WO2016150231A1 - Moteur à combustion interne ayant une chambre de combustion à volume variable et un piston auxiliaire - Google Patents

Moteur à combustion interne ayant une chambre de combustion à volume variable et un piston auxiliaire Download PDF

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Publication number
WO2016150231A1
WO2016150231A1 PCT/CN2016/000164 CN2016000164W WO2016150231A1 WO 2016150231 A1 WO2016150231 A1 WO 2016150231A1 CN 2016000164 W CN2016000164 W CN 2016000164W WO 2016150231 A1 WO2016150231 A1 WO 2016150231A1
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Prior art keywords
cylinder
piston
auxiliary piston
small cylinder
auxiliary
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PCT/CN2016/000164
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English (en)
Chinese (zh)
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韩培洲
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
    • 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 an internal combustion engine, and more particularly to a variable volume combustor internal combustion engine with an auxiliary piston.
  • Internal combustion engines mainly include gasoline engines and diesel engines.
  • gasoline engines and diesel engines the use of a higher compression ratio is the main way to increase efficiency.
  • Gasoline engines are generally affected by knocking, and the compression ratio is generally within 10:1.
  • the diesel engine Due to the compression ignition method, the diesel engine can achieve a compression ratio of 13:1 to 20:1.
  • the compression ratio in the gasoline engine can not be very high.
  • the higher the compression ratio in the diesel engine the greater the gas pressure in the cylinder, which makes the diesel engine more cumbersome. In practice, even if the diesel engine adopts a high compression ratio of 20:1, this part of the gas in the combustion chamber cannot fully participate in the work process in the cylinder.
  • the variable volume combustor internal combustion engine with an auxiliary piston of the present invention includes five different embodiments.
  • the variable volume combustor internal combustion engine with an auxiliary piston in the first embodiment includes a cylinder, a piston in the cylinder, and a connecting rod.
  • the crankshaft connected to the transmission in the crankcase has a small cylinder which is formed in the cylinder head at the position of the side of the cylinder to avoid the volume of the combustion chamber, and an auxiliary piston in the small cylinder, which is close to the small cylinder and An air injector or a spark plug pointing to the small cylinder is arranged at the air passage of the cylinder, and a spring seat is formed on the skirt of the auxiliary piston and is formed on the bottom of the rebound spring.
  • the spring seat is slippery on the cylinder head.
  • the sleeve is slid in the sliding sleeve through the skirt on the spring seat, and the rebound spring is arranged under the spring gland on the cover, so that the auxiliary piston is pressed into the small cylinder, and the spring gland is pressed
  • a hydraulic buffer column with a bottom block extending in the rebound spring is formed, and a hydraulic oil chamber with an upper and a lower buffer section is formed in the hydraulic buffer column, and the hydraulic oil chamber is connected with the oil supply pipe to assist On the piston
  • the sliding rod with the stopper extends in the hydraulic oil chamber of the hydraulic buffer column, and the upper end of the slide shaft at the upper end of the hydraulic oil chamber for accommodating the upper end of the sliding rod passes through the communication hole and is buffered under the hydraulic oil chamber.
  • the bottom side of the segment is formed with a blocking torus that can restrict the auxiliary piston from moving out of the small cylinder; when the compression process is completed in the cylinder and the piston moves to the top dead center position, the auxiliary piston in the small cylinder also overcomes the rebound spring under the action of compressed air. After the elastic force, move up to the bottom of the hydraulic buffer column. The position blocked by the block forms the largest combustion chamber volume, and the speed of the top ring seat on the spring seat of the auxiliary piston is shifted on the bottom block of the hydraulic buffer column by the stopper on the slide bar moving to the hydraulic oil chamber.
  • the oil supply pipe provided at the top position passes through the oil injection hole sealed by the cover, and then passes through the oil passage to the side of the hydraulic oil chamber, the hydraulic oil chamber The other side communicates with the oil return passage to the upper side, and the oil return passage is connected to the oil discharge pipe through the small oil discharge hole through the inspection hole sealed by the cover.
  • An inspection cover facing the upper end of the small cylinder is mounted on the side wall of the cylinder head, and the inner side of the inspection cover serves as an upper and lower air flow passage on the spring seat of the auxiliary auxiliary piston, and a corresponding chute is formed on the inner side of the inspection cover.
  • the piston limits the rotation of the auxiliary piston by means of a slider mounted on the upper spring seat in the chute.
  • the engine in a second variable volume combustor internal combustion engine with an auxiliary piston according to the present invention, includes a cylinder, a piston in the cylinder, and a crankshaft connected to the transmission in the crankcase via a connecting rod, and a cylinder at a side of the cylinder
  • the cover is provided with a small cylinder constituting a combustion chamber volume that escapes into the exhaust valve, an auxiliary piston is installed in the small cylinder, and an injector or a spark plug directed to the small cylinder is installed at an air passage adjacent to the small cylinder and the cylinder.
  • the connecting ejector on the auxiliary piston is integrally connected with the upper spring retaining seat via a gland fixed through the upper side of the small cylinder on the cylinder head, and the spring retaining seat can slide on the cylinder head through the side skirt thereon
  • the sleeve slides correspondingly, and a rebound spring is arranged between the spring retainer and the spring gland on the cover, and the rebound spring can press the auxiliary piston from the inner side of the small cylinder quickly through the spring retainer and the connecting ejector.
  • the connecting rod under the spring retaining seat is provided with a connecting plate which is hinged with the inner ends of the rocking arms on the left and right sides through the shaft pin provided thereon, and the rocker arms on both sides are mounted on the cylinder head through the middle intermediate shaft
  • the corresponding branch on the left and right axle seats On the swing arm, the outer ends of the left and right rocker arms can be simultaneously pressed and controlled by the pressing cams on the corresponding left and right camshafts through the provided rollers, and the lower side of the shaft pin on the connecting jack is formed with a seat.
  • the limit stop plate on the gland when the compression process in the cylinder and the piston move to the upper dead center position, the pressing cams on the left and right camshafts simultaneously drive the auxiliary pressure of the rebound spring through the two left and right rocker arms.
  • the piston moves into the small cylinder.
  • the auxiliary piston has been moved.
  • the inside of the small cylinder forms the largest combustion chamber volume, and the compressed air entering the combustion chamber of the small cylinder is ignited by the fuel injection, and the formed working gas enters the cylinder to push the piston down for work.
  • the left and right camshafts After the piston works downward, the left and right camshafts
  • the pressing cam also rotates the roller on the left and right rocker arms, and the rebound spring that is not pressed will quickly drive the auxiliary piston to press the working gas in the small cylinder into the cylinder with the downward pressure of the piston to participate in the work;
  • the rollers on the left and right rocker arms When moving to the outside of the small cylinder, the rollers on the left and right rocker arms also fall to the descending buffer section on the pressing cam of the left and right camshafts, so that the speed when the auxiliary piston is moved to the outer position is buffered accordingly.
  • the pressing cam provided on the cam shaft on the intake and exhaust valve side is at an intermediate position, and the intake and exhaust cams are respectively disposed on both sides of the pressing cam, and are respectively inserted and discharged.
  • the air cam controlled rocker arm is mounted on the outside of the axle pin fixed on the axle of the position between the two cylinders.
  • the engine includes a cylinder, a piston in the cylinder, and a crankshaft connected via a connecting rod to a crankcase, and a cylinder at a side of the cylinder
  • the cover is provided with a small cylinder constituting the combustion chamber volume that escapes into the exhaust valve, an auxiliary piston is installed in the small cylinder, and an injector directed to the small cylinder is installed at an air passage close to the small cylinder and the cylinder, small
  • the auxiliary piston in the cylinder is connected to the lower end of the intermediate link via the piston pin thereon, and the upper end of the intermediate link is hinged to the small end of the connecting rod on the auxiliary crankshaft on the upper side of the cylinder head via the connecting pin, between the two links
  • the two sides of the connecting rod pin are also hinged with the swinging end of the swing arm, and the other end of the swing arm is mounted on the shaft seat of the side wall of the cylinder head through the shaft pin, and
  • the auxiliary piston in the small cylinder is driven by the auxiliary crankshaft to first press all the working gas in the small cylinder combustion chamber into the cylinder to participate in the work, and then be driven to extend the small cylinder into the cylinder.
  • the auxiliary piston with a longer stroke in the small cylinder is also moved out of the small cylinder to a certain distance into the cylinder; in the subsequent exhaust and intake, the auxiliary piston in the small cylinder It will also be returned to the small cylinder by the auxiliary crankshaft and then removed from the small cylinder and into the cylinder.
  • the engine in a fourth variable volume combustor internal combustion engine with an auxiliary piston according to the present invention, includes a cylinder, a piston in the cylinder, and a crankshaft connected to the transmission in the crankcase via a connecting rod at a bottom dead center position of the cylinder.
  • a scavenging port connected to the compressor is provided, and the cylinder head is arranged on the cylinder head a small cylinder with a combustion chamber volume, an auxiliary piston in a small cylinder, an injector or a spark plug on the side wall of the small cylinder, the auxiliary piston adopts a segmented combined structure, and an intermediate piston rod and an upper skirt Integrally, the skirt pin is hinged to the small head of the connecting rod on the auxiliary crankshaft on the upper side of the cylinder head via the piston pin thereon, and the auxiliary crankshaft has the same rotational speed as the crankshaft in the crankcase, and the upper lateral skirt of the auxiliary piston
  • the direction is formed with a transition skirt, and a plurality of uniformly distributed exhaust ports are formed at the upper position of the transition skirt and the auxiliary piston, and an exhaust passage surrounding the piston rod is formed in the transition skirt, and the upper end of the transition skirt is formed Forming an air outlet opening at a certain distance from the bottom surface of the skirt of the upper side, and
  • the auxiliary piston in the small cylinder is driven downward by the auxiliary crankshaft, and the working gas in the small cylinder is pressed into the cylinder to participate in the work.
  • the driven auxiliary piston extends into the cylinder; when the piston approaches the bottom dead center and communicates with the scavenging port on the cylinder, the exhaust port on the auxiliary piston moved to the lower position is also associated with the cylinder
  • the upper side communicates, and at the same time, the outlet opening of the auxiliary piston communicating with the exhaust port through the exhaust passage is also in communication with the annular exhaust passage on the side wall of the small cylinder, and the scavenging provided by the compressor is taken from the cylinder.
  • the scavenging port enters the cylinder, so that the exhaust gas after the work in the cylinder is exhausted from the exhaust port of the auxiliary piston on the upper side through the exhaust passage on the auxiliary piston and the exhaust pipe on the cylinder head, when the piston goes to After the bottom dead center moves upward to close the scavenging port on the cylinder, the moving auxiliary piston also moves upward from the lower position, and the exhaust port on the auxiliary piston moves into the small cylinder to cut off the communication with the cylinder.
  • an upper position is moved within the small cylinder forming the largest combustion chamber volume.
  • a sealing ring for sealing the seal between the auxiliary piston and the small cylinder is disposed on the inner wall of the small cylinder, and is sealed on the outer circumferential surface of the auxiliary piston by the inner wall surface of the sealing ring,
  • Each sealing ring is mounted in the step of the corresponding L-shaped sealing ring seat, and a plurality of L-shaped sealing ring seats with sealing rings are laminated together to form a plurality of sealing rings for sealing, in the adjacent two L-shaped
  • the chamfered space of the sealing ring seat is provided with a sealing material, and a plurality of L-shaped sealing ring seats which are stacked together are installed in the L-shaped step formed on the small cylinder block body, and are press-fitted on the bottom surface of the cylinder head The corresponding installation space.
  • variable volume combustor internal combustion engine of the present invention When the above-described variable volume combustor internal combustion engine of the present invention is made into a gasoline engine, in a small cylinder
  • the maximum combustion chamber volume formed by the auxiliary piston being returned to the upper position by the compressed air or the pressure cam is equivalent to a compression ratio of 8:1 to 10:1, and the manufactured diesel engine can achieve a compression ratio of 12:1 to 13:1.
  • the engine is operated by compression ignition.
  • the auxiliary piston in the small cylinder will be pushed back into the cylinder by the returning spring in the crank angle of 35 degrees after the top dead center. Push the piston to work outside.
  • the auxiliary piston is also driven by the auxiliary crankshaft to quickly enter the small cylinder combustion chamber.
  • the clearance volume in the small cylinder plus the clearance volume when the piston is at the top dead center in the cylinder can form a ratio of 30:1 to 50:1.
  • the efficiency of the gasoline engine of the present invention is significantly improved, and the efficiency of the diesel engine of the present invention is further improved than that of the conventional diesel engine.
  • the internal combustion engine of the present invention has a very high relative compression ratio of 30:1 to 50:1, since the work gas is pressed into the cylinder after the piston descends, the highest gas pressure generated in the cylinder near the top dead center is not Very high, does not increase the mechanical load of the transmission.
  • variable volume combustor internal combustion engine with an auxiliary piston according to the present invention will now be described in detail with reference to the accompanying drawings.
  • FIG. 1 is a cross-sectional view showing the structure of a variable volume combustor internal combustion engine employing a passive auxiliary piston according to a first embodiment of the present invention.
  • Figure 2 is a state diagram of the auxiliary piston as it moves to the lower side of the small cylinder combustion chamber.
  • Fig. 3 is a cross-sectional view showing the structure of a variable volume combustor internal combustion engine using a double cam control auxiliary piston in a second embodiment of the present invention.
  • Figure 4 is a structural arrangement view of the cam shaft, the cam and the rocker arm in the direction A in Figure 3 .
  • Figure 5 is the engine of the internal combustion engine of Figure 3 being rapidly pressed into the small cylinder combustion chamber by the return spring control.
  • Figure 6 is a view showing the installation position of the fuel injector and the spark plug of Figure 3.
  • Fig. 7 is a cross-sectional view showing the structure of a variable volume combustor internal combustion engine using an auxiliary crankshaft control auxiliary piston in a third embodiment of the present invention.
  • Figure 8 is a cross-sectional view showing the structure of a two-stroke variable-volume combustor internal combustion engine using an auxiliary crankshaft control auxiliary piston in a fourth embodiment of the present invention
  • Fig. 9 is a view showing a state in which the auxiliary piston of the two-stroke internal combustion engine of Fig. 8 has pressed the working gas in the combustion chamber of the small cylinder into the cylinder to participate in work.
  • Fig. 10 is a view showing a state in which the auxiliary piston and the piston of the two-stroke internal combustion engine are descended to the ventilating position.
  • Figure 11 is a view showing the mounting structure of the small cylinder seal ring of the two-stroke internal combustion engine of Figure 8.
  • the present invention forms a variable volume by providing a small cylinder with an auxiliary piston
  • the auxiliary piston is moved to the upper position to make the small cylinder in the maximum combustion chamber volume state, and the high temperature and high pressure gas required for work is generated by the fuel injection ignition in the maximum volume state of the combustion chamber.
  • the work gas in the small cylinder volume is also pushed by the auxiliary piston and quickly enters the cylinder to participate in the work, so that the work volume formed in the small cylinder and the cylinder during the work is not allowed. It is in a minimum state, thereby further improving the efficiency of the internal combustion engine.
  • variable volume combustor internal combustion engine with auxiliary piston of the present invention mainly comprises four different embodiments depending on the manner in which the auxiliary piston is controlled.
  • 1 is a cross-sectional view showing the structure of a passive auxiliary piston variable volume combustor internal combustion engine which is acted upon by a rebound spring in the first embodiment of the present invention.
  • the internal combustion engine includes a cylinder 21, a piston 22 in a cylinder, and A crankshaft connected to the crankcase via a connecting rod 23.
  • the cylinder head 2 at the side position of the cylinder 21 is provided with a small cylinder 26 constituting a combustion chamber volume that escapes the intake and exhaust valve, and an auxiliary piston 31 is disposed in the small cylinder, and is in communication with the cylinder 21 near the small cylinder 26.
  • An injector 5 directed to the small cylinder is mounted at the air passage.
  • the internal combustion engine of the embodiment of Fig. 1 is made of a diesel engine that is operated by compression ignition by providing an injector 5 on a cylinder block 20 of a cylinder.
  • a spring seat 35 projecting on the bottom of the rebound spring 47 is formed laterally on the skirt 33 of the auxiliary piston 31. The spring seat is in the sliding sleeve 12 on the cylinder head 2 and passes through the skirt 36 on the spring seat.
  • the rebounding spring 47 is mounted under the spring gland 105 on the cover 4 to press the auxiliary piston 31 into the small cylinder 26.
  • the elastic force of the set-up spring 47 on the auxiliary piston should be adjusted.
  • the auxiliary piston 31 should be compressed into the small cylinder by the compressed air. Start moving.
  • a pressure equivalent to a 13:1 compression ratio is reached in the cylinder, the auxiliary piston can be fully pressed into the small cylinder and form the largest combustion chamber volume.
  • the 13:1 compression ratio of the compressed air also allows the fuel injected into the small cylinder combustion chamber to be ignited and ignited.
  • auxiliary piston 31 in the small cylinder 26 in Fig. 1 is being pushed by the compressed air to the uppermost position at the maximum combustion chamber volume state, and the injector 5 is also injecting fuel into the small cylinder.
  • a hydraulic buffer column 62 with a bottom stop 63 extending in the rebound spring 47 is formed on the spring gland 105, in the hydraulic buffer column.
  • a hydraulic oil chamber 64 having upper and lower buffer sections 67, 68 is formed therein, and the hydraulic oil chamber is in communication with the oil supply pipe 80.
  • the sliding rod 40 with the stopper 42 disposed on the auxiliary piston 31 extends in the hydraulic oil chamber 64 of the hydraulic buffer column, and the upper end of the slide 65 for receiving the upper end of the sliding rod 40 on the upper side of the hydraulic oil chamber passes through the communication hole 66 Out of the box.
  • a blocking annulus 69 that limits the removal of the auxiliary piston from the small cylinder 26 is formed on the underside of the lower buffer section 68 of the hydraulic oil chamber.
  • the bottom block 63 of the punch 62 blocks the position to form the largest combustion chamber volume, as shown in the state of FIG.
  • the speed at which the top ring seat 37 on the spring seat 35 of the auxiliary piston is moved over the hydraulic buffer column bottom block 63 is slowed by the stop 42 on the slide bar 40 as it moves to the upper buffer section 67 of the hydraulic oil chamber 64. buffer.
  • the work gas generated in the combustion chamber of the small cylinder 26 starts to push the piston 22 to work downward.
  • the small cylinder is pressurized by the spring 47.
  • the auxiliary piston 31 is also rapidly propelled into the small cylinder combustion chamber, and the working gas in the small cylinder is forced into the cylinder 21 to push the piston 22 to work, as shown in the state of FIG.
  • the auxiliary piston 31 drives the stopper 42 on the connected slide bar 40 to move into the lower buffer section 68 on the lower side of the hydraulic oil chamber 64, the stopper 42 connected to the auxiliary piston falls on the blocking ring surface 69 on the bottom surface of the lower buffer section. The speed is slowed down.
  • the auxiliary piston After the auxiliary piston rapidly presses the working gas in the small cylinder into the cylinder and participates in the work in parallel to the lower position, the small cylinder clearance 115 formed at the bottom of the auxiliary piston 31 is added to the double when the piston 22 is at the top dead center position.
  • the ratio of the cylinder clearance volume 116 above the dotted line to the working volume of the cylinder may correspond to a relative compression ratio of 30:1 to 35:1.
  • the hydraulic oil chamber 64 in the hydraulic buffer column 62 must be filled with the buffer oil before the engine is started.
  • the newly assembled engine is filled with buffer oil in advance into the hydraulic oil chamber.
  • the oil supply pipe 80 provided at the top position passes through the oil filling hole 83 sealed by the cover 82, and then flows downward.
  • the oil passage 84 leads to one side of the hydraulic oil chamber 64, and the other side of the hydraulic oil chamber communicates with the oil return passage 87 that leads to the upper side, and the return oil passage is then small through the inspection hole 86 sealed by the cover 85.
  • the oil hole 88 is in communication with the oil discharge pipe 89.
  • the warmed buffer oil passes through the oil return passage 87 from the upper small oil outlet hole 88 and The oil outlet pipe 89 returns to the oil sump of the engine.
  • the auxiliary piston 31 which is acted upon by the rebound spring also drives the stopper 42 on the upper slide 40 to press against the blocking ring surface 69 on the bottom side of the lower buffer section 68.
  • the oil in the hydraulic oil chamber 64 is not leaked, which is beneficial to the next starting operation of the engine.
  • the hydraulic oil chamber in the hydraulic buffer column after the shutdown and the oil in the corresponding oil passage will partially leak into the slide 65 for accommodating the slide rod, so that the oil in the oil feed passage 84 and the return oil passage 87
  • the liquid level of the liquid is correspondingly reduced to the state shown in Figure 2, but does not affect the next start of the engine.
  • the bottom surface 44 of the stopper 42 is tapered, it is also better to not only seal the oil when the machine is stopped, but also increase the contact area of the impacted portion, and also reduce the movement of the stopper up and down. The resistance generated by the time.
  • the side wall 3 of the cylinder head 2 is provided with the small cylinder 26 facing.
  • the inspection cover 91 at the upper end position, the inner side of the inspection cover serves as an upper and lower air flow passage on the communication auxiliary piston spring seat 35, and a corresponding sliding groove 92 is formed on the inner side of the inspection cover, and the auxiliary piston 31 passes through the upper spring seat 35.
  • the slider 38 mounted in the chute 92 limits the rotation of the auxiliary piston.
  • the auxiliary piston is provided to be controlled by the rebound spring and the pressing cam, as shown in FIG.
  • the cylinder head 2 at the side position of the cylinder 21 is provided with a small cylinder 26 constituting a combustion chamber volume that escapes the intake and exhaust valve, and an auxiliary piston 31 is disposed in the small cylinder, and is in communication with the cylinder 21 near the small cylinder 26.
  • a spark plug 6 directed to the small cylinder is mounted at the air passage.
  • the spark plug 6 is mounted on the cylinder block 20 near the cylinder and directs the spark plug to the air passage 28 communicating with the small cylinder.
  • the engine is ignited by a spark plug, and the volume of the combustion chamber in the small cylinder 26 is equivalent to a compression ratio of 8:1 to 10:1.
  • the injector can be installed outside the cylinder and the throttle valve can be used to adjust the power. If the injector is installed next to the spark plug for in-cylinder injection, the throttle can be removed to improve the efficiency of the engine at low and medium power.
  • the connecting ram 45 on the auxiliary piston 31 is integrated with the upper spring retainer 46 via a gland 13 fixed through the upper side of the small cylinder 26 on the cylinder head 2, and the spring retainer is passed through the side skirt 36 thereon.
  • a sliding rebound spring 47 is mounted between the spring retaining seat 46 and the spring gland 105 on the cover 4, and the rebound spring is movable through the spring retaining seat 46 and the connecting jack 45.
  • the auxiliary piston 31 is pushed out from the inside of the small cylinder 26 quickly.
  • a connecting pin 51 hinged to the inner ends of the rocker arms 54 on the left and right sides is mounted on the connecting ram 45 below the spring retainer 46 via the pivot pin 48 provided thereon, and the rocker arms 54 on both sides pass through the middle of the middle
  • the shaft 53 is mounted on the corresponding supporting swing arm 59 provided on the left and right shaft seats 19 on the cylinder head, and the outer ends of the left and right rocker arms 54 are pressed by the corresponding left and right camshafts 99, 90 through the roller 55 provided.
  • the movable cam 70 is simultaneously pressed and controlled, and a limit stop 50 that can be seated on the gland 13 is formed on the lower side of the position of the shaft pin 48 on the connecting jack 45.
  • the auxiliary piston 31 adopts a structure controlled by the rocker arms 54 on both sides. Since the rollers 55 on the rocker arms on both sides are opposite to the direction of movement of the auxiliary piston, the auxiliary piston can be The inertial forces moving up and down are balanced accordingly.
  • the auxiliary piston 31 has been driven to move into the inside of the small cylinder 26 to form the largest combustion chamber volume, and enters the small cylinder combustion.
  • the fuel compression mixture in the chamber is ignited by the spark plug 6, and the formed work gas enters the cylinder 21 to push the piston 22 down.
  • the pressing cam 70 on the left and right camshafts also rotates through the roller 55 on the left and right rocker arms 54, and the rebounding spring 47 that is not pressed will quickly drive the auxiliary piston 31 to the small cylinder.
  • the work gas in the 26 is rapidly pressed into the cylinder 21 as the piston 22 is pressed into the work. Let the work gas originally in the combustion chamber be pressed into the cylinder to expand.
  • the roller 55 on the left and right rocker arms 54 also falls to the descending buffer section 49 on the pressing cam 70 of the left and right camshafts, causing the auxiliary piston to move. The speed to the outer position is buffered accordingly.
  • the auxiliary piston control mechanism shown in Figure 3 is applicable to both a gasoline engine and a small cylinder combustion chamber volume equivalent to a 9:1 compression ratio.
  • the inner ends of the two swing arms 54 may also be directly hinged under the spring retainer 46 to move to the lower position and avoid the gland.
  • the connecting plate 51 of 13 is supported by the shaft seat 61 on both sides of the gland by the middle portion, and then the connecting plate 51 is allowed. Both ends are hinged to the lower portion of the support swing arm 59. This arrangement also increases the strength of the connection between the inner ends of the two swing arms 54 and the spring retainers 46.
  • the rocker arm mounting method as shown in Fig. 4 can be employed to allow the cam shaft 90 provided on the intake and exhaust valve side.
  • the pressing cam 70 is at an intermediate position, and the inlet and exhaust cams 108, 109 are respectively disposed on both sides of the pressing cam, and the rocker arm 18 controlled by the intake and exhaust cams is mounted on the shaft between the two cylinders 21, respectively.
  • the outer side of the shaft pin 17 fixed on the 16 and allows the intermediate pressing cam 70 to be rotated between the shaft pins on both sides.
  • variable-volume combustion chamber internal combustion engine that is made into a gasoline engine should cancel the throttle valve and use the in-cylinder injection to form a fuel-fuel mixture to avoid buffering the spring force of the rebound spring due to the decrease of the intake air amount in the cylinder.
  • the arrangement of the injector and the spark plug is as shown in Fig. 6.
  • the injector 5 together with the spark plug 6 can be arranged at the side of the cylinder on the cylinder 20 so that the oil mist sprayed from the injector can be ignited above the spark plug. .
  • Fig. 7 shows a variable volume combustor internal combustion engine according to a third embodiment of the present invention, in which the auxiliary piston is driven by an auxiliary crankshaft.
  • such an engine includes a cylinder 21, a piston 22 in the cylinder, and a crankshaft 24 coupled to the crankcase via a connecting rod 23.
  • the cylinder head 2 at the side position of the cylinder 21 is provided with a small cylinder 26 constituting a combustion chamber volume that escapes the intake and exhaust valve, and an auxiliary piston 31 is disposed in the small cylinder, and is in communication with the cylinder 21 near the small cylinder 26.
  • An injector 5 directed to the small cylinder is mounted at the air passage.
  • the auxiliary piston 31 in the small cylinder needs to extend into the cylinder 21 for a long stroke, the diameter of the small cylinder is required to be not too large so as to be arranged on the side of the intake and exhaust valve, which also requires that the volume of the small cylinder combustion chamber is not too large.
  • the engine of this type of construction in Fig. 7 is only suitable for a diesel engine that is ignited by compression ignition.
  • the auxiliary piston 31 in the small cylinder 26 is connected to the lower end of the intermediate link 74 via the piston pin 34 thereon, and the upper end of the intermediate link is passed through the link pin 73 and the connecting rod 72 on the auxiliary crankshaft 71 on the upper side of the cylinder head.
  • the two ends of the link pin 73 between the two links are also hinged to the swing end of the swing arm 57, and the other end of the swing arm is mounted on the shaft seat 19 of the side wall 3 of the cylinder head through the shaft pin 58 to assist
  • the crankshaft 71 has the same rotational speed as the crankshaft 24.
  • the auxiliary piston 31 in the small cylinder 26 is also driven by the auxiliary crankshaft to move into the upper side of the small cylinder to form the largest combustion chamber volume (as shown by the two-dot chain line in the figure). The 31' position is shown), and the working gas is generated in the small cylinder.
  • the auxiliary piston 31 in the small cylinder 26 is moved. It is driven by the auxiliary crankshaft 71 to first press all the working gas in the small cylinder combustion chamber into the cylinder to participate in the work (shown by the double-dot chain line 31'' position in the figure), and then to be extended to enter the cylinder 21.
  • the auxiliary piston 31 having a longer stroke in the small cylinder 26 is also moved out of the small cylinder into the cylinder 21 by a certain distance (as shown by the auxiliary piston 31 in Fig. 7).
  • the auxiliary piston in the small cylinder is also driven by the auxiliary crankshaft 71 to return to the small cylinder 26 and then out of the small cylinder and into the cylinder 21.
  • the up and down movement of the auxiliary piston during the exhaust and intake process does not promote the efficiency of the work process, but will occupy a small part of the cylinder working volume during the intake process, and also increase the mechanism of the mechanism. Running wear. It is hoped that the ineffective movement of the auxiliary piston during the exhaust and intake process will not cause large mechanical friction loss, such as not exceeding 1/6 of the gain of efficiency obtained.
  • the auxiliary piston is controlled by the auxiliary crankshaft. The method is simple and reliable in structure, and the balance weight on the auxiliary crankshaft also cancels the reciprocating inertial vibration force generated by some auxiliary pistons and the like.
  • the engine schemes given in the above embodiments are all internal combustion engines operating in a four-stroke manner, and the fourth two-stroke variable-volume combustor internal combustion engine of the present invention is shown in Fig. 8, as shown in Fig. 8.
  • the internal combustion engine includes a cylinder 21, a piston 22 in the cylinder, and a crankshaft 24 connected to the crankcase via a connecting rod 23, and a scavenging port 25 communicating with the compressor 118 at a bottom dead center position of the cylinder 21 is provided at the cylinder 21
  • the cylinder head 2 is provided with a small cylinder 26 constituting a combustion chamber volume, an auxiliary piston 31 is arranged in the small cylinder, and an injector 5 is arranged on the side wall of the small cylinder, and the auxiliary piston 31 adopts a segmented combined structure.
  • the intermediate piston rod 39 is integrally connected with the upper skirt 110, and the skirt pin is hinged to the small end of the connecting rod 72 on the auxiliary crankshaft 71 on the upper side of the cylinder head 2 via the piston pin 34 thereon, and the auxiliary crankshaft 71 is
  • the crankshaft 24 in the crankcase 112 has the same rotational speed.
  • a transition skirt portion 78 is formed on the upper side of the auxiliary piston 31 in the direction of the skirt 110, and a plurality of uniform exhaust ports 77 are formed at the upper position of the transition skirt portion at the junction with the auxiliary piston 31, in the transition skirt portion 78.
  • An exhaust passage 76 is formed around the piston rod 39.
  • the upper end of the transition skirt is spaced from the bottom surface of the upper skirt 110 by a certain distance to form an air outlet opening 75, correspondingly spaced apart from the combustion chamber of the small cylinder 26
  • the small cylinder side wall 27 is provided with an annular exhaust passage 79 communicating with the exhaust duct 29.
  • the driven auxiliary piston 31 projects into the cylinder 21; when the piston 22 descends near the bottom dead center and communicates with the scavenging port 25 on the cylinder 21, it moves to
  • the exhaust port 77 on the auxiliary piston 31 in the lower position also communicates with the upper side of the cylinder 21, while the outlet opening 75 in the auxiliary piston communicating with the exhaust port 77 via the exhaust passage 76 is also ring-shaped on the side wall of the small cylinder.
  • the exhaust passage 79 is in a communicating state, at which time the scavenging gas supplied from the compressor 118 enters the cylinder from the scavenging port 25 on the cylinder 21, so that the exhaust gas after the work in the cylinder is exhausted from the upper auxiliary piston 31.
  • the port 77 is discharged outward through the exhaust passage 76 on the auxiliary piston and the exhaust duct 29 on the cylinder head 2.
  • the simultaneously moving auxiliary piston 31 also moves upward from the lower position, and the exhaust port 77 on the auxiliary piston moves into the small cylinder 26 to cut off the cylinder 21.
  • the communication is completed, and the intake and exhaust ventilation process performed in the cylinder is completed.
  • the auxiliary piston 31 that moves upward also exits the cylinder 21, moving to the upper position in the small cylinder 26 to form the maximum combustion chamber volume, so as to start the next combustion.
  • the process of work is performed.
  • auxiliary piston Since the auxiliary piston has a long stroke and needs to extend into the cylinder, if a seal ring is provided on the auxiliary piston, it will be stuck outside the small cylinder.
  • a seal ring 101 sealed between the cylinders 26 is provided on the inner wall of the small cylinder, and is sealed by the inner wall surface of the seal ring on the outer circumferential surface of the auxiliary piston 31, and each seal ring 101 is mounted on the corresponding L-shaped seal ring seat 102.
  • a plurality of L-shaped sealing ring seats 102 equipped with a sealing ring 101 are laminated together to form a plurality of sealing rings for sealing, and are installed in the chamfered space 104 of the adjacent two L-shaped sealing ring seats 102.
  • the sealant is added, and a plurality of L-shaped seal ring seats 102 which are stacked together are installed in the L-shaped step formed on the small cylinder block 100, and are press-fitted in the corresponding installation spaces on the bottom surface of the cylinder head 2.
  • Figure 11 only the corresponding sealing ring is provided. If necessary, an oil ring can be added to the upper side of the sealing ring, and a small amount of lubricating oil is injected between the oil ring and the sealing ring.
  • the auxiliary piston is controlled by the auxiliary crankshaft and the connecting rod, and is structurally simple and reliable.
  • the auxiliary piston with segmented combination structure plays a dual role, not only to press the high temperature and high pressure gas in the small cylinder into the cylinder on the lower side during the work process, but also as the exhaust valve in the two stroke ventilation process. exhaust.
  • the two-stroke internal combustion engine composed of the auxiliary piston and the air exchange is ventilated by direct current, and the exhaust port on the auxiliary piston can be quickly closed at the end of the exhausting process, so that the cylinder can obtain a better ventilation effect.
  • the auxiliary piston extend into the cylinder to match the air exchange also occupies the intake volume of a small number of cylinders, and the displacement of the cylinder needs to be increased to supplement the volume occupied by the auxiliary piston.

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

Abstract

L'invention concerne un moteur à combustion interne ayant une chambre de combustion à volume variable et un piston auxiliaire. Le moteur à combustion interne comprend un cylindre (21), un piston (22), et un vilebrequin relié selon un mode de transmission par une bielle (23). Une position sur une tête de cylindre (2) et proche d'un côté du cylindre comporte un petit cylindre (26) constituant un volume de chambre de combustion, et le piston auxiliaire commandé (31) est monté à l'intérieur du petit cylindre. Quand un processus de compression est achevé à l'intérieur du cylindre (21), le piston auxiliaire (31) à l'intérieur d'une chambre de combustion de petit cylindre est également entraîné à se déplacer vers une position formant un volume de chambre de combustion maximal, et après que le cylindre (21) a commencé un processus de réalisation de travail, le piston auxiliaire presse rapidement un gaz de réalisation de travail produit à l'intérieur de la chambre de combustion de petit cylindre dans le cylindre pour pousser le piston (22) de façon à effectuer un travail, amenant un volume d'espacement formé entre le petit cylindre (26) et le cylindre (21) à être dans un état minimal, de sorte que le gaz de réalisation de travail qui a été détendu à l'origine dans la chambre de combustion est pressé dans le cylindre pour se détendre et effectuer un travail, ce qui permet d'augmenter encore le rendement du moteur à combustion interne.
PCT/CN2016/000164 2015-03-25 2016-03-23 Moteur à combustion interne ayant une chambre de combustion à volume variable et un piston auxiliaire Ceased WO2016150231A1 (fr)

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CN108625980A (zh) * 2018-07-19 2018-10-09 高文峰 一种可变燃烧室二冲程汽油发动机
CN108661785A (zh) * 2018-07-26 2018-10-16 谭建文 无曲轴旋转式阿特金森循环发动机
WO2019021068A1 (fr) * 2017-07-27 2019-01-31 Wijesinghe Sunil Moteur à combustion interne ayant un taux de compression variable
CN116519917A (zh) * 2023-03-16 2023-08-01 国网浙江省电力有限公司经济技术研究院 一种co2预碳酸化强化触变特性非牛顿流体试验装置及其试验方法

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CN104791076A (zh) * 2015-03-25 2015-07-22 韩培洲 带有辅助活塞的可变容积燃烧室内燃机
CN105909382A (zh) * 2016-04-29 2016-08-31 韩培洲 用辅助曲轴带动辅助活塞的可变容积燃烧室内燃机
CN105840337B (zh) * 2016-05-06 2018-05-25 陈光明 可控弹性内燃机
CN111720212B (zh) * 2019-03-19 2022-02-18 上海汽车集团股份有限公司 一种用于降排放的发动机控制方法和发动机装置
CN111894758A (zh) * 2020-08-27 2020-11-06 重庆潍柴发动机有限公司 一种气缸盖及其内燃机

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CN108661785A (zh) * 2018-07-26 2018-10-16 谭建文 无曲轴旋转式阿特金森循环发动机
CN108661785B (zh) * 2018-07-26 2024-01-23 谭建文 无曲轴旋转式阿特金森循环发动机
CN116519917A (zh) * 2023-03-16 2023-08-01 国网浙江省电力有限公司经济技术研究院 一种co2预碳酸化强化触变特性非牛顿流体试验装置及其试验方法

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