CN113007293A - Double-state double-inner-meshing planetary gear transmission structure - Google Patents
Double-state double-inner-meshing planetary gear transmission structure Download PDFInfo
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- CN113007293A CN113007293A CN202110257366.7A CN202110257366A CN113007293A CN 113007293 A CN113007293 A CN 113007293A CN 202110257366 A CN202110257366 A CN 202110257366A CN 113007293 A CN113007293 A CN 113007293A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a double-state double-inner-meshing planetary gear transmission structure which mainly comprises three double-inner-meshing planetary rows connected in series, a transmission shell, a gear shifting element, a supporting and connecting part and the like. For the sun gear, the planet carrier and the gear ring in each planet row, through the mutual matching of a disc spring in the clutch and a clutch actuator, two of the basic components can be controlled to be connected or one of the basic components can be controlled to be connected and fixed with the transmission shell to form a two-state logic structure, so that the transmission ratio of the transmission can be increased by multiple times, thereby realizing the step change of gears and expanding the transmission range. Each double-inner-meshing planetary row is meshed with the gear ring and the sun gear in an inner-meshing mode through a planetary gear with inner teeth and outer teeth, the power density of the transmission is improved, and the problem of uneven load of the planetary gear cannot occur.
Description
Technical Field
The invention belongs to the technical field of vehicle transmissions, and particularly relates to a double-state double-internal-meshing planetary gear transmission structure.
Background
The engine is used as a mainstream power generation device of the current automobile, has the characteristics of high rotating speed, small torque, small rotating speed and torque variation range and the like, needs the automatic transmission to adjust the rotating speed and the torque, and automatically switches to a gear matched with the rotating speed and the torque according to the external environment change, thereby being widely applied. The hydraulic automatic transmission has the advantages of smooth gear shifting, simple operation and the like, and becomes the automatic transmission with the highest popularization rate, but the existing hydraulic automatic transmission has the problems of lower transmission efficiency, larger planetary gear mechanism volume, lower power density and the like. In order to meet the increasingly high requirements of the market on the dynamic property and the economical efficiency of automobiles, the automatic transmission is developed towards the targets of multi-gear and large speed ratio range, and the structure of the planetary gear is increasingly complex along with the increase of gears. Therefore, how to improve the efficiency, power density and multi-gear of the automatic transmission becomes a problem to be solved urgently.
Some current researches propose a control method for a gear shifting process of a two-state logic transmission, for example, an invention patent with the patent number of CN111810597A discloses a gear shifting process control method for a two-state logic transmission, which divides the gear shifting process into single oil pressure actuated gear shifting and combined oil pressure actuated gear shifting, can obviously reduce gear shifting impact degree and friction work, and improve the gear shifting quality of a whole vehicle, but the patent does not design the structures of important parts of the two-state logic transmission, especially the structures of a support structure and a clutch of a double inner meshing planetary row, which is also a problem to be solved urgently by the current two-state logic transmission technology.
The invention provides a double-state double-internal-meshing planetary gear transmission structure, and discloses an internal structure of a double-state double-internal-meshing planetary gear transmission, which enables the transmission ratio of the transmission to be multiplied, enlarges the transmission range, and improves the transmission efficiency and the power density of the transmission.
Disclosure of Invention
The invention aims to solve the technical problems of low power density, uneven loading of a planetary gear and the like of a traditional planetary gear train, provides a double-inner meshing planetary gear train, and provides a two-state logic structure aiming at the problems of low transmission efficiency, increasingly complex transmission structure and operation along with gear increase and the like of a traditional planetary gear transmission.
In order to solve the technical problems, the invention is realized by adopting the following technical scheme: the double-state double-internal-meshing planetary gear transmission structure is characterized in that the transmission mainly comprises three double-internal-meshing planetary rows X1, X2 and X3 connected in series, a transmission housing, a gear shifting element and other parts, wherein the planetary row X1 comprises a sun gear S1, a gear ring R1, a planet carrier PC1, a planet gear P1, a clutch C1 and a brake C2, the planetary row X2 comprises a sun gear S2, a gear ring R2, a planet carrier PC2, a planet gear P2, a clutch C3 and a brake C4, and the planetary row X3 comprises a sun gear S3, a gear ring R3, a planet carrier PC3, a planet gear P3, a clutch C5 and a brake C6; each double inner meshing planetary row is meshed with a gear ring and a sun gear through a planetary gear with inner and outer teeth to form two pairs of inner meshing pairs for power transmission, the power input end of the speed changer is connected with the gear ring shaft of the X1 planetary row, the sun gear shaft of the X1 planetary row is connected with the sun gear shaft of the X2 planetary row, the gear ring shaft of the X2 planetary row is connected with the sun gear shaft of the X3 planetary row, the gear ring shaft of the X3 planetary row is connected with the output end of the speed changer, and the shafts are connected through splines;
the power transmission conditions of the three series-connected double internal meshing planetary rows are as follows: an X1 planet row gear ring shaft 1 is connected with a power input end of a speed changer through a spline shaft section, an X1 planet row gear ring 9 is in inner meshing with outer teeth of planet wheels 10 to transmit power, inner teeth of the planet wheels 10 are in inner meshing with a sun wheel 8 of the planet wheels to transmit power, a sun wheel shaft 13 of an X1 planet row is in spline connection with a sun wheel shaft 15 of an X2 planet row, and the power is transmitted to an X2 planet row; the X2 planet row sun gear 18 is internally meshed with the internal teeth of the planet gears 19 to transmit power, the external teeth of the planet gears 19 are internally meshed with the ring gear 17 to transmit power, and the X2 planet row ring gear shaft 21 is connected with the X3 planet row sun gear shaft 40 through a spline and transmits the power to the X3 planet row; the X3 planetary row sun gear 36 meshes with the internal teeth of the planetary gears 37 to transmit power, and the external teeth of the planetary gears 37 further mesh with the ring gear 38 to transmit power, and finally the power of the transmission is output through the ring gear shaft 34 of the X3 planetary row.
The main parts of the transmission are supported in the following modes: an X1 gear ring shaft 1 is supported on an X1 planet row left shell 61 through two conical roller bearings 3 and 4, an X1 sun gear shaft 13 is supported on an X1 planet row right shell 55 through two conical roller bearings 12 and 22, an X1 left planet carrier 6 is supported on the gear ring shaft 1 and the sun gear shaft 13 through two deep groove ball bearings 5 and 25 respectively, and a right planet carrier 11 is connected with the left planet carrier 6 through an inner bolt 7; an X2 sun gear shaft 15 is supported on an X2 planet row left shell 54 through two conical roller bearings 3 and 12, an X2 planet row ring gear shaft 21 is supported on an X2 planet row right shell 44 through two conical roller bearings 3 and 4, an X2 planet row right planet carrier 20 is supported on the sun gear shaft 15 and the ring gear shaft 21 through two deep groove ball bearings 45 and 3 respectively, and a left planet carrier 16 and a right planet carrier 20 are connected through an inner bolt 7; an X3 planet row sun gear shaft 40 is supported on an X3 planet row left shell 23 through two conical roller bearings 22, 12, an X3 planet row ring gear shaft 34 is supported on an X3 planet row right shell 28 through two conical roller bearings 27, 29, an X3 planet row right planet carrier 35 is supported on the sun gear shaft 40 and the ring gear shaft 34 through two deep groove ball bearings 25, 26 respectively, a left planet carrier 39 and a right planet carrier 35 are connected through an inner bolt 7, and the planet row left and right shells are connected through an outer bolt 41, a nut 42 and a washer 43; the radial dimension of the double inner meshing planetary gears is large, the axial dimension is small, a standard bearing is selected between the two ends of the planetary gears and the planet carrier to be supported more difficultly, the roller paths are directly processed on the left planet carrier, the right planet carrier and the planetary gears of each planetary row, and cylindrical rollers 60 are filled in the corresponding roller paths to support the planetary gears on the planet carrier.
The structure of the shift elements in each planet row is: the clutch-housing connecting piece 52 and the clutch friction disc a47 are respectively connected and fixed with the planet row left housings 61, 54 and 23 through external bolts 59 and washers 57, the friction disc b48 is respectively supported on the planet carriers 11, 16 and 39 through designed grooves, and keeps synchronous rotation with the planet carrier and can move axially, the friction disc c50 is respectively connected with the planet row sun gear shaft through splines and keeps synchronous rotation with the sun gear shaft, a lug on one side end face of the friction disc d53 is meshed with a concentric V-shaped groove of the friction disc c50, the other side end face is fixed through an elastic retainer ring 56 to limit the axial movement of each friction disc, and the disc spring 46 is mutually matched with the clutch actuator 51 and used for pushing the friction disc b48 to move axially to realize a two-state logic function; when the actuator does not work, the compressed disc spring 46 pushes the friction disc b48 to move towards the friction disc c50, a lug on the end face of the friction disc b48 is meshed with a concentric V-shaped groove on the end face of the friction disc c50, the friction disc b48 and the friction disc c50 rotate synchronously, so that the planet carrier and the sun gear rotate synchronously, the planet gear, the gear ring and the planet carrier rotate synchronously at the moment, and the transmission ratio of the planet carrier is 1; when the clutch actuator 51 works, the clutch actuator pushes the friction disc b48 to move towards the friction disc a47, the disc spring 46 compresses and stores energy, the lug on the end surface of the friction disc b48 is meshed with the concentric V-shaped groove of the friction disc a47, the lug and the concentric V-shaped groove rotate synchronously, and therefore the planet carrier is fixedly connected with the transmission shell, and the transmission ratio of the planet row is related to the characteristic parameter k and the input and output members; through the mutual matching of the disc spring 46 in the clutch and the clutch actuator 51, each planet row has two transmission ratios, the transmission ratio of the transmission is multiplied with the number of the planet rows, the step change of gears is realized, and the transmission range is expanded; the clutches in each planet row are all V-shaped grooves, the friction area of the clutches is increased, the heat dissipation of the clutches is facilitated, the number of other parts needed by the clutches is reduced, the resistance between friction discs of the clutches is almost eliminated during separation, and the separation is quicker than that of a traditional clutch.
Compared with the prior art, the invention has the beneficial effects that:
1. the double inner meshing planetary rows adopted in the double-state double inner meshing planetary gear transmission structure have larger contact ratio, the power density of a transmission device is larger, and the transmission efficiency is higher;
2. according to the double-state double-internal-meshing planetary gear transmission structure, power transmission is carried out through the planetary gear with the inner teeth and the outer teeth, the problem of uneven load of the planetary gear is solved, and a load balancing device is not needed;
3. the structure of the double-state double-internal-meshing planetary gear transmission adopts a double-state logic structure, and each planet row has two transmission ratios through the mutual matching of a disc spring in a clutch and a clutch actuator, the transmission ratio of the transmission is multiplied along with the number of the planet rows, the step change of gears is realized, and the transmission range is enlarged.
4. The clutch in the double-state double-inner-meshing planetary gear transmission structure adopts a V-shaped groove structure, the friction area of the clutch is larger, heat dissipation is facilitated, resistance is small when each clutch element is separated, and separation is quicker.
Drawings
FIG. 1 is a general cross-sectional view of a two-state, dual intermeshing planetary gear transmission configuration of the present invention; the elements represented by the various reference numbers in the figures are: 1-X1 planet row ring gear shaft; 2-oil sealing; 3-tapered roller bearing 30314; 4-tapered roller bearing 30316; 5-deep groove ball bearing 6008; 6-X1 planet row left planet carrier; 7-hexagon socket head cap screw M12; 8-X1 planet row sun gear; 9-X1 planet row ring gear; 10-X1 planetary row planet; 11-X1 planet row right planet carrier; 12-tapered roller bearing 30315; 13-X1 planet row sun gear shaft; 14-a bearing circlip; 15-X2 planet row sun gear shaft; 16-X2 planet row left carrier; 17-X2 planet row ring gear; 18-X2 planet row sun gear; 19-X2 planetary row planet; the 20-X2 planet row right planet carrier; 21-X2 planet row ring gear shaft; 22-tapered roller bearing 30313; 23-X3 planet row left housing; 24-a sleeve; 25-deep groove ball bearing 6212; 26-deep groove ball bearing 6014; 27-tapered roller bearing 30319; 28-X3 planet row right housing; 29-tapered roller bearing 30320; 30-end cap; 31-hex head bolt M12; 32-standard type spring washer M12; 33-adjusting the shim; 34-X3 planet row ring gear shaft; a 35-X3 planet row right planet carrier; 36-X3 planet row sun gear; 37-X3 planetary row planet; 38-X3 planet row ring gear; 39-X3 planet row left carrier; 40-X3 planet row sun gear shaft; 41-bolt M18 for hexagonal head reaming; 42-hex nut M18; 43-standard type spring washer; 44-X2 planet row right housing; 45-deep groove ball bearing 6016; 46-a disc spring; 47-clutch friction disc a; 48-clutch friction disc b; 49-a ball; 50-clutch friction disc c; 51-clutch actuator; 52-clutch-housing connection; 53-clutch friction disc d; 54-X2 planet row left housing; 55-X1 planet row right housing; 56-circlip; 57-standard type spring washer M10; 58-oil seal; 59-hex head bolt M10; 60-cylindrical rollers; the left shell of the 61-X1 planet row;
FIG. 2 is a simplified schematic layout of a two-state dual intermeshing planetary transmission configuration of the present invention;
FIG. 3 is a schematic diagram of a dual internal planetary gear transmission in a two-state dual internal planetary gear transmission configuration according to the present invention;
FIG. 4 is an enlarged partial cross-sectional view of the X1 planet carrier arrangement in a two-state, dual intermeshing planetary transmission configuration of the present invention;
FIG. 5 is an enlarged partial cross-sectional view of an X1 planet row clutch arrangement in a two-state, dual intermeshing planetary transmission configuration according to the present invention;
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a detailed description of the present invention will be made with reference to the accompanying drawings, in which:
referring to fig. 1 and fig. 2, in order to solve the existing technical problems of the automatic transmission, the present invention provides a two-state dual-intermeshing planetary gear transmission structure, the transmission mainly comprises three dual-intermeshing planetary rows X1, X2, X3 connected in series, a transmission housing, a shift element, and other parts, wherein planetary row X1 includes a sun gear S1, a ring gear R1, a planet carrier PC1, a planet gear P1, a clutch C1, and a brake C2, planetary row X2 includes a sun gear S2, a ring gear R2, a planet carrier PC2, a planet gear P2, a clutch C3, and a brake C4, and planetary row X3 includes a sun gear S3, a ring gear R3, a planet carrier PC3, a planet gear P3, a clutch C5, and a brake C6; each double inner meshing planetary row is meshed with a gear ring and a sun gear through a planetary gear with inner and outer teeth to form two pairs of inner meshing pairs for power transmission, the power input end of the speed changer is connected with the gear ring shaft of the X1 planetary row, the sun gear shaft of the X1 planetary row is connected with the sun gear shaft of the X2 planetary row, the gear ring shaft of the X2 planetary row is connected with the sun gear shaft of the X3 planetary row, the gear ring shaft of the X3 planetary row is connected with the output end of the speed changer, and the shafts are connected through splines;
referring to fig. 1 and 3, an X1 planet row ring gear shaft 1 is connected with a power input end of a transmission through a spline shaft section, an X1 planet row ring gear 9 is internally meshed with external teeth of planet gears 10, internal teeth of the planet gears 10 are internally meshed with a sun gear 8, a sun gear shaft 13 of an X1 planet row is connected with a sun gear shaft 15 of an X2 planet row through a spline, an X2 planet row sun gear 18 is internally meshed with internal teeth of planet gears 19, external teeth of the planet gears 19 are internally meshed with a ring gear 17, an X2 planet row ring gear shaft 21 is connected with a sun gear shaft 40 of an X3 planet row through a spline, an X3 planet row sun gear 36 is internally meshed with internal teeth of planet gears 37, external teeth of the planet gears 37 are internally meshed with a ring gear 38, and a ring gear shaft 34 of the X3 planet row is connected with a power output; each double inner meshing planetary row is meshed with the gear ring and the sun gear in an inner meshing mode through a planetary gear with inner teeth and outer teeth so as to transmit power, the contact ratio is larger, the power density of the planetary rows is improved, the problem of uneven loading of the planetary gears is solved, and a load balancing device is not needed;
referring to fig. 1 and 4, the two-state dual internal meshing planetary gear transmission structure of the present invention has the following main component support modes: an X1 ring gear shaft 1 is supported on an X1 planet row left shell 61 through two tapered roller bearings 3 and 4, an X1 sun gear shaft 13 is supported on an X1 planet row right shell 55 through two tapered roller bearings 12 and 22, an X1 left planet carrier 6 is supported on the ring gear shaft 1 and the sun gear shaft 13 through two deep groove ball bearings 5 and 25 respectively, a right planet carrier 11 and the left planet carrier 6 are connected through an inner bolt 7, raceways are machined on a left planet carrier 6, a right planet carrier 11 and planet gears 10, and cylindrical rollers 60 are filled in corresponding raceways so as to support the planet gears 10 on an X1 planet row planet carrier; an X2 sun gear shaft 15 is supported on an X2 planet row left shell 54 through two tapered roller bearings 3 and 12, an X2 planet row ring gear shaft 21 is supported on an X2 planet row right shell 44 through two tapered roller bearings 3 and 4, an X2 planet row right planet carrier 20 is supported on the sun gear shaft 15 and the ring gear shaft 21 through two deep groove ball bearings 45 and 3 respectively, a left planet carrier 16 and a right planet carrier 20 are connected through an inner bolt 7, a raceway is processed on a left planet carrier 16, a right planet carrier 20 and planet gears 19, and a cylindrical roller 60 is filled in the corresponding raceway so as to support the planet gears 19 on an X2 planet row carrier; an X3 planet row sun gear shaft 40 is supported on an X3 planet row left shell 23 through two conical roller bearings 22 and 12, an X3 planet row ring gear shaft 34 is supported on an X3 planet row right shell 28 through two conical roller bearings 27 and 29, an X3 planet row right planet carrier 35 is supported on a sun gear shaft 40 and a ring gear shaft 34 through two deep groove ball bearings 25 and 26 respectively, a left planet carrier 39 and a right planet carrier 35 are connected through an inner bolt 7, a raceway is processed on a left planet carrier 39, a right planet carrier 35 and a planet wheel 37, and a corresponding raceway is filled with cylindrical rollers 60 so as to support the planet wheel 37 on the X3 planet row carrier; the left and right housings of each planetary row are connected by an external bolt 41, a nut 42 and a washer 43.
Referring to fig. 1 and 5, the structure of the shift element in the two-state dual internal meshing planetary gear transmission structure of the present invention is: the clutch-housing connecting piece 52 and the clutch friction disc a47 are respectively connected and fixed with each planet row left housing 61, 54 and 23 through an external bolt 59 and a washer 57, the friction disc b48 is respectively supported on the planet carriers 11, 16 and 39 through designed grooves, keeps synchronous rotation with the planet carrier and can move axially, the friction disc c50 is respectively connected with each planet row sun gear shaft through splines and keeps synchronous rotation with the sun gear shaft, a lug on one side end face of the friction disc d53 is meshed with a concentric V-shaped groove of the friction disc c50, the other side end face is fixed through a retaining ring 56 to limit the axial movement of each friction disc, and the disc spring 46 is mutually matched with the clutch actuator 51 and used for pushing the friction disc b48 to move axially to realize a two-state logic function; when the actuator does not work, the compressed disc spring 46 pushes the friction disc b48 to move towards the friction disc c50, a lug on the end face of the friction disc b48 is meshed with a concentric V-shaped groove on the end face of the friction disc c50, the friction disc b48 and the friction disc c50 rotate synchronously, so that the planet carrier and the sun gear rotate synchronously, the planet gear, the gear ring and the planet carrier rotate synchronously at the moment, and the transmission ratio of the planet carrier is 1; when the clutch actuator 51 works, the clutch actuator pushes the friction disc b48 to move towards the friction disc a47, the disc spring 46 compresses and stores energy, the lug on the end surface of the friction disc b48 is meshed with the concentric V-shaped groove of the friction disc a47, the friction disc b48 and the concentric V-shaped groove rotate synchronously, and therefore the planet carrier is fixedly connected with the transmission shell, and the transmission ratio of the planet row is related to the characteristic parameter k and the input and output members of the planet row; through the mutual matching of the disc spring 46 in the clutch and the clutch actuator 51, each planet row has two transmission ratios, the transmission ratio of the transmission is multiplied with the number of the planet rows, the step change of gears is realized, and the transmission range is expanded; each clutch friction disc adopts a V-shaped groove structure, the friction area of the clutch is larger, heat dissipation is facilitated, resistance is small when each clutch element is separated, and separation is quicker.
In the present invention, unless otherwise expressly stated or limited, the terms "support," "connect," "secure," and the like are to be construed broadly and can, for example, be fixedly connected, releasably connected, or integral; the two elements can be directly connected or indirectly connected through an intermediate medium, and the two elements can be communicated with each other or the two elements can interact with each other, so that the specific meaning of the terms in the invention can be understood according to specific situations by a person skilled in the art.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the present invention, and it will be understood by those skilled in the art that various changes and modifications may be made therein without departing from the spirit and scope of the invention.
Claims (3)
1. A double-state double-internal-meshing planetary gear transmission structure is characterized in that the transmission mainly comprises three double-internal-meshing planetary rows X1, X2 and X3 connected in series, a transmission housing, a gear shifting element and other parts, wherein the planetary row X1 comprises a sun gear S1, a gear ring R1, a planet carrier PC1, a planet gear P1, a clutch C1 and a brake C2, the planetary row X2 comprises a sun gear S2, a gear ring R2, a planet carrier PC2, a planet gear P2, a clutch C3 and a brake C4, and the planetary row X3 comprises a sun gear S3, a gear ring R3, a planet carrier PC3, a planet gear P3, a clutch C5 and a brake C6; each double inner meshing planetary row is meshed with a gear ring and a sun gear through a planetary gear with inner and outer teeth to form two pairs of inner meshing pairs for power transmission, the power input end of the speed changer is connected with the gear ring shaft of the X1 planetary row, the sun gear shaft of the X1 planetary row is connected with the sun gear shaft of the X2 planetary row, the gear ring shaft of the X2 planetary row is connected with the sun gear shaft of the X3 planetary row, the gear ring shaft of the X3 planetary row is connected with the output end of the speed changer, and the shafts are connected through splines;
an X1 planet row ring gear shaft (1) is connected with a power input end of a speed changer through a spline shaft section, an X1 planet row ring gear (9) is internally meshed with external teeth of planet wheels (10), the internal teeth of the planet wheels (10) are internally meshed with a sun wheel (8) of the planet wheels, a sun wheel shaft (13) of an X1 planet row is connected with a sun wheel shaft (15) of an X2 planet row through a spline, an X2 planet row sun wheel (18) is internally meshed with internal teeth of the planet wheels (19), the external teeth of the planet wheels (19) are internally meshed with a ring gear (17), an X2 planet row ring gear shaft (21) is connected with a X3 planet row sun wheel shaft (40) through a spline, an X3 planet row sun wheel (36) is internally meshed with internal teeth of the planet wheels (37), the external teeth of the planet wheels (37) are internally meshed with a ring gear (38), and a spline ring gear shaft (34) of an X3 planet row is connected with.
2. A twin internally meshing planetary gear transmission arrangement as in claim 1, wherein the main components are supported in a manner that: an X1 ring gear shaft (1) is supported on an X1 planet row left shell (61) through two conical roller bearings (3) and (4), an X1 sun gear shaft (13) is supported on an X1 planet row right shell (55) through two conical roller bearings (12) and (22), an X1 left planet carrier (6) is supported on the ring gear shaft (1) and the sun gear shaft (13) through two deep groove ball bearings (5) and (25) respectively, a right planet carrier (11) and the left planet carrier (6) are connected through an inner bolt (7), raceways are machined on the left and right planet carriers (6) and (11) and planet gears (10), and the corresponding cylindrical rollers (60) are filled in the raceways so as to support the planet gears (10) on an X1 planet carrier; an X2 sun wheel shaft (15) is supported on an X2 planet row left shell (54) through two conical roller bearings (3), (12), an X2 planet row ring gear shaft (21) is supported on an X2 planet row right shell (44) through two conical roller bearings (3), (4), an X2 planet row right planet carrier (20) is supported on the sun wheel shaft (15) and a ring gear shaft (21) through two deep groove ball bearings (45), (3) respectively, a left planet carrier (16) and a right planet carrier (20) are connected through an inner bolt (7), raceways are machined on a left planet carrier (16), (20) and a planet wheel (19), and cylindrical rollers (60) are filled in the corresponding raceways so as to support the planet wheel (19) on an X2 planet row planet carrier; an X3 planet row sun gear shaft (40) is supported on an X3 planet row left shell (23) through two conical roller bearings (22), (12), an X3 planet row ring gear shaft (34) is supported on an X3 planet row right shell (28) through two conical roller bearings (27), (29), an X3 planet row right planet carrier (35) is supported on a sun gear shaft (40) and a ring gear shaft (34) through two deep groove ball bearings (25), (26) respectively, a left planet carrier (39) and a right planet carrier (35) are connected through an internal bolt (7), raceways are machined on a left planet carrier (39), (35) and a right planet carrier (37), and cylindrical rollers (60) are filled in the corresponding raceways so as to support the planet carriers (37) on an X3 planet row carrier; the left and right shells of each planet row are connected through an external bolt (41), a nut (42) and a washer (43).
3. A two-state, dual intermeshing planetary gear transmission arrangement as claimed in claim 1, wherein the shift element is configured to: the clutch-shell connecting piece (52) and the clutch friction disc a (47) are respectively connected and fixed with the left shells (61), (54), (23) of each planet row through an external bolt (59) and a gasket (57), the friction disc b (48) is respectively supported on the planet carriers (11), (16), (39) through designed grooves, the friction disc c (50) is respectively connected with the sun gear shafts of the planet rows through splines, the friction disc d (53) is synchronously rotated with the sun wheel shaft, a lug on one side end face of the friction disc d (53) is meshed with a concentric V-shaped groove of the friction disc c (50), the other side end face of the friction disc d (53) is fixed through a retainer ring (56) to limit the axial movement of each friction disc, and a disc spring (46) is matched with a clutch actuator (51) and used for pushing the friction disc b (48) to axially move to realize a two-state logic function; when the actuator (51) does not work, the compressed disc spring (46) pushes the friction disc b (48) to move towards the friction disc c (50), a lug on the end face of the friction disc b (48) is meshed with a concentric V-shaped groove on the end face of the friction disc c (50), the friction disc b (48) and the friction disc c (50) rotate synchronously, so that the planet carrier and the sun gear rotate synchronously, the planet gear, the gear ring and the planet carrier rotate synchronously at the moment, and the transmission ratio of the planet carrier is 1; when the clutch actuator (51) works, the friction disc b (48) is pushed to move towards the friction disc a (47), the disc spring (46) compresses and stores energy, lugs on the end surface of the friction disc b (48) are meshed with the concentric V-shaped grooves of the friction disc a (47), the friction disc b and the friction disc a rotate synchronously, and therefore the planet carrier and the transmission shell are connected and fixed, and the transmission ratio of the planet row is related to the characteristic parameter k and the input and output members.
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| CN202110257366.7A CN113007293A (en) | 2021-03-09 | 2021-03-09 | Double-state double-inner-meshing planetary gear transmission structure |
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