A purely mechanical automatic transmission device
By using a purely mechanical automatic transmission device, which utilizes a clutch and ratchet structure to achieve automatic gear shifting in electric vehicles, the problems of high cost and poor stability of electronically controlled automatic transmissions are solved, achieving low-cost, stable and efficient gear shifting function.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- JIANGSU JINPENG GRP CO LTD
- Filing Date
- 2022-07-28
- Publication Date
- 2026-06-02
AI Technical Summary
Existing electronically controlled automatic transmissions are expensive, have poor versatility, and are not very stable, making them difficult to widely promote in electric vehicles.
It adopts a purely mechanical automatic transmission device, including a primary input shaft assembly, a secondary shaft assembly and a differential. Gear shifting and power transmission are achieved through meshing connections. The transmission function is realized by using a clutch, a sling and a ratchet structure to avoid friction loss and gear slippage.
It achieves automatic gear shifting at any vehicle speed, has a long service life, a simple and compact structure, and can replace electronically controlled automatic transmission systems, reducing costs and improving stability.
Smart Images
Figure CN115539607B_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of gearbox technology, specifically to a purely mechanical automatic transmission device. Background Technology
[0002] Electric vehicles are driven by electric motors. Given the complex and varied road conditions, a multi-speed gearbox is needed to maximize the motor's output. Currently, most automatic gearboxes on the market are electronically controlled automatic gearboxes. The gear-shifting actuators in electronically controlled automatic gearboxes typically include motors or electromagnetic coils, and they require controllers and sensors to function as an automatic transmission system. This necessitates that the automatic gearbox itself have its own matching motor and controller, resulting in poor versatility. Furthermore, the required sensors and actuators are expensive, and the control process is not very stable, limiting its widespread adoption. This paper proposes a low-cost, purely mechanical automatic gearbox with the same gear-shifting function as electronically controlled gearboxes, while also being compatible with various types of controllers and motors. Summary of the Invention
[0003] The purpose of this invention is to provide a purely mechanical automatic transmission device to solve the problems mentioned in the background art.
[0004] To achieve the above objectives, the present invention provides the following technical solution: a purely mechanical automatic transmission device, comprising a primary input shaft assembly, a secondary shaft assembly, and a differential, wherein the primary input shaft assembly is meshed with the secondary shaft assembly, and the secondary shaft assembly is meshed with the differential; the primary input shaft assembly is used to realize gear switching, and the secondary shaft assembly is used to realize non-interference in power transmission between high, low, and reverse gears.
[0005] Preferably, the primary input shaft assembly includes a primary shaft, on which a base is mounted via a spline. The base is provided with multiple main swing blocks, each main swing block having a tension spring lug, a main swing block inclined surface, and a tension spring. The multiple main swing blocks are connected by tension springs. The base is provided with a guide surface that restricts the movement direction of the main swing blocks.
[0006] Preferably, a clutch housing is installed on the outer side of the base, and the clutch housing is provided with a minimum limiting surface, a guide block and a maximum limiting surface.
[0007] Preferably, the clutch housing is equipped with a secondary swing block and is covered by a clutch end cover to ensure that the secondary swing block moves radially along the circumference. The secondary swing block is composed of several uniform fan-shaped blocks forming a complete circle. The secondary swing block is provided with a secondary swing block limiting surface, a secondary swing block guide groove, an O-type spring groove and a limiting surface. An O-type spring is installed in the O-type spring groove.
[0008] Preferably, a pusher is provided on one side of the main throwing block, and the pusher is provided with an inclined block and a ring block. The inclined surface of the inclined block is in contact with the inclined surface of the main throwing block, and the bottom surface of the ring block is in contact with the restricting surface when the secondary throwing block is not opened.
[0009] Preferably, the diameter of the outer circle of the ring block is larger than the diameter of its inner circle when the secondary swing block is closed.
[0010] Preferably, a low-speed drive gear is mounted on the primary shaft, a high-speed drive gear is slidably connected to the primary shaft, a guide cylinder is connected to the primary shaft via a spline, a single-sided gear of a toothed clutch is slidably connected to the guide cylinder via a tooth groove, the high-speed drive gear is provided with a single-sided gear adapted to the single-sided gear of the toothed clutch, and a first compression spring is provided between the high-speed drive gear and the single-sided gear of the toothed clutch.
[0011] Preferably, the secondary shaft assembly includes a secondary shaft, on which a high-speed driven gear, an output gear, an overrunning ratchet, and a reverse ratchet are mounted, and a low-speed driven gear is slidably connected to the secondary shaft.
[0012] Preferably, the low-speed driven gear is provided with a slanted groove and a double-sided ratchet is slidably connected through the slanted groove. A second compression spring is installed on one side of the double-sided ratchet. The low-speed driven gear has uniform holes. The slanted teeth on the other side of the double-sided ratchet pass through the holes on the low-speed driven gear and mesh with the overrunning ratchet under the elastic force of the second compression spring.
[0013] Preferably, the double-sided ratchet is provided with a double-sided ratchet overrunning tooth, a retaining ring groove, and a double-sided ratchet reverse tooth. A reverse drive ring is installed inside the retaining ring groove, and the two can slide when subjected to a certain external force.
[0014] Compared with the prior art, the beneficial effects of the present invention are:
[0015] 1. It can upshift and downshift at any set (reasonably required) speed;
[0016] 2. Used in transmission systems, it enables active gear shifting;
[0017] 3. Long service life; it does not rely on centrifugal friction to transmit torque, so there is no friction loss.
[0018] 4. The automatic transmission body has a simple, compact, and small overall structure;
[0019] 5. It will not slip out of gear;
[0020] 6. The design values for upshifting and downshifting are different, so there will be no repeated upshifting or downshifting.
[0021] 7. The clutch within it can achieve high torque transmission;
[0022] 8. The main alternative to electronically controlled automatic transmission systems. Attached Figure Description
[0023] Figure 1 This is a schematic diagram of the structure of the present invention;
[0024] Figure 2 This is a schematic diagram of the structure of the first-stage input shaft assembly of the present invention;
[0025] Figure 3 This is a schematic diagram of the main throwing block of the present invention;
[0026] Figure 4 This is a schematic diagram of the structure of the secondary throwing block of the present invention;
[0027] Figure 5 This is a schematic diagram of the clutch housing of the present invention;
[0028] Figure 6 This is a schematic diagram of the structure of the pusher component of the present invention;
[0029] Figure 7 This is a schematic diagram of the structure of the two-stage shaft assembly of the present invention;
[0030] Figure 8 This is a schematic diagram of the structure of the double-sided ratchet of the present invention.
[0031] In the diagram: 1. Primary input shaft assembly; 102. Base; 1021. Guide surface; 103. Tension spring; 104. Main throwing block; 1041. Tension spring lug; 1042. Main throwing block inclined surface; 105. Clutch housing; 1051. Minimum limit surface; 1052. Guide block; 1053. Maximum limit surface; 106. Pushing component; 1061. Inclined block; 1062. Circular block; 107. O-ring spring; 108. Secondary throwing block; 1081. Secondary throwing block limiting surface; 1082. Secondary throwing block guide groove; 1083. O-ring spring groove; 1084. Restricting surface; 109. Tooth clutch. 1. Clutch single-sided gear; 110. Guide cylinder; 111. First compression spring; 112. Clutch end cover; 113. High-speed drive gear; 114. Primary shaft; 115. Low-speed drive gear; 2. Secondary shaft assembly; 201. High-speed driven gear; 202. Output gear; 203. Secondary shaft; 204. Overtaking ratchet; 205. Low-speed driven gear; 206. Reverse drive ring; 207. Double-sided ratchet; 2071. Double-sided ratchet overtaking tooth; 2072. Snap ring groove; 2073. Double-sided ratchet reverse tooth; 208. Second compression spring; 209. Reverse ratchet; 3. Differential. Detailed Implementation
[0032] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Example
[0033] Please see Figure 1-8 The present invention provides a technical solution: a purely mechanical automatic transmission device, including a primary input shaft assembly 1, a secondary shaft assembly 2 and a differential 3. The primary input shaft assembly 1 is meshed with the secondary shaft assembly 2, and the secondary shaft assembly 2 is meshed with the differential 3. The primary input shaft assembly 1 is used to realize gear switching, and the secondary shaft assembly 2 is used to realize high, low and reverse gear power transmission without interference.
[0034] like Figure 2 and Figure 3 As shown: The primary input shaft assembly 1 includes a primary shaft 114. A base 102 is mounted on the primary shaft 114 via a spline, so the base 102 will rotate with the primary shaft 114. The base 102 is provided with multiple main swing blocks 104. Each main swing block 104 is provided with a tension spring lug 1041, a main swing block inclined surface 1042, and a tension spring 103. The multiple main swing blocks 104 are connected by the tension spring 103. The base 102 is provided with a guide surface 1021 that restricts the movement direction of the main swing blocks 104 to ensure that the main swing blocks 104 move in a straight line.
[0035] like Figure 2 and Figure 5 As shown: A clutch housing 105 is installed on the outer side of the base 102. The clutch housing 105 is provided with a minimum limiting surface 1051, a guide block 1052 and a maximum limiting surface 1053, which can limit the movement direction and displacement of the auxiliary throwing block 108.
[0036] like Figure 2 and Figure 4 As shown: A secondary sling block 108 is installed on the clutch housing 105 and is covered by the clutch end cover 112 to ensure that the secondary sling block 108 moves radially along the circumference. The secondary sling block 108 is composed of several uniform fan-shaped blocks forming a complete circle. The secondary sling block 108 is provided with a secondary sling block limiting surface 1081, a secondary sling block guide groove 1082, an O-type spring groove 1083 and a limiting surface 1084. An O-type spring 107 is installed in the O-type spring groove 1083.
[0037] like Figure 2 and Figure 6 As shown: A pusher 106 is provided on one side of the main throwing block 104. The pusher 106 is provided with an inclined block 1061 and a ring block 1062. The inclined surface of the inclined block 1061 is in contact with the inclined surface 1042 of the main throwing block. The bottom surface of the ring block 1062 is in contact with the limiting surface 1084 when the secondary throwing block 108 is not opened.
[0038] like Figure 2As shown: the diameter of the outer circle of the ring block 1062 is larger than the diameter of its inner circle when the secondary swing block 108 is closed.
[0039] like Figure 2 As shown: A low-speed drive gear 115 is mounted on the primary shaft 114, and a high-speed drive gear 113 is slidably connected to the primary shaft 114. A guide cylinder 110 is connected to the primary shaft 114 via a spline, so the guide cylinder 110 will rotate with the primary shaft 114. A single-sided gear 109 of a dog clutch is slidably connected to the guide cylinder 110 via a tooth groove. The high-speed drive gear 113 is provided with a single-sided gear adapted to the single-sided gear 109 of the dog clutch. A first compression spring 111 is provided between the high-speed drive gear 113 and the single-sided gear 109 of the dog clutch.
[0040] like Figure 7 As shown: The secondary shaft assembly 2 includes a secondary shaft 203, on which a high-speed driven gear 201, an output gear 202, an overrunning ratchet 204 and a reverse ratchet 209 are mounted, and a low-speed driven gear 205 is slidably connected to the secondary shaft 203.
[0041] like Figure 7 and Figure 8 As shown: The low-speed driven gear 205 is provided with a slanted groove and a double-sided ratchet 207 is slidably connected through the slanted groove. A second compression spring 208 is installed on one side of the double-sided ratchet 207. The low-speed driven gear 205 has uniform holes. The helical teeth on the other side of the double-sided ratchet 207 pass through the holes on the low-speed driven gear 205 and mesh with the overrunning ratchet 204 under the elastic force of the second compression spring 208. This structure enables the low-speed driven gear 205 to rotate unidirectionally on the secondary shaft 203.
[0042] like Figure 7 and Figure 8 As shown: The double-sided ratchet 207 is provided with a double-sided ratchet overrunning tooth 2071, a retaining ring groove 2072, and a double-sided ratchet reverse tooth 2073. A reverse drive ring 206 is installed inside the retaining ring groove 2072. The two can slide when subjected to a certain external force.
[0043] Working principle:
[0044] The primary shaft 114 will rotate as driven by the motor and will rotate at the same speed as the motor. Here, it is assumed that the primary shaft 114 rotates counterclockwise as the forward gear and clockwise as the reverse gear.
[0045] When the motor speed is below 3000 rpm, the centrifugal force on the auxiliary throwing block 108 is small and insufficient to overcome the compression force given by the O-type spring 107. The auxiliary throwing block 108 is in a closed state and will block the pusher 106 from moving axially, causing the single-sided gear 109 of the jaw clutch and the single-sided gear on the high-speed drive gear 113 to disconnect.
[0046] When the motor speed is higher than 3000 rpm, the auxiliary sling block 108 is in the open state, and the pusher 106 is unobstructed. Because the pusher 106 is pushed by the main sling block 104, it will move axially and push the single-sided gear 109 of the jaw clutch to move. The single-sided gear 109 of the jaw clutch overcomes the compression force of the first compression spring 111 and slides obliquely on the guide cylinder 110 until the single-sided gear 109 of the jaw clutch meshes with the single-sided gear on the high-speed drive gear 113, realizing the low speed gear to high speed gear.
[0047] Once the high-speed gear is engaged, the motor will not downshift when the motor speed is below 3000 rpm. Only when the motor speed is below 2000 rpm will the main swing block 104 move towards the axis because the centrifugal force on the main swing block 104 is insufficient to overcome the tension of the tension spring 103. At this time, the pusher 106 will no longer have the thrust of the main swing block 104 on one side, but will have the tension of the first compression spring 111 on the other side. Therefore, the pusher 106 and the single-sided gear 109 of the jaw clutch will return to the initial position.
[0048] Work process description
[0049] In the initial stage: the motor drives the wheels at low speed, the active shifting clutch is not closed, and the power transmission process is that the low-speed driving gear 115 transmits to the low-speed driven gear 205. The low-speed driven gear 205 will drive the double-sided ratchet 207 to rotate. The double-sided ratchet 207 drives the overtaking ratchet 204 to rotate. Since the overtaking ratchet 204 and the output gear 202 are both fixedly connected to the secondary shaft 203, the output gear 202 transmits power to the differential 3, and the vehicle travels at low speed.
[0050] Acceleration Phase: After the vehicle starts, the motor speed increases until it reaches 3000 rpm. At this point, the active shift clutch engages, and the power transmission process is as follows: the first-stage shaft 114 rotates, driving the guide cylinder 110. The guide cylinder 110 rotates, driving the single-sided gear 109 of the jaw clutch. The single-sided gear 109 of the jaw clutch rotates, driving the high-speed drive gear 113. The high-speed drive gear 113 rotates, driving the high-speed driven gear 201. At this time, both the high-speed driven gear 201 and the low-speed driven gear 205 rotate clockwise. Due to the different speed ratios, the speed of the high-speed driven gear 201 is higher than that of the low-speed driven gear 205. Because of the overtaking structure between the ratchet 204, the low-speed driven gear 205, and the double-sided ratchet 207, the effective power transmission at this time is through the high-speed driven gear 201. The power is transmitted to the output gear 202, which then transmits the power to the differential 3. The vehicle accelerates and maintains the high-speed gear.
[0051] Deceleration phase: When the driver releases the throttle / applies the brake / climbs a hill with a full load, the motor speed decreases until it drops to 2000 rpm. At this point, the active shifting clutch disengages, and the gear shifts from a high gear to a low gear.
[0052] In reverse gear mode: The motor rotates clockwise at low speed, and the power is transmitted from the low-speed drive gear 115 to the low-speed driven gear 205. The low-speed driven gear 205 rotates counterclockwise, which drives the double-sided ratchet 207 and the reverse gear drive ring 206 to rotate counterclockwise together. In the structure of the gearbox, there is a reinforcing rib to prevent the reverse gear drive ring 206 from rotating counterclockwise. At this time, the double-sided ratchet 207 is driven by the reverse gear drive ring 206 to have a reverse motion force. The double-sided ratchet 207 overcomes the elastic force of the compression spring 208 and slides along the inclined groove on the low-speed driven gear 205 towards the reverse gear ratchet 209 until the two mesh. The power is transmitted sequentially through the low-speed driven gear 205, the double-sided ratchet 207, the reverse gear ratchet 209, the secondary shaft 203, the output gear 202, and the differential 3, and the vehicle moves in reverse at low speed.
[0053] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.
Claims
1. A purely mechanical automatic transmission device, comprising a primary input shaft assembly (1), a secondary shaft assembly (2), and a differential (3), characterized in that: The first-stage input shaft assembly (1) is meshed with the second-stage shaft assembly (2), and the second-stage shaft assembly (2) is meshed with the differential (3). The first-stage input shaft assembly (1) is used to realize gear switching, and the second-stage shaft assembly (2) is used to realize high, low, and reverse gear power transmission without interference. The primary input shaft assembly (1) includes a primary shaft (114), on which a base (102) is mounted via a spline. The base (102) is provided with multiple main swing blocks (104), and each main swing block (104) is provided with a tension spring lug (1041), a main swing block inclined surface (1042), and a tension spring (103). The multiple main swing blocks (104) are connected by the tension spring (103). The base (102) is provided with a guide surface (1021) that restricts the movement direction of the main swing blocks (104).
2. The purely mechanical automatic transmission device according to claim 1, characterized in that: A clutch housing (105) is installed on the outside of the base (102), and the clutch housing (105) is provided with a minimum limiting surface (1051), a guide block (1052) and a maximum limiting surface (1053).
3. The purely mechanical automatic transmission device according to claim 2, characterized in that: The clutch housing (105) is equipped with a secondary sling block (108) and is covered by the clutch end cover (112) to ensure that the secondary sling block (108) moves radially along the circumference. The secondary sling block (108) is composed of several uniform fan-shaped blocks forming a complete circle. The secondary sling block (108) is provided with a secondary sling block limiting surface (1081), a secondary sling block guide groove (1082), an O-type spring groove (1083) and a limiting surface (1084). An O-type spring (107) is installed in the O-type spring groove (1083).
4. The purely mechanical automatic transmission device according to claim 1, characterized in that: The main throwing block (104) has a pusher (106) on one side. The pusher (106) has an inclined block (1061) and a ring block (1062). The inclined surface of the inclined block (1061) is in contact with the inclined surface (1042) of the main throwing block. The bottom surface of the ring block (1062) is in contact with the limiting surface (1084) when the secondary throwing block (108) is not opened.
5. The purely mechanical automatic transmission device according to claim 4, characterized in that: The diameter of the outer circle of the ring block (1062) is larger than the diameter of its inner circle when the secondary swing block (108) is closed.
6. The purely mechanical automatic transmission device according to claim 1, characterized in that: A low-speed drive gear (115) is mounted on the primary shaft (114). A high-speed drive gear (113) is slidably connected to the primary shaft (114). A guide cylinder (110) is connected to the primary shaft (114) via a spline. A single-sided gear (109) of a toothed clutch is slidably connected to the guide cylinder (110) via a tooth groove. A single-sided gear adapted to the single-sided gear (109) of the toothed clutch is provided on the high-speed drive gear (113). A first compression spring (111) is provided between the high-speed drive gear (113) and the single-sided gear (109) of the toothed clutch.
7. The purely mechanical automatic transmission device according to claim 1, characterized in that: The secondary shaft assembly (2) includes a secondary shaft (203), on which a high-speed driven gear (201), an output gear (202), an overrunning ratchet (204), and a reverse ratchet (209) are mounted, and a low-speed driven gear (205) is slidably connected.
8. A purely mechanical automatic transmission device according to claim 7, characterized in that: The low-speed driven gear (205) is provided with a slanted groove and a double-sided ratchet (207) is slidably connected through the slanted groove. A second compression spring (208) is installed on one side of the double-sided ratchet (207). The low-speed driven gear (205) has uniform holes. The helical teeth on the other side of the double-sided ratchet (207) pass through the holes on the low-speed driven gear (205) and mesh with the overrunning ratchet (204) under the elastic force of the second compression spring (208).
9. A purely mechanical automatic transmission device according to claim 8, characterized in that: The double-sided ratchet (207) is provided with a double-sided ratchet overrunning tooth (2071), a retaining ring groove (2072), and a double-sided ratchet reverse gear tooth (2073). A reverse drive ring (206) is installed inside the retaining ring groove (2072), and the two can slide when subjected to a certain external force.