Method for preventing break point of rotary multi-position switch

Abstract

The present application relates to a kind of methods for preventing breakpoint of rotary multi-position switch, according to the following steps: step one: determine the coaxial series installation mode of dynamic potential energy conversion mechanism and gear switching mechanism;Step two: determine the pre-rotation angle θ of dynamic potential energy conversion mechanism 储 , select compression spring with stiffness coefficient k1, determine the initial torque M0 of compression spring installation, determine the radius r of compression spring installation 簧 ;Step three: determine that the design of dynamic potential energy conversion mechanism satisfies torque monotone increasing, maximum torque M 储 And elastic potential E P ;Step four: on gear switching mechanism, determine the positioning number n, wedge angle θ 楔 , the rotation angle α corresponding to wedge edge, rotation angle γ of smooth section, select n compression spring with stiffness coefficient k2.The remarkable effect of the present application: when switching between switch gears, the overall mechanism torque is always zero, can be passive to realize the instantaneous jump of adjacent gear, does not depend on operator, will not appear the stay between gears, avoid breakpoint.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of rotary multi-position switch, in particular to a method for preventing rotary multi-position switch from having breakpoints. BACKGROUND

[0002] In order to improve the agile response capability and flight reliability of military aircraft, pilots require that all kinds of aircraft have the ability to realize the concept of reliable, safe, comfortable, efficient and personalized in the cockpit. With more and more functions of the aircraft, the control human-machine interface in the cockpit is becoming more and more complex, and the mental workload of the pilot will be increasingly large. The human indicators such as operation response time, rate, force feedback sensitivity will be reduced to different degrees, especially when multiple functions are operated at the same time, the reduction will be multiplied, greatly increasing the operation time. Foreign countries have no technology to avoid breakpoints and achieve rapid change for rotary waveband operation (4-12 positions, continuous motion) core devices. They generally use methods such as improving the machining precision of parts and optimizing the operation force to make up for the deficiency caused by slow operation. However, when the operation is very slow, equipment failure caused by breakpoints and asynchronization may still occur. For important on-board equipment failures, such as engine shutdown, weapons cannot be emergency jettisoned, etc., serious safety accidents may be caused. The basic research on the energy storage jump technology of rotary operation (continuous) devices is weak at home and abroad, and is basically blank. SUMMARY

[0003] The purpose of the present application is to provide a method for preventing rotary multi-position switch from having breakpoints.

[0004] In order to achieve the above purpose, the technical solution of the present application is as follows: a method for preventing rotary multi-position switch from having breakpoints, characterized by the following steps:

[0005] Step 1: Determine the series installation mode of the kinetic potential energy conversion mechanism and the gear position conversion mechanism, and the two are in coaxial state;

[0006] Step 2: Determine the energy storage angle θ of the kinetic potential energy conversion mechanism 储 , select a compression spring with a stiffness coefficient k1, determine the initial torque M0 of the compression spring installation, and determine the radius r 簧 of the compression spring installation;

[0007] Step 3: After passing through a reasonable limiting device, determine that the torque of the kinetic potential energy conversion mechanism is monotonically increasing, the maximum torque M 储 , and the elastic potential energy E P ;

[0008] The stiffness coefficient k1 of the compression spring is determined by the specific material, wire diameter, number of turns, and diameter, etc. 2m (m≥1) compression springs are symmetrically installed in the kinetic potential energy conversion mechanism to form a couple of moments. The energy storage angle θ 储The design is determined by the switch's structural design and limited by a limit structure.

[0009] Step 4: On the gear shifting device, select the double wedge positioning mechanism, and determine the number of positioning parts n and the wedge angle θ. 楔 Given the rotation angle α corresponding to the wedge-shaped edge and the rotation angle γ of the smooth segment, select n compression springs with a stiffness coefficient of k2 and determine the corresponding spring force F. 定 .

[0010] The double-wedge positioning mechanism of the gear shifting device is dovetail-shaped, and is positioned by the cooperation of rotating parts and linear sliding parts. The number of dovetail grooves is kn (k≥1), and the number of linear sliding parts is n. The rotation angle α corresponding to the wedge side should be less than θ. 储 The rotation angle γ of the smooth segment should be less than θ. 储 The smooth section adopts an arc structure.

[0011] Step 5: Determine the maximum torque M during gear shifting. d And the torque difference ΔM formed with the kinetic energy conversion mechanism.

[0012] When the tip of the linear slider corresponds to the end point of the wedge-shaped edge of the rotating component, the maximum torque for gear shifting is reached. Before this, the kinetic energy conversion mechanism has already reached the maximum torque, and the torque difference ΔM is further obtained.

[0013] Step 6: Determine the moment of inertia J of the gear shifting device, the angular acceleration β under the torque difference, and the gear shifting time t.

[0014] The moment of inertia J is related to the volume and material of the rotating component itself.

[0015] The maximum torque M of the kinetic energy conversion mechanism in steps two and three above 储 Its relationship with angle θ 储 A compression spring with stiffness coefficient k1, initial installation torque M0, and installation radius r. 簧 The relationship is as follows:

[0016] M 储 =M0+k1·θ 储 ·r 簧

[0017] The maximum elastic potential energy has the following relationship:

[0018]

[0019] In addition, the number of compression springs symmetrically installed in the kinetic energy conversion mechanism should be even to form a torque couple.

[0020] Furthermore, the double-wedge positioning mechanism of the gear shifting device is dovetail-shaped, consisting of a rotating component and a linear sliding component for positioning. The outer contour of the rotating component is composed of wedge-shaped straight edges and arc segments. Two wedge-shaped straight edges form a dovetail groove, which is multiple of the number of linear sliding components. This ensures that during rotation, the transition tip of the rotating component is always in contact with the straight edge of the linear sliding component, and the direction of the force between them remains unchanged.

[0021] The maximum torque M proposed in step five above d It should be determined according to the following steps:

[0022] A: Let the rotating part rotate counterclockwise by any angle θ. The expression for the angle between the line connecting the transition tip of the rotating part and the center of the circle and the linear sliding part is as follows:

[0023] δ=0.5θ 楔 -α+θ

[0024] B: The force expression of the linear slider under the spring k2 at this time is as follows:

[0025] F 定 =k2·sin(δ)+τ

[0026] Where τ is related to the design dimensions of the gear shifting device.

[0027] C: The forces are orthogonally decomposed, and the expression for the decomposed angles is as follows:

[0028] θ 分解 =90°-γ-θ-0.5θ 楔 +2α

[0029] D: Determine the final torque expression

[0030] M d = [nP·sin(δ)-Q]·sin(θ) 分解 )+[μnP·sin(δ)-μQ]·cos(θ 分解 )

[0031] Where μ is the coefficient of kinetic friction between materials, and P and Q are related to the size design of the gear shifting device.

[0032] Furthermore, the torque difference ΔM is derived, and its expression is as follows:

[0033] ΔM=M d -M 储

[0034] Simultaneous verification:

[0035] (ΔM)'=f'(θ)>0

[0036] Furthermore, the gear shift time is derived, expressed as follows:

[0037]

[0038] The significant advantage of this invention is that it provides a method to prevent breakpoints in rotary multi-position switches. By designing a kinetic energy conversion mechanism and a position switching mechanism based on corresponding structural parameters, the switch can automatically complete position switching as the operator rotates it, independent of operating speed and force. This greatly reduces operational errors, completely avoids breakpoints in the middle of the switch, and improves the agile response capability and flight reliability of military aircraft combat output. Attached Figure Description

[0039] Figure 1 This is a flowchart of the method of the present invention.

[0040] Figure 2 This is a schematic diagram of the force analysis of the gear shifting mechanism in this invention.

[0041] Figure 3 This is a curve showing the relationship between torque and rotation angle in the gear shifting mechanism of this invention.

[0042] Figure 4 This is a schematic diagram of the energy storage jump principle based on torque mutation in this invention. Detailed Implementation

[0043] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0044] Please see Figure 1 The figure shows a method for preventing breakage in rotary multi-position switches, characterized by the following steps:

[0045] Step 1: Determine the series installation method of the kinetic energy conversion mechanism and the gear shifting mechanism, ensuring that they are coaxial;

[0046] Step 2: Determine the energy storage angle θ of the kinetic energy conversion mechanism. 储 Select a compression spring with a stiffness coefficient of k1, determine the initial installation torque M0 of the compression spring, and determine the installation radius r of the compression spring. 簧 ;

[0047] Step 3: After using appropriate limiting devices, determine that the torque of the kinetic energy conversion mechanism increases monotonically, with the maximum torque M... 储 and elastic potential energy E P ;

[0048] The stiffness coefficient k1 of the compression spring is determined by the specific material, wire diameter, number of coils, and mean diameter. Two m (m≥1) springs are symmetrically installed in the kinetic energy conversion mechanism to form a torque couple. Energy storage angle θ 储 The design is determined by the switch's structural design and limited by a limit structure.

[0049] Step 4: On the gear shifting device, select the double wedge positioning mechanism, and determine the number of positioning parts n and the wedge angle θ. 楔 Given the rotation angle α corresponding to the wedge-shaped edge and the rotation angle γ of the smooth segment, select n compression springs with a stiffness coefficient of k2 and determine the corresponding spring force F. 定 .

[0050] The double-wedge positioning mechanism of the gear shifting device is dovetail-shaped, and is positioned by the cooperation of a rotating part and a linear sliding part. The number of dovetail grooves is kn (k≥1), and the number of positioning blocks is n. The rotation angle α corresponding to the wedge side should be less than θ. 储 The rotation angle γ of the smooth segment should be less than θ. 储 The smooth section adopts an arc structure.

[0051] Step 5: Determine the maximum torque M during gear shifting. d And the torque difference ΔM formed with the kinetic energy conversion mechanism.

[0052] When the tip of the linear slider corresponds to the end point of the wedge-shaped edge of the rotating component, the maximum torque for gear shifting is reached. Before this, the kinetic energy conversion mechanism has already reached the maximum torque, and the torque difference ΔM is further obtained.

[0053] Step 5: Determine the moment of inertia J of the gear shifting device, the angular acceleration β under the torque difference, and the gear shifting time t.

[0054] The moment of inertia J is related to the volume and material of the rotating component itself.

[0055] The method of implementing this invention is as follows: when the operator rotates the switch, the kinetic energy conversion mechanism first begins energy storage, M 储 It exhibits a linear monotonically increasing trend, due to M 储 <M d Therefore, the gear shifting mechanism remains stationary during this period. When the torque of the kinetic energy conversion mechanism reaches its maximum, continue rotating the switch, and the gear shifting mechanism begins to move, θ begins to change, due to M d It also shows an increasing trend, therefore the elastic potential energy of the kinetic energy conversion mechanism remains at its maximum at this time. When the tip of the linear slider corresponds to the smooth section of the rotating part, M d The energy level decreases sharply, at which point the kinetic energy conversion mechanism begins to release energy, which serves as the power for the rotating parts to rotate to the end point. At this stage, the shift between gears can be completed without the manual operation of the operator, realizing the leap between gears and avoiding the existence of breakpoints.

[0056] The energy storage angle corresponding to the kinetic energy conversion mechanism in steps two and three above is θ. 储 The corresponding maximum energy storage torque at this time is M. 储 It is a compression spring with an energy storage angular stiffness coefficient of k1, an initial installation torque of M0, and an installation radius of r. 簧 The relationship is as follows:

[0057] M 储 =M0+k1·θ 储 ·r 簧

[0058] The maximum elastic potential energy has the following relationship:

[0059]

[0060] Furthermore, the double-wedge positioning mechanism of the gear shifting device is dovetail-shaped. The outer contour of the rotating component consists of wedge-shaped straight edges and arc segments. Two wedge-shaped straight edges form a dovetail groove, which is a multiple of the number of positioning blocks. In this example, n=4 and k=1. When the rotating component rotates, the transition tip is always in contact with the straight edge of the linear sliding component, and the direction of the force between them remains unchanged.

[0061] The maximum torque M proposed in step five above d It should be determined according to the following steps:

[0062] A: Rotate the scale counterclockwise by any angle θ, such as... Figure 2 As shown. The rotation of the rotating component corresponds to the reciprocating motion of the linear sliding component. The expression for the angle between the line connecting the transition tip of the rotating component and the center of the circle and the linear sliding component is as follows:

[0063] δ=0.5θ 楔 -α+θ

[0064] B: The force expression of the linear slider under the spring k2 at this time is as follows:

[0065] F 定 =k2·sin(δ)+τ

[0066] τ is related to the design dimensions of the gear shifting device.

[0067] C: The forces are orthogonally decomposed, and the expression for the decomposed angles is as follows:

[0068] θ 分解 =90°-γ-θ-0.5θ 楔 +2α

[0069] D: Determine the final torque expression

[0070] M d = [nP·sin(δ)-Q]·sin(θ) 分解 )+[μnP·sin(δ)-μQ]·cos(θ 分解 )

[0071] Where μ is the coefficient of kinetic friction between materials, and P and Q are related to the size design of the gear shifting device. The corresponding torque-rotation angle function curve is shown below. Figure 3 As shown, the gear shifting mechanism in this invention can ensure that the torque increases with the increase of the rotation angle.

[0072] Furthermore, the torque difference ΔM is derived, and its expression is as follows:

[0073] ΔM=M d -M 储

[0074] Simultaneous verification:

[0075] (ΔM)'=f'(θ)>0

[0076] The comparison between the two torques mentioned above is as follows: Figure 4 As shown.

[0077] Furthermore, the gear shift time is derived, expressed as follows:

[0078]

[0079] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A method for preventing breakage in a rotary multi-position switch, the rotary multi-position switch having a kinetic energy conversion mechanism and a position switching mechanism, characterized in that, Perform the following steps in sequence. Step 1: Determine the series assembly form of the kinetic energy conversion mechanism and the gear shifting mechanism, ensuring that they are coaxial. Step 2: Determine the energy storage angle θ of the kinetic energy conversion mechanism. 储 Select a compression spring with a stiffness coefficient of k1, and determine the initial installation torque M0 and the installation radius r of the compression spring. 簧 ; Step 3: After reasonable limiting device and structural design, it is determined that the torque of the kinetic energy conversion mechanism increases monotonically, and the maximum energy storage torque M... 储 and elastic potential energy E P ; Two m units are symmetrically installed in the kinetic potential energy conversion mechanism, where m ≥ 1, to form a torque couple with an energy storage angle θ. 储 The design is determined by the switch's structural design and limited by a limiting structure. Step four: On the gear shifting device, select a positioning mechanism that ensures monotonically increasing torque, determine the number of positioning elements n, and the wedge angle θ. 楔 Given the rotation angle α corresponding to the wedge-shaped edge and the rotation angle γ of the smooth segment, select n compression springs with a stiffness coefficient of k2 and determine the corresponding spring force F. 定 The positioning mechanism of the gear shifting device is dovetail-shaped, consisting of a rotating part with dovetail grooves and a linear sliding part for positioning. The number of dovetail grooves is kn, where k ≥ 1, and the number of linear sliding parts is n. The rotation angle α corresponding to the wedge-shaped side should be less than θ. 储 The rotation angle γ of the smooth segment should be less than θ. 储 The smooth section adopts an arc structure; Step 5: Determine the maximum torque M during gear shifting. d And the torque difference ΔM formed with the energy storage mechanism, when the tip of the linear slider corresponds to the end point of the wedge-shaped edge of the rotating component, the maximum torque is reached during gear shifting. Before this, the kinetic energy conversion mechanism has already reached its maximum torque, further deriving the torque difference ΔM; and, Step 6: Determine the moment of inertia J of the gear shifting mechanism, the angular acceleration β under the torque difference, and the gear shifting time t.

2. The method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, The maximum energy storage torque M of the kinetic energy conversion mechanism 储 Its relationship with the energy storage angle θ 储 A compression spring with stiffness coefficient k1, initial installation torque M0, and installation radius r. 簧 The relationship is as follows: The maximum elastic potential energy has the following relationship: .

3. The method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, In a kinetic energy conversion mechanism, the number of symmetrically installed compression springs should be even to form a torque couple.

4. The method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, The double wedge positioning mechanism of the gear shifting device is dovetail-shaped and is positioned by the cooperation of a rotating part and a linear sliding part. The outer contour of the rotating part is composed of a wedge-shaped straight edge and a circular arc segment. The two wedge-shaped straight edges form a dovetail groove, which is multiple of the number of linear sliding parts. This ensures that during rotation, the transition tip is always in contact with the straight edge of the linear sliding part, and the direction of the force between the two remains unchanged.

5. The method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, Maximum torque M d It should be determined according to the following steps: A: Let the rotating part rotate counterclockwise by any angle θ. The expression for the angle between the line connecting the transition tip of the rotating part and the center of the circle and the linear sliding part is as follows: ; B: The force expression of the linear slider under the spring k2 at this time is as follows: τ is related to the design dimensions of the gear shifting device; C: The forces are orthogonally decomposed, and the expression for the decomposed angles is as follows: ; D: Determine the final torque expression , where μ is the coefficient of kinetic friction between materials, and P and Q are related to the size design of the gear shifting device.

6. The method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, The torque difference ΔM is expressed as follows: Simultaneously verify: .

7. A method for preventing breakage in a rotary multi-position switch according to claim 1, characterized in that, Gear shift time, expressed as follows: .

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