WO2015010446A1 - 定轨转子泵及定轨转子泵组合增压内燃发动机 - Google Patents

定轨转子泵及定轨转子泵组合增压内燃发动机 Download PDF

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Publication number
WO2015010446A1
WO2015010446A1 PCT/CN2014/000700 CN2014000700W WO2015010446A1 WO 2015010446 A1 WO2015010446 A1 WO 2015010446A1 CN 2014000700 W CN2014000700 W CN 2014000700W WO 2015010446 A1 WO2015010446 A1 WO 2015010446A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
cylinder
cylindrical
piston
fixed
Prior art date
Application number
PCT/CN2014/000700
Other languages
English (en)
French (fr)
Inventor
张翼
Original Assignee
Zhang Yi
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201310314697.5A external-priority patent/CN103438000B/zh
Priority claimed from CN201310314677.8A external-priority patent/CN103470369B/zh
Application filed by Zhang Yi filed Critical Zhang Yi
Priority to JP2016528300A priority Critical patent/JP6563919B2/ja
Priority to DE112014003418.5T priority patent/DE112014003418B4/de
Priority to US14/906,884 priority patent/US10161299B2/en
Priority to CN201480040940.1A priority patent/CN105658962B/zh
Publication of WO2015010446A1 publication Critical patent/WO2015010446A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/40—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member
    • F01C1/44—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member with vanes hinged to the inner member
    • 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
    • F02B55/14—Shapes or constructions of combustion chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
    • F04C18/44—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid

Definitions

  • the present invention relates to a rotor pump, in particular a fixed rotor pump and an orbital rotor pump combined turbocharged internal combustion engine.
  • the current engine field mainly uses reciprocating motion piston engines, rotary engines and turbo engines.
  • reciprocating motion piston engines As the earliest reciprocating motion piston engine, although its performance has been greatly improved through continuous technical transformation and improvement, it is still difficult to meet the current high-speed motion conditions of machinery due to its own structure and movement mode. Claim.
  • the rotor engine came into being, and the representative one is the Wankel rotary engine.
  • the Wankel rotary engine Compared with the compound motion piston engine, the Wankel rotary engine has significant advantages such as simple structure and high efficiency.
  • the unique triangular rotor of the Wankel rotary engine also has obvious defects in practical applications.
  • the contact angle between the end angles of the triangular rotor and the inner wall of the cylinder is extremely narrow, and it is difficult to solve the combustion chamber by simply providing a single dicing device at each end angle.
  • the problem of poor sealing performance and high fuel consumption of the mixed gas makes it difficult to fully realize the efficiency, which is one of the main reasons why the rotor engine is difficult to replace the reciprocating piston engine.
  • the turbine engine has remarkable characteristics, it is mainly suitable for long-term constant-speed operation, such as an aero-engine, from the perspective of cost performance.
  • the rotary engine has obvious advantages in the field of automobile engines. If it can overcome the existing technical defects, its development prospect is broad.
  • the object of the present invention is to overcome the defects of the prior art engine, and to provide a fixed-track rotor pump and a fixed-rail rotor pump combined pressurized internal combustion engine composed of a plurality of fixed-orbit rotor pumps, which are compact in structure, small in size, and heavy in weight. Light, stable operation, good sealing performance, stable supercharging performance, high efficiency and remarkable energy saving effect.
  • a fixed-track rotor pump including a cylinder, a cylinder end cap on both sides of the cylinder and a rotor disposed in the cylinder, the rotor shaft penetrates the rotor, the cylinder end cap and the cylinder are fixed a connection between the rotor and the inner wall of the cylinder, wherein the inner side of the cylinder end cover of at least one side is fixed with a fixed orbit, the orbit and the cylinder
  • the rotor shaft is disposed through the cylinder end cover and the fixed rail.
  • the piston is provided along the outer circumferential surface of the rotor.
  • the piston is rotatably connected to the rotor through the piston shaft.
  • the piston shaft is fixed on the rotor, and the piston swings around the piston shaft.
  • the piston groove is disposed on the axial end of the cylindrical rotor, and the piston is disposed in the piston groove.
  • the piston includes a top arc surface, a bottom arc surface and a side arc surface, and the axis of the piston shaft is concentric with the rotor.
  • the line between the three corners of the piston constitutes an equilateral triangle
  • the tip angle of the piston is kept in contact with the inner wall of the cylinder
  • the bottom arc surface of the piston and the outer circumferential surface of the orbit are in an outwardly-cut state.
  • the piston moves around the orbit as a curve.
  • the rotor may be a cylindrical rotor, in which case the side surface of the cylindrical rotor is provided with an annular groove which extends into the annular groove of the end surface of the cylindrical rotor.
  • the cylinder is a cylindrical cylinder
  • the orbit is a cylindrical orbital
  • the rotor is fixed on the rotor shaft
  • the rotor is disposed concentrically with the rotor shaft
  • the cylindrical rotor is eccentrically placed in the cylindrical cylinder
  • the cylindrical rotor and The eccentricity between the cylindrical cylinders is the difference in radius between the cylindrical rotor and the cylindrical cylinder.
  • the rotor shaft is eccentrically penetrated through the cylinder end cap and the cylindrical orbital, and the axis of the piston shaft and the outer circumference of the annular groove The distance is less than 1/2 of the difference between the annular groove and the cylindrical rotor radius, and the piston moves in a circular motion around the cylindrical orbit.
  • the radius of the bottom arc surface and the side arc surface is the difference of the radius between the cylindrical cylinder and the cylindrical orbital, and the arc of the bottom arc surface and the side arc surface are both 60°, the top arc surface
  • the arc is equal to the arc of the inner wall of the cylindrical cylinder, and the top arc surface is inscribed with the piston shaft, and the bottom arc surface does not exceed the outer circumferential surface of the cylindrical rotor.
  • the cylindrical orbit can be a sleeve, the sleeve is cylindrical, and the inner surface and the outer surface are respectively provided with internal teeth and external teeth near the cylinder end cover, and corresponding external teeth are provided on the outer surface of the rotor shaft.
  • the inner teeth of the inner surface of the sleeve mesh with the outer teeth of the outer surface of the rotor shaft; the inner end of the cylindrical rotor is fixedly provided with an inner ring gear, and the inner teeth of the inner ring mesh mesh with the outer teeth of the sleeve, the sleeve
  • the smooth outer surface of the outer circumference is in a state of being tangent to the curved surface of the bottom of the piston.
  • the rotor shaft and the cylindrical orbit can be formed in a one-piece structure, the cylindrical orbit is eccentrically penetrated through the cylinder end cover and the rotor, and the cylinder end cover corresponding to the end surface of the cylindrical orbital is provided with a circular groove, the cylindrical shape
  • the rail and the cylindrical cylinder are concentric, the rotor 3 ⁇ 41 cylindrical rotor includes a rotor ring and a fixing ring fixed at both ends of the rotor ring, and the fixing ring extends into a circular groove on the cylinder end cover, and the inside of the ring is fixed
  • the surface is provided with inner ring teeth, correspondingly, the outer ring teeth are provided on the outer surface of the pillar-shaped fixed rail, and the inner ring teeth are combined with the outer ring tooth phase P3 ⁇ 4. '
  • the outer peripheral surface of the bottom surface of the piston and the cylindrical orbital is 3 ⁇ 4 wide: ⁇ to set the piston support member, each piston corresponds to a support member, and the support member moves in a circular motion along the cylindrical orbit with the piston synchronously, 'piston bearing
  • the supporting member comprises an upper curved surface and a lower curved surface, wherein the upper curved surface is equal to the arc of the bottom curved surface of the piston, the lower curved surface is equal to the arc of the outer peripheral surface of the cylindrical orbital, and the upper and lower curved surfaces of the piston supporting member are arranged.
  • the length is not greater than the length of the bottom surface of the piston.
  • the cylinder may also be an elliptical cylinder.
  • the orbit is an elliptical orbital
  • the cylindrical rotor is concentric with the elliptical cylinder.
  • the rotor shaft concentrically penetrates the elliptical orbit and the cylinder end cap, so the cylindrical rotor, The rotor shaft, the elliptical orbital and the elliptical cylinder are concentrically arranged.
  • the distance between the outer surface of the elliptical orbital and the inner surface of the elliptical cylinder is equivalent, and the piston moves in an elliptical curve around the orbital elliptical orbit.
  • the radius of the bottom arc surface and the side arc surface is the distance between the inner surface of the elliptical cylinder and the outer surface of the elliptical orbital, and the arc of the bottom arc surface and the side arc surface are both 60°.
  • the arc of the top arc surface is smaller than the minimum arc value of the curve of the inner wall of the elliptical cylinder, and the top arc surface is inscribed with the piston shaft, and the bottom arc surface does not exceed the outer circumferential surface of the cylindrical rotor.
  • the left and right symmetrical volume chambers are formed by the tangent point of the cylindrical rotor and the inner wall of the elliptical cylinder, and the inlet and the outlet are respectively arranged in the two volume chambers, and the two volume chambers simultaneously inlet and exhaust.
  • a corner where the top arc surface contacts the inner wall of the cylindrical cylinder is a tip angle.
  • a sealing device may be arranged at the top corner of the piston, the sealing device comprises a semi-cylindrical main seal and a fan-shaped card plate, one side of the semi-cylindrical main seal is in contact with the inner wall of the cylinder, and the contact surface and the cylinder of the semi-cylindrical main seal and the inner wall of the cylinder
  • the inner wall of the shaped cylinder has the same arc, and the center of the semi-cylindrical main seal is disposed on the contact line between the tip end angle of the piston and the inner wall of the cylindrical cylinder, and at least one sealing groove is provided on the contact surface of the semi-cylindrical main seal and the inner wall of the cylinder.
  • a sealing strip is arranged in the sealing groove, and two ends of the semi-cylindrical main sealing strip are respectively mounted with a fan-shaped card board, the fan-shaped card board is concentric with the semi-cylindrical main sealing strip, one end of the fan-shaped card board is fixedly connected with the semi-cylindrical main sealing strip, and The inner side of one end is provided with a circular arc rib, and correspondingly, a circular arc groove is arranged on the sector piston, and the circular arc rib is disposed in the circular arc groove.
  • the sector piston can adopt a cavity shape to reduce the weight of the piston, and the bottom arc surface of the piston is provided with a cavity.
  • Each cylinder end cover is provided with a rotor cooling port and an orbital and piston groove communication, and the circulating oil is used to cool the running parts.
  • the present invention also includes an orbital rotor pump combined supercharged internal combustion engine that is formed by a combination of at least two fixed rail rotor pumps disposed on the same rotor shaft.
  • the fixed-rail rotor pump combined turbocharged internal combustion engine consists of a fixed-orbit rotor pump used as a compressor and a fixed-orbit rotor pump used as an internal combustion engine, or an orbiting rotor used as a compressor
  • the pump consists of a fixed connection of two fixed-track rotor pumps used as internal combustion engines, or an fixed-orbiting rotor pump used as an internal combustion engine and two fixed-ropod rotor pumps used as compressors.
  • the cylinder end caps of the adjacent two fixed-track rotor pumps are in an integrated structure to form a common cylinder end cap. Two adjacent cylinder end caps can be fixedly connected together.
  • At least one cylindrical jet micro-hole is provided on the cylinder end cover shared by the adjacent two fixed-track rotor pumps, and the jet micro-L is an outlet of the orbital rotor pump used as a compressor, and the same day is used as an internal combustion engine
  • the inlet of the orbital rotor pump used which is provided with a fuel nozzle and at least one spark plug on the cylinder of the fixed-track rotor pump used as the internal combustion engine.
  • the axial length of the cylindrical fixed-track rotor pump used as the compressor is greater than
  • the cylinder volume of the cylindrical fixed-track rotor pump used by the compressor is larger than the cylinder volume of the cylindrical fixed-track rotor pump used as the internal combustion engine.
  • the cylinder diameter line passing through the inner wall of the cylindrical cylinder and the tangent point of the cylindrical rotor is set, and the cylinders of the adjacent two cylindrical fixed-track rotor pumps are radially set at an off angle of not more than 60°.
  • a combustion chamber is provided on the cylindrical rotor between adjacent sector pistons used as an internal combustion engine.
  • Cylindrical orbital use as an internal combustion engine when a cylindrical orbital rotor pump combined supercharged internal combustion engine includes two cylindrical fixed orbiting rotor pumps used as compressors for the same cylinder capacity and a cylindrical orbit fixed rotor pump used as an internal combustion engine
  • the rotor pump is located between two cylindrical orbital rotor pumps used as compressors, and the cylinder volume in the middle is smaller than the sum of the cylinder volumes on both sides;
  • the cylindrical orbital rotor pump combined supercharged internal combustion engine includes two cylindrical fixed-orbit rotary rotor pumps used as internal combustion engines and a cylindrical fixed-orbit rotary rotor pump used as a compressor, the column used as a compressor
  • the orbital rotor pump is located between two cylindrical orbital rotor pumps used as internal combustion engines, and the cylinder volume in the middle is greater than the sum of the cylinder volumes on both sides.
  • the orbital rotor pump designed in the present invention realizes the positioning of the same center of the fixed rail and the inner wall of the cylinder, so that the sector piston can perform circular motion in a circular orbit formed between the fixed rail and the inner wall of the cylinder, thereby overcoming
  • the existing type of rotor engine sector piston only relies on the limitation of the spring or spring piece device limit, ensuring that the fan-shaped piston is smooth and smooth under high-speed running conditions, and there is no offset phenomenon, which can fully exert the effect of the piston;
  • ⁇ 1 is a radial cross-sectional view of the cylindrical orbital rotor pump of Embodiment 1;
  • Figure 2 is an axial cross-sectional view of the cylindrical orbital fixed-rotor pump of Figure 1;
  • Figure 3 is a radial cross-sectional view of the combined cylindrical superficial rotor pump combined supercharged engine of the present invention;
  • Figure 4 is an axial cross-sectional view of the cylindrical fixed-track rotor pump combined supercharged engine shown in Figure 3;
  • Figure 5 is a transverse cross-sectional view of the sealing device of the present invention.
  • Figure 6 is an axial cross-sectional view of the sealing device of the present invention.
  • Figure 7 is a radial cross-sectional view of the elliptical orbital fixed-rotor pump of Embodiment 4.
  • Figure 8 is a radial cross-sectional view of the cylindrical orbital fixed-rotor pump of Embodiment 5;
  • Figure 9 is an axial cross-sectional view of the cylindrical fixed-track rotor pump of Figure 8.
  • Figure 10 is a radial cross-sectional view of the cylindrical orbital fixed-rotor pump of Embodiment 6;
  • Figure 11 is an axial cross-sectional view of the cylindrical orbital rotor pump of Figure 10;
  • Figure 12 is a radial cross-sectional view of the cylindrical orbital rotor pump of Embodiment 7;
  • Figure 13 is a perspective view of the piston support member.
  • the cylindrical fixed-track rotor pump comprises the cylindrical cylinder 1 and the cylinder end cover 2.
  • the cylinder end cover 2 is located on both sides of the cylinder bore, and the cylinder end cover 2 is fixedly connected with the cylinder 1.
  • the cylindrical cylinder 1 and the cylinder end cover 2 may be separate components, or the cylinder end caps and cylinders on one side may be separate components, and the cylinder end caps on the other side may be integrally formed with the cylinders.
  • the cylindrical rotor 3 is eccentrically placed in the cylindrical cylinder 1, and the eccentricity between the cylindrical rotor 3 and the cylindrical cylinder 1 is the difference in radius between the cylindrical rotor 3 and the cylindrical cylinder 1, thereby making the cylindrical rotor 3 maintains an inwardly cut state with the inner wall of the cylindrical cylinder 1.
  • Both ends of the cylinder-shaped rotor 3 are provided with an annular groove 9 , and a cylindrical fixed rail 8 is provided on the inner side of the cylinder end cover 2 , and a cylindrical fixed rail 8 can be disposed on the cylinder end cover on one side. It is also possible to set the poison at the cylinder end on both sides at the same time.
  • the cylindrical fixed rail 8 is disposed concentrically with the cylindrical cylinder 1, and the circular fixed rail 8 and the cylinder end cover 2 may have a unitary structure.
  • the cylindrical rotor 3 is circumferentially sleeved on the rotor shaft 4, and the rotor shaft 4 is eccentrically inserted through the cylindrical fixed rail 8 and the cylindrical cylinder 1, And connected to other transmissions, the cylindrical rotor 3 is concentric with the rotor shaft 4.
  • the diameter of the cylindrical fixed rail 8 is larger than the diameter of the rotor shaft 4, which is smaller than the diameter of the cylindrical rotor 3.
  • the length of the cylindrical fixed rail 8 is not more than two-thirds of the length of the cylindrical rotor 3. .
  • the cylindrical fixed rail 8 extends into the annular groove 9 of the end surface of the cylindrical rotor 3, the depth of the annular groove 9 corresponds to the length of the cylindrical fixed rail 8, and the diameter of the annular groove is larger than the cylindrical orbital The diameter of 8 is smaller than the diameter of the cylindrical rotor 3.
  • At least one piston 6 is provided along the outer circumferential surface of the cylindrical rotor 3.
  • the pistons 6 may be evenly distributed along the outer circumferential surface of the cylindrical rotor, or may be symmetrically distributed.
  • the piston 6 is rotatably coupled to the cylindrical rotor 3 via a piston shaft 7, and the piston shaft 7 is fixed to the cylindrical rotor 3, and the piston 6 is circumferentially oscillated about the piston shaft 7.
  • a piston groove 5 is formed in the cylindrical rotor 3 in accordance with the number of the sector pistons.
  • the piston groove 5 penetrates the axial ends of the cylindrical rotor 3, and the piston 6 is disposed in the piston groove 5.
  • the shape and size of the piston groove 5 is completely matched with the piston 6, and the piston 6 is in contact with the cylindrical fixed rail 8 through the piston groove 5.
  • the piston 6 includes a top curved surface 12, a bottom curved surface 10 and a side curved surface 11.
  • the tip end angle of the piston 6 is always in contact with the inner wall of the cylinder, and the line between the three corners of the piston 6 constitutes an equilateral triangle.
  • the piston 6 and the piston shaft 7 can be in a unitary structure.
  • the piston 6 is a triangular piston with a piston shaft.
  • the piston groove 5 is provided with a semicircular groove, and the piston shaft is disposed in the semicircular groove. Rotate inside the semicircular groove.
  • the piston 6 and the piston shaft 7 can also be two separate components, in which case the piston shaft 7 and the cylindrical rotor 3 are of unitary construction, and the piston at this time is a sector piston.
  • the arcuate surface 10 of the sector piston and the arc of the side arc surface 11 are both 60°, and the radius of the bottom and side arc surfaces is the difference in radius between the cylindrical cylinder 1 and the cylindrical orbital 8.
  • the arc surface from the end point of the center of the piston shaft to the tip end of the cylinder is the top arc surface 12, and the arc of the top arc surface 12 is equal to the arc of the cylindrical cylinder 1, which serves to minimize the cylinder tolerance.
  • the gap, the top arc surface 12 and the piston shaft 7 are inscribed.
  • the axis of the piston shaft 7 is located on a circumferential line of the same radius concentric with the cylindrical rotor 3.
  • the distance between the axis of the piston shaft 7 and the outer circumference of the annular groove 9 is smaller than the difference between the annular groove and the cylindrical rotor radius. 1/2 to ensure that the bottom curved surface 10 of the sector piston 6 and the outer circumferential surface of the cylindrical fixed rail 8 are always kept out of phase during operation.
  • the maximum extent of the bottom arc 10 operation is limited to no more than the outer circumference of the cylindrical rotor 3.
  • Each of the sector pistons moves in a circular motion around the cylindrical orbital rail 8.
  • the cylindrical rotor 3 With the cylindrical rotor 3 and the inner wall of the cylindrical cylinder 1 as the boundary, when the cylindrical rotor 3 is operated in the clockwise direction, at least two inlets are provided on the left cylinder wall, and an outlet 14 is provided in the right cylinder wall.
  • the cylindrical rotor 3 is operated counterclockwise. At the time of rotation, at least two inlets are provided on the right cylinder wall, and an outlet 14 is provided on the left cylinder wall.
  • the purpose of setting multiple inlets is to reduce the negative pressure created by the cavity between adjacent pistons during suction.
  • the number of outlets 14 is determined by the number of sector pistons.
  • the cylindrical rotor 3 operates clockwise or counterclockwise, preferably in the direction of rotation of the cylindrical rotor, preferably behind the piston shaft 7.
  • the radial end faces of the sector piston are provided with a sealing groove and a sealing strip, and the inner wall of the two ends of the cylinder corresponds to the position of the cylindrical rotor.
  • the rotor ring 25 having the same radius and a certain thickness can be added to both ends of the cylindrical rotor without affecting the overall performance of the cylinder.
  • Each cylinder end cover is provided with a rotor cooling port 18 and a piston groove communicating, and the circulating oil is used to cool the running member.
  • the cylindrical orbital rotor pump is only used as a general pump and compressor under normal conditions, only a conventional sealing means is adopted, and a narrow sealing groove is provided at the top end of the sector piston, and the sealing groove of the sealing groove can realize the sealing of the sector piston. Or do not make any additional sealing measures on the top end of the fan piston, which makes the sector piston structure relatively simple, thus reducing the manufacturing cost.
  • the cylindrical orbital rotor has high requirements for sealing and lubricating the internal components of the cylinder under high temperature, high pressure and high speed operation conditions.
  • a sealing device as shown in FIG. 5 is used, and the sealing device 19 is disposed at the top corner of the piston. That is, the top arc surface of the piston slides along the inner wall of the cylinder.
  • the sealing device comprises a semi-cylindrical main seal 20 and a sector-shaped card 21, one side of which is in contact with the inner wall of the cylinder, so that the face of the semi-cylindrical main seal 20 completely coincides with the curvature of the inner wall of the cylindrical cylinder.
  • the center of the semi-cylindrical main seal 20 is disposed at a contact line between the tip end angle of the piston and the inner wall of the cylindrical cylinder, and the tip end angle of the piston is the contact angle between the top surface of the piston and the inner wall of the cylindrical cylinder.
  • the contact surface of the sealing device 19 and the inner wall of the cylinder is enlarged, and a plurality of sealing grooves 23 are formed on the contact surface of the semi-cylindrical main strip 20 and the inner wall of the cylinder, and the sealing groove 23 is respectively provided with a seal. Strips to improve the sealing effect.
  • the two ends of the semi-cylindrical main seal 20 are respectively mounted with a fan-shaped card 21, which is concentric with the semi-cylindrical main seal, one end of the fan-shaped card 21 is fixedly connected with the semi-cylindrical main seal 20, and the inner end of the other end is closed.
  • the arcuate rib 22 is provided, correspondingly, a circular arc groove is arranged on the sector piston, and the circular arc rib 22 is disposed in the circular arc groove.
  • the sealing device 19 does not detach.
  • the sealing device and the piston are always kept in a smooth If state, thereby preventing the sealing device 19 from coming off during the operation of the piston.
  • the force applied to the top arc surface 12 of the piston 6 is centripetal force, so the frictional force between the top end of the piston 6 and the inner wall of the cylinder is small.
  • a single cylindrical orbital rotor pump can be used as a rotor pump or compressor.
  • the sector piston rotates. Since the bottom arc surface of the sector piston is always tangent to the cylindrical orbital 8, the fan-shaped piston always rotates around the cylindrical orbital 8.
  • the material enters between the sector pistons from the inlet 13.
  • the material between the pistons is compressed, and the compressed material is discharged through the outlet 14.
  • a cylindrical orbital rotor pump combined supercharged internal combustion engine is constructed by connecting two cylindrical orbital rotary rotor pumps mounted on the same rotor shaft in series. After the two cylindrical fixed-track rotor pumps are connected in series on the rotor shaft on Monday, the adjacent cylinder end caps 2 overlap each other. To ensure the compactness and firmness of the structure, the two adjacent cylinder end caps 2 can be an integral structure.
  • One of the cylindrical fixed-track rotor pumps functions as an air 'compressor, and the other cylindrical fixed-track rotor pump acts as an internal combustion engine. At this time, the outlet of the cylindrical orbital rotor pump used as the compression is disposed on the cylinder end cover 2 shared by the two rotor pumps.
  • the diameter of the diameter of the cylinder is generally 0. l-10mm.
  • the inlet of the cylindrical orbital rotor pump used as an internal combustion engine is a jet micro-hole 15, and the purpose of using the jet micro-electron is to utilize the jet action of the airflow to force the mixed gas to disturb and improve the combustion efficiency.
  • a fuel nozzle 16 and at least one spark plug 17 are mounted on the cylinder 1 of the cylindrical orbital rotary rotor pump used as an internal combustion engine near the gas injection port. If the fuel is diesel, there is no need for a spark plug and direct compression ignition.
  • the injector is installed near the inlet of the rotor pump, and the inlet is opposite to increase the fuel atomization effect.
  • a spark plug is placed near the inscribed position of the cylindrical rotor and the inner wall of the cylinder.
  • the cylindrical rotor between the adjacent sector pistons used as the internal combustion engine is provided with a combustion chamber which enables the compressed gas to escape the restriction of the closed region of the cylindrical rotor and the inner wall of the cylinder, and smoothly transitions to the expansion work area.
  • the axial length of the cylindrical orbital rotor pump used as the compressor can be appropriately increased, the purpose of which is to enlarge the internal volume of the cylinder, and the axial length of the cylindrical fixed-track rotor pump used as the compressor is greater than that used as the internal combustion engine.
  • the increase effect can be achieved, and the larger the cylinder volume difference between the two, the larger the boost value, and the stable supercharging performance can be maintained under any speed condition.
  • the adjacent two cylinders should be set with a certain declination in the radial direction, and the declination angle is not more than 60° to ensure the cylindrical orbital rotor pump combination.
  • the supercharged internal combustion engine can fully perform its functions.
  • the same rotor shaft penetrates the adjacent two cylinders, so that the cylindrical rotors of the two adjacent cylinders do not have a radial offset, so the radial position of the sector pistons on the adjacent two cylindrical rotors still overlap and synchronize.
  • the compressed gas in the internal combustion engine can be prevented from flowing back into the compressor.
  • the piston of the rotor pump as the compressor and the piston in the corresponding combustion work rotor pump always maintain the front and rear positions. It is beneficial to the internal combustion engine to complete the process of intake, further compression, combustion and expansion. A seal is required at the top corner of the piston.
  • the cylindrical fixed-track rotor pump used as the compressor first compresses the air, and the compressed air enters the cylindrical fixed-orbit rotor pump used as the internal combustion engine through the air outlet 15, wherein the cylindrical fixed-rotor rotor
  • the piston in the pump performs the processes of intake, compression, combustion and expansion work in turn under the action of the rotation of the cylindrical rotor.
  • the combination of the cylindrical orbital fixed-rotor pump and the supercharged internal combustion engine is not limited to the combination in the second embodiment, and the following combinations may be employed:
  • Column-column fixed-rail rotor pump combined supercharged internal combustion engine consists of two cylindrical fixed-orbit rotor pumps used as compressors for the same cylinder capacity and a cylindrical fixed-track rotor pump used as an internal combustion engine as a cylinder for internal combustion engines
  • the orbital rotor pump is located at the position of two cylindrical fixed-orbiting rotor pumps used as compressors, and the cylinder volume in the middle is small and the sum of the cylinder volumes on both sides
  • Cylindrical orbital rotor pump combined supercharged internal combustion engine consists of two cylindrical fixed-orbit rotor pumps used as internal combustion engines with the same cylinder capacity and a cylindrical orbit fixed-rotor pump used as a compressor.
  • the rail rotor pump is located between two cylindrical orbital rotor pumps used as internal combustion engines, and the cylinder volume in the middle is greater than the sum of the cylinder volumes on both sides.
  • the above two combinations of internal combustion engines share a cylinder end cap.
  • the common cylinder end cap not only involves the deflection angle problem between adjacent cylinders, but also the difficulty of machining the cylinder components, as well as the robustness and convenience of installation. . Therefore, according to the actual production situation, the common cylinder end cover can adopt the following three structural modes: (1) The two end caps of the intermediate cylinder and the adjacent cylinder end caps are separated; (2) Middle One end cap of the cylinder and the adjacent cylinder end cap are shared with each other, and the other end cap and the adjacent cylinder end cap are separated; (3) both end caps of the intermediate cylinder and the cylinder adjacent thereto The end caps are shared with each other. No matter which type of installation does not affect the installation and removal of the rotor shaft.
  • a recombination method of a cylindrical orbital rotor pump combined with a supercharged internal combustion engine may be employed, that is, a plurality of cylindrical orbit fixed rotor pump combined supercharged internal combustion engines are provided on the same rotor shaft.
  • the elliptical orbital rotor pump is different from the first embodiment in that the cylinder in this embodiment is an elliptical cylinder 1', the cylinder end cover 2 is located on both sides of the cylinder bore, the cylinder end cap 2 and the cylinder. ⁇ Fixed connection.
  • the cylindrical rotor 3 is disposed in an elliptical cylinder ,, the cylindrical rotor 3 is disposed concentrically with the elliptical cylinder, and the cylindrical rotor 3 is inscribed with the apex of the short axis of the arc of the inner wall of the elliptical cylinder ,, thereby forming Two symmetrical, relatively closed volume chambers.
  • Both sides of the cylindrical rotor 3 are provided with an annular groove 9, and the inner side of the cylinder end cover 2 is provided with a convex elliptical fixed rail 8', and the elliptical orbital .8' is concentric with the cylinder end cover 2.
  • the rotor shaft 4 runs concentrically through the elliptical orbital 8' and the cylinder end cap 2 and is connected to other transmissions.
  • the elliptical orbital 8' extends into the annular groove 9 of the end face of the cylindrical rotor 3, the depth of the annular groove 9 corresponds to the length of the elliptical orbital 8', and the diameter of the annular groove is larger than the elliptical shape
  • the minor axis length of the rail 8' is smaller than the diameter of the cylindrical rotor 3.
  • the arrangement of the piston 6 and the piston groove 5 is exactly the same as that of the piston 6 and the piston groove 5 in the first embodiment.
  • the curvature of the bottom arc surface 10 and the side arc surface 11 of the sector piston is 60°
  • the radius of the bottom arc surface and the side arc surface is the inner surface of the cylindrical cylinder 1 and the cylindrical shape.
  • the distance between the outer surfaces of the rails 8. From turning as a piston The arc angle of the end point of the center of the shaft to the top end of the cylinder is the top arc surface 12, the arc of the top arc surface 12 is smaller than the minimum arc value of the curve of the inner wall of the elliptical cylinder, the bottom arc surface 10 and the elliptical orbit determination
  • the outer circumference of 8 ' is always in contact.
  • the axis of the piston shaft 7 is located on a circumferential line of the servo-radius concentric with the elliptical orbital 8'.
  • the cylindrical rotor 3 drives the sector piston to move in an elliptical annular space between the elliptical orbital 8' and the elliptical cylinder bore while performing a circular motion.
  • the maximum extent of operation of the bottom cam surface 10 is limited to no more than the outer circumference of the cylindrical rotor 3.
  • the left and right symmetrical volume chambers are formed by the tangent point of the cylindrical rotor 3 and the inner wall of the elliptical cylinder ,, and the inlet and the outlet are respectively arranged in the two volume chambers, and the two volume chambers simultaneously inlet and exhaust.
  • the above elliptical orbit fixed-rotor pump is provided with a single inlet and an outlet. After installing the ignition device and the fuel injection device in the rotor pump, it can be directly transformed into an internal combustion engine.
  • the cylindrical rotor can be rotated for one week to complete the intake, compression, combustion and exhaust. There is no need to separately set the intake and exhaust valves, and the structure is simple.
  • the shape of the orbit determination and the cylinder is not limited to the elliptical shape described in the embodiment, and may be an approximately elliptical shape composed of a pair of different radii of different radii connected by a smooth curve. As long as it can be ensured that the shape of the orbital and the cylinder is the same and the distance between the two is constant.
  • the combination mode and work principle of the elliptical orbit fixed rotor pump combination internal combustion engine are the same as those of the cylindrical fixed rail rotary pump combined with the supercharged internal combustion engine of the embodiment 2 and the third embodiment, and therefore will not be described again.
  • FIG. 8 and FIG. 9 is a cylindrical orbital rotor pump according to Embodiment 5, which is different from Embodiment 1 in that: the rotor shaft and the cylindrical orbital structure in this embodiment are in an integrated structure, and are cylindrically fixed. A circular groove is formed in the cylinder end cover 2 corresponding to the end surface of the rail 8.
  • the cylindrical orbital 8 and the cylindrical cylinder 1 are concentric.
  • the rotor 3' has a cylindrical shape, and the cylindrical rotor 3' is eccentrically inserted through the cylindrical cylinder.
  • the cylindrical rotor 3' includes a rotor ring 301 and a fixing ring 302 fixed to both ends of the rotor ring 301.
  • the fixing ring 302 extends into the cylinder.
  • the circular groove of the end cap _h serves to strengthen the seal and control the rotation of the rotor ring.
  • the inner surface of the circumference ring 302 is provided with inner ring teeth 27.
  • an outer ring tooth 28 is provided on the outer surface of the cylindrical fixed rail 8, and the inner ring teeth 27 are engaged with the outer ring teeth 28.
  • the rotor ring 301 drives the cylindrical orbital 8 to operate by the engagement between the inner ring teeth and the outer ring teeth, the rotor ring 301 is rotated one revolution, and the cylindrical orbital rotation 8 is rotated more than one revolution.
  • the cylindrical rotor 3' is eccentrically mounted in the cylindrical cylinder 1 and is inscribed with the inner wall of the cylinder.
  • the cylindrical rotor 3' is provided with a piston groove, and the sector piston is disposed in the piston groove.
  • the tip end angle of the sector piston is always maintained with the inner wall of the cylinder.
  • the bottom arc surface of the sector piston is always in contact with the cylindrical fixed rail 8, and each sector piston moves circumferentially around the cylindrical orbital 8.
  • FIG. 10 and FIG. 11 is a cylindrical orbital rotor pump according to Embodiment 6, which is different from Embodiment 1 in that: the cylindrical orbital adopts a sleeve type structure, that is, a cylindrical orbital is a sleeve. 801, the sleeve 801 has a cylindrical shape, and the inner surface and the outer surface are respectively provided with internal teeth and external teeth near the cylinder end cover, and correspondingly, the outer surface of the rotor shaft 4 is provided with external teeth, and the inner surface of the sleeve 801 is inside. The teeth mesh with the outer teeth of the outer surface of the rotor shaft 4.
  • the cylindrical rotor 3 is fixedly provided with an inner ring on the side surface of the side or both sides, and the inner teeth of the inner ring gear mesh with the outer teeth of the sleeve 801.
  • the smooth surface of the outer circumference of the sleeve 801 remains in contact with the bottom surface of the sector piston.
  • the cylindrical rotor 3 drives the cylindrical orbital 8 to rotate by the internal ring gear, and the cylindrical fixed rail 8 drives the rotation of the rotor shaft 4 by the engagement of its internal teeth with the external teeth of the rotor shaft 4, and finally the rotational speed of the rotor shaft 4 is doubled.
  • the combination mode and work principle of the cylindrical orbital-spindle-rotor combined internal combustion engine of the present embodiment are the same as those of the cylindrical fixed-track rotor pump combined with the supercharged internal combustion engine of the second embodiment and the third embodiment, and therefore will not be described again.
  • FIG. 12 and FIG. 13 is a cylindrical orbital rotor pump according to Embodiment 7, which is different from Embodiment 1 in that: a piston bearing member 29 is disposed on a street surface of a piston bottom curved surface and a cylindrical outer rail 8 outer peripheral surface, Each piston corresponds to a support member. The support member moves in a circular motion along the cylindrical orbit with the piston.
  • the piston supporting member 29 includes upper and lower circular arc surfaces, wherein the upper curved surface coincides with the bottom curved surface of the piston, and the arc is equal; the lower curved surface coincides with the outer circumferential surface of the cylindrical orbital, and the arc is equal.
  • the minimum distance between the upper arc surface and the lower arc surface shall be the difference between the original radius dimension of the cylindrical orbit and the rear radius dimension of the support member when the support is not provided.
  • the length of the upper and lower arc faces of the piston receiving member 29 should not be greater than the length of the bottom surface of the fan piston.
  • the bottom surface of the fan-shaped piston in Embodiment 1 can always maintain contact with the outer circumferential surface of the cylindrical orbital rail, there are still two shortcomings: First, the contact surface between the piston and the cylindrical orbital is narrow, and the long-term high-load operation condition will be Excessive wear and tear, resulting in reduced sealing performance. Second, the design position of the fan-shaped piston pivot point has a certain limitation. When the outer peripheral surface of the rotor is too biased, the bottom surface of the piston will be separated from the cylindrical orbital at a local corner position, which will also result in loss of sealing effect. The above problem can be completely solved by the piston holder 29 provided in this embodiment. .
  • the combination mode and work principle of the cylindrical orbital-spindle-rotor combined internal combustion engine of the present embodiment are the same as those of the cylindrical fixed-track rotor pump combined with the supercharged internal combustion engine of the second embodiment and the third embodiment, and therefore will not be described again.

Abstract

一种定轨转子泵及定轨转子泵组合增压内燃发动机。定轨转子泵内，转子轴（4）贯穿转子（3），转子（3）与气缸（1）内壁之间为相内切的状态，至少一侧的气缸端盖（2）的内侧固定有凸起的定轨（8）,定轨（8）与气缸（1）呈同心设置，转子（3）贯穿气缸端盖（2）和定轨（8），沿转子（3）的外圆周面设有活塞（6），活塞（6）通过活塞转轴（7）与转子（3）转动连接，转子（3）上设有活塞槽（5），活塞（5）设置于活塞槽（5）内，活塞（6）包括顶弧面（12）、底弧面（10）和侧弧面（11），活塞（6）的三个角之间的连线构成等边三角形，活塞（6）的顶端角与气缸（1）内壁保持接触，活塞（6）的底弧面（10）和定轨（8）外圆周面为相外切的状态，活塞（6）围绕定轨（8）作曲线运动。

Description

定轨转子泵及定轨转子泵组合增压内燃发动机
技术领域
本发明涉及转子泵， 尤其是定 转子泵及定轨转子泵组合增压内燃发动机。
背景技术
当前发动机领域主要采用往复式运动活塞发动机、 转子发动机和涡轮式发动机。 其中， 作为最早出现的往复式运动活塞发动机， 尽管经过不断地技术改造和完善， 其性能得到极大 的提高， 但是由于受自身结构和运动方式的制约， 仍然难以满足目前机械高转速运动条件的 要求。 针对上述问题， 转子发动机才应运而生， 其中具有代表性是汪克尔转子发动机。 与往 复式运动活塞发动机相比， 汪克尔转子发动机具有结构简单、 效率高等显著优点。 但是汪克 尔转子发动机的特有三角形转子在实际应用中也存在明显的缺陷， 三角转子各端角与气缸内 壁的接触面极其狭小， 仅仅依靠各端角处设置单一划片装置难以解决燃烧室里混燃气体密封 性差、 油耗大的问题， 从而使其效率难以充分发挥， 这也是该转子发动机难以取代往复式活 塞发动机的主要原因之一。 涡轮发动机虽然具有显著的特性， 但是从性价比考虑， 主要还是 适合长时间匀速运转条件下使用， 如航空发动机。 综上所述， 转子发动机在汽车发动机领域 具有明显的优势， 如能克服现有的技术缺陷， 其开发前景广阔。
另外， 随着环保和节能理念的强化， 各国限制发动机减排标准越来越高， 洽理措施越来 越严格。 作为提高发动机功效和有效节能手段之一的增压技术被普遍使用， 而增压离不开压 缩机， 现在普遍采用涡轮增压技术， 虽然是利用排放废气实现节能效果， 但是涡轮增压方式 的主要缺陷还在于低速运转条件下， 增压效果不明显。 其他类形的机械增压器也存在不同程 度消耗发动机动能的缺点。 因此需要一种能适应不同转速条件下保持稳定增压并且降低发动 机动能耗的增压技术设备， 以实现转子发动机的高效节能效果。
发明内容
本发明的目的在于克服现有发动机存在的缺陷， 提出了一种定轨转子泵及由多个定轨转 子泵组合而成的定轨转子泵组合增压内燃发动机， 结构紧凑， 体积小， 重量轻, 运转平稳， 密封性能好，.增压性能稳定， 功效高， 节能效果显著。
本¾:明是采用以下的技术方案实现的： 一种定轨转子泵， 包括气缸、 位于气缸两侧的气 缸端盖和设置在气缸内的转子， 转子轴贯穿转子， 气缸端盖和气缸固定连接， 其中， 转子与 气缸内壁之间为相内切的状态， 至少一侧的气缸端盖的内侧固定有凸起的定轨， 定轨与气缸 呈伺心设置， 转子轴贯穿气缸端盖和定轨， 沿转子的外圆周面设有活塞， 活塞通过活塞转轴 与转子转动连接， 活塞转轴固定在转子上， 活塞绕活塞转轴做圆周摆动， 转子上设有活塞槽， 活塞槽贯通于圆柱形转子的轴向两端， 活塞设置于活塞槽内， 活塞包括顶弧面、 底弧面和侧 弧面， 活塞转轴的轴心位于与转子同心的同一半径的圆周线上， 活塞的三个角之间的连线构 成等边三角形， 活塞的顶端角与气缸内壁保持接触， 活塞的底弧面和定轨外圆周面为相外切 的状态， 活塞围绕定轨作曲线运动。
本发明中， 所述转子可以为掘柱形转子， 此时圆柱形转子的侧面设有环状凹槽， 定轨伸 入圆柱形转子端面的环状凹槽内。
所述气缸为圆筒形气缸， 定轨为圆柱形定轨， 转子固定套在转子轴上， 转子与转子轴同 心设置， 所述圆柱形转子偏心置于圆筒形气缸内， 圆柱形转子与圆筒形气缸之间的偏心值为 圆柱形转子和圆筒形气缸的半径差值， 转子轴偏心贯穿气缸端盖和圆柱形定轨， 活塞转轴的 轴心与环状凹槽外周线之间的距离小于环形凹槽和圆柱形转子半径差的 1/2， 活塞围绕圆柱 形定轨作圆周运动。 所述活塞为扇形活塞时， 其底弧面和侧弧面的半径为圆筒形气缸和圆柱 形定轨的半径差值， 底弧面和侧弧面的弧度均为 60° , 顶弧面的弧度等于圆柱形气缸内壁的 弧度， 顶弧面与活塞转轴相内切， 底弧面运转的幅度不超过圆柱形转子的外圆周面。 以圆柱 形转子和圆筒形气缸内壁的内切切点为界， 圆柱形转子顺时针方向运转时， 左侧气缸壁上至 少设置两个进口， 右侧气缸壁设置一个出口； 圆柱形转子逆时针方向运转时， 右侧气缸壁上 至少设置两个进口， 左侧气缸壁设置一个出口。
所述圆柱形定轨可以为一套筒， 套筒呈圆筒状， 其内表面和外表面靠近气缸端盖处分别 设有内齿和外齿， 对应的在转子轴外表面设有外齿， 套筒内表面的内齿与转子轴外表面的外 齿相啮合； 圆柱形转子至少一侧的端面固定设置内齿环， 内齿环的内齿与套筒的外齿相啮合， 套筒的外圆周平滑面与活塞底弧面保持相切的状态。
所述转子轴和圆柱形定轨可以呈一体式结构， 圆柱形定轨偏心贯穿气缸端盖和转子， 与 圆柱形定轨的端面对应的气缸端盖上设有圆形凹槽， 圆柱形定轨和個筒形气缸同心， 所述转 子¾1圆筒形转子， 包括转子环和固定于转子环两端的固定环， 固定环伸入气缸端盖上的圆形 凹槽内， 囱定环的内表面设有内环齿， 对应的在掘柱形定轨外表面设有外环齿， 内环齿与外 环齿相 P¾合。'
:在活塞底弧面和圆柱定轨的外周面¾阔: ^以设置活塞承托件,每个活塞对应一个承托件， 承托件随活塞同步沿圆柱定轨做圆周运动，'活塞承托件包括上弧面和下弧面，:其中上弧面与 活塞底弧面的弧度相等， 下弧面与圆柱定轨外周面的弧^ 相等， 活塞承托件上弧面和下弧面 的长度不大于活塞底弧面的长度。
所述气缸也可以为椭圆形气缸， 此时定轨为椭圆形定轨， 圆柱形转子与椭圆形气缸呈同 心设置， 转子轴同心贯穿椭個形定轨和气缸端盖， 因此圆柱形转子、 转子轴、 椭圆形定轨和 椭圆形气缸呈同心设置， 椭圆形定轨的外表面与椭圆形气缸内表面之间的距离处处为等值， 活塞围绕定轨椭圆形定轨作椭圆曲线运动。 所述活塞为扇形活塞时， 其底弧面和侧弧面的半 径为椭圆形气缸内表面和椭圆形定轨外表面之间的距离值，底弧面和侧弧面的弧度均为 60° ， 顶弧面的弧度小于椭圆形气缸内壁曲线的最小弧度值， 顶弧面与活塞转轴相内切， 底弧面运 转的幅度不超过圆柱形转子的外圆周面。 以圆柱形转子和椭圆形气缸内壁的切点为界， 形成 左右两个对称的容积腔， 两容积腔内分别设置进口和出口， 两容积腔同时进气和排气。
顶弧面与圆筒形气缸内壁接触的一角为顶端角。 活塞的顶端角处可以设有密封装置， 密 封装置包括半圆柱体主封条和扇形卡板， 半圆柱体主封条的一面与气缸内壁接触， 半圆柱体 主封条与气缸内壁的接触面与圆筒形气缸内壁的弧度相同， 半圆柱体主封条的個心设置在活 塞顶端角与圆筒形气缸内壁的接触线上， 在半圆柱体主封条与气缸内壁的接触面上设有至少 一条密封槽， 密封槽内设有密封条， 半圆柱体主封条的两端分别安装有扇形卡板， 扇形卡板 与半圆柱体主封条同心， 扇形卡板的一端与半圆柱体主封条固定连接， 另一端的内侧设有圆 弧凸条， 对应的在扇形活塞上相设有圆弧凹槽， 圆弧凸条设置在圆弧凹槽内。
为了减少运转的惯性力， 扇形活塞可采用空腔形， 减轻活塞的重量， 活塞的底弧面设腔 口。 各气缸端盖上设置有转子冷却口和定轨、 活塞槽通联， 利用循环机油使运转部件降温。
本发明还包括一种定轨转子泵组合增压内燃发动机， 该发动机由上述至少两个设置在同 一转子轴上的定轨转子泵组合连接而成。 ' 所述定轨转子泵组合增压内燃发动机由一个作为压缩机使用的定轨转子泵和一个作为内 燃发动机使用的定轨转子泵固定连接组成， 或者由一个作为压縮机使用的定轨转子泵和两个 作为内燃发动机使用的定轨转子泵固定连接组成， 或者由一个作为内燃发动机使用的定轨转 子泵和两个作为压縮机使用的定轨转子泵固定连接组成。
所述相邻两定轨转子泵的气缸端盖呈一体式结构， 形成共用的气缸端盖。 两相邻的气缸 端盖可以固定连接在一起。
在相邻两定轨转子泵共用的气缸端盖上设有至少一 ^圆筒形喷气微孔， 该喷气微? L为作 为压缩机使用的定轨转子泵的出口， 同日 t为作为内燃发动机使用的定轨转子泵的进口， 该喷, 气微孔跗近的作为内燃发动机使用的定轨转子泵的气缸上设有燃料喷嘴和至少一支火花塞。
在枏邻气缸半径相同的前提下， 作为压缩机使用的圆柱定轨转子泵轴向长度大于作为内 燃发动机使用的圆柱定轨转子泵轴向长度时， 使压缩机使用的圆柱定轨转子泵气缸容积大于 作为内燃发动机使用的圆柱定轨转子泵气缸容积。
以经过圆筒形气缸内壁和圆柱形转子切点的气缸直径线为界， 相邻两圆柱定轨转子泵的 气缸径向设置偏角， 该偏角不大于 60° 。
作为内燃发动机使用的相邻扇形活塞之间的圆柱形转子上设有燃烧槽。
当圆柱定轨转子泵组合增压内燃发动机包括两个相同缸容的作为压缩机使用的圆柱定轨 转子泵和一个作为内燃发动机使用的圆柱定轨转子泵时， 作为内燃发动机使用的圆柱定轨转 子泵位于两个作为压缩机使用的圆柱定轨转子泵之间， 且位于中间的气缸容积小于位于两侧 的气缸容积之和；
当圆柱定轨转子泵组合增压内燃发动机包括两个相周缸容的作为内燃发动机使用的圆柱 定轨转子泵和一个作为压缩机使用的圆柱定轨转子泵时， 作为压缩机使用的欄柱定轨转子泵 位于两个作为内燃发动机使用的圆柱定轨转子泵之间， 且位于中间的气缸容积大于位于两侧 的气缸容积之和。
本发明的有益效果是：
( 1 )本发明中所设计的定轨转子泵由于实现了定轨和气缸内壁的同圆心的定位，使得扇形活 塞能够在定轨和气缸内壁之间形成的正圆形轨道作圆周运动， 克服了现有类型转子发动机扇 形活塞仅仅依靠弹簧或者弹簧片的装置限位的缺陷， 确保扇形活塞在高速运转条件下平稳顺 滑， 不出现偏位现象， 能够充分发挥出活塞的功效；
(2 ) 由于定轨转子泵具备了上述显著效果， 以由其组合而成的增压发动机功率高:；
(3 )将定轨转子泵组合增压内燃; i动机其中的空气压缩泵的尺寸适当增加， 即气缸容积轴向 延长， 采用增压手段改变相邻转子泵之间的气缸容积差， 比现有发动机各种增压技术具有更 加明显的优势， 该方法解决了现有机械式增压额外耗能， 涡轮增压低速状态下响应慢效果差 的问题， 而且增压能耗小， 同时取消了额外的增压设备， 使得该内燃发动机结构更加简单、 紧凑、 轻便；
( 4)所述密封装置的各部件之间的完全吻合式连接， 扩大了活塞和气缸内壁的接触面， 实现 了可增加不同作甩密封条的数量， 解决了单一封条密封效果差的问题， 密封性能明显提高。 附图说明
屈 1为实施例 1中圆柱定轨转子泵的径向剖视图；
图 2为图 1所示圆柱定轨转子泵的轴向剖视图； 图 3为本发明中圆柱定轨转子泵组合增压发动机的径向剖视图;
图 4为图 3所示圆柱定轨转子泵组合增压发动机的轴向剖视图；
图 5为本发明中密封装置的横向剖视图；
图 6是本发明中密封装置的轴向剖视图；
图 7是实施例 4中椭圆定轨转子泵的径向剖视图；
图 8是实施例 5中圆柱定轨转子泵的径向剖视图；
图 9是图 8所示圆柱定轨转子泵的轴向剖视图；
图 10是实施例 6中圆柱定轨转子泵的径向剖视图；
图 11是图 10所示圆柱定轨转子泵的轴向剖视图；
图 12是实施例 7中圆柱定轨转子泵的径向剖视图；
图 13是活塞承托件的立体图。
图中： 1圆筒形气缸； Γ 椭圆形气缸； 2气缸端盖； 3圆柱形转子； 3' 圆筒形转子； 301 转子环； 302固定环； 4转子轴； 5活塞槽 ; 6活塞； 7活塞转轴； 8圆柱形定轨； 8 ' 椭圆形 定轨； 801套筒； 9环状凹槽; 10底弧面； 11侧弧面； 12顶弧面； 13进口； 14出口； 15喷 气微孔； 16燃料喷嘴； 17火花塞； 18转子冷却口； 19密封装置 ; 20半圆柱封条； 21扇形卡 板； 22圆弧凸条； 23密封槽； 24密封环; 25转子环； 26转子环凹槽 ; 27内齿环； 28外迟 缓； 29活塞承托件。
具体实施方式
下面结合附图和实施例对本发明做进一步说明。
实施例 1
如图 1和图 2所示为圆柱定轨转子泵， 本发明包括圆筒形气缸 1和气缸端盖 2， 气缸端 盖 2位于气缸 Γ的两侧， 气缸端盖 2和气缸 1固定连接， 圆筒形气缸 1和气缸端盖 2可以为 各自单独的部件， 也可以为一侧的气缸端盖与气缸为各自单独的部件， 另一侧的气缸端盖与 气缸呈一体式结构。
圆柱形转子 3偏心置于圆筒形气缸 1内， 圆柱形转子 3与圆筒形气缸 1之间的偏心值为 圆柱形转子 3和圆筒形气缸 1的半径差值， 从而使圆柱形转子 3与圆柱形气缸 1内壁之间保 持相内切的状态。 懷柱形转子 3的两端面均设有环状凹槽 9， 气缸端盖 2的内侧设有 起的 圆柱形定轨 8， 圆柱形定轨 8.可以在 '一侧的气缸端盖设置， 也可以同时在两侧的气缸端毒设 置。 圆柱形定轨 8与圆筒形气缸 1呈同心设置， 圆拄形定轨 8与气缸端盖 2可以呈一体式结 构。 圆柱形转子 3周定套在转子轴 4上， 转子轴 4偏心贯穿圆柱形定轨 8和圆筒形气缸 1， 并与其他传动装置连接， 圆柱形转子 3与转子轴 4同心设置。 圆柱形定轨 8的直径大于转子 轴 4的直径， 小于圆柱形转子 3的直径， 为了保证圆柱形转子 3的强度， 圆柱形定轨 8的长 度不大于圆柱形转子 3长度的三分之二。.圆柱形定轨 8伸入圆柱形转子 3端面的环状凹槽 9 内， 环状凹槽 9的深度与圆柱形定轨 8的长度相对应， 环状凹槽的直径大于圆柱形定轨 8的 直径， 并小于圆柱形转子 3的直径。
沿圆柱形转子 3的外圆周面设有至少一个活塞 6， 活塞 6可以沿圆柱形转子的外圆周面 平均分布， 也可以呈对称分布。 活塞 6通过活塞转轴 7与圆柱形转子 3转动连接， 活塞转轴 7固定在圆柱形转子 3上， 活塞 6绕活塞转轴 7做圆周摆动。 同时在圆柱形转子 3上根据扇 形活塞的数量开设有活塞槽 5， 活塞槽 5贯通于圆柱形转子 3的轴向两端， 活塞 6设置于活 塞槽 5内。 活塞槽 5的^^状和尺寸与活塞 6完全吻合， 活塞 6穿过活塞槽 5与圆柱形定轨 8 接触。活塞 6包括顶弧面 12、底弧面 10和侧弧面 11， 活塞 6的顶端角始终与气缸内壁接触， 活塞 6的三个角之间的连线构成等边三角形。
活塞 6与活塞转轴 7可以呈一体式结构， 此时活塞 6为带有活塞转轴的三角形活塞， 活 塞槽 5内设有半圆状凹槽， 活塞转轴设置在该半圆状凹槽内， 并在该半圆状凹槽内转动。 活 塞 6与活塞转轴 7也可以为两个分离的部件，此时活塞转轴 7和圆柱形转子 3呈一体式结构， 此时的活塞为扇形活塞。 扇形活塞的底弧面 10和侧弧面 11的弧度均为 60° ， 底弧面和侧弧 面的半径为圆筒形气缸 1和圆柱形定轨 8的半径差值。 从作为活塞转轴圆心的端角点到与气 缸内壁接触的顶端角的弧面为顶弧面 12， 顶弧面 12的弧度等于圆柱形气缸 1的弧度， 其作 用在于最大限度地降低缸容余隙， 顶弧面 12与活塞转轴 7相内切。活塞转轴 7的轴心均位于 与圆柱形转子 3同心的同一半径的圆周线上， 活塞转轴 7的轴心与环状凹槽 9外周线之间的 距离小于环形凹槽和圆柱形转子半径差的 1/2， 以保证扇形活塞 6的底弧面 10和圆柱形定轨 8外圆周面在运转过程中始终保持相外切状态。.底弧面 10运转的最大幅度以不超过圆柱形转 子 3的外圆周为限。 各扇形活塞围绕圆柱形定轨 8作圆周运动。
以圆柱形转子 3和圆筒形气缸 1内壁的切点为界， 圆柱形转子 3顺时针方向运转时， 左 侧气缸壁上至少设置两个进口 13，右侧气缸壁设置一个出口 14。圆柱形转子 3逆时针方向运, 转时， 右侧气缸壁上至少设置两个进口 13， 左侧气缸壁设置一个出口 14。设置多个进口的目 的是降低吸进过程中相邻活塞间容腔产生的负压。 出口 14的数量根据扇形活塞的数量决定。 当圆柱定轨转子泵单独作为压缩设备使用时， .圆柱形转子 3无论是顺时针还是逆时针运转， 在沿:圆柱形转子的转动方向上， 活 最好设置在活塞转轴 7的后方。
扇形活塞的径向两端面设有密封槽和密封条， 气缸两端盖内壁对应圆柱形转子的位置设 有圆环形密封槽和密封环 24加强密封性。 以此为基础， 在不影响汽缸整体性能的前提下， 在 圆柱形转子两端还可增加设置与其半径相等且具有一定厚度的转子环 25。 转子环 25对应气 缸端盖内壁上设置转子环凹槽 26δ 为了减少运转的惯性力， 扇形活塞可采用空腔形， 底弧面 设腔口。 各气缸端盖上设置有转子冷却口 18和活塞槽通联， 利用循环机油使运转部件降温。
如果圆柱定轨转子泵仅作为一般条件的普通泵和压缩机使用时， 仅采取常规密封手段， 在扇形活塞顶角端设置狭窄的密封槽， 密封槽内置密封条即可实现扇形活塞的密封。 或者对 扇形活塞顶角端不做任何附加密封措施， 这样做使扇形活塞结构相对简单， 因此可以降低制 作成本。 但圆柱定轨转子在高温、 高压和高速运转工况下对气缸内部件的密封和润滑要求较 高， 此时采用如图 5所示的密封装置， 密封装置 19设置在活塞的顶端角处， 即活塞的顶弧面 沿气缸内壁滑动的角处。 该密封装置包括半圆柱体主封条 20和扇形卡板 21， 半圆柱体主封 条 20的一面与气缸内壁接触， 因此半圆柱体主封条 20的该面与圆筒形气缸内壁的弧度完全 吻合。半圆柱体主封条 20的圆心设置在活塞顶端角与圆筒形气缸内壁的接触线上， 活塞顶端 角为活塞顶弧面与圆筒形气缸内壁的接触角。 通过设置半圆柱体主封条 20， 使密封装置 19 与气缸内壁的接触面扩大， 在半圆柱体主寸条 20与气缸内壁的接触面上多条密封槽 23， 密 封槽 23内分别设有密封条， 提高密封效果。 半圆柱体主封条 20的两端分别安装有扇形卡板 21，扇形卡板 21与半圆柱体主封条同心，扇形卡板 21的一端与半圆柱体主封条 20固定连接， 另一端的内恻设有圆弧凸条 22， 对应的在扇形活塞上设有圆弧凹槽， 圆弧凸条 22设置在圆 弧凹槽内， 当活塞处于任何角度位置， 密封装置 19都不会发生脱离现象， 密封装置和活塞始 终保持顺滑运 If状态，从而防止密封装置 19在活塞运转过程中发生脱离。设置该密封装置后， 活塞 6的顶弧面 12所承受的作用力是向心力， 所以活塞 6顶角端与气缸内壁的摩擦力较小。
单个的圆柱定轨转子泵可以作为转子泵或压缩机使用。 转子泵工作时， 带动当圆柱形转 子 3.转动时， 扇形活塞转动， 由于扇形活塞的底弧面始终与圆柱形定轨 8相切， 因此扇形活 塞始终绕圆柱形定轨 8转动。扇形活塞转动过程中， 物料从进口 13进入扇形活塞之间， 扇形 活塞转动过程中， 对活塞之间的物料进行压缩， 被压缩的^ I料通过出口 14排出。
实施例 2
如图 3和图 4所示为圆柱定轨转子泵组合增压内燃发动机， 该发动机由套在同一转子轴 上的两个圆柱定轨转子泵串联连接而成。 两个圆柱定轨转子泵在周一转子轴上串联后， 相邻 的气缸端盖 2相互重叠， 为保证结构的紧凑牢固， 两相邻的气缸端盖 2可以为一体式结构。 其中一个圆柱定轨转子泵起到空气 '压缩机的作用， 另一个圆柱定轨转子泵起到内燃发 机的 作用。此时， 作为压缩 使用的圆柱定轨转子泵的出口设置在两转子泵共用的气缸端盖 2上， 该出口采用圆筒形喷气微孔 15， 喷气微孔的直径与气缸容积、 活塞数量等因素有关，.其直径 一般为 0. l-10mm。 同样的， 作为内燃发动机使用的圆柱定轨转子泵的进口为喷气微孔 15， 采 用喷气微¾^的目的是利用气流的喷射作用， 强迫混燃气体扰动， 提高燃烧效率。 该喷气口附 近的作为内燃发动机使用的圆柱定轨转子泵的气缸 1上安装燃料喷嘴 16和至少一支火花塞 17。 如果燃料是柴油， 则无需火花塞， 直接压燃。 喷油嘴则安装在该转子泵的进口附近位置， 正对进口可提高燃料雾化效果。 在圆柱形转子和气缸内壁内切位置附近安置火花塞。 作为内 燃发动机使用的相邻扇形活塞之间的圆柱形转子上设有燃烧槽， 该燃烧槽使压缩燃气能够摆 脱圆柱形转子和气缸内壁切点封闭区的限制， 顺利过渡到膨胀做功区域。
本实施例中， 可以适当增加作为压缩机使用的圆柱定轨转子泵的轴向长度， 其目的是扩 大气缸内容积， 当作为压缩机使用的圆柱定轨转子泵轴向长度大于作为内燃发动机使用的圆 柱定轨转子泵轴向长度时， 可以实现增加效果， 并且两者的气缸容积差越大， 增压值越大， 在任何转速条件下都能保持增压性能稳定。
以经过圆筒形气缸 1 内壁和圆柱形转子切点的气缸直径线为准， 相邻两气缸径向需设置 一定的偏角， 该偏角不大于 60° ， 以确保圆柱定轨转子泵组合增压内燃发动机能够充分发挥 其功能。 同一根转子轴贯穿相邻两气缸， 因此两相邻气缸的圆柱形转子不存在径向偏移， 因 此相邻两圆柱形转子上的扇形活塞径向位置仍然呈重叠和同步运转状态。 通过设置该偏角， 可以防止内燃发动机内的压缩气体逆流进入压缩机内， 在发动机运转状态下， 作为压缩机的 转子泵的活塞和相对应的燃烧做功转子泵内的活塞始终保持前后位置， 有利于内燃发动机完 成进气、 进一步压缩、 燃烧、 膨胀做功过程。 活塞的顶端角处需设置密封装置。
该内燃发动机工作时，.作为压缩机使用的圆柱定轨转子泵首先对空气进行压缩， 被压缩 的空气通过喷气口 15进入作为内燃发动机使用的圆柱定轨转子泵内，其中该圆柱定 l转子泵 内的活塞在圆柱形转子的转动作用下， 依次完成进气、 压缩、 燃烧和膨胀做功的工序。
其它同实施例 1。
实施例 3
圆柱定轨转子泵组合增压内燃发动机的组合方式并不限于实施例 2中的组合方式， 也可 以采用以下的组合方式：
( 1 ) 欄柱定轨转子泵组合增压内燃发动机包括两个相同缸容的作为压缩机使用的圆柱 定轨转子泵和一个作为内燃发动机使用的圆柱定轨转子泵， 作为内燃发动机使用的圆柱定轨 转子泵位于两个作为压缩机使用'的圆柱定轨转子泵之伺， 且位于中间的气缸容积小 4位于两 侧的气缸容积之和; (2 ) 圆柱定轨转子泵组合增压内燃发动机包括两个相同缸容的作为内燃发动机使用的 圆柱定轨转子泵和一个作为压缩机使用的圆柱定轨转子泵， 作为压缩机使用的圆柱定轨转子 泵位于两个作为内燃发动机使用的圆柱定轨转子泵之间， 且位于中间的气缸容积大于位于两 侧的气缸容积之和。
上述两种情况下， 相邻的圆柱定轨转子泵之间均存在偏转角， 该偏角相不大于 90° 。 但 是三个圆柱定轨转子泵均被同一根转子轴贯穿。
上述两种组合形式的内燃发动机都会共用一个气缸端盖， 共用气缸端盖不仅涉及到相邻 气缸间存在的偏转角问题， 还涉及到气缸部件加工的难度， 以及安装的牢固性和便捷性问题。 因此， 根据实际的生产情况， 共用的气缸端盖可以采用以下三种结构方式： （1 ) 中间气缸的 两侧端盖和与其相邻的气缸端盖之间均为分离状态； （2 ) 中间气缸的一侧端盖和与其相邻的 气缸端盖相互共用， 另一侧端盖和与其相邻的气缸端盖为分离状态； （3 ) 中间气缸的两侧端 盖和与其相邻的气缸端盖均相互共用。 无论哪一种安装方式都不影响转子轴的安装和拆卸。
另外也可以采用圆柱定轨转子泵组合增压内燃发动机的再组合方式， 即在同一根转子轴 上设有多个圆柱定轨转子泵组合增压内燃发动机。
其它同实施例 1。
实施例 4
如图 7所示为椭圆定轨转子泵， 与实施例 1不同的是， 本实施例中的气缸为椭圆形气缸 1 ' , 气缸端盖 2位于气缸 Γ 的两侧， 气缸端盖 2和气缸 Γ 固定连接。
圆柱形转子 3设置在椭圆形气缸 Γ 内， 圆柱形转子 3与椭圆形气缸 呈同心设置，且 圆柱形转子 3与椭圆形气缸 Γ 内壁圆弧的短轴顶点保持相内切的状态， 从而形成两个对称 的相对封闭的容积腔。 圆柱形转子 3的两侧面均设有环状凹槽 9， 气缸端盖 2的内侧设有凸 起的椭圆形定轨 8' ，椭圆形定轨.8 ' 与气缸端盖 2呈同心设置， 圆柱形转子 3.固定套在转子 轴 4上， 圆柱形转子 3与转子轴 4同心设置， 因此圆柱形转子 3、 转子轴 4、：椭圆形定轨 8' . 和满圆形气缸 Γ 为同心设置， 且椭圆形定轨 8' 外表面与椭圆形气缸 Γ '内表面之间的距离 处处为等值。转子轴 4同心贯穿椭圆形定轨 8' 和气缸端盖 2， 并与其他传动装置连接。椭圆 形定轨 8' 伸入圆柱形转子 3端面的环状凹槽 9内，环状凹槽 9的深度与椭圆形定轨 8 ' 的长 度相对应， 环状凹槽的直径大于椭圆形定轨 8 ' 的短轴长度， 并小于圆柱形转子 3的直径。. 本实施例中， 所述活塞 6和活塞槽 5的设置与实施例 1中活塞 6和活塞槽 5的设置完全 相同。 当活塞 6为扇形活塞时，'扇形活塞的底弧面 10和侧弧面 11的弧度均为 60° '， 底弧面 和侧弧面的半径为圆筒形气缸 1内表面和圆柱形定轨 8外表面之间的距离值。 从作为活塞转 轴圆心的端角点到与气缸内壁接触的顶端角的弧面为顶弧面 12， 顶弧面 12的弧度小于椭圆 形气缸 Γ 内壁曲线的最小弧度值， 底弧面 10与椭圆形定轨 8 ' 的外圆周始终保持接触的状 态。 活塞转轴 7的轴心均位于与椭圆形定轨 8' 同心的伺一半径的圆周线上。 圆柱形转子 3 在做圆周运动的同时带动扇形活塞在椭圆形定轨 8 ' 和椭圆形气缸 Γ 之间的椭圆环状空间 内运动。 底弧面 10运转的最大幅度以不超过圆柱形转子 3的外圆周为限。
以圆柱形转子 3和椭圆形气缸 Γ 内壁的切点为界， 形成左右两个对称的容积腔， 两容 积腔内分别设置进口和出口， 两容积腔同时进气和排气。
上述椭圆定轨转子泵内设置单一的进口和出口， 在转子泵内安装点火设备和喷油设备后 可以直接改造成内燃机， 圆柱形转子转动一周即可完成进气、 压縮、 燃烧和排气， 无需另外 设置进气门和排气门， 结构简单。
所述的定轨和气缸的形状并不限于本实施例所述的椭圆形， 也可以为由平滑曲线连接的 不同半径的对 ¾ ^圆弧构成的近似椭圆形。 只要能够保证定轨与气缸的形状相同且两者之间的 距离处处为定值即可。
椭圆定轨转子泵组合内燃机的组合方式和做功原理与实施例 2和实施例 3中圆柱定轨转 子泵组合增压内燃发动机相同， 因此不再赘述。
其他同实施例 1。
实施例 5
如图 8和图 9所示为实施例 5所述的圆柱定轨转子泵， 与实施例 1不同的是： 本实施例 中的转子轴和圆柱形定轨呈一体式结构， 与圆柱形定轨 8的端面对应的气缸端盖 2上设有圆 形凹槽。 圆柱形定轨 8和圆筒形气缸 1同心。所述转子 3 ' 呈圆筒形， 圆筒形转子 3 ' 偏心贯 穿圆柱形气缸， 圆筒形转子 3 ' 包括转子环 301和固定于转子环 301两端的固定环 302， 固定 环 302伸入气缸端盖 _h的圆形凹槽内， 起到加强密封和控制转子环的转动。 周定环 302的内 表面设有内环齿 27.，对应的在圆柱形定轨 8外表面设有外环齿 28， 内环齿 27与外环齿 28相 啮合。 转子环 301通过内环齿与外环齿之间的啮合， 驱动圆柱形定轨 8运转， 转子环 301转 动一周， 圆柱形定轨 8转动大于一周。
圆筒形转子 3 ' 偏心安装于圆柱形气缸 1内，且与气缸内壁内切。 圆筒形转子 3 ' 上设有. 活塞槽， 扇形活塞设置在活塞槽内。 扇形活塞的顶端角与气缸内壁始终保持接 扇形活塞 的底弧面始终与圆柱形定轨 8保持接触， 各扇形活塞围绕圆柱形定轨 8作圆周运动。
本实施所述的圆柱定 $九转'子泵组合内燃 1的组合方式和做功原理与实施例 2 实施例 3 中圆柱定轨转子泵组合增压内燃发动机相同， 因此不再赘述。 其它伺实施例 1。
实施例 6
如图 10和图 11所示为实施例 6所述的圆柱定轨转子泵， 与实施例 1不同的是： 所述圆 柱形定轨采用套筒式结构， 即圆柱形定轨为一套筒 801， 套筒 801呈圆筒状， 其内表面和外 表面靠近气缸端盖处分别设有内齿和外齿， 对应的在转子轴 4外表面设有外齿， 套筒 801内 表面的内齿与转子轴 4外表面的外齿相啮合。 圆柱形转子 3—侧或两侧的端面固定设置内齿 环， 内齿环的内齿与套筒 801的外齿相啮合。 套筒 801外圆周的平滑面与扇形活塞底弧面仍 保持接触。
圆柱形转子 3通过内齿环驱动圆柱定轨 8转动， 而圆柱定轨 8通过其其内齿与转子轴 4 外齿的啮合驱动转子轴 4转动， 最终实现转子轴 4的转速成倍提高。
本实施所述的圆柱定轨转子泵组合内燃机的组合方式和做功原理与实施例 2和实施例 3 中圆柱定轨转子泵组合增压内燃发动机相同， 因此不再赘述。
其它同实施例 1。
实施例 7
如图 12和图 13所示为实施例 7所述的圆柱定轨转子泵， 与实施例 1不同的是: 在活塞 底弧面和圆柱定轨 8外周面之街设置活塞承托件 29， 每个活塞对应一个承托件。 承托件随活 塞同步沿圆柱定轨做圆周运动。
活塞承托件 29包括上、 下两个圆弧面， 其中上弧面与活塞的底弧面相吻合， 弧度相等； 下弧面与圆柱定轨外周面吻合， 弧度相等。 上弧面和下弧面之间的最小距离应为未设置承托 件时圆柱定轨原有半径尺寸和设置承托件后半径尺寸之间差值。活塞承托件 29上、下弧面的 长度应不大于扇形活塞底弧面的长度。
实施例 1中的扇形活塞底弧面尽管能够和圆柱定轨外周面始终保持接触， 但是仍然存在 以下两方面的不足： 一是活塞和圆柱定轨的接触面狭小， 长期高负荷运转条件下会出现磨损 过快， 导致密封性能降低的情况。 二是扇形活塞轴心点的设计位置有 定局限性， 过于偏向 转子外周面时会导致活塞底弧面在局部转角位置出现与圆柱定轨脱离的状况， 同样会导致失 去密封性作用。 通过本实施例中设置的活塞承托件 29就可以彻底解决上述问题。 .
本实施所述的圆柱定轨转子泵组合内燃机的组合方式和做功原理与实施例 2和实施例 3 中圆柱定轨转子泵组合增压内燃发动机相同， 因此不再赘述。
其它同实施例 1。

Claims

1、 一种定轨转子泵， 包括气缸、 位于气缸两侧的气缸端盖（2)和设置在气缸内的转子， 转子轴 （4) 贯穿转子， 气缸端盖 （2) 和气缸固定连接， 其特征在于： 转子与气缸内壁之间 为相内切的状态， 至少一侧的气缸端盖（2)的内侧固定有凸起的定轨， 定轨与气缸呈同心设 置， 转子轴 （4) 贯穿气缸端盖 （2)和定轨， 沿转子的外圆周面设有活塞 （6)， 活塞 （6)通 过活塞转轴 （7)与转子转动连接， 活塞转轴 （7) 固定在转子上， 活塞（6)绕活塞转轴 （7) 做圆周摆动， 转子上设有活塞槽 （5)， 活塞槽（5) 贯通于圆柱形转子 （3) 的轴向两端， 活 塞 （6) 设置于活塞槽 （5) 内， 活塞 （6)包括顶弧面 （12)、 底弧面 （10) 和侧弧面 （11)， 活塞 (6) 的三个角之间的连线构成等边三角形， 活塞转轴 （7) 的轴心位于与转子同心的同 一半径的圆周线上， 活塞 （6) 的顶端角与气缸内壁保持接触， 活塞 （6) 的底弧面 （10) 和 定轨外圆周面为相外切的状态， 活塞 （6) 围绕定轨作曲线运动。
2、 根据权利要求 1所述的定轨转子泵， 其特征在于： 所述转子为圆柱形转子（3)， 圆柱 形转子 （3) 的端面设有环状凹槽 （9)， 定轨伸入圆柱形转子 （3) 端面的环状凹槽 （9) 内。
3、 据权利要求 2所述的定轨转子泵， 其特征在于： 所述转子固定套在转子轴 （4) 上， 转子与转子轴 （4) 同心设置， 气缸为圆筒形气缸（1)， 定轨为圆柱形定轨（8)， 所述圆柱形 转子 （3)偏心置于圆筒形气缸 （1) 内， 圆柱形转子 （3) 与圆筒形气缸 （1) 之间的偏心值 为圆柱形转子 （3) 和圆筒形气缸 （1) 的半径差值， 转子轴 （4) 偏心贯穿气缸端盖 （2) 和 圆柱形定轨 （8)， 活塞转轴 （7) 的轴心与环状凹槽 （9) 外周线之间的距离小于环形凹槽和 圆柱形转子半径差的 1/2， 活塞 （6) 围绕圆柱形定轨 （8) 作圆周运动。
4、 据权利要求 2所述的定轨转子泵， 其特征在于： 所述气缸为椭圆形气缸（ )， 定轨 为椭圆形定轨 (8' )， 圆柱形转子（3) 与椭圆形气缸（Γ )呈词心设置， 转子轴 （4) 同心. 贯穿椭圆形定轨（8' )和气缸端盖（2)，因此圆柱形转子（3)、转子轴（4)、椭圆形定轨（8' ) 和椭圆形气缸（Γ )呈同心设置， 椭圆形定轨（8' ) 的外表面与椭圆形气缸（ ) 内表面 之间的距离处处为等值， 活塞 （6) 围绕定轨椭圆形定轨 (8' ) 作椭圆曲线运动。
5、 据权利要求 3所述的定轨转子泵， 其特征在于： 所述圆柱形定轨为一套筒（801)， ·套 筒 （801)呈圆筒状， 其内表面和外表面靠近气缸端盖处 （2) 处分别设有内齿和外齿， 对应 的在转子轴 （4)外表面设有外齿， 套筒 （801) 内表面的内齿与转子轴 （4)外表面的外齿相 啮合; 圆柱形转子 （3) 至少一侧的端面固定设置内齿环， 内齿环的内齿与套筒 （801) 的外 齿相啮合， 套筒 （801) 的外圆周平滑面与活塞底弧面保持相切的状态。
6、 根据权利要求 1所述的定轨转子泵， ^特征在于： 所述气缸为圆筒形气缸（1)， 定轨 为圆柱形定轨（8)， 转子轴和圆柱形定轨呈一体式结构， 圆柱形定轨 (8)偏心贯穿气缸端盖 (2) 和转子， 与圆柱形定轨（8) 的端面对^ Z的气缸端盖 （2)上设有圆形凹槽， 圆柱形定轨 (8) 和圆筒形气缸 （1) 同心， 所述转子为圆筒形转子 （3' )， 圆筒形转子 （3' ) 偏心置 于圆筒形气缸（1)内，圆筒形转子（3' )与圆筒形气缸（1)之间的偏心值为圆筒形转子（3' ) 和圆筒形气缸（1)的半径差值， 圆筒形转子（3' )包括转子环（301)和固定于转子环（301) 两端的固定环 （302)， 固定环 （302) 伸入气缸端盖上的圆形凹槽内， 固定环 （302) 的内表 面设有内环齿（27), 对应的在圆柱形定轨 （8)外表面设有外环齿 （28)， 内环齿 （27)与外 环齿 （28) 相啮合， 活塞转轴 （7) 的轴心位于与圆筒形转子 （3' ) 同心的同一半径的圆周 钱上， 活塞转轴 （7) 的轴心与环状凹槽 （9) 外周线之间的距离小于环形凹槽和圆柱形转子 半径差的 1/2， 活塞 （6) 围绕圆柱形定轨 （8) 作圆周运动。
7、 根据权利要求 2、 3、 5或 6所述的定轨转子泵， 其特征在于： 在活塞底弧面（10)和 圆柱定轨 （8) 的外周面之间设置活塞承托件 （29)， 每个活塞对应一个承托件， 承托件随活 塞同步沿圆柱定轨做圆周运动， 活塞承托件 （29) 包括上弧面和下弧面， 其中上弧面与活塞 底弧面的弧度相等， 下弧面与圆柱定轨外周面的弧度相等, 活塞承托件 （29) 上弧面和下弧 面的长度不大于活塞底弧面的长度。
8、 根据权利要求 2、 3、 5、 6或 7所述的定轨转子泵， 其特征在于： 所述活塞（6)为扇 形活塞时， 其底弧面 （10) 和侧弧面 （11) 的半径为圆筒形气缸 （1) 和圆柱形定轨 （8) 的 半径差值， 底弧面 （10)和侧弧面 （11) 的弧度均为 60° ， 顶弧面 （12) 的弧度等于圆柱形 气缸 （1) 内壁的弧度， 顶弧面 (12) 与活塞转轴 （7) 相内切， 底弧面 (10) 运转的幅度不 超过圆柱形转子 （3) 的外圆周面。
9、 根据权利要求 4所述的定轨转子泵， 其特征在于： 所述活塞 (6) 为扇形活塞时， 其 底弧面 （10) 和侧弧面 （11) 的半径为椭湿形气缸 （ ) 内表面和椭圆形定轨 （8' ) 外表 面之间的距离值， 底弧面 (10)和侧弧面 （11) 的弧度均为 60° ， 顶弧面 (12) 的弧度小于 椭圆形气缸 （Γ ) 内壁曲线的最小弧度值， 顶弧面 （12) 与活塞转轴 （7) 相内切， 底弧面
(10) 运转的幅度不超过圆柱形转子 （3) 的外圆周面。
10、 根据权利要求 2、 3、 5、 6或 7所述的定轨转子泵， 其特征在于: 以圆柱形转子 (3) 和圆筒形气缸 （1) 内壁的内切切点为界， 圆柱形转子 (3)顺时针方向运转时， 左侧气缸壁 上至少设置两个进口 （13)， 右侧气缸壁设置一个出口 （14); 圆柱形转子（3)逆时针方向运 转时， 右侧气缸壁上至少设置两个进口 （13)， 左侧气缸壁设置一个出口 （14)。
11、 根据权利要求 8所述的定轨转子泵,'其特征在于： 活塞 (6)的顶端角处设有密封装 置 （19)， 密封装置包括半圆柱体主封条 （20) 和扇形卡板 (21), 半圆柱体主封条 (20) 的 一面与气缸内壁接触， 半圆柱体主封条（20 )与气缸内壁的接触面与圆筒形^ ΐ缸（1 ) 内壁的 弧度相同， 半圆柱体主封条 （20 ) 的圆心设置在活塞顶端角与圆筒形气缸内壁的接触线上， 在半圆柱体主封条（20)与气缸内壁的接触面上设 ¾"至少一条密封槽（23)， 密封槽（23 ) 内 设有密封条（24)， 半圆柱体主封条（20 ) 的两端分别安装有扇形卡板（21 )， 扇形卡板（21 ) 与半圆柱体主封条同心， 扇形卡板 （21 ) 的一端与半圆柱体主封条 （20 ) 固定连接， 另一端 的内侧设有圆弧凸条（22)， 对应的在扇形活塞上相设有圆弧凹槽， 圆弧凸条（22 )设置在圆 弧凹槽内。
12、 根据权利要求 2- 7所述的定轨转子泵， 其特征在于： 各气缸端盖上均设有转子冷却 口 （18 ) 和定轨、 活塞槽通联。
13、 一种定轨转子泵组合增压内燃发动机， 其特征在于： 该发动机由至少两个权利要求 1 - 14所述的设置在同一转子轴上的定轨转子泵组合连接而成。
14、根据权利要求 13所述的定轨转子泵组合增压内燃发动机， 其特征在于： 所述定轨转 子泵组合增压内燃发动机由一个作为压缩机使用的定轨转子泵和一个作为内燃发动机使用的 定轨转子泵固定连接组成， 或者由一个作为压缩机使用的定轨转子泵和两个作为内燃发动机 使用的定轨转子泵固定连接组成， 或者由一个作为内燃发动机使用的定轨转子泵和两个作为 压缩机使用的定轨转子泵固定连接组成。
15、 根据权利要求 13或 14所述的定轨转子泵组合增压内燃发动机， 其特征在于： 所述 相邻两定轨转子泵的气缸端盖 （2 ) 呈一体式结构，.形成共用的气缸端盖 （2)。
16、根据权利要求 15所述的定轨转子泵组合增压内燃发动机，其特征在于： 在相邻两定 轨转子泵共用的气缸端盖 （2 ) 上设有至少一个圆筒形喷气微孔 （15 )， 该喷气微孔为作为压 缩机使用的定轨转子泵的出口， 同时为作为内燃发动机使用的定轨转子泵的进口， 该喷气微 孔附近的作为内燃发动机使用的定轨转子泵的气缸上设有燃料喷嘴 （16 )和至少一支火花塞
( 17)。
17、 根据权利要求 13或 14所述的定轨转子泵组合增压内燃发动机， 其特征在于： 相邻 气缸的半径相同时， 作为压縮机使用的定轨转子泵轴向长度大于作为内燃发动机使用的定轨 转子泵轴向长度时， 使作为压缩机使用的定轨转子泵气缸容积大于作为内燃发动机使用的定 轨转子泵气缸容积。
18、根据权利要求 13所述的定轨转子零组合增压内燃发动机，.其特征在于： 以经过圆筒 形气缸（1 )内壁和圆柱形转子切点的气缸直径线为界， 相邻两圆柱定轨转子泵的气缸径向设 置偏角， 该偏角不大于 60° 。
19、 根据权利要求 14所述的定轨转子泵组合增压内燃发动机， 其特征在于： 作为内燃发 动机使用的相邻扇形活塞之间的圆柱形转子上设有燃烧槽。
PCT/CN2014/000700 2013-07-24 2014-07-24 定轨转子泵及定轨转子泵组合增压内燃发动机 WO2015010446A1 (zh)

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