Adjusting method of disengagement rotating speed, inclined strut clutch, engine and aircraft

Abstract

The invention relates to the field of clutches, and discloses a disengaging rotating speed adjusting method, a diagonal bracing clutch, an engine and an aircraft. The adjusting method comprises the steps of obtaining a target disengagement rotating speed; based on the dynamic balance equation and the target disengaging rotating speed, at least one of the mass of the inclined supporting block, the position of the mass center of the inclined supporting block in the radial direction of the inclined supporting clutch, the shape of the contact face of the inclined supporting block and the outer sleeve, the contact position of the elastic piece and the inclined supporting block, the elastic coefficient of the elastic piece and the mass of the elastic piece is adjusted; wherein the dynamic balance equation is a function relation between the rotating speed of the outer sleeve and the mass of the inclined supporting block, the position of the mass center of the inclined supporting block in the radial direction of the inclined supporting clutch, the shape of the contact face of the inclined supporting block and the outer sleeve, the contact position of the elastic piece and the inclined supporting block, the elastic coefficient of the elastic piece and the mass of the elastic piece when the inclined supporting block is disengaged from the inner sleeve. The adjusting scheme is high in operability, part of parameters of an existing inclined strut clutch can be modified, and the purpose of increasing or reducing the disengaging rotating speed is achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of clutches, and specifically relates to a method for adjusting the disengaging speed, a swashplate clutch, an engine and an aircraft. Background Art

[0002] During the engine starting process, the starting motor needs to transmit power to the engine rotor through a swashplate clutch to drive the engine to reach the ignition speed and achieve self-rotation.

[0003] The swashplate clutch generally includes an inner sleeve, an outer sleeve, swashplate blocks and elastic members. The inner sleeve is connected to the starting motor, and the outer sleeve is connected to the engine rotor. During the engine starting process, the inner sleeve is driven by the starting motor to work, and the inner sleeve drives the outer sleeve to rotate through the swashplate blocks. After the engine rotor reaches a certain speed, the engine ignites and achieves self-rotation. When the speed of the outer sleeve exceeds the speed of the inner sleeve by a preset value, the swashplate blocks are disengaged from the inner sleeve, thereby completing the starting of the engine.

[0004] Having a suitable disengaging speed of the swashplate clutch is the key to ensuring the smooth starting of the engine. The problem to be solved by the present invention is how to adjust the disengaging speed of the swashplate clutch. Summary of the Invention

[0005] In view of this, the present invention provides a method for adjusting the disengaging speed, a swashplate clutch, an engine and an aircraft to solve the problem of how to adjust the disengaging speed of the swashplate clutch.

[0006] In a first aspect, the present invention provides a method for adjusting the disengaging speed, which is applicable to a swashplate clutch. The swashplate clutch includes an inner sleeve, an outer sleeve, swashplate blocks and elastic members. The method includes:

[0007] Obtaining a target disengaging speed;

[0008] Based on the dynamic balance equation and the target disengaging speed, adjusting at least one of the mass of the swashplate block, the position of the center of mass of the swashplate block in the radial direction of the swashplate clutch, the shape of the contact surface between the swashplate block and the outer sleeve, the contact position between the elastic member and the swashplate block, the elastic coefficient of the elastic member, and the mass of the elastic member;

[0009] Wherein, the dynamic balance equation is: when the swashplate block is disengaged from the inner sleeve, the functional relationship between the speed of the outer sleeve and the mass of the swashplate block, the position of the center of mass of the swashplate block in the radial direction of the swashplate clutch, the shape of the contact surface between the swashplate block and the outer sleeve, the contact position between the elastic member and the swashplate block, the elastic coefficient of the elastic member, and the mass of the elastic member.

[0010] In an alternative embodiment, the contact point between the diagonal support block and the outer sleeve is defined as O, and the dynamic balance equation is:

[0011] RES B ×h2 - RES F ×h1 - F CG ×L CG = 0

[0012] Wherein, RES F is the driving force of the elastic member on the first side of the diagonal support block against the diagonal support block; RES B is the driving force of the elastic member on the second side of the diagonal support block against the diagonal support block; h1 is the lever arm from point O to RES F ; h2 is the lever arm from point O to RES B ; F CG is the centrifugal force of the diagonal support block; L CG is the lever arm from point O to F CG ; wherein,

[0013]

[0014] K Wt is the correction coefficient; m G is the mass of a single diagonal support block; η0 is the rotational speed of the outer sleeve; O CG is the diameter of the circle where the centroid of the diagonal support block is located.

[0015] In an alternative embodiment, the first side of the diagonal support block has a first groove, and the second side of the diagonal support block has a second groove. The side wall of the first groove close to the outer sleeve abuts against the elastic member, and the side wall of the second groove close to the inner sleeve abuts against the elastic member.

[0016] Correspondingly, RES F is the resultant force of the elastic force of the elastic member and the centrifugal force of the elastic member.

[0017] In an alternative embodiment, the elastic member is of an annular structure, and the elastic member is provided with a pocket hole for the diagonal support block to be placed therein. Along the circumferential direction of the diagonal clutch, the pocket hole has opposite first and second side edges;

[0018] Wherein, the first side edge abuts against the first side of the diagonal support block, and the second side edge is provided with a spring piece, and the spring piece abuts against the second side of the diagonal support block.

[0019] In an alternative embodiment, the elastic member includes a plurality of sequentially connected elastic units, each elastic unit including a bent portion and a sheet portion connected to each other. Each elastic unit is provided with a corresponding pocket hole, with the first side of the pocket hole provided on the sheet portion and the second side of the pocket hole provided on the bent portion.

[0020] In an alternative embodiment, the elastic sheet is provided as a bent sheet, one end of the bent sheet being connected to the second side, and the other end of the bent sheet being adapted to abut against the diagonal support block.

[0021] In an alternative embodiment, the diagonal support block includes:

[0022] A first curved surface for abutting against the outer sleeve;

[0023] A second curved surface for abutting against the inner sleeve;

[0024] A first connecting surface provided on the first side of the diagonal support block and connected to one end of the first curved surface and one end of the second curved surface respectively;

[0025] A second connecting surface provided on the second side of the diagonal support block and connected to the other end of the first curved surface and the other end of the second curved surface respectively.

[0026] In a second aspect, the present invention also provides a diagonal support clutch adopting the adjustment method of the disengaging speed as described above.

[0027] In a third aspect, the present invention also provides an engine including the diagonal support clutch as described above.

[0028] In a fourth aspect, the present invention also provides an aircraft including the diagonal support clutch as described above or the engine as described above.

[0029] Based on the dynamic equilibrium equation, the adjustment method of the disengaging speed provided by the present invention can obtain the relationship between the disengaging speed and other variables. By adjusting the variables, the purpose of different disengaging speeds can be achieved. This adjustment scheme has strong operability and can modify some parameters of the existing diagonal support clutch to achieve the purpose of increasing or decreasing the disengaging speed.

[0030] Since the diagonal support clutch, engine and aircraft provided by the present invention include features related to the adjustment method of the disengaging speed, they also include all the above advantages of the adjustment method of the disengaging speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for the description of the specific embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0032] Figure 1 Structural schematic diagram of the inclined support block of the inclined support clutch provided by the embodiment of the present invention, with the inclined support block arranged between the inner sleeve and the outer sleeve;

[0033] Figure 2 Structural schematic diagram of the elastic member provided by the embodiment of the present invention;

[0034] Figure 3 For Figure 2 Partial enlarged schematic diagram of A in

[0035] Figure 4 Force schematic diagram of the inclined support block provided by the embodiment of the present invention;

[0036] Figure 5 For Figure 4 Schematic diagram of the force arm of the centrifugal force and the driving force of the elastic member on the inclined support block relative to point O in

[0037] Explanation of reference numerals:

[0038] 1. Inner sleeve; 2. Outer sleeve; 3. Inclined support block; 301. First groove; 302. Second groove; 303. First curved surface; 304. Second curved surface; 305. First connection surface; 306. Second connection surface; 4. Elastic member; 401. Pocket hole; 402. First side; 403. Second side; 404. Elastic piece; 405. Elastic unit; 4051. Bending part; 4052. Sheet part. Specific embodiments

[0039] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the drawings in the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

[0040] In the related art, a cam clutch generally includes an inner sleeve, an outer sleeve, cam blocks, and an elastic member. The inner sleeve is connected to a starting motor, and the outer sleeve is connected to an engine rotor. During engine starting, the starting motor drives the inner sleeve to operate, and the inner sleeve drives the outer sleeve to rotate through the cam blocks. After the engine rotor reaches a certain rotational speed, the engine ignites and achieves self-rotation. When the rotational speed of the outer sleeve exceeds the rotational speed of the inner sleeve by a preset value, the cam blocks disengage from the inner sleeve, thereby completing engine starting.

[0041] The cam clutch having an appropriate disengagement rotational speed is the key to ensuring smooth engine starting. The problem to be solved by the present invention is how to adjust the disengagement rotational speed of the cam clutch.

[0042] To solve the problem of how to adjust the disengagement rotational speed of the cam clutch, the present invention provides a method for adjusting the disengagement rotational speed, a cam clutch, an engine, and an aircraft.

[0043] The following Figures 1 to 5 describes the method for adjusting the disengagement rotational speed provided in the embodiments of the present invention.

[0044] Specifically, the method for adjusting the disengagement rotational speed is applicable to a cam clutch. The cam clutch includes an inner sleeve 1, an outer sleeve 2, cam blocks 3, and an elastic member 4. Among them, the inner sleeve 1 is used to be connected to a starting motor, and the outer sleeve 2 is used to be connected to the rotor of an engine. The cam clutch belongs to an overrunning clutch. The present application does not improve the principle of the cam clutch, so it will not be elaborated herein.

[0045] Among them, the method for adjusting the disengagement rotational speed includes steps S100 to S200. It can be understood that the implementation subject of the method for adjusting the disengagement rotational speed can be either an operator or a processor.

[0046] Step S100: Obtain a target disengagement rotational speed.

[0047] Specifically, the target disengagement rotational speed is the disengagement rotational speed required by the engine, that is, when the engine runs to the disengagement rotational speed, the cam clutch should disengage, so that the transmission between the engine and the starting motor is disconnected, the starting motor will no longer drive the engine to rotate, and the engine will not drive the starting motor to rotate.

[0048] The target disengagement rotational speed can be determined based on the starting rotational speed required by the engine. For example, if the starting rotational speed required by the engine is large, the target disengagement rotational speed is increased; if the starting rotational speed required by the engine is small, the target disengagement rotational speed is decreased.

[0049] Step S200: Adjust at least one of the mass of the swash block 3, the position of the centroid of the swash block 3 in the radial direction of the swash clutch, the shape of the contact surface between the swash block 3 and the outer sleeve 2, the contact position between the elastic member 4 and the swash block 3, the elastic coefficient of the elastic member 4, and the mass of the elastic member 4 based on the dynamic balance equation and the target disengagement speed.

[0050] Among them, the dynamic balance equation is: when the swash block 3 disengages from the inner sleeve 1, the rotational speed of the outer sleeve 2 is a functional relationship with the mass of the swash block 3, the position of the centroid of the swash block 3 in the radial direction of the swash clutch, the shape of the contact surface between the swash block 3 and the outer sleeve 2, the contact position between the elastic member 4 and the swash block 3, the elastic coefficient of the elastic member 4, and the mass of the elastic member 4.

[0051] Specifically, when the swash block 3 is under the action of the forces of the inner sleeve 1 and the outer sleeve 2, its own centrifugal force, and the driving force of the elastic member 4, the state of dynamic balance formed is the critical state of clutch disengagement. The swash block 3 rotates with the outer sleeve 2, so the rotational speed of the swash block 3 is the same as that of the outer sleeve 2.

[0052] Based on this, the functional relationship between the rotational speed of the outer sleeve 2 and the mass of the swash block 3, the position of the centroid of the swash block 3 in the radial direction of the swash clutch, the shape of the contact surface between the swash block 3 and the outer sleeve 2, the contact position between the elastic member 4 and the swash block 3, the elastic coefficient of the elastic member 4, and the mass of the elastic member 4 can be obtained.

[0053] Based on the dynamic balance equation, the relationship between the rotational speed of the outer sleeve 2 and other variables can be obtained when the swash block 3 disengages from the inner sleeve 1. In addition, since the rotor of the engine is connected to the outer sleeve 2, the target disengagement speed is equal to the rotational speed of the outer sleeve 2 when the clutch is in the critical state of disengagement. Therefore, substituting the target disengagement speed into the dynamic balance equation can obtain the relationship between the target disengagement speed and other variables, and thus the corresponding variables can be adjusted based on the target disengagement speed.

[0054] In this embodiment, based on the dynamic balance equation, the relationship between the disengagement speed and other variables can be obtained. By adjusting the variables, the purpose of different disengagement speeds can be achieved. This adjustment scheme has strong operability and can modify some parameters of the existing swash clutch to achieve the purpose of increasing or decreasing the disengagement speed.

[0055] In addition, the adjustment method is implemented based on the disengagement calculation principle of the swash block 3 and can be verified by programming calculation.

[0056] Reference Figure 4 and Figure 5 As shown, in some embodiments provided by the present invention, the contact point between the swash block 3 and the outer sleeve 2 is defined as O. Correspondingly, the dynamic balance equation is:

[0057] RESB ×h2 - RES F ×h1 - F CG ×L CG = 0。

[0058] Wherein, RES F is the driving force of the elastic member 4 on the first side of the brace block 3 against the brace block 3; RES B is the driving force of the elastic member 4 on the second side of the brace block 3 against the brace block 3; h1 is the lever arm from point O to RES F ; h2 is the lever arm from point O to RES B ; F CG is the centrifugal force of the brace block 3; L CG is the lever arm from point O to F CG .

[0059] Wherein,

[0060] K Wt is the correction coefficient; m G is the mass of a single brace block 3; η0 is the rotational speed of the outer sleeve 2; O CG is the diameter of the circle where the centroid of the brace block 3 is located.

[0061] Specifically, the derivation process is as follows:

[0062] Assume that the contact points of the brace block 3 with the inner sleeve 1 and the outer sleeve 2 are point I and point O respectively. The contact point of the first side of the brace block 3 with the elastic member 4 is regarded as contact point F, and the contact point of the second side of the brace block 3 with the elastic member 4 is contact point B. When the inner sleeve 1 rotates clockwise, the force analysis diagram of the brace block 3 is as shown in Figure 4 .

[0063] The brace block 3 is in dynamic balance under the action of the forces of the inner and outer sleeves 2, its own centrifugal force, and the driving force of the elastic member 4. Taking the clockwise direction as positive, taking the moment about the contact point O of the brace block 3 and the outer sleeve 2, there is a moment balance equation:

[0064] F CG ×L CG + RES F ×h1 - RES B ×h2+(R Ni ×sinV + μ k ×R Ni ×cosV)×h = 0.

[0065] In the formula: F CG is the centrifugal force of the brace block 3,

[0066] K Wt is the correction coefficient. For example, optionally, K Wt= 2.205;

[0067] m G is the mass (g) of a single strut block 3;

[0068] η0 is the rotational speed (r / min) of the outer sleeve 2;

[0069] O CG is the diameter (mm) of the circle where the centroid of the strut block 3 is located. It can be understood that the center of the circle where the centroid is located coincides with the rotation axis of the strut clutch;

[0070] L CG is the lever arm (mm) from point O to F CG ;

[0071] h1 is the lever arm (mm) from point O to RES F ;

[0072] h2 is the lever arm (mm) from point O to RES B ;

[0073] RES F is the driving force (N) of the elastic member 4 on the first side of the strut block 3 acting on the strut block 3;

[0074] RES B is the driving force (N) of the elastic member 4 on the second side of the strut block 3 acting on the strut block 3;

[0075] R Ti is the tangential force of the inner sleeve 1 on the strut block 3;

[0076] R Ni is the radial force of the inner sleeve 1 on the strut block 3;

[0077] h is the working height (mm) of the strut block 3;

[0078] V is the contact angle of the strut block 3, that is, the wedge angle between the strut block 3 and the inner sleeve;

[0079] μ k is the dynamic friction coefficient between the strut block 3 and the inner sleeve 1.

[0080] Based on the above moment balance equation, R can be calculated as Ni :

[0081]

[0082] When the strut block 3 is disengaged from the inner sleeve 1, the acting force between the inner sleeve 1 and the strut block 3 is zero. Therefore, R Ni = 0. Based on the above formula, the dynamic balance equation can be obtained:

[0083] RES B × h2 - RESF × h1 - F CG × L CG = 0。

[0084] It can be understood that the position of the centroid of the diagonal support block 3 in the radial direction of the diagonal support clutch is related to the diameter of the circle where the centroid of the diagonal support block 3 is located. By adjusting the diameter of the circle where the centroid is located, the position of the centroid in the radial direction of the diagonal support clutch can be adjusted.

[0085] Changing the shape of the contact surface of the diagonal support block 3 with the outer sleeve 2 can cause the position of the contact point O between the diagonal support block 3 and the outer sleeve 2 to change, thereby causing L CG , h1, and h2 to change. The change in the shape of the contact surface can be represented by the radius of curvature of the contact surface between the diagonal support block 3 and the outer sleeve 2, that is, changing the radius of curvature of the diagonal support block 3 can cause L CG , h1, and h2 to change.

[0086] The contact position of the elastic member 4 with the diagonal support block 3 can also affect h1 and h2. The contact position is related to the shape and size of the elastic member 4 and the shape and size of the diagonal support block 3, that is, adjusting the shape and size changes of the elastic member 4 and the shape and size changes of the diagonal support block 3 may both affect the contact position.

[0087] RES F and RES B The magnitude of RES and RES is related to the elastic coefficient of the elastic member 4 and the mass of the elastic member 4, that is, adjusting the elastic coefficient and mass of the elastic member 4 may affect RES F and RES B and have an impact.

[0088] It can be understood that the above variables can be measured in 3D software according to the 3D model of the diagonal support clutch as needed, or measured based on the physical object of the diagonal support clutch, and no limitation is made thereto.

[0089] Refer to Figure 4 as shown, Figure 4 In the middle, the inner sleeve 1 is connected to the starting motor. The starting motor drives the inner sleeve 1 to rotate clockwise. The inner sleeve 1 drives the diagonal support block 3 to rotate clockwise along with the inner sleeve 1. The diagonal support block 3 itself has a tendency to swing counterclockwise, so that the diagonal support block 3 can be wedged tightly between the inner sleeve 1 and the outer sleeve 2, thereby driving the outer sleeve 2 to rotate clockwise.

[0090] Refer to Figure 2 and Figure 3 as shown. In some embodiments provided by the present invention, the elastic member 4 is of an annular structure. The elastic member 4 is provided with a pocket hole 401 for the diagonal support block 3 to be placed therein. Along the circumferential direction of the diagonal support clutch, the pocket hole 401 has opposite first side edges 402 and second side edges 403.

[0091] Among them, the first side 402 abuts against the first side of the diagonal brace block 3, and the second side 403 is provided with an elastic piece 404, and the elastic piece 404 abuts against the second side of the diagonal brace block 3.

[0092] In this embodiment, the first side 402 and the second side 403 respectively abut against the two sides of the diagonal brace block 3, providing precise limits for the movement of the diagonal brace block 3 within the pocket hole 401, enabling the diagonal brace block 3 to only move within a specified range, ensuring the action accuracy and reliability of the diagonal brace clutch under different working conditions, avoiding problems such as abnormal displacement or jamming of the diagonal brace block 3, and thus ensuring the normal operation of the clutch.

[0093] The design that the elastic piece 404 abuts against the second side of the diagonal brace block 3 enables the elastic member 4 to make an adaptive adjustment through the elastic deformation of the elastic piece 404 according to the actual movement condition and force state of the diagonal brace block 3. For example, when the diagonal brace block 3 has a position offset due to changes in rotational speed or load fluctuations, the elastic piece 404 can automatically adapt to this change, maintain effective support and restraint on the diagonal brace block 3, and maintain the stable working state of the diagonal brace clutch. That is, the elastic piece 404 is used to drive the diagonal brace block 3 to rotate towards the wedging state.

[0094] Reference Figure 4 As shown, in some embodiments provided by the present invention, the first side of the diagonal brace block 3 has a first groove 301, and the second side of the diagonal brace block 3 has a second groove 302. The side wall of the first groove 301 close to the outer sleeve 2 abuts against the elastic member 4, and the side wall of the second groove 302 close to the inner sleeve 1 abuts against the elastic member 4.

[0095] Correspondingly, RES F is the resultant force of the elastic force of the elastic member 4 and the centrifugal force of the elastic member 4.

[0096] In this embodiment, as shown in reference Figure 4 Since the elastic member 4 abuts against the side wall of the first groove 301 close to the outer sleeve 2, and the elastic member 4 has a centrifugal force during rotation, causing the elastic member 4 to have a tendency to move radially outwards, it can thus act on the side wall of the first groove 301. By setting RES F as the resultant force of the elastic force of the elastic member 4 and the centrifugal force of the elastic member 4, the driving effect of the centrifugal force of the elastic member 4 on the diagonal brace block 3 can be analyzed, and thus the relationship between the driving force of the elastic member 4 and the disengaging rotational speed can be obtained more accurately.

[0097] And the elastic member 4 abuts against the side wall of the second groove 302 close to the inner operation, so the centrifugal force of the elastic member 4 will not exert a pressure effect on the second groove 302.

[0098] The elastic force of the elastic member 4 on the first groove 301 or the second groove 302 can be obtained based on the elastic coefficient of the elastic member 4 and the deformation amount of the elastic member 4. The centrifugal force of the elastic member 4 can be obtained according to the rotational speed of the outer sleeve 2, the mass of the elastic member 4, and the centrifugal force equation.

[0099] Reference Figure 2 and Figure 3 As shown in the figures, in some embodiments provided by the present invention, the elastic member 4 includes a plurality of sequentially connected elastic units 405. The elastic unit 405 includes a bent portion 4051 and a sheet portion 4052 connected to each other. Each elastic unit 405 is provided with a corresponding pocket hole 401. The first side 402 of the pocket hole 401 is provided on the sheet portion 4052, and the second side 403 of the pocket hole 401 is provided on the bent portion 4051. A spring piece 404 is provided on the second side 403. It can be understood that between two adjacent elastic units 405, the sheet portion 4052 of one elastic unit 405 is connected to the bent portion 4051 of the other elastic unit 405.

[0100] In this embodiment, by providing a plurality of elastic units 405, and each elastic unit 405 has a pocket hole 401, a plurality of diagonal support blocks 3 can be arranged on the elastic member 4, so as to reduce the load borne by each diagonal support block 3. In addition, the plurality of elastic units 405 endow the elastic member 4 with better segmented elasticity to adapt to complex deformations. The combination of the bent portion 4051 and the sheet portion 4052 improves the overall flexibility to adapt to different working conditions. The connection mode of the elastic units 405 distributes the force evenly and reduces local stress concentration. The sheet portion 4052 of the adjacent elastic units 405 is connected to the bent portion 4051, enhancing the overall stability. The design of the spring piece 404 can automatically adjust the position of the diagonal support block 3 to ensure close contact.

[0101] In some embodiments provided by the present invention, the spring piece 404 is arranged as a bent piece. One end of the bent piece is connected to the second side 403, and the other end of the bent piece is used to abut against the diagonal support block 3.

[0102] In this embodiment, when the bent piece is subjected to the pressure of the diagonal support block 3, it can absorb more energy through its own bending deformation, provide a better elastic buffering effect, and better adapt to the force change of the diagonal support clutch under different working conditions.

[0103] In some embodiments provided by the present invention, the diagonal support block 3 includes a first curved surface 303, a second curved surface 304, a first connection surface 305, and a second connection surface 306.

[0104] Among them, the first curved surface 303 is used to abut against the outer sleeve 2.

[0105] The second curved surface 304 is used to abut against the inner sleeve 1.

[0106] The first connecting surface 305 is provided on the first side of the strut block 3 and is connected to one end of the first curved surface 303 and one end of the second curved surface 304 respectively. For example, a first groove 301 is provided on the first connecting surface 305.

[0107] The second connecting surface 306 is provided on the second side of the strut block 3 and is connected to the other end of the first curved surface 303 and the other end of the second curved surface 304 respectively. A second groove 302 is provided on the second connecting surface 306.

[0108] An embodiment of the present invention also provides a strut clutch.

[0109] Specifically, the strut clutch adopts the above method for adjusting the disengagement speed.

[0110] It should be noted that since the strut clutch adopts the above adjustment method, it also has corresponding advantages.

[0111] Furthermore, the strut clutch includes an inner sleeve 1, an outer sleeve 2, an elastic member 4, and a strut block 3.

[0112] Refer to Figure 2 and Figure 3 As shown, in some embodiments provided by the present invention, the elastic member 4 is of an annular structure, and a pocket hole 401 for placing the strut block 3 is provided on the elastic member 4. Along the circumferential direction of the strut clutch, the pocket hole 401 has opposite first side edges 402 and second side edges 403.

[0113] Among them, the first side edge 402 abuts against the first side of the strut block 3, and a spring piece 404 is provided on the second side edge 403, and the spring piece 404 abuts against the second side of the strut block 3.

[0114] In this embodiment, the first side edge 402 and the second side edge 403 respectively abut against both sides of the strut block 3, providing precise limits for the movement of the strut block 3 in the pocket hole 401, enabling the strut block 3 to only move within a specified range, ensuring the action accuracy and reliability of the strut clutch under different working conditions, avoiding problems such as abnormal displacement or jamming of the strut block 3, and thus ensuring the normal operation of the clutch.

[0115] The design that the spring piece 404 abuts against the second side of the strut block 3 enables the elastic member 4 to perform adaptive adjustment through the elastic deformation of the spring piece 404 according to the actual movement condition and force state of the strut block 3. For example, when the strut block 3 undergoes a position shift due to a change in speed or a load fluctuation, the spring piece 404 can automatically adapt to this change, maintain effective support and restraint on the strut block 3, and maintain the stable working state of the strut clutch. That is, the spring piece 404 is used to drive the strut block 3 to rotate towards the wedging state.

[0116] Refer to Figure 4As shown, in some embodiments provided by the present invention, the first side of the diagonal bracing block 3 has a first groove 301, and the second side of the diagonal bracing block 3 has a second groove 302. The side wall of the first groove 301 close to the outer sleeve 2 abuts against the elastic member 4, and the side wall of the second groove 302 close to the inner sleeve 1 abuts against the elastic member 4.

[0117] Correspondingly, RES F is the resultant force of the elastic force of the elastic member 4 and the centrifugal force of the elastic member 4.

[0118] In this embodiment, referring to Figure 4 as shown, since the elastic member 4 abuts against the side wall of the first groove 301 close to the outer sleeve 2, the elastic member 4 has a centrifugal force during rotation, so that the elastic member 4 has a tendency to move radially outward, and thus can act on the side wall of the first groove 301. By setting RES F as the resultant force of the elastic force of the elastic member 4 and the centrifugal force of the elastic member 4, the driving effect of the centrifugal force of the elastic member 4 on the diagonal bracing block 3 can be analyzed, so that the relationship between the driving force of the elastic member 4 and the disengagement speed can be obtained more accurately.

[0119] The elastic member 4 abuts against the side wall of the second groove 302 close to the inner operation, so the centrifugal force of the elastic member 4 will not exert a pressure effect on the second groove 302.

[0120] The elastic force of the elastic member 4 on the first groove 301 or the second groove 302 can be obtained based on the elastic coefficient of the elastic member 4 and the deformation amount of the elastic member 4. The centrifugal force of the elastic member 4 can be obtained according to the rotation speed of the outer sleeve 2, the mass of the elastic member 4 and the centrifugal force equation.

[0121] Referring to Figure 2 and Figure 3 as shown, in some embodiments provided by the present invention, the elastic member 4 includes a plurality of sequentially connected elastic units 405. The elastic unit 405 includes a bent portion 4051 and a sheet portion 4052 connected to each other. Each elastic unit 405 is provided with a corresponding pocket hole 401. The first side 402 of the pocket hole 401 is provided on the sheet portion 4052, and the second side 403 of the pocket hole 401 is provided on the bent portion 4051. A spring piece 404 is provided on the second side 403. It can be understood that between two adjacent elastic units 405, the sheet portion 4052 of one elastic unit 405 is connected to the bent portion 4051 of the other elastic unit 405.

[0122] In this embodiment, by providing a plurality of elastic units 405, and each elastic unit 405 having a pocket hole 401, a plurality of diagonal support blocks 3 can be arranged on the elastic member 4, so as to reduce the load borne by each diagonal support block 3. In addition, the plurality of elastic units 405 endow the elastic member 4 with better segmented elasticity to adapt to complex deformations. The combination of the bending part 4051 and the sheet part 4052 improves the overall flexibility to adapt to different working conditions. The connection mode of the elastic units 405 distributes the force evenly and reduces local stress concentration. The sheet part 4052 of adjacent elastic units 405 is connected to the bending part 4051 to enhance the overall stability. The design of the elastic piece 404 can automatically adjust the position of the diagonal support block 3 to ensure close contact.

[0123] In some embodiments provided by the present invention, the elastic piece 404 is arranged as a bending piece, one end of the bending piece is connected to the second side 403, and the other end of the bending piece is used to abut against the diagonal support block 3.

[0124] In this embodiment, when the bending piece is subjected to the pressure of the diagonal support block 3, it can absorb more energy through its own bending deformation, provide a better elastic buffering effect, and better adapt to the force changes of the diagonal support clutch under different working conditions.

[0125] In some embodiments provided by the present invention, the diagonal support block 3 includes a first curved surface 303, a second curved surface 304, a first connection surface 305, and a second connection surface 306.

[0126] Among them, the first curved surface 303 is used to abut against the outer sleeve 2.

[0127] The second curved surface 304 is used to abut against the inner sleeve 1.

[0128] The first connection surface 305 is provided on the first side of the diagonal support block 3 and is respectively connected to one end of the first curved surface 303 and one end of the second curved surface 304. For example, a first groove 301 is provided on the first connection surface 305.

[0129] The second connection surface 306 is provided on the second side of the diagonal support block 3 and is respectively connected to the other end of the first curved surface 303 and the other end of the second curved surface 304. A second groove 302 is provided on the second connection surface 306.

[0130] An engine is also provided in the embodiments of the present invention.

[0131] Specifically, the engine includes the diagonal support clutch as described above.

[0132] It should be noted that since the engine includes the diagonal support clutch, it also includes all the above advantages of the diagonal support clutch.

[0133] An aircraft is also provided in the embodiments of the present invention.

[0134] Specifically, the aircraft includes a diagonal brace clutch or an engine as described above.

[0135] It should be noted that if the aircraft includes a diagonal brace clutch, it also includes all the above advantages of the diagonal brace clutch.

[0136] Although embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations fall within the scope defined by the appended claims.

Claims

1. A method for adjusting the disengagement speed, applicable to a sprag clutch, the sprag clutch comprising an inner sleeve (1), an outer sleeve (2), a sprag block (3) and an elastic member (4), characterized in that: Methods include: Get the target disengagement speed; Based on the dynamic equilibrium equation and the target disengagement speed, at least one of the mass of the diagonal support block (3), the position of the center of mass of the diagonal support block (3) in the radial direction of the diagonal support clutch, the shape of the contact surface between the diagonal support block (3) and the outer sleeve (2), the contact position between the elastic member (4) and the diagonal support block (3), the elastic coefficient of the elastic member (4) and the mass of the elastic member (4) is adjusted; The dynamic equilibrium equation is: when the diagonal support block (3) is disengaged from the inner sleeve (1), the rotation speed of the outer sleeve (2) is a function of the mass of the diagonal support block (3), the position of the center of mass of the diagonal support block (3) in the radial direction of the diagonal support clutch, the shape of the contact surface between the diagonal support block (3) and the outer sleeve (2), the contact position between the elastic member (4) and the diagonal support block (3), the elastic coefficient of the elastic member (4) and the mass of the elastic member (4).

2. The method for adjusting the disengagement speed according to claim 1, characterized in that: The contact point between the diagonal support block (3) and the outer sleeve (2) is defined as O, and the dynamic equilibrium equation is: RES B ×h2-RES F ×h1-F CG ×L CG =0 Among them, RES F RES is the driving force of the elastic member (4) on the first side of the diagonal support block (3) on the diagonal support block (3); B is the driving force of the elastic member (4) on the second side of the diagonal support block (3); h1 is the distance from point O to RES F The force arm; h2 is the distance from point O to RES B The force arm; F CG is the centrifugal force of the diagonal support block (3); L CG From O to F CG The force arm of K Wt is the correction factor; m G is the mass of a single diagonal support block (3); η0 is the rotation speed of the outer sleeve (2); CG It is the diameter of the circle where the center of mass of the diagonal support block (3) is located.

3. The method for adjusting the disengagement speed according to claim 2, characterized in that: The first side of the diagonal support block (3) has a first groove (301), and the second side of the diagonal support block (3) has a second groove (302). The first groove (301) is close to the side wall of the outer sleeve (2) and abuts against the elastic member (4), and the second groove (302) is close to the side wall of the inner sleeve (1) and abuts against the elastic member (4). Accordingly, RES F It is the combined force of the elastic force of the elastic member (4) and the centrifugal force of the elastic member (4).

4. The method for adjusting the disengagement speed according to any one of claims 1 to 3, characterized in that: The elastic member (4) is an annular structure, and is provided with a pocket (401) for the diagonal support block (3) to be placed therein, and along the circumference of the diagonal support clutch, the pocket (401) has a first side edge (402) and a second side edge (403) opposite to each other; The first side edge (402) abuts against the first side of the diagonal support block (3), and the second side edge (403) is provided with a spring sheet (404), and the spring sheet (404) abuts against the second side of the diagonal support block (3).

5. The method for adjusting the disengagement speed according to claim 4, characterized in that: The elastic member (4) comprises a plurality of elastic units (405) connected in sequence, wherein the elastic unit (405) comprises a bending portion (4051) and a sheet portion (4052) connected to each other, each of the elastic units (405) is provided with a corresponding pocket (401), and a first side edge (402) of the pocket (401) is provided on the sheet portion (4052), and a second side edge (403) of the pocket (401) is provided on the bending portion (4051).

6. The method for adjusting the disengagement speed according to claim 4, characterized in that: The spring sheet (404) is configured as a bent sheet, one end of which is connected to the second side edge (403), and the other end of which is used to abut against the diagonal support block (3).

7. The method for adjusting the disengagement speed according to claim 1, characterized in that: The diagonal support block (3) comprises: A first curved surface (303) is used for abutting against the outer sleeve (2); A second curved surface (304) is used for abutting against the inner sleeve (1); A first connecting surface (305) is provided on a first side of the diagonal support block (3) and is respectively connected to one end of the first curved surface (303) and one end of the second curved surface (304); The second connecting surface (306) is arranged on the second side of the diagonal support block (3), and is respectively connected to the other end of the first curved surface (303) and the other end of the second curved surface (304).

8. A sprag clutch, characterized in that: A method for adjusting the disengagement speed as described in any one of claims 1 to 7 is adopted.

9. An engine, characterized in that: Comprising the sprag clutch as claimed in claim 8.

10. An aircraft, characterized in that: Comprising the sprag clutch as claimed in claim 8 or the engine as claimed in claim 9.

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