CN113357365B - Hydraulic parking system of double-clutch transmission and vehicle - Google Patents
Hydraulic parking system of double-clutch transmission and vehicle Download PDFInfo
- Publication number
- CN113357365B CN113357365B CN202110586922.5A CN202110586922A CN113357365B CN 113357365 B CN113357365 B CN 113357365B CN 202110586922 A CN202110586922 A CN 202110586922A CN 113357365 B CN113357365 B CN 113357365B
- Authority
- CN
- China
- Prior art keywords
- oil
- communicated
- valve
- withdrawing
- oil way
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
- F16H63/3416—Parking lock mechanisms or brakes in the transmission
- F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention discloses a hydraulic parking system and a vehicle of a double-clutch transmission, which comprise an oil pump, a filter, an oil tank, a first pressure solenoid valve, a second pressure solenoid valve, a main pressure regulating valve, a P withdrawing pressure relief valve, a P withdrawing mechanical valve, a P withdrawing piston cylinder, an unlocking piston cylinder, a first feedback of the P withdrawing mechanical valve and a second feedback of the P withdrawing mechanical valve; the parts are communicated as required through oil passages. The parking unlocking device has the advantages of low cost and simple structure, supports parking unlocking and P withdrawing, and can meet the parking requirement of the double-clutch transmission.
Description
Technical Field
The invention belongs to the technical field of vehicle transmissions, and particularly relates to a hydraulic parking system of a double-clutch transmission and a vehicle.
Background
With the increasing cost requirements, lower cost hydraulic parking is gradually being developed for dual clutch automatic transmissions. For the hydraulic parking function, a hydraulic system is required to have two oil ways capable of respectively controlling pressure, wherein one way is used for controlling unlocking of a parking mechanical structure, and the other way is used for controlling parking to move back a P piston. Therefore, at least two additional independent electromagnetic valves are needed to control two oil passages respectively, and the cost is higher when the number of the electromagnetic valves is larger.
Therefore, it is necessary to develop a new hydraulic parking system of a dual clutch transmission and a vehicle.
Disclosure of Invention
The invention aims to provide a hydraulic parking system of a double-clutch transmission and a vehicle, which have the advantages of low cost, simple structure and support of parking unlocking and P withdrawing.
In a first aspect, the hydraulic parking system of a dual clutch transmission comprises a first oil path, a second oil path, a third oil path, a fourth oil path, a fifth oil path, a sixth oil path, a seventh oil path, an eighth oil path, a ninth oil path, a tenth oil path, an eleventh oil path, a twelfth oil path, a thirteenth oil path, a fourteenth oil path, a fifteenth oil path, a sixteenth oil path, a seventeenth oil path, an eighteenth oil path, a P withdrawing piston cylinder, an unlocking piston cylinder, an oil pump, a filter, an oil tank, a main pressure regulating valve, a P withdrawing relief valve, a P withdrawing mechanical valve, a first pressure electromagnetic valve, a second pressure electromagnetic valve, a first feedback of the P withdrawing mechanical valve and a second feedback of the P withdrawing mechanical valve;
the filter is communicated with the oil tank through a first oil path, an oil inlet of the oil pump is communicated with the filter through a second oil path,
an inlet of the first pressure electromagnetic valve is connected with a fifth oil way through a fourth oil way, the fifth oil way is communicated with oil outlet of the oil pump, and an outlet of the first pressure electromagnetic valve is communicated with a control end on the left side of the main pressure regulating valve through a ninth oil way;
a first inlet of the main pressure regulating valve is communicated with the fifth oil way, a second inlet of the main pressure regulating valve is communicated with the fifth oil way through a sixth oil way, and a right feedback end of the main pressure regulating valve is communicated with the fifth oil way through an eighth oil way and a seventh oil way; the seventh oil way is communicated with the oil supply system through a seventeenth oil way;
a first outlet of the main pressure regulating valve is communicated with the cooling system through an eighteenth oil way, and a second outlet of the main pressure regulating valve is communicated with a second oil way through a third oil way;
an inlet of the P returning pressure relief valve is communicated with the seventh oil path through a tenth oil path, an outlet of the P returning pressure relief valve is communicated with an inlet of the P returning mechanical valve through a twelfth oil path, and the twelfth oil path is communicated with a first feedback of the P returning mechanical valve at the right end of the P returning mechanical valve through a sixteenth oil path;
an outlet of the P withdrawing mechanical valve is communicated with an inlet of the P withdrawing piston cylinder through a fourteenth oil path, the fourteenth oil path is communicated with a second feedback of the P withdrawing mechanical valve at the right end of the P withdrawing mechanical valve through a fifteenth oil path, the first feedback of the P withdrawing mechanical valve is not communicated with the second feedback of the P withdrawing mechanical valve, and the action area of the first feedback of the P withdrawing mechanical valve is smaller than that of the second feedback of the P withdrawing mechanical valve;
an inlet of the second pressure electromagnetic valve is communicated with the seventh oil path, oil outlet of the second pressure electromagnetic valve is communicated with an inlet of the unlocking piston cylinder through a thirteenth oil path, the thirteenth oil path is communicated with a control end on the right side of the P withdrawing pressure relief valve through an eleventh oil path, and the second pressure electromagnetic valve controls the unlocking piston cylinder and the P withdrawing pressure relief valve.
Optionally, the hydraulic control system further comprises a P-returning mechanical valve spring, the P-returning mechanical valve spring is arranged at the left end of the P-returning mechanical valve, when the P-returning mechanical valve is in the left end working position, the twelfth oil path is communicated with the sixteenth oil path, the fourteenth oil path and the fifteenth oil path are communicated with the oil tank, and when the P-returning mechanical valve is in the right end working position, the twelfth oil path is communicated with the fourteenth oil path.
Optionally, the oil tank further comprises a P-returning pressure relief valve spring, the P-returning pressure relief valve spring is arranged at the left end of the P-returning pressure relief valve, the tenth oil path is communicated with the sixteenth oil path when the P-returning pressure relief valve is located at the left end working position, the tenth oil path is disconnected from the sixteenth oil path when the P-returning pressure relief valve is located at the right end working position, and the sixteenth oil path is communicated with the oil tank.
Optionally, the device further comprises a P withdrawing piston spring, the P withdrawing piston spring is arranged at the right end of the P withdrawing piston cylinder, the working position of the left end of the P withdrawing piston cylinder is in a P state, and the working position of the right end of the P withdrawing piston cylinder is in a non-P state.
Optionally, the unlocking device further comprises an unlocking piston spring, the unlocking piston spring is arranged at the right end of the unlocking piston cylinder, the left end working position of the unlocking piston cylinder is in a locking state, and the right end working position of the unlocking piston cylinder is in an unlocking state.
Optionally, when the first pressure solenoid valve is in the left end operating position, the fourth oil path is communicated with the ninth oil path, and when the first pressure solenoid valve is in the right end operating position, the fourth oil path is disconnected from the ninth oil path, and the ninth oil path is communicated with the oil tank.
Optionally, when the second pressure solenoid valve is in the left end operating position, the seventh oil path is disconnected from the thirteenth oil path, the thirteenth oil path is communicated with the oil tank, and when the second pressure solenoid valve is in the right end operating position, the seventh oil path is communicated with the thirteenth oil path.
Optionally, when the main pressure regulating valve is in the left working position, the fifth oil path is not communicated with the eighteenth oil path, and the sixth oil path is not communicated with the third oil path; when the main pressure regulating valve is in the middle working position, the fifth oil way is communicated with the eighteenth oil way, the sixth oil way is not communicated with the third oil way, when the main pressure regulating valve is in the right working position, the fifth oil way is communicated with the eighteenth oil way, and the sixth oil way is communicated with the third oil way.
Optionally, the first pressure solenoid valve and the second pressure solenoid valve are both two-position three-way proportional pressure reducing valves; the main pressure regulating valve is a three-position four-way mechanical valve; the P withdrawing pressure relief valve and the P withdrawing mechanical valve are two-position three-way mechanical valves.
In a second aspect, the invention provides a vehicle, and a hydraulic parking system using the dual clutch transmission of the invention.
The invention has the following advantages: the invention can control the P withdrawing and unlocking actions of hydraulic parking by only using 2 electromagnetic valves, and can normally work by only using 3 electromagnetic valves compared with the prior art, wherein the first pressure electromagnetic valve is the system requirement, and the increase of the parking function is equivalent to the increase of the number of only one electromagnetic valve of the second pressure electromagnetic valve, so the invention has the advantages of low cost and simple structure, and can meet the parking requirement of the double-clutch transmission.
Drawings
FIG. 1 is a schematic view of the structure of the present embodiment;
in the figure: 1-a first oil way, 2-a second oil way, 3-a third oil way, 4-a fourth oil way, 5-a fifth oil way, 6-a sixth oil way, 7-a seventh oil way, 8-an eighth oil way, 9-a ninth oil way, 10-a tenth oil way, 11-an eleventh oil way, 12-a twelfth oil way, 13-a thirteenth oil way, 14-a fourteenth oil way, 15-a fifteenth oil way, 16-a sixteenth oil way, 17-a seventeenth oil way, 18-an eighteenth oil way, 19-a P withdrawing piston cylinder, 20-a unlocking piston cylinder, 21-an oil pump, 22-a filter, 23-an oil tank, 24-a main pressure regulating valve, 25-a P withdrawing relief valve, 26-a P withdrawing mechanical valve, 27-a P withdrawing mechanical valve spring and 28-a P withdrawing relief valve spring, 29-a P withdrawing piston spring, 30-an unlocking piston spring, 31-a first pressure solenoid valve, 32-a second pressure solenoid valve, 33-a P withdrawing mechanical valve first feedback, 34-a P withdrawing mechanical valve second feedback, 35-a cooling system and 36-an oil supply system.
Detailed Description
The invention will be further explained with reference to the drawings.
As shown in fig. 1, a hydraulic parking system of a dual clutch transmission, the hydraulic control system comprises a first oil way 1, a second oil way 2, a third oil way 3, a fourth oil way 4, a fifth oil way 5, a sixth oil way 6, a seventh oil way 7, an eighth oil way 8, a ninth oil way 9, a tenth oil way 10, an eleventh oil way 11, a twelfth oil way 12, a thirteenth oil way 13, a fourteenth oil way 14, a fifteenth oil way 15, a sixteenth oil way 16, a seventeenth oil way 17, an eighteenth oil way 18, an oil pump 21, a filter 22, an oil tank 23, a first pressure electromagnetic valve 31, a second pressure electromagnetic valve 32, a main pressure regulating valve 24, a P withdrawing relief valve 25, a P withdrawing mechanical valve 26, a P withdrawing mechanical valve spring 27, a P withdrawing relief valve spring 28, a P withdrawing piston spring 29, an unlocking piston spring 30, a P withdrawing piston cylinder 19, an unlocking piston cylinder 20, a P withdrawing mechanical valve first feedback 33 and a P withdrawing mechanical valve second feedback 34; the first pressure solenoid valve 31 and the second pressure solenoid valve 32 are both two-position three-way proportional pressure reducing valves; the main pressure regulating valve 24 is a three-position four-way mechanical valve; the P withdrawing pressure relief valve 25 and the P withdrawing mechanical valve 26 are two-position three-way mechanical valves. The connection relation of the above parts is as follows:
the filter 22 is communicated with the oil tank 23 through the first oil path 1, and the oil inlet of the oil pump 21 is communicated with the filter 22 through the second oil path 2. The inlet of the first pressure solenoid valve 31 is connected with the fifth oil path 5 through the fourth oil path 4, the fifth oil path 5 is communicated with the oil outlet of the oil pump 21, and the outlet of the first pressure solenoid valve 31 is communicated with the control end on the left side of the main pressure regulating valve 24 through the ninth oil path 9. A first inlet of the main pressure regulating valve 24 is communicated with the fifth oil path 5, a second inlet of the main pressure regulating valve 24 is communicated with the fifth oil path 5 through a sixth oil path 6, and a right feedback end of the main pressure regulating valve 24 is communicated with the fifth oil path 5 through an eighth oil path 8 and a seventh oil path 7; the seventh oil passage 7 communicates with the oil supply system 36 through the seventeenth oil passage 17. The first outlet of the main pressure-regulating valve 24 communicates with the cooling system 35 through the eighteenth oil passage 18, and the second outlet of the main pressure-regulating valve 24 communicates with the second oil passage 2 through the third oil passage 3. An inlet of the P returning pressure relief valve 25 is communicated with the seventh oil path 7 through a tenth oil path 10, an outlet of the P returning pressure relief valve 25 is communicated with an inlet of the P returning mechanical valve 26 through a twelfth oil path 12, and the twelfth oil path 12 is communicated with a P returning mechanical valve first feedback 33 at the right end of the P returning mechanical valve 26 through a sixteenth oil path 16. An outlet of the P withdrawing mechanical valve 26 is communicated with an inlet of the P withdrawing piston cylinder 19 through a fourteenth oil path 14, the fourteenth oil path 14 is communicated with a P withdrawing mechanical valve second feedback 34 at the right end of the P withdrawing mechanical valve 26 through a fifteenth oil path 15, the P withdrawing mechanical valve first feedback 33 and the P withdrawing mechanical valve second feedback 34 are not communicated, and the action area of the P withdrawing mechanical valve first feedback 33 is smaller than that of the P withdrawing mechanical valve second feedback 34. An inlet of the second pressure electromagnetic valve 32 is communicated with the seventh oil path 7, oil outlet of the second pressure electromagnetic valve 32 is communicated with an inlet of the unlocking piston cylinder 20 through a thirteenth oil path 13, the thirteenth oil path 13 is communicated with a control end on the right side of the P withdrawing pressure relief valve 25 through an eleventh oil path 11, and the second pressure electromagnetic valve 32 controls the unlocking piston cylinder 20 and the P withdrawing pressure relief valve 25.
In this embodiment, the P-returning mechanical valve spring 27 is disposed at the left end of the P-returning mechanical valve 26, when the P-returning mechanical valve 26 is at the left end operating position, the twelfth oil passage 12 communicates with the sixteenth oil passage 16, the fourteenth oil passage 14 communicates with the fifteenth oil passage 15, and when the P-returning mechanical valve 26 is at the right end operating position, the twelfth oil passage 12 communicates with the fourteenth oil passage 14.
In this embodiment, the P-returning relief valve spring 28 is disposed at the left end of the P-returning relief valve 25, when the P-returning relief valve 25 is located at the left end working position, the tenth oil path 10 is communicated with the sixteenth oil path 16, and when the P-returning relief valve 25 is located at the right end working position, the tenth oil path 10 is disconnected from the sixteenth oil path 16, and the sixteenth oil path 16 is communicated with the oil tank.
In this embodiment, the P-withdrawing piston spring 29 is disposed at the right end of the P-withdrawing piston cylinder 19, the left end of the P-withdrawing piston cylinder 19 is in a P state, and the right end of the P-withdrawing piston cylinder 19 is in a non-P state.
In this embodiment, the unlocking piston spring 30 is disposed at the right end of the unlocking piston cylinder 20, the left end working position of the unlocking piston cylinder 20 is in a locking state, and the right end working position of the unlocking piston cylinder 20 is in an unlocking state.
In this embodiment, when the first pressure solenoid valve 31 is in the left end operating position, the fourth oil path 4 is communicated with the ninth oil path 9, and when the first pressure solenoid valve 31 is in the right end operating position, the fourth oil path 4 is disconnected from the ninth oil path 9, and the ninth oil path 9 is communicated with the oil tank 23.
In this embodiment, when the second pressure solenoid valve 32 is in the left end operating position, the seventh oil path 7 is disconnected from the thirteenth oil path 13, the thirteenth oil path 13 is communicated with the oil tank, and when the second pressure solenoid valve 32 is in the right end operating position, the seventh oil path 7 is communicated with the thirteenth oil path 13.
In this embodiment, when the main pressure regulating valve 24 is in the left position, the fifth oil passage 5 is not communicated with the eighteenth oil passage 18, and the sixth oil passage 6 is not communicated with the third oil passage 3, when the main pressure regulating valve 24 is in the middle position, the fifth oil passage 5 is communicated with the eighteenth oil passage 18, and the sixth oil passage 6 is not communicated with the third oil passage 3, and when the main pressure regulating valve 24 is in the right position, the fifth oil passage 5 is communicated with the eighteenth oil passage 18, and the sixth oil passage 6 is communicated with the third oil passage 3.
In this embodiment, only two solenoid valves are used to control the hydraulic parking to move back P and unlock, and compared with the conventional technology, the hydraulic parking device can normally work only by using three solenoid valves, wherein the first pressure solenoid valve 31 is required by the oil supply system 36, and the addition of the parking function is equivalent to the addition of only one solenoid valve (i.e., the second pressure solenoid valve 32), so that the hydraulic parking device is low in cost and simple in structure, and can meet the parking requirement of a dual clutch transmission.
The working process of the embodiment is as follows:
referring to fig. 1, when the oil pump 21 is operated, the working oil in the oil tank 23 enters the inlet of the oil pump 21 through the first oil path 1 and the filter 22. Working oil at the outlet of the oil pump 21 enters the inlet of a first pressure solenoid valve 31 through a fourth oil path 4 and a fifth oil path 5, working oil at the outlet of the first pressure solenoid valve 31 enters the left control end of a main pressure regulating valve 24 through a ninth oil path 9, working oil at the outlet of the oil pump 21 enters the right feedback end of the main pressure regulating valve 24 through the fifth oil path 5, a seventh oil path 7 and an eighth oil path 8, the pressure at the left control end of the main pressure regulating valve 24 is balanced with the pressure at the right feedback end of the main pressure regulating valve, the working position of the main pressure regulating valve 24 is at a middle position or a right position, when the main pressure regulating valve 24 is at the middle working position, the fifth oil path 5 is communicated with an eighteenth oil path 18, the sixth oil path 6 is not communicated with the third oil path 3, when the main pressure regulating valve 24 is at the right working position, the fifth oil path 5 is communicated with the eighteenth oil path 18, and the sixth oil path 6 is communicated with the third oil path 3. The pressures of the hydraulic oil in the fourth oil passage 4 and the fifth, sixth, seventh, eighth, tenth and seventeenth oil passages 5, 6, 7, 8, 10 and 17 are adjusted by adjusting the pressure of the hydraulic oil at the outlet of the first pressure solenoid valve 31.
The working oil with the pressure adjusted by the first pressure solenoid valve 31 enters the inlet of the second pressure solenoid valve 32 through the seventh oil path 7, and the outlet working oil of the second pressure solenoid valve 32 enters the control ends of the unlocking piston cylinder 20 and the P-withdrawing relief valve 25 through the thirteenth oil path 13 and the eleventh oil path 11, so that the second pressure solenoid valve 32 directly controls the working positions of the unlocking piston cylinder 20 and the P-withdrawing relief valve 25.
The spring force of the unlocking piston spring 30 and the acting area of the unlocking piston cylinder 20 are set so that the unlocking piston cylinder 20 acts to complete the unlocking action when the pressure in the thirteenth oil passage 13 is greater than 2 bar. The spring force of the P withdrawing piston spring 29 and the acting area of the P withdrawing piston cylinder 19 are set so that when the pressure in the fourteenth oil passage 14 is greater than 2bar, the P withdrawing piston cylinder 19 acts to complete the P withdrawing action.
The spring force of the P-returning relief valve spring 28 and the control end action area of the P-returning relief valve 25 are set, when the working oil pressure in the eleventh oil path 11 is less than 5bar, the P-returning relief valve 25 is located at the left end working position, the tenth oil path 10 is communicated with the twelfth oil path 12, when the working oil pressure in the eleventh oil path 11 is greater than 6bar, the P-returning relief valve 25 is located at the right end working position, the twelfth oil path 12 is communicated with the oil tank, and the tenth oil path 10 is disconnected from the twelfth oil path 12.
When the P-withdrawing pressure relief valve 25 is at the left end working position, working oil enters the twelfth oil path 12 and the sixteenth oil path 16 from the tenth oil path 10, the spring force of the P-withdrawing mechanical valve spring 27 and the feedback areas of the first feedback 33 of the P-withdrawing mechanical valve and the second feedback 34 of the P-withdrawing mechanical valve are set, when the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is increased from small to large and is smaller than 7bar, the P-withdrawing mechanical valve spring 27 is at the left end working position, the twelfth oil path 12 is disconnected from the fourteenth oil path 14, and the fourteenth oil path 14 and the fifteenth oil path 15 are communicated with an oil tank. When the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is small and greatly increased to be more than 8bar, the P-withdrawing mechanical valve spring 27 is in a right end working position, the twelfth oil path 12 is communicated with the fourteenth oil path 14, and the working oil enters the P-withdrawing piston cylinder 19 from the twelfth oil path 12 and the fourteenth oil path 14. When the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is greatly reduced and is greater than 3.5bar, the P-withdrawing mechanical valve 26 is at the right end working position at the moment, the twelfth oil path 12 is communicated with the fourteenth oil path 14, when the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is greatly reduced and is less than 2.5bar, the P-withdrawing mechanical valve spring 27 is at the left end working position, the fourteenth oil path 14 is communicated with an oil tank, the twelfth oil path 12 is disconnected from the fourteenth oil path 14, and the P-withdrawing piston cylinder 19 is depressurized. Therefore, through the parameter setting of the P withdrawing mechanical valve 26 and the P withdrawing pressure relief valve 25, the working oil pressure of the P withdrawing piston cylinder 19 is controlled by the first pressure solenoid valve 31 and the second pressure solenoid valve 32 through combined logic.
The traditional hydraulic parking scheme needs three solenoid valves, one solenoid valve controls the pressure of the oil supply system 36, and two solenoid valves respectively control the P withdrawing and the unlocking actions. The system in this embodiment has only used two solenoid valves just can control the move back P and the unblock action of hydraulic pressure parking, need use three solenoid valves at least for traditional art just normally to work, wherein first pressure solenoid valve 31 is the system oil supply demand, increases low cost's move back P mechanical valve 26 and move back P relief valve 25, has increased 32 solenoid valve quantity of second pressure solenoid valve simultaneously.
In order to meet the requirement of normal operation of the system, the following settings are required:
through each valve spring and the live area setting, the first working position switching pressure of the P withdrawing mechanical valve 26 is different from the working position switching pressure after working, the first working position switching pressure is greater than the working position switching pressure after working, the first working position switching pressure of the P withdrawing mechanical valve 26 is greater than the working position switching pressure of the P withdrawing pressure release valve 25, and the working position switching pressure of the P withdrawing pressure release valve 25 is greater than the unlocking pressure of the unlocking piston cylinder 20.
In the present embodiment, the logic of the parking control is as follows:
the P withdrawing requirement of the parking mechanical structure is as follows:
in the first step, the pressure of the working oil in the P withdrawing piston cylinder 19 is kept at 0bar, and the oil in the unlocking piston cylinder 20 is filled to more than 2bar for unlocking.
And in the second step, the oil pressure of the unlocking piston cylinder 20 is kept to be more than 2bar, and the P withdrawing piston cylinder 19 is filled with oil to be more than 2bar to complete the P withdrawing action.
And thirdly, after the displacement of the P withdrawing piston cylinder 19 is detected to reach a non-P state, oil is drained to 0bar by the unlocking piston cylinder 20, and the unlocking piston cylinder 20 is in a locking state.
And fourthly, the P withdrawing piston cylinder 19 keeps the oil pressure of more than 2bar, and the displacement of the P withdrawing piston cylinder 19 in the travelling process is prevented.
The parking mechanical structure meets the requirement of P:
in a first step, the unlocking piston cylinder 20 is filled with oil to more than 2bar for unlocking.
And in the second step, the oil pressure of the unlocking piston cylinder 20 is kept to be more than 2bar, the oil is drained to 0bar through the P withdrawing piston cylinder 19, and the P withdrawing piston cylinder 19 is in a P state.
And thirdly, after the displacement of the P withdrawing piston cylinder 19 is detected to reach the P state, oil is drained to 0bar by the unlocking piston cylinder 20, and the unlocking piston cylinder 20 is in a locking state.
In this embodiment, the hydraulic system control logic:
p withdrawing:
in the first step, the first pressure solenoid valve 31 controls the working oil pressure in the seventh oil passage 7 and the tenth oil passage 10 not to exceed the working position switching pressure 7bar of the P-withdrawing mechanical valve 26, for example, the working oil pressure is controlled to be 5 bar. The second pressure solenoid valve 32 controls the pressure in the eleventh oil path 11 and the thirteenth oil path 13 not to exceed the switching pressure of the working position of the P-withdrawing pressure release valve 25 by 5bar, and simultaneously, the pressure is required to be greater than the action pressure of the unlocking piston cylinder 20 by 2bar, for example, the working oil pressure is controlled to be 4 bar. At this time, the P-withdrawing relief valve 25 is in the left end working position, and the tenth oil passage 10 is communicated with the sixteenth oil passage 16. The P withdrawing mechanical valve 26 is in a left end working position, the fourteenth oil channel 14 is communicated with the oil tank, so that the working oil pressure of the P withdrawing piston cylinder 19 is kept at 0bar, and the P withdrawing piston cylinder 19 is in a P state. Meanwhile, the second pressure solenoid valve 32 controls the pressure in the thirteenth oil path 13 to be 4bar, the oil pressure of the working oil in the unlocking piston cylinder 20 exceeds the unlocking oil pressure by 2bar, the mechanical structure executes the unlocking action, and the unlocking piston cylinder 20 is in an unlocking state.
In the second step, the second pressure solenoid valve 32 controls the working oil pressure in the eleventh oil path 11 and the thirteenth oil path 13 to be kept constant at 4bar, at this time, the P-withdrawing pressure relief valve 25 is located at the left end working position, and the tenth oil path 10 is communicated with the sixteenth oil path 16. The first pressure solenoid valve 31 controls the working oil pressure in the twelfth oil passage 12 and the sixteenth oil passage 16 to be larger than the switching pressure of the working position of the P-withdrawing mechanical valve 26 by 8bar, if the working oil pressure is controlled to be 10bar, the P-withdrawing mechanical valve 26 is at the right end working position at the moment, the twelfth oil passage 12 is communicated with the fourteenth oil passage 14, the working oil pressure in the P-withdrawing piston cylinder 19 exceeds the P-withdrawing oil pressure by 2bar, the mechanical structure executes the P-withdrawing action, and the P-withdrawing piston cylinder 19 is in a non-P state.
And thirdly, after the P withdrawing piston cylinder 19 is detected to be displaced to a non-P state, the second pressure solenoid valve 32 controls the working oil pressure in the eleventh oil passage 11 and the thirteenth oil passage 13 to 0bar, the oil in the unlocking piston cylinder 20 is drained to 0bar, and the unlocking piston cylinder 20 is in a locking state.
Fourthly, the first pressure solenoid valve 31 controls the pressure of the working oil in the seventh oil path 7, the tenth oil path 10 and the oil supply system 36 to be greater than 3.5bar, the second pressure solenoid valve 32 controls the pressure of the working oil in the eleventh oil path 11 and the thirteenth oil path 13 to be maintained at 0bar, the P-withdrawing pressure relief valve 25 is located at the left end working position, the tenth oil path 10 is communicated with the twelfth oil path 12, when the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is maintained to be greater than 3.5bar, the P-withdrawing mechanical valve 26 is located at the right end working position, the twelfth oil path 12 is communicated with the fourteenth oil path 14, the P-withdrawing piston cylinder 19 is communicated with the oil supply system 36 to maintain the pressure of the working oil to be greater than 3.5bar, and the displacement of the P-withdrawing piston cylinder 19 in the driving process is prevented.
Entering P:
in the first step, the first pressure solenoid valve 31 controls the pressure of the working oil in the seventh oil passage 7, the tenth oil passage 10 and the oil supply system 36 to 10bar, and the second pressure solenoid valve 32 controls the pressure in the eleventh oil passage 11 and the thirteenth oil passage 13 not to exceed the switching pressure of the working position of the P-withdrawing pressure release valve 25 by 5bar, and simultaneously, the pressure is required to be 2bar higher than the actuating pressure of the unlocking piston cylinder 20, for example, the pressure of the working oil is controlled to 4 bar. The thirteenth oil passage 13 is communicated with the unlocking piston cylinder 20, the oil pressure of the working oil in the unlocking piston cylinder 20 exceeds the unlocking oil pressure by 2bar, the mechanical structure executes the unlocking action, and the unlocking piston cylinder 20 is in an unlocking state.
And secondly, controlling the pressure in the eleventh oil path 11 and the thirteenth oil path 13 to exceed the switching pressure of 6bar when the working position of the P-withdrawing pressure relief valve 25 is closed by the second pressure electromagnetic valve 32, and if the working oil pressure is controlled to be 8bar, the P-withdrawing pressure relief valve 25 is located at the right end working position, disconnecting the tenth oil path 10 from the twelfth oil path 12, and communicating the sixteenth oil path 16 with the oil tank. Therefore, the pressure of the working oil in the twelfth oil path 12 and the sixteenth oil path 16 is 0bar, at this time, the P-withdrawing mechanical valve 26 is in the left end working position, the twelfth oil path 12 is disconnected from the fourteenth oil path 14, the fourteenth oil path 14 is communicated with the oil tank, the fourteenth oil path 14 is communicated with the P-withdrawing piston 61, the oil is drained to 0bar by the P-withdrawing piston cylinder 19, and the P-withdrawing piston cylinder 19 is in a P state.
And thirdly, after the P-withdrawing piston cylinder 19 is detected to be displaced to reach the P state, the first pressure solenoid valve 31 controls the pressure of the working oil in the seventh oil passage 7, the tenth oil passage 10 and the oil supply system 36 to reach 0bar, then the second pressure solenoid valve 32 controls the pressure of the working oil in the eleventh oil passage 11 and the thirteenth oil passage 13 to reach 0bar, oil is drained from the unlocking piston cylinder 20 to reach 0bar, and the unlocking piston cylinder 20 is in an unlocking state. The second pressure solenoid valve 32 cannot be adjusted prior to the first pressure solenoid valve 31 to ensure that the operating position of the P-backing mechanical valve 26 does not switch.
Claims (10)
1. A hydraulic parking system of a dual clutch transmission is characterized in that: comprises a first oil way (1), a second oil way (2), a third oil way (3), a fourth oil way (4), a fifth oil way (5), a sixth oil way (6), a seventh oil way (7), an eighth oil way (8), a ninth oil way (9), a tenth oil way (10), an eleventh oil way (11), a twelfth oil way (12), a thirteenth oil way (13), a fourteenth oil way (14) and a fifteenth oil way (15), a sixteenth oil way (16), a seventeenth oil way (17), an eighteenth oil way (18), a P withdrawing piston cylinder (19), an unlocking piston cylinder (20), an oil pump (21), a filter (22), an oil tank (23), a main pressure regulating valve (24), a P withdrawing pressure relief valve (25), a P withdrawing mechanical valve (26), a first pressure electromagnetic valve (31), a second pressure electromagnetic valve (32), a P withdrawing mechanical valve first feedback (33) and a P withdrawing mechanical valve second feedback (34);
the filter (22) is communicated with the oil tank (23) through a first oil path (1), an oil inlet of the oil pump (21) is communicated with the filter (22) through a second oil path (2),
an inlet of the first pressure electromagnetic valve (31) is connected with a fifth oil path (5) through a fourth oil path (4), the fifth oil path (5) is communicated with the oil outlet of the oil pump (21), and an outlet of the first pressure electromagnetic valve (31) is communicated with a control end on the left side of the main pressure regulating valve (24) through a ninth oil path (9);
a first inlet of the main pressure regulating valve (24) is communicated with a fifth oil way (5), a second inlet of the main pressure regulating valve (24) is communicated with the fifth oil way (5) through a sixth oil way (6), and a right feedback end of the main pressure regulating valve (24) is communicated with the fifth oil way (5) through an eighth oil way (8) and a seventh oil way (7); the seventh oil way (7) is communicated with an oil supply system (36) through a seventeenth oil way (17);
a first outlet of the main pressure regulating valve (24) is communicated with a cooling system (35) through an eighteenth oil way (18), and a second outlet of the main pressure regulating valve (24) is communicated with a second oil way (2) through a third oil way (3);
an inlet of the P returning pressure relief valve (25) is communicated with the seventh oil path (7) through a tenth oil path (10), an outlet of the P returning pressure relief valve (25) is communicated with an inlet of the P returning mechanical valve (26) through a twelfth oil path (12), and the twelfth oil path (12) is communicated with a first feedback (33) of the P returning mechanical valve at the right end of the P returning mechanical valve (26) through a sixteenth oil path (16);
an outlet of the P withdrawing mechanical valve (26) is communicated with an inlet of a P withdrawing piston cylinder (19) through a fourteenth oil path (14), the fourteenth oil path (14) is communicated with a P withdrawing mechanical valve second feedback (34) at the right end of the P withdrawing mechanical valve (26) through a fifteenth oil path (15), a P withdrawing mechanical valve first feedback (33) and a P withdrawing mechanical valve second feedback (34) are not communicated, and the action area of the P withdrawing mechanical valve first feedback (33) is smaller than that of the P withdrawing mechanical valve second feedback (34);
an inlet of the second pressure electromagnetic valve (32) is communicated with the seventh oil path (7), oil outlet of the second pressure electromagnetic valve (32) is communicated with an inlet of the unlocking piston cylinder (20) through a thirteenth oil path (13), the thirteenth oil path (13) is communicated with a control end on the right side of the P withdrawing pressure relief valve (25) through an eleventh oil path (11), and the second pressure electromagnetic valve (32) controls the unlocking piston cylinder (20) and the P withdrawing pressure relief valve (25).
2. The hydraulic parking system of a dual clutch transmission as recited in claim 1, wherein: the hydraulic control system is characterized by further comprising a P returning mechanical valve spring (27), the P returning mechanical valve spring (27) is arranged at the left end of the P returning mechanical valve (26), when the P returning mechanical valve (26) is located at the left end working position, the twelfth oil way (12) is communicated with the sixteenth oil way (16), the fourteenth oil way (14) is communicated with the fifteenth oil way (15) to form an oil tank, and when the P returning mechanical valve (26) is located at the right end working position, the twelfth oil way (12) is communicated with the fourteenth oil way (14).
3. The hydraulic parking system of a dual clutch transmission as set forth in claim 2, wherein: still including moving back P relief valve spring (28), move back P relief valve spring (28) and set up in moving back the left end of P relief valve (25), when moving back P relief valve (25) and being in left end operating position, tenth oil circuit (10) and sixteenth oil circuit (16) intercommunication, when moving back P relief valve (25) and being in right-hand member operating position, tenth oil circuit (10) and sixteenth oil circuit (16) disconnection, sixteenth oil circuit (16) intercommunication oil tank.
4. The hydraulic parking system of a dual clutch transmission as set forth in claim 3, wherein: still including moving back P piston spring (29), move back P piston spring (29) and set up in the right-hand member that moves back P piston cylinder (19), move back the left end operating position of P piston cylinder (19) and be the P state, move back the right-hand member operating position of P piston cylinder (19) and be non-P state.
5. The hydraulic parking system of a dual clutch transmission as set forth in claim 4, wherein: still include unblock piston spring (30), unblock piston spring (30) set up in the right-hand member of unblock piston cylinder (20), and the left end operating position of unblock piston cylinder (20) is the locking state, and the right-hand member operating position of unblock piston cylinder (20) is the unblock state.
6. The hydraulic parking system of a dual clutch transmission as set forth in claim 5, wherein: when the first pressure electromagnetic valve (31) is located at the left end working position, the fourth oil path (4) is communicated with the ninth oil path (9), when the first pressure electromagnetic valve (31) is located at the right end working position, the fourth oil path (4) is disconnected with the ninth oil path (9), and the ninth oil path (9) is communicated with the oil tank (23).
7. The hydraulic parking system of a dual clutch transmission as set forth in claim 6, wherein: when the second pressure electromagnetic valve (32) is in the left end working position, the seventh oil way (7) is disconnected from the thirteenth oil way (13), the thirteenth oil way (13) is communicated with the oil tank, and when the second pressure electromagnetic valve (32) is in the right end working position, the seventh oil way (7) is communicated with the thirteenth oil way (13).
8. The hydraulic parking system of a dual clutch transmission as set forth in claim 7, wherein: when the main pressure regulating valve (24) is in a left working position, the fifth oil way (5) is not communicated with the eighteenth oil way (18), and the sixth oil way (6) is not communicated with the third oil way (3); when the main pressure regulating valve (24) is in a middle working position, the fifth oil way (5) is communicated with the eighteenth oil way (18), the sixth oil way (6) is not communicated with the third oil way (3), when the main pressure regulating valve (24) is in a right working position, the fifth oil way (5) is communicated with the eighteenth oil way (18), and the sixth oil way (6) is communicated with the third oil way (3).
9. The hydraulic parking system of a dual clutch transmission according to any one of claims 1 to 8, characterized in that: the first pressure solenoid valve (31) and the second pressure solenoid valve (32) are both two-position three-way proportional pressure reducing valves; the main pressure regulating valve (24) is a three-position four-way mechanical valve; the P withdrawing pressure relief valve (25) and the P withdrawing mechanical valve (26) are two-position three-way mechanical valves.
10. A vehicle, characterized in that: a hydraulic parking system employing the dual clutch transmission as claimed in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110586922.5A CN113357365B (en) | 2021-05-27 | 2021-05-27 | Hydraulic parking system of double-clutch transmission and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110586922.5A CN113357365B (en) | 2021-05-27 | 2021-05-27 | Hydraulic parking system of double-clutch transmission and vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113357365A CN113357365A (en) | 2021-09-07 |
| CN113357365B true CN113357365B (en) | 2022-07-05 |
Family
ID=77527980
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110586922.5A Active CN113357365B (en) | 2021-05-27 | 2021-05-27 | Hydraulic parking system of double-clutch transmission and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113357365B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009035348A1 (en) * | 2009-07-30 | 2011-02-03 | Volkswagen Ag | Parking lock device for automatic or automated motor vehicle transmission, has slide valve provided between relief valve and hydraulic cylinder in pressure pipe and servo-controlled by shift valve |
| CN104534087A (en) * | 2014-11-25 | 2015-04-22 | 重庆长安汽车股份有限公司 | Parking locking mechanism for automatic transmission |
| WO2016087018A2 (en) * | 2014-12-06 | 2016-06-09 | Daimler Ag | Parking lock device |
| DE102015006323A1 (en) * | 2015-05-16 | 2016-11-17 | Thomas Magnete Gmbh | Parking lock with lock |
| CN107636365A (en) * | 2015-07-24 | 2018-01-26 | 宝马股份公司 | Parking braking system |
| JP2018047825A (en) * | 2016-09-23 | 2018-03-29 | ジヤトコ株式会社 | Park locking device |
| CN109764132A (en) * | 2019-01-29 | 2019-05-17 | 东风汽车集团有限公司 | A kind of hydraulic control method and system of hybrid power gearbox |
| CN112178184A (en) * | 2020-10-15 | 2021-01-05 | 中国第一汽车股份有限公司 | Hydraulic control system of automatic transmission |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011105068A1 (en) * | 2011-06-21 | 2012-07-05 | Daimler Ag | Vehicle parking lock device with at least one locking element |
| DE102016210874B4 (en) * | 2016-06-17 | 2018-06-07 | Audi Ag | Device for actuating a parking brake of an automatic transmission, and parking lock device for such an automatic transmission |
| JP6725615B2 (en) * | 2018-09-21 | 2020-07-22 | 株式会社Ｓｕｂａｒｕ | Parking lock device |
-
2021
- 2021-05-27 CN CN202110586922.5A patent/CN113357365B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009035348A1 (en) * | 2009-07-30 | 2011-02-03 | Volkswagen Ag | Parking lock device for automatic or automated motor vehicle transmission, has slide valve provided between relief valve and hydraulic cylinder in pressure pipe and servo-controlled by shift valve |
| CN104534087A (en) * | 2014-11-25 | 2015-04-22 | 重庆长安汽车股份有限公司 | Parking locking mechanism for automatic transmission |
| WO2016087018A2 (en) * | 2014-12-06 | 2016-06-09 | Daimler Ag | Parking lock device |
| DE102015006323A1 (en) * | 2015-05-16 | 2016-11-17 | Thomas Magnete Gmbh | Parking lock with lock |
| CN107636365A (en) * | 2015-07-24 | 2018-01-26 | 宝马股份公司 | Parking braking system |
| JP2018047825A (en) * | 2016-09-23 | 2018-03-29 | ジヤトコ株式会社 | Park locking device |
| CN109764132A (en) * | 2019-01-29 | 2019-05-17 | 东风汽车集团有限公司 | A kind of hydraulic control method and system of hybrid power gearbox |
| CN112178184A (en) * | 2020-10-15 | 2021-01-05 | 中国第一汽车股份有限公司 | Hydraulic control system of automatic transmission |
Non-Patent Citations (1)
| Title |
|---|
| 曹利民.国产轿车自动变速器维修技术讲座(八十九).《汽车维修技师》.2010,(第12期), * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113357365A (en) | 2021-09-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7410438B2 (en) | Switching-valve arrangement for a shifting system of an automatic transmission | |
| CA2119616C (en) | Selective control valve system with float | |
| US8944232B2 (en) | Hydraulical shifting device for an automatic transmission | |
| CN100549431C (en) | Fluid pressure valve device | |
| CN101560999B (en) | Large-flow quick throttle proportional valve | |
| US10590962B2 (en) | Directional control valve | |
| US7690734B2 (en) | Brake steering method and apparatus | |
| CN103038517A (en) | Valve arrangement | |
| WO2005119100A1 (en) | System for limiting a force load | |
| CN102425582A (en) | Hydraulic control valve and getting-off support leg control system of firefighting vehicle with hydraulic control valve | |
| CN113357365B (en) | Hydraulic parking system of double-clutch transmission and vehicle | |
| EP2603705A1 (en) | Hydraulic control system | |
| WO2012125793A1 (en) | Cushioned swing circuit | |
| EP3482084B1 (en) | System for recovering energy from a hydraulic actuator | |
| US20010035303A1 (en) | Crawler motion control system | |
| CN202381436U (en) | Hydraulic control valve and fire truck off outrigger control system with hydraulic control valve | |
| CN102359586B (en) | Proportional voltage regulation control system for automatic gearbox of forklift truck | |
| CN212055322U (en) | Hydraulic pilot control system and engineering machinery | |
| CN204284053U (en) | For guide's oil circuit relief arrangement and the pilot hydraulic control system of virtual wall function | |
| CN112161046B (en) | Hydraulic control system for transmission of engineering vehicle | |
| CN110259749B (en) | Power control valve block, hydraulic pump assembly and engineering machinery | |
| CN114017450A (en) | Hydraulic control device of automatic transmission | |
| CN210623538U (en) | Hydraulic control device for automatic transmission | |
| JPS6138204A (en) | Multiple pilot valve for multiple hydraulic selector valve | |
| CN111765137B (en) | Compound action detection module, hydraulic system and crane |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |