WO2020157902A1 - すべり軸受構造及びスクロール圧縮機 - Google Patents

すべり軸受構造及びスクロール圧縮機 Download PDF

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Publication number
WO2020157902A1
WO2020157902A1 PCT/JP2019/003345 JP2019003345W WO2020157902A1 WO 2020157902 A1 WO2020157902 A1 WO 2020157902A1 JP 2019003345 W JP2019003345 W JP 2019003345W WO 2020157902 A1 WO2020157902 A1 WO 2020157902A1
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WO
WIPO (PCT)
Prior art keywords
groove
bearing structure
sliding bearing
region
outer peripheral
Prior art date
Application number
PCT/JP2019/003345
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English (en)
French (fr)
Japanese (ja)
Inventor
慎一郎 井戸
辰也 佐々木
朋子 平山
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2019/003345 priority Critical patent/WO2020157902A1/ja
Priority to CN201980089590.0A priority patent/CN113330215B/zh
Priority to JP2019537847A priority patent/JP6618663B1/ja
Publication of WO2020157902A1 publication Critical patent/WO2020157902A1/ja

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only

Definitions

  • the present invention relates to a sliding bearing structure that supports a rotating shaft that drives a scroll portion of a scroll compressor, and a scroll compressor including the sliding bearing structure.
  • a scroll compressor has a rotary shaft for driving an orbiting scroll, and a slide bearing for supporting a radial variable load acting on the rotary shaft.
  • the sliding bearing of the scroll compressor is lubricated by a fluid such as refrigerating machine oil, and a fluid film called an oil film is formed in the gap between the sliding bearing and the rotating shaft.
  • a fluid film called an oil film is formed in the gap between the sliding bearing and the rotating shaft.
  • the refrigerating machine oil is drawn into the narrow space as the rotary shaft rotates, so that the pressure due to the oil film (oil film pressure) is generated to support the radial load applied to the rotary shaft. This is called a wedge effect.
  • scroll compressors used for air conditioning equipment are often required to operate in a low load and low rotation speed range due to high heat insulation of buildings.
  • the cooling operation with a low load is required even when the outside temperature is low. Therefore, it is necessary for the sliding bearing of the scroll compressor to secure a sufficient oil film pressure even at a low rotation speed and suppress the occurrence of seizure.
  • the conventional sliding bearing structure of a scroll compressor avoids the oil film running out and suppresses seizure due to contact with the rotating shaft.
  • the grooves extending in the axial direction are uniformly distributed.
  • the sliding bearing structure is provided with a structure for generating pressure (dynamic pressure) by a pumping action of drawing refrigerating machine oil along the groove (for example, Patent Document 1).
  • the present invention is intended to solve the above problems, effectively increases the oil film pressure in the gap between the rotary shaft of the scroll compressor and the slide bearing, and suppresses seizure of the rotary shaft and the slide bearing.
  • the object is to obtain a sliding bearing structure and a scroll compressor.
  • a sliding bearing structure includes a rotating shaft that drives an oscillating scroll of a scroll compressor, and a sliding bearing that supports a radial load of the rotating shaft, and the rotating shaft is relative to the sliding bearing.
  • a groove extending in the axial direction is provided on the outer peripheral surface of the rotary shaft, the groove is formed so as to generate a pumping action, and the outer peripheral surface of the rotating shaft is an area set in a predetermined angular range in the peripheral direction on the outer peripheral surface. P and a region Q of the outer peripheral surface other than the region P, and a ratio of the groove to the area of the outer peripheral surface in the region P is occupied by the groove to the area of the outer peripheral surface in the region Q. Greater than proportion.
  • the scroll compressor according to the present invention has the above sliding bearing structure.
  • the dynamic pressure is generated by the pumping action by the groove provided in the region where the oil film pressure is generated by the wedge effect, and it becomes an additional resistance force against the radial fluctuation load of the rotary shaft, and the rotary shaft and the slide bearing are
  • the oil film thickness between the two increases.
  • the number of axial grooves per unit area can be made smaller or distributed so that the number of axial grooves becomes zero, so that the dynamic pressure generation effect by the pumping action is The problem of canceling each other out can be solved.
  • the sliding bearing structure and the scroll compressor have the effect of increasing the oil film pressure and suppressing seizure more effectively than in the past.
  • FIG. 3 is a cross-sectional view around the sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment.
  • FIG. 3 is an explanatory view of a cross section of a sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment.
  • 1 is a schematic diagram illustrating a sliding bearing structure 50 of a scroll compressor 100 according to a first embodiment. It is explanatory drawing of the cross-section structure perpendicular
  • FIG. 5 is a diagram showing a modified example of the groove 20 formed on the outer peripheral surface of the rotary shaft 6 of the sliding bearing structure 50 according to the first embodiment.
  • FIG. 5 is a diagram showing a modified example of the groove 20 formed on the outer peripheral surface of the rotary shaft 6 of the sliding bearing structure 50 according to the first embodiment.
  • FIG. 5 is a diagram showing a modified example of the groove 20 formed on the outer peripheral surface of the rotary shaft 6 of the sliding bearing structure 50 according to the first embodiment.
  • FIG. 3 is a cross-sectional view of a state in which the outer circumference of rotary shaft 6 according to the first embodiment is expanded.
  • FIG. 3 is a cross-sectional view of a state in which the outer circumference of rotary shaft 6 according to the first embodiment is expanded.
  • 5 is a schematic diagram illustrating a sliding bearing structure 250 of a scroll compressor 100 according to Embodiment 2.
  • FIG. 5 is a schematic diagram illustrating a sliding bearing structure 350 of a scroll compressor 100 according to a third embodiment.
  • FIG. 1 is an explanatory diagram of a cross-sectional structure of the scroll compressor 100 according to the first embodiment.
  • a scroll compressor 100 includes a fixed scroll 1 in which a lower surface of a base plate 1a is provided with spiral protrusions, and an orbiting scroll 2 in which a upper surface of a base plate 2a is provided with spiral protrusions.
  • a scroll compression mechanism 60 formed by combining and is provided. The spiral projection of the fixed scroll 1 and the spiral projection of the orbiting scroll 2 are combined with each other to form a compression chamber 5.
  • the fixed scroll 1 and the orbiting scroll 2 are arranged in the upper part of the pressure vessel 11.
  • the pressure container 11 has an oil reservoir 12 at the bottom, and a refrigerant suction pipe 13 and a refrigerant discharge pipe 14 are connected to the side walls.
  • One end of the refrigerant suction pipe 13 communicates with the suction port 3 in the pressure container 11, and one end of the refrigerant discharge pipe 14 communicates with the discharge port 4 in the pressure container 11.
  • the refrigerant from the refrigerant circuit flows from the refrigerant suction pipe 13 through the suction port 3 into the compression chamber 5 in the scroll compression mechanism 60, is compressed, and is discharged from the discharge port 4 to the refrigerant circuit from the refrigerant discharge pipe 14.
  • An eccentric hole 2b is provided on the lower surface of the base plate 2a of the orbiting scroll 2, and the rotary shaft 6 is fitted therein.
  • the rotating shaft 6 is connected to an electric motor 9 installed at the center of the pressure vessel 11 in the height direction, and transmits the driving force of the electric motor 9 to the orbiting scroll 2.
  • the electric motor 9 is arranged between the upper housing 8a and the lower housing 8b that form the housing 8.
  • the electric motor 9 includes a rotor 9a and a stator 9b.
  • the rotor 9a is fixed to the outer peripheral surface of the main shaft 6a.
  • the stator 9b is fixed to the inner peripheral surface of the pressure vessel 12, and surrounds the rotor 9a with a predetermined gap.
  • the rotary shaft 6 has an eccentric shaft 6b at the upper end of the main shaft 6a.
  • the eccentric shaft 6b is provided eccentrically with respect to the center of the main shaft 6a.
  • the main bearing 15a that supports the main shaft 6a is provided in the upper housing 8a fixed in the side wall surface of the pressure vessel 11.
  • the main bearing 15a rotatably supports the main shaft 6a.
  • the fixed scroll 1 is fixed to the upper end of the upper housing 8a.
  • the orbiting scroll 2 is located between the fixed scroll 1 and the upper housing 8a.
  • An Oldham ring 10 is provided between the orbiting scroll 2 and the upper housing 8a. The Oldham ring 10 rotates the orbiting scroll 2 while preventing the orbiting scroll 2 from rotating.
  • a sub-bearing 16 is provided in the lower housing 8b fixed in the side wall surface of the pressure vessel 11.
  • the sub bearing 16 rotatably supports the main shaft 6 a below the electric motor 9. That is, the main shaft 6a of the rotary shaft 6 is rotatably supported above the electric motor 9 by the upper housing 8a, and is supported below the electric motor 9 by the lower housing 8b.
  • FIG. 2 is a cross-sectional view around the sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment.
  • the scroll compressor 100 is formed in the slide bearing structure 50a formed in the portion where the upper housing 8a supports the rotating shaft 6 and in the portion where the orbiting scroll 2 and the rotating shaft 6 are connected.
  • a plain bearing structure 50b In the sliding bearing structure 50a, the main bearing 15a fixed to the central hole of the upper housing 8a and the main shaft 6a of the rotary shaft 6 are fitted together.
  • the oscillating bearing 15b fixed in the eccentric hole 2b of the oscillating scroll 2 and the eccentric shaft 6b of the rotary shaft 6 are fitted together.
  • the main bearing 15a and the rocking bearing 15b may be collectively referred to as the slide bearing 15.
  • the main bearing 15a is press-fitted and fixed in a hole formed in the center of the upper housing 8a and slidably supported on the main shaft 6a.
  • the structure of the main bearing 15a is not limited to the form shown in FIG. 1, and for example, the hole itself of the upper housing 8a may be the main bearing 15a, or the main bearing 15a may be a separate body from the upper housing 8a. However, it may be fixed by a method other than press fitting.
  • the rocking bearing 15b is press-fitted and fixed in the eccentric hole 2b provided in the rocking scroll 2 and slidably connected to the eccentric shaft 6b.
  • the structure of the rocking bearing 15b is not limited to the configuration shown in FIG. 1, and the eccentric hole 2b itself may be the rocking bearing 15b, or the rocking bearing 15b may be different from the eccentric hole 2b. Even the body may be fixed by a method other than press-fitting.
  • the rotary shaft 6 is formed with an axial oil supply hole 7a penetrating in the axial direction.
  • the lower end of the rotary shaft 6 is fitted to the pump 7b below the electric motor 9.
  • the lower end opening 7e of the pump 7b is immersed in the refrigerating machine oil in the oil sump 12 below the pressure vessel 11.
  • the axial oil supply hole 7a penetrating in the axial direction of the rotary shaft 6 is connected to a radial oil supply outlet 7c opened on the surface of the main shaft 6a facing the main bearing 15a. Further, the axial oil supply hole 7 a is connected to an oil supply outlet 7 d opened on the upper end surface of the rotary shaft 6.
  • the refrigerating machine oil pumped up from the oil sump 12 by the pump 7b passes through the axial oil supply hole 7a, is split into the radial oil supply outlet 7c and the oil supply outlet 7d, and is supplied to the slide bearing structures 50a and 50b. That is, the axial oil supply hole 7a, the pump 7b, the radial oil supply outlet 7c, and the oil supply outlet 7d constitute an oil supply mechanism for the slide bearing 15 of the scroll compressor 100.
  • the refrigerant sucked into the compression chamber 5 from the suction port 3 via the refrigerant suction pipe 13 gradually increases its pressure, and is pressure-fed from the refrigerant discharge pipe 14 to the refrigerant pipe outside the scroll compressor 100 via the discharge port 4.
  • the gas load due to the compression action of the refrigerant gas and the centrifugal force due to the orbiting motion of the orbiting scroll 2 mainly act on the rotating shaft 6.
  • the resultant force of the gas load and the centrifugal force becomes a radial variable load W that rotates in synchronization with the rotation of the rotary shaft 6.
  • FIG. 3 is an explanatory diagram of a cross section of the sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment.
  • the groove 20 formed in the plain bearing structure 50 is omitted. That is, FIG. 3 shows a slide bearing structure 50 in which the groove 20 is not formed on the outer peripheral surface of the rotary shaft 6 facing the slide bearing 15.
  • the radial fluctuating load W acts on the rotary shaft 6, the radial fluctuating load W causes the rotary shaft 6 to rotate with its axis eccentric from the axis of the slide bearing 15.
  • the region sandwiched between the rotary shaft 6 and the slide bearing 15 is filled with the refrigerating machine oil supplied to the slide bearing 15 through the radial oil supply outlet 7c or the oil supply outlet 7d to form an oil film 18.
  • a region in which the flow path in the circumferential direction gradually narrows in a wedge shape toward the rotation direction due to the eccentricity of the rotating shaft 6 is referred to as a wedge region 18a.
  • a region in which the flow path in the circumferential direction gradually expands in a reverse wedge shape in the direction of rotation opposite to the wedge region 18a is referred to as a reverse wedge region 18b.
  • the refrigerating machine oil is drawn into a narrow region by the rotation of the rotary shaft 6, so that the oil film pressure 19 is generated.
  • the oil film pressure 19 that is sufficient to balance the radial fluctuation load W is generated, the rotating shaft 6 and the slide bearing 15 are separated by the oil film 18, and rotate without direct contact.
  • the direction of the radial variable load W acting on the rotary shaft 6 of the scroll compressor 100 maintains a predetermined phase difference from the circumferential position on the surface of the rotary shaft 6.
  • the circumferential position at which the action line L0 of the radial direction fluctuating load starting from the axial center of the rotary shaft 6 intersects the outer peripheral surface of the rotary shaft 6 is defined as the origin of the circumferential angular position of the outer peripheral surface of the rotary shaft 6.
  • the direction of the angle ⁇ is defined as 0° at the origin, with the direction opposite to the rotation direction of the rotation axis being positive. Therefore, ⁇ takes a value in the range of 0° to 360°.
  • FIG. 4 is a schematic diagram illustrating the sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment.
  • FIG. 5 is an explanatory diagram of a cross-sectional structure perpendicular to the axial direction of the sliding bearing structure 50 of FIG.
  • the sliding bearing structure 50 of the scroll compressor 100 according to the first embodiment has a plurality of grooves 20 extending in the axial direction on the surface of the rotating shaft 6 facing the sliding bearing 15.
  • the ratio of the axially extending groove 20 to the surface area is in the other portion of the outer peripheral surface of the rotating shaft 6. It is larger than the ratio of the groove 20 to the surface area.
  • a region of the outer peripheral surface of the rotation shaft 6 in the circumferential angle range from 0° to ⁇ is referred to as a region P.
  • a region other than the region P on the outer peripheral surface of the rotary shaft 6 is referred to as a region Q.
  • FIG. 4 shows, as an example, a case where the ratio of the groove 20 to the surface area is 0 in the region Q on the outer peripheral surface of the rotary shaft 6. That is, in FIG.
  • the groove 20 extending in the axial direction has a bent shape on the outer peripheral surface of the rotary shaft 6. That is, the groove 20 is composed of two passages whose circumferential position recedes in the opposite direction to the rotational direction from both axial end portions of the outer peripheral surface of the rotary shaft 6 facing the plain bearing 15 toward the central portion, The bent portion 21 is configured so that the two flow paths merge. In other words, the groove 20 is formed in a V shape in which the rotation direction side of the rotation shaft 6 is open.
  • the flow of the refrigerating machine oil from both axial end portions of the groove 20 toward the bent portion 21 along the inner wall surface of the groove 20 is accompanied by the rotation of the rotary shaft 6. Occurs. Furthermore, in the plain bearing structure 50, the flow of the refrigerating machine oil from the axial opposite ends to the central part occurs on the surface of the rotary shaft 6 facing the plain bearing 15. The flow of the refrigerating machine oil joins at the bent portion 21 of the groove 20, and a pressure (dynamic pressure) is generated at the bent portion 21 due to the compression of the refrigerating machine oil. The phenomenon in which the dynamic pressure is generated is called a pumping effect by the dynamic pressure groove.
  • the rotary shaft 6 is provided with an axial oil supply hole 7a that penetrates in the axial direction at the center thereof.
  • the axial oil supply hole 7a and the outer peripheral surface of the rotary shaft 6 are configured to have a radial oil supply outlet 7c that radially penetrates from the shaft center.
  • the opening position of the radial direction oil supply outlet 7c on the outer peripheral surface of the rotary shaft 6 is preferably provided outside the circumferential angle range of 0° to ⁇ on the outer peripheral surface of the rotary shaft 6, that is, in the region Q.
  • the oil supply outlet 7d is provided at the axial end of the eccentric shaft 6b and the refrigerating machine oil is supplied to the gap between the rocking bearing 15b and the eccentric shaft 6b.
  • the groove 20 occupies a large proportion of the outer peripheral surface of the rotary shaft 6 in the wedge region 18a of the oil film 18, and the groove 20 is larger than the rotary shaft 6 in the region other than the wedge region 18a.
  • the groove 20 can be arranged so that the proportion of the peripheral surface is small.
  • the groove 20 is arranged over the entire area of the outer peripheral surface of the rotary shaft 6, and dynamic pressure is generated by the pumping action of the groove 20 over the entire area of the oil film 18. Therefore, the dynamic pressure generated by the pumping action of the groove 20 in the wedge region 18a of the oil film 18 is canceled by the dynamic pressure generated by the pumping action of the groove 20 in the regions other than the wedge region 18a. Therefore, when the groove 20 is arranged over the entire outer peripheral surface of the rotary shaft 6 as in the conventional technique, only the oil film pressure 19 due to the rotation of the rotary shaft 6 is applied to the radial direction varying load W in the wedge region 18a. It becomes a resistance force, and the effect of increasing the oil film thickness cannot be obtained as compared with the sliding bearing structure 50 according to the first embodiment.
  • the dynamic pressure generated by the pumping action acts in addition to the oil film pressure 19, so that the oil film thickness of the wedge region 18a increases and seizure is suppressed. It can be said that the effect is high. That is, in the slide bearing structure 50 according to the first embodiment, in the oil film 18, the proportion of the groove 20 occupying the outer peripheral surface of the rotary shaft 6 is small in the region where the oil film thickness is relatively large, or the groove 20 is small. The ratio occupying the outer peripheral surface can be zero.
  • the sliding bearing structure 50 suppresses the dynamic pressure generated by the pumping action in the region of the oil film 18 other than the wedge region 18a, and generates the dynamic pressure by the pumping action in the wedge region 18a. Therefore, the sliding bearing structure 50 can have resistance to the radial direction varying load W without canceling the dynamic pressure generated by the pumping action generated in the wedge region 18a, and further effectively increases the oil film thickness and burns. It is possible to suppress sticking.
  • FIG. 6 shows the results of fluid lubrication analysis when the region P in which the groove 20 is arranged and the shape of the groove 20 are changed in the sliding bearing structure 50 according to the first embodiment.
  • an angle ⁇ that is the upper limit of the circumferential angle range of the region P in which the groove 20 is provided and an angle ⁇ that is an acute angle component of the angle formed by the flow path of the groove 20 with respect to the circumferential direction are used as parameters.
  • FIG. 6 shows the minimum oil film thickness in each combination of ⁇ and angle ⁇ when the angle ⁇ changes from 0 to 360° and when ⁇ changes from 0° to 90°.
  • the minimum clearance between the slide bearing 15 and the rotary shaft 6 is defined as the minimum oil film thickness.
  • the numerical value of the minimum oil film thickness shown in FIG. 6 is expressed as a ratio (minimum oil film thickness ratio) to the minimum oil film thickness in the sliding bearing when the groove 20 is not provided on the rotary shaft 6.
  • the angle ⁇ which is an acute angle component of the angle formed by the groove 20 with respect to the circumferential direction, is ⁇ shown in FIG. 4, and is an imaginary line parallel to the central axis of the rotary shaft 6 of the flow path forming the groove 20.
  • the inclination angle with respect to the line L1 is shown.
  • FIG. 7 shows the analysis conditions used for the analysis result of FIG.
  • the analysis result of FIG. 6 shows that the dimensions of each part of the slide bearing structure 50 are 30 mm for the inside diameter of the slide bearing 15, 30 mm for the axial length of the slide bearing 15, and 30 ⁇ m for the radial gap between the slide bearing 15 and the rotary shaft 6. It is analyzed by setting the depth of the groove 20 from the outer peripheral surface of the rotary shaft 6 to 30 ⁇ m. Further, the radial variable load W applied from the rotary shaft 6 is 5000 N, and the rotation speed of the rotary shaft 6 is 3000 rpm. The analysis result of FIG. 6 indicates that the minimum oil film thickness ratio exceeds 1 in the combination of the angle ⁇ and the angle ⁇ in the hatched region.
  • the hatched region in FIG. 6 indicates a combination of ⁇ and ⁇ that exceeds the minimum oil film thickness of the conventional slide bearing in the configuration of the slide bearing structure 50 according to the first embodiment.
  • the sliding bearing structure 50 shows a combination of ⁇ and ⁇ that can obtain an oil film pressure higher than that of the conventional sliding bearing.
  • the region in which the combination of ⁇ and ⁇ that exceeds the minimum oil film thickness of the conventional slide bearing exists is a combination of angular ranges.
  • ⁇ and ⁇ can be arbitrarily selected from the above-described angle range.
  • the groove 20 is provided in the region P, and the circumferential angle range of the region P is changed, so that the oil film thickness is smaller than that in the case where the groove 20 is provided all around. Can be increased and seizure can be suppressed.
  • the groove 20 is provided only in the region P on the outer peripheral surface of the rotating shaft 6, and the groove 20 is not provided in the other region Q.
  • the groove 20 may be provided in the region Q. it can.
  • the configuration becomes similar to that described in the prior art document, and the oil film pressure due to the pumping action by the grooves 20 in the wedge region 18a is reduced. The effect of increasing is offset. Therefore, when the groove 20 is provided in the region Q, it is preferable that the ratio of the groove 20 to the area of the outer peripheral surface be smaller than that in the region P.
  • the oil film pressure in the wedge region 18a is increased by the pumping action of the groove 20, and the oil film thickness can be increased as compared with the case where the groove 20 is provided at a uniform ratio over the entire circumference.
  • the seizure can be suppressed.
  • FIG. 8 to 10 are diagrams showing modified examples of the groove 20 formed on the outer peripheral surface of the rotary shaft 6 of the sliding bearing structure 50 according to the first embodiment.
  • the groove 20a As a modified example of the groove 20, there is a groove 20a shown in FIG. 8 in which the position of the bent portion 21a is shifted in the axial direction of the rotary shaft 6. That is, the groove 20 a has a V-shape that is asymmetric in the axial direction of the rotary shaft 6.
  • the groove 20b shown in FIG. 9 has a V-shape in which the widths of the flow paths extending from both ends in the axial direction are unequal widths that become narrower toward the bent portion 21c.
  • the groove 20c shown in FIG. 10 has a U-shaped configuration in which the flow paths extending from both axial ends of the rotary shaft 6 are curved. Since any of the grooves 20a to 20c shown above can generate a dynamic pressure by a pumping action, by providing any of the grooves 20a to 20c like the slide bearing structure 50 to which the groove 20 is applied, The oil film pressure can be increased and seizure can be suppressed.
  • FIG. 11 and 12 are cross-sectional views showing a state where the outer circumference of the rotary shaft 6 according to the first embodiment is expanded.
  • the cross-sectional shape of the groove 20 of the sliding bearing structure 50 according to the first embodiment is, for example, rectangular.
  • the cross-sectional shape of the groove 20 is such that the oil film pressure at the rear end 25, which is the end of the groove 20 located on the rear side in the rotation direction of the rotary shaft 6, decreases due to the reduction of the gap between the rotary shaft 6 and the slide bearing 15.
  • the shape is not limited to a rectangle as long as the shape can occur.
  • the groove 20d shown in FIG. 12 is a modification of the groove 20 shown in FIG. 11 having a rectangular cross section in the circumferential direction.
  • the groove 20d may have a V-shaped cross section.
  • the groove 20d is not limited to a symmetrical shape with respect to an imaginary line passing through the center of the rotating shaft 6 in the cross section of FIG. 12, and may have an asymmetric V shape as shown in FIG. 12, for example.
  • the groove 20d in the slope 23 having a small slope starting from the front end 22 which is the end of the groove 20d located on the front side in the rotation direction of the rotary shaft 6, the rotation of the rotary shaft 6 causes the refrigerating machine oil to move along the slope 23. Is likely to occur.
  • the groove 20d is likely to have the effect of drawing the refrigerating machine oil into the groove 20d.
  • the groove 20d has the slope 24 having a large slope, so that the rotating shaft 6 and the slide bearing 15 are The gap between the two decreases sharply. Therefore, it is easy to obtain the effect of generating a large oil film pressure.
  • the angle of the inclined surface 24 may be right angle to the tangent line of the outer peripheral surface. Further, since the flow of the refrigerating machine oil along the slope 23 is likely to occur in the groove 20d, the flow of the refrigerating machine oil is sharply reduced on the slope 24, so that the oil film pressure can be more easily increased.
  • the angles of the slope 23 and the slope 24 can be changed as appropriate.
  • the groove 20 may be configured such that the angle of the bottom surface 26 of the groove 20 shown in FIG.
  • the slope 23, the slope 24, and the bottom surface 26 may be flat or curved.
  • the slope 23 is referred to as a first slope and the slope 24 is referred to as a second slope.
  • Embodiment 2 The sliding bearing structure 250 of the scroll compressor 100 according to the second embodiment is different from the sliding bearing structure 50 according to the first embodiment in that circumferential oil supply grooves 30 are added to both ends of the rotating shaft 6 in the axial direction. is there.
  • the second embodiment will be described focusing on the changes from the first embodiment.
  • FIG. 13 is a schematic diagram illustrating the sliding bearing structure 250 of the scroll compressor 100 according to the second embodiment.
  • the rotary shaft 6 is provided with the groove 20 in the region P, but the circumferential direction oil supply groove 30 extending in the circumferential direction of the rotary shaft 6 is provided at both axial ends of the groove 20.
  • the circumferential oil supply groove 30 does not face the slide bearing 15 of the rotary shaft 6, and is in a state of protruding from the slide bearing 15.
  • the circumferential oil supply groove 30 is connected to the axial end of the groove 20 extending in the axial direction of the rotary shaft 6.
  • the circumferential oil supply groove 30 can allow refrigerating machine oil to flow from the circumferential oil supply groove 30 into the groove 20.
  • the refrigerating machine oil held in the circumferential oil supply groove 30 is supplied to the gap between the slide bearing 15 and the rotary shaft 6, so that depletion of the refrigerating machine oil in the slide bearing structure 250 can be suppressed. it can.
  • the circumferential oil supply groove 30 is connected to the groove 20 extending in the axial direction of the rotary shaft 6. Therefore, the refrigerating machine oil held by the circumferential oil supply groove 30 flows into the groove 20, and the refrigerating machine oil is drawn into the groove 20 more than in the first embodiment. Therefore, the oil film 18 in the region where the groove 20 is provided can obtain a high oil film pressure.
  • the circumferential oil supply groove 30 Since the circumferential oil supply groove 30 is provided so that its bottom surface does not face the slide bearing 15, the area of the outer peripheral surface of the rotary shaft 6 that can be supported by the slide bearing 15 is not reduced. Therefore, even when the circumferential oil supply groove 30 communicating with the groove 20 is provided, the load that the slide bearing 15 can receive does not decrease.
  • the bottom surface of the circumferential oil supply groove 30 may be connected to the axial oil supply hole 7a and the radial oil supply outlet 7c. Since the circumferential oil supply groove 30 communicates with the radial oil supply outlet 7c, the refrigerating machine oil supplied from the radial oil supply outlet 7c is supplied to the groove 20 extending in the axial direction. Depletion can be suppressed.
  • the refrigerating machine oil supplied from the pump 7b through the axial oil supply hole 7a can directly flow into the circumferential oil supply groove 30. Therefore, the amount of refrigerating machine oil held by the circumferential oil supply groove 30 can be increased more effectively.
  • the opening position of the radial oil supply outlet 7c on the bottom surface of the circumferential oil supply groove 30 is preferably provided at a circumferential position where the amount of refrigerating machine oil flowing into the gap between the rotary shaft 6 and the slide bearing 15 increases. ..
  • the opening of the radial oil supply outlet 7c is provided at a position where ⁇ is 0°, the groove 20 and the radial oil supply outlet 7c are close to each other, and therefore the axial direction oil supply hole 7a passes through the radial oil supply outlet 7c in the circumferential direction.
  • the refrigerating machine oil supplied to the oil supply groove 30 can be supplied to the groove 20 in the shortest path. Therefore, the refrigerating machine oil can be most effectively supplied to the sliding bearing structure 250.
  • Embodiment 3 The sliding bearing structure 350 of the scroll compressor 100 according to the third embodiment is different from the sliding bearing structure 250 according to the second embodiment in that an axial oil supply groove 40 is added to a region Q on the outer peripheral surface of the rotating shaft 6. is there.
  • the third embodiment will be described with a focus on the changes from the first and second embodiments.
  • FIG. 14 is a schematic diagram illustrating a sliding bearing structure 350 of the scroll compressor 100 according to the third embodiment.
  • the groove 20 is provided in the rotating shaft 6 in the axial direction, and the groove 20 is provided in the range of the outer peripheral surface of the rotating shaft 6 in the circumferential angle range of 0° to ⁇ . Further, in the other angle ranges, the point that the groove 20 occupies the surface area is 0, and the point that the groove 20 is configured as a dynamic pressure groove having a bent portion is similar to the first and second embodiments.
  • the sliding bearing structure 350 is the same as that of the second embodiment in that the circumferential oil supply groove 30 connected to the groove 20 is provided.
  • the rotary shaft 6 according to the third embodiment is provided with a radial oil supply outlet 7c provided on the surface facing the slide bearing 15. Further, an axial oil supply groove 40 is provided in a region Q of the outer peripheral surface of the rotary shaft 6 where the groove 20 is not provided.
  • the axial direction oil supply groove 40 has a radial direction oil supply outlet 7c opened on the bottom surface and communicates with the axial direction oil supply hole 7a. Further, both axial ends of the axial oil supply groove 40 are connected to the circumferential oil supply groove 30, and the axial oil supply hole 7 a, the radial oil supply outlet 7 c, the axial oil supply groove 40, and the circumferential oil supply groove 40 are connected. It has a configuration capable of producing a flow of refrigerating machine oil up to 30. Then, the refrigerating machine oil flowing into the circumferential oil supply groove 30 flows into the connected groove 20 extending in the axial direction.
  • the radial oil supply outlet 7c is opened in the circumferential oil supply groove 30 which is not opposed to the slide bearing 15, the refrigeration supplied to the outside from the outer peripheral surface of the rotating shaft 6 facing the slide bearing 15. It is inevitable that machine oil will leak out.
  • the radial oil supply outlet 7c is opened at the outer peripheral surface of the rotary shaft 6 facing the slide bearing 15, the axial oil supply hole 7a and the radial oil supply outlet are provided by the pump 7b. The entire amount of refrigerating machine oil supplied through 7c is supplied into the gap between the slide bearing 15 and the rotary shaft 6. Therefore, it becomes possible to increase the supply of the refrigerating machine oil to the gap between the slide bearing 15 and the rotary shaft 6.
  • the radial oil supply outlet 7c is connected to the axial oil supply groove 40, the refrigerating machine oil can be retained in the axial oil supply groove 40. Therefore, the sliding bearing structure can more effectively prevent the depletion of the refrigerating machine oil. Further, since the axial oil supply groove 40 is connected to the circumferential oil supply groove 30, the refrigerator oil can be held in the circumferential oil supply groove 30 as in the second embodiment, and the groove formed by the circumferential oil supply groove 30 can be held. The supply of refrigerating machine oil to 20 can be increased.
  • the axial oil supply groove 40 is composed of two flow passages whose circumferential position advances in the same direction as the rotational direction from both ends in the axial direction toward the central portion, and the two flow passages are bent portions 41. It is configured to intersect at. That is, the axial oil supply groove 40 has a V-shape that opens in the direction opposite to the rotational direction of the rotary shaft 6.
  • the radial oil supply outlet 7c can be provided in the bent portion 41. That is, the flow path that constitutes the axial oil supply groove 40 and extends in the axial direction from the bent portion 41 joins the radial oil supply outlet 7c at the bent portion 41.
  • the groove 20 described in the first embodiment promotes the inflow of refrigerating machine oil into the gap between the rotary shaft 6 and the slide bearing 15, and effectively generates the dynamic pressure in the direction that supports the radial variable load W by the pumping action. It was intended to let you.
  • the axial oil supply groove 40 is supplied to the clearance between the rotary shaft 6 and the sliding bearing 15 from the axial oil supply hole 7a through the radial oil supply outlet 7c. The purpose is to efficiently generate a flow for supplying the oil to the circumferential oil supply groove 30.
  • the axial oil supply groove 40 has a bent portion 41, and has a structure in which two flow paths extending from the bent portion 41 extend so as to incline in a direction opposite to the rotation direction of the rotating shaft 6. From this, the refrigerating machine oil flowing through the axial oil supply groove 40 is dragged by the wall surface of the axial oil supply groove 40 as the rotary shaft 6 rotates, and a flow toward the circumferential oil supply groove 30 occurs. This flow increases the amount of refrigerating machine oil supplied from the axial oil supply groove 40 to the circumferential oil supply groove 30 and increases the amount of refrigerating machine oil supplied from the circumferential oil supply groove 30 to the groove 20. A high oil film pressure can be obtained in the wedge region 18a. Then, the sliding bearing structure 350 can increase the oil film thickness and suppress seizure while suppressing the depletion of the refrigerating machine oil.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
PCT/JP2019/003345 2019-01-31 2019-01-31 すべり軸受構造及びスクロール圧縮機 WO2020157902A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2019/003345 WO2020157902A1 (ja) 2019-01-31 2019-01-31 すべり軸受構造及びスクロール圧縮機
CN201980089590.0A CN113330215B (zh) 2019-01-31 2019-01-31 滑动轴承构造及涡旋压缩机
JP2019537847A JP6618663B1 (ja) 2019-01-31 2019-01-31 すべり軸受構造及びスクロール圧縮機

Applications Claiming Priority (1)

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PCT/JP2019/003345 WO2020157902A1 (ja) 2019-01-31 2019-01-31 すべり軸受構造及びスクロール圧縮機

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JP2023077131A (ja) * 2021-11-24 2023-06-05 愛知製鋼株式会社 回転電機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58217818A (ja) * 1982-06-14 1983-12-17 Toshiba Corp 自動調心軸受
JPS62106122A (ja) * 1985-10-30 1987-05-16 Mitsubishi Heavy Ind Ltd 反転軸受
JPH0712068A (ja) * 1993-06-22 1995-01-17 Hitachi Ltd スクロール流体機械の軸受給油装置
JP2017172484A (ja) * 2016-03-24 2017-09-28 三菱電機株式会社 スクロール圧縮機

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6250787B2 (ja) * 2014-02-27 2017-12-20 三菱重工業株式会社 浮動ブッシュ軸受装置、及び、該軸受装置を備えるターボチャージャ
CN107208633B (zh) * 2015-04-22 2019-07-30 三菱电机株式会社 涡旋压缩机
JP6758867B2 (ja) * 2016-03-04 2020-09-23 三菱重工サーマルシステムズ株式会社 流体機械

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58217818A (ja) * 1982-06-14 1983-12-17 Toshiba Corp 自動調心軸受
JPS62106122A (ja) * 1985-10-30 1987-05-16 Mitsubishi Heavy Ind Ltd 反転軸受
JPH0712068A (ja) * 1993-06-22 1995-01-17 Hitachi Ltd スクロール流体機械の軸受給油装置
JP2017172484A (ja) * 2016-03-24 2017-09-28 三菱電機株式会社 スクロール圧縮機

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CN113330215B (zh) 2023-02-17
JPWO2020157902A1 (ja) 2021-02-18
CN113330215A (zh) 2021-08-31

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