CN201561075U - Cooling control system of dual-clutch gearbox - Google Patents
Cooling control system of dual-clutch gearbox Download PDFInfo
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- CN201561075U CN201561075U CN 200920218965 CN200920218965U CN201561075U CN 201561075 U CN201561075 U CN 201561075U CN 200920218965 CN200920218965 CN 200920218965 CN 200920218965 U CN200920218965 U CN 200920218965U CN 201561075 U CN201561075 U CN 201561075U
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- cooling
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- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The utility model relates to a cooling control system of a dual-clutch gearbox, which relates to a hydraulic control loop, is simple in structure and can selectively cool clutches. The cooling control system comprises a cooling oil tank and a pump, an input end of the pump is communicated with the cooling oil tank, an output end of the pump is communicated with a main pressure pipeline, the main pressure pipeline is provided with a main pressure regulating valve, the main pressure regulating valve comprises a first bias component and a valve component, a right control end of the valve component is communicated with the main pressure pipeline, a working oil port A of a main pressure regulating electromagnetic valve is connected with a left control end of the main pressure regulating valve, a first clutch hydraulic pipeline and a second clutch hydraulic pipeline are respectively communicated with a first clutch and a second clutch, a hydraulic control two-position three-way valve is further arranged between the first clutch hydraulic pipeline and the second clutch hydraulic pipeline, and the first clutch hydraulic pipeline and the second clutch hydraulic pipeline are respectively connected with a left control end and a right control end of the hydraulic control two-position three-way valve.
Description
Technical field
The utility model relates to a kind of hydraulic control circuit, particularly relates to a kind of cooling control loop that is used for double clutch gearbox.
Background technique
The cooling of dual-clutch transmission is one of key technology important during double-clutch speed changer is designed and developed with lubricating, and it is directly connected to the long-term safety of speed changer and uses and reliability.The subject matter that the clutch cooling and lubricating is paid close attention to has the selectivity cooling of pair clutch and the adjusting of lubrication flow, in the cooling and lubricating system of existing double-clutch automatic gearbox, controlling schemes is more numerous and diverse, function is short of to some extent, at publication number is in the U.S. Patent application of US2006005647A1, US2006009326A1, adopted the scheme of proportional flow control valve pilot pressure, controlled the overflow section of 3-position 4-way guiding valve, regulated the cooling flow, but do not related to selectivity cooling in the loop two clutches.In the gear shift control process of double clutch, there are two clutch and the situation of separating, the heating situation of two clutches is inconsistent, two required cold oil flows of clutch also are inconsistent, (clutching pressure raises gradually to be in the clutch of jointing state gradually, the frictional heating amount is big during joint), need big flow cold oil to carry out cooling and lubricating; And the clutch on-off pressure of another separation reduces gradually, and heating value is thereupon little, and needed cold oil flow is also less relatively.And existing double clutch gearbox cooling system is just unified to adjust to the cold oil flow of two clutches, can not carry out the selectivity adjustment according to the difference of two clutch febrile states, has increased energy consumption, has reduced cooling effectiveness.
The model utility content
The technical problems to be solved in the utility model provides a kind of simple in structure, can carry out the cooling control system of the double clutch gearbox of selectivity cooling to clutch.
The cooling control system of the utility model double clutch gearbox, comprise cooling fuel tank and pump, the input end of described pump is connected with the cooling fuel tank by first filter, delivery side of pump is connected with the principal pressure pipeline, on the described principal pressure pipeline main pressure regulator valve is housed, the oil inlet P 1 of described main pressure regulator valve and P2 are connected with the principal pressure pipeline respectively, the actuator port A of main pressure regulator valve is connected with the adjusting pipeline, the actuator port B of main pressure regulator valve is connected with the input end of pump by suction line, main pressure regulator valve comprises first biasing assembly and valve member, be provided with liquid chunnel in the described valve member, described liquid chunnel is divided into position, a left side with valve member, meta and right position, the liquid chunnel of position, a left side makes the oil inlet P 1 of main pressure regulator valve, P2 and actuator port A, B is in closed condition, the liquid chunnel of meta makes the oil inlet P 1 of main pressure regulator valve be communicated with actuator port A, all the other hydraulic fluid ports are in closed condition, the liquid chunnel of right position makes the oil inlet P 1 of main pressure regulator valve be communicated with actuator port A, oil inlet P 2 is communicated with actuator port B, described first biasing assembly is installed in the left control end of valve member, the right control end of described valve member is connected with the principal pressure pipeline by first restrictor, described adjusting pipeline is connected with the clutch cooling line, described clutch cooling line is connected with a clutch cooling channel and No. two clutch cooling channels respectively by second restrictor and the 3rd restrictor, wherein said principal pressure pipeline is connected by the oil inlet P of second filter with the main pressure regulator solenoid valve, the actuator port A of described main pressure regulator solenoid valve links to each other with the left control end of main pressure regulator valve with the 5th restrictor by the 4th restrictor, the oil return inlet T of main pressure regulator solenoid valve is connected with the cooling fuel tank, by control main pressure regulator solenoid valve the partial pressure in the principal pressure pipeline is discharged from oil return inlet T, residual pressure is regulated control by actuator port A to main pressure regulator valve
Clutch cool stream control valve is housed between described adjusting pipeline and the clutch cooling line, the oil inlet P of described clutch cool stream control valve is connected with the adjusting pipeline, the actuator port A of clutch cool stream control valve is connected with the clutch cooling line, the left control end of clutch cool stream control valve is equipped with second biasing assembly, described principal pressure pipeline is connected by the oil inlet P of the 3rd filter with clutch cooling solenoid valve, the actuator port A of described clutch cooling solenoid valve links to each other with the right control end of the 7th restrictor with clutch cool stream control valve by the 6th restrictor, the oil return inlet T of clutch cooling solenoid valve is connected with the cooling fuel tank, by solenoidoperated cluthes cooling solenoid valve the partial pressure in the principal pressure pipeline is discharged from oil return inlet T, residual pressure is regulated control by actuator port A to the flow of clutch cool stream control valve
Described principal pressure pipeline is connected with the oil inlet P of a Clutch Control solenoid valve and the oil inlet P of No. two Clutch Control solenoid valves respectively by the 4th filter and the 5th filter, the actuator port A of a described Clutch Control solenoid valve and the actuator port A of No. two Clutch Control solenoid valves are connected with a clutch hydraulic pressure pipeline and No. two clutch hydraulic pressure pipelines by the 6th filter and the 7th filter respectively, the oil return inlet T of the oil return inlet T of a Clutch Control solenoid valve and No. two Clutch Control solenoid valves is connected with the cooling fuel tank respectively, the actuator port A of a Clutch Control solenoid valve and the actuator port A of No. two Clutch Control solenoid valves also are provided with the left side of feedback oil circuit and a Clutch Control solenoid valve and No. two Clutch Control solenoid valves respectively, right control end is connected, on the described feedback oil circuit feedback restrictor is housed, when Clutch Control solenoid valve or No. two Clutch Control solenoid valves get when electric, its oil inlet P is connected with actuator port A, when a Clutch Control solenoid valve or No. two Clutch Control solenoid valve outages, its actuator port A is connected with oil return inlet T, a Clutch Control solenoid valve and No. two Clutch Control solenoid valves are to regulate the control ratio pressure valve continuously
A described clutch hydraulic pressure pipeline and No. two clutch hydraulic pressure pipelines are connected with a clutch and No. two clutches respectively, be provided with the cooling selector valve between a clutch hydraulic pressure pipeline and No. two clutch hydraulic pressure pipelines, described cooling selector valve is the hydraulic control two-position three-way valve, the oil inlet P of described hydraulic control two-position three-way valve is connected with the adjusting pipeline, the actuator port A of hydraulic control two-position three-way valve and B are connected with a clutch cooling channel and No. two clutch cooling channels respectively, the left control end of hydraulic control two-position three-way valve is equipped with the 3rd biasing assembly, a described clutch hydraulic pressure pipeline and No. two clutch hydraulic pressure pipelines respectively with the left side of hydraulic control two-position three-way valve, right control end links to each other.
The cooling control system of the utility model double clutch gearbox, wherein said adjusting pipeline is that cooling line is connected with axle, described axle is that cooling line is that cooling nozzle is connected with axle, and axle is to be connected with the 8th restrictor on the cooling line in turn, directly to move relief valve, cooler and the 9th restrictor.
The cooling control system of the utility model double clutch gearbox is equipped with the 8th filter on the wherein said principal pressure pipeline, is parallel with the bypass one-way valve on described the 8th filter.
The cooling control system of the utility model double clutch gearbox is equipped with first accumulator between wherein said the 6th restrictor and the 7th restrictor.
The cooling control system of the utility model double clutch gearbox is equipped with second accumulator between a wherein said Clutch Control solenoid valve and the 6th filter, between described No. two Clutch Control solenoid valves and the 7th filter the 3rd accumulator is housed.
The cooling control system of the utility model double clutch gearbox, wherein said first biasing assembly, second biasing assembly and the 3rd biasing assembly all are bias spring.
The cooling control system difference from prior art of the utility model double clutch gearbox is that the cooling control system of the utility model double clutch gearbox is equipped with clutch cool stream control valve between adjusting pipeline and clutch cooling line, and clutch cooling solenoid valve has been installed on the principal pressure pipeline to be used for clutch cool stream control valve is controlled, clutch cooling solenoid valve is according to the Temperature Feedback of clutch, can regulate the passage section of clutch cool stream control valve, make the cold oil flow that is delivered in the clutch cooling line to increase and decrease according to the temperature of clutch; The cooling selector valve of between clutch hydraulic pressure pipeline and No. two clutch hydraulic pressure pipelines, installing, according to different clutch state in two clutches, automatically the solenoidoperated cluthes cooling line is selected the big clutch of heating value is increased the cold oil flow, makes cooling effectiveness be improved.
The axle that is provided with in the cooling control system of the utility model double clutch gearbox is that cooling line and axle are that cooling nozzle makes when clutch is cooled off, also can the axle and the gear that are in high bit in the gearbox be cooled off, prevent the interior bad phenomenon of high bit part cooling effect that causes owing to the cold oil liquid level is lower of gearbox; The accumulator that installs additional in the native system is the effect for the pressure pulsation of playing absorption system and minimizing compression shock.
Be described further below in conjunction with the cooling control system of accompanying drawing double clutch gearbox of the present utility model.
Description of drawings
Fig. 1 is the schematic diagram of the cooling control system of the utility model double clutch gearbox.
Embodiment
As shown in Figure 1, the cooling control system of the utility model double clutch gearbox comprises cooling fuel tank 1 and pump 2, the input end of pump 2 is connected with cooling fuel tank 1 by first filter 3, the output terminal of pump 2 is connected with principal pressure pipeline 4, be equipped with on the principal pressure pipeline 4 on the 8th filter 47, the eight filters 47 and be parallel with bypass one-way valve 48.Main pressure regulator valve 5 is housed on the principal pressure pipeline 4, the oil inlet P 1 of main pressure regulator valve 5 and P2 are connected with principal pressure pipeline 4 respectively, the actuator port A of main pressure regulator valve 5 is connected with adjusting pipeline 6, the actuator port B of main pressure regulator valve 5 is connected by the input end of suction line 7 with pump 2, main pressure regulator valve 5 comprises first bias spring 8 and valve member 9, be provided with liquid chunnel 10 in the valve member 9, liquid chunnel 10 is divided into position, a left side with valve member 9, meta and right position, the liquid chunnel 10 of position, a left side makes the oil inlet P 1 of main pressure regulator valve 5, P2 and actuator port A, B is in closed condition, the liquid chunnel 10 of meta makes the oil inlet P 1 of main pressure regulator valve 5 be communicated with actuator port A, all the other hydraulic fluid ports are in closed condition, the liquid chunnel 10 of right position makes the oil inlet P 1 of main pressure regulator valve 5 be communicated with actuator port A, oil inlet P 2 is communicated with actuator port B, first bias spring 8 is installed in the left control end of valve member 9, and the right control end of valve member 9 is connected with principal pressure pipeline 4 by first restrictor 11.
Regulating pipeline 6 is connected with clutch cooling line 12, clutch cooling line 12 is connected with a clutch cooling channel 15 and No. two clutch cooling channels 16 respectively by second restrictor 13 and the 3rd restrictor 14, principal pressure pipeline 4 is connected with the oil inlet P of main pressure regulator solenoid valve 18 by second filter 17, the actuator port A of main pressure regulator solenoid valve 18 links to each other with the left control end of main pressure regulator valve 5 with the 5th restrictor 20 by the 4th restrictor 19, the oil return inlet T of main pressure regulator solenoid valve 18 is connected with cooling fuel tank 1, by control main pressure regulator solenoid valve 18 partial pressure in the principal pressure pipeline 4 is discharged from oil return inlet T, residual pressure is regulated control by actuator port A to main pressure regulator valve 5.Less when principal pressure pipeline 4 internal pressures, be positioned at the valve member that first bias spring 8 of main pressure regulator valve 5 left control ends makes and be positioned at position, a left side, the oil inlet P 1 of main pressure regulator valve 5, P2 and actuator port A, B are in closed condition; When principal pressure pipeline 4 internal pressures raise, the pressure of main pressure regulator valve 5 right control ends raises, make valve member 9 be moved to the left meta, the oil inlet P 1 of main pressure regulator valve 5 is communicated with actuator port A, cold oil enters from principal pressure pipeline 4 by main pressure regulator valve 5 and regulates pipeline 6, main pressure regulator solenoid valve 18 is regulated the delivery pressure of its actuator port A according to the variation in pressure in the principal pressure pipeline 4, thereby controls the bias force of main pressure regulator valve 5 left control ends, makes main pressure regulator valve 5 keep the delivery pressure of setting; When the pressure in the principal pressure pipeline 4 is big, the right control end of main pressure regulator valve 5 is subjected to the bias force that big pressure has overcome left control end, promote valve member 9 and move to right position, make the oil inlet P 2 of main pressure regulator valve 5 be communicated with actuator port B, the part cold oil is back to the input end of pump 2 from the actuator port B suction line 7 of flowing through, thereby has reduced the pressure in the principal pressure pipeline 4.
Regulate between pipeline 6 and the clutch cooling line 12 clutch cool stream control valve 21 is housed, the oil inlet P of clutch cool stream control valve 21 is connected with adjusting pipeline 6, the actuator port A of clutch cool stream control valve 21 is connected with clutch cooling line 12, the left control end of clutch cool stream control valve 21 is equipped with second bias spring 22, principal pressure pipeline 4 is connected by the oil inlet P of the 3rd filter 23 with clutch cooling solenoid valve 24, the actuator port A of clutch cooling solenoid valve 24 links to each other with the right control end of the 7th restrictor 26 with clutch cool stream control valve 21 by the 6th restrictor 25, between the 6th restrictor 25 and the 7th restrictor 26 first accumulator 49 is housed, the oil return inlet T of clutch cooling solenoid valve 24 is connected with cooling fuel tank 1, by solenoidoperated cluthes cooling solenoid valve 24 partial pressure in the principal pressure pipeline 4 is discharged from oil return inlet T, residual pressure is regulated control by actuator port A to the flow of clutch cool stream control valve 21.When the temperature of clutch raises, clutch cooling solenoid valve 24 improves the delivery pressure of its actuator port A according to automatically controlled instruction, make the right control end pressure of clutch cool stream control valve 21 improve, thereby improve the flow that cold oil enters clutch cooling line 12.
Regulating pipeline 6 is that cooling line 41 is connected with axle, and axle is that cooling line 41 is that cooling nozzle 42 is connected with axle, spool is to be connected with the 8th restrictor 43 on the cooling line 41 in turn, directly to move relief valve 44, cooler 45 and the 9th restrictor 46.For gear that in gearbox, is in lower position and bearing, owing to be loaded with the cold oil of certain depth in the gearbox, the gear of lower position when rotated, cold oil can be splashed and hold, can lubricate the gear and the bearing of lower position, but for for gear that is in the higher position in the gearbox and bearing, the lubricating system that adopts cold oil to splash is infeasible, and this is that gear and the bearing of cooling nozzle 42 to higher position of living in carries out the lubricated and cooling of hydrojet with regard to needing extra cooling system by the axle that is positioned at the gearbox top.
Principal pressure pipeline 4 is connected with the oil inlet P of a Clutch Control solenoid valve 29 and the oil inlet P of No. two Clutch Control solenoid valves 30 respectively by the 4th filter 27 and the 5th filter 28, the actuator port A of a Clutch Control solenoid valve 29 and the actuator port A of No. two Clutch Control solenoid valves 30 are connected with a clutch hydraulic pressure pipeline 33 and No. two clutch hydraulic pressure pipelines 34 by the 6th filter 31 and the 7th filter 32 respectively, be equipped with between 50, No. two Clutch Control solenoid valves 30 of second accumulator and the 7th filter 32 between Clutch Control solenoid valve 29 and the 6th filter 31 the 3rd accumulator 51 is housed.The oil return inlet T of the oil return inlet T of a Clutch Control solenoid valve 29 and No. two Clutch Control solenoid valves 30 is connected with cooling fuel tank 1 respectively, the actuator port A of a Clutch Control solenoid valve 29 and the actuator port A of No. two Clutch Control solenoid valves 30 also are provided with the left side of feedback oil circuit 35 and a Clutch Control solenoid valve 29 and No. two Clutch Control solenoid valves 30 respectively, right control end is connected, feedback restrictor 36 is housed on the feedback oil circuit 35, when Clutch Control solenoid valve 29 or No. two Clutch Control solenoid valves 30 when electric, its oil inlet P is connected with actuator port A, when a Clutch Control solenoid valve 29 or No. two Clutch Control solenoid valve 30 outages, its actuator port A is connected with oil return inlet T, a Clutch Control solenoid valve 29 and No. two Clutch Control solenoid valves 30 are to regulate the control ratio pressure valve continuously
A clutch hydraulic pressure pipeline 33 and No. two clutch hydraulic pressure pipelines 34 are connected with a clutch 37 and No. two clutches 38 respectively, be provided with the cooling selector valve between a clutch hydraulic pressure pipeline 33 and No. two clutch hydraulic pressure pipelines 34, the cooling selector valve is a hydraulic control two-position three-way valve 39, the oil inlet P of hydraulic control two-position three-way valve 39 is connected with adjusting pipeline 6, the actuator port A of hydraulic control two-position three-way valve 39 and B are connected with a clutch cooling channel 15 and No. two clutch cooling channels 16 respectively, the left control end of hydraulic control two-position three-way valve 39 be equipped with 40, numbers clutch hydraulic pressure pipelines 33 of the 3rd bias spring and No. two clutch hydraulic pressure pipelines 34 respectively with the left side of hydraulic control two-position three-way valve 39, right control end links to each other.When a clutch 37 is in separation, when No. two clutch 38 is in bonding state, the heating value of a clutch 37 reduces, the heating value of No. two clutches 38 increases, No. one clutch hydraulic pressure pipeline 33 interior cold oils flow back in the cooling fuel tank 1 from a Clutch Control solenoid valve 29, make clutch hydraulic pressure pipeline 33 interior pressure reduce, hydraulic control two-position three-way valve 39 moves right under the pressure difference effect of a clutch hydraulic pressure pipeline 33 and No. two clutch hydraulic pressure pipelines 34, the oil inlet P of hydraulic control two-position three-way valve 39 is communicated with actuator port B, thereby has increased cold oil flow No. two clutch cooling channels 16.On the contrary, when a clutch 37 is in combination, when No. two clutch 38 is in separated state, the heating value of No. two clutches 38 reduces, the heating value of a clutch 37 increases, No. two clutch hydraulic pressure pipeline 34 interior cold oils flow back in the cooling fuel tank 1 from No. two Clutch Control solenoid valves 30, make No. two clutch hydraulic pressure pipeline 34 interior pressure reduce, hydraulic control two-position three-way valve 39 is moved to the left under the pressure difference effect of a clutch hydraulic pressure pipeline 33 and No. two clutch hydraulic pressure pipelines 34, the oil inlet P of hydraulic control two-position three-way valve 39 is communicated with actuator port A, thereby increased cold oil flow, thereby realize clutch is optionally increased the cold oil flow to a clutch cooling channel 15.
Above-described embodiment is described preferred implementation of the present utility model; be not that scope of the present utility model is limited; under the prerequisite that does not break away from the utility model design spirit; various distortion and improvement that those of ordinary skills make the technical solution of the utility model all should fall in the definite protection domain of the utility model claims.
Claims (6)
1. the cooling control system of a double clutch gearbox, comprise cooling fuel tank (1) and pump (2), the input end of described pump (2) is connected with cooling fuel tank (1) by first filter (3), the output terminal of pump (2) is connected with principal pressure pipeline (4), main pressure regulator valve (5) is housed on the described principal pressure pipeline (4), the oil-feed P1 of described main pressure regulator valve (5) and P2 are connected with principal pressure pipeline (4) respectively, the actuator port A of main pressure regulator valve (5) is connected with adjusting pipeline (6), the actuator port B of main pressure regulator valve (5) is connected by the input end of suction line (7) with pump (2), main pressure regulator valve (5) comprises first biasing assembly (8) and valve member (9), be provided with liquid chunnel (10) in the described valve member (9), described liquid chunnel (10) is divided into position, a left side with valve member (9), meta and right position, the liquid chunnel (10) of position, a left side makes the oil inlet P 1 of main pressure regulator valve (5), P2 and actuator port A, B is in closed condition, the liquid chunnel of meta (10) makes the oil inlet P 1 of main pressure regulator valve (5) be communicated with actuator port A, all the other hydraulic fluid ports are in closed condition, the liquid chunnel (10) of right position makes the oil inlet P 1 of main pressure regulator valve (5) be communicated with actuator port A, oil inlet P 2 is communicated with actuator port B, described first biasing assembly (8) is installed in the left control end of valve member (9), the right control end of described valve member (9) is connected with principal pressure pipeline (4) by first restrictor (11), described adjusting pipeline (6) is connected with clutch cooling line (12), described clutch cooling line (12) is connected with a clutch cooling channel (15) and No. two clutch cooling channels (16) respectively by second restrictor (13) and the 3rd restrictor (14), it is characterized in that: described principal pressure pipeline (4) is connected by the oil inlet P of second filter (17) with main pressure regulator solenoid valve (18), the actuator port A of described main pressure regulator solenoid valve (18) links to each other with the left control end of the 5th restrictor (20) with main pressure regulator valve (5) by the 4th restrictor (19), the oil return inlet T of main pressure regulator solenoid valve (18) is connected with cooling fuel tank (1), by control main pressure regulator solenoid valve (18) partial pressure in the principal pressure pipeline (4) is discharged from oil return T, residual pressure is regulated control by actuator port A to main pressure regulator valve (5)
Between described adjusting pipeline (6) and the clutch cooling line (12) clutch cool stream control valve (21) is housed, the oil inlet P of described clutch cool stream control valve (21) is connected with adjusting pipeline (6), the actuator port A of clutch cool stream control valve (21) is connected with clutch cooling line (12), the left control end of clutch cool stream control valve (21) is equipped with second biasing assembly (22), described principal pressure pipeline (4) is connected by the oil inlet P of the 3rd filter (23) with clutch cooling solenoid valve (24), the actuator port A of described clutch cooling solenoid valve (24) links to each other with the right control end of the 7th restrictor (26) with clutch cool stream control valve (21) by the 6th restrictor (25), the oil return inlet T of clutch cooling solenoid valve (24) is connected with cooling fuel tank (1), by solenoidoperated cluthes cooling solenoid valves (24) partial pressure in the principal pressure pipeline (4) is discharged from oil return inlet T, residual pressure is regulated control by actuator port A to the flow of clutch cool stream control valve (21)
Described principal pressure pipeline (4) is connected with the oil inlet P of a Clutch Control solenoid valve (29) and the oil inlet P of No. two Clutch Control solenoid valves (30) respectively by the 4th filter (27) and the 5th filter (28), the actuator port A of the actuator port A of a described Clutch Control solenoid valve (29) and No. two Clutch Control solenoid valves (30) is connected with a clutch hydraulic pressure pipeline (33) and No. two clutch hydraulic pressure pipelines (34) by the 6th filter (31) and the 7th filter (32) respectively, the oil return inlet T of the oil return inlet T of a Clutch Control solenoid valve (29) and No. two Clutch Control solenoid valves (30) is connected with cooling fuel tank (1) respectively, the actuator port A of the actuator port A of a Clutch Control solenoid valve (29) and No. two Clutch Control solenoid valves (30) also is provided with the left side of feedback oil circuit (35) and a Clutch Control solenoid valve (29) and No. two Clutch Control solenoid valves (30) respectively, right control end is connected, feedback restrictor (36) is housed on the described feedback oil circuit (35), when a Clutch Control solenoid valve (29) or No. two Clutch Control solenoid valves (30) when electric, its oil inlet P is connected with actuator port A, when a Clutch Control solenoid valve (29) or No. two Clutch Control solenoid valves (30) outage, its actuator port A is connected with oil return inlet T, a Clutch Control solenoid valve (29) and No. two Clutch Control solenoid valves (30) are to regulate the control ratio pressure valve continuously
A described clutch hydraulic pressure pipeline (33) and No. two clutch hydraulic pressure pipelines (34) are connected with a clutch (37) and No. two clutches (38) respectively, be provided with the cooling selector valve between a clutch hydraulic pressure pipeline (33) and No. two clutch hydraulic pressure pipelines (34), described cooling selector valve is hydraulic control two-position three-way valve (39), the oil inlet P of described hydraulic control two-position three-way valve (39) is connected with adjusting pipeline (6), the actuator port A of hydraulic control two-position three-way valve (39) and B are connected with a clutch cooling channel (15) and No. two clutch cooling channels (16) respectively, the left control end of hydraulic control two-position three-way valve (39) is equipped with the 3rd biasing assembly (40), a described clutch hydraulic pressure pipeline (33) and No. two clutch hydraulic pressure pipelines (34) respectively with the left side of hydraulic control two-position three-way valve (39), right control end links to each other.
2. the cooling control system of double clutch gearbox according to claim 1, it is characterized in that: described adjusting pipeline (6) is that cooling line (41) is connected with axle, described axle is that cooling line (41) is that cooling nozzle (42) is connected with axle, and axle is to be connected with the 8th restrictor (43) on the cooling line (41) in turn, directly to move relief valve (44), cooler (45) and the 9th restrictor (46).
3. the cooling control system of double clutch gearbox according to claim 1 and 2 is characterized in that: the 8th filter (47) is housed on the described principal pressure pipeline (4), is parallel with bypass one-way valve (48) on described the 8th filter (47).
4. the cooling control system of double clutch gearbox according to claim 3 is characterized in that: between described the 6th restrictor (25) and the 7th restrictor (26) first accumulator (49) is housed.
5. the cooling control system of double clutch gearbox according to claim 4, it is characterized in that: between a described Clutch Control solenoid valve (29) and the 6th filter (31) second accumulator (50) is housed, between described No. two Clutch Control solenoid valves (30) and the 7th filter (32) the 3rd accumulator (51) is housed.
6. the cooling control system of double clutch gearbox according to claim 5, it is characterized in that: described first biasing assembly (8), second biasing assembly (22) and the 3rd biasing assembly (40) all are bias spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200920218965 CN201561075U (en) | 2009-12-10 | 2009-12-10 | Cooling control system of dual-clutch gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200920218965 CN201561075U (en) | 2009-12-10 | 2009-12-10 | Cooling control system of dual-clutch gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201561075U true CN201561075U (en) | 2010-08-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200920218965 Expired - Lifetime CN201561075U (en) | 2009-12-10 | 2009-12-10 | Cooling control system of dual-clutch gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201561075U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101709776B (en) * | 2009-12-10 | 2012-05-23 | 重庆青山工业有限责任公司 | Cooling control system of dual-clutch gearbox |
| CN109253393A (en) * | 2018-11-07 | 2019-01-22 | 常州信息职业技术学院 | A kind of machinery automatic control formula pipeline reversing arrangement |
-
2009
- 2009-12-10 CN CN 200920218965 patent/CN201561075U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101709776B (en) * | 2009-12-10 | 2012-05-23 | 重庆青山工业有限责任公司 | Cooling control system of dual-clutch gearbox |
| CN109253393A (en) * | 2018-11-07 | 2019-01-22 | 常州信息职业技术学院 | A kind of machinery automatic control formula pipeline reversing arrangement |
| CN109253393B (en) * | 2018-11-07 | 2020-03-17 | 常州信息职业技术学院 | Mechanical self-control type pipeline reversing device |
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