US20030108438A1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
US20030108438A1
US20030108438A1 US10/258,395 US25839502A US2003108438A1 US 20030108438 A1 US20030108438 A1 US 20030108438A1 US 25839502 A US25839502 A US 25839502A US 2003108438 A1 US2003108438 A1 US 2003108438A1
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United States
Prior art keywords
compressor
cylinder
compression
slant
space
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US10/258,395
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English (en)
Inventor
Young-Jong Kim
Hui-Cheol Kim
Bum-Dong Sa
Byung-Ha Ahn
Kwang-Sik Yang
Seung-Jun Lee
Jang-Woo Lee
Hyoung-Joo Cho
Kang-Wook Cha
Jong-Hun Ha
Song-Kie Hong
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LG Electronics Inc
Original Assignee
LG Electronics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020000021955A external-priority patent/KR100324771B1/ko
Priority claimed from KR1020000026760A external-priority patent/KR20010105814A/ko
Priority claimed from KR10-2000-0085808A external-priority patent/KR100394239B1/ko
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AHN, BYUNG-HA, CHA, KANG-WOOK, CHO, HYOUNG-JOO, HA, JONG-HUN, HONG, SOG-KIE, KIM, HUI-CHEOL, KIM, YOUNG-JONG, LEE, JANG-WOO, LEE, SEUNG-JUN, SA, BUM-DONG, YANG, KWANG-SIK
Publication of US20030108438A1 publication Critical patent/US20030108438A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/356—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 outer member
    • F04C18/3568—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 outer member with axially movable vanes
    • 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
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the present invention relates to a compressor, and particularly, to a compressor installed in such devices like a refrigerating cycle system and contracting and exhausting fluid.
  • compressors are apparatuses changing a mechanical energy into a compression energy of compressible fluid, and these can be divided into rotary compressors, reciprocating compressors, and scroll compressors.
  • the scroll compressor is operated as follows. That is, the motor device unit M installed inside the casing 21 , and accordingly the rotator 22 and the rotating shaft 23 are rotated. At that time, a turning scroll 24 connected to the eccentric unit 23 a of the rotating shaft 23 performs a turning movement by meshed with a fixed scroll 25 . Therefore, the fluid is sucked, compressed, and discharged continuously.
  • the rotary compressor shown in FIG. 1 comprises the rotating shaft 3 including the eccentric unit 3 a , the rolling piston 5 press-fitted into the eccentric unit 3 a , and a plurality of balance weights 6 and 6 ′ coupled to the rotator 2 in order to maintain the rotating balance of the eccentric unit 3 a , whereby the number of the components is increased and the structure is complex.
  • the eccentric unit 3 a of the rotating shaft and the rolling piston 5 inserted into the eccentric unit 3 a are located inside the compression space V of the cylinder 4 , and therefore the compression volume is small comparing to the size of the compression devices unit and the compression efficiency is lowered because one compression stroke is made when the rotating shaft is rotated once.
  • a rotating torque is increased by the plurality of balance weights 6 , whereby the power consumption is increased.
  • the eccentric unit 3 a and the rolling piston 5 formed on the rotating shaft 3 are eccentrically rotated, and therefore vibration noise is generated during rotating.
  • the reciprocating compressor shown in FIG. 2 comprises the crank shaft 13 having the eccentric unit 13 a , the piston 14 coupled to the crank shaft 13 , and a balance weight 13 b for balancing the rotating balance of the eccentric unit 13 a , whereby the number of components is increased and the structure is complex.
  • the piston 14 undergoes a linear reciprocating movement inside the cylinder compression space V, and therefore the fluid is compressed. Therefore, the amount of compression discharge may be large when the crank shaft 13 is rotated once, however, one compression stroke is made when the crank shaft 13 is rotated once, whereby the compression efficiency is lowered.
  • the rotating torque is increased by the eccentric unit 13 a of the crank shaft 13 and the balance weight 13 b , whereby the power consumption is increased.
  • the eccentric unit 13 a formed on the crank shaft 13 is eccentrically rotated, and thereby the vibration noise is generated.
  • the valve assembly 16 is operated when the suction and discharge processes are made, whereby the noise is increased.
  • the scroll compressor shown in FIG. 3 comprises a rotating shaft 23 including the eccentric unit 23 a , a turning scroll 24 having wraps 24 a and 25 a of involute curve form and a fixed scroll 25 , and a balance weight 26 for balancing the rotating balance of the eccentric unit 23 a , whereby the number of components are large and structure is very complex. In addition, it is difficult to fabricate the turning scroll 24 and the fixed scroll 25 .
  • the turning movement of the turning scroll 24 and the eccentric movement of the eccentric unit 23 a of the rotating shaft 23 make big vibration noise.
  • the rotary compressor, the reciprocating compressor, and the scroll compressor use the balance weights 6 , 13 b , and 26 because of the eccentric units 3 a , 13 a , and 23 a of the shaft, and therefore the driving force is increased, the vibration and noise are generated, and the reliability is lowered.
  • an object of the present invention is to provide a compressor including a slant compression plate having an upper dead center and a lower dead center inside a compression space, whereby entire structure can be simple, vibration and noise are lowered, and compression efficiency per unit volume is increased.
  • a compressor comprising: a cylinder assembly having a compression space therein, and a suction flowing passage and a discharge flowing passage are connected to the compression space; a rotation driving means inserted inside the compression space of the cylinder assembly for transmitting the rotational force; a slant compression plate located inside the compression space of the cylinder assembly for dividing the compression space into two or more spaces, and at the same time, compressing and discharging fluid in the respective spaces through the discharge flowing passage while rotating by being connected to the rotation driving means; and a vane means adhered to both surfaces of the slant compression plate by being inserted inside the compression space of the cylinder assembly so as to perform reciprocating movement, and dividing the respective spaces partitioned by the slant compression plate into a suction space and a compression space by being located between the suction flowing passage and the discharge flowing passage.
  • the cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by being coupled to the upper and lower parts of the cylinder and at the same time, supporting the rotation driving means.
  • a damping recess of a certain depth is formed in the cylinder assembly so as to suck a pressure pulsation generated during fluid compression process inside the compression space.
  • suction flowing passage and the discharge flowing passage are formed as two pairs so as to have phase difference of 180°.
  • a discharge valve is formed on the discharge flowing passage of the cylinder assembly for opening/closing the discharge of the compressed fluid.
  • Two suction flowing passages are formed in the cylinder so as to have phase difference of 180°, one of those two is formed on an upper part of the cylinder and the other is formed on a lower part of the cylinder.
  • a flowing resistance reducing unit which is an emitted part is formed on an entrance unit located on the compression space side of the cylinder assembly so that the flowing resistance generated when the compressed fluid is discharged can be reduced.
  • a plurality of vane slots are formed on the bearing plates so that the vane means can be inserted and undergoes the reciprocating movement.
  • a coupling protrusion unit of round shape which is protruded to inside of the compression space as a certain height and has a outer diameter corresponding to an inner diameter of the cylinder, is formed on the bearing plates.
  • the slant compression plate is formed to have a plane surface having a plane surface formed as a ring round disk form, and a side surface formed as a sine wave having a upper dead center and a lower dead center adhered to an upper side surface and to a lower side surface of the compression space.
  • the upper dead center and the lower dead center of the slant compression plate are formed to have a phase difference of 180°, and an angle of a certain horizontal line from the outer circumferential surface to the inner circumferential surface and an outer surface in vertical direction of the rotation driving means is formed to make a right-angle.
  • the upper dead center and the lower dead center of the slant compression plate may be formed as a curved surface so as to line contact to the upper surface and to the lower surface of the compression space, or may be formed as a plane surface so as to surface contact to the upper and lower surfaces of the compression space.
  • the slant compression plate includes a labyrinth seal having at least one recess band on the outer circumferential surface which is slide contacted to the cylinder assembly so as to prevent a leakage of the fluid from high-pressure side to the low-pressure side by the pressure difference between the respective compression spaces.
  • the vane means comprises a vane of square shape adhered to the slant compression plate inside the compression space of the cylinder assembly, and an elastic supporting means supported by the cylinder assembly and providing an elastic force so that the vane is adhered to the slant compression plate.
  • the vane is disposed on the cylinder assembly to have a phase difference of 180°, and to be adhered to the upper and lower surfaces of the slant compression plate.
  • the elastic supporting means comprises a spring retainer supported by the cylinder assembly, and a spring supported by the spring retainer for providing an elastic force to the vane.
  • a side surface of the vane is formed to be a concave surface so as to surface contact to the outer circumferential surface of the rotating shaft, and the other side surface of the vane is formed to be a convex surface so as to surface contact to the inner circumferential surface of the cylinder assembly.
  • the vane comprises a contact curved surface unit of round shape formed on a portion to which the slant compression plate is contacted, and the contact curved surface is formed to be enlarged its radius of curvature from the rotational center of the slant compression plate to the outer circumferential surface.
  • the cylinder assembly has two compression spaces centering around the slant compression plate.
  • a first suction passage and a first discharge passage are connected to the first compression space
  • a second suction passage and a second discharge passage are connected to the second compression space.
  • the first discharge passage is connected to the second suction passage, whereby the fluid compressed in the first compression space is recompressed in the second compression space.
  • the vane means are respectively disposed on same vertical surface of the cylinder assembly so as to adhere to the upper surface and the lower surface of the slant compression plate.
  • Two discharge passages are formed in side direction of the cylinder assembly, and some parts of the respective discharge passages are overlapped with the vane means.
  • the suction passage is formed on side wall of the cylinder assembly so that the fluid is sucked into the both compression spaces in turns according to the rotation of the slant compression plate.
  • a spring penetrating hole is formed on the cylinder assembly so that the elastic supporting means can be passed, and the elastic supporting means is connected to the vanes located on the upper and lower sides of the slant compression plate through the spring penetrating hole, whereby the elastic force can be provided.
  • FIG. 1 is a cross-sectional view showing a general rotary compressor
  • FIG. 2 is a cross-sectional view showing a general reciprocating compressor
  • FIG. 3 is a cross-sectional view showing a general scroll compressor
  • FIG. 4 is a longitudinal cross-sectional view showing a compressor according to a first embodiment of the present invention
  • FIG. 5 is a transverse cross-sectional view showing the compressor according to the first embodiment of the present invention.
  • FIGS. 6A, 6B, and 6 C are cross-sectional views of line A-A′, line B-B′, and line C-C′ in FIG. 5;
  • FIG. 7 is a cut perspective view showing principal parts of the compressor of the first embodiment according to the present invention.
  • FIGS. 8 through 10 are longitudinal cross-sectional view and plane cross-sectional views of principal parts showing operation states of the compressor of the first embodiment according to the present invention
  • FIG. 11 is a longitudinal cross-sectional view showing a compressor of a second embodiment according to the present invention.
  • FIG. 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention.
  • FIGS. 13A and 13B are longitudinal cross-sectional views showing operation state of the compressor of the second embodiment according to the present invention.
  • FIG. 14 is a view showing status of fluid flowing in the compressor of the second embodiment according to the present invention.
  • FIG. 15 is a longitudinal cross-sectional view showing a compressor of a third embodiment according to the present invention.
  • FIGS. 16A, 16B are a transverse cross-sectional view showing the compressor of the third embodiment of the present invention, and a cross-sectional view of line D-D′;
  • FIG. 17 is a cut perspective view of principal parts showing the compressor of the third embodiment according to the present invention.
  • FIGS. 18A and 18B are cross-sectional views of principal parts showing an another embodiment of a damping recess in the compressor of the third embodiment according to the present invention.
  • FIG. 19 is a transverse cross-sectional view and an enlarged view of principal parts showing a compressor of a fourth embodiment according to the present invention.
  • FIG. 20 is a longitudinal cross-sectional view and an enlarged view showing the compressor of fourth embodiment according to the present invention.
  • FIGS. 21A, 21B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recess in the compressor of the fourth embodiment according to the present invention.
  • FIG. 22 is a longitudinal cross-sectional view of principal parts showing a compressor of a fifth embodiment according to the present invention.
  • FIG. 23 is a cut perspective view of principal parts showing the compressor of the fifth embodiment according to the present invention.
  • FIG. 24 is a transverse cross-sectional view showing the compressor of the fifth embodiment according to the present invention.
  • FIG. 25 is a cut perspective view of principal parts showing a compressor of a sixth embodiment according to the present invention.
  • FIG. 26 is a longitudinal cross-sectional view and detailed view showing the compressor of the sixth embodiment according to the present invention.
  • FIGS. 27A and 27B are detailed cross-sectional views of principal parts showing modified embodiments of a flowing resistance reducing unit in the compressor of the sixth embodiment according to the present invention.
  • FIG. 28 is a longitudinal cross-sectional view of principal parts showing a compressor of a seventh embodiment according to the present invention.
  • FIG. 29 is a detailed cross-sectional view of line E-E′ in FIG. 28;
  • FIG. 30 is a transverse cross-sectional view showing the compressor of the seventh embodiment according to the present invention.
  • FIG. 31 is a cut perspective view of principal parts showing the compressor of the seventh embodiment according to the present invention.
  • FIG. 32 is a cut perspective view of principal parts showing a compressor of an eighth embodiment according to the present invention.
  • FIG. 33 is a longitudinal cross-sectional view of principal parts showing the compressor of the eighth embodiment according to the present invention.
  • FIG. 34 is a detailed cross-sectional view of line F-F′ in FIG. 33;
  • FIG. 35 is a longitudinal cross-sectional view of principal parts showing a compressor of a ninth embodiment according to the present invention.
  • FIG. 36 is a cut perspective view of principal parts showing the compressor of the ninth embodiment according to the present invention.
  • FIG. 37 is a detailed view of principal parts showing the compressor of ninth embodiment according to the present invention.
  • FIG. 38 is a longitudinal cross-sectional view showing a compressor of a tenth embodiment according to the present invention.
  • FIG. 39 is a transverse cross-sectional view showing the compressor of the tenth embodiment according to the present invention.
  • FIG. 40 is a cut perspective view showing the compressor of the tenth embodiment according to the present invention.
  • FIG. 41 is a transverse cross-sectional view of principal parts for describing the compression processes of the compressor of the tenth embodiment according to the present invention.
  • FIGS. 42A, 42B, 42 C, and 42 D are longitudinal cross-sectional views showing the compression processes of the compressor of the tenth embodiment according to the present invention.
  • FIG. 43 is a longitudinal cross-sectional view showing a compressor of an eleventh embodiment according to the present invention.
  • FIGS. 44A and 44B are detailed cross-sectional views of principal parts showing operation state of a vane of the eleventh embodiment according to the present invention.
  • FIG. 45 is a longitudinal cross-sectional view showing a compressor of a twelfth embodiment according to the present invention.
  • FIG. 46 is a cut perspective view showing the compressor of twelfth embodiment according to the present invention.
  • FIGS. 47A, 47B, and 47 C are a front view, a side view, and an enlarged perspective view of principal parts showing a structure of the vane in the compressor of twelfth embodiment according to the present invention.
  • FIGS. 48A and 48B are plane views showing operation state of the compressor of the twelfth embodiment according to the present invention.
  • FIG. 49 is a plane view showing contact status of the vane in accordance with a rotation of the slant compression plate in the compressor of twelfth embodiment according to the present invention.
  • FIG. 50 is a detailed view showing the contact status of the compression sieve unit and the vane in the compressor of the twelfth embodiment according to the present invention.
  • FIG. 51 is a cut perspective view showing a compressor of thirteenth embodiment according to the present invention.
  • FIG. 52 is a detailed view showing a status of rotating the compressor as 180°;
  • FIG. 53 is a plane view showing principal parts of the compressor of the thirteenth embodiment according to the present invention.
  • FIG. 54 is a perspective view showing a modified embodiment a shaft contact surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
  • FIGS. 4 through 12 A compressor of a first embodiment according to the present invention will be described with reference to FIGS. 4 through 12.
  • FIG. 4 is a longitudinal cross-sectional view showing the compressor of the first embodiment according to the present invention
  • FIG. 5 is a transverse cross-sectional view showing the compressor of the first embodiment according to the present invention
  • FIG. 6 is a cross-sectional view of principal parts of lines A-A′, B-B′, and C-C′
  • FIG. 7 is a cut perspective view showing the compressor of the first embodiment according to the present invention.
  • the compressor of the first embodiment according to the present invention comprises a motor device unit M for generating a rotation force inside a casing C, and a compression device unit P for compressing and discharging fluid.
  • the casing C is formed to have a certain inner volume so as to be sealed, and has at least one or more suction pipe 42 for sucking the fluid formed on one side of the casing and a discharge pipe 43 for discharging the fluid on the other side.
  • the motor device unit M comprises a stator 44 fixedly coupled to the casing C, and a rotator 45 coupled inside the stator 44 so as to be rotational.
  • the compression device unit P comprises a cylinder assembly 50 having a compression space V therein and a plurality of suction passages 53 and discharge passages 54 communicating with the compression space V respectively; a rotating shaft 61 coupled to a rotator 45 of the motor device unit M and penetrating a center portion of the cylinder assembly 50 ; a slant compression plate 70 coupled to the rotating shaft 61 inside the cylinder assembly 40 and dividing the compression space V of the cylinder assembly 50 into a first space V 1 , and a second space V 2 ; a first vane 80 and a second vane 80 ′ penetratingly inserted into the cylinder assembly 50 , and elastically supported so as to contact to the both side surfaces of the slant compression plate 70 , whereby the vanes undergo a reciprocating movement according to the rotation of the slant compression plate 70 and dividing the compression spaces V 1 and V 2 as a suction space and a compression space so as to be changeable with each other; and a discharge valve 90 opening/clos
  • the cylinder assembly 50 comprises a cylinder 55 fixedly installed inside a casing C which has a suction pipe 42 and a discharge pipe 43 , and a first bearing plate 56 and a second bearing plate 57 fixed on an upper and a lower sides of the cylinder 55 and forming the compression space V with the cylinder 55 .
  • the cylinder 55 includes a compression space V therein, and suction passages 53 and 53 ′ communicating with the compression space V respectively are formed to have a phase difference of 180°.
  • the suction passages 53 and 53 ′ are formed to have sizes which are able to be opened/closes by the area of side surface thickness of the slant compression plate 70 .
  • the suction passage 53 of the first space is formed on upper end part of the cylinder 55
  • the suction passage 53 ′ of the second space is formed on lower end part of the cylinder 55 .
  • Shaft holes 56 b and 57 b through which the rotating shaft 60 is inserted, are formed on center parts of the first and second bearing plates 56 and 57 .
  • Vane slots 56 a and 57 a having a phase difference of 180° in vertical direction are formed on a side surfaces of the shaft holes 56 b and 57 b , and the suction passages 53 and 53 ′ and the discharge passages 54 and 54 ′ are disposed on both sides of the vane slots 56 a and 57 a.
  • a first discharge muffler 58 having a large are unit and a small area unit is installed on an upper part of the first bearing plate 56 in order to reduce discharging noise of the fluid discharged from the discharge passage 54
  • a second discharge muffler 59 having a large area unit and a small area unit is installed on a lower part of the second bearing plate 57 in order to reduce discharging noise of the fluid discharged from the discharge passage 54 ′.
  • the cylinder 55 and the first bearing plate 56 may be formed as a single body, and the second bearing plate 57 may cover the cylinder 55 .
  • the cylinder 55 and the second bearing plate 57 may be formed as a single body, and the first bearing plate 56 may cover the cylinder 55 .
  • the rotating shaft 60 is press-fitted into the rotator 45 , and is penetratingly inserted into the cylinder assembly 50 . That is, the rotating shaft 60 is penetratingly inserted into the shaft holes 56 b and 57 b of the first and second bearing plates 56 and 57 , and supported by the first and second bearing plates 56 and 57 so as to rotate relatively.
  • the slant compression plate 70 is formed as ring round disc from plane view, and is formed as a sine wave having an upper dead center R 1 and a lower dead center R 2 from side view.
  • the upper dead center R 1 and the lower dead center R 2 are disposed with a phase difference of 180° therebetween, and is formed as a sine wave when spreading out.
  • an outer circumferential surface of the slant compression plate 70 is formed as a round when projected from plane view so as to sliding contact to the inner circumferential surface of the cylinder 55 .
  • the upper dead center R 1 is always slidingly contacted to a bottom surface of the first bearing plate 56 , however the lower dead center R 2 is disposed to slidingly contact to an upper surface of the second bearing plate 57 .
  • an angle made by a certain horizontal line connected from outer circumferential surface to the inner circumferential surface and by an outer surface of the hub unit 72 in vertical direction is right-angle on the slant compression plate 70 .
  • the thickness of a part making the upper dead center R 1 and the lower dead center R 2 is formed so as to block the suction passages 53 and 53 ′ of the cylinder 55 in the slant compression plate 70 .
  • the rotating shaft 60 and the slant compression plate 70 may be formed such that the rotating shaft 60 , the hub unit 72 , and the slant compression plate 70 are formed as a single body, or these are molded separately and assembled.
  • the rotating shaft 60 and the hub unit 72 , or the hub unit 72 and the slant compression plate 70 may be formed as a single body, and then these may be coupled to another component.
  • vanes 80 and 80 ′ are formed as a square plate so as to have a certain thickness and area, and are inserted into the vane slots 56 a and 57 a formed on the first and the second bearing plates 56 and 57 .
  • the vanes 80 and 80 ′ are constructed so as to change the first space V 1 and the second space V 2 to suction spaces V 1 s and V 2 s , and compression spaces V 1 p and V 2 p respectively, when the slant compression plate 70 is rotated as contacted to the inner circumferential surface of the cylinder compression space V in the state that the vanes 80 and 80 ′ are contacted to the hub unit 72 , to the slant compression plate 70 which are located inside the cylinder compression space V, and to the inner circumferential surface of the cylinder compression space V.
  • vanes 80 and 80 ′ are elastically supported by the elastic supporting means 81 and 81 ′, and the elastic supporting means 81 and 81 ′ are supported by the first and the second bearing plates 56 and 57 , respectively.
  • the discharge valves 90 and 90 ′ are installed on the first and the second bearing plates 56 and 57 respectively so as to open/close the discharge passages 54 and 54 ′ through which the fluid compressed in the compression spaces V 1 p and V 2 p of the first and the second spaces V 1 and V 2 is discharged.
  • oil for lubricating and cooling functions is filled on a part where the compression device unit P and the motor device unit M are slidingly contacted. And an oil pump(not shown) for pumping the oil and as oil passage 61 are formed inside the rotating shaft 60 .
  • FIGS. 8 through 10 are longitudinal and plane cross-sectional views showing operation states of the compressor in the first embodiment according to the present invention.
  • the slant compression plate 70 divides the compression space V of the cylinder 55 into the first space V 1 and the second space V 2 , and the upper dead center R 1 and the lower dead center R 2 are line contacted to the upper and lower surfaces of the compression space V.
  • the suction spaces V 1 s and V 2 s suck the fluid as the volume is enlarged, and the compression spaces V 1 p and V 2 p compress the fluid as the volume therein is reduced.
  • the fluid is sucked, compressed, and discharged in the first and second spaces V 1 and V 2 at the same time according to the rotation of the slant compression plate 70 .
  • the structure of the compressor according to the present invention can be simple because an additional balance weight for balancing the rotation is not used by installing the rotating shaft 60 and the slant compression plate 70 .
  • an additional balance weight does not needed, and therefore the torque rotating the rotating shaft 60 to which the slant compression plate 70 is coupled is reduced. Therefore, the electric consumption can be reduced, and sufficient driving force can be ensured by using the motor device unit M having relatively small capacity.
  • the rotating shaft 60 and the slant compression plate 70 are balanced with each other, and therefore the vibration noise generated during rotation can be reduced.
  • eccentric units are installed inside the rotary, reciprocating, and scroll compressors, and therefore the vibration noise is generated.
  • stable rotation can be made, whereby the vibration noise can be reduced.
  • the slant compression plate 70 is rotated as dividing the cylinder compression space V into the first space V 1 and the second space V 2 , and accordingly, compression force is pressed to the slant compression plate 70 during the processes of compressing the fluid in the first and the second spaces V 1 and V 2 .
  • the generated compression force is applied to the first and the second spaces V 1 and V 2 , at the same time, the force of a tangential component of the slanted surface on the slant compression plate 70 is applied as a repulsive power of the torque and the rotating shaft 60 of the motor device unit M. Therefore, the repulsive power applied to the rotating shaft 60 and to the slant compression plate 70 is relatively small, whereby the rotations of the rotating shaft 60 and of the slant compression plate 70 are stable.
  • a compressor of second embodiment according to the present invention will be described as follows with reference to FIGS. 11 through 14.
  • FIG. 11 is a longitudinal cross-sectional view showing the compressor of the second embodiment according to the present invention
  • FIG. 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention
  • FIGS. 13A and 13B are longitudinal cross-sectional views showing the operation states of the compressor of the second embodiment according to the present invention
  • FIG. 14 is a status view showing the flowing of the fluid in the compressor of the second embodiment according to the present invention.
  • the compressor of the first embodiment uses the method that the compressor compresses and discharges once in both spaces, however, the compressor uses two-steps compression method by which discharged fluid are cooled and compressed again after one compression is completed.
  • the compressor of the second embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for compressing and discharging the fluid inside the casing C, as in the compressor of the first embodiment.
  • the compression device unit P comprises a cylinder assembly 110 for forming a compression space V including a cylinder 111 , a first bearing plate 113 , and a second bearing plate 115 , and the cylinder assembly 110 includes a slant compression plate 120 for dividing the compression space V into the first space V 1 and to the second space V 2 and rotated by coupling to the rotating shaft 122 .
  • a first vane 131 and a second vane 132 which are undergone reciprocating movement to opposite axial directions with each other by contacted to the both surfaces of the slant compression plate 120 and divide the respective spaces V 1 and V 2 into the changeable suction space and the compression space, are installed on the first bearing plate 113 and on the second bearing plate 115 .
  • the cylinder 111 of true round ring form includes a first suction passage 102 on one side connected to the first space V 1 so as to be connected to the suction pipe 101 of the casing C, and a second suction passage 105 is formed as communicated in the second space V 2 on the opposite side with a phase difference of 180° with the first suction passage 102 .
  • the first bearing plate 113 includes a first discharge hole 103 for discharging the firstly compressed fluid from the first space V 1 , and a suction passage 104 is formed on the position having phase difference of 180° with the first discharge hole 103 for inducing the firstly compressed fluid discharged from the first discharge hole 103 through a second suction passage 105 .
  • a first discharge valve 135 which is opened/closed according to pressure of the fluid in the first space V 1 is installed on a front end part of the first discharge hole 103 .
  • the discharge valve 135 may be formed as a various shapes, a rectangular discharge valve having a retainer is used in the present invention.
  • a second discharge hole 106 is formed toward the inner space of the casing C for discharging the fluid secondly compressed in the second space V 2
  • the second bearing plate 115 in the second bearing plate 115 The second discharge valve 136 of same shape as the first discharge valve 135 is installed on a front end part of the second discharge hole 106 so that the second discharge valve 136 can be opened/closed according to the pressure of the fluid in the second space V 2 .
  • a first discharge muffler 117 having a large area unit and a small area unit is installed on the upper surface of the first bearing plate 113 so that discharge noise of the fluid discharged from the first discharge hole 103 is reduced.
  • the first discharge muffler accepts the first discharge hole 103 and the suction passage 104 of the first bearing plate 113 so as to use these as communication members between the first and the second spaces V 1 and V 2 , and the small area unit is located between the first discharge hole 103 and the suction passage 104 .
  • a discharge hole 107 for discharging the fluid which is secondly compressed in the cylinder assembly 110 to the inside of the casing C is formed on a second discharge muffler 119 which is located on the opposite position of the first discharge muffler 117 .
  • the fluid discharged into the casing C is compressed twice by the repeated processes that the fluid is discharged to a refrigerating cycle through the discharge pipe 108 of the casing C going through gaps between the respective members.
  • the compressor of the second embodiment according to the present invention is suitable for the refrigerating cycle for air conditioning which needs high compression ratio, and load of the motor device unit M, the number of components, and the volume of the compressor can be reduced as the minimum because the fluid can be compressed twice in one compression device unit P.
  • the second compression space V 2 has relatively high pressure and supports the rotating shaft 122 and the slant compression plate 120 . Therefore, the axial load and the pressure of the compressor is reduced, whereby the performance of the compressor can be increased.
  • a compressor of a third embodiment according to the present invention will be described as follows with reference to FIGS. 15 through 18.
  • FIG. 15 is a longitudinal cross-sectional view of principal parts showing the compressor of the third embodiment according to the present invention
  • FIGS. 16A and 16B are a transverse cross-sectional view showing the compressor of the third embodiment according to the present invention and a cross-sectional view showing the line D-D
  • FIG. 17 is a cut perspective view of the principal parts showing the compressor of the third embodiment according to the present invention.
  • the compressor of the third embodiment according to the present invention further comprises damping recesses 158 a and 159 a are installed in the cylinder assembly 155 so that the noise can be reduced, besides the components of the compressor of the first embodiment.
  • the compressor of the third embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for compressing and discharging the fluid in the casing C.
  • the compression device unit P comprises a cylinder assembly 150 having a compression space; a rotating shaft 160 penetrating the cylinder assembly 150 from the motor device unit M; a slant compression plate 170 of sine wave form for dividing the compression space V in the cylinder assembly 150 into a plurality of spaces; and a plurality of vanes 180 A and 180 B moving while changing the space in the compression space V into a suction space and a compression space according to the rotation of the slant compression plate 170 .
  • the cylinder assembly 150 comprises a cylinder 150 fixed inside the casing C; and a first bearing plate 158 and a second bearing plate 159 fixed on an upper and a lower part of the cylinder and forming the compression space V with the cylinder 155 .
  • the damping recesses 158 a and 159 a of round recess form having a certain depth are respectively installed on the first bearing plate 158 and on the second bearing plate 159 so that pressure pulsation of the first space V 1 and of the second space V 2 .
  • damping recesses 158 a and 159 a are formed to be located within 180° from the respective vanes 180 A and 180 B range toward the rotational direction of the slant compression plate 170 , and the damping recesses may be formed on one space between the first and the second spaces V 1 and V 2 .
  • the compressor of the third embodiment according to the present invention comprises suction passages 153 A and 154 B and discharge passages 154 A and 154 B formed in the first and the second spaces V 1 and V 2 which are divided by the slant compression plate 170 , same as in the compressor of the first embodiment according to the present invention.
  • vanes 180 A and 180 B are located respectively between the suction passages 153 A and 153 B, and the discharge passages 154 A and 154 B, and the discharge passages 154 A and 154 B are opened/closed by discharge valves 190 A and 190 B.
  • FIGS. 18A and 18B are cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the third embodiment according to the present invention.
  • the damping recess 158 a ′ may be formed as an oval, and as shown in FIG. 18B, the damping recess 158 a ′′ may be formed as two recesses having different inner diameters and stepped inside.
  • the damping recess can be modified its shape, size, and number according to the capacity and the condition of the compressor.
  • the pressure pulsation is generated by the pressure change of the fluid. Arid the pressure pulsation is sucked by the damping recesses 158 a and 159 a formed in the first and the second spaces V 1 and V 2 .
  • the pressure pulsation generated by the pressure change of the fluid is sucked through the damping recesses 158 a and 159 a , in the processes of sucking, compressing, and discharging the fluid in high temperature and pressure by the rotation of the slant compression plate 170 , whereby the noise generated by the pressure pulsation can be reduced.
  • a compressor of a fourth embodiment according to the present invention will be described as follows with reference to FIGS. 19 through 21.
  • FIG. 19 is a longitudinal cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention
  • FIG. 20 is a transverse cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention.
  • the compressor of the fourth embodiment according to the present invention comprises damping recesses so as to reduce the pulsation noise as in the compressor of the third embodiment, however the damping recesses are formed on the inner circumferential surface of a cylinder 155 ′ unlike the damping recesses in the compressor of the third embodiment.
  • the compressor of the fourth embodiment comprises a motor device unit M for generating the rotation force and a compression device unit P for compressing and discharging the fluid inside the casing C, and the compression device unit P comprises a cylinder assembly 150 ′, a rotating shaft 160 ′, a slant compression plate 170 ′, and a plurality of vanes 180 A′ and 180 B′.
  • a cylinder 155 ′, a first bearing plate 158 ′, and a second bearing plate 159 ′ are assembled inside the cylinder assembly 150 ′, and therefore a compression space V is formed.
  • Suction passages 153 A′ and 153 B′ respectively communicated with the compression space V are formed to have a phase difference of 180° with each other on the cylinder 155 ′.
  • the suction passage 153 A′ of the first space V 1 is formed on an upper part of the cylinder 155 ′
  • the suction passage 153 B′ of the second space V 2 is formed on a lower part of the cylinder 155 ′.
  • the suction passages 153 A′ and 153 B′ of the first and the second spaces V 1 and V 2 are formed on positions apart a certain distance from the upper and the lower surfaces of the cylinder 155 ′ which are contacted to the first and the second bearing plates 158 ′ and 159 ′.
  • the slant compression plate 170 ′ is formed to have thicknesses on the upper and lower dead centers can open/close the suction passage 153 A′ of the first space and the suction passage 153 B′ of the second space.
  • the damping recesses 155 A and 155 B are formed between the suction passages 153 A′ and 153 B′, and the first and second bearing plate 158 ′ and 159 ′ of the first and second spaces in the cylinder 155 ′ so as to suck the pressure pulsation.
  • the damping recesses 155 A and 155 B are penetratingly formed from upper or lower sides of the suction passages 153 A′ and 153 B′ of the first and the second spaces to contacted positions with the first and second bearing plate 158 ′ and 159 ′, and are opened toward the inner circumferential surfaces of the cylinder 155 ′.
  • the damping recesses 155 A and 155 B as described above are formed as semicircle on the inner circumferential surface of the cylinder 155 ′ as shown in FIG. 20 and opened toward the compression space V of the cylinder 155 ′, and the size of the opened part k is same as the diameter of the semicircle.
  • the inner diameters of the semicircle of the damping recesses 155 A and 155 B are formed to be smaller than those of the suction passages 153 A′ and 153 B′.
  • discharge passages 154 A′ and 154 B′ are located on the first and the second bearing plate 158 ′ and 159 ′ so that the fluid compressed inside the first and the second spaces V 1 and V 2 can be discharged therethrough.
  • FIGS. 21A, 21B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the fourth embodiment according to the present invention.
  • the damping recess 155 C shown in FIG. 21A is formed by overlapping relatively large semicircle and a relatively small circle, and at that time, the small circle is located inward.
  • the damping recess 155 D shown in FIG. 21B is formed as a circle similar with the damping recess 155 A shown in FIG. 20, and the size of the opened part toward the compression space is smaller than that of the damping recess 155 A. That is, size of the opened part of the damping recess 155 D is smaller than the diameter of the circle.
  • damping recess 155 E shown in FIG. 21C is formed same as the damping recess 155 D in FIG. 21B, however it is installed on a position moved to one side from the center line of the suction passage 153 E.
  • the damping recess 155 E is located to have a center point on the position where is not overlapped with the center line of the suction passage 153 E.
  • the pressure pulsation caused by the pressure change of the fluid is also generated during the processes of sucking, compressing, and discharging the fluid in the first and the second spaces V 1 and V 2 by the volume change of the first and the second spaces V 1 and V 2 of the cylinder assembly 150 ′, and the pressure pulsation is sucked by the damping recesses 155 A and 155 B formed on inner circumferential surface of the cylinder 155 ′ in the first and the second spaces V 1 and V 2 .
  • the damping recesses 155 A and 155 B can suck the pressure pulsation of a certain frequency range by changing the inner volume.
  • the compressor of the fourth embodiment according to the present invention comprises the damping recesses 155 a and 155 B which suck the pressure pulsation generated by the pressure change of the fluid in the processes of sucking, compressing, and discharging the fluid while the rotation of the slant compression plate 170 ′, whereby the vibration and noise generated by the pressure pulsation can be reduced and the reliability of the compressor can be increased.
  • a compressor of a fifth embodiment according to the present invention will be described as follows with reference to FIGS. 22 through 24.
  • FIG. 22 is a longitudinal cross-sectional view of principal parts showing the compressor of the fifth embodiment according to the present invention
  • FIG. 23 is a cut perspective view showing the compressor of the fifth embodiment according to the present invention
  • FIG. 24 is a transverse cross-sectional view showing the compressor of the fifth embodiment according to the present invention.
  • discharge passages are formed on the first and the second bearing plate in the compressor of the first embodiment, however discharge passages 205 and 206 are formed penetrating a cylinder 211 in the compressor of the fifth embodiment according to the present invention.
  • the compressor of the fifth embodiment according to the present invention comprises a casing C, a motor device unit M, and a compression device unit P, and the compression device unit P comprises a cylinder assembly 210 , a slant compression plate 220 , and a first vane 231 and a second vane 232 .
  • a cylinder 211 , a first bearing plate 213 , and a second bearing plate 215 are assembled in the cylinder assembly 210 , whereby a compression space V is formed.
  • a first suction passage 202 is connected to the first space V 1 inside the cylinder 211 so as to be connected to the suction pipe 201 in the casing C, and a suction passage 203 connected to another suction pipe(not shown) is communicatively formed in the second space V 2 having a phase difference of 180° with the first suction passage 202 on the opposite side.
  • discharge recess units 211 a and 211 b which are emitted parts having a phase difference of 180° are formed on both sides of the outer circumferential surface of the cylinder 211 , and the discharge passage 205 and 206 are formed on the discharge recess units 211 a and 211 b so that the fluid compressed in the compression space V can be discharged.
  • discharge valves 235 and 236 opening/closing the discharge passages 205 and 206 are installed by a bolt inside the discharge recess units 211 a and 211 b , and an engraved recess 211 d having a certain depth is formed inside the discharge recess units 211 a and 211 b so that the discharge valves can be mounted as shown in FIG. 24.
  • Vanes 231 and 232 are respectively located between the suction passages 202 and 203 , and the discharge passages 205 and 206 in the compressor of the fifth embodiment according to the present invention.
  • a compressor of a sixth embodiment according to the present invention will be described as follows with reference to FIGS. 25 through 27.
  • FIG. 25 is a cut perspective view of principal parts showing the compressor of the sixth embodiment according to the present invention
  • FIG. 26 is a transverse cross-sectional view and a detailed view showing the compressor of the sixth embodiment according to the present invention.
  • Two discharge passages 205 ′ and 206 ′ having a phase difference of 180° with each other are formed toward the discharge recess units 211 a ′ and 211 b ′ from the compression space V of the cylinder assembly 210 ′ in the compressor.
  • the flowing resistance reducing units 205 a and 206 a which are omitted parts are formed on inlet side the discharge passages 205 ′ and 206 ′, that is, the compression space V of the cylinder 211 so that the flowing resistance generated when the compressed fluid is discharged.
  • the discharge passages 205 ′ and 206 ′ are formed as straight lines so as to face the center direction of the compression space V.
  • the flowing resistance units 205 a and 206 a are formed so that the sizes of the inlet parts of the discharge passages 205 ′ and 206 ′ are larger than those of the outlet parts, and these are slanted so that the size is reduced gradually from the inlet part to the outlet part.
  • the flowing resistance reducing units 205 a and 206 a are formed so as to face counterpart direction of rotation of the slant compression plate 220 ′.
  • FIGS. 27A and 27B are detailed cross-sectional views of principal parts showing modified embodiments of the flowing resistance reducing units in the compressor of the sixth embodiment according to the present invention.
  • the flowing resistance reducing unit 206 c which is narrowed toward the outlet part shown in FIG. 27A is formed as a recess having a plurality of steps and having a certain depth.
  • the flowing resistance reducing unit 206 d is formed same as the flowing resistance reducing unit shown in FIG. 26, and is slanted so as to be reduced its size toward the outlet part of the discharge passage 206 ′.
  • the discharge passage 206 ′ is formed as slanted a certain angle ⁇ against the center direction of the compression space V in the cylinder 211 ′.
  • the flowing resistance reducing units 205 a and 206 a function as resonator for reducing the operation noise of the discharge valves 235 ′ and 236 ′, whereby the noise is reduced and over-compression is prevented.
  • a compressor of a seventh embodiment according to the present invention will be described as follows with reference to FIGS. 28 through 31.
  • FIG. 28 is a longitudinal view showing principal parts of the compressor of the seventh embodiment according to the present invention
  • FIG. 29 is a detailed cross-sectional view of line E-E in FIG. 28
  • FIG. 30 is a transverse cross-sectional view showing the compressor of the seventh embodiment according to the present invention
  • FIG. 31 is a cut perspective view showing the principal parts of the compressor of the seventh embodiment according to the present invention.
  • the adhering structure of the upper dead center R 1 and the lower dead center R 2 on the slant compression plate 270 is changed so that a leakage of the fluid in the space of high pressure toward the space of lower pressure can be prevented.
  • the compressor of the seventh embodiment comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P comprises a cylinder assembly 250 , a rotating shaft 260 and a slant compression plate 270 , and a first vane 281 and a second vane 282 .
  • the slant compression plate 270 of ring round disc shape is formed as a sine wave having the upper dead center R 1 and the lower dead center R 2 with a phase difference of 180°, and outer circumferential surface of the slant compression plate 270 is formed as a true circle when projected from plane so as to be sildingly contacted to inner circumferential surface of the cylinder 255 .
  • the upper dead center R 1 is always slidingly contacted to a bottom surface of the first bearing, plate 256 , however the lower dead center R 2 is located to be slidingly contacted to an upper surface of the second bearing plate 257 always.
  • the slant compression plate 270 is formed as a plane surface having a certain area so that the upper dead center R 1 and the lower dead center R 2 are respectively surface contacted to the first and to the second bearing plates 256 and 257 .
  • the slant compression plate 270 may be formed such that the parts on which the upper dead center R 1 and the lower dead center R 2 are located are cut to be a plane, or may be formed as adding the thickness around the upper dead center R 1 and the lower dead center R 2 in order to form the plane upper and lower dead centers R 1 and R 2 .
  • the slant compression plate 270 divides the compression space V inside the cylinder assembly 250 into the first and the second spaces V 1 and V 2 in longitudinal direction, and the plane upper and lower dead centers R 1 and R 2 divide the respective spaces into the suction space and the discharge space.
  • the upper and lower dead centers R 1 and R 2 are formed as planes, are contacted surfaces to the first and the second bearing plates 256 and 257 , and compress the fluid in the first and second spaces V 1 and V 2 , whereby the leakage of the fluid compressed in the compression spaces V 1 p and V 2 p toward the suction spaces V 1 s and V 2 s can be prevented.
  • the contacted area of the slant compression plate 270 and the first and second bearing plates 256 and 257 is increased, and therefore the leakage of the fluid in the compression spaces V 1 p and V 2 p to the suction spaces V 1 s and V 2 s during compressing the fluid can be reduced, whereby the compression efficiency of the compressor can be increased.
  • a compressor in an eighth embodiment according to the present invention will be described as follows with reference to FIGS. 32 through 34.
  • FIG. 32 is a cut perspective view showing principal parts of the compressor in the eighth embodiment according to the present invention
  • FIG. 33 is a longitudinal cross-sectional view showing the compressor of the eighth embodiment according to the present invention
  • FIG. 34 is a detailed cross-sectional view showing the line F-F in FIG. 33.
  • the compressor in the eighth embodiment according to the present invention is constructed such that a labyrinth seal 311 is formed on outer circumferential surface of a slant compression plate 310 and therefore the leakage of compressed fluid between inner circumferential surface of a cylinder 302 and outer circumferential surface of the slant compression plate 310 can be reduced.
  • the slant compression plate 310 is connected to a rotating shaft 304 in the compression space V of the cylinder 302 , and the outer circumferential surface of the slant compression plate 310 is slidingly contacted to the inner circumferential surface of the cylinder 302 .
  • the slant compression plate 310 divides the compression space V in the cylinder 302 into the first and the second spaces V 1 and V 2 .
  • a labyrinth seal 311 having one or more recess of band shape is formed on the outer circumferential surface of the slant compression plate 310 so as to prevent the leakage of the compressed fluid.
  • the shape of cross-section of the labyrinth seal 311 may be formed as a square, as a triangle form(not shown), or as a circular arc(not shown) when projected from the front side.
  • the compression space V 2 p of the second space V 2 is located on the lower part of the suction space V 1 s of the first space V 2
  • the suction space V 2 s of the second space V 2 is located on the lower part of the first space V 1 centering around the slant compression plate 310 .
  • one side of the first and the second spaces V 1 and V 2 becomes the compression space of high pressure, and the other side becomes the suction space of relatively low pressure making the slant compression plate 310 a border.
  • the labyrinth seal 311 is formed on the outer circumferential surface of the slant compression plate 310 , and therefore the labyrinth seal reduces the pressure of the fluid which is likely to leak through the gap between the outer circumferential surface of the slant compression plate and the inner circumferential surface of the cylinder 302 . Therefore, the labyrinth seal can prevent the leakage of the fluid from the high pressure space to the lower pressure space.
  • the labyrinth seal 311 is formed on the outer circumferential surface of the slant compression plate 310 and minimize the leakage of the fluid from the compression space to the suction space through the gap between the inner circumferential surface of the cylinder 302 and the outer circumferential surface of the slant compression plate 310 , whereby the compression efficiency can be increased.
  • a compressor in a ninth embodiment according to the present invention will be described as follows with reference to FIGS. 35 through 37.
  • FIG. 35 is a longitudinal cross-sectional view showing principal parts of the compressor in the ninth embodiment according to the present invention
  • FIG. 36 is a cut perspective view showing the principal parts of the compressor in the ninth embodiment according to the present invention
  • FIG. 37 is a detailed view showing the principal parts of the compressor in the ninth embodiment according to the present invention.
  • the compressor in the ninth embodiment according to the present invention is constructed such that vanes 481 and 482 can be undergo reciprocating movements smoothly irrespective of around components inside the compression space V of a cylinder assembly 455 .
  • the compressor of the ninth embodiment according to the present invention comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P comprises a cylinder assembly 450 , a rotating shaft 460 and a slant compression plate 470 , and a first vane 481 and a second vane 482 .
  • a first bearing plate 430 and a second bearing plate 440 are assembled on an upper side and on a lower side centering around a cylinder 455 , and thereby the compression space V is formed therein.
  • protruded coupling units 435 and 445 of circular shapes which are protruded inward of the compression space V as a certain height, having outer diameters corresponding to the inner diameter of the cylinder 455 are formed on the first and the second bearing plates 430 and 440 .
  • a hub unit 465 is formed inside the compression space V of the cylinder assembly 450 so that the slant compression plate 470 can be installed around the rotating shaft 460 , and hub coupling recesses 437 and 447 are formed on the first and the second bearing plates 430 and 440 so that upper and lower end parts of the hub unit 465 are inserted into the center part of the protruded coupling units 435 and 445 .
  • the slant compression plate 470 is a curved plate of sine wave form on which the upper dead center R 1 and the lower dead center R 2 are located with a phase difference of 180°.
  • the upper and the lower dead centers R 1 and R 2 are respectively contacted to the lower and the upper surfaces of the protruded coupling units 435 and 445 and rotated.
  • a plurality of suction passages 456 and 457 are formed on the cylinder 455 through which the fluid is sucked into the compression space V, and the suction passages 456 and 456 are penetratingly formed on positions apart a certain distance from the upper surface and from the bottom surface of the cylinder 455 so as to be located on the lower or the upper side of the protruded coupling units 435 and 445 .
  • Three surfaces on frame of the vanes 481 and 482 are contacted respectively to the inner circumferential surface of the cylinder 455 , to upper or lower surface of the slant compression plate 470 , and to the outer circumferential surface of the hub unit 465 of the rotating unit 460 in the state of being inserted to vane slots 433 and 443 , and the vanes are undergone linear reciprocating movement in vertical direction according to the rotation of the slant compression plate 470 .
  • front ends of the vanes 481 and 482 are undergone the linear reciprocating movement only inside the compression space V of the cylinder assembly 450 , and therefore the front ends of the vanes 481 and 482 are not interrupted by the upper or lower end part of the cylinder 455 , and by the upper or lower end part of the hub unit 465 , whereby the vanes 481 and 482 are able to be undergone smooth reciprocating movement.
  • the protruded coupling parts 435 and 445 of the first and second bearing plate 430 and 440 are inserted into the compression space V of the cylinder 455 , and therefore the positions of the compression space V of the vane slots 433 and 443 and the cylinder 455 are fitted correctly, whereby the wrong operation of the vanes 430 and 440 caused by the assembling margin can be prevented.
  • a compressor of a tenth embodiment according to the present invention will be described as follows with reference to FIGS. 38 through 42.
  • FIG. 38 is a longitudinal cross-sectional view showing the compressor in the tenth embodiment
  • FIG. 39 is a transverse cross-sectional view showing principal parts of the compressor in the tenth embodiment according to the present invention
  • FIG. 40 is a cut perspective view showing the principal parts of the compressor in the tenth embodiment according to the present invention.
  • the compressor of the tenth embodiment according to the present invention is constructed to locate vanes 581 and 582 which are located on both sides of a slant compression plate 570 on same vertical surface.
  • the compressor of the tenth embodiment according to the present invention comprises a casing C, a motor device unit M, a compression device unit P, and the compression device unit P comprises a cylinder assembly, a rotating shaft 560 and a slant compression plate 570 , and a first vane 581 and a second vane 582 .
  • a first bearing plate 530 and a second bearing plate 540 are assembled centering around a cylinder 555 on an upper and on a lower side inside the cylinder assembly 550 , whereby a compression space V is formed inside.
  • a vane slot 531 is formed on the first bearing plate 530 so that the first vane 581 is inserted and undergone reciprocating movement, and a vane slot 541 is formed on same position of the second bearing plate 540 in vertical direction of the vane slot 531 of the first bearing plate 530 .
  • the vane slot on the first bearing plate 530 and the vane slot 540 on the second bearing plate 540 are formed to be located on same plane as each other.
  • a suction passage 556 and discharge passages 557 and 558 are respectively formed on the cylinder 555 , the discharge passages 557 and 558 are penetratingly formed from the compression space V of the cylinder assembly 550 to a discharge recess 559 formed on one side of the cylinder 555 as shown in FIG. 40. At that time, the first discharge passage 557 and the second discharge passage 558 are formed in a row in vertical direction.
  • the discharge passages 557 and 558 are respectively formed on the upper end part and the lower end part of the cylinder 55 so that the compressed fluid in the first and the second spaces V 1 and V 2 , and that the size of the discharge passage is smaller than thickness of the slant compression plate 570 .
  • discharge valves 591 and 592 for opening/closing the discharge passages 557 and 558 are installed on the discharge recess 559 .
  • suction passage 556 is located on opposite position of the first and the second discharge 557 and 558 centering around the two vanes 581 and 582 .
  • the first and second vanes 581 and 582 are located on same vertical surface centering around the slant compression plate 570 , and the suction passage 556 and the discharge passages 557 and 558 are located on both sides of the vanes 581 and 582 .
  • first and second vanes 581 and 582 are located to be overlapped with some parts of the first and second discharge passages 557 and 558 .
  • springs 583 and 584 are respectively located behind the first and second vanes 581 and 582 so that the two vanes 581 and 582 are adhered to the slant compression plate 570 , and the springs are supported by spring retainers 585 and 586 which are fixed on the first and second bearing plates 530 and 540 .
  • the slant compression plate 570 is rotated inside the compression space V of the cylinder assembly 550 , and accordingly divides and changes the respective spaces of the first and second spaces V 1 and V 2 into the suction spaces V 1 s and V 2 s and compression spaces V 1 p and V 2 p . And the fluid is sucked, compressed, and discharged through the suction passage 556 and through the discharge passages 557 and 558 .
  • FIG. 41 is a transverse cross-sectional view showing principal parts for describing the compression processes of the compressor in the tenth embodiment
  • FIGS. 42A, 42B, 42 C, and 42 D are longitudinal cross-sectional views showing the compression processes of the compressor in the tenth embodiment according to the present invention.
  • the first and second vanes 581 and 582 are located on intermediate position in the compression space V by lowering.
  • the upper dead center R 1 of the slant compression plate 570 reaches to a position P 5 of 180° from the first and second vanes 581 and 582 as shown in FIGS. 41 and 42C, the suction of fluid and the compression of the sucked fluid are processed at the same time in the first space V 1 , and the discharge of the compressed fluid and the suction of fluid are already completed in the second space V 2 .
  • the first and second vanes 581 and 582 are located on lowest position in lower part.
  • the upper dead center R 1 of the slant compression plate 570 reaches to a position P 6 of 135° from the first and second vanes 581 and 582 as shown in FIGS. 41 and 42D, the discharge of the compressed fluid and the suction of the fluid are almost completed in the first space V 1 , and the suction of the fluid is started and the compression of the sucked fluid is processed in the second space V 2 .
  • the first and second vanes 581 and 582 are located on intermediate part of the compression space V by lowering.
  • the discharge of the fluid is made with the phase difference of 180° in the first and second spaces V 1 and V 2 .
  • the discharge fluid from the cylinder assembly as described above is discharged out of the casing C through the discharge pipe 510 as shown in FIG. 38.
  • the fluid of high pressure and high temperature compressed respectively inside the first and second spaces V 1 and V 2 is discharged having phase difference with each other according to the rotation of the rotating shaft 560 , and therefore the fluid is gradually discharged and the pressure pulsation caused by the discharged fluid is reduced.
  • a rotating body having a rotator 561 and the rotating shaft 560 in the motor device unit M is balanced in rotation, and therefore the stable driving is made without the unbalancing of the rotation.
  • volume which is occupied by the components located in the compression space V of the cylinder assembly 550 that is, the dead volume is reduced, whereby the compression efficiency is increased.
  • a compressor of an eleventh embodiment according to the present invention will be described as follows with reference to FIGS. 43 and 44.
  • FIG. 43 is a longitudinal cross-sectional view showing the compressor in the eleventh embodiment
  • FIGS. 44A and 44B are detailed cross-sectional views of principal parts showing the operation state of a vane in the eleventh embodiment according to the present invention.
  • the compressor in the eleventh embodiment according to the present invention comprises two vanes 681 and 682 located on same vertical surface as in the compressor of the tenth embodiment, however a coil spring 685 for supplying an elastic force to the vanes 681 and 682 is constructed as one.
  • the first and second vanes 681 and 682 are located on the same plane in vane slots 631 and 641 of first and second bearing plates 630 and 640 centering around a slant compression plate 670 .
  • the first and second vanes 681 and 682 are supplied the elastic force by one elastic connecting member.
  • the elastic connecting member comprises a first connecting member 683 coupled to the first vane 681 , a second connecting member 684 coupled to the second vane 682 , and a coil spring 685 connecting the first connecting member 683 and the second connecting member 684 .
  • first and second connecting members 683 and 684 of rod or plate form having a certain length are coupled behind the first and second vanes 681 and 682 respectively.
  • the coil spring 685 is inserted into the first and second bearing plates 630 and 640 and into spring penetrating holes 633 , 643 , and 659 penetrating the cylinder 655 , and both ends of the coil spring 685 are coupled to the first and second connecting members 684 respectively.
  • the first and second vanes 681 and 682 are moved up and down in accordance with the movement of the slant compression plate 670 in the state that the first and second vanes are respectively contacted to upper and lower surfaces of the slant compression plate 670 by the elastic force of the coil spring 685 .
  • the first and second vanes 681 and 682 and the coil spring 685 are moved up and down together along with the curved surface of the slant compression plate 670 in accordance with the rotation of the slant compression plate 670 , and changes the first and second spaces V 1 and V 2 into the suction space and the compression space.
  • the coil spring 685 makes the first and second vanes 681 and 682 be adhered to the slant compression plate 670 with a certain force by set elastic force without distortion of tension or contraction.
  • the first and second vanes 681 and 682 are adhered to the slant compression plate 670 with a certain adhering force, and therefore the sealing force of the first and second spaces in which the fluid is sucked and compressed is increased, whereby the compression efficiency is increased.
  • the structure is simple and the number of the components is small, whereby the production cost can be reduced.
  • FIG. 45 is a longitudinal cross-sectional view showing principal parts of the compressor in the twelfth embodiment
  • FIG. 46 is a cut perspective view showing the principal parts of the compressor in the twelfth embodiment
  • FIGS. 47A, 47B, and 47 C are a front view, a side view, and an enlarged perspective view showing the structure of a vane in the compressor of the twelfth embodiment according to the present invention.
  • the compressor of the twelfth embodiment according to the present invention is constructed so that leakage of fluid from a contacted part of a slant compression plate 730 and vanes 760 and 770 during processes of compressing the fluid can be minimized by improving the structure of the vanes 760 and 770 .
  • vanes 760 and 770 included in the compressor of the twelfth embodiment according to the present invention are contacted to the slant compression plate 730 in the compression space inside a cylinder assembly, and a contacted part T of the vanes 760 and 770 is formed so that a curvature of the contacted part T is gradually enlarged from the rotating center of the slant compression plate 730 toward the outer circumferential surface.
  • the vanes 760 and 770 are made to have a first curved part f which is contacted to center part of the slant compression plate 730 , that is, a rotating shaft 720 side; a second curved part e which is contacted to the outer circumferential surface of the slant compression plate 730 , that is, to the inner circumferential surface of a cylinder 715 ; and a contact curved part g which is a part connected between the first curved part f and the second curved part e.
  • a radius of curvature of the vanes 760 and 770 is gradually enlarged from the first curved part f to the second curved part e.
  • the contact curved part g of the vanes 760 and 770 becomes an entire curvature by connecting curves in which the radiuses of curvature are gradually increased from center line c of the vanes 760 and 770 in vertical direction, as shown in FIG. 47C.
  • the contact curved part g is formed such that shape of section when cut from a certain position in vertical direction of the vanes 760 and 770 is a curvature by connecting tangent lines of circles, in which radiuses of curvature are gradually increased from the center line c centering around the center line c.
  • a lower end line h which is a center of the contact curved part g is a straight line making a right angle with both side surfaces d and d′ of the vanes 760 and 770 , and a connecting line k which is connecting ends of the first curved part f and ends of the second curved part d is formed to be slanted against the lower end line h.
  • vanes 760 and 770 as described above are respectively inserted into slots formed on the cylinder assembly 710 . Therefore, the contacted part T is contacted to the slant compression plate 730 , and the both side surfaces d and d′ are respectively contacted to a hub unit of the rotating shaft 720 and to inner circumferential wall of the cylinder 715 .
  • FIGS. 48A and 48B are plane views showing operating states of the compressor in the twelfth embodiment
  • FIG. 49 is a plane view showing contacting state of the vane in accordance with the rotation of the slant compression plate in the compressor of the twelfth embodiment
  • FIG. 50 is a detailed view of the principal parts showing contacting state of the slant compression plate and the vane in the compressor of the twelfth embodiment according to the present invention.
  • the contacted part T that is, a part including the first and second curved parts f and e and the contact curved part g, on which the vanes 760 and 770 and the slant compression plate 730 are contacted, is formed to correspond to the thickness of the first and second vanes 760 and 770 and to the difference between the curvatures of an upper curve a and a lower curve b, whereby a gap between the slant compression plate 730 and the first and second vanes 760 and 770 can be minimized.
  • vanes 760 and 770 are located within a range of waveform curved surface of the slant compression plate 730 , that is from the front end of the upper dead center R 1 to the front end of the lower dead center R 2 , then a contact line, on which the contact curved part g on the other side of the vane and the waveform curved surface of the slant compression plate 730 are contacted, is made.
  • the slant compression plate 730 is rotated inside the compression space V of the cylinder assembly 710 by the rotation of the rotating shaft 720 , and at the same time, the vanes 760 and 770 contacted to the slant compression plate 730 are moved together, whereby the fluid is sucked, compressed, and discharged continuously.
  • the curvature on the side of the first curved part f is smaller than that of the second curved part e, as in the outer curve b having large curvature than that of the inner curve a of the slant compression plate 730 . Therefore, the gap between the slant compression plate 730 and the vanes 760 and 770 for dividing and changing the suction space of lower pressure and the compression space of higher pressure can be minimized.
  • the contacted part of the vanes 760 and 770 which makes the sealing with the slant compression plate 730 by contacting the slant compression plate 730 , is formed to be corresponded to the thickness of the vanes 760 and 770 and to the curved surface of sine wave form formed by the extended curved surface which connects the inner curve a and the outer curve b of the slant compression plate 730 , whereby the gap between the slant compression plate 730 and the vanes 760 and 770 is minimized. Therefore, the leakage of the fluid caused by the pressure difference between the suction space of lower pressure and the compression space of higher pressure can be prevented, and the compression efficiency can be increased.
  • a compressor of thirteenth embodiment according to the present invention will be described as follows with reference to FIGS. 51 through 54.
  • FIG. 51 is a cut perspective view showing principal parts of the compressor of the thirteenth embodiment
  • FIG. 52 is a detailed view showing a state of rotating the compressor of FIG. 51 as 180°
  • FIG. 53 is a plane view showing the principal parts of the thirteenth embodiment according to the present invention.
  • the vanes 860 and 870 of square plate having a certain thickness has one side surface contacted to a hub unit 825 of the rotating shaft 820 , and other side surface contacted to inner circumferential surface of the cylinder 815 . And the vanes 860 and 870 divide compression spaces V 1 p and V 2 p and suction spaces V 1 s and V 2 s when the fluid is compressed.
  • the both side surfaces of the vanes 860 and 870 are formed as curved surfaces same as the hub unit 825 and as the inner circumferential surface of the cylinder 815 so as to be contacted its surfaces to the hub unit 825 and to the inner circumferential surface of the cylinder 815 .
  • a plate contact curved surface unit 861 having a curvature which is reduced toward outer side as in the twelfth embodiment is formed on the part which is contacted to the slant compression plate 830 , and an axial contact curved surface unit 862 of concave shape is formed on the part which is contacted to the hub unit 825 of the rotating shaft 820 .
  • a cylinder contact curved surface unit 863 of convex shape is formed on the part which is contacted to the inner circumferential surface of the cylinder 815 .
  • the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are formed to have same radiuses of curvature through the entire part of the vanes 860 and 870 in vertical direction.
  • vane slots 817 in which the vane 860 is inserted, are formed on upper and lower surfaces of a cylinder assembly 810 respectively as shown in FIG. 52, and both ends of the vane slots are formed to have same shapes as those of the both side surfaces of the vane 860 .
  • FIG. 54 is a perspective view of the principal parts showing a modified embodiment of the axial contact curved surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
  • the curved surface which is contacted to the rotating shaft is formed to have different shapes on intermediate part and both sides parts.
  • the axial contact curved surface unit 862 ′ same as the outer curved surface of the rotating shaft is formed on the center part so as to be contacted its surface to the outer circumferential surface of the rotating shaft, and plane surface units 862 ′ are formed on both sides of the axial contact curved surface unit 862 ′.
  • the first and second vanes 860 and 870 are inserted into the vane slots 817 of the cylinder assembly 810 , and moved up and down in the state that the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are contacted its surfaces to the outer circumferential surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815 according to the rotation of the slant compression is rotated.
  • the vanes 860 and 870 divide the first and second spaces V 1 and V 2 of the compression space V in the cylinder assembly 810 into the compression spaces V 1 p and V 2 p and suction spaces V 1 s and V 2 s.
  • the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 located on both sides of the first and second vanes 860 and 870 are contacted to the outer circumferential surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815 , and therefore the leakage of the fluid from the compression spaces V 1 p and V 2 p to the suction spaces V 1 s and V 2 s in the first and second spaces V 1 and V 2 is minimized.
  • the leakage of the pressure from the higher pressure space to the lower pressure space can by minimized by the contact structure of the vanes 860 and 870 , the rotating shaft 820 , and the cylinder 815 , whereby the compression efficiency of the compressor can be increased.
  • a slant compression plate of true circle shape is installed inside the cylinder assembly and compresses the fluid, and therefore an additional balance weight is not needed. Therefore, the vibration and noise which may be generated during the fluid compression processes can be reduced, and at the same time, sufficient driving force can be assured with the motor devices having relatively small capacity.
  • the volume of the slant compression plate which is installed inside the cylinder assembly is relatively small, and therefore the dead volume in the compression space can be reduced.
  • the fluid can be compressed and discharged in both spaces centering around the slant compression plate at the same time, whereby high compression efficiency can be made with a simple structure

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US10/258,395 2000-04-25 2001-04-25 Compressor Abandoned US20030108438A1 (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR2000-21955 2000-04-25
KR1020000021955A KR100324771B1 (ko) 2000-04-25 2000-04-25 2단 압축용 밀폐형 압축기
KR2000-26760 2000-05-18
KR1020000026760A KR20010105814A (ko) 2000-05-18 2000-05-18 압축기
KR10-2000-0085808A KR100394239B1 (ko) 2000-12-29 2000-12-29 압축기의 베인 구조
KR2000-85808 2000-12-29

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EP (1) EP1276993A4 (zh)
JP (1) JP2003532008A (zh)
CN (1) CN1430705A (zh)
AU (1) AU5679801A (zh)
BR (1) BR0110375B1 (zh)
CA (1) CA2407403A1 (zh)
WO (1) WO2001081765A1 (zh)

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US20040037706A1 (en) * 2000-05-01 2004-02-26 Greg Hahn Compressor utilizing low volt power tapped from high volt power
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US20060171819A1 (en) * 2005-01-31 2006-08-03 York International Corporation Compressor discharge muffler
US20080145242A1 (en) * 2006-12-01 2008-06-19 Seibel Stephen M Dual chamber discharge muffler
US20080166252A1 (en) * 2006-12-01 2008-07-10 Christopher Stover Compressor with discharge muffler
US20100011806A1 (en) * 2008-07-16 2010-01-21 Lg Electronics Inc. Motor, compressor and air conditioning system having the same
US20100226796A1 (en) * 2005-12-27 2010-09-09 Daikin Industries, Ltd. Rotary compressor
US20130259725A1 (en) * 2012-03-27 2013-10-03 Fujitsu General Limited Rotary compressor
WO2014110659A1 (en) 2013-01-16 2014-07-24 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US20150192128A1 (en) * 2013-01-16 2015-07-09 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US20150369526A1 (en) * 2013-02-07 2015-12-24 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor and refrigeration device
EP3070333A1 (en) 2015-03-20 2016-09-21 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US9964109B2 (en) 2015-12-10 2018-05-08 Albert's Generator Services Inc. Apparatus for driving fluid having a rotating cam and rocker arm
CN108087492A (zh) * 2016-11-23 2018-05-29 上海海立电器有限公司 一种压缩机
CN113550973A (zh) * 2021-08-26 2021-10-26 安徽美芝精密制造有限公司 曲轴、压缩机及制冷设备

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CN100359178C (zh) * 2003-05-20 2008-01-02 乐金电子(天津)电器有限公司 密闭型压缩机的防止气体泄露装置
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US20040037706A1 (en) * 2000-05-01 2004-02-26 Greg Hahn Compressor utilizing low volt power tapped from high volt power
US6964558B2 (en) * 2000-05-01 2005-11-15 Scroll Technologies Compressor utilizing low volt power tapped from high volt power
US6893241B2 (en) 2001-11-06 2005-05-17 Lg Electronics Inc. Compressor
US20040009084A1 (en) * 2001-11-06 2004-01-15 Kwang-Cik Yang Compressor
US20060078441A1 (en) * 2004-09-30 2006-04-13 Sanyo Electric Co., Ltd. Compressor
US7540724B2 (en) * 2004-09-30 2009-06-02 Sanyo Electric Co., Ltd. Compression member and vane of a compressor
US20060171819A1 (en) * 2005-01-31 2006-08-03 York International Corporation Compressor discharge muffler
US7578659B2 (en) 2005-01-31 2009-08-25 York International Corporation Compressor discharge muffler
US20100226796A1 (en) * 2005-12-27 2010-09-09 Daikin Industries, Ltd. Rotary compressor
US8430648B2 (en) * 2005-12-27 2013-04-30 Daikin Industries, Ltd. Rotary compressor
US8057194B2 (en) 2006-12-01 2011-11-15 Emerson Climate Technologies, Inc. Compressor with discharge muffler attachment using a spacer
US20080166252A1 (en) * 2006-12-01 2008-07-10 Christopher Stover Compressor with discharge muffler
US20080145242A1 (en) * 2006-12-01 2008-06-19 Seibel Stephen M Dual chamber discharge muffler
US9404499B2 (en) 2006-12-01 2016-08-02 Emerson Climate Technologies, Inc. Dual chamber discharge muffler
US20100011806A1 (en) * 2008-07-16 2010-01-21 Lg Electronics Inc. Motor, compressor and air conditioning system having the same
US9157437B2 (en) * 2012-03-27 2015-10-13 Fujitsu General Limited Rotary compressor with oiling mechanism
US20130259725A1 (en) * 2012-03-27 2013-10-03 Fujitsu General Limited Rotary compressor
US9695821B2 (en) * 2013-01-16 2017-07-04 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US20150192128A1 (en) * 2013-01-16 2015-07-09 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US8985980B2 (en) 2013-01-16 2015-03-24 Alberts Generator services inc. Compressor with rotating cam and sliding end vanes
EP2946114A4 (en) * 2013-01-16 2016-10-12 Albert S Generator Services Inc COMPRESSORS WITH ROTATING CAMS AND SLIDING END SCREENS
WO2014110659A1 (en) 2013-01-16 2014-07-24 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US20150369526A1 (en) * 2013-02-07 2015-12-24 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor and refrigeration device
EP3070333A1 (en) 2015-03-20 2016-09-21 Albert's Generator Services Inc. Compressor with rotating cam and sliding end vanes
US9964109B2 (en) 2015-12-10 2018-05-08 Albert's Generator Services Inc. Apparatus for driving fluid having a rotating cam and rocker arm
CN108087492A (zh) * 2016-11-23 2018-05-29 上海海立电器有限公司 一种压缩机
CN113550973A (zh) * 2021-08-26 2021-10-26 安徽美芝精密制造有限公司 曲轴、压缩机及制冷设备

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EP1276993A4 (en) 2003-10-29
BR0110375B1 (pt) 2010-06-29
BR0110375A (pt) 2004-02-25
JP2003532008A (ja) 2003-10-28
CN1430705A (zh) 2003-07-16
CA2407403A1 (en) 2001-11-01
WO2001081765A1 (en) 2001-11-01
AU5679801A (en) 2001-11-07
EP1276993A1 (en) 2003-01-22

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