Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
  • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
• • 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
  • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
  • F04C29/02—Lubrication; Lubricant separation
  • F04C29/028—Means for improving or restricting lubricant flow

Definitions

• the present invention relates to a scroll type compressor.
• FIG. 1 is a longitudinal sectional view of a conventional scroll electric compressor, which is disclosed in Japanese Patent Application Laid-Open No. 1-177482, "Scroll Compressor".
• a compression unit 102 is provided inside a closed container 101, and a motor 103 is provided above the compression unit 102, and a main body frame 105 of the compression unit 102 supporting a drive shaft 104 driven by the motor 103;
• a discharge compressor oil reservoir 106 provided between the frame 105 and the motor 103 constitutes a scroll compressor.
• the oil in the discharge chamber oil reservoir 106 provided between the motor 103 and the body frame 105 passes through the oil hole 107 provided in the body frame 105.
• the minute space in the sliding portion has large variations in manufacturing, making it difficult to control the intermediate pressure with high accuracy and to increase the oil flow rate.
• the efficiency of the compressor may be affected, and if the amount becomes large, oil may be compressed and the compression section 102 may be destroyed.
• the present invention enables high-precision control of the oil flow rate, which is a problem of conventional scroll compressors, to improve the efficiency and reliability of the compressor, and to simplify these components. It is about to achieve this.
• a compressor mechanism driven by an electric motor or another drive mechanism is provided, and the compression mechanism is provided with a fixed spiral blade part having a fixed spiral blade formed on a fixed frame, and the fixed spiral blade.
• the swirl vane component that fixes or forms the swirl vanes forming a plurality of compression working spaces on the swivel head plate, and the rotation constrains that only the swirl vane components prevent the self-rotation and turn only Parts, a crankshaft for rotating the spiral blade parts by the power of the electric motor or another driving mechanism, and a bearing part having a main bearing for supporting the main shaft of the crankshaft.
• the structure is such that the pressure on the discharge side acts on the oil reservoir for storing the lubricating oil.
• the pressure on the back side of the swivel head opposite to the swirling vanes of the swivel head is equal to or higher than the suction side pressure of the compression mechanism.
• a back pressure chamber of the body pressure acts to form a pivot drive shaft to the rear the orbiting end plate, and engaging the pivot drive shaft and the eccentric drive bearing of the click run-click axis the swing Slidably between the space where the discharge pressure is applied by the lubricating oil of the oil reservoir provided between the rear surface of the head plate and the bearing component around the turning drive shaft and the back pressure chamber in the outer peripheral direction
• the purpose is to provide a communication hole or gap that communicates with the working space.
• FIG. 1 is a vertical cross section of a conventional scroll compressor
• Fig. 2 is a cross section of an embodiment of a scroll-compressor according to the present invention
• Fig. 3 is a cross-sectional view of a scroll-compressor according to the present invention
• FIG. 4 is a detailed cross sectional view of the drawing resistance component.
• FIG. 2 shows an embodiment of the scroll compressor of the present invention.
• a compression mechanism 2 and a stator 4 of a motor 3 for driving the compression mechanism 2 are fixed in a closed container 1, and a lubricating oil reservoir 5 is provided below the motor 3.
• Compression mechanism 2 Fixed swirl vane component 8 having fixed swirl vanes 7 formed integrally with fixed frame 6, and swirl swirl forming a plurality of compression work spaces 9 by engaging with fixed swirl vanes 7
• the swirl vane part 12 having the winding vane 10 formed on the swivel end plate 11, the rotation restricting part 13 which prevents the swirl vane part 12 from rotating, and only turns.
• a crankshaft 16 having an eccentric drive bearing 15 for eccentrically rotating a swing drive shaft 14 provided on the back of the end plate 11 and a main shaft 17 of the crankshaft 16 are connected to the motor 3. It is composed of a bearing part 20 having a main bearing 19 supported below the rotor 18. The upper end of the crankshaft 16 penetrates into the ball bearing 22 fixed to the partition 21 and the partition 21 is the stator of the motor. The space above the rotor 4 and the rotor 18 is partitioned into a motor-side space 23 and a discharge chamber 24.
• the bearing component 20 is provided with a thrust bearing 25 that receives the axial load of the crankshaft 16.
• the discharge space 31 passes through a communication hole (not shown) penetrating the fixed spiral blade part 8 and the bearing part 20, and exits upward through a passage 33 around a crank shaft 32, and the stator 4 of the motor 3 Through the communication passage 34 provided around the stator 4, it is guided to the motor side space 23 above the stator 4, passes through the passage hole 35, enters the discharge chamber 24, and is discharged from the discharge pipe 36 to the outside of the compressor.
• a structure in which the pressure on the discharge side acts on the oil reservoir 5 for storing the lubricating oil is provided.
• the lubricating oil in the oil reservoir 5 is supplied to a main bearing 19 supporting a main shaft 17 of the crankshaft 16 as shown by an arrow through an oil supply hole 36 provided in the bearing component 20.
• the eccentric drive bearing 15 of the crank shaft 16 is engaged with the eccentric drive bearing 15 at a substantially central portion of the back surface 37 of the slewing plate 11 provided on the slewing head plate 11 to form the slewing drive shaft 14.
• a sliding seal ring 40 that slidably partitions between a space 38 around the turning drive shaft 14 and a back pressure chamber 39 provided on the outer periphery of the turning head 11 is disposed between the bearing component 20 and the bearing component 20. I have.
• the lubricating oil that has lubricated the main bearing 19 flows into the surrounding space 38, lubricates the eccentric drive bearing 15 and reaches the end space 41 of the fighter turning shaft 14.
• the end space 41 and the center of the turning drive shaft 14 are further extended in the axial direction.
• a throttling resistance component for controlling the oil flow to a communication hole A42 for communicating the plate 11 with the back pressure chamber 39 through the radial direction, and to a hole B43 of the communication hole A42 in the axial direction of the turning drive shaft 14. 44 are provided.
• the communication hole A42 supplies the lubricating oil to the compression work space 9 to the communication hole A42, and the lubricating oil of the back pressure chamber 39 is supplied to the other compression work space 9 of the compression work space 9.
• Communication hole B46 is provided.
• the pressure in the surrounding space 38 is slightly lower than the pressure of the discharged refrigerant due to the flow resistance of the lubricating oil passing through the main bearing 15, but almost equal to the discharge pressure.
• the pressure of the lubricating oil in the back pressure chamber 39 is given a flow resistance by the throttle resistance component 44, the flow rate is controlled, and further communicated with the compression work space 9 through the communication hole B46.
• the pressure is reduced by the pressure of the lubricating oil in the surrounding space 38.
• the fluid pressure is the same as or larger than the suction side pressure and smaller than the pressure of the surrounding space 38.
• the resistance of the communication hole # 46 is set to be smaller than the resistance of the aperture resistance component 44. In this way, the flow rate of the lubricating oil is controlled by the throttle resistance component 44 ⁇
• the passage resistance can be made larger than in a small space in the sliding part of the bearing, and the flow rate is low and the accuracy is high
• the passage resistance value can be set, and the supply amount of the lubricating oil to the compression working space 9 can be prevented from increasing.
• FIG. 3 shows another embodiment.
• the components having the same reference numerals as those in FIG. 2 have the same functions, and differ from the configuration in that the drawing resistance component 44 is provided on the bearing component 20.
• the lubricating oil in the oil reservoir 5 flows through the oil supply hole 36 provided in the bearing component 20 into the space 38 around the turning drive shaft 14, is separated by the lid, and one is forward as shown by the arrow. While lubricating the main bearing 19 supporting the main shaft 17 of the crankshaft 16, the lubrication of the eccentric drive bearing 15 and the hole through the end space 41 of the turning shaft 14 are performed. Return to sump 5 from 47.
• the bearing component 20 is provided with a communication hole C48 for communicating with the back pressure chamber 39, and the communication hole C48 is provided with a throttle resistance component 44 for controlling an oil flow rate.
• a communication hole C49 for supplying the lubricating oil of the back pressure chamber 39 to the compression working space 9 through the turning head plate 11 in the radial direction is provided at a symmetrical position.
• the operation and effect of this embodiment are the same as those of the embodiment shown in FIG.
• FIG. 4 shows details of an embodiment of the aperture resistance component used in the embodiment of the present invention shown in FIGS. 2 and 3.
• the aperture resistance component 44 is composed of a thin tube 50 made of stainless steel or a copper material, and a member 52 to be screw-fixed to the communication hole A42 or the communication hole C48 with the screw portion 51.
• Reference numeral 50 denotes a mouthpiece 53, and the member 52 is provided with a hexagonal hole 54 which is tightened to the communication hole by a hexagonal wrench (not shown).
• the lubricating oil is depressurized when passing through the capillary tube 50 and its flow rate is controlled.
• the capillary tube 50 can be manufactured to a highly accurate resistance value.
• the force with the crank axis provided in the vertical direction is the horizontal direction, that is, even if the compressor is of the horizontal type, the lubricating configuration is the differential pressure lubrication structure ⁇
• the operation and effect are the same .
• the motor drive is exemplified, an open type compressor driven by a drive shaft from outside of the sealed container may be used. The same effect can be achieved by using a fixing method such as press-fitting, etc., which restricts the throttle resistance component to the communication hole by screw tightening.
• crank shaft may be configured to be supported at both ends or may be supported at one end.
• Force for engaging the eccentric drive bearing of the link shaft with the turning drive shaft A turning drive bearing is formed on the back of the turning head plate, and an eccentric drive shaft is provided at the tip of the crank shaft to engage the turning drive bearing. This does not depart from the content of the present invention.
• the throttle resistance component is constituted by a thin tube and a member for fixing the narrow tube to the communication hole.

Landscapes

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

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=17711901

Family Applications (1)

Country Status (4)

Cited By (3)

Families Citing this family (5)

Citations (4)

Family Cites Families (6)

• 1989
  • 1989-11-02 JP JP1287013A patent/JP2538078B2/ja not_active Expired - Lifetime
• 1990
  • 1990-11-02 WO PCT/JP1990/001415 patent/WO1991006767A1/ja unknown
  • 1990-11-02 KR KR1019910700663A patent/KR950013893B1/ko not_active IP Right Cessation
  • 1990-11-02 DE DE4092017A patent/DE4092017C1/de not_active Expired - Fee Related

Patent Citations (4)

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