CN107269779B - Three-planet-row six-speed automatic transmission - Google Patents
Three-planet-row six-speed automatic transmission Download PDFInfo
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- CN107269779B CN107269779B CN201710514253.4A CN201710514253A CN107269779B CN 107269779 B CN107269779 B CN 107269779B CN 201710514253 A CN201710514253 A CN 201710514253A CN 107269779 B CN107269779 B CN 107269779B
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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
- 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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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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
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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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
- F16H2057/02091—Measures for reducing weight of gearbox
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
Abstract
The invention relates to the technical field of automobiles, and discloses a three-planet-row six-speed automatic transmission which comprises a first planet row, a second planet row and a third planet row; the first sun gear is connected with the first brake, and the first sun gear is connected with the second sun gear through the first clutch; the first planet carrier is fixedly connected with the second gear ring and then integrally connected with the second brake; the second planet carrier is fixedly connected with the third gear ring; the third sun gear is fixed, and the third planet carrier is connected with the first gear ring through a third clutch; the second sun gear is fixedly connected with the power input component, and the first gear ring is fixedly connected with the power output component; the second clutch is connected between any two of the second ring gear, the second sun gear, and the second carrier. The invention adopts three clutches and two brakes, reasonably combines and connects three planetary rows, and can realize six forward gears and one reverse gear.
Description
Technical Field
The invention relates to the technical field of automobiles, in particular to a three-planet-row six-speed automatic transmission.
Background
The mechanism for effecting a change in speed in an electrically controlled hydrostatic transmission drive train typically includes a plurality of planetary rows. The power of the engine is transmitted into the planetary gear speed change mechanism through the hydraulic torque converter to be changed in speed and then output. The volume, weight, efficiency and load carrying capacity of an automatic transmission are directly related to the planetary gear mechanism. The more gears of the automatic transmission drive train, the lower the fuel consumption of the automobile and the better the economy, but as the number of gears increases, the number of planetary rows and the number of operating clutches and brakes also increase, and the design of satisfying the theoretical step ratio is difficult to realize. People are always seeking to combine a planetary gear speed change mechanism which meets the requirements of automobile performance, has a compact structure, higher strength and better efficiency by using fewer planetary rows, clutches and brakes.
The planetary gear mechanism of the 6-speed automatic transmission used in the current passenger car market mainly comprises: the leperey scheme used by ericsson, ZF and jiri (DSI); protocols used in modern series A6MF and A6 LF; protocols used in the general 6T series; maudada created a 6-speed protocol for the blue sky.
The Lepelelayje scheme is realized by adding a row of planet rows on the basis of a Lavena 4-speed automatic transmission without direct gear; however, the leperedy scheme adopts a ravigneaux structure, and a double planetary wheel structure appears, so that compared with a single planetary wheel, the structure is more complicated, the compactness of the structure is more unfavorable, and the weight and the cost are increased. The general and modern solutions are implemented with three planetary rows, with the difference that the position of the clutch is different, and in modern mass production series A6MF and A6LF, a planetary row also uses a double planetary structure; modern and general scheme, all realize with 2 clutches and 3 brakes, the quantity of brake is more than the quantity of clutch, and the brake is finally connected to the box through friction steel sheet tooth, and more brakes have undoubtedly increased the manufacturing difficulty of box, and because the box material is the aluminum alloy generally, more brakes can undoubtedly can cause the difficulty to realizing lightweight design when can guarantee intensity. The 6-speed scheme used in the creative blue sky is derived from a transverse arrangement scheme used by American ALLISON company on a matched diesel heavy-duty truck, the direct gear is in the fourth gear, and the characteristic of inherent shortage in speed ratio configuration can be realized on the matched gasoline engine.
Disclosure of Invention
The invention aims to provide a three-planetary-row six-speed automatic transmission which can realize six forward gears and one backward gear, has a more compact whole structure and is lower in processing and manufacturing difficulty of a transmission box body.
In order to achieve the above object, the present invention provides a three planetary-row six-speed automatic transmission including a first planetary row, a second planetary row, a third planetary row, a first clutch, a second clutch, a third clutch, a first brake, a second brake, a power input member, and a power output member; the first planet row comprises a first gear ring, a first planet wheel, a first sun gear and a first planet carrier; the second planet row comprises a second gear ring, a second planet wheel, a second sun wheel and a second planet carrier; the third planet row comprises a third gear ring, a third planet wheel, a third sun gear and a third planet carrier;
the first sun gear is connected with one end of the first brake, and the first sun gear is connected with the second sun gear through the first clutch; the first planet carrier is fixedly connected with the second gear ring and then integrally connected with one end of the second brake; the second planet carrier is fixedly connected with the third gear ring; the third sun gear is fixed, and the third planet carrier is connected with the first gear ring through the third clutch; the second sun gear is fixedly connected with the power input member, and the first gear ring is fixedly connected with the power output member;
the second clutch is connected between any two of the second ring gear, the second sun gear, and the second carrier.
Preferably, the third sun gear is fixedly connected with the transmission case.
Preferably, the third sun gear is fixedly connected with the transmission case through a spline or welding.
Preferably, one end of the first brake is connected with the first sun gear, and the other end of the first brake is connected with a transmission case; and the first planet carrier and the second gear ring are fixedly connected and then integrally connected with one end of the second brake, and the other end of the second brake is connected with the transmission box body.
Preferably, the first clutch, the second clutch, and the third clutch are multi-plate wet clutches or dog clutches.
Preferably, the first planet carrier and the second ring gear are fixedly connected through a spline or in a welding mode; the second planet carrier and the third gear ring are fixedly connected in a spline or welding mode; the second sun gear is fixedly connected with the power input member in a spline or welding mode; the first gear ring and the power output component are fixedly connected in a spline or welding mode.
As a preferred scheme, the first planet carrier, the second planet carrier and the third planet carrier are all provided with pin shafts, the first planet gear is mounted on the pin shaft of the first planet carrier through a bearing, the second planet gear is mounted on the pin shaft of the second planet carrier through a bearing, and the third planet gear is mounted on the pin shaft of the third planet carrier through a bearing.
Preferably, the first planet row, the second planet row and the third planet row are sequentially and transversely arranged.
Preferably, the first clutch is disposed on a side of the first planetary row remote from the second planetary row, the third clutch is disposed on a side of the third planetary row remote from the second planetary row, and the second clutch is disposed on a side of the first planetary row remote from the second planetary row or between the second planetary row and the third planetary row.
Preferably, the first brake and the second brake are disposed between the first clutch and the first planetary row.
Compared with the prior art, the three-planetary-row six-speed automatic transmission has the following advantages that:
1. the invention adopts three clutches and two brakes, reasonably combines and connects three planet rows, and can realize six forward gears and one reverse gear;
2. the number of the brakes is less than that of the clutches, and the fewer brakes not only can reduce the processing and manufacturing difficulty of the gearbox body, but also is beneficial to the light weight of the gearbox body, so that the whole gearbox is more compact; in addition, more clutches are adopted, so that the connection relation among the planet rows can be cut off under a specific gear position, the redundant planet rows do not participate in transmission, the oil mixing loss of the belt rows is reduced, and the efficiency is improved;
3. the arrangement of more clutches is beneficial to multi-speed expansion in a mode of adding a planet row or more operating pieces, and the clutches can be nested when the specific structural design is realized, so that the whole transmission structure is more compact.
Drawings
FIG. 1 is a schematic view of a connection structure of a three-planetary-row six-speed automatic transmission according to a first embodiment of the present invention;
FIG. 2 is a schematic illustration of a 1 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 3 is a schematic illustration of a 2 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 4 is a schematic illustration of a 3 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 5 is a schematic illustration of a 4 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 6 is a schematic illustration of a 5 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 7 is a schematic illustration of a6 speed power transmission path of a three planetary-row six speed automatic transmission according to a first embodiment of the present invention;
FIG. 8 is a schematic diagram of an R-speed power transmission path of a three planetary-row six-speed automatic transmission according to a first embodiment of the present invention;
FIG. 9 is a schematic view of a connecting structure of a three planetary-row six-speed automatic transmission according to a second embodiment of the invention;
FIG. 10 is a schematic connecting structure diagram of a three planetary-row six-speed automatic transmission according to a third embodiment of the invention;
wherein, 1, a first planet row; 11. a first ring gear; 12. a first planet gear; 13. a first sun gear; 14. a first carrier; 2. a second planet row; 21. a second ring gear; 22. a second planet wheel; 23. a second sun gear; 24. a second planet carrier; 3. a third planet row; 31. A third ring gear; 32. a third planet gear; 33. a third sun gear; 34. a third carrier; 4. A transmission case; b1, a first brake; b2, a second brake; c1, a first clutch; c2, a second clutch; c3 and a third clutch.
Detailed Description
The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
The invention preferably adopts three embodiments:
the first embodiment is as follows:
as shown in fig. 1, a three planetary-row six-speed automatic transmission includes a first planetary row 1, a second planetary row 2, a third planetary row 3, a first clutch C1, a second clutch C2, a third clutch C3, a first brake B1, a second brake B2, a power input member, and a power output member; the first planet row 1 comprises a first gear ring 11, a first planet wheel 12, a first sun wheel 13 and a first planet carrier 14; the second planet row 2 comprises a second ring gear 21, a second planet gear 22, a second sun gear 23 and a second planet carrier 24; the third planetary row 3 includes a third ring gear 31, a third planetary gear 32, a third sun gear 33, and a third carrier 34. Specifically, the first planetary gear 12 is externally engaged with the first sun gear 13 and internally engaged with the first ring gear 11, and the first planetary gear 12 is mounted on a pin shaft of the first carrier 14; the second planet gear 22 is externally meshed with the second sun gear 23 and internally meshed with the second gear ring 21, and the second planet gear 22 is arranged on a pin shaft of the second planet carrier 24; the third planetary gears 32 are externally engaged with the third sun gear 33 and internally engaged with the third ring gear 31, and the third planetary gears 32 are mounted on pins of the third carrier 34.
The first sun gear 13 is connected to one end of a first brake B1, and the first sun gear 13 is connected to the second sun gear 23 via a first clutch C1; the first planet carrier 14 is fixedly connected with the second ring gear 21 and then integrally connected with one end of a second brake B2; the second planet carrier 24 is fixedly connected with the third ring gear 31; the third sun gear 33 is stationary, the third carrier 34 is connected to the first ring gear 11 via the third clutch C3, the second sun gear 23 is fixedly connected to the power input member, and the first ring gear 11 is fixedly connected to the power output member. It should be noted that, because the second sun gear 23 is fixedly connected with the power input member, the first sun gear 13 can also be connected with the power input member through the first clutch C1, and even can be connected with the second sun gear 23 and the power input member at the same time, and all three connection modes are equivalent technical solutions; likewise, since the first ring gear 11 is fixedly connected with the power output member, the third carrier 34 can also be connected with the power output member through the third clutch C3, and even with both the power output member and the first ring gear 11.
The second clutch C2 is connected between the second ring gear 21 and the second sun gear 23, specifically, the second ring gear 21 is connected with the second sun gear 23 through the second clutch C2, so that the second planetary row 2 is integrally revolved when the second clutch C2 is closed. It should also be noted that, since the first carrier 14 is fixedly connected with the second ring gear 21, and the second sun gear 23 is fixedly connected with the power input member, there may be other equivalent technical solutions, such as the second ring gear 21 is connected with the power input member through the second clutch C2, the first carrier 14 is connected with the power input member through the second clutch C2, the first carrier 14 is connected with the second sun gear 23 through the second clutch C2, and so on.
Therefore, the six-speed automatic transmission with three planetary rows according to the embodiment can realize six forward gears and one reverse gear, and the specific operating logic is shown in table 1, wherein K is a characteristic parameter of a planetary row, the numerical value is equal to the ratio of the tooth number of the ring gear to the tooth number of the sun gear, K1 corresponds to the characteristic parameter of the first planetary row 1, K2 corresponds to the characteristic parameter of the second planetary row 2, and K3 corresponds to the characteristic parameter of the third planetary row 3.
TABLE 1
In order to facilitate the analysis of the power flow direction at each gear, fig. 2 to 8 show the power flow direction of six forward gears and one R gear in a simplified manner, and the specific transmission route of each gear is analyzed as follows:
(1)1, gear 1: when the third clutch C3 and the second brake B2 are closed, the speed ratio i1 is (1+ K2) ((1+ 1/K3)). In this gear, the engagement of the second brake B2 brakes the first carrier 14 and the second ring gear 21, so the 1-gear power transmission route is: the power is output from the second sun gear 23 → the second planetary gears 22 → the second carrier 24 → the third ring gear 31 → the third planetary gears 32 → the third carrier 34 → the third clutch C3 → the first ring gear 11, as shown in fig. 2.
(2) And 2, gear: when the third clutch C3 and the first brake B1 are closed, the speed ratio i1 ═ K3(1+ K1) (1+ K2) + K3(1+ K1+ K2))/(K3(1+ K1)). In this gear, the first sun gear 13 is braked by the closing of the first brake B1, so 2-gear is divided into two power transmission paths: power is output from the second sun gear 23 → the second planetary gear 22 → the second carrier 24 → the third ring gear 31 → the third planetary gear 32 → the third carrier 34 → the third clutch C3 → the first ring gear 11; and the power is output through the second sun gear 23 → the second planet gear 22 → the second ring gear 21 → the first planet carrier 14 → the first planet gear 12 → the first ring gear 11, as shown in fig. 3.
(3) And 3, gear shifting: when the first clutch C1 and the third clutch C3 are closed, the speed ratio i1 ═ K3(1+ K1) (1+ K2) + K3(1+ K1+ K2))/(K3(1+ K1+ K2)). Under this gear position, three planet row all participates in the transmission, and 3 grades divide three power transmission routes: power is input from the second sun gear 23 → the second planetary gear 22 → the second carrier 24 → the third ring gear 31 → the third planetary gear 32 → the third carrier 34 → the third clutch C3 → the first ring gear 11; power input by the second sun gear 23 → the second planetary gear 22 → the second ring gear 21 → the first carrier 14 → the first planetary gear 12 → the first ring gear 11; third, power is input from the second sun gear 23 → the first clutch C1 → the first sun gear 13 → the first planetary gear 12 → the first ring gear 11, and power is output, as shown in fig. 4.
(4)4, gear shifting: when the second clutch C2 and the third clutch C3 are closed, the speed ratio i1 is (1+ K3)/K3). In this gear, the engagement of the second clutch C2 causes the second planetary gear set 2 to participate in the transmission as a whole, 4-gear power transmission path: the power input → the second carrier 24 → the third ring gear 31 → the third planetary gear 32 → the third carrier 34 → the third clutch C3 → the first ring gear 11 is performed by the second planetary row 2 as a whole, and the power output is performed as specifically shown in fig. 5.
(5) And 5, gear shifting: when the first clutch C1 and the second clutch C2 are closed, the speed ratio i1 is equal to 1 for direct gear. In this gear, the simultaneous closing of the first clutch C1 and the second clutch C2 allows the first planetary line 1 and the second planetary line 2 to form a single revolution whole participating in the transmission, and the 5-gear power transmission route: the power input → the power output of the first ring gear 11 is performed by the rotation of the first planetary row 1 and the second planetary row 2 as a whole, as shown in fig. 6.
(6)6, gear 6: when the second clutch C2 and the first brake B1 are closed, an overdrive gear is achieved, and the speed ratio i1 is K1/(1+ K1). In this gear, the engagement of the second clutch C2 causes the second planetary gear set 2 to participate in transmission as a whole, the engagement of the first brake B1 causes the first sun gear 13 to brake, and the 6-speed power transmission route: the second planetary row 2 rotates as a whole and performs power input → the first carrier 14 → the first planetary gear 12 → the first ring gear 11 and performs power output, as shown in fig. 7.
(7) R is gear: when the first clutch C1 and the second brake B2 are closed, reverse gear is achieved, and the speed ratio i1 is-K1. In this gear, the engagement of the second brake B2 brakes the first carrier 14 and the second ring gear 21, and the R-range power transmission route: the second sun gear 23 input → the first clutch C1 → the first sun gear 13 → the first planetary gear 12 → the first ring gear 11, and performs power output, as specifically shown in fig. 8.
In the present embodiment, one end of the first brake B1 is connected to the first sun gear 13, and the other end of the first brake B1 is connected to the transmission case 4; the first carrier 14 and the second ring gear 21 are fixedly connected and then integrally connected to one end of a second brake B2, and the other end of the second brake B2 is connected to the transmission case 4. In fact, the first sun gear 13 is selectively connected with the transmission case 4 through the first brake B1, and the first planet carrier 14 is fixedly connected with the second ring gear 21 and then is selectively connected with the transmission case 4 through the second brake B2, so as to realize the six-speed gear shifting function.
In the process of executing each gear, the third sun gear 33 needs to be fixed, for example, if a brake is used to connect the third sun gear 33 with the transmission case 4, and the brake is kept in a closed state in the process of executing each gear to achieve the purpose of fixing the third sun gear 33, in the process of shifting, the brake will directly impact the transmission case 4 to affect the load condition of the transmission case 4, so as to avoid the problem that the brake directly impacts the transmission case 4 in the process of shifting, and further improve the load condition of the transmission case 4, in this embodiment, the third sun gear 33 is fixedly connected with the transmission case 4.
The first, second, and third clutches C1, C2, and C3 may be multi-plate wet clutches or dog clutches: the multi-plate wet clutch has the advantages of oil film protection, smooth and soft power transmission, long service life and the like; the dog clutch can transmit larger torque, has the characteristics of simple structure and small size, and can enable the whole transmission to be more compact in structure by using the dog clutch. In the present embodiment, a multiplate wet clutch is preferable.
In this embodiment, the first carrier 14 and the second ring gear 21 are fixedly connected by a spline or by welding; the second planet carrier 24 and the third gear ring 31 are fixedly connected in a spline or welding mode; the third sun gear 33 is fixedly connected with the transmission case 4 through a spline or a welding mode; the second sun gear 23 is fixedly connected with the power input member through a spline or in a welding mode; the first ring gear 11 and the power output component are fixedly connected through a spline or welding mode. The spline connection has the characteristic of uniform stress, has good guidance quality, and can bear larger load, thereby ensuring the stability and reliability of the transmission during power transmission; the welding can also ensure the stability and reliability of the transmission in power transmission.
In this embodiment, the first planet carrier 14, the second planet carrier 24, and the third planet carrier 34 are all provided with a pin, the first planet gear 12 is mounted on the pin of the first planet carrier 14 through a bearing, the second planet gear 22 is mounted on the pin of the second planet carrier 24 through a bearing, and the third planet gear 32 is mounted on the pin of the third planet carrier 34 through a bearing. In this way, the first planet gears 12, the second planet gears 22 and the third planet gears 32 can freely rotate on the respective planet carrier and can also rotate along with the respective planet carrier. The bearing may be a rolling bearing or a sliding bearing.
The first planet row 1, the second planet row 2 and the third planet row 3 are sequentially and transversely arranged. On this basis, the first clutch C1 is disposed on the side of the first planetary row 1 away from the second planetary row 2, the third clutch C3 is disposed on the side of the third planetary row 3 away from the second planetary row 2, and the second clutch C2 is disposed on the side of the first planetary row 1 away from the second planetary row 2; a first brake B1 and a second brake B2 are provided between the first clutch C1 and the first planetary row 1. The sequential arrangement can optimize the structural position relation among the planet carriers, the gear rings, the planet carriers and the operating elements (clutches and brakes), reduce the processing and manufacturing difficulty of the transmission, reduce the mutual interference among all structural components and further reduce the vibration and the noise generated by the transmission.
Example two
As shown in fig. 9, the difference from the first embodiment is that: the second clutch C2 is connected between the second sun gear 23 and the second carrier 24, that is, the second carrier 24 is connected to the second sun gear 23 via the second clutch C2, and the second clutch C2 is disposed between the second planetary row 2 and the third planetary row 3. It should be noted that, since the second planet carrier 24 is fixedly connected with the third ring gear 31, and the second sun gear 23 is fixedly connected with the power input member, there are also other equivalent technical solutions, such as the second planet carrier 24 is connected with the power input member through the second clutch C2, the third ring gear 31 is connected with the second sun gear 23 through the second clutch C2, the third ring gear 31 is connected with the power input member through the second clutch C2, and so on. These solutions all achieve the technical effect of making the second planetary row 2 revolve as a whole when the second clutch C2 is closed.
The specific operating logic of the second embodiment is the same as the specific operating logic of the first embodiment, the corresponding speed ratio is also the same, and the power flow directions of the second embodiment are the same as those of the first embodiment.
EXAMPLE III
As shown in fig. 10, the difference from the first embodiment is that: the second clutch C2 is connected between the second carrier 24 and the second ring gear 21, that is, the second carrier 24 is connected with the second ring gear 21 through the second clutch C2, and in addition, the second clutch C2 is disposed between the second planetary row 2 and the third planetary row 3. It should also be noted that, since the second planet carrier 24 is fixedly connected to the third ring gear 31, and the second ring gear 21 is fixedly connected to the first planet carrier 14, there may be other equivalent technical solutions, such as the second planet carrier 24 being connected to the first planet carrier 14 through the second clutch C2, the third ring gear 31 being connected to the second ring gear 21 through the second clutch C2, the third ring gear 31 being connected to the first planet carrier 14 through the second clutch C2, and so on. These solutions all achieve the technical effect of making the second planetary row 2 revolve as a whole when the second clutch C2 is closed.
The specific operating logic of the third embodiment is the same as the specific operating logic of the first embodiment, the corresponding speed ratio is also the same, and the power flow directions of the third embodiment are the same as those of the first embodiment.
In conclusion, the three clutches and the two brakes are adopted, the three planetary rows are reasonably combined and connected, and six forward gears and one reverse gear can be realized; in addition, the number of the brakes is less than that of the clutches, and the fewer brakes not only can reduce the processing and manufacturing difficulty of the transmission case 4, but also is beneficial to the light weight of the case, so that the whole transmission is more compact; moreover, under the condition of meeting the same number of speed ratios, the utilization rate of each brake can be obviously improved by the smaller number of brakes, so that the whole transmission is more compact; thirdly, more clutches are adopted, so that the connection relation among the planet rows can be cut off under a specific gear position, the redundant planet rows do not participate in transmission, the oil mixing loss of the belt rows is reduced, and the efficiency is improved; the arrangement of more clutches is beneficial to multi-speed expansion in a mode of adding a planet row or more operating pieces, and the clutches can be nested when the specific structural design is realized, so that the whole transmission structure is more compact.
The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.
Claims (10)
1. A three-planetary-row six-speed automatic transmission is characterized in that: the planetary gear set comprises a first planetary gear set, a second planetary gear set, a third planetary gear set, a first clutch, a second clutch, a third clutch, a first brake, a second brake, a power input component and a power output component; the first planet row comprises a first gear ring, a first planet wheel, a first sun gear and a first planet carrier; the second planet row comprises a second gear ring, a second planet wheel, a second sun wheel and a second planet carrier; the third planet row comprises a third gear ring, a third planet wheel, a third sun gear and a third planet carrier;
the first sun gear is connected with one end of the first brake, and the first sun gear is connected with the second sun gear through the first clutch; the first planet carrier is fixedly connected with the second gear ring and then integrally connected with one end of the second brake; the second planet carrier is fixedly connected with the third gear ring; the third sun gear is fixed, and the third planet carrier is connected with the first gear ring through the third clutch; the second sun gear is fixedly connected with the power input member, and the first gear ring is fixedly connected with the power output member;
the second clutch is connected between any two of the second ring gear, the second sun gear and the second carrier; the third clutch is arranged on one side of the third planetary row far away from the second planetary row.
2. The three planetary row six speed automatic transmission of claim 1, wherein: and the third sun gear is fixedly connected with the transmission box body.
3. The three planetary row six speed automatic transmission of claim 2, wherein: and the third sun gear is fixedly connected with the transmission box body in a spline or welding mode.
4. The three planetary row six speed automatic transmission of claim 1, wherein: one end of the first brake is connected with the first sun gear, and the other end of the first brake is connected with the transmission box; and the first planet carrier and the second gear ring are fixedly connected and then integrally connected with one end of the second brake, and the other end of the second brake is connected with the transmission box body.
5. The three-planetary-row six-speed automatic transmission according to any one of claims 1 to 4, characterized in that: the first clutch, the second clutch, and the third clutch are multi-plate wet clutches or dog clutches.
6. The three-planetary-row six-speed automatic transmission according to any one of claims 1 to 4, characterized in that: the first planet carrier and the second ring gear are fixedly connected in a spline or welding mode; the second planet carrier and the third gear ring are fixedly connected in a spline or welding mode; the second sun gear is fixedly connected with the power input member in a spline or welding mode; the first gear ring and the power output component are fixedly connected in a spline or welding mode.
7. The three-planetary-row six-speed automatic transmission according to any one of claims 1 to 4, characterized in that: the first planet carrier, the second planet carrier and the third planet carrier are all provided with pin shafts, the first planet wheel is installed on the pin shaft of the first planet carrier through a bearing, the second planet wheel is installed on the pin shaft of the second planet carrier through a bearing, and the third planet wheel is installed on the pin shaft of the third planet carrier through a bearing.
8. The three-planetary-row six-speed automatic transmission according to any one of claims 1 to 4, characterized in that: the first planet row, the second planet row and the third planet row are sequentially and transversely arranged.
9. The three planetary row six speed automatic transmission of claim 8, wherein: the first clutch is arranged on one side of the first planetary row far away from the second planetary row, and the second clutch is arranged on one side of the first planetary row far away from the second planetary row or between the second planetary row and the third planetary row.
10. The three planetary row six speed automatic transmission of claim 9, wherein: the first brake and the second brake are disposed between the first clutch and the first planetary row.
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| CN201710514253.4A CN107269779B (en) | 2017-06-29 | 2017-06-29 | Three-planet-row six-speed automatic transmission |
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| CN201710514253.4A CN107269779B (en) | 2017-06-29 | 2017-06-29 | Three-planet-row six-speed automatic transmission |
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| CN107269779B true CN107269779B (en) | 2021-10-26 |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108194586B (en) * | 2017-12-29 | 2022-06-21 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN108194587B (en) * | 2017-12-29 | 2021-10-26 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN108180265B (en) * | 2017-12-29 | 2021-12-24 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN108278335B (en) * | 2018-03-13 | 2023-08-11 | 广州汽车集团股份有限公司 | Multi-clutch module, clutch oil supply system and electric control hydraulic automatic transmission |
| CN108916326A (en) * | 2018-07-05 | 2018-11-30 | 柳州职业技术学院 | The new 8 speed automobile automatic transmission of one kind and its power transmission scheme |
| CN109469716A (en) * | 2018-12-13 | 2019-03-15 | 贵州凯星液力传动机械有限公司 | A kind of six gear gears of php slurry |
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