CN105422786A - Transmission mechanism of loading machine - Google Patents
Transmission mechanism of loading machine Download PDFInfo
- Publication number
- CN105422786A CN105422786A CN201510943896.1A CN201510943896A CN105422786A CN 105422786 A CN105422786 A CN 105422786A CN 201510943896 A CN201510943896 A CN 201510943896A CN 105422786 A CN105422786 A CN 105422786A
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- grade
- low
- gear
- hub
- regime clutch
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/065—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the friction or endless flexible member type
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention relates to a transmission mechanism of a loading machine. A high-gear clutch assembly and a low-gear clutch assembly are added in a loading machine system, the problems of a high fault rate and low efficiency of a transmission mechanism adopted by a conventional loading machine are solved, the model selection range of a hydraulic torque converter is broadened, and the loading machine is converted from hydrodynamic transmission to mechanical transmission under the working condition of a high speed ratio. The working efficiency is improved, the energy consumption is reduced, and the purposes of high efficiency and energy saving are achieved.
Description
Technical field
The present invention relates to a kind of driving mechanism, be applicable to high, medium and low difference configuration loader, also the driving mechanism of alternative high end loader even can realize the upgrading of other loader transmission mechanism.
Background technique
Existing loader transmission mechanism comprises twin-turbine torque converter and Planetary Power Shift Gearbox structure (two last backstops).Twin-turbine torque converter rate of fault is high, whole efficiency is low.Loader is in actual job, and frequently, in Planetary Power Shift Gearbox, the large free wheel device of supporting pair of hydrotransmitter use is hit greatly in change working, and rate of fault is high for low-speed heave-load and high speed light loading change working.Large free wheel device maintenance inconvenience, cost intensive.For the mating parts that roller, isolating ring, outer ring gear and inner ring gear these 4 is accurate, there is 1 damage, the quality of other parts will be affected, so 1 damage just should be changed together, change separately and cannot ensure reliability.
Summary of the invention
High in order to solve the drive failure rate that existing loader adopts, inefficient problem, the invention provides a kind of driving mechanism, be applicable to domestic high, medium and low difference configuration loader, also the driving mechanism of alternative high end loader even can realize the upgrading of other loader transmission mechanism.
Solving the problems of the technologies described above adopted technological scheme is:
A kind of loader transmission mechanism, its special way is: comprise three element fluid torque converters, high-gear clutch assembly and low regime clutch assembly;
Described three element fluid torque converters comprise hubcap, turbine, guide wheel, pump impeller;
Described high-gear clutch assembly comprises high-grade outer hub, the first high-grade gear, high-grade piston, high-grade friction plate, high-grade separator, high-grade disc spring, high-grade interior hub and the second high-grade gear;
Described low regime clutch assembly comprises low-grade outer hub, the first low regime clutch, low-grade piston, low-grade friction plate, low-grade separator, low-grade disc spring, low-grade interior hub and the second low regime clutch;
The output shaft of three element fluid torque converters is fixedly connected with the first low regime clutch in low regime clutch assembly; Described first low regime clutch is fixedly connected with the outer hub of low grade; The outer hub of described low grade and low-grade separator are by spline pair transmitting torque; Described low-grade separator and low-grade friction plate are by frictional force transmitting torque; In described low-grade friction plate and low grade, hub is by spline pair transmitting torque; In described low grade, hub is fixedly connected with the second low regime clutch;
Described second low regime clutch and the second high-grade gears meshing; Described first high-grade gear is fixedly connected with transmission input shaft; Described second high-grade gear is fixedly connected with the outer hub of top grade; The outer hub of described top grade and high-grade separator are by spline pair transmitting torque; Described high-grade separator and high-grade friction plate are by frictional force transmitting torque; In described high-grade friction plate and top grade, hub is by spline pair transmitting torque; In described top grade, hub is fixedly connected with the second high-grade gear; Described second high-grade gear engages with the first low regime clutch.
Above-mentioned three element fluid torque converters are single-stage monomial fluid torque converter, band coupling converter coupling or closed-end hydraulic torque converter.
The advantage that the present invention has:
1, the present invention owing to increasing high-gear clutch and low regime clutch assembly in system of loaders, widen the type selecting scope of fluid torque converter, make loader under the operating mode of high speed ratio, mechanical transmission is converted to by hydraudynamic drive, mention working efficiency, reduce energy consumption, to reach efficient, energy-conservation object.
2, the present invention is owing to adopting rational structural design, reach usage requirement, for the selection diversification of torque-converters, go for domestic high, medium and low difference configuration loader, also the driving mechanism of alternative high end loader even can realize the upgrading of other loader transmission mechanism, make car load power matching more rationally, oil consumption Economy is higher.
Accompanying drawing explanation
Fig. 1 is transmission principle figure of the present invention;
Fig. 2 is three element torque-converters structural drawing;
Fig. 3 is high-gear clutch assembly assumption diagram;
Fig. 4 is low regime clutch assembly assumption diagram;
Wherein reference character is: 1-hubcap, 2-turbine, 3-guide wheel, 4-pump impeller, the high-grade piston of 11-, the high-grade disc spring of 12-, the high-grade gear of 13-first, the high-grade friction plate of 14-, the high-grade separator of 15-, the outer hub of 16-top grade, hub in 17-top grade, the high-grade gear of 18-second, the low-grade disc spring of 21-, 22-second low regime clutch, hub in 23-low grade, the outer hub of 24-low grade, the low-grade friction plate of 25-, the low-grade separator of 26-, 27-first low regime clutch, the low-grade piston of 28-.
Embodiment
As shown in Figure 1, a kind of loader transmission mechanism, comprises three element fluid torque converters, high-gear clutch assembly and low regime clutch assembly;
As shown in Figure 2, three element fluid torque converters comprise hubcap, turbine, guide wheel, pump impeller;
The output shaft of three element fluid torque converters is fixedly connected with by the mode of electron beam welding with the first low regime clutch in low regime clutch assembly, direct transmitting torque; First low regime clutch is fixedly connected with by the mode of electron beam welding with the outer hub of low grade, direct transmitting torque; Low-grade outer hub and low-grade separator are by spline pair transmitting torque; Low-grade separator and low-grade friction plate are by frictional force transmitting torque; Low-grade friction plate passes through spline pair transmitting torque with hub in low grade; Hub and the second low regime clutch Integral design in low-grade, direct transmitting torque; Second low regime clutch and the second high-grade gears meshing, by gear pair transmitting torque; First high-grade gear and transmission input shaft are Integral designs, direct transmitting torque; Second high-grade gear is fixedly connected with by the mode of electron beam welding with the outer hub of top grade, direct transmitting torque; High-grade outer hub and high-grade separator are by spline pair transmitting torque; Described high-grade separator and high-grade friction plate are by frictional force transmitting torque; High-grade friction plate passes through spline pair transmitting torque with hub in top grade; Hub and the second high-grade gear Integral design in described top grade, direct transmitting torque; Second high-grade gear engages with the first low regime clutch, by gear pair transmitting torque.
Driving mechanism, during high-gear clutch work: first low regime clutch of power in low regime clutch assembly imports into, and pressure oil enters high-gear clutch by oil duct.The second high-grade gear is passed to through one-level gear pair, power is directly passed to high-grade interior hub by the second high-grade gear, in high-grade, transmission of power is given high-grade friction plate by spline pair by hub, high-grade piston moves right under the promotion of pressure oil, compress high-grade disc spring, make high-grade separator, high-grade friction plate tightly fits together, transmission of power is given high-grade separator by frictional force by high-grade friction plate, transmission of power is given high-grade outer hub by spline pair by high-grade separator, power is directly passed to the first high-grade gear by high-grade outer hub, first high-grade direct geared outputs power and is passed to gearbox,
Driving mechanism, when high-gear clutch does not work, pressure oil does not supply, and under the acting in conjunction of high-grade spring force and centrifugal force, high-grade separator, high-grade friction plate are to left movement, separation, and power does not transmit.
Driving mechanism, during low regime clutch work: first low regime clutch of power in described low regime clutch assembly imports into, and pressure oil enters low regime clutch by oil duct.Power is directly imported into low-grade outer hub by the first low regime clutch, transmission of power is given low-grade separator by spline pair by low-grade outer hub, low-grade piston left movement under the promotion of pressure oil, compress low-grade disc spring, make low-grade separator, low-grade friction plate tightly fits together, transmission of power is given low-grade friction plate by frictional force by low-grade separator, transmission of power is given low-grade interior hub by spline pair by low-grade friction plate, in low-grade, transmission of power is directly given the second low regime clutch by hub, transmission of power is given the first high-grade gear by one-level gear pair by the second low regime clutch, first high-grade direct geared outputs power and is passed to gearbox,
Driving mechanism, when low regime clutch does not work, pressure oil does not supply, and under the acting in conjunction of low-grade disc spring elastic force and centrifugal force, low-grade separator, low-grade friction plate move right, are separated, and power does not transmit.
As shown in Figure 2 to 4, this example mainly contains 3 assembly compositions such as torque-converters, high-gear clutch assembly, low regime clutch assembly.Power intake is made up of the first low regime clutch of torque-converters, torque converter output shaft and described low regime clutch assembly, and clutch end is made up of the first high-grade gear of described high-gear clutch assembly and transmission input shaft.
Claims (2)
1. a loader transmission mechanism, is characterized in that: comprise three element fluid torque converters, high-gear clutch assembly and low regime clutch assembly;
Described three element fluid torque converters comprise hubcap, turbine, guide wheel and pump impeller;
Described high-gear clutch assembly comprises high-grade outer hub, the first high-grade gear, high-grade piston, high-grade friction plate, high-grade separator, high-grade disc spring, high-grade interior hub and the second high-grade gear;
Described low regime clutch assembly comprises low-grade outer hub, the first low regime clutch, low-grade piston, low-grade friction plate, low-grade separator, low-grade disc spring, low-grade interior hub and the second low regime clutch;
The output shaft of three element fluid torque converters is fixedly connected with the first low regime clutch in low regime clutch assembly; Described first low regime clutch is fixedly connected with the outer hub of low grade; The outer hub of described low grade and low-grade separator are by spline pair transmitting torque; Described low-grade separator and low-grade friction plate are by frictional force transmitting torque; In described low-grade friction plate and low grade, hub is by spline pair transmitting torque; In described low grade, hub is fixedly connected with the second low regime clutch;
Described second low regime clutch and the second high-grade gears meshing; Described first high-grade gear is fixedly connected with transmission input shaft; Described second high-grade gear is fixedly connected with the outer hub of top grade; The outer hub of described top grade and high-grade separator are by spline pair transmitting torque; Described high-grade separator and high-grade friction plate are by frictional force transmitting torque; In described high-grade friction plate and top grade, hub is by spline pair transmitting torque; In described top grade, hub is fixedly connected with the second high-grade gear; Described second high-grade gear engages with the first low regime clutch.
2. loader transmission mechanism according to claim 1, is characterized in that: described three element fluid torque converters are single-stage monomial fluid torque converter, band coupling converter coupling or closed-end hydraulic torque converter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510943896.1A CN105422786A (en) | 2015-12-16 | 2015-12-16 | Transmission mechanism of loading machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510943896.1A CN105422786A (en) | 2015-12-16 | 2015-12-16 | Transmission mechanism of loading machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105422786A true CN105422786A (en) | 2016-03-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510943896.1A Pending CN105422786A (en) | 2015-12-16 | 2015-12-16 | Transmission mechanism of loading machine |
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| CN (1) | CN105422786A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2193766A (en) * | 1986-06-21 | 1988-02-17 | Brown Gear Ind | Transmission comprising mechanical gearbox and torque converter |
| US4784019A (en) * | 1985-04-03 | 1988-11-15 | Eaton Corporation | Torque converter disconnect and bypass clutch structure for automatic mechanical transmission |
| CN2465977Y (en) * | 2001-03-09 | 2001-12-19 | 常州市亿大汽车自动变速箱制造有限公司 | Stepless moment- and speed-changing box for motor vehicle |
| CN203297548U (en) * | 2013-05-24 | 2013-11-20 | 杭州前进齿轮箱集团股份有限公司 | Hydrodynamic transmission |
| CN204041896U (en) * | 2014-09-17 | 2014-12-24 | 山推工程机械股份有限公司 | A kind of loader counter-shaft power-shift transmission |
| CN205423736U (en) * | 2015-12-16 | 2016-08-03 | 陕西航天动力高科技股份有限公司 | Loader drive mechanism |
-
2015
- 2015-12-16 CN CN201510943896.1A patent/CN105422786A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4784019A (en) * | 1985-04-03 | 1988-11-15 | Eaton Corporation | Torque converter disconnect and bypass clutch structure for automatic mechanical transmission |
| GB2193766A (en) * | 1986-06-21 | 1988-02-17 | Brown Gear Ind | Transmission comprising mechanical gearbox and torque converter |
| CN2465977Y (en) * | 2001-03-09 | 2001-12-19 | 常州市亿大汽车自动变速箱制造有限公司 | Stepless moment- and speed-changing box for motor vehicle |
| CN203297548U (en) * | 2013-05-24 | 2013-11-20 | 杭州前进齿轮箱集团股份有限公司 | Hydrodynamic transmission |
| CN204041896U (en) * | 2014-09-17 | 2014-12-24 | 山推工程机械股份有限公司 | A kind of loader counter-shaft power-shift transmission |
| CN205423736U (en) * | 2015-12-16 | 2016-08-03 | 陕西航天动力高科技股份有限公司 | Loader drive mechanism |
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Application publication date: 20160323 |