CN111550533A - Six-gear planetary automatic transmission - Google Patents
Six-gear planetary automatic transmission Download PDFInfo
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- CN111550533A CN111550533A CN202010236473.7A CN202010236473A CN111550533A CN 111550533 A CN111550533 A CN 111550533A CN 202010236473 A CN202010236473 A CN 202010236473A CN 111550533 A CN111550533 A CN 111550533A
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- Prior art keywords
- clutch
- connecting member
- row
- planetary
- gear
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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
- 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
- F16H2200/20—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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides a six-gear planetary automatic transmission of a vehicle driving system, and belongs to the technical field of vehicle transmission. The transmission comprises three planet rows, an input member, an output member, connecting members, brakes and clutches, wherein the input member and the output member are arranged at two ends of each planet row and are respectively connected with an input shaft and an output shaft, and the number of the planet rows is three, the number of the connecting members is four, the number of the brakes is two, and the number of the clutches is three. Compared with the prior art, the automatic transmission adopts the scheme of three planet rows, two brakes and three clutches, and realizes six forward gears and one reverse gear. The invention is convenient for realizing simple gear shift control and compact structure, and reduces the control difficulty and the volume and weight of the automatic transmission.
Description
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to a six-gear planetary automatic transmission for a road or non-road vehicle.
Background
As a planetary automatic transmission for a vehicle, power of an internal combustion engine or the like is transmitted to an input shaft of the planetary automatic transmission through a torque converter, and after shifting according to a current gear, the power is output from an output shaft and transmitted to left and right drive wheels through a differential, and most of the transmission is composed of a plurality of planetary rows, a brake and a clutch. At present, a mainstream six-gear planetary automatic transmission for a vehicle is basically realized by three planetary rows, three brakes and two clutches, and the brakes occupy more space of a shell and have larger volume and weight; for this reason, a six-speed planetary automatic transmission that uses fewer brakes to achieve smaller size and weight is sought.
Disclosure of Invention
The invention aims to provide a six-gear planetary automatic transmission for a vehicle, which realizes six forward gears and one reverse gear by using three planetary rows, two brakes and three clutches, reduces the space size and weight of a product and meets the use requirement of the vehicle.
The invention provides a six-gear planetary automatic transmission, which comprises a planetary row, an input member 1 and an output member 2, a connecting member, a brake and a clutch, wherein the input member 1 and the output member 2 are arranged at two ends of the planetary row and are respectively connected with an input shaft and an output shaft; the three planet rows are respectively a planet row PGS1, a planet row PGS2 and a planet row PGS 3; the number of the connecting members is four, namely a connecting member 3, a connecting member 4, a connecting member 5 and a connecting member 6; the two brakes are respectively a brake B1 and a brake B2; there are three clutches, clutch C1, clutch C2, and clutch C3.
The sun gear S1, carrier CA1 and ring gear R1 of the planetary row PGS1 are connected to the connecting member 3, connecting member 5 and the housing, respectively;
the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 5, connecting member 4 and output member 2, respectively;
the sun gear S3, carrier CA3 and ring gear R3 of the row PGS3 are connected to the connecting member 6, output member 2 and connecting member 4, respectively;
the input member 1 connects the inner hub of clutch C1, the outer hub of clutch C2 and the outer hub of clutch C3;
the output member 2 connects the ring gear R2 of row PGS2 with the carrier CA3 of row PGS 3;
the connecting member 3 connects the sun gear S1 of the planetary row PGS1, the inner hub of the brake B1 and the inner hub of the clutch C2;
the connecting member 4 connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B2 and the inner hub of clutch C3;
the connecting member 5 connects the carrier CA1 of the planetary row PGS1 and the sun gear S2 of the planetary row PGS 2;
the connecting member 6 connects the sun gear S3 of the planetary row PGS3 with the outer hub of the clutch C1;
the brake B1 is used for braking the connecting member 3;
the brake B2 is used for braking the connecting member 4;
the clutch C1 connects the connecting member 6 with the input member 1;
the clutch C2 connects the input member 1 with the connecting member 3;
the clutch C3 connects the input member 1 with the connecting member 4.
Has the advantages that:
the six-gear planetary automatic transmission adopts the scheme of three planetary rows, two brakes and three clutches to realize six forward gears and one reverse gear, and the number of brakes is less. K values of the three planet rows are within a range of 1.7-2.6, so that a compact structure is convenient to realize, and the volume and the weight of the automatic transmission are reduced.
Drawings
FIG. 1 is a schematic diagram showing the connection of the components of a six-speed planetary automatic transmission according to the present invention,
in the figure, PGS 1-PGS 3 are three planetary rows, S1-S3 are three sun gears, CA 1-CA 3 are three planetary carriers, R1-R3 are three gear rings, B1-B2 are two brakes, C1-C3 are three clutches, 1 is an input member, 2 is an output member, and 3-6 are four connecting members.
Detailed Description
The invention is described in detail below by way of example with reference to the accompanying drawings.
The six-gear planetary automatic transmission is suitable for a vehicle transmission system. Wherein the planetary rows are arranged in a sequence, the planetary rows are connected by a connecting member, and the input shaft is connected to an input member 1, typically a turbine shaft of a torque converter, for transmitting power of an engine to the planetary automatic transmission through the torque converter. 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 planetary automatic transmission is completely symmetrical with respect to the rotation center, and the lower half of the rotation center is omitted in fig. 1, and will not be described below.
The six-speed planetary automatic transmission shown in fig. 1 includes a planetary row, an input member 1 and an output member 2 mounted at both ends to be connected to an input shaft and an output shaft, respectively, a connecting member, a brake, and a clutch. Three planet rows are provided, namely a planet row PGS1, a planet row PGS2 and a planet row PGS 3; the number of the connecting members is four, namely a connecting member 3, a connecting member 4, a connecting member 5 and a connecting member 6; the two brakes are respectively a brake B1 and a brake B2; there are three clutches, clutch C1, clutch C2, and clutch C3.
Each planet row comprises a sun gear, a planet carrier and a gear ring.
The sun gear S1, carrier CA1 and ring gear R1 of the planetary row PGS1 are connected to the connecting member 3, connecting member 5 and the housing, respectively;
the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the connecting member 5, connecting member 4 and output member 2, respectively;
the sun gear S3, carrier CA3 and ring gear R3 of the row PGS3 are connected to the connecting member 6, output member 2 and connecting member 4, respectively;
the input member 1 connects the inner hub of clutch C1, the outer hub of clutch C2 and the outer hub of clutch C3;
the output member 2 connects the ring gear R2 of row PGS2 with the carrier CA3 of row PGS 3;
the connecting member 3 connects the sun gear S1 of the planetary row PGS1, the inner hub of the brake B1 and the inner hub of the clutch C2;
the connecting member 4 connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B2 and the inner hub of clutch C3;
the connecting member 5 connects the carrier CA1 of the planetary row PGS1 and the sun gear S2 of the planetary row PGS 2;
the connecting member 6 connects the sun gear S3 of the planetary row PGS3 with the outer hub of the clutch C1;
the brake B1 is used for braking the connecting member 3;
the brake B2 is used for braking the connecting member 4;
the clutch C1 connects the connecting member 6 with the input member 1;
the clutch C2 connects the input member 1 with the connecting member 3;
the clutch C3 connects the input member 1 with the connecting member 4.
The planet row PGS1, the planet row PGS2 and the planet row PGS3 are all single planet rows.
The brakes B1-B2 and the clutches C1-C3 are multi-plate friction control pieces, and hydraulic oil is used for driving pistons to pressurize; it may also be a sliding sleeve or coupling or dog clutch or other controllable selective disengagement and engagement means. The operating scheme for each gear is shown in table 1.
TABLE 1 schematic diagram of six-gear planetary automatic transmission each gear implementation mode and corresponding transmission ratio and inter-ratio
In the table ". smallcircle" indicates the handling member engagement
Referring now to fig. 1 and table 1, an example of the present invention will be described in detail, wherein the transmission ratio is the ratio of the input shaft speed to the output shaft speed, and the k value of the planetary row is the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear of the planetary row.
When clutch C1 and brake B2 are engaged, the connecting member 6 and the input member 1 rotate as a unit and the connecting member 4 brakes to achieve first gear "1 st".
When clutch C1 and brake B1 are engaged, connecting member 6 and input member 1 rotate as a unit and connecting member 3 brakes to achieve "2 nd" gear.
When clutch C1 and clutch C2 are engaged, connecting member 6 and input member 1 rotate integrally, and input member 1 and connecting member 3 rotate integrally, achieving third gear "3 rd".
When clutch C1 and clutch C3 are engaged, coupling member 6 and input member 1 rotate as a unit, and input member 1 and coupling member 4 rotate as a unit, achieving four gear "4 th".
When clutch C2 and clutch C3 are engaged, input member 1 and coupling member 3 rotate as a unit, and input member 1 and coupling member 4 rotate as a unit, thereby implementing fifth gear "5 th".
When clutch C3 and brake B1 are engaged, the input member 1 and coupling member 4 rotate in unison and coupling member 3 brakes to achieve six gear "6 th".
When clutch C2 and brake B2 are engaged, the input member 1 and connecting member 3 rotate as a unit and connecting member 4 brakes to achieve reverse gear "Rev".
The gear ratios of the gears are determined by the k values of the three planetary rows. For example, when k1 ≈ 1.712, k2 ≈ 1.738, and k3 ≈ 2.510, the gear ratios of the respective gears shown in table 1 can be obtained, and the total gear ratio range (3.510/0.635) of the forward gears reaches 5.528, so that an appropriate gear ratio range is obtained. The k values of the PGS 1-PGS 3 of the planet rows are within the range of 1.7-2.6, the radial sizes of the three PGS 1-PGS 3 of the planet rows are small, only two brakes and three clutches are needed, and the compact structure is convenient to realize. Meanwhile, the operating scheme of each gear in the table 1 shows that only one operating piece needs to be switched for each gear shifting, so that simple gear shifting control is realized conveniently, and the control difficulty is reduced.
In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (2)
1. A six-gear planetary automatic transmission comprises a planetary row, an input member (1) and an output member (2) which are respectively connected with an input shaft and an output shaft at two ends, a connecting member, a brake and a clutch, and is characterized in that: three planet rows are provided, namely a planet row PGS1, a planet row PGS2 and a planet row PGS 3; the number of the connecting components is four, and the connecting components are respectively a connecting component (3), a connecting component (4), a connecting component (5) and a connecting component (6); the number of the brakes is two, namely a brake B1 and a brake B2; the number of the clutches is three, namely a clutch C1, a clutch C2 and a clutch C3;
the sun gear S1, the carrier CA1 and the ring gear R1 of the planetary row PGS1 are connected with the connecting member (3), the connecting member (5) and the housing, respectively;
the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected to the connecting member (5), connecting member (4) and output member (2), respectively;
the sun gear S3, carrier CA3 and ring gear R3 of the planetary row PGS3 are connected to the connecting member (6), output member (2) and connecting member (4), respectively;
the input member (1) connects the inner hub of clutch C1, the outer hub of clutch C2, and the outer hub of clutch C3;
the output member (2) connects the ring gear R2 of the row PGS2 with the carrier CA3 of the row PGS 3;
the connecting member (3) connects the sun gear S1 of the planetary row PGS1, the inner hub of the brake B1 and the inner hub of the clutch C2;
the connecting member (4) connects carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B2 and the inner hub of clutch C3;
the connecting member (5) connects the carrier CA1 of the planetary row PGS1 and the sun gear S2 of the planetary row PGS 2;
the connecting member (6) connects the sun gear S3 of the planetary row PGS3 and the outer hub of the clutch C1;
the brake B1 is used for braking the connecting component (3);
the brake B2 is used for braking the connecting component (4);
the clutch C1 connects the connecting member (6) and the input member (1);
the clutch C2 connects the input member (1) and the connecting member (3);
the clutch C3 connects the input member (1) and the connecting member (4).
2. The six-speed planetary automatic transmission according to claim 1, characterized in that: the planet row PGS1, the planet row PGS2 and the planet row PGS3 are all single planet rows.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010236473.7A CN111550533A (en) | 2020-03-30 | 2020-03-30 | Six-gear planetary automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010236473.7A CN111550533A (en) | 2020-03-30 | 2020-03-30 | Six-gear planetary automatic transmission |
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| Publication Number | Publication Date |
|---|---|
| CN111550533A true CN111550533A (en) | 2020-08-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010236473.7A Pending CN111550533A (en) | 2020-03-30 | 2020-03-30 | Six-gear planetary automatic transmission |
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| Country | Link |
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| CN (1) | CN111550533A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101021254A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN103511565A (en) * | 2013-10-17 | 2014-01-15 | 中国北方车辆研究所 | Automatic six-gear planetary transmission |
| DE102016212366A1 (en) * | 2016-07-07 | 2018-01-11 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN207278803U (en) * | 2017-09-21 | 2018-04-27 | 广州汽车集团股份有限公司 | Six speed automatic transmissions and automobile |
| CN108131428A (en) * | 2017-10-18 | 2018-06-08 | 中国北方车辆研究所 | One kind six keeps off planetary automatic transmission |
| WO2020038633A1 (en) * | 2018-08-20 | 2020-02-27 | Daimler Ag | Hybrid drive device |
-
2020
- 2020-03-30 CN CN202010236473.7A patent/CN111550533A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101021254A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN103511565A (en) * | 2013-10-17 | 2014-01-15 | 中国北方车辆研究所 | Automatic six-gear planetary transmission |
| DE102016212366A1 (en) * | 2016-07-07 | 2018-01-11 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN207278803U (en) * | 2017-09-21 | 2018-04-27 | 广州汽车集团股份有限公司 | Six speed automatic transmissions and automobile |
| CN108131428A (en) * | 2017-10-18 | 2018-06-08 | 中国北方车辆研究所 | One kind six keeps off planetary automatic transmission |
| WO2020038633A1 (en) * | 2018-08-20 | 2020-02-27 | Daimler Ag | Hybrid drive device |
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| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200818 |
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| RJ01 | Rejection of invention patent application after publication |