WO2016150231A1 - 带有辅助活塞的可变容积燃烧室内燃机 - Google Patents
带有辅助活塞的可变容积燃烧室内燃机 Download PDFInfo
- 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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- cylinder
- piston
- auxiliary piston
- small cylinder
- auxiliary
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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
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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
- 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
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- 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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Abstract
一种带有辅助活塞的可变容积燃烧室内燃机,包括汽缸(21)、活塞(22)和经连杆(23)传动相连的曲轴,在缸盖(2)上的靠汽缸侧边位置处设有构成燃烧室容积的小汽缸(26),小汽缸中装有被控制的辅助活塞(31),当汽缸(21)内完成压缩过程时,小汽缸燃烧室中的辅助活塞(31)也被带动移到形成最大燃烧室容积的位置处,在汽缸(21)开始作功过程后,辅助活塞则把小汽缸燃烧室中所产生的作功燃气迅速压进汽缸内推动活塞(22)作功,使小汽缸(26)和汽缸(21)之间所形成的余隙容积处于最小状态,让原来在燃烧室膨胀的作功燃气被压进汽缸膨胀作功,从而进一步提高了内燃机的效率。
Description
技术领域 本发明涉及一种内燃机,特别是一种带有辅助活塞的可变容积燃烧室内燃机。
背景技术 内燃机主要包括汽油机和柴油机,在一般的汽油机和柴油机中,通过采用较高的压缩比是提高效率的主要方式。汽油机由于受爆震的影响,压缩比一般在10∶1以内。柴油机由于采用压燃点火方式,可让压缩比达到13∶1~20∶1。压缩比越高相当于燃烧室的容积越小,留在燃烧室容积内不能参与作功的燃气就相对越少,让发动机的效率也相应越高。但在汽油机中压缩比也不能很高,柴油机中的压缩比越高,汽缸内的燃气压力也就相应越大,会让柴油机变得更为笨重。实际中即使让柴油机采用了20∶1很高的压缩比,燃烧室中的这部分燃气仍不能全部参与汽缸中的作功过程。
发明内容 本发明的目的是提供一种带有辅助活塞的可变容积燃烧室内燃机,在汽缸内开始进行燃烧作功过程后,尽快让小汽缸燃烧室中的辅助活塞下行、把小汽缸燃烧室容积内的大部分作功燃气推到汽缸中作功,从而让发动机的效率进一步提高。
本发明的带有辅助活塞的可变容积燃烧室内燃机包括五种不同实施方式,第一种实施方式中的带有辅助活塞的可变容积燃烧室内燃机包括汽缸、汽缸中的活塞和经连杆与曲轴箱中传动相连的曲轴,在汽缸侧边位置处的缸盖上设有躲开进排气门的构成燃烧室容积的小汽缸,在小汽缸中装有辅助活塞,在靠近小汽缸与汽缸连通的通气道处装有指向小汽缸的喷油器或火花塞,在辅助活塞的裙部上侧向外延出形成有顶在回涨弹簧底部的弹簧座,该弹簧座处在缸盖上的滑套中,并通过弹簧座上的边裙在滑套内相应滑动,所设的回涨弹簧装在机盖上的弹簧压盖下面,使辅助活塞受到压进小汽缸的作用力,在弹簧压盖上形成有伸在回涨弹簧中的带有底部挡座的液力缓冲柱,在液力缓冲柱内形成有带上、下缓冲段的液压油腔,该液压油腔与供油管连通,辅助活塞上所设的带有挡塞的滑杆伸在液力缓冲柱的液压油腔中,液压油腔上侧的容纳滑杆上端的滑道上端经连通孔向外通出,在液压油腔的下缓冲段的底侧形成有可限制辅助活塞移出小汽缸的阻挡环面;当汽缸内完成压缩过程、活塞移到上止点位置时,小汽缸内的辅助活塞也在压缩空气作用下克服回涨弹簧的弹力后上移到被液力缓冲柱的底部
挡座所阻挡位置,形成最大的燃烧室容积,辅助活塞的弹簧座上的顶环座上移顶在液压缓冲柱底部挡座上的速度由滑杆上的挡塞在移到液压油腔的上缓冲段时被减速缓冲;当汽缸内完成压缩过程开始进行作功过程后,小汽缸燃烧室内所产生的作功燃气开始推动活塞下行作功,随着活塞下行作功,小汽缸内被回涨弹簧压力作用的辅助活塞也被迅速推进小汽缸燃烧室内,把小汽缸内的作功燃气压进汽缸推动活塞作功,当辅助活塞带动相连的滑杆上的挡塞移进液压油腔下侧的下缓冲段后,使与辅助活塞相连的挡塞落在下缓冲段底面的阻挡环面上的速度被减速缓冲。
在对液压油腔的连接油路设置中,由设在顶部位置的供油管经用封盖密封的注油孔后向下又经进油路通向液压油腔的一侧,液压油腔的另一侧与通向上侧的回油路相通,该回油路再经用封盖密封的检查孔后经小出油孔与出油管连通。
在缸盖的侧壁上装有面向小汽缸上端位置的检查盖,该检查盖的内侧即作为连通辅助活塞弹簧座上的上下侧气流通道,还在检查盖的内侧形成有相应的滑槽,辅助活塞通过其上弹簧座上所安装的处在滑槽中的滑块限制辅助活塞回转。
在本发明第二种带有辅助活塞的可变容积燃烧室内燃机中,这种发动机包括汽缸、汽缸中的活塞和经连杆与曲轴箱中传动相连的曲轴,在汽缸侧边位置处的缸盖上设有躲开进排气门的构成燃烧室容积的小汽缸,在小汽缸中装有辅助活塞,在靠近小汽缸与汽缸连通的通气道处装有指向小汽缸的喷油器或火花塞,辅助活塞上的连接顶杆经穿过缸盖上的小汽缸上侧所固定的压盖与上端的弹簧挡座连成一体,弹簧挡座通过其上的边裙可在缸盖上的滑套中相应滑动,在弹簧挡座与机盖上的弹簧压盖之间装有回涨弹簧,该回涨弹簧经弹簧挡座和连接顶杆可把辅助活塞从小汽缸的内侧迅速向外压出,在弹簧挡座下面的连接顶杆上通过其上所设的轴销装有与左右两侧的摇臂内端相铰接的连接板,两侧的摇臂通过中部的中间轴安装在缸盖上的左右轴座上所设的相应支撑摆臂上,左右两摇臂的外端通过所设的滚轮可被相应的左、右凸轮轴上的压动凸轮同时压动控制,在连接顶杆上的轴销位置下侧形成有可落座在压盖上的限位挡盘;当汽缸内进行压缩过程、活塞向上止点位置移动时,左右凸轮轴上的压动凸轮也同时通过左右的两摇臂在克服回涨弹簧的压力后带动辅助活塞向小汽缸内移动,当活塞移到上止点完成压缩过程,将要进行作功过程时,辅助活塞已被带动移
进小汽缸内侧形成最大的燃烧室容积,进入小汽缸燃烧室中的压缩空气被喷油点火、所形成的作功燃气进入汽缸中推动活塞下行作功,活塞下行作功后,左右凸轮轴上的压动凸轮也转过左右摇臂上的滚轮,不被压动的回涨弹簧便迅速带动辅助活塞把小汽缸内的作功燃气随着活塞的下行快速压进汽缸参与作功;当辅助活塞将要移到小汽缸外侧时,左右摇臂上的滚轮也落到左右凸轮轴的压动凸轮上的降程缓冲段,使辅助活塞移到外侧位置时的速度被相应缓冲。
也可以让两摆臂的内端直接铰接在弹簧挡座的下面,让挪到下侧位置并躲开压盖的连接板通过中部被压盖两侧的轴座支撑,再让连接板两端与支撑摆臂的下部相铰接。
在凸轮轴上的各凸轮布置中,设在进排气门侧的凸轮轴上的压动凸轮处于中间位置,在压动凸轮两侧分别设有进、排气凸轮,相应地被进、排气凸轮控制的摇臂安装在两汽缸之间位置的轴痤上所固定的轴销的外侧。
在本发明第三种带有辅助活塞的可变容积燃烧室内燃机中,这种发动机包括汽缸、汽缸中的活塞和经连杆与曲轴箱中传动相连的曲轴,在汽缸侧边位置处的缸盖上设有躲开进排气门的构成燃烧室容积的小汽缸,在小汽缸中装有辅助活塞,在靠近小汽缸与汽缸连通的通气道处装有指向小汽缸的喷油器,小汽缸内的辅助活塞经其上的活塞销与中间连杆的下端相连,中间连杆的上端经连杆销与缸盖上侧的辅助曲轴上的连杆小头相铰接,两连杆之间的连杆销的两侧还与摆臂的摆动端相铰接,摆臂的另一端通过轴销安装在缸盖侧壁的轴座上,辅助曲轴与曲轴的转速相同;当汽缸中的活塞行到上止点完成压缩过程时,小汽缸内的辅助活塞也被辅助曲轴带动移进小汽缸上侧形成最大的燃烧室容积、并在小汽缸内产生作功燃气,当汽缸内的活塞被作功燃气推动作功开始向下止点方向移动时,小汽缸内的辅助活塞被辅助曲轴带动先把小汽缸燃烧室内的作功燃气全部压进汽缸参与作功、随后又被带动伸出小汽缸进入汽缸内,当汽缸中的活塞行到下止点位置时,小汽缸中行程较长的辅助活塞也移出小汽缸伸进汽缸内一定的距离;在随后的排气和进气过程中,小汽缸中的辅助活塞也会被辅助曲轴带动返回小汽缸后又移出小汽缸并伸进汽缸。
在本发明第四种带有辅助活塞的可变容积燃烧室内燃机中,这种发动机包括汽缸、汽缸中的活塞和经连杆与曲轴箱中传动相连的曲轴,在汽缸的下止点位置上设有与压气机相连通的扫气口,在汽缸的缸盖上设有构成
燃烧室容积的小汽缸,在小汽缸中装有辅助活塞,在小汽缸的侧壁上装有喷油器或火花塞,辅助活塞采用分段式组合结构、经中间的活塞杆与上部的裙塞连成一体,裙塞再经其上的活塞销与缸盖上侧的辅助曲轴上的连杆的小头相铰接,辅助曲轴与曲轴箱内的曲轴转速相同,在辅助活塞的上侧向裙塞方向形成有过渡裙部,在过渡裙部与辅助活塞相连接处的以上位置形成有若干均布的排气口,在过渡裙部内形成了围绕着活塞杆的排气道,过渡裙部的上端与上侧的裙塞的底面距有一定的距离形成出气开口,相应地在与小汽缸的燃烧室相隔一定距离的小汽缸侧壁上设有与排气管道相连通的环形排气道;当汽缸中的活塞行到上止点位置完成压缩过程时,小汽缸内的辅助活塞也被辅助曲轴带动移进小汽缸上部形成最大燃烧室容积、并在小汽缸内产生作功燃气,当汽缸内的活塞被作功燃气推动作功开始向下止点方向移动时,小汽缸内的辅助活塞被辅助曲轴带动也向下移动、把小汽缸中的作功燃气压进汽缸参与作功,随着活塞的下行作功,被带动的辅助活塞伸进汽缸;当活塞下行接近下止点并与汽缸上的扫气口沟通时,移到下部位置的辅助活塞上的排气口也与汽缸的上侧沟通,同时,辅助活塞内经排气通道与排气口相连通的出气开口也与小汽缸侧壁上的环形排气道处于相通状态,这时由压气机提供的扫气便从汽缸上的扫气口进入汽缸,使汽缸内作功后的废气从上侧的辅助活塞上露出的排气口经辅助活塞上的排气通道和缸盖上的排气管道向外排出,当活塞行到下止点向上移动关闭汽缸上的扫气口后,同时移动的辅助活塞也离开下部位置向上移动、让辅助活塞上的排气口移进小汽缸切断与汽缸的连通,汽缸内所进行的进排气换气过程完成;随着活塞向上移动进行压缩过程到达上止点位置后,同时向上移动的辅助活塞也退出汽缸,移到小汽缸内的上部位置形成最大燃烧室容积。
对于小汽缸和辅助活塞之间的密封,用于密封辅助活塞和小汽缸之间密封的密封环设在小汽缸内壁上,通过密封环的内壁面压在辅助活塞的外圆周面上进行密封,每个密封环装在相应的L型密封环座的台阶内,由多个装有密封环的L型密封环座叠压在一起,构成多道密封环进行密封,在相邻的两L型密封环座的倒角空间内装有密封添料,所设的多个叠压在一起的L型密封环座装在小汽缸缸体上所形成的L形台阶内,并压装在缸盖底面的相应安装空间里。
当把上述本发明的可变容积燃烧室内燃机制成汽油机时,小汽缸中的
辅助活塞被压缩空气或压动凸轮作用回到上部位置所形成的最大燃烧室容积相当于8∶1~10∶1的压缩比,被制成的柴油机可达到12∶1~13∶1的压缩比,发动机靠压燃点火作功。不论被制成的是四行程汽油机还是柴油机,在作功过程开始后,小汽缸内的辅助活塞都会被回涨弹簧在上止点后35度曲轴转角内迅速把燃烧室内的作功燃气压入汽缸中推动活塞对外作功。在被制成的二行程内燃机中,辅助活塞也会被辅助曲轴带动迅速进入小汽缸燃烧室。在辅助活塞移到下侧位置、小汽缸燃烧室处于最小容积状态后,小汽缸内的余隙容积加上汽缸中活塞处于上止点时的余隙容积可形成30∶1~50∶1的很高相对压缩比,只有余隙容积内的少量燃气不能进入汽缸作功,从而让本发明的汽油机效率明显提高,让本发明的柴油机效率比普通柴油机进一步提高。虽然本发明的内燃机具有30∶1~50∶1的很高相对压缩比,但由于作功燃气是在活塞下行后被压进汽缸,汽缸中在上止点附近所产生的最高燃气压力并不很高,不会增加传动机构的机械负荷。
附图说明 下面结合附图对本发明的带有辅助活塞的可变容积燃烧室内燃机进行详细的说明。
图1是本发明第一实施方式中采用被动式辅助活塞的可变容积燃烧室内燃机的结构剖视图。
图2是辅助活塞移到小汽缸燃烧室下侧位置时的状态图。
图3是本发明第二实施方式中采用双侧凸轮控制辅助活塞的可变容积燃烧室内燃机的结构剖视图。
图4是沿图3中A向的凸轮轴、凸轮和摇臂的结构布置图。
图5是图3中内燃机辅助活塞被回涨弹簧控制迅速压进小汽缸燃烧室。
图6是图3中喷油器和火花塞的安装位置图。
图7是本发明第三实施方式中采用辅助曲轴控制辅助活塞的可变容积燃烧室内燃机的结构剖视图。
图8是本发明第四实施方式中采用辅助曲轴控制辅助活塞的二冲程可变容积燃烧室内燃机的结构剖视图
图9是图8中二冲程内燃机的辅助活塞已把小汽缸燃烧室内的作功燃气压进汽缸中参与作功的状态图。
图10是二冲程内燃机的辅助活塞和活塞下行到换气位置的状态图。
图11是图8中二冲程内燃机的小汽缸密封环的安装结构图。
具体实施方式 本发明通过设置带有辅助活塞的小汽缸形成可变容积
燃烧室,在压缩过程结束时让辅助活塞移到上侧位置使小汽缸处于最大燃烧室容积状态,并在燃烧室最大容积状态下通过喷油点火产生作功所需的高温高压燃气,在作功过程开始后,随着活塞下行作功,小汽缸容积内的作功燃气也会被辅助活塞推动、迅速进入汽缸参与作功,让作功时小汽缸和汽缸内所形成的不能作功容积处于最小状态,从而进一步提高了内燃机的效率。根据辅助活塞被控制作用的方式不同,本发明的这种带有辅助活塞的可变容积燃烧室内燃机主要包括四种不同的实施方式。图1给出的是本发明第一实施方式中采用由回涨弹簧作用的被动式辅助活塞可变容积燃烧室内燃机的结构剖视图,在图1中,这种内燃机包括汽缸21、汽缸中的活塞22和经连杆23与曲轴箱中传动相连的曲轴。在汽缸21侧边位置处的缸盖2上设有躲开进排气门的构成燃烧室容积的小汽缸26,在小汽缸中装有辅助活塞31,在靠近小汽缸26与汽缸21连通的通气道处装有指向小汽缸的喷油器5。图1实施方式中的内燃机通过在汽缸的缸体20上设置喷油器5制成的是以压燃点火工作的柴油机。在辅助活塞31的裙部33上侧向外延出形成有顶在回涨弹簧47底部的弹簧座35,该弹簧座处在缸盖2上的滑套12中,并通过弹簧座上的边裙36在滑套内相应滑动,所设的回涨弹簧47装在机盖4上的弹簧压盖105下面,使辅助活塞31受到压进小汽缸26的作用力。所设的顶在辅助活塞上的回涨弹簧47的弹力应调整在当汽缸内达到相当于8∶1~10∶1压缩比的压缩空气压力时,辅助活塞31被压缩空气作用应该向小汽缸内开始移动。当汽缸内达到相当于13∶1压缩比的压力时,辅助活塞能被完全压进小汽缸并形成最大的燃烧室容积。13∶1压缩比的压缩空气升温也能让喷入小汽缸燃烧室中的燃油被压燃点火。图1中小汽缸26内的辅助活塞31正被压缩空气推到最上侧位置处于最大燃烧室容积状态,喷油器5也正在向小汽缸内喷入燃油。为减小辅助活塞在上下移动时产生的冲击并限制其行程,在弹簧压盖105上形成有伸在回涨弹簧47中的带有底部挡座63的液力缓冲柱62,在液力缓冲柱内形成有带上、下缓冲段67、68的液压油腔64,该液压油腔与供油管80连通。辅助活塞31上所设的带有挡塞42的滑杆40伸在液力缓冲柱的液压油腔64中,液压油腔上侧的容纳滑杆40上端的滑道65上端经连通孔66向外通出。在液压油腔的下缓冲段68的底侧形成有可限制辅助活塞移出小汽缸26的阻挡环面69。当汽缸21内完成压缩过程、活塞22移到上止点位置时,小汽缸26内的辅助活塞31也在压缩空气作用下克服回涨弹簧47的弹力后上移到被液力缓
冲柱62的底部挡座63所阻挡位置,形成最大的燃烧室容积,如图1中状态所示。辅助活塞的弹簧座35上的顶环座37上移顶在液压缓冲柱底部挡座63上的速度由滑杆40上的挡塞42在移到液压油腔64的上缓冲段67时被减速缓冲。当汽缸21内完成压缩过程开始进行作功过程后,小汽缸26燃烧室内所产生的作功燃气开始推动活塞22下行作功,随着活塞下行作功,小汽缸内被回涨弹簧47压力作用的辅助活塞31也被迅速推进小汽缸燃烧室内,把小汽缸内的作功燃气压进汽缸21推动活塞22作功,如图2中状态所示。当辅助活塞31带动相连的滑杆40上的挡塞42移进液压油腔64下侧的下缓冲段68后,使与辅助活塞相连的挡塞42落在下缓冲段底面的阻挡环面69上的速度被减速缓冲。
在辅助活塞迅速把小汽缸内的作功燃气压进汽缸参与作功并行到下侧位置后,辅助活塞31底部所形成的小汽缸余隙容积115加上活塞22处于上止点位置时的双点划线以上的汽缸余隙容积116与汽缸的工作容积之比可相当于30∶1~35∶1的相对压缩比。虽然本发明的可变容积燃烧室内燃机达到很高的相对压缩比,但被制成柴油发动机的实际运行最高工作压力只相当于13∶1压缩比时所产生的最高工作压力,在发动机增加动力和提高工作效率后,活塞、连杆和曲轴等所受的最大压力并未增加,不会让动力传动机构更为笨重。
由于为减少辅助活塞在上下移动时所受的冲击而采用了液力缓冲结构,发动机起动运转前,液力缓冲柱62内的液压油腔64内必须要先充入缓冲油液,为能在刚装配完的发动机上向液压油腔内提前充入缓冲油液,如图1所示,由设在顶部位置的供油管80经用封盖82密封的注油孔83后向下又经进油路84通向液压油腔64的一侧,液压油腔的另一侧与通向上侧的回油路87相通,该回油路再经用封盖85密封的检查孔86后经小出油孔88与出油管89连通。在发动机运转过程中,从供油管80来的油液流过液力缓冲柱上的液压油腔64后,已升温的缓冲油液经回油路87从上侧的小出油孔88和出油管89返回发动机的油池。
当这种辅助活塞采用液压结构来缓冲的发动机停止运转后,被回涨弹簧作用的辅助活塞31也带动其上滑杆40上的挡塞42压在下缓冲段68底侧的阻挡环面69上,使液压油腔64内的油液不会外泄,有利于发动机的下一次起动运转。当然,停机后的液力缓冲柱内的液压油腔和相应油路中的油液会部分的泄漏进容纳滑杆的滑道65,使进油路84和回油路87内油
液的液面高度相应降低到如图2所示状态,但并不会影响发动机下一次起动。在把挡塞42的底面44制成锥形时,还可形成更好的既有利于停机时密封油液、也相应加大了受冲击部位的接触面积,并且还能减小挡塞上下移动时所产生的阻力。
由于辅助活塞是经一个较深的滑套12装入小汽缸26内的,为方便带有活塞环的辅助活塞31能装入小汽缸,在缸盖2的侧壁3上装有面向小汽缸26上端位置的检查盖91,该检查盖的内侧即作为连通辅助活塞弹簧座35上的上下侧气流通道,还在检查盖的内侧形成有相应的滑槽92,辅助活塞31通过其上弹簧座35上所安装的处在滑槽92中的滑块38限制辅助活塞回转。
在图3中给出的本发明第二实施方式可变容积燃烧室内燃机中,所设的辅助活塞被回涨弹簧和压动凸轮一起控制,如图3中所示,这种内燃机包括汽缸21、汽缸中的活塞22和经连杆23与曲轴箱中传动相连的曲轴。在汽缸21侧边位置处的缸盖2上设有躲开进排气门的构成燃烧室容积的小汽缸26,在小汽缸中装有辅助活塞31,在靠近小汽缸26与汽缸21连通的通气道处装有指向小汽缸的火花塞6。由于小汽缸26倾斜布置,火花塞6安装在了靠近汽缸的缸体20上,并让火花塞指向与小汽缸连通的通气道28。发动机由火花塞点火作功,小汽缸26内的燃烧室容积相当于8∶1~10∶1压缩比。当只设有火花塞时,可在汽缸外安装喷油器并利用节气阀门调节功率。如在火花塞旁安装喷油器进行缸内喷油,便可去掉节气门使发动机在中低功率下的效率得到提高。辅助活塞31上的连接顶杆45经穿过缸盖2上的小汽缸26上侧所固定的压盖13与上端的弹簧挡座46连成一体,弹簧挡座通过其上的边裙36可在缸盖上的滑套12中相应滑动,在弹簧挡座46与机盖4上的弹簧压盖105之间装有回涨弹簧47,该回涨弹簧经弹簧挡座46和连接顶杆45可把辅助活塞31从小汽缸26的内侧迅速向外压出。在弹簧挡座46下面的连接顶杆45上通过其上所设的轴销48装有与左右两侧的摇臂54内端相铰接的连接板51,两侧的摇臂54通过中部的中间轴53安装在缸盖上的左右轴座19上所设的相应支撑摆臂59上,左右两摇臂54的外端通过所设的滚轮55可被相应的左右凸轮轴99、90上的压动凸轮70同时压动控制,在连接顶杆45上的轴销48位置下侧形成有可落座在压盖13上的限位挡盘50。图3中辅助活塞31采用了被两侧的摇臂54控制的结构方式,因两侧摇臂上的滚轮55与辅助活塞的运动方向相反,可使辅助活塞的
上下移动惯性力被相应平衡。
当汽缸21内进行压缩过程、活塞22向上止点位置移动时,左右凸轮轴99、90上的压动凸轮70也同时通过左右的两摇臂54在克服回涨弹簧47的压力后带动辅助活塞31向小汽缸26内移动。发动机实际运转中,由于进入小汽缸中的压缩空气也会推动辅助活塞上行克服一部分回涨弹簧的压力,可让左右凸轮轴上的两侧压动凸轮70所受到作用力相应减小。当活塞22移到上止点完成压缩过程,将要进行作功过程时,如图3中状态所示,辅助活塞31已被带动移进小汽缸26内侧形成最大的燃烧室容积,进入小汽缸燃烧室中的燃油压缩混合气被火花塞6点火、所形成的作功燃气进入汽缸21中推动活塞22下行作功。
活塞22下行作功后(参看图5),左右凸轮轴上的压动凸轮70也转过左右摇臂54上的滚轮55,不被压动的回涨弹簧47便迅速带动辅助活塞31把小汽缸26内的作功燃气随着活塞22的下行快速压进汽缸21参与作功。让原来在燃烧室内的作功燃气被压进汽缸膨胀。当辅助活塞31将要移到小汽缸26外侧时,如图5所示,左右摇臂54上的滚轮55也落到左右凸轮轴的压动凸轮70上的降程缓冲段49,使辅助活塞移到外侧位置时的速度被相应缓冲。
当辅助活塞上侧的连接顶杆45上的限位挡盘50下移降落在小汽缸上的压盖13上后,回涨弹簧47的压力便经连接顶杆传给下面的压盖,而两侧凸轮轴上的压动凸轮70因已经转过被带动的摇臂上的滚轮55,使滚轮悬停在离凸轮轴表面保持一定间隙距离的位置上不再被压力作用。图3所给出的辅助活塞控制机构既适用于汽油机,形成相当于9∶1压缩比的小汽缸燃烧室容积。也可通过采用容积更小的相当于13∶1的小汽缸容积制成柴油机,并以压燃方式喷油点火。由于所设的回涨弹簧弹力较大,可产生30kg/cm2以上的工作压力,在汽缸开始作功的35度曲轴转角内回涨弹簧便可及时的带动辅助活塞把小汽缸燃烧室中的作功燃气迅速压进汽缸参与作功,让发动机的效率相比普通汽油机大幅度提高,相比普通柴油机也会让效率进一步提高。由于辅助活塞的上下震动惯性力可被摇臂外侧反向动作的滚轮相应平衡,也不会让发动机出现机构的震动现象。
为进一步减小辅助活塞31上的往复惯性质量,如图5所示,也可以让两摆臂54的内端直接铰接在弹簧挡座46的下面,让挪到下侧位置并躲开压盖13的连接板51通过中部被压盖两侧的轴座61支撑,再让连接板51
两端与支撑摆臂59的下部相铰接。这样布置,也增加了两摆臂54内端与弹簧挡座46的连接强度。
在图3的发动机凸轮轴布置中,右侧的凸轮轴90上不仅设有压动凸轮70,还在压动凸轮两侧设有进气凸轮108和排气凸轮109。当装有摇臂18的轴销17处于压动凸轮70的转动半径范围以内时,可采用如图4中所示的摇臂安装方式,让设在进排气门侧的凸轮轴90上的压动凸轮70处于中间位置,在压动凸轮两侧分别设有进、排气凸轮108、109,相应地被进、排气凸轮控制的摇臂18安装在两汽缸21之间位置的轴痤16上所固定的轴销17的外侧,并能让中间的压动凸轮70能从两侧的轴销之间转过。
被制成汽油机的可变容积燃烧室内燃机应取消节气门并采用缸内喷油形成燃油混合气,以避免因汽缸内进气量的减少而降低对回涨弹簧弹力的缓冲。喷油器与火花塞的布置如图6所示,喷油器5与火花塞6一起可被布置在缸体20上的汽缸侧边位置,让喷油器喷出的油雾能处于火花塞上方被点燃。
图7给出的是本发明第三种实施方式的可变容积燃烧室内燃机,这种发动机中的辅助活塞采用了被辅助曲轴控制的传动方式。如图7中所示,这种发动机包括汽缸21、汽缸中的活塞22和经连杆23与曲轴箱中传动相连的曲轴24。在汽缸21侧边位置处的缸盖2上设有躲开进排气门的构成燃烧室容积的小汽缸26,在小汽缸中装有辅助活塞31,在靠近小汽缸26与汽缸21连通的通气道处装有指向小汽缸的喷油器5。由于小汽缸内的辅助活塞31行程较长需要伸进汽缸21,要求小汽缸的直径不能太大,以便能布置在进排气门的侧边,这也要求小汽缸燃烧室的容积不能太大,使图7中这种结构类型的发动机只适合制成以压燃点火的柴油机。小汽缸26内的辅助活塞31经其上的活塞销34与中间连杆74的下端相连,中间连杆的上端经连杆销73与缸盖上侧的辅助曲轴71上的连杆72小头相铰接,两连杆之间的连杆销73的两侧还与摆臂57的摆动端相铰接,摆臂的另一端通过轴销58安装在缸盖侧壁3的轴座19上,辅助曲轴71与曲轴24的转速相同。当汽缸21中的活塞22行到上止点完成压缩过程时,小汽缸26内的辅助活塞31也被辅助曲轴带动移进小汽缸上侧形成最大的燃烧室容积(如图中双点划线31′位置所示)、并在小汽缸内产生作功燃气,当汽缸内的活塞22被作功燃气推动作功开始向下止点方向移动时,小汽缸26内的辅助活塞31
被辅助曲轴71带动先把小汽缸燃烧室内的作功燃气全部压进汽缸参与作功(如图中双点划线31″位置所示)、随后又被带动伸出小汽缸进入汽缸21内。当汽缸中的活塞22行到下止点位置时,小汽缸26中行程较长的辅助活塞31也移出小汽缸伸进汽缸21内一定的距离(如图7中辅助活塞31所示位置)。由于辅助曲轴71与曲轴24的转速相同,在随后的排气和进气过程中,小汽缸中的辅助活塞也会被辅助曲轴71带动返回小汽缸26后又移出小汽缸并伸进汽缸21。在发动机实际运转中,排气和进气过程中辅助活塞的上下移动并不会促进作功过程的效率提高,反而会占用一小部分进气过程中的汽缸工作容积,也增加了一次机构的运转磨损。希望辅助活塞在排气和进气过程中的无效移动并不会产生较大的机械摩擦损失,比如不超过所获得效率收益的1/6。辅助活塞采用辅助曲轴的控制方式在结构上较为简单可靠,辅助曲轴上的平衡重块也会抵消部分辅助活塞等所产生的往复惯性震动力。
以上各实施例中所给出的发动机方案都是以四冲程方式工作的内燃机,在图8中给出了本发明第四种二冲程可变容积燃烧室内燃机,如图8所示,这种内燃机包括汽缸21、汽缸中的活塞22和经连杆23与曲轴箱中传动相连的曲轴24,在汽缸21的下止点位置上设有与压气机118相连通的扫气口25,在汽缸21的缸盖2上设有构成燃烧室容积的小汽缸26,在小汽缸中装有辅助活塞31,在小汽缸的侧壁上装有喷油器5,辅助活塞31采用分段式组合结构、经中间的活塞杆39与上部的裙塞110连成一体,裙塞再经其上的活塞销34与缸盖2上侧的辅助曲轴71上的连杆72的小头相铰接,辅助曲轴71与曲轴箱112内的曲轴24转速相同。在辅助活塞31的上侧向裙塞110方向形成有过渡裙部78,在过渡裙部与辅助活塞31相连接处的以上位置形成有若干均布的排气口77,在过渡裙部78内形成了围绕着活塞杆39的排气道76,过渡裙部的上端与上侧的裙塞110的底面距有一定的距离形成出气开口75,相应地在与小汽缸26的燃烧室相隔一定距离的小汽缸侧壁27上设有与排气管道29相连通的环形排气道79。当汽缸21中的活塞22行到上止点位置完成压缩过程时,小汽缸26内的辅助活塞31也被辅助曲轴71带动移进小汽缸上部形成最大燃烧室容积、并在小汽缸内产生作功燃气,如图8中状态所示。在图9所示状态中,当汽缸内的活塞22被作功燃气推动作功开始向下止点方向移动时,小汽缸26内的辅助活塞31被辅助曲轴带动也向下移动、把小汽缸中的作功燃气压进汽缸21参与作功,
让这种双作用辅助活塞式二冲程内燃机效率进一步提高。在图10所示状态中,随着活塞22的下行作功,被带动的辅助活塞31伸进汽缸21;当活塞22下行接近下止点并与汽缸21上的扫气口25沟通时,移到下部位置的辅助活塞31上的排气口77也与汽缸21的上侧沟通,同时,辅助活塞内经排气通道76与排气口77相连通的出气开口75也与小汽缸侧壁上的环形排气道79处于相通状态,这时由压气机118提供的扫气便从汽缸21上的扫气口25进入汽缸,使汽缸内作功后的废气从上侧的辅助活塞31上露出的排气口77经辅助活塞上的排气通道76和缸盖2上的排气管道29向外排出。当活塞22行到下止点向上移动关闭汽缸上的扫气口25后,同时移动的辅助活塞31也离开下部位置向上移动、让辅助活塞上的排气口77移进小汽缸26切断与汽缸21的连通,汽缸内所进行的进排气换气过程完成。随着活塞22向上移动进行压缩过程到达上止点位置后,同时向上移动的辅助活塞31也退出汽缸21,移到小汽缸26内的上部位置形成最大燃烧室容积,以便开始下一次的燃烧作功过程。
由于辅助活塞行程较长又要伸进汽缸中,如在辅助活塞上设置密封环,就会卡在小汽缸外面,为避免这种情况,如图11所示,用于密封辅助活塞31和小汽缸26之间密封的密封环101设在小汽缸内壁上,通过密封环的内壁面压在辅助活塞31的外圆周面上进行密封,每个密封环101装在相应的L型密封环座102的台阶内,由多个装有密封环101的L型密封环座102叠压在一起,构成多道密封环进行密封,在相邻的两L型密封环座102的倒角空间104内装有密封添料,所设的多个叠压在一起的L型密封环座102装在小汽缸缸体100上所形成的L形台阶内,并压装在缸盖2底面的相应安装空间里。图11中只设置了相应的密封环,如有必要,也可以在密封环上侧增设一道油环,并向油环与密封环之间注入少量的润滑油。
在图8中的二冲程可变容积燃烧室内燃机中,辅助活塞被辅助曲轴和连杆控制,在结构上较为简单可靠。采用分段式组合结构的辅助活塞起到双重作用、不仅要把小汽缸中的高温高压燃气在作功过程中压进下侧的汽缸,还要在二冲程换气过程中作为排气阀门配合排气。这种由辅助活塞配合换气所构成的二冲程内燃机因为采用直流换气,同时辅助活塞上的排气口能在排气过程将结束时快速关闭,可让汽缸获得更好的换气效果,当然,让辅助活塞伸进汽缸配合换气的同时也占用了一小部分汽缸的进气容积,需要相应增加汽缸的排量来补充被辅助活塞所占用的容积。
Claims (9)
- 一种带有辅助活塞的可变容积燃烧室内燃机,包括汽缸(21)、汽缸中的活塞(22)和经连杆(23)与曲轴箱中传动相连的曲轴,在汽缸(21)侧边位置处的缸盖(2)上设有躲开进排气门的构成燃烧室容积的小汽缸(26),在小汽缸中装有辅助活塞(31),在靠近小汽缸(26)与汽缸(21)连通的通气道处装有指向小汽缸的喷油器(5)或火花塞(6),其特征在于:在辅助活塞(31)的裙部(33)上侧向外延出形成有顶在回涨弹簧(47)底部的弹簧座(35),该弹簧座处在缸盖(2)上的滑套(12)中,并通过弹簧座上的边裙(36)在滑套内相应滑动,所设的回涨弹簧(47)装在机盖(4)上的弹簧压盖(105)下面,使辅助活塞(31)受到压进小汽缸(26)的作用力,在弹簧压盖(105)上形成有伸在回涨弹簧(47)中的带有底部挡座(63)的液力缓冲柱(62),在液力缓冲柱内形成有带上、下缓冲段(67、68)的液压油腔(64),该液压油腔与供油管(80)连通,辅助活塞(31)上所设的带有挡塞(42)的滑杆(40)伸在液力缓冲柱的液压油腔(64)中,液压油腔上侧的容纳滑杆(40)上端的滑道(65)上端经连通孔(66)向外通出,在液压油腔的下缓冲段(68)的底侧形成有可限制辅助活塞移出小汽缸(26)的阻挡环面(69);当汽缸(21)内完成压缩过程、活塞(22)移到上止点位置时,小汽缸(26)内的辅助活塞(31)也在压缩空气作用下克服回涨弹簧(47)的弹力后上移到被液力缓冲柱(62)的底部挡座(63)所阻挡位置,形成最大的燃烧室容积,辅助活塞的弹簧座(35)上的顶环座(37)上移顶在液压缓冲柱底部挡座(63)上的速度由滑杆(40)上的挡塞(42)在移到液压油腔(64)的上缓冲段(67)时被减速缓冲;当汽缸(21)内完成压缩过程开始进行作功过程后,小汽缸(26)燃烧室内所产生的作功燃气开始推动活塞(22)下行作功,随着活塞下行作功,小汽缸内被回涨弹簧(47)压力作用的辅助活塞(31)也被迅速推进小汽缸燃烧室内,把小汽缸内的作功燃气压进汽缸(21)推动活塞(22)作功,当辅助活塞(31)带动相连的滑杆(40)上的挡塞(42)移进液压油腔(64)下侧的下缓冲段(68)后,使与辅助活塞相连的挡塞(42)落在下缓冲段底面的阻挡环面(69)上的速度被减速缓冲。
- 根据权利要求1所述的带有辅助活塞的可变容积燃烧室内燃机,其特征在于:由设在顶部位置的供油管(80)经用封盖(82)密封的注油孔 (83)后向下又经进油路(84)通向液压油腔(64)的一侧,液压油腔的另一侧与通向上侧的回油路(87)相通,该回油路再经用封盖(85)密封的检查孔(86)后经小出油孔(88)与出油管(89)连通。
- 根据权利要求2所述的带有辅助活塞的可变容积燃烧室内燃机,其特征在于:在缸盖(2)的侧壁(3)上装有面向小汽缸(26)上端位置的检查盖(91),该检查盖的内侧即作为连通辅助活塞弹簧座(35)上的上下侧气流通道,还在检查盖的内侧形成有相应的滑槽(92),辅助活塞(31)通过其上弹簧座(35)上所安装的处在滑槽(92)中的滑块(38)限制辅助活塞回转。
- 一种带有辅助活塞的可变容积燃烧室内燃机,包括汽缸(21)、汽缸中的活塞(22)和经连杆(23)与曲轴箱中传动相连的曲轴,在汽缸(21)侧边位置处的缸盖(2)上设有躲开进排气门的构成燃烧室容积的小汽缸(26),在小汽缸中装有辅助活塞(31),在靠近小汽缸(26)与汽缸(21)连通的通气道处装有指向小汽缸的喷油器(5)或火花塞(6),其特性在于:辅助活塞(31)上的连接顶杆(45)经穿过缸盖(2)上的小汽缸(26)上侧所固定的压盖(13)与上端的弹簧挡座(46)连成一体,弹簧挡座通过其上的边裙(36)可在缸盖上的滑套(12)中相应滑动,在弹簧挡座(46)与机盖(4)上的弹簧压盖(105)之间装有回涨弹簧(47),该回涨弹簧经弹簧挡座(46)和连接顶杆(45)可把辅助活塞(31)从小汽缸(26)的内侧迅速向外压出,在弹簧挡座(46)下面的连接顶杆(45)上通过其上所设的轴销(48)装有与左右两侧的摇臂(54)内端相铰接的连接板(51),两侧的摇臂(54)通过中部的中间轴(53)安装在缸盖上的左右轴座(19)上所设的相应支撑摆臂(59)上,左右两摇臂(54)的外端通过所设的滚轮(55)可被相应的左右凸轮轴(99、90)上的压动凸轮(70)同时压动控制,在连接顶杆(45)上的轴销(48)位置下侧形成有可落座在压盖(13)上的限位挡盘(50);当汽缸(21)内进行压缩过程、活塞(22)向上止点位置移动时,左右凸轮轴(99、90)上的压动凸轮(70)也同时通过左右的两摇臂(54)在克服回涨弹簧(47)的压力后带动辅助活塞(31)向小汽缸(26)内移动,当活塞(22)移到上止点完成压缩过程,将要进行作功过程时,辅助活塞(31)已被带动移进小汽缸(26)内侧形成最大的燃烧室容积,进入小汽缸燃烧室中的压缩空气被喷油点火、所形成的作功燃气进入汽缸(21)中推动活塞(22)下行作功,活塞(22)下行作功后, 左右凸轮轴上的压动凸轮(70)也转过左右摇臂(54)上的滚轮(55),不被压动的回涨弹簧(47)便迅速带动辅助活塞(31)把小汽缸(26)内的作功燃气随着活塞(22)的下行快速压进汽缸(21)参与作功;当辅助活塞(31)将要移到小汽缸(26)外侧时,左右摇臂(54)上的滚轮(55)也落到左右凸轮轴的压动凸轮(70)上的降程缓冲段(49),使辅助活塞移到外侧位置时的速度被相应缓冲。
- 根据权利要求4所述的带有辅助活塞的可变容积燃烧室内燃机,其特征在于:也可以让两摆臂(54)的内端直接铰接在弹簧挡座(46)的下面,让挪到下侧位置并躲开压盖(13)的连接板(51)通过中部被压盖两侧的轴座(61)支撑,再让连接板(51)两端与支撑摆臂(59)的下部相铰接。
- 根据权利要求4所述的带有辅助活塞的可变容积燃烧室内燃机,其特征在于:设在进排气门侧的凸轮轴(90)上的压动凸轮(70)处于中间位置,在压动凸轮两侧分别设有进、排气凸轮(108、109),相应地被进、排气凸轮控制的摇臂(18)安装在两汽缸(21)之间位置的轴痤(16)上所固定的轴销(17)的外侧。
- 一种带有辅助活塞的可变容积燃烧室内燃机,包括汽缸(21)、汽缸中的活塞(22)和经连杆(23)与曲轴箱中传动相连的曲轴(24),在汽缸(21)侧边位置处的缸盖(2)上设有躲开进排气门的构成燃烧室容积的小汽缸(26),在小汽缸中装有辅助活塞(31),在靠近小汽缸(26)与汽缸(21)连通的通气道处装有指向小汽缸的喷油器(5),其特征在于:小汽缸(26)内的辅助活塞(31)经其上的活塞销(34)与中间连杆(74)的下端相连,中间连杆的上端经连杆销(73)与缸盖上侧的辅助曲轴(71)上的连杆(72)小头相铰接,两连杆之间的连杆销(73)的两侧还与摆臂(57)的摆动端相铰接,摆臂的另一端通过轴销(58)安装在缸盖侧壁(3)的轴座(19)上,辅助曲轴(71)与曲轴(24)的转速相同;当汽缸(21)中的活塞(22)行到上止点完成压缩过程时,小汽缸(26)内的辅助活塞(31)也被辅助曲轴带动移进小汽缸上侧形成最大的燃烧室容积、并在小汽缸内产生作功燃气,当汽缸内的活塞(22)被作功燃气推动作功开始向下止点方向移动时,小汽缸(26)内的辅助活塞(31)被辅助曲轴(71)带动先把小汽缸燃烧室内的作功燃气全部压进汽缸参与作功、随后又被带动伸出小汽缸进入汽缸(21)内,当汽缸中的活塞(22)行到下止点位置 时,小汽缸(26)中行程较长的辅助活塞(31)也移出小汽缸伸进汽缸(21)内一定的距离;在随后的排气和进气过程中,小汽缸中的辅助活塞也会被辅助曲轴(71)带动返回小汽缸(26)后又移出小汽缸并伸进汽缸(21)。
- 一种带有辅助活塞的可变容积燃烧室内燃机,包括汽缸(21)、汽缸中的活塞(22)和经连杆(23)与曲轴箱中传动相连的曲轴(24),在汽缸(21)的下止点位置上设有与压气机(118)相连通的扫气口(25),在汽缸(21)的缸盖(2)上设有构成燃烧室容积的小汽缸(26),在小汽缸中装有辅助活塞(31),在小汽缸的侧壁上装有喷油器(5)或火花塞(6),其特征在于:辅助活塞(31)采用分段式组合结构、经中间的活塞杆(39)与上部的裙塞(110)连成一体,裙塞再经其上的活塞销(34)与缸盖(2)上侧的辅助曲轴(71)上的连杆(72)的小头相铰接,辅助曲轴(71)与曲轴箱(112)内的曲轴(24)转速相同,在辅助活塞(31)的上侧向裙塞(110)方向形成有过渡裙部(78),在过渡裙部与辅助活塞(31)相连接处的以上位置形成有若干均布的排气口(77),在过渡裙部(78)内形成了围绕着活塞杆(39)的排气道(76),过渡裙部的上端与上侧的裙塞(110)的底面距有一定的距离形成出气开口(75),相应地在与小汽缸(26)的燃烧室相隔一定距离的小汽缸侧壁(27)上设有与排气管道(29)相连通的环形排气道(79);当汽缸(21)中的活塞(22)行到上止点位置完成压缩过程时,小汽缸(26)内的辅助活塞(31)也被辅助曲轴(71)带动移进小汽缸上部形成最大燃烧室容积、并在小汽缸内产生作功燃气,当汽缸内的活塞(22)被作功燃气推动作功开始向下止点方向移动时,小汽缸(26)内的辅助活塞(31)被辅助曲轴带动也向下移动、把小汽缸中的作功燃气压进汽缸(21)参与作功,随着活塞(22)的下行作功,被带动的辅助活塞(31)伸进汽缸(21);当活塞(22)下行接近下止点并与汽缸(21)上的扫气口(25)沟通时,移到下部位置的辅助活塞(31)上的排气口(77)也与汽缸(21)的上侧沟通,同时,辅助活塞内经排气通道(76)与排气口(77)相连通的出气开口(75)也与小汽缸侧壁上的环形排气道(79)处于相通状态,这时由压气机提供的扫气便从汽缸(21)上的扫气口(25)进入汽缸,使汽缸内作功后的废气从上侧的辅助活塞(31)上露出的排气口(77)经辅助活塞上的排气通道(76)和缸盖(2)上的排气管道(29)向外排出,当活塞(22)行到下止点向上移动关闭汽缸上的扫气口(25)后,同时移动的辅助活塞(31)也离开下部位置向上移动、让辅助活塞上 的排气口(77)移进小汽缸(26)切断与汽缸(21)的连通,汽缸内所进行的进排气换气过程完成;随着活塞(22)向上移动进行压缩过程到达上止点位置后,同时向上移动的辅助活塞(31)也退出汽缸(21),移到小汽缸(26)内的上部位置形成最大燃烧室容积。
- 根据权利要求8所述的带有辅助活塞的可变容积燃烧室内燃机,其特征在于:用于密封辅助活塞(31)和小汽缸(26)之间密封的密封环(101)设在小汽缸内壁上,通过密封环的内壁面压在辅助活塞(31)的外圆周面上进行密封,每个密封环(101)装在相应的L型密封环座(102)的台阶内,由多个装有密封环(101)的L型密封环座(102)叠压在一起,构成多道密封环进行密封,在相邻的两L型密封环座(102)的倒角空间(104)内装有密封添料,所设的多个叠压在一起的L型密封环座(102)装在小汽缸缸体(100)上所形成的L形台阶内,并压装在缸盖(2)底面的相应安装空间里。
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