JP6171870B2 - Diaphragm actuator and turbocharger - Google Patents

Description

  The present invention is used in a supercharger such as a supercharger for a vehicle having a gas flow rate variable passage for making the flow rate of exhaust gas supplied to a turbine impeller side variable, and an opening of the gas flow rate variable passage is formed The present invention relates to a diaphragm type actuator for operating a flow rate variable valve mechanism that opens and closes.

  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. It is formed. 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. And the structure of the waste gate valve which is one of the flow variable valve mechanisms is as follows.

  In other words, a stem (rotating shaft) is provided in a support hole formed through the outer wall of the turbine housing so as to be able to rotate in the forward and reverse directions, and a base end portion of the stem projects to the outside of the turbine housing. Further, the proximal end portion of the mounting member is integrally connected to the distal end portion of the stem, and a valve that can contact and be separated from the valve seat on the opening side of the bypass passage is provided at the distal end portion of the mounting member. Is provided. Further, the base end portion (one end portion) of the link member is integrally connected to the base end portion of the stem. Here, by swinging the link member in the forward / reverse direction around the axis of the stem, the valve swings in the forward / reverse direction (opening / closing direction) via the stem and the mounting member.

  A diaphragm actuator for operating the wastegate valve is provided on the outer wall of the compressor housing. The configuration of the diaphragm actuator is as follows.

  That is, the diaphragm type actuator has a cylindrical actuator body, and this actuator body has a pressure chamber in which positive pressure can be applied (supplied) from the outlet side of the compressor impeller as a pressure source on the inside (inside). And an atmospheric chamber communicating with the atmosphere. Further, a diaphragm is provided in the actuator main body so as to partition the pressure chamber and the atmospheric chamber, and the central portion of the diaphragm can be displaced in the actuator axial direction. A return spring that biases the pressure chamber is provided in the atmosphere chamber. Furthermore, the base end portion of the operating rod is integrally connected to the central portion of the diaphragm, and the distal end portion of the operating rod is rotatably connected to the distal end portion of the link member. Note that the outlet side of the compressor impeller is, for example, the air discharge port of the compressor housing or the compressor scroll flow path side.

  Therefore, when the supercharging pressure (pressure on the outlet side of the compressor impeller) reaches the set pressure during operation of the vehicle supercharger and positive pressure is applied to the pressure chamber, the central portion of the diaphragm is moved to the return spring. Displaces to one side in the actuator axial direction against the biasing force. Then, the operating rod moves to one side in the actuator axial direction and swings the link member in the forward direction. As a result, the valve can swing in the forward direction (opening direction) via the stem and the mounting member to open the opening of the bypass passage, and a portion of the exhaust gas can be bypassed by the turbine impeller. The flow rate of the exhaust gas supplied to the side can be reduced.

  In addition, after the opening of the bypass passage is opened, when the supercharging pressure becomes less than the set pressure and the application state of positive pressure from the outlet side of the compressor impeller is released, the center of the diaphragm is The part is displaced to the other side in the actuator axial direction. Then, the operating rod moves to the other side in the actuator axial direction and swings the link member in the reverse direction. As a result, the valve swings in the reverse direction (closed direction) via the stem and the mounting member, and the opening of the bypass passage can be closed, the flow of exhaust gas in the bypass passage is shut off, and the turbine impeller The flow rate of the exhaust gas supplied to the 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, during the operation of the vehicle supercharger, the positive pressure applied from the pressure source side may have a pulsating component. In such a case, the operating rod slightly vibrates, and the vibration is linked to a link member or the like. Is transmitted to the valve via. Therefore, there is a concern that the valve comes into contact with the valve seat or the mounting member on the opening side of the bypass passage, and chattering noise is generated from the waste gate valve, leading to a reduction in the quietness of the waste gate valve.

  The above-described problem also occurs in the type of waste gate valve to which negative pressure is applied instead of positive pressure from a pressure source, and in a flow rate variable valve mechanism other than the waste gate valve.

  Accordingly, an object of the present invention is to provide a diaphragm actuator having a novel configuration that can solve the above-described problems.

  A first feature of the present invention is that a gas flow rate variable passage for making a flow rate of exhaust gas supplied to a turbine impeller side variable is provided in a turbine housing or a connection body connected in communication with the turbine housing. A stem (rotating shaft) that is used in the formed turbocharger and is provided in a support hole formed through the outer wall of the turbine housing or the connecting body so as to be rotatable in the forward and reverse directions, and a base end portion of the stem. An integrally connected mounting member, a valve provided at a distal end portion of the mounting member and capable of contacting and separating from a valve seat (peripheral portion) on the opening side of the gas flow rate variable passage, and a base end portion (one end) A diaphragm member for operating a flow rate variable valve mechanism for opening and closing the opening of the gas flow rate variable passage, and a link member integrally connected to the base end portion of the stem. A cylindrical actuator body having a pressure chamber capable of applying (supplying) a positive pressure or a negative pressure from a pressure source and an atmosphere chamber communicating with the atmosphere on the inside (inside), A diaphragm that is provided so as to be divided into a pressure chamber and an atmospheric chamber and that has a central portion that can be displaced in the axial direction of the actuator, and that is provided in the actuator body and resists positive pressure or negative pressure applied to the pressure chamber. A return spring that urges the diaphragm in a direction, and a base end portion that is integrally connected to a central portion of the diaphragm and a tip end portion that is rotatably (swingable) connected to the tip end portion of the link member A rod, a stay provided on the actuator body and extending toward the distal end side of the operating rod, and the operating rod on one side of the actuator in the axial direction with respect to the stay A first damper for biasing, and summarized in that the actuating rod equipped with a, a second damper for urging the other side of the actuator axis with respect to the stay.

  Here, in the specification and claims of the present application, “a connection body connected in a state communicating with the turbine housing” means a pipe or manifold connected in a state communicating with the gas inlet or the gas outlet of the turbine housing. Including the casing and the like. Further, the “variable gas flow rate passage” includes a bypass passage for bypassing a part of the exhaust gas to the turbine impeller, and the “variable flow rate valve mechanism” opens and closes the opening of the bypass passage. Including the waste gate valve. Furthermore, “provided” means that it is provided directly, or indirectly provided via another member, and “connected” means directly connected. In addition to what has been done, it is meant to include being indirectly connected through another member. The “actuator axial direction” refers to the axial direction of the actuator body, and the “tank axial direction” refers to the axial direction of the tank body. Further, the “first damper” includes a first damper spring and a first damper rubber, and the “second damper” includes a second damper spring and a second damper rubber. Note that “provided integrally” includes being integrally formed.

  According to the first aspect of the present invention, when the pressure source is a positive pressure source during operation of the supercharger, when a positive pressure is applied from the pressure source to the pressure chamber, The central portion of the diaphragm is displaced to one side in the actuator axial direction against the urging force of the return spring. Alternatively, when the pressure source is a negative pressure source, when the application state of the negative pressure from the pressure source is released, the central portion of the diaphragm is moved in the actuator axial direction by the urging force of the return spring. Displace to the side. Then, the operating rod moves to one side of the actuator axial direction against the urging force of the second damper, and swings the link member in the forward direction. Thereby, the valve can swing in the forward direction via the stem and the mounting member, and the opening of the gas flow rate variable passage can be opened. Note that the flow rate of the exhaust gas supplied to the turbine impeller side may be decreased or increased by opening the opening of the gas flow rate variable passage.

  In addition, when the pressure source is a positive pressure source after opening the opening of the gas flow rate variable passage, when the application state of the positive pressure from the pressure source is released, the return spring is attached. The central portion of the diaphragm is displaced to the other side in the axial direction of the actuator by the force. Alternatively, when the pressure source is a negative pressure source, when a negative pressure is applied from the pressure source to the pressure chamber, the central portion of the diaphragm resists the urging force of the return spring to actuate the actuator shaft. Displace to the other side of the direction. Then, the operating rod moves to the other side in the actuator axial direction against the biasing force of the first damper, and swings the link member in the reverse direction. Thereby, the valve can swing in the reverse direction (closing direction) via the stem and the mounting member, and the opening of the gas flow rate variable passage can be closed. In addition, the flow rate of the exhaust gas supplied to the turbine impeller side may be increased or decreased by closing the opening of the gas flow rate variable passage.

  The operating rod is biased by the first damper to one side in the actuator axial direction and the second damper to the other side in the actuator axial direction, so that positive pressure or negative pressure applied from the pressure source is applied. Even when it has a pulsating component, the vibration of the operating rod due to the pulsating component can be sufficiently absorbed by the first damper and the second damper. Thereby, the vibration of the valve during operation of the supercharger can be suppressed.

  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 diaphragm actuator according to the first characteristic is provided. Is the gist.

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

  According to the present invention, even when the positive pressure or the negative pressure applied from the pressure source has a pulsating component, the vibration of the valve during operation of the supercharger can be suppressed. Chattering noise from the valve mechanism can be reduced, and the quietness of the variable flow rate valve mechanism can be improved.

FIG. 1 is a cross-sectional view of a diaphragm actuator according to an embodiment of the present invention. FIG. 2A is an enlarged view of the arrow IIA in FIG. 1, and is a diagram for explaining a case where a first disc spring and a second disc spring are used as the first damper spring and the second damper spring. FIG. 2B is a diagram illustrating a case where a first wave washer and a second wave washer are used as the first damper spring and the second damper spring. FIG. 3A is a view for explaining the case where the first coil spring and the second coil spring are used as the first damper spring and the second damper spring, and FIG. 3B is a case where the stay mounting piece is single. It is a figure explaining about. FIG. 4 is a front view of the vehicle supercharger according to the embodiment of the present invention. FIG. 5 is a cross-sectional view taken along line VV in FIG. FIG. 6 is a right side view of the vehicular 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.4 and FIG.7, the supercharger for vehicles (an example of a supercharger) 1 which concerns on embodiment of this invention uses the energy of the exhaust gas from an engine (illustration omitted) to an engine. The supplied 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 for compressing air using centrifugal force is rotatably provided in the compressor housing 11, and the compressor impeller 13 is concentrically integrated with the right end portion of the rotor shaft 9. It is connected.

  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. It is integrally connected to the part concentrically.

  As shown in FIGS. 4, 5, and 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. The port 27 can be connected to an engine exhaust manifold (not shown). 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 exhaust gas flow direction). 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).

  As shown in FIGS. 4 and 5, a bypass passage 33 is provided inside the turbine housing 23 to bypass a part of the exhaust gas introduced from the gas introduction port 27 to the gas discharge port 31 side by bypassing the turbine impeller 25. Is formed. Here, the bypass passage 33 is one of gas flow variable passages for making the flow rate of the exhaust gas supplied to the turbine impeller 25 side variable, and is a known bypass passage disclosed in JP2013-185552A. It has the same composition as.

  A waste gate valve 35 as one of variable flow valve mechanisms for opening and closing the opening of the bypass passage 33 is provided at an appropriate position of the turbine housing 23. The specific configuration of the waste gate valve 35 is as follows.

  In other words, a stem (rotating shaft) 39 is provided in a support hole 37 formed through the outer wall of the turbine housing 23 so as to be able to rotate in the forward and reverse directions via a bush 41. Part) protrudes to the outside of the turbine housing 23. A proximal end portion of an attachment member (attachment plate) 43 is integrally connected to the distal end portion (the other end portion) of the stem 39 by fillet welding. A surface width shape or a circular mounting hole (not shown) is formed through. The base end portion of the mounting member 43 may be integrally connected to the distal end portion of the stem 39 by TIG welding, laser beam welding, caulking, or the like instead of fillet welding.

  A valve 45 is fitted in the mounting hole of the mounting member 43, and the valve 45 is allowed to play (including tilting and fine movement) with respect to the mounting member 43. Further, the valve 45 is formed integrally with a valve body 47 that can be brought into contact with and separated from the valve seat (peripheral part) on the opening side of the bypass passage 33, and is fitted in a mounting hole of the mounting member 43. A combined valve shaft 49 is provided. Here, the backlash of the valve 45 with respect to the mounting member 43 is allowed, so that the followability (adhesion) of the valve body 47 with respect to the valve seat on the opening side of the bypass passage 33 is ensured. Furthermore, an annular stopper (washer) 51 is integrally provided at the tip of the valve shaft 49 by fillet welding. The stopper 51 may be integrally connected to the tip of the valve shaft 49 by TIG welding, laser beam welding, or caulking instead of fillet welding.

Here, instead of the valve shaft 49 being integrally formed at the center of the valve body 47 and the stopper 51 being integrally provided at the tip of the valve shaft 49 by fillet welding or the like, the valve shaft 49 49 may be integrally provided at the center of the valve body 47 by caulking, and the stopper 51 may be integrally formed at the tip of the valve shaft 49. The valve shaft 49 may be integrally provided at the central portion of the valve main body 47 by fillet welding, TIG welding, or laser beam welding instead of caulking.

  A base end portion (one end portion) of a link member (link plate) 53 is integrally connected to the base end portion of the stem 39 by fillet welding. Here, by swinging the link member 53 around the axis of the stem 39 in the forward / reverse direction, the valve 45 swings in the forward / reverse direction (opening / closing direction) via the stem 39 and the mounting member 43. ing. The base end portion of the link member 53 may be integrally connected to the base end portion of the stem 39 by TIG welding, laser beam welding, caulking, or the like instead of fillet welding.

  As shown in FIGS. 1, 4, and 6, a diaphragm actuator 55 for operating the waste gate valve 35 is provided on the outer wall of the compressor housing 11. The specific configuration of the diaphragm actuator 55 is as follows.

  That is, the diaphragm actuator 55 includes a cylindrical actuator body 57 provided on the outer wall of the compressor housing 11, and this actuator body 57 is connected to the inside (inside) from the air discharge port 21 as a pressure source. A pressure chamber 59 capable of applying (supplying) pressure and an atmosphere chamber 61 communicating with the atmosphere are provided along the actuator axial direction (the axial direction of the actuator body 57). A bracket 63 for attaching the diaphragm type actuator 55 (actuator body 57) to the outer wall of the compressor housing 11 is provided on the left side surface of the actuator body 57. Instead of being provided on the outer wall of the compressor housing 11, the actuator body 57 may be provided at an appropriate location on the vehicle supercharger 1 such as the outer wall of the bearing housing 3 or the turbine housing 23.

  As shown in FIGS. 1 and 4, a diaphragm 65 is provided in the actuator main body 57 so as to partition the pressure chamber 59 and the atmospheric chamber 61, and the central portion of the diaphragm 65 is displaced in the actuator axial direction. It is possible (movable). A first retainer plate 67 is provided on the surface of the diaphragm 65 on the pressure chamber 59 side, and a second retainer plate 69 is provided on the surface of the diaphragm 65 on the atmosphere chamber 61 side. In addition, a return spring (coil spring) 71 is provided in the atmosphere chamber 61 to urge the diaphragm 65 toward the pressure chamber 59 (in other words, in a direction against the positive pressure applied to the pressure chamber 59). Yes.

  An actuator rod 73 is provided in the actuator body 57 so as to be movable in the actuator axial direction via a bush 75, and the actuator rod 73 protrudes outward from the actuator body 57. The proximal end portion of the operating rod 73 is integrally connected to the central portion of the diaphragm 65, and the distal end portion of the operating rod 73 is rotatable to the distal end portion of the link member 53 via a connecting pin 77 (swinging). Movable).

  The bracket 63 is provided with a stay 79 that supports an intermediate portion (a portion between the base end portion and the tip end portion) of the operating rod 73 so as to be movable in the actuator axial direction (the axial direction of the actuator body 57, the left-right direction). In other words, a stay 79 is provided on the actuator main body 57 via the bracket 63. The stay 79 includes a pair of attachment pieces 81 and 83 that extend toward the distal end side of the operating rod 73 and face each other in the actuator axial direction. Furthermore, insertion holes 81h and 83h for allowing the mounting pieces 81 and 83 to be inserted in a state where the operation rod 73 is supported are formed through the mounting pieces 81 and 83, respectively. The stay 79 may be provided on the outer wall of the bearing housing 3 or the compressor housing 11 instead of being provided on the actuator body 57. Further, the insertion holes 81 h and 83 h of the attachment pieces 81 and 83 may not support the operating rod 73.

  A damper receiving member 85 is integrally provided between the pair of mounting pieces 81 and 83 in the operating rod 73. As a first damper spring between the damper receiving member 85 and one mounting piece 81 of the operating rod 73, the operating rod 73 is urged toward one side (left direction) in the actuator axial direction with respect to the stay 79. The first disc spring 87 is provided. Further, a second damper spring that urges the operating rod 73 toward the other side (right direction) of the actuator axial direction with respect to the stay 79 between the damper receiving member 85 and the other mounting piece 83 in the operating rod 73. A second disc spring 89 is provided.

  Instead of using the first disc spring 87 and the second disc spring 89 as the first damper spring and the second damper spring, a first wave washer 91 and a second wave washer 93 are used as shown in FIG. As shown in FIG. 3A, a first coil spring 95 and a second coil spring 97 may be used. In the latter case, both ends of the first coil spring 95 are connected to the bottom surface 81 au of the recess 81 a formed on the left side surface of the mounting piece 81 and the bottom surface 85 au of the recess 85 a formed on the right side surface of the damper receiving member 85. Each will be in pressure contact. Similarly, both end portions of the second coil spring 97 are in pressure contact with the bottom surface 83au of the recess 83a formed on the right side surface of the mounting piece 83 and the bottom surface 85bu of the recess 85b formed on the left side surface of the damper receiving member 85, respectively. Become.

  Instead of the stay 79 having the pair of attachment pieces 81 and 83, as shown in FIG. 3B, a single attachment piece 99 may be provided. In this case, an insertion hole 99h for inserting and supporting the operating rod 73 is formed through the mounting piece 99, and damper receiving members 101 and 103 are integrally provided on both sides of the mounting piece 99 in the operating rod 73, respectively. Will be. Further, a first damper spring (only the first disc spring 87 is shown) is provided between the mounting piece 99 and one damper receiving member 101 of the operating rod 73, and the mounting piece 99 and the other damper receiver of the operating rod 73 are provided. A second damper spring (only the second disc spring 89 is shown) is provided between the member 103 and the member 103.

  The spring constant of the second damper spring such as the second disc spring 89 is 0.8 to 1.2 times (specifically, 1.0 times) the spring constant of the first damper spring such as the first disc spring 87. Is set to The spring constants of the first damper spring such as the first disc spring 87 and the second damper spring such as the second disc spring 89 are smaller than the spring constant of the return spring 71 (specifically, the spring constant of the return spring 71). The spring constant is set to 0.1 to 0.5 times.

  The material of the first damper spring such as the first disc spring 87 and the second damper spring such as the second disc spring 89 has heat resistance such as Ni-base alloy, Ni-Co alloy, and stainless steel. Metal is used. Further, heat-resistant coating may be applied to the surface of the first damper spring such as the first disc spring 87 and the surface of the second damper spring such as the second disc spring 89, respectively.

  As shown in FIGS. 1 and 6, a piping path (path) 105 is provided between the air outlet 21 as a pressure source and the pressure chamber 59. In addition, a duty solenoid valve 107 capable of duty control is provided as one of the pressure control valves in the middle of the piping path 105, and the relief solenoid valve 107 and the air introduction port 15 are provided for relief. Are provided so as to communicate with each other.

  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. can do.

  When the supercharging pressure (pressure of the air discharge port 21) reaches a set pressure during operation of the vehicle supercharger 1, and positive pressure is applied to the pressure chamber 59 from the air discharge port 21 as a pressure source, The central portion of the diaphragm 65 is displaced to one side (left direction) in the actuator axial direction. Then, the actuating rod 73 moves to one side of the actuator axial direction against the biasing force of the second damper spring such as the second disc spring 89, and the link member 53 moves in the forward direction (clockwise direction in FIG. 4). It can be swung. As a result, the valve 45 can swing in the forward direction (opening direction) via the stem 39 and the mounting member 43 to open the opening of the bypass passage 33. 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, when the supercharging pressure becomes less than the set pressure after opening the opening of the bypass passage 33 and the application state of the positive pressure from the air discharge port 21 is released, the diaphragm 65 is urged by the urging force of the return spring 71. Is displaced to the other side (right direction) in the actuator axial direction. Then, the actuating rod 73 moves to the other side of the actuator axial direction against the biasing force of the first damper spring such as the first disc spring 87, and the link member 53 moves in the reverse direction (counterclockwise direction in FIG. 4). Swing to. As a result, the valve 45 can swing in the reverse direction (closing direction) via the stem 39 and the mounting member 43, and the opening of the bypass passage 33 can be closed. 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.

  Further, when the supercharging pressure is lower than the set pressure, the central portion of the diaphragm 65 is adjusted in the axial direction of the actuator by adjusting the positive pressure applied to the pressure chamber 59 by controlling the excitation and demagnetization of the duty solenoid valve 107. Displace appropriately. Then, the actuating rod 73 moves in the axial direction of the actuator against the biasing force of the first damper spring such as the first disc spring 87 or the second damper spring such as the second disc spring 89, and the link member 53 is moved forward and backward. It can be swung appropriately in the direction. Thereby, the opening degree of the valve 45 can be adjusted continuously or intermittently, and the flow rate of the exhaust gas supplied to the turbine impeller 25 side can be varied (adjusted) according to the operating state of the engine. .

  The actuating rod 73 is urged to one side in the actuator axial direction by the first damper spring such as the first disc spring 87 and to the other side in the actuator axial direction by the second damper spring such as the second disc spring 89. Even when the positive pressure applied from the air discharge port 21 side has a pulsation component, the first damper spring such as the first disc spring 87 and the second damper spring such as the second disc spring 89 cause the pulsation component. The vibration of the operating rod 73 can be sufficiently absorbed. Thereby, the vibration of the valve 45 during the operation of the vehicle supercharger 1 can be suppressed.

  In particular, the spring constant of the second damper spring such as the second disc spring 89 is set to 0.8 to 1.2 times the spring constant of the first damper spring such as the first disc spring 87, and the first damper spring and the second Since the spring constant of the 2 damper spring is set to a value smaller than the spring constant of the return spring 71, the movement of the operating rod 73 in the actuator axial direction can be stabilized. Thereby, the vibration of the valve 45 during the operation of the vehicle supercharger 1 can be sufficiently suppressed.

  When the first disc spring 87 or the first wave washer 91 is used as the first damper spring, and the second disc spring 89 or the second wave washer 93 is used as the second damper spring, the first damper spring and the second damper are used. The spring constants of the first damper spring and the second damper spring can be easily increased while suppressing an increase in the length of the spring in the actuator axial direction. Thereby, the vibration of the operating rod 73 due to the positive pressure pulsation component applied from the air discharge port 21 side can be absorbed sufficiently and effectively. Therefore, the vibration of the valve 45 during the operation of the vehicle supercharger 1 can be more sufficiently suppressed.

  Therefore, according to the embodiment of the present invention, even when the positive pressure applied from the air discharge port 21 side has a pulsating component, the vibration of the valve 45 during operation of the vehicle supercharger 1 is sufficiently suppressed. Therefore, chattering noise from the waste gate valve 35 can be reduced, and the quietness of the waste gate valve 35 can be improved.

  In addition, this invention is not restricted to description of the above-mentioned embodiment, It can implement in a various aspect as follows.

  That is, for example, instead of providing a waste gate valve 35 for opening and closing the bypass passage 33 at an appropriate position of the turbine housing 23, an exhaust manifold (not shown) connected in a state communicating with the gas inlet 27 of the turbine housing 23 is appropriately used. A waste gate valve (not shown) that opens and closes an opening of a bypass passage (not shown) formed in the exhaust manifold may be provided at the position. Further, instead of allowing the pressure chamber 59 to apply a positive pressure from the air discharge port 21, a negative pressure may be applied from another pressure source (not shown) on the engine side. 71 is provided in the pressure chamber 59. Further, the actuator main body 57 may have another pressure chamber (not shown) capable of applying a negative pressure from another pressure source (not shown) such as a negative pressure pump instead of the atmospheric chamber 61 inside. .

  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.

  DESCRIPTION OF SYMBOLS 1: Vehicle supercharger, 3: Bearing housing, 5: Radial bearing, 9: Rotor shaft, 11: Compressor housing, 13: Compressor impeller, 15: Air inlet, 19: Compressor scroll flow path, 21: Air exhaust Outlet (pressure source), 23: turbine housing, 25: turbine impeller, 27: gas inlet, 29: turbine scroll passage, 31: gas outlet, 33: bypass passage (gas flow variable passage), 35: waste gate Valve (variable flow rate valve mechanism), 37: support hole, 39: stem, 41: bush, 43: mounting member, 45: valve, 53: link member, 55: diaphragm type actuator, 57: actuator body, 59: pressure chamber 61: Atmospheric chamber, 63: Bracket, 65: Diaphragm, 71: Return spring 73: Actuating rod, 79: Stay, 81: Mounting piece, 81h: Insertion hole, 83: Mounting piece, 83h: Insertion hole, 85: Damper receiving member, 87: First disc spring (first damper spring), 89 : Second disc spring (second damper spring), 91: first wave washer (first damper spring), 93: second wave washer (second damper spring), 95: first coil spring (first damper spring) , 97: second coil spring (second damper spring), 99: mounting piece, 99h: insertion hole, 101: damper receiving member, 103: damper receiving member

Claims (5)

Used in a turbocharger in which a gas flow rate variable passage for varying the flow rate of exhaust gas supplied to the turbine impeller side is formed inside a turbine housing or a connection body connected in communication with the turbine housing. ,
A stem provided rotatably in a forward / reverse direction in a support hole formed through the outer wall of the turbine housing or the connection body, a mounting member whose base end is integrally connected to the stem, and A valve provided at the distal end and capable of contacting and separating from the valve seat on the opening side of the gas flow rate variable passage; and a link member integrally connected to the proximal end of the stem. In a diaphragm actuator for operating a flow variable valve mechanism that opens and closes the opening of the gas flow variable passage,
A cylindrical actuator body having a pressure chamber capable of applying a positive pressure or a negative pressure from a pressure source and an atmosphere chamber communicating with the atmosphere inside;
A diaphragm that is provided in the actuator body so as to be divided into the pressure chamber and the atmospheric chamber, and a center portion of which can be displaced in the actuator axial direction;
A return spring that is provided in the actuator body and biases the diaphragm in a direction against positive pressure or negative pressure applied to the pressure chamber;
An actuating rod having a base end integrally connected to a central portion of the diaphragm and a tip end rotatably connected to a tip end of the link member;
A stay provided on the actuator main body and extending toward the tip of the actuating rod;
A first damper that urges the operating rod toward one side of the actuator axial direction with respect to the stay;
A diaphragm type actuator, comprising: a second damper that urges the operating rod toward the other side in the actuator axial direction with respect to the stay. The stay includes a pair of mounting pieces that are opposed to the actuator axial direction and in which an insertion hole for allowing the operation rod to pass therethrough is formed,
A damper receiving member is integrally provided between the pair of mounting pieces in the operating rod,
The first damper is a first damper spring provided between the damper receiving member of the operating rod and one of the mounting pieces, and the second damper is connected to the damper receiving member of the operating rod. The diaphragm actuator according to claim 1, wherein the diaphragm actuator is a second damper spring provided between the other mounting piece. The stay includes an attachment piece in which an insertion hole for allowing the operation rod to pass therethrough is formed,
Damper receiving members are integrally provided on both sides of the mounting piece in the operating rod,
The first damper is a first damper spring provided between the mounting piece of the operating rod and one of the damper receiving members, and the second damper is connected to the mounting piece of the operating rod. 2. The diaphragm actuator according to claim 1, wherein the diaphragm actuator is a second damper spring provided between one of the damper receiving members.   The first damper spring is a first disc spring or a first wave washer, and the second damper spring is a second disc spring or a second wave washer. Diaphragm actuator as described. In the supercharger that supercharges the air supplied to the engine using the energy of the exhaust gas from the engine,
A turbocharger comprising the diaphragm actuator according to any one of claims 1 to 4.

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