WO2015154645A1 - 偏心活动叶片泵 - Google Patents

偏心活动叶片泵 Download PDF

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Publication number
WO2015154645A1
WO2015154645A1 PCT/CN2015/075934 CN2015075934W WO2015154645A1 WO 2015154645 A1 WO2015154645 A1 WO 2015154645A1 CN 2015075934 W CN2015075934 W CN 2015075934W WO 2015154645 A1 WO2015154645 A1 WO 2015154645A1
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WO
WIPO (PCT)
Prior art keywords
rotor
cylinder
movable vane
fluid
eccentric
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2015/075934
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English (en)
French (fr)
Inventor
汤斌
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 CN201420169067.3U external-priority patent/CN203796560U/zh
Priority claimed from CN201420233783.3U external-priority patent/CN204082533U/zh
Priority to BR112016023581A priority Critical patent/BR112016023581A2/pt
Application filed by Individual filed Critical Individual
Priority to KR1020167031235A priority patent/KR20160143785A/ko
Priority to US15/301,396 priority patent/US20170030352A1/en
Priority to CA2944804A priority patent/CA2944804A1/en
Priority to EP15776220.4A priority patent/EP3144532A4/en
Priority to JP2016560961A priority patent/JP6408027B2/ja
Priority to EA201692033A priority patent/EA201692033A1/ru
Publication of WO2015154645A1 publication Critical patent/WO2015154645A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C2/38—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 F04C2/02 and having a hinged member
    • F04C2/39—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 F04C2/02 and having a hinged member with vanes hinged to the inner as well as to the outer member
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating 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
    • F04C18/38—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 F04C18/02 and having a hinged 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
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/063—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • 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
    • F04C2/38—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 F04C2/02 and having a hinged 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details

Definitions

  • the invention relates to an eccentric movable vane pump, in particular to a variable volume eccentric movable vane pump, which can be used for a vacuum pump, a compressor pump, a water pump, a car turbocharger, a gas turbine internal combustion engine, a fan, a hydraulic engine, a steam through Flat pumps, thrusters and stepless fluid couplings.
  • variable displacement pump is mainly a piston pump and a vane pump. They all adopt the principle of friction sealing, so the friction plate is easy to wear, the sealing effect is not good, the working life and efficiency are not high, but the machining precision is high.
  • the friction plate is in high-speed operation, due to the spring elastic force, frequency, working fluid pressure, pressure difference and other working conditions, the efficiency of the equipment will fluctuate greatly, so the working range is narrow and cannot be used for high speed, high pressure, high flow rate, etc. It is required to be used under working conditions, and the effective volume ratio of this type of variable displacement pump is low.
  • the centrifugal pump drives the liquid medium to rotate at a high speed by the impeller, and transfers the mechanical energy to the liquid working medium.
  • the volumetric pump periodically increases and shrinks the working volume by the movement of the working part, and sucks and discharges the liquid, and relies on the working part. Extrusion directly increases the pressure energy of the liquid; the jet pump illuminates the liquid by a high-speed jet generated by the working fluid, and then increases the energy of the drained liquid by momentum exchange.
  • centrifugal pumps and jet pumps are flow-type open energy exchanges
  • volumetric pumps are capacity-type closed energy exchanges. Under the condition of the same power density ratio, from the working mode, the energy utilization rate of the three machines should be the highest, and the energy utilization rate of the volumetric pump should be the highest, followed by the centrifugal pump and again the jet pump.
  • the traditional volumetric pump changes the piston working volume through the crank-link structure.
  • the volumetric pump can effectively solve the leakage of working fluid through the gap size between mechanical parts and the addition of seals. Problem, the optimal volumetric pump efficiency can be designed to reach more than 90%.
  • the crank-cranked slider structure of the conventional positive displacement pump due to the limitation of the crank-cranked slider structure of the conventional positive displacement pump, the working efficiency of the volumetric pump to achieve a wide range of lift and a wide range of flow rates is the same as that of the centrifugal pump, which requires expensive materials and is extremely expensive. Complex mechanical structure and huge mechanical volume.
  • the eccentric movable vane pump of the invention can easily control the leakage of the working fluid, and can realize the working efficiency of the wide range head and the wide range flow rate like the centrifugal pump, and has the high mechanical power density ratio, and has the advantages of simple structure and high efficiency.
  • Low cost, multi-case, high stability, long life, non-required elastic device seal can also work in high speed and ultra-high speed range, and the radial impact is small when working. It can be used in vacuum pumps, compressor pumps, water pumps, automotive turbochargers, gas turbine internal combustion engines, fans, hydraulic engines, steam turbine pumps, thrusters and stepless fluid couplings.
  • the technical solution of the present invention is to provide an eccentric movable vane pump, comprising a cylinder, a first rotor, a second rotor and a movable vane, wherein the first rotor and the second rotor are eccentrically disposed, wherein the first rotor and the movable vane are One end is rotatably connected, the second rotor is in one-to-one correspondence with the movable vane, and the number is greater than or equal to two; the other end of the movable vane is rotatably connected with the second rotor; the first rotor is disposed on the main shaft A fluid inlet and a fluid outlet are respectively disposed on the cylinder corresponding to the expansion region and the compression region of the space between the adjacent movable blades.
  • fixed vanes are further provided on the second rotor, respectively, and the spatial volume between adjacent fixed vanes undergoes periodic compression and expansion changes, so that the fixed vane and the cylinder member constitute a positive displacement pump.
  • each of the fixed vanes and the corresponding second rotor are connected by a fixed ratio mechanism, such that the fixed vane changes from one revolution to one revolution, and the fixed vane rotates one revolution.
  • the rotation speed has a cyclical change of multiple speed conversions, so that the fixed blade rotates one time in the cylinder to generate multiple compression and expansion processes, thereby fixing the blade to rotate one week to complete the gas four-stroke work process.
  • the space between the adjacent movable vane and the cylinder is set in the cylinder corresponding to the space during the rotating operation, in the process that the space approaches the maximum volume and gradually decreases from the maximum volume.
  • the space between the adjacent fixed vanes and the cylinder is set in the cylinder corresponding to the space during the rotating operation, in the process that the space approaches the maximum volume and the maximum volume gradually decreases.
  • the cylinder corresponding to the spatial volume expansion region and the volume compression region is provided with a valve mechanism, and the valve mechanism is closed when the gas is compressed and expanded in the space.
  • the space is opened during intake and exhaust for a four-stroke engine.
  • both sides of the movable blade are curved surfaces, one side of which coincides with the first rotor wall surface and the other side coincides with the second rotor wall surface.
  • the movable blade is rotatably coupled to the first rotor and the second rotor in a shaft hole connection manner or a flexible connection manner.
  • an arc-shaped group portion is further disposed on the second rotor, and the arc-shaped group portions on the second rotor corresponding to the rotational connection of the adjacent movable blades are mutually embedded
  • the sleeve, the volume space between the adjacent movable blades is separated from the gap between the adjacent second rotors by the mutually nested arc segments.
  • a rotor fluid inlet and a rotor fluid outlet are respectively disposed on the first rotor corresponding to the upper and lower portions of the annular wall between adjacent movable blades; the cylinder fluid inlet and the cylinder fluid outlet and the rotor fluid inlet and rotor The fluid outlets are correspondingly disposed in the upper and lower portions of the cylinder; the fluid enters or exits the volume between the adjacent moving blades as the rotor fluid inlet and the cylinder fluid inlet pass through or the rotor fluid outlet and the cylinder fluid outlet.
  • the rotor fluid inlet and the rotor fluid outlet are provided with a controlled valve, and the controlled valve is composed of one of a fluid pressure difference, a centrifugal force, a power, a magnetic force, and an elastic force. More than the above combined force control.
  • the low pressure fluid enters the volume space through the cylinder fluid inlet, and the low pressure fluid is pressurized in the volume space and discharged through the cylinder fluid outlet to form a booster pump;
  • the high pressure fluid enters the volume space through the cylinder fluid inlet, the high pressure fluid After releasing the pressure in the volume space, the pressure is discharged through the cylinder fluid outlet to form a pressure reducing pump; or the low pressure fluid enters the volume space through the rotor fluid inlet, and the low pressure fluid is pressurized in the volume space and discharged through the rotor fluid outlet to form a booster pump;
  • the fluid enters the volumetric space through the rotor fluid inlet, and the high pressure fluid releases the pressure in the volume space and exits through the rotor fluid outlet to form a reduced pressure pump.
  • a control mechanism is further disposed on the cylinder, the control mechanism changes a positional relationship with the cylinder fluid inlet and the cylinder fluid outlet to adjust the shape and size area of the cylinder fluid inlet and the cylinder fluid outlet; or
  • the control mechanism can change the controlled valve switching conditions, such as the switch start position of the controlled valve, thereby changing the volume of fluid entering or exiting the volume space per revolution of the eccentric movable vane pump.
  • two eccentric movable vane pumps are provided, one of which is a booster pump and the other is a decompression pump, and the fluid flows through the booster pump and the decompression pump in succession at the control mechanism.
  • the volume of the booster pump and the decompression pump is changed every one rotation of the booster pump and the decompression pump, so that the speed difference between the booster pump and the decompression pump can be changed as a torque converter, and the continuously variable transmission is used.
  • a booster pump and a pressure reducing pump and a heat exchange chamber are arranged, and the booster pump and the pressure reducing pump are coaxially fixedly connected, and the fluid flows through the booster pump, the heat exchange chamber and
  • the decompression pump can be used as a turbocharger, an internal combustion engine, a gas turbine, or an external combustion engine.
  • a rotor fluid passage is provided on the first rotor corresponding to the annular wall between adjacent moving vanes.
  • the rotor fluid passage is provided with a valve, and the valve is controlled by one of a fluid pressure difference, a centrifugal force, a power, a magnetic force, an elastic force, or a combination of two or more.
  • the track mechanism is composed of two annular guide rails of different diameters, and the two annular guide rails are connected by a cross rail to form a closed loop.
  • the rotor or slider disposed on the valve acts on the track mechanism and corresponds to the open or closed state of the valve when the rotor or slider acts on a different diameter track of the track mechanism.
  • a rotating mechanism provided with a rotatable track mechanism can be changed, and the relative positional relationship between the track mechanism and the first rotor can be changed when the track mechanism is rotated.
  • the position of the eccentric shaft at the cylinder is controlled by an eccentric shaft control mechanism that changes the position of the eccentric shaft on the cylinder to change the eccentricity between the first rotor and the second rotor. distance.
  • the eccentric shaft control mechanism is composed of a control shaft that is eccentrically disposed on the eccentric shaft and eccentrically disposed with the first rotor, and the control shaft is rotatably disposed on the cylinder.
  • the cylinder fluid inlet main region is located in a region where the space between adjacent moving blades is in an expansion phase and the space volume is in a larger state corresponding to the cylinder.
  • the cylinder fluid outlet main region is located in a region where the space between adjacent moving blades is in a compression phase and the space volume is in a larger state corresponding to the cylinder.
  • the present invention also provides an eccentric movable vane pump comprising a cylinder, a first rotor, a second rotor and a movable vane, the first rotor and the second rotor being eccentrically disposed, wherein the first rotor and the movable vane are rotatably connected at one end thereof, The other end of the movable blade is provided with a push rod, and the push rod slides in a slide provided on the second rotor; the number of the movable blades is greater than or equal to 2; corresponding to the adjacent movable blade on the cylinder
  • the expansion region and the compression region of the space between the space are respectively provided with a fluid inlet and a fluid outlet.
  • fixed vanes are further provided on the second rotor, respectively, and the spatial volume between adjacent fixed vanes undergoes periodic compression and expansion changes, so that the fixed vane and the cylinder member constitute a positive displacement pump.
  • the invention has the advantages of simple structure, high efficiency, low cost, multiple working conditions, high stability and long life, can be operated in the high speed and ultra high speed range without the need of elastic device sealing, and has small radial impact during operation. It can be used in vacuum pumps, compressor pumps, water pumps, automotive turbochargers, gas turbine internal combustion engines, fans, hydraulic engines, steam turbine pumps, thrusters and stepless fluid couplings.
  • Figure 1 is a schematic view of a second rotor belt slide of the present invention.
  • Figure 2 is a schematic view showing the structure of the movable blade of Figure 1.
  • Fig. 3 is a schematic view showing the structure of the second rotor of the present invention.
  • Fig. 4 is a schematic view showing the structure of another form of the second rotor of the present invention.
  • Figure 5 is a schematic view showing the concrete structure of the movable blade of Figure 4 of the present invention.
  • Figure 6 is a schematic view showing the structure of a two-stroke engine of the present invention.
  • Figure 7 is a schematic illustration of a four-stroke engine with a valve train of the present invention.
  • Figure 8 is a schematic view showing the internal structure of a positive displacement pump with fixed blades of the present invention.
  • Figure 9 is a schematic illustration of an engine with a fixed ratio mechanism of the present invention.
  • Figure 10 is a schematic view showing the structure of the curved slider and the composite curved slider of the present invention.
  • Figure 11 is a schematic view showing the structure of a curved slider pump of the present invention.
  • Figure 12 is a schematic view showing the structure of a second rotor of the present invention in different forms.
  • Figure 13 is a schematic view showing another internal overall structure of the present invention.
  • Figure 14 is a schematic view showing the structure of the first rotor of Figure 13 of the present invention.
  • Figure 15 is a schematic view showing another second rotor structure of the present invention.
  • Figure 16 is a schematic view showing the second rotor of the four arcuate group portions of the present invention.
  • Fig. 17 is a perspective view showing the arrangement of a fluid outlet and a fluid inlet in the upper and lower wall surfaces of the first rotor of the present invention.
  • Figure 18 is a schematic illustration of the combination of two eccentric movable vane pumps of the present invention.
  • Figure 19 is a schematic view showing the structure of a first rotor of the present invention provided with a controlled valve.
  • Figure 20 is a schematic view showing the structure of the controlled valve of the present invention.
  • Figure 21 is a schematic view showing the structure of the control mechanism slide of the present invention in cooperation with the controlled valve.
  • Figure 22 is a schematic view showing the entire structure of the present invention.
  • Figure 23 is a schematic view showing a second rotor and movable blade connecting structure of the present invention.
  • Figure 24 is a schematic view showing the assembly structure of a first rotor and a controlled valve of the present invention.
  • Figure 25 is a schematic view showing the structure of a track of the composition control mechanism of the present invention.
  • Figure 26 is a schematic view showing the structure of a variable displacement pump with a control shaft of the present invention.
  • Figure 27 is a schematic view showing the overall structure of the present invention as a pusher.
  • Cylinder 1 main shaft 11; bearing 12; eccentric shaft 14; support shaft 114; cylinder cover 15, control shaft 16, isolation ring 17, isolation belt 18, avoidance zone 19;
  • FIG. 1 is an eccentric movable vane pump with four annular groove-shaped slides 45 disposed on the second rotor 4, including the first rotor 2 (refer to FIG. 4), and four The movable blade 21 (see Fig. 2) is combined with a second rotor 4.
  • the second rotor 4 is eccentrically disposed with the first rotor 2, and the second rotor 4 is disposed concentrically with the cylinder 1, the first rotor 2 Or the second rotor 4 is disposed on the main shaft.
  • the lower portion of the outer end portion 23 of the movable vane 21 is in close proximity to the inner wall of the cylinder block 1, and the pusher 26 is provided on the upper portion of the outer end portion 23 of the movable vane 21, and the push rod 26 slides in the chute 45 on the second rotor 4.
  • a position avoidance 27 is left between the push rod 26 and the movable blade 21, and the movable blade outer end portion 23 corresponding to the slide 45 can be provided with elastic means such as a spring spring to reduce the movable blade from slipping.
  • the main shaft can be rotated clockwise or counterclockwise, and can be used for a pressure pump or a power pump.
  • a fluid inlet passage 61 and a fluid outlet passage 62 are provided in the cylinder block 1.
  • the eccentric movable vane pump rotates, the radial and axial rotational speeds of the movable vane 21 periodically change, so that the cavity volume between the adjacent movable vanes 21 periodically changes, corresponding to the inflow and discharge process of the working fluid.
  • the push rod 26 When the slide 45 corresponding to the push rod 26 is a radial slide provided on the second rotor 4, the push rod 26 has a flat structure, and the radial direction of the rotor working push rod 26 in the slide 45
  • the reciprocating motion while the number of the first rotors 2 is plural, corresponds one-to-one with the movable vanes 21, and the second rotor 4 is disposed on the main shaft.
  • FIG. 4 and FIG. 5 four movable blades 21 (see FIG. 5) are disposed in the eccentric movable vane pump, and the inner end portions 22 of the movable vanes 21 are evenly distributed on the outer wall of the first rotor 2 with four circumferences, respectively.
  • the rotor shaft holes 24 are axially connected, and the four different second rotors 4 are axially concentrically arranged.
  • the first rotor 2 is fixed to the main shaft 11.
  • a shaft pin 231 is further provided on the outer end portion 23 of the movable vane 21, and the shaft pin 231 is axially coupled to the rotor shaft hole 44 of the second rotor 4.
  • the movable blade 21 is further provided with a cutout 232 of the other second rotor 4 that is not axially coupled to the movable blade 21.
  • the eccentric movable vane pump When the eccentric movable vane pump is operated, the outer end portion 23 of the movable vane 21 does not correspond to the second rotor 4. The part is close to the inner wall of the cylinder 1.
  • the first rotor 2 and the main shaft 11 are fixedly coupled.
  • the eccentric active vane pump can work clockwise or counterclockwise.
  • a fluid inlet 61 and a fluid outlet 62 are provided in the cylinder.
  • the eccentric movable vane pump is provided with four movable vanes 21 and four second rotors 4, and each of the second rotors 4 is concentrically disposed on the eccentric shaft 14 through the bearing axial direction, and the eccentric shaft 14 and the first rotor 2 eccentrically disposed and fixedly disposed on the cylinder block 1, the first rotor 2 is disposed on the cylinder block 1 by a bearing concentric, and the first rotor 2 is fixed to the main shaft 11.
  • the inner end portions 22 of each of the movable vanes 21 are respectively axially coupled to the rotor shaft holes 24 circumferentially distributed on the first rotor 2, and the outer end portions 23 of each of the movable vanes 21 and the rotors of the four second rotors 4, respectively.
  • the shaft hole 44 is axially connected, and a fluid passage 60 is disposed on the wall surface of the corresponding first rotor 2 between the adjacent movable blades 21, and when the fluid passage 60 is rotated to the position of the fluid inlet 61 and the outlet outlet 62 on the cylinder 1, The fluid is expelled or inhaled.
  • the inner end portion 22 of the movable blade 21 is provided with a shaft pin 231 and a cutout 232. Please refer to FIG. 5.
  • the position of the cylinder 1 corresponding to the space formed by the adjacent movable blade 21 and the cylinder 1 during compression to a small space during operation or the corresponding position of the first rotor 2 is provided with a gas gate device, and the space is compressed to a certain extent.
  • the oil and gas mixture is ignited to a degree that can be used in an internal combustion engine
  • Two identical eccentric movable vane pumps of the present invention are disposed on the same main shaft at 180 degrees to eliminate eccentric vibration. When multiple eccentric movable vane pumps are operated in series, they can be used as multi-stage compression or expansion eccentric movable vane pumps, which can work as a gas turbine by combination.
  • the first rotor 2 has an average of four groups on the upper circumference, and each of the groups is provided with a rotor shaft hole 24 which is respectively axially connected to the inner end portion 22 of the movable blade 21, and the outer end portion 23 of the movable blade 21 is respectively
  • the rotor shaft hole 44 is disposed on the second rotor 4, and four tunnels 25 are respectively disposed on the outer wall of the first rotor 2, and two cylinder covers 15 are disposed on both end faces of the cylinder body 1.
  • the cylinder cover 15 is provided with a composite gas passage 53 which is composed of a fluid inlet 61 and a fluid outlet 62, and the composite gas passage 53 extends through the cylinder 1.
  • the composite gas passage 53 is located in a region where the space between the adjacent two movable blades 21 and the cylinder 1 gradually reaches a maximum volume and coincides with the cylinder cover 15 from a maximum volume.
  • a spark plug is set in the tunnel 25 to ignite and decompress the compressed oil and gas mixture, and the generated high temperature and high pressure gas gradually expands to the composite gas passage 53, and the fresh air is
  • One of the composite gas passages 53 enters, and the high temperature gas in the cylinder is discharged from the other composite gas passage 53.
  • the space between the adjacent movable blades 21 is rotated once a week to complete the work process, which is a two-stroke engine with high compression (ignition)-high expansion-high efficiency replacement gas effect.
  • FIG. 7 and FIG. 6 are basically the same, except that a plurality of gas passages 60 are provided on the first rotor 2, and the opening and closing of the gas passages 60 is controlled by a valve mechanism 55.
  • the valve mechanism 55 opens the gas passage 60 when the space of the adjacent movable vane 21 is in the exhaust and intake state, and the valve train 55 may be electrically controlled or a pulley and a camshaft.
  • This embodiment is a four-stroke engine that performs four processes at a time as an engine.
  • a fixed blade 20 is separately disposed on each of the four second rotors 4 in FIG. 8 , and the volume 56 between adjacent fixed blades 20 periodically changes as the first rotor 2 rotates, thereby
  • a volumetric pump is composed of a fixed blade 20 and a pump body, and the positive displacement pump can also be used in the fields of internal combustion engines, compressors and the like.
  • FIG. 9 includes two movable blades 21 and two second rotors 4 corresponding thereto, and each of the second rotors 4 is connected by a fixed transmission ratio mechanism and two fixed blades 20, respectively.
  • Two blades are symmetrically arranged on the blade, and the fixed transmission ratio mechanism is set as a gear mechanism, and the speed ratio is 1/2.
  • the fixed blade 20 rotates once, so that the fixed blade 20 rotates once, and the rotation speed thereof changes twice, and the rotation of the fixed blade 20 is rotated twice in the pump.
  • the fixed blade 20 rotates one revolution to complete the four processes of the four-stroke engine, and the present embodiment can be used as a conventional pump type as a four-stroke internal combustion engine without a valve structure.
  • FIG. 11 is a schematic view of a water pump provided with four curved slider rotors 34 as the second rotor 4.
  • the inner and outer curved surfaces of the curved slider rotor 34 slide in the slide provided on the cylinder 1.
  • the fluid passage 5 of the cylinder block 1 is set according to the specific position of the space between the adjacent movable vane 21 and the cylinder block.
  • the fluid passage of the cylinder block 1 and the flange connecting portion of the cylinder wall penetrate.
  • the inner wall surface of the cylinder block 1 also has a fluid escape passage.
  • the rotor shaft bore 44 provided in the second rotor 4 in this embodiment is replaced by a connecting shaft 33, i.e., the use of a shaft instead of the shaft bore design is also within the scope of the present invention.
  • FIG. 12 shows various forms of the second rotor 4, one of which is a second rotor 4 fixedly disposed on a partial plane of the end of the connecting shaft 33 with the movable blade 21, and a plurality of second rotors 4 Radially concentrically arranged in turn on the other partial planes of the connecting shaft 33.
  • a shaft hole 44 provided in the group portion of the second rotor 4 is axially coupled to the movable blade 21, and the inner wall surface 31 of the group portion is the same height as the movable blade 21 and coincides with the outer wall surface of the second rotor 4, and the rotor group structure is Higher rotor and moving blade connection strength and sealing results are achieved.
  • FIG. 15 also discloses that the shaft hole disposed on the rotor is also suitable for the protection range of the invention when the shaft hole is changed to the shaft, and the various forms of the connection between the rotor and the movable blade are not explained one by one.
  • a plurality of spaced-apart controlled valves are axially distributed at the fluid passage of the cylinder 1 to increase the working pressure range of the eccentric movable vane pump of the present invention.
  • FIG. 13 is a schematic diagram of an eccentric movable vane pump, FIG.
  • the first rotor cover may be disposed at the upper and lower ends of the first rotor 2, and the first rotor cover may be flush with the first rotor 2 and the upper and lower end faces of the movable blade 21, or may be arranged and movable.
  • the upper and lower end faces of the blade 21 are flush with the cylinder cover fixed to the cylinder block 1.
  • the first rotor 2 is evenly distributed with four fluid passages 60 extending through the outside and four shaft holes rotatably connected to the movable vanes 21.
  • the eccentric shaft 14 is fixed to the cylinder block 1 by a support shaft 114 concentric with the first rotor 2, and the cylinder block 1 is fixed to the frame.
  • the eccentric shaft 14 and the second rotor 4 are concentrically disposed with the first rotor 2 eccentrically.
  • the first rotor 2 is connected to the power input/output shaft, is mounted on the frame through a bearing, or is mounted on the support shaft 114 through a bearing, and the four second rotors 4 are coaxially connected to the eccentric shaft 14 through four bearings in series.
  • the shaft/shaft holes axially connected to the movable vane 21 are respectively rotatably connected to one ends of the four movable vanes 21 on the outer circumferential wall surfaces of the four second rotors 4, respectively.
  • the other ends of the four movable blades are respectively rotatably coupled to the shaft/shaft holes which are respectively disposed on the inner walls of the first rotor 2, respectively.
  • the cylinder fluid inlet 61 and the cylinder fluid outlet 62 provided on the cylinder 1 correspond to a compression region and an expansion region of a volume space between adjacent movable blades 21.
  • both the first rotor 2 and the second rotor 4 are rotated clockwise.
  • the rotational speed of the end portion of the movable vane 21 rotatably coupled to the second rotor 4 is periodically changed while the first rotor 2 is rotated, while the first rotor is The center of the center of the shaft is periodically changed so that the volume between the adjacent movable vanes 21 is also periodically changed to thereby constitute a volumetric pump.
  • the width and position of the cylinder fluid inlet 61 and the cylinder fluid outlet 62 can be adjusted separately when the two control mechanisms 63 are rotated in FIG. 13 to adjust the fluid workload at each revolution of the eccentric movable vane pump.
  • the movable blade 21 and the first rotor 2 and the second rotor 4 may be rotatably connected in a shaft-hole type rigid connection manner or in a flexible connection manner in which a connecting portion is made of a soft material or an elastic material.
  • FIG. 15 is that the second rotor 4 is further provided with a curved group portion, which can improve the connection strength and sealing effect of the second rotor 4 and the movable blade 21.
  • Figure 16 is a plan view showing the cooperation of the four rotors 4 with curved groups in Figure 15 .
  • the upper and lower end faces of the arc group are flush with the cylinder cover or the first rotor cover so that the working fluid cannot flow into the end contact gap generated when the plurality of second rotors 4 are connected in series, and the bearing and the coolant inside the second rotor 4 can also be protected. Or lubricating oil.
  • the adjacent arc-shaped group portions are nested with each other to isolate the outer space and the inner space, and a good sealing effect can be obtained when the elastic sealing body is used.
  • FIG. 17 is a schematic perspective view showing the rotor fluid outlet 59 and the rotor fluid inlet 58 disposed on the upper and lower walls of the first rotor 2, respectively.
  • a spacer ring 17 is also provided between the rotor fluid outlet 59 and the rotor fluid inlet 58 and the spacer ring 17 is disposed on the cylinder block 1.
  • the width and position of the cylinder fluid inlet 58 and the cylinder fluid outlet 59 can be adjusted separately when the two control mechanisms 63 are rotated to adjust the fluid workload at each revolution of the eccentric movable vane pump.
  • An advantage of this embodiment is that the cylinder fluid inlet 61 and the fluid outlet 62 are respectively disposed at the upper and lower portions of the cylinder through the spacers 17, increasing the stroke of the high pressure zone and the low pressure zone while also obtaining a better fluid inlet and fluid outlet. Isolation and sealing effects.
  • FIG. 18 is a combination of two eccentric movable vane pumps.
  • One of the eccentric movable vane pumps is a booster pump that causes the low pressure fluid to enter the eccentric movable vane pump and the pressure is increased, and the other eccentric movable vane pump is decompressed.
  • the pump discharges the high pressure fluid into the eccentric movable vane pump after the pressure is reduced.
  • the fluid is a gas
  • the first rotor of the booster pump and the pressure reducing pump and the eccentric shaft are respectively fixedly connected, and can be used as a turbocharger, a gas turbine, an internal combustion engine or the like.
  • the fluid is a liquid
  • the volume of the pressurized pump and the pressure reducing pump that is adjusted by the control mechanism can be used as a stepless fluid coupling or the like.
  • Figure 19 and Figure 17 are similar, but a rotatable controlled valve 65 on the first rotor 2 is disposed on the rotor fluid inlet 58 and the rotor fluid outlet 59.
  • the controlled valve 65 on the rotor fluid inlet 58 rotates inwardly when the inside of the first rotor 2 is under negative pressure and the controlled valve 65 on the rotor fluid outlet 59 is in the first rotor. 2 When the inside is at a positive pressure, it turns to the outside.
  • the controlled valve on the rotor fluid inlet 58 is rotated outward by the control mechanism 63; and the pressure inside the first rotor 2 is close to The controlled valve on the rotor fluid outlet 59 when the low pressure end of the pressure reducing pump is pressurized is rotated inward by the control mechanism 63.
  • the controlled valve 65 is controlled by one of a fluid pressure difference, a centrifugal force, a power, a magnetic force, an elastic force, or a combined force of two or more.
  • FIG. 20 is a schematic structural view of the controlled valve 65 and the control mechanism 63 in the embodiment of FIG. 5, wherein the controlled valve 65 can be controlled by the position control mechanism.
  • Figure 21 is a schematic illustration of a position control mechanism that cooperates with a controlled valve 65.
  • the controlled valve 65 can also be a radial slide switch.
  • the elastic valve can also be provided on the controlled valve 65 so that the sliding friction portion is worn out without affecting the actual work.
  • the control mechanism can also use electromagnetic force when acting on the controlled valve 65.
  • the pressure reducing pump can greatly reduce the leakage loss and the sealing friction loss at the high and low pressure ends, thereby greatly reducing the machining accuracy of the components.
  • the occurrence of whistling and surge can also be avoided when the fluid is a gas.
  • the booster pump and the decompression pump constitute the internal combustion engine, the combustor oil and gas control technology, the combustion technology including the duty flame, the exhaust gas catalytic purification technology, the manifold oxygen-enriched catalytic technology, etc. can obtain lower exhaust gas emissions, and higher Fuel efficiency.
  • FIG. 22 is substantially the same as FIG. 13 and is a schematic structural view including the fluid passage of the cylinder block 1 and the cylinder block.
  • Figure 23 is a schematic view showing the assembly structure of the second rotor 4 and the movable vane of Figure 22;
  • FIG. 24 is a schematic structural view of the first rotor 2 and the valve 65 with a cam push rod.
  • a cam follower 656 is provided on the valve 65.
  • Four rotor flow passages 60 are evenly distributed on the first rotor 2, and each rotor fluid passage 60 is correspondingly provided with a valve 65, which is controlled by a cam mechanism 655.
  • the cam mechanism 655 is constituted by a cam follower 656 and a cam 657 that opens or closes the valve 65 as the action surface of the cam 657 changes.
  • the track mechanism 101 has two tracks of different diameters, and two tracks of different diameters are connected by the intersecting track 102 to form a closed circuit, that is, a rotor or a slider that acts on the track mechanism 101 and controls the opening or closing of the valve 65 in one of the tracks. After passing through the cross track 102, it can only enter another track, corresponding to the action state in which the valve 65 is opened to close or closed to open.
  • a mechanism such as a guide groove or a guide or an elastic mechanism may be provided on the cross rail 102 to assist in limiting the rail changing action of the slider or the rotor on the rail mechanism 101.
  • the rail mechanism 101 is provided with a rotating mechanism 111.
  • the rotating mechanism 111 can rotate the rail mechanism 101.
  • the relative positional relationship between the rail mechanism 101 and the first rotor 2 and the valve 65 changes, corresponding to the valve.
  • the start position of the open state of 65, the start position of the end position and the closed state, and the end position change, so that the intake air amount, the compression ratio, and the expansion ratio can be changed.
  • FIG. 26 is a schematic structural view of a variable displacement pump with a control shaft 75 added thereto.
  • the spacer 18 separates the high and low pressure regions of the cylinder, and the cutout 19 communicates with the corresponding cylinder fluid inlet 61 or cylinder fluid outlet 62.
  • the control shaft 75 and the eccentric shaft 14 and the first rotor 2 are both eccentrically disposed and rotatably disposed on the cylinder block 1, and their rotation is controlled by a control mechanism.
  • the control mechanism can be stepper motor control or stepper motor wire rod linkage control and other control mechanism control.
  • the adjustment mechanism of the control shaft 75 can also be added to change the position of the control shaft 75 to obtain a better working effect of the eccentric movable vane pump. This embodiment can be used as a stepless fluid coupling and a stepless hydraulic transmission application.
  • FIG. 27 is a schematic structural view of the eccentric movable vane pump as a propeller according to the present invention.
  • the first rotor 2 is disposed on the cylinder block 1
  • the second rotor 4 is disposed on the eccentric shaft 14
  • the movable vane 21 and the first rotor and the second rotor are both rotated clockwise, and the fluid inlet 61 is located adjacent to the activity.
  • the corresponding fluid outlet 62 is located between the adjacent movable blades 21, the space is in the compression phase and the space volume is larger.
  • the fluid passage 60 of the first rotor 2 is maximized, the first rotor 2 is an upper and lower two-piece disc-like structure, and the first rotor 2 has no intermediate annular structure.
  • the flow direction of the fluid in the working state and the action direction of the movable blade 21 generating the thrust are high, and the frontal resistance during the passage of the fluid through the propeller is very small, so that high-efficiency and high-application conditions can be obtained.
  • Propeller. Can be applied to aircraft, nautical vessels, submarines and other facilities.
  • the structure of this embodiment can also be used as a wind engine and a hydraulic engine.

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Abstract

一种偏心活动叶片泵，包括缸体（1），第一转子（2），第二转子（4）和活动叶片（21），第一转子（2）与第二转子（4）偏心设置，活动叶片（21）的数量大于等于2个，第一转子（2）与活动叶片（21）的一端转动连接，另一端与第二转子（4）转动连接；第一转子（2）设置在主轴（11）上；在缸体（1）上对应于相邻的活动叶片（21）之间空间的膨胀区域及压缩区域分别设置有流体入口（61）和流体出口（62）。所述泵具有结构简单、效率高、成本低、多工况、稳定性高和寿命长的优点，且无需弹性装置密封也能在高速及超高速范围内工作，工作时径向冲击小。

Description

偏心活动叶片泵
技术领域
本发明涉及一种偏心活动叶片泵，尤其是一种可变容积式偏心活动叶片泵，可用于真空泵，压缩机泵，水泵，汽车涡轮增压器，燃机内燃机，风机，水力发动机，蒸汽透平泵,推进器及无级液力耦合器等领域。
背景技术
现在可变容积泵主要为活塞泵和滑片泵，它们都采用了摩擦密封的原理，所以导致摩擦片容易磨损，密封效果不佳，工作寿命及效率都不高，但，加工精度要求高。摩擦片处于高速工作时由于弹簧弹性弹力，频率，工作流体压力，压差等工况影响，会导致设备产生效率有很大波动，故工作范围窄，不能用于高速，高压，大流量等高要求工况下使用，同时该类型可变容积泵的有效容积率低。
离心泵是靠叶轮带动液体工质高速回转，而把机械能传递给所输送的液体工质；容积泵是靠工作部件的运动造成工作容积周期性地增大和缩小而吸排液体，并靠工作部件的挤压而直接使液体的压力能增加；喷射泵是靠工作流体产生的高速射流引射液体，然后再通过动量交换而使被引流液体的能量增加。
离心泵和喷射泵都是流速型开式能量交换，容积泵则是容量型闭式能量交换。在同等功率密度比的条件下，从工作方式来看三种机械的能量利用率，容积泵的能量利用率应该最高，其次是离心泵，再次是喷射泵。
泵工作的能量利用率取决于机械能量传导损耗，工质液体摩擦损耗，工质液体泄漏等因素。目前高效率泵的材料昂贵，结构极其复杂和体积庞大。
传统容积泵（柱塞泵，气动隔膜泵）则是通过曲柄连杆结构使活塞式工作容积发生变化，容积泵可通过机械零部件之间的间隙尺寸和添加密封件方式有效解决工质液体泄漏问题，最优化的容积泵泵效率设计可以达到90%以上。但由于传统容积泵的曲柄连杆滑块结构的局限性，相对离心泵而言，容积泵实现宽范围扬程和宽范围流量的工作效率与离心泵实现高效率代价一样，需要昂贵的材料，极其复杂机械结构和庞大的机械体积。
发明内容
本发明的偏心活动叶片泵即可轻易控制工质泄漏，又能像离心泵那样实现宽范围扬程和宽范围流量的工作效率，并且具有较高的机械功率密度比，并且结构简单，高效率，低成本，多工况，高稳定性，长寿命，可无需的弹性装置密封也可在高速及超高速范围内工作，且工作时径向冲击小。可用于真空泵，压缩机泵，水泵，汽车涡轮增压器，燃机内燃机，风机，水力发动机，蒸汽透平泵，推进器及无级液力耦合器等领域。
本发明的技术方案是：提供一种偏心活动叶片泵，包括缸体，第一转子，第二转子和活动叶片，第一转子与第二转子偏心设置，所述的第一转子与活动叶片其中一端可转动连接，所述第二转子与所述的活动叶片一一对应，且数量大于等于2个；所述的活动叶片的另一端与第二转子可转动连接；第一转子设置在主轴上；在缸体上对应于相邻的活动叶片之间空间的膨胀区域及压缩区域分别设置有流体入口和流体出口。
　　作为对本发明的改进，在第二转子上还分别设置有固定叶片，相邻的固定叶片之间的空间体积发生周期性压缩和膨胀变化，从而固定叶片和缸体部件构成容积泵。
　　作为对本发明的改进，每一个固定叶片与其对应连接的第二转子通过定传动比机构连接，这样所述的固定叶片由旋转一周其旋转速度发生一次快慢转换的变化，变为固定叶片旋转一周其旋转速度发生多次快慢转换的周期变化，从而固定叶片在缸体内旋转一周发生多次压缩和膨胀过程，由此固定叶片旋转一周完成气体四冲程做功过程。
　　作为对本发明的改进，相邻的活动叶片与缸体之间的空间在旋转工作过程中，在该空间接近最大体积及由最大体积逐渐变小的过程中，在该空间对应的缸体上设置有复合气体通道，该复合气体通道由流体出口和流体入口共同构成，用于二冲程发动机。
　　作为对本发明的改进，相邻的固定叶片与缸体之间的空间在旋转工作过程中，在该空间接近最大体积及由最大体积逐渐变小的过程中，在该空间对应的缸体上设置有复合气体通道，该复合气体通道由流体出口和流体入口共同构成，用于二冲程发动机。
　　作为对本发明的改进，相邻活动叶片的空间在旋转过程中，该空间体积膨胀区域及体积压缩区域对应的缸体上设置有气门机构，该气门机构在该空间内气体处于压缩和膨胀时关闭而该空间处于进气和排气时打开，用于四冲程发动机。
　　作为对本发明的改进，所述的活动叶片的两侧面为曲面，其中一个侧面与第一转子壁面重合，另一个侧面与第二转子壁面重合。
　　作为对本发明的改进，活动叶片与第一转子和第二转子可转动连接方式为轴孔式连接方式或柔式连接方式。
　　作为对本发明的改进，当第二转子的数量大于等于2时，在第二转子上还设置有弧形群部，对应于相邻活动叶片转动连接的第二转子上的弧形群部相互嵌套，所述的相邻活动叶片之间的容积空间通过相互嵌套的弧形群部与相邻的第二转子之间的间隙隔离。
　　作为对本发明的改进，在第一转子上对应于相邻活动叶片之间的环形壁面的上下部分分别设置转子流体入口和转子流体出口；缸体流体入口和缸体流体出口与转子流体入口和转子流体出口对应设置在缸体的上下部分；当转子流体入口和缸体流体入口贯通时或转子流体出口和缸体流体出口时流体进入或排出相邻活动叶片之间的容积空间。
　　作为对本发明的改进，所述的转子流体入口和所述的转子流体出口上设置有受控阀门，受控阀门由流体压力差，离心力，动力，磁力，弹性作用力中的一种力或两种以上的合力控制。
　　作为对本发明的改进，低压流体通过缸体流体入口进入容积空间，低压流体在容积空间内增压后通过缸体流体出口排出构成增压泵；高压流体通过缸体流体入口进入容积空间，高压流体在容积空间内释放压力后通过缸体流体出口排出构成减压泵；或者低压流体通过转子流体入口进入容积空间，低压流体在容积空间内增压后通过转子流体出口排出构成了增压泵；高压流体通过转子流体入口进入容积空间，高压流体在容积空间内释放压力后通过转子流体出口排出构成了减压泵。
作为对本发明的改进，在缸体上还设置有控制机构，控制机构改变与缸体流体入口和缸体流体出口的位置关系进而调整缸体流体入口和缸体流体出口的形状与尺寸面积；或者控制机构可改变受控阀门开关条件如受控阀门的开关起始位置，由此改变偏心活动叶片泵每旋转一周流体进入容积空间或由容积空间排出的体积。
　　作为对本发明的改进，当流体为液体时，设置有2个偏心活动叶片泵，其中一个为增压泵另一个为减压泵，流体先后流经增压泵和减压泵，在控制机构的作用下改变增压泵和减压泵每旋转一周流体进入增压泵和减压泵的体积，从而改变增压泵和减压泵的速度差可作为液力变矩器，无级变速器使用，当流体为气体时，设置有1个增压泵和1个减压泵和热交换室，且增压泵和减压泵同轴心固定连接，流体先后流经增压泵，热交换室和减压泵，可作为涡轮增压机，内燃机，燃气轮机，外燃机使用。
　　作为对本发明的改进，在第一转子上对应于相邻活动叶片之间的环形壁面上设置转子流体通道。
　　作为对本发明的改进，所述的转子流体通道上设置有阀门，阀门由流体压力差，离心力，动力，磁力，弹性作用力中的一种力或两种以上合力控制。
作为对本发明的改进，轨道机构由2个直径不等的环形导轨组成，2个环形导轨之间通过交叉轨道连接成一个闭合回路。其中设置在阀门上的转子或滑块作用在轨道机构上，当所述的转子或滑块作用在轨道机构的不同直径的轨道上时对应于阀门的开启或者闭合状态。
作为对本发明的改进，设置有可转动轨道机构的旋转机构，轨道机构转动时可改变轨道机构与第一转子之间的相对位置关系。
　　作为对本发明的改进，所述的偏心轴位于缸体的位置由偏心轴控制机构控制，偏心轴控制机构可改变偏心轴位于缸体上的位置从而改变第一转子和第二转子之间的偏心距。
　　作为对本发明的改进，所述的偏心轴控制机构由控制轴组成，控制轴偏心设置在偏心轴上且与第一转子偏心设置，控制轴可转动的设置在缸体上。
　　作为对本发明的改进，所述的缸体流体入口主要区域位于相邻的活动叶片之间空间处于膨胀阶段且该空间体积处于较大状态时对应缸体的区域。
　　作为对本发明的改进，所述的缸体流体出口主要区域位于相邻的活动叶片之间空间处于压缩阶段且该空间体积处于较大状态时对应缸体的区域。
本发明还提供一种偏心活动叶片泵，包括缸体，第一转子，第二转子和活动叶片，第一转子与第二转子偏心设置，所述第一转子与活动叶片其中一端可转动连接，活动叶片另一端上设有推杆，所述推杆在所述的第二转子上设置的滑道内滑动；所述的活动叶片数量大于等于2个；在缸体上对应于相邻的活动叶片之间空间的膨胀区域及压缩区域分别设置有流体入口和流体出口。
　　作为对本发明的改进，在第二转子上还分别设置有固定叶片，相邻的固定叶片之间的空间体积发生周期性压缩和膨胀变化，从而固定叶片和缸体部件构成容积泵。
本发明具有结构简单，高效率，低成本，多工况，高稳定性，长寿命的优点，可无需的弹性装置密封也可在高速及超高速范围内工作，且工作时径向冲击小。可用于真空泵，压缩机泵，水泵，汽车涡轮增压器，燃机内燃机，风机，水力发动机，蒸汽透平泵，推进器及无级液力耦合器等领域。
附图说明
图1是本发明的第二转子带滑道示意图。
图2是图1中活动叶片结构示意图。
图3是本发明的第二转子数量为4个时结构示意图。
图4是本发明的另一种形式的第二转子数量为4个时结构示意图。
图5是本发明的图4中活动叶片具体结构示意图。
图6是本发明的二冲程发动机结构示意图。
图7是本发明的带有气门机构的四冲程发动机示意图。
图8是本发明的带有固定叶片的容积泵内部结构示意图。
图9是本发明的带有定传动比机构的发动机示意图。
图10是本发明的弧形滑块及复合弧形滑块结构示意图。
图11是本发明的弧形滑块泵结构示意图。
图12是本发明的第二转子不同形式的结构示意图。
图13是本发明的另一种内部整体结构示意图。
图14是本发明的图13中的第一转子结构示意图。
图15是本发明的另一种第二转子结构示意图。
图16是本发明的4个带弧形群部的第二转子配合示意图。
图17是本发明的第一转子上下壁面分别设置有流体出口和流体入口的立体结构示意图。
图18是本发明的两个偏心活动叶片泵的组合示意图。
图19是本发明的第一转子设置有受控阀门的结构示意图。
图20是本发明的受控阀门的一种结构示意图。
图21是本发明的与受控阀门配合工作的控制机构滑道的结构示意图。
图22是本发明的一种整体结构示意图。
图23是本发明的一种第二转子和活动叶片连接结构示意图。
图24是本发明的一种第一转子与受控阀门装配结构示意图。
图25是本发明的组成控制机构的轨道结构示意图。
图26是本发明的带有控制轴的可变容积泵的结构示意图。
图27是本发明作为推进器时的整体结构示意图。
具体实施方式
图例说明：
缸体1；主轴11；轴承12；偏心轴14；支撑轴114；缸体盖15；控制轴16；隔离圈17；隔离带18；避空区19；
第一转子2；固定叶片20；活动叶片21；活动叶片内端部22；活动叶片外端部23；轴销231；避空232；转子轴孔24；坑道25；活动叶片推杆26；活动叶片避空27；
连接轴33；弧形滑块转子34；最大空间35；最小空间36；
第二转子4；第二转子的滑道45；
复合气体通道53；气门机构55；转子流体入口58；转子流体出口59；
转子流体通道60；缸体流体入口61；缸体流体出口62；控制机构63；受控阀门65；
控制轴75；
轨道机构101；交叉轨道102；
实施例1
请参见图1和图2，图1是一种在第二转子4上间隔设置有4个环槽形滑道45的偏心活动叶片泵，包含有第一转子2（参考图4），4个活动叶片21（请见图2）与一个第二转子4。第二转子4与第一转子2偏心设置，第二转子4与缸体1同轴心设置，第一转子2 或第二转子4设置在主轴上。活动叶片21的外端部23下部与缸体1内壁贴近，活动叶片21的外端部23上部设置有推杆26，推杆26在第二转子4上的滑道45内滑动。且在推杆26和活动叶片21之间留有与第二转子4的位置避空27，滑道45对应的活动叶片外端部23可设置有弹性装置如弹簧弹片等以降低活动叶片在滑道45中移动的冲击力和振动。在本实施例中，主轴即可顺时针旋转工作也可逆时针旋转工作，可用于压力泵也可用于动力泵。在缸体1上设置有流体入口通道61及流体出口通道62。当偏心活动叶片泵旋转时，活动叶片21的径向及轴向旋转速度发生周期性变化，从而使相邻活动叶片21之间的空腔容积发生周期性变化，对应工质流入和排出过程。
当与推杆26对应作用的滑道45为设置在第二转子4上的径向滑道时，推杆26则为平板状结构，随着转子工作推杆26在滑道45内做径向往复运动，同时第一转子2数量为多个，与活动叶片21一一对应，第二转子4设置在主轴上。
实施例2
请参见图4和图5，偏心活动叶片泵内设置有4个活动叶片21(请见图5），活动叶片21内端部22分别与4个圆周平均分布在第一转子2的外壁上的转子轴孔24轴接，4个不同的第二转子4之间轴向同心排列。第一转子2固定在主轴11上。在活动叶片21外端部23上还设置有轴销231，轴销231与第二转子4的转子轴孔44轴接。活动叶片21上还设置有与不和该活动叶片21轴接的其它第二转子4的避空232，在偏心活动叶片泵工作时，活动叶片21外端部23未对应有第二转子4的部分和缸体1内壁贴近。在本实施例中，第一转子2和主轴11固定连接。偏心活动叶片泵可顺时针或逆时针工作。在缸体上设置有流体入口61及流体出口62。
实施例3
请参见图3，偏心活动叶片泵内设置有4个活动叶片21和4个第二转子4，每个第二转子4通过轴承轴向同心设置在偏心轴14上，偏心轴14与第一转子2偏心设置且固定设置在缸体1上，第一转子2通过轴承同轴心设置在缸体1上，第一转子2固定在主轴11上。每一个活动叶片21内端部22分别与圆周平均分布设置在第一转子2上的转子轴孔24轴接，每一个活动叶片21的外端部23分别与4个第二转子4上的转子轴孔44轴接，在相邻的活动叶片21之间对应的第一转子2壁面上设置有流体通道60，当流体通道60旋转至缸体1上的流体入口61及流通出口62位置时，流体被排出或吸入。本实施例中活动叶片21内端部22设置有轴销231及避空232，请参考图5。
在相邻活动叶片21与缸体1形成的空间在工作过程中处于压缩至较小空间时对应的缸体1位置或在第一转子2对应位置设置有油气门装置，在该空间压缩至一定程度时点燃油气混合物从而可用于内燃机。2个相同的本发明偏心活动叶片泵以180度设置在同一主轴上以消除偏心震动。多个偏心活动叶片泵串联工作时可作为多级压缩或膨胀偏心活动叶片泵，通过组合可作为燃气轮机工作。
实施例4
请参见图6，第一转子2上圆周平均分布有4个群部，每一群部上设置有转子轴孔24分别与活动叶片21内端部22轴接，活动叶片21外端部23又分别与设置在第二转子4上的转子轴孔44轴接，在第一转子2外壁上还分别设置有4个坑道25，在缸体1两个端面上设置有两个缸体盖15，在缸体盖15上设置有复合气体通道53，复合气体通道53由流体入口61和流体出口62共同构成，复合气体通道53贯穿缸体1。该复合气体通道53位于相邻的两个活动叶片21与缸体1之间的空间逐渐达到最大体积及由最大体积逐渐变小时与缸体盖15重合的区域。在本实施例中，所述的该空间气体被逐渐压缩至最小体积时在坑道25内设置火花塞点火引爆被压缩的油气混合物，产生的高温高压气体逐渐膨胀至复合气体通道53处，新鲜空气由其中一个复合气体通道53进入，而缸体内高温气体由另一个复合气体通道53排出。这样就完成了新鲜空气或油气混合物进气过程及燃烧后气体的排气过程，随着活动叶片21继续旋转该空间气体进入压缩环节。本实施例中相邻活动叶片21之间空间旋转一周完成一次做功过程，是一种二冲程发动机，具备有高压缩（点火）-高膨胀-高效置换气效果。
实施例5
请参见图7，图7和图6结构基本一样，不同的是在第一转子2上设置有多个气体通道60，气体通道60的开闭由一个气门机构55控制。当相邻活动叶片21的空间处于排气及进气状态时气门机构55打开气体通道60，气门机构55可以是电控或皮带轮与凸轮轴方式组成。本实施例作为发动机时做功一次完成4个过程，是一种四冲程发动机。
实施例6
请参见图8，图8中4个第二转子4上分别单独设置有一个固定叶片20，随着第一转子2的转动，相邻固定叶片20之间的容积空间56发生周期性变化，从而由固定叶片20及泵体等构件组成一种容积泵，该容积泵同样可用于内燃机，压缩机等领域。
实施例7
请参见图9，图9中包含有2个活动叶片21及与之对应的2个第二转子4，每个第二转子4分别通过定传动比机构和2个固定叶片20连接，每个固定叶片上对称设置有2个扇叶，定传动比机构设定为齿轮机构，速比为1/2。当第二转子每转2圈时固定叶片20旋转了1圈，这样使得固定叶片20旋转一周其旋转速度发生2次快慢转换的周期变化，对应与固定叶片20在泵内旋转一周经过2次压缩和2次膨胀过程，固定叶片20旋转一周完成四冲程发动机的4个过程，本实施例作为四冲程内燃机时可无需气门结构也可作为常规泵类应用。
实施例8
请参见图10，图11。图10为转子的多种结构形式，一种是完整环形转子和弧形转子的复合结构，另一种是弧形转子固定在弧形转子与活动叶片21的连接轴33端面上。图11中设置有4个弧形滑块转子34作为第二转子4的水泵示意图。弧形滑块转子34内外弧面和设置在缸体1上的滑道内滑动。本实施例中缸体1上的流体通道5根据相邻活动叶片21也缸体之间的空间压缩的具体位置设定，本实施例中缸体1流体通道与法兰连接部分缸壁贯通，同时缸体1的内壁面还具有流体避空通道。在本实施例中设置在第二转子4上的转子轴孔44用连接轴33取代作用，即采用轴代替轴孔设计同样在本发明的保护范畴内。
请参见图12，图12为第二转子4的多种形式，其中一种为第二转子4固定设置在与活动叶片21的连接轴33的端部的部分平面上，多个第二转子4依次径向同心设置在连接轴33的其他部分平面上。这种方式可获得较低成本且具有较好密封效果。一种为第二转子4群部上设置的轴孔44与活动叶片21轴接，群部的内壁面31与活动叶片21高度相同且与第二转子4外壁面重合，这种转子群部结构可获得更高的转子与活动叶片连接强度及密封效果。同时图15也同样揭示了设置在转子上的轴孔变更为轴时同样适用于发明保护范围，同时未就转子和活动叶片之间的连接有多种形式逐一说明。
在缸体1流体通道处轴向分布多个隔开受控阀门，可增加本发明偏心活动叶片泵的工作压力使用范围。
实施例9
请参见图13和图14，图13是一种偏心活动叶片泵示意图，图14 为图13中第一转子2的具体结构图，在第一转子2的上下端部可设置有与第一转子2一同旋转和活动叶片21上下端面齐平第一转子盖，或设置有和活动叶片21上下端面齐平的固定在缸体1上的缸体盖。在第一转子2上平均分布设置有4个贯通外部的流体通道60和4个与活动叶片21转动连接的轴孔。在图13中，偏心轴14通过与第一转子2同轴心的支撑轴114固定在缸体1上，缸体1固定在机架上。偏心轴14和第二转子4同轴心和第一转子2偏心设置。第一转子2和动力输入输出轴连接，通过轴承安装在机架上，也可通过轴承安装在支撑轴114上，4个第二转子4依次同轴心通过4个轴承串联安装在偏心轴14上，4个第二转子4的外圆壁面上分别设置有和活动叶片21轴接的轴/轴孔与4个活动叶片21的一端分别转动连接。4个活动叶片的另一端分别和平均分别设置在第一转子2内壁上的轴/轴孔转动连接。在缸体1上设置的缸体流体入口61和缸体流体出口62对应相邻活动叶片21之间的容积空间的压缩区域及膨胀区域。在本实施例中第一转子2和第二转子4都朝顺时针旋转。由于第二转子4和第一转子2为偏心设置，所以在第一转子2旋转时使和第二转子4转动连接的活动叶片21的端部的旋转速度发生周期性变化，同时以第一转子2中心为轴心的径向位置发生周期性变化，从而使相邻活动叶片21之间的容积空间也发生周期性变化由此构成容积泵。
在图13中如设置有2个控制机构63旋转时可分别调整缸体流体入口61和缸体流体出口62的宽度及位置以调整偏心活动叶片泵每一转时的流体工作量
在本发明中活动叶片21和第一转子2及第二转子4转动连接方式可以是轴孔式刚性连接方式也可以是在连接部分采用软材料或弹性材料的柔性连接方式。
实施例10
请参见图15和图16，图15是在第二转子4上还设置有弧形群部，弧形群部可提高第二转子4和活动叶片21的连接强度及密封效果。图16为图15中4个带弧形群部的第二转子4配合工作的平面示意图。弧形群部的上下端面和缸体盖或第一转子盖齐平使工作流体不能流入多个第二转子4串联时产生的端面接触间隙，也可保护第二转子4内部的轴承及冷却液或润滑油。如图4所述，相邻的弧形群部相互嵌套使全部外侧的空间和内侧空间隔离，当采用弹性密封体时能获得很好密封效果。
实施例11
　　请参见图17，图17是在第一转子2的上下壁面分别设置有转子流体出口59和转子流体入口58的立体结构示意图。在转子流体出口59和转子流体入口58之间还设置有隔离圈17，隔离圈17设置在缸体1上。2个控制机构63旋转时可分别调整缸体流体入口58和缸体流体出口59的宽度及位置以调整偏心活动叶片泵每一转时的流体工作量。本实施例的优点是使缸体流体入口61和流体出口62通过隔离圈17分别设置在缸体的上下部分，增加了高压区和低压区的行程同时也可获得更好的流体入口与流体出口的隔离和密封效果。
实施例12
　　请参见图18，图18为2个偏心活动叶片泵的组合，其中一个偏心活动叶片泵为增压泵使低压流体进入偏心活动叶片泵后压力增加后排出，另一个偏心活动叶片泵为减压泵使高压流体进入偏心活动叶片泵后压力降低后排出。当流体为气体时增压泵和减压泵的第一转子和偏心轴都分别固定连接，可作为涡轮增压器，燃气轮机，内燃机等用途。当流体为液体使通过控制机构调整流体的进入增压泵和减压泵的体积可作为无级液力耦合器等用途。
实施例13
　　请参见图19，图19和图17类似，但是在转子流体入口58和转子流体出口59上设置有位于第一转子2上的可转动受控阀门65。如图19所示，作为增压泵时，转子流体入口58上的受控阀门65在第一转子2内侧处于负压时朝内侧转动而转子流体出口59上的受控阀门65在第一转子2内侧处于正压时朝外侧转动。作为减压泵时，在该受控阀65对应的容积空间由最小体积逐渐增加时，转子流体入口58上的受控阀门被控制机构63作用下朝外侧转动；而第一转子2内侧压力接近减压泵低压端压力时转子流体出口59上的受控阀门被控制机构63作用下朝内侧转动。受控阀门65由流体压力差，离心力，动力，磁力，弹性作用力中的一种力或两种以上的合力控制。
实施例14
　　请参见图20，图21，图20是图实施例5中受控阀门65与控制机构63通过凸轮方式作用情况下的一种结构示意图，该结构下受控阀门65可被位置控制机构受控转动；图21是与受控阀门65配合工作的位置控制机构的一种示意图。当改变控制机构63的滑道曲线变化时即可改变受控阀门65的开关位置从而调整实际工作流体的体积。
　　受控阀门65也可是径向滑动开关方式。在受控阀门65上还可设置有弹性补偿装置使的滑动摩擦部分出现损耗时也不影响实际工作。控制机构对受控阀门65作用时还可采用电磁力方式。在本实施例中尤其是减压泵在采用了受控阀门65的应用中可极大的降低高低压端的泄漏损失和密封摩擦损失，极大的降低了零部件的加工精度。在流体为气体情况下还可避免啸气和喘振的发生。当增压泵和减压泵组成内燃机作用时，配合燃烧室油气控制技术，值班火焰在内的燃烧技术，尾气催化净化技术，歧管富氧催化技术等可获得更低尾气排放，更高的燃油效率。
实施例15
　　请参见图22，图22和图13基本一样，为含增加了缸体1及缸体流体通道的结构示意图。图23是图22的第二转子4和活动叶片装配结构示意图。请参见图24，图24为第一转子2及带凸轮推杆的阀门65的结构示意图。在阀门65上设置有凸轮推杆656。在第一转子2上平均分布有4个转子流通通道60，每个转子流体通道60对应设置有阀门65，阀门65由凸轮机构655控制。在本实施例中，凸轮机构655由凸轮推杆656和凸轮657构成，凸轮推杆656随着凸轮657作用面的变化而开启或关闭阀门65。
　　图25为轨道机构101结构示意图。轨道机构101具有2个不同直径的轨道，2个不同直径的轨道通过交叉轨道102连接形成一个封闭的回路，即与轨道机构101作用且控制阀门65开启或闭合的转子或滑块处于其中一个轨道经过交叉轨道102后只能进入另一个轨道，对应于阀门65开启至闭合或闭合至开启的动作状态。交叉轨道102上还可设置有导槽或导道或弹性机构等机构以辅助限制在轨道机构101上的滑块或转子的换轨动作。当滑块或转子处于轨道机构101的其中一个轨道时对应受控阀门65的开启状态，而当滑块或转子处于轨道机构101的其中另一个轨道时对应阀门65的关闭状态，而当滑块或转子处于交叉轨道102时对应阀门65的由开启至关闭或由关闭至开启的状态。本实施例做为四冲程发动机使用。其中轨道机构101中2种轨道使受控阀门65得开启和关闭对应发动机的压缩和膨胀状态。
　　在轨道机构101上设置有旋转机构111，旋转机构111可转动轨道机构101，当旋转机构111动作时，轨道机构101与第一转子2及阀门65之间的相对位置关系发生改变，对应于阀门65的开启状态的起始位置，结束位置及闭合状态的起始位置，结束位置改变，从而可改变进气量，压缩比及膨胀比。
实施例16
　　请参见图26，图26为增加了控制轴75的可变容积泵结构示意图。图26中隔离带18隔离缸体高低压区域，避空区19和对应的缸体流体入口61或缸体流体出口62连通。控制轴75与偏心轴14及第一转子2都为偏心设置，且可转动的设置在缸体1上，由控制机构控制其转动。控制机构可以是步进电机控制或者步进电机加丝杆连杆机构控制及其他控制机构控制。随着控制轴75转动偏心轴14和第一转子2之间的轴心距发生变化从而使得相邻活动叶片之间的最大空间25和最小空间26的差值发生变化从而改变容积泵每转时实际工作流体体积。本实施例中还可增加控制轴75的调整机构以改变控制轴75的位置从而获得偏心活动叶片泵更佳的工作效果。本实施例可作为无级液力偶合器及无级液力变速器应用。
实施例17
　　请参见图27，图27为本发明偏心活动叶片泵作为推进器时结构示意图。图中第一转子2设置在缸体1上，第二转子4设置在偏心轴14上，活动叶片21及第一转子和第二转子都朝顺时针方向旋转，流体入口61位于相邻的活动叶片21之间空间处于膨胀阶段且该空间体积处于较大状态时的对应缸体1的区域，对应的流体出口62位于相邻的活动叶片21之间空间处于压缩阶段且该空间体积处于较大状态时的对应缸体1的区域。本实施例中第一转子2的流体通道60最大化，第一转子2为上下2片式圆片状结构且第一转子2无中间环形结构体。本实施例中推进器在工作状态下流体的流动方向和产生推力的活动叶片21的作用方向重合度高，且在流体通过推进器的过程中的正面阻力非常小从而可以获得高效高应用工况的推进器。可以应用在飞行器，航海船舶，潜艇等设施上。本实施例结构也可以作为风力发动机和水力发动机使用。

Claims (1)

1. 一种偏心活动叶片泵，包括缸体（1），第一转子（2），第二转子（4）和活动叶片（21），其特征在于，第一转子（2）与第二转子（4）偏心设置，所述的第一转子（2）与活动叶片（21）其中一端可转动连接，所述第二转子（4）与所述的活动叶片（21）一一对应，且数量大于等于2个；所述的活动叶片（21）的另一端与第二转子（4）可转动连接；第一转子（2）设置在主轴（11）上；在缸体（1）上对应于相邻的活动叶片（21）之间空间的膨胀区域及压缩区域分别设置有流体入口（61）和流体出口（62）。
　　2. 根据权利要求1所述的偏心活动叶片泵，其特征在于，在第二转子（4）上还分别设置有固定叶片（20），相邻的固定叶片（20）之间的空间体积发生周期性压缩和膨胀变化，从而固定叶片（20）和缸体（1）部件构成容积泵。
　　3. 根据权利要求2所述的偏心活动叶片泵，其特征在于，每一个固定叶片（20）与其对应连接的第二转子（4）通过定传动比机构连接，这样所述的固定叶片（20）由旋转一周其旋转速度发生一次快慢转换的变化，变为固定叶片（20）旋转一周其旋转速度发生多次快慢转换的周期变化，从而固定叶片（20）在缸体内旋转一周发生多次压缩和膨胀过程，由此固定叶片（20）旋转一周完成气体四冲程做功过程。
　　4. 根据权利要求1所述的偏心活动叶片泵，其特征在于，相邻的活动叶片（21）与缸体（1）之间的空间在旋转工作过程中，在该空间接近最大体积及由最大体积逐渐变小的过程中，在该空间对应的缸体（1）上设置有复合气体通道（53），该复合气体通道（53）由流体出口（62）和流体入口（61）共同构成，用于二冲程发动机。
　　5. 根据权利要求1或2所述的偏心活动叶片泵，其特征在于，相邻活动叶片（21）的空间在旋转过程中，该空间体积膨胀区域及体积压缩区域对应的缸体（1）上设置有气门机构（55），该气门机构在该空间内气体处于压缩和膨胀时关闭而该空间处于进气和排气时打开，用于四冲程发动机。
　　6. 根据权利要求1所述的偏心活动叶片泵，其特征在于，所述的活动叶片（21）的两侧面为曲面，其中一个侧面与第一转子（2）壁面重合，另一个侧面与第二转子（4）壁面重合。
　　7. 根据权利要求1所述的偏心活动叶片泵，其特征在于，活动叶片（21）与第一转子（2）和第二转子（4）可转动连接方式为轴孔式连接方式或柔式连接方式。
　　8. 根据权利要求1所述的偏心活动叶片泵，其特征在于，在第二转子（4）上还设置有弧形群部，对应于相邻活动叶片（21）转动连接的第二转子（4）上的弧形群部相互嵌套，所述的相邻活动叶片（21）之间的容积空间（56）通过相互嵌套的弧形群部与相邻的第二转子之间的间隙隔离。
　　9. 根据权利要求1所述的偏心活动叶片泵，其特征在于，在第一转子（2）上对应于相邻活动叶片（21）之间的环形壁面的上下部分分别设置转子流体入口（58）和转子流体出口（59）；缸体流体入口（61）和缸体流体出口（62）与转子流体入口（58）和转子流体出口（59）对应设置在缸体（1）的上下部分；当转子流体入口（58）和缸体流体入口（61）贯通时或转子流体出口（59）和缸体流体出口（62）时流体进入或排出相邻活动叶片（21）之间的容积空间（56）。
　　10. 根据权利要求9所述的偏心活动叶片泵，其特征在于，所述的转子流体入口（58）和所述的转子流体出口（59）上设置有受控阀门（65），受控阀门（65）由流体压力差，离心力，动力，磁力，弹性作用力中的一种力或两种以上的合力控制。
　　11. 根据权利要求9所述的偏心活动叶片泵，其特征在于，低压流体通过缸体流体入口（61）进入容积空间（56），低压流体在容积空间（56）内增压后通过缸体流体出口（62）排出构成增压泵；高压流体通过缸体流体入口（61）进入容积空间（56），高压流体在容积空间（56）内释放压力后通过缸体流体出口（62）排出构成减压泵；或者低压流体通过转子流体入口（58）进入容积空间（56），低压流体在容积空间（56）内增压后通过转子流体出口（59）排出构成了增压泵；高压流体通过转子流体入口（58）进入容积空间（56），高压流体在容积空间（56）内释放压力后通过转子流体出口（59）排出构成了减压泵。
　　12. 根据权利要求1或10所述的偏心活动叶片泵，其特征在于，在缸体（1）上还设置有控制机构（63），控制机构（63）改变与缸体流体入口（61）和缸体流体出口（62）的位置关系进而调整缸体流体入口（61）和缸体流体出口（62）的形状与尺寸面积；或者控制机构（63）可改变受控阀门(65)开关条件如受控阀门的开关起始位置，由此改变偏心活动叶片泵每旋转一周流体进入容积空间（56）或由容积空间（56）排出的体积。
　　13. 根据权利要求11或12所述的偏心活动叶片泵，其特征在于，当工作流体为液体时，设置有2个偏心活动叶片泵，其中一个为增压泵另一个为减压泵，流体先后流经增压泵和减压泵，在控制机构（63）的作用下改变增压泵和减压泵每旋转一周流体进入增压泵和减压泵的体积，从而改变增压泵和减压泵的速度差可作为液力变矩器，无级变速器使用，当流体为气体时，设置有1个增压泵和1个减压泵和热交换室，且增压泵和减压泵同轴心固定连接，流体先后流经增压泵，热交换室和减压泵，可作为涡轮增压机，内燃机，燃气轮机，外燃机使用。
　　14. 根据权利要求1所述的偏心活动叶片泵，其特征在于，在第一转子（2）上对应于相邻活动叶片（21）之间的环形壁面上设置转子流体通道（60）。
　　15. 根据权利要求14所述的偏心活动叶片泵，其特征在于，所述的转子流体通道（60）上设置有受控阀门（65），受控阀门（65）由流体压力差，离心力，动力，磁力，弹性作用力中的一种力或两种以上合力控制。
　　16. 根据权利要求15所述的偏心活动叶片泵，其特征在于，受控阀门（65）可转动的设置在第一转子（2）上。
　　17. 根据权利要求16所述的偏心活动叶片泵，其特征在于，受控阀门（65）的开启或闭合由凸轮机构（655）控制。
　　18. 根据权利要求16所述的偏心活动叶片泵，其特征在于，受控阀门（65）的开启或闭合由设置在缸体（1）或机架上的轨道机构（101）控制。
　　19. 根据权利要求18所述的偏心活动叶片泵，其特征在于，轨道机构（101）由2个直径不等的环形导轨组成，2个环形导轨之间通过交叉轨道（102）连接成一个闭合回路。其中设置在阀门（65）上的转子或滑块作用在轨道机构（101）上，当所述的转子或滑块作用在轨道机构（101）的不同直径的轨道上时对应于阀门（65）的开启或者闭合状态。
　　20. 根据权利要求18所述的偏心活动叶片泵，其特征在于，设置有可转动轨道机构（101）的旋转机构（111），轨道机构（101）转动时可改变轨道机构（101）与第一转子（2）之间的相对位置关系。
　　21. 根据权利要求1所述的偏心活动叶片泵，其特征在于，所述的第二转子(4)同轴心设置在偏心轴（14）上。
　　22. 根据权利要求21所述的偏心活动叶片泵，其特征在于，所述的偏心轴（14）位于缸体（1）的位置由偏心轴控制机构（141）控制，偏心轴控制机构（141）可改变偏心轴（14）位于缸体（1）上的位置从而改变第一转子（2）和第二转子（4）之间的偏心距。
　　23. 根据权利要求22所述的偏心活动叶片泵，其特征在于，所述的偏心轴控制机构（141）由控制轴（75）组成，控制轴（75）偏心设置在偏心轴（14）上且与第一转子（2）偏心设置，控制轴（75）可转动的设置在缸体（1）上。
　　24. 根据权利要求1所述的偏心活动叶片泵，其特征在于，所述的缸体流体入口（61）主要区域位于相邻的活动叶片（21）之间空间处于膨胀阶段且该空间体积处于较大状态时对应缸体（1）的区域。
　　25. 根据权利要求1所述的偏心活动叶片泵，其特征在于，所述的缸体流体出口（62）主要区域位于相邻的活动叶片（21）之间空间处于压缩阶段且该空间体积处于较大状态时对应缸体（1）的区域。
　　26. 根据权利要求1所述的偏心活动叶片泵，其特征在于，所述的偏心活动叶片泵构成推进器。
　　27. 根据权利要求26所述的偏心活动叶片泵，其特征在于，所述推进器是飞行器推进器或船舶推进器。
　　28.一种偏心活动叶片泵，包括缸体（1），第一转子（2），第二转子（4）和活动叶片（21），其特征在于，第一转子（2）与第二转子（4）偏心设置，所述第一转子（2）与活动叶片（21）其中一端可转动连接，活动叶片（21）另一端上设有推杆（26），所述推杆（26）在所述的第二转子（4）上设置的滑道（45）内滑动；所述的活动叶片数量大于等于2个；在缸体（1）上对应于相邻的活动叶片（21）之间空间的膨胀区域及压缩区域分别设置有流体入口（61）和流体出口（62）。
PCT/CN2015/075934 2014-04-09 2015-04-05 偏心活动叶片泵 Ceased WO2015154645A1 (zh)

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EA201692033A EA201692033A1 (ru) 2014-04-09 2015-04-05 Эксцентриковый насос с подвижными лопатками
JP2016560961A JP6408027B2 (ja) 2014-04-09 2015-04-05 偏心可動羽根ポンプ
BR112016023581A BR112016023581A2 (pt) 2014-04-09 2015-04-05 bomba de palhetas móveis excêntricas
KR1020167031235A KR20160143785A (ko) 2014-04-09 2015-04-05 편심 활동 베인 펌프
US15/301,396 US20170030352A1 (en) 2014-04-09 2015-04-05 Eccentric movable vane pump
CA2944804A CA2944804A1 (en) 2014-04-09 2015-04-05 Eccentric movable vane pump
EP15776220.4A EP3144532A4 (en) 2014-04-09 2015-04-05 Eccentric movable vane pump

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CN201420169067.3U CN203796560U (zh) 2014-03-10 2014-04-09 偏心活动叶片泵
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CN201420233783.3 2014-05-08
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017222698A1 (de) * 2017-12-14 2019-06-19 Zf Friedrichshafen Ag Flügelzellenpumpe
US11505327B2 (en) 2020-03-16 2022-11-22 Goodrich Corporation Gas delivery augmenter with pump mechanism
CN115977947A (zh) * 2022-12-29 2023-04-18 江苏湖润泵业科技有限公司 一种高速高压低噪音叶片泵

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109322825A (zh) * 2018-11-22 2019-02-12 白晓瑞 一种复合转子压缩机
KR102202708B1 (ko) 2020-04-14 2021-01-14 안용준 가변임펠러를 이용한 로터리 펌프
CN111377059B (zh) * 2020-05-19 2022-11-04 重庆宇矛航空科技有限公司 高提升力无翼飞行器动力系统
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TR202106685A2 (tr) * 2021-04-15 2021-05-21 Alp Arge Otomotiv Tasarim San Ve Tic A S Yeni̇ bi̇r rotorlu fren vakum pompasi
CN113323876B (zh) * 2021-07-05 2022-03-08 珠海格力电器股份有限公司 一种压缩机的吸气增压结构和压缩机
CN117329127B (zh) * 2023-12-01 2024-02-02 成都理工大学 一种滑片式与离心式复合的压缩机械
CN121474123B (zh) * 2026-01-12 2026-03-27 靖江市奥克斯机械设备有限公司 向心泵级和包含该泵级的真空泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5518380A (en) * 1994-02-28 1996-05-21 Jidosha Kiki Co., Ltd. Variable displacement pump having a changeover value for a pressure chamber
DE19942466A1 (de) * 1998-09-10 2000-03-16 Jidosha Kiki Co Variable Displacement Pump
US20020085923A1 (en) * 2000-12-15 2002-07-04 Unisia Jkc Steering Systems Co, Ltd. Variable displacement pump
JP3441100B2 (ja) * 1992-12-28 2003-08-25 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
CN1954150A (zh) * 2004-08-02 2007-04-25 松下电器产业株式会社 叶片旋转式空气泵
CN102536805A (zh) * 2011-12-31 2012-07-04 张洪领 一种叶片泵

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR479354A (fr) * 1915-07-22 1916-03-17 Franey Shore Company Pompe rotative
US1769079A (en) * 1929-04-29 1930-07-01 Jay M Smith Rotary impeller mechanism
US1886206A (en) * 1929-08-30 1932-11-01 Firm Climax Motorenwerke Und S Rotary blower
US2139856A (en) * 1936-02-27 1938-12-13 Savage Leonard George Pump, engine, and the like
US2464208A (en) * 1945-10-31 1949-03-15 Calvin M Bolster Expansible chamber fluid motor or pump
DE875983C (de) * 1948-12-24 1953-05-07 Hugues Schellenberg Rotationskompressor mit schwenkbaren Schaufeln
DE1403748C3 (de) * 1961-10-13 1974-08-29 Breinlich, Richard, Dr., 7120 Bietigheim Hydraulische Radialkolbenmaschine
DE1453724A1 (de) * 1963-08-14 1969-05-08 Breinlich Dr Richard Kolbenschuhe und Kolbenschuhfuehrungen in Radialkolbenmaschinen
FR1549241A (zh) * 1967-07-28 1968-12-13
JPS608401U (ja) * 1983-06-28 1985-01-21 株式会社島津製作所 ロ−タリ式流体機械

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3441100B2 (ja) * 1992-12-28 2003-08-25 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
US5518380A (en) * 1994-02-28 1996-05-21 Jidosha Kiki Co., Ltd. Variable displacement pump having a changeover value for a pressure chamber
DE19942466A1 (de) * 1998-09-10 2000-03-16 Jidosha Kiki Co Variable Displacement Pump
US20020085923A1 (en) * 2000-12-15 2002-07-04 Unisia Jkc Steering Systems Co, Ltd. Variable displacement pump
CN1954150A (zh) * 2004-08-02 2007-04-25 松下电器产业株式会社 叶片旋转式空气泵
CN102536805A (zh) * 2011-12-31 2012-07-04 张洪领 一种叶片泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3144532A4 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017222698A1 (de) * 2017-12-14 2019-06-19 Zf Friedrichshafen Ag Flügelzellenpumpe
US11505327B2 (en) 2020-03-16 2022-11-22 Goodrich Corporation Gas delivery augmenter with pump mechanism
CN115977947A (zh) * 2022-12-29 2023-04-18 江苏湖润泵业科技有限公司 一种高速高压低噪音叶片泵

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