CN113027601B - Double-rotor internal combustion engine - Google Patents

Double-rotor internal combustion engine Download PDF

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CN113027601B
CN113027601B CN202110304359.8A CN202110304359A CN113027601B CN 113027601 B CN113027601 B CN 113027601B CN 202110304359 A CN202110304359 A CN 202110304359A CN 113027601 B CN113027601 B CN 113027601B
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gear
rotor
main shaft
air
fixedly connected
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CN113027601A (en
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杨文通
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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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B53/14—Adaptations of engines for driving, or engine combinations with, other devices
    • 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
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/02—Pistons
    • 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
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/08—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/16—Admission or exhaust passages in pistons or outer members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • 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

Abstract

The invention discloses a double-rotor internal combustion engine which comprises a cylinder, a main shaft, a left rotor, a right rotor and a left and right intermittent motion mechanism. The cylinder contains the cylinder hole that the axial is link up, the rotor contains blade and supporter, intermittent motion mechanism is the closed differential gear train that contains the non-circular gear pair, can realize continuous steady variable speed. The left rotor, the right rotor and the main shaft are positioned in the cylinder and have coaxial rotational freedom degrees. The vanes of the left rotor and the right rotor are in parallel in the radial direction, the space between the vanes forms a combustion chamber, the two rotors do periodic intermittent rotation in the processes of ignition work doing, exhaust, air suction and compression of the internal combustion engine, the right rotor is static when the left rotor moves, and the left rotor is static when the right rotor moves. The left and right rotors transmit their intermittent rotation to the main shaft through the left and right intermittent motion mechanisms, respectively, and convert them into constant rotation speed. Under the action of inertia, the main shaft feeds back the rotation of the main shaft to the left rotor and the right rotor to control the acceleration, deceleration and static processes of the rotors.

Description

Double-rotor internal combustion engine
Technical Field
The invention relates to the field of internal combustion engines, in particular to a dual-rotor internal combustion engine.
Background
In addition to gas turbines, internal combustion engines generally move pistons by intake, compression, explosion, and exhaust processes, and piston internal combustion engines are the most typical. The piston type internal combustion engine has simple principle, reliable action and good air tightness, thereby being widely applied. However, piston internal combustion engines also have disadvantages. Firstly, the piston type internal combustion engine is loose in structure, and a camshaft of the air inlet and exhaust control mechanism is far away from a main shaft; secondly, the crankshaft manufacturability of a multi-cylinder internal combustion engine is poor; thirdly, the volume of each cylinder of the piston internal combustion engine is limited, and more cylinders are required to be arranged for obtaining higher output power; finally, the most troublesome problem of piston internal combustion engines is their useless reciprocating motion.
The triangle rotor engine and the quasiturbine are few internal combustion engines which do not depend on reciprocating motion to change the volume of a combustion chamber, but the rotors of the internal combustion engines are in line contact with cylinders, so that sealing treatment is difficult to perform, and the internal combustion engines cannot be widely applied. In addition, there is currently no effective mechanism for varying the volume of the combustion chamber of an internal combustion engine in place of the reciprocating motion of the piston.
Disclosure of Invention
Based on the defects of the existing internal combustion engine, the invention provides a double-rotor internal combustion engine which comprises a cylinder, a main shaft, two rotors and two intermittent motion mechanisms. The main shaft is a stepped straight shaft, and the air cylinder comprises an axially through air cylinder hole. The rotor includes a central bore therethrough in an axial direction. The intermittent motion mechanism is a closed differential gear train comprising a non-circular gear pair, the two rotors are placed in a cylinder hole in parallel, the main shaft penetrates through a center hole of the rotors, the two rotors, the main shaft and the cylinder are movably connected, the intermittent motion mechanism comprises a component fixedly connected with the rotors and two components fixedly connected with the main shaft, the two intermittent motion mechanisms are connected with the two rotors in a one-to-one manner, and the two intermittent motion mechanisms are positioned on two sides of the cylinder in the axial direction.
The rotor includes a support body and a blade. The supporting body is an annular object and is provided with a central hole which is axially communicated, and the axial through hole of the rotor is the central hole of the supporting body. The left side and the right side of the vane are planes, and the vane radially comprises an inner cylindrical surface and an outer cylindrical surface. The blades are matched and connected with the supporting body, and the main shaft penetrates through a central through hole in the supporting body and is movably connected with the supporting body. The blade is inside to contain the lubricated oil hole of intercommunication left and right sides face and radial inside and outside cylinder, the blade surface still contains the recess.
The blades are movably matched and connected or fixedly matched and connected with the supporting body.
Further, inside one axial lubrication oil hole and the radial lubrication oil hole of twice that contains of blade, two sides about the axial lubrication oil hole link up the blade, wherein one radial lubrication oil hole link up the radial surface of blade, and another radial lubrication oil hole link up radial internal surface, the axial lubrication oil hole is crossing with the radial lubrication oil hole of twice. The left side surface, the right side surface and the radial inner and outer cylindrical surface of the blade all comprise grooves.
The two intermittent motion mechanisms comprise a differential gear train and an ordinary gear train, and the differential gear train and the ordinary gear train comprise two pairs of gears. The components in the ordinary gear train comprise a first gear, a second gear, a third gear, a fourth gear and a short shaft, wherein the first gear and the second gear are a pair of meshed non-circular gear pairs, the third gear and the fourth gear are a pair of meshed circular gear pairs, and the second gear and the third gear are fixedly connected with the short shaft. The members in the differential gear train include a fifth gear, a sixth gear, planet wheels and a planet carrier. One of the fifth gear, the sixth gear and the planet carrier is fixedly connected with the first gear and the main shaft, the other one of the fifth gear, the sixth gear and the planet carrier is fixedly connected with the fourth gear, and the last remaining one of the fifth gear, the sixth gear and the planet carrier is fixedly connected with the rotor.
Preferably, the differential gear train in the two intermittent motion mechanisms respectively comprises more than 2 planet wheels which are uniformly distributed in the circumferential direction, the shape of the planet carrier is axisymmetric, and the center of mass of the planet carrier coincides with the axis of a main shaft of the planet carrier.
The connection mode of the differential gear train and the ordinary gear train in the intermittent motion mechanism comprises two modes, preferably, a first gear is fixedly connected with a main shaft, and a fourth gear is fixedly connected with a member in the differential gear train; another alternative is to have the fourth gear fixedly connected to the main shaft and the first gear fixedly connected to a member in the differential gear train.
The non-circular gear pair in the intermittent motion mechanism is formed by meshing a first gear and a second gear, and the transmission ratio functions of the non-circular gear pairs in the left and right intermittent motion mechanisms can be expressed as follows:
Figure BDA0002987499100000021
in the formula, theta1Is the angle of rotation of the first gear; and a is the rotation angle range of the first gear arc segment curve, and preferably, a is pi. The parameters J and K satisfy the relation
Figure BDA0002987499100000022
The formula can ensure that the pitch curve of the second gear is also closed on the premise that the pitch curve of the first gear is closed. The pitch curve equation of the first gear and the second gear can be formed by the transmission ratio function and the centerThe pitch determination results in the first gear and the second gear having equal pitch curve circumferences, since the gear ratio function is unique.
The two rotors are respectively a left rotor and a right rotor, and the two intermittent motion mechanisms are respectively a left intermittent motion mechanism and a right intermittent motion mechanism. The left rotor blade is fixedly connected with the left rotor support body, the right rotor blade is fixedly connected with the right rotor support body, the left rotor support body is axially parallel to the right rotor support body, the left rotor blade is circumferentially parallel to the right rotor blade, and the left rotor support body is movably connected with the right rotor support body. One of a fifth gear, a sixth gear and a planet carrier in the left intermittent movement mechanism is fixedly connected with the left rotor support body, and one of the fifth gear, the sixth gear and the planet carrier in the right intermittent movement mechanism is fixedly connected with the right rotor support body. The left intermittent motion mechanism is located on the left side of the air cylinder, and the right intermittent motion mechanism is located on the right side of the air cylinder.
The non-circular gear pairs in the left and right intermittent motion mechanisms have the same shape but have different initial rotation angles
Figure BDA0002987499100000023
And (4) degree. Because the first gears of the two intermittent motion mechanisms are fixedly connected with the main shaft, the rotation angle theta of the main shaft is used100As independent variables, the transmission functions of the first gear and the second gear in the left and right intermittent motion mechanisms are respectively:
Figure BDA0002987499100000024
Figure BDA0002987499100000025
the differential gear train in the intermittent motion mechanism has two optional composition forms, one is a plane differential gear train, and the other is a space differential gear train. In the form of a planar differential gear train, the fifth gear, the sixth gear and the planet gears are all cylindrical gears, wherein the fifth gear is an externally meshed sun gear, the sixth gear is an internally meshed gear ring, and the tooth number of the sixth gear is equal to the tooth number of the sixth and fifth gears plus twice the tooth number of the planet gears. In the form of a spatial differential gear train, the fifth gear, the sixth gear and the planet gears are all bevel gears, and the number of the teeth of the fifth gear is equal to that of the teeth of the sixth gear.
The instantaneous transmission ratio of the first gear to the second gear is recorded as i12(ii) a The constant transmission ratio of the third gear to the fourth gear is i34；
The instantaneous speed of the first gear is omega1Angle of rotation of theta1The first gear rotates through [0, a ]]The time used is T;
the instantaneous speed of the fourth gear is omega4；
The fifth gear has Z teeth number5Instantaneous rotational speed of ω5Angle of rotation of theta5；
The sixth gear has Z teeth6Instantaneous rotational speed of ω6Angle of rotation of theta6；
Instantaneous rotating speed of planet carrier is omega8Angle of rotation of theta8。
The connection mode of the intermittent motion mechanism with the main shaft and the rotor comprises the following 6 types:
connection mode 1: the sixth gear is fixedly connected with the rotor supporting body, the planet carrier is fixedly connected with the first gear on the main shaft, and the fifth gear is fixedly connected with the fourth gear. At this time, the radian of the corner of the sixth gear is equal to
Figure BDA0002987499100000031
The parameter J also satisfies the relation
Figure BDA0002987499100000032
This expression is a condition that the sixth gear can attain 0 rpm.
Connection mode 2: the sixth gear is fixedly connected with the rotor support body, the planet carrier is fixedly connected with the fourth gear, and the fifth gear is fixedly connected with the first gear on the main shaft. At this time, the radian of the corner of the sixth gear is equal to
Figure BDA0002987499100000033
The parameter J also satisfies the relation
Figure BDA0002987499100000034
This expression is a condition that the sixth gear can attain 0 rpm.
Connection mode 3: the fifth gear is fixedly connected with the rotor supporting body, the planet carrier is fixedly connected with the first gear on the main shaft, and the sixth gear is fixedly connected with the fourth gear through a cushion block. At this time, the radian of the corner of the fifth gear is equal to
Figure BDA0002987499100000035
The parameter J also satisfies the relation
Figure BDA0002987499100000036
This expression is a condition that the fifth gear can attain 0 rotation speed.
Connection mode 4: the fifth gear is fixedly connected with the rotor support body, the planet carrier is fixedly connected with the fourth gear, and the sixth gear is fixedly connected with the first gear on the main shaft. At this time, the radian of the corner of the fifth gear is equal to
Figure BDA0002987499100000037
The parameter J also satisfies the relation
Figure BDA0002987499100000038
This expression is a condition that the fifth gear can attain 0 rotation speed.
Connection mode 5: the planet carrier is fixedly connected with the rotor supporting body, the fifth gear is fixedly connected with the first gear on the main shaft, and the sixth gear is fixedly connected with the fourth gear. At this time, the radian of the corner of the planet carrier is equal to
Figure BDA0002987499100000039
The parameter J also satisfies the relation
Figure BDA00029874991000000310
The type is a go-to-go frameThe condition of 0 revolution can be obtained.
Connection mode 6: the planet carrier is fixedly connected with the rotor supporting body, the sixth gear is fixedly connected with the first gear on the main shaft, and the fifth gear is fixedly connected with the fourth gear. At this time, the radian of the corner of the planet carrier is equal to
Figure BDA00029874991000000311
The parameter J also satisfies the relation
Figure BDA00029874991000000312
This equation is a condition that the carrier can obtain 0 rpm.
When the differential wheel is a flat wheel system, the 6 connection modes are different. However, when the differential gear is a space gear train, since the fifth gear and the sixth gear have the same number of teeth, they have the same equivalent, and the result obtained by exchanging the positions is the same, the space differential gear train is as follows:
both attachment 1 and attachment 3 are converted to attachment 7: the rotor supporting body and the fourth gear are fixedly connected with a bevel gear respectively, and the planet carrier and the first gear are fixedly connected to the main shaft. At the moment, the angle radian theta of the bevel gear is changed every time the main shaft rotates for one circle56＝4π(1-J)，
Figure BDA0002987499100000041
Both connection mode 2 and connection mode 4 are converted into connection mode 8: the rotor supporting body is fixedly connected with one bevel gear, the planet carrier is fixedly connected with the fourth gear, and the first gear and the other bevel gear are fixedly connected on the main shaft. At the moment, the angle radian theta of the bevel gear is changed every time the main shaft rotates for one circle56＝2π(J-1)，
Figure BDA0002987499100000042
Both connection 5 and connection 6 are converted to connection 9: the planet carrier is fixedly connected with the rotor supporting body, the first gear is fixedly connected with the main shaft through one bevel gear, and the fourth gear is fixedly connected with the other bevel gear. At this time, the main shaft rotates for one circleThe radian of the corner of the planet carrier is theta8＝＝π(1-J)，
Figure BDA0002987499100000043
The fixed gear train in the intermittent motion mechanism is preferably a plane fixed gear train formed by a cylindrical gear pair.
Of the 9 connection modes, the negative value of J in connection modes 5, 6 and 9 means that one pair of two gear pairs in the fixed-axis gear train is an internal gear pair, or more than 3 pairs of external gear pairs are included.
In the connection mode 1, the rotation angle radian of the sixth gear is calculated according to the following method:
the speed relationship between the differential gear train and the ordinary gear train is as follows:
Figure BDA0002987499100000044
to obtain
Figure BDA0002987499100000045
Let omega 60, get
Figure BDA0002987499100000046
This is the condition that the parameter J in the intermittent motion mechanism connection mode 1 ensures that the sixth gear obtains 0 rotation speed.
Because the first gear and the planet carrier are fixedly connected to the main shaft, the angular speed and the rotation angle of the first gear are the same, and the first gear and the planet carrier are as follows:
dθ100＝dθ1＝ω1dt＝ω8dt, therefore
Figure BDA0002987499100000047
And integrating to obtain a sixth gear corner radian:
Figure BDA0002987499100000048
and (3) combining the second gear pitch curve closed condition and the condition that the sixth gear obtains 0 rotating speed, simplifying an equation set:
Figure BDA0002987499100000051
to obtain
Figure BDA0002987499100000052
The formula shows that under the mechanism connection mode 1, the rotation radian of the sixth gear is theta every time the main shaft rotates 1 circle6。
More specifically, when the main shaft rotates by (0, a), the sixth gear in the left intermittent mechanism is accelerated to the maximum and then decelerated to 0, while the sixth gear in the right intermittent mechanism is stationary; when the main shaft rotates by [ a, 2 pi ], the sixth gear in the left intermittent motion mechanism keeps still, and the sixth gear in the right intermittent motion mechanism accelerates first and then decelerates to 0. The transmission ratio of the non-circular gear pair is continuously and stably changed, so that the adding and decelerating processes of the sixth gear which intermittently rotates as long as the rotating speed of the main shaft is constant are also stably carried out, and severe impact load interception is not generated.
Based on the same principle, the rotation angle calculation formula of the member intermittently rotating in the mechanism connection patterns 2 to 6 can be calculated. The calculation formula of the rotation angle radian of the component which rotates intermittently in the connection modes 7, 8 and 9 can be respectively substituted into Z from the rotation angle radian formula of the connection mode 1 or 3, 2 or 4, 5 or 65＝Z6Thus obtaining the product.
In the initial state, the angular deviation between the actual position and the ideal position of the intermittent member which rotates intermittently in the intermittent mechanism in the static state is recorded as e, n is the least common multiple of the number of teeth of all gears in the intermittent mechanism, and x is an integer less than n, so that the maximum angular deviation between the actual position and the ideal position of the intermittent member is x e when the intermittent member rotates x circles. However, after n rotations of the intermittent member, all the gears in the intermittent mechanism will return to the positions in the initial state, at which time the angular deviation of the actual position of the intermittent member from its ideal position will again become e. This characteristic indicates that the angular deviation of the actual position of the intermittent member at rest from the ideal position is a finite value, rather than increasing infinitely.
The birotor internal combustion engine also comprises two sealing plates, namely a left sealing plate and a right sealing plate. The radial outer surfaces of the two sealing plates are cylindrical surfaces, the axes of the two sealing plates comprise through holes, the left rotor supporting body penetrates through the through hole in the axis of the left sealing plate, and the right rotor supporting body penetrates through the through hole in the axis of the right sealing plate.
The dual-rotor internal combustion engine further comprises two supporting covers which are respectively a left supporting cover and a right supporting cover. The supporting cover comprises a cylindrical surface in the radial direction, the supporting cover shaft comprises a through main shaft hole and a short shaft hole parallel to the main shaft hole, the main shaft penetrates through the main shaft hole of the supporting cover, the short shaft penetrates through the short shaft hole of the supporting cover, and the main shaft and the short shaft are movably connected with the supporting cover.
The connection mode among the sealing plate, the supporting cover and the cylinder is determined by the form of an air inlet and exhaust mechanism, and the double-rotor internal combustion engine further comprises a hand air inlet and exhaust mechanism, wherein the air inlet and exhaust mechanism comprises two forms, one form comprises an air inlet ring and an exhaust ring, and the other form comprises an air inlet mechanism and an exhaust mechanism.
When the air inlet and exhaust mechanism comprises an air inlet ring and an exhaust ring, the sealing plate, the support cover and the cylinder are fixedly connected; when the air inlet and exhaust mechanism comprises an air inlet mechanism and an exhaust mechanism, the supporting cover is fixedly connected with the air cylinder, and the sealing plate is movably connected with the air cylinder and the supporting cover. The sealing plate, the supporting cover and the cylinder are fixedly connected, and the supporting cover is not in contact with the cylinder; the other is that the sealing plate, the supporting cover and the air cylinder are fixedly connected through a group of connecting pieces.
The air inlet ring comprises an air inlet hole, and the air exhaust ring comprises an air exhaust hole. When the air inlet and exhaust mechanism comprises an air inlet ring and an exhaust ring, the circumferential direction of the air cylinder also comprises an air inlet hole and an air exhaust hole, the axial position of the air inlet hole on the air cylinder is the same as that of the air inlet hole on the air inlet ring, the axial position of the air exhaust hole on the air cylinder is the same as that of the air exhaust hole on the exhaust ring, the air inlet ring and the exhaust ring are axially arranged in parallel, the air inlet ring and the exhaust ring are fixedly connected with a rotor respectively, and the air inlet ring and the exhaust ring are in movable contact with the air cylinder.
The air inlet mechanism and the air outlet mechanism comprise cams, air passages, air valves, springs and ejector rods, wherein the air passages are in a cross shape and are fixedly connected with the sealing plates, the cams are fixedly connected with the supporting bodies, the air valves are fixedly connected with the ejector rods, and the springs are sleeved on the ejector rods. When the air inlet and exhaust mechanism comprises an air inlet mechanism and an exhaust mechanism, the sealing plate also comprises an air hole, the supporting cover comprises a notch groove, the outlet end of the air passage is aligned with the air hole on the sealing plate, the air passage passes through the notch groove on the supporting cover, and the inlet end of the air passage is positioned outside the supporting cover.
The birotor internal-combustion engine still includes bearing, key and round nut, pass through bearing swing joint between main shaft and supporter, the supporting lid, the planet carrier passes through bearing swing joint with the planet wheel, the minor axis passes through bearing swing joint with the supporting lid, the minor axis passes through key fixed connection with second gear, third gear, the main shaft passes through key fixed connection with first gear, the main shaft passes through bearing swing joint with the fourth gear, one of fifth gear, sixth gear, planet carrier three passes through bearing swing joint with the main shaft, round nut and main shaft fixed connection.
The parts on the left side and the right side of the double-rotor internal combustion engine have the same functions and can be symmetrical mirror image parts. Specifically, the main shaft and the cylinder are bilaterally symmetrical with respect to the main shaft, the left rotor and the right rotor are structurally symmetrical, the short shaft, the first gear, the second gear, the third gear, the fourth gear, the fifth gear, the sixth gear, the planet wheel and the planet carrier in the left intermittent motion mechanism are structurally symmetrical with the short shaft, the first gear, the second gear, the third gear, the fourth gear, the fifth gear, the sixth gear, the planet wheel and the planet carrier in the right intermittent motion mechanism respectively, the left sealing plate is structurally symmetrical with the right sealing plate, the left supporting cover is structurally symmetrical with the right supporting cover, the air inlet mechanism is structurally symmetrical with the exhaust mechanism, and the air inlet ring is structurally symmetrical with the exhaust ring. In consideration of the anti-reflection requirement in the assembly process, an asymmetric connecting feature is preferably added on the basis of the symmetry of the functional features.
And the axial outer surface of the cylinder is also fixedly connected with a fuel injector.
The double-rotor internal combustion engine can be a gasoline engine, a diesel engine and an underwater internal combustion engine which uses fuel and combustion improver as combustion media.
When the birotor internal combustion engine is a gasoline engine, the outer surface of the axial direction of the cylinder is fixedly connected with a spark plug.
When the dual-rotor internal combustion engine is an oil engine, the blades on the rotor further comprise two axially movable sealing elements and two radially movable sealing elements. The two axial movable sealing pieces are positioned on the left side and the right side of the blade, the two radial movable sealing pieces are positioned at the joint of the blade and the supporting body, and the movable sealing pieces are movably connected with the blade and the supporting body.
The number of the oil injector, the spark plug, the air inlet mechanism and the air outlet mechanism, and the number of the air inlet holes and the air outlet holes on the air inlet ring, the air outlet ring or the sealing plate are determined by the number of working cavities in the cylinder of the birotor internal combustion engine. The installation positions of the spark plug, the air inlet mechanism and the air outlet mechanism are determined by the position of the compression chamber, the spark plug is always aligned with the compression chamber, the air inlet mechanism and the air outlet mechanism can be aligned with the compression chamber or can be deviated from the compression chamber, and the deviation angle between the air inlet mechanism and the compression chamber does not exceed the rotation angle range of the combustion chamber. The fuel injector is directed at the combustion chamber.
The combustion chamber refers to a maximum volume space of a single chamber formed between the left and right rotor blades, and the compression chamber refers to a minimum volume space of the single chamber formed between the left and right rotor blades.
The left rotor and the right rotor may each include N blades, and the N blades included in the left rotor and the N blades included in the right rotor are preferably symmetrical members, where N is an integer greater than 1. When N equals 1, the integral mass of the blade and the support body deviates to one side of the axis of the support body, so that the support body is fixedly connected with a balancing weight to balance the eccentric mass of the rotor. When N >1, the N blades of the single rotor are evenly distributed around the circumferential direction of the support body.
The thickness radian of each blade of the left rotor and the right rotor is t, 2t + theta multiplied by N is less than or equal to 2 pi, wherein theta is the radian of a rotating angle rotated by one-time intermittent rotation of a single rotor and is calculated by a formula in a connection mode from 1 to 9.
The invention has the beneficial effects that:
1) the structure is compact, the main volume of the device is concentrated on the cylinder, and enough displacement can be achieved under the limited volume;
2) the left and right structure parts are symmetrical, so that the model selection of standard parts and the processing and manufacturing of non-standard parts are facilitated;
3) intermittent rotation is directly converted into continuous rotation, no component does reciprocating motion, and the conversion efficiency is high;
4) the enlargement and the reduction have little influence on the manufacturability, and the device can be designed into a slender type or a short and thick type according to the requirement of the installation space;
5) the parts are simple to machine and assemble, and the manufacturability is good;
6) the rotor is in surface contact with the cylinder and the sealing plate, so that effective sealing treatment can be carried out;
7) the power of the internal combustion engine can be increased by increasing the diameter and/or the length of the cylinder without increasing the number of the cylinders, and the internal combustion engine is suitable for being used as a power source of large machinery.
Drawings
FIG. 1: intermittent motion mechanism connection mode 1 wheel train diagram
FIG. 2: intermittent motion mechanism connection mode 2 wheel train diagram
FIG. 3: 3 wheel train diagram of intermittent motion mechanism connection mode
FIG. 4: 4 wheel train diagram of intermittent motion mechanism connection mode
FIG. 5: intermittent motion mechanism connection mode 5 wheel train diagram
FIG. 6: 6 wheel train diagram of intermittent motion mechanism connection mode
FIG. 7: 7 wheel train diagram of intermittent motion mechanism connection mode
FIG. 8: 8-wheel train diagram of intermittent motion mechanism connection mode
FIG. 9: 9 wheel train diagram of intermittent motion mechanism connection mode
FIG. 10: EXAMPLE 1 explosive representation of an internal Combustion Engine Assembly
FIG. 11: EXAMPLE 1 internal Combustion Engine Assembly front and Right side elevation views
FIG. 12: EXAMPLE 1 internal Combustion Engine Assembly A-A three-dimensional vertical section view
FIG. 13: EXAMPLE 1 internal Combustion Engine Assembly A-A section view
FIG. 14: EXAMPLE 1 internal Combustion Engine Assembly B-B section view
FIG. 15: EXAMPLE 1 internal Combustion Engine Assembly C-C section view
FIG. 16: EXAMPLE 1C-C section views under different operating conditions
FIG. 17: example 1 explosion diagram for left and right rotor assembly
FIG. 18: embodiment 1 non-circular gear engagement diagram in right and left intermittent mechanism
FIG. 19: the non-circular gear pair meshing pitch curve chart of the embodiment 1 has the parameters J-7/6 and K-21/32 in the transmission ratio function
FIG. 20: EXAMPLE 1 Movable seal vane
FIG. 21: EXAMPLE 2 front and Right side views of an internal Combustion Engine Assembly
FIG. 22: EXAMPLE 2 Engine Assembly A-A Cross-sectioned overhead view
FIG. 23: EXAMPLE 2 internal Combustion Engine Assembly B-B section view
FIG. 24: EXAMPLE 3 explosive representation of an internal Combustion Engine Assembly
FIG. 25: EXAMPLE 3 three-dimensional section view of internal Combustion Engine Assembly
FIG. 26: EXAMPLE 3 front and Right side views of internal Combustion Engine Assembly
FIG. 27 is a schematic view showing: EXAMPLE 3 internal Combustion Engine Assembly A-A section view
FIG. 28: EXAMPLE 3 internal Combustion Engine Assembly B-B section view
FIG. 29: EXAMPLE 3 internal Combustion Engine Assembly C-C section view
FIG. 30: EXAMPLE 3C-C section views under different operating conditions
FIG. 31: EXAMPLE 4 explosive representation of an internal Combustion Engine Assembly
FIG. 32: EXAMPLE 4 front and Right side views of internal Combustion Engine Assembly
FIG. 33: EXAMPLE 4 internal Combustion Engine Assembly A-A section view
FIG. 34: EXAMPLE 4 internal Combustion Engine Assembly B-B section view
FIG. 35: EXAMPLE 4 internal Combustion Engine Assembly C-C section view
FIG. 36: EXAMPLE 4 internal Combustion Engine Assembly D-D section view
FIG. 37: EXAMPLE 4 cylinders and intake/exhaust rings having increased number of ports
FIG. 38: EXAMPLE 5 explosive representation of an internal Combustion Engine Assembly
FIG. 39: EXAMPLE 5 front and Right side views of internal Combustion Engine Assembly
FIG. 40: EXAMPLE 5 internal Combustion Engine Assembly A-A section view
FIG. 41: EXAMPLE 5 internal Combustion Engine Assembly B-B section view
FIG. 42: EXAMPLE 5C-C three-dimensional section view of internal Combustion Engine Assembly
FIG. 43: EXAMPLE 6 explosive representation of an internal Combustion Engine Assembly
FIG. 44: EXAMPLE 6 front and Right side views of internal Combustion Engine Assembly
FIG. 45: EXAMPLE 6 internal Combustion Engine Assembly A-A section view
FIG. 46: EXAMPLE 6 internal Combustion Engine Assembly B-B section view
Detailed Description
The invention provides a birotor internal combustion engine, the core component of which comprises: the device comprises a cylinder 90, a main shaft 100, a left rotor 3, a right rotor 4, a left intermittent motion mechanism and a right intermittent motion mechanism. Wherein, the part in the left intermittent motion mechanism includes: the left pinion 10, the left first gear 11, the left second gear 12, the left third gear 13, the left fourth gear 14, the left fifth gear 15, the left sixth gear 16, the left planet gear 17 and the left planet carrier 18. The components in the right intermittent mechanism 2 include: the planetary gear set comprises a right stub shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, a right planet gear 27 and a right planet gear 28.
The left rotor and the right rotor are collectively called as rotors, and the left intermittent motion mechanism and the right intermittent motion mechanism are collectively called as intermittent motion mechanisms.
The parts with the same name in the left intermittent motion mechanism and the right intermittent motion mechanism are symmetrical in structure and the same in connection relation. Specifically, the left minor axis 10 is symmetrical to the right minor axis 20; the left first gear 11 is symmetrical with the right first gear 21; the left second gear 12 is symmetrical with the right second gear 22; the left third gear 13 is symmetrical to the right third gear 23; the left fourth gear 14 is symmetrical to the right fourth gear 24; the left fifth gear 15 is symmetrical to the right fifth gear 25; the left sixth gear 16 is symmetrical to the right sixth gear 26; the left planet wheel 17 is symmetrical with the planet wheel 27; the left carrier 18 is symmetrical to the right carrier 28. Respectively collectively called a stub shaft, a first gear, a second gear, a third gear, a fourth gear, a fifth gear, a sixth gear, a planet wheel and a planet carrier.
The first gear and the second gear are a pair of meshed non-circular gear pairs, the third gear and the fourth gear are a pair of meshed circular gear pairs, and the second gear and the third gear are fixedly connected to the short shaft. The first gear, the second gear, the third gear, the fourth gear and the short shaft form a fixed shaft gear train, and the fifth gear, the sixth gear, the planet gear and the planet carrier form a differential gear train.
The connection mode of the main shaft 100, the air cylinder 90, the left rotor 3, the right rotor 4 and the left and right intermittent motion mechanisms comprises the following 9 types:
connection mode 1: the sixth gear is fixedly connected with the rotor, the fifth gear is fixedly connected with the fourth gear, the first gear and the planet carrier are fixedly connected to the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 1.
Connection mode 2: the sixth gear is fixedly connected with the rotor, the planet carrier is fixedly connected with the fourth gear, the first gear and the fifth gear are fixedly connected to the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 2.
Connection mode 3: the fifth gear is fixedly connected with the rotor, the sixth gear is fixedly connected with the fourth gear, the planet carrier is fixedly connected with the first gear on the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 3.
Connection mode 4: the fifth gear is fixedly connected with the rotor, the planet carrier is fixedly connected with the fourth gear, the sixth gear is fixedly connected with the first gear on the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 4.
Connection mode 5: the planet carrier is fixedly connected with the rotor, the sixth gear is fixedly connected with the fourth gear, the fifth gear is fixedly connected with the first gear on the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 5.
Connection mode 6: the planet carrier is fixedly connected with the rotor, the fifth gear is fixedly connected with the fourth gear, the sixth gear is fixedly connected with the first gear on the main shaft, the fifth gear is a sun gear, and the sixth gear is a gear ring, as shown in fig. 6.
Connection mode 7: the sixth gear is fixedly connected with the rotor, the fifth gear is fixedly connected with the fourth gear, the first gear and the planet carrier are fixedly connected to the main shaft, and the sixth gear of the fifth gear is a bevel gear with the same number of teeth, as shown in fig. 7.
Connection mode 8: the sixth gear is fixedly connected with the rotor, the planet carrier is fixedly connected with the fourth gear, the first gear and the fifth gear are fixedly connected with the main shaft, and the sixth gear of the fifth gear is a bevel gear with the same number of teeth, as shown in fig. 8.
Connection mode 9: the planet carrier is fixedly connected with the rotor, the sixth gear is fixedly connected with the fourth gear, the fifth gear is fixedly connected with the first gear on the main shaft, and the sixth gear of the fifth gear is a bevel gear with the same number of teeth, as shown in fig. 9.
The rotor comprises a supporting body and blades, and the components in the intermittent motion mechanism are fixedly connected with the rotor through the fixed connection with the supporting body in the rotor.
Among the 9 connection modes, the connection mode 7 is obtained by converting the connection mode 1 or 3 under the plane differential gear train into a space differential gear train; the connection mode 8 is obtained by converting the connection mode 2 or 4 under the plane differential gear train into a space differential gear train; the connection mode 9 is obtained by converting the connection mode 5 or 6 under the plane differential gear train into a space differential gear train.
The non-circular gear pair formed by the left first gear 11 and the left second gear 12 in the left intermittent mechanism has the same meshing shape with the non-circular gear pair formed by the right first gear 21 and the right second gear 22 in the right intermittent mechanism, but the two gears have phase difference. In the 9 connection modes, the first gear is always fixedly connected with the main shaft 100, so the non-circular gear pairs in the left and right intermittent motion mechanisms can be respectively expressed as:
Figure BDA0002987499100000091
Figure BDA0002987499100000092
at theta100When the phase difference is equal to 0, the instantaneous phase difference between the left first gear 11 and the right first gear 21 is 180 degrees, and the phase difference between the two is dependent on θ100May be changed.
The specific connection mode is selected, the manufacturability of parts and the assembly feasibility of internal combustion are considered, and the following 6 groups of embodiments are obtained after thinning.
Example 1
Referring to fig. 1 to 15, embodiment 1 provides a twin-rotor internal combustion engine including:
a left stub shaft 10, a left first gear 11, a left second gear 12, a left third gear 13, a left fourth gear 14, a left fifth gear 15, a left sixth gear 16, three left planet gears 17 and a left planet carrier 18;
a right stub shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, three right planet gears 27 and a right planet carrier 28;
a left support body 30, a left blade 31 and a left balancing weight 35;
a right support body 40, a right blade 41 and a right balancing weight 45;
a left sealing plate 50, a left support cover 51, a left sealing cover 52;
a right sealing plate 60, a right support cover 61, a right sealing cover 62;
a left cam 70, a left air channel 71, a left air valve 72, a left mandril 73 and a left spring 74;
a right cam 80, a right air channel 81, a right air valve 82, a right mandril 83 and a right spring 84;
cylinder 90, spark plug 91, injector 92;
a main shaft 100;
a left round nut 111;
a right round nut 121;
a left first key 131, a left second key 132;
a right first key 141, a right second key 142;
a left first bearing 151, a left second bearing 152, a left third bearing 153, a left fourth bearing 154, a left fifth bearing 155, a left sixth bearing 156, and a left seventh bearing 157;
a right first bearing 161, a right second bearing 162, a right third bearing 163, a right fourth bearing 164, a right fifth bearing 165, a right sixth bearing 166, and a right seventh bearing 167;
a left first sleeve 171, a left second sleeve 172;
a right first sleeve 181, a right second sleeve 182.
Besides, unnumbered bolts are included.
Wherein, the parts 10 to 18 form a left intermittent motion mechanism, and the parts 20 to 28 form a right intermittent motion mechanism; the parts 30, 31 and 35 form a left rotor, and the parts 40, 41 and 45 form a right rotor; the parts 70 to 74 constitute an intake mechanism, the parts 80 to 85 constitute an exhaust mechanism, and the intake mechanism and the exhaust mechanism together constitute an intake and exhaust mechanism.
The middle of the main shaft 100 is provided with a shaft collar, the left side and the right side of the main shaft are respectively provided with three shaft shoulders, and the small shaft shoulder at the outermost side is used for processing a round nut mounting thread; the left side and the right side of the main shaft 100 are respectively provided with three flat key keyways, the left keyway and the right keyway on the outermost side are used for outputting outwards, the four keyways in the middle are used for connecting parts in the intermittent motion mechanism, the left first key 131 and the right first key 141 are respectively placed in the two closed keyways, and the left second key 132 and the right second key 142 are respectively placed in the two open keyways. The main shaft 100 is a straight shaft having a circular main cross section and a straight axis, and the left and right sides of the main shaft 100 are bilaterally symmetric with respect to the centering plane of the shoulder ring.
The main shaft 100 has the largest diameter at the center and the smallest diameter at both ends so as to be assembled with bearings. A left first bearing 151, a left second bearing 152, a left third bearing 153, a left fourth bearing 154 and a left fifth bearing 155 are arranged on the left side of the main shaft 100; right first bearing 161, right second bearing 162, right third bearing 163, right fourth bearing 164, and right fifth bearing 165 are installed on the right side of main shaft 100. A left first sleeve 171 is used for positioning between the left third bearing 153 and the left fourth bearing 154, a left second sleeve 172 is used for positioning between the left fourth bearing 154 and the left fifth bearing 155, and a part on the left side of the main shaft 100 is finally axially fixed through the left round nut 111; the right third bearing 163 and the right fourth bearing 164 are positioned by a right first sleeve 181, the right fourth bearing 164 and the right fifth bearing 165 are positioned by a right second sleeve 182, and finally, a part on the right side of the main shaft 100 is axially fixed by a right round nut 121.
The cylinder 90 comprises a cylindrical body portion and two supports, each having a flange at each end for connection to other components. The middle of the main body part of the cylinder is provided with an axially-through cylindrical cylinder hole, the outer surface of the main body part of the cylinder is fixedly connected with a spark plug 91 and a fuel injector 92, the spark plug is positioned on an image limit point right below the cylinder 90, the fuel injector 92 and the spark plug 91 are positioned on the same section, an included angle between the two is 45 degrees, and the spark plug 91 and the fuel injector 92 are aligned to the axis of the cylinder hole. The outer cylindrical surface of the cylinder 90 and the inner side surface of the right flange are also marked with arrows indicating the rotation direction of the blades when the internal combustion engine works. Spark plug 91 is forward and injector 92 is aft, with reference to the direction indicated by the arrow. The cylinder 90 is symmetrical on the left and right sides.
The left support body 30 and the left blade 31 are connected in a matching way to form a left rotor; the right support body 40 is matched and connected with the right blade 41 to form a right rotor; the left rotor and the right rotor are symmetrical in structure and are movably connected in parallel, wherein the left support body 30 and the right support body 40 are axially parallel, and the left blade 31 and the right blade 41 are circumferentially parallel.
The left support 30 and the right support 40 are collectively referred to as supports, and both are rings having an axial through center hole, and the ends include splines. The outer surfaces of the two supporting bodies are cylindrical surfaces and are respectively provided with a connecting groove, and the bottom surfaces of the connecting grooves are also provided with radial lubricating oil holes communicated with the central hole of the supporting body, wherein the lubricating oil hole on the left supporting body 30 is numbered 3001, and the lubricating oil hole on the right supporting body 40 is numbered 4001.
The left support 30 and the right support 40 are parallel and movably connected with the main shaft 100, wherein the left support 31 is movably connected with the main shaft 100 through a left first bearing 151 and a left second bearing 152, and the right support 41 is movably connected with the main shaft 100 through a right first bearing 161 and a right second bearing 162.
The left blade 31 and the right blade 41 are collectively referred to as a blade. The blades are fan-shaped, the included angle between the front surface and the rear surface in the thickness direction of the blades is 30 degrees, and the radial outer surfaces of the blades are cylindrical surfaces and are in movable contact with the cylinder holes. The radial inner side of the blade contains a plug, the width of which is half of the width of the blade, which plug cooperates with the coupling groove of the support body. The left side and the right side of the blade are planes, the radial inner side of the blade also comprises a cylindrical surface, after the left rotor and the right rotor are movably connected in parallel, the radial inner cylindrical surface of the left blade 31 is movably contacted with the outer cylindrical surface of the right supporting body 40, and the right blade 41 is movably contacted with the outer cylindrical surface of the left supporting body 30.
The inner part of the blade comprises an axial lubricating oil hole and two radial lubricating oil holes, and the axial lubricating oil hole of the blade is a special-shaped through hole and is communicated with the left side and the right side of the blade; the inner side of a first radial lubricating oil hole on the blade is aligned and connected with a lubricating oil hole on the support body, and the outer side of the first radial lubricating oil hole penetrates through the radial outer cylindrical surface of the blade; the second radial lubricating oil hole on the vane is communicated with the inner cylindrical surface of the vane in the radial direction. The two radial lubricating oil holes are communicated with the axial lubricating oil hole. The number of the first radial lubricating oil hole on the left blade 31 is 3101, and the number of the second radial lubricating oil hole is 3102.
The vane has one notch in the outer cylindrical surface and one notch in the inner cylindrical surface, and the notch can reduce the contact area between the vane and its movable contact part and store lubricating oil from the lubricating oil hole to reduce friction. The axial lubrication oil hole of the vane has the same function as the groove for both the left and right side surfaces thereof, and also has a function of reducing the mass of the vane.
Because the left rotor and the right rotor only comprise one blade, the mass center of the rotor is necessarily deviated to one side of the support body, the left balancing weight 35 is installed at the tail end of the left support body 30, and the right balancing weight 45 is installed at the tail end of the right support body 40. The balancing weight is used for balancing mass eccentricity caused by the blades and also balancing mass eccentricity caused by the cam on the support body, so that the rotor is ensured to meet the static balance requirement at least. Obviously, the smaller the mass of the blade, the smaller the mass and the volume of the counterweight block, so that the axial lubricating oil hole on the blade has the triple functions of reducing the contact area, storing lubricating oil and lightening the mass of the blade.
The axial lubricating oil hole of the blade is close to one side of the axis of the support body and has a certain distance with the outer cylindrical surface of the blade to form a small plane, and the small plane can sweep through the air inlet hole or the air outlet hole in the rotating process of the blade, so that the small plane cannot be communicated with the axial lubricating oil hole. A groove can also be separately formed on the small plane for reducing the contact area of the side surface of the blade.
The left blade 31 and the left support body 31, and the right blade 41 and the right support body 40 are movably connected in a clearance fit manner, the radial translational degree of freedom of the blade is restrained by the support bodies and the cylinder holes, the axial translational degree of freedom of the blade is restrained by the left sealing plate 50 and the right sealing plate 60, the rotational degree of freedom of the blade is restrained by the matching surfaces, and the blade rotates along with the support bodies.
The assembly of the left and right rotor upper blades and the support body is shown in fig. 17.
The left sealing plate 50 is fixedly connected to the flange on the left side of the cylinder 90 by bolts, and the right sealing plate 60 is fixedly connected to the flange on the right side of the cylinder 90 by bolts. The left seal plate 50 is structurally symmetrical to the right seal plate 60, collectively referred to as seal plates.
The sealing plate is composed of a disc and a cylindrical shell, wherein the disc seals the cylinder hole, the cylindrical shell provides an installation space for parts in the intermittent motion mechanism, and the center of the disc of the sealing plate is a through hole. The left support 30 passes through the central through hole of the left sealing plate 50, one end of the left support with a spline extends out of the cylinder hole, and the left support 30 is movably connected with the left sealing plate 50; the right support 40 passes through the central through hole of the right sealing plate 60, one end of the right support having a spline extends out of the cylinder hole, the right support 40 is movably connected with the right sealing plate 60, and the left and right sides of the left blade 31 and the right blade 32 are both movably contacted with the left sealing plate 50 and the right sealing plate 60.
The sealing plate disc comprises a rectangular air hole in the vertical direction, the angle of the rectangular air hole is 180 degrees different from the angle of a spark plug, the rectangular air hole in the left sealing plate 50 is an air inlet hole, and the air hole 6001 in the right sealing plate 60 is an air outlet hole. The cylindrical shell of the sealing plate also comprises a rectangular assembly hole at a position close to the disc, and the rectangular assembly hole is used for assembling an air channel in the air inlet and outlet mechanism, wherein the assembly hole on the left sealing plate 50 is used for installing a left air channel 71 in the air inlet mechanism, and the assembly hole on the right sealing plate 60 is used for installing a right air channel 81 in the air outlet mechanism.
The air inlet and exhaust mechanism consists of an air inlet mechanism and an exhaust mechanism, and the air inlet mechanism and the exhaust mechanism comprise cams, air passages, air valves, ejector rods and springs. The air intake mechanism comprises a left cam 70, a left air channel 71, a left air valve 72, a left mandril 73 and a left spring 74; the exhaust mechanism comprises a right cam 80, a right air channel 81, a right air valve 82, a right mandril 83 and a right spring 84. The left cam 70 is fixedly connected with the left support body 30 through a spline, and the right cam 80 is fixedly connected with the right support body 40 through a spline; the left air duct 71 is fixedly connected to the left sealing plate 50, and the right air duct 81 is fixedly connected to the right sealing plate 60. The inlet end of the left air duct 71 is positioned outside the cylindrical shell of the left sealing plate 50, and the outlet end of the left air duct is aligned with the rectangular air inlet hole on the disc of the left sealing plate 50; the inlet end of right gas duct 81 is located outside the cylindrical shell of right seal plate 60 and its outlet end is aligned with rectangular vent holes 6001 in the disk of right seal plate 60. The air inlet mechanism and the air outlet mechanism are structurally symmetrical.
The corner ranges of the base circular surface and the convex surface of the cam are respectively 180 degrees, and the air passage is a channel shaped like a Chinese character 'ji'. The lower end of the ejector rod is in movable contact with the cam profile surface, the middle of the ejector rod comprises a seat sleeve, and the upper end of the ejector rod penetrates through the air passage and is fixedly connected with the air valve. The spring is sleeved on the ejector rod, the upper end of the spring is supported by the lower bottom surface of the air passage, and the lower end of the spring is supported by the seat sleeve on the ejector rod. The part formed by the ejector rod and the air valve is movably connected with the cam and the air passage.
The left support cover 51 and the right support cover 61 are structurally symmetrical and are collectively referred to as a support cover. The supporting cover is a disk-shaped object and comprises two parallel through holes, wherein the through hole at the axis is a spindle hole, and the other through hole is a short shaft hole. The primary function of the support cap is to provide a support point for the major and minor axes. The main shaft 100 passes through a main shaft hole of the supporting cover and is movably connected with the supporting cover through a fifth bearing; the short shaft penetrates through a short shaft hole in the support cover and is movably connected with the support cover through a seventh bearing. Specifically, the left support cover 51 is movably connected with the main shaft 100 through a left fifth bearing 155, and is movably connected with the left short shaft 30 through a left seventh bearing 157; the right support cover 61 is movably connected with the main shaft 100 through a right fifth bearing 165 and movably connected with the right short shaft 40 through a right seventh shaft follow 167. The left support cover 51 is fixedly attached to the left seal plate 50 by a set of bolts, and the right support cover 61 is fixedly attached to the right seal plate 60 by a set of bolts.
The left sealing plate 50 and the left support cover 51 form a lubricant storage chamber on the left side of the cylinder, the right sealing plate 60 and the right support cover 61 form a lubricant storage chamber on the right side of the cylinder, and the lubricant storage chambers on the left and right sides are communicated through the center holes of the left support body 30 and the right support body 40. When the internal combustion engine works, the liquid level of the lubricating oil is filled to a position higher than the main shaft, so that the lubricating oil can smoothly pass through a gap between the support body and the main shaft. In the rotor rotation process, lubricating oil enters the blade through the lubricating oil holes in the supporting body under the action of centrifugal force, and flows to the left side and the right side of the blade and the radial inner and outer cylindrical surfaces through the lubricating oil holes in the blade for lubrication.
Since the support cover is movably connected to the main shaft 100 and the stub shaft through bearings, and has a gap through which lubricating oil can pass, the seal cover is also fixedly connected to the outside of the support cover. The left sealing cover 52 is fixedly connected with the left supporting cover 51 through a set of bolts, and the right sealing cover 62 is fixedly connected with the right supporting cover 61 through a set of bolts. The left sealing cover 52 and the right sealing cover 62 are both disk-shaped objects, the axis is a spindle hole, and both are movably connected with the spindle 100 after being sealed through the spindle hole. The left sealing cover and the right sealing cover 62 are symmetrical in structure and are collectively called sealing covers.
The space formed by the seal plate and the support cover stores lubricating oil which lubricates both the blade and the intermittent mechanism, and the space provides a space for mounting the intermittent mechanism.
The left intermittent motion mechanism, the right intermittent motion mechanism, the left rotor, the right rotor and the main shaft are connected in a connection mode 3, namely, the fifth gear is fixedly connected with the rotor, the sixth gear is fixedly connected with the fourth gear, and the planet carrier is fixedly connected with the first gear on the main shaft. The fifth gear is a sun gear, and the sixth gear is a gear ring. Wherein, the sixth gear passes through spline fixed connection with the supporter of changeing, and left and right intermittent motion mechanism respectively contains 3 equipartition planet wheels, passes through sixth bearing swing joint between planet wheel and the planet carrier. The back of the sixth gear is provided with a boss, the boss is provided with a sunken rectangular groove, the front of the third gear is provided with a convex rectangular column, and the third gear and the sixth gear are matched and connected through a rectangular shaft hole to transmit torque.
The gear parameters in the left and right intermittent motion mechanisms are the same and are as follows:
Figure BDA0002987499100000121
the non-circular gear pair pitch curve defined by J and K is shown in FIG. 19, where point p1 meshes with point p2, point q1 meshes with point q2, point J1 meshes with point J2, and point K1 meshes with point K2. When p1-p2, q1-q2 and j1-j2 are meshed, the instantaneous transmission ratios of the non-circular gear pair are all i12J, and when k1-k2 are engaged, the non-circular gear instantaneous transmission ratio is i12K. If the main shaft 100 rotates counterclockwise at a constant speed, then i12When J, the sixth gear is stationary; when i is12When the rotating speed of the sixth gear is K, the rotating speed of the sixth gear is highest; when the non-circular gear pair is rotated from the point engagement of p1-p2 to the point engagement of k1-k2, i12Decreasing from J to K, the sixth gear accelerates from 0 to maximum speed; when the first gear is rotated from the engagement of the points k1-k2 to the engagement of the points q1-q2, i12Increasing from K to J again, the sixth gear is stepped down from the maximum speed by 0 and then held stationary. The sixth gear rotates periodically and intermittently, and other components in the intermittent motion do periodic variable speed motion except that the first gear and the planet carrier rotate along with the main shaft.
It can be further seen that when the main shaft 100 rotates counterclockwise through the first half turn, the left sixth gear 16 accelerates from 0 to the highest rotation speed, and then decelerates to 0; while the right sixth gear 26 remains stationary; when the main shaft 100 rotates the second half turn, the left sixth gear 16 remains stationary, and the right sixth gear 26 first accelerates from 0 to the maximum rotation speed and then decelerates to 0. The rotor is driven by the sixth gear, so that the motion rules of the left rotor and the right rotor are the same as those of the left gear and the right gear, namely when the left rotor moves, the right rotor is static; while the right rotor is moving, the left rotor is stationary.
According to the calculation formula of the rotation angle radian of the sixth gear in the connection mode 3, when the main shaft 100 rotates for one circle, the sixth gear rotates for minus pi, and the rotation direction of the sixth gear is opposite to the rotation direction of the main shaft 100. In order to ensure that the left blade 31 and the right blade 41 which are parallel to each other on the rotor do not interfere with each other in the process of moving along with the rotor, the sum of the angle ranges of the left blade and the right blade in the thickness direction must be less than or equal to 180 degrees. In the case where the left and right blades are symmetrical, the angular range in the thickness direction of each blade must be 90 degrees or less.
The operating principle of the internal combustion engine is shown in fig. 16, in which:
w1 is the end of compression, i.e., the condition immediately before ignition, of the engine;
w2 is the explosive termination of the internal combustion engine, i.e. the condition immediately before exhaust;
w3 is the engine exhaust end, i.e., the condition immediately before intake;
w4 is the engine intake end, i.e., the condition immediately before compression.
The angle range in the thickness direction of the left blade 31 and the right blade 41 is actually 30 degrees. The left vane 31 and the right vane 41 divide the space inside the cylinder into two chambers Q1 and Q2. The circumferential corner width of the Q1 cavity after compression is 30 degrees, and the cavity is a compression chamber; the corner width of the completely unfolded cavity Q1 is 210 degrees, and the cavity Q1 is a combustion chamber; the compression ratio of the Q1 cavity is 7. The circumferential corner width of the Q2 cavity after compression is 90 degrees, the corner width after full expansion is 270 degrees, and the compression ratio of the Q2 cavity is 3. To increase the compression ratio of the Q1 cavity, the included angle interval between the left blade 31 and the right blade 41 in the initial state is only required to be reduced. In the moving process of the left rotor and the right rotor, the left blade 31 is not contacted with the right blade 32 all the time, and the stop of the rotor is completely controlled by the intermittent motion mechanism.
The main shaft 100 is actuated by external force drag, having an initial velocity of counterclockwise rotation.
Under the condition of W1, the cavity Q1 is compressed and aligned with the spark plug 91, and after the spark plug 91 is ignited, the cavity Q1 is expanded to produce work. In the W1 operating condition, the non-circular gear engagement is as shown in FIG. 18, and only the left rotor is rotating while the right rotor is stationary. The left rotor accelerates from rest, decelerates after reaching the maximum rotating speed, and reduces the rotating speed to 0 after the left rotor rotates 180 degrees. At the moment, a left ejector rod in the air inlet mechanism is in contact with a base circle surface of a left cam, and the left valve is kept in a closed state under the action of a left spring.
Under the W2 condition, the left rotor is static and the right rotor moves, and the cavity volume of the Q1 is reduced. The right rotor drives the right cam to rotate in the motion process, the right mandril is pushed to move upwards, the right valve is opened, and the combusted waste gas in the cavity of the Q1 is exhausted through the air hole 6001 on the right sealing plate 60 through the exhaust mechanism.
Under the W3 working condition, the left rotor moves and the right rotor is static again, and the cavity volume of the Q1 is increased. The left rotor drives the left cam to move, the left ejector rod is pushed to move upwards, the left air valve is opened, the Q1 cavity generates negative pressure due to the increase of the volume, and external air is sucked in through the air inlet mechanism and the air holes in the left sealing plate 50. Injector 92 begins injecting fuel after left blade 31 sweeps over.
Under the W4 condition, again with the left rotor stationary and the right rotor moving, the Q1 cavity is compressed and the injector 92 ends injecting fuel before the right vane 41 sweeps. At the moment, a mandril in the exhaust mechanism runs on the base circular surface of the right cam, and the exhaust valve is kept closed.
After the W4 operating condition is finished, the operation returns to the W1 operating condition again, and the next cycle is started.
In the running process of the left rotor and the right rotor, the cavity Q2 is also changed continuously, and the cavity Q2 is used as an air spring and has an energy storage function. Although the left and right valves are closed when the Q2 cavity sweeps across the air on the sealing plate, the Q1 cavity is in gas communication with Q2 because the inside of the air passage is always in communication with the cylinder.
After the left and right rotors shown in fig. 17 are installed, the sealing of the Q1 cavity and the Q2 cavity in the cylinder is completely determined by the fit clearance, so that high machining and fit precision is required between parts, and the expansion and contraction deformation of the parts are considered, so that strict sealing requirements are difficult to meet. For this purpose, axial seals may be mounted on the left and right sides of the blade and radial seals may be mounted at the mating connection of the blade to the support body, as shown in FIG. 20. Wherein the two axial seals mounted on the left blade are numbered 301 and 302 and the two radial seals are numbered 303 and 304; the two axial seals mounted on the right vane are numbered 401 and 402 and the two radial seals are numbered 403 and 404.
The left blade and the support body are movably matched, the axial sealing piece is used for translating towards the outer side to press the left sealing plate and the right sealing plate under the high pressure action, the radial sealing plate is used for translating towards the inner side in the radial direction under the high pressure action, and the blades move towards the outer side in the radial direction under the wedging force action of centrifugal force, gravity and the radial sealing piece to press the cylinder hole, so that the sealing purpose is realized.
Example 2
Example 2 is a derivative of example 1, and all the parts contained in example 1 can find the parts opposite to the parts in example 2, and the connection relationship of the parts is kept unchanged. Embodiment 2 provides a twin-rotor internal combustion engine having a specific structure as shown in fig. 21 to 23. The positions and connection relations of the first gear, the second gear, the planet wheel, the first bearing, the second bearing, the sixth bearing and the seventh bearing which are not shown can refer to the same parts in embodiment 1.
Compared with embodiment 1, the constituent parts of embodiment 2 are increased by the second ignition plug 93 and the second fuel injector 94; a left second cam 75, a left second air channel 76, a left second air valve 77, a left second mandril 78 and a left second spring 79; a right second cam 85, a right second air channel 86, a right second valve 87, a right second mandril 88 and a right second spring 89. Meanwhile, one more air hole is added to each of the left sealing plate 50 and the right sealing plate 60. Wherein, two gas pocket numbers on right sealing plate 60 are 6001 and 6002 respectively, and gas pocket 6001 aligns with right gas way 81, and gas pocket 6002 aligns with right second gas way 86. Finally, the angle range of the thickness direction of the left blade 31 and the right blade 41 is increased to 90 degrees, the forward direction of the left blade 31 is instantaneously contacted with the back of the right blade 32 during the movement of the rotor, and the front and back surfaces of the left and right blades respectively comprise a step surface for forming a compression chamber.
In example 2, the minimum and maximum volumes of the Q1 cavity were the same as Q2, both having the same compression ratio. The Q1 chamber is supplied by injector 92 and compressed to align with spark plug 91; the cavity Q2 is supplied by a second injector 94, which compresses and directs fuel to a second spark plug 93. The cavity Q1 and the cavity Q2 are both used as combustion chambers. The air intake and exhaust of the cavity Q1 are still controlled by an air intake mechanism consisting of a left cam 70, a left air channel 71, a left air valve 72, a left mandril 73 and a left spring 74, and an exhaust mechanism consisting of a right cam 80, a right air channel 81, a right air valve 82, a right mandril 83 and a right spring 84; and the air intake and exhaust of the cavity Q2 are controlled by a second air intake mechanism consisting of a left second cam 75, a left second air passage 76, a left second air valve 77, a left second mandril 78 and a left second spring 79, and a second air exhaust mechanism consisting of a right second cam 85, a right second air passage 86, a right second air valve 87, a right second mandril 88 and a right second spring 89.
The azimuth angles of the air inlet mechanism and the air outlet mechanism, the second air inlet mechanism and the second air outlet mechanism are different by 90 degrees and are all positioned above the main shaft 100, and the corresponding spark plug and the corresponding fuel injector are all positioned below the main shaft. The purpose of arranging the air intake and exhaust mechanism above the main shaft is that the air passage is connected with the supporting cover through a special-shaped hole, the sealing cost is high, lubricating oil is stored in the cylindrical shell of the supporting cover, and if the air intake and exhaust mechanism is positioned below the main shaft, the lubricating oil can leak when the air passage and the supporting cover are not sealed well.
Example 3
Referring to fig. 24 to 30, the twin-rotor internal combustion engine provided in embodiment 3 includes:
the left short shaft 10, the left first gear 11, the left second gear 12, the left third gear 13, the left fourth gear 14, the left fifth gear 15, the left sixth gear 16, the three left planet gears 17, the left planet carrier 18 and the left cushion block 19;
a right stub shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, three right planet gears 27, a right planet carrier 28 and a right cushion block 29;
a left support 30, a left first blade 31, a left second blade 32;
a right support 40, a right first blade 41, a right second blade 42;
a left sealing plate 50, a left support cover 51, a left sealing cover 52;
a right sealing plate 60, a right support cover 61, a right sealing cover 62;
a left cam 70, a left first air passage 71, a left first air valve 72, a left first push rod 73 and a left first spring 74; a left second air channel 76, a left second air valve 77, a left second mandril 78 and a left second spring 79;
a right cam 80, a right first air passage 81, a right first air valve 82, a right first push rod 83 and a right first spring 84; a right second air channel 86, a right second air valve 87, a right second mandril 88 and a right second spring 89;
a cylinder 90; a main shaft 100;
first spark plug 911, second spark plug 912;
a first oil injector 921, a second oil injector 922;
a left round nut 111 and a left flywheel 112;
a right round nut 121, a right flywheel 122;
unnumbered flat keys, bearings, sleeves and bolts are also included.
The main shaft 100 is a stepped straight shaft having a circular cross section, and the right end thereof is longer than the left end as an output end. The cylinder 90 is bilaterally symmetric about itself, and the first spark plug 911 and the second spark plug 912; first injector 921 and second injector 922 are located on the symmetrical plane of cylinder 90 and fixedly connected to cylinder 90.
The left first blade 31 and the left second blade 32 are arranged in an axial symmetry manner and are matched and connected with the left support body 30 to form a left rotor; the right first blade 41 and the right second blade 42 are arranged in axial symmetry and are connected with the right support body 40 in a matching way to form a right rotor. The left rotor and the right rotor are structurally symmetrical.
Because the rotor contains two axisymmetrically distributed blades, and the mass center of the rotor is positioned at the axis center, an additional balancing weight does not need to be installed.
The supporter is provided with two connecting grooves, the bottom surfaces of the connecting grooves are planes, and the side surfaces of the connecting grooves are perpendicular to the bottom surfaces of the connecting grooves. The bottom surfaces of the two connecting grooves on the supporting body comprise radial lubricating oil holes communicated with the through hole of the supporting shaft center. The blade and the supporting body are fixedly connected through interference fit.
The inside of the vane comprises two radial lubricating oil holes and an axial lubricating oil hole, wherein one radial lubricating oil hole is connected with the radial inner cylindrical surface, the other radial lubricating oil hole is aligned with the radial lubricating oil hole in the supporting body, and the axial lubricating oil hole penetrates through two side surfaces of the vane.
The left side surface and the right side surface of each blade are respectively provided with two grooves, wherein the groove close to the axle center is communicated with the axial lubricating oil hole of each blade, lubricating oil can be stored, and the groove far away from the axle center is only used for reducing the contact area. The inner and outer cylindrical surfaces of the vane each include a recess communicating with the lubricant oil hole. The maximum rotation angle range of the vane in the thickness direction is 45 degrees, and the front and rear surfaces of the vane are respectively provided with a concave surface for forming a compression chamber.
The main shaft 100, the left rotor, the right rotor, the left intermittent motion mechanism and the right intermittent motion mechanism are connected by a connection mode 1 shown in fig. 1. The movable connection between a component in the intermittent motion mechanism and the main shaft is realized through a bearing, the fixed connection with the main shaft is realized through a flat key, and the sleeve provides axial positioning and supporting between adjacent parts which are not contacted on the main shaft.
The gear parameters in the intermittent motion mechanism are as follows:
Figure BDA0002987499100000141
the angle of rotation of the sixth gear which intermittently rotates when the main shaft 100 rotates for one turn is defined as
Figure BDA0002987499100000142
The left fourth gear 14 and the left fifth gear 15 are fixedly connected through a left cushion block 19 and a bolt; the right fourth gear 24 and the right fifth gear 25 are fixedly connected through a right cushion block 29 and a bolt.
The two sealing plates are annular discs with central holes and are fixed on flanges on the left side and the right side of the air cylinder 90 through bolts. The sealing plate comprises two circular air holes which are axially and symmetrically distributed, the circle center connecting line of the two air holes on the left sealing plate 50 deviates from the horizontal plane by 7 degrees anticlockwise, the two air holes 6001 and 6002 on the right sealing plate 60 deviate from the horizontal plane by 7 degrees clockwise, and the circle center connecting line of the two air holes on the left sealing plate 50 and the circle center connecting line of the two air holes on the right sealing plate form an included angle of 14 degrees. Wherein, two air holes on the left sealing plate 50 are air inlets and are aligned with the air inlet mechanism; the two air holes in the right seal plate 60 are exhaust holes, aligned with the exhaust mechanism.
The air inlet mechanism consists of a left cam 70, a left first air passage 71, a left first air valve 72, a left first mandril 73 and a left first spring 74; the left second air channel 76, the left second air valve 77, the left second ejector rod 78 and the left second spring 79; the exhaust mechanism consists of a right cam 80, a right first air passage 81, a right first air valve 82, a right first mandril 83 and a right first spring 84; a right second air channel 86, a right second air valve 87, a right second mandril 88 and a right second spring 89. The air inlet mechanism and the air outlet mechanism are structurally symmetrical, but the difference between the circumferential arrangement directions of the air inlet mechanism and the air outlet mechanism is 14 degrees.
The cam comprises two bulges which are symmetrically distributed around the base circle axis of the cam, and the angle ranges of the two bulges are both 90 degrees.
The outer side surface of the sealing plate includes an annular boss for increasing the depth of the connection hole. The support cap is fixedly attached to the annular boss of the seal plate by bolts.
The support cover includes a disk portion that provides support of the main shaft and the stub shaft, and a cylindrical shell portion that provides a mounting space for parts in the intermittent mechanism and a storage space for lubricating oil. The supporting cover is movably connected with the main shaft and the short shaft through bearings.
The sealing cover is fixedly connected with the supporting cover through bolts. Wherein, the right sealing cover 62 comprises a central hole, and the right end of the main shaft passes through the central hole of the right sealing cover 62 and is movably connected with the central hole; the left sealing cover 52 is a blank cover, and the left end of the spindle is located inside the left sealing cover 52.
The left end and the right end of the main shaft 100 are respectively fixedly provided with a flywheel for increasing the rotational inertia of the main shaft. Wherein the left flywheel 112 shares a flat key with the left first gear 11, and the right flywheel 122 shares a flat key with the right first gear 21.
The four vanes divide the space in the cylinder into four chambers Q1, Q2, Q3 and Q4, wherein the chambers Q1 and Q3 are combustion chambers, and the chambers Q2 and Q4 are equivalent to air springs.
Under the W1 operating condition, the Q1 and Q3 chambers are compressed, the Q1 chamber is ignited by the first spark plug 911, and fuel is supplied by the first fuel injector 921; the chamber Q3 is ignited by a second spark plug 912 and is provided with fuel by a second fuel injector 922.
In the W2 operating condition, exhaust gas from the Q1 chamber is exhausted through the gas hole 6002 on the right sealing plate 60, and exhaust gas from the Q3 chamber is exhausted through the gas hole 6001.
Under the W3 condition, the Q1 chamber feeds air through the inlet port on the right side of the left sealing plate 50, and the Q3 chamber feeds air through the inlet port on the left side of the left sealing plate.
Under the W4 condition, the combustion gases in the Q1 chamber will be compressed to the position where the second spark plug 912 is aligned, and the combustion gases in the Q3 chamber will be compressed to the position where the first spark plug 911 is aligned.
In the next operating condition, the chamber Q1 will be ignited by the second spark plug 912 and the chamber Q3 will be ignited by the first spark plug 911.
Compared with embodiment 1, embodiment 3 has the following advantages:
firstly, the rotor comprising two blades and the cam on the rotor are axisymmetric, so that no additional balancing weight is required to be installed on the rotor;
secondly, when explosion does work, the stress of two blades on the rotor forms moment of couple, the stress of the supporting body is more uniform, and the transmission is more stable;
thirdly, the angle range of one-time intermittent rotation of the rotor is reduced by half, and the main shaft can output high rotating speed more easily.
On the other hand, example 3 also has inherent drawbacks including:
firstly, the number of parts except the cam in the air inlet and outlet mechanism is doubled, and if four cavities of Q1, Q2, Q3 and Q4 are required to do work at the same time, the number of parts in the air inlet and outlet mechanism is doubled.
Secondly, the radian of the corner of the convex part of the cam is reduced by half, and the curvature change of the cam is more rapid;
thirdly, no matter what arrangement mode is adopted by the air inlet mechanism and the air exhaust mechanism, an air channel is always positioned below the axis of the main shaft, and the liquid level of lubricating oil in the supporting cover is higher than the axis of the main shaft so as to be fully lubricated, so that the air channel and the supporting cover are required to be sealed;
fourthly, the time window of the rotor for acceleration and deceleration is narrowed, and the acceleration load caused by acceleration and deceleration is larger.
Example 4
Referring to fig. 31 to 37, the present embodiment 4 provides a twin-rotor internal combustion engine including:
a left short shaft 10, a left first gear 11, a left second gear 12, a left third gear 13, a left fourth gear 14, a left fifth gear 15, a left sixth gear 16, three left planet gears 17, a left planet carrier 18 and a left cushion block 19 which form the left intermittent motion mechanism;
a right stub shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, three right planet gears 27, a right planet carrier 28 and a right cushion block 29 which form a right intermittent motion mechanism;
a left support body 30, a left first blade 31 and a left second blade 32 which form a left rotor;
a right support 40, a right first blade 41, a right second blade 42 constituting the right rotor;
a left sealing plate 50, a left support cover 51, a left sealing cover 52;
a right sealing plate 60, a right support cover 61, a right sealing cover 62;
a left air ring 7 and a right air ring 8 which form an air inlet and exhaust mechanism;
a cylinder 90; a main shaft 100;
first spark plug 911, second spark plug 912;
a first oil injector 921, a second oil injector 922;
left round nut 111, right round nut 121.
The main shaft 100 is a stepped straight shaft having a circular cross section, and the right end thereof is longer than the left end thereof. The cylinder 90 circumferentially includes two axisymmetric intake holes 9011 and two axisymmetric exhaust holes 9021. First spark plug 911, second spark plug 912; first injector 921 and second injector 922 are located on the symmetrical plane of cylinder 90 and fixedly connected to cylinder 90.
The left rotor and the right rotor respectively comprise two axisymmetrically distributed blades, and the left rotor and the right rotor are structurally symmetrical.
The radial outer surface of the blade consists of 3 cylindrical surfaces, the cylindrical surface in the middle of the blade protrudes to form a boss, and the cylindrical surfaces at the left end and the right end are axially aligned. And one of the cylindrical surfaces at the left end and the right end comprises a pin hole, and the other cylindrical surface comprises a groove communicated with the lubricating oil hole.
The thickness of the blade near the root of the support is turned by 45 degrees, while the thickness of the radially outer portion of the blade is turned by 35 degrees. At the moment of ignition, the blade on the left rotor is in contact with the root of the blade on the right rotor, and the outer parts are separated by an included angle of 10 degrees to form a compression chamber.
The air inlet and outlet mechanism consists of an air outlet ring 7 and an air inlet ring 8, and the air outlet ring 7 and the air inlet ring 8 are structurally symmetrical and are collectively called as an air ring. The middle of the gas ring comprises a wide annular groove which is an antifriction groove; the left end and the right end comprise two narrow annular grooves which are lubricating oil grooves. The air ring also comprises two axisymmetric air holes, four lubricating oil holes which are symmetric in pairs and pin holes. Wherein, the air inlet, the lubricating oil hole and the pin hole on the air inlet ring 7 are respectively numbered 7001, 7011 and 7021.
The exhaust ring 7 is fixed with the left rotor by a pin, the intake ring 8 is fixed with the right rotor by a pin, and the pin is inserted into the pin holes of the blades and the air ring.
The air ring rotates with the rotor, and in the rotation process, the exhaust hole 7001 of the exhaust ring sweeps through the exhaust hole 9011 of the air cylinder 90, and the air inlet hole of the air inlet ring sweeps through the air inlet hole 9021 of the air cylinder 90. The height of the air hole in the air ring is higher than the bottom surface of the groove, the annular antifriction groove and the lubricating oil groove are divided into two sections, and it is ensured that the lubricating oil in the lubricating oil groove cannot enter the air hole in the air ring and the air hole in the air cylinder.
The main shaft 100, the left rotor, the right rotor, the left intermittent motion mechanism, and the right intermittent motion mechanism are connected by a connection manner 7 shown in fig. 7.
The gear parameters in the intermittent motion mechanism are as follows:
Figure BDA0002987499100000161
sixth gear intermittently rotating at every revolution of main shaft 100With a corner radian of
Figure BDA0002987499100000162
The two sealing plates are annular plates with central holes, which can be fixed either to the cylinder 90 by pins or to the blade. When the sealing plate is fixed with the cylinder, the sealing plate is fixed; when the seal plate is fixed with the blade, the seal plate rotates with the rotor.
The support cover comprises a main shaft hole and a short shaft hole, and the support cover is fixedly connected with the cylinder 90 through bolts. The sealing cover is fixedly connected with the supporting cover.
The working principle of the exhaust ring 7 and the intake ring 8 can be respectively referred to fig. 33 and fig. 35, when the internal combustion engine is in a state that the spark plug is about to ignite, the exhaust hole on the exhaust ring 7 is 90 degrees different from the exhaust hole on the cylinder 90, and the intake hole on the intake ring 8 is 90 degrees different from the intake hole on the cylinder 90. Due to the obstruction of the air ring, the air inlet hole and the air outlet hole on the air cylinder cannot be communicated with the inside of the air cylinder hole, and the air inlet hole and the air outlet hole on the air cylinder are both in a closed state.
After the internal combustion engine is ignited, the left-turning belt drives the exhaust ring 7 to intermittently rotate by 90 degrees, exhaust holes in the exhaust ring 7 are aligned with exhaust holes in the cylinder 90, and the exhaust holes in the cylinder are opened; while the right rotor and the intake ring remain stationary and the intake port of the cylinder 90 remains closed.
Then, the left rotor and the exhaust ring are static, the exhaust hole of the cylinder is kept in an open state, and the right rotor drives the air inlet ring to exhaust for 8 degrees. The right rotor rotates 90 degrees and then stands still, the air inlet hole of the air inlet ring 8 is aligned with the air cylinder 90, and the air inlet hole of the air cylinder 90 is opened.
Then the right rotor is kept still, the left rotor moves, air intake is started, and the next circulation is started.
In the process, only two chambers of the four chambers divided by the blades in the cylinder are used as combustion chambers, and the other two chambers are used as energy storage chambers.
In order to enable the four cavities in the cylinder to be used as combustion chambers, only two spark plugs and two oil injectors are needed to be added, the number of the exhaust holes in the exhaust ring 7 and the number of the air inlet holes in the air inlet ring 8 are increased to four, and meanwhile, the number of the exhaust holes and the number of the air inlet holes in the cylinder 90 are increased to four. The four air holes in the air ring are symmetrical about the axis of the main shaft and the symmetrical plane of the blade, as shown in FIG. 37.
Compared to example 3, this example 4 has the following optimization:
the air inlet and exhaust mechanism is simple and only comprises an air inlet ring and an exhaust ring;
secondly, the parameter J of the non-circular gear pair is closer to 1, so that the pitch curve of the non-circular gear is closer to a circle, and the transmission is more stable;
thirdly, the sealing plate and the supporting cover have simple structures;
and fourthly, the supporting cover is directly and fixedly connected with the cylinder, so that the position accuracy of the main shaft hole and the short shaft hole is easily ensured.
Example 5
Referring to fig. 38 to 42, the present embodiment 5 provides an elongated three-lobe, two-rotor internal combustion engine.
The left intermittent motion mechanism consists of a left short shaft 10, a left first gear 11, a left second gear 12, a left third gear 13, a left fourth gear 14, a left fifth gear 15, a left sixth gear 16, three left planet gears 17 and a left planet carrier 18; the right intermittent motion mechanism consists of a right short shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, three right planet gears 27 and a right planet carrier 28.
The planet carrier needs to be split into more than two parts, and the sixth gear can be assembled inside the planet carrier.
The left rotor consists of a left support body 30 and three left blades 31; the right rotor is composed of a right support 40 and 3 right blades 41. The 3 left blades 31 are axially symmetrically distributed with 120-degree included angles; the 3 right blades 41 are distributed in axial symmetry with 120 included angles.
The axial length of cylinder 90 is greater than its diameter, and cylinder 90 is fixedly connected with 6 spark plugs 911 and 6 fuel injectors 921. The spark plugs and the oil injectors are divided into two groups and are axially arranged in parallel. The cylinder 90 circumferentially comprises 3 exhaust holes 9011 and 3 air inlet holes 9021, which are axially parallel to each other.
The cylinder 90, the main shaft 100, the left and right intermittent mechanisms, and the left and right rotors are connected to each other in a connection manner 4 shown in fig. 4.
The gear parameters in the intermittent motion mechanism are as follows:
Figure BDA0002987499100000171
and when the main shaft rotates for one circle, the fifth gear which rotates intermittently rotates for 60 degrees, and the rotating direction of the fifth gear is the same as that of the rotor.
The left support 30 includes a connecting plate portion, a cylindrical shell portion, and a spline shaft portion. The connecting plate part is provided with 3 special-shaped matching holes which are axially symmetrically distributed, the spline shaft part is fixedly connected with the fifth left gear, the cylindrical shell part comprises three open grooves which are axially symmetrically distributed, the opening direction of the open grooves faces to the right, and the cylindrical shell is further provided with 3 exhaust holes 7001, 3 spark plug avoiding holes 7041 and 3 fuel injector avoiding holes 7051 which are all axially symmetrically and uniformly distributed.
The left side of the left blade 31 is provided with a convex boss which is used for matching and connecting with a special-shaped matching hole on the connecting plate part of the left supporting body 30; the radially outer surface of the left blade also includes bosses for engaging open slots in the cylindrical shell portion of the left support 30. The left vane 31 contains an axial lubrication hole inside, which passes through the boss on the left side. The left blade 31 and the left support 30 are in over-constrained fit, and the left support has the functions of the support, the sealing plate and the exhaust ring in embodiment 4.
The right support 40 is a shaft-shaped object, the outer cylindrical surface of which comprises 3 uniformly distributed connecting grooves, and the root of the right blade 41 is inserted into the connecting grooves of the right support and is fixedly matched and connected with the connecting grooves.
The right side of the right blade 41 is provided with a boss, and an axial lubricating oil hole in the right blade penetrates through the boss.
The right seal plate 60 comprises two parts, a disk and a cylindrical shell, wherein the disk part comprises three uniformly distributed matching holes, and the cylindrical shell part comprises 3 air inlet holes 8001. The right sealing plate 60 is fixedly connected with the right blade 41 in a matching way. The right seal plate serves the dual function of the seal plate and the inlet ring of example 4.
The supporting cover comprises a main shaft hole, a short shaft hole, a flange and a positioning ring, and the positioning ring part of the supporting cover extends into the cylinder hole to axially position the shaft.
The supporting cover and the sealing cover are fixedly connected to the air cylinder 90 through the same group of bolts.
The left and right rotors are different in composition. The right rotor support body 40 is a shaft-shaped object, and has poor structural strength and good structural rigidity; the left support 30 is composed of a connecting plate portion, a cylindrical shell portion and a spline shaft, and has good structural strength but poor structural rigidity.
The left blade 31 can only obtain lubricating oil by immersing into the lubricating oil storage chamber inside the left support cover 51 through the internal axial lubricating oil hole thereof; the right rotor can directly obtain lubricating oil from a lubricating storage chamber in the right supporting cover 61 through an axial lubricating oil hole in the right rotor, and can also obtain the lubricating oil from a central hole of the right supporting body 41.
Example 6
Referring to fig. 43 to 46, the present embodiment 6 provides a four-lobe birotor internal combustion engine of a short and thick type, the constituent parts of which include:
a main shaft 100, a cylinder 90, 4 equispaced spark plugs 911, 4 equispaced fuel injectors 921, a left support cover 51, a left seal cover 52, a right support cover 61, a right seal cover 62, left and right rotors and a left and right intermittent motion mechanism, and a left round nut 11 and a right round nut 121.
Wherein, the left rotor is formed by fixedly connecting a left support body 30 and four left blades 31, and the right rotor is formed by fixedly connecting a right support body 40 and four right blades 41; the left intermittent motion mechanism consists of a left short shaft 10, a left first gear 11, a left second gear 12, a left third gear 13, a left fourth gear 14, a left fifth gear 15, a left sixth gear 16, three left planet gears 17 and a left planet carrier 18; the right intermittent motion mechanism consists of a right short shaft 20, a right first gear 21, a right second gear 22, a right third gear 23, a right fourth gear 24, a right fifth gear 25, a right sixth gear 26, three right planet gears 27 and a right planet carrier 28.
The main shaft 100, the air cylinder 90, the left and right rotors, and the left and right intermittent mechanisms are connected to each other in a connection mode 2 shown in fig. 2. And the sixth gear is matched with the rotor supporting body through the rectangular shaft hole to transmit torque, so that the fixed connection is realized.
The gear parameters in the intermittent motion mechanism are as follows:
Figure BDA0002987499100000181
and when the main shaft rotates for one circle, the sixth gear which rotates intermittently rotates for 45 degrees, and the rotation direction of the sixth gear is the same as that of the main shaft.
The main shaft 100 is fixedly connected with the first gear through a spline; and the fourth gear, the planet carrier and the support body are movably connected through clearance fit.
Thrust bearings can be arranged between the fifth gear and the planet carrier and between the fourth gear and the bearing cover for axial supporting and positioning.
The main shaft 100 has the largest middle diameter and the width equal to the width of the cylinder, and has the largest mass and the energy storage function of the flywheel. The fall of the shaft shoulder of the main shaft is large, and a processing space of the spline is provided.
The supporting body is connected with the blades in a matched mode through the special-shaped shaft holes in the side face, the axial lubricating oil holes of the blades are communicated with the outer side of the supporting body, and lubricating oil is obtained by directly immersing the lubricating oil storage chamber provided by the supporting cover in the rotating process.
The flange of the supporting cover contains four uniformly distributed round air holes, and the supporting body also contains four uniformly distributed round air holes. The four air holes of the left support body 30 and the left support cover 51 are air discharge holes, and the four air holes 8001 of the right support body 40 and the four air holes 6101 of the right support cover 61 are air intake holes. The support has the triple functions of the support, the sealing plate and the gas ring in example 4.
Compared to examples 1 to 4, this example 6 has the following features:
firstly, the rotor has simple structural form but poorer structural rigidity, and is suitable for occasions with small axial width of the blade.
And secondly, the vanes directly obtain lubricating oil from the side surface, and the liquid level of the lubricating oil stored in the supporting cover is only higher than the axial lubricating oil hole in the vane below and does not need to be higher than the axle center of the main shaft.
And the main shaft is matched and connected with the fourth gear, the planet carrier and the support body, the diameter of the main shaft is large, the strength is high, and enough shaft shoulder fall can be provided for arranging the spline.

Claims (9)

1. A double-rotor internal combustion engine comprises a cylinder, a main shaft, two rotors and two intermittent motion mechanisms, and is characterized in that: the main shaft is a stepped shaft, the axis of the main shaft is a straight line, the cylinder comprises a cylinder hole which is axially communicated, the rotor comprises a central through hole which is coaxial with the cylinder hole, the intermittent motion mechanism is a closed differential gear train comprising a non-circular gear pair, the two rotors are placed inside the cylinder hole in parallel, the main shaft penetrates through the central through hole of the rotor, the two rotors, the main shaft and the cylinder are movably connected, the two intermittent motion mechanisms are positioned at two sides of the cylinder in the axial direction, the two intermittent motion mechanisms comprise a differential gear train and a fixed shaft gear train, the differential gear train and the fixed shaft gear train comprise two pairs, components in the fixed shaft gear train comprise a first gear, a second gear, a third gear, a fourth gear and a short shaft, the first gear and the second gear are a pair of meshed non-circular gear pair, the third gear and the fourth gear are a pair of meshed circular gear pair, the second gear and the third gear are fixedly connected with the short shaft, components in the differential gear train comprise a fifth gear, a sixth gear, a planet wheel and a planet carrier, one of the fifth gear, the sixth gear and the planet carrier is fixedly connected with the first gear and the main shaft at the same time, the other one of the fifth gear, the sixth gear and the planet carrier is fixedly connected with the fourth gear, and the last remaining one is fixedly connected with the rotor.
2. A twin rotor internal combustion engine as defined in claim 1 wherein: the rotor comprises a support body and blades, the support body is an annular object, the axis of the support body comprises a through hole, the main shaft penetrates through the central through hole in the support body, the main shaft is movably connected with the support body, the left side and the right side of each blade are planes, each blade comprises an inner cylindrical surface and an outer cylindrical surface in the radial direction, the blades are connected with the support body in a matched mode, lubricating oil holes communicated with the left side face and the right side face and the inner cylindrical surface and the outer cylindrical surface in the radial direction are formed in the inner portion of each blade, and the surfaces of the blades further comprise grooves.
3. A twin rotor internal combustion engine as defined in claim 2, wherein: the supporting body is arranged on the outer surface of the sealing plate, the outer surface of the sealing plate is a cylindrical surface, the axis of the sealing plate is provided with a through hole, and the supporting body penetrates through the through hole in the axis of the sealing plate.
4. A twin rotor internal combustion engine as in claim 3 wherein: the bearing cover comprises a cylindrical surface in the radial direction, the bearing cover shaft comprises a through main shaft hole and a short shaft hole parallel to the main shaft hole, the main shaft penetrates through the main shaft hole of the bearing cover, the short shaft penetrates through the short shaft hole of the bearing cover, the main shaft and the short shaft are movably connected with the bearing cover, and the sealing plate and the bearing cover are fixedly connected with the air cylinder.
5. A twin rotor internal combustion engine as in claim 4 wherein: the air inlet ring and the air exhaust ring are axially arranged in parallel, the air inlet ring and the air exhaust ring are fixedly connected with a rotor, and the air inlet ring and the air exhaust ring are in movable contact with the air cylinder.
6. A twin rotor internal combustion engine as in claim 4 wherein: the air inlet mechanism and the air outlet mechanism respectively comprise a cam, an air passage, an air valve, a spring and an ejector rod, the air passage is fixedly connected with the sealing plate, the cam is fixedly connected with the supporting body, the air valve is fixedly connected with the ejector rod, the spring is sleeved on the ejector rod, the air passage is a channel shaped like a Chinese character 'ji', the sealing plate comprises an air hole, the supporting cover comprises a notch groove, the air outlet end of the air passage is aligned to the air hole in the sealing plate, the air passage penetrates through the notch groove in the supporting cover, and the inlet end of the air passage is positioned outside the supporting cover.
7. A twin-rotor internal combustion engine as defined in claim 5 or 6, wherein: the two rotors are respectively a left rotor and a right rotor, the two intermittent motion mechanisms are respectively a left intermittent motion mechanism and a right intermittent motion mechanism, the left rotor comprises a left rotor blade and a left rotor support body, the right rotor comprises a right rotor blade and a right rotor support body, the left rotor blade is fixedly connected with the left rotor support body, the right rotor blade is fixedly connected with the right rotor support body, the left rotor support body is axially parallel to the right rotor support body, the left rotor blade is circumferentially parallel to the right rotor blade, the left rotor support body is movably connected with the right rotor support body, one of a fifth gear, a sixth gear and a planet carrier in the left intermittent motion mechanism is fixedly connected with the left rotor support body, one of the fifth gear, the sixth gear and the planet carrier in the right intermittent motion mechanism is fixedly connected with the right rotor support body, the left intermittent motion mechanism is located on the left side of the air cylinder, the right intermittent motion mechanism is located on the right side of the air cylinder, the two sealing plates are respectively a left sealing plate and a right sealing plate, the two supporting covers are respectively a left supporting cover and a left supporting cover, the left sealing plate is fixedly connected with the left supporting cover, and the right sealing plate is fixedly connected with the right supporting cover.
8. A twin-rotor internal combustion engine as defined in claim 7, wherein: still include bearing, key and round nut, through bearing swing joint between main shaft and supporter, the supporting lid, the planet carrier passes through bearing swing joint with the planet wheel, the minor axis passes through bearing swing joint with the supporting lid, the minor axis passes through key fixed connection with second gear, third gear, the main shaft passes through key fixed connection with first gear, the main shaft passes through bearing swing joint with the fourth gear, one of fifth gear, sixth gear, planet carrier three passes through bearing swing joint with the main shaft, round nut and main shaft fixed connection.
9. A twin-rotor internal combustion engine as defined in claim 8, wherein: the main shaft is bilaterally symmetrical, the air cylinders are bilaterally symmetrical, the left rotor and the right rotor are structurally symmetrical, the short shaft, the first gear, the second gear, the third gear, the fourth gear, the fifth gear, the sixth gear, the planet wheel and the planet carrier in the left intermittent motion are structurally symmetrical with the short shaft, the first gear, the second gear, the third gear, the fourth gear, the fifth gear, the sixth gear, the planet wheel and the planet carrier in the right intermittent motion mechanism respectively, the difference between the initial rotation angle phases of the first gear in the left intermittent motion mechanism and the first gear in the right intermittent motion mechanism is 180 degrees, the left sealing plate and the right sealing plate are structurally symmetrical, and the left supporting cover and the right supporting cover are structurally symmetrical.
CN202110304359.8A 2021-03-22 2021-03-22 Double-rotor internal combustion engine Active CN113027601B (en)

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1485088A (en) * 1974-03-25 1977-09-08 Williams D Rotary piston fluid machine
CN2254483Y (en) * 1996-03-29 1997-05-21 唐禾天 Blade-rotor motor
CN1664329A (en) * 2004-09-02 2005-09-07 冯卫东 Angle variable rotor engine with a planet gear
CN201068818Y (en) * 2007-08-01 2008-06-04 郑海波 Blade wheel internal combustion engine
CN101196124A (en) * 2007-08-08 2008-06-11 邵文英 Vane type cavity capability changing device, vane type gas engine and vane compressor
CN102410349A (en) * 2011-09-14 2012-04-11 北京农业职业学院 Periodic intermittent motion output device
CN102797558A (en) * 2012-08-20 2012-11-28 赛兴嘎 Rotor engine
CN211500796U (en) * 2019-09-05 2020-09-15 王明中 Rotor blade engine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1485088A (en) * 1974-03-25 1977-09-08 Williams D Rotary piston fluid machine
CN2254483Y (en) * 1996-03-29 1997-05-21 唐禾天 Blade-rotor motor
CN1664329A (en) * 2004-09-02 2005-09-07 冯卫东 Angle variable rotor engine with a planet gear
CN201068818Y (en) * 2007-08-01 2008-06-04 郑海波 Blade wheel internal combustion engine
CN101196124A (en) * 2007-08-08 2008-06-11 邵文英 Vane type cavity capability changing device, vane type gas engine and vane compressor
CN102410349A (en) * 2011-09-14 2012-04-11 北京农业职业学院 Periodic intermittent motion output device
CN102797558A (en) * 2012-08-20 2012-11-28 赛兴嘎 Rotor engine
CN211500796U (en) * 2019-09-05 2020-09-15 王明中 Rotor blade engine

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