WO2024158023A1 - アキュームレータ - Google Patents

アキュームレータ Download PDF

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Publication number
WO2024158023A1
WO2024158023A1 PCT/JP2024/002127 JP2024002127W WO2024158023A1 WO 2024158023 A1 WO2024158023 A1 WO 2024158023A1 JP 2024002127 W JP2024002127 W JP 2024002127W WO 2024158023 A1 WO2024158023 A1 WO 2024158023A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
cylindrical portion
header
circumferential surface
hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2024/002127
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English (en)
French (fr)
Japanese (ja)
Inventor
侯史 細川
武治 小澤
真聖 杉野
晃平 福山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujikoki Corp filed Critical Fujikoki Corp
Priority to CN202480004927.4A priority Critical patent/CN120530292A/zh
Priority to EP24747347.3A priority patent/EP4656974A1/en
Priority to JP2024573219A priority patent/JP7840595B2/ja
Publication of WO2024158023A1 publication Critical patent/WO2024158023A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/03—Suction accumulators with deflectors

Definitions

  • the present invention relates to an accumulator.
  • Receiver tanks and accumulators are used to separate the refrigerant circulating through the refrigeration cycle into gas and liquid and store it.
  • Patent Document 1 discloses an example of an accumulator.
  • high-pressure gas-phase refrigerant discharged from a compressor flows into a condenser where it is cooled and condensed by heat exchange with outside air.
  • the liquid refrigerant condensed in the condenser is then depressurized in a pressure reducing device to become mist-like gas-liquid phase.
  • the low-pressure refrigerant after depressurization absorbs heat from the air blown by the air conditioner blower in the evaporator and evaporates.
  • the air cooled by the evaporator is temperature-adjusted in a heater core (not shown) before being blown into the passenger compartment, for example.
  • the refrigerant that has passed through the evaporator is separated into gas and liquid in the accumulator before being drawn into the compressor.
  • the header of the accumulator is formed with a refrigerant inlet and a refrigerant outlet that communicate with the inside of the accumulator.
  • the refrigerant inlet is connected to the evaporator via a pipe
  • the refrigerant outlet is connected to the compressor via a pipe.
  • an accumulator having a gas-liquid separating member (cup) that separates the refrigerant flowing in from a refrigerant inlet into a liquid-phase refrigerant and a gas-phase refrigerant, as disclosed in Patent Document 1.
  • the diameter of the refrigerant outlet formed in the header is determined according to the piping that constitutes the flow path downstream of the accumulator, and this piping is often designed by the manufacturer that assembles the refrigeration cycle.
  • the specifications of the refrigerant outlet of the accumulator are determined by the size of the designed piping, which creates the problem that it is difficult to use an outlet pipe with a large inner diameter regardless of the size of the piping connected to it.
  • the present invention was made in consideration of these problems, and aims to provide an accumulator that can hold a gas-liquid separator and increase the amount of refrigerant passing through while preventing an increase in the number of parts.
  • the accumulator comprises: a body portion having an opening at at least one end; a header having a refrigerant inlet and a refrigerant outlet, the header closing an opening at one end of the body; a gas-liquid separating member disposed within the body portion and facing the refrigerant inlet and the refrigerant outlet; an outflow pipe connected to the refrigerant outflow hole, the outflow pipe includes a small diameter cylindrical portion that is inserted into and fixed to the refrigerant outflow hole, and a large diameter cylindrical portion that is larger in diameter than the small diameter cylindrical portion and that is disposed within the body portion, the gas-liquid separating member is sandwiched between the header and a step surface that is an end surface of the large diameter cylindrical portion on the side of the small diameter cylindrical portion,
  • the outflow pipe has a cylindrical inner circumferential surface formed within the small diameter cylindrical portion, and a tapered inner circumferential surface that is connected to the cylindrical inner circumferential surface and reduces in diameter toward
  • the present invention provides an accumulator that can hold a gas-liquid separator and increase the amount of refrigerant passing through it while preventing an increase in the number of parts.
  • FIG. 1 is a vertical cross-sectional view of an accumulator according to a first embodiment.
  • FIG. 2 is a cross-sectional view showing the header, the cup, and the inner pipe in an exploded state.
  • FIG. 3 is a vertical cross-sectional view of an accumulator according to the second embodiment.
  • FIG. 4 is a vertical cross-sectional view of an inner pipe according to the second embodiment.
  • FIG. 5 is an enlarged cross-sectional view showing the lower end of the inner pipe of this embodiment.
  • FIG. 6 is an enlarged cross-sectional view showing a lower end of an inner pipe according to the first modified example.
  • FIG. 7 is an enlarged cross-sectional view showing a lower end of an inner pipe according to the second modification.
  • FIG. 1 is a vertical cross-sectional view of an accumulator according to a first embodiment.
  • FIG. 2 is a cross-sectional view showing the header, the cup, and the inner pipe in an exploded state.
  • FIG. 3 is a vertical cross
  • FIG. 8 is an enlarged cross-sectional view showing a lower end of an inner pipe according to a third modified example.
  • FIG. 9 is a vertical cross-sectional view of an inner pipe according to the third embodiment.
  • FIG. 10 is a vertical cross-sectional view of an inner pipe according to the fourth embodiment.
  • the accumulator 1 according to an embodiment of the present invention will now be described with reference to the attached drawings.
  • (First embodiment) 1 is a vertical cross-sectional view of an accumulator 1 according to a first embodiment, with only the left half of the strainer shown in cross section.
  • the accumulator 1 has a tank body 2, a double pipe 5 arranged in the tank body 2, a bag 11 containing a desiccant (moisture absorbent) DA, a cup (also called a gas-liquid separating member) 16, and a strainer 20.
  • a desiccant moisture absorbent
  • cup also called a gas-liquid separating member
  • the tank body 2 is composed of a cylindrical body 3 with a bottom and an open top, and a header 4 that is joined to the body 3 by circumferential welding via a weld 10 and closes the opening of the body 3.
  • the body 3 is a body portion having an opening at least at one end.
  • the body 3 and the header 4 are both formed from a metal such as an aluminum alloy.
  • the header 4 side is referred to as the upper side
  • the bottom side of the body 3 is referred to as the lower side.
  • the body 3 may be cylindrical with openings at both ends. In this configuration, one opening is closed by the header 4, and the other opening is closed by a member separate from the body 3. In this configuration, the member that closes the other opening of the body 3 is formed from a metal such as an aluminum alloy.
  • the header 4 is formed in a roughly disk shape, and has a refrigerant inlet hole 8 and a refrigerant outlet hole 9 formed vertically through it.
  • An inner pipe (also called an outlet pipe) 6 that extends close to the inside bottom of the body 3 is connected to the refrigerant outlet hole 9.
  • An outer pipe 7 is fitted around the outside of the inner pipe 6, forming a double pipe 5.
  • a cup 16 is provided as a gas-liquid separating member that separates the mixed refrigerant (a mixture of gas and liquid phases) from the refrigerant inlet 8 into high density liquid phase refrigerant and compressor oil (hereinafter referred to as "oil") and low density gas phase refrigerant.
  • the cup 16 has a cylindrical shape with a top, and is positioned opposite the refrigerant inlet 8 and the refrigerant outlet 9.
  • the inner pipe 6 is made of a metal such as an aluminum alloy, has an open lower end, and has an upper end connected to a refrigerant outlet hole 9 of the header 4, as described below.
  • the outer periphery of the inner pipe 6 is fitted inside a number of pipe ribs 7a protruding from the inner periphery of the outer pipe 7, so that the inner pipe 6 is stably held within the outer pipe 7 with a gap therebetween.
  • the outer pipe 7 is made of synthetic resin and is attached inside the body 3 with its upper end open.
  • a cylindrical strainer 20 is provided at the bottom of the outer pipe 7.
  • the strainer 20 is composed of a cylindrical case 21 with a bottom made of synthetic resin, and a cylindrical mesh filter 22 that is integrated with the case 21 by insert molding or the like.
  • a bag 11 containing a desiccant DA is placed between the outer pipe 7 and the inner circumference of the body 3.
  • FIG. 2 is a cross-sectional view showing the header 4, cup 16, and inner pipe 6 in an exploded state.
  • the header 4 is made up of a large cylindrical portion 4a and a step portion 4c that are stacked and connected together, and the step portion 4c is formed on the outer periphery of the lower end of the large cylindrical portion 4a with which the outer periphery of the upper end of the body 3 engages.
  • the upper surface of the large cylindrical portion 4a is formed, for example, on a plane that is perpendicular to the vertical direction.
  • a cylindrical boss 4d is formed on the underside of the header 4, protruding downward from the large cylindrical portion 4a.
  • a refrigerant outlet hole 9 is formed through the boss 4d, penetrating the header 4 from top to bottom, and a refrigerant inlet hole 8 is formed adjacent to the boss 4d, penetrating the header 4 from top to bottom.
  • the underside of the boss 4d is formed, for example, on a plane that is in surface contact with the upper surface of the top wall 16b of the cup 16, which will be described later.
  • the underside of the boss 4d is formed, for example, on a plane that is perpendicular to the axis of the inner pipe 6.
  • the refrigerant outlet hole 9 has a large diameter hole 9a formed at the top and a female thread 9b formed at the bottom.
  • the inner diameter of the large diameter hole 9a is larger than the root diameter of the female thread 9b.
  • the cup 16 is formed by connecting a side wall 16a and a top wall 16b.
  • a through hole 16c is formed in the top wall 16b.
  • one or more ribs 16b1 are formed on the upper surface of the top wall 16b.
  • the ribs 16b1 are formed in a shape that protrudes upward.
  • the ribs 16b1 constitute a part of the upper surface of the top wall.
  • the upper surface of the top wall 16b of the cup 16 in a range where the lower surface of the boss 4d of the header 4 abuts, is formed in a plane that is in surface contact with the lower surface of the boss 4d.
  • the upper surface of the top wall 16b of the cup 16, in a range where the lower surface of the boss 4d of the header 4 abuts, is formed in a plane that is perpendicular to the axis of the inner pipe 6.
  • a part of the rib 16b1 may be formed in the upper surface of the top wall 16b of the cup 16, in a range where the lower surface of the boss 4d of the header 4 abuts.
  • a recess is formed in the lower surface of the boss 4d of the header 4 to arrange a part of the rib 16b1.
  • This recess has, for example, a shape into which the rib 16b1 fits.
  • the lower surface of the top wall 16b is formed, for example, as a plane that comes into surface contact with a step surface 6d of the inner pipe, which will be described later, and is formed, for example, as a plane that is perpendicular to the axis of the inner pipe.
  • Top wall 16b faces both refrigerant inlet hole 8 and refrigerant outlet hole 9. Furthermore, top wall 16b is a portion against which the refrigerant flowing in from refrigerant inlet hole 8 collides. Furthermore, top wall 16b faces the entire refrigerant inlet hole 8. The facing direction is the axial direction of refrigerant inlet hole 8. Furthermore, the gap between the header 4 and the top wall 16b and the gap between the side wall 16a and the inner circumferential surface of the body 3 are approximately the same. Here, “approximately the same” may include an error in addition to being completely the same.
  • the refrigerant flowing in from the refrigerant inlet hole 8 collides with the top wall 16b and flows downstream, it flows through the gap between the top wall 16b and the header 4 and the gap between the inner circumferential surface of the body 3 and the side wall 16a. If these gaps are "the same", the smooth flow of the refrigerant is maintained. In addition, if there is a small error in these gaps, the state in which the refrigerant flows smoothly can be maintained. The error is an error that can maintain the flow of the refrigerant smoothly in this way.
  • the inner pipe 6 is formed, for example, by cutting an aluminum material, and is made up of a small diameter cylindrical portion (also called a small diameter cylindrical portion) 6a that is inserted and fixed into the refrigerant outflow hole 9, and a large diameter cylindrical portion (also called a large diameter cylindrical portion) 6b that is larger in diameter than the small diameter cylindrical portion 6a and is placed inside the body 3.
  • a male thread 6c is formed on the outer periphery of the small diameter cylindrical portion 6a, which has a diameter smaller than the through hole 16c.
  • the outer diameter of the small diameter cylindrical portion 6a is smaller than the outer diameter of the large diameter cylindrical portion 6b, so that an annular step surface 6d facing the refrigerant outlet hole 9 is formed between the small diameter cylindrical portion 6a and the large diameter cylindrical portion 6b.
  • the step surface 6d which is the end surface of the large diameter cylindrical portion 6b on the small diameter cylindrical portion 6a side, is perpendicular to the axis L of the inner pipe 6.
  • the inner pipe 6 has a cylindrical inner peripheral surface 6e extending inside the small diameter cylindrical portion 6a, and a tapered inner peripheral surface 6f on the lower end side that connects to the cylindrical inner peripheral surface 6e near the step surface 6d.
  • the tapered inner peripheral surface 6f which reduces in diameter toward the cylindrical inner peripheral surface 6e side (upper end side), may extend to the lower end of the inner pipe 6, or may extend to the vicinity of the lower end of the inner pipe 6.
  • the tapered inner peripheral surface 6f and the lower end can be connected by another cylindrical inner peripheral surface.
  • the taper angle ⁇ of the tapered inner peripheral surface 6f is uniform and is preferably 10 degrees or more.
  • a pressure equalizing hole 6g is formed near the step surface 6d of the inner pipe 6.
  • the pressure equalizing hole 6g penetrates the inner pipe 6.
  • the pressure equalizing hole 6g is a hole that prevents the liquid phase refrigerant that has accumulated in the inner pipe 6 from being sucked up by the compressor when the compressor is started again after the refrigeration cycle has stopped (after the compressor has stopped operating).
  • the pressure equalizing hole 6g allows not only the liquid phase refrigerant in the inner pipe 6 but also the gas phase refrigerant outside the inner pipe 6 to be sucked up by the compressor, thereby preventing the liquid phase refrigerant from being sucked up.
  • the lower end of the boss 4d of the header 4 is brought into contact with the upper surface of the cup 16 and the periphery of the through hole 16c.
  • the rib 16b1 is formed, for example, at a position that avoids the area where the boss 4d comes into contact. Therefore, in this embodiment, the lower end of the boss 4d comes into surface contact with the flat portion of the upper surface of the top wall 16b.
  • the inner pipe 6 is brought close to the cup 16 from below. Further, the small diameter cylindrical portion 6a of the inner pipe 6 is inserted into the through hole 16c, and the male thread 6c is screwed into the female thread 9b of the header 4.
  • the inner pipe 6 approaches the header 4, and the step surface 6d comes into contact with the bottom surface of the cup 16 around the through hole 16c.
  • the bottom surface of the top wall 16b of the cup 16 comes into surface contact with the step surface 6d.
  • the cup 16 is clamped and fixed between the bottom end of the boss 4d and the step surface 6d.
  • the flatness of the step surface 6d is ensured to be high, so even if the area of the step surface 6d is small, the cup 16 can be held in an appropriate position by coming into surface contact with the bottom surface of the cup 16.
  • the outer pipe 7 and strainer 20 are assembled into the inner pipe 6, and the assembly formed in this way is installed in the body 3 in which the bag 11 is arranged, and welded to the header 4 to complete the accumulator 1.
  • a small diameter cylindrical portion 6a is formed to match the refrigerant outflow hole 9 of the header 4, and a large diameter cylindrical portion 6b is formed to obtain a flow rate according to the performance required of the accumulator 1, and further, a stepped surface 6d is formed to clamp the cup 16 against the header 4, thereby fixing the cup 16.
  • a stepped surface 6d is formed to clamp the cup 16 against the header 4, thereby fixing the cup 16.
  • the inner pipe 6 is fastened to the header 4 by screwing the female thread 9b into the male thread 6c, eliminating the need for the conventional crimping process of the inner pipe 6 (no crimping portion is provided inside the refrigerant outflow hole 9).
  • the inner diameter of the small diameter cylindrical portion 6a can be expanded regardless of the inner diameter of the refrigerant outflow hole 9, reducing pressure loss inside the inner pipe 6 and ensuring a smooth flow of the refrigerant.
  • the cup 16 is attached to the header 4 by being sandwiched between the step surface 6d formed on the inner pipe 6 and the boss 4d of the header 4, eliminating the need for bulge processing of the inner pipe 6. This reduces the resistance of the refrigerant flowing through the inner pipe 6 and suppresses the occurrence of turbulence, ensuring a smooth flow of the refrigerant.
  • the inner pipe 6 is formed with a tapered inner circumferential surface 6f, so that the inner diameter gradually decreases toward the cylindrical inner circumferential surface 6e, which is the refrigerant outlet side, thereby reducing pressure loss and ensuring an even smoother flow of the refrigerant.
  • the refrigerant When the refrigerant is discharged from the evaporator, it is transported to the accumulator 1 through a connecting pipe (not shown). After reaching the accumulator 1, the refrigerant flows into the body 3 through the refrigerant inlet 8, and then collides with the upper surface of the cup 16, where it is separated into high-density liquid-phase refrigerant and oil, and low-density gas-phase refrigerant (gas refrigerant).
  • the liquid refrigerant and oil are stored in the body 3 due to their own weight. During this process, the liquid refrigerant and oil continue to separate, and the oil accumulates below the liquid refrigerant. At this time, the liquid level of the liquid refrigerant reaches a height position where part of the desiccant-containing bag 11 is immersed. Therefore, both the moisture contained in the liquid refrigerant and the humidity contained in the gas refrigerant are absorbed by the desiccant DA.
  • the gas-phase refrigerant that has been separated into gas and liquid flows in from the upper opening of the outer pipe 7 and descends inside the outer pipe 7. It then turns around at the bottom of the outer pipe 7, passes over the lower end of the inner pipe 6, and flows inside, then rises inside the inner pipe 6 and is led to the refrigerant outlet hole 9.
  • the oil that accumulates at the bottom of the body 3 together with the liquid refrigerant moves to the bottom side of the body 3 due to differences in specific gravity and properties compared to the liquid refrigerant, and is sucked into the gas refrigerant being sucked into the compressor suction side, passing through the mesh filter 22 of the strainer 20, the oil return hole 7e, and the internal space of the inner pipe 6, in that order, before being returned to the compressor suction side together with the gas refrigerant and circulated.
  • foreign matter such as sludge is captured and removed from the circulating refrigerant (including oil).
  • Fig. 3 is a vertical cross-sectional view of an accumulator 1A according to a second embodiment, but only the left half of the strainer is shown in cross section as in Fig. 1.
  • Fig. 4 is a vertical cross-sectional view of an inner pipe 6A according to the second embodiment.
  • Fig. 5 is an enlarged cross-sectional view of the lower end of the inner pipe 6A.
  • the inner pipe 6A in this embodiment is formed, for example, by forging an aluminum material, and is composed of a small diameter cylindrical portion 6Aa and a large diameter cylindrical portion 6Ab connected together.
  • a male thread 6Ac is formed on the outer periphery of the small diameter cylindrical portion 6Aa.
  • the outer diameter of the small diameter cylindrical portion 6Aa is smaller than the outer diameter of the large diameter cylindrical portion 6Ab, so that a step surface 6Ad is formed between the small diameter cylindrical portion 6Aa and the large diameter cylindrical portion 6Ab, and a pressure equalizing hole 6Ag1 is formed in the vicinity of the step surface 6Ad.
  • the step surface 6Ad is perpendicular to the axis L of the inner pipe 6A.
  • the inner pipe 6A has a first cylindrical inner circumferential surface 6Ae on the upper end side, a tapered inner circumferential surface 6Af on the lower end side that connects to the first cylindrical inner circumferential surface 6Ae near the step surface 6Ad, and a second cylindrical inner circumferential surface 6Ag that connects to the tapered inner circumferential surface 6Af.
  • the taper angle ⁇ of the tapered inner circumferential surface 6Af is uniform, and is preferably 60 degrees or more when formed by forging.
  • the second cylindrical inner surface 6Ag maintains a cylindrical shape up to the lower end 6Ah of the inner pipe 6A, and the outer surface of the large diameter cylindrical portion 6Ab maintains a cylindrical shape. Furthermore, the lower end 6Ah is an end surface perpendicular to the axis L (see FIG. 5).
  • the cup 16 is placed between the header 4 and the inner pipe 6A, and then the small diameter cylindrical portion 6Aa of the inner pipe 6A is inserted into the through hole 16c, and the male thread 6Ac is screwed into the female thread 9b of the header 4 to assemble the cup 16. As a result, the cup 16 is clamped and fixed between the lower end of the boss 4d and the step surface 6Ad.
  • Fig. 6 is an enlarged cross-sectional view of the lower end of the inner pipe 6B according to the first modified example.
  • the outer circumferential surface of the large-diameter cylindrical portion 6Bb has a cylindrical shape up to the lower end 6Bh of the inner pipe 6B, but the second cylindrical inner circumferential surface 6Bg gradually expands in diameter from the vicinity of the lower end 6Bh toward the lower end 6Bh, and intersects with the outer circumferential surface of the large-diameter cylindrical portion 6Bb at the lower end 6Bh.
  • the second cylindrical inner circumferential surface 6Bg in the vicinity of the lower end 6Bh preferably has an arc shape.
  • FIG. 7 is an enlarged cross-sectional view of the lower end of the inner pipe 6C according to the second modification.
  • the second cylindrical inner circumferential surface 6Cg has a cylindrical shape up to the lower end 6Ch of the inner pipe 6C, but the outer circumferential surface of the large diameter cylindrical portion 6Cb gradually decreases in diameter from the vicinity of the lower end 6Ch toward the lower end 6Ch, and intersects with the second cylindrical inner circumferential surface 6Cg at the lower end 6Ch.
  • the outer circumferential surface of the large diameter cylindrical portion 6Cb in the vicinity of the lower end 6Ch preferably has an arc shape.
  • FIG. 8 is an enlarged cross-sectional view of the lower end of the inner pipe 6D according to the third modification.
  • the second cylindrical inner circumferential surface 6Dg gradually expands in diameter from the vicinity of the lower end 6Dh of the inner pipe 6D toward the lower end 6Dh
  • the outer circumferential surface of the large diameter cylindrical portion 6Db gradually decreases in diameter from the vicinity of the lower end 6Dh toward the lower end 6Dh
  • the second cylindrical inner circumferential surface 6Cg and the outer circumferential surface of the large diameter cylindrical portion 6Db intersect at the lower end 6Dh.
  • the lower end wall of the large diameter cylindrical portion 6Cb near the lower end 6Ch preferably has a semicircular arc shape.
  • the gas-liquid separated gas-phase refrigerant when the gas-liquid separated gas-phase refrigerant turns around at the bottom of the outer pipe 7 and flows toward the lower end 6Dh of the inner pipe 6D, it flows along the outer peripheral surface of the gradually narrowing large diameter cylindrical section 6Db, and when it passes the lower end 6Dh of the inner pipe 6D and flows inward, it flows along the gradually expanding second cylindrical inner peripheral surface 6Dg, ensuring a smooth flow of the refrigerant.
  • Modifications 1 to 3 can also be applied to the inner pipe 6 in the first embodiment.
  • Fig. 9 is a vertical cross-sectional view of an accumulator 1F according to a third embodiment.
  • the outflow pipe 6F is U-shaped and does not have an outer pipe.
  • a strainer and a bag containing a desiccant are omitted.
  • the configurations of the header 4F and the outflow pipe 6F are different from those of the above-mentioned embodiment, and other configurations are the same as those of the above-mentioned embodiment. Therefore, the same reference numerals are used for the common configurations and a duplicated description will be omitted.
  • the header 4F has a refrigerant outlet hole 9F that does not have a female thread, and has a large diameter hole 9Fa and a small diameter hole 9Fb.
  • the rest of the configuration is the same as in the above-mentioned embodiment.
  • the outflow pipe 6F in this embodiment is formed by connecting a small diameter cylindrical section 6Fa and a large diameter U-shaped tubular section 6Fb that is bent into a U shape.
  • the outer peripheral surface 6Fc of the small diameter cylindrical section 6Fa does not have a male thread, and has an outer diameter that is approximately the same as the inner diameter of the small diameter hole 9Fb.
  • the outer diameter of the small diameter cylindrical portion 6Fa is smaller than the outer diameter of the large diameter U-shaped cylindrical portion 6Fb, so that a step surface 6Fd is formed between the small diameter cylindrical portion 6Fa and the large diameter U-shaped cylindrical portion 6Fb.
  • the outflow pipe 6F has a tapered inner circumferential surface 6Ff near the step surface 6Fd.
  • the outflow pipe 6F also has a pressure equalizing hole 6Fg, as in the above-mentioned embodiment.
  • the small diameter cylindrical portion 6Fa of the outflow pipe 6F is inserted into the through hole 16c, and then the small diameter cylindrical portion 6Fa is fixed to the small diameter hole 9Fb of the header 4 by press fitting, brazing, welding, or the like.
  • the cup 16 is clamped and fixed between the lower end of the boss 4Fd and the step surface 6Fd.
  • the outflow pipe 6F can be attached by moving it linearly without rotating it relative to the header 4, so that the free end of the outflow pipe 6F can be positioned inside the cup 16 in the assembly position shown in Figure 9.
  • Fourth Embodiment 10 is a vertical cross-sectional view of an accumulator 1G according to the fourth embodiment.
  • the accumulator 1G of this embodiment is different from the accumulator 1F of the third embodiment in the shape of the outflow pipe 6G.
  • the bending radius of the bent portion of the large-diameter U-shaped cylindrical portion 6Gb of the outflow pipe 6G is larger than the bending radius of the corresponding portion of the outflow pipe 6F of the third embodiment.
  • the rest of the configuration is the same as in the above-mentioned embodiment.
  • the outflow pipe 6G has a pressure equalizing hole 6Gg as in the above-mentioned embodiment.
  • the cup 16 is one example of a gas-liquid separating member.
  • the gas-liquid separating member faces both the refrigerant inlet hole 8 and the refrigerant outlet hole 9.
  • the gas-liquid separating member has a portion with which the refrigerant that flows in from the refrigerant inlet hole 8 collides.
  • the gas-liquid separating member preferably faces the entire refrigerant inlet hole 8.
  • the facing direction is the axial direction of the refrigerant inlet hole 8.
  • the gas-liquid separating member preferably has a top wall facing both the entire refrigerant inlet hole 8 and the refrigerant outlet hole 9 , and a cylindrical side wall facing the inner circumferential surface of the body 3 .
  • the gap between the header 4 and the top wall and the gap between the inner circumferential surface of the body 3 and the side wall are approximately the same.
  • approximately the same means that in addition to being completely the same, it may include an error. That is, when the refrigerant that flows in from the refrigerant inlet hole 8 collides with the top wall and flows downstream, it flows through the gap between the top wall and the header 4 and the gap between the inner circumferential surface of the body 3 and the side wall. If these gaps are "the same", the smooth flow of the refrigerant is maintained. In addition, even if there is a small error in these gaps, the state in which the refrigerant flows smoothly can be maintained.
  • the error is an error that can maintain the flow of the refrigerant smoothly in this way.
  • the top wall of the gas-liquid separating member is not limited to being in the form of a plate having a constant thickness. Furthermore, another example of the gas-liquid separating member has a structure that does not include a side wall.
  • the header and inner pipe are assembled by screwing together the threads, but as in the third and fourth embodiments, the header and inner pipe may be fixed by press fitting, brazing, welding, or the like.
  • a body portion having an opening at at least one end; a header having a refrigerant inlet and a refrigerant outlet, the header closing an opening at one end of the body; a gas-liquid separating member disposed within the body portion and facing the refrigerant inlet and the refrigerant outlet; an outflow pipe connected to the refrigerant outflow hole, the outflow pipe includes a small diameter cylindrical portion that is inserted into and fixed to the refrigerant outflow hole, and a large diameter cylindrical portion that is larger in diameter than the small diameter cylindrical portion and that is disposed within the body portion, and the gas-liquid separating member is sandwiched between the header and a step surface that is an end surface of the large diameter cylindrical portion on the side of the small diameter cylindrical portion,
  • the outflow pipe has a cylindrical inner circumferential surface formed in the small diameter cylindrical portion, and a tapered inner circumferential surface that is connected to the cylindrical inner circumferential surface and that decreases in diameter toward the ref
  • the tapered inner peripheral surface extends to an end of the large diameter cylindrical portion on an opposite side to the small diameter cylindrical portion.
  • the small diameter cylindrical portion is formed in a cylindrical shape and has a male thread on its outer circumferential surface,
  • the refrigerant outlet hole has an internal thread,
  • the outflow pipe is fixed to the header by threading the male thread into the female thread.
  • the small diameter cylindrical portion is fixed to the refrigerant outlet hole of the header by press-fitting, brazing, or welding.

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  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2024/002127 2023-01-26 2024-01-25 アキュームレータ Ceased WO2024158023A1 (ja)

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CN202480004927.4A CN120530292A (zh) 2023-01-26 2024-01-25 储液器
EP24747347.3A EP4656974A1 (en) 2023-01-26 2024-01-25 Accumulator
JP2024573219A JP7840595B2 (ja) 2023-01-26 2024-01-25 アキュームレータ

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JP (1) JP7840595B2 (https=)
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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59186772U (ja) * 1983-05-31 1984-12-11 三菱電機株式会社 回転式圧縮機のアキユ−ムレ−タ
JPH0432462U (https=) * 1990-07-06 1992-03-17
JP2001082814A (ja) * 1999-09-09 2001-03-30 Denso Corp 冷凍サイクル装置およびそれに用いるアキュムレータ
US6223555B1 (en) * 1999-06-08 2001-05-01 Visteon Global Technologies, Inc. Accumulator for an air conditioning system
JP2008518604A (ja) * 2004-10-29 2008-06-05 オーシャン・ファーム・テクノロジーズ・インコーポレーテッド 魚の養殖漁業のための生け簀
JP2014052139A (ja) 2012-09-07 2014-03-20 Denso Corp アキュムレータ
WO2014178191A1 (ja) * 2013-04-30 2014-11-06 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP2016113916A (ja) * 2014-12-12 2016-06-23 日立オートモティブシステムズ株式会社 外接ギヤポンプ
CN109631432A (zh) * 2018-11-30 2019-04-16 青岛海尔空调器有限总公司 一种应用于压缩机的储液罐
WO2020179777A1 (ja) * 2019-03-05 2020-09-10 株式会社不二工機 冷媒容器

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59186772U (ja) * 1983-05-31 1984-12-11 三菱電機株式会社 回転式圧縮機のアキユ−ムレ−タ
JPH0432462U (https=) * 1990-07-06 1992-03-17
US6223555B1 (en) * 1999-06-08 2001-05-01 Visteon Global Technologies, Inc. Accumulator for an air conditioning system
JP2001082814A (ja) * 1999-09-09 2001-03-30 Denso Corp 冷凍サイクル装置およびそれに用いるアキュムレータ
JP2008518604A (ja) * 2004-10-29 2008-06-05 オーシャン・ファーム・テクノロジーズ・インコーポレーテッド 魚の養殖漁業のための生け簀
JP2014052139A (ja) 2012-09-07 2014-03-20 Denso Corp アキュムレータ
WO2014178191A1 (ja) * 2013-04-30 2014-11-06 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP2016113916A (ja) * 2014-12-12 2016-06-23 日立オートモティブシステムズ株式会社 外接ギヤポンプ
CN109631432A (zh) * 2018-11-30 2019-04-16 青岛海尔空调器有限总公司 一种应用于压缩机的储液罐
WO2020179777A1 (ja) * 2019-03-05 2020-09-10 株式会社不二工機 冷媒容器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4656974A1

Also Published As

Publication number Publication date
EP4656974A1 (en) 2025-12-03
CN120530292A (zh) 2025-08-22
JP7840595B2 (ja) 2026-04-06
JPWO2024158023A1 (https=) 2024-08-02

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