CN112815087A - Hydraulic control system of continuously variable automatic transmission, automatic transmission assembly and vehicle - Google Patents
Hydraulic control system of continuously variable automatic transmission, automatic transmission assembly and vehicle Download PDFInfo
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- CN112815087A CN112815087A CN202110139850.XA CN202110139850A CN112815087A CN 112815087 A CN112815087 A CN 112815087A CN 202110139850 A CN202110139850 A CN 202110139850A CN 112815087 A CN112815087 A CN 112815087A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 98
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- 238000013016 damping Methods 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 17
- 239000010687 lubricating oil Substances 0.000 claims description 15
- 230000001276 controlling effect Effects 0.000 description 11
- 239000002184 metal Substances 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012208 gear oil Substances 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000010727 cylinder oil Substances 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000012827 research and development Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
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- 239000010959 steel Substances 0.000 description 1
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0413—Controlled cooling or heating of lubricant; Temperature control therefor
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
- F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention discloses a hydraulic control system of a stepless automatic transmission, comprising: the outlets of the first oil pump and the second oil pump are connected with the primary pressure oil path; the hydraulic control system of the stepless automatic transmission also comprises a primary pressure control valve, an oil pump displacement switching valve, an active pressure control valve and a passive pressure control valve which are arranged on the primary pressure oil path; an oil inlet of the oil pump displacement switching valve is respectively connected with oil discharge ports of the first oil pump and the second oil pump; and oil inlets of the active pressure control valve and the passive pressure control valve are connected with the primary pressure oil way. The invention also discloses an automatic transmission assembly and a vehicle. The hydraulic control system of the stepless automatic transmission aims to solve the technical problems of low transmission efficiency, large gear shifting impact and large pressure fluctuation of the stepless automatic transmission in the prior art.
Description
Technical Field
The invention belongs to the field of control of stepless automatic transmissions, and particularly relates to an energy-saving hydraulic control system, an automatic transmission assembly and a vehicle.
Background
Since the beginning of the 20 th century, the automatic transmission has been continuously optimized and upgraded to become an important component of a modern vehicle transmission system, wherein the metal belt type continuously variable transmission technology has already become a mature development stage abroad, but the current research and development technical level in China is in a lagging state temporarily, particularly the research and development capability of a hydraulic control system of the continuously variable automatic transmission is always in a lower level, and the research and design capability of the metal belt type continuously variable transmission hydraulic system is deficient.
The existing hydraulic control system of the metal belt type continuously variable transmission has the capability of adjusting the pressure of each branch according to a TCU signal, but due to the characteristics of the hydraulic system, the hydraulic control system has the defects of large pressure fluctuation, incapability of ensuring the stability and the like, so that the problems of large gear shifting impact, strong vehicle running pause and frustration and the like are caused. Meanwhile, the low transmission efficiency caused by hydraulic loss is also an urgent problem to be solved in the hydraulic system.
Disclosure of Invention
Technical problem to be solved
Based on the technical scheme, the invention provides an energy-saving hydraulic control system, which aims to solve the technical problems of large gear shifting impact, large pressure fluctuation and low transmission efficiency of a hydraulic control system of a continuously variable automatic transmission in the prior art.
(II) technical scheme
In order to solve the above technical problem, the present invention provides a hydraulic control system for a continuously variable automatic transmission, including: the outlets of the first oil pump and the second oil pump are connected with the primary pressure oil path; the hydraulic control system of the stepless automatic transmission also comprises a primary pressure control valve, an oil pump displacement switching valve, an active pressure control valve and a passive pressure control valve which are arranged on the primary pressure oil path; an oil inlet of the oil pump displacement switching valve is respectively connected with oil discharge ports of the first oil pump and the second oil pump; the hydraulic control system of the stepless automatic transmission further comprises an active pressure pilot electromagnetic valve for providing pilot pressure for the active pressure control valve; the oil inlet of the passive pressure control valve is connected with the primary pressure oil way, the passive pressure control valve is a pilot type proportional pressure reducing valve, and the hydraulic control system of the continuously variable automatic transmission further comprises a passive pressure pilot electromagnetic valve for providing pilot pressure for the passive pressure control valve; an oil inlet of the primary pressure control valve is connected with the primary pressure oil way, and an oil outlet of the primary pressure control valve is connected with the secondary pressure oil way; the hydraulic control system of the stepless automatic transmission further comprises a clutch pressure control solenoid valve and a gear shifting valve, wherein output oil of the clutch pressure control solenoid valve is communicated to the gear shifting valve, the gear shifting valve is provided with two gear shifting valve oil outlets, the hydraulic control system of the stepless automatic transmission further comprises gear shifting valve oil outlet oil paths respectively connected with the two gear shifting valve oil outlets, and the two gear shifting valve oil outlet oil paths are respectively connected with a plurality of third one-way valves and damping holes in parallel; the hydraulic control system of the stepless automatic transmission further comprises an electromagnetic oil supply valve, the electromagnetic oil supply valve is a direct-acting pressure reducing valve, an oil inlet of the electromagnetic oil supply valve is connected with the primary pressure oil way, and an outlet of the electromagnetic oil supply valve is an electromagnetic valve oil supply oil way; the inlet end of the auxiliary oil path is communicated with the outlet end of the electromagnetic oil supply valve, the W further comprises a torque converter pressure pilot electromagnetic valve, and the active pressure pilot electromagnetic valve, the passive pressure pilot electromagnetic valve, the torque converter pressure pilot electromagnetic valve and the electromagnetic valve oil supply oil path are respectively arranged on the auxiliary oil path.
Preferably, the hydraulic control system of the continuously variable automatic transmission further includes a first filter disposed on the auxiliary oil path, and the output end of the active pressure control valve and the output end of the passive pressure control valve are respectively provided with a first accumulator.
Preferably, the secondary pressure oil path comprises a secondary pressure control valve and a hydraulic torque converter pressure control valve, an input end of the secondary pressure control valve is communicated to an overflow port of the primary pressure control valve, the secondary pressure control valve comprises a secondary pressure control valve spring end, and the secondary pressure control valve spring end is communicated to an output oil path of the electromagnetic oil supply valve; the secondary pressure control valve is an overflow valve and is used for controlling the maximum pressure of the secondary pressure oil way; the maximum pressure of the secondary pressure oil way is smaller than the pressure of the primary pressure oil way; and the secondary pressure oil way is also communicated to an output oil way of the electromagnetic oil supply valve through a damping hole and a one-way valve.
Preferably, the secondary pressure oil passage further includes: the cooling lubricating oil path is provided with a second filter, a transmission oil radiator, an oil pump switching pilot control oil path and a flow distribution damping hole, the pressure of the oil pump switching pilot control oil path is adjusted through the flow distribution damping hole, and the oil pump switching pilot control oil path energy accumulator used for relieving pressure fluctuation is further arranged on the oil path.
Preferably, the active pressure pilot solenoid valve, the passive pressure pilot solenoid valve and the clutch pressure control solenoid valve are all normally open proportional solenoid valves, and the torque converter pressure pilot control solenoid valve is a normally closed proportional solenoid valve.
Preferably, the oil pump displacement switching valve is a pilot operated directional control valve.
Preferably, the primary pressure control valve is a pilot type proportional relief valve, and the pilot pressure of the primary pressure control valve is provided by the active pressure pilot solenoid valve or the passive pressure pilot solenoid valve.
Preferably, the shift valve is a manual reversing valve; the first oil pump and the second oil pump are two independent working cavities of the double-acting vane pump.
The invention also provides a continuously variable automatic transmission assembly, which applies the hydraulic control system of the continuously variable automatic transmission.
The invention also proposes a vehicle comprising a continuously variable automatic transmission assembly as described above.
(III) advantageous effects
Compared with the prior art, the invention has the following beneficial effects:
(1) according to the hydraulic control system of the stepless automatic transmission, the control of a plurality of oil ways can be realized through the hydraulic valve group, so that the transmission can obtain the optimal pressure under each working condition. Compared with a transmission using a traditional hydraulic control system, the transmission innovatively uses the double-acting oil pump, the discharge capacity of the oil pump is adaptively adjusted according to the flow demand of the hydraulic system through the discharge capacity switching control valve of the oil pump, and the energy-saving and emission-reducing functions are realized.
(2) In the hydraulic control system of the stepless automatic transmission, the function of self-adaptive adjustment of the primary pressure according to the pressure requirement of an actuating mechanism is innovatively realized, the pilot pressure of the driving cylinder or the pilot pressure of the driven cylinder is selectively used as the pilot pressure of the primary pressure control valve by introducing the pressure comparison valve, so that the primary pressure always meets the maximum pressure required by the system, compared with the traditional hydraulic system of the stepless transmission, the pilot electromagnetic valve using the primary pressure control valve is reduced, the cost advantage is achieved, the load of the control system is reduced, and the pressure of a primary pressure oil path does not need to be controlled independently.
(3) According to the hydraulic control system of the stepless automatic transmission, the energy accumulator is added, the energy accumulator is arranged on the pilot oil path of each important pressure control slide valve, the pressure fluctuation of the pilot pressure of each control valve is absorbed through the structural characteristics of the energy accumulator, the movement stability of the valve core is effectively controlled, and the pressure regulation is more accurate and stable; meanwhile, a working mode that the one-way valve is matched with the damping hole is adopted in a clutch oil path, the change rate of flow of a clutch in the transmission can be adjusted by matching the one-way valve with the damping hole during oil supply and oil drainage, the problem of gear shifting impact of the transmission caused by the structural characteristics of the transmission is effectively solved, and the comfort of a vehicle carrying the gear shifting device is obviously improved.
Drawings
The features and advantages of the present invention will be more clearly understood by reference to the accompanying drawings, which are illustrative and not to be construed as limiting the invention in any way, and in which:
FIG. 1 is a schematic diagram of a hydraulic control system for a continuously variable automatic transmission according to an embodiment of the present invention;
fig. 2 is a schematic flow diagram of hydraulic oil in the hydraulic control system of the continuously variable automatic transmission according to the embodiment of the present invention.
Description of reference numerals:
1. the hydraulic control system comprises a first oil pump, 2, a second oil pump, 3, a first one-way valve, 4, a second one-way valve, 5, an oil pump displacement switching control valve, 6, a primary pressure control valve, 7, a passive oil cylinder pressure control valve, 8, a first accumulator, 9, an active oil cylinder pressure control valve, 10, an electromagnetic oil supply valve, 11, a first filter, 12, an active pressure pilot electromagnetic valve, 13, a passive pressure pilot electromagnetic valve, 14, a gear shift valve, 15, a clutch pressure control electromagnetic valve, 16, a third filter, 17, a third one-way valve, 18, a reverse gear pressure, 19, a forward gear pressure, 20, an active oil cylinder pressure, 21, a hydraulic torque converter pressure pilot electromagnetic valve, 22, a passive oil cylinder pressure, 23, a torque converter locking oil cavity pressure, 24, a torque converter unlocking oil cavity pressure, 25, a hydraulic torque converter pressure control valve, 26, a flow distribution damping hole, 27, a radiator, 28. second filter, 29 flow distribution orifice, 30 relief valve, 31 second accumulator, 32 secondary pressure control valve.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein, but rather should be construed as broadly as the present invention is capable of modification in various respects, all without departing from the spirit and scope of the present invention.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "connected" and "connected" are to be interpreted broadly, e.g., as being fixed or detachable or integrally connected; the two elements may be mechanically or electrically connected, directly or indirectly connected through an intermediate medium, or connected through the inside of the two elements, or "in transmission connection", that is, connected in a power manner through various suitable manners such as belt transmission, gear transmission, or sprocket transmission. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to fig. 1-2, the direction of the arrows in fig. 2 indicate the flow of hydraulic oil in the hydraulic control system of the continuously variable automatic transmission according to the embodiment of the invention. A hydraulic control system of a continuously variable automatic transmission comprising: a first oil pump 1, a second oil pump 2, a first check valve 3, a second check valve 4, an oil pump displacement switching control valve 5, a primary pressure control valve 6, a passive cylinder pressure control valve 7, a first accumulator 8, an active cylinder pressure control valve 9, an electromagnetic oil supply valve 10, a first filter 11, an active pressure pilot solenoid valve 12, a passive pressure pilot solenoid valve 13, a shift valve 14, a clutch pressure control solenoid valve 15, a third filter 16, a third check valve 17, a reverse range pressure 18, a forward range pressure 19, an active cylinder pressure 20, a torque converter pressure pilot solenoid valve 21, a passive cylinder pressure 22, a torque converter lock-up pressure oil chamber 23, a torque converter unlock oil chamber pressure 24, a torque converter pressure control valve 25, a flow distribution damping hole 26, a radiator 27, a second filter 28, a flow distribution damping hole 29, a safety valve 30, a second accumulator 31, a hydraulic oil pump control valve 15, a hydraulic oil pump control valve 14, a clutch pressure control solenoid, A secondary pressure control valve 32.
The following further describes the scheme of the hydraulic control system of the continuously variable automatic transmission according to the present invention. A hydraulic control system of a continuously variable automatic transmission, comprising: the first oil pump 1, the second oil pump 2, the primary pressure oil path, the secondary pressure oil path, the auxiliary oil path, and outlets of the first oil pump and the second oil pump are all connected with the primary pressure oil path; the hydraulic control system of the stepless automatic transmission also comprises a primary pressure control valve 6, an oil pump displacement switching valve 5, an active pressure control valve 9 and a passive pressure control valve 7 which are arranged on the primary pressure oil path; an oil inlet of the oil pump displacement switching valve 5 is respectively connected with oil discharge ports of the first oil pump 1 and the second oil pump 2; an oil inlet of the active pressure control valve 9 is connected with the primary pressure oil path, the active pressure control valve 9 is a pilot type proportional pressure reducing valve, and the hydraulic control system of the continuously variable automatic transmission further comprises an active pressure pilot electromagnetic valve 12 for providing pilot pressure for the active pressure control valve 9; an oil inlet of the passive pressure control valve 7 is connected with the primary pressure oil way, the passive pressure control valve 7 is a pilot type proportional pressure reducing valve, and the hydraulic control system of the continuously variable automatic transmission further comprises a passive pressure pilot electromagnetic valve 13 for providing pilot pressure for the passive pressure control valve 7; an oil inlet of the primary pressure control valve 6 is connected with the primary pressure oil way, and an oil outlet of the primary pressure control valve 6 is connected with the secondary pressure oil way; the hydraulic control system of the continuously variable automatic transmission further comprises a clutch pressure control solenoid valve 15 and a shift valve 14, output oil of the clutch pressure control solenoid valve 15 is communicated to the shift valve 14, the shift valve 14 is provided with two shift valve oil outlets, the hydraulic control system of the continuously variable automatic transmission further comprises shift valve oil outlet oil passages respectively connected with the two shift valve oil outlets, and the two shift valve oil outlet oil passages are respectively connected with a plurality of third one-way valves 17 and damping holes in parallel; the hydraulic control system of the stepless automatic transmission further comprises an electromagnetic oil supply valve 10, wherein the electromagnetic oil supply valve 10 is a direct-acting pressure reducing valve, an oil inlet of the electromagnetic oil supply valve 10 is connected with the primary pressure oil way, and an outlet of the electromagnetic oil supply valve 10 is an electromagnetic valve oil supply oil way; the inlet end of the auxiliary oil path is communicated with the outlet end of the electromagnetic oil supply valve 10, and the active pressure pilot electromagnetic valve 12, the passive pressure pilot electromagnetic valve 13 and the electromagnetic valve oil supply path are respectively arranged on the auxiliary oil path.
In the above embodiment: the first oil pump and the second oil pump supply oil for a hydraulic system. The first oil pump with the second oil pump is two working chambers of two effect vane pump, and the pump chamber of first oil pump and second oil pump independently work, mutual noninterference, and the effect is equal to two oil pumps with the specification, and two oil pump outlets all are connected to one-level pressure oil circuit. The oil outlet of the active pressure control valve 9 is connected with an active oil cylinder oil way, and the oil outlet of the passive pressure control valve 7 is connected with a passive oil cylinder oil way. The oil pump displacement switching valve 5 can partially or completely unload the second oil pump 2, and further, the first oil pump 1 can be partially unloaded while the second oil pump 2 is completely unloaded. The active pressure control valve 9 can independently control the oil line pressure of the active oil cylinder, and the passive pressure control valve 7 can independently control the oil line pressure of the passive oil cylinder. The gear shifting valve 14 is a manual reversing valve, oil outlets of the two gear shifting valves are respectively communicated to the forward gear clutch oil cylinder and the reverse gear clutch oil cylinder, and a plurality of third one-way valves 17 and damping holes which are connected in parallel are arranged on an oil outlet path of the oil path gear shifting valve between the oil outlet of the gear shifting valve 14 and the forward gear and reverse gear oil cylinders and are used for controlling oil drainage speeds of the forward gear oil cylinder and the reverse gear oil cylinder. The electromagnetic oil supply valve 10 is a direct-acting pressure reducing valve and outputs constant pressure to control the inlet pressure of all the electromagnetic valves.
When the invention is applied to an automatic transmission assembly, high-pressure oil pumped by the first oil pump 1 and the second oil pump 2 is divided into four parts: one part of the oil passes through the active pressure control valve 9 and then is filled into an active pulley oil cylinder in the transmission, and the other part of the oil passes through the passive pressure control valve 7 and then is filled into a passive pulley oil cylinder in the transmission, and the two paths of oil provide clamping force for the steel belt; the other part is decompressed by the electromagnetic oil supply valve 10 and then enters an electromagnetic valve oil supply circuit to provide flow for the pilot electromagnetic valve and the clutch valve; after the pressure requirements of the first pressure control valve and the second pressure control valve are met, the residual oil overflows into a subsequent second-stage pressure oil way through the first-stage pressure control valve 6, wherein the subsequent second-stage pressure oil way comprises a hydraulic torque converter pressure control oil way and a cooling lubricating oil way.
According to the specific embodiment of the present invention, the hydraulic control system of the continuously variable automatic transmission further includes a first filter 11 and a torque converter pressure pilot solenoid valve 21, which are disposed on the auxiliary oil path, and the output end of the active pressure control valve 9 and the output end of the passive pressure control valve 7 are respectively provided with a first accumulator 8.
More specifically, the hydraulic torque converter pilot electromagnetic valve 21 is communicated with the pilot end of a hydraulic torque converter pressure control valve 25 to control the direction and pressure of oil entering the hydraulic torque converter; the input end of the hydraulic torque converter pilot electromagnetic valve 21 is connected to the output end of the electromagnetic oil supply valve 10. In use, the torque converter valve 25 is selectively positioned in one of the unlocked and locked positions under the control of the torque converter pilot solenoid valve 21: when the hydraulic torque converter is located at the unlocking position, oil in the secondary pressure oil way enters the unlocking cavity through the hydraulic torque converter valve 25 and then enters the locking cavity through the one-way valve in the hydraulic torque converter, the unlocking pressure 24 is higher than the locking pressure 23, and the torque converter is unlocked and is in a hydraulic working condition and used for torque increase and shock absorption when the vehicle is at a low speed. When the hydraulic torque converter needs to be locked, the output pressure of a pilot electromagnetic valve 21 of the hydraulic torque converter is gradually changed, the locking pressure 23 and the unlocking pressure 24 are simultaneously increased, and then the unlocking pressure 24 is controlled to be gradually reduced, so that the sliding friction control of the hydraulic torque converter is realized, and the power transmission process is smooth and controllable; when the unlocking pressure is reduced to zero, the pressure difference between the unlocking cavity and the locking cavity of the hydraulic torque converter is the largest, the locking pressure is higher than the unlocking pressure, and the torque converter is in a hard connection state and can transmit the maximum torque.
Preferably, a check valve is provided at the input end of the torque converter pressure control valve 25, i.e., the secondary oil path, and is connected to the electromagnetic oil supply path, so that oil can only flow from the output end of the electromagnetic oil supply valve 10 to the input end of the torque converter pressure control valve 25. After the electromagnetic oil supply oil way meets the flow requirements of all pilot electromagnetic valves, redundant oil can be supplemented for the secondary pressure oil way through the one-way valve.
Preferably, the hydraulic control system of the present embodiment further includes a cooling and lubricating oil path provided in the secondary circuit, a part of the cooling and lubricating oil path directly lubricates a part of the gears and bearings through the housing oil holes, and another part of the oil passes through the radiator 27 and the filter 28 to cool and lubricate the metal belt and the clutch disk.
When the hydraulic torque converter is unlocked, oil overflowed by the primary pressure control valve 6 flows into an unlocking oil cavity of the hydraulic torque converter through the hydraulic torque converter valve 25, flows into a locking oil cavity of the hydraulic torque converter through the one-way valve, flows back to the hydraulic torque converter valve 25, and is finally conveyed to a cooling lubricating oil way; when the hydraulic torque converter is in a locking working condition, after the locking pressure meets the requirement, the oil overflowed by the secondary pressure valve 32 directly passes through the hydraulic torque converter valve 25 and then enters a cooling and lubricating oil way; to protect the radiator and transmission external lines, a relief valve 30 is provided to limit the maximum pressure of the cooling oil circuit.
Preferably, the hydraulic control system of the present embodiment further includes an oil pump displacement control pilot oil path arranged on the cooling and lubricating oil path, the pilot oil path connects the pilot end of the oil pump displacement switching control valve 5 and an oil path between the filter 28 and the flow distribution damping hole 29 in the transmission heat dissipation oil path, and the working state of the oil pump displacement switching control valve is controlled by using the pressure drop generated by the flow passing through the pilot oil path, so as to realize the function of adjusting the oil pump displacement according to the heat dissipation flow.
Preferably, the hydraulic control system of the present embodiment can also realize the basic function of ensuring the transmission in the power-off condition. As shown in fig. 1, the active pilot solenoid valve 12, the passive pilot solenoid valve 13, and the clutch control solenoid valve 15 are normally open solenoid valves, and the torque converter pilot solenoid valve 21 is a normally closed solenoid valve. When the normally open electromagnetic valve is powered off, the maximum pressure is output; when the normally closed electromagnetic valve is powered off, the output pressure is zero. Further, due to the characteristics of the electromagnetic valves, when power failure occurs, the pressure of a primary pressure oil way, the active pressure, the passive pressure and the clutch pressure of the hydraulic control system are all in a high state, so that the clamping force of a metal belt and the combination of the clutch are guaranteed. Meanwhile, by means of the design of the pressure control valve 25 of the torque converter, the hydraulic torque converter is in an unlocking state when no pilot pressure exists, namely, the hydraulic transmission working condition; in conclusion, the vehicle can be started and limped to a repair shop or a safe position when the power failure occurs.
In the present embodiment: the first accumulator 8 is used to reduce the pilot pressure fluctuations, making the pressure control more smooth.
Wherein: the active pressure control valve 9 is arranged on a branch between an oil pump oil outlet and the active oil cylinder and is used for controlling the pressure of oil entering the active oil cylinder; the passive pressure control valve 7 is arranged on a branch between the oil discharge port of the first oil pump 1 and the passive oil cylinder and used for controlling the pressure of oil entering the passive oil cylinder. The oil pressure of the driving cylinder and the oil pressure of the driven cylinder are respectively regulated and controlled through the driving pressure control valve 9 and the driven pressure control valve 7, so that the accurate control of the speed ratio can be realized, the clamping force of a metal belt is further reduced, and the loss of a hydraulic system is reduced.
Preferably, the primary pressure control valve 6, the active pressure control valve 9, and the passive pressure control valve 7 in this embodiment are all mechanical valves, and the hydraulic control system of the continuously variable automatic transmission further includes a pilot oil path pressure control valve group. The active pressure pilot electromagnetic valve 12 is communicated with the pilot ends of the active pressure control valve 9 and the primary pressure control valve 6, and the active pressure and the primary pressure oil path pressure are adjusted by controlling the active pilot pressure; the passive pressure pilot electromagnetic valve 13 is communicated with the pilot ends of the passive pressure control valve 7 and the primary pressure control valve 6, and adjusts the passive pressure and the primary pressure oil path pressure by controlling the passive pilot pressure.
Preferably, the oil supply ends of the pilot oil line pressure control valve group are intersected and communicated to the output end of the electromagnetic valve oil supply valve 10, the input end of the electromagnetic oil supply valve 10 is communicated to the input end of the first-stage pressure control valve 6, and the electromagnetic oil supply valve 10 is a reducing valve and is used for reducing the oil pressure of the previous-stage pressure oil line and then conveying the oil pressure to the input end of each pilot electromagnetic valve.
Preferably, the hydraulic control system for the automatic stepless transmission further comprises a hydraulic circuit for controlling the connection or disconnection of the wet clutch, the output end of the electromagnetic oil supply valve 10 is communicated with the input end of the clutch pressure control electromagnetic valve 15, the clutch pressure control electromagnetic valve 15 is a high-power proportional electromagnetic valve, and the output pressure can directly meet the use requirement of a wet clutch cylinder.
According to the specific embodiment of the invention, the secondary pressure oil path comprises a secondary pressure control valve 32 and a hydraulic torque converter pressure control valve 25, the input end of the secondary pressure control valve 32 is communicated to the overflow port of the primary pressure control valve 6, the secondary pressure control valve 32 comprises a secondary pressure control valve spring end, and the secondary pressure control valve spring end is communicated to the output oil path of the electromagnetic oil supply valve 10; the secondary pressure control valve 32 is an overflow valve, and the secondary pressure control valve 32 is used for controlling the maximum pressure of the secondary pressure oil path; the maximum pressure of the secondary pressure oil way is smaller than the pressure of the primary pressure oil way; the secondary pressure oil path is also communicated to an output oil path of the electromagnetic oil supply valve 10 through a damping hole and a check valve. In the embodiment, the secondary pressure oil path is also communicated to an output oil path of the electromagnetic oil supply valve 10 through a damping hole and a check valve, and the structure can supplement the flow to the secondary pressure oil path through the electromagnetic oil supply oil path when the flow of the secondary pressure oil path is insufficient; in specific implementation, an oil input end of the hydraulic torque converter is communicated to the secondary pressure oil path, and a hydraulic torque converter pressure control valve 25 for controlling the oil pressure flowing into the torque converter and a hydraulic torque converter pilot electromagnetic valve 21 for outputting pilot pressure to the hydraulic torque converter valve 25 to control the hydraulic torque converter valve 25 to output the oil pressure to the torque converter are arranged on the oil input end of the hydraulic torque converter; an inlet of the hydraulic torque converter pilot electromagnetic valve 21 is communicated with an oil outlet of the electromagnetic oil supply valve 10; the output end of the hydraulic torque converter valve 25 is communicated to a locking cavity and an unlocking cavity of the hydraulic torque converter and is used for controlling locking and unlocking of the hydraulic torque converter.
According to an embodiment of the present invention, the secondary pressure oil passage further includes: the oil cooling and lubricating system comprises a cooling and lubricating oil path, an oil pump switching pilot control oil path and a safety valve 30, wherein a second filter 28, a transmission oil radiator 27, the oil pump switching pilot control oil path and a flow distribution damping hole 29 are arranged on the cooling and lubricating oil path, the pressure of the oil pump switching pilot control oil path is controlled by the damping hole 29, and an oil pump switching pilot control oil path energy accumulator 31 for relieving pressure fluctuation is further arranged on the oil path. In the present embodiment, the cooling and lubricating oil path leads to each component in the automatic transmission and is used for cooling and lubricating each component in the automatic transmission. When the hydraulic torque converter is in an unlocking hydraulic working condition, the oil overflowed by the primary pressure control valve 6 flows into an unlocking oil cavity of the hydraulic torque converter through the hydraulic torque converter valve 25, flows into a locking oil cavity of the hydraulic torque converter through the one-way valve, flows back to the hydraulic torque converter valve 25, and is finally conveyed to the cooling lubricating oil way, and when the hydraulic torque converter is in a locking working condition, the oil overflowed by the secondary pressure control valve 32 directly passes through the hydraulic torque converter valve 25 and then enters the cooling lubricating oil way; the oil pump switching pilot control oil way is a branch of a rear lubricating oil way of the radiator, the pressure of the oil pump switching pilot control oil way is controlled through a flow distribution damping hole 29, and an energy accumulator 31 is installed on the oil way to relieve pressure fluctuation.
According to the specific embodiment of the present invention, the active pressure pilot solenoid valve 12, the passive pressure pilot solenoid valve 13, and the clutch pressure control solenoid valve 15 are all normally open proportional solenoid valves, and the torque converter pressure pilot solenoid valve is a normally closed proportional solenoid valve.
According to an embodiment of the present invention, the oil pump displacement switching valve 5 is a pilot operated directional control valve.
According to the specific embodiment of the present invention, the primary pressure control valve 6 is a pilot type proportional relief valve, and the pilot pressure of the primary pressure control valve 6 is provided by the active pressure pilot solenoid valve 12 or the passive pressure pilot solenoid valve 13. In this embodiment, the primary pressure control valve 6 is used to control the working pressure of the primary pressure oil path, the overflow flow rate is supplied to the secondary pressure oil path, the pilot pressure of the primary pressure control valve 6 is supplied by the active pressure pilot solenoid valve 12 or the passive pressure pilot solenoid valve 13, and the two pilot pressures are used as the pilot pressure of the primary pressure control valve 6 by selecting one pilot pressure after passing through the pressure comparison valve.
According to a specific embodiment of the invention, the shift valve is a manual directional valve; the first oil pump and the second oil pump are two independent working cavities of the double-acting vane pump.
The invention also provides an automatic transmission assembly which applies the hydraulic control system of the continuously variable automatic transmission.
The invention also provides a vehicle comprising an automatic transmission assembly as described above.
Compared with the prior art, the hydraulic control system of the stepless automatic transmission can automatically adjust the working effective displacement of the oil pump according to the flow demand of the hydraulic system, and can obviously reduce the loss of the hydraulic system under the steady-state working condition of high rotating speed and low load of an engine; by designing the primary pressure control valve, after the active pilot pressure and the passive pilot pressure are compared, the primary pressure is synchronously controlled, so that the primary pressure always meets the maximum pressure requirement of a hydraulic system, and the material cost and the calibration workload of the transmission can be saved; the pressure change can be accurately adjusted by controlling the pilot pressure, so that the clamping force and the speed ratio can be accurately controlled; the energy accumulator is added on the pilot pressure oil path, so that the motion of the valve core is more stable, the regulation control of each pressure is more stable, the sliding friction control of the hydraulic torque converter and the like can be realized, and the economy and the drivability of a vehicle carrying the hydraulic system are improved; meanwhile, the structure is more compact in the aspect of oil circuit arrangement, and arrangement of a transmission box body is facilitated.
Although the embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations fall within the scope defined by the appended claims.
Claims (10)
1. A hydraulic control system of a continuously variable automatic transmission, characterized by comprising: the first oil pump (1), the second oil pump (2), a primary pressure oil path, a secondary pressure oil path, an auxiliary oil path, and outlets of the first oil pump (1) and the second oil pump (2) are all connected with the primary pressure oil path; the hydraulic control system of the stepless automatic transmission also comprises a primary pressure control valve (6), an oil pump displacement switching valve (5), an active pressure control valve (9) and a passive pressure control valve (7) which are arranged on the primary pressure oil path; an oil inlet of the oil pump displacement switching valve (5) is respectively connected with oil outlets of the first oil pump (1) and the second oil pump (2); an oil inlet of the active pressure control valve (9) is connected with the primary pressure oil way, the active pressure control valve (9) is a pilot type proportional pressure reducing valve, and the hydraulic control system of the continuously variable automatic transmission further comprises an active pressure pilot electromagnetic valve (12) for providing pilot pressure for the active pressure control valve (9); an oil inlet of the passive pressure control valve (7) is connected with the primary pressure oil way, the passive pressure control valve (7) is a pilot type proportional pressure reducing valve, and the hydraulic control system of the continuously variable automatic transmission further comprises a passive pressure pilot electromagnetic valve (13) for providing pilot pressure for the passive pressure control valve (7); an oil inlet of the primary pressure control valve (6) is connected with the primary pressure oil way, and an oil outlet of the primary pressure control valve (6) is connected with the secondary pressure oil way; the hydraulic control system of the stepless automatic transmission further comprises a clutch pressure control electromagnetic valve (15) and a gear shifting valve (14), output oil of the clutch pressure control electromagnetic valve (15) is communicated to the gear shifting valve (14), the gear shifting valve (14) is provided with two gear shifting valve oil outlets, the hydraulic control system of the stepless automatic transmission further comprises gear shifting valve oil outlet oil paths which are respectively connected with the two gear shifting valve oil outlets, and the two gear shifting valve oil outlet oil paths are respectively connected with a plurality of third one-way valves (17) and damping holes in parallel; the hydraulic control system of the stepless automatic transmission further comprises an electromagnetic oil supply valve (10), the electromagnetic oil supply valve (10) is a direct-acting pressure reducing valve, an oil inlet of the electromagnetic oil supply valve (10) is connected with the primary pressure oil way, and an outlet of the electromagnetic oil supply valve (10) is an electromagnetic valve oil supply oil way; the inlet end of the auxiliary oil way is communicated with the outlet end of the electromagnetic oil supply valve (10), the W further comprises a torque converter pressure pilot electromagnetic valve (21), the active pressure pilot electromagnetic valve (12), the passive pressure pilot electromagnetic valve (13), the torque converter pressure pilot electromagnetic valve (21) and the electromagnetic valve oil supply oil way are respectively arranged on the auxiliary oil way.
2. The hydraulic control system of a continuously variable automatic transmission according to claim 1, further comprising a first filter (11) provided on the auxiliary oil passage, and wherein the output of the active pressure control valve (9) and the output of the passive pressure control valve (7) are provided with a first accumulator (8), respectively.
3. The hydraulic control system of a continuously variable automatic transmission according to claim 1, wherein the secondary pressure oil path includes a secondary pressure control valve (32), a torque converter pressure control valve (25), an input end of the secondary pressure control valve (32) is connected to an overflow port of the primary pressure control valve (6), the secondary pressure control valve (32) includes a secondary pressure control valve spring end, and the secondary pressure control valve spring end is connected to an output oil path of the electromagnetic oil feed valve (10); the secondary pressure control valve (32) is an overflow valve, and the secondary pressure control valve (32) is used for controlling the maximum pressure of the secondary pressure oil circuit; the maximum pressure of the secondary pressure oil way is smaller than the pressure of the primary pressure oil way; and the secondary pressure oil way is also communicated to an output oil way of the electromagnetic oil supply valve (10) through a damping hole and a one-way valve.
4. The hydraulic control system of a continuously variable automatic transmission according to claim 3, wherein the secondary pressure oil passage further includes: the oil pump switching pilot control oil circuit comprises a cooling lubricating oil circuit, an oil pump switching pilot control oil circuit and a safety valve (30), wherein a second filter (28), a transmission oil radiator (27), an oil pump switching pilot control oil circuit and a flow distribution damping hole (29) are arranged on the cooling lubricating oil circuit, the pressure of the oil pump switching pilot control oil circuit is adjusted through the flow distribution damping hole (29), and an oil pump switching pilot control oil circuit energy accumulator (31) used for relieving pressure fluctuation is further arranged on the oil circuit.
5. The hydraulic control system of a continuously variable automatic transmission according to claim 1, wherein the active pressure pilot solenoid valve (12), the passive pressure pilot solenoid valve (13), and the clutch pressure control solenoid valve (15) are all normally open type proportional solenoid valves, and the torque converter pressure pilot control solenoid valve (21) is a normally closed type proportional solenoid valve.
6. The hydraulic control system of a continuously variable automatic transmission according to claim 1, characterized in that the oil pump displacement switching valve (5) is a pilot operated type directional control valve.
7. The hydraulic control system of a continuously variable automatic transmission according to claim 1, characterized in that the primary pressure control valve (6) is a pilot type proportional relief valve, and the pilot pressure of the primary pressure control valve (6) is provided by the active pressure pilot solenoid valve (12) or the passive pressure pilot solenoid valve (13).
8. The hydraulic control system of a continuously variable automatic transmission according to claim 1, wherein the shift valve is a manual directional valve; the first oil pump (1) and the second oil pump (2) are two independent working cavities of a double-acting vane pump.
9. A continuously variable automatic transmission assembly characterized in that the automatic transmission assembly employs a continuously variable automatic transmission hydraulic control system according to any one of claims 1 to 8.
10. A vehicle characterized by comprising a continuously variable automatic transmission assembly according to claim 9.
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| CN202110139850.XA CN112815087A (en) | 2021-02-02 | 2021-02-02 | Hydraulic control system of continuously variable automatic transmission, automatic transmission assembly and vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117090927A (en) * | 2023-10-20 | 2023-11-21 | 山东亿嘉农业机械装备股份有限公司 | Tractor drive train lubricating system and control mechanism |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117090927A (en) * | 2023-10-20 | 2023-11-21 | 山东亿嘉农业机械装备股份有限公司 | Tractor drive train lubricating system and control mechanism |
| CN117090927B (en) * | 2023-10-20 | 2023-12-29 | 山东亿嘉农业机械装备股份有限公司 | Tractor drive train lubricating system and control mechanism |
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Effective date of registration: 20240102 Address after: 646003 Section 4, Jiugu Avenue, High tech Zone, Luzhou City, Sichuan Province Applicant after: Luzhou Rongda Intelligent Transmission Co.,Ltd. Address before: No.68, durong Road, Yuelu District, Changsha, Hunan 410000 Applicant before: Hunan Yung Da intelligent transmission Limited by Share Ltd. |
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