WO1995018294A1 - Moteur a cycle de miller - Google Patents

Moteur a cycle de miller Download PDF

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Publication number
WO1995018294A1
WO1995018294A1 PCT/JP1994/002215 JP9402215W WO9518294A1 WO 1995018294 A1 WO1995018294 A1 WO 1995018294A1 JP 9402215 W JP9402215 W JP 9402215W WO 9518294 A1 WO9518294 A1 WO 9518294A1
Authority
WO
WIPO (PCT)
Prior art keywords
volume
piston
chamber
cycle engine
volume chamber
Prior art date
Application number
PCT/JP1994/002215
Other languages
English (en)
Japanese (ja)
Inventor
Takeshi Ishihara
Godou Ozawa
Original Assignee
Komatsu Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd. filed Critical Komatsu Ltd.
Priority to GB9613353A priority Critical patent/GB2300226A/en
Priority to DE4480333T priority patent/DE4480333T1/de
Publication of WO1995018294A1 publication Critical patent/WO1995018294A1/fr

Links

Classifications

    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • 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
    • F02B21/00—Engines characterised by air-storage chambers
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/32—Miller cycle
    • 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 invention relates to a mirror cycle engine, and more particularly to a mirror cycle engine provided with a volume chamber communicating with a cylinder chamber.
  • a method of closing the intake valve early for example, see Japanese Patent Application Laid-Open No. 55-148932
  • a method of closing the intake valve late for example, Japanese Patent Application Laid-Open No. 2-123234 is disclosed.
  • the method of closing the intake valve as shown in the acupressure diagram in Fig. 11 is as follows: intake stroke (between a-b-c), compression stroke (between c-b-d), expansion stroke (e-f ) And the exhaust stroke (between g-b-a), the intake valve is closed early during the intake stroke, and the latter half of the intake stroke (between bc) is expanded.
  • the method of closing the intake valve late as shown in FIG. 12 is as follows: the intake stroke (between h, i, and j), the compression stroke (between j, i, and k), the expansion stroke (between m and n), During the intake stroke, the intake valve is closed late during the intake stroke, and the intake pressure is released early in the compression stroke (between j and i).
  • the intake valve is opened during the compression stroke to provide a stroke without compression, and as the piston rises, a part of the intake air is taken into the intake manifold. To reduce the compression ratio substantially.
  • a screw-type compressor is used on the intake side to supply sufficient air into the cylinder chamber, from which the air flows back to the intake manifold. ing.
  • the intake valve is closed early or late by using a variable valve timing device, or the rotary valve is closed. They were closed early using a blast device, but both had problems with complicated structures and poor durability. Disclosure of the invention
  • the present invention has been made in order to solve the above-mentioned drawbacks of the related art, and has as its object to provide an inexpensive mirror cycle engine with a simple structure in which a volume chamber communicating with a cylinder chamber is simply provided. Aim.
  • the mirror cycle engine according to the present invention is provided with a volume chamber communicating with the cylinder chamber at a predetermined position above the bottom dead center of the stroke of the piston. It is characterized by suppressing the pressure rise in the cylinder chamber.
  • An on-off valve may be provided in a passage connecting the cylinder chamber and the volume chamber.
  • a controller connected to the on-off valve may be provided, and the controller may control opening and closing of the on-off valve.
  • the volume of the volume chamber may be variable.
  • the volume chamber may be provided with a variable mechanism such as a solenoid, a piston or an actuator, and the variable mechanism may make the volume of the volume chamber variable.
  • a controller connected to the variable mechanism may be provided, and the controller may control the volume of the volume chamber.
  • an engine rotation sensor connected to the controller and a rack position detection sensor for the engine fuel injection pump are provided, so that the measured engine speed and rack position can be input to the controller.
  • a pressure screw ring is disposed on the piston scar section, and this pressure screw ring is used to collect fresh air accumulated in the volume chamber in the early stage of the compression stroke and the volume of the fresh air in the early stage of the exhaust stroke. It may be possible to prevent the exhaust gas accumulated in the chamber from leaking into the crankcase.
  • the volume chamber communicating with the cylinder chamber by providing the volume chamber communicating with the cylinder chamber, the pressure rise in the cylinder chamber is suppressed to be low by using the volume of the volume chamber at the beginning of the compression stroke. Moreover, when the piston rises by a predetermined stroke, the hole in the cylinder chamber communicating with the volume chamber is closed, and the pressure in the cylinder chamber is raised to a predetermined value. Therefore, the predetermined pressure is set to a low value because the volume chamber suppresses the pressure rise. It is possible to reduce the compression ratio substantially. As a result, all of the air drawn into the cylinder chamber can be utilized with a simple structure, and the engine output can be obtained with a low compression ratio and a high expansion ratio corresponding to the cylinder volume. Can be improved. In addition, by making the volume chamber variable, it is possible to control the mirror cycle according to the engine speed, and to obtain higher output.
  • FIG. 1 is a conceptual diagram of a main part of a mirror cycle engine according to a first embodiment of the present invention
  • FIG. 2 is a shiatsu diagram of a four-cycle diesel engine of a mirror one-cycle engine according to the present invention
  • FIG. 3 is a conceptual diagram of a main part of a mirror cycle engine according to a second embodiment of the present invention
  • FIG. 4 is a table showing a relationship between an engine speed R and an average effective pressure P me in the second embodiment.
  • FIG. 5 is a conceptual diagram of a main part of a mirror cycle engine according to a third embodiment of the present invention
  • FIG. 6 is a diagram illustrating an engine speed R (rpm), an average effective pressure P me, and a critical maximum explosion pressure in the third embodiment.
  • R engine speed
  • P me average effective pressure
  • P me critical maximum explosion pressure
  • FIG. 7 is a conceptual diagram of a principal part of a mirror cycle engine according to a fourth embodiment of the present invention at the top dead center of the piston.
  • Fig. 8 is a conceptual diagram of the essential parts at the bottom dead center of the piston of the mirror cycle engine according to the fourth embodiment.
  • FIG. 9 is a conceptual diagram showing the initial state of the compression stroke according to the fourth embodiment
  • FIG. 10 is a conceptual diagram showing a state in a later stage of the expansion stroke according to the fourth embodiment
  • FIG. 11 is an acupressure diagram of a 4-cycle diesel engine of a conventional technology, in which the intake valve of a mirror cycle engine is rapidly closed.
  • Fig. 12 is an acupressure diagram of a four-cycle diesel engine with slow closing of the intake valve of a mirror cycle engine according to the prior art.
  • FIG. 1 is a conceptual diagram of a part of a mirror cycle engine according to a first embodiment of the present invention.
  • a piston 2 is pivotally inserted into a cylinder liner 11, and a predetermined stroke S moves up and down by rotation of a crankshaft (not shown).
  • An engine head 3 is disposed at an upper end of the cylinder liner 11, and a cylinder chamber 4 is formed by the piston 2 and the engine head 3.
  • the engine head 3 is provided with an intake pipe 3a and an exhaust pipe 3b.
  • a mushroom-shaped intake valve 5 is provided at a communication port of the intake pipe 3a with the cylinder chamber 4, and an exhaust pipe 3b.
  • a communication hole 7 is formed at a predetermined position of the cylinder liner 1, that is, at a position above a lower dead center of the lower end of the predetermined stroke S of the piston 2, and a predetermined hole is formed in the communication hole 7.
  • Volume room 8 is provided.
  • FIG. 2 showing a four-cycle digital pressure diagram of the present invention.
  • Figure 2 shows the intake stroke (between L1 and L2), the compression stroke (between L2 and L3 and L4), the expansion stroke (between L5 and L6), and the exhaust stroke (between L2 and L1).
  • the intake stroke between L1 and L2
  • the compression stroke between L2 and L3 and L4
  • the expansion stroke between L5 and L6
  • the exhaust stroke between L2 and L1
  • the intake valve 5 is closed, and at the beginning of the compression stroke (between L 2 and L 3), the pressure rise is suppressed low by using the volume of the volume chamber 8.
  • the piston 2 rises further in the compression stroke (hereinafter referred to as the latter half of the compression stroke).
  • the air sucked into the cylinder chamber 4 does not escape to the intake side and does not expand by closing the intake valve 5 early. Therefore, fresh air accumulated in the volume chamber 8 in the early stage of the compression stroke is ejected from the volume chamber 8 to the cylinder chamber 4 in the late stage of the expansion stroke, agitating the combustion gas, promoting oxidation of the combustion gas, and exhaust gas.
  • the compression pressure Pa of the present embodiment is low similarly to the conventional compression pressure Po shown in FIG. 11, a low compression ratio can be obtained. In this case, a low compression ratio and a high expansion ratio can be obtained, and the thermal efficiency and exhaust emission of the engine can be improved.
  • FIG. 3 shows a main part of the engine of the present embodiment, in which a cylinder chamber 4 and a volume chamber 8 are connected.
  • An electromagnetic valve 12 (open / close valve) that opens and closes is disposed in the communication passage 11.
  • This electromagnetic valve 12 is connected to a controller 13.
  • the controller 13 has an engine rotation sensor 14 attached to a crankshaft (not shown) for measuring the engine rotation speed, and a rack position of an injection pump for injecting fuel into the cylinder chamber 4.
  • the rack position detection sensor 15 for detecting is connected.
  • the rack position of the fuel injection pump is set by a command from an accelerator petal or the like (not shown), and the rack position detection sensor 15 detects this rack position.
  • the engine speed is measured by the engine speed sensor 14.
  • the signals from the rack position detection sensor 15 and the engine rotation sensor 14 are sent to the controller 13, and the controller 13 calculates the average effective pressure P m e from both signals.
  • a command signal is output to close the electromagnetic valve 12.
  • FIG. 5 shows a main part of the engine of the present embodiment.
  • a variable volume volume chamber 20 is provided in a communication hole 7 formed at a predetermined position of the cylinder liner 11.
  • This volume chamber 20 is composed of a cylinder 21, a piston 22 that is pivotally inserted into the cylinder 21, and a solenoid 23 that moves the piston 22.
  • the controller 25 connected to this solenoid 23 has an engine rotation sensor 14 that measures the engine speed and a rack position detection that detects the rack position of the injection pump. Sensor 15 is connected.
  • the maximum explosion pressure P max of the conventional mirror cycle is limited by the output indicated by the one-dot chain line in the figure.
  • the output limit is equivalent to the dashed-dotted line Pmax, for example, when the piston 22 is at an intermediate position W having a predetermined volume
  • the average effective pressure Pme is represented by a solid curve.
  • the piston 22 is moved to the position V of FIG. 5 having a larger predetermined volume.
  • the Pme that can be output at the same Pmax can rise to the position indicated by the dotted curve.
  • the engine when the engine load is low, the engine is driven by a normal engine, and when the engine load is high, the piston 22 is retracted to become a mirror cycle engine, and the low compression ratio and high expansion ratio are reduced. As a result, the thermal efficiency of the engine can be improved. As described above, a mirror cycle engine can be obtained with a simple structure.
  • control of the on-off valve 12 and the variable-volume volume chamber 20 was performed using an electromagnetic solenoid, but the actuator, control valve, etc. were controlled by hydraulic pressure, pneumatic pressure, etc.
  • a variable mechanism may be used.
  • FIG. 7 shows the state of the top dead center position of the biston in the mirror cycle engine of the present embodiment.
  • the piston 10 is pivotally connected. Has been inserted.
  • the piston 10 has a pressure piston ring 31 mounted on the upper part and a pressure screw ring 32 mounted on the skirt. When the piston 10 is at the top dead center position, the pressure screw ring 32 of the scart portion is located below the lower end face 7 b of the communication hole 7.
  • Fig. 8 shows the case where piston 10 is at the bottom dead center position, and piston 10 slides up and down by a predetermined stroke S up and down due to rotation of a crankshaft (not shown). You. In addition, at the bottom dead center position, the upper end face 10a of the piston 10 is located below the lower end face 7b of the communication hole 7, and the distance from the upper end face 7a is the same as in the first embodiment. Ha.
  • the Shiatsu diagram for the four-cycle operation of the diesel engine with this configuration is basically the same as the Shiatsu diagram of the first embodiment (FIG. 2), and a description thereof will be omitted.
  • the operation of the piston ring 32 different from the first embodiment will be described.
  • Fig. 9 in the initial stage of the compression stroke of piston 10, fresh air sucked into cylinder chamber 4 rises from the top dead center 10a of piston 10 from bottom dead center. It is stored in the volume chamber 8 as indicated by the solid arrow until it passes the upper end face 7a of the communication hole 7.
  • the piston 10 rises and compresses, and then the fuel burns and expands to a later stage of the expansion stroke, and the upper end face 10 a of the piston 10 becomes the upper end face 7 a of the communication hole 7.
  • the fresh air confined in the volume chamber 8 is blown out into the cylinder chamber 4 as indicated by an arrow, and the combustion gas is stirred to promote oxidation and exhaust. It contributes to gas purification.
  • the volume chamber 8 and the crankcase 33 are shut off by the pressure piston ring 32, as shown in FIG. 7, so that fresh air in the volume chamber 8 does not leak. Therefore, a sufficient amount of fresh air is ejected into the cylinder chamber 4 in the latter half of the expansion stroke.
  • a mirror cycle engine capable of preventing an increase in the provision amount can be obtained. .
  • the explanation is that the simple structure of providing a volume chamber that communicates with the cylinder chamber achieves a low compression ratio and a high expansion ratio to improve the thermal efficiency of the engine and the emission of exhaust gas. By preventing exhaust gas from leaking, it is useful as a mirror cycle engine that can purify exhaust gas and prevent an increase in blow-by volume.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Un moteur à cycle de Miller de construction simple produit un faible rapport de compression et un taux de détente élevé, ce qui permet d'améliorer le rendement thermique et les émissions de gaz du moteur, de purifier les gaz d'échappement et d'empêcher une augmentation des pertes de gaz dans le carter. A cet effet, une chambre de volume (8) communiquant avec une chambre de cylindre (4), à une distance prédéterminée (Ha) au-dessus du point mort inférieur de la course du piston (2), est prévue, la chambre de volume (8) empêchant une augmentation de la pression dans la chambre de cylindre (4) au début d'une course de compression. Par ailleurs, un segment (32) de piston de pression est prévu au niveau de la jupe (10) de ce dernier de manière à empêcher l'air neuf et les gaz d'échappement s'accumulant dans ladite chambre de volume (8) de s'échapper dans le carter (13).
PCT/JP1994/002215 1993-12-28 1994-12-26 Moteur a cycle de miller WO1995018294A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
GB9613353A GB2300226A (en) 1993-12-28 1994-12-26 Miller cycle engine
DE4480333T DE4480333T1 (de) 1993-12-28 1994-12-26 Miller-Motor

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP5/351095 1993-12-28
JP35109593 1993-12-28
JP6/194767 1994-07-27
JP19476794 1994-07-27

Publications (1)

Publication Number Publication Date
WO1995018294A1 true WO1995018294A1 (fr) 1995-07-06

Family

ID=26508723

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1994/002215 WO1995018294A1 (fr) 1993-12-28 1994-12-26 Moteur a cycle de miller

Country Status (3)

Country Link
DE (1) DE4480333T1 (fr)
GB (1) GB2300226A (fr)
WO (1) WO1995018294A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7222614B2 (en) * 1996-07-17 2007-05-29 Bryant Clyde C Internal combustion engine and working cycle

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8215292B2 (en) 1996-07-17 2012-07-10 Bryant Clyde C Internal combustion engine and working cycle
NL1013811C2 (nl) * 1999-12-09 2000-11-28 Prometheus Engineering B V Hydraulisch klepbedieningsmechanisme.
JP2002213244A (ja) 2001-01-19 2002-07-31 Honda Motor Co Ltd 車両用自然吸気式内燃機関
GR1003890B (el) * 2001-06-14 2002-05-20 Κινητηρας εσωτερικης καυσης μεταβλητου κυβισμου, μεταβλητης σχεσης συμπιεσης και εναλλακτικου καυσιμου
WO2024038183A1 (fr) 2022-08-18 2024-02-22 Immunocore Limited Molécules de liaison à domaines multiples

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5991436U (ja) * 1982-12-14 1984-06-21 本田技研工業株式会社 副室を備えた内燃機関
JPS6360038U (fr) * 1986-10-07 1988-04-21

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5991436U (ja) * 1982-12-14 1984-06-21 本田技研工業株式会社 副室を備えた内燃機関
JPS6360038U (fr) * 1986-10-07 1988-04-21

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7222614B2 (en) * 1996-07-17 2007-05-29 Bryant Clyde C Internal combustion engine and working cycle

Also Published As

Publication number Publication date
GB2300226A (en) 1996-10-30
GB9613353D0 (en) 1996-08-28
DE4480333T1 (de) 1997-02-27

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