CN111608851A - Hydraulic power device with swinging blades - Google Patents

Hydraulic power device with swinging blades Download PDF

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Publication number
CN111608851A
CN111608851A CN202010645345.8A CN202010645345A CN111608851A CN 111608851 A CN111608851 A CN 111608851A CN 202010645345 A CN202010645345 A CN 202010645345A CN 111608851 A CN111608851 A CN 111608851A
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CN
China
Prior art keywords
blade
rotor
wall
cylinder body
guide rail
Prior art date
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Pending
Application number
CN202010645345.8A
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Chinese (zh)
Inventor
李光惠
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Individual
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Individual
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Publication date
Application filed by Individual filed Critical Individual
Publication of CN111608851A publication Critical patent/CN111608851A/en
Priority to PCT/CN2020/127509 priority Critical patent/WO2021098542A1/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00Rotary-piston engines
    • F03C2/30Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F03C2/308Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 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 F03C2/08 and having a hinged member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/30Rotary-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
    • F01C1/40Rotary-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
    • F01C1/44Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/04Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08Rotary pistons
    • F01C21/0809Construction of vanes or vane holders
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08Rotary pistons
    • F01C21/0809Construction of vanes or vane holders
    • F01C21/0818Vane tracking; control therefor
    • F01C21/0827Vane tracking; control therefor by mechanical means
    • F01C21/0836Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10Outer members for co-operation with rotary pistons; Casings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Abstract

The invention discloses a hydro-pneumatic power device with a swinging blade, which comprises a cylinder body (1), a cylinder cover (2), a rotor (3) and a blade (4), wherein the rotor (3) is movably connected with the inner edge of the blade (4), and the blade (4) can rotate and swing relative to the rotor (3); the problem of prior art structure itself cause the not enough of equipment working property is solved, adopt swing blade technical structure for the motion of blade is more smooth the reliability higher, and the leakproofness is better, has reduced the frictional force of cylinder body inner wall, more does not have the reverse resistance of machinery itself, has improved power device's work efficiency greatly.

Description

Hydraulic power device with swinging blades
Technical Field
The invention relates to the technical fields of hydraulic pressure, air pressure, low-drop-height hydroelectric power generation, medium-low temperature medium-low pressure thermal steam power conversion and the like, in particular to a hydraulic power device with swing blades.
Background
The volume type rotary power device, such as vane motor, is formed from main components of cylinder body (stator ring), rotor, cylinder cover and vanes, etc., the distances of inner wall of cylinder body and outer wall of rotor are different in different section radial directions, and the vanes are positioned between them, and under the action of pressure liquid or gas the stressed lengths, areas and directions of vanes are different in different radial directions and between inner wall of cylinder body and outer wall of rotor so as to produce torque to drive rotor to rotate.
In the existing vane type hydraulic (pneumatic) motor, a rotor is provided with a vane chute, vanes of the vane type hydraulic (pneumatic) motor do reciprocating motion in the radial direction of the rotor relative to the rotor, the overall motion distance of the vanes is the maximum gap between the rotor and a cylinder body, and the movement of the vanes has large kinetic energy loss; the outward movement of the blades needs to be realized by means of external forces such as springs or hydraulic pressure, air pressure and the like in the rotor, and the rotor has a relatively complex structure and large weight; the existing vane type hydraulic (pneumatic) motor has relatively simple vane design, the radial movement of the vane is powered by a spring or hydraulic (pneumatic) pressure outwards, and when the motor works, the movement of the vane may have hysteresis phenomena, which causes hydraulic (pneumatic) leakage and reduces the motor efficiency; the blades move inwards to provide reverse force by the inner wall of the cylinder body, certain friction force can be generated, the direction of the reverse force is not radial but forms a certain angle, and the reverse force provides the radial force for the blades and resistance force for the movement of the blades and the rotor at the same time, so that the motor efficiency is reduced; the blades are installed in the rotor through the sliding grooves, the length of the blades is limited, the maximum gap between the rotor and the cylinder body is relatively small, and the capacity ratio, the flow ratio and the working efficiency of the motor are affected.
In short, the conventional vane-type hydraulic (pneumatic) motor is greatly limited in flow rate, power ratio and energy conversion efficiency due to the restriction of the vane structure, connection and movement mode.
The existing hydraulic power devices such as water turbines are all of open design, and the kinetic energy of water is utilized or mainly utilized to impact the blades of the water turbine so as to generate power and torque. For small hydroelectric power generation with low water level and small fall, the potential energy is not sufficiently converted due to low water pressure, so that the energy utilization efficiency is not high.
The thermodynamic system of the traditional thermodynamic power device such as a steam turbine and a turbine is generally an open system, the temperature of the system is high, the pressure of the system can reach more than 20MPa, the power is provided by a working medium which moves at high pressure and high speed, and the higher the pressure is, the higher the thermal efficiency of the system is. The working principle is that the pressure and the kinetic energy of a high-pressure and high-speed working medium impact rotor blades to generate power. The thermodynamic working medium is high-temperature high-pressure steam, so that the thermodynamic working medium has high requirements on the manufacture of a heat engine, and the heat engine has a complex structure and high precision requirements, so that the thermodynamic working medium has the advantages of complex manufacturing process, high difficulty and high cost, equipment generally tends to be large-scale, and the thermodynamic working medium has high equipment maintenance requirements and high cost.
However, for medium-low temperature and medium-low pressure thermal power generation, the application of the conventional heat engine as a power plant cannot effectively improve the system thermal efficiency, because the open plant structure can cause partial steam to flow in a reactive manner or pass through the heat engine in a low efficiency. The thermal efficiency of medium-low temperature thermal power generation is usually low (generally 12-30%), how to improve the thermal efficiency is a technical problem which always troubles the development of the medium-low temperature thermal power generation industry, and the technical development of a heat engine is a key factor in the medium-low temperature thermal power generation industry.
In nature and modern society, there are wide low-grade and medium-low temperature heat sources, such as boiler waste heat, geothermal heat, solar energy, etc., and people not only use general life heat supply, but also use the heat energy to generate electricity. The medium-low temperature heat source has the characteristics that the temperature is not high, if the medium-low temperature heat source is used for generating electricity, the problem of low working medium pressure exists, the heat efficiency of the electricity generation is low on the premise of using the prior art and equipment, so that the unit power investment is high, and the utilization of medium-low temperature heat energy is limited.
In recent years, volumetric power devices (such as screw power devices) are gradually applied to medium-low temperature thermal power generation, and the characteristics of the volumetric power devices have certain advantages in the fields of medium-low temperature and medium-low pressure thermal power generation.
The positive displacement power device has a closed steam working space, and on the premise of ensuring the sealing property, the reactive flow energy loss is small even for low-pressure and low-speed steam, so that the heat efficiency of the system can be effectively improved.
Disclosure of Invention
The invention aims to design a hydraulic pneumatic power device with a swing blade, which solves the problem of insufficient performance caused by the structure of the prior art and achieves the purpose of expanding the application range of a positive displacement hydraulic pneumatic power device.
The invention adopts the mode that the rotor is combined with the blades to move in a rotating and swinging manner, so that the blades move more smoothly, the reliability is higher, the sealing performance is better, the friction force of the inner wall of the cylinder body is reduced, the reverse resistance of the machine is avoided, the energy conversion efficiency of the power device is greatly improved, and the power device is more suitable for medium and low pressure liquid steam power devices; meanwhile, the novel technical structure has large single-rotation flow, realizes higher liquid (gas) capacity ratio of the power device, improves the liquid (gas) flow ratio of the power device, and further improves the power ratio of the power device; when the working medium of the power device is gas or steam, a higher expansion ratio or compression ratio of a single machine can be realized.
The invention is realized by the following technical scheme: a hydro-pneumatic power device with swinging blades comprises a cylinder body, a cylinder cover, a rotor and blades, wherein the rotor is movably connected with the inner edge of the blades, and the blades can rotate and swing relative to the rotor.
In order to further realize the invention, the following arrangement structure is adopted: hinges connected with the inner edges of the blades are arranged on the outer wall of the rotor, and the hinges are arranged on the circumference of the rotor at equal intervals; as a preferred arrangement, the shape of the outer wall of the rotor may be a similar regular polygon structure (a circular structure is also possible, but is not limited thereto), a hinge connected to the inner edge of the blade is disposed at a corner of the outer wall of the rotor, the outer wall of the rotor is connected to the inner edge of the blade by the hinge, the blade can rotate and swing around the hinge axis relative to the rotor, so as to avoid the blade from sliding back and forth in the blade slot of the rotor, reduce friction resistance and kinetic energy loss of the blade, and the hinge may be filled with lubricating oil.
In order to further realize the invention, the following arrangement structure is adopted: the shape of the cross section of the inner wall of the cylinder body is formed by two arc sections in tangent or arc transition, and the centers of the two arc sections are eccentrically arranged; the arc center of one of the arc sections of the cylinder body is concentric with the rotation center of the rotor, the length of the arc section is larger than or can cover the length of the arc section of the outer wall of the rotor between two adjacent hinges of the rotor, and the outer wall of the rotor or the inner edge of the blade is matched with the arc section of the inner wall of the cylinder body concentric with the rotation center of the rotor along the tolerance, so that the sealing performance of the power device between the cylinder body and the rotor can be effectively improved.
In order to further realize the invention, the following arrangement structure is adopted: and a blade limiting spring which enables the outer edge of the blade to be tightly attached to the inner wall of the cylinder body is arranged between the rotor and the blade, so that the free movement of the blade is limited, and the outer edge of the blade is tightly attached to the inner wall of the cylinder body.
In order to further realize the invention, the following arrangement structure is adopted: the rotor is provided with a lubricating oil storage bin and a lubricating oil channel, the lubricating oil channel is communicated with the lubricating oil storage bin and the hinge, and the centrifugal force generated when the rotor rotates is utilized to lubricate the moving part.
In order to further realize the invention, the following arrangement structure is adopted: the blade is also provided with a blade lubricating oil channel (or a blade lubricating oil storage bin is arranged on the blade), the lubricating oil storage bin is communicated with the lubricating oil channel through a hinge to lubricate the movable part of the outer edge of the blade, the lubricating oil storage bin (or the blade lubricating oil storage bin) is communicated with a blade round shaft (or a round shaft) of the outer edge of the blade, a blade roller, a blade rolling shaft, a guide rail matching piece and the like through the hinge and the lubricating oil channel, and when the rotor and the blade rotate, the lubricating oil is sent to the hinge connected with the rotor and the blade, the outer edge of the blade, the round shaft (or the blade round shaft) connected with the blade, the blade roller or the blade rolling shaft, the guide rail matching piece and the like by using; the lubricating oil storage bin can be used for supplementing lubricating oil in the working clearance of the motor through an opening of a cylinder cover; according to the rotating speed of the motor, the lubricating oil supply amount, the maintenance period and the like, the flow limiting part is arranged in the lubricating oil channel, so that effective lubrication and safe operation of equipment are realized.
In order to further realize the invention, the following arrangement structure is adopted: a rotor rotating shaft is nested in the rotor, and a rotor axis input pipe penetrating through a cylinder cover on one side is nested in the rotor rotating shaft; an inlet is arranged between two adjacent hinges in the circumferential direction of the rotor, an axis input port is arranged in the radial direction of a rotor rotating shaft, an input pipe input port is arranged on the pipe wall of the rotor axis input pipe, and when the inlet, the axis input port and the input pipe input port are communicated, hydraulic liquid and gas can enter a working chamber of the power device to do work.
In order to further realize the invention, the following arrangement structure is adopted: and a blade roller and a blade circular shaft are embedded in the outer edge of the blade.
In order to further realize the invention, the following arrangement structure is adopted: the cylinder cover is provided with a blade guide rail on the inner side of the inner wall of the cylinder body, the blade guide rail is a groove, the blade guide rail is positioned between the inner wall of the cylinder body and the outer wall of the rotor and close to one side of the inner wall of the cylinder body, and the outer edge of the blade is tightly attached to the inner wall of the cylinder body under the action of the blade guide rail arranged on the cylinder cover; the guide rail inner wall of the blade guide rail of the cylinder cover is matched with the guide rail bearing, when the guide rail inner wall is arranged, the inner wall of the cylinder body can replace the outer wall of the guide rail, and the width of the guide rail groove is slightly larger than the diameter of the guide rail bearing, so that the guide rail bearing is prevented from generating high-speed friction when the positive pressure section and the negative pressure section of the blade rotate in opposite directions; the outer groove wall mainly plays a role in sealing.
In order to further realize the invention, the following arrangement structure is adopted: the blade circular shaft extends out of two ends of the blade, and guide rail fitting pieces capable of moving in a track manner are arranged at two ends of the blade circular shaft, so that the outer edge of the blade and the roller are close to the inner wall of the cylinder body.
In order to further realize the invention, the following arrangement structure is adopted: the rear edge (relative to the motion direction of the blades) of the auxiliary blade is hinged with the outer edge of the blades, auxiliary blade round shafts are arranged at two ends of the front edge of the auxiliary blade, and a guide rail bearing piece or a sliding block piece which can control the front edge of the auxiliary blade to closely cling to the inner wall of the cylinder body to do track motion under the action of a blade guide rail is matched on the auxiliary blade round shafts; the guide rail bearing piece or the sliding block piece controls the front edge movement track of the auxiliary blade under the action of the blade guide rail, so that the auxiliary blade is tightly attached to the inner wall of the cylinder body, and the liquid (gas) leakage is prevented at the corresponding section from the discharge port to the inlet at the outer edge of the blade (when the blade is in a back pressure state), thereby playing a good sealing role; when the structure is particularly applied to a power device of a pneumatic motor, the function of sealing the inlet (air) of the power device in advance can be achieved, the expansion pressure of the air is fully utilized to do work, and the purpose of improving the energy conversion efficiency of the power device is achieved.
In order to further realize the invention, the following arrangement structure is adopted: the blade adopts an A structure: the outer edge of the blade is embedded with a blade roller (a built-in high-speed bearing), the outer edge of the blade axially penetrates through the outer edge of the blade and the blade roller and is also provided with a blade round shaft, the blade round shaft extends out of two ends of the blade, two ends of the blade round shaft are provided with guide rail matching parts capable of doing track motion in the blade guide rail, the guide rail matching parts adopt guide rail bearings or sliders, the outer wall of the blade roller is contacted with the inner wall of the cylinder body, the blade passes through the guide rail matching parts and the blade roller, under the action of the inner wall of the cylinder body and the blade guide rail, the outer edge part of the blade is tightly attached to the inner wall of the cylinder body, and the; the reliability of the movement of the blade is improved, and the aims of improving the sealing performance of the blade and reducing the leakage of liquid (gas) are fulfilled.
In order to further realize the invention, the following arrangement structure is adopted: the blade adopts a structure B: the two ends of the outer edge of each blade are provided with circular shafts for installing a guide rail fitting piece adopting a guide rail bearing or a sliding block, and the motion trail of the outer edge of each blade is controlled under the matching of the guide rails of the blades, so that the outer edge of each blade is tightly attached to the inner wall of the cylinder body.
In order to further realize the invention, the following arrangement structure is adopted: the blade adopts a C structure: the blade is equipped with the circle axle along both ends outward for the installation adopts the guide rail fitting piece of guide rail bearing or slider, is equipped with the roller bearing caulking groove at the blade outer edge, is equipped with the blade roller bearing in the roller bearing caulking groove, and this structure can reduce the frictional resistance between blade and the cylinder body.
In order to further realize the invention, the following arrangement structure is adopted: arranging a discharge port and an inlet on the cylinder body, and when the space of a bin chamber formed by the cylinder body, a cylinder cover, a rotor and blades between the two blades reaches the minimum capacity, the outer edge position of the front blade in the rotation direction of the rotor is the initial position of the liquid (gas) inlet, and the outer edge position of the rear blade is the end position of the liquid (gas) discharge port; when the chamber space reaches the maximum capacity, the outer edge position of the latter blade is the end position of the liquid (gas) inlet, the outer edge position of the former blade is the initial position of the liquid (gas) outlet, and during the setting, the inlet and outlet (outlet and inlet) of the liquid (gas) can be arranged on the cylinder body or the cylinder cover. In practical application, the opening position of the inlet and outlet can be properly adjusted according to the rotating speed of the power device (motor) and the liquid (gas) pressure because the liquid (gas) can generate a hysteresis phenomenon during movement, and in specific arrangement, the inlet end position of the power device for gas or steam can be determined according to the expansion ratio of the gas or steam.
In order to further realize the invention, the following arrangement structure is adopted: back pressure supporting springs are arranged on the inner sides of the blade guide rails on the cylinder cover and on the corresponding sections of the blades subjected to reverse pressure; preferably, aiming at the structure adopting the blade guide rail, a back pressure supporting spring is arranged at the corresponding section from the inner side of the blade guide rail on the cylinder cover and the outlet to the inlet of the inner wall of the cylinder body, so that the gap between the blade and the inner wall of the cylinder body is reduced, and the sealing property between the outer edge of the blade and the inner wall of the cylinder body is improved.
In order to further realize the invention, the following arrangement structure is adopted: the cylinder body adopts a structure that the middle part of the cross section is a straight line section, and the two ends are curved sections, so that the moving track of the blade is more reasonable, the liquid (gas) flow rate ratio of the blade motor is improved to the maximum extent, and the power ratio of the blade motor is improved.
In order to further realize the invention, the following arrangement structure is adopted: the gas or steam powered hydro-pneumatic power device with swinging blades has one side cylinder cover with one power device starting port to provide starting power or torque without communicated gas inlet passage, and the starting port has width or diameter smaller than the thickness of the blades to avoid the communication between two adjacent chambers.
Compared with the prior art, the invention has the following advantages and beneficial effects:
the invention relates to a positive displacement liquid-pneumatic power device, the structure of which is derived from a vane motor in the hydraulic and pneumatic fields, but the positive displacement liquid-pneumatic power device has significant innovation and change, so the application range of the positive displacement liquid-pneumatic power device is not limited in the hydraulic and pneumatic fields, and the positive displacement liquid-pneumatic power device can be expanded in the fields of medium-low temperature and medium-low pressure thermal power generation (low-grade heat energy utilization, such as solar energy, terrestrial heat, waste heat and the like) and low-drop small-sized hydroelectric power generation.
The invention is used for medium and low pressure liquid steam, and enables the pressure liquid steam to efficiently pass through the power device on the premise of ensuring the sealing property, thereby improving the energy conversion efficiency; under the condition of ensuring certain efficiency, the power device can be miniaturized.
The heat engine can be miniaturized and a thermal power generation system can be conveniently and flexibly designed because the scale of the general heat energy of the medium-low temperature heat source is not large, and the invention can be economically and conveniently realized.
Compared with the traditional heat engine such as a steam turbine and a turbine, the invention can realize the miniaturization of equipment, can improve the energy conversion efficiency of medium-low temperature and medium-low pressure thermodynamic systems, has smaller starting torque compared with a positive displacement power equipment such as a double-screw expander, and has large steam flow and large specific power under the condition of similar rotating speed.
The invention relates to a low-drop small hydroelectric station, which is widely applied to the natural world, has low generating efficiency mainly because a water turbine has structural defects, potential energy is not sufficiently converted into kinetic energy due to low water pressure, and low-pressure and low-speed flowing hydraulic resources are generated by water flow or idle flow or pass through the water turbine in low efficiency.
The present invention relates to a hydraulic and pneumatic vane motor, and is characterized by that in the radial direction of rotor, relative to the rotor, its vane can implement reciprocating motion, and the moving distance of whole vane is the maximum gap between rotor and cylinder body.
In the existing hydraulic and pneumatic vane motor, a rotor is provided with vane grooves, a spring needs to be installed or hydraulic and pneumatic channels need to be designed, and the rotor is relatively complex in structure and heavy; the rotor of the invention has the advantages of relatively simple structure, simple manufacturing process, relatively low cost, easy maintenance and light weight.
The existing hydraulic and pneumatic vane motor has relatively simple vane design, the radial movement of the vane is powered by a spring or liquid (gas) pressure, and when the motor works, the vane movement may generate hysteresis, which causes liquid (gas) leakage and reduces the motor efficiency; the vanes provide a reverse force inwards from the inner wall of the cylinder body, a certain friction force can be generated, the direction of the reverse force is not radial, but forms a certain angle with the vanes, and the reverse force provides a radial force for the vanes, and simultaneously provides resistance for the movement of the vanes and the rotor, so that the motor efficiency is reduced; the blade guide rail, the guide rail matching piece, the blade roller or the blade rolling shaft are designed and matched, so that the motion of the blade is smoother, the reliability is higher, the sealing performance is better, the friction force of the inner wall of the cylinder body is reduced, the reverse resistance of the machine is avoided, and the working efficiency is greatly improved; although the blade of the invention has relatively complex design, compared with the complexity and the difficulty of the manufacturing process of the traditional blade motor rotor, the blade is still simple and easy, and the manufacturing cost is also reduced to a certain extent.
The conventional vane type hydraulic (pneumatic) motor has a small capacity of a hydraulic (pneumatic) chamber formed between vanes due to the restriction of a vane structure, and the flow rate ratio and the power ratio of the motor are greatly limited. The liquid (gas) chamber formed between the blades has larger capacity, and compared with the blade motor with the original structure, the power can be greatly improved under the conditions of similar size and same rotating speed.
Compared with the traditional vane motor, the invention optimizes the liquid (gas) inlet and outlet, and makes qualitative design on the opening position and the ending position of the inlet and outlet, thereby being beneficial to fully utilizing the liquid (gas) to generate torque and power and improving the efficiency of the power device.
The invention comprises a plurality of chambers for working, one or two chambers are in a liquid (gas) inlet working state all the time, power can be continuously output, and the blade works reliably under the action of the blade guide rail or the limiting spring.
The invention can directly generate rotary power by utilizing pressurized liquid (water and oil) or gas (including high-pressure fuel gas and high-pressure steam generated by fuel oil and fuel gas), and has higher energy conversion efficiency. The device can be widely used for generating electricity or driving other mechanical devices, and can also be used as a liquid and air pump base structure.
Compared with the hydraulic and pneumatic motors which are widely applied at present, the invention has the advantages of simple structure, reliable work, convenient maintenance, simple manufacturing and mounting process and low manufacturing cost, and has the obvious characteristics of high power ratio and high energy conversion efficiency.
Drawings
Fig. 1 is a schematic diagram of the structure of the present invention shown in example 1 (gas or steam as power).
Fig. 2 is a schematic structural view (liquid is power) of the present invention shown in embodiment 2.
Fig. 3 is a schematic view of the structure of the rotor shaft according to the present invention.
Fig. 4 is a schematic view of the structure of the rotor shaft center input pipe according to the present invention.
Fig. 5 is a schematic structural diagram of a blade (non-blade rail technology) according to the invention.
Fig. 6 is a schematic view of the present invention (in a first operating state of the vane guide).
Fig. 7 is a schematic view of the present invention (in a second operating state of the vane guide).
Fig. 8 is a schematic view of the present invention (in a third operating state of the vane guide).
Fig. 9 is a schematic view of the present invention (in a fourth operating state of the vane guide).
Fig. 10 is a schematic view of a rotor (containing a lubricant reservoir, lubricant channels) according to the present invention.
Fig. 11 is a schematic view of the structure of the cylinder cover (adopting a vane guide rail) of the invention.
Fig. 12 is a schematic structural view of a vane (a roller is adopted in a vane guide rail structure) of the invention.
Fig. 13 is a schematic structural view of the vane (the vane guide rail structure adopts a roller) according to the invention.
Fig. 14 is a schematic structural view of a vane (third vane guide structure) according to the present invention.
Fig. 15 is a schematic view of the structure of the sub-vane (back pressure seal vane).
Figure 16 is a schematic view of the arrangement of the backpressure support springs of the present invention.
Fig. 17 is a front view of the liquid (gas) inlet/outlet (provided on the cylinder) of the present invention (a is a drain port, and B is an inlet port).
Fig. 18 is a schematic view of the structure of the present invention (including the secondary blade structure).
Fig. 19 is a schematic diagram of a modified structure of the present invention (rotor section of a is pentagonal, cylinder section of B is elliptical).
FIG. 20 is a schematic diagram of a power plant having a cylindrical cylinder, a cylindrical rotor, and arcuate vanes, with the cylinder and rotor in an eccentric position.
Wherein, 1-cylinder body, 2-cylinder cover, 3-rotor, 3A-rotor rotating shaft, 3B-rotor axis input pipe, 4-blade, 5-blade guide rail, 6-lubricating oil storage bin, 7-lubricating oil channel, 8-hinge, 9-hinge rotating shaft, 10-blade round shaft, 11-guide rail matching piece, 12-blade roller, 13-blade roller, 14-blade lubricating oil channel, 15-auxiliary blade, 16-auxiliary blade hinge, 17-auxiliary blade round shaft, 18-back pressure supporting spring, 19-discharge port, 20-inlet, 20A-axis input port, 20B-input pipe input port, 21-fixed hole, 22-round shaft, A-inflow direction, B-outflow direction, C-rotor rotation direction.
Detailed Description
The present invention will be described in further detail with reference to examples, but the embodiments of the present invention are not limited thereto.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention.
In the description of the present invention, it is to be understood that the terms etc. indicate orientations or positional relationships based on those shown in the drawings only for the convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
It is worth noting that: in the present application, when it is necessary to apply the known technology or the conventional technology in the field, the applicant may have the case that the known technology or/and the conventional technology is not specifically described in the text, but the technical means is not specifically disclosed in the text, and the present application is considered to be not in compliance with the twenty-sixth clause of the patent law.
Example 1:
as shown in fig. 1, the present embodiment shows a power device using pressurized gas or steam to do work, the cylinder body 1 is a cylinder body structure having a cross-sectional shape formed by two arc segments whose inner walls are transited by tangent lines or arc lines, and mainly comprises a cylinder body 1 (stator ring), two cylinder covers 2, a rotor 3, four blades 4, four blade rollers 12, a rotor rotating shaft 3A, a rotor axis input pipe 3B, and the like.
As shown in the attached drawing 1, the cylinder body 1 is a structure formed by two arc sections with tangent or arc transition in the shape of the section of the inner wall, is an outer structural member of the power device, and can be fixed on the cylinder cover 2 through a flange; the centers of two arc sections of the cylinder body 1 are eccentrically arranged; the rotating center of the rotor 3 is concentric with the arc center of one of the arc sections of the cylinder body 1, the length of the arc section concentric with the rotating center of the rotor 3 is larger than or can cover the length of the arc section between two adjacent connecting positions (a hinge 8) on the rotor 3, and the outer wall of the rotor 3 and the inner wall of the blade 4 are matched with the arc section of the inner wall of the cylinder body 1 concentric with the rotating center of the rotor 3 along the tolerance; the rotor 3 is kept consistent with the cylinder body 1 in the axial direction, and the rotor 3 is limited to rotate relative to the cylinder body 1 and the cylinder cover 2; the cylinder body 1 is provided with a discharge port (gas or steam) 19, and when the space of a chamber formed by the cylinder body 1, the rotor 3, the cylinder cover 2 and the blades 4 reaches the maximum capacity between the two blades 4, the position of the outer edge of the previous blade 4 or the blade roller 12 in the rotation direction of the rotor 3 is the initial position of the discharge port 19; when the chamber space reaches a minimum capacity, the trailing vane 4 outer edge position is the end position of the discharge opening 19.
As shown in fig. 1, 3, 4, 5, and 10, the rotor 3 is shaped like a square column (but not limited thereto, it may also be a diamond, a circle, etc.), and the rotor forms a distance difference between the outer wall of the rotor 3 and the inner wall of the cylinder 1 in different radial directions; hinges 8 are arranged on the outer wall of the rotor 3 at equal intervals in the circumferential direction, and the hinges 8 are matched with hinge rotating shafts 9 and are used for being connected with the blades 4 and enabling the blades 4 to swing on the rotor 3; a rotor rotating shaft 3A is nested in the rotor 3, and one section of the rotor rotating shaft 3A in the rotor 3 is in a hollow tubular shape, extends to the cylinder cover 2 at one side and penetrates through a fixing hole 21 in the cylinder cover 2; the other end of the rotor rotating shaft 3A extends out of the cylinder cover 2 and is a torque and power output part; an inlet 20 is arranged between adjacent hinges 8 of the rotor, and an axial inlet 20A is arranged at the position of the rotor rotating shaft 3A corresponding to the inlet 20; a rotor shaft center input pipe 3B is embedded in the rotor rotating shaft 3A, penetrates through and extends out of the cylinder cover 2 on one side, is fixed on the cylinder cover 2, and the part extending out of the cylinder cover can be used as a liquid-steam input interface; the rotor shaft center input pipe 3B is provided with an input pipe input port 20B in an opening in the axial section of the rotor 3, and the opening size of the input pipe input port 20B depends on the steam pressure or the set steam expansion ratio.
As shown in fig. 5, the vane 4 is in a rectangular plate shape (not limited to a plate shape), a hinge 8 is provided on an inner edge thereof, the vane 4 is located between the cylinder 1 and the rotor 3 and between the two cylinder covers 2, the inner edge of the vane 4 is hinged to the rotor 3 by the hinge 8, and the vane can rotate and swing between the cylinder 1 and the rotor 3; a blade roller 12 is embedded at the outer edge of the blade 4; under the action of steam pressure or air pressure and the rotating centrifugal force of the rotor 3, the outer edge of the blade 4 is closely attached to the inner wall of the cylinder body 1 through the blade roller 12 to run.
The cylinder cover 2 is a plate-shaped structure matched with the cylinder body 1, is an external structural member of the power device, has an external shape enough to cover the end part of the cylinder body 1, and is fixed at the two axial ends of the cylinder body 1; the cylinder cover 2 is internally provided with a fixing hole 21 of the rotor rotating shaft, and the shaft center of the rotor 3 is fixed at the center of an arc section in the cylinder body 1 through the rotor rotating shaft 3A and a bearing.
And a blade limiting spring is arranged between the rotor 3 and the blade 4, so that the outer edge of the blade 4 is kept to be tightly attached to the inner wall of the cylinder body 1 under the influence of no bin negative pressure.
A starting inlet of the power device is arranged on one side of the cylinder cover 2, starting power or torque is provided for the power device under the condition that the power device is not communicated with an air inlet (steam) channel, and the width or the diameter of the starting inlet is smaller than the thickness of the blade.
Lubricating oil may be enclosed in the hinge 8 connecting the rotor 3 and the vane 4, and in the roller 12 on which the vane 4 is mounted.
The working principle of the embodiment is as follows:
taking steam power as an example, as shown in fig. 1, a space formed by a cylinder body 1, a rotor 3, a cylinder cover 2 and blades 4 between the two blades 4 is a steam working chamber. The chamber is in the working stage of the chamber when the steam enters or is in the expansion stage. Under the effect of the steam pressure of the bin, the outer edge of the previous blade 4 moves along the inner wall of the cylinder body 1, the moving radius of the outer edge of the previous blade 4 is increased, the radius of the rotation center of the rotor 3 when the previous blade 4 is stressed is larger than the stress radius of the outer wall of the rotor 3 or the reverse stress radius of the next blade 4, the included angle between the stress direction of the previous blade 4 and the rotation direction of the rotor 3 is smaller than the included angle between the stress of the outer wall of the rotor 3 or the reverse stress direction of the next blade 4 and the rotation direction of the rotor 3, therefore, a moment difference is formed, and a torque is formed.
In the rotating process of the rotor 3, the bin is always in an expansion or steam admission stage, so that the power device can be ensured to output continuous power.
When the power device is started, pressure steam can be input through a starting inlet on the cylinder cover 2 to provide starting torque, and the starting inlet can be closed after the power device is started.
The working process of the embodiment is as follows:
when the rotor 3 rotates, the inlet 20 and the axial input port 20A are communicated with the input pipe input port 20B, and the outer edge of the blade 4 leaves the arc section of the inner wall of the cylinder body 1 concentric with the rotor 3, the chamber enters a steam pressing-in stage, and the chamber is in a work-pushing state at the stage.
The rotor 3 continues to rotate, when the steam entering the bin reaches the set capacity, the inlet 20 and the axis input port 20A are cut off from the input port 20B of the input pipe, the steam does not enter the bin any more, the bin enters a steam expansion stage, and the bin is in an expansion work doing state at the stage.
Then the rotor 3 continues to rotate, when the steam in the bin reaches the set pressure or expansion ratio, the outer edge of the blade 4 in front of the bin crosses the starting position of the discharge port 19 of the cylinder body 1, the bin enters a steam discharge stage until the outer edge of the blade 4 crosses the ending position of the discharge port 19 of the cylinder body 1, enters an inner wall arc section of the cylinder body 1 concentric with the rotor 3, and the steam discharge stage of the bin is ended; when the chamber is in the steam discharge phase, the latter chamber in the direction of rotation of the rotor 3 is in the work phase.
As an optimal implementation scheme, a brand-new structure is adopted, so that the movement of the blades is smoother, the operation reliability of the power device is higher, the friction is smaller, the sealing performance is better, and the energy conversion efficiency and the power of the power device can be greatly improved.
According to the preliminary analysis of the performance, the power device which takes the medium-low pressure steam as a power source is more suitable for the working principle and the device structure, the design and the performance requirements which the small power device should have are preliminarily met, and the power device can be applied to the fields of medium-low temperature (or low grade) thermal power generation, such as waste heat utilization, geothermal power generation, small solar thermal power generation and the like.
The device can be miniaturized, and the obvious characteristics of low rotating speed and moderate power are realized.
Example 2:
the present embodiment is a power device using pressurized liquid to provide power, as shown in fig. 2, the power device of the present embodiment has the same structure as that of embodiment 1, and is different from embodiment 1 in that the input pipe input port 20B of the rotor shaft center input pipe 3B has a larger opening, and the design thereof needs to meet the requirement that the working chamber instantaneously closes the liquid input channel before the liquid begins to discharge.
The working principle of the embodiment is as follows:
the working principle of the embodiment is basically consistent with that of the embodiment 1, and the difference is that liquid always enters the chamber when the liquid working chamber does work, and an expansion working stage is not provided.
In the rotating process of the rotor 3, one or two chambers are always in the working stage, so that the power device can be ensured to output continuous power.
The working process of the embodiment is as follows:
when the rotor 3 rotates, the inlet 20 and the axial input port 20A are communicated with the input port 20B of the input pipe, and the outer edge of the blade 4 leaves the arc section of the inner wall of the cylinder body 1 concentric with the rotor 3, the bin enters a liquid pressing stage and is in a working state.
The rotor 3 continues to rotate, when the capacity of the bin reaches the maximum, the inlet 20, the axis input port 20A and the input pipe input port 20B are cut off, and liquid does not enter the bin any more; meanwhile, the outer edge of the front blade 4 of the bin immediately crosses the starting position of the discharge port 19 of the cylinder body 1, the bin enters a liquid discharge stage, and the working state of the bin is finished; the latter chamber in the direction of rotation of the rotor 3 is still in the working phase.
Example 3:
as shown in fig. 6, 10, 11 and 12, the hydro-pneumatic device with the swinging blades mainly comprises a cylinder body 1 (a stator ring), two cylinder covers 2, a rotor 3, six blades 4, six pairs of guide rail bearings, six blade rollers 12 and the like.
As shown in fig. 6, the cylinder body 1 is cylindrical, is an external structural member of the power device, and can be fixed to the cylinder cover 2 through a flange; the section of the cylinder body 1 is shaped like an annular runway (the invention is not limited to be similar to the annular runway, and can also be round, oval and the like); the cylinder body 1 is provided with a liquid (gas) inlet and outlet (a discharge port 19 and an inlet 20), when the space of a bin chamber formed by the cylinder body 1, the rotor 3, the cylinder cover 2 and the blades 4 reaches the minimum capacity between the two blades 4, the outer edge position of the previous blade 4 in the rotation direction of the rotor 3 is the initial position of the inlet 20, and the outer edge position of the next blade 4 is the end position of the discharge port 19; when the chamber space reaches the maximum capacity, the trailing vane 4 outer edge position is the end position of the inlet 20 and the leading vane outer edge or vane roller 12 position is the start position of the discharge 19.
As shown in fig. 11, the cylinder cover 2 is a plate with a straight line and a circular arc shape, and is an outer structural member of the power device to fix the power device; a fixing hole 21 of the rotor rotating shaft is arranged in the cylinder cover 2, and the rotor 3 is fixed in the cylinder body 1 through the rotor rotating shaft; the cylinder cover is provided with a blade guide rail 5, the blade guide rail 5 is an annular groove and is used for inserting a guide rail bearing of the blade, and the guide rail bearing is matched with the inner wall of the cylinder body 1 to control the motion track of the outer edge of the blade 4.
As shown in fig. 6 and 10, the rotor 3 is in a diamond column shape (but not limited thereto, it may also be in a circular shape), the cross section of the outer wall is in a regular hexagon shape (but not limited thereto, it may also be in a regular hexagon shape, it may also be in any polygon shape), the two ends of the rotor 3 are cylindrical rotor rotating shafts, which pass through the fixing holes 21 in the cylinder cover 2, the rotor 3 is placed at the central position in the cylinder body 1, so that the rotor 3 and the cylinder body 1 are axially kept the same, and the rotor 3 is limited to make a rotational movement relative to the cylinder body; one end of the rotor rotating shaft extends out of the cylinder cover 2 and is a torque and power output part; on the cross section, the different rotor radial directions form the distance difference between the inner wall of the cylinder body 1 and the outer wall of the rotor 3; hinge 8 is established to 3 outer wall edges and corners of rotor, and all hinges 8 equidistance distribute on the rotor outer wall, and hinge 8 cooperation hinge pivot 9 is used for linking with blade 4 and makes blade 4 swing on rotor 3.
As shown in fig. 12, the blade 4 is rectangular plate-shaped (not limited to plate-shaped), the hinge 8 is arranged at the inner edge, and the blade 4 adopts a structure a at the outer edge: the blades 4 are positioned between the cylinder body 1 and the rotor 3 and between the two cylinder covers 2, the inner edges of the blades 4 are connected to the rotor 3 in a hinge mode through hinges 8, and the blades can rotate and swing between the cylinder body 1 and the rotor 3; a blade round shaft 10 is arranged at the outer edge of the blade 4, a blade roller 12 (a built-in high-speed bearing) is embedded at the outer edge of the blade 4, and the blade round shaft 10 axially penetrates through the outer edge of the blade 4 and the blade roller 12 and extends out of the two ends of the blade 4; part of fixed guide rail fitting parts (guide rail bearings are adopted here) 11 extending from both ends of the blade circular shaft 10 control the motion track of the outer edge of the blade 4 under the matching of the blade guide rail 5; the vanes 4 make the outer edges of the vanes 4 tightly attached to the inner wall of the cylinder body 1 under the combined action of liquid (gas) pressure, the inner wall of the cylinder body 1 and the vane guide rails 5 through the guide rail bearings and the vane rollers 12. The diameter of the guide rail bearing is set slightly smaller than the groove width of the blade guide 5.
The working principle of the embodiment is as follows:
as shown in fig. 6, a space formed by the cylinder 1, the rotor 3, the cylinder head 2, and the vane 4 between the two vanes 4 is a motor fluid (gas) chamber. When the chamber is in the stage of pressing in liquid (gas), in the rotating direction of the rotor 3, under the action of the pressure of the liquid (gas) in the chamber, the circumferential force of the previous blade 4, which is transmitted to the hinge 8, is greater than the reverse force of the next blade 4, so that the pressure difference of the rotor 3 in the rotating direction is formed, the torque is formed to push the rotor 3 to rotate, and the chamber is in the working state at the stage. When the chamber is in the liquid (gas) discharge stage, the pressure of the chamber is small due to the release of the liquid (gas) pressure of the chamber, the reverse pressure formed by the front blade 4 and the rear blade 4 of the chamber III and the chamber IV is small, and the resistance formed by the rotation of the rotor 3 is small.
The working process of the embodiment is as follows:
as shown in fig. 6, the capacities of the chambers (i) and (iv) are in the minimum state, and the liquid (gas) in the chamber is in the state of a critical point of discharging, transferring and pressing; the second and fifth chambers are in the working state of continuously pressing in liquid (gas); the chamber is in the state of continuous discharge of liquid (gas).
As shown in fig. 7, when the rotor 3 rotates a certain angle, the chambers (i) and (iv) continue to be in the working state of liquid (gas) pressing from the previous working state; the capacity of the second chamber and the fifth chamber reaches the maximum, the liquid (gas) in the second chamber is at the critical point of pressing in, transferring out and ending the working state of the second chamber; the liquid (gas) in the chamber is in the state of continuous discharge.
As shown in the attached figure 8, the rotor continues to rotate for a certain angle, and the first chamber and the fourth chamber are in a state of continuously pressing in and doing work; the second and fifth chambers are in the liquid (gas) discharge state from the last working state; the chamber is in the state of continuous discharge of liquid (gas).
As shown in figure 9, the rotor rotates a certain angle, the first chamber and the second chamber are in a state of liquid (gas) continuously pressing in to do work, and enter the first chamber and the second chamber (shown in figure 1); the second and fifth chambers are in the state of continuous liquid (gas) discharge and enter the initial third and sixth chambers, the volume of the third and sixth chambers is the minimum, the chamber is in the critical point of liquid (gas) discharge and press-in, and enters the initial fourth and sixth chambers.
The working state of the power device is the working process that the rotor 3 rotates by 60 degrees; when the rotor 3 rotates 180 degrees, each bin can complete the complete process from liquid (gas) entering to discharge or from discharge to entering, namely each bin can complete a complete working process; the rotor 3 rotates 360 degrees, and each chamber can complete two complete working processes.
When the bin is in a working state, the front blade 4 of the bin is in a positive pressure state, and the front blade 4 is tightly attached to the inner wall of the cylinder body 1 due to the liquid (gas) pressure because the blade 4 and the inner wall of the cylinder body 1 form a certain angle, so that a good sealing effect is achieved.
As the preferred embodiment, the defect that the energy conversion efficiency of the motor is low due to the structure of the prior art of the vane motor is overcome, the novel structure is adopted, the movement of the vanes is smoother, the reliability is higher, the sealing performance is better, and the energy conversion efficiency and the power of the motor can be greatly improved.
The embodiment is a power device designed according to the invention, and is preferably a power device taking pressurized liquid as power.
Example 4:
the present embodiment is further optimized based on embodiment 3, and the same parts as those in the foregoing technical solutions will not be described herein again, as shown in fig. 16, in order to better implement the present invention, the following structure is particularly adopted: and a back pressure supporting spring 18 is arranged at the corresponding section (the blade 4 is in a back pressure state) from the discharge port 19 to the inlet 20 at the inner side of the blade guide rail 5 of the cylinder cover 2 and the outer edge of the blade 4, so that the gap between the blade 4 and the inner wall of the cylinder body 1 is reduced, and the sealing property of the blade motor is improved.
When the vane 4 is in a back pressure state, the gap caused by mechanical wear and the action of the liquid (gas) pressure may cause liquid (gas) leakage, and the scheme is an optimized scheme aiming at the problem.
As a preferred embodiment, this scheme aims to further improve the sealing performance and energy conversion efficiency of the power plant.
As shown in fig. 15 and 18, in order to better implement the present invention, an auxiliary blade 15 (back pressure sealing blade) is connected to the outer edge of the blade 4 and in front of the movement of the blade 4, the back edge (relative to the movement direction of the blade) of the auxiliary blade 15 is connected to the outer edge of the blade 4 by an auxiliary blade hinge 16, the two ends of the front edge of the auxiliary blade 15 are provided with auxiliary blade round shafts 17 which are matched with guide rail bearing pieces or sliding block pieces, the front edge movement track of the auxiliary blade 15 is controlled under the action of the blade guide rail 5 to be tightly attached to the inner wall of the cylinder body 1, when the auxiliary blade 15 runs on the corresponding section of the outer edge of the blade 4 from the discharge port 19 to the inlet 20 (the blade 4 is in a back pressure state), liquid (gas) is prevented from leaking; when the structure is particularly applied to a vane motor serving as an air pressure motor, the function of sealing the air inlet (the inlet 20) of the power device in advance can be achieved, the work is done by fully utilizing the expansion pressure of the gas, and the purpose of improving the efficiency of the power device is achieved.
The gas is different from the liquid, the compressed and expanded states exist, the compressed gas has certain energy, the scheme seals the inlet 20 in advance through the auxiliary blade, and the opening positions of the inlet and the outlet are adjusted according to the gas pressure and the expansion rate, so that the energy released by the expansion of the gas can be effectively utilized.
The scheme has a state that an air compression inlet is completely closed, and can be solved by designing a special starting air pressure channel, for example, the starting air pressure channel is designed between an inlet 20 and an outlet 19 of the rotor 3 in the rotating direction, and can be closed after the power device is started.
When the vane 4 is in a back pressure state, the gap caused by mechanical wear and the action of the liquid (gas) pressure can cause liquid (gas) leakage, and the scheme is another optimized scheme aiming at the problem.
As a preferable embodiment, the power device has better sealing performance, can fully utilize gas expansion pressure to do work, has higher energy conversion efficiency, and is suitable for the field with higher requirement on energy conversion efficiency or with the application of pressurized gas.
As shown in fig. 10 and 12, in order to better implement the present invention, a lubricant oil reservoir 6 and a lubricant oil channel 7 are provided on the rotor 3, a vane lubricant oil channel 14 is provided on the vane 4, the lubricant oil reservoir 6 and the hinge 8, the guide rail bearing and the vane roller 12 are communicated through the lubricant oil channel 7 and the vane lubricant oil channel 14, and when the rotor 3 and the vane 4 rotate, the lubricant oil is sent to the hinge 8 connecting the rotor 3 and the vane 4, the vane roller 12 connecting the vane 4, the guide rail bearing and the like by using a centrifugal force, so as to lubricate the movable parts.
As a preferred embodiment, the scheme aims to improve the convenience of equipment maintenance, reduce equipment abrasion and prolong the service life of the equipment.
In fig. 6 to 9, the arrow of the square frame is the flow direction of liquid (gas), and the arrow on the rotor 3 is the rotation direction of the rotor.
Example 5:
the embodiment is further optimized on the basis of the embodiment 3, and the same parts as the technical scheme are not repeated herein, in the embodiment, the design of the setting position of the liquid (gas) inlet and outlet is changed, the corresponding rotor and cylinder cover are also changed, during the setting, a rotor rotating shaft 3A is nested in the rotor 3, and a rotor axis input pipe 3B penetrating through the cylinder cover 2 on one side is nested in the rotor rotating shaft 3A; an inlet 20 is arranged between two adjacent hinges 8 in the circumferential direction of the rotor 3, an axis input port 20A is arranged on the radial direction of a rotor rotating shaft 3A, an input pipe input port 20B is arranged on the pipe wall of a rotor axis input pipe 3B, when the inlet 20, the axis input port 20A and the input pipe input port 20B are communicated, hydraulic fluid and air can enter a working chamber of the power device to do work, a discharge port 19 of the power device is still arranged on the cylinder body 1, and the setting criterion is as follows: when the space between two vanes 4, which is a chamber formed by the cylinder body 1, the rotor 3, the cylinder cover 2 and the vanes 4, reaches the maximum capacity, the position of the outer edge of the preceding vane 4 or the vane roller 12 in the rotation direction of the rotor 3 is the starting position of the discharge port 19, and when the space of the chamber reaches the minimum capacity, the position of the outer edge of the following vane 4 is the ending position of the discharge port 19.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications and equivalent variations of the above embodiments according to the technical spirit of the present invention are within the scope of the present invention.

Claims (11)

1. The utility model provides a swing blade hydropneumatic power device, includes cylinder body (1), cylinder cap (2), rotor (3) and blade (4), its characterized in that: the rotor (3) is movably connected with the inner edge of the blade (4), and the blade (4) can rotate and swing relative to the rotor (3).
2. An oscillating vane hydropneumatic power unit as claimed in claim 1 wherein: the outer wall of the rotor (3) is provided with hinges (8) connected with the inner edges of the blades (4), and the hinges (8) are arranged at equal intervals in the circumferential direction of the rotor (3).
3. An oscillating vane hydropneumatic power unit as claimed in claim 2 wherein: the shape of the section of the inner wall of the cylinder body (1) is formed by two arc sections in tangent or arc transition, and the centers of the two arc sections are eccentrically arranged; the arc center of one of the arc sections of the cylinder body (1) is concentric with the rotation center of the rotor (3), the length of the arc section is larger than or can cover the length of the arc section of the outer wall of the rotor (3) between two adjacent hinges (8) of the rotor (3), and the outer wall of the rotor (3) or the inner wall of the blade (4) is matched with the arc section of the inner wall of the cylinder body (1) concentric with the rotation center of the rotor (3) along the tolerance.
4. An oscillating vane hydropneumatic power unit as claimed in claim 2 wherein: the rotor (3) is provided with a lubricating oil storage bin (6) and a lubricating oil channel (7), the lubricating oil channel (7) is communicated with the lubricating oil storage bin (6) and the hinge (8), and the movable part is lubricated by centrifugal force generated when the rotor (3) rotates.
5. An oscillating vane hydropneumatic power unit as claimed in claim 4 wherein: the blade (4) is provided with a blade lubricating oil channel (14) which is communicated with the lubricating oil channel (7) through a hinge (8) to lubricate the movable part of the outer edge of the blade (4).
6. An oscillating vane hydropneumatic power unit as claimed in claim 2 or 3 or 4 or 5 wherein: a rotor rotating shaft (3A) is nested in the rotor (3), and a rotor shaft center input pipe (3B) penetrating through the cylinder cover (2) on one side is nested in the rotor rotating shaft (3A); an inlet (20) is arranged between two adjacent hinges (8) in the circumferential direction of the rotor (3), an axis input port (20A) is radially arranged on a rotor rotating shaft (3A), an input pipe input port (20B) is arranged on the pipe wall of a rotor axis input pipe (3B), and when the inlet (20), the axis input port (20A) and the input pipe input port (20B) are communicated, pressure liquid and gas can enter a working chamber of the power device to do work.
7. An oscillating vane hydropneumatic power unit as claimed in claim 1 or 2 or 3 or 4 or 5 wherein: the outer edge of the blade (4) is embedded with a blade roller (12).
8. An oscillating vane hydropneumatic power unit as claimed in claim 1 or 2 wherein: the inner wall of the cylinder cover (2) is provided with a blade guide rail (5) on the inner side of the inner wall of the cylinder body (1), the blade guide rail (5) is a groove, and the outer edge of the blade (4) is tightly attached to the inner wall of the cylinder body (1) under the action of the blade guide rail (5) arranged on the cylinder cover (2).
9. An oscillating vane hydropneumatic power unit as claimed in claim 8 wherein: the outer edge of blade (4) inlays and is equipped with blade cylinder (12) and blade circle axle (10), blade circle axle (10) extend the both ends of blade (4), are provided with guide rail fitting piece (11) that can do the orbit motion in blade guide rail (5) on the both ends of blade circle axle (10), make the inner wall that cylinder body (1) is pressed close to along and cylinder (12) outward blade (4).
10. An oscillating vane hydropneumatic power unit as claimed in claim 8 wherein: the outer edge and the motion front of the blade (4) are also connected with an auxiliary blade (15), the rear edge of the motion direction of the auxiliary blade (15) is connected with the outer edge of the blade (4) by an auxiliary blade hinge (16), the two ends of the front edge of the auxiliary blade (15) are provided with auxiliary blade round shafts (17), and the auxiliary blade round shafts (17) are matched with guide rail bearing parts or sliding block parts which can control the front edge of the auxiliary blade (15) to be tightly attached to the inner wall of the cylinder body (1) to move along a track under the action of the blade guide rail (5).
11. An oscillating vane hydropneumatic power unit as claimed in claim 8 wherein: and a back pressure supporting spring (18) is arranged on the inner side of the blade guide rail (5) on the cylinder cover (2) and on the corresponding section of the blade (4) subjected to the reverse pressure.
CN202010645345.8A 2019-11-19 2020-07-07 Hydraulic power device with swinging blades Pending CN111608851A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2020/127509 WO2021098542A1 (en) 2019-11-19 2020-11-09 Swing blade-type hydraulic power device

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Application Number Priority Date Filing Date Title
CN2019111321244 2019-11-19
CN201911132124.4A CN110761937A (en) 2019-11-19 2019-11-19 Oscillating blade motor

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Publication Number Publication Date
CN111608851A true CN111608851A (en) 2020-09-01

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CN201911132124.4A Pending CN110761937A (en) 2019-11-19 2019-11-19 Oscillating blade motor
CN202010645345.8A Pending CN111608851A (en) 2019-11-19 2020-07-07 Hydraulic power device with swinging blades

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CN116357407A (en) * 2023-05-31 2023-06-30 日照职业技术学院 Centrifugal constant speed device for steam turbine

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WO2021098542A1 (en) * 2019-11-19 2021-05-27 李光惠 Swing blade-type hydraulic power device
CN116357407A (en) * 2023-05-31 2023-06-30 日照职业技术学院 Centrifugal constant speed device for steam turbine
CN116357407B (en) * 2023-05-31 2023-08-18 日照职业技术学院 Centrifugal constant speed device for steam turbine

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