CN109139827B - Three-front three-reverse planetary automatic transmission - Google Patents
Three-front three-reverse planetary automatic transmission Download PDFInfo
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- CN109139827B CN109139827B CN201811268805.9A CN201811268805A CN109139827B CN 109139827 B CN109139827 B CN 109139827B CN 201811268805 A CN201811268805 A CN 201811268805A CN 109139827 B CN109139827 B CN 109139827B
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- row
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- planet
- planetary
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 60
- 102100026049 CDP-diacylglycerol-glycerol-3-phosphate 3-phosphatidyltransferase, mitochondrial Human genes 0.000 claims description 16
- 101000692362 Homo sapiens CDP-diacylglycerol-glycerol-3-phosphate 3-phosphatidyltransferase, mitochondrial Proteins 0.000 claims description 16
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000969 carrier Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Classifications
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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
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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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
- F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three 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
- F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three 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
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a planetary automatic transmission with three forward gears and three reverse gears, which is suitable for a large-scale loader. Specifically, there are four planetary rows, four brakes, one clutch, and five transmission members. The automatic transmission adopts the scheme of four planet rows, four brakes and one clutch, and realizes three forward gears and three reverse gears. The structure is simple, and the transmission is stable and reliable; the transmission ratio range is wide, and the operation under different working conditions is convenient.
Description
Technical Field
The invention relates to a transmission device in the field of machinery, in particular to a three-front three-reverse planetary transmission for a vehicle driving system.
Background
Engineering machinery such as loaders, bulldozers, excavators, and underground dump trucks require a transmission with a medium-low vehicle speed and the same forward and reverse vehicle speeds. The use of the three-front three-reverse planetary transmission on engineering machinery can improve the productivity and prolong the service life of the machine.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the automatic transmission has the advantages of same forward and reverse speeds, better performance and capability of meeting the use requirements of engineering machinery vehicles.
The technical scheme of the invention is realized as follows:
a three-front three-reverse planetary automatic transmission comprises a planetary row, an input member, an output member, a transmission member, a brake and a clutch, wherein the input member and the output member are arranged at two ends and are respectively connected with an input shaft and an output shaft;
the number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS 4;
the number of the transmission members is five, and the transmission members are respectively a first transmission member, a second transmission member, a third transmission member, a fourth transmission member and a fifth transmission member;
the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4;
the clutch is a clutch C;
the input member is connected with the sun gear S1 of the planetary row PGS 1;
the output member is connected with the sun gear S3 of the planetary row PGS3, the sun gear S4 of the planetary row PGS4 and the outer hub of the clutch C;
the first drive member connects the ring gear R1 of row PGS1, the inner hub of brake B1 and the sun gear S2 of row PGS 2;
the second transmission member is connected with the carrier CA1 of the planetary row PGS1, the carrier CA2 of the planetary row PGS2 and the carrier CA3 of the planetary row PGS 3;
the third drive member connects the ring gear R2 of the planet row PGS2 and the inner hub of the brake B2;
the fourth transmission member connects the inner hub of brake B3, the ring gear R3 of row PGS3 and the carrier CA4 of row PGS 4;
the fifth transfer member connects the inner hub of brake B4, ring gear R4 of row PGS4, and the inner hub of clutch C.
The transmission member includes various existing transmission structures, such as the simplest shaft, gear transmission structure.
The planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are simple planet rows, namely, the four planet rows are simple planet rows, and each planet row comprises a sun gear, a gear ring and a planet carrier.
The brakes B1-B4 and the clutch C are multi-plate friction control pieces.
Compared with the prior art, the automatic transmission adopts the scheme of four planetary rows, four brakes and one clutch to realize three forward gears and three reverse gears. The three reverse gears satisfy a traction force and a speed variation range for the reverse running of the vehicle, and productivity can be improved. The four planet rows are simple planet rows, the structure is not complex, the manufacture is easy, the use is reliable, and the service life is long.
Drawings
FIG. 1 is a schematic diagram of the connection of the components of a three-forward three-reverse planetary automatic transmission of the present invention;
in the figure, PGS1 to PGS4 are planetary rows, S1 to S4 are sun gears, R1 to R4 are ring gears, CA1 to CA4 are carriers, B1 to B4 are brakes, C is a clutch, 1 is an input member, 2 is an output member, and 3 to 7 are transmission members.
Detailed Description
The invention will be further described with reference to the following drawings and specific examples:
as shown in fig. 1, the planetary automatic transmission according to the present embodiment is suitable for use in construction machines such as bulldozers and loaders. Wherein the planetary rows are arranged in a sequence, the planetary rows are connected by a transmission member, and the input shaft is connected to an input member 1, typically a turbine shaft of a torque converter, for transmitting power from an engine through the torque converter to a transmission. The output shaft is connected with the output member 2, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential. The transmission is completely symmetrical about the center of rotation, and the lower half of the center of rotation is omitted from fig. 1 and will not be described further.
Planetary row PGS1 includes three rotary members, sun gear S1, ring gear R1 and carrier CA1, sun gear S1 is connected to input member 1 for power input, and ring gear R1 is braked by brake B1 so that carrier CA1 acts as an intermediate output member to decelerate the rotational speed of input member 1 for output.
Planetary row PGS2 includes three rotating elements, i.e., sun gear S2, ring gear R2, and carrier CA2, and is configured to brake ring gear R2 by brake B2 in a reduction gear so that carrier CA2 outputs the rotation speed of sun gear S2 at a reduced speed as an intermediate output element, or to brake sun gear S2 by brake B1 so that carrier CA2 outputs rotation speed 1:1 as an intermediate output element.
Planetary row PGS3 includes three rotary members of sun gear S3, ring gear R3 and carrier CA3, and ring gear R3 is braked by brake B3 so that sun gear S3 serves as an output member to increase the rotational speed of carrier CA3 and output it.
Planetary row PGS4 includes three rotary members of sun gear S4, ring gear R4 and carrier CA4, and ring gear R4 is braked by brake B4 so that sun gear S4 serves as an output member to increase the rotational speed of carrier CA3 and output it.
The brake B1 is used for braking the first transmission member 3, the brake B2 is used for braking the third transmission member 5, the brake B3 is used for braking the fourth transmission member 6, and the brake B4 is used for braking the fifth transmission member 7.
The clutch C is used to connect the output member 2 and the fifth transmission member 7. The brakes B1 to B4 and the clutch C are generally multi-plate friction actuators, and are pressurized by a piston driven by hydraulic oil. The operating schemes for the various gears are implemented as shown in the following table.
Table 1 schematic representation of three-forward three-reverse planetary transmission implementation modes and corresponding transmission ratios:
in the table, "O" indicates the manipulator engagement.
An example of the present invention is described in detail below with reference to fig. 1 and table 1, wherein the transmission ratio described herein refers to the ratio of input shaft speed to output shaft speed.
When brake B1 and clutch C are engaged, the input member 1 is connected for rotation with the sun gear S1 of the planetary row PGS1 and the output member 2 outputs the rotational speed of the transmission member 4 in a 1:1 ratio to achieve "forward gear I".
When brake B1 and brake B4 are engaged, the sun gear S1 of the input member 1, which is connected to the planetary row PGS1, rotates, and the fifth transmission member 7, brakes to achieve "forward gear ii" which is a smaller gear ratio than "forward gear i".
When brake B1 and brake B3 are engaged, the sun gear S1 of the input member 1, which is connected to the planetary row PGS1, rotates, and the fourth transmission member 6 is braked, thereby achieving "forward gear iii" which is a smaller gear ratio than "forward gear ii".
When brake B2 and brake C are engaged, the input member 1 is connected for rotation with the sun gear S1 of the planetary row PGS1 and the first transmission member 3 is braked to effect "reverse gear I".
When brake B2 and brake B4 are engaged, the sun gear S1 of the input member 1, which is connected to the planet row PGS1, rotates, and the third transmission member 5 is braked, thereby effecting a "reverse gear II" which is a smaller gear ratio than "reverse gear I".
When brake B2 and brake B3 are engaged, the sun gear S1, which is connected to the planet row PGS1 of the input member 1, rotates, and the fourth transmission member 6 is braked "reverse gear III", which is a smaller ratio than "reverse gear II".
The gear ratios of the gears are determined by the k values of the four planetary rows.
The four planet rows PGS 1-PGS 4 in the scheme are single-planet simple planet rows, and the production is simple.
Although the embodiments of the present invention have been described in detail with reference to the accompanying drawings, the present invention is not limited to the specific embodiments, and various equivalent and modified processes performed by those skilled in the art according to the specific embodiments are also within the scope of the present invention.
Claims (3)
1. The utility model provides a three first three reverse planet automatic gearbox, includes the planet row, installs at both ends and respectively with input shaft, output shaft connected input member (1) and output member (2), drive member, stopper and clutch, its characterized in that:
the number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS 4;
the number of the transmission components is five, and the transmission components are respectively a first transmission component (3), a second transmission component (4), a third transmission component (5), a fourth transmission component (6) and a fifth transmission component (7);
the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; the clutch is a clutch C;
the input member (1) is connected with the sun gear S1 of the planetary row PGS 1;
the output member (2) connects the sun gear S3 of the planetary row PGS3, the sun gear S4 of the planetary row PGS4 and the outer hub of the clutch C;
the first transmission member (3) connects the ring gear R1 of the row PGS1, the inner hub of the brake B1 and the sun gear S2 of the row PGS 2;
the second transmission member (4) is connected with a carrier CA1 of a planetary row PGS1, a carrier CA2 of a planetary row PGS2 and a carrier CA3 of a planetary row PGS 3;
the third transmission member (5) connects the ring gear R2 of the planetary row PGS2 and the inner hub of the brake B2;
the fourth transmission member (6) connects the inner hub of brake B3, the ring gear R3 of row PGS3 and the carrier CA4 of row PGS 4;
the fifth transfer member (7) connects the inner hub of brake B4, ring gear R4 of row PGS4 and the inner hub of clutch C.
2. A three-front three-reverse planetary automatic transmission according to claim 1, characterized in that: the planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are single planet simple rows.
3. A three-front three-reverse planetary automatic transmission according to claim 1, characterized in that: the brakes B1-B4 and the clutch C are multi-plate friction control pieces.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811268805.9A CN109139827B (en) | 2018-10-29 | 2018-10-29 | Three-front three-reverse planetary automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811268805.9A CN109139827B (en) | 2018-10-29 | 2018-10-29 | Three-front three-reverse planetary automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109139827A CN109139827A (en) | 2019-01-04 |
| CN109139827B true CN109139827B (en) | 2021-03-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811268805.9A Active CN109139827B (en) | 2018-10-29 | 2018-10-29 | Three-front three-reverse planetary automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109139827B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4038887A (en) * | 1973-02-26 | 1977-08-02 | Aisin Seiki Kabushiki Kaisha | Speed change gear |
| CN102913597A (en) * | 2012-10-16 | 2013-02-06 | 中国北方车辆研究所 | Seven-level planet automatic speed changer |
| CN103573938A (en) * | 2012-06-22 | 2014-02-12 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN106763568A (en) * | 2016-12-16 | 2017-05-31 | 贵州凯星液力传动机械有限公司 | A kind of six keep off planetary automatic transmission |
| CN106870655A (en) * | 2015-12-10 | 2017-06-20 | 现代自动车株式会社 | For the epicyclic train of the automatic transmission of vehicle |
| CN108223717A (en) * | 2016-12-14 | 2018-06-29 | 现代自动车株式会社 | For the planetary gear train of vehicle automatic speed variator |
-
2018
- 2018-10-29 CN CN201811268805.9A patent/CN109139827B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4038887A (en) * | 1973-02-26 | 1977-08-02 | Aisin Seiki Kabushiki Kaisha | Speed change gear |
| CN103573938A (en) * | 2012-06-22 | 2014-02-12 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN102913597A (en) * | 2012-10-16 | 2013-02-06 | 中国北方车辆研究所 | Seven-level planet automatic speed changer |
| CN106870655A (en) * | 2015-12-10 | 2017-06-20 | 现代自动车株式会社 | For the epicyclic train of the automatic transmission of vehicle |
| CN108223717A (en) * | 2016-12-14 | 2018-06-29 | 现代自动车株式会社 | For the planetary gear train of vehicle automatic speed variator |
| CN106763568A (en) * | 2016-12-16 | 2017-05-31 | 贵州凯星液力传动机械有限公司 | A kind of six keep off planetary automatic transmission |
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| Publication number | Publication date |
|---|---|
| CN109139827A (en) | 2019-01-04 |
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| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
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| CP03 | Change of name, title or address |
Address after: 550000 Gaoping Electromechanical Industrial Park, Huichuan District, Zunyi City, Guizhou Province Patentee after: Guizhou Aerospace Kaixing Intelligent Transmission Co.,Ltd. Country or region after: China Address before: 563003 Guizhou Aerospace hi tech Industrial Park, Dalian Road, Huichuan District, Zunyi City, Guizhou Province (Zunyi Park) Patentee before: GUIZHOU WINSTAR HYDRAULIC TRANSMISSION MACHINERY Co.,Ltd. Country or region before: China |
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| CP03 | Change of name, title or address |