Classifications

• • 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 perform gas-liquid separation and to store a refrigerant that is circulated in a refrigeration cycle.
• Patent Literature 1 discloses an example of an accumulator.
• high-pressure gas phase refrigerant discharged from a compressor flows into a condenser, where the gas phase refrigerant is subjected to heat exchange with outside air and condensed.
• Liquid refrigerant condensed in the condenser is thereafter decompressed in a decompression device and becomes a gas-liquid phase state in a mist form.
• the low-pressure refrigerant after decompression absorbs heat from air blown from an air conditioning blower in an evaporator and is evaporated.
• the blown air cooled in the evaporator is subjected to temperature control by a heater core portion not shown in a well-known manner, and then blown out into an interior of a vehicle, for example.
• the refrigerant having passed through the evaporator is subjected to gas-liquid separation in the accumulator before being sucked into the compressor.
• a refrigerant inflow port and a refrigerant outflow port that are communicated with an interior of the accumulator are formed on a header of the accumulator.
• the refrigerant inflow port is connected to the evaporator via a piping, and the refrigerant outflow port is connected to the compressor via a piping.
• an accumulator having a gas-liquid separating member, i.e., cup, for separating the refrigerant flowing in through the refrigerant inflow port into a liquid phase refrigerant and a gas phase refrigerant is also known.
• Patent Literature 1 Japanese Patent Application Laid-Open Publication No. 2014-52139
• One way to increase the amount of refrigerant that passes through the accumulator is to use an outflow pipe having a large inner diameter as an outflow pipe that is arranged within the accumulator and that is connected to the refrigerant outflow port of the header.
• the diameter of the refrigerant outflow port formed on the header is determined according to the piping constituting a flow passage on a downstream side of the accumulator, and the piping is often designed by the manufacturer that assembles the refrigeration cycle.
• the specification of the refrigerant outflow port of the accumulator is actually determined by the size of the designed piping, and therefore, it is difficult to use an outflow pipe having a large inner diameter regardless of the size of the piping connected to the outflow pipe.
• the preset invention aims at providing an accumulator capable of holding a gas-liquid separating body and increasing an amount of refrigerant that passes through, while preventing an increase in the number of components.
• an accumulator according to the present invention includes:
• the present invention enables to provide an accumulator capable of holding a gas-liquid separating body and increasing an amount of refrigerant that passes through, while preventing an increase in the number of components.
• FIG. 1 is a vertical cross-sectional view of the accumulator 1 according to a first embodiment, with only a left half of a strainer being illustrated in cross section.
• the accumulator 1 includes a tank body 2, a double pipe 5 arranged within the tank body 2, a bag 11 including a drying agent, i.e., desiccant, DA, a cup, also referred to as a gas-liquid separating member, 16, and a strainer 20.
• a drying agent i.e., desiccant, DA
• cup also referred to as a gas-liquid separating member, 16
• a strainer 20 also referred to as a gas-liquid separating member
• the tank body 2 is composed of a body 3 having a cylindrical shape with a bottom that has an upper end opened, and a header 4 that is joined with the body 3 by circumference welding via a welding portion 10 and that blocks an opening of the body 3.
• the body 3 is a body portion that has an opening on at least one end.
• the body 3 and the header 4 are each formed of a metal such as aluminum alloy.
• the header 4 side is referred to as upward, and a bottom side of the body 3 is referred to as downward.
• the body 3 may be tubular with both ends opened. According to this configuration, one of the openings is blocked by the header 4, and the other opening is blocked by a different member as the body 3. According to this configuration, the member that blocks the other opening of the body 3 is formed of metal such as aluminum alloy.
• the header 4 formed to have approximately a disk shape has a refrigerant inflow hole 8 and a refrigerant outflow hole 9 formed to pass therethrough in the up-down direction.
• An inner pipe, also referred to as an outflow pipe, 6 that extends to a vicinity of an inner bottom portion of the body 3 is connected to the refrigerant outflow hole 9.
• An outer pipe 7 is arranged around an outer side of the inner pipe 6, by which the double pipe 5 is formed.
• a cup 16 that serves as a gas-liquid separating member that separates a mixed refrigerant, i.e., refrigerant in which a gas-phase portion and a liquid-phase portion are mixed, from the refrigerant inflow hole 8 into a liquid phase refrigerant and a compressor oil, referred as only oil, having a high density and a gas phase refrigerant having a low density.
• the cup 16 has a cylindrical shape with a top, and it is arranged to face the refrigerant inflow hole 8 and the refrigerant outflow hole 9.
• the inner pipe 6 is formed of metal such as aluminum alloy, with a lower end portion thereof opened and an upper end portion thereof connected to the refrigerant outflow hole 9 of the header 4, as described in detail later. Further, an outer circumference of the inner pipe 6 is fit to an inner side of a plurality of pipe ribs 7a which are disposed to protrude from an inner circumferential surface of the outer pipe 7, and thereby, the inner pipe 6 is held stably within the outer pipe 7 with a gap formed therebetween.
• the outer pipe 7 is formed of synthetic resin, and it is attached within the body 3 with the upper end portion opened.
• a cylindrical strainer 20 is disposed on a bottom portion of the outer pipe 7.
• the strainer 20 is composed of a case 21 made of synthetic resin and having a cylindrical shape with a bottom, and a cylindrical mesh filter 22 that is integrated with the case 21 by insert molding and the like.
• the bag 11 including a drying agent DA is disposed between the outer pipe 7 and an inner circumference of the body 3.
• FIG. 2 is a cross-sectional view illustrating the header 4, the cup 16, and the inner pipe 6 in an exploded state.
• the header 4 is formed by stacking and consecutively connecting a large cylinder portion 4a and a step portion 4c, and the step portion 4c to which is fit an outer circumference of an upper end of the body 3 is formed on an outer circumference at a lower end of the large cylinder portion 4a.
• An upper surface of the large cylinder portion 4a is formed, for example, on a flat surface that is orthogonal to the up-down direction.
• a cylindrical boss 4d that protrudes downward from the large cylinder portion 4a is formed on a lower surface of the header 4.
• the refrigerant outflow hole 9 is formed to pass through the boss 4d and through the header 4 in the up-down direction
• the refrigerant inflow hole 8 is formed to pass through the header 4 in the up-down direction adjacent to the boss 4d.
• a lower surface of the boss 4d is formed, for example, on a flat surface that is in surface contact with an upper surface of a top wall 16b of the cup 16 described below.
• a lower surface of the boss 4d is formed, for example, on a flat surface that is orthogonal to an axis of the inner pipe 6.
• the refrigerant outflow hole 9 includes a large-diameter hole 9a formed at an upper portion, and a female screw 9b formed at a lower portion. An inner diameter of the large-diameter hole 9a is formed larger than a root diameter of the female screw 9b.
• the cup 16 is formed by connecting a side wall 16a and the top wall 16b.
• a through hole 16c is formed on the top wall 16b.
• One or a plurality of ribs 16b1 are formed, for example, on an upper surface of the top wall 16b.
• the ribs 16b1 are shaped to protrude upward.
• the ribs 16b1 constitute a portion of an upper surface of the top wall.
• An area of the upper surface of the top wall 16b of the cup 16 against which a lower surface of the boss 4d of the header 4 abuts, is formed on a flat surface that comes into surface contact with the lower surface of the boss 4d.
• An area of the upper surface of the top wall 16b of the cup 16 against which the lower surface of the boss 4d of the header 4 abuts, is formed, for example, on a flat surface that is orthogonal to the axis of the inner pipe 6.
• a portion of the ribs 16b1 may be formed in an area of the upper surface of the top wall 16b of the cup 16 against which the lower surface of the boss 4d of the header 4 abuts.
• a dented portion in which a portion of the ribs 16b1 is arranged, is formed on the lower surface of the boss 4d of the header 4.
• the dented portion is shaped to allow the ribs 16b1 to be fitted thereto, for example.
• a lower surface of the top wall 16b is formed to have a flat surface that comes into surface contact with a stepped surface 6d of an inner pipe described later, for example.
• the lower surface of the top wall 16b is formed to have a flat surface orthogonal to the axis of the inner pipe, for example.
• the top wall 16b faces both the refrigerant inflow hole 8 and the refrigerant outflow hole 9. Further, the top wall 16b is a portion against which a refrigerant flowing in from the refrigerant inflow hole 8 collides. Further, the top wall 16b faces a whole area of the refrigerant inflow hole 8. The direction that the top wall 16b faces corresponds to an axial direction of the refrigerant inflow hole 8.
• a gap between the header 4 and the top wall 16b is approximately the same as a gap between the side wall 16a and an inner circumferential surface of the body 3.
• Approximately the same means that in addition to being completely the same, there may be some errors included. That is, in a state where the refrigerant flowing in through the refrigerant inflow hole 8 collides against the top wall 16b and flows downstream, it flows through the gap formed between the top wall 16b and the header 4 and through the gap formed between the inner circumferential surface of the body 3 and the side wall 16a. If these gaps are "the same", smooth flow of the refrigerant is maintained. In addition, if the errors of the gaps are small, the state in which refrigerant flows smoothly may be maintained. The errors may be a level of error that enables the flow of the refrigerant to be maintained smoothly.
• the inner pipe 6 is formed by cutting an aluminum material, for example, and it is formed by connecting a small-diameter cylinder portion, also referred to as a small-diameter tube portion, 6a inserted and fixed to the refrigerant outflow hole 9, and a large-diameter cylinder portion, also referred to as a large-diameter tube portion, 6b that has a larger diameter than the small-diameter cylinder portion 6a and that is arranged within the body 3.
• a male screw 6c is formed on an outer circumference of the small-diameter cylinder portion 6a having a smaller diameter than the through hole 16c.
• An outer diameter of the small-diameter cylinder portion 6a is smaller than an outer diameter of the large-diameter cylinder portion 6b, and thereby, the stepped surface 6d having an annular shape facing the refrigerant outflow hole 9 side is formed between the small-diameter cylinder portion 6a and the large-diameter cylinder portion 6b.
• the stepped surface 6d which is an end surface of the large-diameter cylinder portion 6b on the small-diameter cylinder portion 6a side is orthogonal to an axis L of the inner pipe 6.
• the inner pipe 6 includes a cylindrical inner circumferential surface 6e that is formed across the inner side of the small-diameter cylinder portion 6a, and a tapered inner circumferential surface 6f disposed on a lower end side that connects to the cylindrical inner circumferential surface 6e at a vicinity of the stepped surface 6d.
• the tapered inner circumferential surface 6f that reduces in diameter toward the cylindrical inner circumferential surface 6e side, that is, upper end side, may be formed to extend to the lower end of the inner pipe 6, or to extend to the vicinity of the lower end of the inner pipe 6.
• tapered inner circumferential surface 6f extends to the vicinity of the lower end of the inner pipe
• the tapered inner circumferential surface 6f and the lower end may be connected by another cylindrical inner circumferential surface.
• a taper angle ⁇ of the tapered inner circumferential surface 6f is uniform, and preferably 10 degrees or greater.
• a pressure equalizing hole 6g is formed at a vicinity of the stepped surface 6d of the inner pipe 6.
• the pressure equalizing hole 6g passes through the inner pipe 6.
• the pressure equalizing hole 6g is a hole that suppresses a liquid-phase refrigerant accumulated in the inner pipe 6 from being sucked into the compressor when the compressor is restarted after the refrigeration cycle has been stopped, that is, after the operation of the compressor has been stopped. That is, since not only the liquid phase refrigerant within the inner pipe 6 but also the gas phase refrigerant outside the inner pipe 6 are sucked into the compressor through the pressure equalizing hole 6g, the sucking of the liquid-phase refrigerant is suppressed.
• the cup 16, and the inner pipe 6, at first, a lower end of the boss 4d of the header 4 is abutted against a circumference of the through hole 16c which is the upper surface of the cup 16.
• the ribs 16b1 are formed at a position avoiding the area against which the boss 4d abuts, as an example. Therefore, according to the present embodiment, the lower end of the boss 4d is in surface contact with the flat surface potion of the upper surface of the top wall 16b.
• the inner pipe 6 is made to approach the cup 16 from the lower side. Further, the small-diameter cylinder portion 6a of the inner pipe 6 is inserted to the through hole 16c, and the male screw 6c is engaged with the female screw 9b of the header 4.
• the inner pipe 6 approaches the header 4, and the stepped surface 6d abuts against the lower surface of the cup 16 in the circumference of the through hole 16c.
• the lower surface of the top wall 16b of the cup 16 is in surface contact with the stepped surface 6d.
• the cup 16 is nipped between and fixed by the lower end of the boss 4d and the stepped surface 6d.
• a high surface flatness of the stepped surface 6d is ensured, such that even if the area of the stepped surface 6d is small, the cup 16 may be held in an appropriate orientation by the stepped surface 6d coming into surface contact with the lower surface of the cup 16.
• the outer pipe 7 and the strainer 20 are assembled to the inner pipe 6, which is disposed within the body 3 to which the bag 11 is arranged and welded with the header 4, by which the accumulator 1 is completed.
• the small-diameter cylinder portion 6a is formed to correspond to the refrigerant outflow hole 9 of the header 4
• the large-diameter cylinder portion 6b is formed to achieve a flow rate corresponding to the performance required in the accumulator 1
• the stepped surface 6d is formed to nip the cup 16 with respect to the header 4, such that the cup 16 may be fixed.
• the present embodiment enables to provide the accumulator 1 capable of holding the gas-liquid separating body and increasing the amount of refrigerant passing through while preventing the number of components from being increased.
• the inner pipe 6 is engaged to the header 4, such that caulking of the inner pipe 6 that had been conventionally performed becomes unnecessary, that is, no caulking portion is provided in the refrigerant outflow hole 9.
• caulking tools into the refrigerant outflow hole 9
• the cup 16 is attached to the header 4 by nipping the same between the stepped surface 6d formed to the inner pipe 6 and the boss 4d of the header 4, such that bulging of the inner pipe 6 becomes unnecessary. Therefore, resistance of the refrigerant flowing in the inner pipe 6 may be reduced, generation of turbulence and the like may be suppressed, and smooth flow of the refrigerant may be ensured.
• the tapered inner circumferential surface 6f is formed on the inner pipe 6, such that by gradually reducing the inner diameter toward the cylindrical inner circumferential surface 6e, which is the exist side of the refrigerant, pressure drop may be reduced, and even smoother flow of the refrigerant may be ensured.
• FIG. 1 An operation of the accumulator 1 configured as described above will be described with reference to FIG. 1 .
• the accumulator 1 is arranged between the evaporator and the compressor of the refrigeration cycle, moisture contained in the refrigerant from the evaporator is removed to generate a gas refrigerant, and the refrigerant is then returned to the compressor.
• the refrigerant When the refrigerant is discharged from the evaporator, the refrigerant is conveyed through a connection piping (not shown) to the accumulator 1.
• the refrigerant having reached the accumulator 1 flows into the body 3 through the refrigerant inflow hole 8, collides against the upper surface of the cup 16, and is separated into a liquid phase refrigerant and oil having a high density, and a gas phase refrigerant, i.e., gas refrigerant, having a low density.
• the liquid phase refrigerant and the oil after performing the gas-liquid separation are stored within the body 3 by their own weight.
• separation of the liquid phase refrigerant and the oil is advanced, and the oil is accumulated below the liquid phase refrigerant.
• a liquid surface of the liquid phase refrigerant reaches a height position where a portion of the bag 11 containing the drying agent is immersed. Therefore, the moisture contained in the liquid phase refrigerant and the moisture contained in the gas phase refrigerant are both absorbed by the drying agent DA.
• the gas phase refrigerant having been subjected to gas-liquid separation flows in through an upper end opening portion of the outer pipe 7 and descends within the outer pipe 7. Thereafter, the refrigerant is turned back at the bottom portion of the outer pipe 7, flows into the inner side of the inner pipe 6 by passing through the lower end, ascends within the inner pipe 6, and is guided to the refrigerant outflow hole 9.
• the oil accumulated together with the liquid phase refrigerant at the lower portion of the body 3 moves toward the bottom portion side of the body 3 due to the specific weight or the difference of property with respect to the liquid phase refrigerant, sucked by the gas phase refrigerant sucked into the intake side of the compressor, passed through the mesh filter 22 of the strainer 20, an oil return hole 7e, and an inner space of the inner pipe 6 in the named order, and is returned together with the gas phase refrigerant to the intake side of the compressor and circulated.
• foreign substances such as sludges are captured, by which the foreign substances are removed from the circulated refrigerant including oil.
• FIG. 3 is a vertical cross-sectional view of an accumulator 1A according to the second embodiment, wherein only a left half of a strainer is illustrated in cross section, similar to FIG. 1 .
• FIG. 4 is a vertical cross-sectional view of an inner pipe 6A according to the second embodiment.
• FIG. 5 is a cross-sectional view illustrating a lower end of the inner pipe 6A in enlarged view.
• only the inner pipe 6A differs from the first embodiment, and the other configurations are similar to the first embodiment, such that common components are denoted with the same reference numbers, and detailed descriptions thereof are omitted.
• the inner pipe 6A is formed, for example, by forging an aluminum material, and consecutively connecting a small-diameter cylinder portion 6Aa and a large-diameter cylinder portion 6Ab.
• a male screw 6Ac is formed on an outer circumference of the small-diameter cylinder portion 6Aa.
• An outer diameter of the small-diameter cylinder portion 6Aa is smaller than an outer diameter of the large-diameter cylinder portion 6Ab, and thereby, a stepped surface 6Ad is formed between the small-diameter cylinder portion 6Aa and the large-diameter cylinder portion 6Ab, with a pressure equalizing hole 6Ag1 formed at a vicinity thereof.
• the stepped surface 6Ad is orthogonal to the axis L of the inner pipe 6A.
• the inner pipe 6A includes a first cylindrical inner circumferential surface 6Ae formed on an upper end side, a tapered inner circumferential surface 6Af on the lower end side that connects to the first cylindrical inner circumferential surface 6Ae at a vicinity of the stepped surface 6Ad, and a second cylindrical inner circumferential surface 6Ag that connects to the tapered inner circumferential surface 6Af.
• a taper angle ⁇ of the tapered inner circumferential surface 6Af is uniform, and preferably 60 degrees or greater when formed by forging.
• the second cylindrical inner circumferential surface 6Ag maintains a cylindrical shape to a lower end 6Ah of the inner pipe 6A of the present embodiment, and an outer circumferential surface of the large-diameter cylinder portion 6Ab maintains a cylindrical shape.
• the lower end 6Ah is an end face orthogonal to the axis L (refer to FIG. 5 ).
• the small-diameter cylinder portion 6Aa of the inner pipe 6A is inserted to the through hole 16c, the male screw 6Ac is screw-engaged to the female screw 9b of the header 4 to realize assembly, and thereby, the cup 16 is nipped between and fixed by the lower end of the boss 4d and the stepped surface 6Ad.
• FIG. 6 is a cross-sectional view illustrating a lower end of an inner pipe 6B according to a modified example 1 in enlarged view.
• an outer circumferential surface of a large-diameter cylinder portion 6Bb has a cylindrica shape to a lower end 6Bh of the inner pipe 6B, whereas a second cylindrical inner circumferential surface 6Bg gradually expands in diameter from a vicinity of the lower end 6Bh toward the lower end 6Bh, and intersects with an outer circumferential surface of the large-diameter cylinder portion 6Bb at the lower end 6Bh.
• the second cylindrical inner circumferential surface 6Bg at the vicinity of the lower end 6Bh has an arc shape.
• the refrigerant when a gas phase refrigerant that has been subjected to gas-liquid separation is turned back at a bottom portion of the outer pipe 7 and flows through the lower end 6Bh into an inner side of the inner pipe 6B, the refrigerant is flown along the second cylindrical inner circumferential surface 6Bg that gradually expands in diameter, such that a smooth flow of refrigerant may be ensured.
• FIG. 7 is a cross-sectional view illustrating a lower end of an inner pipe 6C according to a modified example 2 in enlarged view.
• a second cylindrical inner circumferential surface 6Cg has a cylindrical shape to a lower end 6Ch of the inner pipe 6C, whereas an outer circumferential surface of a large-diameter cylinder portion 6Cb gradually reduces in diameter from a 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.
• an outer circumferential surface of the large-diameter cylinder portion 6Cb at the vicinity of the lower end 6Ch has an arc shape.
• the refrigerant when a gas phase refrigerant that has been subjected to gas-liquid separation is turned back at a bottom portion of the outer pipe 7 and flows toward the lower end 6Ch of the inner pipe 6C, the refrigerant is flown along the outer circumferential surface of the large-diameter cylinder portion 6Cb gradually reduced in diameter, such that a smooth flow of refrigerant may be ensured.
• FIG. 8 is a cross-sectional view illustrating a lower end of an inner pipe 6D according to a modified example 3 in enlarged view.
• a second cylindrical inner circumferential surface 6Dg has a cylindrical shape that gradually expands in diameter from a vicinity of a lower end 6Dh of the inner pipe 6D toward the lower end 6Dh, whereas an outer circumferential surface of a large-diameter cylinder portion 6Db gradually reduces in diameter from a vicinity of the lower end 6Dh toward the lower end 6Dh, and the second cylindrical inner circumferential surface 6Dg intersects with the outer circumferential surface of the large-diameter cylinder portion 6Db at the lower end 6Dh.
• a lower end wall of the large-diameter cylinder portion 6Db at the vicinity of the lower end 6Dh has a semi-circular shape.
• the refrigerant when a gas phase refrigerant that has been subjected to gas-liquid separation is turned back at a bottom portion of the outer pipe 7 and flows toward the lower end 6Dh of the inner pipe 6D, the refrigerant is flown along the outer circumferential surface of the large-diameter cylinder portion 6Db gradually reduced in diameter, and when the refrigerant is flown through the lower end 6Dh into the inner side of the inner pipe 6D, the refrigerant is flown along the second cylindrical inner circumferential surface 6Dg that gradually expands in diameter, such that a smooth flow of refrigerant may be ensured.
• Modified examples 1 to 3 may similarly be applied to the inner pipe 6 of the first embodiment.
• FIG. 9 is a vertical cross-sectional view of an accumulator 1F according to a third embodiment.
• the accumulator 1F according to the present embodiment has an outflow pipe 6F that is U-shaped, and it does not have an outer pipe.
• the strainer or the bag including a drying agent are not shown.
• the configurations of a header 4F and an outflow pipe 6F differ from the above-described embodiment, and the other configurations are similar to the first embodiment, such that common components are denoted with the same reference numbers, and detailed descriptions thereof are omitted.
• a refrigerant outflow hole 9F does not have a female screw, and has a large diameter hole 9Fa and a small diameter hole 9Fb.
• the other configurations are the same as those of the embodiments described above.
• the outflow pipe 6F is formed by connecting a small-diameter cylinder portion 6Fa and a large-diameter U-shaped tube portion 6Fb bent in a U-shape.
• a male screw is not formed on an outer circumferential surface 6Fc of the small-diameter cylinder portion 6Fa, and the small-diameter cylinder portion 6Fa has an outer diameter that is approximately the same as an inner diameter of the small diameter hole 9Fb.
• the outer diameter of the small-diameter cylinder portion 6Fa is formed smaller than an outer diameter of the large-diameter U-shaped tube portion 6Fb, and thereby, a stepped surface 6Fd is formed between the small-diameter cylinder portion 6Fa and the large-diameter U-shaped tube portion 6Fb.
• the outflow pipe 6F has a tapered inner circumferential surface 6Ff at a vicinity of the stepped surface 6Fd.
• the outflow pipe 6F has a pressure equalizing hole 6Fg, similar to the embodiment described above.
• the small-diameter cylinder portion 6Fa of the outflow pipe 6F is inserted to the through hole 16c, and the small-diameter cylinder portion 6Fa is fixed to the small diameter hole 9Fb of the header 4 via press-fitting, brazing or welding.
• the cup 16 is nipped between a lower end of a boss 4Fd and the stepped surface 6Fd and fixed thereto.
• the outflow pipe 6F may be moved linearly and attached to the header 4 without being rotated, such that at an assembling position illustrated in FIG. 9 , a free end of the outflow pipe 6F may be positioned within the cup 16.
• FIG. 10 is a vertical cross-sectional view of an accumulator 1G according to a fourth embodiment.
• the accumulator 1G according to the present embodiment has a shape of an outflow pipe 6G that differs from the accumulator 1F according to the third embodiment. Specifically, a bend radius of a bent portion of a large-diameter U-shaped tube portion 6Gb of the outflow pipe 6G is formed greater than a bend radius of a corresponding portion of the outflow pipe 6F of the third embodiment.
• the other configurations are similar to the embodiments described above.
• the outflow pipe 6G includes a pressure equalizing hole 6Gg similar to the embodiments described above.
• the cup 16 serves as an example of a gas-liquid separating member.
• the gas-liquid separating member faces both the refrigerant inflow hole 8 and the refrigerant outflow hole 9. Then, the gas-liquid separating member has a portion against which the refrigerant flowing in through the refrigerant inflow hole 8 collides.
• the gas-liquid separating member preferably faces the whole area of the refrigerant inflow hole 8. The facing direction is the axial direction of the refrigerant inflow hole 8.
• the gas-liquid separating member preferably includes a top wall that faces both the whole area of the refrigerant inflow hole 8 and the refrigerant outflow hole 9, and a tubular side wall that faces the inner circumferential surface of the body 3.
• the gap between the header 4 and 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, there may be some errors included. That is, in a state where the refrigerant flowing in through the refrigerant inflow hole 8 collides against the top wall and flows downstream, it flows through the gap formed between the top wall and the header 4 and through the gap formed between the inner circumferential surface of the body 3 and the side wall. If these gaps are "the same", smooth flow of the refrigerant is maintained. In addition, if the errors of the gaps are small, the state in which refrigerant flows smoothly may be maintained. The errors may be a level of error that enables the flow of the refrigerant to be maintained smoothly.
• the top wall of the gas-liquid separating member is not limited to a plate-shaped member having a constant thickness.
• the other example of the gas-liquid separating member is a configuration without a side wall.
• the header and the inner pipe are assembled by engaging screws together, but the header and the inner pipe may be fixed via press-fitting, brazing, or welding, as in the third and fourth embodiments.
• An accumulator including:
• the accumulator according to the first aspect wherein the tapered inner circumferential surface extends to an end portion of the large-diameter tube portion on an opposite side with respect to the small-diameter tube portion.
• an inner circumferential surface of the outflow pipe is configured to gradually expand in diameter from a vicinity of an end portion of the outflow pipe on a side distant from the refrigerant outflow hole toward the end portion.
• an outer circumferential surface of the outflow pipe is configured to gradually reduce in diameter from a vicinity of an end portion of the outflow pipe on a side distant from the refrigerant outflow hole toward the end portion.
• an inner circumferential surface of the outflow pipe is configured to gradually expand in diameter from a vicinity of an end portion of the outflow pipe on a side distant from the refrigerant outflow hole toward the end portion, and an outer circumferential surface of the outflow pipe is configured to gradually reduce in diameter from the vicinity of the end portion toward the end portion.

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