WO2017201895A1 - Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif - Google Patents

Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif Download PDF

Info

Publication number
WO2017201895A1
WO2017201895A1 PCT/CN2016/095995 CN2016095995W WO2017201895A1 WO 2017201895 A1 WO2017201895 A1 WO 2017201895A1 CN 2016095995 W CN2016095995 W CN 2016095995W WO 2017201895 A1 WO2017201895 A1 WO 2017201895A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotating
positioning
rotating device
chamber
eccentric rotor
Prior art date
Application number
PCT/CN2016/095995
Other languages
English (en)
Chinese (zh)
Inventor
姚镇
姚其槐
Original Assignee
姚镇
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201610354113.0A external-priority patent/CN107435628B/zh
Priority claimed from PCT/CN2016/094642 external-priority patent/WO2018027801A1/fr
Application filed by 姚镇 filed Critical 姚镇
Publication of WO2017201895A1 publication Critical patent/WO2017201895A1/fr

Links

Images

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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/24—Compensation of inertia forces of crankshaft systems by particular disposition of cranks, pistons, or the like

Definitions

  • the present invention relates to the field of fluid machinery, and more particularly to a rotating system and a fluid motor, compressor, pump and engine using the same.
  • the eccentric rotor structure is a commonly used structure in the field of fluid machinery. It has the advantages of simple structure and stable operation, and is widely used in fluid motors, compressors, pumps, engines and other fields. For fluid machines with eccentric rotor structures, balancing the weight problem is a problem that must be solved.
  • the rotating device comprises: a cylinder 110 having a cylindrical shape; and front/rear sealing end covers (120, 130) respectively sealed and connected to the front/rear ends of the cylinder body, and forming a joint with the cylinder body a cylindrical inner cavity; the main shaft 200 is rotatably supported by the cylinder block 110 and/or the front/rear sealing end caps (120, 130), the center line of which coincides with the centerline of the cylindrical inner cavity; the eccentric rotor assembly 300
  • the sleeve is disposed on a portion of the main shaft in the cylindrical inner cavity, and forms an axially extending crescent-shaped sealing working space by performing a rotary motion in the cylindrical inner cavity; the isolating mechanism has a front end sealed with the rotor assembly, thereby the shaft Separating the extended crescent-shaped sealing
  • the eccentric rotor assembly 300 includes two eccentric bushings 310 which are respectively sleeved on the star wheel fixing flanges B1 and B2 fixed on the main shaft 200, and the center line and the center line of the main shaft 200 are parallel to each other and are offset by a preset distance.
  • the rolling piston wheel 330 is sleeved on the eccentric bushing 310, and its center line coincides with the center line of the eccentric bushing 310; at least one bearing 320 is disposed between the eccentric shaft 310 and the rolling piston wheel.
  • 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 balance weight A is symmetrically arranged on the lighter side.
  • the balance weight A is generally in the shape of a half moon and is bolted to the star wheel fixing flanges (B1 and B2).
  • the applicant also provides a rotating system including the above-mentioned rotating device of the T stage.
  • the T-table rotating devices share the same main shaft, and the angles at which the phase angles ⁇ of the at least two rotating devices are shifted from each other are larger than the critical interval angle ⁇ 1 .
  • the phase angle ⁇ of the rotating device refers to an angle at which the eccentric rotor assembly rotates in the cylindrical inner cavity from the power stroke of the high-pressure fluid of the current cycle;
  • the critical interval angle ⁇ 1 is: The angle of rotation of the eccentric 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 angles ⁇ at which the phase angles ⁇ of the two rotating devices adjacent to each other in the T-stage rotating device are shifted from each other are 360/T.
  • the Applicant found that the balance weights consume energy in a white space, reducing the energy conversion efficiency, and, although using a balanced weight, guarantees the entire star to a certain extent at a specified speed.
  • the dynamic balance of the rotary rotating device does not completely eliminate the vibration problem of the rotating device of the eccentric rotor structure during operation. When deviating from the rated rotational speed, such as in the acceleration phase and the deceleration phase, vibration is still generated, which will not only Energy consumption occurs, and a series of problems such as noise and loose mechanical parts are generated.
  • the present invention provides a rotating system and a fluid motor, a compressor, a pump and an engine using the same to improve energy conversion efficiency, reduce vibration and noise, simplify mechanical construction, and improve fluid machine working efficiency.
  • a rotary system comprising: at least three rotating devices of an eccentric rotor structure, namely a main rotating device, at least one left rotating device and at least one right rotating device;
  • the rotating devices share the same main shaft, the working chambers are spaced apart from each other and operate independently, wherein the eccentric rotor structure of the at least one left rotating device and the at least one right rotating device balances the eccentric rotor structure of the main rotating device Counterweight.
  • a fluid motor comprising: the above-described rotating system; in the fluid motor, a high-pressure fluid working medium introduced by a fluid inlet pushes a rotating device sequence Working, the torque generated by the main shaft is transmitted to the outside of the rotating system, and the low-pressure fluid working after the work is discharged through the fluid outlet.
  • a pump comprising: the above-described rotating system; wherein, by utilizing the torque transmitted by the main shaft, the rotating means in the rotating system independently pumps the fluid from the fluid inlet.
  • a compressor comprising: the above-described rotating system; wherein, by the torque transmitted by the main shaft, the rotating means in the rotating system sequentially compresses the compressed medium, respectively.
  • an engine comprising: the above-described rotating system; wherein the high-pressure gas entering from the combustion chamber pushes the rotating device in the rotating system to work sequentially, and the generated torque is transmitted to the rotating system through the main shaft The outside.
  • a secondary rotating device is disposed on both sides of the main rotating device, and the auxiliary rotating device performs work independently while balancing the configuration, thereby avoiding the whitening energy consumption of the balance weight in the prior art and improving the energy conversion efficiency;
  • the auxiliary rotating device is symmetrically arranged on both sides of the main rotating mechanism, realizing the complete symmetrical dynamic balance of the system, so that low vibration and low noise can be achieved at various speeds, such as rated speed, acceleration and deceleration.
  • the system can be applied to low vibration and low noise scenes;
  • the partition is used to divide the inner cavity, the structure is simple, the manufacture and assembly are convenient, the cost is low, and the industrial application is convenient;
  • the positioning member and the sealing member are organically combined to form a structure similar to a thrust ball bearing to realize two functions of positioning and sealing, and has the advantages of simple structure and reliable performance;
  • the side seal of the rotating mechanism is realized by the cage of the positioning ball, and the sealing component is not required to be additionally provided, which simplifies the mechanical structure of the component and reduces the cost;
  • a side pressure chamber is arranged between the side of the rolling piston wheel and the positioning sealing assembly, and the pressure generated by the side pressure source in the side pressure chamber is used to press the positioning sealing member against the side of the working chamber to realize the side sealing of the rolling piston wheel.
  • the rolling piston wheel does not have to be in contact with the side surfaces of the working chambers on the left and right sides, but floats between the two sides of the working chamber, thereby achieving a zero-gap reliable sealing movement with minimal friction;
  • FIG. 1 is a schematic view of a prior art rotating device using an eccentric rotor structure
  • FIG. 2 is a schematic structural view of a rotating system according to a first embodiment of the present invention
  • Figure 3 is a schematic view showing the dynamic balance of the three eccentric rotor assemblies in the rotating system shown in Figure 2;
  • FIG. 4 is a schematic view showing the dynamic balance of an eccentric rotor assembly in a rotating system according to a second embodiment of the present invention
  • Figure 5 is a schematic view showing the structure of a rotating device according to a first embodiment of the present invention.
  • Figure 6 is a schematic view showing the structure of a rotating device according to a second embodiment of the present invention.
  • FIG. 7A and 7B are perspective views of the right positioning seal assembly of the rotating device of FIG. 6 at two different viewing angles, respectively;
  • Figure 8 is a schematic view showing the rolling track of the steel ball in the right positioning seal assembly of the rotating device of Figure 6 on the wear liner of the right side of the main chamber;
  • FIG. 9 is a schematic view showing three typical arrangement modes of a positioning hole and a steel ball in the present invention.
  • Figure 10 is a schematic view showing the arrangement of steel balls in a circular arc positioning hole in the present invention.
  • 611a-left positioning portion 611b-right positioning member
  • 911a-inner ring 911b-outer ring
  • the eccentric rotor structure using the auxiliary rotating device of the present invention acts as a balance weight to dynamically balance the main rotating device, on the one hand, avoids the white loss of the energy balanced balance weight, and on the other hand realizes the complete symmetry of the entire rotating system. balance.
  • radial and axial are relative to the working chamber, that is, the direction parallel to the main axis of the working chamber or parallel to the direction is “radial”, vertical
  • the direction of the main axis of the working chamber or the direction parallel to the direction is “axial”.
  • a rotating system is provided.
  • Fig. 2 is a schematic view showing the structure of a rotating system according to a first embodiment of the present invention.
  • the rotating system includes: a cylinder internal cavity partitioned into three mutually independent cylindrical chambers: a left chamber, a main chamber and a right chamber; a spindle 200, a center line thereof Coincident with the center line of the inner cavity, sequentially passing through the left chamber, the main chamber and the right chamber; the main rotating mechanism 610, the left rotating mechanism 620 and the right rotating mechanism 630 are respectively located in the corresponding chambers, and both include:
  • the eccentric rotor assembly is sleeved on the portion of the main shaft where the main shaft is located Forming an axially extending sealed working space by performing a rotary motion in the chamber; wherein the eccentric rotor assembly in the left rotating mechanism and the eccentric rotor assembly in the right rotating mechanism are in the running process of the eccentric rotor assembly of the main rotating mechanism
  • the main chamber and the corresponding main rotating mechanism 610 constitute a main rotating device
  • the left chamber and the corresponding left rotating mechanism 620 constitute a left rotating device
  • the right chamber and the corresponding right rotating mechanism 630 The right turning device, i.e., the rotating system of the present embodiment, actually includes three rotating devices that share the same spindle.
  • the main rotating device is the main output device of the rotating system, and the left rotating device and the right rotating device are used as auxiliary auxiliary output devices.
  • the auxiliary rotating device is symmetrically disposed on both sides of the main rotating device, and the auxiliary rotating device performs work independently while balancing the configuration, thereby avoiding the energy consumption of the balance weight in the prior art and improving the energy. Conversion efficiency, at the same time, the setting of the secondary rotating device makes full use of the cavity space inside the cylinder, which improves the space utilization of the entire system.
  • Static balance that is, the balance of the rigid spindle rotating system in a stationary state
  • Fully symmetrical dynamic balance refers to the structure of the symmetrical structure of the spindle rotation system that can achieve dynamic balance at any speed, which is the highest level of balance.
  • FIG. 3 is a schematic view showing the dynamic balance of the three eccentric rotor assemblies in the rotating system shown in FIG. 2. Please refer to Figure 3. To achieve the above-mentioned complete symmetrical dynamic balance, the rigid spindle rotation system must achieve three points:
  • the left balance weight system when the main shaft rotates, the left balance weight system generates a clockwise torque for the W point due to the F L of the centrifugal force, and the right balance weight system generates a pair due to the influence of the centrifugal force F R .
  • the two torques For the counterclockwise torque at point W, the two torques must be balanced, otherwise the spindle will rotate around W point.
  • the balance weight system of the left and right balance weights should be calculated to achieve the torque balance.
  • the sum of the masses of the left and right balance weight systems must still be equal to the mass of the eccentric rotor assembly of the main rotating device.
  • the left balance weight system refers to the eccentric rotor assembly of the left rotation device
  • the right balance weight system refers to the eccentric rotor assembly of the right rotation device.
  • the sum of the mass m L of the eccentric rotor assembly in the left turning device and the mass m R of the eccentric rotor assembly in the right turning device is equal to the mass m of the eccentric rotor assembly in the main rotating device.
  • the center of mass of the eccentric rotor assembly in the main rotating device is A
  • the center of mass of the eccentric rotor assembly in the left rotating device is L
  • the center of mass of the eccentric rotor assembly in the right rotating device is R.
  • the mass center A, the mass center L, and the mass center R are equal to the distance from the spindle center line O-O', and both are e.
  • phase angle is defined as: a plane perpendicular to the center line O-O' of the main axis as a reference plane, and a perpendicular line of the current mass center to the center line deviates from the reference plane.
  • the centrifugal force vector F generated during the rotation of the center of the eccentric rotor assembly in the main rotating device, the centrifugal force vector F L generated during the rotation of the center of the eccentric rotor assembly in the left rotating device, and the right rotating device The sum of the projections of the centrifugal force vector F R generated on the reference plane TT' during the center of mass of the center eccentric rotor assembly is zero.
  • the mass center A of the eccentric rotor assembly in the main rotating device, the mass center L of the eccentric rotor assembly in the left rotating device, and the mass center R of the eccentric rotor assembly in the right rotating device The sum is zero.
  • the mass of the eccentric rotor assembly in the left rotating device is equal to the mass of the eccentric rotor assembly in the right rotating device, it is 1/2 of the mass of the eccentric rotor assembly in the main rotating device. Therefore, the mass centers of gravity L and R integrated in the eccentric rotor assembly in the left/right rotating device are equal to the distance S of the integrated mass center of mass A of the eccentric rotor assembly in the main rotating device.
  • the mass center and the eccentric rotor assembly in the main rotating device can be calculated according to the corresponding formula.
  • the distance from the center of quality is not described here. In this case, only the “complete dynamic balance” described above can be achieved, and the above-mentioned “completely symmetric dynamic balance” cannot be realized, that is, the symmetrical structure of the spindle rotating system can realize the dynamic balance at any rotational speed.
  • the secondary rotating device is symmetrically disposed on both sides of the main rotating mechanism, realizing complete dynamic balance of the system, so that low vibration can be achieved at various rotational speeds, such as in the rated rotational speed, acceleration and deceleration phases. low noise.
  • the rotating system of this embodiment can be applied to fluid machines such as compressors and fluid motors.
  • fluid machines such as compressors and fluid motors.
  • the fluid motor, pump, compressor, and engine, particularly the fluid motor, to which the above-described rotating system is applied will be described in detail below.
  • a rotation system is also provided.
  • 4 is a schematic view showing the dynamic balance of an eccentric rotor assembly in a rotating system according to a second embodiment of the present invention.
  • the rotation system of the present embodiment is different from the rotation system of the first embodiment in that two rotation devices are respectively provided on both sides of the main rotation device, that is, on the left side of the main rotation device, and there is a left rotation device.
  • the left second rotating device, on the right side of the main rotating device has a right rotating device and a right second rotating device.
  • the inner cavity is divided into five parts: a left chamber, a left chamber, a main chamber, a right chamber, and a right chamber.
  • the left chamber, the left chamber, the main chamber, the right chamber, and the right chamber are respectively a left-hand rotating mechanism, a left-hand rotating mechanism, a main rotating mechanism, a right-hand rotating mechanism, and a right-hand rotating mechanism.
  • Working chamber. Wherein, the chambers are separated by a cylinder partition.
  • the mass of the eccentric rotor assembly in the main rotating device is m
  • the mass of the eccentric rotor assembly in the left rotating device is m L1
  • the mass of the eccentric rotor assembly in the left second rotating device is m L2
  • the eccentric rotor assembly in the right rotating device The mass is m R1
  • the mass of the eccentric rotor assembly in the right second rotating device is m R2 , then they satisfy:
  • the mass center A of the eccentric rotor assembly in the main rotating device, the mass center L1 of the eccentric rotor assembly in the left rotating device, the mass center L2 of the eccentric rotor assembly in the left second rotating device, and the mass of the eccentric rotor assembly in the right rotating device The center R1 of the eccentric rotor assembly in the center R1 and the right second rotating device is equal to the vertical distance of the spindle center line OO', and is e;
  • phase angle ⁇ of the center of mass of the eccentric rotor assembly in the main rotating device; the phase angle of the center of mass of the eccentric rotor assembly in the left rotating device and the right rotating device is ⁇ ', the left second rotating device and the right second rotating device
  • the phase angle of the center of mass of the middle eccentric rotor assembly is ⁇ ′′, ⁇ ′ is different from ⁇ by 180°, and ⁇ ′′ is equal to ⁇ ;
  • the centrifugal force vector F generated during the rotation of the eccentric rotor assembly in the main rotating device, the centrifugal force vector F L1 generated during the rotation of the eccentric rotor assembly in the left rotating device, and the eccentric rotor assembly in the right rotating device are rotating
  • the centrifugal force vector F R1 generated in the process, the centrifugal force vector F L2 generated during the rotation of the eccentric rotor assembly in the left second rotating device, and the centrifugal force vector F R2 generated during the rotation of the eccentric rotor assembly in the left three rotating device are The sum of the projections on the reference plane is 0;
  • the distance between the mass center of the eccentric rotor assembly in the left second rotating device and the axial symmetry plane TT' of the main chamber and the distance between the mass center of the eccentric rotor assembly and the axial symmetry plane TT' of the main chamber in the right second rotating device are both S2 .
  • phase of the eccentric rotor assembly and the centrifugal force vector generated during the rotation, please refer to the related description in the first embodiment, which will not be repeated here.
  • the inner cavity can be divided into any three or more chambers, as long as a main rotating device, a left rotating device and a right rotating device are formed. And the eccentric rotor structure of the left rotating device and the right rotating device may balance the eccentric rotor structure of the main rotating device.
  • the inner cavity can be divided into 2N+1 chambers, and 2N+1 rotating devices are formed with the corresponding eccentric rotor assemblies, that is, symmetrically set N on both sides of the main rotating device
  • N such as process complexity
  • the N is a positive integer greater than or equal to 1, generally not more than three.
  • the invention also provides a fluid motor.
  • the fluid motor employs the rotation system described in the first embodiment.
  • the respective components of the fluid motor of the present embodiment will be described in detail below. Those skilled in the art should be able to have a clearer understanding of the rotating system of the first embodiment by the following description.
  • the cylinder bore is enclosed by the cylinder block 110 and the front and rear end caps (120, 130).
  • the front and rear end covers (120, 130) are fixed to the cylinder by the left end cover positioning bolts 121 and the right end cover positioning bolts 131, respectively.
  • the inner chamber is divided by the partition into three mutually independent cylindrical chambers: a left chamber, a main chamber and a right chamber, respectively serving as working spaces for the respective rotating mechanisms.
  • the main chamber is the working space of the main rotating mechanism, and serves as the main chamber.
  • the left chamber serves as the working space for the left rotating mechanism
  • the right chamber serves as the working space for the right rotating mechanism, both serving as auxiliary chambers.
  • the size of the main chamber is larger than the size of the other two auxiliary chambers.
  • the main chamber is designed in the usual way, while the left and right chambers are designed according to the size of the corresponding eccentric rotor assembly, while the size of the eccentric rotor assembly is designed according to the balance weight. In the design process, special emphasis is placed on the problem of left and right symmetry.
  • the cylinder portion corresponding to the main chamber is named as the main cylinder 111; the cylinder portion corresponding to the left chamber is named as the left cylinder 112; the cylinder corresponding to the right chamber The part is named as the right cylinder 113.
  • the main chamber and the left chamber are separated by a left cylinder partition 501; the main chamber and the right chamber are separated by a right cylinder partition 511.
  • the left cylinder partition 501 and the right cylinder partition 511 are wear-resistant steel sheets having a thickness of between 5 mm and 80 mm and a Brinell hardness (HB) of between 300 and 600, both of which are polished. Smoothing to reduce the resistance of the eccentric rotor assembly during rotation.
  • the inner cavity is divided by the cylinder partition, the structure is simple, the manufacture and assembly are convenient, the cost is low, and the industrial application is convenient.
  • the main shaft 200 is rotatably supported by the cylinder block 110 or the front/rear seal end caps (120, 130), one end of which is located outside the inner chamber, and the other end passes through the left chamber, the main chamber and the right chamber in sequence. Need It is to be noted that although only one end of the main shaft extends beyond the cylindrical inner cavity in the present embodiment, the present invention also includes the case where both ends of the main shaft extend beyond the cylindrical inner cavity to simultaneously output torque from the left and right sides. Those skilled in the art should be aware of how the above technical solutions are implemented, and details are not described herein again.
  • the left rotation mechanism, the main rotation mechanism and the right rotation mechanism are respectively located in the corresponding chambers, and both comprise: an eccentric rotor assembly, which is sleeved in a portion of the main shaft located in the chamber, and passes through the chamber The rotary motion forms an axially extending sealed working space; the isolation mechanism has a front end sealed with the eccentric rotor assembly to separate the axially extending sealed working space into two independent variable volume chambers.
  • the structures of the left rotation mechanism, the main rotation mechanism, and the right rotation mechanism are substantially the same except for the difference in size, which will be described here.
  • the eccentric rotor assembly comprises: an eccentric bushing sleeve sleeved and fixed to a portion of the main shaft located in the cylindrical inner cavity, wherein the center line and the center line of the main shaft are parallel to each other and offset by a preset distance; the rolling piston wheel is sleeved on the eccentric bushing The center line coincides with the center line of the eccentric bushing, the rolling piston wheel rolls along the inner cylindrical surface of the cylinder; the rolling bearing is symmetrically sleeved on the eccentric shaft, and the inner ring is fixed to the eccentric bushing The outer ring is fixed to the rolling piston wheel to isolate the rotation of the two.
  • the rolling piston wheel is pressed against the inner cylindrical surface of the cylindrical inner cavity, so that an axially extending crescent-shaped sealing cavity is formed between the inner cylindrical surface of the cylindrical inner cavity and the outer cylindrical surface of the rolling piston wheel ( C, c1, c2).
  • the eccentric rotor assembly in the main rotating device, includes an eccentric bushing 611, a rolling bearing 612, and a rolling piston wheel 613.
  • the eccentric rotor assembly in the left turning device, includes an eccentric bushing 621, a rolling bearing 622, and a rolling piston wheel 623.
  • the eccentric rotor assembly in the right turning device, includes an eccentric bushing 631, a rolling bearing 632, and a rolling piston wheel 633.
  • the eccentric bushings (611, 621, 631) are directly fixed to the main shaft instead of being fixed to the planetary piston wheel fixing flange as described in the background art.
  • the rotational axial motion error and vibration are shielded and filtered by three rolling bearings without axial constraints (the main rotating device, the left rotating device and the rolling bearing of the eccentric rotor assembly in the right rotating device) to realize the rolling piston.
  • High-precision rotary motion of the wheel are directly fixed to the main shaft instead of being fixed to the planetary piston wheel fixing flange as described in the background art.
  • the portion of the eccentric rotor assembly that is in frictional contact with the outer sealed end cap is provided with a wear resistant liner (522, 532).
  • the wear-resistant lining and the eccentric rotor contact surface are mirror-polished and smoothed to reduce friction and improve sealing.
  • the isolation mechanism separates the crescent-shaped sealing cavity into a high pressure fluid working chamber and a low pressure fluid discharge chamber.
  • the isolation mechanism can use a variety of isolation mechanisms, such as a rotary valve piece (patent application number: 201110154415.0), a rotary valve body with a semi-circular structure (patent application number: 200780027498.9), a gate valve (patent application number: 201110322746.0), Two-way rotary valve piece (201410415170.6) and so on.
  • a predetermined position on the outside of the cylinder, generally above, is provided with a fluid inlet and outlet seat 700.
  • a high-pressure fluid inlet passage and a low-pressure fluid outlet passage respectively communicating with the three high-pressure fluid working chambers and the three low-pressure fluid discharge chambers are opened on the cylinder body inside the fluid inlet and outlet seat.
  • the high-pressure fluid entering passage 800 enters the passage 800 through the fluid inlet and outlet seat 700 into the cylinder 800, and is divided into three, and the high-pressure fluid entering the three rotating devices respectively serves as a working chamber.
  • the fluid of the low pressure fluid discharge chamber of the three rotating devices after the completion of the work is introduced into the fluid inlet and outlet seat 700 through the low pressure fluid outflow passage, and then discharged.
  • the cylinder block For the cylinder block, the main shaft, the front/rear cover, the eccentric rotor assembly, the structure of the isolation mechanism, the assembly relationship, etc., please refer to the applicant's multiple prior applications, such as: rotating device and application for high pressure scenes. Its mechanical device (201410776253.8). Since it is not an innovation of the present invention, it will not be described in detail herein.
  • the high-pressure fluid source continuously flows, and the rotating device is pushed to work sequentially, and the generated torque is transmitted to the outside of the inner cavity through the main shaft.
  • the high pressure fluid can be a liquid or a gas, especially steam.
  • the rotating system of the present embodiment has low cost and high adaptability, and can adapt to various fluid working substances, such as superheated steam, steam protection, steam-water two-phase fluid, Hot water (including high-salt hot water).
  • the sealing structure and the positioning mechanism are respectively designed and assembled, the structure is complicated, and the assembly is difficult.
  • the above sealing scheme requires very high processing precision for the wear liner. Such as If the wear-resistant lining is too thin, it will cause the seal to fail. If the wear-resistant lining is too thick, the rolling piston wheel will be too much pressure, resulting in increased friction, which will affect the working efficiency of the entire rotating system.
  • the solution to the problem in this embodiment is to clearly separate the functional objectives of positioning and sealing, and to perform different tasks with different mechanical elements; and, as far as possible, organically combine different mechanical elements to support each other and accomplish tasks together.
  • the present embodiment combines the positioning member and the sealing member organically to form a structure similar to a thrust ball bearing, and realizes the positioning of the rotating mechanism in the working chamber by using the positioning ball, and realizes the cage by the positioning ball.
  • the side of the rotating mechanism is sealed.
  • a side pressure chamber is arranged between the side of the rolling piston wheel and the positioning sealing assembly, and the pressure generated by the pressure source inside the side pressure chamber is used to press the positioning sealing member against the wear-resistant lining on the side of the chamber to realize the rolling piston wheel. Side seal.
  • the rotating device of this embodiment is similar to a rotating device in the rotating system shown in Fig. 2, wherein the left cylinder partition 501 and the right cylinder partition 511 also employ wear-resistant linings (521, 531), wear-resistant linings.
  • An O-ring seal (534, 535) is also provided between the plate and the radially outer sealing end cap, the main difference being the use of a specially designed side seal structure.
  • the main rotating device will be described as an example.
  • the rotating device of this embodiment includes a main chamber, a main shaft 200, a main rotating mechanism 610, and a side positioning sealing mechanism 900.
  • the central axis of the main shaft 200 coincides with the central axis of the main chamber.
  • the main rotating mechanism 610 includes: an eccentric rotor assembly sleeved on a portion of the main shaft located in the main chamber, forming an axially extending crescent-shaped sealing cavity C by performing a rotary motion in the chamber; the isolation mechanism, the front end and the eccentric rotor assembly The phase seals thereby separating the axially extending crescent-shaped sealed chamber C into mutually independent two-volume variable chambers that are in controllable communication with the outside through fluid inlets and fluid outlets, respectively.
  • the eccentric rotor assembly includes: an eccentric bushing 611 sleeved and fixed to a portion of the main shaft located in the main chamber, the central axis of which is parallel to the central axis of the main shaft and offset by a predetermined distance; the rolling piston wheel 613 is sleeved on the eccentric bushing The central axis coincides with the central axis of the eccentric bushing; the rolling bearing 612 is symmetrically sleeved on the eccentric shaft, the inner ring is fixed to the eccentric bushing, and the outer ring is fixed to the rolling piston wheel to isolate the two Turn.
  • the rolling piston wheel 613 is pressed against the inner cylindrical surface on one side of the working chamber, and rolls along the inner cylindrical surface to form an axis between the inner cylindrical surface of the working chamber and the outer cylindrical surface of the rolling piston wheel.
  • the rolling bearing 612 is bilaterally symmetrical with respect to the main chamber and has a width smaller than the width of the main chamber.
  • a positioning structure of the rolling bearing 612 is provided on the radially outer side of the eccentric bushing 611. Referring to FIG. 5, the left side of the eccentric bushing 611 extends upward to form a left positioning portion 611a. A right positioning member 611b is fixed to the right side of the eccentric bushing. The lower portion of the rolling bearing is sandwiched and positioned between the left positioning portion 611a and the right positioning member 611b.
  • the rolling piston wheel 613 has a cylindrical structure as a whole, and is divided into three portions whose width is gradually increased from the inside to the outside in the radial direction. Among them, the left and right sides of the innermost inner cylindrical portion 613a are flush with the left and right sides of the rolling bearing. The left and right sides of the outermost outer tubular portion 613c are respectively close to but not in contact with the wear-resistant lining 521 on the left side of the cylindrical surface of the main chamber and the wear-resistant lining 531 on the right side, and the gap between the two is ⁇ 1.
  • the inner cylinder portion 613a and the outer cylinder portion 613c are intermediate cylinder portions 613b having a thickness larger than the thicknesses of the inner cylinder portion 613a and the outer cylinder portion 613c. Among them, a first stepped structure is formed between the inner cylindrical portion 613a and the middle cylindrical portion 613b of the rolling piston wheel.
  • the cylindrical structure is divided into an inner tube portion, a middle tube portion and an outer tube portion, but in practice, the three portions may be integrated. In this case, the inner cylinder portion, the middle cylinder portion and the outer cylinder portion are not separated into three parts.
  • NM400, NM450 and harder NM500 can be used; other wear-resistant steels such as Swedish HARDOX400, HARDOX450, HARDOX500 and harder HARDOX600 can also be used.
  • Materials that work at high temperatures can use high temperature resistant steels, as well as industrial ceramics and hard alloys.
  • At least two through holes (613c' and 613c”) are uniformly disposed in the circumferential direction on the left and right sides of the axial direction of the outer cylindrical portion 613c, and the diameter d of the through holes (613c' and 613c") is between Between 0.5mm and 2mm.
  • the side positioning sealing mechanism 900 includes a left positioning sealing assembly 910 and a right positioning sealing assembly 920.
  • the left positioning seal assembly 910 further includes a left side positioning ring 911 and a left floating piston ring 912.
  • the right positioning seal assembly 920 further includes a right side positioning ring 921 and a right floating piston ring 922.
  • the structures of the two are substantially the same.
  • the left side positioning ring 911 has a double-layered annular structure and is embedded in the rolling piston wheel and the main chamber. Between the wear-resistant linings on the left side to achieve the positioning of the rolling piston wheel.
  • the left side positioning ring 911 forms two portions - an inner ring portion 911a and an outer ring portion 911b in the axial direction from the inside to the outside.
  • the right side of the inner ring portion 911a abuts against the left side of the rolling bearing and the inner cylindrical portion 613a of the rolling piston wheel, and the outer ring portion 911b abuts against the wear-resistant lining 521 on the left side surface of the cylindrical surface of the main chamber.
  • the outer ring portion 911b extends outward in the radial direction with respect to the inner ring portion 911a, forming an outer extending portion 911b', and a second stepped structure is formed between the outer extending portion 911b' and the inner ring portion 911a.
  • the first stepped structure is formed between the inner cylindrical portion 613a and the middle cylindrical portion 613b of the rolling piston wheel. The second step structure and the first step structure are engaged with each other, and the positioning of the left side positioning ring to the rolling bearing and the rolling piston wheel is realized.
  • a left accommodation space is formed between the outer extension portion 911b' of the outer ring portion of the left side positioning ring and the outer cylinder portion 613c of the rolling piston wheel.
  • the left floating piston ring 912 is disposed in the left accommodating space.
  • the left floating piston ring 912 it is sealed in the radial direction from the outer tubular portion 911b' of the outer cylindrical portion of the rolling piston wheel and the outer ring portion of the left side positioning ring, respectively.
  • the thickness D1 of the left floating piston ring 912 is greater than the distance ⁇ 1 between the left side of the outer cylindrical portion 613c and the left side surface of the cylindrical surface of the main chamber, so that the left side of the outer cylindrical portion 613c can be The gap between the left side faces of the cylindrical surface of the main chamber is sealed.
  • the thickness D1 is smaller than the distance D between the middle cylindrical portion 613b of the rolling piston wheel and the left side surface of the cylindrical surface of the main chamber, thereby forming a ring-shaped left between the left floating piston ring 912 and the middle cylindrical portion 613b of the rolling piston wheel.
  • Side pressure chamber 913 The left pressure chamber 913 communicates with the crescent-shaped sealing chamber through a through hole 613c' opened in the axially left side of the outer cylindrical portion 613c of the rolling piston wheel.
  • the size of ⁇ 1 is directly related to the machining accuracy, ranging from 5 ⁇ m to 50 ⁇ m, and the axial pressure of the side pressure chamber is between 0.2 mm and 1.0 mm.
  • the rotating device is in operation, and a small amount of high-pressure fluid in the crescent-shaped sealed cavity is introduced into the left pressure chamber 913 through the through hole 613c', and the small amount of splitting causes the left floating piston ring 912 to be in close contact with the main chamber left.
  • the wear liner 521 on the side thereby achieving the left side seal of the rolling piston wheel.
  • the crescent seal chamber C is partitioned by the isolation mechanism into two variable volume chambers that are independent of each other.
  • the two-volume variable chambers are referred to as: a high pressure chamber and a low pressure chamber.
  • the left positioning seal assembly as an example, two flow holes are uniformly formed on the circumference of the left side of the outer cylindrical portion of the rolling piston wheel. It has been proved by experiments that no matter whether the two flow holes are located in the high pressure chamber at the same time, One flow hole is located in the high pressure chamber, the other flow hole is located in the low pressure chamber, or the two flow holes are located in the low pressure chamber.
  • the velocity of the fluid injected into the left pressure chamber is far greater than that in the low pressure chamber when the pressure chamber is located in the high pressure chamber. The speed of the outflow, therefore, the fluid in the left pressure chamber can always maintain a relatively high pressure so that the left floating piston ring 912 does not separate from the wear liner 521 on the left side of the main chamber.
  • 2 to 10 through holes may be uniformly formed in the circumferential direction of the outer cylindrical portion of the rolling piston wheel. If the number of the through holes is excessive, the strength of the outer cylindrical portion of the rolling piston wheel may be adversely affected. If there is only one through hole, the fluid injected into the left pressure chamber will not flow, and it will deteriorate under a long time, which is not conducive to the long-term operation of the rotating device.
  • the number of the flow holes corresponding to the left positioning seal assembly and the right positioning seal assembly is the same and the position is symmetrical.
  • the right positioning seal assembly 920 it is substantially symmetrical with the left positioning seal assembly.
  • the outer ring portion 921b extends radially inwardly to the outer side in the axial direction of the right positioning member 611b with respect to the inner ring portion 921a, and is located close to the position of the eccentric bushing 611.
  • the rolling bearing needs to operate in an oil lubricated environment.
  • the inner extension 921b" is spaced apart from the eccentric bushing by a small distance to prevent loss of lubricating oil of the rolling bearing.
  • the thickness D1 is smaller than the distance D between the middle cylinder portion of the rolling piston wheel and the right side surface of the cylindrical surface of the main chamber, so that the right floating piston ring 922 and the middle cylinder of the rolling piston wheel
  • An annular right side pressure chamber 923 is formed between the portions 613b, and the right side pressure chamber 923 communicates with the crescent-shaped sealing chamber through a through-flow hole 613c" opened in the axially right side of the outer cylindrical portion of the rolling piston wheel.
  • the rotating device is in operation, and a small amount of high-pressure fluid in the crescent-shaped sealed cavity is introduced into the right pressure chamber 923 through the through hole 613c", and the small amount of shunt makes the right floating piston ring 922 close to the main chamber right The wear liner 531 on the side, thereby achieving the right side seal of the rolling piston wheel.
  • the left side positioning ring 911 and the right side positioning ring 921 are disposed on the left and right sides of the rolling piston wheel 613, and wear-resistant linings on both sides of the rolling piston wheel 613 and the left/right side of the main chamber (521) 531) Separate and position to ensure no contact between metal parts. Moreover, a gap of 0.01 mm or more is maintained between the side positioning ring (911, 921) and the wear-resistant lining plate (521, 531) on the corresponding side to prevent The friction is damaged.
  • the material of the side positioning ring (911, 921) is non-ferrous, such as copper or engineering plastics, preferably polytetrafluoroethylene, which has high hardness, low friction, can be flexibly rotated, and does not scratch the wear resistant liner. .
  • the materials of the left floating piston ring 912 and the right floating piston ring 922 are non-ferrous, such as copper or engineering plastics, preferably polytetrafluoroethylene, which is light in weight, high in strength, and low in friction, and can realize the side of the rolling piston wheel. Reliable sealing.
  • the outer tube portion of the outermost rolling piston wheel is close to but not in direct contact with the corresponding side surface of the main chamber, and a small amount of high pressure fluid in the crescent-shaped sealing chamber is introduced into the side pressure through the through hole.
  • the small amount of the splitting causes the floating piston ring to abut the corresponding side of the main chamber, thereby realizing the side seal of the rolling piston wheel, thereby realizing that the rolling piston wheel floats between the wear-resistant linings on both sides and along
  • the cylindrical surface of the cylinder is rolled to achieve zero-gap and reliable sealing movement with minimal friction.
  • the present embodiment is described by taking the main rotating device as an example.
  • the solution of this embodiment performs side sealing.
  • the present embodiment is provided with a positioning sealing assembly on both the left and right sides of the eccentric rotor assembly, in fact, positioning may be provided only on one side of the eccentric rotor assembly without considering the positioning and sealing of the other side.
  • a seal assembly that is equally capable of implementing the present invention.
  • This embodiment also provides a rotating system for a rotating device according to the first embodiment of the rotating device, which adopts a rotating system of a first embodiment of the rotating system or a rotating system, and a positioning seal on the side
  • a rotating system for a rotating device according to the first embodiment of the rotating device, which adopts a rotating system of a first embodiment of the rotating system or a rotating system, and a positioning seal on the side
  • the key is to introduce a small amount of the high-pressure fluid in the crescent-shaped sealed cavity into the side pressure chamber through the through-hole.
  • achieving such a seal is conditional, that is, the fluidity of the fluid is good.
  • the present embodiment provides an improved rotating device.
  • the rotating device differs from the first embodiment of the rotating device in that the side positioning ring and the floating piston ring are integrated to form a positioning sealing assembly similar to a thrust ball bearing, and the side sealing and positioning of the eccentric rotor assembly is realized, and By adding elastic members in the side pressure chamber, the problem of "heavy oil” blocking the through hole and lack of pressure in the side pressure chamber just after starting is solved.
  • the side positioning sealing structure 900 includes a left positioning sealing assembly 910 and a right positioning sealing assembly 920.
  • the left positioning seal assembly 910 and the right positioning seal assembly 920 are bilaterally symmetrical, and the following description is directed to the right positioning seal assembly 920.
  • the right positioning seal assembly 920 includes a seal retainer 926 and a plurality of steel balls 927 .
  • the sealing holder 926 has an annular structure as a whole, and the longitudinal section thereof is rotated by 90° in a "convex" shape.
  • the seal holder 926 forms two layers - an inner ring portion 926a and an outer ring portion 926b in the axial direction from the inside to the outside.
  • the outer ring portion 926b extends outward in the radial direction to form an outer extending portion 926b'; and extends inwardly to form an inner extending portion 926b".
  • the outer extending portion 926b' and the inner extending portion 926b" have corresponding functions, which will be under A detailed description is given in the text.
  • the third step structure is formed between the inner ring portion 923a and the outer extension portion of the outer ring portion.
  • the first stepped structure is formed between the inner cylindrical portion 613a and the middle cylindrical portion 613b of the rolling piston wheel.
  • the third step structure and the first step structure are engaged with each other, and the positioning of the left side positioning ring to the rolling bearing and the rolling piston wheel is realized.
  • the outer extension 926b' of the outer ring portion of the sealing cage corresponds to the floating piston ring in the first embodiment.
  • the outer extension portion 926b' of the outer ring portion extends to a position close to the outer tubular portion of the rolling piston wheel, and the thickness D2 of the outer extension portion 926b' is smaller than the middle cylinder portion 613b of the rolling piston wheel and the main cavity.
  • the distance D of the wear liner on the right side of the cylindrical surface of the cylinder is such that an annular right pressure chamber 923 is formed between the outer extension 926b' and the intermediate tubular portion 613b of the rolling piston wheel.
  • the right pressure chamber 923 passes through the axially right side of the outer tubular portion of the rolling piston wheel
  • the orifice 613c" is in communication with the crescent-shaped sealing chamber.
  • the side seal further includes: an elastic member.
  • the elastic member is axially disposed in the side pressure chamber, and both sides are respectively pressed against the inner side of the sealing cage and the outer side of the middle cylindrical portion of the rolling piston wheel to provide a sealing holder that is closely attached to the corresponding side of the main chamber.
  • the pressure needed may be a spring, a disc spring or an O-ring, and the material thereof may be rubber, plastic, metal or the like. In this embodiment, an O-ring of a fluororubber material is used.
  • the inner extending portion 926b" of the outer ring portion of the sealing cage extends to a position close to the eccentric bushing to prevent the oil lubrication environment from being damaged due to the leakage of the lubricating oil.
  • a hidden danger is that the distance between the inner extension 926b" and the eccentric bushing is between 20 ⁇ m and 100 ⁇ m.
  • the inner extension portion 926b" may have the same thickness as the outer extension portion 926b' or may be different.
  • the inner extension 926b may be omitted without regard to the lubrication leakage of the rolling bearing.
  • the longitudinal section of the seal holder 926 will be rotated “clockwise” by 90°. Instead of a 90-degree “convex” shape that rotates counterclockwise.
  • the outer extending portion 926b' of the outer ring portion of the sealing holder is uniformly disposed with M positioning holes in the circumferential direction, and the M steel balls 927 matched with the positioning holes are respectively accommodated.
  • the positioning hole Corresponding to the positioning hole, and positioned by the positioning hole.
  • the axial inner side of the steel ball 927 is pressed against the middle cylindrical portion 613b of the rolling piston wheel; the axially outer side thereof is pressed against the wear-resistant lining of the right side surface of the main chamber On the board.
  • M 3.
  • the steel ball performs precise and reliable positioning on the rolling piston wheel, and is capable of high-speed and high-efficiency rotational motion.
  • a rolling piston wheel, a wear-resistant steel baffle, a sealing cage and a plurality of steel balls constitute a structure similar to a thrust ball bearing, wherein the rolling piston wheel can be regarded as The moving ring and wear-resistant lining of the thrust ball bearing can be regarded as the fixed ring of the thrust ball bearing, and the sealing cage is equivalent to the piston ring.
  • the axial positioning of the rolling piston wheel is achieved by the plurality of steel balls. It is particularly important to note that due to the high precision of the steel ball, the lateral positioning clearance of the rolling piston wheel can be made small in the case of axial positioning of the steel ball.
  • Figure 8 is a schematic view showing the rolling track of the steel ball in the right positioning seal assembly of the rotating device of Figure 6 on the wear liner of the right side of the main chamber.
  • the rolling track width of the steel ball on the wear-resistant lining plane is 2e.
  • the rolling track of the rolling piston wheel side seal rolling bearing on the wear resistant lining plane illustrates that the movement of the steel ball is complicated by the eccentric motion of the moving coil (rolling piston wheel).
  • the movement of the steel ball is driven by the eccentric movement of the sealing cage moved by the follower ring (rolling piston wheel) around the main shaft, and the steel ball revolves around the main axis on the one hand, and rotates on the one hand due to the eccentric motion.
  • the revolving motion of the steel ball around the main shaft remains on the rolling track corresponding to the side track of the rolling piston wheel, and is a perfect circular shape coaxial with the center of rotation of the rolling piston wheel.
  • Rolling track on the side track of the rolling piston wheel If it is made into an arc-shaped raceway like a normal thrust ball bearing, the contact area between the spherical surface and the raceway can be increased, which directly improves the bearing capacity and the reliable life.
  • the rolling track of the side-sealed rolling bearing steel ball on the plane of the wear-resistant lining is an annular belt with a width of 2e. Although the contact between the steel ball and the wear-resistant lining plane is point contact, it is evenly distributed on the ring plane.
  • the rolling process of the steel ball on the plane of the wear-resistant lining plate is actually the rolling super-finishing of the surface metamorphic layer of the track width ring belt, and the rolling smoothness is greatly improved to achieve the mirror finish.
  • the steel ball is super-finishing of the wear-resistant lining plate, which not only greatly improves the smoothness after rolling, but also the surface work hardening and fine graining after rolling, which contribute to the improvement of contact strength and wear resistance. Therefore, the material of the wear-resistant lining may not be made of bearing steel like a standard commercially available thrust ball bearing, but may be manufactured by a lower-cost wear-resistant steel such as NM400.
  • the rolling trajectory of the steel ball on the side track of the rolling piston wheel is only a straight circular shape coaxial with the center of rotation of the rolling piston wheel, and sometimes appears thin.
  • the locating holes and the steel balls are distributed over two concentric circles of the outer extension of the seal retainer.
  • the rolling trajectory of the steel ball on the side track of the rolling piston wheel has two straight circular lines coaxial with the center of rotation of the rolling piston wheel, which obviously improves the bearing capacity and the reliable life.
  • the steel balls are distributed in the straight long holes, and the steel balls have a larger rolling track range on the side track of the rolling piston wheel, and an annular contact surface can be formed, and the bearing capacity and reliability are reliable. Life expectancy will increase further.
  • the positioning hole is a curved elongated hole.
  • the line connecting the first end of the curved elongated hole has a component in the radial direction of the double-layered annular structure.
  • Three steel balls are placed in each arc-shaped hole.
  • the rolling track of the piston star wheel side track is larger because the steel ball is subjected to the cam-like guiding force of the inner side of the curved long hole and the centrifugal force of the rolling ball during the rotation. More uniform, more load carrying capacity and longer life.
  • the bottom surface of the outer ring portion of the sealing cage is not a flat surface, and a section of the radially inner portion (a section away from the positioning hole) is recessed toward the inner ring portion 926a, hereinafter referred to as Recessed section.
  • the concave section reduces the area of contact between the sealing cage and the wear liner, thereby reducing the friction between the two, which can further improve the operating efficiency and reduce the processing precision of the sealing cage.
  • the rigidity is not so high, and a flexible material suitable for sealing such as rubber, plastic or graphite can be used.
  • a flexible material suitable for sealing such as rubber, plastic or graphite
  • polytetrafluoroethylene has good lubricity and sealing properties, and is very suitable as a sealing cage.
  • the sealing cage can be prepared using a graphite material that is corrosion resistant and has good lubricity, such as dip metal graphite.
  • the steel ball in addition to the bearing steel, it can be replaced by a ball made of other metal or non-metal material having a certain hardness, for example, a cemented carbide, a silicon carbide, a silicon nitride, a zirconia ceramic, or the like.
  • the first embodiment of the rotating device and the rotating device of the present embodiment is slightly different in the positioning manner of the rolling bearing 612.
  • the rolling bearing 612 is sandwiched and positioned between the left positioning portion 611a and the right positioning member 611b.
  • the eccentric bushings respectively fix the left positioning member 611a' and the right positioning member 611b on the left and right sides of the rolling bearing.
  • the lower portion of the rolling bearing 612 is sandwiched and positioned to the left positioning member 611a' and the right side Between bit pieces 611b.
  • This embodiment provides a positioning seal assembly as shown in Figures 7A and 7B that can be applied, for example, to a second embodiment of a rotating device.
  • the positioning seal assembly includes a seal holder 926 and a plurality of steel balls 927.
  • the seal holder 926 is used for sealing, and has a double-layered annular structure as a whole, and the longitudinal section has a "convex" shape rotated counterclockwise by 90°.
  • the outer extending portion 926b' of the outer ring portion of the sealing cage is uniformly disposed with M positioning holes in the circumferential direction, and the M steel balls 927 are accommodated in the positioning holes and are positioned by the positioning holes.
  • the inner extension of the seal holder it may or may not be omitted.
  • the M positioning holes are distributed on one circumference of the outer extension.
  • the M positioning holes may also be disposed on T circumferences of different radii of the outer extension of the outer ring portion of the sealing holder, and the present invention can also be implemented.
  • T 2.
  • the positioning holes are circular, matching the shape of the steel ball, and each positioning hole is provided with a steel ball. In other embodiments of the invention, the positioning holes may also be of other shapes. Typically:
  • the positioning hole may also be a straight elongated hole.
  • the central axis of the straight elongated hole is along the radial direction of the double-layered annular structure, and the length of the elongated strip is larger than the diameter of the positioning ball.
  • one steel ball is disposed in each of the long holes, but in other embodiments of the present invention, two can be disposed in each of the long holes. Or three steel balls, the effect is better than one positioning steel ball; and, based on the balance consideration, the number of steel balls in each elongated hole is preferably equal.
  • the positioning hole may also be a curved elongated hole.
  • the line connecting the first end of each curved elongated hole has a component in the radial direction of the double-layered annular structure.
  • the M curved long holes along the extending portion are arranged in parallel, and three steel balls are arranged in each of the circular arc holes.
  • one or two steel balls may be disposed in each curved elongated hole, but the effect is not as good as setting three steel balls.
  • the pressure track range is larger and more uniform, and the bearing capacity and reliable life are greater.
  • the curve of the curved long hole may be one of a curve such as an arc, an involute, a cycloid, and a logarithmic curve. Further, based on the balance consideration, the number of steel balls in each of the curved elongated holes is preferably equal.
  • the rigidity is not large, and a flexible material suitable for sealing such as rubber, plastic or graphite can be used.
  • a flexible material suitable for sealing such as rubber, plastic or graphite
  • polytetrafluoroethylene has good lubricity and sealing properties, and is very suitable as a sealing cage.
  • the material of the sealing cage can use graphite materials with good corrosion resistance and lubricity, such as dip metal graphite.
  • the steel ball in addition to the bearing steel, it can be replaced by a ball made of other metal or non-metal material having a certain hardness, for example, a cemented carbide, a silicon carbide, a silicon nitride, a zirconia ceramic, or the like.
  • a ball made of other metal or non-metal material having a certain hardness for example, a cemented carbide, a silicon carbide, a silicon nitride, a zirconia ceramic, or the like.
  • the steel ball of bearing steel material has reduced hardness and is easily deformed, and is no longer suitable for high temperature resistance.
  • Rolling spheres made of ceramic materials such as cemented carbide and zirconium dioxide (ZrO 2 ) are very suitable for this. Application in high temperature applications.
  • This embodiment is similar to the third embodiment of the rotating system except that the rotating device given in the second embodiment of the rotating device is applied.
  • the rotating device in the rotating system of the present embodiment reference may be made to the related description of the second embodiment of the rotating device.
  • reference may be made to the structure other than the rotating device reference may be made to the first embodiment of the rotating system and the related description of the second embodiment of the rotating system. , no longer detailed here.
  • the present invention also provides another fluid motor.
  • the fluid motor employs the rotating system described in the third and fourth embodiments of the rotating device or the rotating system described in the first and second embodiments. among them,
  • the high pressure fluid entering the fluid inlet enters the rotating device and is pushed
  • the rolling piston wheel rotates, and the generated torque is transmitted to the outside of the working chamber through the main shaft, and the low-pressure fluid after the work is discharged through the fluid outlet.
  • the high pressure fluid here may be: liquid, gas or steam.
  • the invention also provides a pump.
  • the pump uses the rotating device described in the first and second embodiments of the rotating device or the rotating system described in the first, second, third and fourth embodiments.
  • the main shaft transmits the torque outside the inner cavity to the inner cavity; under the driving of the main shaft, three rolling piston wheels are used as a medium, and three rolling piston wheels roll forward along the cylindrical inner cavity, respectively, independently
  • the fluid entering the fluid inlet is pumped into the crescent-shaped sealed workspace and the fluid is discharged through the fluid outlet.
  • the pump has a small output pressure and flow pulsation, and is linear in average.
  • the invention also provides a compressor.
  • the compressor is applied to the rotating system described in the first, second, third and fourth embodiments of the rotating device or the rotating system according to the first and second embodiments of the rotating device.
  • the main shaft transmits the torque outside the cylindrical inner cavity into the cylindrical inner cavity, and the three eccentric bushings are used as a medium, and the three rolling piston wheels roll forward along the cylindrical inner cavity, respectively.
  • the compressed medium is compressed.
  • the compressor has the advantages of low vibration, low noise, and the like in addition to all the advantages of the rotating device or the rotating system.
  • the invention also provides an engine.
  • the engine uses the rotating system described in the first, second, third and fourth embodiments of the rotating device or the rotating system according to the first and second embodiments of the rotating device.
  • the high-pressure gas entering from the combustion chamber via the fluid inlet and outlet seat and the fluid inlet passage pushes the three rotating devices to work sequentially, thereby driving the spindle to rotate, and then the torque generated by the spindle is transmitted to the outside of the cylinder body cavity.
  • the engine has the advantages of low vibration, low noise, and the like in addition to all the advantages of the rotating device or the rotating system.
  • (1) dividing the inner cavity into a plurality of chambers may also adopt other methods than the cylinder block, for example, the plurality of rotating devices respectively have independent cylinders instead of sharing the same cylinder;
  • the main rotating device and the secondary rotating device may be distinguished, as long as both are rotating devices of the eccentric rotor structure, and two inner cavities are used, and one of them is balanced for the other. Heavy, all belong to the scope of protection of the present invention
  • the isolation mechanism can take various forms, and is not limited to the types listed in the embodiments;
  • the number of holes or the number of the positioning holes and the steel balls provided on the circumference of the outer extension portion of the outer ring portion of the seal holder can be adjusted as needed, and the number of layers T is generally one, two or three layers. , the number is generally greater than 3, and is equally distributed along the circumference;
  • the present invention utilizes the secondary rotating device symmetrically disposed on both sides of the main rotating device to dynamically balance the main rotating mechanism, thereby not only improving energy utilization, but also achieving complete symmetrical dynamic balance, reducing vibration and noise.
  • the rotating system of the invention and the fluid mechanical structure using the same are simple and the realization cost is low; the positioning member and the sealing member are organically combined to provide a similar thrust ball.
  • the positioning and sealing assembly of the bearing can realize the sealing function while positioning; in the rotating device and the rotating system of the positioning sealing assembly, a side pressure chamber is arranged between the side of the rolling piston wheel and the positioning sealing assembly, and the inner side of the side pressure chamber is utilized.
  • the pressure generated by the pressure source causes the positioning sealing member to be pressed against the side of the working chamber to realize the side sealing of the rolling piston wheel, thereby improving the sealing effect and the positioning accuracy of the rolling piston wheel in all aspects, in the engine, the fluid motor, the pump, the compressor And various fields have broad application prospects.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention porte sur un système rotatif, ainsi que sur un moteur hydraulique, sur un compresseur, sur une pompe et sur un moteur utilisant ledit système rotatif. Le système rotatif utilise un dispositif rotatif primaire (610), au moins un dispositif rotatif gauche (620) et au moins un dispositif rotatif droit (630). Des mécanismes de rotor excentrique du ou des dispositifs rotatifs gauches et du ou des dispositifs rotatifs droits contrepèsent un mécanisme de rotor excentrique du dispositif rotatif primaire tout en fonctionnant individuellement, ce qui permet d'éviter une consommation d'énergie moindre par des contrepoids dans l'état de la technique et d'améliorer l'efficacité de conversion de l'énergie. Une pièce de positionnement et une pièce d'étanchéité sont en outre combinées ensemble de manière organique pour constituer une structure similaire à un roulement à billes de poussée, réalisent le positionnement d'un mécanisme rotatif à l'intérieur d'une chambre d'opération en utilisant une boule roulante de positionnement (927) et réalisent l'étanchéité latérale du mécanisme rotatif en utilisant un support (926) de la bille de roulement de positionnement, ce qui permet de simplifier la structure mécanique des dispositifs rotatifs, de réduire les coûts. Une chambre de pression latérale est disposée entre le côté d'une roue de piston de roulement (613, 623, 633) et un ensemble d'étanchéité de positionnement (910, 920) de sorte à réaliser l'étanchéité latérale de la roue de piston de roulement, ce qui permet de réaliser un mouvement étanche fiable à jeu nul à frottement réduit.
PCT/CN2016/095995 2016-05-25 2016-08-19 Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif WO2017201895A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201610354113.0 2016-05-25
CN201610354113.0A CN107435628B (zh) 2016-05-25 2016-05-25 定位密封组件及应用其的转动装置、转动系统和流体机械
CNPCT/CN2016/094642 2016-08-11
PCT/CN2016/094642 WO2018027801A1 (fr) 2016-08-11 2016-08-11 Système rotatif, et moteur hydraulique, compresseur, pompe et moteur utilisant ce dernier

Publications (1)

Publication Number Publication Date
WO2017201895A1 true WO2017201895A1 (fr) 2017-11-30

Family

ID=60411076

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/095995 WO2017201895A1 (fr) 2016-05-25 2016-08-19 Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif

Country Status (1)

Country Link
WO (1) WO2017201895A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3173606A (en) * 1963-04-03 1965-03-16 New York Air Brake Co Pump
US3938477A (en) * 1974-02-20 1976-02-17 Outboard Marine Corporation Thrust bearing arrangement for a rotary piston internal combustion engine having a vertical crankshaft
US5102315A (en) * 1989-09-18 1992-04-07 Sanden Corporation Orbiting member fluid displacement apparatus with rotation preventing mechanism
WO2004040141A1 (fr) * 2002-10-31 2004-05-13 Lg Electronics Inc. Compresseur hermetique possedant une plaque z
CN103967787A (zh) * 2013-01-25 2014-08-06 北京星旋世纪科技有限公司 转动装置及应用其的转子式压缩机和流体马达
CN104100299A (zh) * 2013-04-12 2014-10-15 北京星旋世纪科技有限公司 转动装置及应用其的流体马达、发动机、压缩机和泵
CN106151025A (zh) * 2015-03-25 2016-11-23 姚镇 转动系统及应用其的流体马达、压缩机、泵和发动机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3173606A (en) * 1963-04-03 1965-03-16 New York Air Brake Co Pump
US3938477A (en) * 1974-02-20 1976-02-17 Outboard Marine Corporation Thrust bearing arrangement for a rotary piston internal combustion engine having a vertical crankshaft
US5102315A (en) * 1989-09-18 1992-04-07 Sanden Corporation Orbiting member fluid displacement apparatus with rotation preventing mechanism
WO2004040141A1 (fr) * 2002-10-31 2004-05-13 Lg Electronics Inc. Compresseur hermetique possedant une plaque z
CN103967787A (zh) * 2013-01-25 2014-08-06 北京星旋世纪科技有限公司 转动装置及应用其的转子式压缩机和流体马达
CN104100299A (zh) * 2013-04-12 2014-10-15 北京星旋世纪科技有限公司 转动装置及应用其的流体马达、发动机、压缩机和泵
CN106151025A (zh) * 2015-03-25 2016-11-23 姚镇 转动系统及应用其的流体马达、压缩机、泵和发动机

Similar Documents

Publication Publication Date Title
CN102812208A (zh) 旋转式压缩机和方法
EP2274503B1 (fr) Dispositif a pistons rotatifs utilisable comme compresseur, pompe, pompe a vide, turbine, moteur ou autres machines hydrauliques ou pneumatiques menantes ou menees
RU2683005C2 (ru) Шестеренчатый насос с внешним зацеплением, объединенный с двумя независимо приводимыми в действие первичными приводами
CN104100299B (zh) 转动装置及应用其的流体马达、发动机、压缩机和泵
US10323636B2 (en) Gear pump with end plates or bearings having spiral grooves
US10962004B2 (en) Synchronized conical screw compressor or pump
US7614337B2 (en) Rotary radial piston machine
CN103732921B (zh) 微型泵以及用于微型泵的支承元件和工作方法
CN111396279B (zh) 力平衡式二维柱塞泵
NO329713B1 (no) Eksenterskruepumpe med en indre og en ytre rotor
WO2017202346A1 (fr) Ensemble de positionnement et d'étanchéité et système rotatif, machine fluidique et dispositif rotatif utilisant ce dernier
CN103423150A (zh) 转子流体机械变容机构
US3492948A (en) Hydraulic pump/motor
CA2903906C (fr) Rotor a axe double
WO2017201895A1 (fr) Système rotatif ainsi que moteur hydraulique, compresseur, pompe et moteur utilisant ledit système rotatif
CN207934938U (zh) 转轮活塞同步回旋机构
US7192264B2 (en) Hyrdraulic motor
US20150260184A1 (en) Segmented Positive Displacement Rotor Housing
US3056355A (en) Hydraulic apparatus
WO2018027801A1 (fr) Système rotatif, et moteur hydraulique, compresseur, pompe et moteur utilisant ce dernier
US3136260A (en) Control shaft mounting for fluid handling device
RU2476725C2 (ru) Роторная гидромашина
RU155975U1 (ru) Радиально-поршневой насос с фазово-объемным регулированием подачи
WO2015104191A1 (fr) Moteur à palettes hydraulique placé sur un stator, le fluide sous pression entrant par un arbre creux et continuant radialement dans le rotor à travers un ou des canaux adaptés
CN105179229A (zh) 外啮合齿轮泵及液力变速器液压系统

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16902881

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 16902881

Country of ref document: EP

Kind code of ref document: A1