WO2011148932A1 - スクロール型流体機械 - Google Patents
スクロール型流体機械 Download PDFInfo
- Publication number
- WO2011148932A1 WO2011148932A1 PCT/JP2011/061854 JP2011061854W WO2011148932A1 WO 2011148932 A1 WO2011148932 A1 WO 2011148932A1 JP 2011061854 W JP2011061854 W JP 2011061854W WO 2011148932 A1 WO2011148932 A1 WO 2011148932A1
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- WIPO (PCT)
- Prior art keywords
- scroll
- arc surface
- spiral body
- fixed
- curvature
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/08—Axially-movable sealings for working fluids
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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
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0284—Details of the wrap tips
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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
Definitions
- the present invention relates to a scroll type fluid machine suitable for a refrigeration circuit used for air conditioning of a vehicle.
- This type of scroll-type fluid machine includes a fixed scroll and a movable scroll each having an end plate and a spiral body integral with the end plate, and the spiral body and the end plate are in sliding contact with each other between the fixed and movable scrolls.
- a compression chamber or expansion chamber for the working fluid formed between the spiral bodies is defined.
- a root portion of the radius of curvature (r) is provided at a corner on the end plate side of the scroll body of one scroll, and the radius of curvature (R) is provided at a corner of the tip end portion of the spiral body of the other scroll.
- a scroll compressor is disclosed in which a rounded portion is provided and the radius of curvature (R) is larger than the radius of curvature (r).
- Patent Document 2 an arc-shaped first chamfered portion is provided at the base of the spiral body, and an arc-shaped second chamfered portion slightly smaller than the first chamfered portion is provided at the corner of the tip of the spiral body.
- a scroll compressor is disclosed in which the radius of the first and second chamfered portions is 5% or less of the thickness of the spiral body.
- Patent Document 3 discloses a scroll compressor in which a gap portion of a compression chamber is formed on at least one surface of both scrolls and is filled with a surface treatment material having a lower hardness than the other scroll. Yes.
- Patent Document 4 discloses a scroll type fluid machine in which an interference escape portion with a base portion of a spiral body is formed on a second end plate (bottom plate). Further, in Patent Document 5, the spiral body and the end plate are in sliding contact with each other through a chip seal provided on the spiral body between the fixed and movable scrolls, and the cross-sectional shape is made concave or convex at the tip of the spiral body.
- a scroll type fluid machine equipped with a tip seal is disclosed.
- Japanese Patent No. 4126815 Japanese Patent Laid-Open No. 5-187371 JP 2001-342979 A Japanese Unexamined Patent Publication No. 57-148085 JP 2000-352388 A
- the scroll unit of the scroll type fluid machine generally has a cantilever structure in which the movable scroll revolves with respect to the fixed scroll. Therefore, in order to secure the discharge capacity while reducing the size of the scroll unit, the spiral body must be formed high, and the spiral body is easily damaged. Therefore, the spiral body is expensive in order to prevent the spiral body from being damaged. It must be molded with a high strength material. When a high-strength material cannot be used, the height of the spiral body has to be lowered, and there has been a restriction on promoting miniaturization of the fluid machine.
- the curvature radius of the fillet portion is set to 5% or less of the wall thickness of the spiral body as described in Patent Document 2, the fillet portion is too small particularly in the case of a small fluid machine, and the above three-month gap is formed. Filling with certainty is difficult, and stress concentration generated in the spiral body may not be sufficiently suppressed.
- Patent Document 3 it is considered that the surface treatment material is worn on the fillet portion with a surface treatment material, for example, soft metal plating, so that the surface treatment material is worn to an appropriate film thickness and the three-month gap can be filled. It is.
- the surface treatment material is generally formed with a thin thickness of the order of microns, it does not have a thickness that assumes wear.
- the surface treatment material that is too thick may be peeled off along with the orbiting movement of the movable scroll. Therefore, even if the fillet portion is treated with the surface treatment material, it is difficult to fill the three-month gap, and stress concentration generated in the spiral body may not be sufficiently suppressed.
- Patent Document 4 it is clear that not only the above three-month gap but also a gap may be formed between the root of the spiral body and the bottom plate, and the airtightness of the compression chamber or the expansion chamber cannot be ensured. It is.
- Patent Document 5 it is considered that the three-month gap can be filled with the tip seal by attaching a concave or convex tip seal to the tip of the spiral body.
- the above three-month gap is surely filled and the spiral is generated. There remains a problem to sufficiently suppress the stress concentration.
- the present invention suppresses the stress concentration generated in the fixed and movable spiral bodies, improves the airtightness of the compression chamber or expansion chamber of the working fluid formed between the spiral bodies, and improves the operation efficiency.
- a scroll type fluid machine which can be miniaturized.
- the scroll type fluid machine of the present invention includes a fixed scroll and a movable scroll each having an end plate and a spiral body integral with the end plate, and the spiral body and the end plate are provided between the fixed and movable scrolls on the spiral body.
- a scroll type fluid machine that partitions a pressure chamber of a working fluid formed between the spiral bodies by sliding contact with each other via a tip seal, and the spiral body of at least one scroll is located at a corner on the end plate side.
- a tip seal of the other scroll has a root portion formed by a concave arc surface, and has a fillet portion formed of a first convex arc surface that is in sliding contact with the concave arc surface at a corner of the tip.
- the chip seal has a locking portion locked to the spiral body, and the locking portion is provided on the inner side in the width direction of the chip seal than the fillet portion.
- the width of the spiral body is W1 and the width of the tip seal is W2, the relationship represented by W2> W1 is satisfied.
- the tip seal has a second convex arc surface covering the central end of the spiral body, and when the radius of curvature of the first convex arc surface is R1, and the radius of curvature of the second convex arc surface is R2, R2 The relationship indicated by> R1 is satisfied.
- the radius of curvature of the concave arc surface is R0 and the radius of curvature of the first convex arc surface is R1, the relationship represented by (R0 ⁇ 0.1 mm) ⁇ R1 ⁇ (R0 + 0.1 mm) is satisfied.
- the first convex arc surface of the fillet portion is provided with an auxiliary rib for assisting the seal with the concave arc surface with the third convex arc surface, and the radius of curvature of the concave arc surface is R0.
- the radius of curvature of the convex arc surface is R1
- the radius of curvature of the third convex arc surface is R3
- the relationship represented by R3 ⁇ R0 ⁇ R1 is satisfied.
- the plurality of auxiliary ribs are provided densely toward the center end of the spiral body.
- the tip seal since the tip seal has the fillet portion formed of the first convex arc surface at the corner of the tip portion, it suppresses the stress concentration generated at the corner of the tip portion of the fixed and movable spiral body. Can do.
- the fillet portion formed by the first convex arc surface of the tip seal of the other scroll is in sliding contact with the root portion formed by the concave arc surface of the scroll body of one scroll, it is formed between the spiral bodies.
- the air tightness of the compression chamber or the expansion chamber of the working fluid can be improved, and the operation efficiency of the fluid machine can be improved, and the size can be reduced.
- the tip seal has a locking portion locked to the spiral body, the locking portion is provided on the inner side in the width direction of the chip seal than the fillet portion, and the sliding of the fillet portion with respect to the root portion is performed. A slight deformation of the fillet portion is allowed with the contact. Therefore, when the fillet portion is pressed against the root portion, the sealing performance between the spiral bodies and the airtightness of the pressure chamber can be further improved, and the operating efficiency of the fluid machine can be further improved.
- the width of the spiral body is W1 and the width of the tip seal is W2, the relationship represented by W2> W1 is satisfied, so that the tip surface of the spiral body is reliably protected with the tip seal.
- the fillet part can be reliably pressed against the root part, and the sealing performance between the spiral bodies and, in turn, the airtightness of the pressure chamber can be further improved, further improving the operating efficiency of the fluid machine. can do.
- the tip seal has the second convex arc surface covering the central end of the spiral body, the curvature radius of the first convex arc surface is R1, and the curvature radius of the second convex arc surface is R2. Then, since the relationship represented by R2> R1 is satisfied, the tip seal can be formed with a continuous curved surface at the center end of the spiral body, and the sealing performance between the spiral bodies, and thus the pressure chamber Since the airtightness can be further increased, the operating efficiency of the fluid machine can be further improved.
- the radius of curvature of the concave arc surface is R0 and the radius of curvature of the first convex arc surface is R1, (R0 ⁇ 0.1 mm) ⁇ R1 ⁇ (R0 + 0.1 mm). Since the relationship is satisfied, the radius of curvature of the concave arc surface and the first convex arc surface can be set within an appropriate range taking into account the elastic deformation of the tip seal, and the sealing performance between the spiral bodies and the airtightness of the pressure chamber can be improved. Since it can be further increased, the operating efficiency of the fluid machine can be further improved.
- the first convex arc surface of the fillet portion is provided with the auxiliary rib for assisting the seal with the concave arc surface with the third convex arc surface, and the curvature radius of the concave arc surface is increased.
- R0 the radius of curvature of the first convex arc surface
- R3 the radius of curvature of the third convex arc surface
- R3 the relationship represented by R3 ⁇ R0 ⁇ R1 is satisfied, so the wear of the auxiliary ribs is taken into account.
- the radius of curvature of the concave arc surface and the first convex arc surface can be set in a range, and the sealing performance between the spiral bodies and, further, the airtightness of the pressure chamber can be further improved, so that the operating efficiency of the fluid machine is further improved. be able to.
- the radius of curvature of the concave arc surface and the first convex arc surface can be set in a range that takes into account the above, and the sealing performance between the spiral bodies and the airtightness of the pressure chamber can be further effectively improved. The operating efficiency can be further improved.
- FIG. 3 is a cross-sectional view of the fixed spiral body of FIG. 2 as viewed from the III-III direction. It is sectional drawing which showed the root part of the movable spiral body which concerns on 2nd Embodiment of this invention. It is sectional drawing which showed the fixed chip
- FIG. 12 is a cross-sectional view of the fixed spiral body of FIG. 11 viewed from the XII-XII direction. It is principal part sectional drawing which showed the time of the turning motion of the movable scroll which concerns on the modification of this invention. It is the top view which showed the movable scroll which concerns on another modification of this invention.
- FIG. 15 is a cross-sectional view of the movable scroll of FIG. 14 as seen from the XV-XV direction.
- FIG. 1 shows a scroll compressor (scroll type fluid machine) 1 according to the present invention.
- This compressor 1 is incorporated in a refrigeration circuit for air-conditioning a vehicle and compresses refrigerant (working fluid) circulating in the refrigeration circuit. used.
- the compressor 1 includes a rear housing 2 and a front housing 4, and a scroll unit 6 is accommodated in the rear housing 2.
- the scroll unit 6 includes a fixed scroll 8 fixed to the rear housing 2 and a movable scroll 10 assembled so as to mesh with the fixed scroll 8. A series of processes from suction of refrigerant through compression to discharge is continuously performed.
- a discharge chamber 12 is formed in the rear housing 2 between its end plate and the fixed scroll 8 of the scroll unit 6, and this discharge chamber 12 is a discharge hole formed in the end plate 8 a of the fixed scroll 8. 14 is connectable to the refrigerant circulation path of the refrigeration circuit via a discharge port (not shown) formed in the rear housing 2.
- the rear housing 2 is also provided with a refrigerant suction port (not shown).
- the suction port introduces the refrigerant into the rear housing 2 from the refrigerant circulation path, and the introduced refrigerant enters the scroll unit 6.
- a drive shaft 18 is disposed in the front housing 4, and the drive shaft 18 has a large-diameter end portion 20 and a small-diameter shaft portion 22.
- the large diameter end portion 20 is rotatably supported by the front housing 4 via a needle bearing 24, and the small diameter shaft portion 22 is rotatably supported by the front housing 4 via a ball bearing 26.
- a lip seal 28 is disposed between the small diameter shaft portion 22 and the front housing 4, and the lip seal 28 partitions the front housing 4 in an airtight manner.
- the drive pulley 30 is rotatably supported by the front housing 4 via a bearing 32. ing.
- the driving pulley 30 is connected to an output pulley on the engine side of the vehicle via a belt, and is rotated by receiving power from the engine. Therefore, during driving of the engine, if the electromagnetic clutch in the drive pulley 30 is on, the drive shaft 18 rotates with the drive pulley 30.
- crank pin 34 protrudes from the large-diameter end 20 of the drive shaft 18 toward the movable scroll 10, and the crank pin 34 supports the boss 40 of the movable scroll 10 via an eccentric bush 36 and a needle bearing 38. ing. Therefore, when the drive shaft 18 is rotated, the movable scroll 10 performs a turning motion via the crank pin 34 and the eccentric bush 36.
- a rotation prevention coupling is disposed between the front housing 4 and the end plate 10 a of the movable scroll 10.
- the rotation prevention coupling comprises a so-called EM coupling 42, and the EM coupling 42 is configured by sandwiching a ball 48 between the annular race grooves of both the movable plate 44 and the fixed plate 46 each having a ring shape. ing.
- the fixed scroll 8 has a fixed spiral 50 integrally formed with the end plate 8a
- the movable scroll 10 also has a movable spiral 52 integrally formed with the end plate 10a.
- the inner and outer surfaces of the fixed and movable spiral bodies 50 and 52 are formed of an involute curved surface except for the central end thereof, and are formed of an aluminum alloy such as A4032-T6.
- the discharge hole 14 described above is positioned in the vicinity of the central end portion 54 of the fixed spiral body 50, and a certain clearance is secured between the inner surface of the central end portion 54.
- the fixed tip seal 56 is provided at the tip 50 a of the fixed spiral body 50, and the movable tip seal 58 is provided at the tip 52 a of the movable spiral body 52.
- the fixed and movable tip seals 56 and 58 have an elastic coefficient of about 1/30 or less of that of the fixed and movable spiral bodies 50 and 52 formed from the aluminum alloy as described above, for example, engineering such as polyphenylene sulfide (PPS). ⁇ Molded from plastic.
- the fixed spiral body 50 and the end plate 10 a are slidably contacted with each other via a fixed tip seal 56, while the movable spiral body 52 and the end plate 8 a are slidably contacted with each other via a movable tip seal 58. Due to the sliding contact between the fixed and movable scrolls 8 and 10, a refrigerant compression chamber (pressure chamber) 60 is defined between the fixed and movable spiral bodies 50 and 52, and the above-described series of processes continues. Executed.
- the shapes of the root portion 62 of the movable spiral body 52, the fixed tip seal 56, and the distal end portion 50 a of the fixed spiral body 50 of the first embodiment will be described. This will be described in detail.
- the root part of the fixed spiral body 50, the movable tip seal 58, and the tip end part 52a of the movable spiral body 52 have the same shape, description thereof will be omitted and fixed in all embodiments described later.
- the spiral body 50 may be simply referred to as a spiral body 50
- the fixed chip seal 56 may be simply referred to as a chip seal 56.
- the movable spiral body 52 is formed to have a width W1, and has a root portion 62 at a corner on the end plate 10a side.
- the root portion 62 is formed to have a concave arc surface 64 with a radius of curvature R0 by a cutting tool such as an end mill at the stage of cutting the movable spiral body 52.
- the fixed tip seal 56 has substantially the same length as that of the fixed spiral body 50 in the spiral direction, and is formed in a concave cross section in the present embodiment.
- the fixed spiral body 50 is formed in a convex shape in cross section, and a convex portion 66 is formed at the tip 50 a of the fixed spiral body 50.
- a fixed chip seal 56 is fixed to the fixed spiral body by fitting a concave portion (locking portion) 68 that forms a concave shape in cross section of the fixed chip seal 56 into the convex portion 66 of the fixed spiral body 50 along the spiral direction of the fixed spiral body 50. 50 is locked and attached.
- the fixed chip seal 56 has fillet portions 70 at both corners of the front end portion 56a on the side in sliding contact with the end plate 10a.
- the fillet portion 70 is formed to have a first convex arc surface 72 having a radius of curvature R ⁇ b> 1, and the first convex arc surface 72 is brought into sliding contact with the concave arc surface 64 of the root portion 62 by the turning motion of the movable scroll 10. Further, the fixed tip seal 56 is locked to the fixed spiral body 50 at a concave portion 68, that is, a portion on the inner side in the width direction of the fixed tip seal 56 with respect to the fillet portion 70.
- the width W2 between the outer peripheral surfaces 56c of the side portions 56b forming the recess 68 is at least larger than the width W1 of the fixed and movable spiral bodies 50 and 52, and the fixed chip seal 56 is located on the side portion from the tip portion 56a. It has a divergent shape over 56b.
- FIG. 3 shows a cross-sectional view of the fixed spiral body 50 of FIG. 2 as seen from the III-III direction.
- the convex portion 66 of the fixed spiral body 50 is formed over the central end portion 54 of the fixed spiral body 50
- the fixed chip seal 56 is a bag shape covering the entire central end portion 54 of the solid spiral body 50.
- the central end 74 is formed with a second convex arc surface 76 having a radius of curvature R2 in the vicinity of the tip.
- the curvature radius R0 of the concave arc surface 64, the curvature radius R1 of the first convex arc surface 72, and the curvature radius R2 of the second convex arc surface 76 satisfy the following relationship.
- the tip seal 56 has the fillet portion 70 formed of the first convex arc surface 72 at the corner of the tip end portion 56a. It is possible to suppress the stress concentration that has occurred at the corner of the tip of 52. Further, since the first convex arc surface 72 of the tip 56a is in sliding contact with the concave arc surface 64 of the root portion 62, the airtightness of the refrigerant compression chamber 60 formed between the spiral bodies 50, 52 is improved, The size of the compressor 1 can be reduced while improving the compression efficiency.
- the concave portion 68 is provided on the inner side in the width direction of the chip seal 56 than the fillet portion 70, slight deformation of the fillet portion 70 is allowed with the sliding contact of the fillet portion 70 with respect to the root portion 62.
- the fillet portion 70 is deformed to fill a minute crescent-shaped gap between the fillet portion 70 and the root portion 62, thereby sealing between the spiral bodies 50 and 52, and thus the compression chamber.
- the airtightness of 60 can be further increased.
- the radius of curvature of the concave arc surface 64 is R0 and the radius of curvature of the first convex arc surface 72 is R1, the relationship represented by (R0 ⁇ 0.1 mm) ⁇ R1 ⁇ (R0 + 0.1 mm) is satisfied. Therefore, the radius of curvature of the concave arc surface 64 and the first convex arc surface 72 can be set within an appropriate range taking into account the elastic deformation of the tip seal 56, and the sealing performance between the spiral bodies 50 and 52, and consequently the compression chamber 60, can be set. The airtightness can be further improved.
- FIGS. 4 to 6 show details of the shapes of the root portion 62 of the movable spiral body 52, the fixed tip seal 56, and the distal end portion 50a of the fixed spiral body 50 according to the second embodiment, respectively.
- FIG. 9 shows a state in which the movable scroll 10 according to the second embodiment is assembled, and FIG. 9 shows a state in which the movable scroll 10 according to the second embodiment is turned.
- the angle between the outer peripheral surface 56c of the side portion 56b and the distal end surface 56d of the distal end portion 56a, that is, the angle representing the degree of expansion of the fixed tip seal 56 is formed at an angle ⁇ 2.
- the fixed spiral body 50 is formed with a stepped portion 78 having a width W3 from the convex portion 66 on both sides of the convex portion 66 at the tip portion 50a, while the fixed tip seal 56 has a side portion thereof.
- 56b is formed having a width of W4.
- the fixed spiral body 50 has a width W1 in the width direction
- the fixed chip seal 56 is formed with a width W2 between the outer peripheral surfaces 56c of the side portions 56b.
- the fixed chip seal 56 is formed such that the tip end portion 56a has a thickness T1 in the height direction and the side portion 56b has a thickness T2 in the height direction.
- the thickness T1 of the part 56a and the thickness T2 of the side part 56b satisfy the following relationship.
- the fixed tip seal 56 has a divergent width having an angle ⁇ 2. Because of the shape, a wedge-shaped gap G is formed between the side portion 56 b opposite to the side surface 80 side of the movable spiral body 52 and the convex portion 66.
- the relational expressions of the dimensions and shapes of the root portion 62, the fixed tip seal 56, and the fixed spiral body 50 described above are established.
- the width of the spiral body 50 is W1
- the part 70 can be reliably pressed, and the sealing performance between the spiral bodies 50 and 52 and the airtightness of the compression chamber 60 can be further enhanced.
- FIG. 10 shows details of the shape of the fixed tip seal 56 according to the third embodiment
- FIG. 11 shows the movable scroll 10 according to the third embodiment during a turning motion
- FIG. 12 shows the fixed spiral body 50 of FIG. Is a cross-sectional view as seen from the XII-XII direction.
- the auxiliary rib 86 that assists the seal between the first convex arc surface 72 and the concave arc surface 64 of the root portion 62 with the third convex arc surface 84 is a fillet portion. 70 and a single unit.
- the auxiliary rib 86 has a lower abrasion resistance than at least the end plate 10 a of the movable scroll 10, preferably higher in abrasion resistance than the fixed chip seal 56, and at least equal to or more than the elastic coefficient of the fixed chip seal 56. It is shape
- the curvature radius R3 of the third convex arc surface 84 described above satisfies the following relationship.
- R3 ⁇ R0 ⁇ R1 (R0: radius of curvature of concave arc surface 64, R1: radius of curvature of first convex arc surface 72) If the above equation holds, it is possible to realize a smooth swiveling motion of the movable spiral body 52 while ensuring the seal between the fillet portion 70 and the root portion 62 in consideration of the moldability of the fixed tip seal 56. is there.
- the auxiliary rib 86 is formed from the material having the above-described wear resistance and elastic coefficient, and the above-described third convex arc surface 84. Therefore, the third convex arc surface 84 is worn in a complementary shape of the concave arc surface 64 of the root portion 62 as it slides on the root portion 62. As a result, a fourth convex circular arc surface 88 having a radius of curvature R4 substantially equal to R0 is formed, and the elastic force of the fixed tip seal 56 itself is combined to further ensure the seal between the fillet portion 70 and the root portion 62.
- the auxiliary rib 86 is formed such that the length of the fixed spiral body 50 in the spiral direction gradually decreases as it approaches the central end portion 54, and the auxiliary rib 86 becomes denser as it approaches the central end portion 54. It is preferable to arrange them sequentially.
- the auxiliary rib 86 is provided on the first convex arc surface 72 of the fillet portion 70, the radius of curvature of the concave arc surface 64 is R 0, and the first convex arc surface 72.
- the wedge-shaped oil film formed in the region where the compression chamber 60 is formed cooperates with the auxiliary rib 86, whereby the refrigerant
- the leakage path can be completely blocked, and the sealing performance between the spiral bodies 50 and 52 and the airtightness of the compression chamber 60 can be effectively enhanced.
- the refrigerant leakage path can be completely blocked, it is possible to prevent the backflow of the refrigerant, the refrigerant pressure drop, and the noise accompanying the fluctuation of the movable scroll caused by these.
- auxiliary ribs 86 are densely provided closer to the central end portion 54 of the spiral body 50, the wear of the auxiliary ribs 86 is taken into account in the vicinity of the central end portion 54 where the pressure in the compression chamber 60 becomes the highest.
- the radius of curvature of the concave arc surface 64 and the first convex arc surface 72 can be set, and the sealing performance between the spiral bodies 50 and 52 and thus the airtightness of the compression chamber 60 can be further enhanced.
- the shape of the chip seal 56 of the present invention is not necessarily limited to a concave cross section, and for example, a convex portion (locking portion) 92 of a chip seal 90 formed in a convex cross section as shown in FIG. You may mount in the formed recessed part 94.
- the tip seal 56 and the auxiliary rib 86 of the present invention are not necessarily provided over the entire circumference of the spiral bodies 50 and 52. For example, as shown in FIGS. It may be provided only in the range of one spiral from the central end portion of the movable spiral body 52. In this case, the sealing of the compression chamber 60 that is high pressure near the central end portion of the movable spiral body 52 is effective at low cost. It is preferable that it can assist.
- the outer end portion 96 of the movable tip seal 58 is shaped so that the end surface thereof is along the turning direction of the movable scroll 10 (the arrow direction in FIG. The outer end 96 is pressed against the tip 50a of the fixed spiral body 50 by the pressure of the compression chamber 60 formed on the portion side, which is preferable because the compression chamber 60 can be reliably sealed.
- the fillet portion 70 and the auxiliary rib 86 may be provided on the tip seal of the scroll body of at least one of the fixed and movable scrolls 8 and 10, and these portions are not necessarily fixed and movable chips. It is not necessary to provide both the seals 56 and 58 or both the fixed and movable spiral bodies 50 and 52.
- the present invention can be applied not only to a scroll compressor but also to scroll-type fluid machines in general such as a scroll expander in which an expansion chamber is defined as a refrigerant pressure chamber.
- Scroll compressor (scroll type fluid machine) 8 Fixed scroll 8a End plate 10 Movable scroll 10a End plate 50 Fixed spiral body (spiral body) 52 Movable spiral body (spiral body) 54 Center end 56 Fixed chip seal (chip seal) 56a Tip 58 Movable tip seal (tip seal) 60 Compression chamber (pressure chamber) 62 Root part 64 Concave arc surface 68 Concave part (locking part) 70 Fillet portion 72 First convex arc surface 76 Second convex arc surface 84 Third convex arc surface 86 Auxiliary rib 90 Fixed chip seal (chip seal) 92 Convex (locking part)
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Abstract
Description
そして、特許文献1には、一方のスクロールの渦巻体の端板側の隅に曲率半径(r)の根元部を設け、他方のスクロールの渦巻体の先端部の角に曲率半径(R)の丸み部を設け、曲率半径(R)を曲率半径(r)よりも大きくしたスクロール型圧縮機が開示されている。
また、特許文献3には、圧縮室の隙間部は、両スクロールの少なくとも一方の表面に形成されるとともに、他方のスクロールよりも硬度の低い表面処理材によって埋められるスクロール型圧縮機が開示されている。
また、特許文献5には、固定及び可動スクロール間で渦巻体及び端板がその渦巻体に設けたチップシールを介して互いに摺接し、渦巻体の先端部に断面形状を凹状や凸状にしたチップシールを装着したスクロール型流体機械が開示されている。
しかしながら、スクロール型流体機械のスクロールユニットは、一般に、固定スクロールに対して可動スクロールが公転旋回運動する片持ち梁構造となる。従って、スクロールユニットを小型化しつつその吐出容量を確保するためには渦巻体を高く形成せざるを得ず、渦巻体の破損を生じ易いため、渦巻体の破損を防止するために渦巻体を高価な高強度材料で成形せざるを得ない。高強度材料を使用できない場合には渦巻体高さを低くせざるを得ず、流体機械の小型化促進に制約が生じていた。
そこで、上記特許文献1及び2では、渦巻体の根元部及び先端部に円弧状のいわゆるフィレット部を形成し、渦巻体の破損防止を図っている。しかし、これらフィレット部の曲率半径は互いに異なり、また、これらフィレット部は渦巻体自体に形成されるため、可動スクロールの旋回運動に伴い摩耗するおそれがある。また、固定及び可動の渦巻体間の根元部と先端部との間に三ヶ月状断面の隙間が生じることにより、圧縮室または膨張室の気密性を確保できず、ひいては流体機械の作動効率が著しく低下するおそれもある。
一方、上記特許文献3では、フィレット部に表面処理材、例えば軟金属メッキで表面処理することによって、表面処理材が適当な膜厚に摩耗し、上記三ヶ月状隙間を埋めることが可能とも思われる。しかし、そもそも表面処理材は、一般にミクロンオーダーの薄い厚みで形成されているため、摩耗を想定した厚みを有していない。また、厚すぎる表面処理材は可動スクロールの公転旋回運動に伴い剥離しかねない。従って、フィレット部に表面処理材による処理を施しても三ヶ月状隙間を埋めることは困難であり、また、渦巻体に生じる応力集中も十分に抑制できないおそれがある。
そこで、上記特許文献5に記載のように、渦巻体の先端部に凹状や凸状のチップシールを装着することにより、チップシールによって上記三ヶ月状隙間を埋めることができるとも思われる。しかし、チップシールの先端部の角の形状や可動スクロールの旋回運動に伴うチップシールの変形については格別な配慮がなされていないため、上記三ヶ月状隙間を確実に埋め、且つ、渦巻体に生じる応力集中を十分に抑制するには依然として課題が残されている。
好ましくは、渦巻体の幅をW1とし、チップシールの幅をW2としたとき、W2>W1で示される関係が満たされる。
好ましくは、チップシールは渦巻体の中央端部を覆う第2凸円弧面を有し、第1凸円弧面の曲率半径をR1とし、第2凸円弧面の曲率半径をR2としたとき、R2>R1で示される関係が満たされる。
好ましくは、フィレット部の第1凸円弧面には、凹円弧面との間のシールを第3凸円弧面にて補助する補助リブが設けられ、凹円弧面の曲率半径をR0とし、第1凸円弧面の曲率半径をR1とし、第3凸円弧面の曲率半径をR3としたとき、R3≦R0≦R1で示される関係が満たされる。
圧縮機1はリアハウジング2及びフロントハウジング4を備え、リアハウジング2内にスクロールユニット6が収容されている。スクロールユニット6はリアハウジング2に固定された固定スクロール8と、この固定スクロール8に対して噛み合うように組付けられた可動スクロール10とからなり、この可動スクロール10の公転旋回運動によりスクロールユニット6は冷媒の吸入から圧縮を経て吐出までの一連のプロセスを連続して実行する。
一方、フロントハウジング4内には駆動軸18が配置され、この駆動軸18は大径端部20及び小径軸部22を有する。大径端部20はニードル軸受24を介してフロントハウジング4に回転自在に支持され、小径軸部22はボール軸受26を介してフロントハウジング4に回転自在に支持されている。更に、小径軸部22とフロントハウジング4との間にはリップシール28が配置され、このリップシール28はフロントハウジング4内を気密に区画している。
なお、上述した吐出孔14は、固定渦巻体50の中央端部54の近傍に位置付けられ、この中央端部54の内面との間には一定のクリアランスが確保されている。
固定チップシール56は、固定渦巻体50の渦巻き方向の長さとほぼ同じ長さを有し、本実施形態の場合には断面凹状に形成されている。一方、固定渦巻体50は断面凸状に形成され、固定渦巻体50の先端部50aには凸部66が形成されている。固定渦巻体50の渦巻き方向に沿って、固定渦巻体50の凸部66に固定チップシール56の断面凹状を形作る凹部(係止部)68を嵌め込むことにより、固定チップシール56は固定渦巻体50に係止、装着される。
また、固定チップシール56は凹部68、すなわち、フィレット部70よりも固定チップシール56の幅方向内側の部位において固定渦巻体50に係止されている。更に、凹部68を形成する各側部56bの各外周面56c間の幅W2は、少なくとも固定及び可動渦巻体50,52の幅W1よりも大きく、固定チップシール56はその先端部56aから側部56bにかけて末広がりの形状をなしている。
R2>R1
(R0-0.1mm)≦R1≦(R0+0.1mm)
上式が成立していれば、固定チップシール56の成形性を考慮した上で、フィレット部70と根元部62とのシールを確保しつつ、可動渦巻体52の円滑な旋回運動を実現可能である。
更に、第1凸円弧面72の曲率半径をR1とし、第2凸円弧面76の曲率半径をR2としたとき、R2>R1で示される関係が満たされるから、チップシール56を渦巻体50の中央端部54において連続した滑らかな曲面で形成することが可能となり、渦巻体50,52間のシール性、ひいては圧縮室60の気密性を更に高めることができる。
図4~6から明らかなように、可動渦巻体52は根元部62が角度θ1(通常はθ1=90°)をなして端板10aから立設され、固定チップシール56は、凹部68を形成する側部56bの外周面56cと先端部56aの先端面56dとの角度、すなわち固定チップシール56の末広がり具合を表す角度が角度θ2をなして形成されている。
更に、上述したように、固定渦巻体50はその幅方向の幅W1を有し、固定チップシール56は各側部56bの各外周面56c間が幅W2を有して形成される。また、固定チップシール56は、先端部56aがその高さ方向の厚みT1を有し、側部56bがその高さ方向の厚みT2を有して形成されている。
W2>W1
(W3―W4)<0.2mm
θ1<θ2
T2>R1
(R1:第1凸円弧面72の曲率半径)
T1>1mm
具体的には、図7に示されるように、固定スクロール8に対する可動スクロール10の組み付け時に根元部62とフィレット部70とが離間して対向した状態では、固定チップシール56が角度θ2を有する末広がり形状であることから、可動渦巻体52の側面80側とは反対側の側部56bと凸部66との間にくさび状の隙間Gが形成されている。
次に、図9に示されるように、固定チップシール56の先端面56dに可動スクロール10の端板10aが押し付けられ、固定及び可動渦巻体50,52同士が完全に噛み合うと、隙間Gがほぼ完全に押し潰され、固定チップシール56自体の有する弾性力によってフィレット部70と根元部62とのシールが補助される。
図10に示されるように、本実施形態では、第1凸円弧面72に根元部62の凹円弧面64との間のシールを第3凸円弧面84にて補助する補助リブ86がフィレット部70と一体に設けられている。補助リブ86は、少なくとも可動スクロール10の端板10aよりも耐摩耗性が低く、好ましくは固定チップシール56よりも耐摩耗性が高い、かつ、少なくとも固定チップシール56と同等かそれ以上の弾性係数を有する材料から成形されている。
R3≦R0≦R1
(R0:凹円弧面64の曲率半径、R1:第1凸円弧面72の曲率半径)
上式が成立していれば、固定チップシール56の成形性を考慮した上で、フィレット部70と根元部62とのシールを確保しつつ、可動渦巻体52の円滑な旋回運動を実現可能である。
上述したように、第3実施形態の圧縮機1では、フィレット部70の第1凸円弧面72に補助リブ86が設けられ、凹円弧面64の曲率半径をR0とし、第1凸円弧面72の曲率半径をR1とし、第3凸円弧面84の曲率半径をR3としたとき、R3≦R0≦R1で示される関係が満たされ、R0とほぼ同等の曲率半径R4を有する第4凸円弧面88を形成されるから、補助リブ86の摩耗を加味した範囲で凹円弧面64及び第1凸円弧面72の曲率半径の設定が可能となり、渦巻体50,52間のシール性、ひいては圧縮室60の気密性を更に高めることができる。
また、冷媒の漏れ経路を完全に遮断することができるため、冷媒の逆流や冷媒圧力低下、これらに起因する可動スクロールの変動を伴う騒音を防止することもできる。
例えば、本発明のチップシール56の形状は必ずしも断面凹状に限定されず、例えば図13に示されるような断面凸状に形成したチップシール90の凸部(係止部)92を先端部50aに形成した凹部94に装着しても良い。
また、本発明のチップシール56や補助リブ86は必ずしも渦巻体50,52の全周に亘って設ける必要はなく、例えば図14及び15に示されるように、本発明の可動チップシール58を少なくとも可動渦巻体52の中央端部から渦巻きの1巻範囲にのみに設けても良く、この場合には低コストで可動渦巻体52の中央端部近傍の高圧となる圧縮室60のシールを効果的に補助することができて好適である。
更にまた、本発明では、固定及び可動スクロール8,10のうち、少なくとも一方のスクロールの渦巻体のチップシールにフィレット部70や補助リブ86を設ければ良く、必ずしもこれらの部位を固定及び可動チップシール56,58の両方、または固定及び可動渦巻体50,52の両方に設けなくても良い。
8 固定スクロール
8a 端板
10 可動スクロール
10a 端板
50 固定渦巻体(渦巻体)
52 可動渦巻体(渦巻体)
54 中央端部
56 固定チップシール(チップシール)
56a 先端部
58 可動チップシール(チップシール)
60 圧縮室(圧力室)
62 根元部
64 凹円弧面
68 凹部(係止部)
70 フィレット部
72 第1凸円弧面
76 第2凸円弧面
84 第3凸円弧面
86 補助リブ
90 固定チップシール(チップシール)
92 凸部(係止部)
Claims (7)
- 各々が端板及び該端板と一体の渦巻体を有した固定スクロール及び可動スクロールを備え、前記固定及び可動スクロール間で前記渦巻体及び前記端板がその渦巻体に設けたチップシールを介して互いに摺接することにより前記渦巻体間に形成される作動流体の圧力室を区画するスクロール型流体機械であって、
少なくとも前記一方のスクロールの渦巻体は、その端板側の隅に凹円弧面からなる根元部を有し、前記他方のスクロールのチップシールは、その先端部の角に凹円弧面に摺接する第1凸円弧面からなるフィレット部を有することを特徴とするスクロール型流体機械。 - 前記チップシールは前記渦巻体に係止される係止部を有し、前記係止部は前記フィレット部よりも前記チップシールの幅方向内側に設けられることを特徴とする請求項1記載のスクロール型流体機械。
- 前記渦巻体の幅をW1とし、
前記チップシールの幅をW2としたとき、
W2>W1
で示される関係が満たされることを特徴とする請求項1記載のスクロール型流体機械。 - 前記チップシールは前記渦巻体の中央端部を覆う第2凸円弧面を有し、
第1凸円弧面の曲率半径をR1とし、
第2凸円弧面の曲率半径をR2としたとき、
R2>R1
で示される関係が満たされることを特徴とする請求項1記載のスクロール型流体機械。 - 前記凹円弧面の曲率半径をR0とし、
前記第1凸円弧面の曲率半径をR1としたとき、
(R0-0.1mm)≦R1≦(R0+0.1mm)
で示される関係が満たされることを特徴とする請求項1記載のスクロール型流体機械。 - 前記フィレット部の前記第1凸円弧面には、前記凹円弧面との間のシールを第3凸円弧面にて補助する補助リブが設けられ、
前記凹円弧面の曲率半径をR0とし、
前記第1凸円弧面の曲率半径をR1とし、
前記第3凸円弧面の曲率半径をR3としたとき、
R3≦R0≦R1
で示される関係が満たされることを特徴とする請求項1記載のスクロール型流体機械。 - 複数の前記補助リブが前記渦巻体の中央端部に近づくほど密に設けられることを特徴とする請求項6記載のスクロール型流体機械。
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JP2010121537A JP2011247183A (ja) | 2010-05-27 | 2010-05-27 | スクロール型流体機械 |
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FR3047775B1 (fr) * | 2016-02-16 | 2018-03-02 | Danfoss Commercial Compressors | Dispositif de compression a spirales ayant un dispositif d'etancheite, et un compresseur a spirales comportant un tel dispositif de compression a spirales |
WO2018150525A1 (ja) * | 2017-02-17 | 2018-08-23 | 三菱電機株式会社 | スクロール圧縮機 |
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5715996U (ja) * | 1980-07-01 | 1982-01-27 | ||
JPH06280760A (ja) * | 1993-03-30 | 1994-10-04 | Tokico Ltd | スクロール式流体機械 |
JPH06288361A (ja) * | 1993-04-07 | 1994-10-11 | Hitachi Ltd | スクロール圧縮機 |
JPH07158568A (ja) * | 1993-12-09 | 1995-06-20 | Hitachi Ltd | スクロール流体機械 |
JP2001342979A (ja) * | 2000-05-31 | 2001-12-14 | Denso Corp | スクロール型圧縮機およびそのスクロール部材の製造方法 |
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JPH0625782A (ja) * | 1991-04-12 | 1994-02-01 | Hitachi Ltd | 高延性アルミニウム焼結合金とその製造法及びその用途 |
JP2002213377A (ja) * | 2001-01-19 | 2002-07-31 | Toyota Industries Corp | スクロール型圧縮機,スクロールおよびその製造方法 |
JP4535885B2 (ja) * | 2005-01-12 | 2010-09-01 | サンデン株式会社 | スクロール型流体機械 |
JP2006233958A (ja) * | 2005-01-31 | 2006-09-07 | Hitachi Ltd | スクロール式流体機械 |
-
2010
- 2010-05-27 JP JP2010121537A patent/JP2011247183A/ja active Pending
-
2011
- 2011-05-24 WO PCT/JP2011/061854 patent/WO2011148932A1/ja active Application Filing
- 2011-05-24 US US13/700,418 patent/US20130071279A1/en not_active Abandoned
- 2011-05-24 CN CN2011800259487A patent/CN102918275A/zh active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5715996U (ja) * | 1980-07-01 | 1982-01-27 | ||
JPH06280760A (ja) * | 1993-03-30 | 1994-10-04 | Tokico Ltd | スクロール式流体機械 |
JPH06288361A (ja) * | 1993-04-07 | 1994-10-11 | Hitachi Ltd | スクロール圧縮機 |
JPH07158568A (ja) * | 1993-12-09 | 1995-06-20 | Hitachi Ltd | スクロール流体機械 |
JP2001342979A (ja) * | 2000-05-31 | 2001-12-14 | Denso Corp | スクロール型圧縮機およびそのスクロール部材の製造方法 |
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