WO2022048524A1 - 一种双转子发动机及其运行参数的调控方法 - Google Patents

一种双转子发动机及其运行参数的调控方法 Download PDF

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Publication number
WO2022048524A1
WO2022048524A1 PCT/CN2021/115504 CN2021115504W WO2022048524A1 WO 2022048524 A1 WO2022048524 A1 WO 2022048524A1 CN 2021115504 W CN2021115504 W CN 2021115504W WO 2022048524 A1 WO2022048524 A1 WO 2022048524A1
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Prior art keywords
rotor
dual
engine
stator
main shaft
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PCT/CN2021/115504
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English (en)
French (fr)
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赵新年
李军生
计超
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陕西新年动力科技集团有限公司
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Publication of WO2022048524A1 publication Critical patent/WO2022048524A1/zh

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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
    • F02B53/02—Methods of operating
    • 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
    • F02B53/04—Charge admission or combustion-gas discharge
    • 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
    • F02B53/04—Charge admission or combustion-gas discharge
    • F02B53/08—Charging, e.g. by means of rotary-piston pump
    • 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
    • F02B53/10—Fuel supply; Introducing fuel to combustion space
    • 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
    • F02B55/08—Outer members for co-operation with rotary pistons; Casings
    • F02B55/10—Cooling thereof
    • 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
    • F02B55/14—Shapes or constructions of combustion chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention belongs to the technical field of internal combustion engines, and particularly relates to a dual-rotor engine and a method for regulating and controlling operating parameters thereof.
  • the rotary engine uses the rotary motion of the rotor in the cylinder to control the compression and discharge. Unlike the traditional reciprocating piston engine, the linear reciprocating motion is changed to a rotary motion. Compared with the reciprocating engine, the rotary engine cancels the useless linear motion, so the rotary engine with the same power is smaller in size, lighter in weight, and lower in vibration and noise. It is a novel and efficient engine in the automotive industry.
  • a more representative rotary engine technology is the triangular rotary engine of Mazda Company, such as the rotary piston engine disclosed in publication number CN101413436 and its design method, while its rotating part orbits the output shaft, it is parallel to the output shaft and The offset eccentric shaft rotates around the center, and the rotor is approximately triangular in shape when viewed from the shaft direction.
  • the rotary engine with this structure has high fuel consumption and low compression ratio, so it can only use the compression ignition type combustion method, which has restrictions on the type of fuel.
  • a twin-rotor engine has two rotors, and the rotating mechanisms of the two rotors can provide the same or different rotational speeds.
  • patent CN109899154A proposes a dual-rotor engine, in which the piston performs rotary motion, and no redundant mechanism is required to convert the motion form; the rotor is a symmetrical structure without eccentric motion, the first end of the engine main shaft has external splines, and the second end has internal splines.
  • the spline is matched with the bearing on the rotor; the stroke action of the second rotor is the same as that of the first rotor during operation.
  • the rotor in the above design has no eccentric movement, which can reduce the wear on the cylinder, but has the defect of small output.
  • the connection mechanism of the shafts of the two rotors in this technology is complicated, which also increases the difficulty of processing.
  • the first object of the present invention is to provide a dual-rotor engine.
  • the second object of the present invention is to propose a method for regulating the operating parameters of the dual-rotor engine based on the structure of the dual-rotor engine.
  • a third object of the present invention is to propose a method of operating the twin-rotor engine.
  • a dual-rotor engine comprising a stator and a rotor, the dual-rotor engine comprising two series-connected rotors, respectively a first rotor and a second rotor, the two rotors are both "8"-shaped, and the "8" of the two rotors
  • the included angle of the long axis of the glyph is 180 degrees;
  • the stator has a three-lobed cavity surrounded by three arcs, and the rotor is located in the three-lobed cavity inside the stator.
  • the two-rotor engine has 2 stators, namely the first stator and the second stator (that is, the first rotor is located in the three-lobed cavity of the first stator, and the second rotor is located in the second stator. in the three-lobed cavity of the stator);
  • Each arc-shaped inner wall of the three-lobed cavity is provided with radially outward combustion chambers, and one stator has three symmetrically distributed combustion chambers.
  • the center of the rotor is provided with a main shaft
  • the main shaft includes multiple sections
  • the part located in the first rotor is the first main shaft
  • the part located in the second rotor is the second main shaft
  • the first main shaft and The axes of the second section of the main shaft do not coincide, and the two sections of the main shaft are connected by connecting pieces.
  • the connecting piece is a cylinder, and the connecting piece is provided with two holes whose centers are located on the same diameter, which are respectively inserted into the first-section main shaft and the second-section main shaft; further preferably, the first-section main shaft and The distance between the axes of the second section of the main shaft is 30 to 50 mm.
  • the rotor has an arc-shaped side wall, and when the head of the "8"-shaped rotor is located in a cavity in the three-lobed cavity, the distance between the arc-shaped side wall of the rotor and the arc-shaped inner wall of the cavity is 1 ⁇ 3mm.
  • the shape of the combustion chamber is a cone, the tip of the cone faces outward along the radial direction of the stator, and a fuel injection nozzle is provided at a position opposite to the tip of the cone.
  • the opening of the combustion chamber on the arc-shaped inner wall is circular or elliptical, and the arc of the opening is 20-30% of the arc of the arc-shaped inner wall.
  • the height of the opening is about 50-60% of the height of the stator.
  • the depth of the combustion chamber is 20-40 mm.
  • the casing of the dual-rotor engine is assembled from multiple parts, including a front end cover, a first outer offset cover, a first stator, a first inner offset cover, a middle section casing, and a second outer offset cover that are connected in sequence. , the second stator, the second inner partial cover and the rear end cover.
  • a preferred technical solution of the present invention is that the front end cover and the rear end cover are provided with an air inlet and a cooling liquid passage; the included angle between the air inlet and the axis of the cooling liquid passage is 80-95 degrees, and / or
  • a vent hole is provided on the side wall of the middle-section housing.
  • each group has 2 holes, and the hole area of each group of holes is 10-30 cm 2 .
  • a method for regulating and controlling operating parameters of a dual-rotor engine comprising:
  • the hole area of each group of openings is 10-12cm 2 , and the displacement of the engine is 0.7-0.75 liters.
  • the hole area of each group of openings is 12-18cm 2 , and the displacement of the engine is 1.3-1.7 liters.
  • the hole area of each group of openings is 18-30 cm 2 , and the displacement of the engine is 2.4-2.6 liters.
  • a method for operating a dual-rotor engine comprising:
  • the fuel of the dual-rotor engine is oil, and the oil is one of kerosene, gasoline, diesel oil, and methanol;
  • the rotation of the rotor makes the gas and oil mix well in a swirling shape, so that the fuel is fully burned.
  • the two rotors are connected in series with the main shaft, and the first-section main shaft and the second-section main shaft are inserted into the through hole of the connecting piece, which simplifies the processing difficulty and has better mechanical strength;
  • the invention adds a combustion chamber on the side wall of the rotor, when the head of the "8"-shaped rotor is located in a cavity in the three-lobed cavity, in addition to the arc-shaped side wall of the rotor and the arc-shaped inner wall of the cavity.
  • the spacing provides a combustion space, and there is an additional combustion space for the combustion chamber, so that the oil and gas can be mixed more evenly.
  • the included angle between the axes of the two rotors is 180 degrees, which provides greater output power; the difference between the maximum stroke and the minimum stroke of the rotors is larger, thereby improving the compression ratio, and when diesel is used as fuel
  • the compression ratio can reach 22.3.
  • FIG. 1 is a perspective view of the appearance of the twin-rotor engine of the present invention.
  • FIG. 2 is a top view of the first stator.
  • FIG. 3 is a schematic diagram of the connection mode of the first section of the main shaft and the second section of the main shaft.
  • Figure 4 is a perspective view of the rotor.
  • 1 is the front end cover
  • 201 is the first stator
  • 202 is the second stator
  • 3 is the partial cover
  • 4 is the main shaft
  • 401 is the first main shaft
  • 402 is the second main shaft
  • 5 is the air inlet
  • 6 is the cooling Liquid channel
  • 7 is the rear end cover
  • 8 is the rotor
  • 9 is the combustion chamber
  • 10 is the bearing of the rotor
  • 11 is the opening on the side wall of the rotor
  • 12 is the exhaust port
  • 13 is the position of the fuel injection nozzle
  • 14 is the The connecting piece
  • 15 is the middle section shell.
  • a dual-rotor engine includes a stator and a rotor 8.
  • the dual-rotor engine includes two series-connected rotors 8, which are a first rotor and a second rotor respectively, and the two rotors are both "8" shaped (see FIG. 4), 2
  • the angle between the long axes of the "8" shape of each rotor is 180 degrees;
  • FIG. 2 shows a top view of the first stator 201.
  • the stator has a three-lobed cavity surrounded by three arcs, and the rotor is located in the three-lobed cavity inside the stator. In the cavity, the arc of the head of the "8" is matched with the arc forming the three-lobed cavity; the double-rotor engine has two stators, which are the first stator 201 and the second stator respectively.
  • 202 ie, the first rotor is located in the three-lobed cavity of the first stator 201 and the second rotor is located in the three-lobed cavity of the second stator 202).
  • the center of the rotor is provided with a main shaft 4 .
  • the main shaft includes multiple sections.
  • the part located in the first rotor is the first main shaft 401
  • the part located in the second rotor is the second main shaft 402 .
  • the main shaft of the first section and the main shaft of the second section are connected by a connecting piece 14, the connecting piece 14 is in the shape of a cylinder, and the connecting piece is provided with two holes centered on the same diameter, which are respectively inserted into the main shaft of the first section 401 and the main shaft of the second section.
  • the distance between the axes of the first segment spindle and the second segment spindle is 30-50 mm.
  • the rotor 8 has an arc-shaped side wall.
  • the distance between the arc-shaped side wall of the rotor and the arc-shaped inner wall of the cavity is 1-3 mm.
  • the three-lobed cavity has an arc-shaped inner wall, and three symmetrically distributed combustion chambers 9 are opened on the arc-shaped inner wall of the three-lobed cavity;
  • the tip faces outwards in the radial direction of the stator, and the position opposite to the conical tip is the position 13 of the fuel injection nozzle.
  • the depth of the combustion chamber is 20-40 mm.
  • the casing of the dual-rotor engine is assembled from multiple parts, including the front end cover 1 , the first outer offset cover, the first stator 201 , the first inner offset cover, the middle section casing 15 , which are connected in sequence.
  • the second outer offset cover, the second stator 202 , the second inner offset cover and the rear end cover 7 are connected in sequence.
  • the front end cover 1 and the rear end cover 7 are provided with an air inlet 5 and a cooling liquid passage 6; the included angle between the air inlet 5 and the axis of the cooling liquid passage 6 is 90 degrees.
  • a vent hole 12 is provided on the side wall of the .
  • each group has two holes, and the hole area of the holes 11 on the side wall of each group of rotors is 10-30 cm 2 .
  • the front end cover 1 is made of aluminum alloy, with a diameter of 512mm (without the four ears, and the ears are 600mm).
  • the length and width of the rotor are 349.3mm and 259.2mm, the thickness is 125mm, and the weight of this rotary engine is about 600kg.
  • the thickness of the gland of the rotor (the inner cover and the outer cover, the thickness is the same) is 40mm.
  • the outer diameter of the bearing 10 of the rotor is 130 mm.
  • the distance between the axes of the first and second main shafts is 50mm, and the distances between the axes of the first and second main shafts and the center of the connecting piece 14 are both 25mm.
  • the opening of the combustion chamber 7 on the arc inner wall of the stator is elliptical, and the shape of the combustion chamber is cone.
  • the arc occupied by the opening of the combustion chamber is about 30 degrees, and the arc of the arc-shaped inner wall where it is located is 120 degrees.
  • the size of the opening of the combustion chamber is 58 mm in the short axis (the short axis of the opening is about 50-60% of the height of the stator), the long axis is 88 mm, and the depth is 40 mm.
  • each group of openings 11 on the side wall of the rotor is 21.86 cm 2
  • the distance d between the arc-shaped side wall of the rotor and the arc-shaped inner wall of the three-lobed cavity of the stator is 3 mm.
  • This embodiment is a method for regulating and controlling the operating parameters of a dual-rotor engine based on the structure of Example 1 and an operating method for the dual-rotor engine in Example 1:
  • Lubricating oil circulates itself in the twin-rotor engine to lubricate the rotors.
  • the fuel is diesel and the coolant is engine oil.
  • the dual-rotor engine adopts compression ignition, the compression ratio is above 17, and the temperature can reach 600-700 °C. During operation, the rotor rotates to make the gas and oil fully mix in a swirl shape, so that the fuel is fully burned.
  • the fuel of the dual-rotor engine is diesel, the displacement of the engine is 2.5, and the rotational speed is 3000-5000.
  • the engine compression ratio is 22.3.
  • a dual-rotor engine includes a stator and a rotor 8.
  • the dual-rotor engine includes two series-connected rotors 8, which are the first rotor and the second rotor respectively. "The included angle of the long axis of the glyph is 180 degrees,
  • the stator has a three-lobed cavity surrounded by three arcs, and the rotor is located in the three-lobed cavity inside the stator.
  • the arcs are adapted; the dual rotor engine has two stators, namely the first stator 201 and the second stator 202 .
  • the center of the rotor is provided with a main shaft 4, the main shaft includes multiple sections, the part located in the first rotor is the first section main shaft 401, the part located in the second rotor is the second section main shaft 402, the first section main shaft and the second section main shaft 402.
  • the two main shafts are connected by a connecting piece 14, the connecting piece 14 is in the shape of a cylinder, and two holes on the same diameter are inserted into the first main shaft 401 and the second main shaft 402 respectively.
  • the three-lobed cavity has an arc-shaped inner wall, and three symmetrically distributed combustion chambers 9 are opened on the arc-shaped inner wall of the three-lobed cavity;
  • the radial direction of the nozzle is outward, and the position opposite to the tapered tip is the position 13 of the fuel injection nozzle.
  • the casing of the dual-rotor engine in this embodiment is assembled from multiple parts, including a front end cover 1, a first outer offset cover, a first stator 201, a first inner offset cover, a middle section casing 15, a second outer offset cover, The partial cover, the second stator 202 , the second inner partial cover and the rear end cover 7 .
  • the front end cover 1 and the rear end cover 7 are provided with an air inlet 5 and a cooling liquid passage 6; the included angle between the air inlet 5 and the axis of the cooling liquid passage 6 is 90 degrees.
  • a vent hole 12 is provided on the side wall of the .
  • Two groups of holes are opened on the side wall of the rotor 8, and each group has two holes.
  • the length and width of the rotor are 349.3mm and 259.2mm, the thickness is 125mm, and the weight of this rotary engine is about 500kg.
  • the thickness of the gland of the rotor (including the inner partial cover and the outer partial cover, the thickness is the same) is 40mm.
  • the outer diameter of the bearing 10 of the rotor is 130 mm.
  • the distance between the shaft centers of the first and second main shafts is 40mm, and the distances between the shaft centers of the first and second main shafts and the center of the connecting piece 14 are both 20mm.
  • the opening of the combustion chamber 7 on the arc-shaped inner wall of the stator is elliptical, the shape of the combustion chamber is conical, and the depth is 35 mm.
  • the hole area of each group of openings 11 on the side wall of the rotor is 16 cm 2 , and the distance d between the arc-shaped side wall of the rotor and the arc-shaped inner wall of the three-lobed cavity of the stator is 1.5 mm.
  • the present embodiment provides a method for regulating and controlling the operating parameters of the rotary engine of the third embodiment, which is based on the rotor parameters of the third embodiment, and the operating method of the dual-rotor engine:
  • Lubricating oil circulates itself in the rotary engine to lubricate the rotors.
  • the fuel is diesel;
  • the fuel of the rotary engine is diesel, the displacement of the engine is 1.5, and the rotational speed is 5000-7000.
  • the distance between the axes of the first and second main shafts is 32 mm, and the distances between the axes of the first and second main shafts and the center of the connecting piece 14 are both 16 mm.
  • the opening of the combustion chamber 7 on the arc-shaped inner wall of the stator is elliptical, the shape of the combustion chamber is conical, and the depth is 35 mm.
  • the hole area of each group of openings 11 on the side wall of the rotor is 22 cm 2 , and the distance d between the arc-shaped side wall of the rotor and the arc-shaped inner wall of the three-lobed cavity of the stator is 3 mm.
  • Lubricating oil circulates itself in the rotary engine to lubricate the rotors.
  • the fuel is diesel;
  • the fuel of the rotary engine is diesel with a compression ratio of 22.3.
  • the displacement of the engine is 0.7 and the speed is 7000-11000.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

一种双转子发动机，包括定子和转子（8），该双转子发动机包括2个串联的转子（8），分别为第一转子和第二转子，2个转子均为"8"字形，2个转子的"8"字形的长轴的夹角为180度，定子内部具有三段弧形侧壁围成的三瓣形空腔，转子（8）位于定子内部的三瓣形空腔中，"8"字的头部的弧与构成三瓣形空腔的圆弧相适配；该双转子发动机有2个定子，分别为第一定子（201）和第二定子（202）。该双转子发动机在转子的侧壁上增加了燃烧室，当"8"字形转子（8）的头部位于三瓣形空腔中的一个空腔时，除了转子的弧形侧壁和该空腔的弧形内壁间距提供燃烧空间，还额外有燃烧室的燃烧空间，使油气混合更加均匀。还公开了一种双转子发动机运行参数的调控方法及一种双转子发动机的运行方法。

Description

一种双转子发动机及其运行参数的调控方法 技术领域
本发明属于内燃发动机技术领域，具体涉及一种双转子发动机及其运行参数的调控方法。
背景技术
转子发动机采用在缸体内的转子旋转运动来控制压缩和排放，不同于传统的往复活塞式发动机，把直线往复运动改成了旋转运动。与往复式发动机相比，转子发动机取消了无用的直线运动，因而同样功率的转子发动机尺寸较小，重量较轻，而且振动和噪声较低，是汽车工业领域内新颖而高效的一款发动机。比较具有代表性的转子发动机技术是马自达公司的三角形转子发动机，例如公开号CN101413436所公开的转子活塞发动机及其设计方法，其转动部绕输出轴做轨道运动的同时，以平行于该输出轴且偏置的偏心轴为中心旋转，并且从轴方向看转子近似呈三角形状。该结构转子发动机油耗较大，压缩比较小，因此只能用压燃式的燃烧方式，对燃料种类有限制。
双转子发动机有两个转子，两个转子的转动机构可以提供相同或不同的转速。例如专利CN109899154A提出一种双转子发动机，其中活塞做旋转运动，无需多余机构转换运动形式；其中的转子为对称结构，无偏心运动，发动机主轴的第一端有外花键，第二端有内花键，与转子上的轴承配合；运行时第二转子与第一转子的冲程动作相同。上述设计中的转子无偏心运动，可减少对缸体的磨损，但存在出力较小的缺陷。该技术两个转子的轴的连接机构复杂，也增加了加工的难度。
发明内容
为解决上述现有技术的问题，本发明的第一个目的是提供一种双转子发动机。
本发明第二个目的是基于双转子发动机的结构，提出所述的双转子发动机的运行参数的调控方法。
本发明的第三个目的是提出所述双转子发动机的运行方法。
实现本发明上述目的的技术方案为：
一种双转子发动机，包括定子和转子，所述双转子发动机包括2个串联的转子，分别为第一转子和第二转子，2个转子均为“8”字形，2个转子的“8”字形的长轴的夹角为180度；
所述定子内部具有三段圆弧围成的三瓣形空腔，转子位于定子内部的三瓣形空腔中，“8”字的头部的弧与构成所述三瓣形空腔的圆弧相适配；所述双转子发动机有2个定子，分别为第一定子和第二定子(即，第一转子位于第一定子的三瓣形空腔中，第二转子位于第二定子的三瓣形空腔中)；
在所述三瓣形空腔的每段弧形内壁上开有径向向外的燃烧室，一个定子上有3个对称分布的燃烧室。
其中，所述转子的中心设置有主轴，所述主轴包括多段，位于第一转子内的部分为第一段主轴，位于第二转子内的部分为第二段主轴，所述第一段主轴和第二段主轴的轴心不重合，两段主轴以连接件连接。
优选地，所述连接件为圆柱体，连接件上开有圆心位于同一条直径上的二个孔，分别插入所述第一段主轴和第二段主轴；进一步优选所述第一段主轴和第二段主轴的轴心距离为30～50mm。
其中，所述转子具有弧形侧壁，当“8”字形转子的头部位于三瓣形空腔中的一个空腔时，转子的弧形侧壁和该空腔的弧形内壁间距为1～3mm。
进一步地，所述燃烧室形状为锥形，锥形的尖部沿定子的径向方向朝外，与所述锥形尖部相对的位置处设置有喷油嘴。
优选地，燃烧室在所述弧形内壁上燃烧室的开口为圆形或椭圆形，开口的弧度为所在弧形内壁的弧度的20～30％。开口的高度约为定子高度的50～60％。
进一步优选地，所述燃烧室深度为20～40mm。
其中，所述双转子发动机的壳体由多部分组装而成，包括顺序连接的前端盖、第一外偏盖、第一定子、第一内偏盖、中段壳体、第二外偏盖、第二定子、第二内偏盖和后端盖。
本发明的一种优选技术方案为，所述前端盖和后端盖上均设置有进气口和冷却液道；所述进气口与冷却液道的轴线的夹角为80～95度，和/或
在所述中段壳体的侧壁上设置有排气孔。
进一步优选地，在所述转子的侧壁上开有两组孔，每组有2个，每组开孔的孔面积为10～30cm 2。
一种双转子发动机运行参数的调控方法，包括：
在所述转子侧壁上开有两组孔，通过调整转子侧壁开孔尺寸而调整发动机的排量，
每组开孔的孔面积为10～12cm 2，发动机的排量为0.7～0.75升，
每组开孔的孔面积为12～18cm 2，发动机的排量为1.3～1.7升，
每组开孔的孔面积为18～30cm 2，发动机的排量为2.4～2.6升。
一种双转子发动机的运行方法，包括：
组装完成所述双转子发动机后，向所述双转子发动机内注入润滑油；
所述双转子发动机的燃料为油，所述油是煤油、汽油、柴油、甲醇中的一种；
转子转动使气和油以漩涡状充分混合，使燃料充分燃烧。
本双转子发动机的运行参数中，排量和转速的对于关系为：
排量0.7，转速7000-11000
1.33   5000-7000
2.5    3000-5000
本发明的有益效果在于：
本发明提出的双转子发动机，两个转子以主轴串联，在连接件的贯通孔内插入所述第一段主轴和第二段主轴，简化了加工的难度，且具有更好的机械强度；
本发明在转子的侧壁上增加了燃烧室，当“8”字形转子的头部位于三瓣形空腔中的一个空腔时，除了转子的弧形侧壁和该空腔的弧形内壁间距提供燃烧空间，还额外有燃烧室的燃烧空间，使油气混合更加均匀，转子转动使气和油以漩涡状充分混合，燃料得以充分燃烧。
本发明提出的双转子发动机，两个转子的轴线夹角为180度，提供了更大的输出功率；转子最大行程和最小行程的差值更大，从而提高了压缩比，以柴油为燃料时压缩比可达22.3。
附图说明
图1为本发明双转子发动机外观的立体视图。
图2为第一定子的俯视图。
图3为第一段主轴和第二段主轴连接方式的示意图。
图4为转子的立体视图。
图中，
1为前端盖，201为第一定子，202为第二定子，3为偏盖，4为主轴，401为第一段主轴，402为第二段主轴，5为进气口，6为冷却液道，7为后端盖，8为转子，9为燃烧室，10为转子的轴承，11为转子侧壁上的开孔，12为排气口，13为喷油嘴的位置，14为连接件，15为中段壳体。
具体实施方式
以下实施例用于说明本发明，但不用来限制本发明的范围。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明保护范围的限制。
实施例中，如无特殊说明，所采用的技术手段均为本领域已有的技术手段。
实施例1
一种双转子发动机，包括定子和转子8，本双转子发动机包括2个串联的转子8，分别为第一转子和第二转子，2个转子均为“8”字形(参见图4)，2个转子的“8”字形的长轴的夹角为180度；
第一定子和第二定子形状相同，图2示出第一定子201的俯视视图，所述定子内部具有三段圆弧围成的三瓣形空腔，转子位于定子内部的三瓣形空腔中，“8”字的头部的弧与构成所述三瓣形空腔的圆弧相适配；所 述双转子发动机有2个定子，分别为第一定子201和第二定子202(即，第一转子位于第一定子201的三瓣形空腔中，第二转子位于第二定子202的三瓣形空腔中)。
参见图3，转子的中心设置有主轴4，所述主轴包括多段，位于第一转子内的部分为第一段主轴401，位于第二转子内的部分为第二段主轴402，所述第一段主轴和第二段主轴以连接件14连接，所述连接件14为圆柱体形状，连接件上开有圆心位于同一条直径的二个孔，分别插入所述第一段主轴401和第二段主轴402，优选所述第一段主轴和第二段主轴的轴心距离为30～50mm。
转子8具有弧形侧壁，当“8”字形转子的头部位于三瓣形空腔中的一个空腔时，转子的弧形侧壁和该空腔的弧形内壁间距为1～3mm。
参见图2，所述三瓣形空腔具有弧形内壁，在三瓣形空腔的弧形内壁上开有3个对称分布的燃烧室9；所述燃烧室形状为锥形，锥形的尖部沿定子的径向方向朝外，与所述锥形尖部相对的位置处为喷油嘴的位置13。优选地，所述燃烧室深度为20～40mm。
参见图1，所述双转子发动机的壳体由多部分组装而成，包括顺序连接的前端盖1、第一外偏盖、第一定子201、第一内偏盖、中段壳体15、第二外偏盖、第二定子202、第二内偏盖和后端盖7。
在前端盖1和后端盖7上均设置有进气口5和冷却液道6；所述进气口5与冷却液道6的轴线的夹角为90度，在所述中段壳体15的侧壁上设置有排气孔12。
在所述转子8的侧壁上开有两组孔，每组有2个，每组转子侧壁上的开孔11的孔面积为10～30cm 2。
本实施例的部分部件参数为：前端盖1为铝合金材质，直径512mm(不加四个耳朵，加上耳朵是600mm)。转子的长宽是349.3mm和259.2，厚度是125mm，本转子发动机重量约600公斤。转子的压盖(内偏盖和外偏盖，厚度一样)的厚度为40mm。转子的轴承10的外径为130mm。第一段主轴和第二段主轴的轴心距离为50mm，第一段主轴和第二段主轴的轴心与连接件14中心的距离均为25mm。
燃烧室7在定子的弧形内壁上的开口为椭圆形，该燃烧室的形状为锥 型。燃烧室开口所占的弧度约30度，其所在弧形内壁的弧度为120度。燃烧室开口尺寸为短轴58mm(开口的短轴约为定子的高度的50～60％)长轴88mm，深度40mm。转子侧壁上的开孔11每组的孔面积为21.86cm 2，转子的弧形侧壁和定子三瓣形空腔的弧形内壁的间距d为3mm。
实施例2
本实施例为基于实施例1结构调控双转子发动机运行参数的方法以及实施例1双转子发动机的运行方法：
组装完成所述双转子发动机后，向双转子发动机注入润滑油至加满。润滑油在双转子发动机内自循环，以润滑转子。本运行实施例中，燃料为柴油，冷却剂为机油。本双转子发动机采用压燃点火，压缩比达到17以上，温度即可达600-700℃，运行时，转子转动使气和油以漩涡状充分混合，使燃料充分燃烧。
所述双转子发动机的燃料为柴油，发动机的排量为2.5，转速3000-5000。发动机压缩比为22.3。
实施例3
一种双转子发动机，包括定子和转子8，本双转子发动机包括2个串联的转子8，分别为第一转子和第二转子，2个转子均为“8”字形，2个转子的“8”字形的长轴的夹角为180度，
所述定子内部具有三段圆弧围成的三瓣形空腔，转子位于定子内部的三瓣形空腔中，“8”字的头部的弧与构成所述三瓣形空腔的圆弧相适配；所述双转子发动机有2个定子，分别为第一定子201和第二定子202。
转子的中心设置有主轴4，所述主轴包括多段，位于第一转子内的部分为第一段主轴401，位于第二转子内的部分为第二段主轴402，所述第一段主轴和第二段主轴以连接件14连接，所述连接件14为圆柱体形状，二个位于同一条直径上的孔，分别插入所述第一段主轴401和第二段主轴402。
所述三瓣形空腔具有弧形内壁，在三瓣形空腔的弧形内壁上开有3个对称分布的燃烧室9；所述燃烧室形状为锥形，锥形的尖部沿定子的径向方向朝外，与所述锥形尖部相对的位置处为喷油嘴的位置13。
本实施例双转子发动机的壳体由多部分组装而成，包括顺序连接的前 端盖1、第一外偏盖、第一定子201、第一内偏盖、中段壳体15、第二外偏盖、第二定子202、第二内偏盖和后端盖7。
在前端盖1和后端盖7上均设置有进气口5和冷却液道6；所述进气口5与冷却液道6的轴线的夹角为90度，在所述中段壳体15的侧壁上设置有排气孔12。在所述转子8的侧壁上开有两组孔，每组有2个。
本实施例的部分部件参数为：
转子的长宽是349.3mm和259.2，厚度是125mm，本转子发动机重量约500公斤。转子的压盖(包括内偏盖和外偏盖，厚度一样)的厚度为40mm。转子的轴承10的外径为130mm。第一段主轴和第二段主轴的轴心距离为40mm，第一段主轴和第二段主轴的轴心与连接件14中心的距离均为20mm。
燃烧室7在定子的弧形内壁上的开口为椭圆形，该燃烧室的形状为锥型，深度35mm。转子侧壁上的开孔11每组的孔面积为16cm 2，转子的弧形侧壁和定子三瓣形空腔的弧形内壁的间距d为1.5mm。
本实施例双转子发动机其他结构同实施例1。
实施例4
本实施例对实施例3转子发动机提供一种运行参数的调控方法，是基于实施例3的转子参数，以及该双转子发动机的运行方法：
组装完成所述转子发动机后，从润滑油孔注入润滑油，至加满。润滑油在转子发动机内自循环，以润滑转子。本运行实施例中，燃料为柴油；
所述转子发动机的燃料为柴油，发动机的排量为1.5，转速5000-7000。
实施例5
本实施例的部分部件参数为：
第一段主轴和第二段主轴的轴心距离为32mm，第一段主轴和第二段主轴的轴心与连接件14中心的距离均为16mm。
燃烧室7在定子的弧形内壁上的开口为椭圆形，该燃烧室的形状为锥型，深度35mm。转子侧壁上的开孔11每组的孔面积为22cm 2，转子的弧形侧壁和定子三瓣形空腔的弧形内壁的间距d为3mm。
本实施例双转子发动机其他结构同实施例1。
实施例6
本实施例为基于实施例5结构调控转子发动机运行参数的方法以及实施例5转子发动机的运行方法：
组装完成所述转子发动机后，从润滑油孔注入润滑油，至加满。润滑油在转子发动机内自循环，以润滑转子。本运行实施例中，燃料为柴油；
所述转子发动机的燃料为柴油，压缩比22.3。发动机的排量为0.7，转速7000-11000。
虽然，以上通过实施例对本发明进行了说明，但本领域技术人员应了解，在不偏离本发明精神和实质的前提下，对本发明所做的改进和变型，均应属于本发明的保护范围内。

Claims (10)

  1. 一种双转子发动机，包括定子和转子，其特征在于，所述双转子发动机包括2个串联的转子，分别为第一转子和第二转子，2个转子均为“8”字形，2个转子的“8”字形的长轴的夹角为180度；
    所述定子内部具有三段弧形侧壁围成的三瓣形空腔，转子位于定子内部的三瓣形空腔中，“8”字的头部的弧与构成所述三瓣形空腔的圆弧相适配；所述双转子发动机有2个定子，分别为第一定子和第二定子；
    在所述三瓣形空腔的每段弧形内壁上开有径向向外的燃烧室，一个定子上有3个对称分布的燃烧室。
  2. 根据权利要求1所述的双转子发动机，其特征在于，所述转子的中心设置有主轴，所述主轴包括多段，位于第一转子内的部分为第一段主轴，位于第二转子内的部分为第二段主轴，所述第一段主轴和第二段主轴的轴心不重合，两段主轴以连接件连接。
  3. 根据权利要求2所述的双转子发动机，其特征在于，所述连接件为圆柱体，连接件上开有圆心位于同一条直径上的二个孔，分别插入所述第一段主轴和第二段主轴；优选所述第一段主轴和第二段主轴的轴心距离为30～50mm。
  4. 根据权利要求1所述的双转子发动机，其特征在于，所述转子具有弧形侧壁，当“8”字形转子的头部位于三瓣形空腔中的一个空腔时，转子的弧形侧壁和该空腔的弧形内壁间距为1～3mm。
  5. 根据权利要求1所述的双转子发动机，其特征在于，所述燃烧室形状为锥形，锥形的尖部沿定子的径向方向朝外，与所述锥形尖部相对的位置处设置有喷油嘴。
  6. 根据权利要求1所述的双转子发动机，其特征在于，所述双转子发动机的壳体由多部分组装而成，包括顺序连接的前端盖、第一外偏盖、第一定子、第一内偏盖、中段壳体、第二外偏盖、第二定子、第二内偏盖和后端盖。
  7. 根据权利要求6所述的双转子发动机，其特征在于，所述前端盖和后端盖上均设置有进气口和冷却液道；所述进气口与冷却液道的轴线的 夹角为80～95度，和/或
    在所述中段壳体的侧壁上设置有排气孔。
  8. 根据权利要求1～7任一项所述的双转子发动机，其特征在于，在所述转子的侧壁上开有两组孔，每组有2个，每组开孔的孔面积为10～30cm 2。
  9. 一种双转子发动机运行参数的调控方法，其特征在于，包括:
    在所述转子侧壁上开有两组孔，通过调整转子侧壁开孔尺寸而调整发动机的排量，
    每组开孔的孔面积为10～12cm 2，发动机的排量为0.7～0.75升，
    每组开孔的孔面积为12～18cm 2，发动机的排量为1.3～1.7升，
    每组开孔的孔面积为18～30cm 2，发动机的排量为2.4～2.6升。
  10. 一种双转子发动机的运行方法，其特征在于，包括：
    组装完成所述双转子发动机后，向所述双转子发动机内注入润滑油；
    所述双转子发动机的燃料为油，所述油是煤油、汽油、柴油、甲醇中的一种；
    转子转动使气和油以漩涡状充分混合，使燃料充分燃烧。
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