US20050180871A1 - Fluid compressor - Google Patents
Fluid compressor Download PDFInfo
- Publication number
- US20050180871A1 US20050180871A1 US10/982,927 US98292704A US2005180871A1 US 20050180871 A1 US20050180871 A1 US 20050180871A1 US 98292704 A US98292704 A US 98292704A US 2005180871 A1 US2005180871 A1 US 2005180871A1
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- United States
- Prior art keywords
- rotation shaft
- pump
- oil passage
- pump member
- oil
- 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
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Classifications
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- 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
- F04B39/02—Lubrication
-
- 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
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
- F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
Definitions
- the present invention relates to a fluid compressor comprising a rotation shaft having an oil passage, and particularly to the one suitably used as a coolant compressor for cooling or air conditioning, or a fluid compressor for air or the like.
- a conventional fluid compressor is disclosed, for example, in JP-A-2001-349291.
- a scroll compressor shown in FIG. 1 of JP-A-2001-349291 comprises in its sealed container, a compression mechanism for compressing fluid, a rotation shaft connected to the compression mechanism and having an oil passage, a motor for driving the rotation shaft, a main bearing for supporting the rotation shaft above the motor, a sub-bearing for supporting the rotation shaft below the motor, and a positive displacement pump part for supplying oil reserved in the bottom of the sealed container through the oil passage to the compression mechanism and the bearings.
- the rotation shaft integrally comprises a main shaft portion fixed to a rotor of the motor, a crank portion eccentrically provided at the upper end of the main shaft portion and connected to the compression mechanism, and a small-diameter, sub-bearing supported portion provided at the lower end of the main shaft portion and supported by the sub-bearing.
- the oil passage of the rotation shaft is a small-diameter hole that extends from the lower end of the sub-bearing supported portion to the upper end of the crank portion and is concentrically provided with the rotation shaft.
- a conventional fluid compressor is disclosed, for example, in JP-A-2-245492.
- a scroll compressor shown in FIGS. 1 to 3 of JP-A-2-245492 comprises in its sealed container, a compression mechanism for compressing fluid, a rotation shaft connected to the compression mechanism and having an oil passage, a motor for driving the rotation shaft, an upper main bearing portion for supporting the rotation shaft, and a centrifugal pump part (cap) for supplying oil reserved in the bottom of the sealed container through the oil passage to the compression mechanism and the bearings.
- the rotation shaft integrally comprises a main shaft portion fixed to a rotor of the motor, a crank pin eccentrically provided at the upper end of the main shaft portion and connected to the compression mechanism, and a portion provided at the lower end of the main shaft portion with the same diameter and projecting downward below the motor.
- the oil passage of the rotation shaft includes a first oil passage extending upward from the lower end and a second oil passage of a small diameter that is communicated with the first oil passage in a plain thereof and extends to the upper end of the crank pin.
- the oil passage through the main shaft portion has a small diameter to ensure the strength of the main shaft portion of the rotation shaft.
- JP-A-2001-349291 employs the positive displacement pump part to ensure the amount of oil supply.
- the positive displacement pump part generally has a disadvantage of its expensiveness compared to centrifugal pump parts.
- the scroll compressor of JP-A-2-245492 employs the centrifugal pump part thereby having an inexpensive structure.
- it presents a problem in ensuring a substantial amount of oil supply since the second oil passage is communicated with the first oil passage in a plain thereof and there is provided only one second oil passage.
- Another problem is that a raised temperature of oil makes it difficult to ensure the required amount of oil supply since it lowers the viscosity of the oil and thus lowers the centrifugal effect acting on the inner wall in the centrifugal pump part.
- the present invention provides a fluid compressor comprising in a sealed container: a compression mechanism for compressing fluid; a rotation shaft connected to the above described compression mechanism and having an oil passage; a motor for driving the above described rotation shaft; a main bearing for supporting the above described rotation shaft above the above described motor; a sub-bearing for supporting the above described rotation shaft below the above described motor; and a centrifugal pump part for supplying oil reserved in a bottom of the above described sealed container through the above described oil passage to the above described compression mechanism and the above described bearings, wherein the above described rotation shaft integrally comprises a main shaft portion fixed to a rotor of the above described motor, a crank pin eccentrically provided at an upper end of the above described main shaft portion and connected to the above described compression mechanism, and a small-diameter, sub-bearing supported portion provided at a lower end of the above described main shaft portion and supported by the above described sub-bearing; the above described oil passage of the above described rotation shaft comprises a first oil passage extending
- a fluid compressor that has an inexpensive structure, ensures a substantial amount of oil supply, and is excellent in reliability.
- FIG. 1 is a longitudinal section view of a scroll compressor according to a first embodiment of the present invention
- FIG. 2A is a longitudinal section view of a lower portion of a rotation shaft and a pump part of the scroll compressor of FIG. 1 ;
- FIG. 2B is a section view taken along IIB-IIB in FIG. 2A ;
- FIG. 3A is a top view of a pump member used in a scroll compressor according to a second embodiment of the present invention.
- FIG. 3B is a front view of a pump member used in a scroll compressor according to a second embodiment of the present invention.
- FIG. 3C is a side view of a pump member used in a scroll compressor according to a second embodiment of the present invention.
- FIG. 4 is a characteristic curve of a pump part according to a second embodiment
- FIG. 5A is a top view of a pump member used in a scroll compressor according to a third embodiment of the present invention.
- FIG. 5B is a front view of a pump member used in a scroll compressor according to a third embodiment of the present invention.
- FIG. 5C is a side view of a pump member used in a scroll compressor according to a third embodiment of the present invention.
- FIG. 6A is a longitudinal section view of a pump part of a scroll compressor according to a fourth embodiment of the present invention.
- FIG. 6B is a side view of a single pump blade of a scroll compressor according to a fourth embodiment of the present invention.
- FIG. 6C is a section view taken along VIC-VIC in FIG. 6A ;
- FIG. 7A is a longitudinal section view of a pump part of a scroll compressor according to a fifth embodiment of the present invention.
- FIG. 7B is a side view of a single pump blade of a scroll compressor according to a fifth embodiment of the present invention.
- FIG. 7C is a section view taken along VIIC-VIIC in FIG. 7A ;
- FIG. 8A is a longitudinal section view of a pump part of a scroll compressor according to a sixth embodiment of the present invention.
- FIG. 8B is a side view of a single pump blade of a scroll compressor according to a sixth embodiment of the present invention.
- FIG. 8C is a section view taken along VIIIC-VIIIC in FIG. 8A ;
- FIG. 9A is a longitudinal section view of a pump part of a scroll compressor according to a seventh embodiment of the present invention.
- FIG. 9B is a side view of a single pump blade of a scroll compressor according to a seventh embodiment of the present invention.
- FIG. 9C is a section view taken along IXC-IXC in FIG. 9A ;
- FIG. 10A is a longitudinal section view of a lower portion of a rotation shaft of a scroll compressor according to an eighth embodiment of the present invention.
- FIG. 10B is a section view taken along XB-XB in FIG. 10A ;
- FIG. 11A is a longitudinal section view of a lower portion of a rotation shaft of a scroll compressor according to a ninth embodiment of the present invention.
- FIG. 11B is a section view taken along XIB-XIB in FIG. 11A .
- FIG. 1 is a longitudinal section view of a scroll compressor according to the first embodiment of the present invention.
- FIG. 2A is a longitudinal section view of a lower portion of a rotation shaft and a pump part of the scroll compressor of FIG. 1 .
- FIG. 2B is a section view taken along IIB-IIB in FIG. 2A .
- a scroll compressor 1 contains a compression mechanism 2 and a driving part 3 in a sealed container 700 .
- it is a vertical scroll compressor in which there are provided from upper to lower in order the compression mechanism 2 , the driving part 3 and an oil reservoir 730 , and the compression mechanism 2 and the driving part 3 are connected through a rotation shaft 300 .
- the compression mechanism 2 comprises as basic elements, a fixed scroll 100 , a orbiting scroll 200 and a frame 400 .
- the frame 400 is fixed to the sealed container 700 and constitutes a member for placing a roller bearing 401 .
- the fixed scroll 100 comprises as basic elements, a base plate 101 , a whirl lap 102 , an intake inlet 103 , and a discharge outlet 104 and is fixed to the frame 400 with a bolt 405 .
- the lap 102 is vertically placed on one side of the base plate 101 .
- the orbiting scroll 200 comprises as basic elements, a base plate 201 , a whirl lap 202 , a boss 203 , and a backpressure hole.
- the lap 202 is vertically placed on one side of the base plate 201 .
- the boss 203 is vertically projecting from the other side of the base plate 201 (opposite to the lap).
- Each element of the orbiting scroll 200 is formed by machining a mold consisting of a material
- a compression chamber 130 in which the fixed scroll 100 and the orbiting scroll 200 are in engagement, performs compressing action such that its volume is reduced by the orbiting motion of the orbiting scroll 200 .
- the orbit movement of the orbiting scroll 200 causes working fluid to be taken into the compression chamber 130 through an intake tube 711 and the intake inlet 103 .
- the taken working fluid after a compression stroke, is discharged from the discharge outlet 104 of the fixed scroll 100 into the sealed container 700 , then delivered through a discharge tube 701 and discharged from the sealed container 700 . This maintains the pressure of the space within the sealed container 700 at a discharge pressure.
- the sealed container 700 has an upper cap 710 and a lower cap 720 .
- the upper cap 710 and the lower cap 720 are engaged over a center barrel of the sealed container.
- the edges of the engagement are welded by a welding torch that heats the edges with upward inclination and downward inclination.
- a leg 721 is attached to the bottom face of the sealed container 700 .
- a hermetic terminal 702 On a side face of the sealed container 700 is provided a hermetic terminal 702 and a terminal cover 703 that allows power supply to a motor 600 .
- the hermetic terminal 702 is disposed through the sealed container 700 and placed between an end coil of a stator 601 and the frame 400 while opposing a maximum diameter portion 407 a of a balance weight 407 .
- the discharge tube 701 is provided on a side face of the sealed container 700 opposite to the hermetic terminal 702 through the sealed container 700 .
- the discharge tube 701 is placed between the end coil of the stator 601 and the frame 400 while opposing a maximum diameter portion 407 a of a balance weight 407 .
- the driving part 3 that drives the orbiting scroll 200 to orbit comprises as basic elements, the motor 600 having the stator 601 and a rotor 602 , the rotation shaft 300 , an Oldham coupling 500 which is a main component of a mechanism for preventing the rotation of the orbiting scroll 200 , the frame 400 , the roller bearings 401 and 803 , and the boss 203 .
- the rotation shaft 300 integrally comprises a main shaft portion 302 , a crank pin 301 , and a sub-bearing supported portion 303 .
- the roller bearings 401 and 803 constitute a rotation shaft supporting portion that rotatably is engaged to the main shaft portion 302 and the sub-bearing supported portion 303 of the rotation shaft 300 .
- the boss 203 is provided to the orbiting scroll 200 such that the boss 203 is engaged to the crank pin 301 of the rotation shaft 300 movably in a thrust direction which is a direction of the rotation axis and rotatably.
- the roller bearing 401 is placed above the motor 600 .
- the roller bearing (sub-bearing) 803 that constitutes a main component of a sub-bearing part 800 is placed below the motor 600 .
- a housing 802 is fixed by a bolt 805 to a lower frame 801 that is fixed to the sealed container 700 .
- the roller bearing 803 is inserted into the housing 802 from upper side, and a housing cover 804 is also mounted over them from upper side.
- a pump part 900 is provided at the lower end of the rotation shaft 300 .
- the pump part 900 comprises a pump member 901 and a pump blade 902 .
- the pump member 901 comprises a portion that is attached to the lower end of the rotation shaft 300 , and a portion extending therefrom downward in which the section area of the fluid passage decreases.
- the pump member 901 comprises an upper cylindrical portion 901 a and a lower conical potion 901 b .
- the upper end of the upper cylindrical portion 901 a is inserted into and fixed to the lower end of the rotation shaft 300 .
- An opening is provided at the lower end of the lower conical portion 901 b of the pump member 901 .
- the pump blade 902 has an outer shape that is identical to an inner shape of the pump member 901 , and is press-fitted in the pump member 901 . That is, the pump blade 902 is provided to extend from an upper position in the pump member 901 to the opening at the lower end.
- a centrifugal effect in the pump part 900 rotated with the rotation shaft 300 causes oil reserved in the oil reservoir 730 at the bottom of the sealed container 700 to be taken from the lower end of the pump part and then supplied into an oil passage 311 that is provided in the rotation shaft 300 .
- the oil passage 311 of the rotation shaft 300 comprises a first oil passage 311 a that extends from the lower end of the sub-bearing supported portion 303 to the lower part of the main shaft portion 302 , and a second oil passage 311 b that is communicated with the first oil passage 311 a and extends to the upper end of the crank pin 301 .
- the first oil passage 311 a is provided concentrically with the rotation shaft 300 .
- the second oil passage 311 b has a passage portion that has a smaller diameter than and is placed at an outer of the first oil passage 311 a .
- the second oil passage 311 b overlaps the first oil passage 311 a so that the second oil passage 311 b is communicated with the first oil passage 311 a on the peripheral thereof in a substantial length in the axial direction.
- the second oil passage 311 b is placed at a position eccentric to the center axis of the rotation shaft 300 . This eccentricity provides the action of a second centrifugal pump.
- the Oldham coupling 500 is disposed on the back face of the base plate 201 of the orbiting scroll 200 .
- one set slides in a key groove that is formed in the frame 400 and is a receiving portion for the Oldham coupling 500
- the other set slides in a key groove formed in the orbiting scroll lap 202 on its back face. Accordingly, the orbiting scroll 200 orbits with respect to the fixed scroll 100 without rotation in a plain vertical to the axial direction in which the scroll lap 202 is provided.
- the orbiting scroll 200 performs orbiting motion with respect to the fixed scroll 100 while not performing the rotation because of the action of a mechanism for preventing the rotation of the Oldham coupling 500 , and gas is then taken through the intake tube 711 and the intake inlet 103 into the compression chamber 130 that is formed of the scroll laps and 102 and 202 .
- the orbiting motion of the orbiting scroll 200 causes the compression chamber 130 to move toward the center and its volume to be reduced to compress the gas, and the compressed gas is discharged from the discharge outlet 104 into a discharge chamber.
- the gas discharged into the discharge chamber is circulated around the compression mechanism 3 and the motor 600 , and then discharged from the discharge tube 701 to the outside of the compressor.
- the base plate 201 of the orbiting scroll 200 is provided with a backpressure hole through which the compression chamber 130 and a backpressure chamber 411 on the orbiting back face are communicated with each other, so that the pressure of the backpressure chamber 411 is maintained at a pressure between intake pressure and discharge pressure (i.e. intermediate pressure).
- the backpressure chamber 411 provided on the back face side of the orbiting scroll 200 is a space that is surrounded by the orbiting scroll 200 , the frame 400 and the fixed scroll 100 .
- the frame 400 is also a constituent member of the backpressure chamber 411 .
- a seal ring 410 provided at a groove 409 in the frame 400 prevents the flow of the discharged gas into the backpressure chamber 411 .
- the orbiting scroll 200 is pressed against the fixed scroll 100 with the resultant force of the intermediate pressure in the backpressure chamber 411 and the discharge pressure acting on the internal side of the seal ring 410 .
- the inside diameter of the seal ring 410 is smaller than the outside diameter of the roller bearing 401 .
- this embodiment is adapted so that the roller bearing 401 is inserted into the frame 400 from the rotation driving means side of the frame 400 and the inserted roller bearing 401 is fixed by a frame cover 403 .
- a thrust bearing 402 is provided to the frame cover 403 .
- the frame cover 403 is provided separately from the frame 400 .
- the frame cover 403 is fixed to the frame 400 with the bolt 406 . This bolt fixation ensures the sealing between the frame cover 403 and the frame 400 thereby preventing the oil leakage from the oil supply passage.
- frame cover 403 comprises a portion that is inserted to the inside the frame 400 and pushes the roller bearing 401 , and a portion that abuts the side face of the rotation driving means side of the frame 400 and is fixed thereto.
- the balance weight 407 is provided to the rotation shaft 300 in the motor side with respect to the roller bearing 401 .
- the balance weight 407 is provided separately from the rotation shaft 300 and press-fitted to the rotation shaft 300 to be fixed thereto.
- the balance weight 407 may be provided integrally with the rotation shaft 300 .
- the maximum diameter portion 407 a of the balance weight 407 is projecting from a peripheral face of the coil end of the stator 601 , and has a larger diameter than the inside diameter of the coil end.
- the balance weight cover 404 is also fixed to the frame 400 , fastened along with the frame cover 403 with the bolt 406 .
- the sidewall of the balance weight cover 404 is provided between the discharge tube 701 and the maximum diameter portion 407 a of the balance weight 407 , and also between the hermetic terminal 702 and the maximum diameter portion 407 a of the balance weight 407 .
- the balance weight cover 404 confines the space between the frame 400 and the end face of the end coil of the stator 601 . That is, outside space of the maximum diameter portion 407 a of the balance weight 407 is substantially confined by the balance weight cover 404 .
- the pump part 900 delivers oil in the oil reservoir 730 to the oil passage 311 in the rotation shaft.
- Part of the oil delivered to the oil passage 311 flows through the lateral hole 312 to the sub-bearing 803 (ball bearing), and then returns to the oil reservoir 730 .
- the oil that has reached the upper portion of the crank pin 301 through the oil passage 311 passes a orbit bearing 210 and then flows to the roller bearing 401 .
- Most of the oil that has lubricated the roller bearing 401 passes an oil discharge pipe 408 and returns to the oil reservoir 730 .
- Part of the oil that has lubricated the roller bearing 401 passes the gap between the frame cover 403 and the rotation shaft 300 , then reaches the balance weight 407 , and is scattered by the balance weight 407 .
- the scattered oil attaches to the interior surface of the side wall 404 b of the balance weight cover 404 to be recovered, and returns to the oil reservoir 730 , for example, by flowing down to the motor 600 .
- an oil supply pocket 205 On the peripheral face of the boss 203 of the orbiting scroll 200 is provided an oil supply pocket 205 , which reciprocates between the inside and outside of the seal ring 410 with the orbiting motion of the orbiting scroll 200 so that part of oil between the orbit bearing 210 and the bearing 401 is delivered to the backpressure chamber 411 .
- the delivered oil is supplied to the Oldham coupling 500 , and then supplied to the sliding faces of a mirror plate face 105 of the fixed scroll and the base plate 201 of the orbiting scroll 200 .
- the oil delivered to the backpressure 411 flows through the backpressure hole or a narrow aperture in the mirror plate sliding face into the compression chamber 130 .
- the oil that has flowed into the backpressure chamber 130 is discharged along with compressed coolant gas from the discharge outlet 104 , then separated from the coolant gas in the sealed container 700 , and returns to the oil reservoir 730 .
- the rotation shaft 300 integrally comprises the main shaft portion 302 fixed to the rotor 602 of the motor 600 , the crank pin 301 eccentrically provided at the upper end of the main shaft portion 302 and connected to the compression mechanism 2 , and the small-diameter, sub-bearing supported portion 303 provided at the lower end of the main shaft portion 302 and supported by the sub-bearing 803 , so that the sub-bearing 803 precisely bears the sub-bearing supported portion 303 while ensuring the required strength for the rotation shaft 300 .
- the centrifugal pump part since the centrifugal pump part is used, it is possible to reduce the cost compared with the case of using a positive displacement pump part. Moreover, since the pump blade 902 extends to the lower end of the pump member 901 , the capability of supplying oil is substantially maintained even when the amount of oil in the oil reservoir 730 decreased with the action of the centrifugal pump blade 902 extending to the lower end of the pump member 901 , and therefore, a more reliable pump mechanism can be provided.
- the oil passage 311 of the rotation shaft 300 comprises the first oil passage 311 a that extends from the lower end of the sub-bearing supported portion 303 to the lower portion of the main shaft portion 302 , and the second oil passage 311 b that is communicated with the first oil passage 311 a and extends to the upper end of the crank pin 301 ;
- the second oil passage 311 b has a passage portion that has a smaller diameter than the first oil passage 311 a and is placed at an outer of it; a plurality of such second oil passages 311 b are provided within the plain of the crank pin 301 , thereby ensuring both a substantial centrifugal force and a substantial section area of the fluid passage within the limited section area of the rotation shaft 300 while the features of the rotation shaft 300 are satisfied.
- the second oil passage 311 b acts as a second centrifugal pump, and the substantial amount of oil supply is ensured with an inexpensive structure, a reliable scroll compressor is achieved.
- FIGS. 3A to 3 C are diagrams for a pump member of a scroll compressor according to the second embodiment of the present invention: FIG. 3A is a top view; FIG. 3B is a front view; and FIG. 3C is a side view.
- FIG. 4 is a characteristic curve of a pump part according to a second embodiment.
- a pump part 900 has only a pump member 901 as constituent member and no pump blade 902 as used in the first embodiment.
- the pump member 901 is generally in a conical shape in which the connecting portion with the rotation shaft 300 is in a cylindrical shape, and the portion opposite to the rotation shaft 300 is in a flat shape, with the connecting portion and the flat shape portion on the opposite end formed of smooth curves.
- the centrifugal effect acts on the entire section area of the flat shape portion of the pump member 901 , the capability of supplying oil existing in the pump member 901 is enhanced, thereby reducing the influence of the oil viscosity and achieving stable oil supply.
- the reduction in oil viscosity in raised temperature reduces the amount of oil supply dramatically as shown in characteristic curve (b) in FIG. 4 .
- the pump member 901 in a flat shape according to the second embodiment there is only small change in the amount of oil supply as shown in characteristic curve (a) in FIG. 4 , thereby achieving stable oil supply.
- the pump part 900 can be constituted of a single member, and thus can have an inexpensive structure.
- FIGS. 5A to 5 C are diagrams for a pump member of a scroll compressor according to the third embodiment of the present invention: FIG. 5A is a top view; FIG. 5B is a front view; and FIG. 5C is a side view.
- a pump member 901 is generally in a cylindrical shape in which the portion connected with the rotation shaft 300 is in a cylindrical shape, and the portion opposite to the rotation shaft 300 is in a flat shape.
- the pump member 901 according to the third embodiment because of its generally cylindrical shape, can have an inexpensive structure.
- FIGS. 6A to 6 C are diagrams for a pump part of a scroll compressor according to the fourth embodiment of the present invention: FIG. 6A is a longitudinal section view of a pump part; FIG. 6B is a side view of a single pump blade of the pump part; and FIG. 6C is a section view taken along VIC-VIC in FIG. 6A .
- a projection 901 c is provided inside a pump member 901 .
- a pump blade 902 which is placed inside the pump member 901 and rotates along with the pump member 901 , is subject to inertia force of the fluid in the pump 901 driven by the rotation shaft 300 and thus subject to force opposite to the rotation direction of the rotation shaft 300 .
- the projection 901 c is provided inside the pump member 901 that serves as a stopper against the pump blade 902 .
- the projection 901 c provided to the pump member 901 securely supports the pump blade 902 , so that the pump part 900 can have a simple, inexpensive structure and enhanced reliability. Note that the lower end of the pump blade 902 extends only to the cylindrical portion of the pump member 901 , and the upper portion of the pump blade 902 extends into the oil passage 311 .
- FIGS. 7A to 7 C are diagrams for a pump part of a scroll compressor according to the fifth embodiment of the present invention: FIG. 7A is a longitudinal section view of a pump part; FIG. 7B is a side view of a single pump blade of the pomp part; and FIG. 7C is a section view taken along VIIC-VIIC in FIG. 7A .
- a pair of projections 901 c is provided inside a pump member 901 .
- a pump blade 902 is placed so that both the ends thereof are sandwiched between respective pairs of projections 901 c .
- the pump blade 902 is securely supported to supply oil when the rotation shaft 300 is rotated either in normal direction or in reverse direction.
- FIGS. 8A to 8 C are diagrams for a pump part of a scroll compressor according to the sixth embodiment of the present invention: FIG. 8A is a longitudinal section view of a pump part; FIG. 8B is a side view of a single pump blade of the pomp part; and FIG. 8C is a section view taken along VIIIC-VIIIC in FIG. 8A .
- the sixth embodiment is different from the fifth embodiment in that a pump blade 902 extends to the lower end of a pump member 901 , but the other features of the sixth embodiment are the same as those of the fifth embodiment.
- the capability of supplying oil is substantially maintained even when the amount of oil in the oil reservoir 730 decreased with the action of the centrifugal pump blade 902 extending to the lower end of the pump member 901 , and therefore, a more reliable pump mechanism can be obtained.
- FIGS. 9A to 9 C are diagrams for a pump part of a scroll compressor according to the seventh embodiment of the present invention: FIG. 9A is a longitudinal section view of a pump part; FIG. 9B is a side view of a single pump blade of the pomp part; and FIG. 9C is a section view taken along IXC-IXC in FIG. 9A .
- the seventh embodiment is different from the sixth embodiment in that the portion of a pump member 901 opposite to the connecting portion thereof to the rotation shaft 300 has a spherical surface, but the other features of the seventh embodiment are the same as those of the sixth embodiment.
- the inner wall of the pump member 900 has steeper slope with respect to the axis of the rotation shaft 300 than the case of conical shape or cylindrical shape, so as to enhance the centrifugal pump effect and achieve the capability of stable oil supply, and therefore a more reliable pump mechanism can be provided.
- FIG. 10A and FIG. 10B are diagrams for a lower portion of a rotation shaft of a scroll compressor according to an eighth embodiment of the present invention: FIG. 10A is a longitudinal section view of a lower portion of a rotation shaft; and FIG. 10B is a section view taken along XB-XB in FIG. 10A .
- a pump member 901 has a periphery portion consisting of double cylinders.
- the outer space in the pump member 901 is open to the lower face of the sub-bearing part 800 .
- the inner space in the pump member 901 is similar to that of the first embodiment.
- the cylindrical portion disposed at the periphery of the pump member 901 provides a third centrifugal pump effect. Oil discharged from the upper end of the third centrifugal pump is used for lubricating the sub-bearing 803 placed in the sub-bearing part 800 . Therefore, stable oil supply to the sub-bearing 803 can be achieved, and since the oil supply passage is separated from the oil supply into the pump member 901 , an oil supply structure can be obtained that is easily designed and has a higher reliability.
- FIG. 11A and FIG. 11B are diagrams for a lower portion of a rotation shaft of a scroll compressor according to a ninth embodiment of the present invention: FIG. 11A is a longitudinal section view of a lower portion of a rotation shaft; and FIG. 11B is a section view taken along XIB-XIB in FIG. 11A .
- means for connecting a pump member 901 to a rotation shaft 300 is a thread having a screw thread whose screw direction is the same as the rotation direction of the rotation shaft 300 .
- the pump member 901 is subject to force opposite to the rotation direction of the rotation shaft 300 .
- the thread of the connection means is subject to force in the direction for tightening the screw, due to the force opposite to the rotation direction of the rotation shaft 300 that acts on the pump member 901 , and therefore the pump member 901 is not disconnected from the rotation shaft 300 , and a more reliable pump structure can be obtained.
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Abstract
A fluid compressor 1 comprises a rotation shaft 300 having a compression mechanism 2 and an oil passage 311, a motor 600, bearings 401 and 803, and a centrifugal pump part 900 for supplying oil through the oil passage 311. The rotation shaft 300 integrally comprises a main shaft portion 302, a crank pin 301 eccentrically provided to the main shaft portion 302, and a sub-bearing supported portion 303 having a smaller diameter than the main shaft portion 302. The oil passage 311 has a first oil passage 311 a extending from a lower end of the sub-bearing supported portion 303 to a lower portion of the main shaft portion 302, and a second oil passage 311 b that is communicated with the first oil passage 311 a and extends to an upper end of the crank pin 301. The second oil passage 311 b comprises a passage portion that has a smaller diameter than and is placed at an outer of the first oil passage 311 a, a plurality of the second oil passages 311 b are provided within a plain of said crank pin 311.
Description
- The present invention relates to a fluid compressor comprising a rotation shaft having an oil passage, and particularly to the one suitably used as a coolant compressor for cooling or air conditioning, or a fluid compressor for air or the like.
- A conventional fluid compressor is disclosed, for example, in JP-A-2001-349291. A scroll compressor shown in
FIG. 1 of JP-A-2001-349291 comprises in its sealed container, a compression mechanism for compressing fluid, a rotation shaft connected to the compression mechanism and having an oil passage, a motor for driving the rotation shaft, a main bearing for supporting the rotation shaft above the motor, a sub-bearing for supporting the rotation shaft below the motor, and a positive displacement pump part for supplying oil reserved in the bottom of the sealed container through the oil passage to the compression mechanism and the bearings. - The rotation shaft integrally comprises a main shaft portion fixed to a rotor of the motor, a crank portion eccentrically provided at the upper end of the main shaft portion and connected to the compression mechanism, and a small-diameter, sub-bearing supported portion provided at the lower end of the main shaft portion and supported by the sub-bearing. Note that the small diameter of the sub-bearing supported portion of the rotation shaft allows the sub-bearing to precisely bear the sub-bearing supported portion. The oil passage of the rotation shaft is a small-diameter hole that extends from the lower end of the sub-bearing supported portion to the upper end of the crank portion and is concentrically provided with the rotation shaft.
- A conventional fluid compressor is disclosed, for example, in JP-A-2-245492. A scroll compressor shown in FIGS. 1 to 3 of JP-A-2-245492 comprises in its sealed container, a compression mechanism for compressing fluid, a rotation shaft connected to the compression mechanism and having an oil passage, a motor for driving the rotation shaft, an upper main bearing portion for supporting the rotation shaft, and a centrifugal pump part (cap) for supplying oil reserved in the bottom of the sealed container through the oil passage to the compression mechanism and the bearings.
- The rotation shaft integrally comprises a main shaft portion fixed to a rotor of the motor, a crank pin eccentrically provided at the upper end of the main shaft portion and connected to the compression mechanism, and a portion provided at the lower end of the main shaft portion with the same diameter and projecting downward below the motor. The oil passage of the rotation shaft includes a first oil passage extending upward from the lower end and a second oil passage of a small diameter that is communicated with the first oil passage in a plain thereof and extends to the upper end of the crank pin.
- Generally, it is desirable that the oil passage through the main shaft portion has a small diameter to ensure the strength of the main shaft portion of the rotation shaft.
- In the case of the scroll compressor of JP-A-2001-349291 where the oil passage of the rotation shaft is a small-diameter hole that extends from the lower end of the sub-bearing supported portion to the upper end of the crank portion and is provided concentrically with the rotation shaft, the expected centrifugal force on the oil with the oil passage is not so substantial. Accordingly, JP-A-2001-349291 employs the positive displacement pump part to ensure the amount of oil supply. However, the positive displacement pump part generally has a disadvantage of its expensiveness compared to centrifugal pump parts.
- The scroll compressor of JP-A-2-245492 employs the centrifugal pump part thereby having an inexpensive structure. However, it presents a problem in ensuring a substantial amount of oil supply since the second oil passage is communicated with the first oil passage in a plain thereof and there is provided only one second oil passage. Another problem is that a raised temperature of oil makes it difficult to ensure the required amount of oil supply since it lowers the viscosity of the oil and thus lowers the centrifugal effect acting on the inner wall in the centrifugal pump part.
- It is an object of the present invention to provide a fluid compressor that has an inexpensive structure, ensures a substantial amount of oil supply, and is excellent in reliability.
- To achieve the above object, the present invention provides a fluid compressor comprising in a sealed container: a compression mechanism for compressing fluid; a rotation shaft connected to the above described compression mechanism and having an oil passage; a motor for driving the above described rotation shaft; a main bearing for supporting the above described rotation shaft above the above described motor; a sub-bearing for supporting the above described rotation shaft below the above described motor; and a centrifugal pump part for supplying oil reserved in a bottom of the above described sealed container through the above described oil passage to the above described compression mechanism and the above described bearings, wherein the above described rotation shaft integrally comprises a main shaft portion fixed to a rotor of the above described motor, a crank pin eccentrically provided at an upper end of the above described main shaft portion and connected to the above described compression mechanism, and a small-diameter, sub-bearing supported portion provided at a lower end of the above described main shaft portion and supported by the above described sub-bearing; the above described oil passage of the above described rotation shaft comprises a first oil passage extending from a lower end of the above described sub-bearing supported portion to a lower portion of the above described main shaft portion, and a second oil passage that is communicated with the above described first oil passage and extends to an upper end of the above described crank pin; and the above described second oil passage comprises a passage portion that has a smaller diameter than and is placed at an outer of the above described first oil passage; a plurality of the above described second oil passages are provided within a plain of the above described crank pin.
- According to the present invention, a fluid compressor is provided that has an inexpensive structure, ensures a substantial amount of oil supply, and is excellent in reliability.
- Other objects, features and advantages of the invention will become apparent from the following description of the embodiments of the invention taken in conjunction with the accompanying drawings.
-
FIG. 1 is a longitudinal section view of a scroll compressor according to a first embodiment of the present invention; -
FIG. 2A is a longitudinal section view of a lower portion of a rotation shaft and a pump part of the scroll compressor ofFIG. 1 ; -
FIG. 2B is a section view taken along IIB-IIB inFIG. 2A ; -
FIG. 3A is a top view of a pump member used in a scroll compressor according to a second embodiment of the present invention; -
FIG. 3B is a front view of a pump member used in a scroll compressor according to a second embodiment of the present invention; -
FIG. 3C is a side view of a pump member used in a scroll compressor according to a second embodiment of the present invention; -
FIG. 4 is a characteristic curve of a pump part according to a second embodiment; -
FIG. 5A is a top view of a pump member used in a scroll compressor according to a third embodiment of the present invention; -
FIG. 5B is a front view of a pump member used in a scroll compressor according to a third embodiment of the present invention; -
FIG. 5C is a side view of a pump member used in a scroll compressor according to a third embodiment of the present invention; -
FIG. 6A is a longitudinal section view of a pump part of a scroll compressor according to a fourth embodiment of the present invention; -
FIG. 6B is a side view of a single pump blade of a scroll compressor according to a fourth embodiment of the present invention; -
FIG. 6C is a section view taken along VIC-VIC inFIG. 6A ; -
FIG. 7A is a longitudinal section view of a pump part of a scroll compressor according to a fifth embodiment of the present invention; -
FIG. 7B is a side view of a single pump blade of a scroll compressor according to a fifth embodiment of the present invention; -
FIG. 7C is a section view taken along VIIC-VIIC inFIG. 7A ; -
FIG. 8A is a longitudinal section view of a pump part of a scroll compressor according to a sixth embodiment of the present invention; -
FIG. 8B is a side view of a single pump blade of a scroll compressor according to a sixth embodiment of the present invention; -
FIG. 8C is a section view taken along VIIIC-VIIIC inFIG. 8A ; -
FIG. 9A is a longitudinal section view of a pump part of a scroll compressor according to a seventh embodiment of the present invention; -
FIG. 9B is a side view of a single pump blade of a scroll compressor according to a seventh embodiment of the present invention; -
FIG. 9C is a section view taken along IXC-IXC inFIG. 9A ; -
FIG. 10A is a longitudinal section view of a lower portion of a rotation shaft of a scroll compressor according to an eighth embodiment of the present invention; -
FIG. 10B is a section view taken along XB-XB inFIG. 10A ; -
FIG. 11A is a longitudinal section view of a lower portion of a rotation shaft of a scroll compressor according to a ninth embodiment of the present invention; and -
FIG. 11B is a section view taken along XIB-XIB inFIG. 11A . - Embodiments of the present invention will be described with reference to drawings. Like reference numerals and characters in the drawings refers to like elements or equivalents.
- A scroll compressor of a first embodiment of the present invention will be described with reference to
FIG. 1 ,FIG. 2A andFIG. 2B .FIG. 1 is a longitudinal section view of a scroll compressor according to the first embodiment of the present invention.FIG. 2A is a longitudinal section view of a lower portion of a rotation shaft and a pump part of the scroll compressor ofFIG. 1 .FIG. 2B is a section view taken along IIB-IIB inFIG. 2A . - A scroll compressor 1 contains a
compression mechanism 2 and a drivingpart 3 in a sealedcontainer 700. In this embodiment, it is a vertical scroll compressor in which there are provided from upper to lower in order thecompression mechanism 2, the drivingpart 3 and anoil reservoir 730, and thecompression mechanism 2 and the drivingpart 3 are connected through arotation shaft 300. - The
compression mechanism 2 comprises as basic elements, afixed scroll 100, aorbiting scroll 200 and aframe 400. Theframe 400 is fixed to the sealedcontainer 700 and constitutes a member for placing aroller bearing 401. The fixedscroll 100 comprises as basic elements, abase plate 101, awhirl lap 102, anintake inlet 103, and adischarge outlet 104 and is fixed to theframe 400 with abolt 405. Thelap 102 is vertically placed on one side of thebase plate 101. Theorbiting scroll 200 comprises as basic elements, abase plate 201, awhirl lap 202, aboss 203, and a backpressure hole. Thelap 202 is vertically placed on one side of thebase plate 201. Theboss 203 is vertically projecting from the other side of the base plate 201 (opposite to the lap). Each element of theorbiting scroll 200 is formed by machining a mold consisting of a material such as cast iron or aluminum. - A
compression chamber 130, in which the fixedscroll 100 and theorbiting scroll 200 are in engagement, performs compressing action such that its volume is reduced by the orbiting motion of theorbiting scroll 200. In this compressing action, the orbit movement of theorbiting scroll 200 causes working fluid to be taken into thecompression chamber 130 through anintake tube 711 and theintake inlet 103. The taken working fluid, after a compression stroke, is discharged from thedischarge outlet 104 of the fixedscroll 100 into the sealedcontainer 700, then delivered through adischarge tube 701 and discharged from the sealedcontainer 700. This maintains the pressure of the space within the sealedcontainer 700 at a discharge pressure. - The sealed
container 700 has anupper cap 710 and alower cap 720. Theupper cap 710 and thelower cap 720 are engaged over a center barrel of the sealed container. The edges of the engagement are welded by a welding torch that heats the edges with upward inclination and downward inclination. Aleg 721 is attached to the bottom face of the sealedcontainer 700. - On a side face of the sealed
container 700 is provided ahermetic terminal 702 and aterminal cover 703 that allows power supply to amotor 600. Thehermetic terminal 702 is disposed through the sealedcontainer 700 and placed between an end coil of astator 601 and theframe 400 while opposing amaximum diameter portion 407 a of abalance weight 407. - The
discharge tube 701 is provided on a side face of the sealedcontainer 700 opposite to thehermetic terminal 702 through the sealedcontainer 700. Thedischarge tube 701 is placed between the end coil of thestator 601 and theframe 400 while opposing amaximum diameter portion 407 a of abalance weight 407. - The driving
part 3 that drives theorbiting scroll 200 to orbit comprises as basic elements, themotor 600 having thestator 601 and arotor 602, therotation shaft 300, anOldham coupling 500 which is a main component of a mechanism for preventing the rotation of theorbiting scroll 200, theframe 400, theroller bearings boss 203. - The
rotation shaft 300 integrally comprises amain shaft portion 302, acrank pin 301, and a sub-bearing supportedportion 303. Theroller bearings main shaft portion 302 and the sub-bearing supportedportion 303 of therotation shaft 300. Theboss 203 is provided to theorbiting scroll 200 such that theboss 203 is engaged to the crankpin 301 of therotation shaft 300 movably in a thrust direction which is a direction of the rotation axis and rotatably. - The
roller bearing 401 is placed above themotor 600. The roller bearing (sub-bearing) 803 that constitutes a main component of asub-bearing part 800 is placed below themotor 600. Ahousing 802 is fixed by abolt 805 to alower frame 801 that is fixed to the sealedcontainer 700. Theroller bearing 803 is inserted into thehousing 802 from upper side, and ahousing cover 804 is also mounted over them from upper side. - A
pump part 900 is provided at the lower end of therotation shaft 300. Thepump part 900 comprises apump member 901 and apump blade 902. Thepump member 901 comprises a portion that is attached to the lower end of therotation shaft 300, and a portion extending therefrom downward in which the section area of the fluid passage decreases. In other words, thepump member 901 comprises an uppercylindrical portion 901 a and a lowerconical potion 901 b. The upper end of the uppercylindrical portion 901 a is inserted into and fixed to the lower end of therotation shaft 300. An opening is provided at the lower end of the lowerconical portion 901 b of thepump member 901. Thepump blade 902 has an outer shape that is identical to an inner shape of thepump member 901, and is press-fitted in thepump member 901. That is, thepump blade 902 is provided to extend from an upper position in thepump member 901 to the opening at the lower end. - Thus, a structure is provided in which a centrifugal effect in the
pump part 900 rotated with therotation shaft 300 causes oil reserved in theoil reservoir 730 at the bottom of the sealedcontainer 700 to be taken from the lower end of the pump part and then supplied into anoil passage 311 that is provided in therotation shaft 300. - The
oil passage 311 of therotation shaft 300 comprises afirst oil passage 311 a that extends from the lower end of the sub-bearing supportedportion 303 to the lower part of themain shaft portion 302, and asecond oil passage 311 b that is communicated with thefirst oil passage 311 a and extends to the upper end of thecrank pin 301. Thefirst oil passage 311 a is provided concentrically with therotation shaft 300. Thesecond oil passage 311 b has a passage portion that has a smaller diameter than and is placed at an outer of thefirst oil passage 311 a. There are provided a plurality ofsecond oil passages 311 b (two in this embodiment) within the plain of thecrank pin 301. Thesecond oil passage 311 b overlaps thefirst oil passage 311 a so that thesecond oil passage 311 b is communicated with thefirst oil passage 311 a on the peripheral thereof in a substantial length in the axial direction. Thesecond oil passage 311 b is placed at a position eccentric to the center axis of therotation shaft 300. This eccentricity provides the action of a second centrifugal pump. - The
Oldham coupling 500 is disposed on the back face of thebase plate 201 of theorbiting scroll 200. Of two sets of keys that are provided to theOldham coupling 500 and perpendicular to each other, one set slides in a key groove that is formed in theframe 400 and is a receiving portion for theOldham coupling 500, while the other set slides in a key groove formed in theorbiting scroll lap 202 on its back face. Accordingly, theorbiting scroll 200 orbits with respect to the fixedscroll 100 without rotation in a plain vertical to the axial direction in which thescroll lap 202 is provided. - In the
compression mechanism 2, when the rotation of therotation shaft 300 connected to themotor 600 causes eccentric rotation of thecrank pin 301, theorbiting scroll 200 performs orbiting motion with respect to the fixedscroll 100 while not performing the rotation because of the action of a mechanism for preventing the rotation of theOldham coupling 500, and gas is then taken through theintake tube 711 and theintake inlet 103 into thecompression chamber 130 that is formed of the scroll laps and 102 and 202. The orbiting motion of theorbiting scroll 200 causes thecompression chamber 130 to move toward the center and its volume to be reduced to compress the gas, and the compressed gas is discharged from thedischarge outlet 104 into a discharge chamber. The gas discharged into the discharge chamber is circulated around thecompression mechanism 3 and themotor 600, and then discharged from thedischarge tube 701 to the outside of the compressor. - The
base plate 201 of theorbiting scroll 200 is provided with a backpressure hole through which thecompression chamber 130 and abackpressure chamber 411 on the orbiting back face are communicated with each other, so that the pressure of thebackpressure chamber 411 is maintained at a pressure between intake pressure and discharge pressure (i.e. intermediate pressure). Thebackpressure chamber 411 provided on the back face side of theorbiting scroll 200 is a space that is surrounded by theorbiting scroll 200, theframe 400 and the fixedscroll 100. Thus, theframe 400 is also a constituent member of thebackpressure chamber 411. - A
seal ring 410 provided at agroove 409 in theframe 400 prevents the flow of the discharged gas into thebackpressure chamber 411. Theorbiting scroll 200 is pressed against the fixedscroll 100 with the resultant force of the intermediate pressure in thebackpressure chamber 411 and the discharge pressure acting on the internal side of theseal ring 410. - Here, the inside diameter of the
seal ring 410 is smaller than the outside diameter of theroller bearing 401. To have this configuration, this embodiment is adapted so that theroller bearing 401 is inserted into theframe 400 from the rotation driving means side of theframe 400 and the insertedroller bearing 401 is fixed by aframe cover 403. Athrust bearing 402 is provided to theframe cover 403. Theframe cover 403 is provided separately from theframe 400. Theframe cover 403 is fixed to theframe 400 with thebolt 406. This bolt fixation ensures the sealing between theframe cover 403 and theframe 400 thereby preventing the oil leakage from the oil supply passage. Note thatframe cover 403 comprises a portion that is inserted to the inside theframe 400 and pushes theroller bearing 401, and a portion that abuts the side face of the rotation driving means side of theframe 400 and is fixed thereto. - The
balance weight 407 is provided to therotation shaft 300 in the motor side with respect to theroller bearing 401. In this embodiment, thebalance weight 407 is provided separately from therotation shaft 300 and press-fitted to therotation shaft 300 to be fixed thereto. However, thebalance weight 407 may be provided integrally with therotation shaft 300. Themaximum diameter portion 407 a of thebalance weight 407 is projecting from a peripheral face of the coil end of thestator 601, and has a larger diameter than the inside diameter of the coil end. - A
balance weight cover 404 of metal that is formed in a cylinder shape, consisting of a bottom wall and a sidewall, is provided to cover the periphery of themaximum diameter portion 407 a of thebalance weight 407. Thebalance weight cover 404 is also fixed to theframe 400, fastened along with theframe cover 403 with thebolt 406. The sidewall of thebalance weight cover 404 is provided between thedischarge tube 701 and themaximum diameter portion 407 a of thebalance weight 407, and also between thehermetic terminal 702 and themaximum diameter portion 407 a of thebalance weight 407. - Thus, the
balance weight cover 404 confines the space between theframe 400 and the end face of the end coil of thestator 601. That is, outside space of themaximum diameter portion 407 a of thebalance weight 407 is substantially confined by thebalance weight cover 404. - Next, the oil supply passage will be described. When the
rotation shaft 300 is rotated, thepump part 900 delivers oil in theoil reservoir 730 to theoil passage 311 in the rotation shaft. Part of the oil delivered to theoil passage 311 flows through thelateral hole 312 to the sub-bearing 803 (ball bearing), and then returns to theoil reservoir 730. The oil that has reached the upper portion of thecrank pin 301 through theoil passage 311 passes aorbit bearing 210 and then flows to theroller bearing 401. Most of the oil that has lubricated theroller bearing 401 passes anoil discharge pipe 408 and returns to theoil reservoir 730. Part of the oil that has lubricated theroller bearing 401 passes the gap between theframe cover 403 and therotation shaft 300, then reaches thebalance weight 407, and is scattered by thebalance weight 407. The scattered oil attaches to the interior surface of theside wall 404 b of thebalance weight cover 404 to be recovered, and returns to theoil reservoir 730, for example, by flowing down to themotor 600. - On the peripheral face of the
boss 203 of theorbiting scroll 200 is provided anoil supply pocket 205, which reciprocates between the inside and outside of theseal ring 410 with the orbiting motion of theorbiting scroll 200 so that part of oil between theorbit bearing 210 and thebearing 401 is delivered to thebackpressure chamber 411. The delivered oil is supplied to theOldham coupling 500, and then supplied to the sliding faces of amirror plate face 105 of the fixed scroll and thebase plate 201 of theorbiting scroll 200. - The oil delivered to the
backpressure 411 flows through the backpressure hole or a narrow aperture in the mirror plate sliding face into thecompression chamber 130. The oil that has flowed into thebackpressure chamber 130 is discharged along with compressed coolant gas from thedischarge outlet 104, then separated from the coolant gas in the sealedcontainer 700, and returns to theoil reservoir 730. - According to this embodiment, the
rotation shaft 300 integrally comprises themain shaft portion 302 fixed to therotor 602 of themotor 600, thecrank pin 301 eccentrically provided at the upper end of themain shaft portion 302 and connected to thecompression mechanism 2, and the small-diameter, sub-bearing supportedportion 303 provided at the lower end of themain shaft portion 302 and supported by the sub-bearing 803, so that the sub-bearing 803 precisely bears the sub-bearing supportedportion 303 while ensuring the required strength for therotation shaft 300. - Further, according to this embodiment, since the centrifugal pump part is used, it is possible to reduce the cost compared with the case of using a positive displacement pump part. Moreover, since the
pump blade 902 extends to the lower end of thepump member 901, the capability of supplying oil is substantially maintained even when the amount of oil in theoil reservoir 730 decreased with the action of thecentrifugal pump blade 902 extending to the lower end of thepump member 901, and therefore, a more reliable pump mechanism can be provided. - Further, according to this embodiment, the
oil passage 311 of therotation shaft 300 comprises thefirst oil passage 311 a that extends from the lower end of the sub-bearing supportedportion 303 to the lower portion of themain shaft portion 302, and thesecond oil passage 311 b that is communicated with thefirst oil passage 311 a and extends to the upper end of thecrank pin 301; thesecond oil passage 311 b has a passage portion that has a smaller diameter than thefirst oil passage 311 a and is placed at an outer of it; a plurality of suchsecond oil passages 311 b are provided within the plain of thecrank pin 301, thereby ensuring both a substantial centrifugal force and a substantial section area of the fluid passage within the limited section area of therotation shaft 300 while the features of therotation shaft 300 are satisfied. By means of it, thesecond oil passage 311 bacts as a second centrifugal pump, and the substantial amount of oil supply is ensured with an inexpensive structure, a reliable scroll compressor is achieved. - Next, second to ninth embodiments will be described with reference to
FIG. 3A toFIG. 11B . The description will be made about the features which is different from the first embodiment, and the other features are substantially the same as those of the first embodiment. - A second embodiment will be described with reference to
FIGS. 3A toFIG. 4 .FIGS. 3A to 3C are diagrams for a pump member of a scroll compressor according to the second embodiment of the present invention:FIG. 3A is a top view;FIG. 3B is a front view; andFIG. 3C is a side view.FIG. 4 is a characteristic curve of a pump part according to a second embodiment. - In the second embodiment, a
pump part 900 has only apump member 901 as constituent member and nopump blade 902 as used in the first embodiment. Thepump member 901 is generally in a conical shape in which the connecting portion with therotation shaft 300 is in a cylindrical shape, and the portion opposite to therotation shaft 300 is in a flat shape, with the connecting portion and the flat shape portion on the opposite end formed of smooth curves. - According to the second embodiment, since the centrifugal effect acts on the entire section area of the flat shape portion of the
pump member 901, the capability of supplying oil existing in thepump member 901 is enhanced, thereby reducing the influence of the oil viscosity and achieving stable oil supply. Specifically, in the case of a merelyconical pump member 901, the reduction in oil viscosity in raised temperature reduces the amount of oil supply dramatically as shown in characteristic curve (b) inFIG. 4 . However, in the case of thepump member 901 in a flat shape according to the second embodiment, there is only small change in the amount of oil supply as shown in characteristic curve (a) inFIG. 4 , thereby achieving stable oil supply. - Moreover, according to the second embodiment, since a stable amount of oil supply can be achieved as described above, the
pump part 900 can be constituted of a single member, and thus can have an inexpensive structure. - Next, a third embodiment will be described with reference to
FIGS. 5A to 5C.FIGS. 5A to 5C are diagrams for a pump member of a scroll compressor according to the third embodiment of the present invention:FIG. 5A is a top view;FIG. 5B is a front view; andFIG. 5C is a side view. - In the third embodiment, a
pump member 901 is generally in a cylindrical shape in which the portion connected with therotation shaft 300 is in a cylindrical shape, and the portion opposite to therotation shaft 300 is in a flat shape. Thepump member 901 according to the third embodiment, because of its generally cylindrical shape, can have an inexpensive structure. - Next, a fourth embodiment will be described with reference to
FIGS. 6A to 6C.FIGS. 6A to 6C are diagrams for a pump part of a scroll compressor according to the fourth embodiment of the present invention:FIG. 6A is a longitudinal section view of a pump part;FIG. 6B is a side view of a single pump blade of the pump part; andFIG. 6C is a section view taken along VIC-VIC inFIG. 6A . - In the fourth embodiment, a
projection 901 cis provided inside apump member 901. Apump blade 902, which is placed inside thepump member 901 and rotates along with thepump member 901, is subject to inertia force of the fluid in thepump 901 driven by therotation shaft 300 and thus subject to force opposite to the rotation direction of therotation shaft 300. In order to resist the force acting on thepump blade 902 and opposing to the rotation direction, the projection 901 c is provided inside thepump member 901 that serves as a stopper against thepump blade 902. The projection 901 c provided to thepump member 901 securely supports thepump blade 902, so that thepump part 900 can have a simple, inexpensive structure and enhanced reliability. Note that the lower end of thepump blade 902 extends only to the cylindrical portion of thepump member 901, and the upper portion of thepump blade 902 extends into theoil passage 311. - Next, a fifth embodiment will be described with reference to
FIGS. 7A to 7C.FIGS. 7A to 7C are diagrams for a pump part of a scroll compressor according to the fifth embodiment of the present invention:FIG. 7A is a longitudinal section view of a pump part;FIG. 7B is a side view of a single pump blade of the pomp part; andFIG. 7C is a section view taken along VIIC-VIIC inFIG. 7A . - In the fifth embodiment, a pair of projections 901 c is provided inside a
pump member 901. There are provided two pairs of projections 901 c at two respective opposite positions. Apump blade 902 is placed so that both the ends thereof are sandwiched between respective pairs of projections 901 c. Thus thepump blade 902 is securely supported to supply oil when therotation shaft 300 is rotated either in normal direction or in reverse direction. - Next, a sixth embodiment will be described with reference to
FIGS. 8A to 8C.FIGS. 8A to 8C are diagrams for a pump part of a scroll compressor according to the sixth embodiment of the present invention:FIG. 8A is a longitudinal section view of a pump part;FIG. 8B is a side view of a single pump blade of the pomp part; andFIG. 8C is a section view taken along VIIIC-VIIIC inFIG. 8A . - The sixth embodiment is different from the fifth embodiment in that a
pump blade 902 extends to the lower end of apump member 901, but the other features of the sixth embodiment are the same as those of the fifth embodiment. According to the sixth embodiment, similar to the first embodiment, the capability of supplying oil is substantially maintained even when the amount of oil in theoil reservoir 730 decreased with the action of thecentrifugal pump blade 902 extending to the lower end of thepump member 901, and therefore, a more reliable pump mechanism can be obtained. - Next, a seventh embodiment will be described with reference to
FIGS. 9A to 9C.FIGS. 9A to 9C are diagrams for a pump part of a scroll compressor according to the seventh embodiment of the present invention:FIG. 9A is a longitudinal section view of a pump part;FIG. 9B is a side view of a single pump blade of the pomp part; andFIG. 9C is a section view taken along IXC-IXC inFIG. 9A . - The seventh embodiment is different from the sixth embodiment in that the portion of a
pump member 901 opposite to the connecting portion thereof to therotation shaft 300 has a spherical surface, but the other features of the seventh embodiment are the same as those of the sixth embodiment. According to the seventh embodiment, the inner wall of thepump member 900 has steeper slope with respect to the axis of therotation shaft 300 than the case of conical shape or cylindrical shape, so as to enhance the centrifugal pump effect and achieve the capability of stable oil supply, and therefore a more reliable pump mechanism can be provided. - Next, an eighth embodiment will be described with reference to
FIG. 10A andFIG. 10B .FIG. 10A andFIG. 10B are diagrams for a lower portion of a rotation shaft of a scroll compressor according to an eighth embodiment of the present invention:FIG. 10A is a longitudinal section view of a lower portion of a rotation shaft; andFIG. 10B is a section view taken along XB-XB inFIG. 10A . - In the eighth embodiment, a
pump member 901 has a periphery portion consisting of double cylinders. The outer space in thepump member 901 is open to the lower face of thesub-bearing part 800. The inner space in thepump member 901 is similar to that of the first embodiment. - According to the eighth embodiment, the cylindrical portion disposed at the periphery of the
pump member 901 provides a third centrifugal pump effect. Oil discharged from the upper end of the third centrifugal pump is used for lubricating the sub-bearing 803 placed in thesub-bearing part 800. Therefore, stable oil supply to the sub-bearing 803 can be achieved, and since the oil supply passage is separated from the oil supply into thepump member 901, an oil supply structure can be obtained that is easily designed and has a higher reliability. - Next, a ninth embodiment will be described with reference to
FIG. 11A andFIG. 11B .FIG. 11A andFIG. 11B are diagrams for a lower portion of a rotation shaft of a scroll compressor according to a ninth embodiment of the present invention:FIG. 11A is a longitudinal section view of a lower portion of a rotation shaft; andFIG. 11B is a section view taken along XIB-XIB inFIG. 11A . - In the ninth embodiment, means for connecting a
pump member 901 to arotation shaft 300 is a thread having a screw thread whose screw direction is the same as the rotation direction of therotation shaft 300. Thepump member 901 is subject to force opposite to the rotation direction of therotation shaft 300. Accordingly, the thread of the connection means is subject to force in the direction for tightening the screw, due to the force opposite to the rotation direction of therotation shaft 300 that acts on thepump member 901, and therefore thepump member 901 is not disconnected from therotation shaft 300, and a more reliable pump structure can be obtained. - It should be further understood by those skilled in the art that although the foregoing description has been made on embodiments of the invention, the invention is not limited thereto and various changes and modifications may be made without departing from the spirit of the invention and the scope of the appended claims.
Claims (10)
1. A fluid compressor comprising in a sealed container: a compression mechanism for compressing fluid; a rotation shaft connected to said compression mechanism and having an oil passage; a motor for driving said rotation shaft; a main bearing for supporting said rotation shaft above said motor; a sub-bearing for supporting said rotation shaft below said motor; and a centrifugal pump part for supplying oil reserved in a bottom of said sealed container through said oil passage to said compression mechanism and said bearings,
wherein said rotation shaft integrally comprises a main shaft portion fixed to a rotor of said motor, a crank pin eccentrically provided at an upper end of said main shaft portion and connected to said compression mechanism, and a small-diameter, sub-bearing supported portion provided at a lower end of said main shaft portion and supported by said sub-bearing;
said oil passage of said rotation shaft comprises a first oil passage extending from a lower end of said sub-bearing supported portion to a lower portion of said main shaft portion, and a second oil passage that is communicated with said first oil passage and extends to an upper end of said crank pin; and
said second oil passage comprises a passage portion that has a smaller diameter than and is placed at an outer of said first oil passage; a plurality of said second oil passages are provided within a plain of said crank pin.
2. The fluid compressor according to claim 1 , wherein said first oil passage is provided concentrically with said rotation shaft, and said second passage overlaps said first oil passage so that said second oil passage is communicated with said first oil passage on a peripheral thereof in a substantial length in an axial direction.
3. The fluid compressor according to claim 1 , wherein said pump part comprises a pump member in a cylindrical shape attached to the lower end of said rotation shaft, and a pump blade placed inside said pump member; said pump member comprises a portion that is attached to the lower end of said rotation shaft, and a portion extending therefrom downward in which the section area of the fluid passage decreases; and said pump blade has an outer shape that is identical to an inner shape of said pump member, and is press-fitted in said pump member so as to reach a lower end of the inside of said pump member.
4. The fluid compressor according to claim 3 , wherein the portion of said pump member in which the section area of the fluid passage decreases has a spherical shape.
5 The fluid compressor according to claim 1 , wherein said pump part comprises a cylindrical pump member, and said pump member has a cylindrical connecting portion to said rotation shaft and a flat portion opposite to said connecting portion.
6. The fluid compressor according to claim 1 , wherein said pump member comprises a cylindrical pump member attached to the lower end of said rotation shaft, and a pump blade placed inside said pump member; and the pump member has a projection for preventing rotation of said pump blade.
7. The fluid compressor according to claim 1 , wherein said pump part comprises a cylindrical pump member, and projections of said pump member are configured to sandwich a pump blade.
8. The fluid compressor according to claim 1 , wherein said pump part comprises a cylindrical pump member, and said pump member has a connecting portion to said rotation shaft that is connected by a thread having a screw thread whose screw direction is the same as the rotation direction of said rotation shaft.
9. A fluid compressor comprising in a sealed container: a compression mechanism for compressing fluid; a rotation shaft connected to said compression mechanism and having an oil passage; a motor for driving said rotation shaft; a bearing for supporting said rotation shaft; and a centrifugal pump part for supplying oil reserved in a bottom of said sealed container through said oil passage to said compression mechanism and said bearings,
wherein said pump part comprises a cylindrical pump member, and said pump member has a cylindrical connecting portion to said rotation shaft and a flat portion opposite to said connecting portion.
10. A fluid compressor comprising in a sealed container: a compression mechanism for compressing fluid; a rotation shaft connected to said compression mechanism and having an oil passage; a motor for driving said rotation shaft; a main bearing for supporting said rotation shaft above said motor; a sub-bearing for supporting said rotation shaft below said motor; and a centrifugal pump part for supplying oil reserved in a bottom of said sealed container through said oil passage to said compression mechanism and said bearings,
wherein said pump part comprises a double cylindrical pump member, and the outer space in said pump member is open to a lower face of said sub-bearing.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003379436A JP2005140066A (en) | 2003-11-10 | 2003-11-10 | Fluid compressor |
JP2003-379436 | 2003-11-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050180871A1 true US20050180871A1 (en) | 2005-08-18 |
Family
ID=34689487
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/982,927 Abandoned US20050180871A1 (en) | 2003-11-10 | 2004-11-08 | Fluid compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20050180871A1 (en) |
JP (1) | JP2005140066A (en) |
KR (1) | KR100657038B1 (en) |
CN (1) | CN100376800C (en) |
Cited By (6)
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US20100150752A1 (en) * | 2008-12-15 | 2010-06-17 | Hitachi Appliances, Inc. | Revolution type compressor |
WO2011009186A1 (en) * | 2009-07-24 | 2011-01-27 | Whirlpool S.A | Hermetic compressor |
US20160222967A1 (en) * | 2015-02-03 | 2016-08-04 | Emerson Climate Technologies, Inc. | Compressor with oil pump assembly |
EP2626981A4 (en) * | 2010-10-06 | 2017-01-04 | ULVAC, Inc. | Eccentric rotation drive device |
WO2019037976A1 (en) * | 2017-08-21 | 2019-02-28 | Arcelik Anonim Sirketi | A compressor with improved lubrication performance |
EP3995696A1 (en) * | 2020-11-06 | 2022-05-11 | LG Electronics Inc. | Hermetic compressor |
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CN102102671B (en) * | 2009-12-17 | 2012-11-07 | 广东美芝制冷设备有限公司 | Oil supply device of compressor and application thereof |
US9689388B2 (en) | 2013-06-05 | 2017-06-27 | Lg Electronics Inc. | Scroll compressor |
EP3001039B1 (en) * | 2015-09-11 | 2019-06-19 | Pfeiffer Vacuum Gmbh | Vacuum pump |
AT15828U1 (en) * | 2016-12-27 | 2018-07-15 | Secop Gmbh | LUBRICANT CONSUMPTION FOR A REFRIGERANT COMPRESSOR AND REFRIGERANT COMPRESSOR |
CN106949060B (en) * | 2017-04-19 | 2019-03-05 | 西安庆安制冷设备股份有限公司 | A kind of rotor-type compressor oil suction structure and its design method |
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Also Published As
Publication number | Publication date |
---|---|
KR20050045850A (en) | 2005-05-17 |
CN100376800C (en) | 2008-03-26 |
KR100657038B1 (en) | 2006-12-12 |
JP2005140066A (en) | 2005-06-02 |
CN1616828A (en) | 2005-05-18 |
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Legal Events
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Owner name: HITACHI, LTD., TRUSTEE, FOR THE BENEFIT OF HITACHI Free format text: TRUST AGREEMENT;ASSIGNOR:HITACHI AIR CONDITIONING SYSTEMS CO., LTD.;REEL/FRAME:016772/0091 Effective date: 20050629 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |