WO2021229682A1 - スクロール圧縮機 - Google Patents
スクロール圧縮機 Download PDFInfo
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- WO2021229682A1 WO2021229682A1 PCT/JP2020/018962 JP2020018962W WO2021229682A1 WO 2021229682 A1 WO2021229682 A1 WO 2021229682A1 JP 2020018962 W JP2020018962 W JP 2020018962W WO 2021229682 A1 WO2021229682 A1 WO 2021229682A1
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- φos
- scroll
- winding start
- fixed
- stage
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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
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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
- 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
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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
- F04C18/0276—Different wall heights
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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
- F04C2240/20—Rotors
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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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
Definitions
- This disclosure relates to a scroll compressor that compresses working gas.
- Patent Document 1 discloses a configuration in which the winding start portion, which is the central portion of the spiral portion of the spiral portion, has a stepped shape in which the wall thickness decreases from the root side to the tip side in this type of scroll compressor. ing.
- Patent Document 1 by making the winding start portion stepped, the innermost compression chamber of the plurality of compression chambers and the second compression chamber radially outer of the innermost compression chamber are gradually communicated with each other for winding. The stress generated at the base of the beginning is reduced. However, no specific study has been made on which range of the winding start portion should be stepped, and it is unclear whether sufficient stress can be reduced.
- Patent Document 1 does not consider this point at all.
- the present disclosure has been made to solve at least one of the above-mentioned problems, and an object of the present disclosure is to provide a scroll compressor capable of reducing the stress generated at the root of the winding start portion. do.
- a plurality of compression chambers are formed by combining the swinging spiral portion of the swinging scroll and the fixed spiral portion of the fixed scroll, and the swinging scroll driven by the spindle is used with respect to the fixed scroll.
- It is a scroll compressor that compresses the working gas in a plurality of compression chambers by performing a revolving motion.
- Each has a winding start portion having a bulb shape connected to the extension start point by a plurality of arcs, and at least one winding start portion has n (n ⁇ 2) bulb shapes in the axial direction of the main axis.
- the extension start point angle of the outward surface involute curve at each step of the winding start portion formed in a stepped shape of n stacked steps is ⁇ os (1) in order from the tip side to the root side.
- ⁇ os (2), ⁇ os (3), ..., ⁇ os (n) ⁇ os (1)> ⁇ os (2)> ⁇ os (3) >> ...> ⁇ os (n) and 0. It satisfies the relationship of 3 ⁇ ⁇ os (1) ⁇ os (n) ⁇ 0.7 ⁇ .
- a plurality of compression chambers are formed by combining the swinging spiral portion of the swinging scroll and the fixed spiral portion of the fixed scroll, and the swinging scroll driven by the spindle is used with respect to the fixed scroll.
- It is a scroll compressor that compresses the working gas in a plurality of compression chambers by performing a revolving motion.
- Each has a winding start portion having a bulb shape connected to the extension start point by a plurality of arcs, and at least one winding start portion has n (n ⁇ 2) bulb shapes in the axial direction of the main axis.
- each step at the start of winding is from the tip side to the root side.
- the nth stage was set toward, and the swinging spiral portion and the fixed spiral portion were separated from each other in the nth stage of the winding start portion, so that there was no communication before the separation.
- the communication between the two compression chambers is expressed as the communication of the nth stage, the line while the swing scroll revolves in the range from the crank angle at which the first stage communicates to the crank angle at which the nth stage communicates.
- a relief portion is formed on the outward surface of the swinging spiral portion or the fixed spiral portion so that at least the outermost contact point is non-contact.
- the scroll compressor according to the present disclosure by making the winding start portion stepped, the innermost compression chamber among the plurality of compression chambers and the second compression chamber radially outer of the innermost compression chamber are staged. It is possible to reduce the stress generated at the base of the winding start part by communicating with each other. Then, by setting 0.3 ⁇ ⁇ os (1) ⁇ os (n) ⁇ 0.7 ⁇ , a sufficient strength improving effect of the winding start portion can be obtained.
- the winding start portion of the spiral portion on the material side having a large coefficient of linear expansion is the innermost compression chamber and the innermost compression chamber, which are two compression chambers that were not communicated before separation. 2 Until the pressure equalization with the compression chamber is completed, it is supported by the side surface of the spiral portion of the scroll made of the material on the side having the smaller coefficient of linear expansion. Therefore, it is possible to suppress the generation of a large stress at the root of the winding start portion of the spiral portion made of the material on the side having the larger coefficient of linear expansion.
- the gap between the spiral portion on the material side having a large linear expansion coefficient during operation can be made smaller than that in the case where the relief portion is not provided. , It is possible to suppress the generation of large stress at the base of the winding start part.
- FIG. 3 is an enlarged perspective view showing a winding start portion of a fixed scroll of the scroll compressor according to the first embodiment.
- FIG. 3 is an enlarged perspective view showing a winding start portion of a swing scroll of the scroll compressor according to the first embodiment.
- FIG. 3 is a plan view showing a further enlarged view of a winding start portion of a fixed scroll of the scroll compressor according to the first embodiment.
- FIG. 3 is an enlarged plan view showing a winding start portion of a fixed scroll and a swing scroll of the scroll compressor according to the first embodiment. It is explanatory drawing of the pressure acting on the winding start part at the start of pressure equalization in a comparative example. It is explanatory drawing of the pressure acting on the winding start part at the start of pressure equalization in the scroll compressor which concerns on Embodiment 1. FIG. It is explanatory drawing of the pressure acting on the winding start part after the pressure equalization completion in the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the change of the stress generated at the root of the winding start part with the change of the crank angle in the scroll compressor which concerns on Embodiment 1. FIG. FIG. FIG.
- FIG. 5 is an enlarged view of a winding start portion when ⁇ os (1) ⁇ os (n) is 0.2 ⁇ in the scroll compressor according to the first embodiment.
- FIG. 5 is an enlarged view of a winding start portion when ⁇ os (1) ⁇ os (n) is 0.5 ⁇ in the scroll compressor according to the first embodiment.
- It is a comparative example, and is a figure which shows the relationship between the direction of action of a load with respect to the winding start part in the conventional structure, and the wall thickness of the winding start part which receives the load.
- ⁇ os (1) ⁇ os (n) is 0. It is a figure which shows the case of .2 ⁇ . In the figure showing the relationship between the acting direction of the load on the winding start portion and the wall thickness of the winding start portion that receives the load in the scroll compressor according to the first embodiment, ⁇ os (1) ⁇ os (n) is 0. It is a figure which shows the case of .5 ⁇ .
- FIG. 5 is an enlarged schematic view of a vertical cross section around a winding start portion in the scroll compressor according to the first embodiment. It is a cross-sectional schematic diagram of the compression part of the scroll compressor which concerns on Embodiment 2. FIG. It is a perspective view which shows the relief part of the scroll compressor which concerns on Embodiment 2.
- FIG. 1 It is a figure which shows the gap dimension ⁇ s of each gap at the time of operation in the compression part of the scroll compressor which concerns on Embodiment 2.
- FIG. It is a cross-sectional schematic diagram of the compression part of the scroll compressor which concerns on Embodiment 3.
- FIG. 1 is a figure which shows the gap dimension ⁇ s of each gap at the time of operation in the compression part of the scroll compressor which concerns on Embodiment 2.
- FIG. It is a cross-sectional schematic diagram of the compression part of the scroll compressor which concerns on Embodiment 3.
- FIG. 1 is a schematic vertical cross-sectional view of the scroll compressor according to the first embodiment.
- the scroll compressor 1 sucks in a working gas such as a refrigerant that circulates in the refrigeration cycle, compresses it, and discharges it in a high temperature and high pressure state.
- the scroll compressor 1 has a compression unit 5, a motor 4 that drives the compression unit 5 via a spindle 7, and other components, and these are housed inside a shell 2 that constitutes an outer shell. have.
- the compression unit 5 is arranged on the upper side and the motor 4 is arranged on the lower side in the shell 2.
- Below the shell 2 is an oil sump 3a for storing lubricating oil.
- the frame 6 and the subframe 20 are arranged on the shell 2 so as to face each other with the motor 4 interposed therebetween.
- the frame 6 is arranged on the upper side of the motor 4 and is located between the motor 4 and the compression unit 5, and the subframe 20 is located on the lower side of the motor 4.
- the frame 6 and the subframe 20 are fixed to the inner peripheral surface of the shell 2 by shrink fitting, welding, or the like.
- a main bearing 8a is provided in the central portion of the frame 6, and an auxiliary bearing 8b composed of, for example, a ball bearing is press-fitted and fixed in the central portion of the subframe 20.
- the spindle 7 is rotatably supported by the main bearing 8a and the auxiliary bearing 8b.
- the subframe 20 is equipped with a positive displacement oil pump 3, and a pump shaft that transmits rotational force to the oil pump 3 is integrally molded with the main shaft 7.
- An oil hole 7b penetrating from the lower end of the pump shaft to the upper end of the main shaft 7 is provided in the center of the spindle 7, and the oil hole 7b communicates with the oil pump 3 on the lower end side.
- the shell 2 is composed of three parts, an upper shell 2a, a middle shell 2b, and a lower shell 2c.
- the shell 2 is provided with a suction pipe 11 for sucking the refrigerant and a discharge pipe 12 for discharging the refrigerant.
- the refrigerant sucked into the shell 2 from the suction pipe 11 is sucked into the compression chamber 5a described later of the compression unit 5 via the suction port 6a formed in the frame 6.
- the compression unit 5 has a function of compressing the refrigerant sucked from the suction pipe 11 and discharging the compressed refrigerant to the high-pressure unit formed above the shell 2.
- the compression unit 5 includes a fixed scroll 30, a swing scroll 40, an old dam ring 15 for preventing the swing scroll 40 from rotating during an eccentric turning motion (swing motion) of the swing scroll 40, and the like.
- the fixed scroll 30 is arranged on the upper side and fixed to the shell 2 via the frame 6, and the swing scroll 40 is arranged on the lower side and is swingably supported by the spindle 7.
- the fixed scroll 30 includes a fixed base plate portion 30a and a spiral-shaped fixed spiral portion 30b formed on one surface of the fixed base plate portion 30a.
- the swing scroll 40 includes a swing base plate portion 40a and a spiral swing spiral portion 40b formed on one surface of the swing base plate portion 40a.
- the fixed spiral portion 30b and the rocking spiral portion 40b are formed, for example, following an involute curve.
- the fixed scroll 30 and the swing scroll 40 are arranged in the shell 2 in a state where the fixed spiral portion 30b and the swing spiral portion 40b are combined so as to mesh with each other.
- a plurality of compression chambers 5a whose volume decreases from the outer side to the inner side in the radial direction are formed as the spindle 7 rotates.
- a discharge port 30f for discharging a compressed and high-pressure refrigerant is formed in the central portion of the fixed scroll 30.
- a discharge chamber 13 is provided on the outlet side of the discharge port 30f.
- a discharge valve 13a having a reed valve structure is provided at the discharge port of the discharge chamber 13.
- a muffler 14 that suppresses the pulsation of the working gas discharged from the discharge chamber 13 is provided.
- a swing bearing 40f is formed in the center of the surface of the swing base plate portion 40a of the swing scroll 40 opposite to the surface on which the swing spiral portion 40b is formed.
- the inner diameter portion of the oscillating bearing 40f rotatably supports the slider 9 described later.
- the central axis of the oscillating bearing 40f is parallel to the central axis of the main shaft 7.
- An old dam ring 15 is provided between the swing scroll 40 and the frame 6.
- the old dam ring 15 has a ring portion, a pair of old dam keys formed on the upper surface of the ring portion, and a pair of old dam keys formed on the lower surface of the ring portion.
- the old dam key on the upper surface is inserted into a key groove formed in the swing scroll 40, and is slidable in one direction.
- the old dam key on the lower surface is inserted into a key groove formed in the frame 6 and is slidable in a direction intersecting the above one direction. With this configuration, the swing scroll 40 revolves without rotating.
- the motor 4 has a stator 4b fixed to the inner circumference of the shell 2 and a rotor 4a arranged on the inner circumference side of the stator 4b.
- the rotor 4a is fixed to the spindle 7 by shrink fitting or the like. Power is supplied to the stator 4b via the power supply terminal 21 provided on the shell 2.
- the rotor 4a rotates integrally with the spindle 7 when the stator 4b is energized.
- An eccentric shaft portion 7a is provided at the upper end portion of the spindle 7.
- the eccentric shaft portion 7a is arranged eccentrically in a predetermined eccentric direction with respect to the central axis of the main shaft 7.
- the eccentric shaft portion 7a is slidably fitted with the slider 9 described later.
- the slider 9 constitutes a variable crank mechanism in which the orbital radius of the swing scroll 40 is variable along the side surface shape of the fixed spiral portion 30b of the fixed scroll 30.
- the side surface of the fixed spiral portion 30b and the side surface of the rocking spiral portion 40b come into contact with each other during the revolution operation of the swing scroll 40.
- the overall operation of the scroll compressor 1 will be briefly explained.
- the stator 4b When the stator 4b is energized, the rotor 4a rotates.
- the rotational driving force of the rotor 4a is transmitted to the swing scroll 40 via the spindle 7, the eccentric shaft portion 7a, and the slider 9.
- the swing scroll 40 to which the rotational driving force is transmitted is restricted from rotating by the old dam ring 15, and swings with respect to the fixed scroll 30.
- the low-pressure gas refrigerant sucked into the shell 2 from the suction pipe 11 is taken into the compression chamber 5a through the suction port 6a formed in the frame 6 and is taken into the compression chamber 5a. Compressed within.
- the compressed high-pressure gas refrigerant is discharged into the discharge chamber 13 via the discharge port 30f.
- the high-pressure gas refrigerant in the discharge chamber 13 pushes up the discharge valve 13a and is discharged into the space in the muffler 14, and then is discharged into the shell 2 from the discharge hole of the muffler 14.
- the discharged refrigerant is discharged from the discharge pipe 12 to the outside of the scroll compressor 1.
- FIG. 2 is a spiral operation diagram showing a compression process of the scroll compressor according to the first embodiment.
- the compression process will be described with reference to FIG. The details of the shape of the central portion of the spiral, which is the starting portion of the winding, will be described later.
- the innermost compression chamber 5a is the innermost compression chamber 5a1
- the outermost compression chamber 5a is the outermost compression chamber 5a3, the innermost compression chamber 5a1 and the outermost compression chamber 5a3.
- the compression chamber 5a between them is referred to as a second compression chamber 5a2.
- FIG. 2A shows a state when the swing scroll 40 combined with the fixed scroll 30 is in the position where the suction is completed forming the outermost compression chamber 5a3.
- B shows a state when the swing scroll 40 is in a position where the swing scroll 40 revolves 90 deg from the state when the suction is completed in (a).
- C shows a state when the swing scroll 40 is in a position where the swing scroll 40 revolves 180 deg from the state when the suction is completed in (a).
- D shows the state when the swing scroll 40 is in the position where the swing scroll 40 revolves 270 deg from the state when the suction is completed in (a).
- the swing scroll 40 performs a swing motion in the order of (a) ⁇ (b) ⁇ (c) ⁇ (d) ⁇ (a), that is, a revolution motion without rotation.
- the volume of each compression chamber 5a is reduced from the outermost compression chamber 5a3 to the innermost compression chamber 5a1 via the second compression chamber 5a2.
- the sucked refrigerant is compressed and sequentially sent to the center, and is discharged from the innermost compression chamber 5a1 to the outside of the scroll compressor 1 via the discharge port 30f provided in the fixed scroll 30.
- the winding start portion which is the spiral center portion of the spiral portion of the fixed scroll 30 and the swing scroll 40, connects the extension start points of each involute curve constituting the inward surface and the outward surface with two arcs of a small circle and a great circle. It has a so-called bulb shape.
- the winding start portion of the first embodiment is formed in a stepped shape in which a plurality of bulb shapes are overlapped in the axial direction of the main shaft 7.
- the shape of such a winding start portion may be referred to as a staircase bulb shape.
- FIG. 3 is a schematic cross-sectional view of the compressor mechanism portion of the scroll compressor according to the first embodiment.
- FIG. 4 is an enlarged perspective view showing the winding start portion of the fixed scroll of the scroll compressor according to the first embodiment.
- FIG. 5 is an enlarged perspective view showing the winding start portion of the oscillating scroll of the scroll compressor according to the first embodiment.
- the winding start portion 30e of the fixed spiral portion 30b of the fixed scroll 30 has a three-stage stacking shape of, for example, the first stage 30e1, the second stage 30e2, and the third stage 30e3 from the tip side. Is formed in.
- the winding start portion 30e of the fixed spiral portion 30b of the fixed scroll 30 is arranged so that the position of the small arc portion gradually shifts toward the winding start end direction from the tip side (upper part in the figure) to the root side (lower part in the figure). Has been done.
- an example of stacking three stages is shown, but the number of stages may be n stages (n ⁇ 2). That is, the winding start portion 30e of the fixed spiral portion 30b may be formed in an n-step stacking step shape in which n (n ⁇ 2) bulb shapes are stacked in the axial direction.
- the small arc portion on the most tip side is the small arc portion 301
- the small arc portion closer to the root is the small arc portion 301a, which is the most root side (third stage).
- the small arc portion is the small arc portion 301b.
- the small arc portion 301a of the second stage is arranged so as to be offset in the winding start end direction from the small arc portion 301 of the first stage.
- the small arc portion 301b in the third stage is arranged so as to be further displaced in the winding start end direction than the small arc portion 301a in the second stage.
- the great circle radius of the great circle radius of the winding start portion 30e of the fixed spiral portion 30b is the same in all of the first stage, the second stage, and the third stage, and the great circle portion of each stage is the common great circle portion 302. It has become.
- the fixed scroll 30 ends the contact with the inward surface of the spiral portion on the swing scroll 40 side at different timings in the order of the first stage, the second stage, and the third stage. ..
- the winding start portion 40e of the swing spiral portion 40b of the swing scroll 40 is, for example, from the tip side, for example, the first stage 40e1 and the second stage 40e2, as in the fixed scroll 30.
- the third step 40e3 is formed in a three-tiered staircase shape.
- the position of the small arc portion gradually shifts in the winding start direction from the tip side (upper part in the figure) to the root side (lower part in the figure).
- the number of stages may be n stages (n ⁇ 2). That is, the winding start portion 40e of the swing spiral portion 40b may be formed in an n-step stacking step shape in which n (n ⁇ 2) bulb shapes are stacked in the axial direction.
- the small arc portion on the most tip side (first stage) is the small arc portion 401
- the small arc portion closer to the root (second stage) is the small arc portion 401a, which is the most root side (third stage).
- the small arc portion is the small arc portion 401b.
- the small arc portion 401a of the second stage is arranged so as to be offset in the winding start end direction from the small arc portion 401 of the first stage.
- the small arc portion 401b of the third stage is arranged so as to be further displaced in the winding start end direction than the small arc portion 401a of the second stage.
- the great circle radius of the winding start portion 40e of the swing spiral portion 40b of the swing scroll 40 is the largest.
- the great circle radius of the great circle portion 402a of the second stage is smaller than that of the great circle portion 402.
- the great circle radius of the great circle portion 402b of the third stage is further smaller than that of the great circle portion 402a.
- the extension start point angle of the involute introvert curve in the swing scroll 40 is the same in all of the first stage, the second stage, and the third stage. That is, the great circle radius in each stage of the swing scroll 40 changes according to the change in the small circle radius.
- the swing scroll 40 ends the contact with the inward surface of the spiral on the fixed scroll 30 side at different timings in the order of the first stage, the second stage, and the third stage. Further, when the stages of the winding start portion 30e of the fixed spiral portion 30b and the stages of the winding start portion 40e of the swinging spiral portion 40b are not distinguished, no reference numerals are given and the first stage and the second stage are simply used. , There is a third stage.
- the small circle radius and the great circle radius are the same in all of the first, second, and third stages, but on the swing scroll 40 side, the small circle radius and the great circle radius are the same.
- the small circle radius of the small arc portion 401 of the first stage is the smallest
- the small circle radius of the small arc portion 401a of the second stage is larger than that of the small arc portion 401
- the small arc portion of the third stage is even larger than that of the small arc portion 401a.
- the great circle radius of the great circle portion 402 of the first stage is the largest, the great circle radius of the great circle portion 402a of the second stage is smaller than that of the large arc portion 402, and the third stage.
- the great circle radius of the great arc portion 402b is even smaller than that of the great arc portion 402a.
- the extension start point angle of the involute surface involute curve in the swing scroll 40 is the same in all of the first stage, the second stage, and the third stage. That is, the great circle radius in each stage of the swing scroll 40 changes according to the change in the small circle radius.
- FIG. 6 is a plan view showing a further enlarged view of the winding start portion of the fixed scroll of the scroll compressor according to the first embodiment.
- the extension angle (extension start point angle) of the connection point (extension start point 303) between the small arc portion 301 of the first stage and the outward involute curve is ⁇ os (1).
- ⁇ os (2) be the extension angle (extension start point angle) of the connection point (extension start point 303a) between the small arc portion 301a of the second stage and the outward surface involute curve.
- ⁇ os (3) be the extension angle (extension start point angle) of the connection point (extension start point 303b) between the small arc portion 301b of the third stage and the outward plane involute curve.
- the extension start point angle of each stage is ⁇ os (1)> ⁇ os (2)> ⁇ os (3). Since the number of stages is the nth stage (n ⁇ 2), the extension start point angle of each stage is ⁇ os (1)> ⁇ os (2) ...> ⁇ os (n) in a generalized expression. It's a relationship.
- the central portion of the spiral of the swing scroll 40 has the same configuration as that of the fixed scroll 30 in terms of the extension start point angle of the outward surface involute curve. That is, the extension start point angle of the outward surface involute curve of the first stage is ⁇ os (1), the extension start point angle of the outward surface involute curve of the second stage is ⁇ os (2), and the outward surface involute curve of the third stage is set. Assuming that the extension start point angle of is ⁇ os (3), ⁇ os (1)> ⁇ os (2)> ⁇ os (3).
- FIG. 7 is an enlarged plan view showing the winding start portion of the fixed scroll and the swing scroll of the scroll compressor according to the first embodiment.
- the spiral shape of the fixed scroll 30 and the swing scroll 40 of the scroll compressor 1 will be described in detail with reference to FIG. 7.
- FIG. 7A shows a state (crank angle: ⁇ 0) when the second compression chamber 5a2 communicates with the innermost compression chamber 5a1 in the center.
- FIG. 7B shows a state (crank angle: ⁇ 0 + 15deg) when the swing scroll revolves by 15deg after communication.
- FIG. 7 (c) shows a state (crank angle: ⁇ 0 + 30 deg) when the swing scroll revolves 30 deg after communication.
- FIG. 7A shows a state (crank angle: ⁇ 0) when the second compression chamber 5a2 communicates with the innermost compression chamber 5a1 in the center.
- FIG. 7B shows a state (crank angle: ⁇ 0 + 15deg) when the swing scroll revolves by 15deg
- FIG. 7D shows a state (crank angle: ⁇ 0 + 45deg) when the swing scroll revolves 45 deg after communication.
- FIG. 7 (e) shows a state (crank angle: ⁇ 0 + 60 deg) when the swing scroll revolves 60 deg after communication.
- FIG. 7 (f) shows a state (crank angle: ⁇ 0 + 90 deg) when the swing scroll revolves 90 deg after communication.
- the contact point t between the winding start portion of the fixed scroll 30 and the winding start portion of the swing scroll 40 is the extension angle of the involute curve constituting the side surface of the spiral portion. Moves to the smaller side.
- the position of the crank angle ⁇ 0 at the time of communication shown in FIG. 7A shows a state in which the contact point t reaches the extension start point angle ⁇ os (1) of the involute curve of the first stage.
- the second compression chamber 5a2 communicates with the innermost compression chamber 5a1 via the communication flow path 50 (see FIG. 9 described later) formed in the stepped portion with the second stage.
- the high-pressure refrigerant flows from the innermost compression chamber 5a1 to the second compression chamber 5a2, and pressure equalization begins.
- the second compression occurs.
- the chamber 5a2 further communicates with the innermost compression chamber 5a1 via a communication flow path 51 formed in a step portion between the second stage and the third stage. In this way, communication between the second compression chamber 5a2 and the innermost compression chamber 5a1 occurs step by step, first in the first stage, then in the second stage, and finally in the third stage.
- the winding start portion of the conventional structure corresponds to a shape in which the first stage and the second stage are not provided in the winding start portion of the first embodiment, and the third stage continues from the root side to the tip side.
- an example of the pressure acting on the winding start portion of the swinging spiral portion will be described, but the same applies to the winding start portion of the fixed spiral portion.
- FIG. 8 is an explanatory diagram of the pressure acting on the winding start portion at the start of pressure equalization in the comparative example.
- the load due to the difference pressure between the pressure of the second compression chamber 5a2 and the pressure of the innermost compression chamber 5a1 swings and swirls. It acts on the portion 40b. Since the swinging spiral portion 40b and the fixed spiral portion 30b are separated from each other at the time of communication, as shown in FIG. 8, the swinging spiral portion 40b is tilted by the load due to the differential pressure, and the swinging spiral portion 40b becomes the root portion of the swinging spiral portion 40b. Has a large stress. A similar stress state also occurs in a compressor that does not have a variable crank mechanism and is operated in a state where the contact between the side surfaces of both spiral portions is not maintained.
- the stress generated at the root of the spiral portion can be reduced by forming the winding start portion into a staircase bulb shape. This point will be described with reference to FIGS. 9, 10 and 11 below.
- FIG. 9 is an explanatory diagram of the pressure acting on the winding start portion at the start of pressure equalization in the scroll compressor according to the first embodiment.
- FIG. 10 is an explanatory diagram of the pressure acting on the winding start portion after the pressure equalization is completed in the scroll compressor according to the first embodiment.
- the scroll compressor 1 of the first embodiment is equipped with a variable crank mechanism, the side surface of the swinging spiral portion 40b and the side surface of the fixed spiral portion 30b are in contact with each other during operation.
- the contact point t reaches the extension start point angle ⁇ os (1) of the involute curve of the first stage, as described above, the fixed spiral portion 30b and the swinging spiral portion 40b are separated from each other in the first stage and communicate with each other.
- Pressure equalization is started through the flow path 50.
- the swinging spiral portion 40b is supported in contact with the side surface of the fixed spiral portion 30b as shown in FIG.
- the reaction force R acts from the fixed spiral portion 30b on the load P due to the differential pressure between the pressures of the innermost compression chamber 5a1 and the second compression chamber 5a2 acting on the swinging spiral portion 40b, so that the swinging portion R swings.
- the stress generated at the base of the spiral portion 40b can be reduced.
- FIG. 11 is a diagram showing a change in stress generated at the root of a winding start portion with a change in the crank angle in the scroll compressor according to the first embodiment.
- the horizontal axis is the crank angle and the vertical axis is the stress.
- the solid line shows the stress at the winding start portion of the first embodiment, and the broken line shows the stress at the winding start portion of the conventional structure.
- the crank angle is the extension start angle of the first stage (the extension start angle of the first stage).
- the first stage communicates and pressure equalization starts, so that the stress generated at the base of the winding start portion decreases.
- the stress continues to increase, and when the extension start angle ( ⁇ 0 in this example) is reached, the stress increases due to the winding start portion losing support, and then the stress increases. The stress decreases due to the pressure equalization.
- the maximum stress acting on the root of the winding start portion is ⁇ 2
- the maximum stress in the first embodiment is ⁇ 1, which can be reduced as compared with the conventional structure.
- the extension start point angle of each step has a relationship of ⁇ os (1)> ⁇ os (2) ...> ⁇ os (n) as described above.
- the staircase bulb shape at the winding start portion has a structure satisfying the relationship of 0.3 ⁇ ⁇ os (1) ⁇ os (n) ⁇ 0.7 ⁇ . By satisfying this relationship, it is possible to further reduce the stress generated at the base of the winding start portion.
- the difference in the shape of the staircase bulb at the winding start portion according to the value of " ⁇ os (1) - ⁇ os (n)" will be described.
- FIG. 12 is an enlarged view of the winding start portion when ⁇ os (1) ⁇ os (n) is 0.2 ⁇ in the scroll compressor according to the first embodiment.
- FIG. 13 is an enlarged view of a winding start portion when ⁇ os (1) ⁇ os (n) is 0.5 ⁇ in the scroll compressor according to the first embodiment.
- FIG. 14 is a comparative example and is a diagram showing the relationship between the direction of action of a load on the winding start portion and the wall thickness of the winding start portion that receives the load in the conventional structure.
- the arrow indicates the direction of action of the load determined by integrating the differential pressure acting on the bulb portion.
- the length of the arrow indicates the wall thickness of the winding start portion on the cut surface where the winding start portion is cut at the position of the arrow, in other words, the wall thickness of the winding start portion with respect to the acting direction of the load.
- the meaning of the arrow is the same in FIG. 15 below.
- FIG. 14 only the first stage and the nth stage are shown, and the illustration of the other stages is omitted. This point is the same in FIGS. 15 to 17 below.
- FIG. 15 is a diagram showing the relationship between the direction of action of a load on the winding start portion and the wall thickness of the winding start portion that receives the load in the scroll compressor according to the first embodiment, and is a diagram showing ⁇ os (1) ⁇ os ( It is a figure which shows the case where n) is 0.2 ⁇ .
- FIG. 16 is a diagram showing the relationship between the direction of action of a load on the winding start portion and the wall thickness of the winding start portion that receives the load in the scroll compressor according to the first embodiment, and is a diagram showing ⁇ os (1) ⁇ os ( It is a figure which shows the case where n) is 0.5 ⁇ .
- FIG. 15 is a diagram showing the relationship between the direction of action of a load on the winding start portion and the wall thickness of the winding start portion that receives the load in the scroll compressor according to the first embodiment, and is a diagram showing ⁇ os (1) ⁇ os ( It is a figure which shows the case where n) is 0.5
- 17 is a diagram showing the relationship between the direction of action of a load on the winding start portion and the wall thickness of the winding start portion that receives the load in the scroll compressor according to the first embodiment, and is a diagram showing ⁇ os (1) ⁇ os ( It is a figure which shows the case where n) is 0.7 ⁇ .
- ⁇ os (1) - ⁇ os (n) When ⁇ os (1) - ⁇ os (n) is 0.2 ⁇ , it corresponds to a state where the stress decreases from the position of the crank angle ⁇ 0.2 ⁇ in light of FIG. 11 above.
- ⁇ os (1) ⁇ os (n) When ⁇ os (1) ⁇ os (n) is 0.5 ⁇ , it corresponds to a state where the stress decreases from the position of the crank angle ⁇ 0.5 ⁇ in light of FIG. 11 above. In this way, the maximum stress acting at the start of winding can be changed according to the value of ⁇ os (1) ⁇ os (n).
- the strength improvement range when changing ⁇ os (1) - ⁇ os (n) from 0.5 ⁇ to 0.7 ⁇ is when changing ⁇ os (1) - ⁇ os (n) from 0.2 ⁇ to 0.5 ⁇ . Is smaller than. That is, if the difference between the extension start point angles of the first stage and the nth stage ( ⁇ os (1) - ⁇ os (n)) is small, the amount of increase in the moment of inertia is small, which is commensurate with the increase in the cost of processing in a stepped shape. The strength improvement effect cannot be obtained.
- ⁇ os (1) - ⁇ os (n) the more the strength does not increase endlessly, but the strength improving effect shrinks, while the performance under the high compression ratio condition is ⁇ os (1)-.
- FIG. 18 is a diagram showing the strength analysis result of the winding start portion in the scroll compressor according to the first embodiment.
- the horizontal axis is ⁇ os (1) ⁇ os (n)
- the vertical axis is the winding start stress reduction rate.
- the bulb shape at the start of winding so that the degree of decrease in the stress reduction rate is within the range of 0.3 ⁇ ⁇ os (1) - ⁇ os (n) ⁇ 0.7 ⁇ .
- the strength improving effect can be obtained.
- the nth stage can be communicated.
- the boundary at which the nth stage can communicate after the innermost compression chamber 5a1 and the second compression chamber 5a2 are surely equalized satisfies the relationship of ⁇ os (1) ⁇ os (n)> 0.3 ⁇ . If. Conversely, if ⁇ os (1) ⁇ os (n) ⁇ 0.3 ⁇ , the nth stage communicates with the innermost compression chamber 5a1 and the second compression chamber 5a2 before the pressure is surely equalized.
- the nth stage communicates with the innermost compression chamber 5a1 and the second compression chamber 5a2 before the pressure is surely equalized, the nth stage is not supported by the spiral portion on the other side at the time of communication. Therefore, by satisfying the relationship of ⁇ os (1) ⁇ os (n)> 0.3 ⁇ , the innermost compression chamber 5a1 and the second compression chamber 5a2 are surely equalized in pressure until the differential pressure becomes 0.
- the n-stage can be configured to be supported by the spiral portion on the other side.
- the size of the small circle at each stage of the winding start can be decided without any restrictions. However, as shown in FIG. 3, since the winding start portion 40e of the swing spiral portion 40b exists at a position overlapping with the discharge port 30f, the flow path area of the discharge port 30f is partially blocked. In order to avoid this, the small circle of the first stage of the winding start portion 40e of the swing spiral portion 40b may be set small so as not to block the discharge port 30f. By reducing the wall thickness of the first stage of the winding start portion 40e, the discharge port 30f is prevented from being blocked, and a secondary effect of improving the performance by reducing the discharge pressure loss can be obtained.
- FIG. 19 is an enlarged schematic view of a vertical cross section around a winding start portion in the scroll compressor according to the first embodiment.
- the radius of curvature R1 at the base of the first stage is made larger than the radius of curvature Rn at the base of the nth stage.
- the reason why the radius of curvature R1 at the base of the first stage can be made larger than the radius of curvature at the base of the nth stage is as follows.
- the root portion of the nth stage forms a leakage flow path of the compression chamber 5a, and if the radius of curvature is increased, performance deterioration due to refrigerant leakage occurs.
- the radius of curvature R1 of the first stage can be set larger than the radius of curvature Rn of the root of the nth stage.
- the second to n-1th stages can be set to be larger than the radius of curvature Rn at the base of the nth stage.
- the ratio of the total height Hn-1 of the first to n-1 steps of the winding start portion to the total Hn of the heights of the first step to the nth step should be set to 25% to 50%.
- this ratio is less than 25%, the flow path area for the innermost compression chamber 5a1 and the second compression chamber 5a2 to equalize the pressure is insufficient, and when the nth stage communicates, the innermost compression chamber 5a1 and the second compression chamber 5a1 are communicated with each other. 2
- the differential pressure of the compression chamber 5a2 remains, and a sufficient strength improving effect cannot be obtained.
- the above ratio exceeds 50%, the stress at the roots of the first to n-1 stages increases, and the first to n-1 stages can be destroyed before the roots of the nth stage. There is sex.
- both the fixed scroll 30 and the swing scroll 40 have a stepped winding start portion, but only one of the fixed scroll 30 and the swing scroll 40 has a stepped winding start portion. You may have.
- the swing scroll 40b of the swing scroll 40 and the fixed spiral portion 30b of the fixed scroll 30 are combined to form a plurality of compression chambers 5a, and the swing scroll 40 is driven by the spindle 7.
- Each of the winding start portions having a bulb shape connecting the start point and the extension start point of the involute of a circle with a plurality of arcs is provided, and at least one winding start portion has n (n ⁇ 2).
- the shape of the bulb is formed in an n-step stacking step shape in which the main shaft 7 is stacked in the axial direction. Further, the extension start point angle of the outward surface involute curve at each step of the winding start portion formed in a stepped shape is set in order from the tip side to the root side, ⁇ os (1), ⁇ os (2), ⁇ os (3), and so on. ..., When ⁇ os (n) is set, ⁇ os (1)> ⁇ os (2)> ⁇ os (3) >> ...> ⁇ os (n) and 0.3 ⁇ ⁇ os (1) - ⁇ os (n) The relationship of ⁇ 0.7 ⁇ , is satisfied.
- the innermost compression chamber 5a1 of the plurality of compression chambers 5a and the second compression chamber 5a2 on the radial outer side of the innermost compression chamber 5a1 are communicated stepwise. It is possible to reduce the stress generated at the base of the winding start portion. Then, by satisfying the relationship of 0.3 ⁇ ⁇ os (1) ⁇ os (n) ⁇ 0.7 ⁇ , a sufficient strength improving effect of the winding start portion corresponding to the cost increase of processing in a stepped shape can be obtained. Further, the nth stage can be supported by the spiral portion on the other side until the innermost compression chamber 5a1 and the second compression chamber 5a2 are surely equalized and the differential pressure becomes zero.
- Embodiment 2 Hereinafter, the second embodiment will be described, but some of the parts that overlap with the first embodiment will be omitted.
- the temperature of the swing scroll 40 and the fixed scroll 30 becomes a high temperature of 100 ° C. or higher, so that the swing spiral portion 40b and the fixed spiral portion 30b thermally expand. It will be described in detail later that materials having different linear expansion coefficients are used, such as one of the swing scroll 40 and the fixed scroll 30 being made of aluminum and the other being made of cast iron. Can generate a large amount of pressure.
- the second embodiment reduces the stress generated at the root of the winding start portion due to the difference in the linear expansion coefficient between the material constituting the swing scroll 40 and the material constituting the fixed scroll 30.
- the linear expansion coefficient of the swing scroll 40 is larger than the linear expansion coefficient of the fixed scroll 30 will be described as an example.
- FIG. 20 is a schematic cross-sectional view of the compression portion of the scroll compressor according to the second embodiment.
- FIG. 21 is a perspective view showing a relief portion of the scroll compressor according to the second embodiment.
- a relief portion 30c1 is provided on the inward surface involute 30c (hereinafter referred to as the fixed inward surface involute 30c) of the fixed spiral portion 30b.
- the relief portion 30c1 is a recess provided in the fixed inward surface involute 30c in parallel with the axial direction.
- the relief portion 30c1 is provided to partially make the fixed inward surface involute 30c and the outward surface involute 40d of the swinging spiral portion 40b (hereinafter referred to as swinging outward surface involute 40d) non-contact.
- the range in which the relief portion 30c1 is provided is defined by using the following seven parameters.
- -Outward surface involute extension start point angle of the nth stage of the swinging spiral portion 40b: ⁇ os4 (n) -Number of contact points of the swinging outer surface involute 40d with the fixed inward surface involute 30c (hereinafter referred to as swinging outer surface side contact points): m [(
- a relief portion 30c1 is provided so that the swinging outer surface involute 40d and the fixed inward surface involute 30c are not in contact with each other.
- the swing scroll 40 revolves in the range from the crank angle with which the first stage communicates to the crank angle with which the nth stage communicates, the swing spiral portion made of the material on the side having the larger linear expansion coefficient.
- a relief portion 30c1 is provided in the fixed inward surface involute 30c so that the contact points other than the innermost contact points among the contact points on the swinging outward surface side of 40b are non-contact.
- FIG. 22 is a schematic cross-sectional view when the swing scroll is combined without being eccentric with respect to the fixed scroll in the compression portion of the comparative example, and is between the swing outward surface involute and the fixed inward surface involute at room temperature. It is explanatory drawing of the gap.
- FIG. 23 is a schematic cross-sectional view when the swing scroll is combined without being eccentric with respect to the fixed scroll in the compression portion of the comparative example, and is between the swing outward surface involute and the fixed inward surface involute during operation. It is explanatory drawing of the gap.
- FIG. 24 is a diagram showing the gap dimension ⁇ 0 in each gap when the swing scroll is eccentric to the fixed scroll and combined at room temperature in the compression portion of the comparative example.
- FIG. 25 is a diagram showing the amount of change ⁇ a of the gap dimension between normal temperature and operation in the compressed portion of the comparative example.
- FIG. 26 is a diagram showing the gap dimension ⁇ s of each gap during operation in the compression portion of the comparative example.
- the horizontal axis indicates the position of each gap, and the vertical axis indicates the gap dimension ( ⁇ m).
- each point of i is a swinging outward surface side contact point.
- the swinging outer surface side contact point is a point where the swinging outer surface involute 40d comes into contact with the fixed inward surface involute 30c when the swinging scroll 40 is eccentric with respect to the fixed scroll 30.
- the swinging inward surface side contact point is a point where the swinging inward surface involute 40c comes into contact with the fixed outward surface involute 30d when the swinging scroll 40 is eccentric with respect to the fixed scroll 30.
- the same notation shall be applied to the contact points of other numbers.
- each gap between the swinging outward surface involute 40d and the fixed inward surface involute 30c is set to ⁇ o1, ⁇ o2, and ⁇ o3 from the winding start portion toward the radial outer side. Further, the gaps between the swinging inward surface involute 40c and the fixed outward surface involute 30d are set to ⁇ i1, ⁇ i2, and ⁇ i3 in the order of radial outside from the winding start portion.
- the temperature of the swing scroll 40 and the fixed scroll 30 becomes a high temperature of 100 ° C. or higher as described above, so that the swing spiral portion 40b and the fixed spiral portion 30b thermally expand. .. Since the swinging spiral portion 40b is made of a material having a coefficient of linear expansion larger than that of the fixed spiral portion 30b, it expands more than the fixed spiral portion 30b as shown in FIG. 23.
- the amount of change ⁇ a in the gap dimension of each gap during operation with respect to normal temperature increases from the winding start portion toward the outer side in the radial direction.
- the gap size is narrower in each gap of ⁇ o1, ⁇ o2, and ⁇ o3 during operation than at room temperature.
- the clearance dimension is narrower on the outer side in the radial direction. Therefore, as shown in FIG. 25, in each of the gaps of ⁇ o1, ⁇ o2, and ⁇ o3, the amount of change ⁇ a obtained by subtracting the gap size at room temperature from the gap size during operation becomes a negative value and changes more in the radial direction.
- the quantity ⁇ a increases.
- each gap between normal temperature and operation in a state where the swing scroll 40 is combined without being eccentric with respect to the fixed scroll 30 has been described, but during actual operation, the swing scroll 40 is referred to by the arrow in FIG. 23. It will be driven in a state of being eccentric in the direction.
- the gap dimension ⁇ s of the gap ⁇ o3 becomes 0 as shown in FIG.
- the gap dimension ⁇ s of each of the other gaps of ⁇ o2, ⁇ o1, ⁇ i1, ⁇ i2, and ⁇ i3 does not become 0, and increases in this order.
- the gap ⁇ o1 and the gap ⁇ i1 are gaps located at the winding start portion, and if the operation is performed in a state where the gap dimension ⁇ s in the gap ⁇ o1 and the gap ⁇ i1 is not 0, the following problems occur. That is, before the innermost compression chamber 5a1 and the second compression chamber 5a2 equalize the pressure, each of the fixed spiral portion 30b and the swinging spiral portion 40b loses support at the winding start portion, and at the root of the winding start portion. Large stress is generated. Therefore, it is required to make the gap dimension ⁇ s in the gap ⁇ o1 and the gap ⁇ i1 at the winding start portion 0 or small.
- the gap ⁇ o3 and the gap ⁇ o2 excluding the gap ⁇ o1 at the winding start portion. It is effective to make the gap dimension ⁇ 0 at room temperature as large as possible.
- the introverted surface involute 30c is provided in anticipation of the expansion of the swinging spiral portion 40b that occurs during operation.
- the gap ⁇ o3 and the gap ⁇ o2 when the swing scroll 40 is eccentrically combined with respect to the fixed scroll 30 at room temperature can be expanded in advance as shown in FIG. 27 below.
- FIG. 27 is a diagram showing a gap dimension ⁇ 0 in each gap when a swing scroll is eccentricly combined with respect to a fixed scroll at room temperature in the compression portion of the scroll compressor according to the second embodiment.
- FIG. 28 is an explanatory diagram of the action of the relief portion in the compression portion of the scroll compressor according to the second embodiment, and is a difference between the gap dimension at room temperature of the comparative example and the gap dimension during operation of the second embodiment. It is a figure which shows ⁇ b.
- the value shown in FIG. 28 corresponds to the sum of the value in FIG. 25 and the value in FIG. 27.
- FIG. 29 is a diagram showing the gap dimension ⁇ s of each gap during operation in the compression unit of the scroll compressor according to the second embodiment.
- the horizontal axis indicates the position of each gap
- the vertical axis indicates the gap dimension ( ⁇ m).
- the gap dimension ⁇ 0 of the gap ⁇ o2 and the gap ⁇ o3 at room temperature can be secured in advance as shown in FIG. 27.
- the state where the gap dimension ⁇ s of the gap ⁇ o1 is 0 is maintained at least from the communication of the first stage of the winding start portion to the communication of the nth stage. That is, until the pressure equalization of the innermost compression chamber 5a1 and the second compression chamber 5a2 is completed, the winding start portion 40e of the swing spiral portion 40b is supported by the side surface of the fixed spiral portion 30b and is at the base of the winding start portion. It is possible to suppress the generation of large stress, and the effect of improving strength can be obtained.
- the gap dimension is as shown in FIG. ⁇ s does not become 0, and a gap remains.
- the winding start portion 30e of the fixed spiral portion 30b collapses when it receives a load due to the differential pressure between the pressure of the second compression chamber 5a2 and the pressure of the innermost compression chamber 5a1. Deform.
- the winding start portion 30e of the fixed spiral portion 30b is deformed so as to fall down, it is supported by the spiral side surface on the swinging spiral portion 40b side when it is deformed by the gap size ⁇ s. Therefore, the smaller the gap size ⁇ s, the smaller the stress generated at the base of the winding start portion. Comparing the gap dimension ⁇ s in the gap ⁇ i1 of FIG. 29 with the gap dimension ⁇ s in the same gap ⁇ i1 of FIG. 26 when there is no relief portion 30c1, the gap dimension ⁇ s in the gap ⁇ i1 of FIG. 29 is smaller. ing. Therefore, by providing the relief portion 30c1, the strength improving effect can be obtained also for the winding start portion 30e of the fixed spiral portion 30b.
- a relief portion 30c1 may be provided. That is, while the swing scroll 40 revolves in the range from the crank angle through which the first stage communicates to the crank angle through which the nth stage communicates, the swing spiral portion 40b made of the material on the side having the larger linear expansion coefficient
- the relief portion 30c1 may be provided on the fixed inward surface involute 30c so that at least the outermost contact point among the swinging outward surface side contact points is non-contact.
- the strength improving effect can be obtained.
- the relief portion 30c1 is provided only on the outermost side, it corresponds to providing the relief portion 30c1 only in the portion where the differential pressure is relatively small and the refrigerant leakage is unlikely to occur, so that the refrigerant leakage can be suppressed. , High performance can be obtained.
- the number of places where the relief portion 30c1 is provided may be determined with a degree of freedom according to the strength and performance required for the product.
- the strength improving effect by providing the relief portion 30c1 of the second embodiment is that the shape of the staircase bulb at the winding start portion described in the first embodiment is 0.3 ⁇ ⁇ os (1) ⁇ os (n). ) It is more effective when applied to a structure satisfying the relationship of ⁇ 0.7 ⁇ .
- the second embodiment is not limited to the application to this structure.
- the swinging scroll portion 40b of the swinging scroll 40 and the fixed spiral portion 30b of the fixed scroll 30 are combined to form a plurality of compression chambers 5a, and the swinging scroll 40 driven by the spindle 7.
- the swinging spiral portion 40b and the fixed spiral portion 30b have a winding start portion having a bulb shape in which the extension start point of the outward surface involute curve and the extension start point of the inward surface involute curve are connected by a plurality of arcs.
- At least one of the winding start portions is formed in an n-step stacking step shape in which n (n ⁇ 2) bulb shapes are stacked in the axial direction of the main shaft 7.
- the swing scroll 40 and the fixed scroll 30 are configured by using materials having different linear expansion coefficients.
- Each stage of the winding start portion is defined as a first stage, a second stage, ... Nth stage from the tip side to the root side.
- the communication between the two compression chambers that were not in communication before the separation is expressed as the nth stage communicating. do.
- the gap between the spiral portion on the material side having a large linear expansion coefficient during operation can be made smaller than that in the case where the relief portion 30c1 is not provided. Therefore, it is possible to suppress the generation of a large stress at the base of the winding start portion, and the effect of improving the strength of the winding start portion can be obtained.
- Embodiment 3 Hereinafter, the third embodiment will be described, but some of the parts that overlap with the first and second embodiments will be omitted.
- FIG. 30 is a schematic cross-sectional view of the compression portion of the scroll compressor according to the third embodiment.
- the fixed inward surface involute 30c is provided with the relief portion 30c1
- the rocking outward surface involute 40d is provided with the relief portion 40d1.
- the range in which the relief portion 40d1 is provided is defined by using the following seven parameters.
- -Outward surface involute extension start point angle of the nth stage of the swinging spiral portion 40b: ⁇ os4 (n) -Number of contact points of the swinging outward surface involute 40d with the fixed inward surface involute 30c: m [( ⁇ ie3- ⁇ is3 (n)) / 2 ⁇
- a relief portion 40d1 is provided so that the swinging outer surface involute 40d and the fixed inward surface involute 30c are not in contact with each other.
- the swing scroll 40 revolves in the range from the crank angle with which the first stage communicates to the crank angle with which the nth stage communicates, the swing spiral portion made of the material on the side having the larger coefficient of linear expansion.
- a relief portion 40d1 is provided in the swing outward surface involute 40d so that the contact points other than the innermost contact points among the swing outward surface side contact points of 40b are non-contact.
- 40d1 may be provided. That is, while the swing scroll 40 revolves in the range from the crank angle through which the first stage communicates to the crank angle through which the nth stage communicates, the swing spiral portion 40b made of the material on the side having the larger coefficient of linear expansion is used.
- a relief portion 40d1 may be provided on the swing outward surface involute 40d so that at least the outermost contact point of the swing outward surface side contact points is non-contact.
- the swing scroll 40 and the fixed scroll 30 are configured by using materials having different linear expansion coefficients.
- Each stage of the winding start portion is defined as a first stage, a second stage, ... Nth stage from the tip side to the root side.
- the communication between the two compression chambers that were not in communication before the separation is expressed as the nth stage communicating. do.
- the swing scroll 40 revolves in the range from the crank angle through which the first stage communicates to the crank angle through which the nth stage communicates, the spiral portion of the scroll made of the material on the side having the larger linear expansion coefficient.
- a relief portion 40d1 is formed in the swinging swirl portion 40b so that at least the outermost contact point is non-contact among a plurality of contact points in which the outward surface involute of a circle is in contact with the inward surface involute of the spiral portion on the other side. Has been done.
- the effect obtained by the third embodiment is the same as that of the second embodiment.
- 1 scroll compressor 2 shell, 2a upper shell, 2b middle shell, 2c lower shell, 3 oil pump, 3a oil reservoir, 4 motor, 4a rotor, 4b stator, 5 compression part, 5a compression chamber, 5a1 innermost compression chamber, 5a2 2nd compression chamber, 5a3 outermost compression chamber, 6 frame, 6a suction port, 7 spindle, 7a eccentric shaft, 7b oil hole, 8a main bearing, 8b auxiliary bearing, 9 slider, 11 suction pipe, 12 discharge pipe, 13 discharge chamber, 13a discharge valve, 14 muffler, 15 oldam ring, 20 subframe, 21 power supply terminal, 30 fixed scroll, 30a fixed base plate part, 30b fixed spiral part, 30c fixed inward surface involute, 30c1 relief part, 30c1a start point , 30c1b end point, 30c2 extension end point, 30d fixed outward surface involut, 30e winding start part, 30e1 first stage, 30e2 second stage, 30e3 third stage, 30f discharge port, 40 rocking scroll,
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Abstract
Description
図1は、実施の形態1に係るスクロール圧縮機の縦断面模式図である。
以下、図1に基づいて、スクロール圧縮機1について説明する。スクロール圧縮機1は、冷凍サイクルを循環する冷媒等の作動ガスを吸入して圧縮し、高温高圧の状態にして吐出するものである。スクロール圧縮機1は、圧縮部5と、主軸7を介して圧縮部5を駆動するモータ4と、その他の構成部品とを有し、これらが外郭を構成するシェル2の内部に収納された構成を有している。そして、図1に示すように、シェル2内において圧縮部5が上側に、モータ4が下側に、それぞれ配置されている。そして、シェル2の下方は潤滑油を貯留する油溜り3aとなっている。
図11に示すように、本実施の形態1では、実線に示すようにクランク角が進むにつれて、巻き始め部に発生する応力は増加していき、クランク角が第1段の伸開開始角(この例では、ψ0-0.3π)に達すると、第1段が連通して均圧が始まることで、巻き始め部の根元に発生する応力は低下していく。一方、従来構造では、破線に示すように、そのまま応力は増加していき、伸開始角(この例ではψ0)に達すると、巻き始め部が支えを失うことによる応力増加が発生し、その後、均圧によって応力が低下していく。
図19に示す通り、第1段の根元の曲率半径R1を第n段の根元の曲率半径Rnよりも大きくしている。これにより、第1段の根元の応力集中を軽減し、強度も確保できる。第1段の根元の曲率半径R1を第n段の根元の曲率半径よりも大きくできる理由としては、次の理由がある。第n段の根元部は、圧縮室5aの漏れ流路を形成していて、曲率半径を大きくすると冷媒漏れによる性能低下が発生する。これに対し、第1段の根元部は漏れ流路ではないため、性能低下の懸念がない。よって、第1段の曲率半径R1は、第n段の根元の曲率半径Rnよりも大きく設定可能である。第2段~第n-1段についても同様の理由で、第n段の根元の曲率半径Rnよりも大きく設定可能である。
以下、本実施の形態2について説明するが、実施の形態1と重複するものについては、一部の説明を省略する。
固定渦巻部30bの内向面インボリュート30c(以下、固定内向面インボリュート30cという)には、逃がし部30c1が設けられている。逃がし部30c1は、図21に示すように固定内向面インボリュート30cに軸方向と平行に設けられた凹部である。逃がし部30c1は、固定内向面インボリュート30cと揺動渦巻部40bの外向面インボリュート40d(以下、揺動外向面インボリュート40dという)とを部分的に非接触とするために設けられている。
・逃がし部30c1の始点30c1aの伸開角:φia3
・逃がし部30c1の終点30c1bの伸開角:φib3
・固定内向面インボリュート30cの伸開終点30c2の伸開角:φie3
・固定渦巻部30bの第n段の内向面インボリュート伸開始点角:φis3(n)
・揺動渦巻部40bの第1段の外向面インボリュート伸開始点角:φos4(1)
・揺動渦巻部40bの第n段の外向面インボリュート伸開始点角:φos4(n)
・揺動外向面インボリュート40dの固定内向面インボリュート30cとの接触点(以下、揺動外向面側接触点という)の数:m=[(φie3-φis3(n))/2π]ここで、[]は小数点以下切り捨てを表す。
「i≧2」かつ「φia3<(φos1(n)+π)+2π×(i-1)」かつ「φib3>(φos1(1)+π)+2π×(i-1)」を満足する範囲に逃がし部30c1を設ける。なお、図20の例では、m=3の例を示している。以下では、m=3の例で説明を行う。
以下、本実施の形態3について説明するが、実施の形態1及び実施の形態2と重複するものについては、一部の説明を省略する。
上記実施の形態2では、固定内向面インボリュート30cに逃がし部30c1を設けていたが、本実施の形態3では、揺動外向面インボリュート40dに逃がし部40d1を設けている。
・逃がし部40d1の始点40d1aの伸開角:φoa4
・逃がし部40d1の終点40d1bの伸開角:φob4
・固定内向面インボリュート30cの伸開終点30c2の伸開角:φie3
・固定渦巻部30bの第n段の内向面インボリュート伸開始点角:φis3(n)
・揺動渦巻部40bの第1段の外向面インボリュート伸開始点角:φos4(1)
・揺動渦巻部40bの第n段の外向面インボリュート伸開始点角:φos4(n)
・揺動外向面インボリュート40dの固定内向面インボリュート30cとの接触点の数:m=[(φie3-φis3(n))/2π]ここで、[]は小数点以下切り捨てを表す。
「i≧2」かつ「φoa4<(φos1(n))+2π×(i-1)」かつ「φob4>(φos1(1))+2π×(i-1)」を満足する範囲に逃がし部40d1を設ける。
Claims (7)
- 揺動スクロールの揺動渦巻部と固定スクロールの固定渦巻部とが組み合わされて複数の圧縮室が形成され、主軸によって駆動された前記揺動スクロールが前記固定スクロールに対して公転運動を行うことで前記複数の圧縮室にて作動ガスの圧縮を行うスクロール圧縮機であって、
前記揺動渦巻部及び前記固定渦巻部は、外向面インボリュート曲線の伸開始点と内向面インボリュート曲線の伸開始点との間を複数の円弧で結んだ球根形状を有する巻き始め部をそれぞれ備えており、少なくとも一方の前記巻き始め部は、n個(n≧2)の球根形状が前記主軸の軸方向に重ねられたn段重ねの階段状に形成され、
階段状に形成された前記巻き始め部の各段における前記外向面インボリュート曲線の伸開始点角を、先端側から根元側に向かって順にφos(1),φos(2),φos(3),・・・,φos(n)としたとき、
φos(1)>φos(2)>φos(3)>・・・>φos(n)
かつ、0.3π<φos(1)-φos(n)<0.7π、の関係を満たすスクロール圧縮機。 - 揺動スクロールの揺動渦巻部と固定スクロールの固定渦巻部とが組み合わされて複数の圧縮室が形成され、主軸によって駆動された前記揺動スクロールが前記固定スクロールに対して公転運動を行うことで前記複数の圧縮室にて作動ガスの圧縮を行うスクロール圧縮機であって、
前記揺動渦巻部及び前記固定渦巻部は、外向面インボリュート曲線の伸開始点と内向面インボリュート曲線の伸開始点との間を複数の円弧で結んだ球根形状を有する巻き始め部をそれぞれ備えており、少なくとも一方の前記巻き始め部は、n個(n≧2)の球根形状が前記主軸の軸方向に重ねられたn段重ねの階段状に形成され、
前記揺動スクロールと前記固定スクロールとは、互いに異なる線膨張係数の素材を用いて構成されており、
前記巻き始め部の各段を、先端側から根元側に向かって第1段、第2段、・・・第n段とし、
前記巻き始め部の前記第n段において前記揺動渦巻部と前記固定渦巻部とが離間することで、離間前に非連通であった2つの前記圧縮室が連通することを、前記第n段が連通すると表現するとき、
前記第1段が連通するクランク角から前記第n段が連通するクランク角までの範囲で前記揺動スクロールが公転運動する間、線膨張係数の大きい側の素材で構成されたスクロールの渦巻部の外向面インボリュートが、線膨張係数の小さい側の素材で構成されたスクロールの渦巻部の内向面インボリュートと接触する複数の接触点のうち、少なくとも最も外側の接触点が非接触となるように、前記揺動渦巻部又は前記固定渦巻部に逃がし部が形成されているスクロール圧縮機。 - 階段状に形成された前記巻き始め部の各段における前記外向面インボリュート曲線の伸開始点角を、先端側から根元側に向かって順にφos(1),φos(2),φos(3),・・・,φos(n)としたとき、
φos(1)>φos(2)>φos(3)>・・・>φos(n)
かつ、0.3π<φos(1)-φos(n)<0.7π、の関係を満たす請求項2記載のスクロール圧縮機。 - 前記逃がし部は、最も内側の接触点以外が非接触となるように前記揺動渦巻部又は前記固定渦巻部に形成されている請求項2又は請求項3記載のスクロール圧縮機。
- 前記揺動スクロールの素材にアルミ材、前記固定スクロールの素材に鋳鉄材を用いた請求項2~請求項4の何れか一項に記載のスクロール圧縮機。
- 前記巻き始め部の第1段~第n-1段の高さの合計の、第1段~第n段の高さの合計に対する比率が、25%~50%である請求項1~請求項5の何れか一項に記載のスクロール圧縮機。
- 第1段~第n-1段のそれぞれの根元の曲率半径Rが、第n段の根元の曲率半径よりも大きい請求項1~請求項6の何れか一項に記載のスクロール圧縮機。
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US17/910,426 US20230132581A1 (en) | 2020-05-12 | 2020-05-12 | Scroll compressor |
GB2214508.0A GB2609324A (en) | 2020-05-12 | 2020-05-12 | Scroll compressor |
PCT/JP2020/018962 WO2021229682A1 (ja) | 2020-05-12 | 2020-05-12 | スクロール圧縮機 |
JP2022522135A JPWO2021229682A1 (ja) | 2020-05-12 | 2020-05-12 |
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PCT/JP2020/018962 WO2021229682A1 (ja) | 2020-05-12 | 2020-05-12 | スクロール圧縮機 |
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0286979A (ja) * | 1988-09-26 | 1990-03-27 | Mitsubishi Electric Corp | スクロール圧縮機 |
JPH09151865A (ja) * | 1995-12-04 | 1997-06-10 | Mitsubishi Heavy Ind Ltd | スクロール流体機械 |
JP2008309020A (ja) * | 2007-06-13 | 2008-12-25 | Panasonic Corp | スクロール式流体機械 |
JP2009174406A (ja) * | 2008-01-24 | 2009-08-06 | Panasonic Corp | スクロール圧縮機 |
WO2015040720A1 (ja) * | 2013-09-19 | 2015-03-26 | 三菱電機株式会社 | スクロール圧縮機 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN107709782B (zh) * | 2015-06-10 | 2019-12-10 | 三菱电机株式会社 | 涡旋压缩机 |
-
2020
- 2020-05-12 GB GB2214508.0A patent/GB2609324A/en active Pending
- 2020-05-12 JP JP2022522135A patent/JPWO2021229682A1/ja active Pending
- 2020-05-12 WO PCT/JP2020/018962 patent/WO2021229682A1/ja active Application Filing
- 2020-05-12 US US17/910,426 patent/US20230132581A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0286979A (ja) * | 1988-09-26 | 1990-03-27 | Mitsubishi Electric Corp | スクロール圧縮機 |
JPH09151865A (ja) * | 1995-12-04 | 1997-06-10 | Mitsubishi Heavy Ind Ltd | スクロール流体機械 |
JP2008309020A (ja) * | 2007-06-13 | 2008-12-25 | Panasonic Corp | スクロール式流体機械 |
JP2009174406A (ja) * | 2008-01-24 | 2009-08-06 | Panasonic Corp | スクロール圧縮機 |
WO2015040720A1 (ja) * | 2013-09-19 | 2015-03-26 | 三菱電機株式会社 | スクロール圧縮機 |
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GB2609324A (en) | 2023-02-01 |
GB202214508D0 (en) | 2022-11-16 |
JPWO2021229682A1 (ja) | 2021-11-18 |
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