KR101416107B1 - Controlling apparatus for dual clutch - Google Patents

Abstract

The present invention can control the DCT by using one electric pump so that it can be operated only when the hydraulic pressure is required, thereby improving the efficiency by lowering the consumption power to be used in comparison with the mechanical pump of the always- And to provide a control device for a dual clutch transmission.
In addition, the present invention provides an accumulator capable of maximizing the efficiency by minimizing the load applied to the hydraulic pump and using the filled hydraulic pressure when necessary, by accumulating and using unused oil pressure, Another object is to provide a control device for a clutch transmission.

Description

[0001] CONTROLLING APPARATUS FOR DUAL CLUTCH [0002]

The present invention relates to a control apparatus for a dual clutch transmission, and more particularly, to a control apparatus for a dual clutch transmission, and more particularly to a control apparatus for a dual clutch transmission, The present invention relates to a control device that maximizes efficiency by minimizing the amount of drainage of hydraulic pressure generated once as well as increasing efficiency by lowering power.

Generally, the dual clutch transmission is provided with two shift clutches, so that the shifting of the even-numbered gears and the odd-numbered gears can be achieved for each of the shifting clutches. These dual-clutch transmissions are fast-moving and smooth, so more and more vehicles are on the way.

Patent Document 1 discloses a method and a control system for controlling the hydraulic pressure of such a dual clutch transmission (DCT). (HPS) for providing oil to the actuators (ACT) of the DCT; providing oil to the lubrication and cooling system (LCS) of the DCT; A low pressure section (LPS); And adjuster means (030) for sending excess oil from said high pressure portion (HPS) to said lubrication and cooling system (LCS) and maintaining the pressure at said high pressure portion (HPS) constant; And a hydraulic control means, wherein the pump means (020) is a fixed displacement double action pump comprising a first pressure outlet (X) and a second pressure outlet (Y)

The hydraulic control means includes: (LPS) between the pump means 020 and the lubrication and cooling system LCS is connected to the branch line 060L of the low pressure portion LPS which is connected to the high pressure portion HPS A directional valve (050) controlled by an on / off valve (040) formed between the check valve (060) formed; A 2/2-way valve (051) for connecting the second pressure outlet (Y) linked to the low pressure portion (LPS) to the suction side (SS) of the pump means (020); (HPS) main line (ML) branching from the main line (ML) at a first branch point (P1) between the pump means (020) and the actuators (ACT) A proportional pressure relief valve (030) formed in the first branch line (030L) And a proportional pressure reducing valve (080) formed in a second branch line (080L) of a main line (ML) of the high pressure portion (HPS) and communicating with the proportional pressure relief valve (030) by a first feedback line (FBL1) .

However, such a conventional control method has the following problems.

1) Normally, in case of wet DCT, since a large amount of flow is required, a continuously driven oil pump is used, and therefore, a large amount of power is required for driving the pump.

2) Not only the structure is complicated, but also a large number of spool valves are required for hydraulic control to each control element.

3) Especially, the spool valve used for the pressure control consumes a large amount of the flow rate required for the DCT control device because it requires a lot of oil in the control of the hydraulic pressure, and as a result, the control device itself becomes large in size.

4) It is necessary to secure a sufficient amount of flow formed by the always-driven pump and unnecessary drain amount of the flow having the energy in the function of the spool valve is increased, thereby acting as a factor to lower the efficiency of the vehicle.

Korean Patent Laid-Open No. 10-2008-0007530 (2008.01.22)

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a motor pump capable of controlling DCT using an electric pump so as to be operated only when oil pressure is required, And it is an object of the present invention to provide a control apparatus for a dual clutch transmission capable of reducing consumption power and improving efficiency.

In addition, the present invention provides an accumulator capable of maximizing the efficiency by minimizing the load applied to the hydraulic pump and using the filled hydraulic pressure when necessary, by accumulating and using unused oil pressure, Another object is to provide a control device for a clutch transmission.

To achieve these and other advantages and in accordance with the purpose of the present invention, as embodied and broadly described herein, there is provided a control apparatus for a dual clutch transmission, comprising: an electric oil pump for generating oil pressure from an oil pan at a predetermined pressure and storing the oil pressure in an accumulator; At least one clutch control valve for branching the oil pressure generated from the electric oil pump to control the clutch of the dual clutch; At least one pressure regulating valve for diverting the oil pressure applied from the electric oil pump to lower the pressure; At least one flow control valve connected to each of the pressure control valves to operate a shift actuator; A pressure holding valve for supplying oil pressure supplied from the electric oil pump as lubricant required by the dual clutch; And a pressure relief valve for bypassing the oil pressure supplied from the electric oil pump when the oil pressure reaches a predetermined pressure or higher, and a check valve is provided on the output side of the accumulator.

In particular, the electric oil pump is an internal gear or an external gear type oil pump, and is driven by a BLDC motor. This electric oil pump is selectively driven (ON-Demand) only when constant driving or axial pressure is required.

Further, the clutch control valve is provided with a residual pressure valve. Further, a fail-safe valve is further provided between the clutch control valve and the dual clutch so as to prevent the clutch from being operated when the clutch fails.

Further, the pressure control valves may be a pair, and the flow control valves may include four pairs of pressure control valves. At this time, the pressure regulating valve is independently controlled, and the flow control valve is capable of bi-directional flow control. Each of the flow control valves is a three-port-two-way flow control valve.

The pressure holding valve is connected to the pressure regulating valve and supplies the necessary lubricating oil. In addition, a cooler for cooling the oil supplied from the pressure holding valve and a pressure sensor for controlling the pressure of the oil to be output are further provided.

In the control device for a dual clutch transmission according to the present invention, a built-in strainer and a bypass pipe are provided in parallel between the electric oil pump and the accumulator, and the backflow prevention valve has an inlet side and an outlet side ; A ball moving within the body; And a bypass pipe formed between the outlet side and the body.

Such a check valve includes a body having an inlet side and an outlet side; A valve body sliding inside the body and communicating the inlet side and the outlet side through a flow path formed therein; And a bypass pipe formed between the outlet side and the body.

The accumulator may be a spring type accumulator or a gas accumulator.

The dual clutch according to the present invention is a dual clutch for wet or dry dual clutch transmission.

Finally, the outlet side of the accumulator is provided with a pressure holding valve to maintain the hydraulic pressure state branched to the clutch control valve, the pressure control valve, the flow control valve, and the pressure holding valve.

According to the control apparatus for dual clutch transmission of the present invention, the following effects can be obtained.

1) By using only one electric pump, it is possible to selectively drive (ON-demand) only when necessary axial pressure is required to obtain necessary power and oil pressure for lubrication. .

2) By using the oil pressure generated from the oil pump by accumulating pressure in the accumulator, it is possible to continuously use the generated oil pressure, thereby improving the operating efficiency of the system.

3) By applying a pressure holding valve for line pressure control, the hydraulic pressure to be drained unnecessarily is minimized, and the flow rate supplied from the hydraulic pump can be minimized. At this time, the pressure holding valve is able to be controlled even when the flow rate from the input side port to the output side and the control side port does not have a flow rate to be drained during the pressure control.

4) By applying a pressure holding valve as a control valve to control the pressure required for lubrication, it is possible to control unnecessary flow loss because the control can be performed without a flow amount to be drained during pressure control for reducing pressure.

5) By simplifying the structure of the hydraulic circuit, it is possible to reduce the occurrence factor of the abnormality as well as to easily keep track of the abnormality even when the abnormality occurs, which is easy to maintain.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a hydraulic circuit diagram showing a flow of hydraulic pressure for explaining a configuration of a control apparatus for dual clutch transmission according to Embodiment 1 of the present invention. FIG.
2 is a schematic view schematically showing a configuration of a check valve according to the present invention.
3 is a schematic view schematically showing a configuration of a modified example of the check valve according to the present invention.
4 is a hydraulic circuit diagram showing a flow of hydraulic pressure for explaining a configuration of a control apparatus for dual clutch transmission according to a second embodiment of the present invention.
5 is a hydraulic circuit diagram showing the flow of hydraulic pressure for explaining a configuration of a control apparatus for dual clutch transmission according to a third embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. Prior to this, terms and words used in the present specification and claims should not be construed as limited to ordinary or dictionary terms, and the inventor should appropriately interpret the concepts of the terms appropriately It should be interpreted in accordance with the meaning and concept consistent with the technical idea of the present invention based on the principle that it can be defined.

Therefore, the embodiments described in the present specification and the configurations shown in the drawings are merely the most preferred embodiments of the present invention and are not intended to represent all of the technical ideas of the present invention. Therefore, various equivalents It should be understood that water and variations may be present.

1 is a hydraulic circuit diagram showing a flow of hydraulic pressure for explaining a configuration of a control device for dual clutch transmission according to a first embodiment of the present invention. FIG. 2 is a schematic diagram 3 is a schematic view schematically showing a configuration of a modified example of the check valve according to the present invention

The control device according to the present invention includes one electric oil pump 10 for generating oil pressure from the oil pan OP and at least one clutch control valve 20a for controlling the dual clutch DC using this oil pressure And at least one pressure control valve 30a and 30b for controlling the actuators G1, G2, G3 and G4 for speed change by partially dividing the hydraulic pressure generated from the electric oil pump 10, A pressure holding valve 50 for branching off the hydraulic pressure and supplying lubricating oil for the dual clutch DC and a pressure relief valve 60 for protecting the control device .

The actuators G1, G2, G3 and G4 are firstly subjected to pressure reduction by the pressure control valves 30a and 30b and then are controlled by the flow control valves 40a, 40b, 40c and 40d in both directions The operation is controlled by the control.

In the present invention, a solenoid-type valve is employed in place of the spool-type valve to minimize the leak rate when using such various valves.

Hereinafter, this configuration will be described in more detail as follows.

The electric oil pump 10 functions to generate oil pressure required from the oil pan OP to the entire controller.

It is preferable that the electric oil pump 10 uses a gear type, for example, an internal gear or an external gear type oil pump so as to minimize drive control and leakage of oil during pressure generation. Needless to say, such an electric oil pump requires an electric motor or the like for driving. In the present invention, the BLDC motor 11 is used as the electric motor. The control of such an electric motor may be separately provided or may be controlled using a TCU or an MCU already mounted on the vehicle.

On the other hand, in the preferred embodiment of the present invention, the oil pressure generated from the electric oil pump 10 is stored in the accumulator 12. The accumulator 12 stores the oil pressure formed from the electric oil pump 10 and supplies the oil pressure at a constant pressure, thereby increasing the efficiency of the accumulation and increasing the power density.

In the preferred embodiment of the present invention, the accumulator 12 may use a gas such as nitrogen gas to vary the accumulation capacity so as to supply the required flow rate in the system in a short period of time, or when the space constituting the system is sufficient A spring type accumulator may be applied.

A built-in strainer 13 and a bypass pipe 14 are provided in parallel between the electric oil pump 10 and the oil pan OP. The built-in strainer 13 functions to filter foreign matters contained in the oil outputted from the electric oil pump 10 so that other constituent elements are not limited in operation due to foreign matter being stuck. When the built-in strainer 13 is clogged by a foreign substance or the like, the bypass pipe 14 functions as a bypass, thereby allowing the flow rate of the built-in strainer 13 to be supplied even if the built-in strainer 13 is clogged.

A check valve (15) is provided on the output side of the accumulator (12). The backflow prevention valve 15 supplies the oil pressure to the system from the accumulator 12. The oil pressure supplied to the system prevents the oil pressure from flowing back to the oil pan OP, The minimum oil pressure required for operation also enables control operation. This reverse flow prevention function also improves the operation reaction speed since the pressure of the accumulator 12 can be used immediately in the next operation.

On the other hand, the backflow prevention valve 15 may be a ball type as an embodiment. 2, the backflow prevention valve 15 includes a body 15a having an inlet side for receiving hydraulic pressure from the accumulator 12 side and an outlet side for supplying hydraulic pressure to the system side, And a ball 15b which moves in accordance with the hydraulic pressure difference between both sides of the oil pressure difference. The backflow prevention valve 15 further includes a bypass pipe 15c between the outlet side and the body 15a so that the hydraulic pressure distribution can be adjusted so that the ball 15b can move more smoothly by the hydraulic pressure difference. .

Also, the check valve 15 may be a valve 70 of a valve body 72 type to be slid. 3, the valve 70 includes a body 71 having an inlet side and an outlet side for supplying hydraulic pressure. Particularly, the inlet side and the outlet side are perpendicular to the longitudinal direction of the body 71 And is formed at both ends thereof. The body 71 is provided with a valve body 72 having a flow path 72a. Further, the body 71 is provided with a bypass pipe 73 between it and the outlet side. The valve body 72 is moved along the body 71 and selectively communicates the inlet side and the outlet side by the flow path 72a. 3, (a) and (b) show the state before and after the operation of the valve 70 for preventing the backflow, respectively.

Of course, a conventional ball type check valve may be used in the present invention.

The electric oil pump 10 may be controlled so as to constantly generate the oil pressure required for shifting through the constant drive system. However, it is preferable that the electric oil pump 10 may accumulate a predetermined pressure in the accumulator 12, Therefore, it is preferable to control by the ON-demand method which selectively drives only when necessary.

The clutch control valves 20a and 20b are control valves for controlling the dual clutches DC. These clutch control valves 20a and 20b are respectively used to control the dual clutch DC by branching the oil pressure generated from the electric oil pump 10. [

Here, the dual clutch (DC) according to the present invention can be applied not only to a wet type but also to a dual clutch for dry dual clutch transmission.

The clutch control valves 20a and 20b control the clutches K1 and K2 of the dual clutches DC so that these control valves can be independently controlled so that any one of them can not be used It is desirable to make some available.

By providing a residual pressure valve (not shown) in each of the clutch control valves 20a and 20b, it is preferable that the remaining control pressure is removed after the control operation so that the next control operation can be performed more accurately . Further, it is preferable that each of these control valves is provided with a pressure sensor 22 so as to be able to control the clutches K1 and K2 with a preset pressure by receiving the output pressure.

Finally, it is preferable to further provide a fail-safe valve 21 between the clutch control valves 20a, 20b and the dual clutch DC. The fail-safe valve 21 acts as a safety device for shutting off the control pressure so that the number of gear teeth is not engaged when an abnormality occurs in the clutches K1 and K2 of the dual clutches DC.

The pressure control valves 30a and 30b branch the oil pressure applied from the electric oil pump 10 to the flow control valves 40a, 40b, 40c and 40d. The pressure regulating valves 30a and 30b lower the applied oil pressure primarily to facilitate control.

At least one of the pressure regulating valves 30a and 30b may be used depending on the number of DCT transmission steps. In the preferred embodiment of the present invention, two pressure regulating valves 30a and 30b are used.

The flow control valves 40a, 40b, 40c and 40d are valves for controlling the actuators G1, G2, G3 and G4, which perform a substantially shifting action by using the hydraulic pressure supplied from the pressure control valves 30a and 30b .

Particularly, since these flow control valves 40a, 40b, 40c and 40d use valves capable of bidirectional flow control because the actuators G1, G2, G3 and G4 interact with each other, these actuators G1, G3, and G4) in order to be able to cope with the interaction.

In the preferred embodiment of the present invention, the flow control valves 40a, 40b, 40c, and 40d may be connected to the pressure control valves 30a and 30b in a one-to-one correspondence manner, It is preferable to connect them to the pressure regulating valves 30a and 30b in pairs.

The pressure holding valve 50 is a valve for providing the lubricant required for the dual clutch (DC). The pressure holding valve 50 receives oil pressure directly from the electric oil pump 10 and supplies oil to the dual clutch DC as lubricating oil.

In the preferred embodiment of the present invention, it is preferable that the pressure holding valve 50 is operated in conjunction with the pressure regulating valves 30a and 30b so as to perform lubrication. This is because the shifting operation of the clutch is performed by the actuators G1, G2, G3 and G4 substantially. Since the actuators G1, G2, G3 and G4 are controlled by the pressure control valves 30a and 30b, It is preferable to cooperate with each other to effect lubrication.

On the other hand, a cooler 51 for cooling the oil and a pressure sensor 52 for detecting the oil pressure are further provided at the outlet side of the pressure holding valve 50. The cooler 51 is for maintaining an appropriate temperature so that the lubricating effect of the oil supplied to the dual clutch DC is not lowered as the temperature of the oil is too hot to decrease the viscosity, To determine the appropriate oil pressure and flow rate.

The pressure relief valve (60) is mounted on the outlet side of the check valve (15). The pressure relief valve 60 returns oil pressure to the oil pan OP to prevent damage to the control device when the oil supplied to the control device side through the accumulator 12 becomes equal to or higher than a preset oil pressure.

4 is a hydraulic circuit diagram showing the flow of hydraulic pressure for explaining a configuration of a control apparatus for dual clutch transmission according to a second embodiment of the present invention. Here, the same components as those in the first embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

The hydraulic circuit according to the second embodiment of the present invention is further provided with a pressure holding valve 80 so as to maintain the hydraulic pressure generated from the electric oil pump 10 in comparison with the first embodiment.

At this time, the pressure holding valve 80 is mounted on the outlet side of the accumulator 12, so that the hydraulic pressure required in the overall system constituting the hydraulic circuit can be maintained without returning. That is, the hydraulic pressure generated from the accumulator 12 is supplied to the clutch control valves 20a and 20b, the pressure control valves 30a and 30b, the flow control valves 40a, 40b, 40c, and 40d, The pressure maintaining valve 80 allows the pressure to be maintained without returning hydraulic pressure from these valves, so that the amount of drain can be minimized.

That is, the hydraulic pressure discharged from the accumulator 12 varies to some extent, and the pressure fluctuation width is reduced by the pressure holding valve 80, so that the hydraulic pressure required by the control device can be maintained.

On the other hand, in Fig. 4, the hydraulic circuit according to the second embodiment of the present invention shows a state in which the fail-safe valve 21 is not provided, unlike the first embodiment.

5 is a hydraulic circuit diagram showing the flow of hydraulic pressure for explaining a configuration of a control apparatus for dual clutch transmission according to a third embodiment of the present invention.

The hydraulic circuit according to the third embodiment of the present invention differs from the second embodiment in the configuration of the flow control valves 40a ', 40b', 40c ', and 40d'. That is, any one of the actuators G1, G2, G3 and G4 connected to the respective flow control valves 40a ', 40b', 40c 'and 40d' 40b ', 40c', 40d ') controlled by the control pressure of the flow control valves 40a', 40b ', 40c', 40d 'while the other (for example, .

Accordingly, the actuators G1, G2, G3 and G4 can be applied not only to withstand high pressures but also with a relatively low-cost flow control solenoid.

In the control device according to the present invention, the oil pressure generated through one electric oil pump is accumulated through the accumulator and branched to a control valve requiring pressure, and in particular, the pressure holding valve The lubricating action required by the double clutch can be achieved.

Therefore, it is possible to supply both the control pressure and the lubricating oil using a single electric oil pump while the structure is simple.

10: Electric oil pump
11: BLDC motor
12: Accumulator
13: Built-in type
14: Bypass pipe
15: Backflow prevention valve
20a, 20b: clutch control valve
30a, 30b: pressure regulating valve
40a, 40b, 40c, 40d: Flow control valve
50: Pressure holding valve

Claims (16)

An electric oil pump 10 for generating an oil pressure from the oil pan OP at a predetermined pressure and storing the oil pressure in the accumulator 12;
Two clutch control valves 20a and 20b for branching the oil pressure generated from the electric oil pump 10 to control the clutches K1 and K2 of the dual clutches DC;
At least one pressure control valve (30a, 30b) for diverting the oil pressure applied from the electric oil pump (10) to lower the pressure;
At least one flow control valve (40a, 40b, 40c, 40d) connected to each of the pressure control valves (30a, 30b) for operating the actuators (G1, G2, G3, G4) for speed change;
A pressure holding valve (50) for supplying oil pressure supplied from the electric oil pump (10) as lubricant required by the dual clutch (DC); And
And a pressure relief valve (60) for bypassing the oil pressure supplied from the electric oil pump (10) when the oil pressure reaches a predetermined pressure or more,
A check valve (15) is provided on the output side of the accumulator (12)
The check valve (15)
A body (15a) having an inlet side and an outlet side;
A ball 15b moving within the body 15a; And
And a bypass pipe (15c) formed between the outlet side and the body (15a).
An electric oil pump 10 for generating an oil pressure from the oil pan OP at a predetermined pressure and storing the oil pressure in the accumulator 12;
Two clutch control valves 20a and 20b for branching the oil pressure generated from the electric oil pump 10 to control the clutches K1 and K2 of the dual clutches DC;
At least one pressure control valve (30a, 30b) for diverting the oil pressure applied from the electric oil pump (10) to lower the pressure;
At least one flow control valve (40a, 40b, 40c, 40d) connected to each of the pressure control valves (30a, 30b) for operating the actuators (G1, G2, G3, G4) for speed change;
A pressure holding valve (50) for supplying oil pressure supplied from the electric oil pump (10) as lubricant required by the dual clutch (DC); And
And a pressure relief valve (60) for bypassing the oil pressure supplied from the electric oil pump (10) when the oil pressure reaches a predetermined pressure or more,
A check valve (15) is provided on the output side of the accumulator (12)
The check valve (15)
A body (71) having an inlet side and an outlet side;
A valve body 72 which slides inside the body 71 and communicates the inlet side and the outlet side through a flow path 72a formed therein; And
And a bypass pipe (73) formed between the outlet side and the body (71).
3. The method according to claim 1 or 2,
The electric oil pump 10 is an internal-gear or an external-gear-type oil pump,
Is driven by the BLDC motor (11).
The method of claim 3,
Wherein the electric oil pump (10) is selectively driven (ON-Demand) only when driving or axial pressure is required at all times.
delete 3. The method according to claim 1 or 2,
The pressure regulating valves 30a and 30b are a pair,
Wherein the flow control valves 40a, 40b, 40c, and 40d have four pairs of pressure control valves 30a and 30b.
The method according to claim 6,
The pressure regulating valves 30a and 30b are independently controlled,
Wherein the flow control valves (40a, 40b, 40c, 40d) are bi-directional flow controllable.
3. The method according to claim 1 or 2,
Wherein the pressure holding valve (50) is connected to the pressure regulating valves (30a, 30b) to supply the required lubricating oil.
9. The method of claim 8,
A cooler 51 for cooling the oil supplied from the pressure holding valve 50 and a pressure sensor 52 for controlling the pressure of the oil to be output. .
delete 3. The method according to claim 1 or 2,
Wherein a built-in strainer (13) and a bypass pipe (14) are provided in parallel between the electric oil pump (10) and the accumulator (12).
delete delete 3. The method according to claim 1 or 2,
Wherein the accumulator (12) is a spring-type accumulator or a gas accumulator.
3. The method according to claim 1 or 2,
Wherein the dual clutch (DC) is a dual clutch for wet or dry dual clutch transmission.
3. The method according to claim 1 or 2,
A pressure holding valve (80) is provided at the outlet side of the accumulator (12)
The oil pressure state branched to the clutch control valves 20a and 20b, the pressure control valves 30a and 30b, the flow control valves 40a, 40b, 40c and 40d, and the pressure holding valve 50 is maintained For a dual clutch transmission.

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