WO2014114222A1 - 转动装置及应用其的转子式压缩机和流体马达 - Google Patents

转动装置及应用其的转子式压缩机和流体马达 Download PDF

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Publication number
WO2014114222A1
WO2014114222A1 PCT/CN2014/070972 CN2014070972W WO2014114222A1 WO 2014114222 A1 WO2014114222 A1 WO 2014114222A1 CN 2014070972 W CN2014070972 W CN 2014070972W WO 2014114222 A1 WO2014114222 A1 WO 2014114222A1
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WIPO (PCT)
Prior art keywords
rolling
valve body
rotating device
rotary valve
chamber
Prior art date
Application number
PCT/CN2014/070972
Other languages
English (en)
French (fr)
Inventor
姚镇
姚其槐
Original Assignee
Yao Frank
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
Application filed by Yao Frank filed Critical Yao Frank
Priority to US14/762,609 priority Critical patent/US10215025B2/en
Priority to JP2015554035A priority patent/JP2016505769A/ja
Priority to EP14743623.2A priority patent/EP2942524B1/en
Publication of WO2014114222A1 publication Critical patent/WO2014114222A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/38—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/40—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member
    • F01C1/46—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member with vanes hinged to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/38—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/02 and having a hinged member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
    • F04C18/46—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/38—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/02 and having a hinged member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/46—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function

Definitions

  • the present invention relates to the field of fluid machinery technology, and more particularly to a rotating device and a rotor compressor and a fluid motor using the same. Background technique
  • the most commonly used positive displacement compressors on the market are mainly divided into four types: reciprocating piston type, screw type, scroll type and rotor type.
  • reciprocating piston type screw type
  • scroll type rotor type
  • rotor compressor when the main shaft rotates, the eccentric rotor rotates close to the inner wall of the cylinder, causing the crescent-shaped volume to periodically change, thereby completing the process of suction, compression and exhaust. Due to the smooth and balanced compression process of the rotor compressor, it has been widely used in household refrigeration equipment such as air conditioners and refrigerators.
  • the rotor compressor includes a cylinder 1, a rolling rotor 2, an eccentric sleeve 3, a drive shaft 4 having an eccentric shaft portion, a swinging stopper, and a coil spring.
  • An eccentric sleeve 3 is provided between the eccentric shaft portion of the drive shaft 4 and the rolling rotor 2 so as to be flexibly rotatable therebetween, so that the eccentricity of the rolling rotor 2 is adjusted and a flexible rolling contact seal is realized in operation.
  • the eccentric sleeve 3 rotates around the center of the eccentricity while revolving around the drive shaft.
  • the rotating portion of the swinging block is pressed against the outer circumferential surface of the rolling rotor 2 by the spring force of the coil spring to realize the swinging isolation.
  • the rotor type compressor shown in Fig. 1 is slidably rubbed under the high-intensity working conditions, especially when the rotational frequency is very high, the sliding shafts of the drive shaft 4 with the eccentric shaft portion and the rolling rotor 2 and the eccentric sleeve 3
  • the energy loss is large and must be lubricated with oil.
  • the lubricating oil entering the cylinder must be separated from the compressed medium and discharged.
  • the lubricating oil in the moving gap is to be sealed, in order to separate the lubricating oil from the exhaust gas, a high pressure is required in the casing of the system.
  • the coil spring drives one end of the swinging block to make the pendulum
  • the other end of the movable block is pressed against the rolling rotor 2. Since the coil spring works under high-strength conditions for a long time, it is very easy to cause failure and damage, which affects the service life of the entire rotor compressor. It is necessary to find a more sophisticated and reliable swing stopper resetting and pressing mechanism.
  • the force between the swinging block and the rolling rotor 2 is not easy to control, and the force is too large, which not only increases the wear of the swinging block, but also consumes the power of the compressor; if the force is too small, it cannot be guaranteed.
  • the seal of the cylinder is not only increases the wear of the swinging block, but also consumes the power of the compressor; if the force is too small, it cannot be guaranteed.
  • the head of the swinging block is connected with the outer cylindrical surface of the rolling sealing ring 2, and the head of the swinging block is fixed with the position of the outer cylindrical surface of the rolling sealing ring.
  • the present invention provides a rotating device and a rotor type compressor and a fluid motor using the same.
  • a turning device comprises: a cylinder body; a front end cover and a rear end cover, sealingly connected to the front end and the rear end of the cylinder body, which together with the cylinder body define a cylindrical inner cavity; the main shaft, the cylinder body and/or the front and the rear
  • the end cap is rotatably supported, partially located in the cylindrical inner cavity, the central axis of which coincides with the central axis of the cylinder;
  • the eccentric rotor assembly is sleeved on the portion of the main shaft located in the cylindrical inner cavity, comprising: an eccentric shaft,
  • the central axis of the main shaft is offset from the central axis of the main shaft by a predetermined position;
  • the rolling piston wheel is sleeved on the eccentric shaft, and the central axis thereof coincides with the central axis of the eccentric shaft; at least one
  • the rolling bearing is symmetrically sleeved on the eccentric shaft, the inner ferrule is fixed to the eccentric shaft, and
  • a rotor compressor is also provided.
  • the rotor type compressor includes the above rotating device, wherein: the first chamber communicates with the low pressure compressed medium input port through the first group of through holes; the second chamber passes through the second group of through holes and the compressed high pressure compressed medium discharge port
  • the main shaft communicates the torque outside the cylindrical inner cavity into the cylindrical inner cavity, and compresses the compressed medium through the eccentric rotor assembly.
  • a fluid motor is also provided.
  • the fluid motor includes the above rotating device, wherein: the second chamber communicates with the high pressure fluid inlet through the second set of through holes; the first chamber communicates with the low pressure fluid outlet through the first set of through holes; the high pressure fluid pushes the eccentric rotor to rotate The torque generated by the main shaft is transmitted to the outside of the cylindrical cavity.
  • the rotating device of the present invention and the rotor compressor and the fluid motor using the same have the following beneficial effects:
  • Rolling bearings are used between the eccentric shaft and the rolling piston wheel. After the rolling bearing is used, the rotor compressor achieves no oil or less oil (ie oil lubrication in a small area), thus overcoming the lubrication due to heavy use. Many shortcomings caused by oil, the rotating device can be applied in the field of large compressors and air compressors;
  • the balance weight scheme is adopted to reduce the momentum imbalance caused by the eccentric rotation of the rotating device.
  • the rotor compressor designed by the rotor momentum balance is more in line with the precision engineering principle, and the vibration is small and the noise is low;
  • the rotary valve body reset pin is constructed as a conventional pressure cylinder, or a more powerful, more stable, more precise and longer-life pneumatic component is used to control the swing of the rotary valve body, ensuring reliable operation of the entire rotating device. Sex and maintenance convenience;
  • FIG. 1 is a schematic structural view of a prior art rotor compressor
  • FIG. 2A is a schematic longitudinal sectional view of a rotor type compressor according to an embodiment of the present invention
  • Figure 2B is a cross-sectional view of the rotor compressor of Figure 2A taken along line A-A;
  • Figure 3 is a partial right side elevational view of the eccentric rotor assembly of the rotor compressor of Figure 2A;
  • Figure 4 is a perspective view of a portion of the eccentric rotor assembly of the rotor compressor of Figure 2A;
  • Figure 5A is a rotor compression in accordance with an embodiment of the present invention.
  • 5B is a schematic view showing a second assembly manner of a 0-type elastic rubber ring in a rotor type compressor according to an embodiment of the present invention
  • Figure 5C is a schematic view showing the assembly of a rectangular elastic rubber ring in a rotor type compressor according to an embodiment of the present invention
  • 6A is a schematic view of a spring piece ferrule in an eccentric rotor assembly of a rotor compressor according to an embodiment of the present invention
  • Figure 6B is a schematic view showing the assembly of the spring piece ferrule shown in Figure 6A;
  • FIG. 7A is a left side view of an eccentric rotor assembly in a rotor type compressor according to an embodiment of the present invention
  • FIG. 7B is a schematic view of an eccentric rotor assembly in a rotor type compressor according to an embodiment of the present invention
  • FIGS. 8A and 8B are views of an embodiment of the present invention The schematic diagram of the second rotary valve body in the rotor type compressor isolation mechanism in the pressed state and the extended state respectively;
  • Figure 9 is a perspective view of a third type of rotary valve body in the rotor type compressor isolation mechanism according to the present invention
  • Figures 10A and 10B are schematic views of the rotary valve body shown in Figure 9 in a pressed state and an extended state, respectively;
  • 11A is a schematic structural view of a second type of rotary valve body reset mechanism in a rotor type compressor isolation mechanism according to an embodiment of the present invention
  • 11B is a schematic structural view of a third rotary valve body reset mechanism in a rotor type compressor isolation mechanism according to an embodiment of the present invention
  • FIGS. 12A-12E are schematic views showing the operation of a rotor type compressor according to an embodiment of the present invention.
  • Fig. 13 is a cross-sectional view showing a fluid motor according to an embodiment of the present invention.
  • 351-0 type elastic rubber ring 352-ratio elastic rubber ring;
  • the present invention provides a rotating device and a rotor compressor and a fluid motor using the same.
  • a rolling bearing is adopted between the eccentric shaft and the rolling piston wheel, and the cylinder is reliably sealed by the elastic pre-tightening element, and the vibration and noise problems of the rotor compressor are overcome by the balance weight, thereby avoiding
  • the use of lubricating oil has increased the size of the compressor.
  • a new rotary valve body reset mode is provided, and the rotary valve body is improved to ensure the overall operational reliability of the rotary device and the rotor compressor and fluid motor to which it is applied.
  • the present invention provides a turning device comprising: a cylinder block, a front/rear cover, a main shaft, an eccentric rotor assembly, and an isolating mechanism.
  • a turning device comprising: a cylinder block, a front/rear cover, a main shaft, an eccentric rotor assembly, and an isolating mechanism.
  • the cylinder body and the front/rear cover on the front/rear sides thereof define a cylindrical inner cavity.
  • the main shaft is supported by the cylinder or its front/rear cover, partially within the cylindrical inner chamber, the central axis of which coincides with the central axis of the cylinder.
  • the eccentric rotor assembly is disposed on the portion of the main shaft located in the cylindrical inner cavity, and comprises: an eccentric shaft disposed on a portion of the main shaft located in the cylindrical inner cavity, wherein a central axis thereof is parallel to the central axis of the main shaft and is offset by a preset distance; a rolling piston wheel is sleeved on the eccentric shaft, the central axis of which coincides with the central axis of the eccentric shaft; at least one rolling bearing is symmetrically sleeved on the eccentric shaft, the inner ferrule is fixed to the eccentric shaft, and the outer ring is fixed to the rolling a piston wheel to isolate the rotation of the two, the pre-tightening elastic force between the at least one rolling bearing and the rolling piston wheel presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity, so that the cylindrical inner cavity
  • the inner cylindrical surface and the outer cylindrical surface of the rolling piston wheel form an axially extending sealed chamber.
  • the isolation mechanism divides the sealed chamber into mutually independent first chamber
  • the rotating device can be applied to a fluid machine such as a compressor or a fluid motor.
  • a fluid machine such as a compressor or a fluid motor.
  • the settings of the suction through hole and the discharge port are as follows:
  • the first chamber communicates with the low-pressure compressed medium input port through the first group of through holes;
  • the second chamber passes through the second group of through holes and the compressed high-pressure compressed medium
  • the mass discharge port is connected;
  • the main shaft transmits the torque outside the cylindrical inner cavity into the cylindrical inner cavity, and compresses the compressed medium through the eccentric rotor assembly;
  • the second chamber communicates with the high pressure fluid inlet through the second set of through holes;
  • the first chamber communicates with the low pressure fluid outlet through the first set of through holes;
  • the eccentric rotor rotates, and the torque generated by the main shaft is transmitted to the outside of the cylindrical inner cavity.
  • the number of the through holes in each set of through holes may be one or plural.
  • the rolling bearing may be a roller bearing, a ball bearing, a needle bearing, an aerodynamic rolling bearing or a composite bearing.
  • the number of rolling bearings is one, but is preferably one set, two sets, three sets, and four sets, and each set includes two rolling bearings symmetrically disposed left and right along the cylindrical inner cavity. Symmetry herein refers to symmetry with respect to a plane that is at the center of the cylindrical inner cavity portion and perpendicular to the central axis of the main shaft.
  • Fig. 2A is a schematic longitudinal sectional view of a rotary compressor in accordance with an embodiment of the present invention.
  • Figure 2B is a cross-sectional view of the rotor compressor of Figure 2A taken along line A-A.
  • the rotor compressor of the present embodiment includes: a cylinder block 110, a front end cover 120/rear end cover 130, a main shaft 200, an eccentric rotor assembly 300, and an isolation mechanism 400. The individual components are described in detail below.
  • the cylinder block 110 and the front end cover 120/rear end cover 130 on the front and rear sides thereof define a cylindrical inner cavity.
  • the cylindrical inner chamber is the cylinder of the compressor, and the cylinder has a radius of R2 and a height of H.
  • the cylinder block 110 includes a cylinder main body 111, and a front cylinder head 112 and a rear cylinder head 113 which are respectively disposed at front/rear end faces of the cylinder main body 111.
  • a cylinder head 140 is provided at a predetermined position outside the cylinder main body 111, generally upward.
  • the rotary valve body of the subsequent isolation mechanism and its reset mechanism are all set to the position of the cylinder head 140, which will be described in detail below.
  • the main shaft 200 is supported by the front and rear cylinder heads (112 and 113) of the cylinder, and its central axis coincides with the central axis of the cylindrical inner chamber, and has a diameter of zero.
  • the first portion of the main shaft 200 is located outside the cylindrical inner cavity, is connected to the external power source, and transmits the torque input from the external power source to the cylindrical inner cavity; the second portion is located in the cylindrical inner cavity, using external power Source input torque drives eccentric rotor set
  • the piece 300 rotates.
  • a spindle bearing 210 is disposed between the spindle 200 and the front and rear cylinder heads (112 and 113), respectively.
  • the spindle bearing 210 is preferably a high-capacity, long-life, high-precision tapered roller bearing to ensure that the gap between the rotor side and the cylinder head surface is precisely controlled.
  • the position of the spindle bearing 210 is locked by the bearing lock nut 211.
  • a main shaft seal ring 212 is provided therebetween.
  • a front end cap sealing rubber ring 121 is disposed between the two; in order to achieve a seal between the rear end cover and the rear cylinder head, a rear end cap seal is provided between the two Apron 131.
  • main shaft 200 is rotatably supported by the front cylinder head 112 and the rear cylinder head 113 in this embodiment, it may be rotatably supported by the front/rear end cover. Further, although in the present embodiment, only one end of the main shaft extends beyond the cylindrical inner cavity, the present invention also includes the case where both ends of the main shaft extend out of the cylindrical inner cavity, and torque is simultaneously input from the left and right sides. It should be clear to those skilled in the art how to implement the above technical solutions, and details are not described herein again.
  • the eccentric rotor assembly 300 is located within the cylindrical inner chamber described above.
  • Figure 3 is a partial right side elevational view of the eccentric rotor assembly 300 of the rotor compressor of Figure 2A.
  • Figure 4 is a perspective view showing a portion of the eccentric rotor assembly of the rotor type compressor shown in Figure 2A.
  • the eccentric rotor assembly includes: an eccentric shaft 310 disposed on the second portion of the main shaft 200 in the cylindrical inner cavity, the central axis of which is parallel to the central axis of the main shaft 200 and is staggered.
  • the rolling piston wheel 330 is sleeved on the eccentric shaft 310, and its central axis coincides with the central axis of the eccentric shaft 310, and has a radius R1; at least one rolling bearing 320 is symmetrically sleeved on the eccentric shaft 310.
  • the ferrule is fixed to the eccentric shaft 310, and the outer ring is fixed to the rolling piston wheel 330 to isolate the rotation of the two.
  • the pre-tightening elastic force between the rolling bearing and the rolling piston wheel presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity, and the inner cylindrical surface of the cylindrical inner cavity and the outer cylinder of the rolling piston wheel
  • the face forms an axially extending sealed chamber.
  • the magnitude of the eccentricity e of the eccentric shaft 310 depends on factors such as the displacement of the compressor and the fluid pressure. For example, when the displacement is 53 cc and the pressure is IMPa, 4.5 mm can be taken. The larger the displacement, the more the eccentricity e is. Big.
  • the spindle 200 drives the eccentric shaft 310 to rotate. Then, under the driving of the eccentric shaft 310, the rolling piston wheel 330 revolves in a manner of rolling along the inner cylindrical surface of the cylinder while revolving along the central axis of the main shaft, the rotation of the rolling piston wheel 330 and the eccentric shaft 310 Rotating by rolling bearing
  • the rolling bearing 320 as described above may be a roller bearing, a ball bearing, a needle bearing, an aerodynamic rolling bearing or a composite bearing, preferably a ball bearing.
  • two symmetrical (ie, one set) rolling bearings 320 are disposed between the eccentric shaft 310 and the rolling piston wheel 330.
  • the rolling bearings can be designed as needed. If the axial distance of the cylindrical inner cavity, that is, the height H of the cylinder, is large, the rolling bearing can be two sets of symmetrical, 3 groups or 4 groups, two in each group. Of course, the rolling bearing may also be one having a larger cross-sectional area, but it should also be symmetrically disposed left and right along the cylindrical inner cavity.
  • the rotor compressor By using the contemporary rolling technology of the rotor compressor which is mass-produced by mature industrial technology and is still in the process of rolling forward, it is possible to reduce the friction energy consumption and improve the energy efficiency by rolling friction instead of sliding friction; and after using the rolling bearing, the rotor compressor is It is expected to achieve no oil or less oil (ie, oil lubrication in a small area), and it is expected to overcome many shortcomings caused by the large use of lubricating oil, and it is applied in large compressors and air compressors.
  • oil or less oil ie, oil lubrication in a small area
  • the experience of mechanical design tells us that the adjacent moving surface can have good air tightness under the gap of 0.01 ⁇ 0.03mm.
  • the most ideal low-cost, high-quality basic sealing condition is: no sliding between the moving surfaces, so there is no gap, and even Micro interference fit to achieve zero leakage.
  • the rolling piston wheel and the inner wall of the cylinder body The pre-tightening design is used to achieve the best seal.
  • the control target of the rolling piston wheel and the cylinder sealing gap in the rotor compressor is that the rolling piston wheel must have zero sealing gap ⁇ at the contact point when rolling along the inner wall of the cylinder.
  • the sealing gap is ⁇ ;
  • the cylinder inner cylinder radius is R;
  • the outer cylinder radius of the rolling piston wheel is r;
  • the eccentric amount of the rolling piston wheel and the center of the cylinder is e;
  • the radial clearance of the rolling piston wheel support bearing is ⁇ .
  • the above parameters should be measured in advance and matched. Due to the cylinder radius R of the cylinder wall, the eccentricity of the rolling piston wheel and the center of the cylinder (ie the eccentric radius of the crankshaft) e, the radial clearance of the rolling bearing, once the machining is not well corrected, the rolling is usually adopted.
  • the outer cylinder radius r of the piston wheel is modified and adjusted.
  • control target of the rolling piston wheel and the cylinder seal gap of the rotor type compressor may be an interference fit, that is, the seal gap ⁇ is less than zero. This means that the pre-tightening is applied at the contact point of the rolling piston wheel and the cylinder to produce a microscopic elastic deformation, and the resulting air gap seal can be extended from the line to the surface.
  • the pre-tightening pressure can not be too large (about 1 ⁇ ⁇ ), can not exceed the allowable elastic range of the assembly size chain system, and can not cause the permanent deformation of the assembly size chain system;
  • the micro-elastic deformation caused by the pre-tightening pressure can automatically compensate the friction loss deformation, and ensure that the sealing gap between the rolling piston wheel and the cylinder of the rotor compressor is not greater than zero. Control target.
  • the manufacturing site often imposes too severe precision requirements on the radial assembly dimensions of the various components that make up the eccentric rotor.
  • the pre-tightening elastic force between the rolling bearing 320 and the rolling piston wheel 330 presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity to achieve sealing of both.
  • the pre-tensioning force can result from an interference fit between the rolling bearing 320 and the rolling piston wheel 330.
  • the interference fit is too large, there is a possibility that the rotor compressor may not operate smoothly.
  • One or more inlaid grooves are symmetrically distributed in the radial center line of the groove, and an elastic pretensioning element is disposed in the setting groove, and the height of the elastic pretensioning element in a normal state is greater than the depth of the inlay groove to realize the rolling piston wheel Pre-tightening pressure between the inner cylindrical surface of the 330 and the outer cylindrical surface of the rolling bearing 330.
  • the elastic pretensioning element is also capable of absorbing and compensating for errors on its own.
  • the elastic pretensioning element can adopt a wide-type 0-type elastic rubber ring 351 with a sealing pressure of 1.33 X 10 - 5 Pa to 400 MPa (movable seal up to 35 MPa).
  • the material of the 0-type elastic rubber ring is preferably fluororubber.
  • the fluororubber has good elastic force, wear resistance and pressure resistance, and its continuous use temperature can reach 210 °C.
  • Fig. 5A is a schematic view showing the first assembling manner of the 0-type elastic rubber ring in the rotor type compressor according to the embodiment of the present invention.
  • a plurality of inlaid grooves are formed in the inner cylindrical surface of the rolling piston wheel, and the axial positions of the plurality of inlaid grooves are symmetric and evenly distributed with respect to the radial center line of the rolling bearing (steel ball) groove of the rolling bearing.
  • a plurality of 0-type elastic rubber rings 351 can be embedded in the mounting groove.
  • the outer cylindrical surface of the rolling bearing compresses the 0-type elastic rubber ring 351 to generate an elastic deformation, and the outer cylindrical surface of the rolling piston wheel 330 is tightly pressed against the inner cylindrical surface of the cylinder body, thereby realizing Zero clearance seal for preload.
  • the rolling bearing outer ring is pre-tensioned by the 0-type elastic rubber ring 351 to the inner cylindrical surface of the rolling bearing installation positioning, which is floating relative to the center position of the piston wheel bearing mounting positioning inner cylindrical surface, so it is required to be disposed between them There is enough clearance ⁇ to compress the 0-type elastic rubber ring.
  • the inner diameter ⁇ of the piston roller installed and positioned by the rolling bearing must be larger than the outer diameter of the rolling bearing ring.
  • the size of the clearance ⁇ depends on the bearing size, and its value ranges from 0.1 to 1 mm. .
  • the correction of the outer cylinder radius r of the rolling piston wheel is usually carried out to ensure that the sealing gap ⁇ at the contact point of the rotor is zero when the rotor rolls along the inner wall of the cylinder.
  • the 0-type elastic rubber ring is used to pre-tighten the rolling piston wheel, there is a gap ⁇ between the outer cylindrical surface of the rolling bearing outer ring and the cylindrical surface of the rolling bearing installation positioning. At this time, the radial clearance of the rolling piston wheel supporting the rolling bearing is zero.
  • the sealing gap is ⁇ ;
  • the cylinder inner cylinder radius is R;
  • the outer cylinder radius of the rolling piston wheel is r;
  • the amount of eccentricity of the rolling piston wheel and the center of the cylinder is e;
  • the outer cylinder radius r of the rolling piston wheel is pre-incremented to ⁇ .
  • the reaction force of the compression deformation of the 0-type elastic rubber ring is proportional to the variation of the gap ⁇ ⁇ , and has the following mathematical expression:
  • the ⁇ value must be correctly selected through practical experience. While ensuring that the sealing gap ⁇ is zero, it is necessary to make the outer cylinder of the rolling piston wheel face the cylindrical surface of the cylinder inner wall at a moderate contact point. Elastic preloading pressure can be used to avoid excessive preloading.
  • Figure 5 is a schematic view showing a second assembly mode of a 0-type elastic rubber ring in a rotor type compressor according to an embodiment of the present invention.
  • the assembly method of the 0-type elastic rubber ring in Fig. 5 ⁇ is similar to that of Fig. 5 ⁇ , except that the inlaid groove is opened on the outer cylindrical surface of the rolling bearing outer ring, and the working principle is the same as that of the elastic rubber ring shown in Fig. 5 ⁇ . It will not be repeated here.
  • the sectional size is the key to the design.
  • three key conditions are met:
  • the rotor system is transmitted through a 0-type elastic rubber ring to a suitable elastic preloading pressure at the contact of the outer cylindrical surface of the rolling piston wheel with the cylindrical surface of the cylinder inner wall;
  • the cross-sectional diameter of the 0-type elastic rubber ring should be large enough.
  • the contact area between the 0-type elastic rubber ring and the rolling bearing of the rolling piston wheel should be large enough to satisfy the system's soft elasticity. Absorb vibration and noise.
  • the cross-sectional area of the 0-type elastic rubber ring is large enough to have sufficient fatigue strength and no permanent Deformation.
  • expansion-compensated deep groove ball bearing anti-slip bearing
  • AC bearing anti-slip bearing
  • the cross-sectional shape of the elastic rubber ring can also be designed as a rectangle or other shape that is advantageous for satisfying the appropriate elastic preload pressure, absorbing vibration and noise, and having sufficient fatigue strength and prolonged service life, one of which is A rectangular elastic toothed rubber ring 352 as shown in Fig. 5C.
  • the above-mentioned 0-type or rectangular elastic rubber ring may be softened or destroyed by heat after long-term operation under repeated high-frequency impact pressure, so it is considered to be more heat-resistant.
  • High-strength elastic materials such as: elastic rings made of multi-strand fine wire mesh, or metal spring rings, etc., the metal is preferably alloy steel or other elastic metal material.
  • the metal spring ferrule includes: a spring piece with a continuous U-shaped smooth arc curved surface, and a rigid base edge supporting the spring piece.
  • the rigid base edge As shown in FIG. 6B, a groove is formed in the inner cylindrical surface of the rolling piston wheel, and the center line of the groove coincides with the center line of the rolling bearing.
  • the metal spring ring 353 with a U-shaped smooth arc curved surface is assembled in the above-mentioned mosaic. Inside the slot.
  • the diameter of the rigid base rim of the metal spring ferrule 353 can be elastically reduced, it can be pre-inlaid into a rectangular groove in which the rolling bearing is mounted and positioned on the inner cylindrical surface to complete the positioning, and after the lubricant is applied, it can be easily Press the rolling bearing outer ring into the assembly. Due to the stamping process, metal spring ferrules are easy to mass-produce, ensuring quality and reducing costs.
  • the outer cylindrical surface of the rolling bearing compresses the elastic pretensioning element to generate an elastic deformation force
  • the rolling piston is The outer cylindrical surface of the wheel is pressed tightly against the inner cylindrical surface of the cylinder, regardless of the accuracy of the radial assembly dimensions of the various parts constituting the eccentric rotor assembly, and regardless of the radial rotation of the eccentric rotor assembly Any deviations can be randomly absorbed by the elastic deformation of the elastic pretensioning element to ensure a zero gap seal with elastic preload. Therefore, not only can the goal of good and reliable sealing quality of the compressor eccentric rotor assembly be achieved, but also the excessively demanding precision requirements for the radial assembly dimensions of the various components constituting the eccentric rotor assembly can be avoided, and the cost can be reduced.
  • an eccentric shoulder 311 is provided at the position where the eccentric shaft is sleeved with the rolling bearing, as shown in FIG.
  • the portion of the eccentric shaft other than the eccentric shoulder 311 can be saved to balance the weight, and the specific balance weight method is as follows.
  • the balance block 340 is symmetrically disposed along the eccentric axis between the two eccentric shoulders.
  • the size and weight of the weight 340 depends on the volume and eccentricity of the cylindrical cavity.
  • the present invention provides an additional plurality of balancing weights.
  • the weight 341 in the eccentric rotor assembly is no longer a separate piece, but is a curved balance weight region that is connected to the lighter side of the eccentric shaft, as shown in Fig. 7A. .
  • This type of counterweight is easy to manufacture and has a good balance.
  • the eccentric rotor assembly adopts a weight notch 342 on the heavier side of the eccentric shaft to reduce the weight here, thereby achieving balance during the rotation of the eccentric shaft, as shown in Fig. 7B. Show.
  • the invention utilizes the use of a rolling bearing to design a weight structure that is possible to balance the rotor momentum between two symmetrically arranged rolling bearing span spaces.
  • the use of a balanced weighting scheme alleviates the problem of momentum imbalance caused by the eccentric rotation of the rotor compressor, and is more in line with the principles of precision engineering.
  • the rotor type compressor designed by the rotor momentum balance is of course small in vibration and low in noise.
  • the position of the rolling bearing wheel is prevented from shifting during the rotation of the rolling piston wheel.
  • the positioning of the inner and outer ring axial positions of the two rolling bearings fixed on the eccentric rotor assembly of the compressor belongs to the pre-tightening position, and the rolling piston wheel is adopted.
  • the inner cylindrical surface and the positioning shoulder on the eccentric spindle journal eliminate the axial clearance of the rolling bearing, so that the rolling bearing reduces the axial sway during the rotation.
  • the positioning of the rolling piston wheel can be either of the following two:
  • the axial position of the inner ring of the two rolling bearings fixed on the inner cylindrical surface of the rolling piston wheel is set by the shoulder provided on the eccentric spindle journal and the spindle journal.
  • the bearing compression washer 331 is completed.
  • the shoulder shoulders respectively support the inner ring of the bearing from the inner side between the two rolling bearings; the outer side of the inner ring of the rolling piston bearing is pressed and positioned from the two sides of the cylinder by the bearing pressing gasket, thereby realizing the
  • the inner rings of two or more rolling bearings are axially positioned.
  • the outer ring of the two rolling bearings is positioned by applying a pressure to the inner side of the outer ring by the shoulder provided in the middle of the cylindrical surface of the rolling piston wheel.
  • the axial position of the inner ring of the two rolling bearings fixed on the inner cylindrical surface of the rolling piston wheel is completed by a shoulder provided on the eccentric spindle journal, and the shoulders are respectively from two
  • the inner side between the rolling bearings bears against the inner ring of the bearing; and the outer ring of the two rolling bearings is positioned, and the shoulder provided at the left end of the cylindrical surface of the rolling piston wheel applies pressure to the side of a bearing outer ring which is in close contact
  • the outer side of the outer ring of the other bearing is inwardly locked by a bearing snap ring 325 disposed in the groove at the right end of the cylindrical surface of the rolling piston wheel.
  • the positioning method of the rolling bearing of the rotor compressor of the present invention is not limited to the above two types, and other positioning methods are also conceivable by those skilled in the art based on the above description.
  • a side sealing piece 321 is provided.
  • the sealing sheet elastic rubber ring 322 in the front (rear) cylinder head is pressed against the outer side of the side sealing piece 321 with an appropriate pressure to prevent leakage.
  • the lateral sealing sheet 321 may be made of a friction-reducing alloy or a polytetrafluoroethylene (PTFE) material.
  • the isolation mechanism 400 divides the axially extending sealed chamber formed by the inner cylindrical surface of the cylinder and the outer cylindrical surface of the rolling piston wheel into a first chamber and a second chamber.
  • the first chamber is a suction chamber 430 that communicates with the low pressure compressed medium input port through the suction through hole 401;
  • the second chamber is a compression chamber 440, that is, a high pressure chamber, which passes through the discharge through hole 402 is in communication with the discharge port of the compressed high pressure compressed medium.
  • the main shaft 200 transmits torque outside the cylindrical inner cavity into the cylindrical inner cavity, and the compressed medium is compressed by the eccentric rotor assembly.
  • an opening and closing valve 427 is provided between the discharge through hole 402 and the high pressure compressed medium discharge port 404.
  • the opening and closing valve 427 can be opened only when the air pressure of the discharge through hole 402 reaches a predetermined pressure threshold, thereby outputting the compressed compressed medium to the high pressure compressed medium discharge port.
  • the on-off valve 427 is always closed when the air pressure of the discharge through hole 402 does not reach the preset pressure threshold.
  • the isolation mechanism 400 includes a rotary valve body 410 and a rotary valve body reset mechanism.
  • the rotary valve body is preferably a sheet-like structure, that is, a rotary valve piece, and may be a semicircular structure as shown in Fig. 1 or the like.
  • other types of valve bodies and their corresponding reset mechanisms can be used, such as: gate valves, etc., refer to the applicant.
  • the previously applied patent Patent Application No.: 201110322746.0
  • the manner of which it is installed is well known to those skilled in the art, and will not be described in detail herein.
  • the position of the cylinder main body 111 corresponding to the cylinder head 140 is formed with an axially extending receiving recess that opens toward the cylindrical inner cavity.
  • the rotary valve body 410 is fitted in the receiving recess and rotatably supported by the slot, so that the rotary valve body 410 swings within a predetermined angular range.
  • the eccentric rotor assembly is rotated to the upper position, the rotary valve body 410 is pressed into the receiving recess and is pressed into the state.
  • the eccentric rotor assembly is rotated to the lower position, the rotary valve body swings to its maximum position and is in an extended state.
  • the end of the rotary valve body is always pressed against the outer cylindrical surface of the rolling piston wheel, thereby isolating the first chamber from the second chamber.
  • the chamber facing the front side is a second chamber, that is, a compression chamber 440, which communicates with the compressed high-pressure compressed medium discharge port 404 through the discharge through-hole 402;
  • the chamber facing the back of the rotary valve body is a first chamber, that is, a suction chamber 430,
  • the suction through hole 401 is in communication with the low pressure compressed medium input port.
  • the eccentric motion of the rolling piston wheel is a 360-degree process of continuously driving the cam for the rotary valve body.
  • the cam's angle of elevation is small. Therefore, the small torque input by the spindle can generate a great thrust to the rotary valve body, and the effect of compressing the high-pressure gas (liquid) body can be achieved, and at the same time, the head of the rotary valve is always kept pressed against the outer cylindrical surface of the rolling piston wheel. Sealed on top.
  • the rotary valve body 410 is fitted in the receiving recess, and is rotatably supported by the receiving recess, and includes: a connecting portion located at a root of the rotary valve body and hinged with the receiving recess; The body of the rotary valve body is oscillated within a predetermined angle range with the connecting portion as an axis.
  • a sliding cylindrical hole having a circular arc notch is disposed in the receiving groove, and the circular arc notch of the sliding cylindrical hole communicates with the receiving groove.
  • the connecting portion is a supporting cylinder.
  • the support cylinder is inserted into the sliding cylinder bore and is constrained by the coating of the sliding cylinder bore.
  • the rotary valve body has a support cylinder as an axis, and is free to swing between the pressed state and the extended state within a predetermined angle range.
  • the angle of the arcuate notch of the sliding cylindrical hole is about 110°, and the corresponding body of the rotary valve body is swingable by more than 250°.
  • the height of the supporting cylinder should be slightly shorter than the height H of the cylinder.
  • the single-side clearance is preferably about 0.01 mm.
  • the movement is flexible and leak-free, and the matching surface of the supporting cylinder and the sliding cylindrical hole should be lubricated, such as adding lubricant, or
  • the surface of the supporting cylinder is plated with polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • the rotary valve body 410 can also adopt the mandrel structure in the patent application (Patent Application No. 201010196950.8) filed by the applicant of the present invention.
  • the rolling cylinder method of the present embodiment eliminates the need for positioning holes in the cylinder head opening core, thereby greatly improving the ease of processing, simple assembly, improved accuracy, and reduced cost.
  • a rolling wheel is further disposed at the head of the rotary valve body.
  • the rolling wheel When the rotary valve body and the rolling piston wheel move relative to each other, the rolling wheel generates rolling, thereby minimizing the rotation of the rotary valve body and the rolling piston wheel. Friction between.
  • the rolling piston wheel When the eccentric shaft rotates one revolution, the rolling piston wheel is pressed by the rolling bearing and elastically affixed to the inner wall of the cylinder without running for one week. Since the diameter of the cylinder is larger than the diameter of the rolling piston wheel, the rolling piston wheel is revolving. In one week, the bearing outer ring rotates for less than one week (the rotation direction is opposite to the revolution direction), which means that the rotary valve body head structure is in contact with the outer cylindrical surface of the rolling piston wheel. The relative sliding speed at the point can be greatly reduced, which is particularly advantageous for sealing.
  • the present invention provides additional plurality of rotary valve body head configurations.
  • FIGS. 8A and 8B are schematic views of the second rotary valve body in the press-in state and the extended state, respectively, in the rotor type compressor isolation mechanism according to the embodiment of the present invention.
  • the rotary valve body 410' shown in Figs. 8A and 8B the rotary valve body is entirely made of a friction reducing material, or is coated with a friction reducing material on its surface.
  • the antifriction material may be SiN ceramic, polytetrafluoroethylene, bronze alloy or the like.
  • Figure 9 is a perspective view of a third type of rotary valve body in a rotor type compressor isolation mechanism according to the present invention.
  • 10A and 10B are schematic views of the rotary valve body of Fig. 9 in a pressed state and an extended state, respectively.
  • the rotary valve body 410 further includes: a swing sealing slider 411.
  • the head of the oscillating sealing sliding head has a cylindrical shape and is slidably wrapped to restrict positioning in a sliding cylindrical hole at the end of the body of the rotary valve body.
  • the contact surface of the swing sealing slider 411 and the rolling piston wheel 330 is a sealing arc surface which is in close contact with the rolling piston wheel 330 and which is slidable on the surface of the rolling piston wheel 330.
  • Figure 10A shows the situation when the rolling piston wheel is rotated to the highest position of the cylinder. At this time, the rotary valve body and the swing seal slider 411 which is fitted to the head of the rotary valve body are retracted into the cylinder recess.
  • Figure 10B shows the situation when the rolling piston wheel roller is rotated to the lowest position of the cylinder block. At this time, the rotary valve body and the swinging sealing sliding head 411 embedded in the head of the rotary valve body are under the thrust of the valve plate reset pin, from the cylinder block.
  • the groove is unscrewed counterclockwise, and the oscillating sealing slide 411 is always pressed against the outer cylindrical surface of the planetary piston roller.
  • the arc-shaped sealing effect of the bottom surface of the oscillating sealing sliding head and the outer cylindrical surface of the planetary piston roller is better.
  • the load pressure can be dispersed to the utmost extent.
  • the oscillating sealing sliding head 411 may be made of a suitable metal material such as tin bronze, beryllium bronze, tin phosphor bronze or the like, and may also be used to heat-harden engineering plastics such as polyphenol aldehyde and polytetrafluoroethylene.
  • a surface of the oscillating sealing slider 411 and the outer cylindrical surface of the planetary piston roller are coated with a layer of Teflon plastic to reduce friction.
  • a compressed gas-liquid passage 411a is provided at the head of the rotary valve body sealing slider 411,
  • the compressed gas-liquid passage 411a can ensure that the compressed medium can smoothly enter the secondary compression chamber through the moment when the rotary valve body is about to enter the receiving recess.
  • a shallow hydrostatic bearing pressure chamber 411b having a depth of between 0.1 mm and 2 mm is formed on the arcuate surface of the oscillating sealing slider 411.
  • the gas-liquid fluid distributed in the hydrostatic bearing pressure chamber 411b acts like a lubricating oil, and the outer cylindrical surface of the swing sealing sliding head 411 and the rolling piston wheel 330 can be greatly reduced. The friction between.
  • connection manner of the swing sealing sliding head and the rotary valve body is not limited to the above-mentioned rolling cylindrical type, and the same can also be adopted in the form of a pivoting connection, a mandrel, etc., as long as the swing sealing sliding head and the rotary valve body can be rotatably connected. It will not be described in detail.
  • the reset mechanism is used to always press the rotary valve body to the outer cylindrical surface of the rolling piston wheel.
  • the position of the side-rotating valve body is opened with a blind hole for the pin.
  • the head of the reset pin 421 bears against the rotary valve body body 410 in the direction toward the rolling piston wheel, thereby realizing the reset sealing of the rotary valve body.
  • the angle between the central axis of the blind hole of the pin and the perpendicular of the rotary valve body being pressed into the receiving recess is between 10 and 20, preferably 13, as shown in Fig. 2B.
  • the contact point of the reset pin 421 with the rotary valve body is: The spin valve body is pressed against the end of the rolling piston wheel, and the rotary valve body is 1/5 to 1/2 of the length of the rotary valve body, preferably 2/5.
  • the revolving motion of the rotary valve body is performed under the non-leakage sliding condition, and the reset pressure is transmitted to the rotary valve body head, thereby improving the service life of the return spring and the rotary valve body in the rotor compressor. And reliability.
  • This design expands the design space of the rotary valve body reset mechanism, unlike the conventional rotor compressor, which is limited only to the narrow space of the support shaft core of the rotary valve body.
  • the spring that is the power to reset the rotary valve body uses a compression spring that has been proven to be reliable. Since the pressure point applied by the rotary valve body reset pin is close to the rotary valve body head, the rotary valve body head (for example, the bottom surface of the roller or the swing seal sliding head) pressed against the outer cylindrical surface of the planetary piston roller can be more accurately ensured. The contact pressure achieves a long-life, reliable seal with minimal sliding friction.
  • FIG. 11A is a schematic view showing the structure of a second type of rotary valve body reset mechanism in the rotor type compressor isolation mechanism according to the present invention.
  • a nitrogen gas spring 423 is disposed in the pin hole, and the free end of the nitrogen gas spring abuts against the moving end of the reset pin 421, and is reset by the reset pin 421 against the rotary valve body to the outer cylindrical surface of the rolling piston wheel 430.
  • the nitrogen gas spring has the characteristics of good sealing, high strength and long service life. As a standard part, it can be easily replaced once it is damaged.
  • the pin hole may be a through hole, and the pin hole is sealed to the outside of the cylinder by the end of the gas spring 423.
  • Figure 11B is a schematic view showing the structure of a third type of rotary valve body reset mechanism in a rotor type compressor according to an embodiment of the present invention.
  • the compressed high pressure gas at the high pressure compressed medium discharge port 404 is introduced into the pin hole of the compression spring 425 above the valve plate reset pin by the high pressure gas passage 424.
  • the high-pressure gas acts as an elastic member to ensure that sufficient gas pressure is applied to the reset pin 421, and the end of the rotary valve body is always sealed with the outer cylindrical surface of the rolling piston wheel 430.
  • the compression spring 425 is only used to withstand the valve plate reset pin when there is no pressure in the high pressure cylinder.
  • the compression spring 425 can be omitted under the premise that it can reliably withstand the valve reset pin even when there is no pressure in the high pressure cylinder.
  • a pressure regulating device such as a one-way valve or a pressure regulating valve, is provided between the compressor high pressure compressed medium discharge port 404 and the high pressure gas passage 424, thereby ensuring a substantially constant pressure in the pin bore above the valve plate reset pin.
  • the rotor type compressor of the present embodiment operates under the condition of sealing sliding by the rotary valve body reset pin, and transmits the reset pressure to the head of the rotary valve body, thereby improving the service life and reliability of the return spring in the rotor type compressor. Thereby providing a highly reliable and practical compressor.
  • the suction stroke as shown in Fig. 12A, is located at the uppermost position of the cylindrical inner cavity, thereby completely pressing the rotary valve body into the receiving recess, and the pin is located at the innermost position of the pin hole.
  • the diameter thereof is 0° with the vertical direction, and the compression chamber surrounded by the outer cylindrical surface of the rolling piston wheel and the inner cylindrical surface of the cylinder is the largest, and the compression chamber is connected with the suction port of the compressor, thereby Inhaling a gaseous compressed medium into the compression chamber;
  • the first-stage compression stroke as shown in Fig. 12B, the eccentricity of the rolling piston wheel is sealed and rolled along the inner surface of the cylinder, and the compression is started after the suction port is passed.
  • the rotary valve body is gradually opened first, and then slowly closed, correspondingly, the pin protrudes first in the pin hole and then retracts.
  • the volume of the compression chamber becomes smaller and smaller.
  • the rolling piston wheel is located at the lowest position of the cylindrical inner cavity. After this point, it reaches as shown in Fig. 12D. Position, the gas in the compression chamber is compressed and pressurized, and gradually enters the cylinder above the rotary valve body;
  • the secondary compression stroke as shown in Fig. 12E, the outer circle of the eccentric roller and the inscribed point of the cylinder circle are at 270 degrees. At this time, the inscribed point position is close to the end position, and the eccentricity of the rolling piston wheel is sealed along the inner surface of the cylinder.
  • the rotary valve body is quickly closed, the high-pressure gas blows the one-way shut-off valve piece, and the gas is compressed and pressurized to enter the cylinder above the rotary valve body, and is further squeezed into the high-pressure gas storage chamber by the rotary valve body.
  • the end position is as shown in Fig. 12A, that is, the position where the rotary valve body returns to the cylinder groove. At this time, the fluid retained in the so-called secondary compression chamber (high pressure chamber) is all pushed into the high pressure gas storage chamber, and is down. The time period is intercepted by the one-way stop valve shown in Fig. 2B.
  • FIG. 13 is a schematic cross-sectional view of a fluid motor in accordance with an embodiment of the present invention.
  • the second chamber of the rotating device that is, the working chamber 530, communicates with the high pressure fluid inlet 510 through the second set of through holes; the first chamber, that is, the discharge chamber 540, passes through the first group of through holes and the low pressure.
  • the fluid outlets 520 are in communication.
  • the high pressure fluid pushes the eccentric rotor to rotate, and the torque generated by the main shaft is transmitted to the outside of the cylindrical cavity.
  • the high pressure fluid can be a liquid or a gas.
  • the working flow of the fluid motor of the present embodiment will be described below.
  • the high pressure fluid flows from the high pressure fluid inlet 510, enters the working chamber through the second set of through holes, and drives the eccentric rotor 300 assembly to rotate and revolve in the counterclockwise direction.
  • the eccentric rotor assembly 300 The revolution rotates the spindle 200; after the eccentric rotor assembly passes its uppermost end, it enters the next stroke, and the fluid after the work flows out through the first set of through holes to the low pressure fluid outlet 520.

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Abstract

一种转动装置，其包括缸体（110）、前端盖（120）和后端盖（130）、主轴（200）、偏心转子组件（300）和隔离机构（400）。偏心转子组件（300）包括偏心轴（310）、滚动活塞轮（330）和至少一滚动轴承（320）。在该转动装置中，偏心轴（310）和滚动活塞轮（330）之间采用滚动轴承（320）方式隔离转动，通过弹性预紧力实现缸体的可靠密封。及应用该转动装置的转子式压缩机和流体马达。还对该转动装置中的旋阀体和旋阀体复位机构进行了改进。

Description

转动装置及应用其的转子式压縮机和流体马达 技术领域
本发明涉及流体机械技术领域， 尤其涉及一种转动装置及应用其的转 子式压缩机和流体马达。 背景技术
目前，市场上最常用的容积式压缩机主要分为四种类型：往复活塞式、 螺杆式、 涡旋式和转子式。 对于转子式压缩机而言， 在主轴旋转时， 偏心 转子紧贴气缸内壁回转，造成月牙状容积空间周期性变化，从而完成吸气、 压缩和排气的过程。 由于转子式压缩机的压缩过程圆滑平稳、 平衡， 已被 广泛应用于空调、 冰箱等家用制冷设备中。
图 1为现有技术转子式压缩机的结构示意图。该转子式压缩机记载于 参考文献 2 (专利申请号： 200780027498.9) 中。 请参照图 1， 该转子式压 缩机包括缸体 1、 滚动转子 2、 偏心套 3、 带有偏心轴部分的驱动轴 4、 摆 动挡块、 螺旋弹簧。 在驱动轴 4的偏心轴部分与滚动转子 2之间设置能在 他们之间灵活转动的偏心套 3， 从而使滚动转子 2的偏心距得以调整并在 工作中实现柔性滚动接触密封。 偏心套 3在绕驱动轴做公转的同时， 绕偏 心中心做自转。 而摆动挡块的转动部分在螺旋弹簧的弹簧力作用下， 以摆 动部分紧压在滚动转子 2的外圆表面上， 实现摆动式隔离。
然而， 图 1所示的转子式压缩机在高强度工作条件下， 尤其是在转动 频率非常高时， 带有偏心轴部分的驱动轴 4与滚动转子 2和偏心套 3的各 滑动面滑动磨擦的能量损耗较大， 必须用油润滑。 进入缸内的润滑油与压 缩介质混合排放后必须再分离。 此外， 由于要靠运动间隙中的润滑油进行 密封， 为了从排气中分离出润滑油， 系统的机壳内需做成高压。 由于机壳 内还同时安装有驱动转子式压缩机旋转的电动机， 机壳内形成的高温高压 环境对驱动电机的绝缘散热十分不利， 电机容易过热。 转子式压缩机由于 偏心转子构造尺寸特别紧凑， 加上前述通过采用油液来填补缸体和密封套 圈接触处的间隙等原因， 使用油润滑已成为习惯， 这就限制了它在大型空 压机和低温用空压机中的使用。
对于图 1所示的转子式压缩机， 螺旋弹簧驱动摆动挡块的一端， 使摆 动挡块的另一端压在滚动转子 2上。 由于螺旋弹簧长时间在高强度条件下 工作，非常容易产生故障而损坏，从而影响整台转子式压缩机的使用寿命， 有必要寻找更精良可靠的摆动挡块复位加压机构。 此外， 由于存在杠杆作 用， 摆动挡块与滚动转子 2之间的力度不容易控制， 力度过大， 不仅增加 摆动挡块的磨损， 而且还会消耗压缩机的功率； 力度过小， 则不能保证气 缸的密封。
此外， 在摆动挡块的头部与滚动转子 2的外圆柱面接触处， 承受着较 大的压力， 并且有高速的相对滑动运动， 因此必须有低磨擦、 耐磨损、 高 效率、 长寿命的密封构造才可以， 如果没有相应措施， 接触处就很容易破 坏。 然而现有技术中的做法， 是把摆动挡块的头部与滚动密封套圈 2的外 圆柱面接触处连接起来， 摆动挡块头部随滚动密封套圈外圆柱面的位置而 固定， 这样虽然能够解决其接触处的磨损和密封问题， 但是， 滚动密封套 圈 2的外圆柱面和缸体 1的圆筒内壁之间就不可能实现滚动了， 导致磨擦 磨损和间隙问题的发生。虽然可以通过采用油液来填补缸体和密封套圈接 触处的间隙， 但是又带来了压缩介质与润滑油分离的问题。 发明内容
(一） 要解决的技术问题
为解决上述的一个或多个问题， 本发明提供了一种转动装置及应用其 的转子式压缩机和流体马达。
(二） 技术方案
根据本发明的一个方面， 提供了一种转动装置。 该转动装置包括： 缸 体； 前端盖和后端盖， 密封连接于缸体的前端和后端， 其与缸体共同限定 一圆筒形内腔； 主轴， 由缸体和 /或前、 后端盖可转动地支撑， 部分地位于 圆筒形内腔内， 其中心轴线与缸体的中心轴线重合； 偏心转子组件， 套设 于主轴位于圆筒形内腔的部分， 包括： 偏心轴， 套设于主轴位于圆筒状内 腔的部分， 其中心轴线与主轴的中心轴线错开预设位置； 滚动活塞轮， 套 设于偏心轴上， 其中心轴线与偏心轴的中心轴线重合； 至少一滚动轴承， 对称地套设于偏心轴上， 其内套圈固定于偏心轴， 其外套圈固定于滚动活 塞轮， 以隔绝两者的转动， 该至少一个滚动轴承与滚动活塞轮之间的预紧 弹性力将滚动活塞轮压紧于圆筒形内腔的内圆筒面， 使圆筒形内腔的内圆 筒面和滚动活塞轮的外圆柱面形成轴向延伸的密封腔室； 隔离机构， 将密 封腔室分隔为相互独立的第一腔室和第二腔室， 该第一腔室和第二腔室分 别与设置在缸体上的第一组通孔和第二组通孔相连通。
根据本发明的另一个方面， 还提供了一种转子式压缩机。 该转子式压 缩机包括上述转动装置， 其中： 第一腔室通过第一组通孔与低压压缩介质 输入口相连通； 第二腔室通过第二组通孔与压缩后高压压缩介质的排出口 相连通； 主轴将圆筒形内腔外的扭矩传递至圆筒形内腔内， 通过偏心转子 组件以对压缩介质进行压缩。
根据本发明的再一个方面， 还提供了一种流体马达。 该流体马达包括 上述转动装置， 其中： 第二腔室通过第二组通孔与高压流体进口相连通； 第一腔室通过第一组通孔与低压流体出口相连通； 高压流体推动偏心转子 转动， 通过主轴将产生的扭矩传递至圆筒形内腔外。
(三） 有益效果
从上述技术方案可以看出， 本发明转动装置及应用其的转子式压缩机 和流体马达具有以下有益效果：
( 1 ) 偏心轴和滚动活塞轮之间采用滚动轴承， 使用滚动轴承后， 转 子压缩机就实现了无油化或者说少油化 （即局部小范围内的油润滑）， 从 而克服了因大量使用润滑油而带来的诸多缺点， 使转动装置可以在大型的 压缩机和空压机领域应用；
( 2 ) 在滚动轴承外套圈的外圆柱面与滚动轴承安装定位内圆筒面之 间留有径向间隙， 其间夹有弹性预紧元件， 该弹性预紧元件在达成压缩机 转子良好可靠密封的同时， 不仅可以避免对构成偏心转子的各个零件的径 向装配尺寸的过于苛刻的精度要求， 降低成本， 还具有吸收振动和噪音的 功能；
( 3 ) 采用平衡配重方案， 减轻了转动装置由于偏心转动而引起的动 量不平衡的问题， 经过转子动量平衡设计的转子式压缩机， 更加符合精密 工学原理， 运行起来振动小， 噪音低；
( 4 ) 通过复位销钉将压缩弹簧的复位压力直接传递至靠近旋阀体头 部的侧面位置， 可以精准地调节压在行星活塞滚轮外圆柱面上的旋阀体头 部的接触压力， 实现最小滑动摩擦力下的可靠密封， 提高了转动装置的工 作可靠性；
(5)将旋阀体复位销钉打造成传统压力气缸的构造， 或使用更有力、 更稳定、 更精密和更长寿的气动元件来控制旋阀体的摆动， 保证了整台转 动装置的工作可靠性和维修的便利性；
(6) 在旋阀体的远端采用滚轮或者摆动密封滑头， 进一歩减小了旋 阀体与滚动活塞轮的摩擦力， 提高了工作效率。 附图说明
图 1为现有技术转子式压缩机的结构示意图；
图 2A为根据本发明实施例转子式压缩机的纵切面示意图；
图 2B为图 2A所示转子式压缩机沿 A-A面的剖视图；
图 3为图 2A所示转子式压缩机中偏心转子组件局部的右视图； 图 4为图 2A所示转子式压缩机中偏心转子组件局部的立体图； 图 5A为根据本发明实施例转子式压缩机中 0型弹性橡胶圈的第一种 装配方式的示意图；
图 5B为根据本发明实施例转子式压缩机中 0型弹性橡胶圈的第二种 装配方式的示意图；
图 5C为根据本发明实施例转子式压缩机中矩型弹性橡胶圈的装配方 式的示意图；
图 6A为根据本发明实施例转子式压缩机偏心转子组件中弹簧片套圈 的示意图；
图 6B为图 6A所示弹簧片套圈装配的示意图；
图 7A为根据本发明实施例转子式压缩机中偏心转子组件的左视图； 图 7B为根据本发明实施例转子式压缩机中偏心转子组件的示意图； 图 8A和图 8B为根据本发明实施例转子式压缩机隔离机构中第二种 旋阀体分别在压入状态和伸出状态的示意图；
图 9为根据本发明转子式压缩机隔离机构中第三种旋阀体的立体图； 图 10A和图 10B为图 9所示旋阀体分别在压入状态和伸出状态的示 意图；
图 11A为根据本发明实施例转子式压缩机隔离机构中第二种旋阀体 复位机构的结构示意图； 图 11B 为根据本发明实施例转子式压缩机隔离机构中第三种旋阀体 复位机构的结构示意图；
图 12A-图 12E为根据本发明实施例转子式压缩机工作流程的示意图； 图 13为根据本发明实施例流体马达的剖视图。 具体实施方式
为使本发明的目的、 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， 对本发明进一歩详细说明。 需要说明的是， 在附图或 说明书描述中， 相似或相同的部分都使用相同的图号。 附图中未绘示或描 述的实现方式， 为所属技术领域中普通技术人员所知的形式。
为方便理解， 首先将本发明各实施例所涉及主要元件进行编号说明， 如下所示：
【本发明主要元件符号说明】
110-缸体； 111-缸体主体；
112-前缸盖； 113-后缸盖；
120-前端盖； 121-前端盖密封胶圈;
130-后端盖； 131-后端盖密封胶圈
140-气缸头；
200-主轴； 210-主轴轴承；
211-轴承锁紧螺母； 212-主轴密封胶圈；
300-偏心转子组件；
310-偏心轴； 320-滚动轴承；
330-滚动活塞轮； 340-平衡块；
311-偏心轴肩； 321-侧面密封片；
322-密封片弹性胶圈； 325-轴承卡环；
331、 341-轴承压紧垫片； 342-配重缺口；
351-0型弹性橡胶圈； 352-矩型弹性橡胶圈;
353-弹簧片套圈；
400-隔离机构； 401-吸入通孔；
402-排出通孔； 403-开闭阀；
404-高压压缩介质排出口； 410， 410'-旋阀体; 411-摆动密封滑头; 411a-压缩气液通路；
421-复位销钉；
422-复位销钉弹簧； 423-氮气弹簧；
424-高压气通道； 425-压缩弹簧；
430-压缩机吸入腔； 440-压缩机压缩腔；
510-高压流体进口； 520-低压流体出口；
530-流体马达做功腔; 540-流体马达排出腔。
本发明提供了一种转动装置及应用其的转子式压缩机和流体马达。在 该转动装置中， 偏心轴和滚动活塞轮之间采用滚动轴承方式， 并通过弹性 预紧元件实现缸体的可靠密封， 通过平衡配重克服了转子式压缩机的振动 和噪音问题， 从而避免了润滑油的使用， 实现了压缩机的大型化。 同时， 还提供了一种全新的旋阀体复位方式， 并对旋阀体进行了改进， 保证了转 动装置及应用其的转子式压缩机和流体马达的整体工作可靠性。
首先， 本发明提供了一种转动装置， 该转动装置包括： 缸体、 前 /后端 盖、 主轴、 偏心转子组件和隔离机构。 其中， 缸体与位于其前 /后两侧的前 /后端盖限定一圆筒形内腔。 主轴由缸体或其前 /后端盖支撑， 部分地位于 圆筒形内腔内， 其中心轴线与缸体的中心轴线重合。 偏心转子组件， 套设 于主轴位于圆筒形内腔的部分， 包括： 偏心轴， 套设于主轴位于圆筒状内 腔的部分， 其中心轴线与主轴的中心轴线平行且错开预设距离； 滚动活塞 轮， 套设于偏心轴上， 其中心轴线与偏心轴的中心轴线重合； 至少一滚动 轴承， 对称地套设于偏心轴上， 其内套圈固定于偏心轴， 其外套圈固定于 滚动活塞轮， 以隔绝两者的转动， 该至少一个滚动轴承与滚动活塞轮之间 的预紧弹性力将滚动活塞轮压紧于圆筒形内腔的内圆筒面， 使圆筒形内腔 的内圆筒面和滚动活塞轮的外圆柱面形成轴向延伸的密封腔室。 隔离机构 将密封腔室分隔为相互独立的第一腔室和第二腔室， 该第一腔室和第二腔 室分别与设置在缸体的第一组通孔和第二组通孔相连通。
该转动装置可以应用于压缩机、 流体马达等流体机械中， 其应用于压 缩机和流体马达时， 吸入通孔和排出口的设置如下：
( 1 ) 当该转动装置应用于压缩机时， 第一腔室通过第一组通孔与低 压压缩介质输入口相连通； 第二腔室通过第二组通孔与压缩后高压压缩介 质的排出口相连通； 主轴将圆筒形内腔外的扭矩传递至圆筒形内腔内， 通 过偏心转子组件以对压缩介质进行压缩；
(2) 当该转动装置应用于流体马达时， 第二腔室通过第二组通孔与 高压流体进口相连通； 第一腔室通过第一组通孔与低压流体出口相连通； 高压流体推动偏心转子转动， 通过主轴将产生的扭矩传递至圆筒形内腔 外。
该转动装置中， 每组通孔中通孔的数量可以为 1个， 也可以为多个。 并且， 滚动轴承可以为滚柱轴承、 滚球轴承、 滚针轴承、 空气动力学滚动 轴承或复合轴承。 滚动轴承的数量为 1个， 但优选为 1组、 2组、 3组、 4 组， 每组包括沿圆筒形内腔左右对称设置的两个滚动轴承。 此处的对称， 指的是相对于以下平面对称： 该平面过主轴位于圆筒形内腔部分的中心 点， 且垂直于主轴的中心轴线。
以下将对应用该转动装置的转子式压缩机和流体马达， 尤其是转子式 压缩机， 进行详细说明。 通过以下的说明， 本领域技术人员应当可以对本 发明的转动装置有更加清楚的了解。
本发明还提供了一种转子式压缩机。 图 2A为根据本发明实施例转子 式压缩机的纵切面示意图。 图 2B为图 2A所示转子式压缩机沿 A-A面的 剖视图。 请参照图 2A和图 2B, 本实施例转子式压缩机包括： 缸体 110、 前端盖 120/后端盖 130、 主轴 200、偏心转子组件 300和隔离机构 400。 以 下分别对各个组成部分进行详细说明。
请参照图 2A， 缸体 110与位于其前后两侧的前端盖 120/后端盖 130 共同限定一圆筒状内腔。 该圆筒状内腔即为压缩机的气缸， 该气缸半径为 R2， 高度为 H。 缸体 110包括缸体主体 111、 分别设置在该缸体主体 111 前 /后端面的前缸盖 112和后缸盖 113。 在缸体主体 111外侧的预设位置， 一般为上方， 设置气缸头 140。 后续隔离机构的旋阀体及其复位机构均对 应该气缸头 140的位置进行设置， 这些内容将在下文进行详细说明。
主轴 200 由缸体前后缸盖 （112和 113 ) 支撑， 其中心轴线与圆筒形 内腔的中心轴线重合， 其直径为0。 该主轴 200的第一部分位于圆筒状内 腔外， 与外界动力源相接， 将外界动力源输入的扭矩传输至圆筒状内腔； 第二部分位于圆筒状内腔内， 利用外界动力源输入的扭矩带动偏心转子组 件 300转动。
为了减小摩擦， 主轴 200和前后缸盖 （112和 113 ) 之间分别设置主 轴轴承 210。 该主轴轴承 210优选采用高承载能力、 长寿命、 高精度的圆 锥滚柱轴承， 以保证转子侧面和缸盖面的间隙精密可控。 由轴承锁紧螺母 211锁紧主轴轴承 210的位置。此外， 为了实现主轴与前端盖之间的密封， 在两者之间设置主轴密封胶圈 212。为了实现前端盖与前缸盖之间的密封， 在两者之间设置前端盖密封胶圈 121 ; 为了实现后端盖与后缸盖之间的密 封， 在两者之间设置后端盖密封胶圈 131。
需要说明的是，虽然本实施例中主轴 200是由前缸盖 112和后缸盖 113 可转动地支撑， 但其也可以由前 /后端盖可转动的支撑。此外， 虽然本实施 例中主轴只有一端伸出圆筒形内腔外， 但是， 本发明同样包括主轴两端伸 出圆筒形内腔外， 由左右两侧同时输入扭矩的情况。 本领域技术人员应当 很清楚的明了上述技术方案如何实现， 此处不再赘述。
偏心转子组件 300位于上述圆筒状内腔内。 图 3为图 2A所示转子式 压缩机中偏心转子组件 300局部的右视图。 图 4为图 2A所示转子式压缩 机中偏心转子组件局部的立体图。请参照图 2B、 图 3及图 4， 该偏心转子 组件包括： 偏心轴 310， 套设于主轴 200位于圆筒状内腔的第二部分， 其 中心轴线与主轴 200的中心轴线平行且错开预设距离； 滚动活塞轮 330， 套设于偏心轴 310上， 其中心轴线与偏心轴 310的中心轴线重合， 其半径 为 R1 ; 至少一滚动轴承 320， 对称地套设于偏心轴 310上， 其内套圈固定 于偏心轴 310， 其外套圈固定于滚动活塞轮 330， 以隔绝两者的转动。 该 些滚动轴承与滚动活塞轮之间的预紧弹性力将滚动活塞轮压紧于圆筒形 内腔的内圆筒面， 使圆筒形内腔的内圆筒面和滚动活塞轮的外圆柱面形成 轴向延伸的密封腔室。 偏心轴 310的偏心度 e的大小根据压缩机排量、 流 体压力等因素而定，例如当排量为 53 c.c，压力为 IMPa 时取 4.5mm即可， 排量越大， 偏心度 e就越大。
主轴 200带动偏心轴 310转动。 继而， 在偏心轴 310的带动下， 滚动 活塞轮 330在沿主轴中心轴线进行公转的同时， 以沿缸体的内圆筒面滚动 的方式进行自转， 滚动活塞轮 330的转动和偏心轴 310的转动由滚动轴承 如上所述的滚动轴承 320可以为滚柱轴承、 滚球轴承、 滚针轴承、 空 气动力学滚动轴承或复合轴承， 优选为滚球轴承。 在图 2B、 图 3及图 4 中， 偏心轴 310和滚动活塞轮 330之间设置对称的 2个（即 1组） 的滚动 轴承 320。 本领域技术人员应当清楚， 该滚动轴承的个数可根据需要进行 设计， 如果圆筒形内腔的轴向距离， 即缸体高度 H， 较大的情况下， 该滚 动轴承可以为对称的 2组、 3组或者 4组， 每组两个。 当然， 该滚动轴承 也可以为截面积较大的一个， 但其也应当是沿圆筒形内腔左右对称设置 的。
在传统的转子式压缩机设计中， 因为转子式压缩机的排量和外形尺寸 都较小， 偏心转子构造的尺寸又特别紧凑， 加上前述必须采用润滑油来填 补缸体和密封套圈接触处的间隙等原因， 导致机壳内必须做成高压， 使用 润滑油的滑动轴承已成为习惯， 至今未见在转子式压缩机的滚动活塞轮和 偏心轴之间通过滚动轴承进行减磨的技术。 然而， 市场要求转子式压缩机 能够进化为符合大型与低温使用要求的致冷压缩机， 现有的采用润滑油进 行润滑的转子式压缩机已经不能满足需求， 就必须要有新变革。
通过在转子式压缩机采用成熟工业化技术大量生产的并且还不断在 进歩的当代滚动轴承， 不仅可以通过滚动磨擦代替滑动磨擦来大大减少磨 擦能耗， 提高能效； 并且使用滚动轴承后， 转子压缩机就有望实现无油化 或者说少油化 （即局部小范围内的油润滑）， 就有望克服因大量使用润滑 油而带来的诸多缺点， 在大型的压缩机和空压机中应用。
然而， 需要说明的是： 虽然参考本申请说明书循序渐进的说明， 用滚 动轴承方式来代替现有的油润滑的方式是技术发展的必然趋势， 但要在压 缩机转子结构上合理地导入滚动轴承以代替当前的油润滑滑动轴承， 以滚 动磨擦代替当前的滑动磨擦， 并不是一件简单的事情， 否则也就无法解释 现有技术中没有采用滚动轴承的事实了。
机械设计的经验总结告诉我们，相邻运动面在 0.01~0.03mm的间隙下， 才能够有良好的气密性。 本实施例转子式压缩机中， 由于偏心轴和滚动活 塞轮之间使用滚动轴承构造， 最理想的低成本、 高质量基本密封条件是： 运动面之间无滑动， 因此可无间隙， 甚至于可微过盈配合， 实现零泄漏。 为了实现上述的基本密封条件， 在偏心轴、 滚动活塞轮和缸体本体内壁之 间采用预紧弹性设计， 以实现最好的密封。
转子式压缩机中滚动活塞轮与缸体密封间隙的控制目标， 就是必须保 证滚动活塞轮在沿缸体内壁滚动时， 在其接触切点处的密封间隙△为零， 则有下述数学表达式：
Δ = R— e— r— Ψ = 0
其中： 密封间隙为 Δ ;
缸体内壁圆筒半径为 R;
滚动活塞轮的外圆筒半径为 r ;
滚动活塞轮与缸体中心的偏心量为 e ;
滚动活塞轮支撑轴承的径向游隙为 Ψ。
因此， 在转子式压缩机滚动活塞轮装配之前， 要预先测量好上述各参 数， 进行选配。 由于缸体内壁圆筒半径 R、 滚动活塞轮与缸体中心的偏心 量 （即曲轴偏心半径） e、 滚动轴承的径向游隙 Ψ， 一旦加工成形后都不 太好修正， 所以通常采用对滚动活塞轮的外圆筒半径 r进行修正调节选配 的办法。
在本实施例中， 转子式压缩机滚动活塞轮与缸体密封间隙的控制目标 可以采用过盈配合， 就是说密封间隙△小于零。 这意味着在滚动活塞轮和 缸体的接触切点处预紧加压， 产生一个微观弹性变形， 形成的气隙密封就 能够由线扩展到面。 需要注意的是， 预紧加压量不能太大 （大约在 1〜 ΙΟΟμπι) ,不能超过装配尺寸链系统允许的弹性范围，更不能造成装配尺寸 链系统的永久变形事故； 当压缩机经过初期的跑合运行阶段之后， 各零部 件尺寸磨合稳定下来时， 上述预紧加压产生的微观弹性变形就能够自动补 偿摩擦损耗变形， 确保转子式压缩机滚动活塞轮与缸体密封间隙△不大于 零的控制目标。 但是， 这样一来， 制造现场就往往会对构成偏心转子的各 个零部件的径向装配尺寸提出过于苛刻的精度要求。
通过以上分析可知， 滚动轴承 320与滚动活塞轮 330之间的预紧弹性 力将滚动活塞轮压紧于圆筒形内腔的内圆筒面从而实现两者的密封是可 行的。一般情况下，该预紧弹性力可来自于滚动轴承 320与滚动活塞轮 330 之间采用过盈配合。 然而， 过盈配合如果太大的话， 就有可能导致转子式 压缩机出现运行不畅的问题。 为了解决上述难题， 就需要在滚动活塞轮 330的内圆筒面和滚动轴承 320的外圆柱面两者之一上开设相对于滚动轴承滚动体 （例如， 对于滚珠 轴承， 其滚动体就是钢球）沟槽径向中心线呈对称分布的一条或多条镶嵌 槽， 在该镶嵌槽内设置弹性预紧元件， 该弹性预紧元件在正常状态下的高 度大于上述镶嵌槽的深度， 以实现滚动活塞轮 330的内圆筒面和滚动轴承 330的外圆柱面之间的预紧加压。 此外， 该弹性预紧元件还能够自行吸收 和补偿误差。
该弹性预紧元件可以采用使用范围很广的 0型弹性橡胶圈 351， 其密 封压力从 1.33 X 10— 5Pa到 400MPa (动密封可达 35MPa)。 0型弹性橡胶圈 的材料以氟橡胶为好， 氟橡胶有很好的弹性力， 耐磨耐压， 并且其连续使 用温度可达 210°C。
图 5A为根据本发明实施例转子式压缩机中 0型弹性橡胶圈的第一种 装配方式的示意图。 如图 5A所示， 在滚动活塞轮的内圆筒面开多条镶嵌 槽， 多条镶嵌槽的轴向位置相对于滚动轴承滚动体（钢球）沟槽径向中心 线呈对称且平均分布， 以便能够均衡吸收压力变形， 多条 0型弹性橡胶圈 351可以镶嵌在该镶嵌槽内。 当偏心主轴转动时， 滚动轴承外圆柱面就会 压缩 0型弹性橡胶圈 351产生一个弹性变形，把滚动活塞轮 330的外圆柱 面紧紧地压贴在缸体的内圆筒面上， 实现有预紧力的零间隙密封。
滚动轴承外套圈通过 0型弹性橡胶圈 351预紧固定在滚动轴承安装定 位内圆筒面上， 其相对于活塞轮轴承安装定位内圆筒面的中心位置来说是 浮动的，因此它们之间需要设有足够的间隙 β来压缩 0型弹性橡胶圈才行， 滚动轴承安装定位的活塞滚轮内径 Ω必须比滚动轴承套圈外径大， 间隙 β 的大小视轴承尺寸而定， 其值范围在 0.1到 1mm左右。
在前面， 提到了通常采用对滚动活塞轮的外圆筒半径 r进行修正调节 选配的办法， 来保证转子在沿缸体内壁滚动时， 在其接触切点处的密封间 隙 Δ为零。 当使用 0型弹性橡胶圈预紧固定滚动活塞轮后， 滚动轴承外 套圈外圆柱面和滚动轴承安装定位内圆筒面之间有了间隙 β， 此时滚动活 塞轮支撑滚动轴承的径向游隙 ψ为零。
当把滚动活塞轮的外圆筒半径 r预先加大一个值 Ar后则有下述数学表 达式： △=R_e_ (Γ+ΔΓ) =0
其中： 密封间隙为 Δ;
缸体内壁圆筒半径为 R;
滚动活塞轮的外圆筒半径为 r;
滚动活塞轮与缸体中心的偏心量为 e;
滚动活塞轮的外圆筒半径 r预先加大值为 ΔΓ。
滚动轴承外套圈外圆柱面和滚动活塞轮的圆柱面之间的间隙为 β， 令 间隙 β的压缩减少量为 Δβ，滚动轴承的径向游隙为 ψ， 则有下述数学表达 式：
△Γ= ψ+Δβ
0型弹性橡胶圈压缩变形的反作用力和间隙 β的变化量 Δβ成正比， 有下述数学表达式：
0<Δβ^β
因此， 在设计时， 必须通过实践经验来正确选定 Δβ值， 在保证密封 间隙 Δ为零的同时，要做到滚动活塞轮外圆柱面对缸体内壁圆柱面在接触 切点处有适度的弹性预紧压力即可， 避免过度预紧。
图 5Β为根据本发明实施例转子式压缩机中 0型弹性橡胶圈的第二种 装配方式的示意图。 图 5Β中 0型弹性橡胶圈的装配方式与图 5Α类似， 不同之处仅在于镶嵌槽开设于滚动轴承外套圈的外圆柱面， 其工作原理同 图 5Α所示的弹性橡胶圈的工作原理相同， 此处不再重述。
对于图 5Α和图 5Β的 0型弹性橡胶圈来说， 其断面尺寸大小是设计 的关键， 在这里重点要满足三个条件：
( 1 ) 转子系统通过 0型弹性橡胶圈传递到滚动活塞轮的外圆柱面与 缸体内壁圆筒面接触处的合适的弹性预紧压力；
(2) 0型弹性橡胶圈的断面直径要足够大， 0型弹性橡胶圈与滚动 活塞轮的滚动轴承安装定位内圆筒面的接触面积也要有足够大， 才能满足 系统有足够柔软的弹性， 吸收振动和噪音。
(3 ) 由于 0型弹性橡胶圈周而复始地在活塞轮与缸体内壁的接触点 受到挤压变形， 因此， 0型弹性橡胶圈的截面积要足够大， 才能有足够的 疲劳强度， 不发生永久变形。 在市场上有一种叫做膨胀补正深沟球轴承（防止打滑轴承） 的标准轴 承， 在外圈外圆柱面上设有两个矩型沟槽， 沟槽里镶嵌有高膨胀率的高分 子材料， 用来防止系统温度升高后轴承定位处因热膨胀而造成的松动； 还 有一种叫做 AC轴承 （防止打滑轴承） 的标准轴承， 在外圈外圆柱面上设 有两个矩型沟槽，沟槽里镶嵌有 0型橡胶圈，用在轴承外圈不能紧配固定 时防止打滑用。 然而， 上述两种轴承的主要目的是防止打滑及热膨胀， 与 本实施例的利用滚动轴承与滚动活塞轮之间的预紧弹性力来进行密封存 在本质区别。
此外， 上述各种滚动轴承由于在其外圈设置沟槽， 会严重影响滚动轴 承自身的承载力和稳定性。 因此， 不提倡不经计算就直接使用上述市场少 见的防止打滑的标准轴承， 而是提倡采用市场多见的普通球轴承或者滚柱 轴承， 并在滚动活塞轮 320的内圆筒面开镶嵌槽。 这样的话， 整体结构更 加合理化， 形式更加多样化， 效果更加精益化。
为此， 弹性橡胶圈的截面形状还可以设计成矩形或者其它更多的有利 于满足合适的弹性预紧压力、 吸收振动和噪音、 有足够的疲劳强度使用寿 命延长的形状， 其中方案之一为如图 5C所示的矩形弹性带齿橡胶圈 352。
如图 5C所示， 由于镶嵌矩形弹性带齿橡胶圈 352的沟槽宽度几乎和 轴承套圈的宽度一样， 不可以在本来就是薄壁结构的轴承套圈上再开挖镶 嵌沟槽了， 只能把镶嵌沟槽开到滚动活塞轮的滚动轴承安装定位内圆筒面 上，这样镶嵌沟槽的深度也可开的更深一些，弹性空间更大一些。装配时， 在矩形弹性带齿橡胶圈 352的牙齿上抹上黄油即可长期工作。
特别值得注意的是： 当偏心主轴高速运转时， 上述 0型或矩形弹性橡 胶圈在受到高频率反复的冲击压力长期工作后， 有可能因发热而软化乃至 破坏， 因此要考虑采用更加耐热的高强度弹性材料， 例如： 多股细金属丝 网做成的弹性圈， 或者金属弹簧套圈等， 该金属优选为合金钢或其他弹性 较大的金属材料。
图 6A为根据本发明实施例转子式压缩机偏心转子组件中弹簧片套圈 的示意图。 请参照图 6A, 该金属弹簧套圈包括： 带有连续 U字形光滑圆 弧曲面拱起的弹簧片， 及支撑该弹簧片的刚性底座边沿。 该刚性底座边沿 如图 6B所示， 在滚动活塞轮的内圆筒面开设镶嵌槽， 凹槽中心线与 滚动轴承中心线重合， 该带有 U字形光滑圆弧曲面拱起的金属弹簧套圈 353装配于上述镶嵌槽内。 在装配时， 由于金属弹簧套圈 353刚性底座边 沿的直径可以弹性缩小， 所以能够预先镶嵌入滚动轴承安装定位内圆筒面 上的矩形沟槽内完成定位， 抹上润滑剂后， 就可以容易地把滚动轴承外套 圈压入装配。 由于采用冲压工艺， 所以金属弹簧套圈容易大规模量产， 保 证质量， 降低成本。
本实施例中， 通过在滚动轴承外套圈的外圆柱面滚动轴承之间安装弹 性预紧元件， 当偏心主轴转动时， 滚动轴承的外圆柱面就会压缩弹性预紧 元件产生一个弹性变形力， 把滚动活塞轮的外圆柱面紧紧地压贴在缸体的 内圆筒面上， 不管构成偏心转子组件的各个零件的径向装配尺寸有什么精 度误差， 也不管偏心转子组件的旋转外圆轨迹径向有何偏差跳动， 都可被 弹性预紧元件的弹性变形所随机吸收， 保证实现有弹性预紧力的零间隙密 封。 因此， 不仅在得以达成压缩机偏心转子组件良好可靠密封质量目标的 同时， 还可以避免对构成偏心转子组件的各个零件的径向装配尺寸的过于 苛刻的精度要求， 降低成本。
为了节约缸体空间，在偏心轴套设滚动轴承的位置设置偏心轴肩 311， 如图 3所示。 除该偏心轴肩 311之外的偏心轴的部位就可以节省出来进行 平衡配重， 具体的平衡配重方法如下文所述。
请参照图 2A、 图 3及图 4， 在偏心轴较轻的一侧， 两偏心轴肩之间， 沿偏心轴对称设置平衡块 340。 该平衡块 340的大小及重量视圆筒形内腔 的体积及偏心度而定。
此外， 除了上述平衡配重方式之外， 本发明还提供了另外的多种平衡 配重方式。
在第一种平衡配重方式中， 偏心转子组件中的平衡块 341不再是单独 的一块， 而是在偏心轴较轻一侧的连成一片的弧形平衡块区域， 如图 7A 所示。 这种类型的平衡块易于制造， 并且平衡效果好。
在第二种平衡配重方式中， 偏心转子组件采用在偏心轴较重一侧开配 重缺口 342， 来减小此处的配重， 实现在偏心轴转动过程中的平衡， 如图 7B所示。 在其他平衡配重方式中， 还可以通过在偏心轴偏重的一侧开多个配重 孔， 以减轻配重。 此外， 也可以在偏心轴的加工上尽量减少其与主轴的偏 心度， 乃至同心的方式来平衡配重。
在现有技术中， 虽然动量平衡的重要性早已家喻户晓， 但是在当今不 少转子式压缩机上， 鲜见做到， 那是因为采用油润滑与油密封技术的偏心 轴滑动轴承的空间太狭小， 配重难以展开。 本发明由于滚动轴承的利用， 使得在两个对称布置的滚动轴承跨度空间之间有可能进行转子动量平衡 的配重构造设计了。 采用平衡配重方案， 减轻了由于转子式压缩机由于偏 心转动而引起的动量不平衡的问题， 更加符合精密工学原理。 经过转子动 量平衡设计的转子式压缩机， 当然运行起来振动小， 噪音低。
为了实现滚动轴承的定位， 避免在滚动活塞轮转动过程中其位置出现 偏移， 固定在压缩机偏心转子组件上的两个滚动轴承的内外圈轴向位置的 定位， 属于预紧定位， 通过滚动活塞轮内圆筒面和偏心主轴轴颈上的定位 轴肩来消除滚动轴承的轴向游隙， 使滚动轴承在转动时减少轴向晃动， 滚 动活塞轮的定位方式可以采用以下两种中任意一种：
一、 如图 2A所示， 固定在滚动活塞轮内圆筒面上的两个滚动轴承的 内圈轴向位置的定位， 由设在偏心主轴轴颈上的轴肩和设在主轴轴颈上的 轴承压紧垫片 331完成。轴肩分别从两个滚动轴承之间的内侧向外顶住轴 承的内圈； 滚动活塞轴承的内圈的外侧， 则由轴承压紧垫片从缸体的两侧 进行压紧定位， 从而实现该两个或多个滚动轴承的内圈轴向定位。 而两个 滚动轴承的外圈定位， 则由滚动活塞轮内圆筒面中间所设的轴肩对外圈内 侧面施加压力进行定位。
二、 如图 7B所示， 固定在滚动活塞轮内圆筒面上的两个滚动轴承的 内圈轴向位置的定位， 由设在偏心主轴轴颈上的轴肩完成， 轴肩分别从两 个滚动轴承之间的内侧向外顶住轴承的内圈； 而两个滚动轴承的外圈定 位， 则由滚动活塞轮内圆筒面左端所设的轴肩对贴紧的一个轴承外圈的侧 面施加压力进行定位， 另一个轴承的外圈的外侧面则由设在滚动活塞轮内 圆筒面右端沟槽内的轴承卡环 325向内锁紧定位。
当然， 本发明转子式压缩机的滚动轴承的定位方式也不限于以上的两 种， 本领域技术人员根据以上的描述也可以想到其他的定位方式。 此外， 滚动活塞轮侧面的密封十分重要， 在滚动活塞轮的两侧， 设置 侧面密封片 321。 嵌入前 （后） 缸盖内的密封片弹性胶圈 322以适当的压 力压住侧面密封片 321的外侧， 以防泄漏。 该侧向密封片 321可用减磨合 金或者聚四氟乙烯 （PTFE) 材料制成。
如图 2A和图 2B所示， 隔离机构 400将由缸体的内圆筒面和滚动活 塞轮的外圆柱面形成的轴向延伸的密封腔室分隔为第一腔室和第二腔室。 对于压缩机来讲， 该第一腔室为吸入腔 430， 其通过吸入通孔 401与低压 压缩介质输入口相连通； 该第二腔室为压缩腔 440， 即高压腔， 其通过排 出通孔 402与压缩后高压压缩介质的排出口相连通。主轴 200将圆筒形内 腔外的扭矩传递至圆筒形内腔内， 通过偏心转子组件以对压缩介质进行压 缩。 需要注意的是， 在排出通孔 402和高压压缩介质排出口 404之间， 具 有开闭阀 427。 只有当排出通孔 402的气压达到一预设压力阈值时， 该开 闭阀 427才可以打开， 从而将压缩后的压缩介质输出至高压压缩介质排出 口。 在排出通孔 402的气压未达到该预设压力阈值时， 该开闭阀 427是始 终是关闭的。
隔离机构 400包括旋阀体 410和旋阀体复位机构。 其中， 该旋阀体优 选为片状结构， 即旋阀片，也可以是如图 1所示的半圆形结构等等。当然， 本领域技术人员也应当清楚， 除了下文中公布的旋阀体及其复位机构之 外， 还可以采用其他类型的阀体及其相应的复位机构， 例如： 闸阀等， 可 参考申请人在先前申请的专利（专利申请号： 201110322746.0)， 其安装方 式对于本领域技术人员来讲是公知的， 此处不再详细描述。
缸体主体 111上对应气缸头 140的位置形成有一轴向延伸的、 朝向圆 筒形内腔敞开的容放凹槽。该旋阀体 410配装在该容放凹槽内并由该槽可 转动的支撑， 使得旋阀体 410在预定的角度范围内摆动。 当偏心转子组件 的转动至上部位置时， 旋阀体 410被压入该容放凹槽内， 呈压入状态。 当 偏心转子组件转动至下部位置时，旋阀体摆动至其最大位置，呈伸出状态。 而旋阀体的末端始终压设于滚动活塞轮的外圆柱面， 从而将第一腔室和第 二腔室隔离。 其中， 当旋阀体从容放凹槽内摆出时， 其正面朝向的腔室为 第二腔室， 即压缩腔 440， 其通过排出通孔 402与压缩后高压压缩介质排 出口 404相连通； 旋阀体背面朝向的腔室为第一腔室， 即吸入腔 430， 其 通过吸入通孔 401与低压压缩介质输入口相连通。
滚动活塞轮的偏心运动， 对于旋阀体来说， 就是一个 360度连绵不断 地驱动凸轮的过程。 在该过程当中， 凸轮的升角很小。 因此， 主轴输入的 很小的扭矩， 就可以对旋阀体产生极大的推力， 达到压缩高压气 （液） 体 的效果， 同时保证旋阀的头部始终保持压在滚动活塞轮外圆柱面上密封。
请参照图 2B, 旋阀体 410配装在该容放凹槽内， 并由该容放凹槽可 转动的支撑， 包括： 连接部， 位于旋阀体的根部， 与容放凹槽铰接； 旋阀 体本体， 以连接部为轴， 在预定的角度范围内摆动。
具体来讲， 容放凹槽内设置具有圆弧缺口的滑动圆柱孔， 滑动圆柱孔 的圆弧缺口与容放凹槽连通。 该连接部为一支撑圆柱。 该支撑圆柱插入滑 动圆柱孔内， 受到滑动圆柱孔的包覆制约定位。 旋阀体本体以支撑圆柱为 轴， 在预定的角度范围内， 在压入状态和伸出状态间自由摆动。 优选地， 滑动圆柱孔的圆弧缺口的角度大约为 110°，对应的旋阀体本体可摆动的幅 度大于 250°。
支撑圆柱的高度应比缸体高度 H稍矮，单边间隙在 0.01mm左右为佳， 运动灵活且无泄漏， 且支撑圆柱与滑动圆柱孔的配合面应采取润滑措施， 如加润滑剂， 或者支撑圆柱的表面镀聚四氟乙烯 （PTFE)。 聚四氟乙烯 (PTFE)在塑料中它有最佳的老化寿命， 同时是固体材料中摩擦系数最低 的材料。
当然，旋阀体 410也可以采用本发明的申请人先前提交的专利申请 (专 利申请号： 201010196950.8) 中的芯轴结构。 但是， 相比于芯轴结构， 本 实施例滚动圆柱方式无需在缸盖开芯轴定位孔， 从而大大改善了加工容易 度， 装配简单， 精度提高而成本降低。
如图 2B所示， 在旋阀体头部还设置滚动轮， 在旋阀体与滚动活塞轮 相对运动时， 该滚动轮产生滚动， 从而最大限度的减小了旋阀体和滚动活 塞轮之间的摩擦。
当偏心轴旋转一周， 滚动活塞轮被滚动轴承压住， 弹性地贴在缸体内 壁上无滑动地跑过一周，因为缸体的直径要比滚动活塞轮的直径大，所以， 滚动活塞轮在公转一周时， 其轴承外套圈的自转远不到一周 （自转方向和 公转方向相反）， 这意味着旋阀体头部构造物和滚动活塞轮外圆柱面接触 处的相对滑动速度可大大减少， 特别有利于密封。
除了图 2B所示的旋阀体头部构造之外， 本发明还提供了另外的多种 旋阀体头部构造。
图 8A和图 8B为根据本发明实施例转子式压缩机隔离机构中第二种 旋阀体分别在压入状态和伸出状态的示意图。 在图 8A和图 8B所示的旋 阀体 410'中， 旋阀体整体上采用减磨材料制成， 或者是在其表面镀减磨材 料。 该减磨材料可以为 SiN陶瓷， 聚四氟乙烯、 青铜合金等。 在实际运行 中， 旋阀体 410'头部和滚动活塞轮的接触面不但会自然跑合密封， 而且可 自动随旋阀体的摆动幅度变大， 摩擦损耗量得到补偿。
图 9为根据本发明转子式压缩机隔离机构中第三种旋阀体的立体图。 图 10A和图 10B为图 9所示旋阀体分别在压入状态和伸出状态的示意图。 请参照图 9及图 10A、 图 10B , 旋阀体 410还包括： 摆动密封滑头 411。 该摆动密封滑头的头部呈圆柱形， 可摆动地包覆制约定位于旋阀体本体端 部的滑动圆柱孔内。 摆动密封滑头 411与滚动活塞轮 330的接触面为贴紧 滚动活塞轮 330， 并可在滚动活塞轮 330表面滑动的密封圆弧面。 图 10A 所示为滚动活塞轮旋转到缸体最高位时的情况。 此时， 旋阀体本体和镶在 旋阀体本体头部的摆动密封滑头 411一起缩回了缸体凹槽内。图 10B所示 为滚动活塞轮滚轮旋转到缸体最低位时的情况， 此时旋阀体本体和镶在旋 阀体头部的摆动密封滑头 411在阀片复位销钉的推力下， 从缸体凹槽内沿 逆时针方向旋出， 摆动密封滑头 411始终压在行星活塞滚轮外圆柱面上。 这种摆动密封滑头底面和行星活塞滚轮外圆柱面的圆弧面状密封效果较 好。 并且， 由于有较大的密封面积， 可以最大限度的分散载荷压力。
由于摆动密封滑头 411底面和行星活塞滚轮 330外圆柱面的表面之间 的相对运动速度较大， 因此， 摆动密封滑头的减磨设计， 必须严格按照磨 擦学 （Tribology) 的减磨要求， 选定适当的润滑方法， 参考相近功能要求 的轴瓦形式进行。摆动密封滑头 411在材料上可选用适当的金属材料如锡 青铜、 鈹青铜、 锡磷青铜等， 也可用纤维强化热硬化聚酚醛、 聚四氟乙烯 等工程塑料。 优选地， 在摆动密封滑头 411底面和行星活塞滚轮外圆柱面 的表面镀上一层聚四氟乙烯塑料， 可以减少磨擦。
如图 9所示， 在旋阀体密封滑头 411的头部设置压缩气液通路 411a， 该压缩气液通路 411a可以保证即使在旋阀体即将进入容放凹槽内的瞬间， 压缩介质仍然可以通过其顺利进入二级压缩室。
此外， 在摆动密封滑头 411的圆弧面状底面上开有浅浅的流体静压轴 承压力腔 411b， 其深度介于 0.1mm至 2mm之间。在该转子式压缩机运行 的过程中， 流体静压轴承压力腔 411b 中分布的气液流体起到类似润滑油 的作用， 可以极大地减小了摆动密封滑头 411和滚动活塞轮 330外圆柱面 之间的摩擦。
此外， 摆动密封滑头与旋阀体本体的连接方式不限于上述滚动圆柱形 式， 同样也可以采用枢接、 芯轴等形式， 只要能够保证摆动密封滑头与旋 阀片本体可转动连接即可， 此处不再详细说明。
如图 2A和图 2B所示， 复位机构用于使旋阀体始终压设于滚动活塞 轮的外圆柱面。 如图 2B所示， 在容放凹槽的底部， 侧对旋阀体位置， 开 有一个销钉盲孔。 销钉盲孔内置复位销钉弹簧 422， 复位销钉 421插入销 钉盲孔， 顶住复位销钉弹簧 422的自由端， 可滑动密封。 复位销钉 421的 头部沿朝向滚动活塞轮的方向顶住旋阀体本体 410， 实现旋阀体的复位密 封。 优选地， 该销钉盲孔的中心轴线与旋阀体压入容放凹槽内的垂线之间 的夹角介于 10°至 20°之间， 优选为 13° , 如图 2B所示。 该复位销钉 421 与旋阀体的接触点为： 自旋阀体压住滚动活塞轮一端开始， 旋阀体长度的 1/5至 1/2处， 优选地为 2/5处。
本实施例中， 通过旋阀体复位销钉在不漏气的滑动条件下往复运动， 把复位压力传至旋阀体头部， 从而提升了转子式压缩机中复位弹簧和旋阀 体的使用寿命和可靠性。这样的设计，扩展了旋阀体复位机构的设计空间， 不像传统转子式压缩机的那样， 仅仅局限在旋阀体的支撑轴芯狭小空间。
同时， 作为旋阀体复位动力的弹簧采用已被实践证明为可靠的压缩弹 簧。 由于通过旋阀体复位销钉施加的压力点靠近旋阀体头部， 可以更大程 度上精准地保证压在行星活塞滚轮外圆柱面上的旋阀体头部（例如滚轮或 者摆动密封滑头底面） 的接触压力， 实现最小滑动磨擦力下的长寿命可靠 密封。
除了上述旋阀体复位机构外， 本发明还提供另外两种形式的旋阀体复 位机构。 图 11A为根据本发明转子式压缩机隔离机构中第二种旋阀体复位机 构的结构示意图。 如图 11A所示， 在销钉孔内设置氮气弹簧 423， 该氮气 弹簧的自由端顶住复位销钉 421的运动端， 通过复位销钉 421顶住旋阀体 往滚动活塞轮 430外圆柱表面复位密封。 氮气弹簧有密封好， 力量大， 寿 命长的特点， 作为标准件， 一旦损坏也容易更换。 此时， 该销钉孔可以为 通孔， 通过氮气弹簧 423的末端将该销钉孔与气缸外侧密封。
图 11B 为根据本发明实施例转子式压缩机中第三种旋阀体复位机构 的结构示意图。如图 11B所示， 用高压气通道 424把高压压缩介质排出口 404 处的经过压缩后的高压气体引入阀片复位销钉上方的装有压缩弹簧 425的销钉孔。 该高压气体作为弹性元件可以保证有足够的气体压力压住 复位销钉 421， 并使旋阀体末端始终与滚动活塞轮 430外圆柱表面复位密 封。此处，压缩弹簧 425只用于在高压气缸内无压力时顶住阀片复位销钉。 在能够保证在高压气缸内无压力时也能可靠顶住阀片复位销钉的前提下， 该压缩弹簧 425可以省略。 优选地， 在压缩机高压压缩介质排出口 404和 高压气通道 424之间设置压力调节装置， 例如单向阀或调压阀， 从而可以 保证阀片复位销钉上方的销钉孔内压力的基本恒定。
本实施例转子式压缩机通过旋阀体复位销钉在密封滑动条件下工作， 通过它把复位压力传至旋阀体头部， 从而提升了转子式压缩机中复位弹簧 的使用寿命和可靠性， 从而提供了一种高可靠性、 实用的压缩机。
通过上述说明， 已经完整介绍了本实施例转子式压缩机各部分的构 造。以下将介绍本实施例转子式压缩机的三个工作冲程 -吸气冲程、一级压 缩冲程和二级压缩冲程：
吸气冲程，如图 12A所示，滚动活塞轮位于圆筒状内腔最上方的位置， 从而将旋阀体完全压入容放凹槽内，销钉位于销钉孔的最内侧位置。此时， 其直径与垂直向上的方向呈 0°，滚动活塞轮外圆柱面和缸体的内圆筒面所 围成的压缩腔最大， 该压缩腔与压缩机的吸气口相连接， 从而将气态的压 缩介质吸入该压缩腔；
一级压缩冲程， 如图 12B所示， 滚动活塞轮偏心沿缸体内表面密封滚 动， 要过了吸气口之后才能开始压缩。 旋阀体首先逐渐打开， 而后又慢慢 闭合， 与之相对应， 销钉在销钉孔内先伸出而后又缩回。 随着滚动活塞轮 在缸体内表面的密封滚动， 压缩腔的体积越来越小， 如图 12C所示， 滚动 活塞轮位于圆筒状内腔最下方的位置， 过了此点后， 到达如图 12D所示位 置， 该压缩腔内的气体被压缩升压后逐渐进入旋阀体上方的气缸；
二级压缩冲程， 如图 12E, 偏心滚轮外圆与缸体内圆的内切点在 270 度方位上， 这时内切点位置已接近终点位置， 滚动活塞轮偏心沿缸体内表 面密封滚动， 旋阀体快速闭合， 高压气体将单向截止阀片吹开， 气体被压 缩升压进入旋阀体上方的气缸后， 进一歩被旋阀体二次挤压进入高压储气 室。 终点位置如图 12A所示， 即旋阀体回到缸体槽的位置， 此时， 在所谓 二级压缩室（高压室） 内滞留的流体全部被挤入高压储气室， 并且在下来 的时间段里被图 2B所示的单向截止阀片所截流。
至此， 本实施例转子式压缩机介绍完毕。
此外， 本发明还提供了一种流体马达。 该流体马达的构造与上述的转 子式压缩机类似， 区别仅在于出入口设计及相应流体的方向的不同。图 13 为根据本发明实施例流体马达的截面示意图。请参照图 13，转动装置的第 二腔室， 即做功腔 530， 通过第二组通孔与高压流体进口 510相连通； 第 一腔室， 即排出腔 540， 通过第一组通孔与低压流体出口 520相连通。 高 压流体推动偏心转子转动， 通过主轴将产生的扭矩传递至圆筒形内腔外。 此外， 需要注意的是， 在高压流体进口 510和第二组通孔之间， 并没有如 图 2B所示的开闭阀， 从而高压流体能够源源不断流入。 该高压流体可以 为液体或者气体。
以下将介绍本实施例流体马达的工作流程： 高压流体从高压流体进口 510流入， 通过第二组通孔进入做功腔， 沿逆时针方向推动偏心转子 300 组件自转并公转， 该偏心转子组件 300的公转带动主轴 200转动； 当偏心 转子组件经过其最上端之后， 进入下一个冲程， 做功后的流体通过第一组 通孔流出至低压流体出口 520。
至此， 本实施例流体马达介绍完毕。
依据以上对转子式压缩机和流体马达的描述， 本领域技术人员应当对 本发明的转动装置有了清楚的认识。
综上所述， 本发明转动装置及应用其的转子式压缩机和流体马达中， 偏心轴和滚动活塞轮之间采用滚动轴承方式， 通过弹性预紧力实现缸体的 可靠密封， 同时， 对旋阀体和旋阀体复位机构进行了改进， 从而提供了一 种高可靠性、 可大型化的流体机械。 需要注意的是， 出于简单明了表示图中元件的目的， 图中元件并不一 定是按照严格比例进行绘制的。 此外， 以上对本发明的多处特征及有益效 果给予了说明， 但关于该发明的结构和功能方面的细节描述仅是为了披露 阐释的需要， 其各种细节上的变换也应落在本发明的保护范围之内， 特别 是关于该发明的形状、 尺寸和零部件的排列布置等， 均应落在本说明书所 附权利要求所表达的发明精神囊括范围之内。 此外， 以下实施例中提到的 方向用语， 例如 "上"、 "下"、 "前"、 "后"、 "左"、 "右"等， 仅是参考附 图的方向。 因此， 使用的方向用语是用来说明并非用来限制本发明。
以上所述的具体实施例， 对本发明的目的、 技术方案和有益效果进行 了进一歩详细说明， 所应理解的是， 以上所述仅为本发明的具体实施例而 已， 并不用于限制本发明， 凡在本发明的精神和原则之内， 所做的任何修 改、 等同替换、 改进等， 均应包含在本发明的保护范围之内。

Claims

权 利 要 求
1、 一种转动装置， 其特征在于， 包括：
缸体；
前端盖和后端盖， 密封连接于所述缸体的前端和后端， 其与所述缸体 共同限定一圆筒形内腔；
主轴， 由所述缸体和 /或前、后端盖可转动地支撑， 部分地位于所述圆 筒形内腔内， 其中心轴线与所述圆筒形内腔的中心轴线重合；
偏心转子组件， 套设于所述主轴位于圆筒形内腔的部分， 包括： 偏心轴， 套设于所述主轴位于圆筒状内腔的部分， 其中心轴线与 所述主轴的中心轴线相互平行且错开预设距离；
滚动活塞轮， 套设于所述偏心轴上， 其中心轴线与所述偏心轴的 中心轴线重合； 以及
至少一滚动轴承， 对称地套设于所述偏心轴上， 其内套圈固定于 所述偏心轴， 其外套圈固定于所述滚动活塞轮， 以隔绝两者的转动， 该至 少一个滚动轴承与所述滚动活塞轮之间的预紧弹性力将所述滚动活塞轮 压紧于所述圆筒形内腔的内圆筒面， 使所述圆筒形内腔的内圆筒面和滚动 活塞轮的外圆柱面之间形成轴向延伸的密封腔室； 以及
隔离机构， 其将所述密封腔室分隔为相互独立的第一腔室和第二腔 室， 该第一腔室和第二腔室分别与设置在缸体上的第一组通孔和第二组通 孔相连通。
2、 根据权利要求 1 所述的转动装置， 其特征在于， 所述至少一滚动 轴承与所述滚动活塞轮之间采用过盈配合， 该过盈配合产生所述的预紧弹 性力。
3、 根据权利要求 1 所述的转动装置， 其特征在于， 所述滚动活塞轮 的内圆筒面和滚动轴承的外圆柱面两者之一上开设相对于滚动轴承滚动 体沟槽径向中心线对称分布的一条或多条镶嵌槽；
所述偏心转子组件还包括： 一个或多个弹性预紧元件， 分别嵌设于所 述镶嵌槽内， 其在不受力的状态下的高度大于所述镶嵌槽的深度， 该一个 或多个弹性预紧元件产生所述预紧弹性力。
4、 根据权利要求 3所述的转动装置， 其特征在于， 所述镶嵌槽为多 条， 该多条镶嵌槽相对于滚动轴承滚动体沟槽径向中心线对称分布；
所述弹性预紧元件为： 0型弹性橡胶圈或多股细金属丝网做成的弹性 圈，该 0型弹性橡胶圈或多股细金属丝网做成的弹性圈分别嵌设于所述多 条镶嵌槽中。
5、 根据权利要求 3所述的转动装置， 其特征在于， 所述镶嵌槽开设 于所述滚动活塞轮的内圆筒面。
6、 根据权利要求 5所述的转动装置， 其特征在于， 所述镶嵌槽为一 条， 该条镶嵌槽相对于滚动轴承滚动体沟槽径向中心线对称分布；
所述弹性预紧元件为： 矩形弹性橡胶圈， 该矩型弹性橡胶圈嵌设于所 述镶嵌槽中。
7、 根据权利要求 6所述的转动装置， 其特征在于， 所述矩形弹性橡 胶圈伸出镶嵌槽的一侧带齿。
8、 根据权利要求 5所述的转动装置， 其特征在于， 所述镶嵌槽为一 条， 该条镶嵌槽相对于滚动轴承滚动体沟槽径向中心线对称分布；
所述弹性预紧元件为金属弹簧套圈； 所述金属弹簧套圈包括： 带有连 续 U字形光滑圆弧曲面拱起的弹簧片， 及支撑该弹簧片的刚性底座边沿， 该刚性底座边沿的直径可弹性缩小。
9、 根据权利要求 1所述的转动装置， 其特征在于， 所述偏心轴包括: 多个偏心轴肩， 分别与所述至少一滚动轴承其中之一相对应， 设置于 套设滚动轴承的偏心轴位置；
平衡配重， 设置于两个偏心轴肩之间， 沿所述偏心轴对称设置， 以平 衡所述偏心轴的配重。
10、根据权利要求 9所述的转动装置， 其特征在于，所述平衡配重为： 平衡块， 设置于所述偏心轴的较轻侧， 以增加该较轻侧的配重； 或 配重缺口或配重孔， 设置于所述偏心轴的较重侧， 以减轻该较重侧的 配重。
11、 根据权利要求 1所述的转动装置， 其特征在于， 所述缸体主体上 开设轴向延伸的、 朝向内腔敞开的容放凹槽； 所述隔离机构包括：
旋阀体， 配装在该容放凹槽内并由该容放凹槽可转动的支撑， 使得旋 阀体在预定的角度范围内摆动， 包括：
连接部， 位于所述旋阀体的根部， 与所述容放凹槽铰接； 旋阀体本体， 以所述连接部为轴， 在预定的角度范围内摆动； 旋阀体复位机构， 用于将旋阀体的末端始终压设于滚动活塞轮的外圆 柱面， 以将所述密封腔室分隔为相互独立的第一腔室和第二腔室， 旋阀体 从容放凹槽内摆出时， 其正面朝向的腔室为第二腔室， 其背面朝向的腔室 为第一腔室。
12、 根据权利要求 11 所述的转动装置， 其特征在于， 所述旋阀体整 体采用减磨材料或至少所述旋阀片本体与滚动活塞轮相接触的表面镀减 磨材料。
13、 根据权利要求 11 所述的转动装置， 其特征在于， 所述旋阀体还 包括：
摆动密封滑头， 铰接于所述旋阀体末端， 其与所述滚动活塞轮的接触 面为贴紧所述滚动活塞轮并可在所述滚动活塞轮表面滑动的密封圆弧面。
14、 根据权利要求 13所述的转动装置， 其特征在于， 摆动密封滑头 与所述滚动活塞轮接触的底部面上开设有流体静压轴承压力腔。
15、 根据权利要求 13所述的转动装置， 其特征在于， 所述旋阀体本 体的末端具有滑动圆柱孔；
所述摆动密封滑头的头部呈圆柱形， 该圆柱形头部可摆动的包覆制约 定位于旋阀体本体末端的滑动圆柱孔内。
16、 根据权利要求 11 所述的转动装置， 其特征在于， 所述容放凹槽 内设置具有圆弧缺口的滑动圆柱孔； 所述旋阀体中：
所述连接部为支撑圆柱， 该支撑圆柱插入所述滑动圆柱孔内， 受到滑 动圆柱孔的包覆制约定位；
旋阀体本体， 以所述支撑圆柱为轴， 在预定的角度范围内摆动。
17、 根据权利要求 11 所述的转动装置， 其特征在于， 所述旋阀体复 位机构包括：
销钉孔， 开设于所述容放凹槽底部， 侧对所述旋阀体本体的位置， 其 与缸体外部隔绝密封；
复位销钉， 可滑动地插入所述销钉孔内； 弹性件， 位于所述复位销钉内侧的销钉孔内， 其末端抵接于所述复位 销钉的尾部， 产生的弹性力使复位销钉的头部沿朝向滚动活塞轮的方向顶 住旋阀体本体。
18、 根据权利要求 17所述的转动装置， 其特征在于， 所述销钉孔的 中心轴线与所述容放凹槽的垂线之间的夹角介于 5°至 30°之间；
所述销钉孔与所述旋阀体的接触点为： 自旋阀体压住滚动活塞轮一端 开始， 旋阀体长度的 1/5至 1/2处。
19、 根据权利要求 17所述的转动装置， 其特征在于， 所述销钉孔为 盲孔， 所述弹性件为：
压缩弹簧， 位于所述销钉孔内， 其一端抵接于销钉孔的底部， 其另一 端抵接于所述复位销钉的尾部。
20、 根据权利要求 17所述的转动装置， 其特征在于， 所述弹性件为： 氮气弹簧；
该氮气弹簧位于所述销钉孔内， 其一端将圆筒形内腔与缸体外部隔绝 密封， 其另一端抵接于所述复位销钉的尾部。
21、 根据权利要求 17所述的转动装置， 其特征在于， 所述复位销钉 可滑动密封的插入所述销钉孔内；
所述复位销钉内侧的销钉孔空间通过气通道与所述转动装置的第二 腔室相连通， 所述弹性件为进入所述销钉孔内的压缩气体或高压流体。
22、 根据权利要求 21 所述的转动装置， 其特征在于， 所述销钉孔与 所述高压室之间设置气压调节装置。
23、 根据权利要求 21 所述的转动装置， 其特征在于， 所述复位销钉 内侧的销钉孔空间还设置有压缩弹簧。
24、 根据权利要求 1至 23中任一项所述的转动装置， 其特征在于， 所述偏心转子组件还包括：
两侧面密封片， 对称设置于所述滚动活塞轮的两侧；
密封片弹性胶圈， 设置于所述侧面密封片和外侧缸体之间， 以使所述 侧面密封片紧压住所述滚动活塞轮的外侧， 实现密封。
25、 根据权利要求 1至 23中任一项所述的转动装置， 其特征在于： 所述滚动轴承为滚柱轴承、 滚球轴承、 滚针轴承、 空气动力学滚动轴 承或复合轴承；
所述滚动轴承的数量为 1组、 2组、 3组、 4组， 每组包括沿圆筒形内 腔左右对称设置的两个滚动轴承。
26、 一种转子式压缩机， 其特征在于， 包括权利要求 1至 25中任一 项所述的转动装置， 其中：
所述第一腔室通过第一组通孔与低压压缩介质输入口相连通； 所述第二腔室通过第二组通孔与压缩后高压压缩介质的排出口相连 通；
所述主轴将圆筒形内腔外的扭矩传递至圆筒形内腔内， 通过所述偏心 转子组件以对所述压缩介质进行压缩。
27、 一种流体马达， 其特征在于， 包括权利要求 1至 25中任一项所 述的转动装置， 其中：
所述第二腔室通过第二组通孔与高压流体进口相连通；
所述第一腔室通过第一组通孔与低压流体出口相连通；
所述高压流体推动所述偏心转子转动， 通过所述主轴将产生的扭矩传 递至所述圆筒形内腔外。
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