WO2019198135A1 - Waste gate valve device and turbocharger provided with said waste gate valve device - Google Patents

Waste gate valve device and turbocharger provided with said waste gate valve device Download PDF

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Publication number
WO2019198135A1
WO2019198135A1 PCT/JP2018/014967 JP2018014967W WO2019198135A1 WO 2019198135 A1 WO2019198135 A1 WO 2019198135A1 JP 2018014967 W JP2018014967 W JP 2018014967W WO 2019198135 A1 WO2019198135 A1 WO 2019198135A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve
spring
wastegate
chamber
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PCT/JP2018/014967
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French (fr)
Japanese (ja)
Inventor
直樹 奥村
田中　健吾
信之介 長船
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三菱重工エンジン＆ターボチャージャ株式会社
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Application filed by 三菱重工エンジン＆ターボチャージャ株式会社 filed Critical 三菱重工エンジン＆ターボチャージャ株式会社
Priority to PCT/JP2018/014967 priority Critical patent/WO2019198135A1/en
Publication of WO2019198135A1 publication Critical patent/WO2019198135A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present disclosure relates to a wastegate valve device and a turbocharger including the wastegate valve device.
  • the wastegate valve described in Patent Document 1 is controlled by a drive source including a diaphragm that uses engine intake pressure.
  • This wastegate valve is configured such that the diaphragm changes according to the intake pressure of the engine and opens and closes by swinging the lever via the link mechanism. Since the waste gate valve is configured to be moved by the intake pressure of the engine, the cost can be reduced as compared with an air-operated butterfly valve or an electric waste gate valve.
  • the wastegate valve described in Patent Document 1 is configured such that the diaphragm changes according to the intake pressure of the engine, and is opened and closed by swinging the lever via the link mechanism. Since the wastegate valve is not moved directly, the opening adjustment accuracy of the wastegate flow path is low, and the controllability of the opening is particularly low when the wastegate flow path is in a very small opening state. there were.
  • At least one embodiment of the present disclosure provides a wastegate valve device with improved controllability of opening adjustment of the wastegate flow path and a turbocharger including the wastegate valve device. Objective.
  • a wastegate valve device includes: A wastegate valve for controlling an opening degree of a wastegate passage formed in a turbine housing of an exhaust turbine of a turbocharger, comprising a valve body configured to contact a valve seat formed in the turbine housing Westgate valve, A drive mechanism for driving the wastegate valve;
  • the drive mechanism is An elastic member configured to impart an elastic force to the wastegate valve to press the valve body toward the valve seat;
  • a cylinder portion for accommodating the elastic member;
  • a communication pipe communicating the discharge side flow path of the compressor of the turbocharger and the inside of the cylinder part;
  • a differential pressure adjusting valve for adjusting and adjusting the differential pressure in the cylinder portion by the pressure in the discharge-side flow path of the compressor;
  • the elastic force applied to the wastegate valve is adjusted by applying a pressure based on the differential pressure to the elastic member in the cylinder portion.
  • the elastic force applied to the wastegate valve is applied to the elastic member by applying a pressure based on the differential pressure formed by the pressure in the discharge side flow path of the compressor in the cylinder portion. Since it is adjusted, the controllability of adjusting the opening degree of the wastegate channel can be improved.
  • the cylinder part In the cylinder part, the cylinder part is partitioned into a first chamber containing the elastic member and a second chamber containing a part of the wastegate valve, and the pressure based on the differential pressure in the cylinder part and the A partition member that can slide according to the elastic force is provided,
  • the communication pipe is A first branch pipe portion communicating with the first chamber; A second branch pipe portion communicating with the second chamber,
  • the differential pressure adjusting valve adjusts a flow passage area of the second branch pipe portion to make the pressure in the first chamber and the pressure in the second chamber different from each other, thereby forming the differential pressure.
  • the differential pressure is adjusted by changing the difference between the pressure in one chamber and the pressure in the second chamber.
  • the differential pressure adjusting valve adjusts the differential pressure by changing the difference between the pressure in the first chamber and the pressure in the second chamber, and the pressure based on the differential pressure is applied to the elastic member.
  • the elastic force applied to the wastegate valve is adjusted, the controllability of the opening adjustment of the wastegate flow path can be improved.
  • the wastegate valve further includes a rod that connects the valve body and the partition member.
  • the wastegate valve has a globe valve structure that moves linearly in the direction of the elastic force of the elastic member, so that the risk of sticking due to wrinkles can be reduced.
  • a pressure detector for detecting the pressure on the discharge side of the compressor When the differential pressure adjusting valve adjusts the differential pressure based on a value detected by the pressure detector, the waste gate valve controls the opening degree of the waste gate flow path.
  • the pressure on the discharge side of the compressor can be adjusted to the supercharging pressure determined based on the ECU map of the vehicle equipped with the turbocharger provided with this wastegate valve device.
  • the elastic member includes a first spring and a second spring arranged in series, The spring constant of the first spring and the spring constant of the second spring are different from each other.
  • the wastegate flow path is It is possible to improve the controllability of the opening when it is in a minute opening state.
  • the elastic member is an unequal pitch coil spring including the first spring and the second spring having different coil pitches.
  • the amount of movement of the wastegate valve can be finely controlled by contracting from the state in which each of the first spring and the second spring is stretched. It is possible to improve the controllability of the opening when it is in a minute opening state.
  • a turbocharger is: The wastegate valve device according to any one of the above (1) to (6) is provided.
  • a pressure based on a differential pressure formed by a pressure in the discharge-side flow path of the compressor is applied to the elastic member to be applied to the wastegate valve. Since the elastic force is adjusted, the controllability of the opening adjustment of the wastegate flow path can be improved.
  • the turbocharger 1 includes a compressor 2 and an exhaust turbine 3.
  • the compressor 2 includes an impeller 2a and a compressor housing 2b that includes the impeller 2a.
  • the exhaust turbine 3 includes an impeller 3a and a turbine housing 3b that includes the impeller 3a.
  • the impeller 2a and the impeller 3a are connected by a rotating shaft 4.
  • the discharge-side flow path 12 of the compressor 2 communicates with each cylinder of the engine 10 via an intake manifold (not shown).
  • an intercooler 14 for cooling the intake air of the engine 10 compressed by the compressor 2 and a pressure in the discharge side flow path 12 between the intercooler 14 and the engine 10 are detected.
  • a pressure sensor 15 which is a pressure detection unit.
  • the suction side flow path 13 of the exhaust turbine 3 communicates with each cylinder of the engine 10 via an exhaust manifold (not shown).
  • a waste gate channel 17 is formed that communicates the suction side channel 13 of the exhaust turbine 3 and the discharge side channel 16 of the exhaust turbine 3. That is, the wastegate flow path 17 is a flow path that bypasses the impeller 3 a of the exhaust turbine 3.
  • the turbocharger 1 includes a wastegate valve device 20 for adjusting the flow rate of exhaust gas from the engine 10 flowing through the wastegate flow path 17, that is, the flow rate of exhaust gas flowing through the impeller 3a of the exhaust turbine 3.
  • the wastegate valve device 20 includes a wastegate valve 21 that controls the opening degree of the wastegate flow path 17 and a drive mechanism 30 that drives the wastegate valve 21.
  • the wastegate valve 21 has a valve body 22 configured so as to be able to contact a valve seat 5 formed on a part of an inner peripheral surface defining the wastegate flow path 17 in the turbine housing 3 b, and one end of the valve body 22. And a rod 23 connected to.
  • the drive mechanism 30 includes a spring 31 that is an elastic member, a cylinder portion 32 that houses the spring 31, a communication pipe 33 that communicates the discharge-side flow path 12 of the compressor 2 and the inside of the cylinder portion 32, and a differential pressure And an electromagnetic valve 34 which is a regulating valve.
  • the communication pipe 33 has a tip portion on the cylinder part 32 side that branches into a first branch pipe part 33a and a second branch pipe part 33b, and an electromagnetic valve 34 is provided on one of the second branch pipe parts 33b. Yes.
  • the electromagnetic valve 34 has a function of adjusting the flow passage area of the second branch pipe portion 33b by adjusting the opening degree, and a function of opening and closing the relief pipe 36 that communicates the waste gate flow passage 17 and the second chamber 32b. It is a valve.
  • the solenoid valve 34 and the pressure sensor 15 are electrically connected to an ECU 18 that is a control unit that controls the vehicle on which the turbocharger 1 and the engine 10 are mounted.
  • An accelerator opening sensor 9 that detects the opening of the accelerator 8 of the vehicle is also electrically connected to the ECU 18.
  • a partition member 35 that partitions the cylinder part 32 into a first chamber 32a and a second chamber 32b and is slidable.
  • a first branch pipe section 33a is connected to the first chamber 32a, and a second branch pipe section 33b is connected to the second chamber 32b.
  • a part of the rod 23 of the wastegate valve 21 is inserted into the first chamber 32 a, and the other end of the rod 23 is connected to the partition member 35.
  • a spring 31 is accommodated in the second chamber 32 b, and one end of the spring 31 is in contact with or connected to the partition member 35.
  • the intake air compressed by the compressor 2 is cooled by the intercooler 14 when flowing through the discharge-side flow path 12, and then sucked into each cylinder of the engine 10 and burned together with fuel.
  • the exhaust gas generated by the combustion flows through the suction side flow path 13, flows into the exhaust turbine 3, rotates the impeller 3 a, and then flows through the discharge side flow path 16.
  • the rotation of the impeller 3b due to the exhaust gas is transmitted to the impeller 2a via the rotating shaft 4 to rotate the impeller 2a.
  • the opening of the accelerator 8 detected by the accelerator opening sensor 9 is transmitted to the ECU 18.
  • the ECU 18 is based on a map incorporated in the ECU 18 in advance, and the boost pressure required for the intake air sucked into each cylinder of the engine 10 from the transmitted opening of the accelerator 8 (hereinafter referred to as a required boost pressure). To decide.
  • the detected value by the pressure sensor 15 is also transmitted to the ECU 18.
  • the value detected by the pressure sensor 15 corresponds to the pressure of intake air sucked into each cylinder of the engine 10 (hereinafter, actual intake pressure). Therefore, the ECU 18 compares the required supercharging pressure with the actual intake pressure, and when the former is larger than the latter, the opening of the wastegate flow path 17 is reduced by the electromagnetic valve 34 and flows into the exhaust turbine 3. Increase the flow rate of exhaust gas. As a result, the rotational speed of the impeller 3a increases, and the rotational speed of the impeller 2a increases accordingly, so that the actual intake pressure increases. On the other hand, when the latter is larger than the former, the opening degree of the waste gate flow path 17 is increased by the electromagnetic valve 34 to reduce the flow rate of the exhaust gas flowing into the exhaust turbine 3. As a result, the rotational speed of the impeller 3a decreases, and the rotational speed of the impeller 2a decreases accordingly, so that the actual intake pressure decreases.
  • the ECU 18 controls the opening degree of the waste gate channel 17 by the electromagnetic valve 34.
  • the spring 31 presses the partition member 35, whereby the elastic force of the spring 31 is transmitted to the waste gate valve 21, and the waste gate valve 21 moves in the direction in which the valve body 22 faces the valve seat 5.
  • the electromagnetic valve 34 is fully opened, part of the intake air in the discharge side flow passage 12 flows into the first chamber 32a and the second chamber 32b, and the pressure in the first chamber 32a and the pressure in the second chamber 32b.
  • the force applied to the wastegate valve 21 is only the elastic force of the spring 31. If the force applied to the wastegate valve 21 is only the elastic force of the spring 31, the valve element 22 contacts the valve seat 5 and closes the wastegate flow path 17. That is, the opening degree of the waste gate channel 17 becomes zero.
  • the ECU 18 adjusts the opening degree of the electromagnetic valve 34 so as to decrease the flow area of the second branch pipe portion 33b.
  • the pressure in the second chamber 32b becomes smaller than the pressure in the first chamber 32a due to the pressure loss in the electromagnetic valve 34.
  • a differential pressure is generated between the first chamber 32 a and the second chamber 32 b via the partition member 35, and the pressure based on this differential pressure is opposed to the direction of the elastic force of the spring 31 via the partition member 35.
  • the elastic force applied from the spring 31 to the wastegate valve 21 is reduced.
  • the ECU 18 adjusts the opening of the electromagnetic valve 34 to be small, the pressure based on this differential pressure can be made larger than the elastic force of the spring 31. Then, the spring 31 is pressed and contracted by the partition member 35, and as a result, the waste gate valve 21 moves in the direction in which the spring 31 contracts, so that the valve body 22 moves away from the valve seat 5, and the waste gate channel 17 The opening increases from zero. On the other hand, the ECU 18 adjusts the opening degree of the solenoid valve 34 to increase the differential pressure, so that the elastic force applied to the wastegate valve 21 by the spring 31 increases, and the wastegate flow path 17. The degree of opening decreases.
  • the opening degree of the wastegate channel 17 can be controlled by adjusting the differential pressure between the first chamber 32a and the second chamber 32b by adjusting the opening degree of the electromagnetic valve 34, the engine 10 in particular.
  • the waste gate channel 17 can be closed by opening the electromagnetic valve 34.
  • the excessive reactivity becomes good and the follow-up of the accelerator 8 is accelerated.
  • the electromagnetic valve 34 opens the escape pipe 36 to release the intake air in the second chamber 32b to the waste gate flow path 17 through the pipe 36.
  • the differential pressure between the first chamber 32a and the second chamber 32b is maximized, so that the wastegate channel 17 is fully opened.
  • the elastic force given to the wastegate valve 21 is applied by applying a pressure based on the differential pressure formed by the pressure in the discharge side flow path 12 of the compressor 2 to the spring 31. Since it is adjusted, the controllability of opening degree adjustment of the wastegate flow path 17 can be improved. In particular, the controllability of the opening degree when the wastegate channel 17 is in the minute opening state becomes good, and the output fluctuation when the engine 10 is in the high load operation state can be reduced.
  • the wastegate valve 21 has a configuration in which the valve body 22 and the partition member 35 are connected by the rod 23, the wastegate valve 21 moves linearly in the direction of the elastic force of the spring 31. Since it has a globe valve structure, the risk of sticking due to wrinkles can be reduced.
  • the wastegate valve device according to the second embodiment is obtained by changing the configuration of the elastic member with respect to the first embodiment.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
  • the spring 31 includes a first spring 31a and a second spring 31b arranged in series.
  • the spring 31 is an unequal pitch coil spring in which the pitch interval of the first springs 31a is larger than the pitch interval of the second springs 31b.
  • pitch interval of the first spring 31a is greater than the pitch of the second spring 31b
  • the spring constant k 1 of the first spring 31a is smaller than the spring constant k 2 of the second spring 31b (k 1 ⁇ k 2 It has become.
  • the first spring 31a and the second spring 31b may be connected to each other at one end, or may be in contact with each other without being connected to each other. Other configurations are the same as those of the first embodiment.
  • the graph of FIG. 3 shows the spring characteristics of the spring 31 which is an unequal pitch coil spring.
  • shrinkage amount is small range of spring 31, between that is, from the contraction amount is 0 to x 1
  • the first spring 31a spring constant is small contracts mainly.
  • contraction amount x 1 the first spring 31a is gradually is primarily contracted
  • pitch interval of the first spring 31a is equivalent to the amount of contraction of the whole spring 31 when it becomes equal to the pitch of the second spring 31b To do.
  • the amount of shrinkage is more than x 1, since the first spring 31a and the second spring 31b is contracted in the same way, in this range, as the spring 31 is contracted by the spring constant between the spring constant k 1 and the spring constant k 2 become.
  • the respective spring constants are made different by making the pitch intervals of the first spring 31a and the second spring 31b different, but it is not limited to such a form.
  • the spring constants can also be made different by making the diameters of the first spring 31a and the second spring 31b different, and one of the first spring 31a and the second spring 31b can be quenched.
  • the spring constants can also be made different by making the respective stiffnesses different.
  • the electromagnetic valve 34 is provided only in the second branch pipe portion 33b. However, the electromagnetic valve 34 is also provided in the first branch pipe portion 33a to adjust the opening degree of each electromagnetic valve 34. Thus, the differential pressure in the cylinder part 32 may be adjusted.
  • the elastic member is the spring 31, but is not limited to the spring. Any member can be used as long as it generates an elastic force.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Abstract

This waste gate valve device is provided with a waste gate valve that includes a valve body configured to be capable of abutting a valve seat formed on a turbine housing, and a drive mechanism for driving the waste gate valve. The drive mechanism is provided with an elastic member that is configured so as to be capable of imparting an elastic force to the waste gate valve, a cylinder part that contains the elastic member, and a pressure differential regulation valve that regulates a pressure differential formed inside the cylinder part due to the pressure in a discharge-side flow path of a compressor. A pressure based on the pressure differential inside the cylinder part is applied to the elastic member, whereby the elastic force imparted to the waste gate valve is regulated.

Description

ウェストゲートバルブ装置及びこのウェストゲートバルブ装置を備えるターボチャージャWastegate valve device and turbocharger equipped with this wastegate valve device
　本開示は、ウェストゲートバルブ装置及びこのウェストゲートバルブ装置を備えるターボチャージャに関する。 The present disclosure relates to a wastegate valve device and a turbocharger including the wastegate valve device.
　ターボチャージャを搭載した車両が急勾配の路面を上る場合や急加速をする場合、ターボチャージャにおいてウェストゲート流路の開度が調整されて、排気タービンへの排気ガスの供給量の調整が行われる。ウェストゲートバルブには、エンジンに搭載したコンプレッサを駆動源とする空制バタフライ弁や、圧力の制御性を重視して電制ウェストゲートバルブを採用する場合が多いが、これらのウェストゲートバルブは、部品点数が増加することから高コストとなる傾向がある。 When a vehicle equipped with a turbocharger climbs a steep road surface or accelerates rapidly, the opening of the wastegate passage is adjusted in the turbocharger, and the amount of exhaust gas supplied to the exhaust turbine is adjusted. . Westgate valves often employ air-operated butterfly valves that use a compressor mounted on the engine as a drive source, and electric-controlled wastegate valves that emphasize pressure controllability. Since the number of parts increases, it tends to be expensive.
　特許文献１に記載のウェストゲートバルブは、エンジンの吸気圧を利用したダイヤフラムを備える駆動源によって制御されている。このウェストゲートバルブは、エンジンの吸気圧に応じたダイヤフラムの変動がリンク機構を介してレバーを揺動させることによって開閉するように構成されている。エンジンの吸気圧によってこのウェストゲートバルブを動かすように構成されているため、空制バタフライ弁や電制ウェストゲートバルブに比べてコストを低下させることができる。 The wastegate valve described in Patent Document 1 is controlled by a drive source including a diaphragm that uses engine intake pressure. This wastegate valve is configured such that the diaphragm changes according to the intake pressure of the engine and opens and closes by swinging the lever via the link mechanism. Since the waste gate valve is configured to be moved by the intake pressure of the engine, the cost can be reduced as compared with an air-operated butterfly valve or an electric waste gate valve.
特開昭６０－２５２１２３号公報JP 60-252123 A
　しかしながら、特許文献１に記載のウェストゲートバルブは、エンジンの吸気圧に応じたダイヤフラムの変動がリンク機構を介してレバーを揺動させることによって開閉するように構成されており、エンジンの吸気圧によって直接ウェストゲートバルブを動かすものではないので、ウェストゲート流路の開度調整の精度が低く、特に、ウェストゲート流路が微小開度状態である場合の開度の制御性が低いといった問題点があった。 However, the wastegate valve described in Patent Document 1 is configured such that the diaphragm changes according to the intake pressure of the engine, and is opened and closed by swinging the lever via the link mechanism. Since the wastegate valve is not moved directly, the opening adjustment accuracy of the wastegate flow path is low, and the controllability of the opening is particularly low when the wastegate flow path is in a very small opening state. there were.
　上述の事情に鑑みて、本開示の少なくとも１つの実施形態は、ウェストゲート流路の開度調整の制御性を向上したウェストゲートバルブ装置及びこのウェストゲートバルブ装置を備えるターボチャージャを提供することを目的とする。 In view of the above circumstances, at least one embodiment of the present disclosure provides a wastegate valve device with improved controllability of opening adjustment of the wastegate flow path and a turbocharger including the wastegate valve device. Objective.
（１）本発明の少なくとも１つの実施形態に係るウェストゲートバルブ装置は、
　ターボチャージャの排気タービンのタービンハウジングに形成されたウェストゲート流路の開度を制御するウェストゲートバルブであって、前記タービンハウジングに形成された弁座に当接可能に構成された弁体を含むウェストゲートバルブと、
　前記ウェストゲートバルブを駆動する駆動機構と
を備え、
　前記駆動機構は、
　前記弁体を前記弁座に向けて押し付ける弾性力を前記ウェストゲートバルブに付与可能に構成された弾性部材と、
　前記弾性部材を収容するシリンダ部と、
　前記ターボチャージャのコンプレッサの吐出側流路と前記シリンダ部の内部とを連通する連通管と、
　前記コンプレッサの前記吐出側流路内の圧力によって前記シリンダ部内に差圧を形成するとともに調整する差圧調整弁と
を備え、
　前記シリンダ部内において前記差圧に基づく圧力が前記弾性部材に加えられることによって、前記ウェストゲートバルブに付与される前記弾性力が調節される。 (1) A wastegate valve device according to at least one embodiment of the present invention includes:
A wastegate valve for controlling an opening degree of a wastegate passage formed in a turbine housing of an exhaust turbine of a turbocharger, comprising a valve body configured to contact a valve seat formed in the turbine housing Westgate valve,
A drive mechanism for driving the wastegate valve;
The drive mechanism is
An elastic member configured to impart an elastic force to the wastegate valve to press the valve body toward the valve seat;
A cylinder portion for accommodating the elastic member;
A communication pipe communicating the discharge side flow path of the compressor of the turbocharger and the inside of the cylinder part;
A differential pressure adjusting valve for adjusting and adjusting the differential pressure in the cylinder portion by the pressure in the discharge-side flow path of the compressor;
The elastic force applied to the wastegate valve is adjusted by applying a pressure based on the differential pressure to the elastic member in the cylinder portion.
　上記（１）の構成によると、シリンダ部内において、コンプレッサの吐出側流路内の圧力により形成された差圧に基づく圧力が弾性部材に加えられることによって、ウェストゲートバルブに付与される弾性力が調節されるので、ウェストゲート流路の開度調整の制御性を向上することができる。 According to the configuration of (1) above, the elastic force applied to the wastegate valve is applied to the elastic member by applying a pressure based on the differential pressure formed by the pressure in the discharge side flow path of the compressor in the cylinder portion. Since it is adjusted, the controllability of adjusting the opening degree of the wastegate channel can be improved.
（２）いくつかの実施形態では、上記（１）の構成において、
　前記シリンダ部内には、前記弾性部材を収容する第１室と、前記ウェストゲートバルブの一部を収容する第２室とに前記シリンダ部内を仕切るとともに前記シリンダ部内で前記差圧に基づく圧力及び前記弾性力に応じてスライド可能な仕切部材が設けられ、
　前記連通管は、
　前記第１室に連通する第１分岐管部と、
　前記第２室に連通する第２分岐管部と
を含み、
　前記差圧調整弁は、前記第２分岐管部の流路面積を調整することによって、前記第１室内の圧力及び前記第２室内の圧力を互いに異ならせて前記差圧を形成するとともに前記第１室内の圧力と前記第２室内の圧力との差を変化させて前記差圧を調整する。 (2) In some embodiments, in the configuration of (1) above,
In the cylinder part, the cylinder part is partitioned into a first chamber containing the elastic member and a second chamber containing a part of the wastegate valve, and the pressure based on the differential pressure in the cylinder part and the A partition member that can slide according to the elastic force is provided,
The communication pipe is
A first branch pipe portion communicating with the first chamber;
A second branch pipe portion communicating with the second chamber,
The differential pressure adjusting valve adjusts a flow passage area of the second branch pipe portion to make the pressure in the first chamber and the pressure in the second chamber different from each other, thereby forming the differential pressure. The differential pressure is adjusted by changing the difference between the pressure in one chamber and the pressure in the second chamber.
　上記（２）の構成によると、差圧調整弁が第１室内の圧力と第２室内の圧力との差を変化させることによって差圧を調整し、差圧に基づく圧力が弾性部材に加えられることによって、ウェストゲートバルブに付与される弾性力が調節されるので、ウェストゲート流路の開度調整の制御性を向上することができる。 According to the configuration of (2) above, the differential pressure adjusting valve adjusts the differential pressure by changing the difference between the pressure in the first chamber and the pressure in the second chamber, and the pressure based on the differential pressure is applied to the elastic member. Thus, since the elastic force applied to the wastegate valve is adjusted, the controllability of the opening adjustment of the wastegate flow path can be improved.
（３）いくつかの実施形態では、上記（２）の構成において、
　前記ウェストゲートバルブは、前記弁体と前記仕切部材とを連結するロッドをさらに含む。 (3) In some embodiments, in the configuration of (2) above,
The wastegate valve further includes a rod that connects the valve body and the partition member.
　上記（３）の構成によると、前記ウェストゲートバルブは、弾性部材の弾性力の方向に直線的に移動するグローブバルブ構造を有するので、煤に起因する固着リスクを低減することができる。 According to the configuration of (3) above, the wastegate valve has a globe valve structure that moves linearly in the direction of the elastic force of the elastic member, so that the risk of sticking due to wrinkles can be reduced.
（４）いくつかの実施形態では、上記（１）～（３）のいずれかの構成において、
　前記コンプレッサの吐出側の圧力を検出する圧力検出部をさらに備え、
　前記差圧調整弁が前記圧力検出部による検出値に基づいて前記差圧を調整することによって、前記ウェストゲートバルブが前記ウェストゲート流路の開度を制御する。 (4) In some embodiments, in any one of the above configurations (1) to (3),
A pressure detector for detecting the pressure on the discharge side of the compressor;
When the differential pressure adjusting valve adjusts the differential pressure based on a value detected by the pressure detector, the waste gate valve controls the opening degree of the waste gate flow path.
　上記（４）の構成によると、コンプレッサの吐出側の圧力を、このウェストゲートバルブ装置が設けられたターボチャージャを備える車両のＥＣＵマップに基づいて決定された過給圧に調整することができる。 According to the configuration of (4) above, the pressure on the discharge side of the compressor can be adjusted to the supercharging pressure determined based on the ECU map of the vehicle equipped with the turbocharger provided with this wastegate valve device.
（５）いくつかの実施形態では、上記（１）～（４）のいずれかの構成において、
　前記弾性部材は、直列に配置された第１ばね及び第２ばねを含み、
　前記第１ばねのばね定数と第２ばねのばね定数とは互いに異なる。 (5) In some embodiments, in any one of the above configurations (1) to (4),
The elastic member includes a first spring and a second spring arranged in series,
The spring constant of the first spring and the spring constant of the second spring are different from each other.
　上記（５）の構成によると、第１ばね及び第２ばねのそれぞれが伸びた状態から縮むことによるウェストゲートバルブの移動量の制御を細かく行うことができるようになるので、ウェストゲート流路が微小開度状態である場合の開度の制御性を向上することができる。 According to the configuration of (5) above, since the amount of movement of the wastegate valve can be finely controlled by contracting from the state in which each of the first spring and the second spring is stretched, the wastegate flow path is It is possible to improve the controllability of the opening when it is in a minute opening state.
（６）いくつかの実施形態では、上記（５）の構成において、
　前記弾性部材は、互いにコイルピッチが異なる前記第１ばね及び前記第２ばねを含む不等ピッチコイルばねである。 (6) In some embodiments, in the configuration of (5) above,
The elastic member is an unequal pitch coil spring including the first spring and the second spring having different coil pitches.
　上記（６）の構成によると、第１ばね及び第２ばねのそれぞれが伸びた状態から縮むことによるウェストゲートバルブの移動量の制御を細かく行うことができるようになるので、ウェストゲート流路が微小開度状態である場合の開度の制御性を向上することができる。 According to the configuration of (6) above, the amount of movement of the wastegate valve can be finely controlled by contracting from the state in which each of the first spring and the second spring is stretched. It is possible to improve the controllability of the opening when it is in a minute opening state.
（７）本発明の少なくとも１つの実施形態に係るターボチャージャは、
　上記（１）～（６）のいずれかのウェストゲートバルブ装置を備える。 (7) A turbocharger according to at least one embodiment of the present invention is:
The wastegate valve device according to any one of the above (1) to (6) is provided.
　上記（７）の構成によると、ターボチャージャの排気タービンに設けられたウェストゲート流路の開度調整の制御性を向上することができる。 According to the configuration of (7) above, it is possible to improve the controllability of opening degree adjustment of the wastegate flow path provided in the exhaust turbine of the turbocharger.
　本開示の少なくとも１つの実施形態によれば、シリンダ部内において、コンプレッサの吐出側流路内の圧力により形成された差圧に基づく圧力が弾性部材に加えられることによって、ウェストゲートバルブに付与される弾性力が調節されるので、ウェストゲート流路の開度調整の制御性を向上することができる。 According to at least one embodiment of the present disclosure, in the cylinder portion, a pressure based on a differential pressure formed by a pressure in the discharge-side flow path of the compressor is applied to the elastic member to be applied to the wastegate valve. Since the elastic force is adjusted, the controllability of the opening adjustment of the wastegate flow path can be improved.
本開示の実施形態１に係るウェストゲートバルブ装置を備えたターボチャージャの構成模式図である。It is a block diagram of the structure of the turbocharger provided with the wastegate valve apparatus which concerns on Embodiment 1 of this indication. 本開示の実施形態２に係るウェストゲートバルブ装置に用いられるばねの構成模式図である。It is a structure schematic diagram of the spring used for the wastegate valve apparatus which concerns on Embodiment 2 of this indication. 本開示の実施形態２に係るウェストゲートバルブ装置に用いられるばねのばね特性を表すグラフである。It is a graph showing the spring characteristic of the spring used for the wastegate valve apparatus concerning Embodiment 2 of this indication.
　以下、図面を参照して本発明のいくつかの実施形態について説明する。ただし、本発明の範囲は以下の実施形態に限定されるものではない。以下の実施形態に記載されている構成部品の寸法、材質、形状、その相対配置などは、本発明の範囲をそれにのみ限定する趣旨ではなく、単なる説明例に過ぎない。 Hereinafter, some embodiments of the present invention will be described with reference to the drawings. However, the scope of the present invention is not limited to the following embodiments. The dimensions, materials, shapes, relative arrangements, and the like of the component parts described in the following embodiments are not merely intended to limit the scope of the present invention, but are merely illustrative examples.
（実施形態１）
　図１に示されるように、ターボチャージャ１はコンプレッサ２及び排気タービン３を備えている。コンプレッサ２は、インペラ２ａと、インペラ２ａを内部に含むコンプレッサハウジング２ｂとを備えている。排気タービン３は、インペラ３ａと、インペラ３ａを内部に含むタービンハウジング３ｂとを備えている。インペラ２ａとインペラ３ａとは回転軸４によって連結されている。 (Embodiment 1)
As shown in FIG. 1, the turbocharger 1 includes a compressor 2 and an exhaust turbine 3. The compressor 2 includes an impeller 2a and a compressor housing 2b that includes the impeller 2a. The exhaust turbine 3 includes an impeller 3a and a turbine housing 3b that includes the impeller 3a. The impeller 2a and the impeller 3a are connected by a rotating shaft 4.
　コンプレッサ２の吐出側流路１２は、図示しないインテークマニホールドを介してエンジン１０の各シリンダに連通している。吐出側流路１２には、コンプレッサ２によって圧縮されたエンジン１０の吸気を冷却するためのインタークーラ１４と、インタークーラ１４とエンジン１０との間における吐出側流路１２内の圧力を検出するための圧力検出部である圧力センサ１５とが設けられている。 The discharge-side flow path 12 of the compressor 2 communicates with each cylinder of the engine 10 via an intake manifold (not shown). In the discharge side flow path 12, an intercooler 14 for cooling the intake air of the engine 10 compressed by the compressor 2 and a pressure in the discharge side flow path 12 between the intercooler 14 and the engine 10 are detected. And a pressure sensor 15 which is a pressure detection unit.
　排気タービン３の吸入側流路１３は、図示しないエキゾーストマニホールドを介してエンジン１０の各シリンダに連通している。タービンハウジング３ｂには、排気タービン３の吸入側流路１３と排気タービン３の吐出側流路１６とを連通するウェストゲート流路１７が形成されている。すなわち、ウェストゲート流路１７は、排気タービン３のインペラ３ａをバイパスする流路である。 The suction side flow path 13 of the exhaust turbine 3 communicates with each cylinder of the engine 10 via an exhaust manifold (not shown). In the turbine housing 3 b, a waste gate channel 17 is formed that communicates the suction side channel 13 of the exhaust turbine 3 and the discharge side channel 16 of the exhaust turbine 3. That is, the wastegate flow path 17 is a flow path that bypasses the impeller 3 a of the exhaust turbine 3.
　ターボチャージャ１は、ウェストゲート流路１７を流れるエンジン１０からの排ガスの流量、すなわち排気タービン３のインペラ３ａを流れる排ガスの流量を調整するためのウェストゲートバルブ装置２０を備えている。ウェストゲートバルブ装置２０は、ウェストゲート流路１７の開度を制御するウェストゲートバルブ２１と、ウェストゲートバルブ２１を駆動する駆動機構３０とを備えている。 The turbocharger 1 includes a wastegate valve device 20 for adjusting the flow rate of exhaust gas from the engine 10 flowing through the wastegate flow path 17, that is, the flow rate of exhaust gas flowing through the impeller 3a of the exhaust turbine 3. The wastegate valve device 20 includes a wastegate valve 21 that controls the opening degree of the wastegate flow path 17 and a drive mechanism 30 that drives the wastegate valve 21.
　ウェストゲートバルブ２１は、タービンハウジング３ｂ内においてウェストゲート流路１７を画定する内周面の一部に形成された弁座５に当接可能に構成された弁体２２と、一端が弁体２２に接続されたロッド２３とを備えている。 The wastegate valve 21 has a valve body 22 configured so as to be able to contact a valve seat 5 formed on a part of an inner peripheral surface defining the wastegate flow path 17 in the turbine housing 3 b, and one end of the valve body 22. And a rod 23 connected to.
　駆動機構３０は、弾性部材であるばね３１と、ばね３１を内部に収容するシリンダ部３２と、コンプレッサ２の吐出側流路１２とシリンダ部３２の内部とを連通する連通管３３と、差圧調整弁である電磁弁３４とを備えている。連通管３３は、シリンダ部３２側の先端部分が第１分岐管部３３ａ及び第２分岐管部３３ｂに分岐しており、それらの一方の第２分岐管部３３ｂに電磁弁３４が設けられている。 The drive mechanism 30 includes a spring 31 that is an elastic member, a cylinder portion 32 that houses the spring 31, a communication pipe 33 that communicates the discharge-side flow path 12 of the compressor 2 and the inside of the cylinder portion 32, and a differential pressure And an electromagnetic valve 34 which is a regulating valve. The communication pipe 33 has a tip portion on the cylinder part 32 side that branches into a first branch pipe part 33a and a second branch pipe part 33b, and an electromagnetic valve 34 is provided on one of the second branch pipe parts 33b. Yes.
　電磁弁３４は、開度調整によって第２分岐管部３３ｂの流路面積を調整する機能と、ウェストゲート流路１７と第２室３２ｂとを連通する逃し配管３６を開閉する機能とを有する三方弁である。電磁弁３４及び圧力センサ１５はそれぞれ、ターボチャージャ１及びエンジン１０が搭載された車両の制御を行う制御部であるＥＣＵ１８に電気的に接続されている。また、車両のアクセル８の開度を検出するアクセル開度センサ９も電気的にＥＣＵ１８に接続されている。 The electromagnetic valve 34 has a function of adjusting the flow passage area of the second branch pipe portion 33b by adjusting the opening degree, and a function of opening and closing the relief pipe 36 that communicates the waste gate flow passage 17 and the second chamber 32b. It is a valve. The solenoid valve 34 and the pressure sensor 15 are electrically connected to an ECU 18 that is a control unit that controls the vehicle on which the turbocharger 1 and the engine 10 are mounted. An accelerator opening sensor 9 that detects the opening of the accelerator 8 of the vehicle is also electrically connected to the ECU 18.
　シリンダ部３２内には、シリンダ部３２内を第１室３２ａと第２室３２ｂとに仕切るとともにスライド可能な仕切部材３５が設けられている。第１室３２ａには第１分岐管部３３ａが接続し、第２室３２ｂには第２分岐管部３３ｂが接続している。第１室３２ａ内には、ウェストゲートバルブ２１のロッド２３の一部が挿入されており、ロッド２３の他端が仕切部材３５に接続されている。第２室３２ｂ内にはばね３１が収容されており、ばね３１の一端が仕切部材３５に当接又は接続されている。 In the cylinder part 32, there is provided a partition member 35 that partitions the cylinder part 32 into a first chamber 32a and a second chamber 32b and is slidable. A first branch pipe section 33a is connected to the first chamber 32a, and a second branch pipe section 33b is connected to the second chamber 32b. A part of the rod 23 of the wastegate valve 21 is inserted into the first chamber 32 a, and the other end of the rod 23 is connected to the partition member 35. A spring 31 is accommodated in the second chamber 32 b, and one end of the spring 31 is in contact with or connected to the partition member 35.
　次に、実施形態１に係るウェストゲートバルブ装置２０の動作について説明する。
　エンジン１０の稼働時において、コンプレッサ２によって圧縮された吸気は、吐出側流路１２を流通する際にインタークーラ１４で冷却された後、エンジン１０の各シリンダに吸引されて燃料と共に燃焼される。燃焼によって生じた排ガスは吸入側流路１３を流通し、排気タービン３に流入してインペラ３ａを回転させた後、吐出側流路１６を流通する。排ガスによるインペラ３ｂの回転は、回転軸４を介してインペラ２ａに伝達されて、インペラ２ａを回転させる。 Next, the operation of the wastegate valve device 20 according to the first embodiment will be described.
During the operation of the engine 10, the intake air compressed by the compressor 2 is cooled by the intercooler 14 when flowing through the discharge-side flow path 12, and then sucked into each cylinder of the engine 10 and burned together with fuel. The exhaust gas generated by the combustion flows through the suction side flow path 13, flows into the exhaust turbine 3, rotates the impeller 3 a, and then flows through the discharge side flow path 16. The rotation of the impeller 3b due to the exhaust gas is transmitted to the impeller 2a via the rotating shaft 4 to rotate the impeller 2a.
　後述する動作でウェストゲート流路１７の開度が調整されると、その開度に応じた流量で、エンジン１０の各シリンダから流出した排ガスの一部がウェストゲート流路１７を流通する。ウェストゲート流路１７を流通する排ガスの流量に応じて、排気タービン３に流入する排ガスの流量が変化し、インペラ３ｂの回転状態が変化するので、それに応じてインペラ２ａの回転状態も変化し、吐出側流路１２内の圧力も変化する。 When the opening degree of the wastegate flow path 17 is adjusted by the operation described later, a part of the exhaust gas flowing out from each cylinder of the engine 10 flows through the wastegate flow path 17 at a flow rate corresponding to the opening degree. The flow rate of the exhaust gas flowing into the exhaust turbine 3 changes according to the flow rate of the exhaust gas flowing through the wastegate flow path 17, and the rotation state of the impeller 3 b changes. Accordingly, the rotation state of the impeller 2 a also changes accordingly, The pressure in the discharge side flow path 12 also changes.
　ターボチャージャ１及びエンジン１０が搭載された車両の走行中、アクセル開度センサ９によって検出されたアクセル８の開度がＥＣＵ１８に伝送される。ＥＣＵ１８は、ＥＣＵ１８に予め組み込まれたマップに基づいて、伝送されたアクセル８の開度から、エンジン１０の各シリンダに吸引される吸気に要求される過給圧（以下、要求過給圧という）を決定する。ＥＣＵ１８には、圧力センサ１５による検出値も伝送される。 While the vehicle equipped with the turbocharger 1 and the engine 10 is traveling, the opening of the accelerator 8 detected by the accelerator opening sensor 9 is transmitted to the ECU 18. The ECU 18 is based on a map incorporated in the ECU 18 in advance, and the boost pressure required for the intake air sucked into each cylinder of the engine 10 from the transmitted opening of the accelerator 8 (hereinafter referred to as a required boost pressure). To decide. The detected value by the pressure sensor 15 is also transmitted to the ECU 18.
　圧力センサ１５による検出値は、エンジン１０の各シリンダに吸引される吸気の圧力（以下、実吸気圧）に相当する。そこで、ＥＣＵ１８は、要求過給圧と実吸気圧とを比較し、前者が後者よりも大きい場合には、電磁弁３４によってウェストゲート流路１７の開度を小さくして、排気タービン３に流入する排ガスの流量を増加させる。これにより、インペラ３ａの回転数が増加し、それに伴いインペラ２ａの回転数が増加するので、実吸気圧が上昇する。一方、後者が前者よりも大きい場合には、電磁弁３４によってウェストゲート流路１７の開度を大きくして、排気タービン３に流入する排ガスの流量を低下させる。これにより、インペラ３ａの回転数が低下し、それに伴いインペラ２ａの回転数が低下するので、実吸気圧が低下する。 The value detected by the pressure sensor 15 corresponds to the pressure of intake air sucked into each cylinder of the engine 10 (hereinafter, actual intake pressure). Therefore, the ECU 18 compares the required supercharging pressure with the actual intake pressure, and when the former is larger than the latter, the opening of the wastegate flow path 17 is reduced by the electromagnetic valve 34 and flows into the exhaust turbine 3. Increase the flow rate of exhaust gas. As a result, the rotational speed of the impeller 3a increases, and the rotational speed of the impeller 2a increases accordingly, so that the actual intake pressure increases. On the other hand, when the latter is larger than the former, the opening degree of the waste gate flow path 17 is increased by the electromagnetic valve 34 to reduce the flow rate of the exhaust gas flowing into the exhaust turbine 3. As a result, the rotational speed of the impeller 3a decreases, and the rotational speed of the impeller 2a decreases accordingly, so that the actual intake pressure decreases.
　次に、ＥＣＵ１８が電磁弁３４によってウェストゲート流路１７の開度を制御する動作について説明する。
　シリンダ部３２内において、ばね３１が仕切部材３５を押圧することにより、ウェストゲートバルブ２１にばね３１の弾性力が伝達されて、弁体２２が弁座５に向かう方向にウェストゲートバルブ２１が移動する。電磁弁３４を全開にすると、吐出側流路１２内の吸気の一部が第１室３２ａ内及び第２室３２ｂ内に流入し、第１室３２ａ内の圧力と第２室３２ｂ内の圧力とが同じになって釣り合うため、ウェストゲートバルブ２１に加わる力はばね３１の弾性力のみとなる。ウェストゲートバルブ２１に加わる力がばね３１の弾性力のみであれば、弁体２２が弁座５に当接し、ウェストゲート流路１７を閉止する。すなわち、ウェストゲート流路１７の開度がゼロになる。 Next, the operation in which the ECU 18 controls the opening degree of the waste gate channel 17 by the electromagnetic valve 34 will be described.
In the cylinder portion 32, the spring 31 presses the partition member 35, whereby the elastic force of the spring 31 is transmitted to the waste gate valve 21, and the waste gate valve 21 moves in the direction in which the valve body 22 faces the valve seat 5. To do. When the electromagnetic valve 34 is fully opened, part of the intake air in the discharge side flow passage 12 flows into the first chamber 32a and the second chamber 32b, and the pressure in the first chamber 32a and the pressure in the second chamber 32b. Are equal to each other, and the force applied to the wastegate valve 21 is only the elastic force of the spring 31. If the force applied to the wastegate valve 21 is only the elastic force of the spring 31, the valve element 22 contacts the valve seat 5 and closes the wastegate flow path 17. That is, the opening degree of the waste gate channel 17 becomes zero.
　ウェストゲート流路１７の開度をゼロから増加するためには、ＥＣＵ１８は電磁弁３４の開度が小さくなるように調節して、第２分岐管部３３ｂの流路面積を減少させる。第２分岐管部３３ｂの流路面積が減少すると、電磁弁３４における圧力損失によって、第２室３２ｂ内の圧力は第１室３２ａ内の圧力よりも小さくなる。そうすると、仕切部材３５を介して第１室３２ａと第２室３２ｂとの間に差圧が生じ、この差圧に基づく圧力が、仕切部材３５を介して、ばね３１の弾性力の方向と対向する方向にばね３１に加えられる。この圧力はばね３１の弾性力の一部と相殺するので、ばね３１からウェストゲートバルブ２１に付与される弾性力が小さくなる。 In order to increase the opening degree of the waste gate flow path 17 from zero, the ECU 18 adjusts the opening degree of the electromagnetic valve 34 so as to decrease the flow area of the second branch pipe portion 33b. When the flow path area of the second branch pipe portion 33b decreases, the pressure in the second chamber 32b becomes smaller than the pressure in the first chamber 32a due to the pressure loss in the electromagnetic valve 34. Then, a differential pressure is generated between the first chamber 32 a and the second chamber 32 b via the partition member 35, and the pressure based on this differential pressure is opposed to the direction of the elastic force of the spring 31 via the partition member 35. To the spring 31 in the direction of Since this pressure cancels out part of the elastic force of the spring 31, the elastic force applied from the spring 31 to the wastegate valve 21 is reduced.
　ＥＣＵ１８が電磁弁３４の開度を小さくするように調節することにより、この差圧に基づく圧力をばね３１の弾性力よりも大きくすることができる。そうすると、ばね３１は仕切部材３５に押圧されて縮み、その結果、ばね３１が縮む方向にウェストゲートバルブ２１が移動するので、弁体２２が弁座５から離れていき、ウェストゲート流路１７の開度がゼロから上昇する。一方、ＥＣＵ１８が電磁弁３４の開度を大きくするように調整することにより、この差圧が小さくなるので、ばね３１によってウェストゲートバルブ２１に付与される弾性力が増加し、ウェストゲート流路１７の開度が低下する。 When the ECU 18 adjusts the opening of the electromagnetic valve 34 to be small, the pressure based on this differential pressure can be made larger than the elastic force of the spring 31. Then, the spring 31 is pressed and contracted by the partition member 35, and as a result, the waste gate valve 21 moves in the direction in which the spring 31 contracts, so that the valve body 22 moves away from the valve seat 5, and the waste gate channel 17 The opening increases from zero. On the other hand, the ECU 18 adjusts the opening degree of the solenoid valve 34 to increase the differential pressure, so that the elastic force applied to the wastegate valve 21 by the spring 31 increases, and the wastegate flow path 17. The degree of opening decreases.
　電磁弁３４の開度を調節して第１室３２ａと第２室３２ｂとの間の差圧を調整することで、ウェストゲート流路１７の開度を制御することができるので、特にエンジン１０が高回転数の状態で急加速を行うような場合に、電磁弁３４を開くことでウェストゲート流路１７を閉止することができる。その結果、過度反応性が良好となり、アクセル８の追従が早くなる。 Since the opening degree of the wastegate channel 17 can be controlled by adjusting the differential pressure between the first chamber 32a and the second chamber 32b by adjusting the opening degree of the electromagnetic valve 34, the engine 10 in particular. When sudden acceleration is performed at a high rotational speed, the waste gate channel 17 can be closed by opening the electromagnetic valve 34. As a result, the excessive reactivity becomes good and the follow-up of the accelerator 8 is accelerated.
　ウェストゲート流路１７を全開にする場合には、電磁弁３４が逃し配管３６を開くことによって第２室３２ｂ内の吸気を逃し配管３６を介してウェストゲート流路１７に排気する。その結果、第１室３２ａと第２室３２ｂとの間の差圧が最大になるので、ウェストゲート流路１７が全開となる。 When the waste gate flow path 17 is fully opened, the electromagnetic valve 34 opens the escape pipe 36 to release the intake air in the second chamber 32b to the waste gate flow path 17 through the pipe 36. As a result, the differential pressure between the first chamber 32a and the second chamber 32b is maximized, so that the wastegate channel 17 is fully opened.
　このように、シリンダ部３２内において、コンプレッサ２の吐出側流路１２内の圧力により形成された差圧に基づく圧力がばね３１に加えられることによって、ウェストゲートバルブ２１に付与される弾性力が調節されるので、ウェストゲート流路１７の開度調整の制御性を向上することができる。特に、ウェストゲート流路１７が微小開度状態である場合の開度の制御性が良好となり、エンジン１０が高負荷運転状態である場合の出力変動を低減することができる。 Thus, in the cylinder part 32, the elastic force given to the wastegate valve 21 is applied by applying a pressure based on the differential pressure formed by the pressure in the discharge side flow path 12 of the compressor 2 to the spring 31. Since it is adjusted, the controllability of opening degree adjustment of the wastegate flow path 17 can be improved. In particular, the controllability of the opening degree when the wastegate channel 17 is in the minute opening state becomes good, and the output fluctuation when the engine 10 is in the high load operation state can be reduced.
　また、ウェストゲートバルブ２１が、弁体２２と仕切部材３５とをロッド２３によって連結する構成を有していることにより、ウェストゲートバルブ２１は、ばね３１の弾性力の方向に直線的に移動するグローブバルブ構造となっているので、煤に起因する固着リスクを低減することができる。 Further, since the wastegate valve 21 has a configuration in which the valve body 22 and the partition member 35 are connected by the rod 23, the wastegate valve 21 moves linearly in the direction of the elastic force of the spring 31. Since it has a globe valve structure, the risk of sticking due to wrinkles can be reduced.
　また、ノッキング等の発生によって排気タービン３の入口圧力が急上昇した場合、その圧力によって弁体２２が押されて、ウェストゲート流路１７の開度が増加する方向にウェストゲートバルブ２１を迅速に移動することができる。このため、コンプレッサ２のインペラ２ａの過回転によるインペラ２ａの破損及び焼き付きの発生を抑制することができる。 Further, when the inlet pressure of the exhaust turbine 3 suddenly increases due to the occurrence of knocking or the like, the valve body 22 is pushed by the pressure, and the wastegate valve 21 is quickly moved in the direction in which the opening degree of the wastegate passage 17 increases. can do. For this reason, it is possible to suppress the impeller 2a from being damaged and seized due to the excessive rotation of the impeller 2a of the compressor 2.
（実施形態２）
　次に、実施形態２に係るウェストゲートバルブ装置について説明する。実施形態２に係るウェストゲートバルブ装置は、実施形態１に対して、弾性部材の構成を変更したものである。尚、実施形態２において、実施形態１の構成要件と同じものは同じ参照符号を付し、その詳細な説明は省略する。 (Embodiment 2)
Next, a wastegate valve device according to the second embodiment will be described. The wastegate valve device according to the second embodiment is obtained by changing the configuration of the elastic member with respect to the first embodiment. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
　図２に示されるように、ばね３１は、直列に配置された第１ばね３１ａ及び第２ばね３１ｂを含んでいる。ばね３１は、第１ばね３１ａのピッチ間隔が第２ばね３１ｂのピッチ間隔よりも大きい不等ピッチコイルばねである。第１ばね３１ａのピッチ間隔が第２ばね３１ｂのピッチ間隔よりも大きいことで、第１ばね３１ａのばね定数ｋ１は、第２ばね３１ｂのばね定数ｋ２よりも小さく（ｋ１＜ｋ２）なっている。第１ばね３１ａと第２ばね３１ｂとは、一端同士が互いに接続されてもよいし、一端同士が互いに接続されずに接触するようにしてもよい。その他の構成は実施形態１と同じである。 As shown in FIG. 2, the spring 31 includes a first spring 31a and a second spring 31b arranged in series. The spring 31 is an unequal pitch coil spring in which the pitch interval of the first springs 31a is larger than the pitch interval of the second springs 31b. By pitch interval of the first spring 31a is greater than the pitch of the second spring 31b, the spring constant k 1 of the first spring 31a is smaller than the spring constant k 2 of the second spring 31b (k 1 <k 2 It has become. The first spring 31a and the second spring 31b may be connected to each other at one end, or may be in contact with each other without being connected to each other. Other configurations are the same as those of the first embodiment.
　不等ピッチコイルばねであるばね３１のばね特性を図３のグラフに示す。ばね３１に荷重が加えられてばね３１が縮む際、ばね３１の縮み量が小さい範囲、すなわち縮み量が０からｘ１までの間は、ばね定数が小さい第１ばね３１ａが主に縮む。ここで、縮み量ｘ１は、第１ばね３１ａが主に縮んでいき、第１ばね３１ａのピッチ間隔が第２ばね３１ｂのピッチ間隔と同等になったときのばね３１全体の縮み量に相当する。縮み量がｘ１を超えると、第１ばね３１ａ及び第２ばね３１ｂが同じ様に縮むので、この範囲では、ばね定数ｋ１とばね定数ｋ２との間のばね定数でばね３１が縮むようになる。 The graph of FIG. 3 shows the spring characteristics of the spring 31 which is an unequal pitch coil spring. When the spring 31 load is applied to the spring 31 is contracted, shrinkage amount is small range of spring 31, between that is, from the contraction amount is 0 to x 1, the first spring 31a spring constant is small contracts mainly. Here, contraction amount x 1, the first spring 31a is gradually is primarily contracted, pitch interval of the first spring 31a is equivalent to the amount of contraction of the whole spring 31 when it becomes equal to the pitch of the second spring 31b To do. When the amount of shrinkage is more than x 1, since the first spring 31a and the second spring 31b is contracted in the same way, in this range, as the spring 31 is contracted by the spring constant between the spring constant k 1 and the spring constant k 2 Become.
　その結果、図３に示されるように、縮み量が０からｘ１までの範囲の方が、縮み量がｘ１を超える範囲よりも、ばね３１の縮み量に対するばね３１に加えられる荷重が小さくなる。これは、ばね３１に加えられる荷重の増加量が同じでも、縮み量が０からｘ１までの範囲の方が、縮み量がｘ１を超える範囲よりも縮み量の変化が大きいことを意味する。ばね３１の縮み量が０のときにばね３１が最も伸びた状態であるので、このときにウェストゲート流路１７（図１参照）の開度が全閉となる。そうすると、ウェストゲート流路１７が微小開度状態である場合に、ばね３１に加えられる荷重の変化が小さくてもウェストゲートバルブ２１（図１参照）の移動量は、ウェストゲート流路１７の開度が大きい場合に比べて大きくなる。その結果、ウェストゲート流路１７が微小開度状態である場合に、ウェストゲートバルブ２１の移動量の制御を細かく行うことができるようになるので、ウェストゲート流路１７の開度の制御性を向上することができる。 As a result, as shown in FIG. 3, it ranges from the contraction amount is 0 to x 1 is than the range contraction amount exceeds x 1, the load applied to the spring 31 against the contraction of the spring 31 is small Become. This also increase the amount of load applied to the spring 31 is the same, the amount of shrinkage is more in the range from 0 to x 1, the amount of shrinkage means that the change in the amount of shrinkage than the range above x 1 is greater . Since the spring 31 is in the most extended state when the amount of contraction of the spring 31 is 0, the opening degree of the wastegate channel 17 (see FIG. 1) is fully closed at this time. As a result, when the wastegate channel 17 is in a very small opening state, the movement amount of the wastegate valve 21 (see FIG. 1) can be reduced even if the load applied to the spring 31 is small. It becomes larger than when the degree is large. As a result, when the wastegate channel 17 is in a minute opening state, the amount of movement of the wastegate valve 21 can be finely controlled. Can be improved.
　実施形態２では、第１ばね３１ａ及び第２ばね３１ｂそれぞれのピッチ間隔を異ならせることによって、それぞれのばね定数を異ならせていたが、このような形態に限定するものではない。第１ばね３１ａ及び第２ばね３１ｂそれぞれの直径の大きさを異ならせることによっても、それぞれのばね定数を異ならせることができるし、第１ばね３１ａ及び第２ばね３１ｂの一方に焼き入れをしてそれぞれの堅さを異ならせることによっても、それぞれのばね定数を異ならせることができる。 In Embodiment 2, the respective spring constants are made different by making the pitch intervals of the first spring 31a and the second spring 31b different, but it is not limited to such a form. The spring constants can also be made different by making the diameters of the first spring 31a and the second spring 31b different, and one of the first spring 31a and the second spring 31b can be quenched. The spring constants can also be made different by making the respective stiffnesses different.
　実施形態１及び２では、電磁弁３４は第２分岐管部３３ｂのみに設けられていたが、第１分岐管部３３ａにも電磁弁３４を設けて、各電磁弁３４の開度を調節することにより、シリンダ部３２内の差圧を調整するようにしてもよい。 In the first and second embodiments, the electromagnetic valve 34 is provided only in the second branch pipe portion 33b. However, the electromagnetic valve 34 is also provided in the first branch pipe portion 33a to adjust the opening degree of each electromagnetic valve 34. Thus, the differential pressure in the cylinder part 32 may be adjusted.
　実施形態１及び２では、弾性部材はばね３１であったが、ばねに限定するものではない。弾性力を生じるものであれば、任意の部材を用いることができる。 In the first and second embodiments, the elastic member is the spring 31, but is not limited to the spring. Any member can be used as long as it generates an elastic force.
１　ターボチャージャ
２　コンプレッサ
２ａ　（コンプレッサの）インペラ
２ｂ　コンプレッサハウジング
３　排気タービン
３ａ　（排気タービンの）インペラ
３ｂ　タービンハウジング
４　回転軸
５　弁座
８　アクセル
９　アクセル開度センサ
１０　エンジン
１２　（コンプレッサの）吐出側流路
１３　（排気タービンの）吸入側流路
１４　インタークーラ
１５　圧力センサ（圧力検出部）
１６　（排気タービンの）吐出側流路
１７　ウェストゲート流路
１８　ＥＣＵ（制御部）
２０　ウェストゲートバルブ装置
２１　ウェストゲートバルブ
２２　弁体
２３　ロッド
３０　駆動機構
３１　ばね（弾性部材）
３１ａ　第１ばね
３１ｂ　第２ばね
３２　シリンダ部
３２ａ　第１室
３２ｂ　第２室
３３　連通管
３３ａ　第１分岐管部
３３ｂ　第２分岐管部
３４　電磁弁（差圧調整弁）
３５　仕切部材
３６　逃し配管 1 turbocharger 2 compressor 2a (compressor) impeller 2b compressor housing 3 exhaust turbine 3a (exhaust turbine) impeller 3b turbine housing 4 rotary shaft 5 valve seat 8 accelerator 9 accelerator opening sensor 10 engine 12 (compressor) discharge side flow Path 13 (exhaust turbine) suction side flow path 14 intercooler 15 pressure sensor (pressure detector)
16 Discharge side flow path 17 (of exhaust turbine) Waste gate flow path 18 ECU (control unit)
20 Wastegate valve device 21 Wastegate valve 22 Valve body 23 Rod 30 Drive mechanism 31 Spring (elastic member)
31a 1st spring 31b 2nd spring 32 Cylinder part 32a 1st chamber 32b 2nd chamber 33 Communication pipe 33a 1st branch pipe part 33b 2nd branch pipe part 34 Solenoid valve (differential pressure regulation valve)
35 Partition member 36 Relief piping

Claims (7)

  1. 　ターボチャージャの排気タービンのタービンハウジングに形成されたウェストゲート流路の開度を制御するウェストゲートバルブであって、前記タービンハウジングに形成された弁座に当接可能に構成された弁体を含むウェストゲートバルブと、
    　前記ウェストゲートバルブを駆動する駆動機構と
    を備え、
    　前記駆動機構は、
    　前記弁体を前記弁座に向けて押し付ける弾性力を前記ウェストゲートバルブに付与可能に構成された弾性部材と、
    　前記弾性部材を収容するシリンダ部と、
    　前記ターボチャージャのコンプレッサの吐出側流路と前記シリンダ部の内部とを連通する連通管と、
    　前記コンプレッサの前記吐出側流路内の圧力によって前記シリンダ部内に差圧を形成するとともに調整する差圧調整弁と
    を備え、
    　前記シリンダ部内において前記差圧に基づく圧力が前記弾性部材に加えられることによって、前記ウェストゲートバルブに付与される前記弾性力が調節されるウェストゲートバルブ装置。     A wastegate valve for controlling an opening degree of a wastegate passage formed in a turbine housing of an exhaust turbine of a turbocharger, comprising a valve body configured to contact a valve seat formed in the turbine housing Westgate valve,
    A drive mechanism for driving the wastegate valve;
    The drive mechanism is
    An elastic member configured to impart an elastic force to the wastegate valve to press the valve body toward the valve seat;
    A cylinder portion for accommodating the elastic member;
    A communication pipe communicating the discharge side flow path of the compressor of the turbocharger and the inside of the cylinder part;
    A differential pressure adjusting valve for adjusting and adjusting the differential pressure in the cylinder portion by the pressure in the discharge-side flow path of the compressor;
    A wastegate valve device in which the elastic force applied to the wastegate valve is adjusted by applying a pressure based on the differential pressure to the elastic member in the cylinder portion.
  2. 　前記シリンダ部内には、前記弾性部材を収容する第１室と、前記ウェストゲートバルブの一部を収容する第２室とに前記シリンダ部内を仕切るとともに前記シリンダ部内で前記差圧に基づく圧力及び前記弾性力に応じてスライド可能な仕切部材が設けられ、
    　前記連通管は、
    　前記第１室に連通する第１分岐管部と、
    　前記第２室に連通する第２分岐管部と
    を含み、
    　前記差圧調整弁は、前記第２分岐管部の流路面積を調整することによって、前記第１室内の圧力及び前記第２室内の圧力を互いに異ならせて前記差圧を形成するとともに前記第１室内の圧力と前記第２室内の圧力との差を変化させて前記差圧を調整する、請求項１に記載のウェストゲートバルブ装置。     In the cylinder part, the cylinder part is partitioned into a first chamber containing the elastic member and a second chamber containing a part of the wastegate valve, and the pressure based on the differential pressure in the cylinder part and the A partition member that can slide according to the elastic force is provided,
    The communication pipe is
    A first branch pipe portion communicating with the first chamber;
    A second branch pipe portion communicating with the second chamber,
    The differential pressure adjusting valve adjusts a flow passage area of the second branch pipe portion to make the pressure in the first chamber and the pressure in the second chamber different from each other, thereby forming the differential pressure. The wastegate valve device according to claim 1, wherein the differential pressure is adjusted by changing a difference between a pressure in one chamber and a pressure in the second chamber.
  3. 　前記ウェストゲートバルブは、前記弁体と前記仕切部材とを連結するロッドをさらに含む、請求項２に記載のウェストゲートバルブ装置。 The waste gate valve device according to claim 2, wherein the waste gate valve further includes a rod that connects the valve body and the partition member.
  4. 　前記コンプレッサの吐出側の圧力を検出する圧力検出部をさらに備え、
    　前記差圧調整弁が前記圧力検出部による検出値に基づいて前記差圧を調整することによって、前記ウェストゲートバルブが前記ウェストゲート流路の開度を制御する、請求項１～３のいずれか一項に記載のウェストゲートバルブ装置。     A pressure detector for detecting the pressure on the discharge side of the compressor;
    4. The opening pressure of the waste gate flow path is controlled by the waste gate valve according to claim 1, wherein the differential pressure adjusting valve adjusts the differential pressure based on a value detected by the pressure detection unit. The wastegate valve device according to one item.
  5. 　前記弾性部材は、直列に配置された第１ばね及び第２ばねを含み、
    　前記第１ばねのばね定数と第２ばねのばね定数とは互いに異なる、請求項１～４のいずれか一項に記載のウェストゲートバルブ装置。     The elastic member includes a first spring and a second spring arranged in series,
    The wastegate valve device according to any one of claims 1 to 4, wherein a spring constant of the first spring and a spring constant of the second spring are different from each other.
  6. 　前記弾性部材は、互いにコイルピッチが異なる前記第１ばね及び前記第２ばねを含む不等ピッチコイルばねである、請求項５に記載のウェストゲートバルブ装置。 The wastegate valve device according to claim 5, wherein the elastic member is an unequal pitch coil spring including the first spring and the second spring having different coil pitches.
  7. 　請求項１～６のいずれか一項に記載のウェストゲートバルブ装置を備えるターボチャージャ。 A turbocharger comprising the wastegate valve device according to any one of claims 1 to 6.
PCT/JP2018/014967 2018-04-09 2018-04-09 Waste gate valve device and turbocharger provided with said waste gate valve device WO2019198135A1 (en)

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