KR20150051397A - Dual Pneumatic Pressure type Actuator and Engine Power Air Flux Control Device in Vehicle therefor - Google Patents

Abstract

A double pneumatic integrated actuator (1-1) of the present invention comprises: a diaphragm (4) defining an internal space of a damper cover (1) as a positive-pressure forming chamber, and an internal space of a canister (7) as a negative-pressure forming chamber; and a rod (19) opening a flow passage by movement due to a contraction of the diaphragm (4) generated by a negative pressure, or the expansion of the diaphragm (4) generated by a positive pressure. Therefore, the present invention is capable of replacing a back-pressure control valve (300-1) of an electric waste gate valve (100) or a variable control module (200) or a low pressure-exhaust gas recirculation device (300) and a motor of an exhaust gas recirculation (EGR) valve by opening and closing the flow passage due to the operation of the double pneumatic integrated actuator (1-1) not only in a positive pressure condition, but also in a negative pressure condition (vacuum pressure). Accordingly, the present invention is capable of reducing costs due to an omission of the expensive motor.

Description

Technical Field [0001] The present invention relates to a dual-pneumatic coupling type actuator,

The present invention relates to an actuator, and more particularly, to a dual-pneumatic coupling type actuator capable of opening and closing a flow passage in the same manner as a positive pressure even at a negative pressure (vacuum pressure) and an engine performance enhancing device using the same.

Generally, various engine performance enhancing devices are applied to the vehicle to improve the engine performance and improve the fuel efficiency.

For example, a turbocharger system, a variable control module (VCM), and a low-pressure exhaust gas recirculation (LP-EGR) flow rate control device are exemplified.

Normally, in the turbocharger system, VCM or LP-EGR, the air flow rate to be supplied to the engine should be optimally controlled in accordance with the driving conditions of the vehicle. For this purpose, a passage opening / closing device for controlling the flow rate is also applied.

As examples of such passage opening and closing devices, there are an electric wasted gate valve (EWGA) applied to a turbocharger system, a motor applied to a VCM, an EGR valve used for LP-EGR, and a back pressure regulating valve .

Therefore, by controlling the motor of the EWGA, the bypass flow rate can be controlled in the turbocharger system, and the air flow rate can be adjusted in the VCM by driving the motor, and the motor of the EGR valve and the motor of the back- The EGR gas flow rate can be regulated in the LP-EGR.

Korean Patent Publication No. 10-2009-0064200 (June 18, 2009)

However, EWGA, VCM, EGR valve, or backpressure regulating valve are all made of motor to open and close the passage, which is a cause of cost increase.

In view of the above, the present invention operates the pneumatic actuator even at a negative pressure (vacuum pressure) as well as a static pressure, and by connecting the operation of the pneumatic actuator to the opening and closing of the flow passage, the motor used in the engine performance enhancing device can be removed In particular, it is an object of the present invention to provide an engine performance enhancing device using a dual-pneumatically-coupled actuator that can be lowered in cost by eliminating a relatively high-cost motor.

In order to accomplish the above object, the present invention provides a double-pneumatic coupling actuator comprising a damper cover having an internal space into which a static pressure is introduced, a canister having an internal space coupled to the damper cover to receive a negative pressure, A diaphragm that divides the internal space into a static pressure forming chamber while separating the internal space of the canister into a negative pressure forming chamber, and a flow by contraction of the diaphragm formed by expansion or negative pressure of the diaphragm formed by the static pressure, And a spring for closing the flow passage by returning the rod to the initial position when the static pressure or the negative pressure is released.

The static pressure forming chamber includes a space formed by an outer diameter of the diaphragm and an inner space of the damper cover, and the negative pressure forming chamber includes a space formed by an inner diameter of the diaphragm and an inner space of the canister.

The diaphragm includes a diaphragm cover having a hollow truncated conical shape communicating with the static pressure forming chamber and inserted into the inner diameter of the diaphragm, and a hollow pipe-shaped hollow pipe for receiving the diaphragm cover, Further comprising a diaphragm plate; In the diaphragm cover, an insertion section of the rod except the exposure section exposed to the outside of the canister is fixed.

The insertion section of the rod is coupled to a sleeve provided on an inner circumferential surface of the diaphragm cover for fixing the position of the rod and a bellows provided in the inner space of the canister And a supporting portion.

The bellows is fixed to the bellows cover and the bellows plate at a joint portion between the bellows cover and the bellows plate. The bellows plate is disposed in the inner space of the bellows plate.

The spring is supported by a winding wire at one end in the inner space of the diaphragm and is supported by a winding wire at the other end in the inner space of the canister and is compressed by deformation of the diaphragm for moving the rod, .

The canister is provided with a bracket for bolting the other parts, and a supporter is provided between the bracket and the canister. The bracket, the canister, and the supporter are each formed with a through hole through which the rod passes.

According to another aspect of the present invention, there is provided an engine performance enhancing device including a damper cover having an internal space into which a static pressure is introduced, a canister having an internal space coupled to the damper cover to receive negative pressure, A diaphragm for dividing an internal space of the canister into a positive pressure forming chamber and a negative pressure forming chamber for dividing an internal space of the canister into a negative pressure generating chamber, and a diaphragm formed by expansion and contraction of the diaphragm, A dual-pneumatic coupling actuator having a rod for opening the flow passage and a spring for closing the flow passage by returning the rod to the initial position when the positive pressure or the negative pressure is released; A first valve provided in a positive pressure line connected to the positive pressure nipple of the double-pneumatically-coupled actuator, the flow passage being opened at a positive pressure formed in the positive pressure line; A second valve provided in a negative pressure line connecting the negative pressure nipple and the vacuum pump of the double pneumatic coupling actuator and having a flow passage opened by a negative pressure formed in the negative pressure line; The positive pressure line is connected to the compressor of the turbocharger, and the negative pressure line is connected to a vacuum pump.

And the static pressure line is connected to a variable flow control mechanism. And the constant-pressure line is connected to an EGR valve or a back pressure regulating valve of a low-pressure exhaust circulation device (LP-EGR). The static pressure is a pressure due to an exhaust gas flow rate generated at an engine speed of 1800 to 2000 rpm or more.

The vacuum pump is controlled by an ECU (Engine Control Unit) that connects the brake booster and the intake manifold with a vacuum line and performs CAN communication.

In the present invention, a pneumatic actuator that opens and closes a passage at a negative pressure (vacuum pressure) as well as a static pressure replaces a motor that has been applied to an EWGA, a VCM, an EGR valve, or a back pressure regulating valve, It is effective.

In addition, the present invention can be applied to EWGA, VCM, EGR valve or back pressure regulating valve by replacing the double-pneumatic pneumatic actuator with a motorless EWGA turbocharger system, motorless VCM, motorless EGR valve or motorless back pressure regulating valve There is an effect that the cost of the LP-EGR can be reduced.

Further, the present invention has an effect that the negative pressure (vacuum pressure) provided in the pneumatic actuator is associated with the vacuum pump which is the basic constituent device of the vehicle, so that the engine layout change is hardly required.

FIG. 2 is a diagram showing an example in which a dual-pneumatic coupling type actuator according to the present invention is applied to a turbocharger system. FIG. 3 is a schematic view of a double-pneumatic coupling type actuator according to a second embodiment of the present invention. (B), (b), (c) and (c) of FIG. 5, in which the pneumatic coupling type actuator is operated under a positive pressure, Is an example in which the dual pneumatic coupling type actuator according to the present invention is applied to an electronic wastegate valve, an intake flow enhancing mechanism (Variable Control Module), or a low pressure exhaust circulation system (LP-EGR).

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings, which illustrate exemplary embodiments of the present invention. The present invention is not limited to these embodiments.

Fig. 1 shows a configuration of a dual-pneumatic coupling type actuator according to the present embodiment.

As shown in the figure, the double-pneumatic coupling type actuator 1-1 is provided with a damper cover 1 for forming an internal space, a canister 7 for forming an internal space, A diaphragm 4 for dividing into two spaces, a rod 19 which is moved for opening and closing the passage, and a spring 11 for returning the rod 19 to its initial position.

The damper cover 1 is provided with a static pressure nipple for introducing a static pressure. The static pressure is a pressure formed when the engine speed is 1800 to 2000 rpm after the engine is started, and is a pressure provided to the compressor of the turbocharger.

The canister (7) is provided with a negative pressure nipple (14) for forming a negative pressure. The negative pressure is a vacuum pressure provided in the vacuum pump as vacuum pressure, and is a pressure associated with the brake booster.

The damper cover 1 and the canister 7 are coupled to each other to form an empty space.

The diaphragm 4 is provided in a hollow space formed by coupling the damper cover 1 and the canister 7, thereby separating the static pressure forming chamber from the negative pressure forming chamber.

 The pressure forming chamber is formed by a space formed by the outer diameter of the diaphragm 4 and the inner space of the damper cover 1. The inner diameter of the diaphragm 4 and the inner space of the canister 7 As shown in FIG.

A diaphragm cover 3 inserted into the through hole of the diaphragm 4 and a diaphragm plate 5 closely fitted to the inner diameter of the diaphragm 4 are coupled to the diaphragm 4. The diaphragm cover (3) has a hollow truncated cone shape, and the diaphragm plate (5) has a hollow pipe shape.

Therefore, the inner space of the diaphragm cover 3 communicates with the static pressure forming chamber. The diaphragm cover 3 is made of a material which can be expanded to a pressure to which a static pressure is applied. The diaphragm plate 5 is made of a material which can be contracted by a pressure applied by a negative pressure.

One end of the diaphragm cover 3 is placed on the periphery of the aperture of the diaphragm 4 and the remaining portion of the diaphragm cover 3 is located in the inner space of the diaphragm plate 5 through the aperture of the diaphragm 4 . To this end, the diaphragm cover 3 is coupled with the safety clip 2, and the safety clip 2 is inserted between one end of the diaphragm cover 3 and the perimeter of the diaphragm 4 .

The rod 19 is connected to the diaphragm cover 3 and has an insertion section positioned in the inner space formed by the damper cover 1 and the canister 7 and an insertion section extending from the canister 7 to the outside Respectively.

The insertion section is divided into a fixing section fixed for fixing the position and a supporting section supported for preventing the left and right flapping.

The sleeve 6 is engaged with the fixing portion and the sleeve 6 is engaged with the inner peripheral surface of the diaphragm cover 3 so that the rod 19 forms a fixing force. The bellows 13 is fixed to the supporting portion by using a joint between the bellows cover 12 and the bellows plate 15 and is fixed to the inner space of the bellows cover 12 and the bellows plate 15 .

The bellows cover 12 is formed with a through hole into which the end portion of the diaphragm cover 3 is inserted and a bushing 17 and an o-ring 18 are provided in the inner space of the bellows plate 15 do. The bushing (17) is passed through a rod (19).

A rod nut 19-1 is provided in the exposure section.

The spring 11 is made of a coil type in which the winding wire at one end is positioned inside the diaphragm plate 5 and the winding wire at the other end is wound around the bellows cover 12 and the bellows plate 15 Lt; / RTI >

Therefore, the spring 11 is compressively deformed by the rod 19 when the rod 19 is moved by the positive pressure or the negative pressure, and provides an elastic restoring force to move the rod 19 to the initial position when the positive pressure or the negative pressure is released give.

At this time, the movement of the rod 19 compressively deforming the spring 11 is the opening of the fluid passage, and the movement of the rod 19 by the elastic restoring force of the spring 11 means the closing of the fluid passage.

In addition, the double-pneumatic coupling type actuator 1-1 further includes a bracket 16 coupled to the canister 7, and the bracket 16 is bolted to the other components. A supporter 8 is interposed between the bracket 16 and the canister 7 and a through hole through which the bellows plate 15 passes is formed in the bracket 16 and the canister 7 and the supporter 8.

Further, the flange nut 9 and the screw 10 are further fastened to the bracket 16 and the bellows plate 15.

On the other hand, FIG. 2 shows an example in which a dual-pneumatic coupling type actuator according to the present embodiment is applied to a turbocharger system.

As shown in the figure, the turbocharger system is provided with a dual-pneumatic coupling type actuator 1-1 and a turbocharger 20. The compressor of the turbocharger 20 and the positive pressure nipple The second valve 40 is connected to the negative pressure line connecting the vacuum pump 50 and the negative pressure nipple 14 of the dual pneumatic coupling actuator 1-1. Respectively.

The dual-pneumatic coupling type actuator 1-1 has the same configuration as the dual-pneumatic coupling type actuator 1-1 described with reference to Fig. Further, the double-pneumatic coupling type actuator 1-1 is configured so that the flow passage is opened by the positive pressure supplied from the turbocharger 20 or the flow passage is opened by the negative pressure supplied from the vacuum pump 50, EWGA (Electronic Wastegate Valve) function is performed.

Therefore, the double-pneumatic coupling type actuator 1-1 can replace the motor in the EWGA, and the wastegate valve using the double-pneumatic coupling type actuator 1-1 can be defined as a motorless EWGA to which no motor is applied .

The pneumatic pressure provided by the double-pneumatic coupling type actuator 1-1 in the compressor of the turbocharger 20 is a pressure due to the exhaust gas flow rate generated at an engine speed of 1800 to 2000 rpm or more.

The first valve 30 is opened with a positive pressure caught by the compressor of the turbocharger 20 and the second valve 40 is opened with a negative pressure (vacuum pressure) formed in the vacuum pump 50.

The vacuum pump 50 is connected to an ECU (Engine Control Unit) 60 through CAN communication and is controlled for operation. The vacuum pump 50 connects the brake booster 70 and the intake manifold 80 with a vacuum line. The negative pressure of the vacuum pump 50 is supplied to the double pneumatic coupling type actuator 1-1 when the negative pressure (vacuum pressure) in the case of the shortage of the positive pressure due to the engine rotational speed of 1800 to 2000 rpm or less and the exhaust gas flow rate generated in the idle do.

3 shows a state in which the dual-pneumatic coupling actuator applied to the turbocharger system according to the present embodiment is operated under static pressure.

As shown, a static pressure Pa is supplied to the double-pneumatic coupling type actuator 1-1. At this time, the static pressure Pa is a pressure formed when the engine speed is 1800-2000 rpm after the engine is started. The positive pressure supplied to the positive pressure nipple of the double-pneumatic coupling type actuator 1-1 is transmitted to the positive pressure line of the compressor 1 of the turbocharger 20 and the positive pressure line of the double-pneumatic coupling type actuator 1-1, Valve 30 is provided.

Subsequently, the static pressure Pa is applied to the diaphragm cover 3 after filling the inner space of the diaphragm cover 3 coupled with the diaphragm 4 and thereafter forming the static pressure forming chamber formed by the outer diameter of the diaphragm 4 and the inner space of the damper cover 1 Fill. This static pressure Pa expands the diaphragm cover 3 and the diaphragm 4 so that the diaphragm 4 pushes the rod 19 out.

As a result, the rod 19 is moved downward as indicated by the arrow in FIG. 3 in the direction of the arrow indicated by the side of the rod 19, so that the flow passage is opened, thereby switching the dual-pneumatic coupling actuator 1-1 to the operating state.

At this time, the spring 11 is switched to the compressed state, and when the static pressure is released, the rod 19 is raised upward to provide an elastic restoring force to return to the initial position.

In this example, the hot exhaust gas to the compressor of the turbocharger 20 is diverted to the exhaust line of the exhaust system so that the catalyst's catalyst activation time (Catalyst Light-off Time) is promoted to the hot exhaust gas, For example.

Meanwhile, FIG. 4 shows a state in which the dual-pneumatic coupling actuator applied to the turbocharger system according to the present embodiment is operated under negative pressure.

As shown in the figure, a negative pressure Pb is supplied to the dual-pneumatic coupling type actuator 1-1. At this time, the negative pressure Pb is the pressure provided by the vacuum pump 50. [ The negative pressure supplied to the negative pressure nipple 14 of the dual-pneumatic coupling type actuator 1-1 is applied to the negative pressure line connecting the vacuum pump 50 and the negative pressure nipple 14 of the dual- And the second valve 40 provided in the second chamber 40 is opened.

Subsequently, the negative pressure Pb lowers the pressure in the negative pressure forming chamber formed by the inner space of the diaphragm plate 5 and the inner space of the canister 7. This action of the negative pressure Pb shrinks the diaphragm plate 5 and the diaphragm 4, so that the diaphragm 4 pushes the rod 19 out.

As a result, the rod 19 is moved downward in the direction of the arrow shown by the side of the rod 19 in Fig. 4 to open the flow passage, whereby the double-pneumatic coupling actuator 1-1 is switched to the operating state.

At this time, the spring 11 is switched to the compressed state, and when the negative pressure is released, the rod 19 is raised upward to provide an elastic restoring force so as to return to the initial position.

In this example, when the pressure due to the engine rotational speed of 1800 to 2000 rpm or less after starting the engine or the exhaust gas flow rate generated in the idle state is not reached to the positive pressure, the high temperature exhaust gas to the compressor of the turbocharger 20 The gas is bypassed to the exhaust line of the exhaust system so that the catalytic activation time of the catalyst is promoted to a high-temperature exhaust gas which does not lose exhaust heat to the compressor.

On the other hand, Fig. 5 shows various examples of the engine performance enhancing device to which the double-pneumatic coupling type actuator 1-1 according to the present embodiment is applied.

5A is an electric wastegate valve 100 in which an electric wastegate valve 100 is opened and closed by a double pneumatic coupling actuator 1-1 Therefore, even in such an electric wastegate valve 100, the same operation as that in the case where the motor is applied can be performed without using a motor.

5 (B) shows an intake flow enhancing mechanism (Variable Control Module) 200 in which a flow path opening / closing of an intake flow enhancing mechanism (Variable Control Module) 200 is implemented by a dual pneumatic coupling type actuator 1-1 For example. Therefore, the same action as that in the case where the motor is applied can be performed without using the motor in the intake flow enhancing mechanism (Variable Control Module) 200 as well.

5 (C) shows a low-pressure exhaust gas recirculation 300 equipped with a back-pressure regulating valve 300-1 and an EGR valve 300-2. The back-pressure regulating valve 300-1 is a low- And the flow passage opening / closing of the EGR valve 300-2 is realized by the double air-pressure coupling type actuator 1-1. Therefore, even in this back pressure regulating valve 300-1 and the EGR valve 300-2 The same operation as that in the case where the motor is applied can be performed without using the motor.

As described above, in the double-pneumatic coupling actuator 1-1 according to the present embodiment, the internal space of the damper cover 1 is divided into the static pressure forming chambers, while the internal space of the canister 7 is divided into the negative pressure forming chambers And the rod 19 that opens the flow passage by the movement of the diaphragm 4 formed by the static pressure or the contraction of the diaphragm 4 formed by the expansion or negative pressure of the diaphragm 4, The electronic wastegate valve 100 or the variable flow control module 100 can be opened or closed by the open / close action of the flow passage implemented by the double-pneumatic coupling actuator 1-1 even at negative pressure (vacuum pressure) It is possible to replace the motor of the back pressure regulating valve 300-1 and the EGR valve 300-2 of the low pressure exhaust gas recirculation unit 300 or the low pressure exhaust gas recirculation unit 300, Cost reduction can also be achieved.

1-1: Actuator 1: Damper cover
2: Safety clip 3: Diaphragm cover
4: diaphragm 5: diaphragm plate
6: Sleeve 7: Canister
8: Supporter 9: Flange nut
10: screw 11: spring
12: Bellows cover 13: Bellows
14: Negative pressure nipple 15: Bellows plate
16: Bracket 17: Bushing
18: O-ring 19: LOAD
19-1: Rod nut
20: Turbocharger 30: First valve
40: second valve 50: vacuum pump
60: ECU (Engine Control Unit)
70: Brake booster 80: Intake manifold
100: Electric Waste Gate Valve
100-1: EWGA motor
200: Variable Control Module
300: Low Pressure Exhaust Gas Recirculation
300-1: Backpressure regulating valve 300-2: EGR valve

Claims (12)

A damper cover having an internal space into which a static pressure is introduced, a canister having an internal space into which the negative pressure is introduced, the internal space of the damper cover being divided into a static pressure forming chamber, Forming chamber, a rod for opening the flow passage by movement of the diaphragm formed by the expansion or expansion of the diaphragm formed by the static pressure by contraction of the diaphragm, Spring returning to the position to close the flow passage
Wherein the actuator is a double pneumatic actuator.
[2] The vacuum cleaner of claim 1, wherein the static pressure forming chamber comprises a space formed by an outer diameter of the diaphragm and an inner space of the damper cover, wherein the negative pressure forming chamber defines a space defined by the inner diameter of the diaphragm and the inner space of the canister And a second pneumatic coupling type actuator.
The diaphragm of claim 1, wherein the diaphragm has a hollow truncated conical shape communicating with the static pressure forming chamber and inserted into an inner diameter of the diaphragm, and a hollow pipe- Further comprising a diaphragm plate coupled with an inner diameter of the diaphragm plate;
Wherein the diaphragm cover has an insertion section of the rod fixed except for an exposure section exposed to the outside of the canister.
4. The diaphragm cover according to claim 3, wherein the inserting section of the rod includes a fixing part coupled with a sleeve provided on an inner circumferential surface of the diaphragm cover for fixing the position of the rod, And a support portion coupled to the bellows.
[6] The bellows of claim 4, wherein the bellows is fixed to the bellows cover and the bellows plate at a joint portion between the bellows cover and the bellows plate, and a bushing having the rod through the bellows plate is provided in an inner space of the bellows plate Wherein the actuator is a double pneumatic actuator.
[2] The apparatus as set forth in claim 1, wherein the spring is supported by a winding wire at one end in an inner space of the diaphragm, a winding wire at the other end is supported in an inner space of the canister, Wherein the coil spring is a coil spring.
The canister of claim 1, wherein the canister is coupled to a bracket that is bolted to the other part, and a supporter is provided between the bracket and the canister, and a through hole is formed in the bracket, the canister, Wherein the actuator is a double pneumatic actuator.
A first valve provided in a static-pressure line connected to a static-pressure nipple of the dual-pneumatic actuator according to any one of claims 1 to 7, the flow passage being opened at a constant pressure formed in the static-pressure line;
A second valve provided in a negative pressure line connecting the negative pressure nipple and the vacuum pump of the double pneumatic coupling actuator and having a flow passage opened by a negative pressure formed in the negative pressure line;
Wherein the positive pressure line is connected to the compressor of the turbocharger and the negative pressure line is connected to a vacuum pump.
9. The engine performance enhancer according to claim 8, wherein the static pressure line is connected to an intake flow enhancing mechanism (Variable Control Module).
The engine performance enhancer according to claim 8, wherein the static pressure line is connected to an EGR valve or a back pressure regulating valve of a low-pressure exhaust circulation system (LP-EGR).
The engine performance enhancer according to claim 8, wherein the static pressure is a pressure based on an exhaust gas flow rate generated at an engine speed of 1800 to 2000 rpm or more.
The engine performance enhancer according to claim 8, wherein the vacuum pump is controlled by an ECU (Engine Control Unit) that connects the brake booster and the intake manifold with a vacuum line and performs CAN communication. .

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