JP2010196543A - Turbocharger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbocharger including both a turbine provided with nozzle vanes and a compressor provided with diffuser vanes, having excellent mountability, and suppressing an increase in the number of components. <P>SOLUTION: This turbocharger 1 includes a common drive device 40 driving each of a plurality of nozzle vanes 9 and a plurality of diffuser vanes 30. The drive device 40 is provided with a drive ring 42 rotatively driven by a single actuator 41, a first transmission mechanism 43 transmitting the rotational movement of the drive ring 42 to each of the plurality of nozzle vanes 9, and a second transmission mechanism 44 transmitting the rotational movement of the drive ring 42 to each of the plurality of diffuser vanes 30. Each of the transmission mechanism 43, 44 has first and second drive arms 52, 56 respectively coupled to the inner periphery and outer periphery of the drive ring 42. Positions with the drive arms 52, 56 coupled are overlapped in the rotating axis direction of the drive ring. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a turbocharger that rotates a turbine by utilizing exhaust gas or the like of an internal combustion engine and drives a compressor by the rotation of the turbine.

  A turbocharger equipped with a turbine in which a plurality of nozzle vanes are provided on the outer periphery of a turbine wheel, which is an inlet of the turbine, and the capacity of the turbine vane can be changed by changing the inclination angle of each nozzle vane to change the turbine inlet area is widely known. ing. There is also a turbocharger equipped with a compressor that has a plurality of diffuser vanes on the outer periphery of the compressor wheel that is the outlet of the compressor, and the supercharging characteristics can be changed to prevent surging by changing the inclination angle of each diffuser vane. It is widely known (for example, see Patent Document 1). In addition, Patent Documents 2 and 3 exist as prior art documents related to the present invention.

JP 2005-163691 A JP-A-8-254127 JP 2006-169985 A

  When configuring a turbocharger that combines a turbine equipped with nozzle vanes and a compressor equipped with diffuser vanes, the nozzle vanes and the diffuser vanes must be driven. In the case where the driving devices responsible for driving these vanes are provided separately, there are problems such as an increase in the size of the turbocharger and a drop in the mountability and an increase in the number of parts.

  Accordingly, an object of the present invention is to provide a turbocharger that has both a turbine equipped with a nozzle vane and a compressor equipped with a diffuser vane, and has good mountability and can suppress an increase in the number of parts.

  The turbocharger of the present invention includes a turbine having a plurality of nozzle vanes arranged in the circumferential direction and capable of changing an inclination angle, a compressor having a plurality of diffuser vanes arranged in the circumferential direction and capable of changing an inclination angle, And a common drive device that drives each of the plurality of diffuser vanes, and the drive device is disposed between the turbine and the compressor and is driven to rotate by a single actuator. A ring, a first transmission mechanism that transmits the rotational motion of the drive ring to each of the plurality of nozzle vanes, and a second transmission mechanism that transmits the rotational motion of the drive ring to each of the plurality of diffuser vanes. The first transmission mechanism has one end linked to the inner periphery of the drive ring and the other end forward. The second transmission mechanism includes a plurality of first drive arms coupled to a nozzle vane so as to be integrally rotatable. One end of the second transmission mechanism is linked to the outer peripheral side of the drive ring, and the other end rotates integrally with the diffuser vane. A plurality of second drive arms coupled to each other, wherein the first drive arm and the second drive arm have the coupling position with respect to the drive ring overlapped with respect to a rotation axis direction of the drive ring. It is linked to the ring (claim 1).

  According to this turbocharger, the nozzle vane and the diffuser vane are driven by a common driving device, and the driving device transmits the rotational motion of the driving ring driven by a single actuator to the first transmission. This is transmitted to the nozzle vane via the mechanism and to the diffuser vane via the second transmission mechanism. Therefore, as compared with the case where the nozzle vane driving device and the diffuser vane driving device are provided separately, an increase in size can be prevented, so that the mountability is improved. Moreover, since the drive ring driven by a single actuator is shared, an increase in the number of parts can be suppressed. Further, the first drive arm is linked to the inner peripheral side of the drive ring, the second drive arm is linked to the outer peripheral side of the drive ring, and the coupling position of the first drive arm with respect to the drive ring and the second drive Since the coupling position of the arms overlaps with respect to the axial direction of the drive ring, an increase in dimension in the axial direction is suppressed, and the mountability is further improved.

  In one aspect of the turbocharger of the present invention, the turbocharger further includes: a support plate that supports the diffuser vane; and a roller pin that rotatably supports the drive ring while being in contact with an inner periphery of the drive ring. The support plate may be cantilevered so that one end is coupled to the support plate and the other end is a free end. According to this aspect, since the roller pin that rotatably supports the drive ring is cantilevered by the support plate that is a member having a lower temperature than the turbine side, the roller pin is hardly affected by thermal expansion. As a result, it is possible to prevent the drive ring from malfunctioning due to the clearance between the inner peripheral surface of the drive ring due to the thermal expansion of the roller pin.

  As described above, according to the turbocharger of the present invention, the common drive device transmits the rotational motion of the drive ring, which is rotationally driven by a single actuator, to the nozzle vane via the first transmission mechanism. Since it is transmitted to the diffuser vane via the transmission mechanism, compared with the case where the nozzle vane drive device and the diffuser vane drive device are provided separately, it is possible to prevent an increase in size and suppress an increase in the number of parts. .

The front view which showed the principal part of the turbocharger which concerns on one form of this invention. The cross-sectional schematic diagram regarding the II-II line | wire of FIG.

  FIG. 1 is a front view showing a main part of a turbocharger according to one embodiment of the present invention, and FIG. 2 is a schematic sectional view taken along line II-II in FIG. As shown in these drawings, the turbocharger 1 includes a turbine 2 driven by exhaust from an internal combustion engine (not shown) and a compressor 3 driven by the turbine 2.

  The turbine 2 includes a turbine wheel 4 provided with a plurality of turbine blades 4 a in the circumferential direction, a turbine shaft 5 to which the turbine wheel 4 is fixed, a turbine wheel 4 and a spiral inlet passage 6 and a turbine shaft 5. And a turbine housing 8 that forms an outlet passage 7 that opens in the direction of the rotation axis Ax.

  The turbine housing 8 includes a plurality of nozzle vanes 9 arranged in the inlet passage 6 and arranged along the outer periphery of the turbine wheel 4, a nozzle shroud 10 covering each nozzle vane 9, and the nozzle shroud 10 sandwiching each nozzle vane 9. A support plate 11 provided on the opposite side and rotatably supporting each nozzle vane 9 is provided. A seal ring 12 is provided between the nozzle shroud 10 and the turbine housing 8 to ensure a sealing property between the nozzle shroud 10 and the turbine housing 8.

  By changing the inclination angle of each nozzle vane 9, the opening area of the inlet passage 6 with respect to the turbine wheel 4 can be continuously changed from the smallest minimum opening to the widest maximum opening. That is, each nozzle vane 9 forms a nozzle that narrows the flow path area in the flow direction, and the opening area of the nozzle can be changed by changing the inclination angle of each nozzle vane 9. Thereby, the turbine 2 functions as a variable capacity turbine.

  The compressor 3 is provided with a plurality of compressor blades 15 a in the circumferential direction, a compressor wheel (impeller) 15 fixed to the turbine shaft 5, and an inlet passage 16 that houses the compressor wheel 15 and opens in the direction of the rotation axis Ax. And a compressor housing 18 that forms a spiral outlet passage 17. The compressor housing 18 is connected via a rib-like connecting member 26 to a common housing 25 coupled to a bearing housing 22 on which bearings 20 and 21 that rotatably support the turbine shaft 5 are mounted. An oil seal 28 for preventing oil leakage is provided between the bearing housing 22 and the turbine shaft 5. The compressor housing 18 is provided with a plurality of diffuser vanes 30 arranged along the outer periphery of the compressor wheel 15 and a support plate 31 that rotatably supports the diffuser vanes 30.

  By changing the inclination angle of each diffuser vane 30, the passage area from the compressor wheel 15 to the outlet passage 17 can be changed from the narrowest minimum opening to the widest maximum opening. That is, each diffuser vane 30 forms a diffuser that expands the flow path area in the flow direction, and the opening area of the diffuser can be changed by changing the inclination angle of each diffuser vane 30. Thereby, the compressor 3 functions as a variable geometry compressor (VGC) capable of changing the supercharging characteristic so as to prevent surging.

  The support plate 11 that supports each nozzle vane 9 and the support plate 31 that supports each diffuser vane 30 are coupled to a coupling plate 35 disposed between the turbine 2 and the compressor 3, and the coupling plate 35 is a seal. It is attached to the outer periphery of the turbine shaft 5 via a ring 36. The compressor housing 18 is coupled to the turbine housing 8 via a support plate 31.

  The nozzle vanes 9 and the diffuser vanes 30 are driven by a common driving device 40. The drive device 40 includes a single actuator 41, a drive ring 42 that is rotationally driven by the actuator 41, a first transmission mechanism 43 that transmits the rotational motion of the drive ring 42 to each nozzle vane 9, and rotation of the drive ring 42. And a second transmission mechanism 44 that transmits the motion to each diffuser vane 30. The actuator 41 is configured as a vacuum actuator that generates a linear motion using negative pressure. The drive ring 42 is rotatably supported by the compressor housing 18 via a plurality of roller pins 46 (FIG. 1) in contact with the inner peripheral surface 42a. Each roller pin 46 is cantilevered by a support plate 31 mounted on the compressor housing 18, and a free end on the opposite side holds a minute gap with the support plate 11 on the turbine 2 side. Since the roller pin 46 is cantilevered by the support plate 31 that is a member having a temperature lower than that of the turbine 2, the roller pin 46 is hardly affected by thermal expansion. As a result, it is possible to prevent the malfunction of the drive ring 42 due to the absence of a gap between the roller pin 46 and the inner peripheral surface 42a of the drive ring 42 due to thermal expansion.

  The actuator 41 and the drive ring 42 are connected by a rod 45 having one end linked to the drive ring 42 and the other end coupled to the actuator 42. As a result, the linear motion indicated by the arrow F in FIG. 1 by the actuator 41 is converted into rotational motion, and the drive ring 42 is rotationally driven around the rotational axis Ax by the actuator 41.

  The first transmission mechanism 43 includes a rotary shaft 51 that rotates integrally with each nozzle vane 9, and a first drive arm 52 that extends from the rotary shaft 51 in one direction (upward in FIG. 2). The first drive arm 52 has an end 52 a that is rotatably fitted in a recess 53 formed in the inner peripheral surface 42 a of the drive ring 42. As a result, the end 52 a of the first drive arm 52 is linked to the inner peripheral side of the drive ring 42. Since the first drive arm 52 extends integrally from the rotating shaft 51 in one direction, the other end 52b opposite to the end 52a is coupled to each nozzle vane 9 so as to be integrally rotatable. On the other hand, the second transmission mechanism 44 includes a rotation shaft 55 that rotates integrally with each diffuser vane 30, and a second drive arm 56 that extends from the rotation shaft 55 in one direction (downward in FIG. 2). The end 56a of the second drive arm 56 is rotatably fitted in a recess 57 formed on the outer peripheral surface 42b of the drive ring 42. As a result, the end 56 a of the second drive arm 56 is linked to the outer peripheral side of the drive ring 42. Since the second drive arm 56 extends integrally from the rotation shaft 55 in one direction, the other end portion 56b opposite to the end portion 56a is coupled to each diffuser vane 30 so as to be integrally rotatable. .

  According to the turbocharger 1 described above, when the drive ring 42 is rotationally driven by the drive device 40 in the direction of the arrow F1 in FIG. 1, the respective tilt angles of the nozzle vanes 9 and the diffuser vanes 30 change simultaneously to the closed side. Can be made. On the contrary, when the drive ring 42 is rotationally driven in the direction of the arrow F2 in FIG. 1, the inclination angles of the nozzle vanes 9 and the diffuser vanes 30 can be simultaneously changed to the open side. Surging of the compressor 3 can be avoided by simultaneously changing the inclination angles of the nozzle vanes 9 and the diffuser vanes 30 toward the closed side. By changing the inclination angle of each nozzle vane 9 and each diffuser vane 30 to the open side simultaneously, the flow rate of the compressor 3 increases, so that the output does not decrease.

  Further, according to the turbocharger 1, each nozzle vane 9 and each diffuser vane 30 are driven by a common drive device 40, and the drive device 40 is driven to rotate by a single actuator 41. The rotational movement of the ring 42 is transmitted to each nozzle vane 9 via the first transmission mechanism 43 and to each diffuser vane 30 via the second transmission mechanism 44. Therefore, since the drive device for each nozzle vane 9 and the drive device for each diffuser vane 30 are provided separately, the size can be prevented from being increased, and the mountability is improved. Further, since the drive ring 42 driven by a single actuator 41 is shared, an increase in the number of parts can be suppressed. Further, the coupling positions of the first drive arm 52 and the second drive arm 56 with respect to the drive ring 42 overlap with respect to the direction of the rotation axis Ax. Therefore, since the dimensions in the direction of the rotation axis Ax can be shortened compared to the case where these are offset, the mountability is further improved.

  This invention is not limited to the said form, You may implement with a various form. The actuator 41 according to the above embodiment is configured as a vacuum actuator that generates a linear motion using negative pressure, but the actuator according to the present invention is an actuator using an electric motor or solenoid having the same function as the actuator 41. It is also possible to implement as.

DESCRIPTION OF SYMBOLS 1 Turbocharger 2 Turbine 3 Compressor 9 Nozzle vane 30 Diffuser vane 31 Support plate 40 Drive apparatus 41 Actuator 42 Drive ring 43 1st transmission mechanism 44 2nd transmission mechanism 46 Roller pin 52 1st drive arm 52a End part 52b End part 56 2nd drive Arm 56a End 56b End Ax Rotation axis

Claims (2)

A turbine having a plurality of nozzle vanes arranged in the circumferential direction and capable of changing an inclination angle, a compressor having a plurality of diffuser vanes arranged in the circumferential direction and capable of changing an inclination angle, the plurality of nozzle vanes, and the plurality of diffusers A common drive for driving each of the vanes,
The drive device is disposed between the turbine and the compressor and is driven to rotate by a single actuator, and a first transmission for transmitting the rotational motion of the drive ring to each of the plurality of nozzle vanes. A mechanism and a second transmission mechanism for transmitting the rotational movement of the drive ring to each of the plurality of diffuser vanes,
The first transmission mechanism has a plurality of first drive arms having one end portion linked to the inner peripheral side of the drive ring and the other end portion coupled to the nozzle vane so as to be integrally rotatable.
The second transmission mechanism includes a plurality of second drive arms having one end linked to the outer peripheral side of the drive ring and the other end coupled to the diffuser vane so as to be integrally rotatable.
The turbocharger, wherein the first drive arm and the second drive arm are link-coupled to the drive ring in a state where a coupling position with the drive ring overlaps with respect to a rotation axis direction of the drive ring. A support plate that supports the diffuser vane; and a roller pin that rotatably supports the drive ring while being in contact with the inner periphery of the drive ring,
The turbocharger according to claim 1, wherein the roller pin is cantilevered by the support plate so that one end is coupled to the support plate and the other end is a free end.

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