WO2010058788A1 - Sliding nozzle variable turbocharger - Google Patents
Sliding nozzle variable turbocharger Download PDFInfo
- Publication number
- WO2010058788A1 WO2010058788A1 PCT/JP2009/069546 JP2009069546W WO2010058788A1 WO 2010058788 A1 WO2010058788 A1 WO 2010058788A1 JP 2009069546 W JP2009069546 W JP 2009069546W WO 2010058788 A1 WO2010058788 A1 WO 2010058788A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- nozzle
- exhaust
- variable turbocharger
- slide
- type variable
- Prior art date
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- 230000000903 blocking effect Effects 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims description 2
- 238000002347 injection Methods 0.000 abstract 3
- 239000007924 injection Substances 0.000 abstract 3
- 230000006835 compression Effects 0.000 abstract 1
- 238000007906 compression Methods 0.000 abstract 1
- 238000004891 communication Methods 0.000 description 17
- 230000008929 regeneration Effects 0.000 description 11
- 238000011069 regeneration method Methods 0.000 description 11
- 239000013618 particulate matter Substances 0.000 description 6
- 238000000746 purification Methods 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 230000004308 accommodation Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- 230000005856 abnormality Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000004071 soot Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
- F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/167—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes of vanes moving in translation
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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
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
Definitions
- the present invention relates to a slide nozzle type variable turbocharger.
- an exhaust gas purification device in the exhaust path of a diesel engine.
- an exhaust gas purifying apparatus there is one provided with a soot filter that captures particulate matter (PM) contained in exhaust gas.
- PM particulate matter
- a suit filter if the amount of trapped PM exceeds a predetermined amount, clogging occurs and the filter does not function as a filter.
- the regeneration temperature required to reliably burn the PM is usually easily obtained when the engine is operated at a medium load or higher, but becomes low at no load or low load operation. May not be reached.
- a turbocharger that supercharges intake air by utilizing fluid energy of exhaust gas has been known.
- a variable turbocharger is also known in which the flow area of the exhaust gas to the exhaust turbine can be made variable. Therefore, in a no-load or low-load operation that does not require supercharging, the exhaust gas opening to the exhaust turbine is intentionally reduced compared to that during normal operation, and the exhaust pressure is increased at the same time. It has been proposed to raise the exhaust gas temperature above the regeneration temperature.
- the structure of a nozzle portion for injecting exhaust gas into an exhaust turbine is formed by a pair of exhaust introduction walls facing each other, and one exhaust introduction wall is connected to the other exhaust introduction wall
- the gap opening area of the nozzle part of the exhaust introduction wall
- Patent Document 1 by moving one exhaust introduction wall toward the other position to the maximum proximity position, the flow of exhaust gas is suppressed and the exhaust temperature is raised to the regeneration temperature.
- the exhaust pressure on the upstream side of the variable turbocharger also increases, so if the exhaust pressure becomes higher than necessary, the engine exhaust valve will malfunction. It can happen. And because of the need to avoid the occurrence of abnormalities on the engine side, if the exhaust pressure rises too much before the exhaust gas temperature reaches the regeneration temperature, it must be returned to the direction of widening the opening area of the nozzle portion, and the exhaust gas The temperature cannot be raised to the regeneration temperature.
- Patent Document 1 adopts a structure in which the exhaust gas guided to the exhaust introduction path is bypassed to the downstream side of the nozzle portion when the exhaust introduction wall is positioned at the maximum proximity position. By bypassing the exhaust gas, the exhaust gas temperature is reliably raised to the regeneration temperature while preventing the exhaust pressure on the upstream side from rising excessively.
- the exhaust introduction wall includes a slidable nozzle ring, and the nozzle ring and the surrounding turbine housing are sealed by a seal ring provided on the inner surface of the turbine housing.
- the nozzle ring is provided with a slit for bypassing the exhaust gas.
- the nozzle ring slides in the forward / backward direction as long as the slit does not exceed the seal ring, so the exhaust introduction path and the downstream side of the nozzle portion are not communicated by the slit.
- the slit moves to the nozzle part side of the seal ring, and the exhaust introduction path communicates with the downstream side of the nozzle part through the slit. And exhaust gas bypasses.
- Patent Document 1 exhaust gas is bypassed through the sliding portion of the nozzle ring, and whether or not to bypass is determined by the position of the nozzle ring with respect to the seal ring. If there is a minute gap between the seal ring and the nozzle ring due to wear of the seal surface, exhaust gas always bypasses through the gap regardless of the position of each other. There is concern that the performance during operation will be reduced.
- An object of the present invention is to provide a variable turbocharger that can prevent exhaust gas from bypassing during normal operation due to aging of components and the like and maintain good performance.
- the slide nozzle type variable turbocharger of the present invention includes a nozzle portion formed by a pair of exhaust introduction walls facing each other, a nozzle ring forming one of the exhaust introduction walls, and the nozzle ring as the other exhaust.
- a slide mechanism for advancing and retreating with respect to the introduction wall a bypass passage for communicating the nozzle portion and an exhaust outlet for discharging exhaust gas downstream of the turbine wheel; a valve member for communicating and blocking the bypass passage; and the nozzle And a pressing portion provided on the ring, wherein the bypass passage is communicated when the valve member is pressed by the pressing portion.
- the bypass flow path is formed in an annular recess that accommodates the nozzle portion.
- the nozzle ring is provided with a plurality of nozzle vanes along a circumferential direction, and the pressing portion protruding in the advancing direction of the nozzle vanes. .
- the slide mechanism is provided with a support rod that is connected to the nozzle ring and advances and retracts the nozzle ring, and the valve member is disposed at a position corresponding to the support rod. It is preferable that
- the slide mechanism is preferably driven by a hydraulic actuator.
- the valve member may be set to be opened and closed by the pressing portion at a position where the nozzle ring is closest to the other exhaust introduction wall.
- exhaust gas can be bypassed to the exhaust outlet side without being effectively injected from the nozzle part to the turbine wheel, and before the exhaust gas temperature reaches the regeneration temperature of the suit filter, It is possible to prevent the exhaust pressure from rising excessively.
- the valve member opens and closes by the pressing part that moves forward and backward with the nozzle ring, there is no worry of being affected by wear of the sliding part, etc., and it is possible to prevent the exhaust gas from bypassing during steady operation of the engine, It can be maintained well. It should be noted that a large amount of exhaust gas that does not cause the turbine wheel to work flows into the suit filter while maintaining its temperature at or above the regeneration temperature, and regeneration with the suit filter can be reliably performed.
- the exhaust gas can be guided to the bypass flow path from many positions in the circumferential direction, and the exhaust gas can be discharged efficiently.
- the length dimension as a press part can be shortened, the intensity
- valve member at a position corresponding to the support rod of the slide mechanism, it is possible to prevent the nozzle ring from being distorted while the valve member is being pressed by the pressing portion, and also to improve durability.
- the position of the nozzle ring can be controlled more accurately.
- the pressing portion can be pressed with a larger pressing force.
- the valve member can be reliably opened and closed by the hydraulic actuator even when the bypass flow path is blocked by a large force by the valve member.
- the bypass flow path can be closed with a large force of the valve member, there is no concern that the on-off valve will open due to the pressure of the exhaust gas, such as when exhaust gas does not want to escape through the bypass flow path.
- the flow path can be reliably blocked.
- the hydraulic actuator may have a configuration in which the position of the nozzle ring is feedback-controlled by a hydraulic servo mechanism, or in which feed-forward control is performed without using the hydraulic servo mechanism.
- FIG. 1 is a perspective view of a variable turbocharger according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the variable turbocharger and a cross-sectional view taken along arrow II-II in FIG. 1.
- FIG. 3 is a cross-sectional view showing the main part of the slide mechanism, and is a cross-sectional view taken along arrow III-III in FIG.
- FIG. 4 is a cross-sectional view taken along arrow IV-IV in FIG. 2.
- Sectional drawing which expands and shows the principal part of 1st Embodiment.
- FIG. 6 is a cross-sectional view taken along arrow VI-VI in FIG. 5.
- FIG. 7 is a cross-sectional view taken along arrow VII-VII in FIG. 6.
- FIG. 6 is a view seen from arrows VIII-VIII in FIG. 5. The whole perspective view which shows a valve member. Sectional drawing which shows the principal part of 2nd Embodiment of this invention.
- FIG. 1 is a perspective view of a slide nozzle type variable turbocharger 1 according to a first embodiment of the present invention
- FIG. 2 is a cross-sectional view of the variable turbocharger 1, and a cross-section taken along arrow II-II in FIG. FIG. 1 and 2
- the variable turbocharger 1 includes a turbine 2 on the right side in the drawing, a compressor 3 on the left side, and a hydraulic servo drive device 40 between the turbine 2 and the compressor 3. Not attached to the engine body.
- an exhaust gas purification device (not shown) having a PM capture suit filter is provided in the middle of the exhaust path of the engine provided with the variable turbocharger 1 of the present embodiment.
- a turbine wheel 5 is accommodated in the turbine housing 4 on the turbine 2 side, and a compressor impeller 7 is accommodated in the compressor housing 6 on the compressor 3 side.
- a shaft 8 is provided integrally with the turbine wheel 5, and a compressor impeller 7 is attached to the tip of the shaft 8.
- the shaft 8 is rotatably supported by the center housing 9. Therefore, the rotation of the turbine wheel 5 rotated by the exhaust gas is transmitted to the compressor impeller 7 via the shaft 8, and the intake air is compressed and supercharged by the rotation of the compressor impeller 7.
- the turbine housing 4 is provided with a volute-shaped exhaust introduction path 11 for introducing exhaust gas from the engine body.
- a nozzle portion 12 for ejecting exhaust gas to the turbine wheel 5 side is continuously provided in the circumferential direction, and the exhaust gas ejected from the nozzle portion 12 rotates the turbine wheel 5. It is exhausted from the exhaust outlet 13 later.
- the nozzle portion 12 is formed by a pair of exhaust introduction walls 14 and 15 that face each other.
- One exhaust introduction wall 14 is formed by a side surface 17 of a nozzle ring 16 having a U-shaped cross section.
- the nozzle ring 16 is housed in an annular housing space 18 provided in the center housing 9.
- the housing space 18 and the nozzle portion 12 side are sealed by a pair of seal rings 18A and 18B provided in the center housing 9.
- a plurality of nozzle vanes 19 projecting toward the other exhaust introduction wall 15 side are attached to the side surface 17 of the nozzle ring 16 at equal circumferential intervals.
- the other exhaust introduction wall 15 is formed on the shroud plate 22.
- the shroud plate 22 is formed with a plurality of cutout holes 23 through which the nozzle vanes 19 of the nozzle ring 16 are inserted along the circumferential direction. By inserting each nozzle vane 19 through the cutout hole 23, the tip of each nozzle vane 19 is shroud.
- the plate 22 is accommodated in an annular recess 21 on the back side. In such a structure, by moving the nozzle ring 16 forward and backward by the slide mechanism 20, the exhaust introduction wall 14 is moved closer to and away from the exhaust introduction wall 15, and the opening area as the nozzle opening degree of the nozzle portion 12 is changed. .
- FIG. 3 is a cross-sectional view showing the main part of the slide mechanism 20, and is a cross-sectional view taken along arrow III-III in FIG. 4 is a cross-sectional view taken along arrow IV-IV in FIG. 3 and 4,
- the slide mechanism 20 has a structure for moving the nozzle ring 16 forward and backward by rotationally driving a drive shaft 24 inserted through the lower side of the center housing 9.
- a pair of arms 25, 25 extending in an arc shape upward is fixed at an intermediate position in the axial direction of the drive shaft 24.
- a pin 26 protruding outward in the horizontal direction is attached to the distal end side of each arm 25, and a slider 27 is fitted into the pin 26.
- the slider 27 is slidably fitted in a sliding groove 29 on the base end side of the support rod 28 parallel to the shaft 8 described above.
- the tip of the support rod 28 is joined to the back side of the nozzle ring 16.
- the arm 25 swings along the axial direction of the shaft 8, the support rod 28 moves to move the nozzle ring 16, and one exhaust introduction wall 14 becomes the other exhaust introduction wall 15. It will advance and retreat. That is, the nozzle ring 16 is closely spaced from the shroud plate 22.
- the drive shaft 24 of the slide mechanism 20 is rotationally driven by a hydraulic servo drive device 40 via an arm 31 provided at the end thereof.
- the hydraulic servo drive device 40 has a structure that rotates the drive shaft 24 by moving the servo piston 41 up and down.
- the outer periphery of the servo piston 41 is provided with a sliding groove 33 orthogonal to the axial direction, and the arm 31 on the drive shaft 24 side is provided with a pin 34 protruding to the sliding groove 33 side.
- a slider 35 is fitted into the pin 34, and the slider 35 is slidably fitted into the sliding groove 33.
- the slide mechanism 20 is driven as described above, the support rod 28 moves, and the nozzle ring 16 advances and retreats with respect to the shroud plate 22, whereby the nozzle of the variable turbocharger 1 is moved.
- the nozzle opening degree of the part 12 is adjusted.
- the side surface 17 of the nozzle ring 16 is provided with a communication opening 16A (FIG. 2) that allows the nozzle portion 12 and the accommodation space 18 to communicate with each other. Due to the communication opening 16A, when the nozzle ring 16 advances and retreats, the internal pressure in the accommodation space 18 and the static pressure acting on the side surface 17 become equal, and the nozzle ring 16 slides smoothly.
- FIG. 5 is an enlarged cross-sectional view showing a main part of the present embodiment.
- 6 is a cross-sectional view taken along arrows VI-VI in FIG. 5
- FIG. 7 is a cross-sectional view taken along arrows VII-VII in FIG. 6
- FIG. 8 is a view taken from arrows VIII-VIII in FIG.
- the illustration of the shroud plate 22 is omitted.
- a hollow portion 51 that is recessed in the advancing direction of the nozzle ring 16 is provided in the recess 21.
- the hollow portion 51 has a long hole shape, and a pair is provided at a position corresponding to the support rod 28 (FIG. 4).
- a communication groove 52 continuous along the circumferential direction is provided in the inner peripheral portion of the exhaust outlet 13 of the turbine housing 4.
- the communication groove 52 and the hollow portion 51 communicate with each other through a pair of communication holes 53.
- the opening portion of the hollow portion 51 on the shroud plate 22 side is closed with a cover plate 54 that is curved corresponding to the shape of the recess 21.
- the cover plate 54 is provided with a rectangular opening 55, and at least one nozzle vane 19 faces the position of the opening 55.
- valve member 60 formed of a spring material is accommodated in the hollow portion 51. Therefore, the valve member 60 in the hollow portion 51 is also disposed at a position corresponding to the support rod 28 of the slide mechanism 20.
- the width dimension of the valve member 60 is substantially the same as the groove width dimension of the hollow portion 51, and there is no fear of displacement in the width direction when the valve member 60 is accommodated in the hollow portion 51.
- such a valve member 60 includes a leaf spring portion 61 formed in a V shape and an opening / closing piece 62 fixed to one piece of the leaf spring portion 61. ing.
- a round hole 63 is provided on the tip side of the other piece of the leaf spring part 61.
- the round hole 63 is provided at a position extending from the tip of one piece.
- a sleeve 64 is arranged at a position corresponding to the round hole 63 so as not to interfere with one piece and the opening / closing piece 62.
- the valve member 60 is fixed in the hollow portion 51 by a screw 65 that passes through the insertion hole 56, the sleeve 64, and the round hole 63 of the cover plate 54 and is screwed into the screw hole 57 on the back side of the hollow portion 51. .
- a pair of flow holes 66 are provided in the other piece of the leaf spring portion 61. As shown in FIGS. 6, 7, and 9, these flow holes 66 correspond to the above-described communication holes 53 that allow the hollow portion 51 and the communication groove 52 to communicate with each other. By providing the flow hole 66, there is no concern that the leaf spring portion 61 blocks the communication hole 53, and a good communication state between the hollow portion 51 and the communication groove 52 is ensured. As described above, when the valve member 60 is accommodated and fixed in the hollow portion 51, the opening / closing piece 62 is brought into contact with the cover plate 54 while being urged by the leaf spring portion 61 and closes the opening 55.
- a pressing portion 58 protruding along the advance direction of the nozzle ring 16 is provided at the tip of the nozzle vane 19 positioned facing the opening 55.
- the pressing portion 58 may be provided separately from the nozzle vane 19 and may be joined to the nozzle vane 19 by an appropriate joining means, or may be manufactured integrally with the nozzle vane 19 from the beginning.
- Such a pressing portion 58 is provided at the position where the nozzle ring 16 slides to the position closest to the exhaust introduction wall 15 as shown by the two-dot chain line position in FIGS. 5 and 6. Is pressed against the urging force of the leaf spring portion 61 (two-dot chain line in FIG. 9), and the opening 55 of the cover plate 54 is opened.
- the nozzle portion 12 communicates with the exhaust outlet 13 side through the gap between the shroud plate 22 and the nozzle vane 19, the concave portion 21, the hollow portion 51, the communication hole 53, and the communication groove 52. Most of the exhaust gas is discharged by bypassing the nozzle portion 12 without being injected into the turbine wheel 5. That is, in this embodiment, the bypass flow path 50 of the present invention is formed including the recess 21, and the valve member 60 is disposed so as to cut off the communication of the bypass flow path 50.
- variable turbocharger 1 during steady operation, the nozzle ring 16 slides within a range that does not reach the maximum proximity position, and the opening area of the nozzle portion 12 is adjusted according to the engine speed and load.
- the nozzle ring 16 is slid to the maximum proximity position, and the opening area of the nozzle portion 12 is minimized. Increase pressure.
- the pressing portion 58 provided in the predetermined nozzle vane 19 is pressed against the valve member 60 and pressed, and the opening 55 is opened to exhaust the exhaust gas into the nozzle portion. Bypass to the exhaust outlet 13 without passing through 12.
- the valve member 60 can be pressed with a sufficient pressing force against the urging force, and the opening 55 can be reliably opened.
- the hydraulic servo drive device 40 as a hydraulic actuator that generates a large driving force
- the nozzle ring 16 is slid to the maximum proximity position and stopped at the proximity position, for example, the nozzle ring
- a protruding stopper 16 ⁇ / b> B is provided on the 16 side, and it is necessary to stop the stopper 16 ⁇ / b> B by contacting the shroud plate 22.
- the stopper 16B comes into contact with the shroud plate 22 while maintaining a large driving force by the hydraulic servo drive device 40. May occur, which may affect durability and position control of the nozzle ring 16.
- the pressing portion 58 of the nozzle vane 19 starts to press the valve member 60, so that a part of the driving force of the hydraulic servo drive device 40 is pressed. It is used as a pressure, so that the driving force when the stopper 16B comes into contact with the shroud plate 22 can be reduced to eliminate the impact, and the durability and accuracy during position control can be improved.
- FIG. 10 shows a second embodiment of the present invention.
- the valve member 60 in the first embodiment includes the V-shaped leaf spring portion 61
- the valve member 70 of the present embodiment is a flat plate made entirely of a spring material, and is attached to the cover plate 54. It is fixed and functions as a reed valve.
- the valve member 70 is pressed by the pressing portion 58 provided on the nozzle vane 19.
- the hollow portion 51 and the exhaust outlet 13 are directly communicated with each other through the communication hole 53.
- the communication groove 52 is provided in the exhaust outlet 13 as in the first embodiment, and this communication is performed.
- the communication hole 53 may be communicated with the groove 52.
- valve members 60 and 70 are pressed by the pressing portion 58 provided in the nozzle vane 19, but even when such a pressing portion 58 is directly provided in the nozzle ring 16, Included in the invention.
- a configuration can be applied when the nozzle vane 19 is provided not on the nozzle ring 16 side but on the shroud plate 22 side. That is, a notch hole for avoiding interference with the nozzle vane 19 is provided on the nozzle ring 16 side, and the nozzle vane 19 penetrates into the accommodating space 18 through the notch hole as the nozzle ring 16 moves back and forth. This is the case.
- valve members 60 and 70 are not limited to the structure accommodated in the hollow portion 51 provided in the recess 21, and the hollow portion 51 is provided at an arbitrary position facing the nozzle ring 16 in the turbine housing 4.
- the valve members 60 and 70 may be accommodated in the hollow portion 51.
- exhaust gas flows into the recesses 21 from around all the nozzle vanes 19, the exhaust when the exhaust gas is bypassed by providing the hollow portions 51 (bypass channels 50) in the recesses 21. There is an effect that the efficiency can be improved.
- the present invention is an engine mounted on a construction machine, a civil engineering machine, a transportation vehicle, and a railway vehicle, and can be used effectively as a variable turbocharger for an engine that is used in combination with an exhaust gas purification device having a suit filter.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
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- General Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
Abstract
Disclosed is a sliding nozzle variable turbocharger (1) equipped with: a nozzle part (12) formed by a pair of opposing exhaust/injection walls (14, 15); a nozzle ring (16) that forms one exhaust/injection wall (14); a slide mechanism that causes the nozzle ring (16) to advance/retreat with respect to the other exhaust/injection wall (15); a bypass flow path (50) that connects the nozzle unit part (12) and an exhaust exit (13) that exhausts exhaust gas; a valve member (60) that connects/blocks the bypass flow path (50); and a compression part (58) that is used to open/close the valve member and that advances/retreats with the nozzle ring (16), making contact with/separating from the valve member (60).
Description
本発明は、スライドノズル形可変ターボ過給機に関する。
The present invention relates to a slide nozzle type variable turbocharger.
近年では、ディーゼルエンジンの排気経路中に排気ガス浄化装置を取り付けることが知られている。排気ガス浄化装置としては、排気ガス中に含まれるパーティキュレート・マター(particulate matter:PM)を捕捉するスーツフィルタ(soot filter)を備えたものがある。
スーツフィルタでは、PMの捕捉量が所定量を超えると目詰まりが生じ、フィルタとして機能しなくなるため、このような状況に近づくと、捕捉されたPMを排気ガスの熱を利用して燃焼、除去し、目詰まりが生じていない状態に再生することが行われる。
PMを確実に燃焼させるのに必要な再生温度は通常、エンジンが中負荷以上で運転されている場合には容易に得られるが、無負荷あるいは低負荷運転の場合には低温度となり、再生温度に達しない場合がある。 In recent years, it is known to install an exhaust gas purification device in the exhaust path of a diesel engine. As an exhaust gas purifying apparatus, there is one provided with a soot filter that captures particulate matter (PM) contained in exhaust gas.
In a suit filter, if the amount of trapped PM exceeds a predetermined amount, clogging occurs and the filter does not function as a filter. When approaching such a situation, the trapped PM is burned and removed using the heat of the exhaust gas. Then, reproduction is performed so that clogging does not occur.
The regeneration temperature required to reliably burn the PM is usually easily obtained when the engine is operated at a medium load or higher, but becomes low at no load or low load operation. May not be reached.
スーツフィルタでは、PMの捕捉量が所定量を超えると目詰まりが生じ、フィルタとして機能しなくなるため、このような状況に近づくと、捕捉されたPMを排気ガスの熱を利用して燃焼、除去し、目詰まりが生じていない状態に再生することが行われる。
PMを確実に燃焼させるのに必要な再生温度は通常、エンジンが中負荷以上で運転されている場合には容易に得られるが、無負荷あるいは低負荷運転の場合には低温度となり、再生温度に達しない場合がある。 In recent years, it is known to install an exhaust gas purification device in the exhaust path of a diesel engine. As an exhaust gas purifying apparatus, there is one provided with a soot filter that captures particulate matter (PM) contained in exhaust gas.
In a suit filter, if the amount of trapped PM exceeds a predetermined amount, clogging occurs and the filter does not function as a filter. When approaching such a situation, the trapped PM is burned and removed using the heat of the exhaust gas. Then, reproduction is performed so that clogging does not occur.
The regeneration temperature required to reliably burn the PM is usually easily obtained when the engine is operated at a medium load or higher, but becomes low at no load or low load operation. May not be reached.
一方、従来、排気ガスの流体エネルギを利用して吸気を過給するターボ過給機が知られている。また、このようなターボ過給機として、排気タービンへの排気ガスの流路面積を可変にすることができるようにした可変ターボ過給機も知られている。
そこで、過給を必要としない無負荷あるいは低負荷運転の状態において、排気タービンへの排気ガスの開口量を通常の運転時よりも意図的に少なくし、排圧を上昇させて同時に排気温度も上昇させ、このことによって排気ガス温度を再生温度以上に上昇させることが提案されている。 On the other hand, a turbocharger that supercharges intake air by utilizing fluid energy of exhaust gas has been known. As such a turbocharger, a variable turbocharger is also known in which the flow area of the exhaust gas to the exhaust turbine can be made variable.
Therefore, in a no-load or low-load operation that does not require supercharging, the exhaust gas opening to the exhaust turbine is intentionally reduced compared to that during normal operation, and the exhaust pressure is increased at the same time. It has been proposed to raise the exhaust gas temperature above the regeneration temperature.
そこで、過給を必要としない無負荷あるいは低負荷運転の状態において、排気タービンへの排気ガスの開口量を通常の運転時よりも意図的に少なくし、排圧を上昇させて同時に排気温度も上昇させ、このことによって排気ガス温度を再生温度以上に上昇させることが提案されている。 On the other hand, a turbocharger that supercharges intake air by utilizing fluid energy of exhaust gas has been known. As such a turbocharger, a variable turbocharger is also known in which the flow area of the exhaust gas to the exhaust turbine can be made variable.
Therefore, in a no-load or low-load operation that does not require supercharging, the exhaust gas opening to the exhaust turbine is intentionally reduced compared to that during normal operation, and the exhaust pressure is increased at the same time. It has been proposed to raise the exhaust gas temperature above the regeneration temperature.
例えば、可変ターボ過給機として、排気ガスを排気タービンに噴出するノズル部の構造を、互いに対向する一対の排気導入壁で形成するとともに、一方の排気導入壁を他方の排気導入壁に対して進退させることにより、排気導入壁の隙間(ノズル部の開口面積)を調整できるようにしたものがある。このような可変ターボ過給機では、一方の排気導入壁を他方へ向けて最大近接位置まで移動させることにより、排気ガスの流れを抑制して排気温度を再生温度まで上昇させる(特許文献1)。
For example, as a variable turbocharger, the structure of a nozzle portion for injecting exhaust gas into an exhaust turbine is formed by a pair of exhaust introduction walls facing each other, and one exhaust introduction wall is connected to the other exhaust introduction wall There are some which can adjust the gap (opening area of the nozzle part) of the exhaust introduction wall by advancing and retreating. In such a variable turbocharger, by moving one exhaust introduction wall toward the other position to the maximum proximity position, the flow of exhaust gas is suppressed and the exhaust temperature is raised to the regeneration temperature (Patent Document 1). .
ところが、排気ガスの流れを抑制することにより、可変ターボ過給機の上流側での排圧も上昇するため、排圧が必要以上に高くなってしまうと、エンジンの排気バルブの動きに異常が生じる可能性がある。そして、エンジン側での異常発生を回避する必要性から、排気ガスの温度が再生温度に達する前に排圧が上がり過ぎると、ノズル部の開口面積を広げる方向に戻さざるを得ず、排気ガス温度を再生温度まで上昇させることができない状態となる。
However, by suppressing the flow of exhaust gas, the exhaust pressure on the upstream side of the variable turbocharger also increases, so if the exhaust pressure becomes higher than necessary, the engine exhaust valve will malfunction. It can happen. And because of the need to avoid the occurrence of abnormalities on the engine side, if the exhaust pressure rises too much before the exhaust gas temperature reaches the regeneration temperature, it must be returned to the direction of widening the opening area of the nozzle portion, and the exhaust gas The temperature cannot be raised to the regeneration temperature.
このため、特許文献1では、排気導入壁を最大近接位置に位置させている状態では、排気導入路に導かれた排気ガスがノズル部の下流側にバイパスする構造を採用しており、排気ガスをバイパスさせることで、上流側での排圧が過剰に上昇するのを防止しつつ、排気ガスの温度を再生温度に確実に上昇させている。
For this reason, Patent Document 1 adopts a structure in which the exhaust gas guided to the exhaust introduction path is bypassed to the downstream side of the nozzle portion when the exhaust introduction wall is positioned at the maximum proximity position. By bypassing the exhaust gas, the exhaust gas temperature is reliably raised to the regeneration temperature while preventing the exhaust pressure on the upstream side from rising excessively.
具体的に排気導入壁は、摺動自在なノズルリングを備えて構成されており、ノズルリングと周囲のタービンハウジングとの間は、タービンハウジングの内面に設けられたシールリングによってシールされている。また、ノズルリングには、排気ガスをバイパスさせるためのスリットが設けられている。
Specifically, the exhaust introduction wall includes a slidable nozzle ring, and the nozzle ring and the surrounding turbine housing are sealed by a seal ring provided on the inner surface of the turbine housing. The nozzle ring is provided with a slit for bypassing the exhaust gas.
可変ターボ過給機の通常作動時においてノズルリングは、スリットがシールリングを越えない範囲で進退方向に摺動するため、排気導入路とノズル部の下流側とはスリットによって連通されることはない。これに対して、排気温度を上昇させるためにノズルリングを最大に進出させると、スリットがシールリングよりもノズル部側に移動し、スリットを介して排気導入路とノズル部の下流側とが連通し、排気ガスがバイパスする。
During normal operation of the variable turbocharger, the nozzle ring slides in the forward / backward direction as long as the slit does not exceed the seal ring, so the exhaust introduction path and the downstream side of the nozzle portion are not communicated by the slit. . In contrast, when the nozzle ring is advanced to the maximum in order to increase the exhaust temperature, the slit moves to the nozzle part side of the seal ring, and the exhaust introduction path communicates with the downstream side of the nozzle part through the slit. And exhaust gas bypasses.
しかしながら、特許文献1では、排気ガスがノズルリングの摺動部分を通してバイパスするようになっており、バイパスするかしないかは、シールリングに対するノズルリングの位置によって決まるため、シールリングの摩耗やノズルリングのシール面の摩耗等によって、シールリングとノズルリングとの間に微小な隙間が生じると、互いの位置に関係なくその隙間を通して排気ガスが常時バイパスすることになり、可変ターボ過給機の通常作動時の性能が低下するといった懸念がある。
However, in Patent Document 1, exhaust gas is bypassed through the sliding portion of the nozzle ring, and whether or not to bypass is determined by the position of the nozzle ring with respect to the seal ring. If there is a minute gap between the seal ring and the nozzle ring due to wear of the seal surface, exhaust gas always bypasses through the gap regardless of the position of each other. There is concern that the performance during operation will be reduced.
本発明の目的は、構成部材の経年的な摩耗等によって通常作動時に排気ガスがバイパスするのを防止でき、性能を良好に維持できる可変ターボ過給機を提供することにある。
An object of the present invention is to provide a variable turbocharger that can prevent exhaust gas from bypassing during normal operation due to aging of components and the like and maintain good performance.
本発明のスライドノズル形可変ターボ過給機は、互いに対向する一対の排気導入壁により形成されたノズル部と、一方の前記排気導入壁を形成するノズルリングと、前記ノズルリングを他方の前記排気導入壁に対して進退させるスライド機構と、前記ノズル部とタービンホイールの下流に排気ガスを排出する排気出口とを連通させるバイパス流路と、前記バイパス流路を連通遮断する弁部材と、前記ノズルリングに設けられた押圧部と、を備え、前記押圧部で前記弁部材を押圧しているときに前記バイバス流路を連通することを特徴とする。
The slide nozzle type variable turbocharger of the present invention includes a nozzle portion formed by a pair of exhaust introduction walls facing each other, a nozzle ring forming one of the exhaust introduction walls, and the nozzle ring as the other exhaust. A slide mechanism for advancing and retreating with respect to the introduction wall; a bypass passage for communicating the nozzle portion and an exhaust outlet for discharging exhaust gas downstream of the turbine wheel; a valve member for communicating and blocking the bypass passage; and the nozzle And a pressing portion provided on the ring, wherein the bypass passage is communicated when the valve member is pressed by the pressing portion.
本発明のスライドノズル形可変ターボ過給機では、前記バイパス流路は、前記ノズル部を収容する環状の凹部に構成されていることが好ましい。
In the slide nozzle type variable turbocharger of the present invention, it is preferable that the bypass flow path is formed in an annular recess that accommodates the nozzle portion.
本発明のスライドノズル形可変ターボ過給機では、前記ノズルリングには、周方向に沿って複数のノズルベーンが設けられ、前記ノズルベーンの進出方向に突出した前記押圧部が設けられていることが好ましい。
In the slide nozzle type variable turbocharger of the present invention, it is preferable that the nozzle ring is provided with a plurality of nozzle vanes along a circumferential direction, and the pressing portion protruding in the advancing direction of the nozzle vanes. .
本発明のスライドノズル形可変ターボ過給機では、前記スライド機構は、前記ノズルリングに接続されて当該ノズルリングを進退させる支持ロッドが設けられ、前記弁部材は前記支持ロッドに対応した位置に配置されていることが好ましい。
In the slide nozzle type variable turbocharger of the present invention, the slide mechanism is provided with a support rod that is connected to the nozzle ring and advances and retracts the nozzle ring, and the valve member is disposed at a position corresponding to the support rod. It is preferable that
本発明のスライドノズル形可変ターボ過給機では、前記スライド機構は、油圧アクチュエータによって駆動されることが好ましい。
In the slide nozzle type variable turbocharger of the present invention, the slide mechanism is preferably driven by a hydraulic actuator.
以上の発明によれば、ノズルリングを他方の排気導入壁に対して最大に近接させた位置で、押圧部により弁部材を開閉させる設定とすればよい。このような設定により、排気ガスをノズル部からタービンホイールに対して有効に噴射させることなく排気出口側にバイパスでき、排気ガス温度がスーツフィルタの再生温度に達する以前に、ノズル部上流側での排圧が過剰に上昇するのを防止できる。そして、弁部材は、ノズルリングと共に進退する押圧部によって開閉動作するため、摺動部分の摩耗等に影響される心配がなく、エンジンの定常運転時に排気ガスがバイパスするのを防止でき、性能を良好に維持できる。
なお、タービンホイールに仕事させることのない多くの排気ガスは、その温度を再生温度以上に維持したままスーツフィルタに流入することになり、スーツフィルタでの再生を確実に実施できる。 According to the above-described invention, the valve member may be set to be opened and closed by the pressing portion at a position where the nozzle ring is closest to the other exhaust introduction wall. With such a setting, exhaust gas can be bypassed to the exhaust outlet side without being effectively injected from the nozzle part to the turbine wheel, and before the exhaust gas temperature reaches the regeneration temperature of the suit filter, It is possible to prevent the exhaust pressure from rising excessively. And since the valve member opens and closes by the pressing part that moves forward and backward with the nozzle ring, there is no worry of being affected by wear of the sliding part, etc., and it is possible to prevent the exhaust gas from bypassing during steady operation of the engine, It can be maintained well.
It should be noted that a large amount of exhaust gas that does not cause the turbine wheel to work flows into the suit filter while maintaining its temperature at or above the regeneration temperature, and regeneration with the suit filter can be reliably performed.
なお、タービンホイールに仕事させることのない多くの排気ガスは、その温度を再生温度以上に維持したままスーツフィルタに流入することになり、スーツフィルタでの再生を確実に実施できる。 According to the above-described invention, the valve member may be set to be opened and closed by the pressing portion at a position where the nozzle ring is closest to the other exhaust introduction wall. With such a setting, exhaust gas can be bypassed to the exhaust outlet side without being effectively injected from the nozzle part to the turbine wheel, and before the exhaust gas temperature reaches the regeneration temperature of the suit filter, It is possible to prevent the exhaust pressure from rising excessively. And since the valve member opens and closes by the pressing part that moves forward and backward with the nozzle ring, there is no worry of being affected by wear of the sliding part, etc., and it is possible to prevent the exhaust gas from bypassing during steady operation of the engine, It can be maintained well.
It should be noted that a large amount of exhaust gas that does not cause the turbine wheel to work flows into the suit filter while maintaining its temperature at or above the regeneration temperature, and regeneration with the suit filter can be reliably performed.
また、バイパス流路を凹部を含んで構成した場合には、周方向の多くの位置から排気ガスをパイパス流路に導くことができ、排気ガスを効率よく排出できる。
Further, when the bypass flow path is configured to include the recess, the exhaust gas can be guided to the bypass flow path from many positions in the circumferential direction, and the exhaust gas can be discharged efficiently.
そして、押圧部をノズルリングに設けることで、押圧部としてはその長さ寸法を短くでき、押圧部の強度を容易に確保できて耐久性を向上させることができる。
And by providing a press part in a nozzle ring, the length dimension as a press part can be shortened, the intensity | strength of a press part can be ensured easily, and durability can be improved.
さらに、スライド機構の支持ロッドに対応した位置に弁部材を設けることで、押圧部で弁部材を押圧している間、ノズルリングに歪み等が生じるのを防止でき、やはり耐久性を向上させることができ、また、ノズルリングの位置制御をより正確にできる。
Furthermore, by providing the valve member at a position corresponding to the support rod of the slide mechanism, it is possible to prevent the nozzle ring from being distorted while the valve member is being pressed by the pressing portion, and also to improve durability. In addition, the position of the nozzle ring can be controlled more accurately.
さらに、スライド機構を油圧アクチュエータにて駆動する構成では、より大きな押圧力にて押圧部を押圧できる。換言すれば、弁部材による大きな力でバイパス流路を遮断した場合でも、弁部材を油圧アクチュエータにより確実に開閉できる。すなわち、弁部材の大きな力でバイパス流路を塞いでおくことができるため、バイパス流路を介して排気ガスを逃がしたくない場合など、排気ガスの圧力で開閉弁が開く心配がなく、当該バイパス流路を確実に遮断できる。
なお、油圧アクチュエータとしては、ノズルリングの位置を油圧サーボ機構によってフィードバック制御したりする構成の他、油圧サーボ機構を用いることなく、フィードフォワード制御したりする構成であってもよい。 Further, in the configuration in which the slide mechanism is driven by the hydraulic actuator, the pressing portion can be pressed with a larger pressing force. In other words, the valve member can be reliably opened and closed by the hydraulic actuator even when the bypass flow path is blocked by a large force by the valve member. In other words, since the bypass flow path can be closed with a large force of the valve member, there is no concern that the on-off valve will open due to the pressure of the exhaust gas, such as when exhaust gas does not want to escape through the bypass flow path. The flow path can be reliably blocked.
The hydraulic actuator may have a configuration in which the position of the nozzle ring is feedback-controlled by a hydraulic servo mechanism, or in which feed-forward control is performed without using the hydraulic servo mechanism.
なお、油圧アクチュエータとしては、ノズルリングの位置を油圧サーボ機構によってフィードバック制御したりする構成の他、油圧サーボ機構を用いることなく、フィードフォワード制御したりする構成であってもよい。 Further, in the configuration in which the slide mechanism is driven by the hydraulic actuator, the pressing portion can be pressed with a larger pressing force. In other words, the valve member can be reliably opened and closed by the hydraulic actuator even when the bypass flow path is blocked by a large force by the valve member. In other words, since the bypass flow path can be closed with a large force of the valve member, there is no concern that the on-off valve will open due to the pressure of the exhaust gas, such as when exhaust gas does not want to escape through the bypass flow path. The flow path can be reliably blocked.
The hydraulic actuator may have a configuration in which the position of the nozzle ring is feedback-controlled by a hydraulic servo mechanism, or in which feed-forward control is performed without using the hydraulic servo mechanism.
〔第1実施形態〕
図1は、本発明の第1実施形態に係るスライドノズル形の可変ターボ過給機1の斜視図、図2は可変ターボ過給機1の断面図であり、図1の矢印II-II断面図である。
図1、図2において、可変ターボ過給機1は、図中右側のタービン2と、左側のコンプレッサ3と、タービン2およびコンプレッサ3間の油圧サーボ駆動装置40とを備えた構成であり、図示しないエンジン本体に取り付けられる。また、本実施形態の可変ターボ過給機1を備えたエンジンの排気経路途中には、PM捕捉用のスーツフィルタを有した図示しない排気ガス浄化装置が設けられる。 [First Embodiment]
FIG. 1 is a perspective view of a slide nozzletype variable turbocharger 1 according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view of the variable turbocharger 1, and a cross-section taken along arrow II-II in FIG. FIG.
1 and 2, thevariable turbocharger 1 includes a turbine 2 on the right side in the drawing, a compressor 3 on the left side, and a hydraulic servo drive device 40 between the turbine 2 and the compressor 3. Not attached to the engine body. Further, an exhaust gas purification device (not shown) having a PM capture suit filter is provided in the middle of the exhaust path of the engine provided with the variable turbocharger 1 of the present embodiment.
図1は、本発明の第1実施形態に係るスライドノズル形の可変ターボ過給機1の斜視図、図2は可変ターボ過給機1の断面図であり、図1の矢印II-II断面図である。
図1、図2において、可変ターボ過給機1は、図中右側のタービン2と、左側のコンプレッサ3と、タービン2およびコンプレッサ3間の油圧サーボ駆動装置40とを備えた構成であり、図示しないエンジン本体に取り付けられる。また、本実施形態の可変ターボ過給機1を備えたエンジンの排気経路途中には、PM捕捉用のスーツフィルタを有した図示しない排気ガス浄化装置が設けられる。 [First Embodiment]
FIG. 1 is a perspective view of a slide nozzle
1 and 2, the
タービン2側のタービンハウジング4内にはタービンホイール5が収容され、コンプレッサ3側のコンプレッサハウジング6内にはコンプレッサインペラ7が収容されている。タービンホイール5にはシャフト8が一体に設けられ、シャフト8の先端にコンプレッサインペラ7が取り付けられている。シャフト8はセンターハウジング9に回転自在に支持されている。このため、排気ガスによって回転するタービンホイール5の回転が、シャフト8を介してコンプレッサインペラ7に伝達され、コンプレッサインペラ7の回転によって吸気が圧縮過給される。
A turbine wheel 5 is accommodated in the turbine housing 4 on the turbine 2 side, and a compressor impeller 7 is accommodated in the compressor housing 6 on the compressor 3 side. A shaft 8 is provided integrally with the turbine wheel 5, and a compressor impeller 7 is attached to the tip of the shaft 8. The shaft 8 is rotatably supported by the center housing 9. Therefore, the rotation of the turbine wheel 5 rotated by the exhaust gas is transmitted to the compressor impeller 7 via the shaft 8, and the intake air is compressed and supercharged by the rotation of the compressor impeller 7.
タービンハウジング4には、エンジン本体からの排気ガスを導入するボリュート状の排気導入路11が設けられている。排気導入路11には、排気ガスをタービンホイール5側に噴出するためのノズル部12が周方向に連続して設けられており、ノズル部12から噴出した排気ガスがタービンホイール5を回転させた後に排気出口13から排気される。ノズル部12は、互いに対向する一対の排気導入壁14,15によって形成されている。
The turbine housing 4 is provided with a volute-shaped exhaust introduction path 11 for introducing exhaust gas from the engine body. In the exhaust introduction path 11, a nozzle portion 12 for ejecting exhaust gas to the turbine wheel 5 side is continuously provided in the circumferential direction, and the exhaust gas ejected from the nozzle portion 12 rotates the turbine wheel 5. It is exhausted from the exhaust outlet 13 later. The nozzle portion 12 is formed by a pair of exhaust introduction walls 14 and 15 that face each other.
一方の排気導入壁14は、断面コ字形で環状とされたノズルリング16の側面17によって形成されている。ノズルリング16は、センターハウジング9に設けられた環状の収容空間18内に収容されている。収容空間18とノズル部12側とは、センターハウジング9に設けられた一対のシールリング18A,18Bにてシールされている。ノズルリング16の側面17には、他方の排気導入壁15側に向けて突出した複数のノズルベーン19が等周間隔で取り付けられている。
One exhaust introduction wall 14 is formed by a side surface 17 of a nozzle ring 16 having a U-shaped cross section. The nozzle ring 16 is housed in an annular housing space 18 provided in the center housing 9. The housing space 18 and the nozzle portion 12 side are sealed by a pair of seal rings 18A and 18B provided in the center housing 9. A plurality of nozzle vanes 19 projecting toward the other exhaust introduction wall 15 side are attached to the side surface 17 of the nozzle ring 16 at equal circumferential intervals.
他方の排気導入壁15は、シュラウドプレート22に形成されている。シュラウドプレート22には、ノズルリング16のノズルベーン19を挿通させる複数の切欠孔23が周方向に沿って形成され、各ノズルベーン19が切欠孔23に挿通されることで、各ノズルベーン19の先端がシュラウドプレート22裏側の環状の凹部21内に収容される。このような構造においては、ノズルリング16をスライド機構20によって進退させることにより、排気導入壁14を排気導入壁15に対して近接離間させ、ノズル部12のノズル開度としての開口面積を変更する。
The other exhaust introduction wall 15 is formed on the shroud plate 22. The shroud plate 22 is formed with a plurality of cutout holes 23 through which the nozzle vanes 19 of the nozzle ring 16 are inserted along the circumferential direction. By inserting each nozzle vane 19 through the cutout hole 23, the tip of each nozzle vane 19 is shroud. The plate 22 is accommodated in an annular recess 21 on the back side. In such a structure, by moving the nozzle ring 16 forward and backward by the slide mechanism 20, the exhaust introduction wall 14 is moved closer to and away from the exhaust introduction wall 15, and the opening area as the nozzle opening degree of the nozzle portion 12 is changed. .
なお、コンプレッサ3側の構成は、通常のターボ過給機と同じであり、公知であるため、ここでの詳細な説明を省略する。以下には、スライド機構20について詳説する。
In addition, since the structure by the side of the compressor 3 is the same as a normal turbocharger and is well-known, detailed description here is abbreviate | omitted. Hereinafter, the slide mechanism 20 will be described in detail.
図3は、スライド機構20の要部を示す断面図であり、図2の矢印III-III断面図である。図4は、図2の矢印IV-IV断面図である。
図3、図4において、スライド機構20は、センターハウジング9の下部側に挿通された駆動シャフト24を回動駆動することで、ノズルリング16を進退させる構造である。駆動シャフト24の軸方向の途中位置には、上方に向かって円弧状に延設された一対のアーム25,25が固定されている。各アーム25の先端側には、水平方向外側に突出したピン26が取り付けられ、このピン26にはスライダ27が嵌め込まれている。スライダ27は、前述のシャフト8と平行な支持ロッド28の基端側の摺動溝29に摺動自在に嵌合している。支持ロッド28の先端はノズルリング16の裏面側に接合されている。 FIG. 3 is a cross-sectional view showing the main part of theslide mechanism 20, and is a cross-sectional view taken along arrow III-III in FIG. 4 is a cross-sectional view taken along arrow IV-IV in FIG.
3 and 4, theslide mechanism 20 has a structure for moving the nozzle ring 16 forward and backward by rotationally driving a drive shaft 24 inserted through the lower side of the center housing 9. A pair of arms 25, 25 extending in an arc shape upward is fixed at an intermediate position in the axial direction of the drive shaft 24. A pin 26 protruding outward in the horizontal direction is attached to the distal end side of each arm 25, and a slider 27 is fitted into the pin 26. The slider 27 is slidably fitted in a sliding groove 29 on the base end side of the support rod 28 parallel to the shaft 8 described above. The tip of the support rod 28 is joined to the back side of the nozzle ring 16.
図3、図4において、スライド機構20は、センターハウジング9の下部側に挿通された駆動シャフト24を回動駆動することで、ノズルリング16を進退させる構造である。駆動シャフト24の軸方向の途中位置には、上方に向かって円弧状に延設された一対のアーム25,25が固定されている。各アーム25の先端側には、水平方向外側に突出したピン26が取り付けられ、このピン26にはスライダ27が嵌め込まれている。スライダ27は、前述のシャフト8と平行な支持ロッド28の基端側の摺動溝29に摺動自在に嵌合している。支持ロッド28の先端はノズルリング16の裏面側に接合されている。 FIG. 3 is a cross-sectional view showing the main part of the
3 and 4, the
駆動シャフト24が回動すると、アーム25がシャフト8の軸方向に沿って揺動し、支持ロッド28が移動してノズルリング16を動かし、一方の排気導入壁14が他方の排気導入壁15に対して進退することになる。すなわち、ノズルリング16は、シュラウドプレート22に対して近接離間する。
When the drive shaft 24 rotates, the arm 25 swings along the axial direction of the shaft 8, the support rod 28 moves to move the nozzle ring 16, and one exhaust introduction wall 14 becomes the other exhaust introduction wall 15. It will advance and retreat. That is, the nozzle ring 16 is closely spaced from the shroud plate 22.
スライド機構20の駆動シャフト24は、その端部に設けられたアーム31を介して油圧サーボ駆動装置40によって回動駆動される。油圧サーボ駆動装置40は、サーボピストン41を上下に進退運動させることで駆動シャフト24を回動させる構造である。このためにサーボピストン41の外周には、軸方向に対して直交した摺動溝33が設けられ、駆動シャフト24側のアーム31には、摺動溝33側に突出したピン34が設けられ、このピン34にスライダ35が嵌め込まれ、スライダ35が摺動溝33に対して摺動自在に嵌合している。
The drive shaft 24 of the slide mechanism 20 is rotationally driven by a hydraulic servo drive device 40 via an arm 31 provided at the end thereof. The hydraulic servo drive device 40 has a structure that rotates the drive shaft 24 by moving the servo piston 41 up and down. For this purpose, the outer periphery of the servo piston 41 is provided with a sliding groove 33 orthogonal to the axial direction, and the arm 31 on the drive shaft 24 side is provided with a pin 34 protruding to the sliding groove 33 side. A slider 35 is fitted into the pin 34, and the slider 35 is slidably fitted into the sliding groove 33.
つまり、サーボピストン41を上下動させると、それに伴ってスライダ35が上下動するとともに摺動溝33に沿って(図3の紙面表裏方向に沿って)摺動し、このスライダ35の動きとピン34の回動とによりアーム31の円弧動を許容し、アーム31を回動させることが可能である。この駆動シャフト24の回動によって、前述したようにスライド機構20が駆動され、支持ロッド28が移動し、ノズルリング16がシュラウドプレート22に対して進退することで、可変ターボ過給機1のノズル部12のノズル開度が調整されるようになっている。
That is, when the servo piston 41 is moved up and down, the slider 35 is moved up and down along with it, and slides along the sliding groove 33 (along the front and back direction in FIG. 3). By rotating 34, the arc movement of the arm 31 is allowed, and the arm 31 can be rotated. By the rotation of the drive shaft 24, the slide mechanism 20 is driven as described above, the support rod 28 moves, and the nozzle ring 16 advances and retreats with respect to the shroud plate 22, whereby the nozzle of the variable turbocharger 1 is moved. The nozzle opening degree of the part 12 is adjusted.
ここで、ノズルリング16の側面17には、ノズル部12と収容空間18とを連通させる連通開口16A(図2)が設けられている。連通開口16Aにより、ノズルリング16の進退時には、収容空間18内の内圧と側面17に作用する静圧とが等しくなり、ノズルリング16の摺動がスムースに行われるようになっている。
Here, the side surface 17 of the nozzle ring 16 is provided with a communication opening 16A (FIG. 2) that allows the nozzle portion 12 and the accommodation space 18 to communicate with each other. Due to the communication opening 16A, when the nozzle ring 16 advances and retreats, the internal pressure in the accommodation space 18 and the static pressure acting on the side surface 17 become equal, and the nozzle ring 16 slides smoothly.
図5は、本実施形態の要部を拡大して示す断面図である。図6は、図5の矢印VI-VI断面図、図7は、図6の矢印VII-VII断面図、図8は、図5の矢印VIII-VIIIから見た図である。なお、図8において、シュラウドプレート22の図示を省略してある。
図5~図8において、凹部21内には、ノズルリング16の進出方向に窪んだ中空部51が設けられている。中空部51は長孔形状とされ、支持ロッド28(図4)に対応した位置に一対設けられている。 FIG. 5 is an enlarged cross-sectional view showing a main part of the present embodiment. 6 is a cross-sectional view taken along arrows VI-VI in FIG. 5, FIG. 7 is a cross-sectional view taken along arrows VII-VII in FIG. 6, and FIG. 8 is a view taken from arrows VIII-VIII in FIG. In FIG. 8, the illustration of theshroud plate 22 is omitted.
5 to 8, ahollow portion 51 that is recessed in the advancing direction of the nozzle ring 16 is provided in the recess 21. The hollow portion 51 has a long hole shape, and a pair is provided at a position corresponding to the support rod 28 (FIG. 4).
図5~図8において、凹部21内には、ノズルリング16の進出方向に窪んだ中空部51が設けられている。中空部51は長孔形状とされ、支持ロッド28(図4)に対応した位置に一対設けられている。 FIG. 5 is an enlarged cross-sectional view showing a main part of the present embodiment. 6 is a cross-sectional view taken along arrows VI-VI in FIG. 5, FIG. 7 is a cross-sectional view taken along arrows VII-VII in FIG. 6, and FIG. 8 is a view taken from arrows VIII-VIII in FIG. In FIG. 8, the illustration of the
5 to 8, a
また、図6、図7において、タービンハウジング4の排気出口13の内周部分には、周方向に沿って連続した連通溝52が設けられている。連通溝52と中空部51とは、一対の連通孔53によって連通している。中空部51のシュラウドプレート22側の開口部分は、凹部21の形状に対応して湾曲したカバープレート54で塞がれている。ただし、カバープレート54には、四角形状の開口55が設けられており、この開口55の位置には、少なくとも1つのノズルベーン19が対向するようになっている。
6 and 7, a communication groove 52 continuous along the circumferential direction is provided in the inner peripheral portion of the exhaust outlet 13 of the turbine housing 4. The communication groove 52 and the hollow portion 51 communicate with each other through a pair of communication holes 53. The opening portion of the hollow portion 51 on the shroud plate 22 side is closed with a cover plate 54 that is curved corresponding to the shape of the recess 21. However, the cover plate 54 is provided with a rectangular opening 55, and at least one nozzle vane 19 faces the position of the opening 55.
中空部51内には、バネ材料で形成された弁部材60が収容されている。従って、中空部51内の弁部材60も、スライド機構20の支持ロッド28に対応した位置に配置されることになる。弁部材60の幅寸法は、中空部51の溝幅寸法とほぼ同じで、弁部材60が中空部51内に収容された状態では、幅方向に位置ずれする心配がない。
このような弁部材60は、図9に拡大して示すように、V字形状に形成された板バネ部61と、板バネ部61の一方の片に固定された開閉片62とで構成されている。 Avalve member 60 formed of a spring material is accommodated in the hollow portion 51. Therefore, the valve member 60 in the hollow portion 51 is also disposed at a position corresponding to the support rod 28 of the slide mechanism 20. The width dimension of the valve member 60 is substantially the same as the groove width dimension of the hollow portion 51, and there is no fear of displacement in the width direction when the valve member 60 is accommodated in the hollow portion 51.
As shown in an enlarged view in FIG. 9, such avalve member 60 includes a leaf spring portion 61 formed in a V shape and an opening / closing piece 62 fixed to one piece of the leaf spring portion 61. ing.
このような弁部材60は、図9に拡大して示すように、V字形状に形成された板バネ部61と、板バネ部61の一方の片に固定された開閉片62とで構成されている。 A
As shown in an enlarged view in FIG. 9, such a
板バネ部61の他方の片の先端側には丸孔63が設けられている。丸孔63は、一方の片の先端よりも延出した位置に設けられている。丸孔63に対応した位置には、一方の片および開閉片62と干渉しないようにスリーブ64が配置される。弁部材60は、カバープレート54の挿通孔56、スリーブ64、および丸孔63を貫通し、かつ中空部51奥側のネジ穴57に螺合するスクリュー65にて中空部51内に固定される。
A round hole 63 is provided on the tip side of the other piece of the leaf spring part 61. The round hole 63 is provided at a position extending from the tip of one piece. A sleeve 64 is arranged at a position corresponding to the round hole 63 so as not to interfere with one piece and the opening / closing piece 62. The valve member 60 is fixed in the hollow portion 51 by a screw 65 that passes through the insertion hole 56, the sleeve 64, and the round hole 63 of the cover plate 54 and is screwed into the screw hole 57 on the back side of the hollow portion 51. .
さらに、板バネ部61の他方の片には一対の流通孔66が設けられている。図6、図7および図9に示すように、これらの流通孔66は、中空部51と連通溝52とを連通させる前述した連通孔53に対応している。流通孔66が設けられることにより、板バネ部61が連通孔53を塞ぐ心配がなく、中空部51と連通溝52との連通状態が良好に確保される。
このように、弁部材60が中空部51内に収容、固定されると、開閉片62は、板バネ部61で付勢された状態でカバープレート54に当接され、その開口55を塞ぐ。 Further, a pair of flow holes 66 are provided in the other piece of theleaf spring portion 61. As shown in FIGS. 6, 7, and 9, these flow holes 66 correspond to the above-described communication holes 53 that allow the hollow portion 51 and the communication groove 52 to communicate with each other. By providing the flow hole 66, there is no concern that the leaf spring portion 61 blocks the communication hole 53, and a good communication state between the hollow portion 51 and the communication groove 52 is ensured.
As described above, when thevalve member 60 is accommodated and fixed in the hollow portion 51, the opening / closing piece 62 is brought into contact with the cover plate 54 while being urged by the leaf spring portion 61 and closes the opening 55.
このように、弁部材60が中空部51内に収容、固定されると、開閉片62は、板バネ部61で付勢された状態でカバープレート54に当接され、その開口55を塞ぐ。 Further, a pair of flow holes 66 are provided in the other piece of the
As described above, when the
一方、開口55に対向して位置するノズルベーン19の先端には、ノズルリング16の進出方向に沿って突出した押圧部58が設けられている。押圧部58としては、ノズルベーン19とは別体に設けておき、適宜な接合手段でノズルベーン19に接合してもよく、初めからノズルベーン19と一体に作製してもよい。このような押圧部58は、ノズルリング16が図5、図6中の2点鎖線位置に示すように、排気導入壁15に対する最大近接位置まで摺動した位置では、弁部材60の開閉片62を板バネ部61の付勢力に抗して押圧し(図9中の2点鎖線)、カバープレート54の開口55を開放させる。
On the other hand, a pressing portion 58 protruding along the advance direction of the nozzle ring 16 is provided at the tip of the nozzle vane 19 positioned facing the opening 55. The pressing portion 58 may be provided separately from the nozzle vane 19 and may be joined to the nozzle vane 19 by an appropriate joining means, or may be manufactured integrally with the nozzle vane 19 from the beginning. Such a pressing portion 58 is provided at the position where the nozzle ring 16 slides to the position closest to the exhaust introduction wall 15 as shown by the two-dot chain line position in FIGS. 5 and 6. Is pressed against the urging force of the leaf spring portion 61 (two-dot chain line in FIG. 9), and the opening 55 of the cover plate 54 is opened.
開口55が開放されると、ノズル部12は、シュラウドプレート22とノズルベーン19との間の隙間、凹部21、中空部51、連通孔53、および連通溝52を介して排気出口13側と連通し、殆どの排気ガスがタービンホイール5に噴射されることなくノズル部12をバイパスして排出される。すなわち、本実施形態では、凹部21を含んで本発明のバイパス流路50が形成され、このバイパス流路50を連通遮断するように弁部材60が配置されている。
When the opening 55 is opened, the nozzle portion 12 communicates with the exhaust outlet 13 side through the gap between the shroud plate 22 and the nozzle vane 19, the concave portion 21, the hollow portion 51, the communication hole 53, and the communication groove 52. Most of the exhaust gas is discharged by bypassing the nozzle portion 12 without being injected into the turbine wheel 5. That is, in this embodiment, the bypass flow path 50 of the present invention is formed including the recess 21, and the valve member 60 is disposed so as to cut off the communication of the bypass flow path 50.
以上の可変ターボ過給機1において、定常運転時にはノズルリング16が最大近接位置に到達しない範囲で摺動し、エンジンの回転数や負荷に応じてノズル部12の開口面積が調整される。
In the variable turbocharger 1 described above, during steady operation, the nozzle ring 16 slides within a range that does not reach the maximum proximity position, and the opening area of the nozzle portion 12 is adjusted according to the engine speed and load.
これに対して、エンジンの無負荷運転あるいは低負荷運転時において、スーツフィルタの再生を行う場合には、ノズルリング16を最大近接位置まで摺動させ、ノズル部12の開口面積を最小にして排圧を上昇さる。この際、ノズルリング16を最大近接位置に達した時点では、所定のノズルベーン19に設けられた押圧部58を弁部材60に当接させて押圧し、開口55を開放して排気ガスをノズル部12を通さずに排気出口13にバイパスする。
On the other hand, when the suit filter is regenerated during the no-load operation or low-load operation of the engine, the nozzle ring 16 is slid to the maximum proximity position, and the opening area of the nozzle portion 12 is minimized. Increase pressure. At this time, when the nozzle ring 16 reaches the maximum proximity position, the pressing portion 58 provided in the predetermined nozzle vane 19 is pressed against the valve member 60 and pressed, and the opening 55 is opened to exhaust the exhaust gas into the nozzle portion. Bypass to the exhaust outlet 13 without passing through 12.
このことにより、排気ガス温度を確実に再生温度まで上昇させるとともに、排気ガス温度が再生温度に達する前に排気圧が上がり過ぎるのを防止でき、エンジンの排気バルブの動きなどに支障を来すのを防ぐことができる。
しかも、本実施形態では、特許文献1に記載されている構造とは異なって、シールリングやこれと接触する部分の摩耗度合いに影響されることなく、ノズルベーン19が最大近接位置に達した場合に排気ガスをバイパスさせることができ、定常運転時で排気ガスがバイパスすることによるターボ性能の低下を抑制できる。 This ensures that the exhaust gas temperature is raised to the regeneration temperature, prevents the exhaust pressure from rising too much before the exhaust gas temperature reaches the regeneration temperature, and hinders the movement of the engine exhaust valve. Can be prevented.
Moreover, in the present embodiment, unlike the structure described inPatent Document 1, when the nozzle vane 19 reaches the maximum proximity position without being affected by the degree of wear of the seal ring and the portion in contact therewith. Exhaust gas can be bypassed, and degradation of turbo performance due to exhaust gas bypassing during steady operation can be suppressed.
しかも、本実施形態では、特許文献1に記載されている構造とは異なって、シールリングやこれと接触する部分の摩耗度合いに影響されることなく、ノズルベーン19が最大近接位置に達した場合に排気ガスをバイパスさせることができ、定常運転時で排気ガスがバイパスすることによるターボ性能の低下を抑制できる。 This ensures that the exhaust gas temperature is raised to the regeneration temperature, prevents the exhaust pressure from rising too much before the exhaust gas temperature reaches the regeneration temperature, and hinders the movement of the engine exhaust valve. Can be prevented.
Moreover, in the present embodiment, unlike the structure described in
また、ノズルリング16は、大きな駆動力を発生させることができる油圧式のサーボ駆動装置40にて駆動されるので、ノズルリング16を摺動させながら開口55を開放させる場合でも、弁部材60の付勢力に抗した十分な押圧力で弁部材60を押圧でき、開口55を確実に開放させることができる。
Further, since the nozzle ring 16 is driven by a hydraulic servo drive device 40 capable of generating a large driving force, even when the opening 55 is opened while the nozzle ring 16 is slid, the valve member 60 The valve member 60 can be pressed with a sufficient pressing force against the urging force, and the opening 55 can be reliably opened.
さらに、大きな駆動力を生じさせる油圧アクチュエータとしての油圧サーボ駆動装置40を用いると、ノズルリング16を最大近接位置まで摺動させて、この当該近接位置にて停止させる場合には、例えば、ノズルリング16側に図5に示すように突起状のストッパ16Bを設け、このストッパ16Bをシュラウドプレート22に当接させることで停止させる必要がある。この場合、本実施形態のような弁部材60を設けていないと、ストッパ16Bが油圧サーボ駆動装置40による大きな駆動力を保持したままシュラウドプレート22に当接することになるので、当接時に衝撃等が発生し易く、耐久性やノズルリング16の位置制御に影響を及ぼしかねない。これに対して本実施形態では、ノズルリング16が最大近接位置に近づくと、ノズルベーン19の押圧部58が弁部材60を押圧し始めるので、油圧サーボ駆動装置40の駆動力の一部がその押圧力として利用されるようになり、ストッパ16Bのシュラウドプレート22への当接時の駆動力を低減させて衝撃をなくすことができ、耐久性や位置制御時の精度を向上させることができる。
Furthermore, when the hydraulic servo drive device 40 as a hydraulic actuator that generates a large driving force is used, when the nozzle ring 16 is slid to the maximum proximity position and stopped at the proximity position, for example, the nozzle ring As shown in FIG. 5, a protruding stopper 16 </ b> B is provided on the 16 side, and it is necessary to stop the stopper 16 </ b> B by contacting the shroud plate 22. In this case, if the valve member 60 is not provided as in the present embodiment, the stopper 16B comes into contact with the shroud plate 22 while maintaining a large driving force by the hydraulic servo drive device 40. May occur, which may affect durability and position control of the nozzle ring 16. On the other hand, in this embodiment, when the nozzle ring 16 approaches the maximum proximity position, the pressing portion 58 of the nozzle vane 19 starts to press the valve member 60, so that a part of the driving force of the hydraulic servo drive device 40 is pressed. It is used as a pressure, so that the driving force when the stopper 16B comes into contact with the shroud plate 22 can be reduced to eliminate the impact, and the durability and accuracy during position control can be improved.
〔第2実施形態〕
図10には、本発明の第2実施形態が示されている。前記第1実施形態での弁部材60は、V字形状の板バネ部61を備えていたが、本実施形態の弁部材70は、全体がバネ材料からなる平板状とされ、カバープレート54に固定されてリード弁として機能する。そして、この弁部材70がノズルベーン19に設けられた押圧部58によって圧されることになる。
なお、図10で示した例は、中空部51と排気出口13とを連通孔53にて直接連通させていたが、第1実施形態と同様に排気出口13に連通溝52を設け、この連通溝52に連通孔53を連通させてもよい。 [Second Embodiment]
FIG. 10 shows a second embodiment of the present invention. Although thevalve member 60 in the first embodiment includes the V-shaped leaf spring portion 61, the valve member 70 of the present embodiment is a flat plate made entirely of a spring material, and is attached to the cover plate 54. It is fixed and functions as a reed valve. The valve member 70 is pressed by the pressing portion 58 provided on the nozzle vane 19.
In the example shown in FIG. 10, thehollow portion 51 and the exhaust outlet 13 are directly communicated with each other through the communication hole 53. However, the communication groove 52 is provided in the exhaust outlet 13 as in the first embodiment, and this communication is performed. The communication hole 53 may be communicated with the groove 52.
図10には、本発明の第2実施形態が示されている。前記第1実施形態での弁部材60は、V字形状の板バネ部61を備えていたが、本実施形態の弁部材70は、全体がバネ材料からなる平板状とされ、カバープレート54に固定されてリード弁として機能する。そして、この弁部材70がノズルベーン19に設けられた押圧部58によって圧されることになる。
なお、図10で示した例は、中空部51と排気出口13とを連通孔53にて直接連通させていたが、第1実施形態と同様に排気出口13に連通溝52を設け、この連通溝52に連通孔53を連通させてもよい。 [Second Embodiment]
FIG. 10 shows a second embodiment of the present invention. Although the
In the example shown in FIG. 10, the
なお、本発明を実施するための最良の構成、方法などは、以上の記載で開示されているが、本発明は、これに限定されるものではない。すなわち、本発明は、主に特定の実施形態に関して特に図示され、かつ説明されているが、本発明の技術的思想および目的の範囲から逸脱することなく、以上述べた実施形態に対し、形状、数量、その他の詳細な構成において、当業者が様々な変形を加えることができるものである。
従って、上記に開示した形状、数量などを限定した記載は、本発明の理解を容易にするために例示的に記載したものであり、本発明を限定するものではないから、それらの形状、数量などの限定の一部もしくは全部の限定を外した部材の名称での記載は、本発明に含まれるものである。 The best configuration, method, and the like for carrying out the present invention have been disclosed above, but the present invention is not limited to this. That is, the invention has been illustrated and described with particular reference to certain specific embodiments, but without departing from the spirit and scope of the invention, Various modifications can be made by those skilled in the art in terms of quantity and other detailed configurations.
Therefore, the description limited to the shape, quantity and the like disclosed above is an example for easy understanding of the present invention, and does not limit the present invention. The description by the name of the member which remove | excluded the limitation of one part or all of such restrictions is included in this invention.
従って、上記に開示した形状、数量などを限定した記載は、本発明の理解を容易にするために例示的に記載したものであり、本発明を限定するものではないから、それらの形状、数量などの限定の一部もしくは全部の限定を外した部材の名称での記載は、本発明に含まれるものである。 The best configuration, method, and the like for carrying out the present invention have been disclosed above, but the present invention is not limited to this. That is, the invention has been illustrated and described with particular reference to certain specific embodiments, but without departing from the spirit and scope of the invention, Various modifications can be made by those skilled in the art in terms of quantity and other detailed configurations.
Therefore, the description limited to the shape, quantity and the like disclosed above is an example for easy understanding of the present invention, and does not limit the present invention. The description by the name of the member which remove | excluded the limitation of one part or all of such restrictions is included in this invention.
例えば、前記各実施形態では、弁部材60,70がノズルベーン19に設けられた押圧部58によって押圧される構造であったが、そのような押圧部58をノズルリング16に直接設けた場合でも本発明に含まれる。
このような構成は、ノズルベーン19がノズルリング16側ではなく、シュラウドプレート22側に設けられている場合に適用できる。つまり、ノズルリング16側には、ノズルベーン19との干渉を避けるための切欠孔が設けられ、ノズルリング16の進退動作に伴ってノズルベーン19が当該切欠孔を貫通して収容空間18内に入り込む構造の場合である。 For example, in each of the embodiments described above, the valve members 60 and 70 are pressed by the pressing portion 58 provided in the nozzle vane 19, but even when such a pressing portion 58 is directly provided in the nozzle ring 16, Included in the invention.
Such a configuration can be applied when thenozzle vane 19 is provided not on the nozzle ring 16 side but on the shroud plate 22 side. That is, a notch hole for avoiding interference with the nozzle vane 19 is provided on the nozzle ring 16 side, and the nozzle vane 19 penetrates into the accommodating space 18 through the notch hole as the nozzle ring 16 moves back and forth. This is the case.
このような構成は、ノズルベーン19がノズルリング16側ではなく、シュラウドプレート22側に設けられている場合に適用できる。つまり、ノズルリング16側には、ノズルベーン19との干渉を避けるための切欠孔が設けられ、ノズルリング16の進退動作に伴ってノズルベーン19が当該切欠孔を貫通して収容空間18内に入り込む構造の場合である。 For example, in each of the embodiments described above, the
Such a configuration can be applied when the
また、弁部材60,70は、凹部21内に設けられた中空部51に収容される構造に限らず、タービンハウジング4内のノズルリング16と対向する任意の位置に中空部51を設け、このような中空部51内に弁部材60,70を収容してもよい。
ただし、凹部21には、全てのノズルベーン19周りから排気ガスが流入するため、このような凹部21内に中空部51(バイパス流路50)を設けることで、排気ガスをバイパスさせた際の排気効率を良好にできるという効果がある。 Further, the valve members 60 and 70 are not limited to the structure accommodated in the hollow portion 51 provided in the recess 21, and the hollow portion 51 is provided at an arbitrary position facing the nozzle ring 16 in the turbine housing 4. The valve members 60 and 70 may be accommodated in the hollow portion 51.
However, since exhaust gas flows into therecesses 21 from around all the nozzle vanes 19, the exhaust when the exhaust gas is bypassed by providing the hollow portions 51 (bypass channels 50) in the recesses 21. There is an effect that the efficiency can be improved.
ただし、凹部21には、全てのノズルベーン19周りから排気ガスが流入するため、このような凹部21内に中空部51(バイパス流路50)を設けることで、排気ガスをバイパスさせた際の排気効率を良好にできるという効果がある。 Further, the
However, since exhaust gas flows into the
前記各実施形態では、一対の弁部材60,70が支持ロッド28に対応した位置に設けられた例で説明したが、弁部材60,70の個数や配置位置は、その実施にあたって適宜決められてよく、前記各実施形態での例に限定されない。
In each of the above embodiments, the example in which the pair of valve members 60 and 70 are provided at positions corresponding to the support rod 28 has been described. However, the number and arrangement positions of the valve members 60 and 70 are appropriately determined in the implementation. Well, it is not limited to the examples in the above embodiments.
本発明は、建設機械、土木機械、輸送車両、鉄道車両に搭載されるエンジンで、特にスーツフィルタを有した排気ガス浄化装置と組み合わせて用いられるエンジンの可変ターボ過給機として有効に利用できる。
The present invention is an engine mounted on a construction machine, a civil engineering machine, a transportation vehicle, and a railway vehicle, and can be used effectively as a variable turbocharger for an engine that is used in combination with an exhaust gas purification device having a suit filter.
1…可変ターボ過給機、12…ノズル部、13…排気出口、14,15…排気導入壁、16…ノズルリング、19…ノズルベーン、20…スライド機構、21…凹部、28…支持ロッド、40…油圧サーボ駆動装置、50…バイパス流路、58…押圧部、60,70弁部材。
DESCRIPTION OF SYMBOLS 1 ... Variable turbocharger, 12 ... Nozzle part, 13 ... Exhaust outlet, 14, 15 ... Exhaust introduction wall, 16 ... Nozzle ring, 19 ... Nozzle vane, 20 ... Slide mechanism, 21 ... Recess, 28 ... Support rod, 40 ... Hydraulic servo drive device, 50 ... Bypass flow path, 58 ... Pressing part, 60,70 valve member.
Claims (5)
- 互いに対向する一対の排気導入壁により形成されたノズル部と、
一方の前記排気導入壁を形成するノズルリングと、
前記ノズルリングを他方の前記排気導入壁に対して進退させるスライド機構と、
前記ノズル部とタービンホイールの下流に排気ガスを排出する排気出口とを連通させるバイパス流路と、
前記バイパス流路を連通遮断する弁部材と、
前記ノズルリングに設けられた押圧部と、を備え、
前記押圧部で前記弁部材を押圧しているときに前記バイバス流路を連通する
ことを特徴とするスライドノズル形可変ターボ過給機。 A nozzle portion formed by a pair of exhaust introduction walls facing each other;
A nozzle ring forming one exhaust introduction wall;
A slide mechanism for moving the nozzle ring forward and backward with respect to the other exhaust introduction wall;
A bypass passage for communicating the nozzle part and an exhaust outlet for discharging exhaust gas downstream of the turbine wheel;
A valve member for communicating and blocking the bypass flow path;
A pressing portion provided in the nozzle ring,
The slide nozzle type variable turbocharger, wherein the bypass passage is communicated when the valve member is pressed by the pressing portion. - 請求項1に記載のスライドノズル形可変ターボ過給機において、
前記バイパス流路は、前記ノズル部を収容する環状の凹部に構成されている
ことを特徴とするスライドノズル形可変ターボ過給機。 In the slide nozzle type variable turbocharger according to claim 1,
The bypass flow path is configured by an annular recess that accommodates the nozzle portion. A slide nozzle type variable turbocharger, wherein: - 請求項1または請求項2に記載のスライドノズル形可変ターボ過給機において、
前記ノズルリングには、周方向に沿って複数のノズルベーンが設けられ、
前記ノズルベーンの進出方向に突出した前記押圧部が設けられている
ことを特徴とするスライドノズル形可変ターボ過給機。 In the slide nozzle type variable turbocharger according to claim 1 or 2,
The nozzle ring is provided with a plurality of nozzle vanes along the circumferential direction,
The slide nozzle type variable turbocharger, wherein the pressing portion protruding in the advancing direction of the nozzle vane is provided. - 請求項1ないし請求項3のいずれかに記載のスライドノズル形可変ターボ過給機において、
前記スライド機構は、前記ノズルリングに接続されて当該ノズルリングを進退させる支持ロッドが設けられ、
前記弁部材は前記支持ロッドに対応した位置に配置されている
ことを特徴とするスライドノズル形可変ターボ過給機。 In the slide nozzle type variable turbocharger according to any one of claims 1 to 3,
The slide mechanism is provided with a support rod that is connected to the nozzle ring and moves the nozzle ring back and forth.
The said valve member is arrange | positioned in the position corresponding to the said support rod. The slide nozzle type variable turbocharger characterized by the above-mentioned. - 請求項1ないし請求項4のいずれかに記載のスライドノズル形可変ターボ過給機において、
前記スライド機構は、油圧アクチュエータによって駆動される
ことを特徴とするスライドノズル形可変ターボ過給機。 In the slide nozzle type variable turbocharger according to any one of claims 1 to 4,
The slide mechanism is driven by a hydraulic actuator. A slide nozzle type variable turbocharger.
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Cited By (4)
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CN104141513A (en) * | 2013-05-09 | 2014-11-12 | 株式会社Ihi | Variable nozzle unit and variable geometry system turbocharger |
GB2555872A (en) * | 2016-11-15 | 2018-05-16 | Cummins Ltd | Vane arrangement for a turbo-machine |
US10508592B2 (en) * | 2018-05-04 | 2019-12-17 | Hyundai Motor Company | VGT for vehicle |
CN111197526A (en) * | 2018-11-20 | 2020-05-26 | 现代自动车株式会社 | Turbocharger |
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JP6165564B2 (en) * | 2013-09-05 | 2017-07-19 | 三菱重工業株式会社 | Axial turbine, turbocharger, internal combustion engine, and ship |
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JP2005320970A (en) * | 2004-05-06 | 2005-11-17 | Cummins Inc | Method for determining temperature in exhaust gas for post-treatment system in internal combustion engine using variable geometry turbine |
JP2008185019A (en) * | 2007-01-31 | 2008-08-14 | Komatsu Ltd | Variable turbocharger |
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JP2004169703A (en) * | 2002-11-19 | 2004-06-17 | Holset Eng Co Ltd | Variable form turbine |
JP2005320970A (en) * | 2004-05-06 | 2005-11-17 | Cummins Inc | Method for determining temperature in exhaust gas for post-treatment system in internal combustion engine using variable geometry turbine |
JP2008185019A (en) * | 2007-01-31 | 2008-08-14 | Komatsu Ltd | Variable turbocharger |
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CN104141513A (en) * | 2013-05-09 | 2014-11-12 | 株式会社Ihi | Variable nozzle unit and variable geometry system turbocharger |
US9702264B2 (en) | 2013-05-09 | 2017-07-11 | Ihi Corporation | Variable nozzle unit and variable geometry system turbocharger |
GB2555872A (en) * | 2016-11-15 | 2018-05-16 | Cummins Ltd | Vane arrangement for a turbo-machine |
US11441435B2 (en) | 2016-11-15 | 2022-09-13 | Cummins Ltd | Vane arrangement for a turbo-machine |
US10508592B2 (en) * | 2018-05-04 | 2019-12-17 | Hyundai Motor Company | VGT for vehicle |
CN111197526A (en) * | 2018-11-20 | 2020-05-26 | 现代自动车株式会社 | Turbocharger |
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JP4956675B2 (en) | 2012-06-20 |
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