JP2014218945A - Flow rate variable valve mechanism and supercharger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure stability of operation of a waste gate valve 35, and to reduce chattering sounds from the waste gate valve 35.SOLUTION: A bush 39 is press-fitted to a support hole 37 formed so as to penetrate through the outer wall of a turbine housing 23. A stem 41 is rotatably supported to the bush 39. The base end part of a link member 43 is integrally connected to one end part of the stem 41, and a fitting member 53 is integrally formed to the other end part of the stem 41. A valve 61 is fitted to a fitting hole 59 of the fitting member 53. An annular spring member 71 is formed in a gap C between one end surface 39e of the bush 39 and one side surface 43f of the link member 43, and absorbs vibration of the link member 43.

Description

  The present invention relates to a variable flow rate valve mechanism that opens and closes an opening of a gas flow rate variable passage for making the flow rate of exhaust gas supplied to a turbine impeller side of a supercharger such as a vehicle supercharger variable.

  As a measure for preventing an excessive increase in the supercharging pressure by the vehicle supercharger, a bypass passage for bypassing a part of the exhaust gas to the turbine impeller is usually provided inside the turbine housing of the vehicle supercharger. A waste gate valve that opens and closes the opening of the bypass passage is provided at an appropriate position of the turbine housing. Here, the bypass passage is one of gas flow variable passages that make the flow rate of exhaust gas supplied to the turbine impeller side variable, and the waste gate valve is a flow rate that opens and closes the opening of the gas flow passage variable passage. One of the variable valve mechanisms. The general configuration of a waste gate valve, which is one of the variable flow valve mechanisms, is as follows.

  A bush is press-fitted into a support hole formed through the outer wall of the turbine housing. Further, a stem (rotating shaft) is supported by the bush so as to be rotatable in forward and reverse directions, and a base end portion (one end portion) of the stem protrudes to the outside of the turbine housing. Further, the base end portion (one end portion) of the link member is integrally connected to the base end portion of the stem, and this link member swings in the forward and reverse directions around the axis of the stem by driving the actuator. To do.

  An attachment member is integrally provided at the distal end portion (the other end portion) of the stem, and an attachment hole is formed through the attachment member. Further, a valve is fitted in the mounting hole of the mounting member, and this valve is allowed to play (including tilting and fine movement) with respect to the mounting member. Further, the valve includes a valve body that can be brought into contact with and separated from the valve seat on the opening side of the bypass passage, and a valve shaft that is integrally formed with the valve body and fitted into a mounting hole of the mounting member. Here, the backlash of the valve (valve body) with respect to the valve seat on the opening side of the bypass passage is ensured by allowing the backlash of the valve with respect to the mounting member. Furthermore, a stopper for making the valve non-detachable from the mounting member is integrally provided at the tip of the valve shaft.

  Therefore, when the supercharging pressure (pressure on the outlet side of the compressor impeller) reaches the set pressure during operation of the vehicle supercharger, the actuator is driven to swing the link member in the forward direction, and the stem is moved in the forward direction. , The valve is swung in the forward direction (opening direction) to open the opening of the bypass passage. Thereby, a part of exhaust gas can be bypassed by a turbine impeller, and the flow volume of the exhaust gas supplied to the turbine impeller side can be decreased.

  If the supercharging pressure becomes less than the set pressure after opening the bypass passage, the actuator is driven to swing the link member in the reverse direction and rotate the stem in the reverse direction to reverse the valve. The opening of the bypass passage is closed by swinging in the direction (closing direction). Thereby, the flow of the exhaust gas in the bypass passage can be blocked, and the flow rate of the exhaust gas supplied to the turbine impeller side can be increased.

  In addition, there exist some which are shown to patent document 1 and patent document 2 as a prior art relevant to this invention.

JP 2009-236088 A JP 2008-101589 A

  By the way, in order to prevent the swing failure (operation failure) of the link member and ensure the stability of the operation of the waste gate valve, it is necessary to provide a gap between the end surface of the bush and the side surface of the link member. On the other hand, if a gap is provided between the end surface of the bush and the side surface of the link member, when the valve vibrates due to the pulsation pressure of the exhaust gas during operation of the vehicle supercharger, the vibration is caused by the mounting member and the stem. Is transmitted to the link member, and not only the valve but also the link member vibrates. Along with these vibrations, the valve contacts the valve seat or mounting member on the opening side of the bypass passage, and chattering noise is generated from the waste gate valve. That is, there is a problem that it is difficult to improve the quietness of the waste gate valve while ensuring the stability of the operation of the waste gate valve.

  The above-mentioned problem occurs not only in the waste gate valve provided in the turbine housing but also in other flow variable valve mechanisms used in the supercharger.

  Therefore, an object of the present invention is to provide a variable flow rate valve mechanism or the like having a novel configuration that can solve the above-described problems.

  The first feature of the present invention is that the gas flow rate is variable for making the flow rate of exhaust gas supplied to the turbine impeller side variable in the turbine housing or in the connection body connected in communication with the turbine housing. In a variable flow valve mechanism used for a supercharger having a passage formed therein and opening and closing an opening of the gas flow variable passage, provided in a support hole formed through the outer wall of the turbine housing or the outer wall of the connection body. A bush, a stem rotatably supported in the forward and reverse directions by the bush, a base end portion (one end portion) protruding to the outside of the turbine housing or the connection body, and a base end portion (one end portion) of the stem A link member that is integrally connected to the base end and swings in the forward / reverse direction around the axis of the stem when driven by an actuator, and is provided integrally with the stem. A mounting member having a mounting hole formed therethrough, a valve main body fitted into the mounting hole of the mounting member, and capable of contacting and separating from a valve seat on the opening side of the gas flow rate variable passage; and the valve A valve provided with a valve shaft integrally provided in the center of the main body and fitted in the mounting hole of the mounting member; and provided integrally with a distal end portion of the valve shaft; An annular ring that is provided so as to surround the stem in a gap between the stopper plate for disengagement and the end surface of the bush and the side surface of the base end portion of the link member to absorb the vibration of the link member And a spring member.

  Here, in the specification and claims of the present application, the “gas flow variable passage” means a bypass passage for bypassing a part of the exhaust gas to the turbine impeller, and “the flow variable valve mechanism”. "Means a waste gate valve that opens and closes the opening of the bypass passage. In addition, the “connecting body connected in a state communicating with the turbine housing” includes a pipe, a manifold, a casing, and the like connected in a state communicating with the gas inlet or the gas outlet of the turbine housing. Furthermore, “provided integrally” means that it is integrally formed, and “annular spring member” means a disc spring, a stacked disc spring in which two disc springs are stacked in series, Including coil springs and wave washers.

  According to a first aspect of the present invention, during operation of the supercharger, the link member is swung in the forward direction by driving the actuator, and the stem is rotated in the forward direction, thereby rotating the valve. By swinging in the forward direction (opening direction), the opening of the gas flow rate variable passage is opened. Thereby, the flow rate of the exhaust gas supplied to the turbine impeller side may be decreased or increased.

  In addition, after opening the opening of the gas flow rate variable passage, the valve is swung in the reverse direction (closed) by swinging the link member in the reverse direction by driving the actuator and rotating the stem in the reverse direction. The opening of the gas flow rate variable passage is closed. As a result, the flow rate of the exhaust gas supplied to the turbine impeller side may be increased or decreased (normal operation of the variable flow rate valve mechanism).

  Since the annular spring member is provided in the gap between the end surface of the bush and the side surface of the link member so as to surround the stem, the swinging failure (operation failure) of the link member is prevented. When the valve vibrates due to exhaust gas pulsation pressure or the like during operation of the supercharger, vibration transmitted from the valve to the link member via the mounting member and the stem is caused by the spring member. Absorption can be reduced and, as a result, vibration of the valve itself can be reduced (a characteristic action of the variable flow rate valve mechanism).

  According to a second aspect of the present invention, in the supercharger that supercharges the air supplied to the engine using the energy of the exhaust gas from the engine, the flow rate variable valve mechanism according to the first feature is provided. This is the gist.

  According to the 2nd characteristic, there exists an effect | action similar to the effect | action by a 1st characteristic.

  According to the present invention, the vibration transmitted from the valve to the link member during the operation of the supercharger is absorbed by the spring member and reduced while preventing the swinging failure of the link member, and Since the vibration of the valve itself can be reduced, the chattering sound from the variable flow valve mechanism is reduced and the quietness of the variable flow valve mechanism is improved while ensuring the stability of the operation of the variable flow valve mechanism. be able to.

FIG. 1 is an enlarged view of an arrow I in FIG. 2A is an enlarged view of the arrow IIA in FIG. 1, and FIG. 2B is an enlarged cross-sectional view taken along the line IIB-IIB in FIG. FIG. 3A is a diagram illustrating a case where a flange portion is formed on a stacked disc spring as an annular spring member, and FIG. 3B is a diagram illustrating a case where a disc spring is used as the annular spring member. It is. FIG. 4A is a diagram illustrating a case where a wave washer is used as an annular spring member, and FIG. 4B is a diagram illustrating a case where a coil spring is used as the annular spring member. FIG. 5 is a sectional view taken along line VV in FIG. FIG. 6 is a partial front view of the vehicle supercharger according to the embodiment of the present invention. FIG. 7 is a front sectional view of the vehicle supercharger according to the embodiment of the present invention.

  An embodiment of the present invention will be described with reference to FIGS. As shown in the drawing, “L” is the left direction and “R” is the right direction.

  As shown in FIG. 7, a vehicular supercharger (an example of a supercharger) 1 according to an embodiment of the present invention is supplied to an engine using the energy of exhaust gas from an engine (not shown). The air is supercharged (compressed). And the specific structure of the supercharger 1 for vehicles is as follows.

  The vehicle supercharger 1 includes a bearing housing 3, and a pair of radial bearings 5 and a pair of thrust bearings 7 are provided in the bearing housing 3. In addition, a rotor shaft (turbine shaft) 9 extending in the left-right direction is rotatably provided in the plurality of bearings 5, 7. In other words, the rotor shaft 9 is provided in the bearing housing 3. , 7 are rotatably provided.

  A compressor housing 11 is provided on the right side of the bearing housing 3. A compressor impeller 13 that compresses air using centrifugal force is rotatably provided in the compressor housing 11, and the compressor impeller 13 is concentric with the right end (one end) of the rotor shaft 9. Are integrally connected to each other.

  An air introduction port (air introduction passage) 15 for introducing air is formed on the inlet side of the compressor impeller 13 in the compressor housing 11 (upstream side in the air flow direction). It can be connected to an air cleaner (not shown) for purifying air. An annular diffuser flow path 17 that pressurizes compressed air is formed on the outlet side of the compressor impeller 13 between the bearing housing 3 and the compressor housing 11 (downstream side in the air flow direction). Further, a spiral compressor scroll passage 19 is formed in the compressor housing 11 so as to surround the compressor impeller 13, and the compressor scroll passage 19 communicates with the diffuser passage 17. An air discharge port (air discharge passage) 21 for discharging compressed air is formed at an appropriate position on the outer wall of the compressor housing 11, and the air discharge port 21 is connected to the compressor scroll flow channel 19. It communicates and can be connected to an air supply manifold (not shown) of the engine.

  A turbine housing 23 is provided on the left side of the bearing housing 3. A turbine impeller 25 that generates a rotational force (rotational torque) using the pressure energy of the exhaust gas is rotatably provided in the turbine housing 23, and the turbine impeller 25 is provided at the left end of the rotor shaft 9. Concentrically and integrally connected to the portion (the other end).

  As shown in FIG. 5 to FIG. 7, a gas introduction port (gas introduction passage) 27 for introducing exhaust gas is formed at an appropriate position on the outer wall of the turbine housing 23. It can be connected to an engine exhaust manifold (not shown). Further, a spiral turbine scroll passage 29 is formed on the inlet side of the turbine impeller 25 inside the turbine housing 23 (upstream side in the flow direction of the exhaust gas). It communicates with the inlet 27. A gas discharge port (gas discharge passage) 31 for discharging exhaust gas is formed at the outlet side of the turbine impeller 25 in the turbine housing 23 (downstream side in the flow direction of the exhaust gas). The outlet 31 can be connected to a catalyst (not shown) for purifying exhaust gas via a connecting pipe (not shown).

  In the turbine housing 23, a part of the exhaust gas introduced from the gas introduction port 27 is led to the gas discharge port 31 side by bypassing the turbine impeller 25. In other words, the exhaust gas is supplied to the turbine impeller 25 side. A bypass passage (one of gas flow variable passages) 33 for changing the flow rate of the exhaust gas is formed. A waste gate valve (one of variable flow valve mechanisms) 35 that opens and closes the opening of the bypass passage 33 is provided at an appropriate position of the turbine housing 23. And the concrete structure of the waste gate valve 35 which is the principal part of embodiment of this invention is as follows.

  As shown in FIGS. 1, 2 (b), and 5, a bush 39 is press-fitted into a support hole 37 formed through the outer wall of the turbine housing 23. One end of the bush 39 is , Projecting outside the turbine housing 23. Further, a stem (rotating shaft) 41 is supported by the bush 39 so as to be rotatable in forward and reverse directions, and a proximal end portion (one end portion) of the stem 41 protrudes to the outside of the turbine housing 23.

  A base end portion (one end portion) of a link member (link plate) 43 is integrally connected to the base end portion of the stem 41 by fillet welding or the like, and the link member 43 can reciprocate in the left-right direction. By driving an actuator 47 having an actuating rod 45, it swings in the forward and reverse directions around the axis of the stem 41. Further, the distal end portion (the other end portion) of the link member 43 is rotatably connected to the distal end portion of the operating rod 45 via a connection pin 49, a retaining ring 51, and the like. Here, the actuator 47 is a diaphragm actuator as shown in, for example, Japanese Patent Laid-Open Nos. 10-103609 and 2008-25442, and the supercharging pressure (pressure on the outlet side of the compressor impeller 13) is set pressure. The link member 43 is swung in the forward direction (one direction) when the pressure reaches, and the link member 43 is swung in the reverse direction (the other direction) when the supercharging pressure becomes less than the set pressure. Instead of using a diaphragm actuator as the actuator 47, an electric actuator by electronic control or a hydraulic actuator by hydraulic drive may be used.

  An attachment member (attachment plate) 53 is integrally provided at the distal end portion (the other end portion) of the stem 41 by fillet welding or the like, and the attachment member 53 is located in the turbine housing 23. The mounting member 53 includes a mounting sleeve 55 provided integrally with the stem 41, and a mounting tongue 57 provided integrally with the mounting sleeve 55. The mounting tongue 57 has a two-sided width or circular shape. A mounting hole 59 having a shape is formed therethrough.

  A valve 61 is fitted in the mounting hole 59 of the mounting tongue 57 (mounting member 53). The valve 61 is allowed to play (including tilting and fine movement) with respect to the mounting member 53. The valve 61 is a valve main body 65 that can be brought into contact with and separated from the valve seat 63 on the opening side of the bypass passage 33, and a valve that is integrally formed in the center of the valve main body 65 and fitted in the mounting hole 59 of the mounting tongue 57. A shaft 67 is provided. Here, the backlash of the valve body 65 with respect to the valve seat 63 on the opening side of the bypass passage 33 is ensured by allowing the backlash of the valve 61 to the mounting member 53. Furthermore, a washer 69 as an annular stopper for preventing the valve 61 from being detached from the mounting member 53 is integrally provided at the tip of the valve shaft 67 by fillet welding or caulking.

  Instead of the valve shaft 67 being integrally formed at the center of the valve body 61 and the washer (stopper) 69 being integrally provided at the tip of the valve shaft 67 by fillet welding or caulking, the valve shaft 67 The clasp 69 may be integrally formed at the center of the main body 65 by caulking or the like, and the stopper 69 may be integrally formed at the tip of the valve shaft 67.

  As shown in FIGS. 1 and 2A, the vibration of the link member 43 is absorbed in the gap C between the one end surface 39e of the bush 39 and one side surface (side surface on the bush 39 side) 43f of the link member 43. An overlapping spring 71 is provided as an annular spring member. The overlapping spring 71 is formed by stacking two disc springs 73 and 75 in series. Further, the side surface 73f of one disc spring 73 is in pressure contact with one end surface 39e of the bush 39, and the side surface 75f of the other disc spring 75 is in pressure contact with one side surface 43f of the link member 43. The outer peripheral edge portion 73 and the outer peripheral edge portion of the other disc spring 75 are joined together. Further, the stacking disc spring 71 is configured to urge the link member 43 toward the proximal end of the stem 41 in a state where the other end surface of the bush 39 and one end surface of the mounting tongue 61 are in contact with each other. The outer diameter of 71 is set to be equal to or smaller than the outer diameter of the bush 39. It should be noted that the outer peripheral edge of one disc spring 73 and the outer peripheral edge of the other disc spring 75 may be in pressure contact instead of being integrally joined.

  The configuration of the annular spring member and the like can be changed as follows.

  That is, as shown in FIG. 3 (a), a hollow flange portion 77 that is elastically deformable in the radial direction of the stem 41 is integrally formed on the inner peripheral edge of one disc spring 73. The flange portion 77 of 73 is press-fitted between the inner peripheral surface 79 s of the annular concave step portion 79 formed on one end side of the inner peripheral surface of the bush 39 and the outer peripheral surface of the stem 41. Note that the flange portion 77 of the one disc spring 73 may have a curled shape instead of a hollow shape.

  As shown in FIG. 3B, a disc spring 81 may be used instead of the overlapping disc spring 71 as an annular spring member. In this case, the inner peripheral edge (one side) 81 a of the disc spring 81 is in pressure contact with the one end surface 39 e of the bush 39, and the outer peripheral edge (other side) 81 b of the disc spring 81 is connected to the link member 43. Is pressed against one side surface 43f. The outer diameter of the disc spring 81 is set to be equal to or smaller than the outer diameter of the bush 39.

  As shown in FIG. 4 (a), a wave washer 83 may be used instead of the overlapping disc spring 71 or the like as the annular spring member. In this case, one side 83a of the wave washer 83 is in pressure contact with one end surface 39e of the bush 39, and the other side 83b of the wave washer 83 is in pressure contact with one side 43f of the link member 43. The outer diameter of the wave washer 83 is set to be equal to or smaller than the outer diameter of the bush 39.

  As shown in FIG. 4B, a coil spring 85 may be used in place of the stacked disc spring 71 or the like as the annular spring member. In this case, one end portion 85 a of the coil spring 85 is in pressure contact with a bottom surface 87 d of an annular recess 87 formed on one end surface 39 e of the bush 39, and the other end portion 85 b of the coil spring 85 is one side surface of the link member 43. It is in pressure contact with the bottom surface 89d of the annular recess 89 formed in 43f.

  The material of the annular spring member such as the stacked disc spring 71 is selected in consideration of heat resistance, spring constant, and the like, and examples of the material of the annular spring member include heat resistance such as Ni-based alloy and Ni-Co alloy. Metal or heat-resistant rubber or metal is used. In addition, a heat resistant coating may be applied to the surface of an annular spring member such as the overlapping plate spring 71.

  Then, the effect | action and effect of embodiment of this invention are demonstrated.

  Exhaust gas introduced from the gas inlet 27 flows from the inlet side to the outlet side of the turbine impeller 25 via the turbine scroll flow path 29, so that a rotational force (rotational torque) is generated using the pressure energy of the exhaust gas. Thus, the rotor shaft 9 and the compressor impeller 13 can be rotated integrally with the turbine impeller 25. Thereby, the air introduced from the air introduction port 15 can be compressed and discharged from the air discharge port 21 via the diffuser flow path 17 and the compressor scroll flow path 19, and the air supplied to the engine is supercharged. (Normal operation of the vehicle supercharger 1).

  When the supercharging pressure (pressure on the outlet side of the compressor impeller 13) reaches a set pressure during operation of the vehicle supercharger 1, the link member 43 is swung in the forward direction by driving the actuator 47, and the stem 41 Is rotated in the forward direction, the valve 61 is swung in the forward direction (opening direction), and the opening of the bypass passage 33 is opened. Thereby, a part of the exhaust gas introduced from the gas inlet 27 can be bypassed by the turbine impeller 25, and the flow rate of the exhaust gas supplied to the turbine impeller 25 side can be reduced.

  Further, after the opening of the bypass passage 33 is opened, when the supercharging pressure becomes less than the set pressure, the link member 43 is swung in the reverse direction by driving the actuator 47 and the stem 41 is rotated in the reverse direction. Then, the valve 61 is swung in the reverse direction (closing direction) to close the opening of the bypass passage 33. Thereby, the flow of the exhaust gas in the bypass passage 33 can be cut off, and the flow rate of the exhaust gas supplied to the turbine impeller 25 side can be increased (normal operation of the waste gate valve 35).

  Since an annular spring member such as a stacked disc spring 71 is provided in the gap C between the one end surface 39e of the bush 39 and the one side surface 43f of the link member 43 so as to surround the stem 41, the link member 43 swings. When the valve 61 vibrates due to exhaust gas pulsation pressure or the like during operation of the vehicle supercharger 1 while preventing malfunction (malfunction), the link member is connected from the valve 61 via the mounting member 53 and the stem 41. The vibration transmitted to 43 is absorbed and reduced by the annular spring member, and as a result, the vibration of the valve 61 itself can also be reduced.

  In particular, when the flange portion 77 of one disc spring 73 is press-fitted between the inner peripheral surface 79 s of the concave step portion 79 as the inner peripheral surface of the bush 39 and the outer peripheral surface of the stem 41, The vibration of the stem 41 can be absorbed by the flange portion 77 of the spring 73, and the vibration of the link member 43 and the valve 61 can be further reduced. Further, when the stacking disc spring 71 is used as the annular spring member, the spring constant of the annular spring member can be easily increased while suppressing an increase in the outer diameter of the annular spring member. The vibration transmitted to the member 43 can be effectively absorbed by the annular spring member (characteristic action of the waste gate valve 35).

  Therefore, according to the embodiment of the present invention, the vibration transmitted from the valve 61 to the link member 43 during the operation of the vehicle supercharger 1 is prevented while preventing the swinging failure of the link member 43. Since the vibration of the valve 61 itself can be reduced, the chattering sound from the waste gate valve 35 can be reduced while ensuring the stability of the operation of the waste gate valve 35. Silence can be improved.

  Further, since a clearance C between the one end surface 39e of the bush 39 and the one side surface 43f of the link member 43, in other words, an annular spring member such as a stacked disc spring 71 is provided outside the turbine housing 25. The temperature around the annular spring member such as the stacked disc spring 71 is relatively low, and deterioration of the annular spring member such as the stacked disc spring 71 can be suppressed.

  The present invention is not limited to the description of the above-described embodiment. For example, instead of providing a waste gate valve 35 that opens and closes the bypass passage 33 at an appropriate position of the turbine housing 23, gas introduction into the turbine housing 23 is performed. A waste gate valve (not shown) that opens and closes an opening of a bypass passage (not shown) formed in the exhaust manifold is provided at an appropriate position of an exhaust manifold (not shown) connected in communication with the port 27. The present invention can be implemented in various modes by making appropriate changes.

  The scope of rights encompassed by the present invention is not limited to the above-described embodiment. That is, the flow rate variable valve mechanism of the present application is not limited to the above-described waste gate valve 35. For example, as shown in Japanese Utility Model Laid-Open Nos. 61-33923 and 2001-263078, the turbine housing A switching valve mechanism (not shown) that switches the supply state and the supply stop state of the exhaust gas to any one of the turbine scroll passages (not shown) formed in (not shown). ) Is also applicable. The variable flow rate valve mechanism of the present application is, for example, as shown in JP 2010-209688 A, JP 2011-106358 A, etc. The present invention can also be applied to a switching valve mechanism (not shown) that switches between an exhaust gas supply state and a supply stop state with respect to the housing.

  C: Clearance, 1: Supercharger for vehicle (supercharger), 3: Bearing housing, 9: Rotor shaft, 11: Compressor housing, 13: Compressor impeller, 23: Turbine housing, 25: Turbine impeller, 33: Bypass Passage (gas flow variable passage), 35: waste gate valve (flow variable valve mechanism), 37: support hole, 39: bush, 39e: one end face of bush, 41: stem, 43: link member, 43f: link member One side, 47: Actuator, 53: Mounting member, 55: Mounting sleeve, 57: Mounting tongue, 59: Mounting hole, 61: Valve, 63: Valve seat, 65: Valve body, 67: Valve shaft, 69: Washer ( Clasp), 71: stacked disc spring (annular spring member), 73: disc spring, 73f: side surface of disc spring, 75: disc spring, 75f Side face of disc spring, 77: flange portion of disc spring, 79: concave step portion of bush, 79s: inner peripheral surface (inner circumferential surface of bush) of bush, 81: disc spring (annular spring member) 81a: inner peripheral edge of the disc spring, 81b: outer peripheral edge of the disc spring, 83: wave washer (annular spring member), 83a: one side of the wave washer, 83b: other side of the wave washer, 85: Coil spring (annular spring member), 85a: one end portion of the coil spring, 85b: the other end portion of the coil spring, 87: a recess portion of the bush, 87d: a bottom surface of the recess portion of the bush (one end surface of the bush), 89: a recess portion of the link member, 89d: bottom surface of recess of link member (one side surface of link member)

Claims (5)

A turbocharger in which a gas flow rate variable passage for changing the flow rate of exhaust gas supplied to a turbine impeller side is formed in a turbine housing or in a connection body connected in communication with the turbine housing. Used,
In the variable flow valve mechanism for opening and closing the opening of the gas flow variable passage,
A bush provided in a support hole formed through the outer wall of the turbine housing or the outer wall of the connection body;
A stem that is supported by the bush so as to be rotatable in the forward and reverse directions, and a base end portion of which protrudes to the outside of the turbine housing or the connection body;
A link member that is integrally connected to a base end portion of the stem and swings in a forward / reverse direction around an axis of the stem by driving an actuator;
A mounting member provided integrally with the stem and having a mounting hole formed therethrough;
A valve body that is fitted in the mounting hole of the mounting member and is capable of coming into contact with and separated from a valve seat on the opening side of the gas flow rate variable passage; A valve having a valve shaft fitted in the mounting hole of the mounting member;
A stopper provided integrally with the tip of the valve shaft, for making the valve non-detachable from the mounting member;
An annular spring member that is provided so as to surround the stem in a gap between an end surface of the bush and a side surface of a base end portion of the link member, and absorbs vibration of the link member. Variable flow valve mechanism.   The said spring member is comprised so that the said link member may be urged | biased in the base end direction of the said stem in the state which the end surface of the said bush and the end surface of the said attachment member contact | abutted. The variable flow valve mechanism described.   3. The variable flow rate valve mechanism according to claim 1, wherein the spring member is a stacked disc spring in which two disc springs are stacked in series.   A flange portion that is elastically deformable in the radial direction of the stem is formed on the inner peripheral edge of the one disc spring, and the flange portion is press-fitted between the inner peripheral surface of the bush and the outer peripheral surface of the stem. The flow rate variable valve mechanism according to claim 3. In the supercharger that supercharges the air supplied to the engine using the energy of the exhaust gas from the engine,
A supercharger comprising the variable flow valve mechanism according to any one of claims 1 to 4.

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