection strength requirement.

[0014] A further technical solution of the present invention is: When the contact stress between the pressure-bearing cup and the pressing disc contact surface does not meet the use requirements, increase the diameter of the pressure-bearing cup and recalculate until a pressure-bearing cup diameter that meets the requirements is obtained, and ensure that the contact stress is less than or equal to the allowable compressive stress of the pressing disc material during the calculation.

[0015] A further technical solution of the present invention is: When the bending stress borne by the pressure-bearing cup does not meet the use requirements, increase the diameter and thickness of the annular stepped groove of the pressure-bearing cup and recalculate until a diameter and thickness of the annular stepped groove that meet the requirements are obtained, and ensure that the bending stress borne by the pressure-bearing cup is less than or equal to the allowable bending stress of the material during the calculation.

[0016] The beneficial effects of the present invention are as follows: A composite pressing disc assembly and its design method according to the present invention improve the existing pressing disc structure. Corresponding mounting slots are designed on the pressing disc at the positions of the thrust of each hydraulic actuator piston rod. A steel pressure-bearing disc is installed in each mounting slot, and the pressure-bearing disc is riveted and fixed to the pressing disc. The thrust from the hydraulic actuator is transferred to the pressing disc through the pressure-bearing disc. At the same time, the contact area between the pressure-bearing cup and the pressing disc is larger than the contact area between the piston rod in the hydraulic actuator and the pressing disc in the original structure, so that the thrust transmitted by the hydraulic actuator is evenly distributed on the pressing disc, avoiding local pressure on a small area of the pressing disc. Through the thrust transfer of the pressure-bearing cup, the present invention avoids the deformation of the pressing disc, makes the force on the pressing disc uniform, and further makes the thrust of the pressing disc on other brake discs uniform, ensuring the braking performance. Since the deformation of the pressing disc is avoided, the hydraulic actuator also always maintains centering operation, thus avoiding damage and oil leakage of the hydraulic actuator. At the same time, avoiding the deformation of the pressing disc also improves the service life of the pressing disc.

[0017] In the present invention, the pressure-bearing cup is made of steel material, and its thermal conductivity is lower than that of the carbon fiber composite material of the pressing disc. While bearing pressure, the pressure-bearing cup can also block the heat transfer from the pressing disc to the hydraulic actuator, reducing the temperature of the hydraulic actuator and improving the reliability of the hydraulic actuator.

[0018] The present invention is provided with an installation embedded groove on the pressure-bearing cup, that is, a ring-shaped step groove is provided on the outer diameter of the side of the pressure-bearing cup facing the pressing disc. The outer diameter of the ring-shaped step groove is in interference fit with the inner diameter of the ring-shaped inner convex platform provided on the large diameter section of the pressing disc, which can avoid the shear of the rivet under landing conditions, improve the connection reliability between the pressure-bearing cup and the pressing disc, and the installation embedded groove can increase the compression stability and also play an installation guiding role, facilitating the installation of the pressure-bearing cup.

[0019] The pressing disc assembly of the present invention has a wear indicator rod, which can identify the remaining life of the heat reservoir assembly during use. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0021] Figure 1 It is an axonometric schematic diagram of a composite pressing disc assembly according to the present invention; Figure 2 It is a structural schematic diagram of a composite pressing disc assembly according to the present invention; Figure 3 For Figure 2 The enlarged view at A in Figure 4 Is the axonometric view of the pressing disc in the present invention; Figure 5 Is the structural view of the pressing disc in the present invention; Figure 6 Is the axonometric view of the pressure-bearing cup in the present invention; Figure 7 Is the structural view of the pressure-bearing cup in the present invention Figure 8 Is the axonometric structural view of the rivet in the present invention; Figure 9 Is the cross-sectional view of the rivet in the present invention; Figure 10 Is the partial view of the riveting part of the rivet in the present invention; Figure 11 Is the usage view of the composite pressing disc assembly of the present invention, where (a) shows the state when the hydraulic actuator is not in contact with the pressure-bearing cup, and (b) shows the state when the hydraulic actuator is in contact with the pressure-bearing cup.

[0022] In the figure: 1. Pressing disc, 11. Mounting slot holes, 111. Large diameter section, 112. Small diameter section, 113. Middle diameter section, 114. Ring-shaped inner convex platform, 12. Index rod mounting hole, 2. Pressure-bearing cup, 21. Ring-shaped step groove, 22. Rivet hole, 3. Rivet, 4. Gasket ring, 5. Index rod, 6. Hydraulic actuator. Specific embodiments

[0023] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0024] An embodiment of a composite pressing disc assembly of the present invention is as Figures 1 - 3 shown. The composite pressing disc assembly includes a pressing disc 1, five pressure-bearing cups 2 mounted on the pressing disc 1, five rivets 3 for connecting the pressure-bearing cups 2 and the pressing disc 1, and five gasket rings 4, and further includes an index rod 5 mounted on the pressing disc 1 through an index rod mounting seat.

[0025] Specifically, as Figure 4As shown, this embodiment is designed and improved on the basis of the existing pressing disc. The function of the pressing disc 1 is to absorb the heat during the braking process of the aircraft wheel and bear the hydraulic thrust transmitted by the hydraulic actuator during braking. It has a ring structure and is made of carbon fiber composite material. Concave key grooves for fixing in cooperation with the aircraft wheel brake are evenly distributed on its inner circle. In this embodiment, 5 mounting holes 11 are evenly distributed on the same circumference concentric with the axis of the pressing disc 1 for mounting the pressure bearing cup 2. The positions of the 5 mounting holes 11 are coaxial and correspond one by one to the 5 hydraulic actuators 6 of the hydraulic system.

[0026] As Figure 3 , Figure 5 shown, the mounting hole 11 is a stepped through hole. From the side facing the hydraulic actuator 6 to the side facing the brake disc, the mounting hole 11 successively includes a large-diameter section 111, a small-diameter section 112, and a medium-diameter section 113. The pressure bearing cup 2 is embedded and installed in the large-diameter section 111. The axial depth of the large-diameter section 111 is the same as the thickness of the pressure bearing cup 2. The stepped surface formed between the large-diameter section 111 and the small-diameter section contacts the inner end surface of the pressure bearing cup 2. The outer side of the pressure bearing cup 2 faces the hydraulic actuator 6. The pressure bearing cup 2 is used to receive the thrust of the hydraulic actuator 6 and transmit the thrust to the pressing disc 1.

[0027] Refer to Figure 3 , Figure 6 and Figure 7 , the main body of the pressure bearing cup 2 is a ring-shaped sheet structure and is made of steel or titanium alloy. Its outer diameter is larger than the diameter of the hydraulic actuator 6. A rivet hole 22 penetrating the pressure bearing cup 2 is provided at the central axis position of the pressure bearing cup 2 for riveting and fixing with the pressing disc 1 through the rivet 3. The rivet hole 22 is a stepped hole, and the internal stepped surface is used to contact the rivet head for axial limit. A ring-shaped stepped groove 21 is provided at one end of the outer diameter wall of the pressure bearing cup 2 close to the pressing disc 1. A ring-shaped inner protrusion 114 matching the ring-shaped stepped groove 21 is provided in the large-diameter section 111. The outer diameter of the ring-shaped stepped groove 21 and the inner diameter of the ring-shaped inner protrusion 114 of the large-diameter section 111 are in interference fit. This interference fit design can effectively avoid the shear of the rivet under the landing condition. At the same time, the cooperation between the inner ring-shaped protrusion 114 of the large-diameter section 111 and the outer ring-shaped stepped groove 21 of the pressure bearing cup 2 forms an installation embedded groove, which improves the connection reliability between the pressure bearing cup 2 and the pressing disc 1, increases the compression stability, and can also play an installation guiding role.

[0028] Refer to Figure 3 , Figures 8 - 10, the pressure-bearing cup 2 and the pressing disc 1 are riveted and fixed by the rivet 3. The rivet 3 is a hollow rivet, and the riveting is achieved by cooperating with the spacer ring 4. The pressure-bearing cup 2 is embedded in the large-diameter section 111 of the mounting slot hole 11. The rivet 3 passes through the rivet hole 22 of the pressure-bearing cup 2, the small-diameter section 112 of the mounting slot hole 11 of the pressing disc 1, and the central through-hole of the spacer ring 4 located in the middle-diameter section 113 in sequence from the outside of the pressure-bearing cup 2. The tail end of the rivet 3 is expanded to make it fit with the tapered hole surface of the central through-hole of the spacer ring 4, realizing the riveting and fixing of the pressure-bearing cup 2 and the pressing disc 1. The spacer ring 4 is of a circular ring structure, and its central through-hole includes a straight hole section and a trumpet-shaped tapered hole section. The straight hole section is close to the rivet head end of the rivet 3, and the trumpet-shaped tapered hole end is close to the tail end of the rivet 3. The tapered surface of the tapered hole section is for the expansion and positioning of the tail end of the rivet.

[0029] Refer to Figure 1 , Figure 2 , the composite pressing disc assembly further includes an indicating rod 5. The indicating rod 5 is vertically installed in the indicating rod mounting hole 12 of the pressing disc 1 through the indicating rod seat. The indicating rod 5 is installed on the same side as the pressure-bearing cup 2. The indicating rod 5 is used to indicate the wear condition of the heat reservoir assembly. As the heat reservoir assembly wears, the indicating rod 5 moves axially towards the brake disc assembly along with the pressing disc 1, and the movement amount of the indicating rod 5 is used to indicate the wear condition of the heat reservoir assembly.

[0030] During operation, as Figure 1 , Figure 11 shown, the hydraulic system of the brake system simultaneously drives 5 hydraulic actuators 6 towards the pressing disc 1. Since a pressure-bearing disc 2 is installed on the pressing disc 1 at the force application end facing the hydraulic actuator 6, the thrust from the hydraulic actuator 6 is transferred through the pressure-bearing disc 2 and transmitted to the pressing disc 1, increasing the contact area between the hydraulic actuator 6 and the pressing disc 1, avoiding the direct contact between the hydraulic actuator 6 and the pressing disc 1, and preventing the pressing disc 1 from being extruded and deformed.

[0031] In this embodiment, a design method for the above composite pressing disc assembly is also provided. The method includes: Design of the pressure-bearing cup: Since the pressure-bearing cup not only bears the axial thrust, and under the axial thrust, it is required that the pressing disc connected to the pressure-bearing cup is not crushed, and the edge of the pressure-bearing cup cannot be damaged due to bending, it is necessary to calculate the stress of the pressure-bearing cup and determine the size of the pressure-bearing cup through the stress requirements.

[0032] Specifically, according to the brake pressure and the piston rod diameter of the hydraulic actuator, calculate the thrust of the hydraulic actuator borne by a single pressure-bearing cup; based on the contact stress between the pressure-bearing cup and the pressing disc under the action of the thrust being less than or equal to the allowable compressive stress of the pressing disc material, and combined with the rivet hole diameter of the pressure-bearing cup, determine the diameter of the pressure-bearing cup; based on the bending stress borne by the pressure-bearing cup under the action of the thrust being less than or equal to the allowable bending stress of the material, determine the diameter and thickness of the annular stepped groove, and select the distance from the inner stepped surface of the annular stepped groove to the other end surface of the pressure-bearing cup to calculate the thickness of the pressure-bearing cup.

[0033] Exemplarily, in a specific embodiment, it is calculated by the following method: Calculate the thrust of the hydraulic actuator borne by a single pressure-bearing cup : (1) In the formula, d is the piston rod diameter of the hydraulic actuator; P is the brake pressure; Calculate the diameter of the pressure-bearing cup: Based on the contact stress between the pressure-bearing cup and the pressing disc under the action of the thrust should be less than the allowable compressive stress of the pressing disc material for calculation, (2) In the formula, as Figure 7 shown, D is the diameter of the pressure-bearing cup, is the rivet hole diameter of the pressure-bearing cup, take the rivet diameter d1 + 0.2mm, and the rivet diameter d1 is selected according to the design manual; The diameter D of the pressure-bearing cup is first designed with an initial value according to the structural requirements, and then calculated according to formula (2) , when the contact stress between the pressure-bearing cup and the pressing disc does not meet the usage requirements, increase the diameter D of the pressure-bearing cup and recalculate until the required diameter D of the pressure-bearing cup is obtained. During the calculation, ensure that ≤ .

[0034] Calculate the thickness of the pressure-bearing cup: Based on the bending stress borne by the pressure-bearing cup under the action of the thrust should be less than or equal to the allowable bending stress of the material for calculation, (3) In the formula, as Figure 7 shown, is the diameter of the annular stepped groove of the pressure-bearing cup, is the thickness of the annular stepped groove of the pressure-bearing cup.

[0035] The thickness of the pressure-bearing cup is first designed with an initial value according to the structural requirements, and then calculated according to Equation (3). When the pressure-bearing cup bears bending stress and does not meet the usage requirements, the diameter D1 of the annular stepped groove of the pressure-bearing cup and the thickness of the annular stepped groove are increased and recalculated until the required D1 and are obtained. During the recalculation, it is necessary to ensure that ≤ .

[0036] Select with a thickness generally ranging from 2 to 5 mm. is the distance from the inner stepped surface of the annular stepped groove to the outer end face of the pressure-bearing cup. The thickness of the pressure-bearing cup = + . Thus, the thickness of the pressure-bearing cup can be calculated through the values of and .

[0037] Design of the mounting slot holes of the pressing disc: Based on the design data of the pressure-bearing cup, determine the dimensions of the mounting slot holes. The outer diameter of the large-diameter section of the mounting slot hole matches the outer diameter of the pressure-bearing cup, and the dimensions of the annular inner boss of the large-diameter section are designed according to the dimensions of the annular stepped groove of the pressure-bearing cup; the diameter of the small-diameter section of the hole is the same as the diameter of the rivet hole of the pressure-bearing cup; the diameter of the middle-diameter section of the hole only needs to meet the installation of the spacer ring.

[0038] And the rivet design: Calculate the rivet length according to the axial thickness at the internal step of the rivet hole of the pressure-bearing cup, the axial thickness of the small-diameter section of the pressing disc, the axial effective thickness of the inner hole of the spacer ring, the rivet diameter, and the empirical coefficient.

[0039] The rivet length is calculated by the formula: (4) In the formula, as Figure 10 shown, is the axial thickness at the internal step of the rivet hole of the pressure-bearing cup (i.e., at the position with a diameter of ); is the axial thickness of the small-diameter section of the pressing disc; is the axial effective thickness of the inner hole of the spacer ring, that is, the axial thickness of the straight-hole section of the inner hole of the spacer ring; is the rivet diameter, is the empirical coefficient, with a value ranging from 1.3 to 1.5.

[0040] Based on the determined diameter and thickness of the pressure-bearing cup, the diameter and thickness of the annular stepped groove, the dimensions of the mounting slot holes of the pressing disc, and the rivet length, the design of the composite pressing disc assembly is completed.

[0041] Specific application example: The pressing disc 1 is machined from carbon fiber composite material, with an inner diameter of 194 mm, an outer diameter of 355 mm, and a thickness of 20 mm. Five mounting slots 11 for the pressure-bearing cups 2 with a depth of 3 mm are evenly distributed on it.

[0042] The pressure-bearing cup 2 is machined from TC11 material, with an outer diameter of 40 mm and a thickness of 3 mm. The rivet holes 22 are stepped rivet holes with diameters of 8 mm and 3.5 mm. The 8-mm diameter hole accommodates the rivet head, and the 3.5-mm diameter hole passes through the shank of the rivet.

[0043] The rivet 3 is machined from TC4 material, with a head diameter of 7 mm and a shank diameter of 3 mm. An axial blind hole with a diameter of 2 mm and a depth of 5 mm is provided at the tail end of the shank of the rivet 3 for riveting the pressure-bearing cup 2.

[0044] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A composite compression plate assembly, comprising a compression plate, characterized in that: The clamping plate has a plurality of mounting slots uniformly distributed on the same circumference concentric with its axis; it also includes a pressure cup, which is embedded in the mounting slot of the clamping plate and used to receive the thrust of the hydraulic actuator and transmit the thrust to the clamping plate; Among them, the positions of multiple installation slots correspond coaxially to multiple hydraulic actuators, one side of the pressure cup faces the hydraulic actuator, and the other side contacts the step surface in the installation slot, and the diameter of the pressure cup is larger than the diameter of the hydraulic actuator.

2. A composite pressure plate assembly according to claim 1, characterized in that: The mounting slot is a stepped through hole, which includes a large diameter section, a small diameter section and a middle diameter section in sequence. The pressure cup is installed on the large diameter section, the axial depth of the large diameter section is the same as the thickness of the pressure cup, and the internal step surface of the large diameter section is in contact with the inner end surface of the pressure cup; the small diameter section and the middle diameter section are used to pass through the fasteners connecting the pressure cup and the pressure plate.

3. A composite pressure plate assembly according to claim 2, characterized in that: An annular step groove is provided on one end of the outer diameter wall of the pressure cup facing the clamping plate, and an annular inner boss matching the annular step groove is provided in the large diameter section. The outer diameter of the annular step groove is interference fit with the inner diameter of the annular inner boss of the large diameter section.

4. A composite pressure plate assembly according to claim 3, characterized in that: The fastener comprises a rivet, and a through rivet hole is axially provided at the center of the pressure cup for riveting and fixing with the clamping plate through the rivet; the rivet hole is a stepped hole, and the inner step surface is used for contacting with the rivet head for axial limitation.

5. A composite pressure plate assembly according to claim 4, characterized in that: The fastener also includes a gasket, and the rivet passes through the rivet hole of the pressure cup, the small diameter section of the installation slot hole and the gasket located at the middle diameter section in sequence to rivet and fix the pressure cup and the clamping plate.

6. The composite pressure plate assembly according to claim 1, characterized in that: The composite compression plate assembly also includes an indicator rod, which is installed on the compression plate through an indicator rod seat and is used to indicate the wear condition of the heat storage assembly.

7. A method for designing the composite pressure plate assembly according to claim 5, comprising: Pressure cup design: According to the brake pressure and the piston rod diameter of the hydraulic actuator, calculate the thrust of the hydraulic actuator borne by a single pressure cup; based on the contact stress between the contact surface of the pressure cup and the pressure plate should be less than or equal to the allowable compressive stress of the pressure plate material under the thrust, and combined with the rivet hole diameter of the pressure cup, determine the diameter of the pressure cup; based on the bending stress borne by the pressure cup should be less than or equal to the allowable bending stress of the material under the thrust, determine the diameter and thickness of the annular step groove, and select the distance from the inner step surface of the annular step groove to the other end surface of the pressure cup to calculate the thickness of the pressure cup; Design of mounting slots of the compression plate: Determine the size of the mounting slots according to the design data of the pressure cup; And rivet design: calculate the rivet length according to the axial thickness of the inner step of the rivet hole of the pressure cup, the axial thickness of the small diameter section of the pressure plate, the axial effective thickness of the inner hole of the gasket, the rivet diameter and the empirical coefficient; The design of the composite clamping plate assembly is completed based on the diameter and thickness of the pressure cup, the diameter and thickness of the annular step groove, the installation slot hole size of the clamping plate and the rivet length determined above.

8. The method according to claim 7, characterized in that The diameter of the rivet hole of the pressure cup is determined according to the rivet diameter, wherein the rivet diameter is selected according to the connection strength requirement.

9. The method according to claim 7, characterized in that: When the contact stress between the contact surface of the pressure cup and the pressure plate does not meet the use requirements, increase the diameter of the pressure cup and recalculate until the pressure cup diameter that meets the requirements is obtained. During the calculation, ensure that the contact stress is less than or equal to the allowable compressive stress of the pressure plate material.

10. The method according to claim 7, characterized in that When the bending stress borne by the pressure cup does not meet the use requirements, the diameter and thickness of the annular step groove of the pressure cup are increased and recalculated until the diameter and thickness of the annular step groove that meet the requirements are obtained. During the calculation, it is ensured that the bending stress borne by the pressure cup is less than or equal to the allowable bending stress of the material.

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