WO2003074880A1 - Double compressor having planetary rotors - Google Patents

Double compressor having planetary rotors Download PDF

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Publication number
WO2003074880A1
WO2003074880A1 PCT/KR2003/000403 KR0300403W WO03074880A1 WO 2003074880 A1 WO2003074880 A1 WO 2003074880A1 KR 0300403 W KR0300403 W KR 0300403W WO 03074880 A1 WO03074880 A1 WO 03074880A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
planetary
compression chamber
gas
vane
Prior art date
Application number
PCT/KR2003/000403
Other languages
French (fr)
Inventor
Bong-Hyun Cho
Original Assignee
Bong-Hyun Cho
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 Bong-Hyun Cho filed Critical Bong-Hyun Cho
Priority to AU2003212670A priority Critical patent/AU2003212670A1/en
Publication of WO2003074880A1 publication Critical patent/WO2003074880A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner 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
    • F04C18/34—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 relative reciprocation between the co-operating members
    • F04C18/344—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C18/34—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 relative reciprocation between the co-operating members
    • F04C18/344—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C23/005—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 dissimilar working principle
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to a double compressor having planetary rotors, and more particularly to a double compressor having planetary rotors, wherein a first compressed gas can be high-effectively compressed with a second compression by using trochoid and vane in a vane compression structure.
  • a vane compressor comprises a cylinder and a rotor, which is provided eccentrically inside the cylinder and provided with a plurality of vanes on the circumference.
  • the vanes protrude in the circumferential direction with centrifugal force caused by this revolution while making contact with the inner diameter of the cylinder to accomplish gaseous compression.
  • a rotor revolves and a plurality of vanes imbedded in the circumferential direction of the rotor protrude from the groove portion by centrifugal force and the tips of vanes give pressure to make contact with the inner diameter of the cylinder, and the suction space forms a vacuum to inhale coolant through a suction passage, and the inhaled coolant is compressed and discharged through a channel in the discharge portion.
  • the conventional vane compressor there is a problem of producing pulsation and chattering since higher pressure inside the cylinder can make contact unstable between the vanes and the inner diameter of the cylinder by the pressure developed between the tips of vanes and non-contact surfaces of the inner diameter of the cylinder.
  • the bearing portion is separately provided to reduce friction force against the inner diameter of the cylinder, while revolving the vanes that are formed at planetary rotors, and the inner diameter of the cylinder contacted by the vanes is revolving together with the planetary rotors, thereby minimizing heat and abrasion in the inner diameter of the cylinder.
  • the present invention is provided to solve these problems as described above, and it is an object of the invention to provide a double compressor, wherein a trochoid curved surface and a vane are provided in the circumference of the inner rotor that revolves by power supplied from the initial rotary axis, a planetary rotor tooth-combined with the trochoid curved surface of the inner rotor in the outside of the inner rotor is provided, and another vane in the circumference of the planetary rotor is provided, while providing an outer rotor in the outside of the planetary rotor. So, gas is first compressed between the outer rotor and the planetary rotor, and then second compressed between the planetary rotor and the inner rotor to accomplish high-efficient compression.
  • a double compressor comprises a housing, wherein a suction passage is formed at one side and a discharge passage is formed at the other side; a first rotor supported by metal bearings inside the housing; a planetary rotor provided eccentrically inside the first rotor, wherein a first suction chamber that is connected with the suction passage and a first compression chamber that the gas inhaled into the first suction chamber is compressed are provided against the first rotor and the inner circumference is formed with a trochoid curved surface; a plurality of first vanes provided in the outer circumference of the planetary rotor, wherein gas is first compressed in the first compression chamber when the planetary rotor revolves in the inner circumference of the first rotor; a second rotor having a trochoid curved surface provided on the same axis with the first rotor inside the planetary rotor, as well as tooth-combined with the trochoid curved surface of the planetary rotor
  • the number of trochoid curved surface gear of the second rotor is one less than the number of the trochoid curved surface gear of the planetary rotor.
  • a back pressure groove that compressed gas flows is formed at a portion located in the outside of the compression chamber of the first rotor within the inner circumference of the metal bearing.
  • first vane grooves are formed at a portion that the first vane of the first planetary rotor is provided, a plurality of second vane grooves being formed at a portion that the second vane of the second planetary rotor is provided, and the first vane groove and the second vane groove are connected with the first compression chamber.
  • a cover plate is provided at one end and at the other end of the first rotor, the planetary rotor and the second rotor inside the housing.
  • the cover plate is formed with a first suction opening that is connected with the first suction chamber and becomes wider when going further in the revolution direction of the planetary rotor, a first discharge opening that is connected with the first compression chamber and becomes narrower when going further in the revolution direction of the planetary rotor, a second suction opening that is connected with the second suction chamber and becomes wider when going further in the revolution direction, and a second discharge opening that is connected with the second compression chamber and the compressed coolant is discharged into the discharge passage.
  • the second discharge opening is formed together with a cutting hole, which is cut, opened and extended respectively in the anti-revolution direction of the second rotor to prevent from being clogged by the trochoid gear portion of the second rotor when the second rotor revolves.
  • FIG. 1 is a side-sectional view showing a double compressor having planetary rotors according to the invention.
  • FIG. 2 is a plane-sectional view showing the double compressor having planetary rotors according to the invention.
  • FIG. 3 is a plane view showing a cover plate that is provided in the double compressor having planetary rotors according to the invention.
  • FIG. 4 is a projective view showing a vane that is provided in the double compressor having planetary rotors according to the invention.
  • FIG. 5 is a cross-sectional view showing a ring that is provided in the double compressor having planetary rotors according to the invention.
  • the double compressor using planetary rotors includes a housing 10, which is formed with a suction passage 15 for inhaling gas at one side and a discharge passage 16 for discharging compressed gas at the other side with a shape substantially like a cylinder.
  • a plurality of rotors 50, 60 and 70 as described later are installed at one side of the housing opened, and a rotary axis 12 passing through the housing for revolving the rotors 50, 60 and 70 is provided, which is supported by bushes 18. And a cover 11 combined with one side of the housing opened, for sealing the interior, is combined with a fastening bolt 17.
  • three rotors 50, 60 and 70 as shown above, are provided eccentrically one after another in the outer circumference of the rotary axis 12.
  • a first rotor 50 is provided at the outside, and a planetary rotor 60 is provided inside the first rotor 50, and a second rotor 70 is provided inside the planetary rotor 60.
  • a metal bearing 21 is provided between the first rotor 50 and within the housing 10 to support the first rotor 50 to make its revolution possible.
  • two cover plates 30 and 40 are provided at either side of each rotor 50, 60 and 70, which are formed with a plurality of suction openings 31 and 32 and a plurality of discharge openings 33 and 34, for guiding gas that flows in and out between them.
  • a first suction chamber 80 for inhaling gas is formed at the portion where the gap against the first rotor 50 installed eccentrically inside the planetary 60 becomes wider.
  • a first compression chamber 81 for compressing the inhaled gas is formed at the portion where the gap against the first rotor 50 becomes narrower.
  • a separate back pressure groove 21a is formed at the inner circumference surface of the metal bearing 21 positioning at the place corresponding to the first compression chamber 81, and this back pressure groove 21a functions as a pressure buffer against the interior pressure of the first compression chamber 81.
  • the cover plates 30 and 40 as shown in FIG. 3, moreover, it is formed with a first suction opening 31 which is connected to the first suction chamber 80.
  • gas being inhaled from the first suction opening 31 and compressed at the first compression chamber 81, is accomplished by a plurality of first vanes 62 provided in the outer circumference of the planetary rotor 60, and a plurality of first vane grooves 61 are formed in the outer circumference of the planetary rotor 60 for providing these first vanes 62.
  • Gas discharged from the first compression chamber 81 flows into the first vane grooves 61, and a separate first back pressure chamber port 35 is formed in the cover plates 30 and 40 for this purpose.
  • the first vane 61 protrudes by centrifugal force resulted from the revolution of the planetary rotor 60 and the compressed gas that is inhaled into the first vane groove 61, and revolves in the inner circumference of the first rotor 50 at the state of zero slip while making contact with it.
  • the inner circumference surface of the planetary rotor 60 is formed with a trochoid curved surface having seven gear tooth profiles
  • the inside of the planetary rotor 60 is provided by a second rotor 70, which is tooth combined with the trochoid curved surface of the planetary rotor 60 and formed with a trochoid curved surface having six gear tooth profiles in the outer circumference, one less than the number of tooth profiles of the planetary rotor 60.
  • This second rotor 70 is fixed by a key 19 at the rotary axis 12 that is installed in the housing 10, and the planetary rotor 60 is tooth combined eccentrically with the outer circumference of this second rotor 70.
  • a separate second vane groove 71 is formed in the outer circumference of this second rotor 70 at each end of every gear, and a second vane 72 is provided in this second vane groove 71 respectively.
  • gas discharged from the first compression chamber 81 flows into the second vane grooves 61, and a separate second back pressure chamber port 36 is formed in the cover plates 30 and 40 for this purpose.
  • a second suction chamber 90 that the gap becomes wider when going further in the revolution direction, is formed between the planetary rotor 60 and the second rotor 70, which is tooth combined in the state of a trochoid curved surface as described above, on the other hand, a second compression chamber 91 is fo ⁇ ned at the portion where the gap becomes narrower.
  • a second suction opening 32 and a second discharge opening 34 are formed in the cover plates 30 and 40 corresponding to these.
  • the second suction opening 32 is connected with the aforementioned first discharge opening
  • the second discharge opening 34 has a shape for functioning of an orifice valve as shown in FIG. 3.
  • the shape in detail is set up in proportion to the volume and speed, being reduced by compression according to the compression rate of the second compression chamber 91, and this second discharge opening 34a is formed with a slit, being cut and opened at a predetermined size in both directions of revolution and anti-revolution of the second rotor 70, for the second discharge opening 34 to operate as a valve to maintain constant pressure inside the second compression chamber 91.
  • the second discharge opening 34 will not be completely blocked due to the revolution of the second rotor 70 to prevent compression pressure from being instantly high in the second compression chamber 91, thereby, compressed and discharged gas, maintaining constant pressure at all times.
  • the pressure added to the first suction chamber 80 by the second compression chamber 91 maintains substantially same as the pressure added to the second suction chamber 90 by the first compression chamber 81, to prevent chattering due to their pressure difference and vibration and noise due to gas pulsation, when the planetary rotor 60 revolves.
  • a separate reservoir is provided to increase compression efficiency of second compressed gas by radiating a part of compression heat of first compressed gas between the first compression chamber 81 and the second suction chamber 90 inside the housing 10.
  • This reservoir can be provided inside the housing 10, or separately installed outside the housing 10.
  • a ring 13 and a ring-shaped plate spring 14 is installed to make compression possible with high pressure and high efficiency.
  • both a first vane 62 and a second vane 72 are formed with the same constituent. As shown in FIG.4, it is formed with a left vane piece 63 and a right vane piece 64, being divided into left and right, as well as an insertion piece, being inserted through the bottom of these two vane pieces 63 and 64.
  • the constituent of these vanes 62 and 72 is described in the Utility Model No. 1997- 5930, which has been filed and registered by this applicant.
  • a second rotor 70 begins revolving first when external power initially supplied to a rotary axis 12 to start the rotary axis 12 revolving, and a planetary rotor 60 begins eccentric revolving, which is tooth combined with the outer circumference of the second rotor 70 in trochoid tooth profile.
  • a first vane 62 and a second vane 72 which are provided respectively at the planetary rotor 60 and the second rotor 70, protrude outward by centrifugal force that is produced at the time of revolution, and by pressure of compressed gas that is transferred to the respective vane grooves 61 and 71.
  • the first vane 62 it revolves together with a first rotor 50 at the state of zero slip while making contact with the inner circumference of the first rotor 50.
  • the second vane 72 it revolves at the state of zero slip while making contact with the inner circumference of the first rotor 60.
  • the initial gas is inhaled through a suction chamber 80.
  • the inhaled gas is guided by the first vane 62 and transferred to a first compression chamber 81.
  • the gas is first compressed, and then discharged through a first discharge opening 33 of the cover plates 30 and 40.
  • a part of the discharged gas is supplied to a back pressure groove 21a of a metal bearing 21, as well as the respective vane grooves 61 and 71, and all the rest is guided to a second suction chamber 90 between the planetary rotor 60 and the second rotor 70 through a second suction opening 32 of the cover plates 30 and 40.
  • gas guided to the second suction chamber 90 first passes through a reservoir, not shown in the drawing. In the reservoir, heat produced while being compressed in the first compression chamber 81 is dissipated, thereby increasing the efficiency of gaseous compression at the time of second compression.
  • the gas passed through the reservoir 20 is inhaled into the second suction chamber 90, and then guided by the second vane 72 to accomplish second compression in the second compression chamber 91. And the gas finished second compression at a certain pressure is discharged through a second discharge opening 34, and then finally discharged outward through a discharge passage 16 of the housing 10.
  • the double compressor according to the invention makes high-efficient compression possible through two-stage compression by using planetary rotors.
  • planetary rotors Basically, if other modifications make gas compression possible by providing a planetary rotor between two rotors and a vane in the planetary rotor and the second rotor positioning inside the planetary rotor, and if they are driven by combining the planetary rotor and the second rotor with a trochoid tooth profile, then it should be regarded within the technical scope of this invention.
  • the double compressor having planetary rotors according to the invention enables gas to have high-efficient compression at high pressure through two-stage compression cycle.
  • the planetary rotor for power transmission and the second rotor are combined with a trochoid tooth profile to accomplish power transmission and compression drive, so that there is an effect of minimizing abrasion due to friction at each portion of power transmission to improve durability of the compressor, as well as maintaining uniform pressure distribution remarkably when gas is inhaled and discharged to minimize vibration and noise of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

The present invention relates to a double compressor, and the double compressor comprises a housing, a first rotor supported by metal bearings inside the housing, a planetary rotor provided eccentrically inside the first rotor, wherein a first suction chamber and a first compression chamber are provided against the first rotor and the inner circumference is formed with a trochoid curved surface, a plurality of first vanes provided in the outer circumference of the planetary rotor, wherein gas is first compressed in the first compression chamber when the planetary rotor revolves; a second rotor having a trochoid curved surface provided on the same axis with the first rotor inside the planetary rotor, as well as tooth-combined with a trochoid curved surface of the planetary rotor to form a second suction chamber that the first compressed gas is inhaled and a second compression chamber that the gas inhaled into the second suction chamber is compressed; a second vane provided in the outer circumference of the second rotor, wherein the gas is second compressed and discharged into the discharge passage; and a rotary axis fixed at the center portion of the second rotor for revolving the second rotor.

Description

DOUBLE COMPRESSOR HAVING PLANETARY
ROTORS
TECHNICAL FIELD
The present invention relates to a double compressor having planetary rotors, and more particularly to a double compressor having planetary rotors, wherein a first compressed gas can be high-effectively compressed with a second compression by using trochoid and vane in a vane compression structure.
BACKGROUND ART
In general, a vane compressor comprises a cylinder and a rotor, which is provided eccentrically inside the cylinder and provided with a plurality of vanes on the circumference. For the operation, when the rotor revolves by external power source, the vanes protrude in the circumferential direction with centrifugal force caused by this revolution while making contact with the inner diameter of the cylinder to accomplish gaseous compression.
In the conventional vane compressor, a rotor revolves and a plurality of vanes imbedded in the circumferential direction of the rotor protrude from the groove portion by centrifugal force and the tips of vanes give pressure to make contact with the inner diameter of the cylinder, and the suction space forms a vacuum to inhale coolant through a suction passage, and the inhaled coolant is compressed and discharged through a channel in the discharge portion. ' In the conventional vane compressor, however, there is a problem of producing pulsation and chattering since higher pressure inside the cylinder can make contact unstable between the vanes and the inner diameter of the cylinder by the pressure developed between the tips of vanes and non-contact surfaces of the inner diameter of the cylinder.
Moreover, since a part of coolant that has been compressed and discharged is supplied to the bottom of vanes to bring the vanes into contact with the inner diameter of the cylinder, friction force between the tips of vanes and the inner diameter of the cylinder becomes large, thereby producing excessive heat or resulting in burn-on and abrasion, so that it may have a problem of reducing the life span of a compressor. When gas is excessively compressed at high pressure, furthermore, it may have a problem of deepening burn-on and abrasion due to friction between the tips of vanes and the inner diameter of the cylinder.
In order to solve these problems, a patent has been filed and registered by this applicant. The registered patent (the Korean Patent No. 182390) makes gas compression possible through two-stage compression cycle by using two-stage vane planetary rotors, thereby compressing the gas at higher pressure as compared with the conventional one-stage vane compressor.
At the same time, also, the bearing portion is separately provided to reduce friction force against the inner diameter of the cylinder, while revolving the vanes that are formed at planetary rotors, and the inner diameter of the cylinder contacted by the vanes is revolving together with the planetary rotors, thereby minimizing heat and abrasion in the inner diameter of the cylinder.
In the double vane compressor of this registered patent, however, there is a problem that the vanes do not properly protrude at low-speed revolution, and also there is another problem of producing excessive friction in the inner diameter of the cylinder, as each rotor revolves with friction force while making contact with the vanes.
Moreover, since the position of planetary rotors is not properly supported, chattering is produced, so the efficiency of compression is decreased, thereby producing a problem of inducing excessive noise.
DISCLOSURE OF THE INVENTION
The present invention is provided to solve these problems as described above, and it is an object of the invention to provide a double compressor, wherein a trochoid curved surface and a vane are provided in the circumference of the inner rotor that revolves by power supplied from the initial rotary axis, a planetary rotor tooth-combined with the trochoid curved surface of the inner rotor in the outside of the inner rotor is provided, and another vane in the circumference of the planetary rotor is provided, while providing an outer rotor in the outside of the planetary rotor. So, gas is first compressed between the outer rotor and the planetary rotor, and then second compressed between the planetary rotor and the inner rotor to accomplish high-efficient compression.
Related to the aforementioned object, it is another object of the invention to provide a double compressor, wherein the vanes provided in the inner rotor and the planetary rotor can protrude through pressure by the first compressed gas.
In order to accomplish the foregoing object of the invention, a double compressor comprises a housing, wherein a suction passage is formed at one side and a discharge passage is formed at the other side; a first rotor supported by metal bearings inside the housing; a planetary rotor provided eccentrically inside the first rotor, wherein a first suction chamber that is connected with the suction passage and a first compression chamber that the gas inhaled into the first suction chamber is compressed are provided against the first rotor and the inner circumference is formed with a trochoid curved surface; a plurality of first vanes provided in the outer circumference of the planetary rotor, wherein gas is first compressed in the first compression chamber when the planetary rotor revolves in the inner circumference of the first rotor; a second rotor having a trochoid curved surface provided on the same axis with the first rotor inside the planetary rotor, as well as tooth-combined with the trochoid curved surface of the planetary rotor to form a second suction chamber that the gas passed through the first compression chamber is inhaled at a gap against the planetary rotor, and a second compression chamber that the gas inhaled into the second suction chamber is compressed; a second vane provided at the end of the outer circumference of the second rotor, wherein the gas is second compressed and discharged into the discharge passage in the second compression chamber; and a rotary axis fixed at the center portion of the second rotor for revolving the second rotor eccentrically.
And it is preferable that the number of trochoid curved surface gear of the second rotor is one less than the number of the trochoid curved surface gear of the planetary rotor. Moreover, it is preferable that a back pressure groove that compressed gas flows is formed at a portion located in the outside of the compression chamber of the first rotor within the inner circumference of the metal bearing.
Moreover, it is preferable that a plurality of first vane grooves are formed at a portion that the first vane of the first planetary rotor is provided, a plurality of second vane grooves being formed at a portion that the second vane of the second planetary rotor is provided, and the first vane groove and the second vane groove are connected with the first compression chamber.
Moreover, it is preferable that a cover plate is provided at one end and at the other end of the first rotor, the planetary rotor and the second rotor inside the housing.
Moreover, it is preferable that the cover plate is formed with a first suction opening that is connected with the first suction chamber and becomes wider when going further in the revolution direction of the planetary rotor, a first discharge opening that is connected with the first compression chamber and becomes narrower when going further in the revolution direction of the planetary rotor, a second suction opening that is connected with the second suction chamber and becomes wider when going further in the revolution direction, and a second discharge opening that is connected with the second compression chamber and the compressed coolant is discharged into the discharge passage. Moreover, it is preferable that the second discharge opening is formed together with a cutting hole, which is cut, opened and extended respectively in the anti-revolution direction of the second rotor to prevent from being clogged by the trochoid gear portion of the second rotor when the second rotor revolves.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a side-sectional view showing a double compressor having planetary rotors according to the invention.
FIG. 2 is a plane-sectional view showing the double compressor having planetary rotors according to the invention. FIG. 3 is a plane view showing a cover plate that is provided in the double compressor having planetary rotors according to the invention.
FIG. 4 is a projective view showing a vane that is provided in the double compressor having planetary rotors according to the invention. FIG. 5 is a cross-sectional view showing a ring that is provided in the double compressor having planetary rotors according to the invention.
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, the preferred embodiments of a double compressor using planetary rotors according to the invention will be described in detail with the accompanying diagrams.
As illustrated in FIG. 1 and FIG. 2, the double compressor using planetary rotors according to the invention includes a housing 10, which is formed with a suction passage 15 for inhaling gas at one side and a discharge passage 16 for discharging compressed gas at the other side with a shape substantially like a cylinder.
Within this housing 10, a plurality of rotors 50, 60 and 70 as described later are installed at one side of the housing opened, and a rotary axis 12 passing through the housing for revolving the rotors 50, 60 and 70 is provided, which is supported by bushes 18. And a cover 11 combined with one side of the housing opened, for sealing the interior, is combined with a fastening bolt 17.
On the other hand, three rotors 50, 60 and 70 as shown above, are provided eccentrically one after another in the outer circumference of the rotary axis 12. A first rotor 50 is provided at the outside, and a planetary rotor 60 is provided inside the first rotor 50, and a second rotor 70 is provided inside the planetary rotor 60.
Here, a metal bearing 21 is provided between the first rotor 50 and within the housing 10 to support the first rotor 50 to make its revolution possible. And two cover plates 30 and 40 are provided at either side of each rotor 50, 60 and 70, which are formed with a plurality of suction openings 31 and 32 and a plurality of discharge openings 33 and 34, for guiding gas that flows in and out between them.
In the planetary rotor 60 provided inside the first rotor 50, on the other hand, a first suction chamber 80 for inhaling gas is formed at the portion where the gap against the first rotor 50 installed eccentrically inside the planetary 60 becomes wider. And a first compression chamber 81 for compressing the inhaled gas is formed at the portion where the gap against the first rotor 50 becomes narrower.
And a separate back pressure groove 21a is formed at the inner circumference surface of the metal bearing 21 positioning at the place corresponding to the first compression chamber 81, and this back pressure groove 21a functions as a pressure buffer against the interior pressure of the first compression chamber 81. In the cover plates 30 and 40, as shown in FIG. 3, moreover, it is formed with a first suction opening 31 which is connected to the first suction chamber 80.
Here, gas, being inhaled from the first suction opening 31 and compressed at the first compression chamber 81, is accomplished by a plurality of first vanes 62 provided in the outer circumference of the planetary rotor 60, and a plurality of first vane grooves 61 are formed in the outer circumference of the planetary rotor 60 for providing these first vanes 62. Gas discharged from the first compression chamber 81 flows into the first vane grooves 61, and a separate first back pressure chamber port 35 is formed in the cover plates 30 and 40 for this purpose. Accordingly, the first vane 61 protrudes by centrifugal force resulted from the revolution of the planetary rotor 60 and the compressed gas that is inhaled into the first vane groove 61, and revolves in the inner circumference of the first rotor 50 at the state of zero slip while making contact with it.
Moreover, the inner circumference surface of the planetary rotor 60 is formed with a trochoid curved surface having seven gear tooth profiles, and the inside of the planetary rotor 60 is provided by a second rotor 70, which is tooth combined with the trochoid curved surface of the planetary rotor 60 and formed with a trochoid curved surface having six gear tooth profiles in the outer circumference, one less than the number of tooth profiles of the planetary rotor 60. This second rotor 70 is fixed by a key 19 at the rotary axis 12 that is installed in the housing 10, and the planetary rotor 60 is tooth combined eccentrically with the outer circumference of this second rotor 70.
Furthermore, a separate second vane groove 71 is formed in the outer circumference of this second rotor 70 at each end of every gear, and a second vane 72 is provided in this second vane groove 71 respectively. Here, gas discharged from the first compression chamber 81 flows into the second vane grooves 61, and a separate second back pressure chamber port 36 is formed in the cover plates 30 and 40 for this purpose.
Accordingly, when the second rotor 70 revolves, the second vanes 72 protrude to the outer circumference, by centrifugal force at this time and the compressed gas applied to the second vane groove 71, thereby making contact with the inner circumference of the first rotor 60 at the state of zero slip, and at the same time, revolution force is transferred to the planetary rotor 60 according to the state of tooth combined with the planetary rotor 60.
Moreover, a second suction chamber 90 that the gap becomes wider when going further in the revolution direction, is formed between the planetary rotor 60 and the second rotor 70, which is tooth combined in the state of a trochoid curved surface as described above, on the other hand, a second compression chamber 91 is foπned at the portion where the gap becomes narrower.
Furthermore, a second suction opening 32 and a second discharge opening 34 are formed in the cover plates 30 and 40 corresponding to these. The second suction opening 32 is connected with the aforementioned first discharge opening
33, and a second discharge opening 34 is connected with the discharge passage 16 of the housing 10.
Here, the second discharge opening 34 has a shape for functioning of an orifice valve as shown in FIG. 3. The shape in detail is set up in proportion to the volume and speed, being reduced by compression according to the compression rate of the second compression chamber 91, and this second discharge opening 34a is formed with a slit, being cut and opened at a predetermined size in both directions of revolution and anti-revolution of the second rotor 70, for the second discharge opening 34 to operate as a valve to maintain constant pressure inside the second compression chamber 91.
So, the second discharge opening 34 will not be completely blocked due to the revolution of the second rotor 70 to prevent compression pressure from being instantly high in the second compression chamber 91, thereby, compressed and discharged gas, maintaining constant pressure at all times. Moreover, due to the profile of the second discharge opening 34, the pressure added to the first suction chamber 80 by the second compression chamber 91 maintains substantially same as the pressure added to the second suction chamber 90 by the first compression chamber 81, to prevent chattering due to their pressure difference and vibration and noise due to gas pulsation, when the planetary rotor 60 revolves.
Furthermore, a separate reservoir is provided to increase compression efficiency of second compressed gas by radiating a part of compression heat of first compressed gas between the first compression chamber 81 and the second suction chamber 90 inside the housing 10. This reservoir, not shown in the drawing, can be provided inside the housing 10, or separately installed outside the housing 10.
Between the second rotor 70 and the respective cover plates 30 and 40, as shown in FIG.l and FIG. 5, on the other hand, a ring 13 and a ring-shaped plate spring 14 is installed to make compression possible with high pressure and high efficiency.
Moreover, both a first vane 62 and a second vane 72 are formed with the same constituent. As shown in FIG.4, it is formed with a left vane piece 63 and a right vane piece 64, being divided into left and right, as well as an insertion piece, being inserted through the bottom of these two vane pieces 63 and 64. The constituent of these vanes 62 and 72 is described in the Utility Model No. 1997- 5930, which has been filed and registered by this applicant.
Hereinafter, the operation of a double compressor having planetary rotors according to the invention, as described above, will be described. In the double compressor according to the invention, a second rotor 70 begins revolving first when external power initially supplied to a rotary axis 12 to start the rotary axis 12 revolving, and a planetary rotor 60 begins eccentric revolving, which is tooth combined with the outer circumference of the second rotor 70 in trochoid tooth profile. This time, a first vane 62 and a second vane 72, which are provided respectively at the planetary rotor 60 and the second rotor 70, protrude outward by centrifugal force that is produced at the time of revolution, and by pressure of compressed gas that is transferred to the respective vane grooves 61 and 71. In other words, in case of the first vane 62, it revolves together with a first rotor 50 at the state of zero slip while making contact with the inner circumference of the first rotor 50. In case of the second vane 72, it revolves at the state of zero slip while making contact with the inner circumference of the first rotor 60. With this operation, simultaneously, when gas is inhaled through a suction passage 15 of the housing 10, the initial gas is inhaled through a first suction chamber 80. And the inhaled gas is guided by the first vane 62 and transferred to a first compression chamber 81. In the first compression chamber 81, the gas is first compressed, and then discharged through a first discharge opening 33 of the cover plates 30 and 40.
Moreover, a part of the discharged gas is supplied to a back pressure groove 21a of a metal bearing 21, as well as the respective vane grooves 61 and 71, and all the rest is guided to a second suction chamber 90 between the planetary rotor 60 and the second rotor 70 through a second suction opening 32 of the cover plates 30 and 40. This time, gas guided to the second suction chamber 90, first passes through a reservoir, not shown in the drawing. In the reservoir, heat produced while being compressed in the first compression chamber 81 is dissipated, thereby increasing the efficiency of gaseous compression at the time of second compression.
As described above, the gas passed through the reservoir 20 is inhaled into the second suction chamber 90, and then guided by the second vane 72 to accomplish second compression in the second compression chamber 91. And the gas finished second compression at a certain pressure is discharged through a second discharge opening 34, and then finally discharged outward through a discharge passage 16 of the housing 10.
INDUSTRIAL APPLICABILITY
As described above, the double compressor according to the invention makes high-efficient compression possible through two-stage compression by using planetary rotors. Basically, if other modifications make gas compression possible by providing a planetary rotor between two rotors and a vane in the planetary rotor and the second rotor positioning inside the planetary rotor, and if they are driven by combining the planetary rotor and the second rotor with a trochoid tooth profile, then it should be regarded within the technical scope of this invention.
The double compressor having planetary rotors according to the invention enables gas to have high-efficient compression at high pressure through two-stage compression cycle. Addition to this second compression, also, the planetary rotor for power transmission and the second rotor are combined with a trochoid tooth profile to accomplish power transmission and compression drive, so that there is an effect of minimizing abrasion due to friction at each portion of power transmission to improve durability of the compressor, as well as maintaining uniform pressure distribution remarkably when gas is inhaled and discharged to minimize vibration and noise of the compressor.

Claims

1. A double compressor comprising: a housing, wherein a suction passage is formed at one side and a discharge passage is formed at the other side; a first rotor supported by metal bearings inside said housing; a planetary rotor provided eccentrically inside said first rotor, wherein a first suction chamber that is connected with said suction passage and a first compression chamber that the gas inhaled into said first suction chamber is compressed are provided, and the inner circumference is formed with a trochoid curved surface; a plurality of first vanes provided in the outer circumference of said planetary rotor, wherein gas is first compressed in said first compression chamber when said planetary rotor revolves in the inner circumference of said first rotor; a second rotor having a trochoid curved surface provided on the same axis with said first rotor inside said planetary rotor, as well as tooth-combined with the trochoid curved surface of said planetary rotor to form a second suction chamber that the gas passed through said first compression chamber is inhaled at a gap against said planetary rotor, and a second compression chamber that the gas inhaled into said second suction chamber is compressed; a second vane provided at the end of the outer circumference of said second rotor, wherein said gas is second compressed and discharged into said discharge passage in said second compression chamber; and a rotary axis fixed at the center portion of said second rotor for revolving said second rotor eccentrically.
2. The double compressor of claim 1, wherein the number of trochoid curved surface gear of said second rotor is one less than the number of the trochoid curved surface gear of said planetary rotor.
3. The double compressor of claim 1, wherein a back pressure groove that compressed gas flows is formed at a portion located in the outside of the compression chamber of said first rotor within the inner circumference of said metal bearing.
4. The double compressor of claim 1, wherein a plurality of first vane grooves are formed at a portion that said first vane of said first planetary rotor is provided, a plurality of second vane grooves being formed at a portion that said second vane of said second planetary rotor is provided, and said first vane groove and said second vane groove are connected with said first compression chamber.
5. The double compressor of claim 1 , wherein a cover plate is provided at one end and at the other end of said first rotor, said planetary rotor and said second rotor inside said housing.
6. The double compressor of claim 5, wherein said cover plate is formed with a first suction opening that is connected with said first suction chamber and becomes wider when going further in the revolution direction of said planetary rotor, a first discharge opening that is connected with said first compression chamber and becomes narrower when going further in the revolution direction of said planetary rotor, a second suction opening that is connected with said second suction chamber and becomes wider when going further in the revolution direction, and a second discharge opening that is connected with said second compression chamber and the compressed coolant is discharged into said discharge passage.
7. The double compressor having planetary rotors of claim 6, wherein said second discharge opening is formed together with a cutting hole, which is cut, opened and extended respectively in the anti-revolution direction of said second rotor to prevent from being clogged by the trochoid gear portion of said second rotor when said second rotor revolves.
PCT/KR2003/000403 2002-03-06 2003-03-03 Double compressor having planetary rotors WO2003074880A1 (en)

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KR10-2002-0011835A KR100423125B1 (en) 2002-03-06 2002-03-06 Double compressor having planetary rotors

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CN103334924A (en) * 2013-07-16 2013-10-02 北京工业大学 High-duty pump combining vane pump with gear pump
CN110043462A (en) * 2019-06-03 2019-07-23 武汉航瑞船舶设备有限公司 A kind of planetary rotation formula vane pump

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KR0182390B1 (en) * 1996-12-24 1999-05-01 조봉현 Dual vane compressor
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Publication number Priority date Publication date Assignee Title
CN103334924A (en) * 2013-07-16 2013-10-02 北京工业大学 High-duty pump combining vane pump with gear pump
CN103334924B (en) * 2013-07-16 2015-11-11 北京工业大学 The large discharge pump that a kind of vane pump and gear pump combine
CN110043462A (en) * 2019-06-03 2019-07-23 武汉航瑞船舶设备有限公司 A kind of planetary rotation formula vane pump
CN110043462B (en) * 2019-06-03 2024-05-10 武汉航瑞船舶设备有限公司 Planetary rotary vane pump

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KR100423125B1 (en) 2004-03-16
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