CN210087703U - Hydraulic system for section changing and cooling lubrication of tractor hydraulic machine continuously variable transmission - Google Patents
Hydraulic system for section changing and cooling lubrication of tractor hydraulic machine continuously variable transmission Download PDFInfo
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- CN210087703U CN210087703U CN201920119276.XU CN201920119276U CN210087703U CN 210087703 U CN210087703 U CN 210087703U CN 201920119276 U CN201920119276 U CN 201920119276U CN 210087703 U CN210087703 U CN 210087703U
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Abstract
A section changing and cooling and lubricating hydraulic system of a tractor hydraulic machine continuously variable transmission relates to the technical field of hydraulic transmission. The hydraulic system comprises an oil supply control system, a wet clutch section changing control system and a cooling and lubricating control system, the oil supply control system comprises two hydraulic oil sources of a first oil pump and an energy accumulator, the wet clutch section changing control system comprises seven wet clutch control oil paths which are mutually connected in parallel, and the cooling and lubricating control system comprises a plurality of cooling and lubricating oil paths which are mutually connected in parallel, so that reasonable and sufficient cooling and lubricating of the hydraulic mechanical continuously variable transmission are realized. The hydraulic system is applied to the hydraulic mechanical continuously variable transmission of the heavy intelligent tractor, the section-changing control of the hydraulic mechanical continuously variable transmission with four sections is realized, the control of section-changing pressure is realized through the section-changing electro proportional valve, the hydraulic system can control the gear-changing process more accurately, better cooling lubrication is realized simultaneously, and the service life of the transmission is prolonged.
Description
Technical Field
The utility model belongs to the technical field of hydraulic transmission, concretely relates to tractor hydraulic press buncher trades section and cooling lubrication hydraulic system.
Background
The heavy tractor is mainly used for field operation, needs large transmitted power and wide speed change range, but has severe operation environment, and requires the engine and the transmission to change the rotating speed or torque in real time to adapt to the continuous change of load or running resistance so as to ensure the dynamic property, the fuel economy and the driving comfort of the heavy tractor. With the development of the technical level of the tractor continuously variable transmission in China, people continuously put forward new higher requirements on the performance of the transmission, and simultaneously put forward higher requirements on the section changing and cooling and lubricating hydraulic system of the transmission. Generally, the quality of the section changing depends on two aspects, namely the selection of the clutch and the structural characteristics of the clutch, and the other aspect is a section changing hydraulic system, and the latter aspect has larger influence. Whether the hydraulic system of the section changing hydraulic system is reasonable or not and whether the cooling and lubricating hydraulic system is reasonable or not determine the transmission efficiency and the service life of the whole transmission to a great extent. The working efficiency of the tractor can be improved by the lifting of the section changing quality and good cooling and lubricating, so that the tractor is more comfortable to drive, and the tractor has great practical significance for improving the working performance of the heavy tractor in China and promoting the technical innovation in the field.
At present, the domestic research on the hydraulic mechanical stepless speed changer of the tractor is just started, and the reasonable and complete design of an actuating mechanism hydraulic system which is important for the hydraulic mechanical stepless speed changer is lacked so as to realize the multi-stage displacement control and the sufficient cooling and lubrication of the speed changer.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the technical problem that overcome prior art not enough, provide a tractor hydraulic press buncher section of shifting and cooling lubrication hydraulic system, realize the control of section of shifting pressure through the section of shifting electric proportional valve, make hydraulic system more accurate to the control of process of shifting to optimize cooling lubrication system, prolonged the life of derailleur.
The utility model provides a section changing and cooling and lubricating hydraulic system of a tractor hydraulic machine stepless speed changer, which comprises an oil supply control system, a wet clutch section changing control system and a cooling and lubricating control system; the oil supply control system comprises an oil tank (1), a first oil pump (2), an energy accumulator (4), a filter (5), a first oil way (16) and a second oil way (17), wherein the oil tank (1) is connected with the oil pump (2), the oil pump (2) is connected with the energy accumulator (4) through the first oil way, and the energy accumulator (4) is connected with the filter (5) through the second oil way (17); the wet clutch section-changing control system comprises seven wet clutch control oil paths and a third oil path (18), wherein the wet clutch control oil paths are mutually connected in parallel, each wet clutch control oil path comprises a hydraulic operation cylinder and a section-changing electric proportional valve which are connected in series, and the input end of each section-changing electric proportional valve is connected with the third oil path (18); the cooling and lubricating control system comprises a second oil pump (3), a fourth oil way (19), a cooler (13), a fifth oil way (20), an oil pressure control valve group and a plurality of cooling and lubricating oil ways which are connected in parallel, one end of the second oil pump (3) is connected with the oil tank (1), the other end of the second oil pump is connected with the fourth oil way, the cooler (13) is arranged between the fourth oil way (19) and the fifth oil way (20), and each cooling and lubricating oil way is connected with the fifth oil way (20).
As a further technical scheme of the utility model, the hydraulic pressure operation jar is the wet clutch piston cylinder among the wet clutch section-changing control system, and it has friction disc and the steel sheet engaged state of cavity oil charge and friction disc and the steel sheet disengagement state of cavity oil drain.
Furthermore, a damping hole is formed between the hydraulic operation cylinder and the section-changing electric ratio valve, and a pressure sensor is arranged between the section-changing electric ratio valve and the damping hole.
Furthermore, a pressure sensor is arranged between the first oil pump (2) and the filter (5), and a temperature sensor is arranged between the filter (5) and the energy accumulator (4).
Furthermore, the oil pressure control valve group of the cooling and lubricating control system comprises a first check valve (14) and a second check valve (15), the first check valve (14) is arranged between a fourth oil way (19) and a fifth oil way (20), when the oil pressure of the fourth oil way (19) is larger than the back pressure value of the first check valve (14), oil in the fourth oil way (19) is allowed to flow into the fifth oil way (20) through the first check valve (14), the second check valve (15) is arranged on the fifth oil way (20), and when the oil pressure of the fifth oil way (20) is larger than the back pressure value of the second check valve (15), oil in the fifth oil way (20) is allowed to flow into the oil tank (1) through the second check valve (15).
Further, the cooling/lubricating oil passages connected in parallel include a lubricating oil distribution passage L1, a PTO front half shaft member lubricating passage L2, a PTO rear half shaft member lubricating passage L3, and a brake lubricating passage L4.
Further, a pressure sensor is mounted on the fifth oil path (20).
The hydraulic system is applied to the hydraulic mechanical continuously variable transmission of the heavy intelligent tractor, the section-shifting control of the hydraulic mechanical continuously variable transmission with four sections is realized, the control of section-shifting pressure is realized through the section-shifting electro proportional valve, the hydraulic system is more accurate in gear-shifting process control, and meanwhile, the system optimizes cooling lubrication and prolongs the service life of the transmission.
Drawings
FIG. 1 is a transmission schematic diagram of a tractor hydraulic mechanical stepless speed changer of the utility model;
fig. 2 is a schematic diagram of the system of the present invention.
In the figure: 1. the hydraulic system comprises an oil tank, 2 an oil supply system oil pump, 3 a cooling and lubricating system oil pump, 4 an accumulator, 5 a filter, 6, 7, 8, 9, 10, 11 and 12 a section-changing electric proportional valve, 13 a cooler, 14 a first check valve, 15 a second check valve, 16 a first oil way, 17 a second oil way, 18 a third oil way, 19 a fourth oil way, 20 a fifth oil way and 21 a sixth oil way.
Detailed Description
Referring to fig. 1 and fig. 2, the present embodiment provides a stepless transmission section-changing and cooling and lubricating hydraulic system of a tractor hydraulic machine, which includes an oil supply control system, a wet clutch section-changing control system and a cooling and lubricating control system; the oil supply control system comprises an oil tank 1, a first oil pump 2, an energy accumulator 4, a filter 5, a first oil way 16 and a second oil way 17, wherein the oil tank 1 is connected with the oil pump 2, the oil pump 2 is connected with the energy accumulator 4 through the first oil way 16, and the energy accumulator 4 is connected with the filter 5 through the second oil way 17; the oil tank 1 provides power media for hydraulic transmission, hydraulic oil is provided for the first oil pump 2 to be pumped out, the energy accumulator 4 serves as an auxiliary oil source and an emergency power source, leakage can be supplemented, constant pressure can be kept, hydraulic impact can be absorbed, and the two hydraulic sources provide enough power sources for a hydraulic system. The fine filter 5 fine filters out clean hydraulic oil to be supplied to the third oil path 18 so as to meet the use requirement of the stage-changing electric proportional valve.
The wet clutch section-changing control system comprises seven wet clutch control oil paths and a third oil path 18 which are connected in parallel, each wet clutch control oil path comprises a hydraulic operating cylinder and a section-changing electric proportional valve which are connected in series, and the input end of each section-changing electric proportional valve is connected with the third oil path 18; the section-changing electric proportional valve is controlled by a proportional electromagnet, so that the output pressure is in direct proportion to the input current, and the pressure can be accurately and continuously controlled by changing the input electric signal.
The cooling and lubricating control system comprises a second oil pump 3, a fourth oil way 19, a cooler 13, a fifth oil way 20, an oil pressure control valve group and a plurality of cooling and lubricating oil ways which are connected in parallel, one end of the second oil pump 3 is connected with the oil tank 1, the other end of the second oil pump is connected with the fourth oil way 19, the cooler 13 is arranged between the fourth oil way 19 and the fifth oil way 20, and each cooling and lubricating oil way is connected with the fifth oil way 20.
The hydraulic operating cylinder in the wet clutch section-changing control system is a wet clutch piston cylinder which has a state that a chamber is filled with oil and the friction plate and the steel sheet are connected and a state that the chamber is drained with oil and the friction plate and the steel sheet are separated.
A damping hole is arranged between the hydraulic operation cylinder and the section-changing electric ratio valve, a detection hole is reserved between the section-changing electric ratio valve and the damping hole, a pressure sensor can be installed, and the change conditions of flow and pressure in the working state can be detected in real time.
A pressure sensor is arranged between the first oil pump 2 and the filter 5, and a temperature sensor is arranged between the filter 5 and the accumulator 4.
The oil pressure control valve group of the cooling and lubricating control system comprises a first check valve 14 and a second check valve 15, the first check valve 14 is arranged between a fourth oil way 19 and a fifth oil way 20, when the oil pressure of the fourth oil way 19 is larger than the back pressure value of the first check valve 14, oil in the fourth oil way 19 is allowed to flow into the fifth oil way 20 through the first check valve 14, the second check valve 15 is arranged on the fifth oil way 20, and when the fifth oil way 20 is larger than the back pressure value of the second check valve 15, oil in the fifth oil way 20 is allowed to flow into the oil tank 1 through the second check valve 15. And a pressure sensor is arranged on the fifth oil path 20 to detect the pressure change condition in the working state in real time.
The cooling and lubricating oil passages connected in parallel comprise a lubricating oil distribution passage L1, a PTO front half shaft component lubricating passage L2, a PTO rear half shaft component lubricating passage L3 and a brake lubricating passage L4; lubricating and cooling oil path L1 provides distribution oil for clutches of the tractor except for a section-changing clutch, lubricating and cooling oil path L2 provides lubricating and cooling oil for PTO front half-shaft clutches C1, C2, C3, C4, bearings, gears, splines and other high-speed rotating parts, lubricating and cooling oil path L3 provides lubricating and cooling oil for PTO rear half-shaft clutches CV, CR, bearings, gears, splines and other high-speed rotating parts, and lubricating and cooling oil path L4 provides lubricating and cooling oil for brake B.
All clutch drain oil in the system flows into the tank through the sixth oil passage 21.
The operation flow of the system is as follows:
with forward F1 operating, the CV clutch, the C1 clutch, and the B brake require oil supply engagement. At this time, the section-changing electro-proportional valve 6, the section-changing electro-proportional valve 8 and the section-changing electro-proportional valve 12 need to be electrified. When the corresponding electric proportional valve is electrified, oil paths of the CV clutch, the C1 clutch and the B brake are connected and respectively enter an oil charging state, so that the transmission is in the F1 gear. When the forward gear F1 upshifts to F2, the C1 clutch is drained and the C2 clutch is filled with oil. The CV clutch and the B brake continue to maintain the oil-filled state. At the moment, only the power-on state of the electric proportional valve 9 of the conversion section needs to be changed, and the size of the damping hole is adjusted in advance in an experiment so as to meet the requirement of the quality of the conversion section. When the corresponding electro-proportional valve is energized, the CV clutch, the C2 clutch and the B brake are each in an oil filled state, causing the transmission to engage F2. When the forward gear F2 upshifts to F3, the B brake is drained and the C3 clutch is filled with oil. The CV clutch and the C2 clutch continue to remain filled. Only the power-up state of the changeover-section electro-proportional valve 10 needs to be changed at this time. When the respective electro-proportional valves are energized, the CV clutch, the C2 clutch, and the C3 clutch are each in an oil filled state, causing the transmission to engage F3. When the forward gear F3 is shifted up to F4, the C3 clutch is drained and the C4 clutch is filled with oil. The CV clutch and the C2 clutch continue to remain filled. Only the power-on state of the three-position four-way electro-proportional valve 11 needs to be changed at this time. When the respective solenoid valves are energized, the CV clutch, the C2 clutch, and the C4 clutch are each in an oil filled state, causing the transmission to engage F4.
When the forward gear F4 downshifts to F3, the C4 clutch is drained and the C3 clutch is filled with oil. The CV clutch and the C2 clutch continue to remain filled. Only the power-on state of the three-position four-way electro-proportional valve 10 needs to be changed at this time. When the respective solenoid valves are energized, the CV clutch, the C2 clutch, and the C3 clutch are each in an oil filled state, causing the transmission to engage F3. When the forward gear F3 downshifts to F2, the C3 clutch is drained and the B clutch is filled with oil. The CV clutch and the C2 clutch continue to remain filled. Only the power-on state of the electro proportional valve 12 needs to be changed at this time. When the corresponding solenoid valve is electrified, the CV clutch, the C2 clutch and the B clutch are respectively in an oil charging state, so that the transmission is connected with the F2 gear. When the forward gear F2 downshifts to F1, the C2 clutch is drained and the C1 clutch is filled with oil. The CV clutch and the B brake continue to maintain the oil-filled state. Only the power-on state of the electro proportional valve 8 needs to be changed at this time. When the corresponding electro-proportional valve is energized, the CV clutch, the C2 clutch and the B brake are each in an oil filled state, causing the transmission to engage F1. When the vehicle is stopped, the electro proportional valve 6, the electro proportional valve 8 and the electro proportional valve 12 are powered off, and the CV clutch, the C1 clutch and the B brake respectively drain oil, so that the transmission stops transmitting power.
When the reverse gear R1 is in operation, the CR clutch, the C1 clutch, and the B brake require fuel engagement. At the moment, the electric proportional valve 7, the electric proportional valve 8 and the electric proportional valve 12 need to be electrified, and after the corresponding electromagnetic valves are electrified, oil paths of the CR clutch, the C1 clutch and the B brake are connected and respectively enter an oil charging state, so that the transmission is in a gear R1. When the reverse gear R1 is shifted up to R2, the C1 clutch is drained and the C2 clutch is filled with oil. The CR clutch and B brake continue to maintain the oil-filled state. At the moment, only the power-on state of the electro-proportional valve 9 needs to be changed, and the size of the damping hole is adjusted in advance in an experiment to meet the requirement of section-changing quality. When the corresponding solenoid valves are electrified, the CR clutch, the C2 clutch and the B brake are respectively in an oil charging state, so that the transmission is connected with the R2 gear. When the reverse gear R2 upshifts to R3, the B clutch is drained and the C3 clutch is filled with oil. The CR clutch and the C2 clutch continue to remain filled. Only the power-on state of the electro proportional valve 10 needs to be changed at this time. When the respective solenoid valves are energized, the CR clutch, the C2 clutch, and the C3 clutch are each in an oil filled state, causing the transmission to engage R3. When the reverse gear R3 is shifted up to R4, the C3 clutch is drained and the C4 clutch is filled with oil. The CR clutch and the C2 clutch continue to remain filled. Only the power-on state of the electro proportional valve 11 needs to be changed at this time. When the respective solenoid valves are energized, the CR clutch, the C2 clutch, and the C4 clutch are each in an oil filled state, causing the transmission to engage R4.
In this embodiment, when the reverse gear R4 downshifts to R3, the C4 clutch is drained and the C3 clutch is filled with oil. The CR clutch and the C2 clutch continue to remain filled. Only the power-on state of the electro proportional valve 10 needs to be changed at this time. When the respective solenoid valves are energized, the CR clutch, the C2 clutch, and the C3 clutch are each in an oil filled state, causing the transmission to engage R3. When the reverse gear R3 downshifts to R2, the C3 clutch is drained and the B clutch is filled with oil. The CR clutch and the C2 clutch continue to remain filled. Only the power-on state of the electro proportional valve 12 needs to be changed at this time. When the corresponding solenoid valve is electrified, the CR clutch, the C2 clutch and the B clutch are respectively in an oil charging state, so that the transmission is connected with the R2 gear. When the reverse gear R2 downshifts to R1, the C2 clutch is drained and the C1 clutch is filled with oil. The CR clutch and B brake continue to maintain the oil-filled state. At the moment, only the power-on state of the electro-proportional valve 8 needs to be changed, and after the corresponding electromagnetic valves are powered on, the CR clutch, the C1 clutch and the B brake are respectively in an oil-filled state, so that the transmission is in the R1 gear. When the vehicle is stopped, the electro-proportional valve 7, the electro-proportional valve 8 and the electro-proportional valve 12 are de-energized, and the CR clutch, the C1 clutch and the B brake drain oil respectively, so that the transmission stops transmitting power.
The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are given by way of illustration only, and that various changes and modifications may be made without departing from the spirit and scope of the invention as defined by the appended claims. The scope of the invention is defined by the claims and their equivalents.
Claims (7)
1. A section changing and cooling and lubricating hydraulic system of a tractor hydraulic machine continuously variable transmission is characterized by comprising an oil supply control system, a wet clutch section changing control system and a cooling and lubricating control system; the oil supply control system comprises an oil tank (1), a first oil pump (2), an energy accumulator (4), a filter (5), a first oil way (16) and a second oil way (17), wherein the oil tank (1) is connected with the oil pump (2), the oil pump (2) is connected with the energy accumulator (4) through the first oil way, and the energy accumulator (4) is connected with the filter (5) through the second oil way (17); the wet clutch section-changing control system comprises seven wet clutch control oil passages and a third oil passage (18), wherein the wet clutch control oil passages are mutually connected in parallel, each wet clutch control oil passage comprises a hydraulic operation cylinder and a section-changing electric ratio valve which are connected in series, and the input end of each section-changing electric ratio valve is connected with the third oil passage (18); the cooling and lubricating control system comprises a second oil pump (3), a fourth oil way (19), a cooler (13), a fifth oil way (20), an oil pressure control valve group and a plurality of cooling and lubricating oil ways which are connected in parallel, one end of the second oil pump (3) is connected with an oil tank (1), the other end of the second oil pump is connected with the fourth oil way (19), the cooler (13) is arranged between the fourth oil way (19) and the fifth oil way (20), and each cooling and lubricating oil way is connected with the fifth oil way (20).
2. The hydraulic system of claim 1, wherein the hydraulic cylinder in the wet clutch range-changing control system is a wet clutch piston cylinder having a chamber oil-filled friction plate and steel sheet engaged state and a chamber oil-drained friction plate and steel sheet disengaged state.
3. The hydraulic system for the section changing and cooling lubrication of the continuously variable transmission of the hydraulic machine of the tractor according to claim 1, wherein a damping hole is formed between the hydraulic operation cylinder and the section changing electric ratio valve, and a pressure sensor is installed between the section changing electric ratio valve and the damping hole.
4. The hydraulic system for the stepless speed changer, the section changing, the cooling and the lubrication of the hydraulic machine of the tractor as per claim 1, is characterized in that a pressure sensor is arranged between the first oil pump (2) and the filter (5), and a temperature sensor is arranged between the filter (5) and the accumulator (4).
5. The hydraulic system for the stepless speed changer, the section changing and the cooling and lubricating of the tractor hydraulic machine as claimed in claim 1, characterized in that the oil pressure control valve group of the cooling and lubricating control system comprises a first check valve (14) and a second check valve (15), the first check valve (14) is provided between the fourth oil passage (19) and the fifth oil passage (20), when the oil pressure of the fourth oil passage (19) is greater than the back pressure value of the first check valve (14), the oil in the fourth oil passage (19) is allowed to flow into the fifth oil passage (20) through the first check valve (14) on which the second check valve (15) is provided, when the fifth oil path (20) is larger than the back pressure value of the second check valve (15), the oil in the fifth oil passage (20) is allowed to flow into the oil tank (1) through the second check valve (15).
6. The hydraulic system for the shift stage and the cooling and lubricating of the continuously variable transmission of the tractor hydraulic machine as claimed in claim 1, wherein the cooling and lubricating oil paths connected in parallel comprise a lubricating oil distribution path L1, a PTO front half shaft component lubricating path L2, a PTO rear half shaft component lubricating path L3 and a brake lubricating path L4.
7. The hydraulic system for the stepless transmission section changing and the cooling and lubricating of the tractor hydraulic machine as claimed in claim 1, characterized in that a pressure sensor is mounted on the fifth oil path (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920119276.XU CN210087703U (en) | 2019-01-24 | 2019-01-24 | Hydraulic system for section changing and cooling lubrication of tractor hydraulic machine continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920119276.XU CN210087703U (en) | 2019-01-24 | 2019-01-24 | Hydraulic system for section changing and cooling lubrication of tractor hydraulic machine continuously variable transmission |
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| CN210087703U true CN210087703U (en) | 2020-02-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201920119276.XU Active CN210087703U (en) | 2019-01-24 | 2019-01-24 | Hydraulic system for section changing and cooling lubrication of tractor hydraulic machine continuously variable transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111075914A (en) * | 2020-03-09 | 2020-04-28 | 扬州维邦园林机械有限公司 | Control system and control method of continuously variable transmission |
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2019
- 2019-01-24 CN CN201920119276.XU patent/CN210087703U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111075914A (en) * | 2020-03-09 | 2020-04-28 | 扬州维邦园林机械有限公司 | Control system and control method of continuously variable transmission |
| CN111075914B (en) * | 2020-03-09 | 2023-07-21 | 扬州维邦园林机械有限公司 | Control system and control method of continuously variable transmission |
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