JP6263973B2 - Valve actuator and supercharger - Google Patents

Description

  The present invention operates a flow rate variable valve mechanism that opens and closes an opening of a gas flow rate variable passage for varying the flow rate of exhaust gas supplied to a turbine impeller side in a turbocharger such as a vehicular turbocharger. The present invention relates to a valve operating device.

  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 is provided on the outer wall of the compressor housing as a valve operating device for operating the waste gate valve. The diaphragm actuator swings the link member in the forward and reverse directions. 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 actuator atmosphere chamber communicating with the atmosphere. Further, a diaphragm is provided in the actuator main body so as to partition the pressure chamber and the actuator atmospheric chamber, and the central portion of the diaphragm can be displaced in the actuator axial direction (the axial direction of the actuator main body). An actuator urging member that urges the actuator air chamber toward the pressure chamber side is provided. 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. The outlet side of the compressor impeller is, for example, an air discharge port of the compressor housing or a compressor scroll flow path.

  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 from the outlet side of the compressor impeller, the diaphragm The central portion is displaced to one side in the actuator axial direction against the biasing force of the actuator biasing member. Then, the operating rod moves to one side in the actuator axial direction, and the link member can be swung 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.

  Further, after the opening of the bypass passage is opened, when the supercharging pressure becomes lower than the set pressure and the application state of the positive pressure from the outlet side of the compressor impeller is released, the diaphragm is driven by the biasing force of the actuator biasing member. The central part of the actuator 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 the link member can be swung 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.

  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.

A first aspect of the present invention, the interior of the connecting body connected in a state of communication with the turbine housing or the turbine housing, the gas flow rate variable passage it the flow rate of the exhaust gas supplied to the turbine impeller side variable is formed Used for the turbocharger
Stem (rotary shaft) provided in a support hole formed in the outer wall of the turbine housing or the connection body so as to be rotatable in forward and reverse directions, a mounting member whose base end is connected to the stem, and a distal end of the mounting member And a link member having a base end portion (one end portion) connected to the base end portion of the stem, and a valve that can contact and separate from a valve seat (peripheral portion) on the opening side of the gas flow rate variable passage. comprising, in the valve actuating device Ru operates the variable flow valve mechanism for opening and closing the opening of the gas flow rate variable passage, positive or from the pressure source to the inside (interior) of the negative pressure can be applied (can be supplied) pressure chamber A cylindrical actuator body having an actuator atmosphere chamber in communication with the atmosphere; the actuator body is provided so as to partition the pressure chamber and the actuator atmosphere chamber; Displaceable diaphragm axially, positive or applied to the pressure chamber actuator biasing member for urging the diaphragm in a direction opposing the negative pressure, and a proximal end coupled to a central portion of the diaphragm and A distal end portion (the other end portion) includes an operating rod that is rotatably (swingable) connected to the tip end portion of the link member, and a diaphragm actuator that swings the link member in the forward and reverse directions; pressure source and the middle (the middle portion) communicating with the receiving chamber and a cylindrical tank body having a tank air chamber communicating with the atmosphere of the pipe path (route) contact the pressure chamber, the said tank body receiving chamber and the provided so as to divide the tank atmosphere chamber and slidable partition member to the tank axis (piston), and the positive pressure or applied to the receiving chamber is the partition section in a direction against the negative pressure Comprising a tank biasing member for biasing the positive pressure or from the pressure source to the surge tank for receiving the negative pressure (receiving tank), comprising a, the outer wall of the compressor housing said diaphragm actuator in the turbocharger provided, Ru der that the surge tank is positioned opposite a region of the diaphragm actuator around the axis of the turbine impeller in an outer wall of the compressor housing.

  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.

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 in the actuator axial direction, and the link member can be swung in the forward direction. Thereby, the valve can swing in the forward direction (opening 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.

Further, when the pressure source is a positive pressure source, when the application state of the positive pressure from the pressure source is released after opening the opening of the gas flow rate variable passage, 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 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. Note that closing the opening of the gas flow rate variable passage may increase or decrease the flow rate of the exhaust gas supplied to the turbine impeller side (normal operation according to the first aspect of the present invention). .

During operation of the supercharger, positive pressure or negative pressure is applied to the pressure chamber from the pressure source, and positive pressure or negative pressure is received from the pressure source to the receiving chamber. partition member slides to one side or the other side of the tank axial direction against the biasing force of the tank biasing member. Thereby, even when the positive pressure or the negative pressure applied from the pressure source side has a pulsating component, the pulsating component can be sufficiently absorbed by the surge tank (mainly the tank urging member). . Therefore, it is possible to sufficiently suppress the vibration of the operating rod during the operation of the supercharger and the vibration of the valve due to the vibration (the specific action according to the first aspect of the present invention).

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 valve operating device according to the first aspect is provided. der Ru.

According to the 2nd mode of the present invention, the same operation as the operation by the 1st mode of the present invention is produced.

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

FIG. 1 is a right side view of a vehicle supercharger according to an embodiment of the present invention. FIG. 2 is a diagram illustrating a diaphragm actuator, a surge tank, and the like. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a front view of the vehicle supercharger according to the embodiment of the present invention. FIG. 5 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 FIGS. 4 and 5, a vehicular supercharger (an example of a supercharger) 1 according to an embodiment of the present invention uses the energy of exhaust gas from an engine (not shown) to the 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. 3 to 5, 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). 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. 3 and 4, a bypass passage for introducing 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 provided in the turbine housing 23. 33 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 central portion of the valve body 47 and the clasp 51 being integrally provided at the tip of the valve shaft 49 by fillet welding or the like, the valve shaft 49 is attached to the valve body 47. The clasp 51 may be integrally formed at the center portion of the valve shaft 49 and may be integrally formed by caulking. 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, 2, and 4, a valve operating device 55 for operating the wastegate valve 35 is provided on the outer wall of the compressor housing 11. The specific configuration of the valve operating device 55 is as follows.

  That is, a diaphragm actuator 57 for swinging the link member 53 in the forward / reverse direction is provided on the outer wall of the compressor housing 11 via the bracket 59, and the diaphragm actuator 57 is connected to the valve actuator 55. One of the main components. The diaphragm actuator 57 includes a cylindrical actuator body 61 provided on the outer wall of the compressor housing 11 via a bracket 59. Further, the actuator body 61 has a pressure chamber 63 capable of applying (supplying) positive pressure from the air discharge port 21 as a pressure source and an actuator atmosphere chamber 65 communicating with the atmosphere on the inside (inside) of the actuator in the axial direction. It has along (the axial direction of the actuator main body 61). Instead of being provided on the outer wall of the compressor housing 11, the actuator body 61 may be provided at an appropriate location of the vehicle supercharger 1 such as the outer wall of the bearing housing 3 or the turbine housing 23.

  As shown in FIGS. 2 and 4, a diaphragm 67 is provided in the actuator main body 61 so as to partition the pressure chamber 63 and the actuator atmospheric chamber 65, and the central portion of the diaphragm 67 extends in the actuator axial direction. Displaceable (movable). A first retainer plate 69 is provided on the surface of the diaphragm 67 on the pressure chamber 63 side, and a second retainer plate 71 is provided on the surface of the diaphragm 67 on the actuator atmosphere chamber 65 side. A coil spring 73 is provided in the actuator atmosphere chamber 65 as an actuator urging member that urges the diaphragm 67 toward the pressure chamber 63 (in other words, a direction against the positive pressure applied to the pressure chamber 63). It has been.

  An actuator rod 75 is provided on the actuator body 61 so as to be movable in the actuator axial direction via a bush 77. The actuator rod 75 protrudes outward from the actuator body 61. The proximal end portion of the operating rod 75 is integrally connected to the central portion of the diaphragm 67, and the distal end portion of the operating rod 75 is rotatable via a connecting pin 79 to the distal end portion of the link member 53 (swinging). Movable).

  As shown in FIGS. 1 and 2, a piping path (path) 81 is provided between the air outlet 21 as a pressure source and the pressure chamber 63 so as to communicate with each other. Further, a duty solenoid valve 83 capable of duty control is provided as one of the pressure control valves in the middle of the piping path 81, and between the duty solenoid valve 83 and the air inlet 15 is used for relief. Are provided so as to communicate with each other.

  A surge tank (accepting tank) 87 that receives positive pressure from the air discharge port 21 is provided on the outer wall of the compressor housing 11. The surge tank 87 is one of the main components of the valve operating device 55 and is located in a region on the opposite side of the diaphragm actuator 57 around the axis of the compressor impeller 13.

  The surge tank 87 includes a cylindrical tank body 91 provided on the outer wall of the compressor housing 11 via a bracket 89. Further, the tank body 91 has an inner side (inside) a receiving chamber 93 communicating with the middle (intermediate portion) of the piping path 81 for connecting the air discharge port 21 and the pressure chamber 63, and a tank atmosphere chamber communicating with the atmosphere. 95 along the tank axial direction (the axial direction of the tank body 91, the left-right direction). Further, in order to absorb the pulsation of exhaust gas from the engine side, the cross-sectional area of the receiving chamber 93 is preferably set larger than the opening area of the opening portion of the bypass passage 33, specifically, the bypass passage. It is preferable that the opening area of the 33 openings is set to be four times or more. The long side portion 91a of the tank body 91 has a first port 97 communicating with the portion on the duty solenoid valve 83 side in the piping path 81 and a second port 99 communicating with the portion on the actuator body 61 side in the piping path 81. Are formed respectively. Instead of the tank body 91 being provided on the outer wall of the compressor housing 11, the tank body 91 may be provided at an appropriate location of the vehicle supercharger 1, such as the outer wall of the bearing housing 3 or the turbine housing 23, an appropriate location on the engine side, etc. It may be formed integrally with a part of the housing 11.

  A plate-like partition member (piston) 101 is provided in the tank body 91 so as to partition the receiving chamber 93 and the tank atmosphere chamber 95, and this partition member 101 is arranged in the tank axial direction via an O-ring 103. Airtightly slidable (movable). In addition, an annular stopper 105 that can come into contact with one side surface (right side surface) of the partition member 101 in the tank axial direction is provided in the tank body 91. Further, the tank atmosphere chamber 95 (in the tank body 91) is a tank urging member that urges the partition member 101 toward the stopper 105 (in other words, the direction against the positive pressure applied to the receiving chamber 93). The coil spring 107 is provided. Here, the spring constant of the coil spring 107 is set to 0.1 to 1.5 times the spring constant of the coil spring 73. In addition, when the airtightness at the time of sliding of the partition member 101 is not required, the O-ring 103 may be omitted, and elastic deformation made of rubber (resin) or the like is possible instead of the plate-like partition member 101. A film-like partition member (not shown) may be used. Further, instead of the coil spring 107 being provided in the tank atmosphere chamber 95, another tank urging member (not shown) that urges the partition member 101 toward the stopper 105 may be provided outside the tank main body 91. .

  In the middle of the piping path 81 (between the pressure chamber 63 and the receiving chamber 93 or between the duty solenoid valve 83 and the receiving chamber 93 in the middle of the piping path 81), the air discharge port 21 can be expanded and contracted. A storage bag (not shown) for receiving the positive pressure from the pipe may be branched, or a part of the piping path 81 may be made of rubber that can expand and contract. Further, an orifice (not shown) that narrows the flow path area (path area) in the piping path 81 (between the pressure chamber 63 and the receiving chamber 93 or between the duty solenoid valve 83 and the receiving chamber 93 in the piping path 81). ) May be provided.

  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 the operation of the vehicle supercharger 1, and positive pressure is applied to the pressure chamber 63 from the air discharge port 21 as a pressure source, The central portion of the diaphragm 67 is displaced to one side (left direction) in the actuator axial direction. Then, the operating rod 75 moves to one side of the actuator axial direction, and the link member 53 can be swung in the forward direction (clockwise direction in FIG. 4). 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, after the opening of the bypass passage 33 is opened, when the supercharging pressure becomes less than the set pressure and the application state of the positive pressure from the air discharge port 21 is released, the diaphragm 67 is applied by the urging force of the coil spring 73. Is displaced to the other side (right direction) in the actuator axial direction. Then, the operating rod 75 moves to the other side in the actuator axial direction and swings the link member 53 in the reverse direction (counterclockwise direction in FIG. 4). 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 67 is adjusted in the axial direction of the actuator by adjusting the positive pressure applied to the pressure chamber 63 by controlling the excitation and demagnetization of the duty solenoid valve 83. Displace appropriately. Then, the operating rod 75 can be appropriately moved in the actuator axial direction, and the link member 53 can be appropriately swung in the forward and reverse directions. 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. (Normal operation of the embodiment of the present invention).

  During operation of the vehicle supercharger 1, the positive pressure is applied from the air discharge port 21 to the pressure chamber 63, and the positive pressure is received from the air discharge port 21 to the receiving chamber 93. Slides airtightly to one side (left direction) in the tank axial direction against the urging force of the coil spring 107. Thereby, even when the positive pressure applied from the air discharge port 21 side has a pulsating component, the pulsating component can be sufficiently absorbed by the surge tank 87 (mainly the coil spring 107). Therefore, it is possible to sufficiently suppress the vibration of the operating rod 75 and the vibration of the valve 45 due to the vibration during the operation of the vehicle supercharger 1.

  Particularly, since the spring constant of the coil spring 107 is set to 0.8 to 1.5 times the spring constant of the coil spring 73, the absorbability of the positive pressure pulsation component by the coil spring 107 is increased. Further, since the first port 97 and the second port 99 are respectively formed in the long side portion 91a of the tank body 91, the receiving chamber is compared with the case where they are formed in the short side portion 91b of the tank body 91, respectively. In 93, the positive pressure pulsation component is easily relaxed (dispersed). Thereby, the vibration of the operating rod 75 during the operation of the vehicle supercharger 1 can be more sufficiently suppressed.

  Since the surge tank 87 is located in a region on the opposite side of the diaphragm actuator 57 centering on the axis of the compressor impeller 13, even if the vehicle turbocharger 1 is equipped with the valve operating device 55, the vehicle overload The weight balance of the feeder 1 can be stabilized. (Specific operation of the embodiment of the present invention).

  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 the operation of the vehicle supercharger 1 is more sufficiently achieved. Therefore, chattering noise from the waste gate valve 35 can be reduced, and the quietness of the waste gate valve 35 can be improved.

  Further, even if the vehicle supercharger 1 is equipped with the valve actuating device 55, the weight balance of the vehicle supercharger 1 can be stabilized, so that the mountability of the vehicle supercharger 1 to the vehicle is improved. be able to.

  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. In addition, instead of allowing the pressure chamber 63 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. 73 is provided in the pressure chamber 63 and the coil spring 107 is provided in the receiving chamber 93.

  The actuator body 61 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 actuator atmospheric chamber 65 inside. Further, when the absorbability of the pulsating component by the tank main body 91 is sufficiently high, the partition member 101, the stopper 105, and the coil spring 107 may be omitted from the surge tank 87.

  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.

  1: vehicle turbocharger, 3: bearing housing, 5: radial bearing, 9: rotor shaft, 11: compressor housing, 13: compressor impeller, 15: air inlet, 17: diffuser flow path, 21: air 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: valve actuator, 57: diaphragm actuator, 61: actuator body 63: Pressure chamber, 65: Actuator atmosphere chamber, 67: Diaphragm, 73: Carp Spring (actuator urging member), 75: Actuating rod, 81: Piping path, 87: Surge tank, 91: Tank body, 93: Receiving chamber, 95: Tank atmosphere chamber, 101: Partition member, 105: Stopper, 107: Coil spring (tank urging member)

Claims (3)

Inside the connection body connected in a state of communication with the turbine housing or the turbine housing is used the flow rate of the exhaust gas supplied to the turbine impeller side supercharger gas flow variable passage is formed shall be the variable,
The turbine housing or said rotatable provided stem to a support hole formed in the outer wall of the connecting member to the forward and reverse directions, the mounting member having a base end portion connected to the stem, and provided at the distal end portion of said mounting member the gas flow rate variable passage opening side of the abutment spaced valving on the valve seat, and includes a link member having a base end portion is connected to the base end portion of the stem, closing the opening of the gas flow rate variable passage in the valve actuating device Ru operates the variable flow valve mechanism,
A cylindrical actuator body having a pressure chamber capable of applying a positive pressure or a negative pressure from a pressure source and an actuator atmosphere chamber communicating with the atmosphere inside, so that the pressure chamber and the actuator atmosphere chamber are partitioned in the actuator body A diaphragm having a central portion that is displaceable in the axial direction of the actuator, an actuator urging member that urges the diaphragm in a direction against positive pressure or negative pressure applied to the pressure chamber, and a base end portion. provided is connected to the center portion of the diaphragm and tip rotatably linked actuating rod to the distal end portion of the link member, a diaphragm actuator for oscillating the link member to the forward and reverse directions,
Wherein said pressure source inside the pressure chamber cylindrical tank body having a tank atmospheric chamber communicating with the receiving chamber and the atmosphere communicating in the middle of the to that piping channel contact, and said receiving chamber to said tank body A partition member provided to partition the tank atmosphere chamber and slidable in the tank axial direction, and a tank bias for biasing the partition member in a direction against a positive pressure or a negative pressure applied to the receiving chamber A surge tank comprising a member and receiving a positive pressure or a negative pressure from the pressure source ,
The diaphragm actuator is provided on an outer wall of the compressor housing in the turbocharger, and the surge tank is located in a region on the opposite side of the diaphragm actuator around the axis of the turbine impeller on the outer wall of the compressor housing. The valve actuator. A valve operating device for operating a variable flow rate valve mechanism of a supercharger,
A diaphragm type actuator having an operating rod connected to the variable flow rate valve mechanism;
A surge tank provided independently of the diaphragm actuator and disposed in the middle of a piping path connecting the diaphragm actuator and a pressure source ;
The surge tank includes a receiving chamber that receives gas from the pressure source, a tank atmospheric chamber that communicates with the atmosphere, a partition member that partitions the receiving chamber and the tank atmospheric chamber, and is slidable, and the receiving chamber A tank biasing member that biases the partition member in a direction against a pressure applied to the valve actuating device. In the supercharger that supercharges the air supplied to the engine using the energy of the exhaust gas from the engine,
To claim 1 or claim 2 equipped with a valve actuation system according supercharger.

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