WO2012144067A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
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- WO2012144067A1 WO2012144067A1 PCT/JP2011/059938 JP2011059938W WO2012144067A1 WO 2012144067 A1 WO2012144067 A1 WO 2012144067A1 JP 2011059938 W JP2011059938 W JP 2011059938W WO 2012144067 A1 WO2012144067 A1 WO 2012144067A1
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- WIPO (PCT)
- Prior art keywords
- loss
- eccentric portion
- eccentric
- groove
- scroll compressor
- Prior art date
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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
- 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
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
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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
- F04C29/023—Lubricant distribution through a hollow driving shaft
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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
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
Definitions
- the present invention relates to a scroll compressor used in a refrigerating and air-conditioning apparatus, and more particularly to a scroll compressor provided with an orbiting sliding bearing that engages and slides with an eccentric portion of a crankshaft.
- the scroll compressor is a compressor that compresses a gas such as a refrigerant by relatively swiveling two scroll members having a spiral tooth shape.
- the other movable orbiting scroll is configured to orbit with respect to a fixed scroll that is constrained by screws or welding.
- the orbiting scroll is provided with an orbiting sliding bearing that engages and slides with the eccentric portion of the crankshaft, while the eccentric portion of the crankshaft and the orbiting sliding bearing slide through the lubricating oil, Many mechanisms have been adopted in which the rotational movement of the crankshaft is transmitted to the orbiting scroll for the orbiting movement.
- Patent Document 1 Japanese Patent Laid-Open No. 2003-239876
- Patent Document 2 Another conventional technique is described in Japanese Patent Laid-Open No. 11-159484 (Patent Document 2).
- Patent Document 2 states that “a D-cut is formed on the outer peripheral surface of the eccentric pin portion within the range of 30 ° or more and 120 ° or less from the eccentric direction of the eccentric pin portion to the crankshaft in the counter-rotating direction with respect to the crankshaft. It is described.
- the D cut is described as “a lubrication notch is provided in a relatively large area between the eccentric shaft portion and the bearing portion”.
- JP 2003-239876 A Japanese Patent Laid-Open No. 11-159484
- An object of the present invention is to reduce bearing loss during fluid lubrication by reducing the shear resistance of an oil film caused by lubricating oil existing between the outer peripheral surface of the eccentric portion of the crankshaft and the inner peripheral surface of the orbiting slide bearing. It is to reduce.
- the present invention provides a fixed scroll, a turning scroll meshing with the fixed scroll, a crankshaft having an eccentric portion at the end for turning the turning scroll, and a shaft inside the crankshaft.
- An oil supply hole penetrating in the direction and having an opening at an end surface of the eccentric portion, a orbiting sliding bearing provided in the orbiting scroll and slidably engaged with the eccentric portion of the crankshaft, and the eccentric portion of the crankshaft.
- An oil supply passage provided on the outer periphery of the eccentric portion so as to communicate the upper end side and the lower end side of the eccentric portion, and lubrication between the eccentric portion and the orbiting slide bearing is performed by the lubricating oil supplied from the oil supply hole.
- an axial loss reduction groove provided separately from the oil supply passage on the outer periphery of the eccentric portion of the crankshaft, and the offset in the loss reduction groove. Characterized in that it comprises a sealing portion provided at least one end face side and the base end side parts.
- the shear resistance of the oil film due to the lubricating oil existing between the outer peripheral surface of the eccentric part of the crankshaft and the inner peripheral surface of the orbiting sliding bearing can be reduced, and the bearing loss during fluid lubrication is reduced. There is an effect that can be done.
- FIG. 2 is an enlarged perspective view near an eccentric portion shown in FIG. 1. It is an expanded sectional view of the eccentric part vicinity shown in FIG.
- FIG. 4 is a cross-sectional view taken along line AA in FIG. 3.
- FIG. 4 is a sectional view taken along line BB in FIG. 3.
- FIG. 4 is a sectional view taken along the line CC of FIG. 3.
- FIG. 4 is a diagram for explaining a shaft rotation direction, an angular position, and a bearing load direction in a BB cross section of FIG. 3.
- FIG. 4 is a diagram for explaining a shaft rotation direction, an angular position, and a bearing load direction in a BB cross section of FIG. 3.
- FIG. 4 is a diagram for explaining a start position of a loss reduction groove in the present invention, where (a) is a diagram for explaining the relationship between the start position of the loss reduction groove and relative bearing loss, and (b) is a relative view of the start position of the loss reduction groove It is a diagram explaining the relationship with the minimum oil film thickness. It is a diagram explaining the relationship between the depth of the loss reduction groove
- FIG. 1 is a longitudinal sectional view showing Embodiment 1 of the scroll compressor of the present invention.
- a scroll compressor 1 shown in FIG. 1 is a hermetic scroll compressor used for an air conditioner such as an air conditioner or a refrigeration air conditioner such as a refrigeration apparatus.
- a fixed scroll 112 and an orbiting scroll 109 that engages with the fixed scroll 112 and performs an orbiting motion are provided at the upper part in the sealed container 2.
- An electric motor 102 is provided in the sealed container 2, and a crankshaft 103 is connected to the electric motor 102, and the crankshaft 103 is a main bearing provided on a frame 104 fixed in the sealed container 2.
- 105 and a sub-bearing 107 provided on the lower frame 106 are rotatably supported.
- An eccentric part 108 is provided at the upper part of the crankshaft 103, and the eccentric part 108 engages and slides with the orbiting sliding bearing 110 provided on the lower surface of the end plate of the orbiting scroll 109.
- the whirling rotational motion (eccentric motion) is transmitted to the orbiting scroll 109.
- the orbiting scroll 109 is controlled to rotate by the Oldham ring 111 and revolves with respect to the fixed scroll 112. Thereby, the low-pressure refrigerant gas is sucked from the suction port 113 and compressed, and then discharged to the outside through the discharge port 114.
- the crankshaft 103 is provided with an oil supply hole 115 penetrating from the lower end thereof to the end surface (upper end surface) side of the eccentric portion 108, and the lubricating oil 3 stored in the lower part of the sealed container receives the pressure difference. Or by a pump separately attached to the lower end portion of the crankshaft so as to be pushed up through the oil supply hole 115 and supplied to a sliding portion such as each bearing portion (main bearing 105, sub-bearing 107, slewing sliding bearing 110). It is configured.
- the inside of the sealed container 2 has a discharge pressure
- the intermediate chamber (back pressure chamber) 119 on the back of the end plate of the orbiting scroll 109 has an intermediate pressure between the discharge pressure and the suction pressure. . For this reason, the lubricating oil stored in the lower part of the sealed container is supplied to the bearings and the like through the oil supply holes 115 due to a pressure difference between the discharge pressure and the intermediate pressure.
- FIG. 2 is an enlarged perspective view near the eccentric portion 108 shown in FIG.
- the oil supply hole 115 is opened at the upper end surface of the eccentric portion 108.
- the eccentric portion 108 is provided with an axial oil supply passage 116 so as to communicate from the upper end (end surface) 108a side to the lower end (base end) 108b side.
- a loss reduction groove 117 is formed in the axial direction by digging the outer peripheral surface of the eccentric portion 108.
- seal portions 118a and 118b are provided on the upper end 108a side and the lower end 108b side of the loss reducing groove 117.
- FIG. 3 is an enlarged sectional view near the eccentric portion 108 shown in FIG.
- An orbiting sliding bearing 110 is provided in the orbiting boss 109a of the orbiting scroll 109, and an eccentric part 108 of the crankshaft 103 is inserted into and engaged with the orbiting sliding bearing 110.
- the sliding bearing 110 slides and slides.
- the space enclosed between the upper end (end surface) 108a of the eccentric part 108 and the orbiting scroll 109 communicates with the oil supply hole 115, and since the upstream of the oil supply path, the pressure of the lubricating oil supplied here is The discharge pressure is almost the same.
- the pressure on the lower end (base end) 108b side of the eccentric portion 108 communicates with the intermediate chamber 119 having a lower pressure than the upper end 108 side, and the lubricating oil supplied from the oil supply hole 115 passes through the orbiting scroll 109. And the space surrounded by the eccentric portion 108 and the orbiting and sliding bearing 110 (the inner space of the orbiting boss portion) 4 is filled, and then discharged to the lower intermediate chamber 119 through the oil supply passage 116 and the like.
- the oil supply passage 116 is formed by a digging groove or a notch formed by digging the outer periphery of the eccentric portion 108 inward, and the oil supply passage 116 enlarges a gap between the eccentric portion 108 and the orbiting / sliding bearing 110, and The slewing bearing 110 extends across the axial direction and communicates with both the upper end 108a side and the lower end 108b side of the eccentric portion 108. Therefore, the flow resistance of the lubricating oil in the inner space 4 of the swivel boss portion flowing through the oil supply passage 116 to the intermediate chamber 119 is greater than the flow resistance of the lubricating oil flowing through a portion other than the oil supply passage 116 on the outer peripheral surface of the eccentric portion 108. Get smaller.
- the loss reduction groove 117 is also formed by a digging groove or a notch formed by digging the outer periphery of the eccentric portion 108 inward.
- the loss reduction groove 117 has an eccentricity on the upper end 108a side and the lower end 108b side.
- a seal portion 118 having the same diameter as the outer peripheral surface of the portion 108 is formed, and the axial length of the loss reducing groove 117 is shorter than that of the orbiting slide bearing 110. Therefore, the loss reducing groove 117 does not straddle the slewing plain bearing 110 in the axial direction, and does not open simultaneously on the upper end 108a side and the lower end 108b side of the eccentric portion 108.
- the gap between the outer periphery of the eccentric portion 108 and the inner periphery of the orbiting / sliding bearing 110 is equal to the portion other than the oil supply passage 116 on the outer periphery of the eccentric portion 108. That is, the flow resistance flowing from the upper end 108a to the lower end 108b of the eccentric portion 108 through the loss reducing groove 117 is substantially equal to the flow resistance flowing through a portion other than the oil supply passage 116 on the outer peripheral surface of the eccentric portion 108.
- the lubricating oil supplied from the oil supply hole 115 to the inner space 4 of the turning boss part preferentially passes through the oil supply passage 116 and easily flows to the intermediate chamber 119 side.
- the flow resistance in which the lubricating oil flows in the axial direction in the entire portion of the slewing bearing 110 is substantially the same as that in the case where the loss reducing groove 117 is not provided, and even if the loss reducing groove 117 is provided, the amount of oil supply is increased. Is prevented.
- FIG. 4 is a cross-sectional view taken along the line AA in FIG. 3
- FIG. 5 is a cross-sectional view taken along the line BB in FIG. 3
- FIG. 6 is a cross-sectional view taken along the line CC in FIG. Since the diameter of the outer peripheral surface of the eccentric part 108 is smaller than the diameter of the inner peripheral surface of the orbiting / sliding bearing 110, there is a gap between them, and this gap is filled with lubricating oil.
- the oil supply passage 116 opens at a portion of the upper end 108 a of the eccentric portion 108, and a gap between the oil supply passage 116 and the swivel bearing 110 is a portion where the oil supply passage 116 is not provided.
- the gap between the eccentric portion 108 and the slewing plain bearing 110 is particularly wide.
- the gap between the oil supply passage 116 of the eccentric portion 108 and the swivel slide bearing 110 and the loss reduction groove 117 of the eccentric portion 108 is particularly wider than the gap between the other part of the eccentric portion 108 and the slewing plain bearing 110.
- the loss reduction groove 117 does not exist, and the portion of the oil supply passage 116 of the eccentric portion 108 and the slewing slide bearing 110 is particularly wider than the gap between the eccentric portion 108 where the oil supply passage 116 is not provided and the slewing plain bearing 110.
- FIG. 7 is a diagram for explaining the shaft rotation direction, the angular position, and the bearing load direction in the BB cross section of FIG.
- FIG. 7 shows the positions in the bearing load direction 121 where the swivel bearing 110 is pressed against the oil supply passage 116, the loss reduction groove 117, the rotation direction 120 of the crankshaft 103, and the eccentric portion 108. This will be described in more detail.
- the angular positions of various parts will be described using a coordinate system in which the center of the eccentric part 108 is used as a reference and the opposite side of the eccentric part 108 is 0 °.
- the orbiting scroll 109 When the crankshaft 103 rotates in the clockwise direction as shown in the axial rotation direction 120, the orbiting scroll 109 has a resultant force of a reaction force that compresses the gas and a centrifugal force that the orbiting scroll is swung in the eccentric direction. A bearing load is generated in the bearing load direction 121. At this time, the gap between the eccentric portion 108 and the orbiting / sliding bearing 110 is not uniform in the circumferential direction but is biased, and is minimized at the minimum gap portion 122 shifted from the bearing load direction 121 to the counter-rotating direction.
- the loss reduction groove 117 is provided on the outer periphery of the shaft, and the bearing loss due to oil film shear when the shaft is slid with respect to the cylindrical sliding bearing through the lubricating oil is evaluated. The effect of reducing bearing loss was verified. The verification results are shown in FIGS. From this result, the position, depth, and width of the loss reducing groove 117 that can effectively reduce the bearing loss were examined. In this verification, the verification is performed assuming that the shaft diameter of the eccentric portion is 14 to 18 mm in a scroll compressor for an air conditioner. Hereinafter, this will be described in detail with reference to FIGS.
- FIG. 8 is a diagram for explaining the starting position of the loss reducing groove 117 according to the present invention.
- FIG. 8A is a diagram for explaining the relationship between the starting position of the loss reducing groove 117 and the relative bearing loss, and
- FIG. It is a diagram explaining the relationship between the starting position of a groove
- the loss reduction groove 117 is formed by digging the outer periphery of the shaft into a digging groove, and is caused by oil film shearing when sliding is performed on the cylindrical slide bearing through the lubricating oil.
- the bearing loss is shown, and the evaluation is performed by changing various circumferential start positions of the loss reducing groove 117 formed on the outer periphery of the shaft.
- the horizontal axis represents the circumferential start position of the loss reducing groove 117, and the vertical axis represents the relative bearing loss relative to the bearing loss when the shaft without the loss reducing groove 117 is used.
- the loss reducing groove 117 is a digging groove having a depth of 0.1 mm and an angular range (angular width) of 30 degrees in the circumferential direction.
- the relative bearing loss tends to decrease particularly when the starting angle of the loss reducing groove is in the range of 140 degrees to 210 degrees.
- the starting position of the loss reducing groove 117 is preferably provided in the range of 140 ° to 210 °, and by setting this range, the bearing loss can be reduced by at least 2% or more.
- the reduction effect is greatest. If the loss reduction groove 117 is provided so that at least a part of the loss reduction groove 117 exists in the range of 140 ° to 210 °, the bearing loss reduction effect can be reduced as compared with the conventional one.
- FIG. 7B is a diagram showing the relationship between the start position of the loss reduction groove and the relative minimum oil film thickness, where the horizontal axis represents the circumferential start position of the loss reduction groove 117 and the vertical axis represents the loss reduction groove 117.
- the minimum oil film thickness when using a shaft without a mark is 100%, and the relative minimum oil film thickness is shown.
- the starting position of the loss reducing groove 117 is 140 degrees or less, the starting position of the loss reducing groove 117 is close to the angle at which the minimum oil film thickness is obtained. If the reduction groove 117 is provided, the bearing behavior becomes unstable, and wear due to contact between the shaft and the bearing is likely to proceed.
- the start position of the loss reduction groove 117 in an angle range of at least 140 degrees or more.
- the minimum oil film thickness is sufficiently large even if a part of the loss reduction groove 117 covers 210 ° or more, so if the start position of the loss reduction groove 117 is in the range of 140 ° to 210 °, the end The position may be a position of 210 degrees or more.
- FIG. 9 is a diagram for explaining the relationship between the depth of the loss reducing groove 117 and the relative bearing loss in the present invention.
- the loss reduction groove 117 is a digging groove formed by digging the outer periphery of the shaft, and indicates a bearing loss due to oil film shear when sliding is performed on the cylindrical sliding bearing through the lubricating oil.
- the depth of the loss reducing groove 117 formed in was variously evaluated.
- the horizontal axis represents the depth of the loss reduction groove 117 (digging depth), and the vertical axis represents the bearing loss when a shaft without the loss reduction groove 117 is used as 100%, and shows the relative bearing loss relative thereto. Yes.
- the loss reduction groove 117 was formed in an angle range (angle width) of 30 degrees in the circumferential direction, and the start angle of the loss reduction groove was 150 degrees.
- the bearing loss can be reduced by at least 2% by setting the depth of the loss reducing groove to 0.002 mm or more. Further, if the depth of the loss reducing groove is 0.01 mm or more, there is at least a 5% or more bearing loss reducing effect, and if the depth of the loss reducing groove is 0.05 mm or more, the bearing loss reducing effect is the largest. Become. If the depth of the loss reducing groove 117 is excessively increased, the rigidity of the shaft is reduced. Therefore, the depth of the loss reducing groove 117 is 20% or less of the shaft diameter (the shaft diameter of the eccentric portion of the crankshaft) at the maximum. It is preferable. Therefore, generally, the depth of the loss reducing groove is preferably about 0.05 to 0.5 mm.
- FIG. 10 is a diagram illustrating the relationship between the circumferential angle width of the loss reducing groove and the relative bearing loss in the present invention.
- the loss reduction groove 117 is a digging groove formed by digging the outer periphery of the shaft, and indicates a bearing loss due to oil film shear when sliding is performed on the cylindrical sliding bearing through the lubricating oil.
- the evaluation was performed by changing the circumferential angle width of the loss reducing groove 117 formed in various ways.
- the horizontal axis represents the angular width in the circumferential direction of the loss reducing groove 117, and the vertical axis represents the relative bearing loss with respect to the bearing loss when the shaft without the loss reducing groove 117 is used as 100%.
- the depth of the loss reducing groove 117 was 0.1 mm, and the starting angle of the groove was 150 degrees.
- the relative bearing loss is an angle of 10 degrees or more in the circumferential direction from the position of the starting angle 150 degrees in the circumferential direction of the loss reducing groove 117 in this example, that is, 10 degrees or more.
- the bearing loss can be reduced by at least 2%.
- the angle width is preferably in the range of 20 ° to 60 ° in consideration of the workability of the bearing loss groove 117 and the like.
- the angle range from 140 degrees to 210 degrees in the coordinate system shown in FIG.
- the starting position of the loss reduction groove 117 is set at an angle of about 150 degrees in the coordinate system shown in FIG. It was verified that a great bearing loss reduction effect can be obtained by setting the position, the angular width of the groove to 20 ° to 60 °, and the depth of the groove to 0.01 mm or more.
- FIG. 11 is a diagram illustrating the relationship between the rotational speed of the shaft and the relative bearing loss in the present invention. That is, it shows the bearing loss due to oil film shearing when a shaft with a loss reduction groove 117 on the outer periphery and a shaft without a loss reduction groove are slid with respect to a cylindrical bearing through lubricating oil.
- the evaluation was made by changing the rotational speed of the shaft in various ways.
- the horizontal axis in FIG. 11 is the rotational speed
- the vertical axis is the bearing loss when rotating at a rotational speed of 6000 rpm using an axis without a loss reduction groove, and the relative bearing loss relative to this is shown. Show.
- the loss reduction groove 117 is a digging groove having a depth of 0.1 mm, and the loss reduction groove 117 is formed in an angular range (angle width) of 30 degrees in the circumferential direction, and the start angle of the loss reduction groove is Was 150 degrees.
- the loss reduction groove 117 is preferably a digging groove having a depth of 0.05 mm or more from the shaft outer peripheral surface before processing.
- a notch shape may be used, and a bearing loss reduction effect that is almost the same as that in the case of the digging groove can be obtained.
- the depth from the outer peripheral surface of the shaft before machining to the axial center direction continuously increases or decreases from 0 mm depending on the angular position in the circumferential direction.
- a wider circumferential angular width is required.
- the notch shape as shown in FIG. 12 has an effect that the processing cost can be reduced as compared with the case of forming the digging groove as shown in FIG.
- a seal part 118a is provided on the end face 108a side of the eccentric part in the loss reducing groove 117, and a seal part 118b is provided on the base end 108b side. It may be provided in at least one of the portions 118a and 118b.
- the seal portion 118 is provided only on the base end 108 b side (intermediate chamber side) of the loss reducing groove 117. In this case, the lubricating oil flowing out from the oil supply hole 115 opened at the upper end of the eccentric portion 108 is likely to flow into the loss reduction groove 117, and the amount of oil supply increases somewhat.
- FIG. 13 the seal portion 118 is provided only on the base end 108 b side (intermediate chamber side) of the loss reducing groove 117.
- the area of the loss reduction groove 117 can be increased, so that there is an advantage that the bearing loss reduction effect can be further improved.
- the seal portion 118 is provided adjacent to the intermediate chamber side (base end side), an extreme increase in the amount of oil supply can be prevented.
- a plurality of loss reduction grooves 117 may be formed in the circumferential direction of the eccentric portion 108 as shown in FIG. That is, when the position of 140 degrees in the anti-eccentric direction of the eccentric part 108 in the counter-rotating direction of the crankshaft is the start position of the loss reduction groove 117 and the end position of the groove is 210 degrees, the loss reduction groove 117
- the circumferential angular width is 70 degrees.
- the loss reduction groove 117 is divided into a loss reduction groove 117a in the range of 140 ° to 165 ° and a loss reduction groove 117b in the range of 185 ° to 210 ° at the angular position, and the loss reduction groove 117 is provided. A portion not provided with the notch is left in a range of 165 ° to 185 ° of the intermediate portion.
- the loss reduction groove 117 does not easily form an oil film pressure that supports the bearing load.
- the loss reduction groove is divided into a plurality of portions in the circumferential direction.
- both of the plurality of loss reduction grooves 117a and 117b whose circumferential start positions are located around the center of the eccentric portion from the anti-eccentric direction of the eccentric portion. It is preferable to provide at a position of 140 ° to 210 ° in the counter-rotating direction of the crankshaft. However, at least one circumferential start position of the plurality of loss reduction grooves is a position of the 140 ° to 210 °.
- the bearing loss reduction effect can be obtained by providing it in
- the outer peripheral surface of the eccentric portion of the crankshaft and the inner peripheral surface of the orbiting sliding bearing slide through the lubricating oil
- the outer peripheral surface of the eccentric portion and the inner peripheral surface of the slide bearing Since the shear resistance of the oil film due to the lubricating oil existing between the surfaces can be reduced, bearing loss during fluid lubrication can be reduced. This effect will be described in more detail.
- the shear stress ⁇ of a thin fluid lubricating oil film has a relationship of increasing with a change gradient dU / dh in the direction of the oil film thickness h in the axial rotation direction flow velocity U of the lubricating oil and the lubricating oil viscosity ⁇ . ing.
- the digging groove is formed in the outer periphery of the eccentric shaft so that the gap between the outer periphery of the eccentric shaft and the inner periphery of the orbiting slide bearing becomes relatively small. Or it can expand by providing the loss reduction groove
- the oil film thickness h by the lubricating oil that fills the loss reduction groove can be increased, so that the change gradient dU / dh can be reduced to reduce the shear stress of the oil film. Therefore, since the shear resistance of the oil film, which is the integral value of the shear stress, is reduced, bearing loss can be reduced.
- the loss reducing groove straddles the slewing bearing in the axial direction and does not communicate with the end face side and the base end side of the eccentric part at the same time.
- the oil supply passage is configured to communicate with the end face side and the base end side of the eccentric portion across the slewing plain bearing in the axial direction.
- the lubricating oil supply state in the eccentric portion is maintained in the same manner as the conventional one not provided with the loss reduction groove, and even if the loss reduction groove is provided as in this embodiment, the amount of oil supply increases. It is possible to prevent the oiling condition from getting worse.
- the start position of the loss reducing groove is provided around the center of the eccentric shaft within an angle range of 140 ° to 210 ° from the anti-eccentric direction of the eccentric portion to the counter-rotating direction of the crankshaft. It is said. As described above, if the start position of the loss reducing groove is 140 degrees or less, the generation of the oil film pressure supporting the load is hindered, the effect of reducing the bearing loss is lost, and the oil film pressure is reduced. Therefore, the oil film may be cut, so the angle is 140 degrees or more.
- the loss reducing groove has a portion having a radial depth of 0.002 mm or more (preferably 0.01 to 0.05 mm or more) from the outer peripheral circle of the eccentric part before processing. It is formed so that it exists in the range of 140 ° to 210 ° (preferably 145 ° to 180 °) from the anti-eccentric direction of the part to the counter-rotating direction of the crankshaft, so that there is little variation due to dimensional errors, etc. Can reduce the bearing loss.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
この軸受損失の低減を図るようにした従来技術としては、特開2003-239876号公報(特許文献1)に記載のものがある。この文献には、「旋回スクロールの下部に形成されたハブの挿入溝にフローティングリング部材が自転と空転自在に保持され、フローティングリング部材の中心には、回転軸の偏心部に固定されたスライドブッシュが挿入されてスクロール圧縮機の摩擦損失低減装置を構成する」と記載されている。 In recent years, in order to reduce the energy consumption of the scroll compressor and reduce the load on the electric motor, reduction of bearing loss caused by sliding between the shaft and the bearing has been an issue.
As a conventional technique for reducing the bearing loss, there is a technique described in Japanese Patent Laid-Open No. 2003-239876 (Patent Document 1). This document states that “a floating ring member is rotatably and idly held in a hub insertion groove formed in a lower part of the orbiting scroll. Is inserted to constitute a friction loss reducing device for a scroll compressor. "
図1に示すスクロール圧縮機1は、エアコンなどの空調装置や冷凍装置などの冷凍空調用に使用される密閉形のスクロール圧縮機である。密閉容器2内の上部には固定スクロール112と、この固定スクロール112と噛み合って旋回運動する旋回スクロール109が設けられている。また、密閉容器2内には電動機102が設けられ、この電動機102にはクランク軸103が接続され、このクランク軸103は、密閉容器2内に固設されたフレーム104に設けられている主軸受105、及び下フレーム106に設けられた副軸受107により回転自在に支持されている。 FIG. 1 is a longitudinal sectional
A
以下、図8~図11を用いて詳細に説明する。 The
Hereinafter, this will be described in detail with reference to FIGS.
前記損失低減溝117については、図9から明らかなように、加工前の軸外周面から深さ0.05mm以上掘り込んだ掘り込み溝とすることが望ましいが、図12に示すように、切欠き形状としても良く、掘り込み溝とした場合とほぼ同様の軸受損失低減効果を得ることができる。 12 to 14 are enlarged perspective views of the vicinity of the eccentric portion showing another example of the
As is apparent from FIG. 9, the
102:電動機、103:クランク軸、104:フレーム、105:主軸受、
106:下フレーム、107:副軸受、
108:偏心部、108a:端面(上端)、108b:基端(下端)、
109:旋回スクロール、110:旋回滑り軸受、
111:オルダムリング、
112:固定スクロール、
113:吸入口、
114:吐出口、
115:給油穴、
116:給油通路、
117,117a,117b:損失低減溝、
118,118a,118b:シール部、
119:中間室(背圧室)、
120:軸回転方向、121:軸受荷重方向、
122 最小隙間部。 1: Scroll compressor, 2: Sealed container, 3: Lubricating oil, 4: Space in the rotating boss part,
102: Electric motor, 103: Crankshaft, 104: Frame, 105: Main bearing,
106: lower frame, 107: auxiliary bearing,
108: eccentric part, 108a: end face (upper end), 108b: base end (lower end),
109: orbiting scroll, 110: orbiting sliding bearing,
111: Oldham ring,
112: Fixed scroll,
113: inlet
114: discharge port,
115: Refueling hole,
116: Refueling passage,
117, 117a, 117b: loss reduction grooves,
118, 118a, 118b: seal part,
119: Intermediate chamber (back pressure chamber),
120: shaft rotation direction, 121: bearing load direction,
122 Minimum gap.
Claims (9)
- 固定スクロールと、この固定スクロールと噛み合う旋回スクロールと、
この旋回スクロールを旋回運動させるために端部に偏心部を有するクランク軸と、
該クランク軸内を軸方向に貫通し、前記偏心部の端面に開口部を有する給油穴と、
前記旋回スクロールに設けられ前記クランク軸の偏心部と係合して摺動する旋回滑り軸受と、
前記クランク軸の偏心部の外周に、該偏心部の端面側と基端側を連通するように設けられた給油通路とを備え、
前記給油穴から供給された潤滑油により前記偏心部と前記旋回滑り軸受との間を潤滑するように構成されたスクロール圧縮機において、
前記クランク軸の偏心部の外周に、前記給油通路とは別に設けられた軸方向の損失低減溝と、
この損失低減溝における前記偏心部の端面側と基端側の少なくとも一方に設けられたシール部と
を備えることを特徴とするスクロール圧縮機。 A fixed scroll, a turning scroll meshing with the fixed scroll,
A crankshaft having an eccentric portion at an end portion thereof for turning the orbiting scroll;
An oil supply hole penetrating the crankshaft in the axial direction and having an opening at an end face of the eccentric part;
An orbiting slide bearing that is provided on the orbiting scroll and engages and slides with an eccentric portion of the crankshaft;
An oil supply passage provided on the outer periphery of the eccentric portion of the crankshaft so as to communicate the end face side and the base end side of the eccentric portion;
In the scroll compressor configured to lubricate between the eccentric portion and the orbiting and sliding bearing with the lubricating oil supplied from the oil supply hole,
An axial loss reduction groove provided separately from the oil supply passage on the outer periphery of the eccentric portion of the crankshaft;
A scroll compressor comprising: a seal portion provided on at least one of an end face side and a base end side of the eccentric portion in the loss reducing groove. - 請求項1に記載のスクロール圧縮機において、前記損失低減溝の開始位置は、前記偏心部の中心周りに、前記偏心部の反偏心方向から前記クランク軸の反回転方向に、140°~210°の位置に設けられていることを特徴とするスクロール圧縮機。 The scroll compressor according to claim 1, wherein the start position of the loss reducing groove is around 140 ° to 210 ° around the center of the eccentric portion from the anti-eccentric direction of the eccentric portion to the anti-rotating direction of the crankshaft. A scroll compressor characterized by being provided at the position of.
- 請求項2に記載のスクロール圧縮機において、前記損失低減溝の開始位置は、前記偏心部の中心周りに、前記偏心部の反偏心方向から前記クランク軸の反回転方向に、145°~180°の位置に設けられていることを特徴とするスクロール圧縮機。 The scroll compressor according to claim 2, wherein the starting position of the loss reducing groove is 145 ° to 180 ° around the center of the eccentric portion from the anti-eccentric direction of the eccentric portion to the counter-rotating direction of the crankshaft. A scroll compressor characterized by being provided at the position of.
- 請求項2に記載のスクロール圧縮機において、前記給油通路及び前記損失低減溝は、それぞれ前記偏心部の外周に、掘り込み溝或いは切欠きにより形成されており、且つ、前記損失低減溝はその加工前の前記偏心部外周円から0.002mm以上の径方向深さとなる部分が存在するよう形成されていることを特徴とするスクロール圧縮機。 3. The scroll compressor according to claim 2, wherein the oil supply passage and the loss reduction groove are each formed by an excavation groove or a notch on an outer periphery of the eccentric portion, and the loss reduction groove is processed. A scroll compressor characterized in that a portion having a radial depth of 0.002 mm or more from the previous outer peripheral circle of the eccentric portion exists.
- 請求項4に記載のスクロール圧縮機において、前記損失低減溝の深さを0.01mm以上とし、且つ前記偏心部の軸径の20%以下としたことを特徴とするスクロール圧縮機。 5. The scroll compressor according to claim 4, wherein a depth of the loss reducing groove is 0.01 mm or more and 20% or less of a shaft diameter of the eccentric portion.
- 請求項5に記載のスクロール圧縮機において、前記損失低減溝の深さを0.05~0.5mmとしたことを特徴とするスクロール圧縮機。 6. The scroll compressor according to claim 5, wherein the loss reducing groove has a depth of 0.05 to 0.5 mm.
- 請求項1に記載のスクロール圧縮機において、前記損失低減溝は、前記偏心部の周方向に複数個形成されていることを特徴とするスクロール圧縮機。 2. The scroll compressor according to claim 1, wherein a plurality of the loss reducing grooves are formed in a circumferential direction of the eccentric portion.
- 請求項7に記載のスクロール圧縮機において、複数個形成されている前記損失低減溝のうちの少なくとも1つは、前記偏心部の中心周りに、前記偏心部の反偏心方向から前記クランク軸の反回転方向に、140°~210°の位置に設けられていることを特徴とするスクロール圧縮機。 8. The scroll compressor according to claim 7, wherein at least one of the plurality of loss reduction grooves formed around the center of the eccentric portion is opposite to the crankshaft from the eccentric direction of the eccentric portion. A scroll compressor provided at a position of 140 ° to 210 ° in the rotational direction.
- 請求項1に記載のスクロール圧縮機において、前記シール部は、前記損失低減溝における前記偏心部の基端側には少なくとも設けられていることを特徴とするスクロール圧縮機。 2. The scroll compressor according to claim 1, wherein the seal portion is provided at least on a proximal end side of the eccentric portion in the loss reduction groove.
Priority Applications (6)
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EP11863892.3A EP2700818B1 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
CN201180070247.5A CN103502645B (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
JP2013510807A JP5581440B2 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
TR2018/16164T TR201816164T4 (en) | 2011-04-22 | 2011-04-22 | Snail compressor. |
KR20137023891A KR101484728B1 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
PCT/JP2011/059938 WO2012144067A1 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
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PCT/JP2011/059938 WO2012144067A1 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
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JP (1) | JP5581440B2 (en) |
KR (1) | KR101484728B1 (en) |
CN (1) | CN103502645B (en) |
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JP2014228003A (en) * | 2013-05-22 | 2014-12-08 | オプリスト エンジニアリング ゲーエムベーハーOBRIST ENGINEERING GmbH | Scroll compressor and co2 vehicle air conditioning system including scroll compressor |
JP2014228002A (en) * | 2013-05-22 | 2014-12-08 | オプリスト エンジニアリング ゲーエムベーハーOBRIST ENGINEERING GmbH | Scroll compressor and co2 vehicle air conditioning system including scroll compressor |
CN113954577A (en) * | 2021-11-17 | 2022-01-21 | 浙江四和机械有限公司 | Light-weight energy-saving hub unit with ABS sensor |
CN114922817A (en) * | 2022-06-24 | 2022-08-19 | 广东美的环境科技有限公司 | Eccentric sliding block for crankshaft, scroll compressor and temperature control equipment |
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CN108266374A (en) * | 2017-12-26 | 2018-07-10 | 广州万宝集团压缩机有限公司 | A kind of horizontal type scroll compressor |
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TR201816164T4 (en) | 2018-11-21 |
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KR101484728B1 (en) | 2015-01-20 |
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