Inertia slip meshing speed reduction type one-way clutch and control method thereof

Abstract

The invention relates to an inertia slip meshing speed reduction type one-way clutch and a control method thereof. The transmission comprises an input shaft; an inner spline matched with the involute spline is arranged in an inner hole of the spline shaft sleeve; an involute gear matched with an engine gear ring is arranged on the outer circle of the driving gear, a wedge-shaped roller path is arranged in a right inner hole of the driving gear, and a pin roller and a supporting spring are arranged in the wedge-shaped roller path; the transmission gear sleeves the periphery of the input shaft; the centrifugal mechanism generates a centrifugal effect at the moment when the transmission gear drives the spline shaft sleeve to rotate; the spacer sleeve is connected to the periphery of the second step of the input shaft in a sleeving mode, the locating cover I is connected to the periphery of the spacer sleeve in a sleeving mode, and the locating cover II is connected to the periphery of the locating cover I and the left outer circle of the driving gear in a sleeving mode; the left end of the compression spring abuts against the positioning cover I, and the right end of the compression spring abuts against the positioning cover II. The invention has the advantages of compact size, small volume and light weight, and is suitable for mass production.

Description

Technical Field

[0001] This invention relates to the field of one-way clutch technology, and in particular to an inertial slip engagement deceleration one-way clutch and its control method. Background Technology

[0002] Currently, the drive gear of the one-way clutch in an internal combustion engine starter typically moves axially by an electromagnetic switch pushing a shift fork. The shift fork then moves the one-way clutch forward, causing its drive gear to mesh with the engine ring gear, thus completing the engine start-up. This type of structure relies on an electromagnetic switch and a shift fork mechanism, resulting in a relatively complex overall structure that occupies a large space and is quite heavy.

[0003] For small internal combustion engines such as lawnmowers and yachts, the traditional one-way clutch structure is difficult to meet the requirements of lightweighting and compactness due to the strict limitations on the size and weight of the whole machine. At the same time, it puts forward higher requirements for starting stability and reliability. Summary of the Invention

[0004] Therefore, the present invention provides an inertial slip engagement deceleration one-way clutch and its control method. The one-way clutch structure uses inertial slip to achieve engagement and also has a deceleration function. It is compact, small in size, light in weight and suitable for mass production.

[0005] To solve the above-mentioned technical problems, the present invention provides an inertial slip engagement deceleration type one-way clutch, comprising: The input shaft has a first step, a second step, a third step and a fourth step formed sequentially along the axial direction. The outer periphery of the third step is provided with an involute spline. The spline bushing has an inner hole that mates with the involute spline, allowing the spline bushing to slide and transmit torque to the input shaft. The drive gear has an involute gear on its outer circumference that matches the engine ring gear. The right inner hole of the drive gear has a wedge-shaped raceway. A roller and a support spring are installed in the wedge-shaped raceway. One side of the roller is in line contact with the wedge-shaped raceway, and the other side is in line contact with the outer circumference of the left end of the spline bushing. A transmission gear is sleeved on the outer circumference of the input shaft and is used to mesh with the starter transmission mechanism and input power to the input shaft. A centrifugal mechanism is provided on the outer periphery of the right end of the splined bushing. The centrifugal mechanism generates a centrifugal force at the instant when the transmission gear drives the splined bushing to rotate. A retaining sleeve, a positioning cover I, and a positioning cover II, wherein the retaining sleeve is fitted around the outer periphery of the second step of the input shaft, the positioning cover I is fitted around the outer periphery of the retaining sleeve, and the positioning cover II is fitted around the outer periphery of the positioning cover I and the left outer circle of the drive gear; A compression spring is sleeved between the retaining sleeve, the positioning cover I, the positioning cover II, and the drive gear. The left end of the compression spring abuts against the positioning cover I, and the right end abuts against the positioning cover II, and applies a restoring force to the drive gear to make it move backward axially.

[0006] In one embodiment of the present invention, an annular groove is provided between the first step and the second step of the input shaft, and a wire retaining ring is assembled in the annular groove. The wire retaining ring is used to axially limit the retaining sleeve; a washer is sleeved on the first step. The outer circle of the retaining sleeve includes two cylindrical surfaces of different diameters. The right outer circle of the retaining sleeve is sequentially fitted into the left inner hole of the positioning cover I and the inner hole of the compression spring. The end face of the retaining sleeve abuts against the left end face of the positioning cover I.

[0007] In one embodiment of the present invention, the positioning cover I is a barrel-shaped part, the left inner hole of which is sleeved on the right outer circle of the retaining sleeve, the bottom surface of the positioning cover I abuts against the left end face of the compression spring, and the outer circle of the positioning cover I is sleeved on the left inner hole of the positioning cover II. The positioning cover II is a barrel-shaped part, with its left inner hole fitted onto the outer circle of the positioning cover I and the outer circle of the compression spring, and its right inner hole fitted onto the left outer circle of the drive gear. The right end face of the positioning cover II abuts against the stepped end face of the left outer circle of the drive gear.

[0008] In one embodiment of the present invention, the left inner hole of the drive gear is a smooth cylindrical hole and a bushing II is provided between it and the second step of the input shaft. The large outer circle of the left end of the spline bushing is in line contact with the roller, and a bushing I is provided between the left step of the inner hole of the spline bushing and the outer periphery of the second step of the input shaft.

[0009] In one embodiment of the present invention, a cover is also included. The cover is a barrel-shaped part formed by stretching sheet metal. The left inner hole of the cover is sleeved on the right outer circle of the drive gear and the outer circle of the circular insert. The cover is riveted to the inclined connecting area on the outer periphery of the drive gear by means of inward shrinkage of the extruded end, so as to achieve a fixed connection with the drive gear.

[0010] In one embodiment of the present invention, the centrifugal mechanism includes a baffle, an expansion spring, a centrifugal block and a support. The baffle and the support are respectively sleeved on the outer periphery of the right end of the splined bushing and rotate synchronously with it. The centrifugal block is disposed between the baffle and the support. The centrifuge blocks are multiple blocks of the same shape, and the multiple centrifuge blocks are arranged at intervals along the circumference; the outer periphery of the support is provided with multiple circumferentially distributed U-shaped blocks, which are used to circumferentially isolate and limit adjacent centrifuge blocks; The expansion spring is a ring structure and is sleeved on the outer periphery of the centrifugal block. It is used to apply a radially inward tightening force to the centrifugal block so that the centrifugal block is against the outer periphery of the splined bushing when the clutch is stationary.

[0011] In one embodiment of the present invention, the outer periphery of the spline bushing is provided with a polygonal mating section for installing the baffle and the bracket, and the end of the spline bushing is provided with a retaining ring groove, in which a steel retaining ring is fitted to limit the axial movement of the centrifugal mechanism.

[0012] In one embodiment of the present invention, an outer cover is further included. The inner hole of the outer cover is configured as three cylindrical hole segments with successively decreasing diameters along the axial direction. The left inner hole and the middle inner hole are sleeved on the outer circle of the centrifugal mechanism, and the right inner hole is sleeved on the outer circle of the left end of the square groove on the outer periphery of the fourth step of the input shaft. The connecting end face of the hole segment of the outer cover abuts against the end face of the step of the input shaft to achieve axial positioning.

[0013] In one embodiment of the present invention, the bottom of the outer cover is provided with a cylindrical boss, and the inner hole of the transmission gear is provided with an inner hole section that mates with the cylindrical boss. The cylindrical boss is embedded in the inner hole section to restrict the loosening and rotation of the outer cover relative to the transmission gear.

[0014] The present invention also provides a control method for an inertial slip engagement deceleration type one-way clutch, comprising: S1. After the starter is powered on, the starter transmission mechanism drives the transmission gear to rotate, causing the input shaft, which is fastened to the transmission gear, to rotate synchronously. The input shaft transmits torque to the spline sleeve through the involute spline on the outer periphery of the third step and drives the spline sleeve to rotate. S2. At the instant when the spline bushing obtains angular acceleration, the centrifugal block of the centrifugal mechanism moves radially outward under the action of centrifugal force, overcoming the radial inward tightening force of the expansion spring, thereby enhancing the inertia and rotational torque of the drive gear. S3. Under the action of the support spring, the roller enters the wedge-shaped raceway in the wedge-shaped position, thereby locking the spline bushing in one direction with the drive gear and transmitting the torque from the spline bushing to the drive gear. S4. While obtaining torque, the drive gear overcomes the restoring force of the compression spring and slides forward axially under the action of inertial slippage, meshing with the engine ring gear to drive the engine to start. S5. After the start-up is completed, the drive gear will retract axially to reset under the action of the compression spring, and the centrifugal block will return to the position of abutting the outer circumference of the splined bushing under the action of the expansion spring. S6. When the engine gear ring drives the drive gear in the opposite direction or the speed of the drive gear is higher than the speed of the spline bushing, the rollers retract to the release position in the wedge raceway, causing the drive gear to rotate relative to the spline bushing, thereby realizing unidirectional power transmission and slippage protection under reverse working conditions.

[0015] The technical solution of the present invention has the following advantages compared with the prior art: The present invention discloses an inertial sliding engagement deceleration type one-way clutch and its control method. Due to the use of a centrifugal mechanism, the starting gear is engaged by inertial sliding, which eliminates the need for a starter electromagnetic switch and shift fork mechanism, greatly reducing the size of the starter and lowering production costs.

[0016] Because the invention employs a centrifugal mechanism, during operation, the three centrifugal blocks receive centrifugal force to overcome the clamping force of the expansion spring, and move outward rapidly to enhance the inertia and rotational torque of the drive gear. The drive gear slides forward and flexibly meshes with the engine gear ring, and no tooth milling phenomenon occurs during meshing.

[0017] When the one-way clutch of this invention is stationary, the three centrifugal blocks remain firmly attached to the right outer circle of the splined bushing under the tension of the expansion spring. Because the drive gear does not gain inertia, even when propelled forward with an acceleration not exceeding 200 m / s, the drive gear will not contact the engine ring gear. This prevents the drive gear from engaging with the engine ring gear during vehicle operation, thus avoiding reverse drag and malfunction. Attached Figure Description

[0018] To make the content of this invention easier to understand, the invention will be further described in detail below with reference to specific embodiments and accompanying drawings.

[0019] Figure 1 This is a schematic diagram of the inertial slip engagement deceleration one-way clutch of the present invention.

[0020] Figure 2 This is a CC cross-sectional view of the present invention.

[0021] Figure 3 This is a schematic diagram of the expansion spring of the present invention.

[0022] Figure 4 This is a front view of the bracket of the present invention.

[0023] Figure 5 This is a side view of the bracket of the present invention.

[0024] Figure 6 This is a front view of the centrifuge block of the present invention.

[0025] Figure 7 This is a side view of the centrifuge block of the present invention.

[0026] Explanation of reference numerals on the accompanying drawings: 1. Input shaft; 2. Washer; 3. Wire retaining ring; 4. Retaining sleeve; 5. Positioning cover I; 6. Compression spring; 7. Positioning cover II; 8. Drive gear; 9. Cover; 10. Circular insert; 11. Centrifugal mechanism; 12. Outer cover; 13. Steel retaining ring; 14. Splined bushing; 15. Support spring; 16. Roller; 17. Transmission gear; 18. Bushing I; 19. Bushing II; 1101. Baffle plate; 1102. Expansion spring; 1103. Centrifugal block; 1104. Support frame; 1201. Cylindrical boss; 1701. The inner hole of the transmission gear; 8011, wedge-shaped raceway. Detailed Implementation

[0027] The present invention will be further described below with reference to the accompanying drawings and specific embodiments, so that those skilled in the art can better understand and implement the present invention. However, the embodiments described are not intended to limit the present invention.

[0028] In this invention, when directions (up, down, left, right, front, and back) are described, it is only for the convenience of describing the technical solution of this invention, and does not indicate or imply that the technical features referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this invention.

[0029] In this invention, "several" means one or more, "multiple" means two or more, "greater than," "less than," "exceeding," etc., are understood to exclude the stated number; "above," "below," "within," etc., are understood to include the stated number. In the description of this invention, the terms "first" and "second" are used only to distinguish technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0030] In this invention, unless otherwise explicitly defined, the terms "setting," "installing," and "connecting" should be interpreted broadly. For example, they can refer to a direct connection or an indirect connection through an intermediate medium; a fixed connection, a detachable connection, or an integrally formed connection; a mechanical connection, an electrical connection, or a connection capable of mutual communication; or the internal connection of two components or the interaction between two components. Those skilled in the art can reasonably determine the specific meaning of the above terms in this invention based on the specific content of the technical solution.

[0031] Reference Figure 1As shown, an inertial slip engagement deceleration type one-way clutch of the present invention includes an input shaft 1, a washer 2, a wire retaining ring 3, a retaining sleeve 4, a positioning cover I 5, a compression spring 6, a positioning cover II 7, a drive gear 8, a cover 9, a circular insert 10, a centrifugal mechanism 11, an outer cover 12, a steel sheet retaining ring 13, a spline bushing 14, a support spring 15, a roller 16, a transmission gear 17, a bushing I 18, and a bushing II 19.

[0032] Specifically, the input shaft 1 is a long shaft part, and its outer circle forms a first step, a second step, a third step, and a fourth step from left to right. The first and second steps are both smooth cylindrical surfaces, and an annular groove is provided between the first and second steps. A steel wire retaining ring 3 is embedded in the annular groove to axially limit the movement of the retaining sleeve 4. A washer 2 is fitted onto the outer circle of the first step, and the outer circle of the second step, from left to right, sequentially fits into the inner hole of the retaining sleeve 4, the inner hole of bushing II 19, and the inner hole of bushing I 18.

[0033] Specifically, the outer circle of the third step is machined with an involute spline, which mates with the involute spline in the right inner hole of the spline sleeve 14 for power transmission. The outer circle of the fourth step is a smooth cylindrical surface with a square groove in its axial center. The outer circle of the left end of the square groove fits into the inner hole of the outer cover 12 and the transmission gear 17 from left to right. The washer 2 is an annular part, and its inner hole fits into the outer circle of the first step of the input shaft 1.

[0034] Specifically, the retaining sleeve 4 is a sleeve-type part, the outer circle of which is composed of two smooth cylindrical surfaces of different diameters. The right outer circle fits into the left inner hole of the positioning cover I5 and the inner hole of the compression spring 6 from left to right. The stepped end face between the left and right outer circles abuts against the left end face of the positioning cover I5. The inner hole of the retaining sleeve 4 is composed of two cylindrical holes of different diameters. The connecting end face between the two cylindrical holes is connected to the left inner hole through a connecting arc surface, which abuts against the wire arc surface of the wire retaining ring 3.

[0035] Specifically, the positioning cover I5 is a barrel-shaped part. Its left plane abuts against the connecting end face of the left outer circle and the right outer circle of the retaining sleeve 4, its bottom plane abuts against the left end face of the compression spring 6, its left inner hole is fitted into the right outer circle of the retaining sleeve 4, its right inner hole is fitted into the outer circle of the compression spring 6, and its outer circle is fitted into the inner hole on the left side of the positioning cover II7.

[0036] Specifically, the compression spring 6 is a cylindrical helical spring, with its outer circle sleeved in the right inner hole of positioning cover I5 and the right inner hole of positioning cover II7. Its left inner hole is sleeved in the right outer circle of the retaining sleeve 4, and its right inner hole is sleeved in the left outer circle of the drive gear 8. Its left end face abuts against the bottom surface of positioning cover I5, and its right end face abuts against the bottom plane of positioning cover II7.

[0037] Specifically, the positioning cover II7 is a barrel-shaped part. Its left inner hole is fitted onto the outer circle of the positioning cover I5 and the outer circle of the compression spring 6, and its right inner hole is fitted onto the left outer circle of the drive gear 8. Its right end face abuts against the connecting end face of the left outer circle and the middle outer circle of the drive gear 8.

[0038] Reference Figure 2 As shown, the left outer circle of the drive gear 8 is a smooth cylindrical surface and is fitted into the right inner hole of the compression spring 6 and the positioning cover II 7; its middle outer circle is provided with an involute gear that matches the engine gear ring, and the right outer circle is fitted into the left inner hole of the outer cover 12 and connected to the middle outer circle through the inclined surface a. The inclined surface a and the right outer circle are connected by an arc R. The left inner hole of the drive gear 8 is a smooth cylindrical hole and is fitted into the outer circle of the bushing II 19; its right inner hole is provided with a wedge-shaped raceway 8011, and a roller 16 and a support spring 15 are provided in the wedge-shaped raceway 8011. One side of the roller 16 is in line contact with the wedge-shaped raceway 8011, and the other side is in line contact with the large outer circle of the left end of the spline bushing 14.

[0039] When the splined bushing 14 rotates toward the far end of the wedge-shaped raceway 8011 away from the center, the splined bushing 14 rotates relative to the drive gear 8, and the drive gear 8 is in a free-spinning slipping state; when the splined bushing 14 rotates toward the near end of the wedge-shaped raceway 8011 away from the center, the splined bushing 14 and the drive gear 8 are wedge-locked together by the roller 16, and the power is transmitted from the splined bushing 14 to the drive gear 8.

[0040] Specifically, the cover 9 is a barrel-shaped part formed by stretching sheet metal. Its left inner hole is fitted onto the smooth cylindrical surface of the right outer circle of the drive gear 8 and the outer circle of the circular insert 10. It is also riveted to the R-arc connecting the inclined surface a of the drive gear 8 and the right outer circle by squeezing and shrinking the end inward, thereby fixing the axial relative position of the drive gear 8, the circular insert 10, the roller 16 and the spline bushing 14.

[0041] Reference Figure 1 As shown, the centrifugal mechanism 11 consists of a baffle 1101, an expansion spring 1102, a centrifugal block 1103, and a support 1104. The baffle 1101 is a ring-shaped part with an 10-sided hole in its center consisting of 5 arcs and 5 planes, and is fitted onto the 10-sided surface of the right outer circle of the splined bushing 14.

[0042] Specifically, refer to Figure 3 , Figure 4 , Figure 6 , Figure 7As shown, the expansion spring 1102 is first wound into a cylindrical spring structure from steel wire, and then its beveled end e is inserted into the inner hole of the other end to form a ring structure, which is then fitted onto the outer circle d of the centrifugal block 1103 to apply a radially inward tightening force to the centrifugal block 1103, thereby constraining the radial movement of the centrifugal block 1103. The centrifugal block 1103 is composed of multiple (three in this embodiment) identical ring bodies, with its inner and outer circles each composed of two arc surfaces of different diameters. The three centrifugal blocks 1103 are respectively installed in the circumferential space formed by the sides of the three convex wings f of the bracket 1104 and the left end face of the baffle 1101, and are circumferentially isolated by the three U-shaped baffles g on the outer circle of the bracket 1104. The small inner hole is fitted onto the right outer circle of the spline bushing 14.

[0043] Specifically, refer to Figure 4 As shown, the outer circumference of the bracket 1104 has three semi-kidney-shaped protrusions f and three U-shaped blocks g inclined towards the center, all evenly distributed along the circumference; its bottom has an decagonal hole composed of 5 arcs and 5 planes, which fits onto the decagonal surface of the right outer circumference of the splined bushing 14. When power is transmitted from the transmission gear 17 to the splined bushing 14, the three centrifugal blocks 1103, under the action of centrifugal force, overcome the clamping force of the expansion spring 1102 and move radially outward, thereby enhancing the inertia and rotational torque of the drive gear 8. This causes the drive gear 8 to quickly overcome the thrust of the compression spring 6 and slide forward axially, engaging with the engine ring gear to start the engine. After starting, the drive gear 8 retracts under the action of the compression spring 6, the centrifugal blocks 1103 quickly reset, and the drive gear 8 stops moving axially.

[0044] Specifically, the outer cover 12 is a barrel-shaped part formed by stamping sheet metal. Its outer circle is composed of two cylindrical surfaces with different diameters. The inner hole has three cylindrical hole segments with decreasing diameters from left to right. The left inner hole and the middle inner hole are fitted onto the outer circle of the centrifugal mechanism 11, and the right inner hole is fitted onto the outer circle of the left end of the square groove of the fourth step of the input shaft 1. The connecting end face between the right inner hole and the middle inner hole abuts against the connecting end face between the third step and the fourth step of the input shaft 1. The bottom of the outer cover 12 has a cylindrical boss 1201 at the midpoint between the right inner hole and the right outer circle. The cylindrical boss 1201 is embedded in the inner hole 1701 of the transmission gear 17 to limit the loosening and rotation of the outer cover 12.

[0045] Specifically, the spline bushing 14 is a sleeve-type part. Its left end face abuts against the connecting end face of the left and right inner holes of the drive gear 8, and its right end face abuts against the connecting end face of the middle inner hole and the right inner hole of the outer cover 12. The inner hole has two steps. The left step is a smooth cylinder and fits onto the outer circle of the bushing I 18. The right step has an involute spline and slides on the involute spline of the outer circle of the third step of the input shaft 1. The outer circle has two steps. The left step is a cylindrical surface and makes line contact with the roller 16. The right step has an decagonal hole composed of 5 arcs and 5 planes. From left to right, the centrifugal mechanism 11 baffle 1101, centrifugal block 1103 and bracket 1104 are fitted. The end has a retaining ring groove. A steel retaining ring 13 is inlaid in the groove. The left end face of the steel retaining ring 13 abuts against the connecting end face of the inner hole of the bracket 1104 of the centrifugal mechanism 11. The axial movement of the centrifugal mechanism 11, including the baffle 1101, centrifugal block 1103, and support 1104, is constrained.

[0046] Specifically, the outer circle of the transmission gear 17 is provided with an involute gear that meshes with the starter transmission mechanism. Its inner hole is a smooth cylindrical hole. During assembly, the transmission gear 17 is first heated to 400°C to 500°C, and then fastened to the left outer circle of the retaining ring groove on the fourth step of the input shaft 1 by means of thermal expansion and contraction. Its inner hole has an inner hole section in the middle, which is used to cooperate with the cylindrical boss 1201 on the bottom of the outer cover 12.

[0047] The working principle of the one-way clutch of the present invention is as follows: When the starter is powered on and the rotor rotates, the power is transmitted from the transmission gear 17 to the spline bushing 14 at the instant. The centrifugal block 1103 of the centrifugal mechanism 11 receives centrifugal force, overcomes the fastening force of the expansion spring 1102, and moves outward rapidly to enhance the inertia and rotational torque of the drive gear 8. This causes the drive gear 8 to quickly overcome the thrust of the compression spring 6 and rotate forward to engage with the engine ring gear to start the engine. After the starter is powered off, the drive gear 8 retracts under the elastic force of the compression spring 6, and the centrifugal block 1103 quickly resets, thus ending one start.

[0048] The specific control process is as follows: S1. After the starter is powered on, the starter transmission mechanism drives the transmission gear 17 to rotate, causing the input shaft 1, which is fastened to the transmission gear 17, to rotate synchronously. The input shaft 1 transmits torque to the spline sleeve 14 through the involute spline on the outer periphery of the third step and drives the spline sleeve 14 to rotate. S2. At the instant when the spline bushing 14 obtains angular acceleration, the centrifugal block 1103 of the centrifugal mechanism 11 moves radially outward under the action of centrifugal force, overcoming the radial inward tightening force of the expansion spring 1102, thereby enhancing the inertia and rotational torque of the drive gear 8. S3, under the action of the support spring 15, the roller 16 enters the wedge position of the wedge raceway 8011, thereby locking the spline bushing 14 and the drive gear 8 in one direction and transmitting the torque from the spline bushing 14 to the drive gear 8. S4, while obtaining torque, the drive gear 8 overcomes the restoring force of the compression spring 6 and slides forward along the axis under the action of inertial slippage, meshing with the engine ring gear to drive the engine to start; S5. After the start-up is completed, the drive gear 8 will retract and reset along the axial direction under the action of the compression spring 6, and the centrifugal block 1103 will return to the position of abutting the outer periphery of the spline bushing 14 under the action of the expansion spring 1102. S6. When the engine gear ring drives the drive gear 8 in the opposite direction or the speed of the drive gear 8 is higher than the speed of the spline bushing 14, the roller 16 retracts to the release position in the wedge raceway 8011, causing the drive gear 8 to rotate freely relative to the spline bushing 14, thereby realizing unidirectional power transmission and slippage protection under reverse working conditions.

[0049] Finally, it should be noted that the above specific embodiments are only used to illustrate the technical solutions of the present invention and not to limit it. Although the present invention has been described in detail with reference to examples, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. An inertial slip engagement reduction type one-way clutch, characterized in that, include: The input shaft (1) has a first step, a second step, a third step and a fourth step formed sequentially along the axial direction. The third step is provided with an involute spline on its outer periphery. Spline bushing (14), the inner hole of the spline bushing (14) is provided with an internal spline that matches the involute spline, so that the spline bushing (14) and the input shaft (1) can be slidably connected and transmit torque. The drive gear (8) has an involute gear on its outer circle that matches the engine ring gear. The right inner hole of the drive gear (8) has a wedge-shaped raceway (8011). A roller (16) and a support spring (15) are provided in the wedge-shaped raceway (8011). One side of the roller (16) is in line contact with the wedge-shaped raceway (8011), and the other side is in line contact with the outer circle of the left end of the spline bushing (14). A transmission gear (17) is sleeved on the outer circumference of the input shaft (1) and is used to mesh with the starter transmission mechanism and input power to the input shaft (1); Centrifugal mechanism (11) is located on the outer periphery of the right end of the spline bushing (14). The centrifugal mechanism (11) generates centrifugal force at the instant when the transmission gear (17) drives the spline bushing (14) to rotate. The retaining sleeve (4), the positioning cover I (5) and the positioning cover II (7) are provided, wherein the retaining sleeve (4) is sleeved on the outer periphery of the second step of the input shaft (1), the positioning cover I (5) is sleeved on the outer periphery of the retaining sleeve (4), and the positioning cover II (7) is sleeved on the outer periphery of the positioning cover I (5) and the left outer circle of the drive gear (8). A compression spring (6) is sleeved between the retaining sleeve (4), the positioning cover I (5), the positioning cover II (7) and the drive gear (8). The left end of the compression spring (6) abuts against the positioning cover I (5) and the right end abuts against the positioning cover II (7), and applies a restoring force to the drive gear (8) to make it move backward axially.

2. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, An annular groove is provided between the first step and the second step of the input shaft (1), and a wire retaining ring (3) is installed in the annular groove. The wire retaining ring (3) is used to axially limit the retaining sleeve (4); a washer (2) is sleeved on the first step. The outer circle of the retainer (4) includes two cylindrical surfaces of different diameters. The right outer circle of the retainer (4) is sequentially fitted into the left inner hole of the positioning cover I (5) and the inner hole of the compression spring (6). The end face of the retainer (4) abuts against the left end face of the positioning cover I (5).

3. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, The positioning cover I (5) is a barrel-shaped part, and its left inner hole is fitted into the right outer circle of the retainer (4). The bottom surface of the positioning cover I (5) abuts against the left end face of the compression spring (6). The outer circle of the positioning cover I (5) is fitted into the left inner hole of the positioning cover II (7). The positioning cover II (7) is a barrel-shaped part. Its left inner hole is sleeved on the outer circle of the positioning cover I (5) and the outer circle of the compression spring (6). Its right inner hole is sleeved on the left outer circle of the drive gear (8). The right end face of the positioning cover II (7) abuts against the stepped end face of the left outer circle of the drive gear (8).

4. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, The left inner hole of the drive gear (8) is a smooth cylindrical hole and a bushing II (19) is provided between it and the second step of the input shaft (1). The large outer circle of the left end of the spline bushing (14) is in line contact with the roller (16), and a bushing I (18) is provided between the left step of the inner hole of the spline bushing (14) and the outer periphery of the second step of the input shaft (1).

5. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, It also includes a cover (9), which is a barrel-shaped part formed by stretching sheet metal. The left inner hole of the cover (9) is sleeved on the right outer circle of the drive gear (8) and the outer circle of the circular insert (10). The cover (9) is riveted to the inclined connection area of ​​the outer periphery of the drive gear (8) by shrinking the extruded end inward, so as to achieve a fixed connection with the drive gear (8).

6. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, The centrifugal mechanism (11) includes a baffle (1101), an expansion spring (1102), a centrifugal block (1103), and a support (1104). The baffle (1101) and the support (1104) are respectively sleeved on the outer periphery of the right end of the spline bushing (14) and rotate synchronously with it. The centrifugal block (1103) is disposed between the baffle (1101) and the support (1104). The centrifuge block (1103) consists of multiple blocks of the same shape, and the multiple centrifuge blocks (1103) are arranged at intervals along the circumference; the support (1104) is provided with multiple circumferentially distributed U-shaped blocks on its outer periphery, and the U-shaped blocks are used to circumferentially isolate and limit adjacent centrifuge blocks (1103); The expansion spring (1102) is a ring structure and is sleeved on the outer periphery of the centrifugal block (1103). It is used to apply a radially inward tightening force to the centrifugal block (1103) so that when the clutch is stationary, the centrifugal block (1103) is against the outer periphery of the spline bushing (14).

7. The inertial slip engagement reduction type one-way clutch according to claim 6, characterized in that, The outer periphery of the spline bushing (14) is provided with a polygonal mating section for installing the baffle (1101) and the bracket (1104). The end of the spline bushing (14) is provided with a retaining ring groove, and a steel retaining ring (13) is fitted in the retaining ring groove to axially limit the centrifugal mechanism (11).

8. The inertial slip engagement reduction type one-way clutch according to claim 1, characterized in that, It also includes an outer cover (12), the inner hole of which is set as three cylindrical hole segments with successively smaller diameters along the axial direction. The left inner hole and the middle inner hole are sleeved on the outer circle of the centrifugal mechanism (11), and the right inner hole is sleeved on the outer circle of the left end of the square groove on the outer periphery of the fourth step of the input shaft (1). The connecting end face of the hole segment of the outer cover (12) abuts against the step end face of the input shaft (1) to achieve axial positioning.

9. The inertial slip engagement reduction type one-way clutch according to claim 8, characterized in that, The bottom of the outer cover (12) is provided with a cylindrical boss (1201), and the inner hole (1701) of the transmission gear is provided with an inner hole section that cooperates with the cylindrical boss (1201). The cylindrical boss (1201) is embedded in the inner hole section to restrict the loosening and rotation of the outer cover (12) relative to the transmission gear (17).

10. A control method for an inertial slip engagement deceleration one-way clutch according to any one of claims 1-9, characterized in that, include: S1. After the starter is powered on, the starter transmission mechanism drives the transmission gear (17) to rotate, causing the input shaft (1) which is fastened to the transmission gear (17) to rotate synchronously. The input shaft (1) transmits torque to the spline sleeve (14) through the involute spline on the outer periphery of the third step and drives the spline sleeve (14) to rotate. S2. At the instant when the spline bushing (14) obtains angular acceleration, the centrifugal block (1103) of the centrifugal mechanism (11) moves radially outward under the action of centrifugal force, overcoming the radial inward tightening force of the expansion spring (1102), thereby enhancing the inertia and rotational torque of the drive gear (8). S3. The roller (16) enters the wedge position of the wedge raceway (8011) under the action of the support spring (15), thereby locking the spline bushing (14) and the drive gear (8) in one direction and transmitting the torque from the spline bushing (14) to the drive gear (8). S4. While obtaining torque, the drive gear (8) overcomes the restoring force of the compression spring (6) and slides forward along the axis under the action of inertial slippage, meshing with the engine ring gear to drive the engine to start. S5. After the start-up is completed, the drive gear (8) is retracted and reset along the axial direction under the action of the compression spring (6), and the centrifugal block (1103) returns to the position of abutting the outer periphery of the spline bushing (14) under the action of the expansion spring (1102). S6. When the engine gear ring drives the drive gear (8) in the opposite direction or the speed of the drive gear (8) is higher than the speed of the spline bushing (14), the roller (16) retracts to the release position in the wedge raceway (8011), so that the drive gear (8) rotates relative to the spline bushing (14) in the freewheeling position, thereby realizing unidirectional power transmission and slippage protection under reverse working conditions.

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