WO2014166431A1 - Dispositif de rotation et moteur hydraulique, moteur, compresseur et pompe correspondants - Google Patents

Dispositif de rotation et moteur hydraulique, moteur, compresseur et pompe correspondants Download PDF

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Publication number
WO2014166431A1
WO2014166431A1 PCT/CN2014/075221 CN2014075221W WO2014166431A1 WO 2014166431 A1 WO2014166431 A1 WO 2014166431A1 CN 2014075221 W CN2014075221 W CN 2014075221W WO 2014166431 A1 WO2014166431 A1 WO 2014166431A1
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WIPO (PCT)
Prior art keywords
rotating device
cylinder
cylindrical
rotary valve
rotor assembly
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Ceased
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PCT/CN2014/075221
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English (en)
Chinese (zh)
Inventor
姚镇
姚其槐
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Individual
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Individual
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Publication of WO2014166431A1 publication Critical patent/WO2014166431A1/fr
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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/46—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the outer 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • 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
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to the field of fluid machinery, and more particularly to a rotating device and its corresponding fluid motor, engine, compressor and pump. Background technique
  • the star-rotating device includes: a cylinder body including a cylindrical cavity; and a main shaft supported by a cylinder sealing end cover on both sides of the cylinder block, the center sun wheel roller is sleeved on the main shaft;
  • the outer cylindrical surface of the wheel drum and the inner cylindrical surface of the cylinder form an annular piston space;
  • the annular piston space can communicate with the fluid inlet/outlet through the first set of through holes, and can pass through the second set of through holes and the fluid outlet/inlet
  • the planetary piston wheel is placed in the annular piston space in a rolling manner, and the two ends extending outside the annular piston space are connected to the main shaft through a connecting member;
  • the planetary piston wheel is a cylindrical roller; and the isolation structure is located in the annular piston space.
  • the eccentric rotor compressor is one of the existing compressors.
  • a typical eccentric rotor compressor is given in Reference 2 (Patent Application No.: 200780027498.9).
  • the rolling rotor type compressor includes a cylinder 1, a rolling rotor 2, an eccentric sleeve 3, a drive shaft 4 having an eccentric crank portion, a swinging stopper, and a coil spring.
  • An eccentric sleeve 3 capable of flexibly rotating between them is provided between the children 2, so that the eccentricity of the rolling rotor 2 is adjusted and a flexible rolling contact seal is realized in operation.
  • the eccentric sleeve 3 the surface revolves around the drive shaft, and rotates around the center of the eccentricity.
  • This type of eccentric rotor compressor has the advantages of simple structure and stable operation, and has a very wide application in the field of compressors.
  • the present invention provides an eccentric rotor type rotating device capable of achieving a reliable cylinder seal in an oil-free working scene and its corresponding fluid motor, engine, compressor and pump.
  • a turning device comprises: a cylinder body having a cylindrical shape; and a front/rear sealing end cover respectively sealed and connected to the front/rear ends of the cylinder body, and forming a cylindrical inner cavity together with the cylinder body; the main shaft, the cylinder body And/or the front/rear sealing end cap is rotatably supported, the central axis of which coincides with the central axis of the cylindrical inner cavity; the rotor assembly is sleeved over the portion of the main shaft located in the cylindrical inner cavity, through the cylindrical shape
  • the rotary motion in the cavity forms an axially extending sealed working space;
  • the isolation mechanism has an end sealed with the rotor assembly, thereby separating the axially extending sealed working spaces from each other independently through the first one disposed on the cylinder a first volume variable chamber and a second volume variable chamber communicating with the second through hole and the outer side of the cylinder; and a cylinder sealing assembly located outside the rotor assembly in the cylindrical inner
  • a fluid motor is also provided.
  • the fluid motor includes the above-described rotating device, wherein the second set of through holes of the rotating device are in communication with the high pressure fluid inlet; the first set of through holes are in communication with the low pressure fluid outlet.
  • an engine is also provided.
  • the engine includes the above-described rotating device, wherein the second set of through holes of the rotating device are in communication with the combustion chamber; the first set of through holes are in communication with the exhaust gas discharge port.
  • a compressor is also provided.
  • the compressor includes the above-described rotating device, wherein the second set of through holes of the rotating device are connected to the input port of the low pressure compressed medium, and the first set of through holes communicate with the discharge port of the compressed high pressure compressed medium.
  • a pump is also provided.
  • the pump includes the above-described rotating device, wherein the first set of through holes of the rotating device are in communication with the fluid inlet; and the second set of through holes are in communication with the fluid outlet.
  • the rotating device of the present invention and its corresponding fluid mechanical device have the following beneficial effects:
  • the non-contact sealing of the cylinder cavity is realized by the gas film or liquid film lubrication design between the expansion piston ring and the star wheel fixing flange, so that the rotating device can operate in a high frequency-oil-free working environment.
  • FIG. 1 is a schematic structural view of a prior art star-rotating device
  • FIG. 2 is a schematic structural view of a prior art eccentric rotor compressor
  • Figure 3A is a cross-sectional view of a rotating device in accordance with an embodiment of the present invention.
  • Figure 3B is a cross-sectional view of the rotating device of Figure 3A in the AA direction of the air inlet opening state
  • Figure 3C is a cross-sectional view of the rotating device of Figure 3A in the AA direction of the air inlet closing state
  • Figure 4A is the rotation of Figure 3
  • FIG. 4B is a perspective view of the components inside the cylindrical surface of the rotating device shown in FIG. 3
  • FIG. 4C is a star wheel fixing flange of the rotating device shown in FIG. 3A; a partial enlarged view of the rolling piston wheel, the eccentric crankshaft and the rolling bearing joint;
  • Figure 5 is a schematic view showing the friction between the expansion piston ring and the cylinder block and the star wheel fixing flange in the rotating device according to the embodiment of the present invention
  • FIG. 6A is a schematic view showing the matching of an expansion piston ring in a cylinder seal assembly and an outer cylindrical surface of a star wheel fixing flange in a rotary device according to another embodiment of the present invention
  • 6B is a schematic view showing the matching of the expansion piston ring of the cylinder seal assembly and the outer cylindrical surface of the star wheel fixing flange in the cylinder sealing assembly according to still another embodiment of the present invention
  • 6C is a schematic view showing the matching of the expansion piston ring of the cylinder seal assembly and the outer cylindrical surface of the star wheel fixing flange in the cylinder sealing assembly according to still another embodiment of the present invention
  • FIG. 7A to 7H are schematic views showing the operation of a fluid motor according to an embodiment of the present invention.
  • Fig. 8 is a cross-sectional view showing a fluid motor including two rotating devices according to an embodiment of the present invention.
  • 9A is an output torque curve of a fluid motor including only one rotating device according to an embodiment of the present invention.
  • Figure 9B is an output torque curve of a fluid motor including two rotating devices in accordance with an embodiment of the present invention. detailed description
  • the applicant of the present invention draws on the structure of the eccentric rotor compressor in the prior art, and proposes a non-mechanical contact reliability of the cylinder cavity by means of the piston wheel fixing flange and the expansion piston ring. Sealed rotating device and its corresponding fluid motor, engine, compressor and pump.
  • 600-cylinder seal assembly 611, 612-star wheel fixed flange
  • A-first rotating device B-second rotating device
  • a rotating device is provided.
  • 3A is a cross-sectional view of a rotating device in accordance with an embodiment of the present invention.
  • 3B and 3C are cross-sectional views of the rotating device of Fig. 3A in the AA direction in two states, respectively.
  • the rotating device includes: a cylinder block 110 having a cylindrical shape, and a cylinder main body 111 and a front cylinder head 112 and a rear cylinder head 113 respectively disposed at front/rear end faces of the cylinder main body 111.
  • the front/rear sealing end caps (120, 130) are respectively sealed on the cylinder heads connected to the front and rear ends of the cylinder block, and form a cylindrical inner cavity together with the cylinder block;
  • the main shaft 200 is composed of the cylinder block 110 And/or front/rear sealing end caps (120, 130) are rotatably supported,
  • the central axis coincides with the central axis of the cylindrical inner cavity;
  • the rotor assembly is sleeved on the portion of the main shaft 200 located in the cylindrical inner cavity, and the axially extending sealed working space is formed by rotating motion in the cylindrical inner cavity
  • An isolation mechanism having a front end sealed with the rotor assembly to partition the axially extending sealing working space into mutually independent first volume variable chambers and second volume variable chambers, the first volume variable chamber And the second volume variable chamber communicates with the outside of the cylinder through the first set of through holes and the second set of through holes provided on the cylinder; and the cylinder seal assembly 600, the rotor assembly in the cylindrical
  • the cylinder seal assembly 600 includes: two star wheel fixing flanges (611 and 612) respectively disposed in a cylindrical inner cavity inside the front/rear cover, interlocking with the rotor assembly, and engaging the main shaft through the key.
  • An inlay groove is formed in a middle portion of the outer cylindrical surface;
  • two expansion piston rings (621, 622) are respectively respectively fixed and fixed in the inlay groove of the outer cylindrical surface of the two star wheel fixing flange, and are sealingly matched with the inner cylindrical surface of the cylinder body, and Forming a gap with a predetermined size of the bottom and the side wall of the inlaid groove; a trace of fluid leaking from the gap forms a fluid film under the rotation of the star wheel fixing flange, and the fluid film realizes the inside of the cylinder The seal of the cavity.
  • the preset size is between 0.02mm and 0.3mm.
  • the cylinder block 110 has a cylindrical shape and has an inner cylindrical surface.
  • the cylinder block 110 includes a cylinder main body 111, and a front cylinder head 112 and a rear cylinder head 113 which are respectively disposed at front/rear end faces of the cylinder main body 111.
  • a cylinder head 140 is provided at a predetermined position outside the cylinder main body 111, generally upward.
  • the rotary valve body of the subsequent isolation mechanism and its reset mechanism are set corresponding to the position of the cylinder head 140, which will be described in detail below.
  • the front/rear sealing end caps (120 and 130) are respectively sealed to the front/rear ends of the front/rear cylinder heads (112 and 113) of the cylinder block 110, and together with the cylinder block 110 constitute a cylinder. Shape the lumen.
  • the cylindrical inner cavity is the working area of the rotating device of this embodiment.
  • the radial positioning and axial positioning of the spindle 200 in the middle of the cylinder is very important. Normally, both radial and axial positioning are accomplished by rolling bearings. The radial clearance and axial clearance of the rolling bearing must meet the requirements of the spindle's rotation accuracy.
  • the main shaft 200 transmits torque between the outside and the inside of the cylindrical inner cavity. Taking the compressor as an example: Referring to FIG. 3A, the first portion of the main shaft 200 is located outside the cylindrical inner cavity, and is connected to the external power source to transmit the torque input from the external power source to the cylindrical inner cavity; In the cylindrical inner cavity, the torque input by the external power source drives the eccentric rotor assembly 300 to rotate.
  • the rotor assembly is sleeved over a portion of the main shaft 200 that is located in the cylindrical inner cavity, and an axially extending sealed working space is formed by rotational movement within the cylindrical inner cavity.
  • the front end of the isolation mechanism is sealed with the rotor assembly, thereby separating the sealed working space into mutually independent first volume variable chambers and second volume variable chambers, the first volume being The variable chamber and the second variable volume chamber are respectively in communication with the outside of the cylinder through a first set of through holes and a second set of through holes provided in the cylinder.
  • Fig. 4A is a cross-sectional view showing the components inside the cylindrical surface of the cylinder in the rotating device shown in Fig. 3.
  • Figure 4B is a perspective view of the components inside the cylindrical surface of the cylinder in the rotating device of Figure 3. It should be noted that in Fig. 4B, in order to clearly show the components such as the rolling bearing 320, the rolling piston wheel 330 outside the rolling bearing 320 is omitted.
  • the rotor assembly is an eccentric rotor assembly 300.
  • the eccentric rotor assembly 300 is sleeved on a portion of the main shaft 200 located in the cylindrical inner cavity, and includes: an eccentric crankshaft 310 disposed on a portion of the main shaft 200 located in the cylindrical inner cavity, the central axis of which is parallel to the central axis of the main shaft 200 And shifting the preset distance; the rolling piston wheel 330 is sleeved on the eccentric crankshaft 310, and its central axis coincides with the central axis of the eccentric crankshaft 310.
  • the rolling piston wheel 330 rolls along the inner cylindrical surface of the cylinder block 110, and an axially extending crescent-shaped sealing working space is formed between the inner cylindrical surface of the cylinder block 110 and the outer cylindrical surface of the rolling piston wheel 330.
  • the selection of the eccentric amount e of the eccentric crankshaft is the key to the design of the mechanism, which cannot be designed too large or too small.
  • the eccentricity is too small, the diameter of the eccentric crankshaft is too large, and the output torque of the motor is smaller; the eccentricity e is too large, although the torque becomes larger, the instantaneous power required for starting the motor is larger, the device starts up. Difficulties, practicality is affected. Only when the eccentricity e is between R/8 and R/5 can the balance be achieved under high torque and low starting power, which meets the practical requirements, where R is the radius of the cylindrical surface in the cylinder.
  • the rotating device of the embodiment in order to reduce the friction between the eccentric crankshaft 310 and the rolling piston wheel 330, the rotating device of the embodiment further includes: at least two rolling bearings 320 symmetrically sleeved on the eccentric crankshaft 310, wherein the inner ring is fixed to The eccentric crankshaft 310 has an outer ring fixed to the rolling piston wheel 330 to isolate the rotation of the two.
  • the pre-tightening elastic force between the rolling bearing and the rolling piston wheel presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity, and the inner cylindrical surface of the cylindrical inner cavity and the outer cylinder of the rolling piston wheel
  • the face forms an axially extending crescent-shaped sealed chamber.
  • the star wheel fixing flange is in an "L" shape toward the center of the cylindrical cavity; the left star wheel fixing flange 611 and the right star wheel fixing flange 612 are symmetrically arranged.
  • the outer side of the eccentric crankshaft 310 On the main shaft, the outer side of the eccentric crankshaft 310.
  • the star wheel mounting flanges on the same side are integrally formed or separately formed with the eccentric crankshaft. There is no relative movement between the eccentric crankshaft and the star wheel mounting flange, and zero leakage is achieved.
  • the machining difficulty of the eccentric crankshaft depends on the structure.
  • the machining accuracy of the integrated eccentric crankshaft is not easy to guarantee.
  • the eccentric crankshaft is divided into two parts: the rotating center base and the crankshaft neck, the connection between the mother and the crankshaft is fixed. Positioning the eccentric hole on the crankshaft neck and opening an eccentric hole in a symmetrical cylinder ensures accuracy. As long as there is an eccentric hole, the machining assembly of the eccentric curved shaft is much easier.
  • Fig. 4C is an enlarged view of the joint portion of the star wheel fixing flange, the rolling piston wheel, the eccentric curved shaft and the rolling bearing in the rotating device shown in Fig. 3A.
  • the inner side of the eccentric crankshaft is provided with a shoulder
  • the inner ring of the rolling bearing is fixed to the shoulder of the eccentric crankshaft
  • the outer ring is fixed to the rolling piston wheel.
  • the "L" shaped labyrinth seal is formed between the side of the rolling piston wheel and the corresponding position of the side of the star wheel fixing flange of the outer side, and the corresponding part of the outer side of the eccentric crankshaft shoulder and the cylindrical surface of the rolling piston wheel. .
  • the two end faces of the high-speed rotating rolling piston wheel can be stably maintained for a long time under the guarantee of the radial and axial precision positioning of the star-rail supporting rolling bearing.
  • the frictional interface has a small gap that effectively controls the leak.
  • the values of the gap ⁇ are: 0.03 mm; 0.04 mm; 0.05 mm; 0.055 mm; 0.06 mm.
  • the cylindrical internal cavity of the five fluid motors is well sealed.
  • the rotor assembly can be other types of rotor assemblies, such as the applicant of the present invention in prior patents.
  • the proposed star-rotor rotor assembly comprises: a central sun gear roller sleeved on the main shaft and a plurality of cylindrical planets forming an annular piston space rolling on an outer cylindrical surface of the central sun gear drum and an inner cylindrical surface of the cylinder body Piston wheel.
  • the isolation mechanism is a rotary valve body isolation mechanism 400.
  • the rotary valve body isolation mechanism 400 includes: a rotary valve body 412 and a rotary valve body reset mechanism 420.
  • the rotary valve body 412 is pressed by the rotary valve body reset mechanism 420, and the end is always pressed against the outer surface of the rolling piston wheel, thereby separating the crescent-shaped sealing working space into mutually independent first variable volume chambers and second volume. Variable chamber.
  • the position of the cylinder main body 111 corresponding to the cylinder head 140 is formed with an axially extending receiving recess which is open toward the cylindrical inner cavity.
  • the rotary valve body 412 is fitted in the receiving recess and rotatably supported by the receiving recess and is swung within a predetermined angular range.
  • the eccentric rotor assembly is rotated to the upper position, the rotary valve body 412 is pressed into the receiving recess and is pressed.
  • the eccentric rotor assembly is rotated to the lower position, the rotary valve body swings to its maximum position and is extended.
  • the rotary valve body 412 divides the axially extending sealing working space into mutually independent first volume variable chambers and second volume variable chambers, and the chamber whose front surface is defined is a second chamber, the back side thereof The chamber facing is the first chamber.
  • the ⁇ may be between 30° and 40°.
  • the rotary valve body is a sheet-like structure, that is, a rotary valve piece.
  • the rotary valve body may also be a semicircular structure as shown in FIG. 2 or the like.
  • the isolation mechanism of the present invention can also adopt other types of valve bodies, such as: rotary valve disc (patent application number: 200780027498.9); gate valve (patent Application Number: 201110322746.0); Rotary rotary valve (patent application number: 201110145313.2) and so on.
  • the installation methods of these isolation mechanisms can be referred to the relevant literature and will not be described in detail here.
  • the rotary valve body return mechanism 420 is for pressing the rotary valve body to the outer cylindrical surface of the rolling piston wheel at all times.
  • the position of the side-rotating valve body is opened with a blind hole for the pin.
  • a slidably sealable reset pin 422 is inserted into the pin blind bore with the end facing in the direction of the rotary valve body.
  • the elastic member is located in the pin hole inside the reset pin 422, and the end thereof abuts against the tail portion of the reset pin 422, and the elastic force generated causes the head of the reset pin 422 to bear against the rotary valve body in the direction toward the rotary valve body. , achieving a reset seal of the rotary valve body.
  • the rotary valve body reset mechanism can also be other types of reset mechanisms, such as a mechanical reset mechanism disposed outside the cylinder.
  • the mechanical resetting mechanisms are described in detail in the applicant's prior patent (patent application number: 201120071995.2), which is not repeated here.
  • the cylinder seal assembly 600 is located in the cylindrical inner cavity, and the outer side of the rotor assembly includes: two star wheel fixing flanges (611 and 612) respectively disposed on the front/rear cover (120 And 130) in the inner cylindrical inner cavity, by the key and the main shaft, interlocking with the rotor assembly, the middle of the outer cylindrical surface is provided with a setting groove; the two expansion piston rings (621 and 622) are respectively expanded and fixed to the two star wheel
  • the fixing flanges (611 and 612) have a sealing fit with the inner cylindrical surface of the cylinder 110 in the inlaid groove of the outer cylindrical surface (such as the fastening sealing surface shown in FIG. 5), and have the bottom and side walls of the mounting groove.
  • the gap of the preset size for example: 0.02mm ⁇ 0.3mm gap.
  • the two-wheel fixed flange and the eccentric crankshaft are fixed by a flange crankshaft fixing pin, and the fixed flange still has to be engaged with the main shaft through the key.
  • the two-wheel fixed flange is coupled to the cylindrical planetary piston wheel.
  • the fixed flange is keyed to the spindle.
  • Fig. 5 is a schematic view showing the friction between the expansion piston ring and the cylinder block and the star wheel fixing flange in the rotating device according to the embodiment of the present invention. The wear of the piston ring and the outer cylinder inner wall and the inner star wheel fixing flange will be analyzed and described below with reference to FIG.
  • the clearance between the outer cylindrical surface of the star wheel fixing flange and the cylindrical surface of the cylinder is 0.08 mm AC 0.3 mm.
  • the expansion piston rings (621 and 622) and the star wheel fixing flanges (611 and 612) have a fine gap of 0.02 mm to 0.3 mm between the side and the bottom of the mounting groove, which ensures the sealed working space. It is substantially complete and can ensure that trace gases are leaked from the fine gap.
  • the secret of the cylindrical inner cavity sealing of the present invention lies in the leaked trace gas.
  • the rotating motion of the star wheel fixing flanges (611 and 612) will bring a trace of gas into the fine gap to form a gas film, which will produce fluid lubrication effect, which will ensure the friction loss of the contact surface between the star wheel fixing flange and the piston ring is minimized.
  • a highly efficient and low-cost rotary dynamic seal for the cylindrical cavity is achieved.
  • the leaked pressure fluid forms a pressure gradient difference in the axial inner and outer sides of the expansion piston ring, that is, the pressure gradient difference formed by the high pressure gas zone inside the star wheel fixed flange and the outer low pressure gas zone. .
  • the fine gap ⁇ of the expansion piston ring and the sidewall of the mounting groove satisfies: 0.05 mm ⁇ AA ⁇ 0.3 mm
  • the expansion piston ring and the mounting groove The fine gap ⁇ at the bottom satisfies: 0.1 mm AB 0.3 mm.
  • the expansion piston ring is an open piston ring.
  • the material is selected according to the working conditions, such as centrifugally cast bronze alloy at high temperature and high-strength aluminum alloy at normal temperature. The following are the values of the gaps in the five fluid motors prepared by applying the present invention:
  • the present invention also provides additional cylinder sealing assemblies.
  • a two-stage expansion piston ring is used in the first type of cylinder seal assembly.
  • the two-stage expansion piston ring constitutes a two-stage sealing surface, that is, as shown in the figure.
  • This construction has a better sealing effect than the configuration of the first sealing surface shown in Fig. 5.
  • those skilled in the art can set the number of the expansion piston rings as needed, for example: 3, 4, 5, or even more.
  • a labyrinth seal is used between the expansion piston ring and the inlay groove, and the inner annular surface of the expansion piston ring and the bottom of the inlay groove are engaged with each other, thereby optimizing the sealing effect.
  • the inner ring of the expansion piston ring has a sawtooth shape
  • the bottom of the inlay groove also has a corresponding serration
  • the shape thus constitutes a toothed sealing surface as shown in Fig. 6B.
  • the sawtooth shape may also be an irregular relief structure or stripe, and may also produce the same effect.
  • the bottom of the star wheel fixed flange inlay groove and the inner ring of the expansion piston ring each have an arcuate ball channel in which spherical balls are arranged.
  • the ball channel Under the action of the gradient pressure gas, the ball channel will be clamped by the distance ⁇ , and the spherical ball will be clamped.
  • the gap between the inner circumference of the expansion piston ring and the bottom of the star wheel fixing flange is about 0.1mm. ) It can be made small due to the reliable positioning support of the spherical ball, which improves the sealing precision, and the clamped spherical ball generates radial pressure on the expansion piston ring, making it more tightly fixed to the cylinder wall, as shown in Fig.
  • the expansion piston rings of this type of cylinder seal assembly can also be fabricated in sections, especially for large fluid machines.
  • the spherical ball can be selected from steel balls, and the material of the ball channel of the expansion piston ring and the star wheel fixing flange can be referred to the bearing material.
  • the rotor assembly is an eccentric rotor assembly
  • a balance weight in order to ensure the dynamic balance of the entire star-rotating device, a balance weight must be performed at a suitable position.
  • the balance weight In the conventional rotating device rotor assembly, the balance weight is located in the cylindrical inner cavity and is fixed on the eccentric crankshaft or the main shaft.
  • the star wheel fixing flange provides a suitable carrier for the balance weight. .
  • the balance weight 630 is symmetrically disposed on the lighter side of the eccentric crankshaft.
  • the balance weight is generally in the form of an incomplete ring and is fixed to the eccentric crankshaft by a flanged pin.
  • the balance weight is located in the cylindrical inner cavity, the balance weight is disposed on the outer side of the cylindrical inner cavity to facilitate the adjustment of the later dynamic balance.
  • a fluid motor in another exemplary embodiment of the invention, is also provided.
  • the fluid motor includes the above rotating device, and in the rotating device, the second variable volume chamber passes through the second The group of through holes is in communication with the high pressure fluid inlet; the first volume variable chamber communicates with the low pressure fluid outlet through the first set of through holes; the high pressure fluid pushes the eccentric rotor to rotate, and the torque generated by the main shaft is transmitted to the cylindrical inner cavity outer.
  • the rotary device shown therein includes a rotary valve body reset mechanism that is particularly applied to fluid motors and engines.
  • the top end of the pin blind hole communicates with the second set of through holes through the first bypass, and the bottom communicates with the receiving groove through the second bypass, and the elastic member is a high pressure fluid that enters the pin hole.
  • Figure 9A is a schematic illustration of the output torque of a fluid motor including a rotating device in accordance with an embodiment of the present invention. As shown in Fig. 9A, the torque output by the fluid motor is not stable, there are cases of output torque peaks and troughs, and in some cases there is a starting dead point.
  • a fluid motor comprises a T-stage rotating device in series, wherein in any one of the T-rotating devices: the second set of through holes communicate with the high pressure fluid inlet; the first set of through holes and the low pressure fluid outlet Connected.
  • the phase angles ⁇ of the at least two rotating devices in the T-turn rotating device are offset from each other by an angle greater than a critical interval angle ⁇ 1 ⁇ where the phase angle ⁇ of the rotating device means: starting from the high-pressure fluid working stroke of the cycle, the rotor assembly is in a circle The angle of rotation in the cylindrical cavity.
  • the critical section angle 6i refers to the angle of rotation of the rotor assembly in the cylindrical interior cavity from the beginning of the low pressure fluid discharge stroke of the previous cycle to the beginning of the high pressure fluid work stroke of the cycle.
  • the value of the 0 1 is generally between 20° and 40°.
  • the phase angles ⁇ of the two rotating devices adjacent in phase in the T-table rotating device are mutually offset by an angle of 360/T.
  • the phase angles ⁇ of the two rotating devices are shifted by 180° from each other;
  • the phases of the three rotating devices At some point, the corners are: 0°, 120. , 240. .
  • a fluid motor including two rotating devices sharing the same main shaft is shown in Fig. 8.
  • the left and right two rotating devices ( ⁇ and ⁇ ) are separated by a sealing partition C, and the phases of the rolling piston wheels of the two are shifted by 180 degrees, when the rolling piston wheel of one rotating device passes the motor
  • the piston roller has no thrust, that is, at the dead point, but the piston roller of the other rotating device whose phase is shifted by 180 degrees has thrust and is at the maximum torque point, thus overcoming the problem of starting dead point.
  • the output combined torque of the two rolling piston wheels is filled with each other due to the pulse peaks and valleys of the "respective", and becomes a flat constant torque.
  • Figure 9 is a schematic view showing the output torque of a fluid motor including two rotating devices in parallel according to an embodiment of the present invention. Comparing Fig. 9 ⁇ with Fig. 9 ⁇ , it can be seen that the output torque of the fluid motor including the two rotating devices in parallel is much smoother and there is no dead point.
  • an engine including the above-described rotating device, and wherein the second variable-capacity chamber communicates with the combustion chamber through the second set of through holes
  • the first volume variable chamber communicates with the exhaust gas discharge port through the first set of through holes.
  • the high pressure gas entering from the combustion chamber pushes the eccentric rotor assembly to roll along the cylindrical inner cavity, and the eccentric rotor assembly drives the main shaft to rotate, and the torque generated by the main shaft is transmitted to the outside of the cylindrical inner cavity.
  • the rotary valve body reset mechanism in the fluid motor embodiment can also be applied to the engine of the embodiment.
  • the working stroke of the engine of the present embodiment is similar to the working stroke of the above-described compressor, except that only the high-pressure fluid that drives the eccentric rotor is moved, but the high-pressure gas generated in the combustion chamber.
  • an engine in order to ensure a smooth output torque of the engine and avoid a start dead point, in still another exemplary embodiment of the present invention, is also provided.
  • the engine includes the above-described rotating device of the S stage sharing the same main shaft, wherein S ⁇ 2, the detailed configuration of which is similar to that described in the fluid motor, and will not be repeated here.
  • a compressor is further provided.
  • the first variable volume chamber is a suction chamber that communicates with a low pressure compressed medium input port through a second set of through holes;
  • the second variable volume chamber is a compression chamber, that is, a high pressure chamber, It communicates with the discharge port of the compressed high pressure compressed medium by discharging the first set of through holes.
  • the main shaft transfers torque outside the cylindrical inner cavity into the cylindrical inner cavity and compresses the compressed medium through the eccentric rotor assembly.
  • a pump is again provided.
  • the first variable volume chamber is in communication with the fluid inlet through the first set of through holes;
  • the second variable volume chamber is in communication with the fluid outlet through the second set of through holes.
  • the main shaft transmits the torque outside the cylindrical inner cavity into the cylindrical inner cavity; under the driving of the main shaft, the rolling piston wheel rolls forward along the cylindrical inner cavity, and the fluid entering from the fluid inlet is pumped into the crescent seal working.
  • the space discharges the fluid through the fluid outlet.
  • the present invention provides a rotating device and its corresponding engine, fluid motor, compressor and pump.
  • the sealed working space is realized at high frequency and without oil. Reliable sealing under the condition; further, a fluid motor and an engine having a reset mechanism for fluid opening and closing of the rotary valve plate are proposed, which simplifies the mechanical structure and improves the working efficiency of the rotating device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un dispositif de rotation et un moteur hydraulique, un moteur, un compresseur et une pompe comprenant le dispositif de rotation. Dans le dispositif de rotation, des rainures d'incrustation permettant la fixation de segments de piston de détente (621, 622) sont formées au milieu de surfaces cylindriques externes de deux bords fixes d'une roue en étoile (611, 612), les segments de piston de détente (621, 622) sont en ajustement étanche avec la surface cylindrique interne d'un cylindre et présentent des espaces d'une taille prédéterminée par rapport aux parties inférieures et parois latérales des rainures d'incrustation, une toute petite quantité de fluide fuyant des espaces est entraînée par le mouvement de rotation des bords fixes de la roue en étoile (611, 612) pour former une lubrification par film de gaz ou une lubrification par film de fluide, et un joint sans contact pour une cavité interne cylindrique est par conséquent réalisé et le dispositif de rotation peut fonctionner dans un environnement à haute fréquence sans huile.
PCT/CN2014/075221 2013-04-12 2014-04-12 Dispositif de rotation et moteur hydraulique, moteur, compresseur et pompe correspondants Ceased WO2014166431A1 (fr)

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CN201310127518.7A CN104100299B (zh) 2013-04-12 2013-04-12 转动装置及应用其的流体马达、发动机、压缩机和泵

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CN106151025B (zh) * 2015-03-25 2018-04-20 北京星旋世纪科技有限公司 转动系统及应用其的流体马达、压缩机、泵和发动机
CN106468178B (zh) 2015-08-21 2018-06-08 北京星旋世纪科技有限公司 应用压动闸阀机构的转动装置、转动系统及流体机械
BR112018008036A2 (pt) 2015-11-18 2018-10-23 Nestec S.A. disposição de compressor giratório
WO2018027801A1 (fr) * 2016-08-11 2018-02-15 姚镇 Système rotatif, et moteur hydraulique, compresseur, pompe et moteur utilisant ce dernier
CN107435628B (zh) * 2016-05-25 2019-05-10 北京星旋世纪科技有限公司 定位密封组件及应用其的转动装置、转动系统和流体机械
WO2017201895A1 (fr) * 2016-05-25 2017-11-30 姚镇 Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif
CN107489459A (zh) * 2016-06-13 2017-12-19 天津思高科技发展有限公司 一种气体高压封闭式整体发电装置
CN106768566B (zh) * 2017-03-15 2023-05-05 广西大学 一种滚动活塞压缩机滑片与滑槽的摩擦力测量装置
CN110332114A (zh) * 2019-06-10 2019-10-15 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机泵体结构、装配方法及转子压缩机
CN111396367A (zh) * 2020-05-11 2020-07-10 山东省章丘鼓风机股份有限公司 一种减阻抗磨渣浆泵蜗壳
CN111878389A (zh) * 2020-09-08 2020-11-03 青岛大学 一种内燃式摆动刮板泵
CN113383811A (zh) * 2021-07-01 2021-09-14 江西兆瑞机械设备制造有限责任公司 一种猪酮体单刀开边装置

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