WO2017202346A1 - 定位密封组件及应用其的转动装置、转动系统和流体机械 - Google Patents

定位密封组件及应用其的转动装置、转动系统和流体机械 Download PDF

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Publication number
WO2017202346A1
WO2017202346A1 PCT/CN2017/085772 CN2017085772W WO2017202346A1 WO 2017202346 A1 WO2017202346 A1 WO 2017202346A1 CN 2017085772 W CN2017085772 W CN 2017085772W WO 2017202346 A1 WO2017202346 A1 WO 2017202346A1
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WO
WIPO (PCT)
Prior art keywords
positioning
working chamber
sealing
rolling piston
piston wheel
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PCT/CN2017/085772
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English (en)
French (fr)
Inventor
姚其槐
Original Assignee
姚镇
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Application filed by 姚镇 filed Critical 姚镇
Publication of WO2017202346A1 publication Critical patent/WO2017202346A1/zh

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    • 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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F11/00—Arrangements of sealings in combustion engines 
    • F02F11/007—Arrangements of sealings in combustion engines  involving rotary applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F04C27/006—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type pumps, e.g. gear pumps

Definitions

  • the present disclosure relates to the field of fluid machinery technology, and more particularly to a positioning seal assembly and a rotating device, a rotating system and a fluid machine using the same.
  • a fluid machine is an energy conversion device that converts fluid pressure energy from mechanical energy, such as a fluid motor, a compressor, a pump, an engine, and the like.
  • the eccentric rotor structure is a structure commonly used in the field of fluid machinery, and has the advantages of simple structure and stable operation.
  • the present disclosure provides a positioning seal assembly and a rotating device, a rotating system and a fluid machine therewith to simplify the mechanical construction of the fluid machine and improve the working efficiency of the fluid machine.
  • a positioning seal assembly includes: N positioning balls 927; and a sealing cage 926 having a double-layered annular structure including: an inner ring portion 926a and an outer ring portion 926b; wherein the outer ring portion extends toward the radially outer side to form
  • the outer extension portion 926b' forms a third step structure between the outer extension portion 926b' and the inner ring portion 926a; the positioning holes are uniformly disposed on the outer extension portion in the circumferential direction, and one or more positioning holes are disposed in each positioning hole Position the ball, where M ⁇ 3.
  • a rotating device comprises: a working chamber; a main shaft 200 whose central axis coincides with a central axis of the working chamber; a rotating mechanism 610, which is sleeved on a portion of the main shaft located in the working chamber, and forms a shaft by rotating motion in the working chamber The extended sealing working space; and the side positioning sealing mechanism 900, comprising: one or two of the above-mentioned positioning sealing assemblies mounted between the rotating mechanism side and the corresponding side of the working chamber for sealing the corresponding side of the rotating mechanism .
  • a rotating device comprises: a working chamber; a main shaft 200 whose central axis coincides with a central axis of the working chamber; a rotating mechanism 610, which is sleeved on a portion of the main shaft located in the working chamber, and forms a shaft by rotating motion in the working chamber An extended sealing working space; and a side positioning sealing mechanism 900, including: one or Two positioning sealing assemblies are mounted between one side of the rotating mechanism and the corresponding side of the working chamber for achieving sealing of the corresponding side of the rotating mechanism.
  • the positioning sealing assembly comprises: a side positioning ring 911 having a double-layered annular structure as a whole, comprising: an inner ring portion 911a and an outer ring portion 911b, the outer ring portion 911b extending outward in a radial direction to form an outer extending portion 911b', A second stepped structure is formed between the outer extension portion 911b' and the inner ring portion 911a; and a floating piston ring 912 is mounted between the rotating mechanism 610 and the outer extension portion 911b' of the side positioning ring.
  • a rotation system comprises: 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 at least three rotating devices are the rotating devices described above. Wherein, the at least three rotating devices share the same main shaft, and the working chambers are separated from each other and work independently.
  • a fluid machine comprises: the above-mentioned rotating device or the above-mentioned rotating system, including but not limited to the following four cases:
  • the fluid machine is a fluid motor in which the high-pressure fluid entering from the fluid inlet pushes the rolling piston wheel to rotate, and the torque generated by the main shaft is transmitted to the outside of the working chamber, and the low-pressure fluid after the work is discharged through the fluid outlet. ;or
  • the fluid machine is a pump, in which the main shaft transmits torque to the working chamber; under the driving of the main shaft, the rolling piston wheel rolls forward along the working chamber, and the fluid entering from the fluid inlet is pumped into the working chamber. And discharging the fluid through the fluid outlet; or
  • the fluid machine is a compressor in which the main shaft transmits torque to the working chamber, the rolling piston wheel rolls forward along the working chamber, compresses the compressed medium, and the compressed medium is discharged through the fluid outlet;
  • the fluid machine is an engine in which the high-pressure gas entering from the combustion chamber pushes the rolling piston wheel to roll forward along the working chamber, and the torque generated by the main shaft is transmitted to the outside of the working chamber, and the low-pressure gas after work is performed. Discharge through the fluid outlet.
  • a fluid motor is also provided.
  • the fluid motor includes the above-described rotating device or rotating system.
  • the high-pressure fluid entering the fluid inlet enters the rotating device to push the rolling piston wheel to rotate, 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.
  • a pump is also provided.
  • the pump includes the above-described rotating device or rotating system.
  • the main shaft transmits torque to the working chamber;
  • the rolling piston wheel rolls forward along the working chamber, pumping fluid entering from the fluid inlet into the working chamber and discharging the fluid through the fluid outlet.
  • a compressor is also provided.
  • the compressor includes the above-described rotating device or rotating system.
  • the main shaft transmits torque to the working chamber, and the rolling piston wheel rolls forward along the working chamber to compress the compressed medium, and the compressed medium is discharged through the fluid outlet.
  • an engine is also provided.
  • the engine includes the above-described rotating device or rotating system.
  • the high pressure gas entering from the combustion chamber pushes the rolling piston wheel forward along the working chamber, and the torque generated by the main shaft is transmitted to the outside of the working chamber, and the low pressure gas after the work is discharged through the fluid outlet.
  • 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;
  • 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;
  • An elastic member such as a pressure spring or an O-ring is disposed in the side pressure chamber, and the elastic member makes the roller
  • the sealing member on the inside of the piston wheel presses against the wear liner on the side of the chamber, in which case a reliable seal of the side of the rolling piston wheel can be achieved even if the through hole on the rolling piston wheel is blocked.
  • FIG. 1 is a longitudinal sectional view of a prior art three-cylinder rotating system
  • FIG. 2 is a schematic structural view of a rotating device according to a first embodiment of the present disclosure
  • FIG. 3 is a schematic structural view of a rotating device according to a second embodiment of the present disclosure.
  • FIG. 4A and 4B are perspective views of the right positioning seal assembly of the rotating device of FIG. 3 at two different viewing angles, respectively;
  • Figure 5 is a schematic view showing the rolling track of the steel ball in the right positioning seal assembly of the rotating device of Figure 3 on the wear liner of the right side of the main chamber;
  • FIG. 6 is a schematic view showing three typical arrangement modes of a positioning hole and a steel ball in the present disclosure
  • Fig. 7 is a schematic view showing the arrangement of steel balls in a circular arc positioning hole in the present disclosure.
  • 611a-left positioning portion 611b-right positioning member
  • 911a-inner ring 911b-outer ring
  • 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 having a central axis thereof The central axes of the inner chambers coincide, passing through the left chamber, the main chamber and the right chamber in sequence; the main rotating mechanism 610, the left rotating mechanism 620 and the right rotating mechanism 630 are respectively located in the corresponding chambers, including: eccentric The rotor assembly is sleeved on a portion of the main shaft located in the chamber, and forms an axially extending crescent-shaped sealing chamber (C, c1, c2) by rotating motion in the chamber; wherein the eccentric rotor assembly in the left rotating mechanism And the eccentric rotor assembly in the right rotating mechanism balances the eccentric force generated by the eccentric rotor assembly of the main rotating mechanism during operation.
  • a cylinder internal cavity partitioned into three mutually independent cylindrical chambers: a left chamber, a main chamber and a right chamber
  • 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 rotating mechanism 630 constitutes a right rotating device, that is, the rotating system of the present embodiment actually includes three rotating devices sharing the same main shaft.
  • the main rotating device is the main output device of the rotating system
  • the left rotating device and the right rotating device are used as auxiliary auxiliary output devices.
  • the side seal is one of the key factors affecting the reliability of the life of the entire rotating system.
  • the part of the eccentric rotor assembly that is in contact with the outer sealed end cap is set.
  • the wear-resistant lining and the eccentric rotor contact surface are mirror-polished and smoothed to reduce friction and improve sealing.
  • an O-ring sealing ring (523, 533, 534, 535) is disposed between the wear-resistant lining and the radially outer sealing end cover, and the O-shaped sealing rubber ring can effectively ensure the sealing inside the chamber.
  • the applicant found that the above-mentioned sealing structure and positioning mechanism are separately designed and assembled, the structure is complicated, and the assembly is difficult; in addition, the above sealing scheme requires very high processing precision for the wear-resistant lining, if If the lining plate is too thin, it will cause the seal to fail. If the wear lining plate is too thick, the rolling piston wheel will be too much pressure, which will increase the friction and affect the working efficiency of the entire rotating system. The applicant has therefore further proposed the present disclosure.
  • the idea of solving the problem in the present disclosure 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 disclosure organically combines the positioning member and the sealing member 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 rotation by using the cage of the positioning ball.
  • the side seal of the mechanism the present disclosure provides a side pressure chamber between the side of the rolling piston wheel and the positioning seal assembly, and the pressure generated by the pressure source inside the side pressure chamber causes the positioning sealing member to press the wear liner 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 of the rotating system of Fig. 1, except that a specially designed side sealing structure is employed.
  • 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 seal seals the axially extending crescent-shaped sealed chamber C into two mutually independent variable volume chambers, respectively, through the fluid inlet and the fluid The exit is controllable to the outside world.
  • 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 supporting 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 The rotation.
  • 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 support 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 that supports the bearing 612 is provided on a radially outer side of the eccentric bushing 611. Referring to FIG. 2, 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 support 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 support 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 also 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 outer cylindrical portion 613c in the axial direction, and the diameter d of the through holes (613c' and 613c") is introduced. It is 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 integrally embedded between the rolling piston wheel and the wear-resistant lining of the left side of the main chamber to realize 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 support 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 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 support 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
  • the left side pressure chamber 913 is introduced through the through hole 613c', and the small amount of the splitting causes the left floating piston ring 912 to abut against the wear liner 521 on the left side of the main chamber, thereby achieving the left side face 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 and the other flow hole is located in the low pressure chamber, or two flow holes are located in the low pressure chamber at the same time, and the pressure chamber to the left side is located in the high pressure chamber.
  • the velocity of the injected fluid is much greater than the velocity of the liquid in the left pressure chamber when in the low pressure chamber, so that the fluid in the left pressure chamber can always maintain a high pressure, so that the left floating piston ring 912 is in close contact with the main chamber.
  • the wear liner 521 on the left side of the chamber does not separate.
  • 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 support bearing needs to work in an oil lubrication environment.
  • the inner extension 921b" is spaced apart from the eccentric bushing by a small distance to prevent loss of lubricating oil for the support 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 is formed by a through hole 613c" opened in the axially right side of the outer cylindrical portion of the rolling piston wheel. The sealed chambers are connected.
  • 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 friction damage.
  • 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 610 as an example.
  • the left rotating device 620 in the rotating system shown in FIG. 1 and the rotating device 630, or the rotating device including only one chamber The side seal can be applied using the solution of the embodiment.
  • 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 disclosure.
  • a rotation system to which the rotating device of the first embodiment is applied.
  • the rotating system of the present embodiment is similar to the rotating system shown in FIG. 1, and includes three rotating devices of an eccentric rotor structure, that is, a main rotating device, a left rotating device and a right rotating device; the three rotating devices are rotating The rotating device of the first embodiment of the device.
  • the three rotating devices share the same main shaft, and the working chambers are spaced apart from each other and work independently, wherein the eccentric rotor structure of the left rotating device and the right rotating device balances the eccentric rotor structure of the main rotating device.
  • the disclosure is not limited thereto.
  • the inner cavity can be divided into 2N+1 chambers, and the corresponding eccentric rotor assembly is composed of 2N+1 rotating devices, that is, symmetrically on both sides of the main rotating device.
  • the present disclosure can also be implemented by providing N sub-rotating devices. However, considering N such as process complexity, the N is a positive integer greater than or equal to 1, generally not more than three.
  • 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 is different from the rotating device of the first embodiment 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 to the side pressure chamber Solve the problem of "heavy oil” blocking the flow hole and lack of pressure on the side pressure chamber just after starting.
  • 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 support 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 communicates with the crescent-shaped sealing chamber through a through-hole 613c" opened in the axially right side of the outer cylindrical portion of the rolling piston wheel.
  • 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 holder 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 supporting bearing lubrication leakage.
  • the longitudinal section of the seal holder 926 will be rotated “clockwise” by 90 degrees.
  • Type instead of a “convex” shape that rotates 90° counterclockwise.
  • 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 matched with the positioning holes are respectively accommodated in corresponding positions.
  • the axially inner side of the steel ball 927 is pressed against the middle cylindrical portion 613b of the rolling piston wheel; its axially outer side is pressed against the wear-resistant liner on the right side surface of the main chamber.
  • 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 5 is a schematic view showing the rolling track of the steel ball in the right positioning seal assembly of the rotating device of Figure 3 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 sealing rolling bearing on the wear-resistant lining plane shows 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 positioning holes and the steel balls are distributed on two concentric circles of the outer extension of the seal holder.
  • 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 surface of the rolling piston wheel, which can form an annular contact surface, and has a bearing capacity and reliability. 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 on the sidetrack of the piston star wheel 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 rotating device of the present embodiment is slightly different from the positioning device of the first embodiment in the positioning manner of the support bearing 612.
  • the support 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 support bearing.
  • the lower portion of the support bearing 612 is sandwiched and positioned between the left positioning member 611a' and the right positioning member 611b.
  • This embodiment provides a positioning seal assembly as shown in Figs. 4A and 4B, which can be applied, for example, to the third embodiment of the 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 disclosure may 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 present disclosure, the positioning holes may also be 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 disclosure, two can be set in each long hole. 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 sealing cage does not directly bear the load of the rolling piston wheel, the rigidity is not large and can be made Use a flexible material suitable for sealing such as rubber, plastic or graphite.
  • 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 first 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.
  • the present disclosure also provides a fluid motor.
  • the fluid motor employs the rotating device described in the first and third embodiments or the rotating system described in the second and fifth embodiments. among them,
  • the high-pressure fluid entering the fluid inlet enters the rotating device to push the rolling piston wheel to rotate, 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 present disclosure also provides a pump.
  • the pump employs the rotating device described in the first and third embodiments or the rotating system described in the second and fifth embodiments.
  • the main shaft transmits torque to the working chamber; under the driving of the main shaft, the rolling piston wheel rolls forward along the working chamber, and the fluid entering from the fluid inlet is pumped into the working chamber, and the fluid is discharged through the fluid outlet. discharge.
  • the present disclosure also provides a compressor.
  • the compressor employs the rotating device described in the first and third embodiments or the rotating system described in the second and fifth embodiments.
  • the main shaft transmits torque to the working chamber, and the eccentric bushing is used as a medium.
  • the rolling piston wheel rolls forward along the working chamber to compress the compressed medium; the compressed medium is discharged through the fluid outlet.
  • the present disclosure also provides an engine.
  • the engine employs the rotating device described in the first and third embodiments or the rotating system described in the second and fifth embodiments.
  • the high-pressure gas entering from the combustion chamber pushes the rolling piston wheel forward along the working chamber, and the generated torque is transmitted to the outside of the working chamber through the main shaft, and the low-pressure gas after the work is discharged through the fluid outlet.
  • 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 disclosure organically combines the positioning member and the sealing member, and provides a positioning sealing assembly similar to a thrust ball bearing, which can realize the sealing function while positioning; in the application of the rotating device 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 pressure generated by the pressure source inside 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, thereby
  • the sealing effect and the positioning accuracy of the rolling piston wheel are improved in all aspects, and have broad application prospects in various fields such as an engine, a fluid motor, a pump, and a compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

一种定位密封组件，包括N个定位滚球（927）和呈双层环状结构的密封保持架（926），密封保持架（926）包括内环部（926a）和外环部（926b）；外环部（926b）朝向径向外侧延伸形成外延伸部（926b'），外延伸部（926b'）与内环部（926a）之间形成第三台阶结构，外延伸部（926b'）上沿圆周方向均匀设置M个定位孔，每个定位孔内配置一个或多个定位滚球（927）。还包括应用该定位密封组件的转动装置、转动系统和流体机械。该定位密封组件利用定位滚球实现工作腔室内转动机构的定位，利用定位滚球的保持架实现转动机构的侧面密封，简化了转动装置的机械机构，降低了成本。

Description

定位密封组件及应用其的转动装置、转动系统和流体机械 技术领域
本公开涉及流体机械技术领域，尤其涉及一种定位密封组件及应用其的转动装置、转动系统和流体机械。
背景技术
流体机械是一种将流体压力能与机械能之间进行相互转换的能量转换装置，典型的如：流体马达、压缩机、泵、发动机等。偏心转子结构是流体机械领域颇为常用的一种结构，具有结构简单、运行平稳等优点。
公开内容
(一)要解决的技术问题
本公开提供了一种定位密封组件及应用其的转动装置、转动系统和流体机械，以简化流体机械的机械构造，提高流体机械的工作效率。
(二)技术方案
根据本公开的一个方面，提供了一种定位密封组件。该定位密封组件包括：N个定位滚球927；以及密封保持架926，呈双层环状结构，包括：内环部926a和外环部926b；其中，外环部朝向径向外侧延伸，形成外延伸部926b′，该外延伸部926b′与内环部926a之间形成第三台阶结构；该外延伸部上沿圆周方向均匀设置M个定位孔，每一定位孔内配置一个或多个定位滚球，其中，M≥3。
根据本公开的另一个方面，还提供了一种转动装置。该转动装置包括：工作腔室；主轴200，其中心轴线与工作腔室的中心轴线重合；转动机构610，套设于主轴位于工作腔室的部分，通过在工作腔室中做旋转运动形成轴向延伸的密封工作空间；以及侧面定位密封机构900，包括：一个或两个上述的定位密封组件，安装于转动机构一侧与工作腔室相应侧面之间，用于实现转动机构相应侧面的密封。
根据本公开的再一个方面，还提供了一种转动装置。该转动装置包括：工作腔室；主轴200，其中心轴线与工作腔室的中心轴线重合；转动机构610，套设于主轴位于工作腔室的部分，通过在工作腔室中做旋转运动形成轴向延伸的密封工作空间；以及侧面定位密封机构900，包括：一个或 两个定位密封组件，该定位密封组件安装于转动机构的一侧与工作腔室相应侧面之间，用于实现转动机构相应侧面的密封。其中，该定位密封组件包括：侧面定位环911，整体呈双层环状结构，包括：内环部911a和外环部911b，外环部911b朝向径向外侧延伸，形成外延伸部911b′，该外延伸部911b′与内环部911a之间形成第二台阶结构；以及浮动活塞环912，安装于转动机构610与侧面定位环的外延伸部911b′之间。
根据本公开的又一个方面，还提供了一种转动系统。该转动系统包括：至少三个偏心转子结构的转动装置，即一主转动装置，至少一左转动装置和至少一右转动装置；该至少三个转动装置为上述的转动装置。其中，该至少三个转动装置共用同一根主轴、工作腔室彼此隔开且独立工作。
根据本公开的又一个方面，提供了一种流体机械。该流体机械包括：上述的转动装置或上述的转动系统，其中，包括但不限于以下四种情况：
(1)流体机械为流体马达，该流体马达中，由流体进口进入的高压流体推动滚动活塞轮转动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压流体通过流体出口排出；或者
(2)流体机械为泵，该泵中，主轴将扭矩传递至工作腔室内；在主轴的带动下，滚动活塞轮沿工作腔室向前滚动，将由流体进口进入的流体泵入工作腔室内，并通过流体出口将流体排出；或者
(3)流体机械为压缩机，该压缩机中，主轴将扭矩传递至工作腔室内，滚动活塞轮沿工作腔室向前滚动，对压缩介质进行压缩，压缩后的介质通过流体出口排出；或者
(4)流体机械为发动机，该发动机中，由燃烧室进入的高压气体推动滚动活塞轮沿工作腔室向前滚动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压气体通过流体出口排出。
根据本公开的又一个方面，还提供了一种流体马达。该流体马达包括：上述的转动装置或转动系统。该流体马达中，流体进口进入的高压流体进入转动装置，推动滚动活塞轮转动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压流体通过流体出口排出。
根据本公开的又一个方面，还提供了一种泵。该泵包括：上述的转动装置或转动系统。该泵中，主轴将扭矩传递至工作腔室内；在主轴的带动 下，滚动活塞轮沿工作腔室向前滚动，将由流体进口进入的流体泵入工作腔室内，并通过流体出口将流体排出。
根据本公开的又一个方面，还提供了一种压缩机。该压缩机包括：上述的转动装置或转动系统。该压缩机中，主轴将扭矩传递至工作腔室内，滚动活塞轮沿工作腔室向前滚动，对压缩介质进行压缩，压缩后的介质通过流体出口排出。
根据本公开的又一个方面，还提供了一种发动机。该发动机包括：上述的转动装置或转动系统。该发动机中，由燃烧室进入的高压气体推动滚动活塞轮沿工作腔室向前滚动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压气体通过流体出口排出。
(三)有益效果
从上述技术方案可以看出，本公开定位密封组件及应用其的转动装置、转动系统和流体机械至少具有以下有益效果其中之一：
(1)提供了一种不同以往的、新颖的定位密封解决方案；
(2)将定位件和密封件有机结合在一起，构成类似推力球轴承的结构，来实现定位和密封两种功能，具有结构简单和性能可靠的优点；
(3)利用定位滚球实现工作腔室内转动机构的定位，将滑动摩擦转换为滚动摩擦，减小了摩擦损耗，提高了转动装置的工作效率，同时提升了定位精度；
(4)利用定位滚球的保持架实现转动机构的侧面密封，不必再额外设置密封部件，简化了部件的机械结构，降低了成本；
(5)在滚动活塞轮侧面与定位密封组件之间设置侧压力腔，利用侧压力腔内的侧压力源产生的压力使定位密封部件压紧工作腔室侧面，实现滚动活塞轮的侧面密封，在这种情况下，滚动活塞轮不必与左右两侧的工作腔室侧面接触，而是在工作腔室两侧面之间浮起来，从而实现了磨擦最小化的零间隙可靠密封运动；
(6)在滚动活塞轮上开设通流孔，把缸体内的高压流体的极少量分流导入侧压力腔，将该高压流体作为弹性件，利用其产生的压力使侧压力腔内的密封部件压紧腔室侧面的耐磨衬板，实现滚动活塞轮的侧面密封；
(7)在侧压力腔内设置压力弹簧或O型圈等弹性件，该弹性件使滚 动活塞轮内侧的密封部件压紧腔室侧面的耐磨衬板，在这种情况下，即使滚动活塞轮上的通流孔被阻塞，仍然可以实现滚动活塞轮侧面的可靠密封。
附图说明
图1为现有技术三缸式转动系统的纵剖面示意图；
图2为根据本公开第一实施例转动装置的结构示意图；
图3为根据本公开第二实施例转动装置的结构示意图；
图4A和图4B分别为图3所示转动装置中右定位密封组件在两不同视角下的立体图；
图5为图3所示转动装置中右定位密封组件中钢球在主腔室右侧面的耐磨衬板上滚动轨迹的示意图；
图6为本公开中定位孔和钢球三种典型设置方式的示意图；
图7为本公开中在圆弧形定位孔内设置钢球的示意图。
【主要元件符号说明】
200-主轴
521、522、531、532-耐磨衬板；523、533、534、535-O型密封胶圈；
610-主转动机构；620左转动机构；630右转动机构；
611-偏心轴套；
611a-左定位部；611b-右定位件；
612-支撑轴承；
613-滚动活塞轮；
613a-内筒部；613b-中筒部；
613c-外筒部；613c′、613c″-通流孔；
900-侧面定位密封机构；
910-左定位密封组件；
911-左侧面定位环；912-左浮动活塞环；913-左侧压力腔；
911a-内环部；911b-外环部；
911b′-外环部的外延伸部；
920-右定位密封组件；
921-右侧面定位环；922右浮动活塞环；923-右侧压力腔；
921a-内环部；921b-外环部；
921b″-外环部的内延伸部；
926-密封保持架；
926a-内环部；926b-外环部；
926b′-外环部的外延伸部；926b″-外环部的内延伸部；
927-钢球；
C-转动系统中主转动机构对应的月牙形密封腔；
c1、c2-转动系统中左、右转动机构对应的月牙形密封腔。
具体实施方式
本申请的申请人在2015年3月15日提交了一份中国专利申请(中国专利申请号：201510134609.2)。在该份中国专利申请中，申请人提供了一种采用副转动装置的偏心转子结构作为平衡配重块对主转动装置进行动平衡的转动系统。请参照图1，该转动系统包括：缸体内腔，其被分隔为三个相互独立的圆筒形的腔室：左腔室、主腔室和右腔室；主轴200，其中心轴线与内腔的中心轴线重合，依次穿过左腔室、主腔室和右腔室；主转动机构610、左转动机构620和右转动机构630，分别位于相应的腔室内，均包括：偏心转子组件，套设于主轴位于所在腔室的部分，通过在所在腔室中做旋转运动形成轴向延伸的月牙形密封腔(C，c1，c2)；其中，左转动机构中偏心转子组件和右转动机构中偏心转子组件对主转动机构的偏心转子组件在运行过程中所产生偏心力进行平衡配重。
在图1所示的转动系统中，主腔室和与相应的主转动机构610组成主转动装置，左腔室与相应的左转动机构620组成左转动装置，右腔室与相应的右转动机构630组成右转动装置，即本实施例转动系统实际上包含共用同一根主轴的三个转动装置。而主转动装置为转动系统的主出力设备，左转动装置和右转动装置作为辅助的副出力设备。
对于图1所示的转动系统，侧面密封是影响整个转动系统寿命可靠性的关键因素之一，在左(右)腔室的外侧，偏心转子组件与外侧密封端盖相接触摩擦的部分，设置有环状的耐磨衬板(522、521、531、532)。该耐磨衬板与偏心转子的接触平面进行镜面抛光平滑加工，减少磨擦与提高密封。并且，耐磨衬板与径向外侧的密封端盖之间设置有O型密封胶圈(523、533、534、535)，该O型密封胶圈可以有效地保证腔室内的密封。
然而，在后续的生产实践中，申请人发现：上述密封结构和定位机构分别设计和装配，结构复杂，装配比较困难；此外，上述密封方案对耐磨衬板的加工精度要求非常高，如果耐磨衬板过薄，则会造成密封的失效，如果耐磨衬板过厚，则会给滚动活塞轮太大的压力，导致其摩擦加大，从而影响整个转动系统的工作效率。故申请人进一步提出了本公开。
本公开解决问题的思路在于：把定位与密封的功能目标明确分开，用不同的机械要素去完成不同的任务；并且，尽量把不同的机械要素有机组合起来，互相支持，共同去完成任务。
在上述思路的指导下，本公开将定位件和密封件有机结合在一起，构成类似推力球轴承的结构，利用定位滚球实现工作腔室内转动机构的定位，利用定位滚球的保持架实现转动机构的侧面密封。同时，本公开在滚动活塞轮侧面与定位密封组件之间设置侧压力腔，利用侧压力腔内侧压力源产生的压力使定位密封部件压紧腔室侧面的耐磨衬板，实现滚动活塞轮的侧面密封。
为使本公开的目的、技术方案和优点更加清楚明白，以下结合具体实施例，并参照附图，对本公开进一步详细说明。
需要说明的是，为了表述清楚和简洁，在下文中的多处采用了“径向”和“轴向”的表述方式。如无特别注明，此处的“径向”和“轴向”均是相对于工作腔室而言的，即沿工作腔室主轴方向或与该方向平行的方向为“径向”，垂直于工作腔室主轴方向或与该方向平行的方向为“轴向”。这也是本领域技术人员通常采用的表述方式，后续不再赘述。
一、转动装置第一实施例
本实施例转动装置与图1所示转动系统中的一转动装置类似，区别在于采用了特别设计的侧面密封结构。下文中以主转动装置为例进行说明。
本实施例转动装置包括：主腔室、主轴200、主转动机构610和侧面定位密封机构900。其中，主轴200的中心轴线与主腔室的中心轴线重合。主转动机构610包括：偏心转子组件，套设于主轴位于主腔室的部分，通过在所在腔室中做旋转运动形成轴向延伸的月牙形密封腔C；隔离机构，其前端与偏心转子组件相密封，从而将轴向延伸的月牙形密封腔C分隔为相互独立的两容积可变腔室，该两容积可变腔室分别通过流体入口和流体 出口与外界可控连通。
偏心转子组件包括：偏心轴套611，套设并固定于主轴位于主腔室的部分，其中心轴线与主轴的中心轴线相互平行且错开预设距离；滚动活塞轮613，套设于偏心轴套上，其中心轴线与偏心轴套的中心轴线重合；支撑轴承612，对称地套设于偏心轴上，其内套圈固定于偏心轴套，其外套圈固定于滚动活塞轮，以隔绝两者的转动。其中，滚动活塞轮613压紧于工作腔室一侧的内圆筒面，并沿该内圆筒面滚动，使工作腔室的内圆筒面和滚动活塞轮的外圆柱面之间形成轴向延伸的月牙形密封腔C。
本实施例中，支撑轴承612相对于主腔室左右对称，并且其宽度小于主腔室的宽度。
在偏心轴套611的径向外侧具有支撑轴承612的定位结构。请参照图2，偏心轴套611的左侧向上方延伸形成左定位部611a。偏心轴套的右侧固定有右定位件611b。支撑轴承的下部被夹置定位于左定位部611a和右定位件611b之间。
滚动活塞轮613整体呈筒状结构，其在径向上，由内而外分为宽度逐步增加的三部分。其中，最内侧的内筒部613a的左右两侧与支撑轴承的左右两侧相平齐。最外侧的外筒部613c的左右两侧分别与主腔室内圆筒面左侧面的耐磨衬板521和右侧面的耐磨衬板531靠近但不接触，两者之间的间隙为Δ1。内筒部613a和外筒部613c之间为中筒部613b，该中筒部613b的厚度大于内筒部613a和外筒部613c的厚度。其中，滚动活塞轮的内筒部613a与中筒部613b之间形成第一台阶结构。
需要说明的是，为了表述方便，本文将筒状结构分为内筒部、中筒部和外筒部，但实际上，该三部分也可以是一体的。在这种情况下，内筒部、中筒部和外筒部并非是分离的三部分。
耐磨衬板(521、531)的材料，可用中国产耐磨钢板NM400、NM450及更硬的NM500；也可使用其它耐磨钢材如瑞典产HARDOX400、HARDOX450、HARDOX500及更硬的HARDOX600。在高温下工作的材料可以使用耐高温的钢材，乃至工业陶瓷和硬质合金。
在外筒部613c的轴向的左侧和右侧分别在圆周方向上均匀设置至少2个通流孔(613c′和613c″)，该通流孔(613c′和613c″)的直径d介 于0.5mm～2mm之间。
请参照图2，侧面定位密封机构900包括：左定位密封组件910和右定位密封组件920。左定位密封组件910进一步包括：左侧面定位环911和左浮动活塞环912。右定位密封组件920进一步包括：右侧面定位环921和右浮动活塞环922。
对于左定位密封组件910和右定位密封组件920，两者的结构大体相同，以下主要以左定位密封组件910为例进行详细说明。
左侧面定位环911整体呈双层环状结构，嵌设于滚动活塞轮与主腔室左侧面的耐磨衬板之间，以实现滚动活塞轮的定位。该左侧面定位环911在轴向由内向外的方向形成两部分-内环部911a和外环部911b。内环部911a的右侧抵接于支撑轴承的左侧和滚动活塞轮的内筒部613a，外环部911b抵接于主腔室内圆筒面左侧面的耐磨衬板521。
相对于内环部911a，外环部911b朝向径向外侧延伸，形成外延伸部911b′，该外延伸部911b′与内环部911a之间形成第二台阶结构。如上所述，滚动活塞轮的内筒部613a与中筒部613b之间形成第一台阶结构。该第二台阶结构和该第一台阶结构相互卡合，实现了左侧面定位环对支撑轴承和滚动活塞轮的定位。
左侧面定位环的外环部的外延伸部911b′与滚动活塞轮的外筒部613c之间形成左容置空间。左浮动活塞环912被设置于左容置空间内。
对于左浮动活塞环912而言，其在径向上分别与滚动活塞轮的外筒部和左侧面定位环的外环部的外延伸部911b′密封。而在轴向上，左浮动活塞环912的厚度D1大于外筒部613c的左侧与主腔室内圆筒面的左侧面之间的距离Δ1，从而可以将外筒部613c的左侧与主腔室内圆筒面的左侧面之间的间隙封住。并且，厚度D1小于滚动活塞轮的中筒部613b与主腔室内圆筒面左侧面的距离D，从而在左浮动活塞环912与滚动活塞轮的中筒部613b之间形成环状的左侧压力腔913。该左侧压力腔913通过开设于滚动活塞轮的外筒部613c的轴向左侧的通流孔613c′与月牙形密封腔相连通。一般情况下，Δ1的尺寸与加工精度有直接关系，介于5μm～50μm之间，侧压力腔的轴向尺寸介于0.2mm～1.0mm之间。
本实施例转动装置在运转过程中，而月牙形密封腔内的少量高压流体 通过通流孔613c′被导入左侧压力腔913，该少量分流使左浮动活塞环912紧贴与主腔室左侧的耐磨衬板521，从而实现了滚动活塞轮的左侧面密封。
如上所述，月牙形密封腔C被隔离机构分隔为相互独立的两容积可变腔室。为表述方便起见，将该两容积可变腔室称为：高压腔和低压腔。虽然通流孔自身的位置不变，但其随着滚动活塞轮不断向前滚动，从而会周期性的处于高压腔和低压腔。
以左定位密封组件为例，在滚动活塞轮的外筒部左侧的圆周上均匀开设有2个流通孔。经由实验证明，无论该2个流通孔是同时位于高压腔，一个流通孔位于高压腔另一个流通孔位于低压腔，还是2个流通孔同时位于低压腔，由于位于高压腔时向左侧压力腔注入流体的速度远远大于处于低压腔时左侧压力腔液体流出的速度，因此，在左侧压力腔内的流体能够始终保持较高的压力，从而使左浮动活塞环912紧贴与主腔室左侧的耐磨衬板521不会分开。
一般情况下，可以在滚动活塞轮的外筒部沿圆周方向均匀开设2～10个通流孔。如果通流孔过多的话，可能会对滚动活塞轮的外筒部的强度产生不利影响。而如果通流孔只有一个的话，则注入左侧压力腔的流体将不会流动，在长时间情况下会产生变质，并不利于转动装置的长时间运转。
此外，可以理解的是，基于平衡的考虑，左定位密封组件和右定位密封组件对应的流通孔数目相同，位置对称。
关于右定位密封组件920，其与左定位密封组件基本对称。需要说明的是：在右侧面定位环921中，相对于内环部921a，外环部921b朝向径向内侧延伸至右定位件611b的轴向外侧，靠近偏心轴套611的位置，形成内延伸部921b″。其中，内延伸部921b′′与偏心轴套611的距离介于20μm～100μm之间。
本实施例中，支撑轴承需要工作在油润滑环境中。内延伸部921b″与偏心轴套之间仅隔开很小的距离，可以防止支撑轴承的润滑油流失。
同样，对于右浮动活塞环922而言，其厚度D1小于滚动活塞轮的中筒部与主腔室内圆筒面右侧面的距离D，从而在右浮动活塞环922与滚动活塞轮的中筒部613b之间形成环状的右侧压力腔923，该右侧压力腔923通过开设于滚动活塞轮的外筒部的轴向右侧的通流孔613c″与月牙形密 封腔相连通。
本实施例转动装置在运转过程中，而月牙形密封腔内的少量高压流体通过通流孔613c″被导入右侧压力腔923，该少量分流使右浮动活塞环922紧贴与主腔室右侧的耐磨衬板531，从而实现了滚动活塞轮的右侧面密封。
左侧面定位环911和右侧面定位环921设置于在滚动活塞轮613的左右两侧，将滚动活塞轮613的两侧与主腔室的左/右侧面的耐磨衬板(521、531)隔开并定位，保障金属零件之间不接触。并且，侧面定位环(911，921)与相应侧的耐磨衬板(521、531)之间保持0.01mm以上间隙，防止磨擦损坏。
其中，侧面定位环(911，921)的材料为非铁，如铜或者工程塑料，优选为聚四氟乙烯，其硬度高、摩擦力小，可以灵活转动，同时不会划伤耐磨衬板。
同样，左浮动活塞环912和右浮动活塞环922的材料为非铁，如铜或者工程塑料，优选为聚四氟乙烯，其重量轻、强度高、摩擦力小，可以实现滚动活塞轮侧面的可靠密封。
本实施例转动装置在运转过程中，滚动活塞轮最外侧的外筒部与主腔室的相应侧面靠近但不直接接触，而月牙形密封腔内的少量高压流体通过通流孔被导入侧压力腔，该少量分流使浮动活塞环紧贴与主腔室的相应侧面，从而实现了滚动活塞轮的侧面密封，从而实现了滚动活塞轮在两侧的耐磨衬板之间浮起来，并沿缸体内圆筒面滚动，实现磨擦最小化的零间隙可靠密封运动。
需要说明的是，本实施例以主转动装置610为例进行说明，对于图1所示转动系统中的左转动装置620和由转动装置630，或者是仅包含一个腔室的转动装置，均可以应用本实施例的方案进行侧面密封。此外，虽然本实施例在偏心转子组件的左右两侧均设置了定位密封组件，但事实上，如果不考虑另一侧定位与密封的情况下，也可以仅在偏心转子组件的一侧设置定位密封组件，其同样能够实现本公开。
本实施例中，关于缸体内腔、主轴、偏心转子组件、隔离机构等，可以参照背景技术提到的专利申请(申请号：201510134609.2)中的相关说明。由于其同本公开的创新之处无关，此处不再赘述。
二、转动系统第一实施例
在本公开的第二个实施例中，还提供了一种应用第一实施例所述转动装置的转动系统。
本实施例转动系统与图1所示的转动系统类似，包括三个偏心转子结构的转动装置，即一主转动装置，一左转动装置和一右转动装置；该三个转动装置为转动装置第一实施例所述的转动装置。该三个转动装置共用同一根主轴、工作腔室彼此隔开且独立工作，其中，左转动装置和右转动装置的偏心转子结构对所述主转动装置的偏心转子结构进行平衡配重。
本领域技术人员应当清楚，虽然本实施例以3个腔室为例进行说明，但本公开并不以此为限。在本公开其他实施例转动系统中，可以将内腔分为2N+1个腔室，并与相应的偏心转子组件组成2N+1个转动装置，即在主转动装置的两侧，分别对称地设置N个副转动装置，同样可以实现本公开。但是，考虑到工艺复杂度等因素，该N为大于等于1的正整数，一般不超过三个。
本实施例中，关于侧面的定位密封组件，可以参照转动装置第一实施例的相关说明，此处不再重述。
三、转动装置第二实施例
对于转动装置第一实施例的转动装置，其关键在于将月牙形密封腔内的高压流体的少量分流通过通流孔被导入侧压力腔。然而，实现这样的密封是有条件的，即流体的流动性要好才行。
当流体的粘度比较大时，流体不容易通过较细的通流孔，因此侧压力腔容易失效。例如，在石油开采现场，由于石油的流体的粘度太大，流动性不好，造成管道输送的困难，这直接影响到石油输送的压力泵的构造，必须能够在所谓“稠油”的条件下运行。滚动活塞轮的侧面定位密封结构必须寻找更可靠的方法。此外，在转动装置刚刚启动的时刻，并没有高压流体注入侧压力腔，此时侧面密封同样是失效的。
在第一实施例转动装置的基础上，本实施例提供了一种改进后的转动装置。该转动装置与第一实施例转动装置的区别在于：将侧面定位环和浮动活塞环合为一体，形成一类似推力球轴承的定位密封组件，利用其实现偏心转子组件的侧面密封与定位，并且，通过在侧压力腔内增加弹性件来 解决“稠油”阻塞通流孔和刚启动时侧压力腔缺乏压力的问题。
同样，本实施例中，侧面定位密封结构900包括：左定位密封组件910和右定位密封组件920。其中，左定位密封组件910和右定位密封组件920左右对称，以下针对右定位密封组件920进行详细说明。
请参照图3、图4A和图4B，该右定位密封组件920包括：密封保持架926和若干个钢球927。其中，密封保持架926整体呈环状结构，其纵切面逆时针旋转90°的“凸”字型。
同样，密封保持架926在轴向由内向外的方向形成两层-内环部926a和外环部926b。其中，外环部926b朝向径向外侧延伸，形成外延伸部926b′；朝向内侧延伸，形成内延伸部926b″。其中，外延伸部926b′和内延伸部926b″均有相应功用，将在下文中进行详细说明。
其中，内环部923a和外环部的外延伸部之间形成第三台阶结构。如上所述，滚动活塞轮的内筒部613a与中筒部613b之间形成第一台阶结构。该第三台阶结构和该第一台阶结构相互卡合，实现了左侧面定位环对支撑轴承和滚动活塞轮的定位。
可以看出，密封保持架的外环部的外延伸部926b′相当于第一实施例中的浮动活塞环。请参照图3，外环部的外延伸部926b′延伸至靠近滚动活塞轮的外筒部的位置，并且，该外延伸部926b′的厚度D2小于滚动活塞轮的中筒部613b与主腔室内圆筒面右侧面的耐磨衬板的距离D，从而在外延伸部926b′与滚动活塞轮的中筒部613b之间形成环状的右侧压力腔923。右侧压力腔923通过开设于滚动活塞轮的外筒部的轴向右侧的通流孔613c″与月牙形密封腔相连通。
同样，转动装置在运转过程中，月牙形密封腔内的高压流体的少量分流通过通流孔被导入侧压力腔内，该少量分流使密封保持架紧贴与主腔室的相应侧面，从而实现了滚动活塞轮的侧面密封。同时，由于滚动活塞轮最外侧的外筒部与主腔室的相应侧面的耐磨衬板靠近但不直接接触，从而实现了滚动活塞轮在两侧的耐磨衬板之间浮起来，并沿缸体内圆筒面滚动，实现磨擦最小化的零间隙可靠密封运动。
如上所述，在应用至粘稠流体场景下时，通流孔经常被粘稠流体所阻塞，从而造成侧压力腔内缺乏压力，不能使密封保持架紧贴在主腔室的相 应侧面，造成侧面密封的失效。同时，在转动装置刚刚启动的时刻，并没有高压流体注入侧压力腔，此时侧面密封同样是失效的。
为了解决上述问题，该侧面密封件还包括：弹性件。该弹性件在侧压力腔内沿轴向设置，两侧分别抵压于密封保持架的内侧以及滚动活塞轮的中筒部的外侧，以提供密封保持架紧贴在主腔室的相应侧面所需要的压力。其中，该弹性件可以是弹簧、碟簧或者O型圈，其材料可以是橡胶、塑料、金属等。本实施例中采用的是氟橡胶材质的O型圈。
本领域技术人员可以理解，在侧压力腔内设置弹性件提供的侧向压力足够大情况下，滚动活塞轮的外筒部613c的通流孔也可以省略。
与第一实施例转动装置类似，本实施例中，密封保持架的外环部的内延伸部926b″延伸至靠近偏心轴套的位置，以防止由于润滑油泄露而导致的油润滑环境被破坏的隐患。其中，该内延伸部926b″与偏心轴套的距离介于20μm～100μm之间。此外，关于内延伸部926b″，其厚度可以与外延伸部926b′的厚度相同，也可以不同。
本领域技术人员应当清楚，在不考虑支撑轴承润滑泄露的情况下，该内延伸部926b″也可以省略。此时，密封保持架926的纵切面将呈顺时针旋转90°的“7”字型，而不再是逆时针旋转90°的“凸”字形。
请参照图3和图4，密封保持架的外环部的外延伸部926b′沿圆周方向均匀设置M个定位孔，M个与定位孔相匹配的钢球927分别被容置于相应的定位孔内，并由该定位孔定位。钢球927的轴向内侧抵压于滚动活塞轮的中筒部613b；其轴向外侧抵压于主腔室的右侧面的耐磨衬板上。其中，M≥3。
本实施例中，钢球对滚动活塞轮进行精密可靠的定位，能够进行高速高效率的旋转运动。联想到机械领域的推力球轴承，本实施例中，由滚动活塞轮、耐磨钢隔板、密封保持架和若干个钢球组成一个类似推力球轴承的结构，其中，滚动活塞轮可以看作推力球轴承的动圈、耐磨衬板可以看作推力球轴承的定圈、密封保持架相当于活塞环。在该结构中，由该若干个钢球实现滚动活塞轮的轴向定位。尤其需要注意的是，由于钢球的精度很高，因此，在钢球轴向定位的情况下，滚动活塞轮的侧面定位间隙可以做的很小。
图5为图3所示转动装置中右定位密封组件中钢球在主腔室右侧面的耐磨衬板上滚动轨迹的示意图。由图5可知，在偏心转子组件中偏心轴套的偏心量为e的情况下，钢球在耐磨衬板平面上的滚动轨迹宽度为2e。
请继续参照图5，滚动活塞轮侧面密封滚动轴承在耐磨衬板平面上的滚动轨迹说明，钢球的运动由于动圈(滚动活塞轮)的偏心运动而变得复杂化。钢球的运动由随动圈(滚动活塞轮)而动的密封保持架绕主轴的偏心运动而带动，钢球一方面绕主轴公转，一方面由于偏心运动而自转。
钢球绕主轴公转运动留在相当于滚动活塞轮侧面跑道上的滚压轨迹，为与滚动活塞轮转动中心同轴的正圆线形。滚动活塞轮侧面跑道上的滚压轨迹，如果做成和普通止推球轴承那样的圆弧状滚道，球面与滚道的接触面积可以增大，直接提高了承载能力和可靠寿命。侧面密封滚动轴承钢球在耐磨衬板平面上的滚动轨迹为宽度2e的环带，钢球与耐磨衬板平面的接触虽说是点接触，但是均匀地分布在环平面上。钢球在耐磨衬板平面上的滚动过程，实际上就是对轨迹宽度环带表面变质层的滚压超精加工，滚压后光洁度大大提高，达镜面光洁度。钢球对耐磨衬板的滚压超精加工，不仅滚压后光洁度大大提高，而且滚压后的表面加工硬化和晶粒细密化，都有助于提高接触强度和耐磨性。因此，耐磨衬板的材料可以不必像标准市售推力球轴承那样用轴承钢来做，而用成本较低的耐磨钢如NM400等制造即可。
本实施例中，钢球在滚动活塞轮侧面跑道上的滚压轨迹，只有与滚动活塞轮转动中心同轴的一个正圆线形，有时显得单薄了一些。如图6中(b)所示，定位孔和钢球分布在密封保持架的外延伸部的两个同心圆周上。在这种情况下，钢球在滚动活塞轮侧面跑道上的滚压轨迹，有与滚动活塞轮转动中心同轴的两个正圆线形，显然直接提高了承载能力和可靠寿命。此外，如图6中(c)所示，钢球分布在直长条孔中，钢球在滚动活塞轮侧面跑道上的滚压轨迹范围更大，可以形成环状接触面，承载能力和可靠寿命将进一步提高。
如图7所示，在本公开的另一个实施例中，定位孔为曲线形长条孔。该曲线形长条孔的首末端的连线在双层环状结构的径向上具有分量。每一圆弧状孔内设置3个钢球。
对于图7所示的定位密封结构，转动时由于钢球受到曲线形长条孔内侧面的凸轮般的导向力与滚球离心力的综合作用，活塞星轮侧面跑道上的滚压轨迹范围更大更均匀，承载能力和可靠寿命更大。
还需要注意的是，本实施例中，密封保持架的外环部的底面并非一平面，位于径向内侧部分的一段(远离定位孔的一段)朝向内环部926a凹入，以下称之为凹入段。该凹入段减小了密封保持架与耐磨衬板接触的面积，进而减小了两者之间的摩擦，可以进一步提高了运行效率，同时降低了了密封保持架加工精度的要求。
由于密封保持架不直接承受滚动活塞轮的载荷，故对刚度的要求并不太高，可以使用适合于密封的柔性材料如橡胶、塑料或者石墨等。其中，聚四氟乙烯的润滑性和密封性都较好，作为密封保持架非常合适。在高温条件下，密封保持架可使用耐腐蚀且润滑性均较好的石墨材料制备，如浸锑金属石墨等。
关于钢球，除了轴承钢之外，其可以采用由其他具有一定硬度的金属或非金属材料制作的滚球来代替，例如：硬质合金、碳化硅、氮化硅、二氧化锆陶瓷等。
此外，本实施例转动装置与第一实施例转动装置在支撑轴承612的定位方式上还略有不同。请参照图2，在第一实施例转动装置中，支撑轴承612被夹置定位于左定位部611a和右定位件611b之间。而在本实施例转动装置中，偏心轴套在支撑轴承的左右两侧分别固定左定位件611a′和右定位件611b。支撑轴承612的下部被夹置定位于左定位件611a′和右定位件611b之间。
本实施例转动装置的其他结构可参照第一实施例的说明，此处不再详细描述。
四、定位密封组件实施例
本实施例提供了一种如图4A和图4B所示的定位密封组件，其可以应用于例如第三实施例转动装置中。
请参照图4A、图4B，该定位密封组件包括：密封保持架926和若干个钢球927。其中，密封保持架926用于实现密封，其整体呈双层环状结构，纵切面呈逆时针旋转90°的“凸”字型。
密封保持架的外环部的外延伸部926b′沿圆周方向均匀设置M个定位孔，M个钢球927被容置于该定位孔内，并由该定位孔定位。关于密封保持架的内延伸部，其可以有，也可以省略。
本实施例中，M个定位孔分布于外延伸部的一个圆周上。而在本公开其他实施例中，M个定位孔还可以设置于所述密封保持架的外环部的外延伸部的不同半径的T个圆周上，同样可以实现本公开。一般情况下，2＜T≤4。在图6中(b)所示的实施例中，T＝2。
本实施例及图6中(b)所示的实施例中，定位孔为圆形，与钢球的形状相匹配，每一定位孔设置一个钢球。而在本公开其他实施例中，定位孔还可以是其他形状。典型地：
(1)如图6中(c)所示，定位孔还可以为直长条孔。该直长条孔的中心轴线沿双层环状结构的径向，并且该长条形的长度大于所述定位滚球的直径。需要说明的是，虽然图6中(c)所示的实施例中，每一直长条孔内设置一个钢球，但在本公开其他实施例中，每一直长条孔内也可以设置2个或3个的钢球，其效果较1个定位钢球效果更好；并且，基于平衡考虑，各个长条形孔内钢球的数目最好相等。
(2)如图7所示，定位孔还可以为曲线形长条孔。每一曲线形长条孔的首末端的连线在双层环状结构的径向上具有分量。在沿延伸部上的M个曲线形长条孔平行设置，每一圆弧状孔内设置3个钢球。在本公开其他实施例中，每一曲线形长条孔内也可以设置1个或2个的钢球，但其效果不如设置3个钢球好。
如上文所述，对于图7所示的定位密封结构，转动时由于钢球受到曲线形长条孔内侧面的凸轮般的导向力与滚球离心力的综合作用，活塞星轮侧面跑道上的滚压轨迹范围更大更均匀，承载能力和可靠寿命更大。其中，曲线形长条孔的曲线可以为圆弧、渐开线、摆线、对数曲线等曲线中的一种。此外，基于平衡考虑，各个曲线形长条形孔内钢球的数目最好相等。
需要说明的是，对于图6中(c)和图7所示的结构，在设置2个或3个滚球的情况下，需要合理设计钢球之间的间隙，其并非本公开的核心所在，此处不再展开。
由于密封保持架不直接承受滚动活塞轮的载荷，故刚度不大，可以使 用适合于密封的柔性材料如橡胶、塑料或者石墨等。其中，聚四氟乙烯的润滑性和密封性都较好，作为密封保持架非常合适。在高温条件下，密封保持架的材料可使用耐腐蚀和润滑性均较好的石墨材料，如浸锑金属石墨等。
关于钢球，除了轴承钢之外，其可以采用由其他具有一定硬度的金属或非金属材料制作的滚球来代替，例如：硬质合金、碳化硅、氮化硅、二氧化锆陶瓷等。尤其是在高温环境下，轴承钢材质的钢球硬度降低，容易变形，不再适用于耐高温，而硬质合金及二氧化锆(ZrO2)等陶瓷材料制作的滚动球体则非常适合在这种高温场合下应用。
五、转动系统第二实施例
本实施例与转动系统第一实施例类似，区别仅在于应用转动装置第二实施例中所给出的转动装置。关于本实施例转动系统中的转动装置，可参照转动装置第二实施例的相关说明，关于除转动装置之外的结构，可参照转动系统第一实施例的相关说明，此处均不再详细说明。
六、流体马达实施例
本公开还提供了一种流体马达。该流体马达应用第一、三实施例所述的转动装置或第二、五实施例中所述的转动系统。其中，
本实施例流体马达中，流体进口进入的高压流体进入转动装置，推动滚动活塞轮转动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压流体通过流体出口排出。其中，此处的高压流体可以为：液体、气体或蒸汽。
七、泵实施例
本公开还提供了一种泵。该泵应用第一、三实施例所述的转动装置或第二、五实施例中所述的转动系统。
本实施例泵中，主轴将扭矩传递至工作腔室内；在主轴的带动下，滚动活塞轮沿工作腔室向前滚动，将由流体进口进入的流体泵入工作腔室，并通过流体出口将流体排出。
八、压缩机实施例
本公开还提供了一种压缩机。该压缩机应用第一、三实施例所述的转动装置或第二、五实施例中所述的转动系统。
本实施例压缩机中，主轴将扭矩传递至工作腔室内，以偏心轴套为媒介，滚动活塞轮沿工作腔室向前滚动，对压缩介质进行压缩；压缩后的介质通过流体出口排出。
六、发动机
本公开还提供了一种发动机。该发动机应用第一、三实施例所述的转动装置或第二、五实施例中所述的转动系统。
本实施例发动机中，由燃烧室进入的高压气体推动滚动活塞轮沿工作腔室向前滚动，通过主轴将产生的扭矩传递至工作腔室外，做功之后的低压气体通过流体出口排出。
至此，已经结合附图对本公开五个实施例进行了详细描述。依据以上描述，本领域技术人员应当对本公开定位密封组件及应用其的转动装置、转动系统和流体机械有了清楚的认识。
需要说明的是，在附图或说明书正文中，未绘示或描述的实现方式，均为所属技术领域中普通技术人员所知的形式，并未进行详细说明。此外，上述对各元件和方法的定义并不仅限于实施例中提到的各种具体结构、形状或方式，本领域普通技术人员可对其进行简单地更改或替换，例如：
(1)该密封保持架的外环部的外延伸部的圆周上设置定位孔和钢球的层数或个数，可以根据需要进行调整，层数T一般为1层、2层或3层，个数一般情况下大于3个，并且沿圆周等距离分布；
(2)关于密封保持架的材料和尺寸，以及滚球本身的材料和尺寸，本领域技术人员可以根据需要合理选择，并不局限于上述实施例中提到的材料和尺寸；
(3)虽然上述实施例均以偏心转子形式的转动结构为例进行说明，但本领域技术人员应当清楚，其他类型的转动机构，例如：申请人在前期专利201110145313.2中所提到的太阳轮和行星活塞轮所组成的转动结构，同样适用于本公开。
还需要说明的是，本文可提供包含特定值的参数的示范，但这些参数无需确切等于相应的值，而是可在可接受的误差容限或设计约束内近似于相应值。一般情况下，其表达的含义是指包含由特定数量在一些实施例中±10％的变化、在一些实施例中±5％的变化。
实施例中提到的方向用语，例如“上”、“下”、“前”、“后”、“左”、“右”等，仅是参考附图的方向，并非用来限制本公开的保护范围。并且图中各部件的形状和尺寸不反映真实大小和比例，而仅示意本公开实施例的内容。另外，在权利要求中，不应将位于括号之间的任何参考符号构造成对权利要求的限制。
说明书与权利要求中所使用的序数例如“第一”、“第二”等的用词，以修饰相应的元件，其本身并不代表该元件有任何的序数，也不代表某一元件与另一元件的顺序，该些序数的使用仅用来使具有某命名的一元件得以和另一具有相同命名的元件能做出清楚区分。再者，单词“包含”不排除存在未列在权利要求中的元件。位于元件之前的单词“一”或“一个”不排除存在多个这样的元件。
综上所述，本公开将定位件和密封件有机结合在一起，提供了一种类似推力球轴承的定位密封组件，可以在定位的同时实现密封功能；在应用该定位密封组件的转动装置、转动系统中，在滚动活塞轮侧面与定位密封组件之间设置侧压力腔，利用侧压力腔内侧压力源产生的压力使定位密封部件压紧工作腔室侧面，实现滚动活塞轮的侧面密封，从而全方面地提高了密封效果和滚动活塞轮的定位精度，在发动机、流体马达、泵、压缩机等各个领域均有广阔的应用前景。
类似地，应当理解，为了精简本公开并帮助理解各个公开方面中的一个或多个，在上面对本公开的示例性实施例的描述中，本公开的各个特征有时被一起分组到单个实施例、图、或者对其的描述中。然而，并不应将该公开的方法解释成反映如下意图：即所要求保护的本公开要求比在每个权利要求中所明确记载的特征更多的特征。更确切地说，如下面的权利要求书所反映的那样，公开方面在于少于前面公开的单个实施例的所有特征。因此，遵循具体实施方式的权利要求书由此明确地并入该具体实施方式，其中每个权利要求本身都作为本公开的单独实施例。
以上所述的具体实施例，对本公开的目的、技术方案和有益效果进行了进一步详细说明，所应理解的是，以上所述仅为本公开的具体实施例而已，并不用于限制本公开，凡在本公开的精神和原则之内，所做的任何修改、等同替换、改进等，均应包含在本公开的保护范围之内。

Claims (18)

  1. 一种定位密封组件，其特征在于，包括：
    N个定位滚球(927)；以及
    密封保持架(926)，呈双层环状结构，包括：内环部(926a)和外环部(926b)；
    其中，所述外环部朝向径向外侧延伸，形成外延伸部(926b′)，该外延伸部(926b′)与内环部(926a)之间形成第三台阶结构；该外延伸部上沿圆周方向均匀设置M个定位孔，每一定位孔内配置一个或多个定位滚球，其中，M≥3。
  2. 根据权利要求1所述的定位密封组件，其特征在于，所述定位孔为：
    圆孔，每一定位孔内配置1个定位滚球；或者
    直长条孔，其中心轴线沿双层环状结构的径向，并且该直长条孔的长度大于所述定位滚球的直径，每一直长条孔内配置1个或多个定位滚球，且各个直长条孔内定位滚球的数目相同；或者
    曲线形长条孔，其首末端的连线在双层环状结构的径向上具有分量，并且该曲线形长条孔的长度大于所述定位滚球的直径，每一曲线形长条孔内配置1个或多个定位滚球，且各个曲线形长条孔内定位滚球的数目相同。
  3. 根据权利要求1所述的定位密封组件，其特征在于，所述M个定位孔设置于所述密封保持架的外环部的外延伸部的不同半径的T个圆周上，其中，T≥2，M≥6。
  4. 根据权利要求1所述的定位密封组件，其特征在于，所述外环部朝向径向内侧延伸，形成内延伸部(926b″)；所述密封保持架(926)的纵切面整体上呈顺时针或逆时针旋转90°的“凸”字形。
  5. 根据权利要求4所述的定位密封组件，其特征在于，所述密封保持架的外环部位于径向内侧的一段环朝向内环部凹入。
  6. 根据权利要求1至5中任一项所述的定位密封组件，其特征在于，所述密封保持架(926)的材料为橡胶、塑料或者石墨；和/或所述滚球的材料为硬质合金、碳化硅、氮化硅或二氧化锆陶瓷。
  7. 一种转动装置，其特征在于，包括：
    工作腔室；
    主轴(200)，其中心轴线与所述工作腔室的中心轴线重合；
    转动机构(610)，套设于所述主轴位于工作腔室的部分，通过在工作腔室中做旋转运动形成轴向延伸的密封工作空间；以及
    侧面定位密封机构(900)，包括：一个或两个如权利要求1至6中任一项所述的定位密封组件，安装于所述转动机构一侧与工作腔室相应侧面之间，用于实现所述转动机构相应侧面的密封。
  8. 根据权利要求7所述的转动装置，其特征在于：
    所述转动机构为偏心转子组件，包括：滚动活塞轮(613)，其在所述工作腔室的内圆筒面滚动而形成所述轴向延伸的月牙形密封腔；
    所述滚动活塞轮(613)整体呈筒状结构，其在径向由内而外分为宽度逐步增加的三部分：内筒部(613a)、中筒部(613b)和外筒部(613c)，所述内筒部(613a)与中筒部(613b)之间形成第一台阶结构；
    所述定位密封组件的密封保持架的第三台阶结构与所述滚动活塞轮的第一台阶结构相互卡合，所述定位密封组件中的N个定位滚球抵压于滚动活塞轮的中筒部(613b)与工作腔室相应侧面之间。
  9. 根据权利要求8所述的转动装置，其特征在于，所述滚动活塞轮的外筒部(613c)与工作腔室相应侧靠近但不接触，两者之间的距离Δ1满足：
    Δ1＜D2
    其中，D2为所述密封保持架的外环部的外延伸部(926b′)的厚度。
  10. 根据权利要求8所述的转动装置，其特征在于：
    所述密封保持架的外环部的外延伸部(926b′)延伸至滚动活塞轮的外筒部(613c)的位置，并且，该外延伸部的厚度D2小于中筒部(613b)与工作腔室相应侧面的距离D，从而在所述外延伸部(926b′)与中筒部(613b)之间形成环状的侧压力腔(923)；
    所述侧压力腔(923)内具有侧压力源，该侧压力源提供压力使所述密封保持架的外延伸部紧贴在工作腔室相应侧。
  11. 根据权利要求8所述的转动装置，其特征在于：
    所述偏心转子组件还包括：偏心轴套(611)，套设并固定于所述主轴 位于工作腔室的部分，其中心轴线与主轴的中心轴线相互平行且错开预设距离；以及支撑轴承(612)，对称地套设于所述偏心轴套和滚动活塞轮之间，其左右两侧与所述滚动活塞轮的内筒部的左右两侧相平齐；
    其中，所述密封保持架的外环部朝向径向内侧延伸，形成内延伸部(926b″)，该内延伸部(926b″)延伸至靠近偏心轴套(611)的位置，两者之间的距离介于20μm～100μm之间。
  12. 一种转动装置，其特征在于，包括：
    工作腔室；
    主轴(200)，其中心轴线与工作腔室的中心轴线重合；
    转动机构(610)，套设于所述主轴位于工作腔室的部分，通过在工作腔室中做旋转运动形成轴向延伸的密封工作空间；以及
    侧面定位密封机构(900)，包括：一个或两个定位密封组件，该定位密封组件安装于所述转动机构的一侧与工作腔室相应侧面之间，用于实现所述转动机构相应侧面的密封，所述定位密封组件包括：
    侧面定位环(911)，整体呈双层环状结构，包括：内环部(911a)和外环部(911b)，所述外环部(911b)朝向径向外侧延伸，形成外延伸部(911b′)，该外延伸部(911b′)与所述内环部(911a)之间形成第二台阶结构；以及
    浮动活塞环(912)，安装于所述转动机构(610)与所述侧面定位环的外延伸部(911b′)之间。
  13. 根据权利要求12所述的转动装置，其特征在于：
    所述转动机构为偏心转子组件，包括：滚动活塞轮(613)，其在所述工作腔室的内圆筒面滚动而形成所述轴向延伸的月牙形密封腔；
    所述滚动活塞轮(613)整体呈筒状结构，其在径向由内而外分为宽度逐步增加的三部分：内筒部(613a)、中筒部(613b)和外筒部(613c)，所述内筒部(613a)与中筒部(613b)之间形成第一台阶结构；
    所述侧面定位环的第二台阶结构与所述滚动活塞轮的第一台阶结构相互卡合。
  14. 根据权利要求13所述的转动装置，其特征在于：
    对于所述浮动活塞环(912)，其在径向上分别与滚动活塞轮的外筒部 (613c)和侧面定位环的外环部的外延伸部(911b′)密封；而在轴向上，其厚度D1小于滚动活塞轮的中筒部(613b)与工作腔室相应侧面的距离D，从而在浮动活塞环(912)与滚动活塞轮的中筒部(613b)之间形成环状的侧压力腔(913)；
    所述侧压力腔(913)内具有侧压力源，该侧压力源提供压力使所述浮动活塞环(912)紧贴在工作腔室相应侧。
  15. 根据权利要求10或14所述的转动装置，其特征在于：
    由弹簧、碟簧或者O型圈作为侧压力源或侧压力源的一部分；和/或
    所述外筒部(613c)相应侧开设有至少一个流通孔(613c″)，由所述月牙形密封腔通过该流通孔导入所述侧压力腔的压力流体作为所述侧压力源或侧压力源的一部分；和/或
    所述外筒部(613c)相应侧沿圆周方向均匀开设有2～10个通流孔；；和/或
    所述侧压力腔的轴向尺寸介于0.2mm～1.0mm之间。
  16. 根据权利要求7至14中任一项所述的转动装置，其特征在于，所述侧面定位密封机构包括：两个定位密封组件，分别安装于所述转动机构的一侧与工作腔室相应侧面之间，用于实现所述转动机构两侧的密封；
    其中，所述工作腔室的两侧设置衬板，所述两个定位密封组件分别安装于所述转动机构的一侧与工作腔室相应侧的衬板之间。
  17. 一种转动系统，其特征在于，包括：至少三个偏心转子结构的转动装置，即一主转动装置，至少一左转动装置和至少一右转动装置；
    其中，该至少三个转动装置中至少其中之一为权利要求8-11、13-16中任一项所述的转动装置。
  18. 一种流体机械，其特征在于，包括：权利要求8-11、13-16中任一项所述的转动装置或权利要求17所述的转动系统，其中：
    所述流体机械为流体马达，该流体马达中，由流体进口进入的高压流体推动滚动活塞轮转动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压流体通过流体出口排出；或者
    所述流体机械为泵，该泵中，主轴将扭矩传递至工作腔室内；在主轴的带动下，滚动活塞轮沿工作腔室向前滚动，将由流体进口进入的流体泵 入工作腔室内，并通过流体出口将流体排出；或者
    所述流体机械为压缩机，该压缩机中，主轴将扭矩传递至工作腔室内，滚动活塞轮沿工作腔室向前滚动，对压缩介质进行压缩，压缩后的介质通过流体出口排出；或者
    所述流体机械为发动机，该发动机中，由燃烧室进入的高压气体推动滚动活塞轮沿工作腔室向前滚动，通过主轴将产生的扭矩传递到工作腔室的外部，做功之后的低压气体通过流体出口排出。
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