Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
• • 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
  • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
  • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
• • 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
  • F04C29/0021—Systems for the equilibration of forces acting on the pump

Definitions

• the present invention relates to a compressor, and more particularly, to a compressor which can reduce vibration and noise by applying one directional force to a rotational shaft and thus by preventing axial directional fluctuation of the rotational shaft.
• a compressor is a device for converting mechanical energy into compression energy of compressible fluid, and is classified into a reciprocating compressor, a scroll compressor, a centrifugal compressor, a rotary compressor, and etc. by a compression method.
• the rotary compressor is a compressor for sucking, compressing, and discharging fluid by rotating a body of rotation and thus consecutively changing a suction region and a compression region under a state that a vane is inserted into the body of rotation and thus an inner space of a cylinder is divided into the suction region and the compression region.
• Figure 1 is a longitudinal section view showing main parts of a compressor in accordance with the conventional art
• Figure 2 is a perspective view showing a compression unit of the conventional compressor
• the conventional compressor comprises: a hermetic container 10 to which a suction pipe 35 and a discharge pipe (not shown) are connected; a electronic driving unit 12 installed in the hermetic container 10 for generating a rotation force; and a compression unit 14 installed in the hermetic container 10 with a predetermined interval from the driving unit 12 for sucking, compressing, and discharging compressible fluid by the rotation force generated from the driving unit 12.
• the driving unit 12 is composed of a stator 16 closely fixed to an inner circumference sur ace of the hermetic container 10, and a rotor 18 installed to have a maintain a constant air gap from the inner circumference surface of the stator 16 for generating a rotation force by electromagnetic interaction with the stator 16.
• the compression unit 14 comprises: a cylinder assembly 31 installed in the hermetic container 10 and forming a compression space V where compressible fluid sucked from outside is compressed; a rotational shaft 20 rotatably fixed to the cylinder assembly 31 and closely fixed to an inner circumference surface of the rotor 18 thus to be rotated together when the rotor 18 is rotated; a compression member 23 rotated by being engaged to the rotational shaft 20 and for dividing the compression space V in the cylinder assembly 31 into a first space V1 and a second space V2; and first and second vanes 60 and 70 respectively contacted on upper and lower surfaces of the compression member 23 and for dividing the first and second spaces V1 and V2 into suction regions Via, V2a and compression regions V1 b, V2b by being reciprocated towards inner and outer direction of the compression space V along the upper and lower surfaces of the compression member 23 when the compression member 23 is rotated.
• the cylinder assembly 31 comprises: a cylinder 30 formed with a cylindrical shape and having a suction flow path 36 through which gas is sucked to the first and second spaces V1 and V2, the suction flow path 36 connected to the suction pipe 35; and first and second bearing plates 40 and 50 fixed to both sides of the cylinder 30 thus to form a compression space V with the cylinder 30 and for supporting the rotational shaft 20.
• the first and second bearing plates 40 and 50 are formed as a disc shape having a predetermined thickness and area, and comprises: journal portions 42 and 52 prolonged respectively to have a predetermined height and an outer diameter and having a penetrated center for rotatably inserting the rotational shaft 20; first and second vane slots 44 and 54 formed by penetrating the first and second bearing plates 40 and 50 at one side of the journal portions 42 and 52 for inserting the first and second vanes 60 and 70; discharge flow paths 46 and 56 formed at one side of the first and second vane slots 44 and 54 for discharging gas compressed in the compression space V of the cylinder assembly 31. Also, a first discharge muffler 45 and a second discharge muffler 55 are respectively mounted at upper and lower sides of the first and second bearing plates 40 and 50 by being covered.
• the rotational shaft 20 comprises: a shaft portion 21 formed to have a predetermined outer diameter and a length and inserted into the journal portions 42 and 52 of the first and second bearing plates 40 and 50; a supporting portion 22 integrally enlarged at a circumference of the shaft portion 21 thus to be supported on inner surfaces of the first and second bearing plates 40 and 50, and engaged to the compression member 23 inside the cylinder assembly 31 ; an oil flow path 25 penetratingly formed inside of the shaft portion 21 of the rotational shaft 20, and an oil feeder 24 formed at a lower end of the rotation shaft 20 for supplying oil contained at a lower portion of the hermetic container 10 to an upper side of the hermetic container 10.
• the supporting portion 22 of the rotational shaft 20 is concentric with the shaft portion 21 of the rotational shaft 20.
• a radial load of the rotational shaft 20 is supported on a radial bearing surface R of the journal portions 42 and 52 of the first and second bearing plates 40 and 50, and a axial load of the rotational shaft 20 is supported on a thrust bearing surface T of the inner surfaces of the first and second bearing plates 40 and 50.
• a surface pressure is applied as the arrow direction of Figure 3 at a sliding part between the supporting portion 22 of the rotational shaft 20 and a thrust bearing surface T of the first and second bearing plates 40 and 50, and friction of a predetermined size is generated at
• the compression member 23 is formed as a disc shape in a plane view so that an outer circumference surface thereof can have a sliding contact with an inner circumference surface of the cylinder 30, and formed as a cam shape of sine wave having the same thickness from the inner circumference surface to the outer circumference surface in a laterally projective view. According to this, a side having an upper dead point D1 of the compression member 23 slidably contacts with a lower surface of the first bearing plate 40, and a side having a lower dead point D2 slidably contacts with an upper surface of the second bearing plate 50.
• the first and second vanes 60 and 70 are formed as a rectangular plate shape and adhere to the cam surface of the compression member 23 in the compression space V of the cylinder assembly 31.
• the vanes reciprocate up and down along a height of the cam surface of the compression member 23 when the compression member 23 is rotated, and thus divide the compression spaces V1 and V2 into the suction regions Via, V2a and the compression regions V1 b, V2b.
• the first and second vanes 60 and 70 are elastically supported by an elastic supporting member 90 mounted at the first and second bearing plates 40 and 50.
• the first space V1 located at an upper portion of the compression member 23 is divided into the suction region Via and the compression region V1 b on the basis of the upper dead point D1 of the compression member 23 and the first vane 60.
• the second space V2 located at a lower portion of the compression member 23 is divided into the suction region V2a and the compression region V2b on the basis of the lower dead point D2 and the second vane 70.
• capacities of the suction regions Via, V2a and the compression regions V1 b, V2b of the first and second spaces V1 and V2 are varied as the upper dead point D1 and the lower dead point D2 of the compression member 23 move by rotation of the compression member 23.
• the first and second vanes 60 and 70 respectively reciprocate in different directions on the basis of the compression member 23.
• the fluid discharged outside the cylinder assembly 31 passes through the first and second discharge mufflers 45 and 55, and the fluid is discharged outside the hermetic container 10 through the discharge pipe.
• gas introduced into the cylinder assembly 31 is compressed by a changed volume by the movement the compression member 23 and the first and second vanes 60 and 70. According to this, gas suction, compression, and discharge are performed in the first and second spaces V1 and V2 at different time point with phase difference of 180°.
• the second vane 70 in the second space V2 is located near the upper dead point D1 of the compression member 23. According to this, a compression cycle of the second space V2 is in a process just before or after the discharge process.
• the compression cycle of the second space V2 is in the suction and compression processes. Accordingly, a pressure of the suction region Via and the compression region V1 b of the first space V1 is different from a pressure of the suction region V2a and the compression region V2b of the second space V2.
• an object of the present invention is to provide a compressor, in which volumes of compression spaces divided by a compression member are differently formed thus to have different pressures in each compression space and a axial load is applied to a rotational shaft from a high pressure space towards a low pressure space thus to prevent fluctuation of the rotational shaft and the compression member, thereby preventing vibration and noise.
• Another object of the present invention is to provide a compressor, in which a space portion having a predetermined volume is formed at a sliding part between a supporting portion of a rotational shaft and a bearing plate, and a connection passage for connecting outside of a cylinder assembly and the space portion is formed, thereby reducing a frictional loss of the sliding part generated in accordance with that a surface pressure of the sliding part between the rotational shaft and the bearing plate is increased by a axial load of the rotational shaft due to pressure difference of each compression space.
• a compressor comprising: a cylinder arranged in a hermetic container for forming a compression space therein; a rotational shaft fixed to a driving force generating means and for transmitting a rotational force generated from the driving force generating means; bearing plates mounted on both side of the cylinder for supporting a axial load and a radial load of the rotational shaft; and a compression member arranged in the cylinder by being fixed to a circumference of the rotational shaft and for dividing the compression space of the cylinder into a first space and a second space, varying capacities of the first and second spaces by being rotated for sucking and compressing fluid, wherein each capacity of the first and second spaces is formed to be different from each other for applying axial directional force to the rotational shaft and the compression member.
• a space portion having a predetermined volume is formed between a supporting portion of the rotational shaft and the bearing plate, and a connection passage for connecting outside of the cylinder assembly to the space portion is formed in order to introduce discharged gas outside the cylinder assembly into the space portion.
• Figure 1 is a longitudinal section view showing main parts of a compressor in accordance with the conventional art
• Figure 2 is a perspective view showing the conventional compressor by partially cutting
• Figure 3 is a partial section view showing a state that a surface pressure is applied between a bearing plate and a rotational shaft of the conventional compressor;
• Figure 4 is a schematic view showing a compression unit of the conventional compressor and showing that the rotational shaft and the compression member fluctuate downwardly by a pressure difference of each compression space when the compressor operates;
• Figure 5 is a schematic view showing the compression unit of the conventional compressor and showing that the rotational shaft and the compression member fluctuate upwardly by a pressure difference of each compression space when the compression member operates;
• Figure 6 is a longitudinal section view showing main parts of the compressor according to one embodiment of the present invention.
• Figure 7 is a disassembled perspective view showing a compression unit of the compressor according to one embodiment of the present invention by partially cutting;
• Figure 8 is a longitudinal section view showing the compression unit of the compressor according to one embodiment of the present invention.
• Figure 9 is a longitudinal section view showing an operation state of the compressor according to one embodiment of the present invention.
• Figure 10 is a longitudinal section view showing an operation state of the compressor according to one embodiment of the present invention.
• Figure 11 is a longitudinal section view showing a compression unit of a compressor according to another embodiment of the present invention
• Figure 12 is a longitudinal section view showing a compression unit of a compressor according to still another embodiment of the present invention.
• Figure 6 is a longitudinal section view showing main parts of the compressor according to one embodiment of the present invention.
• FIG. 7 is a disassembled perspective view showing a compression unit of the compressor according to one embodiment of the present invention by partially cutting.
• the compressor comprises: a hermetic container 10 to which a suction pipe 36 and a discharge pipe (not shown) are respectively connected; a driving force generating means arranged in the hermetic container 10 and for generating a rotation force; and a compression unit 14 for sucking, compressing, and discharging compressible fluid by the driving force generated from the driving force generating means.
• the compressor In the compressor, fluid is sucked into the compression unit 14, compressed, and discharged into the hermetic container 10. The fluid is discharged outside the hermetic container 10 through the discharge pipe engaged to the hermetic container 10. Accordingly, if the compressor is operated, a predetermined pressure is always applied in the hermetic container 10 by the discharged gas.
• the compression unit 14 comprises: a cylinder assembly 31 installed in the hermetic container 10 and forming a compression spaces V where compressible fluid sucked from outside is compressed; a rotational shaft 120 for transmitting a rotation force of the driving force generating means; a compression member 23 arranged in the cylinder assembly 31 by being fixed to a periphery of the rotational shaft 120 and having a cam surface of a predetermined curvature so that a capacity of the compression space V can be changed at the time of rotation with the rotational shaft 120, the compression member for dividing the compression space V into a first compression space V1 and a second compression space V2 ; and first and second vanes 60 and 70 for dividing the first and second spaces V1 and V2 into suction regions and compression regions by being reciprocated towards inner and outer side directions of the cylinder 30 along the cam surface of the compression member 23 when the compression member 23 is rotated.
• the cylinder assembly 31 comprises: a cylinder 30 formed with a cylindrical shape; and first and second bearing plates 40 and 50 fixed to both sides of
• the first and second bearing plates 40 and 50 are formed as a disc shape having a predetermined thickness and area, and comprises: journal portions 42 and 52 prolonged to have a predetermined height and an outer diameter and having a penetrated center for rotatably inserting the rotational shaft 120; and first and second vane slots 44 and 54 penetratingly formed in the bearing plates 40 and 50 for slidably inserting the first and second vanes 60 and 70.
• the rotational shaft 120 formed to have a predetermined outer diameter and a length comprises: a shaft portion 121 inserted into the journal portions 42 and 52 of the first and second bearing plates 60 and 70 and for supporting a radial load of the rotational shaft 120 on the journal portions 42 and 52 of the first and second bearings 60 and 70; and supporting portions 122 and 123 integrally formed at a periphery of the shaft portion 121 thus for supporting a axial load of the rotational shaft 120 on inner surfaces of the first and second bearing plates 40 and 50, and engaged to the compression member 23 in the cylinder assembly 31. Accordingly, the radial load of the rotational shaft 120 is supported on the journal portions 42 and 52 of the first and second bearing plates 40 and 50, and the axial load of the rotational shaft 120 is supported on the inner surfaces of the first and second bearing plates 40 and 50.
• the supporting portions 122 and 123 is divided into a first supporting portion 122 located in the first space V1 and a second supporting portion 123 located in the second space V2. Also, the first and second supporting portions 122 and 123 are formed to be concentric with the shaft portion 121 of the rotational shaft 120. In the meantime, a capacity of the second space V2 is formed to be larger than that of the first space V1 of the compression space V of the cylinder assembly 31 in order to apply the axial directional force to the rotational shaft 120.
• a diameter L1 of the first supporting portion 122 is formed to be larger than a diameter L2 of the second supporting portion 123.
• the compression member 23 Since the pressure of compressed gas applied in the second space V2 is greater than the pressure applied in the first space V1 , the compression member 23 is pushed upwardly by the pressure difference and thus the axial directional force is applied to the rotational shaft 120 in the upper direction. According to this, the first supporting portion 122 of the rotational shaft 120 is rotated by adhering to a lower surface of the first bearing plate 40 more closely, thereby preventing an axial directional fluctuation of the rotational shaft 120.
• the capacity of the first space V1 can be greater than that of the second space V2 thus to apply downward force to the rotational shaft 120, and the diameter of the second supporting portion 123 can be formed to be larger than that of the first supporting portion 122 of the rotational shaft 120 so that the second supporting portion 123 can be rotated by adhering to a lower surface of the second bearing plate 50.
• the compression member 23 is formed as a disc shape in a plane view so that an outer circumference surface thereof can have a sliding contact with an inner circumference surface of the cylinder 30, and formed as a cam surface of sine wave having the same thickness from the inner circumference surface to the outer circumference surface at the time of a lateral projection. According to this, a side having an upper dead point of the compression member 23 slidably rotates a lower surface of the first bearing plate 40, and a side having a lower dead point slidably rotates an upper surface of the second bearing plate 50.
• the first and second vanes 60 and 70 are formed as a rectangular plate shape and adhere to upper and lower lateral surfaces of the compression member 23 in the compression space V of the cylinder assembly 31 , outer circumference surfaces of the first and second supporting portions 122 and 123, and an inner circumference surface of the cylinder 30.
• the vanes reciprocate up and down along a height of the cam surface of the compression member 23 when the compression member 23 is rotated in the compression space of the cylinder assembly 31 , and thus divide the compression spaces V1 and V2 into the suction regions and the compression regions.
• widths of the first and second vanes 60 and 70 are varied according to diameters of the first and second supporting portions 122 and 123. Accordingly, when a diameter of the first supporting portion 122 is larger than that of the second supporting portion 123, the width of the first vane 60 is formed to be narrower than the width of the second vane 70. On the contrary, when a diameter of the first supporting portion 122 is smaller than that of the second supporting portion 123, the width of the first vane 60 is formed to be wider than that of the second vane 70.
• the first space V1 located at an upper portion of the compression member 23 is divided into the suction region and the compression region on the basis of the upper dead point of the compression member 23 and the first vane 60.
• the second space V2 located at a lower portion of the compression member 23 is divided into the suction region and the compression region on the basis of the lower dead point and the second vane 70.
• first and second vanes 60 and 70 reciprocate towards different directions along the height of the cam surface on the basis of the compression member 23.
• the fluid discharged outside the cylinder assembly 31 passes through inside of the hermetic container 10, and is discharged outside the hermetic container 10 through the discharge pipe (not shown). Also, as the rotational shaft 120 is rotated, oil contained in the lower portion of the hermetic container 10 is sucked by an oil feeder mounted at a lower end of the rotational shaft 120 through the oil flow path, and dispersed at an upper end portion of the rotational shaft 20, thereby being supplied to sliding components in the compressor.
• the compression member 23 is pushed upwardly with the rotational shaft 120 by the pressure difference of the first and second spaces V1 and V2. Accordingly, the first supporting portion 122 of the rotational shaft 120 closely adheres to the lower surface of the first bearing plate 40, and the second supporting portion 123 forms a predetermined interval t at the upper surface of the second bearing plate 50. Also, the first supporting portion 122 of the rotational shaft 120 is rotated by closely adhering to the lower surface of the first bearing plate 40 under a state that the rotational shaft 120 is pushed upward with a constant height by the pressure of the second space V2 which is greater than that of the first space
• Figure 11 is a longitudinal section view showing a compression unit of a compressor according to another embodiment of the present invention.
• a capacity of the second space V2 is formed to be greater than that of the first space V1 so that pressures of gas compressed in the first and second spaces V1 and V2 can be different to each other.
• a pressure of the second space V2 is larger than that of the first space V1 , and by the pressure difference of the first and second spaces V1 and V2, force is applied to the rotational shaft 120 towards the upper direction.
• a surface pressure of a sliding part between the first supporting portion 122 and the inner surface of the first bearing plate 40 is increased. According to this, frictional loss of the sliding part is increased and abrasion of the components is generated thus to lower the performance of the compressor.
• a space portion 48 having a predetermined width and depth is concavely formed in the lower surface of the first bearing plate 40, and a connection passage 49 for introducing discharged gas out of the cylinder assembly 31 into the space portion 48 and for introducing lubrication oil out of the cylinder assembly 31 into the space portion 48 is formed by penetrating the first bearing plate 40.
• a predetermined pressure is applied in the space portion 48.
• the pressure is applied in the opposite direction to the surface pressure applied at the lower surface of the first bearing plate 40 and the first supporting portion 122, so that a size of the surface pressure applied to the lower surface of the first bearing plate 40 and the supporting portion 122 can be reduced.
• lubrication oil out of the cylinder assembly 31 is introduced into the space portion 48 through the connection passage 49, and the introduced oil is supplied to the sliding part between the lower surface of the first bearing plate 40 and the first supporting portion 122, so that friction of the sliding part between the lower surface of the first bearing plate 40 and the first supporting portion 122 can be reduced.
• the space portion 48 can be formed as a ring shape at the time of a plan projection, or can be formed as a circular arc shape. Also, the space portion 48 is not limited to said ring shape or the circular arc shape, but can be formed as various shapes. It is preferable that a plurality of space portions are formed with the same interval without being eccentric from the center of the rotational shaft 120.
• the connection passage 49 is preferably formed at the first bearing plate 40 by penetrating thereto towards the shaft direction, and an area thereof is smaller than a horizontal area of the space portion 48. Also, a processing is easy when sectional areas of the connection passage 49 are equally formed from outside of the first bearing plate 40 to the space portion 48. However, the sectional areas of the connection passage can be increased towards the space portion 48 in order to smoothly introduce discharged gas and oil out of the cylinder assembly 31 into the space portion 48.
• the rotational shaft 120 is rotated by being inserted into the journal portions 42 and 52 of the first and second bearing plates 40 and 50.
• the shaft portion 121 of the rotational shaft 120 is rotated by being supported on the journal portions 42 and 52 of the first and second bearing plates 40 and 50, and both sides of the first and second supporting portions 122 and 123 of the rotational shaft 120 are supported on the upper and lower surfaces of the first and second bearing plates 40 and 50.
• a surface pressure of a predetermined size is applied to sides of the first and second supporting portions 122 and 123 of the rotational shaft 120 which are opposite
• the space portion 48 at the lower surface of the first bearing plate 40, the area of the sliding part with the first supporting portion 122 is reduced. Also, a part of the discharged gas discharged into the hermetic container 10 is introduced into the space portion 48 through the connection passage 49 which connects the space portion 48 to outside of the cylinder assembly 31 through the connection passage 49, so that a predetermined pressure is formed in the space portion 48. By the pressure of the space portion 48, the surface pressure between the first supporting portion 122 of the rotational shaft 120 and the first bearing plate 40 is reduced.
• lubrication oil out of the cylinder assembly 31 is introduced into the space portion 48 through the connection passage 49, and the oil introduced into the space portion 48 is supplied to the sliding part between the lower surface of the first bearing plate 40 and the first supporting portion 122 of the rotational shaft 120 thus to perform a lubrication operation. According to this, friction of the sliding part is reduced thus to improve efficiency of the compressor. In the meantime, when a downward load is applied to the rotational shaft
• the space portion 48 having a predetermined width and depth and the connection passage 49 which connects the space portion 48 to outside of the cylinder assembly 31 can be formed at the second bearing plate 50.
• the space portion 48 and the connection passage 49 are preferably formed at a part having a greater adhesion force among the sliding part of the first bearing plate 40 and the first supporting portion 122 and the sliding part of the second bearing plate 50 and the second bearing portion 123.
• the space portion 48 can be formed at said two sliding parts, respectively.
• Figure 12 is a longitudinal section view showing a compression unit of a compressor according to still another embodiment of the present invention.
• a capacity of the second space V2 is formed to be greater than that of the first space V1 so that pressures of gas compressed in the first and second spaces V1 and V2 can be different to each other.
• the pressure difference of the first and second spaces V1 and V2 is formed to be greater than that of the first space V1 so that pressures of gas compressed in the first and second spaces V1 and V2 can be different to each other.
• the compression space in the cylinder assembly is divided by the compression member, compression capacities thereof are differently formed, and thus pressures applied in the respective compression spaces are differently formed. According to this, a axial load is applied to the rotational shaft towards one direction by the pressure difference of the compression spaces, thereby preventing longitudinal fluctuation of the rotational shaft and thus reducing vibration and noise of the compressor.
• the space portion having a predetermined volume is formed at the sliding part between the thrust bearing portion of the bearing plate and the supporting portion of the rotational shaft where the axial load of the rotational shaft is rotatably supported, and the connection passage for connecting outside of the cylinder assembly and the space portion is formed. According to this, frictional loss is reduced by reducing the surface pressure of the sliding part and abrasion of the components is reduced, thereby increasing the performance of the compressor.

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

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Citations (3)

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• 2002
  • 2002-10-25 KR KR1020020065576A patent/KR20040036975A/ko not_active Application Discontinuation
• 2003
  • 2003-07-23 WO PCT/KR2003/001470 patent/WO2004038226A1/en not_active Application Discontinuation
  • 2003-07-23 AU AU2003250561A patent/AU2003250561A1/en not_active Abandoned

Patent Citations (3)

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