Speed ​​Shifting Mechanism

Abstract

The present invention aims to solve the defects of existing speed transmission devices, such as power interruption and impact, as well as large friction loss and energy consumption during speed switching, and provides a speed switching mechanism. During speed switching, the separation and engagement processes are synchronized and overlapped, and no friction torque is required. Power is maintained by multiple screw grooves to reduce impact. The speed transmission device using the present invention can transmit continuously and smoothly, reduce friction materials, reduce friction loss and energy consumption, and simplify manual operation and automatic control.

Description

Technical Field

[0001] The invention relates to the field of variable speed transmission, and in particular to a mechanism for switching transmission routes with different speeds during transmission. Background Art

[0002] Commonly used speed transmission devices include sliding gear reducers, tooth clutch reducers, elastic sliding key reducers, manual transmissions, dual clutch transmissions, clutch planetary gear transmissions, etc. These speed transmission devices are equipped with operating mechanisms including pull rods, cables, cylindrical cams, hydraulic pistons or electromagnetic push rods and transmission routes with different speeds, and also equipped with speed switching mechanisms, including multiple pairs of components as switching members, the switching members are driven to rotate by the input, or driven to rotate by the output, or can fix the epicyclic gear train components, each pair of switching members of the current route is kept engaged, and each pair of other switching members are kept separated at different speeds. The operating mechanism controls the speed switching under manual or automatic control, so that one pair of the current route is separated and one pair of the target route is engaged, thereby switching the transmission routes with different speeds and changing the input-output transmission ratio.

[0003] For example, a sliding gear reducer, the driving gear and the driven gear of each gear are each pair of switching parts; the driving gear of the current gear is kept in mesh with the driven gear, the transmission route is from the input shaft through the driving gear, the driven gear to the output shaft, the other driving gears are driven by the input, and the other driven gears are driven by the output, and each pair has different speeds and is not meshed; the operating mechanism includes a shift fork, which pushes the current gear to slide so that the two are no longer meshed, and pushes the target gear to slide so that the two are meshed, thereby switching to the transmission route of the target gear. Separation first and then engagement, there is power interruption and impact between gears.

[0004] For example, a tooth clutch reducer has a gear ring on the end face of the driving gear on the input shaft, and a coupling sleeve with a tooth ring splined to the input shaft, which forms a tooth clutch with the gear ring, and is a pair of switching parts; the coupling sleeve driven by the input meshes with the gear ring of the current gear, and the other gear rings are driven by the output and do not mesh with the coupling sleeve at different speeds; the operating mechanism includes a shift fork, which pushes the current coupling sleeve away from the current gear ring and pushes the target coupling sleeve close to the target gear ring until it meshes. There is a power interruption and the impact of the speed difference during engagement.

[0005] For example, an elastic sliding key reducer, also known as a pull-key reducer, has a keyway on the inner rotating surface of each gear driven gear on the output shaft, and a long straight groove is axially provided on the annular output shaft, which runs through the inner and outer rotating surfaces. The elastic sliding key of the shaft can be axially moved, and its elastically connected key passes through the straight groove and cooperates with the gear keyway. It is a pair of switching parts with each driven gear, and the elastic sliding key is a common component; the key remains engaged in the current keyway, and the transmission route is from the input shaft through the gear, keyway, key, straight groove to the output shaft. Other keyways are driven by the input through other transmission routes. The gears are separated at different speeds; the joystick pulls the elastic sliding key to make the key leave the current keyway and move axially to the position of the adjacent keyway. When the two rotate to face each other, the elastic connection allows the key to enter the keyway to complete the engagement. The elastic connection can reduce the impact, but there is still power interruption.

[0006] For example, a manual transmission uses an inertial synchronizer as a speed-shifting mechanism, which is similar to a tooth clutch, with a synchronizer ring and a friction surface. When the shift fork pushes the coupling sleeve close to the gear ring, the friction surface makes the two speeds approach the same before meshing. At the same time, the friction clutch connecting the input shaft and the power source is manually operated to assist in shifting. The impact is effectively reduced, but there is still power interruption, and friction torque is required to complete the engagement.

[0007] For example, a dual-clutch transmission is similar to a manual transmission. Two coaxial input shafts connected to the two driven discs of the dual clutch are respectively provided with driving gears and inertia synchronizers of odd and even gears. The two driven discs of the dual clutch are respectively connected to the driving disc of the power source as two pairs of switching parts. The driven disc of the current gear input shaft remains engaged with the driving disc, and the inertia synchronizer of the other input shaft has engaged the target gear to preselect the target transmission route, so that the driven disc of the other input shaft is driven by the output and remains separated from the driving disc at different speeds. The operating mechanism includes two pressure plates. Changing the pressure of the pressure plate corresponding to the current driven disc separates the switching parts, and changing the pressure of the pressure plate corresponding to the other driven disc engages the other pair of switching parts. The inertia synchronizer is not operated in this separation and engagement and does not serve as a switching part. Friction torque is required to complete the engagement. The overlap of separation and engagement can maintain continuous transmission, but precise control is required to avoid interference caused by excessive overlap.

[0008] For example, a clutch-type planetary gear transmission is provided with multiple sets of clutches as multiple pairs of switching parts, connecting the input shaft, sun gear, planet carrier, outer gear ring and housing of the planetary gear transmission mechanism; multiple sets of clutches in the current transmission route remain engaged, and other clutches are driven by the input shaft or the planetary gear mechanism, and remain separated at different speeds; the planetary gear mechanism is designed to separate and engage only one set of clutches between adjacent gears; the operating mechanism includes a hydraulic piston, which changes the pressure of a set of clutches in the current route to separate it, and changes the pressure of a set of clutches in the target route to engage it. Friction torque is required to complete the engagement, and the overlap of separation and engagement can maintain continuous transmission, but precise control is required to avoid interference caused by excessive overlap.

[0009] The above commonly used transmissions have defects such as power interruption and impact during speed switching, as well as large friction loss and energy consumption. The separation and engagement overlap requires complex and precise automatic control, which increases costs.

[0010] The patented "7-speed transmission" (publication number CN103069195A) optimizes the gear setting and automatic control so that the separation and engagement of the two sets of inertia synchronizers overlap appropriately, reducing power interruption, but friction torque is still required.

[0011] The patent "A Transmission" (publication number CN101469762B) uses a one-way clutch that can separate by itself to simplify control, but still requires other clutches to engage, which requires friction torque.

[0012] The patent "Clutchless Automatic Transmission" (Announcement No. CN102734395B) uses a pair of switching parts with internal and external threads respectively. No friction torque is required for engagement, but the input speed must be reduced to separate and then the speed must be restored to engage. There is power interruption and there is still impact when the engagement is completed. Its preferred example introduces a friction buffer structure to reduce the impact. Summary of the invention

[0013] The object of the present invention is to provide a speed change switching mechanism which can continuously transmit, reduce impact and does not require friction torque.

[0014] The technical solution adopted by the present invention is: a speed switching mechanism, which is applied to a speed transmission device including an operating mechanism and different speed transmission routes, and includes multiple pairs of components as switching components. The switching components are driven to rotate by an input, or driven to rotate by an output, or can fix the components of the revolving gear train. Each pair of switching components of the current route remains engaged, and each pair of other switching components are separated at different speeds. The operating mechanism controls the speed switching, so that one pair of the current route is separated and one pair of the target route is engaged, wherein: each pair of switching components is coaxial, one of which is provided with at least two screw grooves with opposite rotation directions centered on the axis, and the other is provided with at least one screw groove that cooperates with the screw groove Sliding or rolling pins; when each pair of switching parts remains engaged, the position of the pin in the screw groove is the closed position, and the screw grooves with opposite rotation directions are connected or connected and extend to the closed position; the non-closed end of the screw groove is the open position; when each pair of switching parts is engaged, part or all of the pins enter the screw groove from the open position of the screw groove with the rotation direction corresponding to the speed difference, and move to the closed position; when each pair of switching parts is separated, part or all of the pins move from the closed position along the screw groove with the rotation direction corresponding to the speed difference, and separate at the open position; the switching parts engaged with the target route and the switching parts separated with the current route are controlled by the operating mechanism to move synchronously, so that the movement of the pins to engage and the movement of the pins to separate along the screw groove start and are basically completed at the same time.

[0015] One of each pair of switching parts is a large annular wheel, and the other is a small wheel with an outer diameter slightly smaller than the inner diameter of the large wheel. The inner rotating surface of the large wheel and the outer rotating surface of the small wheel are the switching surfaces; the screw groove is a three-dimensional spiral, with the axis as the center line, arranged along the switching surface, the closed position is parallel to the axis, and the open position is at the end surface of the switching part; the pin is perpendicular to the switching surface; the operating mechanism applies an axial force to the engaged switching parts to make the two axially close, and at the same time applies an axial force to the separated switching parts to make the two axially separate, the engaged pin enters the screw groove from the open position opening to start engaging, and the separated pin leaves the screw groove from the open position opening to complete separation.

[0016] The closing position extends to the end face opening of the switching member; the engaged part of the pin enters the switching member from the closing position opening, and the separated part of the pin leaves the switching member from the closing position opening.

[0017] One of the switching parts engaged with the target route and one of the switching parts separated from the current route are a common component, which is coaxial with the other two switching parts; the operating mechanism applies an axial force toward the other engaged switching part to the common component to make it move axially, approaching the other engaged switching part and leaving the other separated switching part.

[0018] The screw groove is a variable pitch spiral, and the helix angle near the closed position is smaller than the helix angle near the closed position.

[0019] The screw groove is a planar spiral with the axis as the center point and is arranged along the end face of the switching member. The tangent of the divided position is perpendicular to or nearly perpendicular to the radial line, and the depth of the closed position is greater than the screw groove depth; the pin moves radially perpendicular to the end face of the switching member; the operating mechanism applies an axial force to the engaged switching member to make the two axially close, and at the same time applies an axial force to the separated switching member to make the two axially separate, and synchronizes the radial movement of the engaged and separated pins, the engaged pin increases in depth when it moves to the closed position, and the separated pin reduces in depth and starts to move from the closed position.

[0020] The switching member with pins is provided with radial slots, and the engaged and disengaged pins are provided with fixed connections and move synchronously along the radial slots.

[0021] The side surface where the screw groove meets the engaged position is an inclined surface, and the side surface where the screw groove meets the separated position is an inclined surface.

[0022] The screw groove is a variable pitch spiral, and the angle between the tangent line and the radial line near the closing position is smaller than the angle between the tangent line and the radial line near the separation position.

[0023] The beneficial effects of the present invention are: continuous transmission during speed switching, reduced impact and no need for friction torque. The speed transmission device using the present invention can continuously and smoothly transmit, reduce friction materials to reduce friction loss and energy consumption, and simplify manual operation and automatic control. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1-1 It is a three-dimensional diagram of the first embodiment of the present invention.

[0025] Figure 1-2 It is a perspective exploded view of the first embodiment of the present invention.

[0026] Figure 1-3 This is an end view of the sheave according to the first embodiment of the present invention.

[0027] Figure 1-4 This is an axial schematic diagram of the switching from first gear to second gear in the first embodiment of the present invention.

[0028] Figure 1-5 This is an axial schematic diagram of switching from second gear to first gear according to the first embodiment of the present invention.

[0029] Figure 1-6 This is an end view of a groove wheel with more grooves according to the second embodiment of the present invention.

[0030] Figure 2-1 It is a stereogram of the second embodiment of the present invention.

[0031] Figure 2-2 This is an exploded view of the second embodiment of the present invention.

[0032] Figure 2-3 This is a rotating surface diagram of the groove wheel of the second embodiment of the present invention.

[0033] Figure 2-4 This is a schematic diagram of switching from first gear to second gear in embodiment 2 of the present invention.

[0034] Figure 2-5 This is a schematic diagram of switching from second gear to first gear according to the second embodiment of the present invention.

[0035] Figure 2-6 3D diagram of a groove wheel with various screw groove number schemes according to the second embodiment of the present invention.

[0036] Figure 2-7 This is a rotating surface diagram of a groove wheel with more screw grooves according to the second embodiment of the present invention.

[0037] Figure 2-8 This is a three-dimensional diagram of a sheave with a baffle according to the second embodiment of the present invention.

[0038] Figure 2-9 This is a simplified diagram of a large wheel and small wheel interchange solution according to the second embodiment of the present invention.

[0039] Figure 3-1 It is a three-dimensional diagram of embodiment 3 of the present invention.

[0040] Figure 3-2 This is an exploded view of embodiment 3 of the present invention.

[0041] Figure 3-3 This is a stereoscopic diagram of a sheave according to Embodiment 3 of the present invention.

[0042] Figure 3-4This is a schematic diagram of switching from first gear to second gear in embodiment 3 of the present invention.

[0043] Figure 3-5 This is a schematic diagram of switching from second gear to first gear according to the third embodiment of the present invention.

[0044] Figure 4-1 It is a three-dimensional diagram of the fourth embodiment of the present invention.

[0045] Figure 4-2 This is an exploded view of embodiment 4 of the present invention.

[0046] Figure 4-3 It is a perspective view of the inner rotating surface of the sheave according to the fourth embodiment of the present invention.

[0047] Figure 4-4 It is a perspective schematic diagram of switching from first gear to second gear according to the fourth embodiment of the present invention.

[0048] Figure 4-5 It is a perspective schematic diagram of switching from second gear to first gear according to the fourth embodiment of the present invention.

[0049] Figure 5-1 It is a three-dimensional diagram of embodiment 5 of the present invention.

[0050] Figure 5-2 This is an exploded view of the fifth embodiment of the present invention.

[0051] Figure 5-3 This is a rotating surface diagram of the groove wheel of embodiment 5 of the present invention.

[0052] Figure 5-4 This is a schematic diagram of switching from first gear to second gear in embodiment 5 of the present invention.

[0053] Figure 5-5 This is a schematic diagram of switching from second gear to first gear in embodiment 5 of the present invention.

[0054] Figure 6-1 The present invention is applied to a clutch type planetary gear transmission device. DETAILED DESCRIPTION

[0055] The present invention is further described below with reference to a plurality of embodiments and drawings.

[0056] Reference below Figure 1-1 to Figure 1-5 Embodiment 1 is described.

[0057] The first sheave 11 and the second sheave 12 are driven wheels for the first and second gears, respectively, and are coaxially sleeved on the output shaft 14. The first sheave 11 and the second sheave 12 are provided with a first screw groove 11A, a second screw groove 11B, a third screw groove 12A and a fourth screw groove 12B on the opposite end faces thereof, respectively, and are all half-turn plane spirals, with the axis as the spiral center. The first screw groove 11A and the third screw groove 12A are opposite in rotation to the second screw groove 11B and the fourth screw groove 12B, respectively, and are symmetrical about the axial section.

[0058] The side surfaces of the first quartile 11C, the second quartile 11D, the third quartile 12C, and the fourth quartile 12D at one end of the first screw groove 11A, the second screw groove 11B, the third screw groove 12A, and the fourth screw groove 12B are all inclined surfaces. The first screw groove 11A and the third screw groove 12A are connected to the second screw groove 11B and the fourth screw groove 12B at the first joint 11P and the second joint 12P respectively, and the depth is greater than the screw groove, and the side surfaces are inclined surfaces. The axial distances of the first joint 11P, the third quartile 12C, and the fourth quartile 12D are the same, and are greater than the second joint 12P, the first quartile 11C, and the second quartile 11D with the same axial distance. The tangents of the first quartile 11C, the second quartile 11D, the third quartile 12C, and the fourth quartile 12D are perpendicular or nearly perpendicular to the radial line.

[0059] The pin wheel 13 is spline-connected to the output shaft 14 and can move axially between the first groove wheel 11 and the second groove wheel 12. The pin wheel 13 is provided with a straight groove 13C that penetrates the end face in the radial direction, and the first pin 13A and the second pin 12B facing the first groove wheel 11 and the second groove wheel are provided at both ends, respectively, and the two are connected by bolts 13D. An annular protrusion is provided in the middle of each pin, and the outer edge diameter is larger than the width of the straight groove 13C, which is perpendicular to the pin wheel 13 and axially fixed. The width of each pin matches the width of each screw groove, and the length of each pin matches the depth of the first closing position 11P and the second closing position 12P. When the first pin 13A is located at the first closing position 11P, there is only a small gap between the second pin 13B and the end face of the second groove wheel 12, and they are not in contact.

[0060] The working process of the first embodiment is described below by taking the example that the rotation speed of the second sheave 12 is higher than that of the first sheave 11 .

[0061] During assembly, the pin wheel 13 is axially moved and rotated so that the first pin 13A faces and enters the first closing position 11P. This is a first gear, and the transmission route passes through the first closing position 11P and the first pin 13A, and the pin wheel 13 is a first gear speed of the first groove wheel 11.

[0062] When the second gear needs to be switched, the operating mechanism applies an axial force to the pin wheel 13 toward the second groove wheel 12, and the end face of the second pin 13B abuts against the end face of the second groove wheel 12, and the pin wheel 13 cannot move. Figure 1-4 A. When the fourth position 12D of the pin wheel 13 rotates to face the second pin 13B at a higher speed than the fourth position 12D, the pin wheel 13 is pushed by the axial force to move toward the second groove wheel 12, and the second pin 13B enters the fourth position 12D and the fourth screw groove 12B of the rotation direction corresponding to the speed difference. At the same time, the first pin 13A axially leaves the first engagement position 11P to reduce the depth to match the first screw groove 11A. Figure 1-4 B.

[0063] The second pin 13B moves along the fourth screw groove 12B with a higher rotation speed to the second closing position 12P. Due to the pressure generated by the fourth screw groove 12B, the rotation speed of the pin wheel 13 tends to be close to the second groove wheel 12 and higher than the first groove wheel 11, so that the first pin 13A moves along the first screw groove 11A corresponding to the rotation direction of the speed difference to the first split position 11C. At the same time, the first pin 13A and the second pin 13B move along the straight groove 13C toward the axis, as shown in FIG. Figure 1-4 C. The first pin 13A and the second pin 13B gradually move away from the first closing position 11P and the fourth partial position 12D, and gradually approach the first partial position 11C and the second closing position 12P, respectively. The rotation speed of the pin wheel 13 gradually approaches the second groove wheel 12. Figure 1-4 D. Figure 1-4 E.

[0064] The pin wheel 13 and the first groove wheel 11 are a pair of switching parts separated by the first gear route, and the pin wheel 13 and the second groove wheel 12 are a pair of rotating parts engaged by the second gear route. The bolt 13D connects the first pin 13A and the second pin 13B, and moves radially synchronously. The separation and engagement processes start basically at the same time, and all pins move along the screw groove for continuous transmission to reduce impact.

[0065] Keeping the axial force on the pin wheel 13, the first pin 13A moves to the first split position 11C and leaves the first screw groove 11A, and the second pin 13B moves to the second closed position 12P, axially entering the second closed position 12P to increase the depth, such as Figure 1-4 F. The first pin 13A is completely separated from the first groove wheel 11, and the second pin 13B is completely engaged with the second groove wheel 12, and the separation and engagement processes are basically completed at the same time. This is the second gear, the transmission route passes through the second closing position 12P and the second pin 13B, and the pin wheel 13 is the second gear speed of the second groove wheel 12.

[0066] When it is necessary to switch to the first gear, the operating mechanism applies an axial force to the pin wheel 13 toward the first groove wheel 11. When the second position 11D with a rotation speed lower than that of the pin wheel 13 rotates to face the first pin 13A, the pin wheel 13 moves toward the first groove wheel 11, and the first pin 13A enters the second position 11D and the second screw groove 11B of the rotation direction corresponding to the rotation speed difference. At the same time, the second pin 13B axially leaves the second engagement position 12P to reduce the depth to match the third screw groove 12A. Figure 1-5 A. Figure 1-5 B.

[0067] The first pin 13A moves along the second screw groove 11B with a lower rotation speed to the first closing position 11P. Due to the pressure generated by the second screw groove 11B, the rotation speed of the pin wheel 13 tends to be close to the first groove wheel 11 and lower than the second groove wheel 12, so that the second pin 13B moves along the third screw groove 12A with a rotation direction corresponding to the rotation speed difference to the third position 12C. At the same time, the first pin 13A and the second pin 13B move away from the axis along the straight groove 13C. Figure 1-5 C. Figure 1-5 D. Figure 1-5 E.

[0068] The pin wheel 13 and the second groove wheel 12 are a pair of switching parts separated in the second gear, and the pin wheel 13 and the first groove wheel 11 are a pair of rotating parts engaged in the first gear. The bolt 13D connects the first pin 13A and the second pin 13B to move radially synchronously.

[0069] Keeping the axial force on the pin wheel 13, the second pin 13B moves to the third split position 12C and leaves the third screw groove 12A, and the first pin 13A moves to the first closing position 11P, axially enters the first closing position 11P to increase the depth, such as Figure 1-4 F. This is the first gear, and the pin wheel 13 is the first gear speed of the first groove wheel 11.

[0070] The switching process in which the rotation speed of the first groove wheel 11 is higher than that of the second groove wheel 12 is similar to the above process, and the pin moves along the screw groove in the opposite direction to the above process.

[0071] Reference below Figure 2-1 to Figure 2-5 The second embodiment is described.

[0072] The first pin wheel 21, the second pin wheel 22 and the third pin wheel 23 are respectively the first gear, the second gear and the third gear annular driven large wheels, which are coaxially and equidistantly sleeved in the bracket 26 in sequence and have the same inner diameter. The first pin 21A and the fourth pin 21B, the second pin 22A and the fifth pin 22B, the third pin 23A and the sixth pin 23B are respectively provided vertically and rotationally symmetrically on the inner rotating surface.

[0073] The groove wheel 24 is a small wheel, spline-connected with the output shaft 25 and axially movable, with an outer diameter slightly smaller than the inner diameter of each coaxial pin wheel, and the inner rotating surface of the pin wheel and the outer rotating surface of the groove wheel are switching surfaces. The outer rotating surface of the groove wheel 24 is provided with a first screw groove 24A, a second screw groove 24B, a third screw groove 24C, a fourth screw groove 24D, a fifth screw groove 24E, a sixth screw groove 24F, a seventh screw groove 24G, and an eighth screw groove 24H, all of which are a quarter-turn three-dimensional spiral with the axis as the spiral center. The first screw groove 24A, the fourth screw groove 24D, the fifth screw groove 24E, and the eighth screw groove 24H are right-handed, and the second screw groove 24B, the third screw groove 24C, the sixth screw groove 24F, and the seventh screw groove 24G are left-handed.

[0074] The first screw groove 24A, the second screw groove 24B, the third screw groove 24C, and the fourth screw groove 24D are rotationally symmetrical with the fifth screw groove 24E, the sixth screw groove 24F, the seventh screw groove 24G, and the eighth screw groove 24H, respectively. The first screw groove 24A, the third screw groove 24C, the fifth screw groove 24E, and the seventh screw groove 24G are symmetrical with the second screw groove 24B, the fourth screw groove 24D, the sixth screw groove 24F, and the eighth screw groove 24H, respectively, about the cross section of the middle part of the sheave 24. The first screw groove 24A, the second screw groove 24B, the fifth screw groove 24E, and the sixth screw groove 24F are symmetrical with the third screw groove 24C, the fourth screw groove 24D, the seventh screw groove 24G, and the eighth screw groove 24H, respectively, about the axial section.

[0075] The second screw groove 24B and the fourth screw groove 24D open on the end face of the groove wheel 24 facing the third pin wheel 23 to form the second position 24S and the fourth position 24U respectively with the eighth screw groove 24H and the sixth screw groove 24F; the first screw groove 24A and the third screw groove 24C open on the other end face of the groove wheel 24 to form the first position 24R and the third position 24T respectively with the seventh screw groove 24G and the fifth screw groove 24E.

[0076] The first screw groove 24A and the second screw groove 24B are connected to the third screw groove 24C and the fourth screw groove 24D at the first interface 24K and the second interface 24L near the middle of the sheave 24, respectively, and extend to the first joint position 24P in the middle of the sheave 24. The fifth screw groove 24E and the sixth screw groove 24F are connected to the seventh screw groove 24G and the eighth screw groove 24H at the third interface 24M and the fourth interface 24N near the middle of the sheave 24, respectively, and extend to the second joint position 24Q in the middle of the sheave 24. The tangents of the first joint position 24P and the second joint position 24Q are parallel to the axis.

[0077] The width and height of each pin are matched with the width and depth of each screw groove. When the first pin 21A is located at the first closing position 24P, there is only a small gap between the second pin 22A and the end surface of the groove wheel 24 without contact.

[0078] The pin wheel can be axially fixed in the bracket 26 by a thrust ring, or a bearing can be provided between the pin wheel and the bracket 26. An annular driven gear, pulley or sprocket with an inner diameter larger than the inner diameter of the pin wheel and a width smaller than the pin wheel spacing can be provided on one end face of the pin wheel to drive the pin wheel; or the axial length of the pin wheel can be increased, and a driven tooth can be provided at one end of the outer rotating surface and the other end can be connected to the bracket 26.

[0079] The working process of the second embodiment is described below by taking the example that the second pin wheel 22 rotates faster than the first pin wheel 21 and slower than the third pin wheel 23 (the description of the rotationally symmetrical part of the pin wheel and the groove wheel is omitted in the following text to save space).

[0080] During assembly, the groove wheel 24 is axially moved and rotated so that the first pin 21A faces and enters the second split position 24S, and moves along the second screw groove 24B to the first closing position 24P. This is the first gear, the transmission route passes through the first pin 21A and the first closing position 24P, and the groove wheel 24 is the first gear speed of the first pin wheel 21.

[0081] When the second gear needs to be switched, the operating mechanism applies an axial force to the groove wheel 24 toward the second pin wheel 22, and the side surface of the second pin 22A abuts against the end surface of the groove wheel 24, so that the groove wheel 24 cannot move. Figure 2-4 A. When the second pin 22A with a higher speed than the groove wheel 24 rotates to face the second position 24S, the groove wheel 24 is pushed by the axial force to move toward the second pin wheel 22, and the second pin 22A enters the second position 24S and the second screw groove 24B corresponding to the rotation direction of the speed difference. At the same time, the first pin 21A moves toward the first interface 24K. Figure 2-4 B. Figure 2-4 C.

[0082] The second pin 22A with a higher rotation speed moves along the second screw groove 24B toward the second interface 24L, generating pressure on the second screw groove 24B, pushing the groove wheel 24 to continue to move axially, and the rotation speed tends to be close to the second pin wheel 22 and higher than the first pin wheel 21, so that the first pin 21A moves along the first screw groove 24A in the rotation direction corresponding to the rotation speed difference to the first position 24R. Figure 2-4 D. The first pin 21A and the second pin 22A gradually move away from the first interface 24K and the second position 24S, and gradually approach the first position 24R and the second interface 24L, respectively. The groove wheel 24 continues to move axially, and the rotation speed gradually approaches the second pin wheel 22. Figure 2-4 E.

[0083] The groove wheel 24 and the first pin wheel 21 are a pair of switching parts that separate the first gear route, and the groove wheel 24 and the second pin wheel 22 are a pair of switching parts that engage the second gear route, wherein the groove wheel 24 is a shared component, and the separation and engagement processes start basically at the same time, and all pins move along the screw groove for continuous transmission to reduce impact.

[0084] Maintaining the axial force on the groove wheel 24, the first pin 21A moves to the first split position 24R and leaves the first screw groove 24A, and the second pin 22A moves to the second interface 24L. Since the rotation speeds are substantially the same, it continues to move to the first closed position 24P. Figure 2-4 F. Figure 2-4 G. The first pin 21A is completely separated from the groove wheel 24, and the second pin 22A is completely engaged with the groove wheel 24, and the separation and engagement processes are basically completed at the same time. This is the second gear, the transmission route passes through the second pin 22A and the first engagement position 24P, and the groove wheel 24 is the second gear speed of the second pin wheel 22.

[0085] The process of switching from the second gear to the third gear is similar to the above process, the third pin wheel 23 is engaged with the groove wheel 24, and the second pin wheel 22 is separated from the groove wheel 24.

[0086] When it is necessary to switch to the first gear, the operating mechanism applies an axial force to the groove wheel 24 toward the first pin wheel 21. When the first pin 21A, which has a rotation speed lower than that of the groove wheel 24, rotates to face the third position 24T, the groove wheel 24 moves toward the first pin wheel 21, and the first pin 21A enters the third position 24T and the third screw groove 24C corresponding to the rotation direction of the rotation speed difference. At the same time, the second pin 22A moves toward the second interface 24L. Figure 2-5 A. Figure 2-5 B. Figure 2-5 C.

[0087] The first pin 21A with a lower rotation speed moves along the third screw groove 24C toward the first interface 24K, generating pressure on the third screw groove 24C, so that the rotation speed of the groove wheel 24 tends to be close to the first pin wheel 21 and lower than the second pin wheel 22, so that the second pin 22A moves along the fourth screw groove 24D of the rotation direction corresponding to the rotation speed difference to the fourth position 24U. Figure 2-5 D. Figure 2-5 E.

[0088] The sheave 24 and the second pin wheel 22 are a pair of switching parts for separating the second gear, and the sheave 24 and the first pin wheel 21 are a pair of switching parts for engaging the first gear, wherein the sheave 24 is a common and identical component.

[0089] Maintaining the axial force on the groove wheel 24, the second pin 22A moves to the fourth split position 24U and leaves the fourth screw groove 24D, and the first pin 21A moves to the first interface 24K. Since the rotation speed is basically the same, it continues to move to the first closed position 24P. Figure 2-5 F. Figure 2-5 G. This is the first gear, and the groove wheel 24 is the first gear speed of the first pin wheel 21.

[0090] The process of switching from the third gear to the second gear is similar to the above process, the second pin wheel 22 is engaged with the groove wheel 24, and the third pin wheel 23 is separated from the groove wheel 24.

[0091] The switching process in which the first pin wheel 21 rotates faster than the second pin wheel 22 is similar to the above process, and the pin moves along the screw groove in the opposite direction to that in the above process.

[0092] Reference below Figure 3-1 to Figure 3-5 The third embodiment is described.

[0093] The first pin wheel 31, the second pin wheel 32 and the third pin wheel 33 are respectively the first gear, the second gear and the third gear annular driven large wheels, which are coaxially and equidistantly sleeved in the bracket 36 in sequence, have the same inner diameter, and the first pin 31A and the fourth pin 31B, the second pin 32A and the fifth pin 32B, the third pin 33A and the sixth pin 33B are vertically provided at both ends of the inner rotating surface with a half circle interval, and the first pin 31A and the second pin 32A are close to the fifth pin 32B and the sixth pin 33B respectively.

[0094] The groove wheel 34 is a small wheel, which is spline-connected with the output shaft 35 and can move axially. The outer diameter is slightly smaller than the inner diameter of each coaxial pin wheel. The outer rotating surface of the groove wheel 34 is provided with a first screw groove 34A, a second screw groove 34B, a third screw groove 34C, and a fourth screw groove 34D, all of which are half-turn three-dimensional spirals. The first screw groove 34A and the fourth screw groove 34D are right-handed, and the second screw groove 34B and the third screw groove 34C are left-handed. The first screw groove 34A and the third screw groove 34C are respectively arranged half a turn away from the second screw groove 34B and the fourth screw groove 34D. The first screw groove 34A and the fourth screw groove 34D are respectively symmetrical with the third screw groove 34C and the second screw groove 34B about the axial section.

[0095] The second screw groove 34B and the fourth screw groove 34D open at the end surface of the groove wheel 34 facing the third pin wheel 33 as the first position 34R, and the first screw groove 34A and the third screw groove 34C open at the other end surface of the groove wheel 34 as the second position 34S. The first screw groove 34A and the second screw groove 34B are connected with the third screw groove 34C and the fourth screw groove 34D at the first interface 34K near the first position 34R and the second interface 34L near the second position 34S, respectively, and extend to the first closing position 34P and the second closing position 34Q, respectively, and continue to extend to the first position 34R and the second position 34S. The tangents of the first closing position 34P and the second closing position 34Q are parallel to the axis.

[0096] The axial length of each pin wheel is the same as the axial length of the groove wheel 34, and there is only a small gap between the pin wheels without contact.

[0097] The working process of the third embodiment is described below by taking the example that the rotation speed of the second pin wheel 32 is higher than that of the first pin wheel 31 and lower than that of the third pin wheel 33 .

[0098] During assembly, the groove wheel 34 is axially moved and rotated, so that the fourth pin 31B faces and enters the first split position 34R, and moves along the second screw groove 34B to the second closed position 34Q. At this time, the first pin 31A faces and enters the first split position 34R and moves to the first closed position 34P. This is the first gear, and the transmission route passes through the first pin 31A and the fourth pin 31B, the first closed position 34P and the second closed position 34Q. The groove wheel 34 is the first gear speed of the first pin wheel 31.

[0099] When it is necessary to switch to the second gear, the operating mechanism applies an axial force to the groove wheel 34 toward the second pin wheel 32. When the fifth pin 32B, which has a higher rotation speed than the groove wheel 34, rotates to face the first position 34R, the groove wheel 34 moves toward the second pin wheel 32, and the fifth pin 32B enters the first position 34R and the second screw groove 34B corresponding to the rotation direction of the speed difference. At the same time, the first pin 31A moves toward the first interface 34K, and the fourth pin 31B leaves the groove wheel 34 from the second closing position 34Q through the second position 34S. Figure 3-4 A. Figure 3-4 B.

[0100] The fifth pin 32B with a higher rotation speed moves along the second screw groove 34B toward the second interface 34L, generates pressure on the second screw groove 34B, pushes the groove wheel 34 to continue to move axially, and the rotation speed tends to be close to the second pin wheel 32 and higher than the first pin wheel 31, so that the first pin 31A moves along the first screw groove 34A in the rotation direction corresponding to the rotation speed difference to the second position 34S. Figure 3-4 C. Figure 3-4 D.

[0101] The groove wheel 34 and the first pin wheel 31 are a pair of switching parts separated in the first gear, and the groove wheel 34 and the second pin wheel 32 are a pair of switching parts engaged in the second gear, wherein the groove wheel 34 is a common component, and the separation and engagement processes start basically at the same time, and some pins move along the screw groove for continuous transmission to reduce impact.

[0102] Maintaining the axial force on the groove wheel 34, the first pin 31A moves to the second split position 34S and leaves the first screw groove 34A, and the fifth pin 32B moves to the second interface 34L. Since the rotation speed is basically the same, it continues to move to the second closed position 34Q. At this time, the second pin 32A moves to the first closed position 34P opposite to the first split position 34R, and the separation and connection processes are basically completed at the same time. Figure 3-4 E. Figure 3-4 F. This is the second gear, the transmission line passes through the second pin 32A and the fifth pin 32B, the first closing position 34P and the second closing position 34Q, and the groove wheel 34 is the second gear speed of the second pin wheel 32.

[0103] The process of switching from the second gear to the third gear is similar to the above process, the third pin wheel 33 is engaged with the groove wheel 34, and the second pin wheel 32 is separated from the groove wheel 34.

[0104] When it is necessary to switch to the first gear, the operating mechanism applies an axial force to the groove wheel 34 toward the first pin wheel 31. When the first pin 31A with a rotation speed lower than that of the groove wheel 34 rotates to face the second position 34S, the groove wheel 34 moves toward the first pin wheel 31, and the first pin 31A enters the second position 34S and the third screw groove 34C of the rotation direction corresponding to the rotation speed difference. At the same time, the fifth pin 32B moves toward the second interface 34L, and the second pin 32A leaves the groove wheel 34 from the first position 34P through the first position 34R. Figure 3-5 A. Figure 3-5B.

[0105] The first pin 31A with a lower rotation speed moves along the third screw groove 34C toward the first interface 34K, generating pressure on the third screw groove 34C, so that the rotation speed of the groove wheel 34 tends to be close to the first pin 31A and lower than the second pin wheel 32, so that the fifth pin 32B moves along the fourth screw groove 34D of the rotation direction corresponding to the rotation speed difference to the first position 34R. Figure 3-5 C. Figure 3-5 D.

[0106] The sheave 34 and the second pin wheel 32 are a pair of switching parts for separating the second gear, and the sheave 34 and the first pin wheel 31 are a pair of switching parts for engaging the first gear, wherein the sheave 34 is a common and identical component.

[0107] Maintaining the axial force on the groove wheel 34, the fifth pin 32B moves to the first split position 34R and leaves the fourth screw groove 34D, and the first pin 31A moves to the first interface 34K. Since the rotation speed is basically the same, it continues to move to the first closed position 34P. At this time, the fourth pin 31B moves to the second closed position 34Q opposite to the second split position 34S. Figure 3-5 E. Figure 3-5 F. This is the first gear, and the groove wheel 34 is the first gear speed of the first pin wheel 31.

[0108] The process of switching from the third gear to the second gear is similar to the above process, the second pin wheel 32 is engaged with the groove wheel 34, and the third pin wheel 33 is separated from the groove wheel 34.

[0109] The switching process in which the rotation speed of the first pin wheel 31 is higher than that of the second pin wheel 32 is similar to the above process, and the pin moves along the screw groove in the opposite direction to that in the above process.

[0110] Reference below Figure 4-1 to Figure 4-5 Embodiment 4 is described.

[0111] The first sheave 41, the second sheave 42, and the third sheave 43 are respectively the first, second, and third gear annular driven large wheels, which are coaxially and equidistantly sleeved in the bracket 46 in sequence and have the same inner diameter. The inner rotating surface of the first sheave 41 is provided with the first screw groove 41A, the second screw groove 41B, the third screw groove 41C, and the fourth screw groove 41D, which are all half-turn three-dimensional spirals with the axis as the spiral center. The first screw groove 41A and the fourth screw groove 41D are left-handed, and the second screw groove 41B and the third screw groove 41C are right-handed. The first screw groove 41A and the third screw groove 41C are respectively set half a turn away from the second screw groove 41B and the fourth screw groove 41D. The first screw groove 41A and the fourth screw groove 41D are symmetrical with the third screw groove 41C and the second screw groove 41B about the axial section.

[0112] The second screw groove 41B and the fourth screw groove 41D open at the end face of the groove wheel 41 facing the second groove wheel 42 as the first position 41R, and the first screw groove 41A and the third screw groove 41C open at the other end face of the groove wheel 41 as the second position 41S. The first screw groove 41A and the second screw groove 41B are connected to the third screw groove 41C and the fourth screw groove 41D at the first interface 41K near the first position 41R and the second interface 41L near the second position 41S, respectively, and extend to the first closing position 41P and the second closing position 41Q, respectively, and continue to extend to the first position 41R and the second position 41S. The tangents of the first closing position 41P and the second closing position 41Q are parallel to the axis.

[0113] The inner rotating surface of the second groove wheel 42 is provided with a fifth groove 42A, a sixth groove 42B, a seventh groove 42C, an eighth groove 42D, a third interface 42K, a fourth interface 42L, a third closing position 42P, a fourth closing position 42Q, a third split position 42R, and a fourth split position 42S, which are respectively identical in structure to the first groove 41A, the second groove 41B, the third groove 41C, the fourth groove 41D, the first interface 41K, the second interface 41L, the first closing position 41P, the second closing position 41Q, the first split position 41R, and the second split position 41S. The third groove wheel 43 is identical in structure to the first groove wheel 41.

[0114] The pin wheel 44 is a small wheel, spline-connected to the output shaft 45 and axially movable, with an outer diameter slightly smaller than the inner diameter of each coaxial groove wheel, and the inner rotating surface of the groove wheel and the outer rotating surface of the pin wheel are switching surfaces. A first pin 44A is vertically arranged on the outer rotating surface of the pin wheel 44 on one side facing the third groove wheel 43, and a second pin 44B is vertically arranged on the other side at a distance of half a circle.

[0115] The axial length of each sheave is the same as the axial length of the pin wheel 44, and there is only a small gap between the sheaves without contact.

[0116] The working process of the fourth embodiment is described below by taking the example that the rotation speed of the second sheave 42 is higher than that of the first sheave 41 and lower than that of the third sheave 43 .

[0117] During assembly, the pin wheel 44 is axially moved and rotated, so that the first pin 44A faces and enters the second split position 41S, and moves along the first screw groove 41A to the first closed position 41P. At this time, the second pin 44B faces and enters the second split position 41S and moves to the second closed position 41Q. This is the first gear, and the transmission route passes through the first closed position 41P and the second closed position 41Q, the first pin 44A and the second pin 44B. The pin wheel 44 is the first gear speed of the first groove wheel 41.

[0118] When it is necessary to switch to the second gear, the operating mechanism applies an axial force to the pin wheel 44 toward the second groove wheel 42, the first pin 44A moves to the first position 41R, and the second pin 44B moves to the second interface 41L. When the fourth position 42S with a higher speed rotates to face the first position 41R, the pin wheel 44 continues to move toward the second groove wheel 42, and the first pin 44A leaves the first position 41R and enters the fourth position 42S and the fifth screw groove 42A of the rotation direction corresponding to the speed difference. Figure 4-4 A.

[0119] The first pin 44A moves toward the third interface 42K along the fifth screw groove 42A with a higher rotation speed. Due to the pressure generated by the fifth screw groove 42A, the pin wheel 44 continues to move axially, and the rotation speed tends to be close to the second groove wheel 42 and higher than the first groove wheel 41, so that the second pin 44B moves toward the first position 41R along the second screw groove 41B in the rotation direction corresponding to the rotation speed difference. Figure 4-4 B.

[0120] The pin wheel 44 and the first groove wheel 41 are a pair of switching parts separated in the first gear, and the pin wheel 44 and the second groove wheel 42 are a pair of switching parts engaged in the second gear, wherein the pin wheel 44 is a common and identical component, and the separation and engagement processes start basically at the same time, with continuous transmission, and part of the pin moves along the screw groove to reduce impact.

[0121] The axial force on the pin wheel 44 is maintained, and the first pin 44A moves to the third interface 42K. Since the rotation speed is basically the same, it continues to move to the third closing position 42P. The second pin 44B moves to the first partial position 41R and leaves the second screw groove 41B. At this time, the first partial position 41R is opposite to the fourth partial position 42S. The second pin 44B moves to the fourth closing position 44Q. The separation and joining processes are basically completed at the same time. Figure 4-4 C. Figure 4-4 D. This is the second gear, the transmission line passes through the third closing position 42P and the fourth closing position 42Q, the first pin 44A and the second pin 44B, and the pin wheel 44 is the second gear speed of the second groove wheel 42.

[0122] The process of switching from the second gear to the third gear is similar to the above process, the pin wheel 44 is engaged with the third groove wheel 43, and the pin wheel 44 is separated from the second groove wheel 42.

[0123] When it is necessary to switch to the first gear, an axial force is applied to the pin wheel 44 toward the first groove wheel 41, the second pin 44B moves toward the fourth position 42S, and the first pin 44A moves toward the third interface 42K. When the first position 41R with a lower speed rotates to face the fourth position 42S, the pin wheel 44 continues to move toward the first groove wheel 41, and the second pin 44B leaves the fourth position 42S and enters the first position 41R and the fourth screw groove 41D of the rotation direction corresponding to the speed difference. Figure 4-5 A.

[0124] The second pin 44B moves toward the second interface 41L along the fourth screw groove 41D with a lower rotation speed. Due to the pressure generated by the fourth screw groove 41D, the rotation speed of the pin wheel 44 tends to be close to the first groove wheel 41 and lower than the second groove wheel 42, so that the first pin 44A moves toward the fourth position 42S along the seventh screw groove 42C with a rotation direction corresponding to the rotation speed difference. Figure 4-5 B.

[0125] The pin wheel 44 and the second groove wheel 42 are a pair of switching parts for separating the second gear, and the pin wheel 44 and the first groove wheel 41 are a pair of switching parts for engaging the first gear, wherein the pin wheel 44 is a common and identical component.

[0126] Keeping the axial force on the pin wheel 44, the second pin 44B moves to the second interface 41L. Since the rotation speed is basically the same, it continues to move to the second closing position 42Q. The first pin 44A moves to the fourth partial position 42S and leaves the seventh screw groove 42C. At this time, the fourth partial position 42S is opposite to the first partial position 41R. The first pin 44A moves to the first closing position 41P. Figure 4-5 C. Figure 4-5 D. This is the first gear, and the pin wheel 44 is the first gear speed of the first groove wheel 41.

[0127] The process of shifting from the third gear to the second gear is similar to the above process, the second pin 44B is engaged with the second sheave 42, and the first pin 44A is separated from the third sheave 43.

[0128] The switching process in which the first groove wheel 41 rotates faster than the second groove wheel 42 is similar to the above process, and the pin moves along the screw groove in the opposite direction to the above process.

[0129] Reference below Figure 5-1 to Figure 5-5 Embodiment 5 is described.

[0130] The first pin wheel 51 and the second pin wheel 52 are respectively the first gear and the second gear annular driven large wheels, which are loosely sleeved in the bracket and have the same inner diameter. The first pin 51A and the third pin 51B, the second pin 52A and the fourth pin 52B are respectively provided vertically and rotationally symmetrically on the inner rotating surface.

[0131] The first groove wheel 53 is a small wheel, which is spline-connected to the output shaft 55 and can move axially. The outer diameter is slightly smaller than the inner diameter of the coaxial first pin wheel 51. The outer rotating surface of the first groove wheel 53 is provided with a first screw groove 53A, a second screw groove 53B, a third screw groove 53C, and a fourth screw groove 53D, all of which are a quarter-turn three-dimensional spiral. The first screw groove 53A and the fourth screw groove 53D are right-handed, and the second screw groove 53B and the third screw groove 53C are left-handed. The first screw groove 53A and the third screw groove 53C are rotationally symmetrical with the fourth screw groove 53D and the second screw groove 53B, respectively. The first screw groove 53A and the second screw groove 53B are symmetrical with the third screw groove 53C and the fourth screw groove 53D, respectively, about the axial section of the first groove wheel 53.

[0132] The first screw groove 53A, the third screw groove 53C, the second screw groove 53B, and the fourth screw groove 53D are respectively opened at the first split position 53R and the second split position 53S on the end surface of the first groove wheel 53 facing the first pin wheel 51. The first screw groove 53A, the second screw groove 53B, the third screw groove 53C, and the fourth screw groove 53D are respectively connected to the first interface 53K and the second interface 53M near the other end of the first groove wheel 53, and extend to the first closing position 53P and the second closing position 53Q respectively. The tangents of the first closing position 53P and the second closing position 53Q are parallel to the axis.

[0133] The second sheave 54 is a small wheel, spline-connected with the intermediate shaft 56 and movable along the axial direction, and its outer diameter is slightly smaller than the inner diameter of the coaxial second pin wheel 52. The outer rotating surface of the second sheave 54 is provided with a fifth screw groove 54A, a sixth screw groove 54B, a seventh screw groove 54C, an eighth screw groove 54D, a third interface 54K, a fourth interface 54M, a third closing position 54P, a fourth closing position 54Q, a third split position 54R, and a fourth split position 54S, which are respectively the same in structure as the first screw groove 53A, the second screw groove 53B, the third screw groove 53C, the fourth screw groove 53D, the first interface 53K, the second interface 53M, the first closing position 53P, the second closing position 53Q, the first split position 53R, and the second split position 53S.

[0134] The operating mechanism includes a shift fork 57, and the empty sleeve can move axially on the shift fork bracket 57A, and the axis is parallel to the output shaft 55. The shift claws on both sides of the shift fork 57 respectively abut against the end faces of the first groove wheel 53 and the second groove wheel 54, so that the first groove wheel 53 and the second groove wheel 54 move axially synchronously.

[0135] The intermediate shaft 56 is parallel to the output shaft 55, and the two are connected to the spline belt 58 near the same end to maintain the same speed and rotation direction. When the first pin 51A is located at the first closing position 53P, there is only a small gap between the second pin 52A and the end surface of the second groove wheel 54 without contact.

[0136] The working process of the fifth embodiment is described below by taking the example that the second pin wheel 52 rotates faster than the first pin wheel 51 (the description of the rotationally symmetrical part of the pin wheel and the groove wheel is omitted in the following text to save space).

[0137] During assembly, the first groove wheel 53 is axially moved and rotated, so that the first pin 51A faces and enters the first split position 53R, and moves along the first screw groove 53A to the first closed position 53P. This is the first gear, and the transmission route passes through the first pin 51A and the first closed position 53P. The first groove wheel 53 and the output shaft 55 are the first gear speed of the first pin wheel 51.

[0138] When it is necessary to switch to the second gear, the shift fork 57 applies an axial force toward the second pin wheel 52. When the second pin 52A with a rotation speed higher than that of the second groove wheel 54 rotates to face the fourth position 54S, the second groove wheel 54 moves toward the second pin wheel 52, and the second pin 52A enters the seventh screw groove 54C with a rotation direction corresponding to the fourth position 54S and the rotation speed difference. At the same time, the first groove wheel 53 moves axially synchronously, and the first pin 51A moves toward the first interface 53K. Figure 5-4 A. Figure 5-4 B.

[0139] The second pin 52A with a higher rotation speed moves along the seventh screw groove 54C toward the third interface 54K, generating pressure on the seventh screw groove 54C, pushing the second groove wheel 54 to continue to move axially, and the rotation speed tends to be close to the second pin wheel 52 and higher than the first pin wheel 51. At the same time, the first groove wheel 53 moves axially synchronously, and the first pin 51A moves along the first screw groove 53A in the rotation direction corresponding to the rotation speed difference to the first position 53R. Figure 5-4 C.

[0140] The first groove wheel 53 and the first pin wheel 51 are a pair of switching parts separated in the first gear, and the second groove wheel 54 and the second pin wheel 52 are a pair of switching parts engaged in the second gear. The separation and engagement processes start basically at the same time, and all pins move along the screw grooves for continuous transmission to reduce impact.

[0141] The shift fork 57 maintains the axial force, the first pin 51A moves to the first split position 53R and leaves the first screw groove 53A, the second pin 52A moves to the third interface 54K, and because the rotation speeds are substantially the same, it continues to move to the third engagement position 54P, and the separation and engagement processes are substantially completed at the same time. Figure 5-4 D. Figure 5-4 E. This is the second gear, the transmission line passes through the second pin 52A, the third position 54P, the intermediate shaft 56, the second groove wheel 54 and the output shaft 55 is the second gear speed of the second pin wheel 52.

[0142] When it is necessary to shift to the first gear, the shift fork 57 applies an axial force toward the first pin wheel 51. When the first pin 51A, which has a rotation speed lower than that of the first groove wheel 53, rotates to face the second position 53S, the first groove wheel 53 moves toward the first pin wheel 51, and the first pin 51A enters the second position 53S and the third screw groove 53C of the rotation direction corresponding to the rotation speed difference. At the same time, the second groove wheel 54 moves axially synchronously, and the second pin 52A moves toward the third interface 54K. Figure 5-5 A. Figure 5-5 B.

[0143] The first pin 51A with a lower rotation speed moves along the third screw groove 53C toward the first interface 53K, generating pressure on the third screw groove 53C, pushing the first groove wheel 53 to continue to move axially, and the rotation speed tends to be close to the first pin wheel 51 and lower than the second pin wheel 52. At the same time, the second groove wheel 54 moves axially synchronously, and the second pin 52A moves along the fifth screw groove 54A of the rotation direction corresponding to the rotation speed difference to the third position 54R. Figure 5-5 C.

[0144] The second sheave 54 and the second pin wheel 52 are a pair of switching elements for separating the second gear, and the first sheave 53 and the first pin wheel 51 are a pair of switching elements for engaging the first gear.

[0145] The shift fork 57 maintains the axial force, the second pin 52A moves to the third split position 54R and leaves the fifth screw groove 54A, the first pin 51A moves to the first interface 53K, and because the rotation speed is substantially the same, it continues to move to the first closed position 53P. Figure 5-5 D. Figure 5-5 E. This is the first gear, and the first groove wheel 53 and the output shaft 55 are the first gear speed of the first pin wheel 51.

[0146] The switching process in which the rotation speed of the first pin wheel 51 is higher than that of the second pin wheel 52 is similar to the above process, and the pin moves along the screw groove in the opposite direction to that in the above process.

[0147] The shift fork 57 may be replaced by other shapes or technical means, and the first sheave 53 and the second sheave 54 should be able to move axially synchronously.

[0148] The toothed belt 58 can be replaced by other technical means such as a chain or a gear, and the transmission ratio between the intermediate shaft 56 and the output shaft 55 should satisfy that when the output shaft 55 is at the first gear speed, the intermediate shaft 56 rotates lower than the second pin wheel 52. The intermediate shaft 56 and the output shaft 55 rotate in the opposite direction, and the second pin wheel 52 and the first pin wheel 51 rotate in the opposite direction.

[0149] The pin wheels, the groove wheels and the shift forks can be coaxially arranged.

[0150] In the above embodiment, the transmission direction can be reversed, the output shaft can be used as the input shaft, and the driven wheels can be used as driving wheels to drive other mechanisms.

[0151] In the above embodiment, the plane screw groove adopts a variable pitch spiral, and the angle between the tangent and the radial line near the closing position is smaller than the angle between the tangent and the radial line near the separation position; an equidistant spiral can be adopted, and the switching process is the same as that of the variable pitch spiral.

[0152] In the above embodiment, the three-dimensional screw groove adopts a variable pitch helix, and the helix angle near the closed position is smaller than the helix angle near the separated position; an equidistant helix can be adopted, and the switching process is the same as that of the variable pitch helix.

[0153] In the above embodiment, the number of screw grooves can be smaller and more positions can be provided. Figure 2-6 A takes Example 2 as an example to show a solution of a screw groove less than a quarter of a circle. The second screw groove 24B1 and the eighth screw groove 24H1 are respectively provided with a left position 24S1 and a right position 24S2 at one end of the groove wheel 24, and the position structures of other screw grooves are the same and symmetrical. When the first gear is switched to the second gear, the second pin 22A with a rotation speed higher than that of the groove wheel 24 can enter the second screw groove 24B1 from the left position 24S1, but is pushed out by the eighth screw groove 24H1 when entering the right position 24S2.

[0154] In the above embodiment, the number of spiral grooves can be larger, and the spiral grooves intersect to form a cross. Figure 2-6 B shows a scheme of a half-circle screw groove by taking Example 2 as an example. One pin of each pin wheel has a large width and a small height, and the first combined position 24P and the four connected screw grooves have a large width and a small depth. Another pin of each pin wheel has a small width and a large height, and the second combined position 24Q and the four connected screw grooves have a small width and a large depth. The pin with a large width and a small height moves along the screw groove with a large width and a small depth, and cannot enter the screw groove with a small width when passing through an intersection. The pin with a small width and a large height moves along the screw groove with a small width and a large depth, and cannot enter the screw groove with a small depth when passing through an intersection. A scheme can be adopted in which different pins have different shapes on the top, and the matching screw groove bottoms have matching shapes.

[0155] In the third and fourth embodiments, the pin that should move along the screw groove may enter the opening extending to the end face in the closing position, and a similar Figure 2-6 A scheme B, one pin of each pin wheel has a large width and a small height, the first screw groove 34A, the third screw groove 34C, the first closing position 34P and their end face openings have a large width and a small depth, the other pin of each pin wheel has a small width and a large height, the second screw groove 34B, the fourth screw groove 34D, the second closing position 34Q and their end face openings have a small width and a large depth.

[0156] In the above embodiment, the groove wheel can be rotationally symmetrically provided with more grooves. Figure 1-6 Taking Example 1 as an example, a solution with four screw grooves is shown. Each screw groove has a quarter of a turn, each groove wheel is rotationally symmetrically provided with two groups of two screw grooves, the two groups of screw grooves are connected at two positions, and the pin wheel is rotationally symmetrically provided with two straight grooves and two groups of two pins.

[0157] Figure 2-7 Taking Example 2 as an example, a scheme with twelve screw grooves is shown. Each screw groove has one sixth of a turn, six screw grooves are right-handed and six screw grooves are left-handed, six screw grooves are symmetrically arranged on both sides of the cross section in the middle of the groove wheel, three groups of four screw grooves are rotationally symmetrical, the three groups of screw grooves are connected to three positions in the middle of the groove wheel, and three pins are rotationally symmetrically arranged on the rotating surface of the pin wheel.

[0158] More screw grooves may form intersections. Taking the third embodiment as an example, a group of half-circle screw grooves with the same structure are rotationally symmetrical to form eight crossed screw grooves. At the same time, a group of pins are rotationally symmetrically provided on the pin wheel. More screw grooves and pins can transmit greater power.

[0159] For some applications with heavy loads, the pin may enter a screw groove that does not correspond to the direction of rotation. A mechanism that limits the direction of movement can be used. Figure 2-8 A solution is demonstrated by taking the second embodiment as an example. A first baffle 28A is provided near the first interface 24K of the third screw groove 24C, a fan-shaped groove with a positioning hole is provided between the adjacent sides of the first screw groove 24A and the third screw groove 24C, and a first oblique groove 28C and a second oblique groove 28D are provided on the opposite sides. The first baffle 28A has arc-shaped sides, one end is a positioning column 28B inserted into the positioning hole of the fan-shaped groove, and the other end abuts against the first oblique groove 28C and can be rotated to abut against the second oblique groove 28D. An elastic sheet 28E is provided between the first baffle 28A and the first screw groove 24A. A second baffle 28F is provided near the second interface 24L of the second screw groove 24B, and the structure is symmetrical with the first baffle 28A.

[0160] When the first gear is switched to the second gear, the first baffle 28A prevents the first pin 21A from entering the third screw groove 24C, and the second pin 22A pushes the second baffle 28F along the second screw groove 24B, and continues to move to the first closing position 24P, and the second baffle 28F returns to its original position. When the second gear is switched to the first gear, the second baffle 28F prevents the second pin 22A from entering the second screw groove 24B, and the first pin 21A pushes the first baffle 28A along the third screw groove 24C, and continues to move to the first closing position 24P, and the first baffle 28A returns to its original position.

[0161] In the above embodiment, the large wheel and the small wheel can be interchanged, and the switching surface can be interchanged. Figure 2-9 A solution is shown by taking the second embodiment as an example. The first pin wheel 29A, the second pin wheel 29B, and the third pin wheel 29C are respectively connected to the first gear, the second gear, and the third gear driven wheels, and the outer rotating surfaces are provided with pins, which are respectively the same as the inner rotating surfaces of the first pin wheel 21, the second pin wheel 22, and the third pin wheel 23. The groove wheel 29D is spline-connected to the output shaft 29E and can move axially, and the inner rotating surface is provided with screw grooves, which is the same as the outer rotating surface structure of the groove wheel 24.

[0162] A solution for applying the present invention to a dual clutch transmission is: using the first embodiment or the second embodiment to replace the dual clutch, and Figure 2-9 Similarly, the first groove wheel 11 or the first pin wheel 29A, the second groove wheel 12 or the second pin wheel 29B are respectively connected to the two coaxial input shafts of the driving wheels of each gear of the dual-clutch transmission, and the pin wheel 13 or the groove wheel 29D is connected to a single-plate clutch and then connected to the power source. The single-plate clutch remains engaged after the power source is started, and the speed switching is completed by the groove wheel and the pin wheel.

[0163] Figure 6-1A shows a clutch-type planetary gear transmission device, which is equipped with double-row planetary gears, an input shaft 61, an output shaft 62, a first clutch 63A connecting the front planet carrier and the frame, a second clutch 63B connecting the front sun gear and the frame, a third clutch 63C connecting the front planet carrier and the input shaft, and a fourth clutch 63D connecting the front planet carrier and the rear outer gear ring. Each clutch is operated by a hydraulic device.

[0164] The two pairs of switching parts engaged in the first gear are the first clutch 63A and the fourth clutch 63D, and the front sun gear rotates in the opposite direction; when switching to the second gear, the first clutch 63A is disengaged, the second clutch 63B is engaged, and the fourth clutch 63D is maintained, and the speed of the front planetary carrier is lower than that of the input shaft; when switching to the third gear, the second clutch 63B is disengaged, the third clutch 63C is engaged, and the fourth clutch 63D is maintained, and the speed of the front sun gear and the front planetary carrier is the same as that of the input shaft; when switching to the fourth gear, the fourth clutch 63D is disengaged, the second clutch 63B is engaged, and the third clutch 63C is maintained, and the speed of the rear outer ring gear is higher than that of the front planetary carrier.

[0165] Figure 6-1 B shows the application of the present invention to Figure 6-1 A scheme of a planetary gear transmission device of embodiment A. A first sheave 64A, a second sheave 64B, and a third sheave 64C are provided, which are respectively connected to the front planet carrier, the front sun gear, and the front planet carrier. The outer rotating surface of each sheave and the inner rotating surface of the first sheave 64A are the same as the first sheave 53 of embodiment 5. A first pin wheel 65A, a second pin wheel 65B, a third pin wheel 65C, and a fourth pin wheel 65D are provided, which are respectively spline-connected to the frame, the frame, the input shaft, and the rear outer gear ring. The first sheave 64A, the second sheave 64B, the third sheave 64C, and the first sheave 64A are respectively connected to the first pin wheel 65A, the second pin wheel 65B, the third pin wheel 65C, and the fourth pin wheel 65D as four pairs of switching parts, which respectively replace the first clutch 63A, the second clutch 63B, the third clutch 63C, and the fourth clutch 63D.

[0166] In the first gear, the first pin wheel 65A is engaged with the first groove wheel 64A, and the fourth pin wheel 65D is engaged with the first groove wheel 64A; when switching to the second gear, the first pin wheel 65A is separated from the first groove wheel 64A, and the second pin wheel 65B is engaged with the second groove wheel 64B; when switching to the third gear, the second pin wheel 65B is separated from the second groove wheel 64B, and the third pin wheel 65C is engaged with the third groove wheel 64C; when switching to the fourth gear, the fourth pin wheel 65D is separated from the first groove wheel 64A, and the second pin wheel 65B is engaged with the second groove wheel 64B. The cylindrical cam 66 is connected to the shift fork to manipulate the synchronous axial movement of each pin wheel, and the separation and engagement process is basically started and completed at the same time.

Claims

1. A speed change switching mechanism is used in a speed change transmission device including a control mechanism and transmission routes with different speeds, and includes multiple pairs of components as switching components. The switching components are driven to rotate by the input, or driven to rotate by the output, or can fix the epicyclic gear train components. Each pair of switching components of the current route remains engaged, and each pair of other switching components are separated at different speeds. The speed change switching is controlled by the control mechanism, so that one pair of the current route is separated and one pair of the target route is engaged. The characteristics of this speed change switching mechanism are: One of each pair of switching members is a large annular wheel, and the other is a small wheel with an outer diameter slightly smaller than the inner diameter of the large wheel, and the inner rotating surface of the large wheel and the outer rotating surface of the small wheel are switching surfaces; Each pair of switching members is coaxial, one of which is provided with at least two screw grooves with opposite rotation directions centered on the axis, and the other is provided with at least one pin that slides or rolls in cooperation with the screw groove; The screw groove is a three-dimensional spiral, with the axis as the center line, arranged along the switching surface, parallel to the axis at the closed position, and open at the end surface of the switching member at the open position; The pin is perpendicular to the switching surface; When each pair of switching members is kept engaged, the position of the pin in the screw groove is the closed position, and the screw grooves with opposite rotation directions are connected to or connected to extend to the closed position; The end of the screw groove that is not in the closed position is the split position; When each pair of switching parts is engaged, part or all of the pins enter the screw groove from the open position of the screw groove corresponding to the rotation direction of the speed difference and move to the closed position; When each pair of switching parts separates, part or all of the pins move from the closed position along the screw groove in the direction corresponding to the rotation direction of the speed difference, and separate in the open position; The switching member for engaging the target route and the switching member for separating the current route are controlled by the operating mechanism to move synchronously, so that the movement of the pin engaging and the movement of the pin separating along the screw groove start and finish at the same time; The operating mechanism applies an axial force to the engaged switching member to bring the two axially closer together, and at the same time applies an axial force to the separated switching member to separate the two axially. The engaged pin enters the screw groove from the split opening to start engaging, and the separated pin leaves the screw groove from the split opening to complete separation.

2. The speed change switching mechanism according to claim 1, characterized in that: The closing position extends to the end face opening of the switching member; the engaged portion of the pin enters the switching member from the closing position opening, and the separated portion of the pin leaves the switching member from the closing position opening.

3. The speed change switching mechanism according to claim 1 or 2, characterized in that: One of the switching parts engaged with the target route and one of the switching parts separated from the current route are a common component, which is coaxial with the other two switching parts; the operating mechanism applies an axial force toward the other engaged switching part to the common component to make it move axially, approaching the other engaged switching part and leaving the other separated switching part.

4. The speed change switching mechanism according to claim 1 or 2, characterized in that: The screw groove is a variable pitch screw, and the helix angle near the closing position is smaller than the helix angle near the closing position.

5. The speed change switching mechanism according to claim 3, characterized in that: The screw groove is a variable pitch screw, and the helix angle near the closing position is smaller than the helix angle near the closing position.

6. A speed change switching mechanism, which is used in a speed change transmission device including a control mechanism and transmission routes with different speeds, and includes multiple pairs of components as switching components. The switching components are rotated by the input drive, or driven to rotate by the output, or can fix the epicyclic gear train components. Each pair of switching components of the current route remains engaged, and each pair of other switching components are separated at different speeds. The speed change switching is controlled by the control mechanism, so that one pair of the current route is separated and one pair of the target route is engaged; Each pair of switching members is coaxial, one of which is provided with at least two screw grooves with opposite rotation directions centered on the axis, and the other is provided with at least one pin that slides or rolls in cooperation with the screw groove; When each pair of switching members is kept engaged, the position of the pin in the screw groove is the closed position, and the screw grooves with opposite rotation directions are connected to or connected to extend to the closed position; The end of the screw groove that is not in the closed position is the split position; When each pair of switching parts is engaged, part or all of the pins enter the screw groove from the open position of the screw groove corresponding to the rotation direction of the speed difference and move to the closed position; When each pair of switching parts separates, part or all of the pins move from the closed position along the screw groove in the direction corresponding to the rotation direction of the speed difference, and separate in the open position; The switching member for engaging the target route and the switching member for separating the current route are controlled by the operating mechanism to move synchronously, so that the movement of the pin engaging and the movement of the pin separating along the screw groove start and finish at the same time; The characteristics of the speed change switching mechanism are as follows: the screw groove is a plane spiral, with the axis as the center point, and is arranged along the end surface of the switching member, the tangent line of the split position is perpendicular or nearly perpendicular to the radial line, and the closed position depth is greater than the screw groove depth; The pin moves radially perpendicular to the end surface of the switching member; The operating mechanism applies axial force to the engaged switching member to bring the two axially closer together, and at the same time applies axial force to the separated switching member to make the two axially separate, and synchronizes the radial movement of the engaged and separated pins. The engaged pin increases its depth when it moves to the closed position, and the separated pin decreases its depth and starts to move from the closed position.

7. The speed change switching mechanism according to claim 6, characterized in that: The switching member provided with the pin is provided with a radial slot, and a fixed connection is provided between the engaged and disengaged pins, and the pins move synchronously along the radial slot.

8. The speed change switching mechanism according to claim 6 or 7, characterized in that: The side surface of the screw groove connected to the closing position is an inclined surface, and the side surface of the opening position is an inclined surface.

9. The speed change switching mechanism according to claim 6 or 7, characterized in that: The screw groove is a variable pitch screw, and the angle between the tangent line and the radial line close to the closing position is smaller than the angle between the tangent line and the radial line close to the separation position.

10. The speed change switching mechanism according to claim 8, characterized in that: The screw groove is a variable pitch screw, and the angle between the tangent line and the radial line close to the closing position is smaller than the angle between the tangent line and the radial line close to the separation position.

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