Multi-gear transmission with multi-connected planet wheels matched with multi-gear ring structure and working method of multi-gear transmission

Abstract

The invention relates to a multi-gear transmission with a multi-linkage planet gear matched with a multi-gear ring structure and a working method thereof.The multi-gear transmission with the multi-linkage planet gear matched with the multi-gear ring structure comprises an input shaft, a sun gear fixedly arranged in the middle of the input shaft and an input shaft gear fixedly arranged at the end of the input shaft, and the sun gear is meshed with the multi-linkage planet gear; a first gear, a second gear and a third gear which are coaxially and fixedly arranged in sequence and are different in diameter are arranged on the multi-connection planet wheel, the third gear is in meshing transmission with the sun wheel, and the first gear, the second gear and the third gear are meshed with inner teeth of the gear ring A, the gear ring B and the gear ring C correspondingly; outer teeth of the gear ring A, the gear ring B and the gear ring C are respectively meshed with a gear ring control gear a, a gear ring control gear b and a gear ring control gear c which can be selectively stopped; according to the device, only one planet row is used, and the requirement for multi-gear variable speed transmission is met with few elements and small size and weight.

Description

Technical Field

[0002] The invention relates to a multi-speed transmission with a multi-connected planetary gear and multi-gear ring structure and a working method thereof. Background Art

[0004] In a speed transmission constructed with planetary gears, there are three elements on a planetary row. By controlling the states of two of the elements, two different transmission ratios can be obtained. If more than two transmission ratios are to be obtained, multiple planetary rows must be combined and configured; therefore, a multi-speed transmission generally contains multiple planetary rows; although multiple planetary rows can be simplified by using a common sun gear or a common planetary carrier, their essence is still a combination of multiple planetary rows, so the existing planetary structure multi-speed transmission still has many gear parts.

[0005] A Chinese patent has been retrieved so far, the invention name: power-shifted multi-speed transmission, announcement number CN101275630B, including a plurality of gear transmissions and a plurality of shifting elements. The transmission includes two parallel shaft systems, the two parallel shaft systems include three planetary rows, each shaft system contains at least one planetary row, each planetary row includes a sun gear, a ring gear and a planetary carrier with a plurality of planetary gears, and the planetary rows are arranged on the two shaft systems. Although a short transmission length can be obtained, the overall design can be made more compact; however, the multi-speed transmission still has a large number of gear parts.

[0006] And the Chinese patent retrieved so far, the invention name: multi-speed automatic transmission, publication number CN105443685B, including a first shaft system WS1, a second shaft system WS2, a first fixed shaft gear set TG69, a second fixed shaft gear set TG56, a third fixed shaft gear set TG17, a first planetary gear set PG1, a second planetary gear set PG2, a third planetary gear set PG3 and 6 shift elements, namely a first brake B1, a second brake B2, a first clutch C1, a second clutch C2, a third clutch C3, and a fourth clutch C4; power is input from the first shaft system WS1, output to the differential Diff through the second shaft system WS2, and then transmitted to the wheels on both sides through the output ends of the differential; the first shaft system and the second shaft system are arranged in parallel, although it is suitable for front-engine front-wheel drive vehicles; the structure is compact, which makes the vehicle shift response faster, but the multi-speed transmission still has more gear parts. Summary of the invention

[0008] In view of the deficiencies of the above-mentioned existing technologies, an object of the present invention is to provide a multi-speed transmission with a multi-coupled planetary gear and a multi-ring gear structure and a working method thereof. The multi-speed transmission with a multi-coupled planetary gear and a multi-ring gear structure and a working method thereof are reasonably designed, which is conducive to reducing the number of gear parts of the planetary structure multi-speed transmission.

[0009] The present invention discloses a multi-speed transmission with a multi-link planetary gear and multi-gear ring structure, characterized in that it comprises an input shaft, a sun gear fixedly arranged on the middle of the input shaft, and an input shaft gear fixedly arranged on the end of the input shaft, wherein the sun gear meshes with a multi-link planetary gear, and the multi-link planetary gear has a first gear, a second gear, and a third gear coaxially fixedly arranged in sequence but with different diameters, wherein the third gear meshes with the sun gear for transmission, and the first gear, the second gear, and the third gear mesh with the internal teeth of the gear ring A, the gear ring B, and the gear ring C, respectively, and the gear rings are connected to the first gear, the second gear, and the third gear. The outer teeth of ring A, ring B and ring C are respectively meshed with the ring control gear a, ring control gear b and ring control gear c which can be selectively stopped to achieve the stopping of ring A, ring B or ring C; the input shaft is coaxially provided with an unconnected output shaft, the output shaft is fixedly provided with an output shaft gear, the outer sleeve of the output shaft gear is provided with a coupling sleeve which can rotate coaxially and slide axially, and the side of the coupling sleeve is provided with an inner ring which can selectively mesh with the input shaft gear or the planetary carrier gear on the multi-jointed planetary gear.

[0010] Preferably, the above-mentioned ring gear control gear a, ring gear control gear b and ring gear control gear c are meshed and connected to the fixed shaft with an empty sleeve, and a stopping hub fixed on the fixed shaft and a sliding sleeve provided on the stopping hub are provided on the side of the ring gear control gear a, ring gear control gear b and ring gear control gear c. After axial movement, different sliding sleeves engage with the stopping teeth on the ring gear control gear a, ring gear control gear b or ring gear control gear c to limit the rotation of the ring gear control gear a, ring gear control gear b or ring gear control gear c, as well as to limit the rotation of the ring gear A, ring gear B or ring gear C.

[0011] Preferably, the above-mentioned sliding sleeve is a spline sleeve, and its outer periphery has a first groove for driven axial movement, and the outer peripheries of the stopping hub and the stopping tooth are spline teeth. The sliding sleeve is always spline-connected to the stopping hub, and the sliding sleeve is driven axially to selectively connect or disengage with the stopping tooth spline.

[0012] Preferably, the central axis of the multi-jointed planetary gear is connected to the planetary carrier, and the planetary carrier gear is arranged on the planetary carrier.

[0013] Preferably, the above-mentioned coupling sleeve is a spline sleeve, and its outer periphery has a second groove for driven axial movement. The planetary carrier gear, input shaft gear and output shaft gear are spline teeth. The coupling sleeve is always spline-connected to the output shaft gear. The coupling sleeve is driven axially to selectively connect or disengage with the planetary carrier gear and input shaft gear spline.

[0014] Preferably, the diameters of the first gear, the second gear and the third gear decrease successively, the inner tooth diameters of the ring gear A, the ring gear B and the ring gear C decrease successively, and the outer tooth diameters of the ring gear A, the ring gear B and the ring gear C are the same.

[0015] The working method of the multi-speed transmission of the multi-linked planetary gear with multi-gear ring structure of the present invention is characterized by: With the sun gear on the input shaft as input, the coupling sleeve moves so that the fourth gear on the planetary carrier and the output shaft gear are connected with the coupling sleeve as output, and the control of each ring gear control wheel can obtain 3 movements with different transmission ratios; first, the maximum transmission ratio condition: locking the ring gear control wheel c, that is, making the ring gear C stationary, the sun gear input, the planetary carrier can obtain the maximum deceleration with the same direction; second, the transmission ratio condition of one level smaller: locking the ring gear control wheel b, that is, making the ring gear B stationary, under the same speed input of the sun gear 1, the planetary carrier can obtain the same direction but slightly faster rotation output; third, the second level smaller transmission ratio condition: locking the ring gear control wheel a, that is, making the ring gear A stationary, under the same speed input of the sun gear 1, the planetary carrier can obtain the same direction but faster rotation output; when the sun gear is used as input and the input shaft gear and the output shaft gear are connected through the coupling sleeve as output, the minimum transmission ratio of 1:1 with the highest rotation efficiency can be obtained, that is, the direct gear.

[0016] The multi-speed transmission with a multi-linked planetary gear and multi-ring gear structure of the present invention can obtain 4 ideal transmission ratios by properly configuring the gear parameters of each component. The device of the invention uses only one planetary gear to achieve the requirements of multi-speed transmission with fewer components, smaller size and weight; the ring gear control wheel can be controlled by friction or a coupling sleeve synchronizer structure. When controlled by friction, smooth gear shifting can be achieved, and power is not interrupted during the gear shifting process. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments are briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without creative work.

[0019] The central control reset pedal and its combined connection method of the present invention are further described in detail below in conjunction with the accompanying drawings and specific implementation structures.

[0020] Figure 1 It is a schematic diagram of the present invention; Figure 2-4 It is the principle diagram of three different transmission ratios of the present invention; Figure 5 It is the principle diagram of the direct file of the present invention. DETAILED DESCRIPTION

[0022] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings here can be arranged and designed in various different configurations.

[0023] The multi-speed transmission with a multi-connected planetary gear and multi-ring gear structure of the present invention comprises an input shaft 1, a sun gear 2 fixedly arranged on the middle of the input shaft and an input shaft gear 3 fixedly arranged on the end of the input shaft. The sun gear 2 and the input shaft gear 3 are arranged at intervals in the axial direction of the input shaft for the arrangement of other components.

[0024] The sun gear 2 is meshed with a multi-jointed planetary gear 4 (specifically, the sun gear 2 is meshed with the third gear 7 on the multi-jointed planetary gear 4 for transmission), and the multi-jointed planetary gear 4 has a first gear 5, a second gear 6 and a third gear 7 which are coaxially fixedly arranged in sequence but have different diameters, that is, the first gear 5, the second gear 6 and the third gear 7 are solid coaxial components, and the diameters of the first gear, the second gear and the third gear are reduced in sequence.

[0025] The first gear 5, the second gear 6 and the third gear 7 are respectively meshed with the inner teeth of the ring gear A, the ring gear B and the ring gear C, and the outer teeth of the ring gear A, the ring gear B and the ring gear C are respectively meshed with the ring gear control gear a, the ring gear control gear b and the ring gear control gear c that can be selectively stopped to achieve the stopping of the ring gear A, the ring gear B or the ring gear C; the specific structures for achieving the outer teeth of the ring gear A, the ring gear B and the ring gear C are respectively meshed with the ring gear control gear a, the ring gear control gear b and the ring gear control gear c that can be selectively stopped to achieve the stopping of the ring gear A, the ring gear B or the ring gear C can be several kinds, among which the friction method or the coupling sleeve synchronizer structure can be used to control the selective stopping of the ring gear control wheel.

[0026] The stop structure of the gear ring A, gear ring B or gear ring C implemented in this application is specifically as follows: The meshing ring gear control gear a, the ring gear control gear b and the ring gear control gear c are all connected to the fixed shaft 12 with an empty sleeve. The sides of the ring gear control gear a, the ring gear control gear b and the ring gear control gear c are provided with a stopper hub 13 fixed on the fixed shaft 12 and a sliding sleeve 14 provided on the stopper hub. The sliding sleeve 14 is a spline sleeve, and its outer periphery has a first groove 16 for driven axial movement (through the fork or the like inserted into the first groove for axial movement); after the axial movement of different sliding sleeves 14, they are connected to the ring gear control gear a and the ring gear control gear b or the stop tooth 15 on the ring gear control gear c engages to limit the rotation of the ring gear control gear a, the ring gear control gear b or the ring gear control gear c, and limits the rotation of the ring gear A, the ring gear B or the ring gear C. Specifically, the outer periphery of the stop hub and the stop tooth is a spline tooth, the sliding sleeve is always spline connected to the stop hub, and the sliding sleeve is driven axially to selectively connect or disengage with the stop tooth spline. After the sliding sleeve 14 moves, the sliding sleeve 14 is spline connected to the stop tooth 15, thereby realizing the ring gear control gear and the ring gear stopping of the stop tooth.

[0027] The input shaft 1 is coaxially provided with an unconnected output shaft 8, on which an output shaft gear 9 is fixedly provided, and the outer sleeve of the output shaft gear 9 is provided with a coupling sleeve 10 which can rotate coaxially and slide axially, and the side of the coupling sleeve 10 is provided with an inner gear ring which can selectively engage with the input shaft gear 3 or the planetary carrier gear 11 on the multi-connected planetary gear; the above-mentioned coupling sleeve 10 is a spline sleeve, and its outer periphery has a second groove 18 for driven axial movement, and the planetary carrier gear, input shaft gear and output shaft gear are spline teeth, and the coupling sleeve is always spline-connected with the output shaft gear, and the coupling sleeve is driven axially to selectively connect or disengage with the planetary carrier gear and the input shaft gear spline.

[0028] The central axis of the multi-jointed planetary gear 4 is connected to the planet carrier 17, and the planet carrier gear 11 is arranged on the planet carrier.

[0029] The working method of the multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure of the present invention uses the sun gear on the input shaft as input, moves the coupling sleeve, and connects the fourth gear on the planet carrier with the output shaft gear as output through the coupling sleeve, and controls each gear ring control wheel to obtain three different transmission ratios; the first, the maximum transmission ratio condition (such as Figure 2 As shown): Lock the ring gear control wheel c, that is, make the ring gear C stationary, the sun gear input, the planetary carrier can get the maximum deceleration with the same direction; the second, the smaller transmission ratio working condition (such as Figure 3 As shown): Lock the ring gear control wheel b, that is, make the ring gear B stationary, under the same speed input of the sun gear 1, the planetary carrier can obtain the same direction but slightly faster rotation output; third, small secondary transmission ratio working condition (such as Figure 4As shown): Lock the ring gear control wheel a, that is, make the ring gear A stationary, and under the same speed input of the sun gear 1, the planetary carrier obtains the same direction but faster rotation output; when the sun gear is used as input, and the input shaft gear and the output shaft gear are connected through the coupling sleeve as output, the minimum transmission ratio of 1:1 with the highest rotation efficiency can be obtained, that is, the direct gear.

[0030] The multi-speed transmission with a multi-linked planetary gear and multi-ring gear structure of the present invention can obtain 4 ideal transmission ratios by properly configuring the gear parameters of each component. The device of the invention uses only one planetary gear to achieve the requirements of multi-speed transmission with fewer components, smaller size and weight; the ring gear control wheel can be controlled by friction or a coupling sleeve synchronizer structure. When controlled by friction, smooth gear shifting can be achieved, and power is not interrupted during the gear shifting process.

[0031] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention.

Claims

1. A multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure, characterized in that: The invention comprises an input shaft (1), a sun gear (2) fixedly arranged on the middle of the input shaft, and an input shaft gear (3) fixedly arranged on the end of the input shaft, wherein the sun gear (2) meshes with a multi-linked planetary gear (4), and the multi-linked planetary gear (4) has a first gear (5), a second gear (6), and a third gear (7) which are coaxially fixedly arranged in sequence but have different diameters, wherein the third gear (7) meshes with the sun gear (2) for transmission, and the first gear (5), the second gear (6), and the third gear (7) respectively mesh with the internal teeth of a gear ring A, a gear ring B, and a gear ring C, wherein the gear ring A, the gear ring B, and the gear ring C are meshed with each other. The outer teeth of ring C are respectively meshed with the ring gear control gear a, the ring gear control gear b and the ring gear control gear c which can be selectively stopped, so as to achieve the stopping of the ring gear A, the ring gear B or the ring gear C; the input shaft (1) is coaxially provided with an unconnected output shaft (8), the output shaft (8) is fixedly provided with an output shaft gear (9), the outer periphery of the output shaft gear (9) is provided with a coupling sleeve (10) which can coaxially rotate and axially slide, and the side of the coupling sleeve (10) is provided with an inner ring gear which can selectively mesh with the input shaft gear (3) or the planetary carrier gear (11) on the multi-link planetary gear.

2. The multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure according to claim 1, characterized in that: The ring gear control gear a, the ring gear control gear b and the ring gear control gear c are all connected to a fixed shaft (12) by meshing with an idler sleeve. A stop hub (13) fixed to the fixed shaft (12) and a sliding sleeve (14) provided on the stop hub are provided on the side of the ring gear control gear a, the ring gear control gear b and the ring gear control gear c. After axial movement, the different sliding sleeves (14) engage with the stop teeth (15) on the ring gear control gear a, the ring gear control gear b or the ring gear control gear c to limit the rotation of the ring gear control gear a, the ring gear control gear b or the ring gear control gear c, and to limit the rotation of the ring gear A, the ring gear B or the ring gear C.

3. The multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure according to claim 2, characterized in that: The sliding sleeve (14) is a spline sleeve, and its outer periphery has a first groove (16) for driven axial movement. The outer peripheries of the stop hub and the stop tooth are spline teeth. The sliding sleeve is always spline-connected to the stop hub, and the sliding sleeve is driven axially to selectively connect or disengage with the stop tooth spline.

4. The multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure according to claim 1, 2 or 3, characterized in that: The central axis of the multi-jointed planetary gear (4) is connected to a planetary carrier (17), and the planetary carrier gear (11) is arranged on the planetary carrier.

5. The multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure according to claim 1, 2 or 3, characterized in that: The coupling sleeve (10) is a spline sleeve, and its outer periphery has a second groove (18) for driven axial movement. The planetary carrier gear, input shaft gear and output shaft gear are spline teeth. The coupling sleeve is always spline-connected with the output shaft gear. The coupling sleeve is driven axially moved to selectively connect or disengage with the planetary carrier gear and the input shaft gear spline.

6. The multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure according to claim 1, 2 or 3, characterized in that: The diameters of the first gear, the second gear and the third gear decrease in sequence, the inner tooth diameters of the gear rings A, B and C decrease in sequence, and the outer tooth diameters of the gear rings A, B and C are the same.

7. A method for operating a multi-speed transmission with a multi-linked planetary gear and multi-gear ring structure as claimed in any one of claims 1 to 6, characterized in that: With the sun gear on the input shaft as input, the coupling sleeve moves so that the fourth gear on the planet carrier and the output shaft gear are connected with the coupling sleeve as output. By controlling each ring gear control wheel, three different transmission ratios are obtained. First, the maximum transmission ratio condition: lock the ring gear control wheel C, that is, make the ring gear C stationary, the sun gear is input, and the planet carrier can obtain the maximum deceleration with the same direction. Second, the transmission ratio condition with one level smaller: lock the ring gear to control wheel b, that is, make the ring gear B stationary, and under the same speed input of sun gear 1, the planetary carrier can obtain a rotation output in the same direction but slightly faster; Third, the transmission ratio condition with two levels smaller: lock the ring gear to control wheel a, that is, make the ring gear A stationary, and under the same speed input of sun gear 1, the planetary carrier can obtain a rotation output in the same direction but faster; When the sun gear is used as input and the input shaft gear and the output shaft gear are connected through a coupling sleeve as output, the minimum transmission ratio of 1:1 with the highest rotation efficiency can be obtained, that is, direct gear.

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