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WO2012026496A1 - Compresseur frigorifique équipé d'un accumulateur et d'un dispositif de cycle de réfrigération du type à compression de vapeur - Google Patents

Compresseur frigorifique équipé d'un accumulateur et d'un dispositif de cycle de réfrigération du type à compression de vapeur Download PDF

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Publication number
WO2012026496A1
WO2012026496A1 PCT/JP2011/069066 JP2011069066W WO2012026496A1 WO 2012026496 A1 WO2012026496 A1 WO 2012026496A1 JP 2011069066 W JP2011069066 W JP 2011069066W WO 2012026496 A1 WO2012026496 A1 WO 2012026496A1
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WIPO (PCT)
Prior art keywords
refrigerant
accumulator
inlet pipe
diffuser
guide
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/JP2011/069066
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English (en)
Japanese (ja)
Inventor
哲英 横山
雷人 河村
関屋　慎
利秀 幸田
佐々木　圭
白藤　好範
英明 前山
谷　真男
宏樹 長澤
勝巳 遠藤
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.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2012530691A priority Critical patent/JP5518200B2/ja
Publication of WO2012026496A1 publication Critical patent/WO2012026496A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/03—Suction accumulators with deflectors
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a refrigerant compressor provided with an accumulator, for example, and a vapor compression refrigeration cycle apparatus using the refrigerant compressor.
  • a vapor compression refrigeration cycle using a rotary compressor is used for a vapor compression refrigeration cycle such as a refrigerator-freezer, an air conditioner, or a heat pump water heater. From the viewpoint of preventing global warming, it is necessary to save energy and improve efficiency of the vapor compression refrigeration cycle.
  • the conventional accumulator disposed on the refrigerant circuit liquid side in the vapor compression refrigeration cycle is designed to store a predetermined liquid refrigerant and is designed to adjust the amount of refrigerant circulating in the refrigerant circuit.
  • the pressure loss on the refrigerant circuit liquid side is smaller than that on the refrigerant circuit gas side, and therefore no attempt has been made to reduce the pressure loss.
  • the conventional gas-liquid separator (or oil separator) used for the refrigerant circuit of a vapor compression refrigeration cycle prevents the COP fall and reliability fall which arise when liquid refrigerant (or oil) circulates in a refrigerant circuit. It is used as a means and designed to improve gas-liquid separation efficiency (or oil separation efficiency), but it is usually placed on the high-pressure side after compression with a refrigerant compressor, and the pressure loss is small at low flow rate, so the pressure No effort has been made to reduce the loss.
  • the conventional accumulator attached to the suction side of the refrigerant compressor is arranged on the upstream side of the compression mechanism to prevent the refrigerant from being sucked in a large amount and transiently sucking the refrigerant.
  • the refrigerant sucked into this accumulator is in a low-pressure, low-density gas state, is relatively fast, and the pressure loss accounts for a large proportion of the power loss, and is compressed due to underexpanded (undershoot) loss during the compression cylinder suction process. This is one of the main causes of a decrease in efficiency and a decrease in the refrigeration cycle COP.
  • An airtight container with a cylindrical body, an inlet pipe above the airtight container, and an outlet pipe below the airtight container.
  • the refrigerant flowing into the airtight container from the inlet pipe is separated into gas and liquid in the internal space of the airtight container, and then the liquid refrigerant Is stored in a sealed container and the gas refrigerant is sucked into the compression cylinder through the outlet pipe.
  • a partition plate that blocks the flow of the refrigerant flowing from the inlet pipe is provided between the inlet pipe and the outlet pipe opening, and functions to separate the liquid from the gas-liquid mixed refrigerant.
  • the cylindrical barrel-shaped sealed container internal space is divided into an upstream space and a downstream space by a partition plate and is provided with a communication port that communicates with the downstream space while avoiding the partition plate, but the refrigerant flows from the inlet pipe to the outlet pipe opening.
  • the communication port and the outlet tube opening are arranged so as not to overlap each other when viewed from directly above (usually from the inlet tube side of the cylindrical barrel-shaped accumulator).
  • Patent Document 1 shows an example of an accumulator that is attached to a two-cylinder compressor in which two compression cylinders in an airtight container are arranged in parallel on the upper side and the lower side.
  • One inlet pipe and two outlet pipes are provided.
  • One outlet pipe communicates with the first compression cylinder
  • the other outlet pipe communicates with the second compression cylinder.
  • the first compression cylinder and the second compression cylinder perform compression operations in opposite phases, and the timing of sucking the refrigerant from the inside of the accumulator sealed container is shifted by 180 °, so that the flow direction of the refrigerant fluctuates unsteadyly in the sealed container Since the loss increases, the compressor efficiency decreases due to an increase in undershoot loss.
  • the refrigerant flowing from the inlet pipe is caused to collide with the wall surface of the accumulator hermetic container by an involute bent pipe.
  • a gas-liquid separation method is disclosed. According to this gas-liquid separation method, high gas-liquid separation efficiency is obtained by the centrifugal separation effect and the wall surface adhesion effect, and the vapor compression refrigeration cycle to which this is applied can improve the efficiency and stability.
  • the diffuser is a means for recovering velocity energy to pressure energy with a small loss of fluid.
  • the spread angle 2 ⁇ is 0 to 40 degrees. Within the range, the diffuser efficiency (static pressure recovery efficiency) ⁇ is improved.
  • a resistance coefficient is disclosed in which a pressure resistance received by an object having a representative shape from a flow is made dimensionless by dynamic pressure.
  • ⁇ In the case of 3D object shape; The resistance coefficient when the convex side of the hemisphere faces upstream is 0.42, the resistance coefficient when the apex angle 60 degrees faces upstream is 0.5, and the resistance coefficient when the disc is orthogonal to the flow is 1.17. It is.
  • the resistance coefficient is 1.2 when the semicircular convex side faces upstream, the resistance coefficient when the apex angle 60 degrees faces upstream is 1.25, and the resistance coefficient when the flat plate is orthogonal to the flow is 2.3. From the above, the pressure resistance received by the flat plate portion orthogonal to the flow of the partition plate is hemispherical, or It is expected to be about twice the pressure resistance experienced by the acute angled surface.
  • the refrigerant In the accumulator attached to the compressor suction side, the refrigerant is in a low-pressure and low-density gas state, and the pressure loss is large, which greatly affects the reduction in compressor efficiency and the reduction in refrigeration cycle COP.
  • the main places where pressure loss occurs in the accumulator are shown below. (1) A suddenly expanding flow occurs at the inlet flowing into the upstream space from the inlet pipe, and the refrigerant flow is separated from the inner wall of the sealed container, resulting in a pressure loss. (2) When the refrigerant passes through the communication port from the upstream space to the downstream space partitioned by the partition plate, pressure loss occurs due to the collision flow to the partition plate, the distribution flow to the communication port, the bending flow, the contraction flow, and the expansion flow Occurs.
  • the accumulator sealed container is a high-pressure container, and the upper end plate has a hemispherical shape or a dish shape.
  • the angle formed by the upper end plate inner wall portion of the accumulator sealed container and the axial direction is large (approximately 180 degrees). It is a problem that the pressure loss is large by peeling away from the part immediately and creating a large peeling vortex.
  • a partition plate in which a large number of round hole-shaped communication ports are formed in a disk orthogonal to the axial flow is provided. Is positioned so as not to overlap the outlet pipe opening when viewed from directly above, preventing the risk of liquid refrigerant entering directly and damaging the compression cylinder. Further, the refrigerant of the partition plate collides at a right angle, and also functions as a gas-liquid separation. However, the ratio of the area where the refrigerant flowing from the inlet pipe collides with the partition plate at a right angle is large.
  • Patent Document 2 since the opening of the outlet pipe is arranged in the umbrella, the gas refrigerant colliding with the inner wall of the sealed container flows backward and then flows into the opening of the outlet pipe. The problem is that the structure is easily lost and the pressure loss is large.
  • the shape near the inlet of the upper end plate connected to the inlet pipe into which the refrigerant flows is a trumpet conical diffuser, and the spread angle (2 ⁇ ) near the inlet is sufficient. Since it can be read as small (within about 40 degrees from the figure), it flows into the sealed container with almost no peeling.
  • the refrigerant flows into the opening of the outlet pipe after gas-liquid separation by the partition plate (baffle) on the downstream side. Therefore, the flow in the rectified state that does not separate while passing near the diffuser-shaped inlet pipe is abruptly disturbed by the partition plate (baffle) on the downstream side, and it is predicted that the diffuser effect in the first half is greatly impaired.
  • the detailed structure of the accumulator is unknown, and the pressure loss reduction effect is not particularly mentioned.
  • the present invention pays particular attention to the pressure loss improvement methods (1) and (2) above, and the present invention reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator attached to the refrigerant compressor. The goal is to improve efficiency.
  • the refrigerant compressor to which the accumulator of this invention is attached is In the refrigerant compressor with an accumulator,
  • the accumulator is A cylindrical sealed container having an internal space;
  • An inlet pipe connected to the sealed container and for allowing the refrigerant to flow in an axial direction straight from the opening of the end portion into the internal space of the sealed container;
  • An outlet pipe connected to the sealed container and sucking the refrigerant in the inner space of the sealed container from the opening of the end and sending it out to the compression cylinder;
  • a diffuser-type flow path that is disposed in the internal space and gradually expands in cross-section as the axial direction in which the refrigerant flows from the opening of the inlet pipe toward the downstream side from a position near the opening of the inlet pipe.
  • an inlet pipe flow guide for flowing out the refrigerant flowing in from the opening of the inlet pipe through the diffuser type flow path, On the downstream side of the diffuser-shaped flow path, on a straight line connecting the opening of the inlet pipe and the outlet pipe, the flow path space is arranged on the upstream side in the axial direction from the opening of the outlet pipe, A partition plate having an inclined surface and a top that block the flow in the inflow direction; A communication port disposed upstream of the opening of the outlet pipe in the axial direction, bypassing the partition plate and communicating from the inlet pipe to the opening of the outlet pipe;
  • the accumulator is The inlet pipe flow guide and the partition plate guide the flow of the refrigerant flowing from the inlet pipe to the communication port and prevent liquid from flowing into the opening of the outlet pipe.
  • FIG. 3 is a longitudinal sectional view of “a refrigerant compressor with an accumulator” according to the first embodiment. The figure which looked directly under the AA cross section showing the 1st guide of the accumulator of FIG. 1 which concerns on Embodiment 1.
  • FIG. FIG. 6 is a longitudinal sectional view of “an accumulator attached to a refrigerant compressor” according to a second embodiment. The figure which looked directly under the AA cross section showing the 1st guide of the accumulator of FIG. 3 which concerns on Embodiment 2.
  • FIG. FIG. 6 is a longitudinal sectional view of “an accumulator attached to a refrigerant compressor” according to a third embodiment.
  • FIG. 6 is a view of the first accumulator of FIG.
  • FIG. 6 is a longitudinal sectional view of “an accumulator attached to a refrigerant compressor” according to a fourth embodiment.
  • FIG. 10 is a diagram of the first view of the accumulator of FIG. 7 according to the fourth embodiment when viewed directly from the AA cross section.
  • FIG. 10 is a longitudinal sectional view of “an accumulator attached to a refrigerant compressor” according to a fifth embodiment.
  • FIG. 10 is a view of the first accumulator of FIG. 9 according to the fifth embodiment as viewed from the AA cross section representing the first guide.
  • FIG. 12 is a diagram of the first view of the accumulator of FIG. 11 according to the sixth embodiment as viewed directly from the AA cross section. The figure which looked directly under the AA cross section showing the curved flow guide of "the accumulator attached to a refrigerant compressor” of FIG. 1 which concerns on Embodiment 7 (except a 1st guide).
  • FIG. 10 is a longitudinal sectional view of an “accumulator attached to a refrigerant compressor” according to an eighth embodiment (upstream from the discharge pipe).
  • FIG. 18 is a diagram of the first view of the accumulator of FIG.
  • FIG. 10 is a perspective view of a bending flow guide according to an eighth embodiment.
  • FIG. FIG. 18 is a view seen directly from the AA cross-sectional view showing the first guide of the accumulator of FIG. 17 according to the ninth embodiment.
  • FIG. 18 is a diagram (except for the first guide) seen directly from the AA cross section showing the bending flow guide of the accumulator of FIG. 17 according to the ninth embodiment.
  • FIG. 18 is a view (excluding the first guide) seen directly from the AA cross-section representing the bending flow guide of “accumulator attached to the refrigerant compressor” of FIG. 1 according to the tenth embodiment.
  • FIG. 19 is a longitudinal sectional view of an “accumulator attached to a refrigerant compressor” according to a twelfth embodiment (upstream from the discharge pipe).
  • FIG. 22 is a view seen directly from the AA cross section showing the bending flow guide of the accumulator of FIG. 22 according to the twelfth embodiment (except for the first guide).
  • FIG. 19 is a longitudinal sectional view showing a configuration of “a refrigerant compressor with an accumulator” according to a thirteenth embodiment.
  • FIG. 19 is a longitudinal sectional view of “an accumulator attached to a refrigerant compressor” according to a fourteenth embodiment.
  • FIG. 28 is an AA transverse cross-sectional view of the accumulator of FIG. 27 according to the fourteenth embodiment.
  • FIG. 17 is a longitudinal sectional view showing a configuration of “an accumulator attached to a refrigerant compressor” according to a fifteenth embodiment.
  • FIG. 30 is a view of the AA cross section of the accumulator of FIG. 29 according to the fifteenth embodiment when viewed from directly above (except for the accumulator sealed container 11).
  • FIG. 18 is a configuration diagram of a vapor compression refrigeration cycle 70 according to a sixteenth embodiment.
  • the longitudinal cross-sectional view which shows the structure of the inlet_port
  • Embodiments 1 to 16 will be described with reference to the drawings.
  • an accumulator attached to the refrigerant compressor will be described.
  • a two-cylinder compressor which is a refrigerant compressor having two upper and lower compression cylinders, a first compression cylinder and a second compression cylinder
  • an accumulator In the thirteenth to fifteenth embodiments, the case where a single cylinder compressor, which is a refrigerant compressor, is provided with an accumulator will be described.
  • a vapor compression refrigeration cycle will be described. In the figure, the refrigerant flow is indicated by a double arrow, and the refrigerant tributary flow is indicated by a dotted arrow.
  • FIG. 1 is a longitudinal sectional view showing a configuration of “a refrigerant compressor provided with an accumulator 10” according to the first embodiment.
  • FIG. 2 is a view of the AA cross section of the accumulator 10 of FIG.
  • FIG. 1 is a CC longitudinal sectional view of FIG.
  • the accumulator 10 is attached outside the compressor hermetic container 2 of the two-cylinder compressor 1.
  • the accumulator sealed container 11 gas-liquid separates the gas-liquid two-layer refrigerant and temporarily stores the liquid refrigerant. It has the function of storing automatically.
  • Two rotary compression cylinders, a first compression cylinder 3 and a second compression cylinder 4, are arranged vertically below the inside of the compressor sealed container 2 of the two-cylinder compressor 1.
  • the accumulator sealed container 11 is a pressure-resistant container configured by welding a cylindrical body 11b, an upper end plate 11a, and a lower end plate 11c, which are axial objects with respect to the central axis 9.
  • the upper end plate 11a is provided with an inlet pipe 12 through which refrigerant flows into the accumulator internal space 20, and the lower end panel 11c has a first outlet pipe 13 through which refrigerant flows out from the accumulator internal space 20 to the first compression cylinder 3, and a second A second outlet pipe 14 through which the refrigerant flows out to the compression cylinder 4 is attached.
  • tube 14 is arrange
  • the openings 13a and 14a of the outlet pipe are main flow paths that are sucked into the compression cylinder, and exclude small holes such as an oil hole provided near the bottom of the accumulator sealed container 11.
  • the upper end plate 11a has a hemispherical dish shape, and the upper end plate 11a having a hole in the center shaft 9 is bent inward to form a cylindrical hole whose inner diameter is + tolerance from the outer diameter of the inlet tube 12. Weld through the inlet tube 12.
  • the diffuser type flow path (40-1), first guide 41) On the downstream side of the inlet pipe 12 having a circular channel cross section, a diffuser type channel (40-1) and a first guide 41 constituting the outer periphery of the diffuser type channel 40-1 are provided.
  • the first guide 41 is determined so that the position of the starting point and the cross-sectional shape coincide with the opening 12 a of the inlet pipe 12.
  • the first guide 41 has a conical diffuser shape in which a circular channel cross-section gradually spreads at an angle (2 ⁇ ) along the direction of the central axis 9 straight from the inlet pipe 12 into which the refrigerant flows.
  • the diffuser type flow path (40-1) in FIG. 1 has a rotating body shape having a straight line in the refrigerant inflow direction 335c as a rotation axis, and is constant because it spreads linearly. Therefore, since it is sufficiently small (here, about 20 degrees), it is predicted that the refrigerant in the diffuser type flow path (40-1) flows with almost no separation.
  • the spread angle (2 ⁇ ) is at most 40 degrees or less.
  • the first guide 41 is a non-pressure-resistant member disposed inside the accumulator sealed container 11.
  • the shape of the upper end plate 11a is processed to form a diffuser-type flow path, but the upper end plate 11a is naturally a pressure-resistant member and not a non-pressure-resistant member.
  • the inlet pipe 12 is disposed on the upper end plate 11a.
  • the inlet pipe 12 flows the refrigerant in the axial direction (here, coincides with the central axis 9) toward the lower side of the accumulator sealed container 11 (inflow direction 335c), but the diffuser channel (40-1) has a starting end (
  • the diameter of the cross section of the flow path of the inlet pipe opening 12a is D1
  • the pressure loss in the diffuser type flow path (40-1) can be reduced when L1 / D1 is larger than a certain value.
  • L1 / D1 should be at least about 2 to 3.
  • the curved flow guide (second guide) 31 (partition section, mountain-shaped flow guide) is an opening of the outlet pipe from the inlet pipe 12 to the downstream side of the diffuser-shaped flow path (40-1) inside the accumulator sealed container 11. It arrange
  • the second guide 31 has a rectangular rectangular shape with respect to the central axis 9, and as shown in FIGS. 1 and 2, four slopes 31a, 31b, 31c, 31d having a triangular inclination angle ⁇ and a rectangular bottom face.
  • the convex part vertex 321 formed by overlapping two slopes and overlapping four ridge lines 311 faces the upstream side of the central axis.
  • the second guide 31 distributes the flow in the axial direction into four axial directions (distribution in the direction below the four inclined surfaces), so that the momentum of the refrigerant is not easily lost. Furthermore, the angle 2 ⁇ formed by the slopes facing each other in the vicinity of the convex vertex 321 is about 120 degrees, and the momentum is less likely to be lost compared to a flat plate.
  • the second guide 31 is welded to the cylindrical body 11 b of the accumulator sealed container 11. Specifically, the four corners of the square bottom surface of the second guide 31 are welded and fixed to the guide mounting flange 29 by welding portions 331.
  • the first guide 41 is welded and fixed to the second guide 31 by making cuts 351 at four locations that overlap the ridgeline 311 of the second guide 31 at the end portion.
  • the bending flow guide 31 has a mountain shape and is arranged so that the top side faces the opening 12 a of the inlet pipe 12. Further, the curved flow guide 31 has a shape that is substantially symmetrical with respect to the front side and the other side of the specific surface by a specific surface including a straight line in the refrigerant inflow direction 335c. Further, as shown in FIG. 2, the bending flow guide 31 covers the openings 13a and 14a of the outlet pipe when the top is viewed from the opening 12a side of the inlet pipe 12.
  • Communication ports 301a, 301b, 301c, 301d Communication ports 301a, 301b, 301c, 301d
  • communication ports 301 a, 301 b, 301 c, and 301 d that connect the upstream space 21 and the downstream space 22 are formed between the bottom four sides of the rectangular pan and the guide mounting flange 29.
  • These communication ports 301a to 301d are arranged on the extensions that slide down in the radial direction of the inclined surfaces 31a, 31b, 31c, and 31d.
  • These communication ports 301a to 301d are flow paths that bypass and pass the second guide 31 that blocks the flow of the refrigerant in the axial direction from the inlet pipe 12 toward the openings 13a and 14a of the outlet pipe.
  • the first outlet pipe 13 and the second outlet pipe 14 are connected to the accumulator sealed container 11 and allow the refrigerant to flow out of the accumulator sealed container 11.
  • the refrigerant outlets (openings) 13a and 14a of the first outlet pipe 13 and the second outlet pipe 14 are located in the downstream space 22 below the second guide 31 with respect to the central axis 9, and the communication ports 301a and 301b, It arrange
  • the two outlet pipes of the first outlet pipe 13 and the second outlet pipe 14 are arranged such that the respective refrigerant outlets are arranged side by side when viewed from above the accumulator sealed container 11 as shown in FIG. The state is almost hidden from 31.
  • FIG. 1 and FIG. 2 the flow of the refrigerant in the accumulator 10 will be described.
  • the flow of the refrigerant is indicated by double line arrows.
  • the refrigerant that has flowed into the upstream space 21 from the inlet pipe 12 in the direction of the central axis 9 is first flowed by the first guide 41 having an axial length L2 and a diffuser shape.
  • the cross-sectional inner diameter gradually increases in the radial direction from D1 to D2, and advances in the axial direction.
  • the diffuser-type flow path (40-1) in FIG. 1 is a conical diffuser that linearly spreads, and the spread angle 2 ⁇ is constant and coincides with the average spread angle 2 ⁇ m.
  • the effect of the diffuser can be obtained when the divergence angle 2 ⁇ is greater than 0 ° and not more than 40 °. In particular, it is better to make the divergence angle (2 ⁇ 1) at the start end sufficiently small.
  • the refrigerant collides with the vicinity of the convex vertex 321 (in the circular region with the radius D2 / 2) of the square guide-shaped second guide 31 that blocks the axial flow. Then, the refrigerant is changed from the direction of the central axis 9 to the four directions parallel to the inclined surfaces 31a, 31b, 31c, 31d having an inclination angle ⁇ with respect to the central axis 9, and spreads in the radial direction. It flows toward the four communication ports 301a, 301b, 301c, 301d on the top.
  • the liquid refrigerant contained in the suction refrigerant hits the wall surface, and the liquid refrigerant adheres to the wall surface and falls.
  • the gas refrigerant is sucked into the outlet pipes 13 and 14 while changing the flow direction toward the openings 13a and 14a of the outlet pipes. Thereby, the gas-liquid separation function required for the accumulator is ensured.
  • the starting position and the cross-sectional shape of the first guide 41 are determined so as to coincide with the opening 12 a of the inlet pipe 12. Further, as described above, the conical diffuser type channel (40-1) having a spread angle 2 ⁇ of 40 degrees or less was used. For this reason, the pressure loss generated when the refrigerant flows into the accumulator sealed container 11 from the inlet pipe 12 can be reduced. Further, in the “accumulator 10 attached to the refrigerant compressor” shown in FIG. 1 of the first embodiment, the flow direction is gradually changed from the axial direction to the radial direction by the second guide 31 and gas-liquid separation is performed.
  • the refrigerant outlets (openings) 13a and 14a of the first outlet pipe 13 and the second outlet pipe 14 are hidden by the second guide 31 when viewed from above, but are arranged at a distance below the second guide 31.
  • the accumulator in the “refrigerant compressor with an accumulator” according to Embodiment 1 includes the first guide 41 and the curved flow path 30-1 that constitute the diffuser-type flow path (40-1).
  • the four communication ports 301a, 301b, 301c, and 301d are formed on the radial extension of the slope that constitutes the second guide 31. For this reason, it is possible to reduce the pressure loss generated when the refrigerant flows into the compressor sealed container 2 from the inlet pipe 12 and the pressure loss generated during the gas-liquid separation while maintaining the gas-liquid separation function.
  • the two-cylinder compressor provided with the accumulator 10 according to the first embodiment it is possible to reduce the pressure loss and improve the compressor efficiency while maintaining the gas-liquid separation function of the accumulator.
  • FIG. 3 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 4) of the accumulator 10 according to the second embodiment.
  • 4 is a cross-sectional view taken along line AA of FIG. 3 showing the first guide 42 of the “accumulator 10 attached to the refrigerant compressor” according to the second embodiment.
  • the second embodiment is different from the first embodiment in that the first guide has a rear half portion that spreads in a trumpet shape. Only differences from the first embodiment will be described.
  • the first half portion 42a of the first guide 42 of the first embodiment has a diffuser-type flow path (in which the flow path cross-sectional inner diameter extends from D1 to D2 at a gentle angle (here, 2 ⁇ is approximately 20 degrees), as in the first embodiment. 40-2).
  • the extended second half portion 42b of the first guide 42 having the length L3 has a spread angle 2 ⁇ that increases abruptly (in this case from 40 degrees to 180 degrees), and the outer peripheral portion that spreads in a trumpet shape is a cylinder of the accumulator sealed container. A shape reaching the vicinity of the inner wall 411 of the body 11b is formed.
  • tubular first guide rear part 42b that spreads in a trumpet shape, four-direction curved flow paths (30-2) are formed between the inclined surfaces 31a, 31b, 31c, and 31d of the second guide 31 that are spread in the shape of a rectangular cone inside. ) Is formed, and a flow path that distributes four substantially symmetrically by a specific surface including the straight central axis 9 into which the refrigerant flows from the opening of the inlet pipe is configured so as not to impair the momentum in the axial direction.
  • the flow can be expanded in four directions.
  • the cross-sectional area obtained by cutting the four distributed curved flow paths (30-2) by a cross section perpendicular to the axial direction is the cross-sectional area ( ⁇ / 4 ⁇ D2) of the diffuser flow path outlet of the front half 42a of the first guide 42. Since it spreads in the radial direction while gradually changing from the square of (2), it can be guided to the communication port 301 so that the flow does not peel off. Compared with the curved flow path (30-1) in which the upper part of the first embodiment is opened, the momentum is less likely to be lost and the pressure loss is small. Further, as shown in FIG. 4, the first guide 42 is fixed by welding the terminal portion to the guide mounting flange 29, and four cuts 342 are made in the overlapping portion of the ridgeline 311 of the square guide of the second guide. It is good to fix to.
  • the pressure loss is reduced while maintaining the gas-liquid separation function of the accumulator. It is possible to improve the compressor efficiency.
  • FIG. 5 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 6) of the “accumulator 10 attached to the refrigerant compressor” according to the third embodiment.
  • 6 is a cross-sectional view taken along the line AA in FIG. 5 showing the first guide 42 of the accumulator 10 according to the third embodiment.
  • the third embodiment is different from the second embodiment in that the guide mounting flanges of the first guide 42 and the second guide 31 are provided. Only differences from the second embodiment will be described.
  • the height of the guide mounting flange 29a for fixing the first guide 42 by welding is different from the height of the guide mounting flange 29b for fixing the second guide 31 by welding. Accordingly, the first guide 42 can be disposed so as not to overlap the ridgeline 311 of the second guide 31 at the end portion. Therefore, the notch 351 is not necessary, and the first guide 42 has a trumpet shape extending to the end portion. Further, the ridgeline 311 of the second guide 31 is a straight line, and the first guide rear half 42b is a curve.
  • the ridgeline 311 of the 2nd guide 31 and the 1st guide latter half part 42b become a positional relationship which contact
  • the angle ⁇ at which the refrigerant after passing through the communication port 301 collides with the closed container wall surface is defined as an angle formed by the extending direction down the inclined surface and the downward direction of the closed container wall surface, the inclination angle is obtained when the inclined surface is a plane.
  • ⁇ is approximately equal to ⁇ and ⁇ is about 45 degrees, which is an angle suitable for achieving both gas-liquid separation efficiency improvement and pressure loss reduction. Furthermore, the angle 2 ⁇ formed by the slopes facing each other in the vicinity of the convex vertex 321 is about 90 degrees, and the pressure loss can be reduced to about half that of the flat plate.
  • the pressure loss is reduced while maintaining the gas-liquid separation function of the accumulator, or more than that of the first embodiment. The effect of improving the efficiency is obtained.
  • FIG. 7 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 8) of “accumulator 10 attached to refrigerant compressor” according to the fourth embodiment.
  • 8 is a cross-sectional view taken along line AA of FIG. 7 showing the first guide 42 of the accumulator 10 of FIG. 7 according to the fourth embodiment.
  • the fourth embodiment is different from the second embodiment in the shape of the second guide. Only differences from the second embodiment will be described.
  • the inclined surface of the rectangular pancreas constituting the second guide 31 is a flat triangle, whereas in the fourth embodiment, the inclined surfaces 32a, 32b, 32c of the second guide 32 are provided.
  • 32d is a curved surface.
  • the four inclined surfaces 32a, 32b, 32c, and 32d have a small inclination angle ⁇ with respect to the central axis 9 of the inclined surface near the convex vertex 322 (about 30 degrees), but a large inclination angle ⁇ near the end of the inclined surface (about 60 degrees). ) Being. As shown in FIG.
  • the slope of the second guide 31 has a curved surface that is recessed with respect to the refrigerant inflow direction 335c.
  • the curved flow path (30-4) configured by being sandwiched between the second guide 32 and the first guide rear portion 42b smoothly converts the flow of the refrigerant from the axial direction to the radial direction.
  • the curved flow path (30-4) has approximately four communication ports 301a, 301b, 301c, 301d.
  • the flow path is divided into four parts for guiding the refrigerant.
  • the refrigerant flows through the curved flow path (30-4) and then collides with the inner wall 411 of the cylindrical body 11b of the accumulator sealed container 11.
  • the collision angle ⁇ is substantially equal to the inclination angle ⁇ near the end of the slope.
  • the inclination angle ⁇ near the end of the inclined surface is about 60 degrees.
  • the tubular first guide rear part 42b that spreads in a trumpet shape and the slopes 32a, 32b, 32c, and 32d of the second guide 32 that spreads in the shape of a square cone inside the tube are distances.
  • the cross-sectional area of the flow path cut by the cross section perpendicular to the axial direction is the front half portion 42a of the first guide 42.
  • the cross-sectional area ( ⁇ / 4 ⁇ D2 squared) of the diffuser flow path of the diffuser gradually spreads in four directions that are uniform with respect to the central axis 9, so that the flow does not impair the axial momentum.
  • the communication port 301 can be guided so as not to peel off.
  • the fourth embodiment in which the slopes 32a, 32b, 32c, and 32d of the second guide are formed with curves is more smooth than the curved flow path (30-4) of the second and third embodiments. Can be converted from the axial direction to the radial direction, so the momentum is not easily lost.
  • the pressure loss is reduced while maintaining the gas-liquid separation function of the accumulator, as well as or equal to the first embodiment. It is possible to improve the compressor efficiency.
  • FIG. 9 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 10) of “accumulator 10 attached to the refrigerant compressor” according to the fifth embodiment.
  • FIG. 10 is a cross-sectional view taken along line AA in FIG. 9 showing the first guide 43 of the accumulator 10 in FIG. 9 according to the fifth embodiment.
  • the fifth embodiment is different from the fourth embodiment in the shape of the first guide. Only differences from the fourth embodiment will be described.
  • the first guide 43 has substantially the same shape as the first guide 42 of the fourth embodiment, but has a later-described diffuser blowout port 48a (suction port), diffuser blowout hole 48b (suction port), and diffuser suction hole 49. The point is different.
  • the accumulator 10 of the fifth embodiment shown in FIG. 9 there is a gap between the start end of the first guide first half 43a constituting the conical diffuser type flow path (40-5) and the opening 12a of the inlet pipe 12.
  • eight small round holes are provided radially on the circumference that transitions from the first guide first half 43a to the first guide second half 43b to form the diffuser blowout holes 48b.
  • the flow resistance of the tributary 345 is greater than the flow resistance generated in the curved flow path (30-5). It is possible if it is small.
  • each of the diffuser suction hole 49, the diffuser blowout port 48a, the diffuser blowout hole 48b, and the curved flow path (30-5) The fluid resistance can be adjusted by the flow area of each part.
  • the pressure loss can be reduced and the compressor efficiency can be improved while maintaining the gas-liquid separation function of the accumulator. Is possible.
  • FIG. 11 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 12) of the upstream space 21 of the “accumulator 10 attached to the refrigerant compressor” according to the sixth embodiment.
  • 12 is a cross-sectional view taken along line AA of FIG. 11 showing the first guide 44 of the accumulator 10 of FIG. 11 according to the sixth embodiment. Only differences from the fifth embodiment will be described.
  • the diffuser suction hole 49 is provided in the vicinity of the outlet of the curved flow path (30-6), so that the four sides of the circular end portion of the first guide rear half portion 44b are cut off.
  • the third guide 81 is reduced to the first guide 44.
  • the accumulator sealed container 11 The third guide 81 is formed integrally with the first guide 44, and the first guide 44 itself has the same shape as the first guide 43 except that the end portion is cut off.
  • the pressure loss is reduced while maintaining the gas-liquid separation function, and compression is performed. It is possible to improve the efficiency.
  • FIG. 13 is a view of the second guide 33 of the “accumulator 10 attached to the refrigerant compressor” according to the seventh embodiment viewed from directly above. Only differences from the first to sixth embodiments will be described.
  • the shape of the second guide 33 is the same as that of the first to sixth embodiments, but the horizontal posture is different.
  • the slope 31a and the slope 31b of the second guide 31 are arranged on the CC cross section where the openings 13a and 14a of the outlet pipe are arranged.
  • the ridge line 313 of the second guide 33 is disposed on the CC cross section where the openings 13a and 14a of the outlet pipe are disposed. That is, the second guide 31 according to the first embodiment is different in that the second guide 31 is arranged in a posture that is rotated 45 degrees clockwise with respect to the central axis 9.
  • the second guide 33 may be the second guide 32 having a flat slope, or the second guide 32 having a curvature on the slope.
  • the second guide 33 is formed by rotating them.
  • the “two-cylinder compressor provided with the accumulator 10” according to the seventh embodiment has almost the same effect as the second guide of the first to sixth embodiments, and maintains the gas-liquid separation function of the accumulator while maintaining the pressure loss. To improve compressor efficiency.
  • FIG. Embodiment 8 will be described with reference to FIGS. 14, 15, and 16.
  • FIG. FIG. 14 is a longitudinal sectional view of the upstream space 21 of the “accumulator 10 attached to the refrigerant compressor” according to the eighth embodiment.
  • FIG. 15 is a cross-sectional view taken along line AA showing the first guide 44 of the accumulator 10 of FIG. 14 according to the eighth embodiment.
  • FIG. 16 is a perspective view of the second guide 34 according to the eighth embodiment.
  • the eighth embodiment is similar to the sixth embodiment, and the second guide is different from the sixth embodiment. Only differences from the sixth embodiment will be described.
  • the shape of the second guide is a square conical shape.
  • the second guide 34 according to the eighth embodiment has a bifurcated shape in which a ridge line 314 where the two inclined surfaces 34a and 34b intersect each other is formed as a convex vertex 324 and faces the upstream side of the flow.
  • the two inclined surfaces 34a and 34b may be flat, or may have a curvature that protrudes in the lower direction of the sealed container, like the inclined surface of the second guide 32.
  • the second guide 34 is welded to the lower surface side of the guide mounting flange 29 fixed to the cylindrical body 11b of the sealed container, and the gap is formed as communication ports 304a and 304b.
  • Reference numeral 334 in FIG. 16 denotes a welded portion.
  • the refrigerant flowing in from the inlet pipe 12 passes through the diffuser channel (40-4) formed by the first guide first half 44a, and then passes through the two communication ports 304a through the curved channel 30-8 formed by the two-shaped second guide. Are distributed and guided to the communication port 304b.
  • the communication ports 304a and 304b are arranged on the CC cross section where the openings 13a and 14a of the outlet pipe are arranged, and after passing through the communication ports 304a and 304b, the refrigerant passes through the openings 13a and 14a of the outlet pipe.
  • the flow resistance is small because it leads in the direction of placement.
  • the two-cylinder compressor provided with the accumulator 10 according to the eighth embodiment has the same effect as the second guide of the sixth embodiment, reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator, It is possible to improve the compressor efficiency.
  • FIG. 17 is a longitudinal sectional view (CC longitudinal sectional view of FIG. 18) of the upstream space 21 of the “accumulator 10 attached to the refrigerant compressor” according to the ninth embodiment.
  • 18 is a cross-sectional view taken along line AA of FIG. 17 showing the first guide 45 of the accumulator 10 of FIG. 17 according to the ninth embodiment.
  • FIG. 19 shows the second guide according to the ninth embodiment as viewed from directly above. The points different from the fifth to eighth embodiments and the insufficient description will be additionally described.
  • the shape of the first guide 45 of the ninth embodiment is basically the same as that of the first guide 44 of the fifth to eighth embodiments.
  • the diffuser-shaped first guide 45 spreads in a trumpet shape along the axial direction, and the spread angle 2 ⁇ of the diffuser-shaped channel (40-9) gradually increases.
  • the spread angle 2 ⁇ is about 0 to 5 degrees at the start end. If it is designed to be 40 degrees or less at the end (position from L2 to L3), the effect of reducing the pressure loss by the diffuser can be obtained.
  • the diffuser-type flow path (40-1) in FIG. 1 is a conical diffuser that linearly spreads, and the spread angle 2 ⁇ is constant and coincides with the average spread angle 2 ⁇ m.
  • the effect of the diffuser can be obtained when the divergence angle 2 ⁇ is greater than 0 ° and not more than 40 °. In particular, it is better to make the divergence angle (2 ⁇ 1) at the start end sufficiently small.
  • the difference is that the inlet pipe diffuser outlet 48a is composed of eight radial round holes.
  • the second guide 35 of the ninth embodiment is characterized in that it has a conical shape. However, here, the tip of the convex portion of the second guide 35 is processed into a rounded spherical shape.
  • the second guide mountain flow guide
  • the conical second guide 35 is welded and fixed to the cross fixing band 337, and this is fixed to the accumulator sealed container 11 by welding with a guide mounting flange.
  • 334 is a welded portion between the cross fixing band 337 and the guide mounting flange 29
  • 336 is a welded portion between the second guide 35 and the cross fixing band 337.
  • the third guide 82 disposed between the first guide 45 and the accumulator airtight container 11 is completely partitioned so that the tributary 347 sucked from the diffuser blowing port 48a and the diffuser blowing hole 48b and sucked from the diffuser suction hole 49 can be obtained.
  • the flow is made smooth to reduce the flow resistance.
  • the refrigerant compressor provided with the accumulator 10 according to the ninth embodiment has the same effects as the fifth to eighth embodiments, reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator, and improves the compressor efficiency. It is possible to improve.
  • FIG. 20 shows a second guide of “accumulator 10 attached to the refrigerant compressor” according to the tenth embodiment, viewed from directly above. Only differences from the ninth embodiment will be described.
  • the second guide 36 of the tenth embodiment is characterized in that it has an elliptical cone shape.
  • the bottom surface of the elliptical cone-shaped second guide 36 on the long axis side is fixed to the guide mounting flange 29, and the guide mounting flange 29 is fixed to the accumulator sealed container 11 by welding.
  • the second guide 36 has a slope 36 a and a convex vertex 326.
  • Two communication ports 306a and 306b are formed between the second guide 36 and the cylindrical body 11b, and the refrigerant is guided from the upstream space to the outlet pipe openings 13a and 14a.
  • the refrigerant compressor provided with the accumulator 10 according to the tenth embodiment has the same effect as the fifth to ninth embodiments, and reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator. It is possible to improve the compressor efficiency.
  • FIG. 21 is a view of the second guide 37 of the “accumulator 10 attached to the refrigerant compressor” according to the eleventh embodiment as viewed from directly above. Only differences from the ninth embodiment will be described.
  • the second guide 37 of the eleventh embodiment is characterized by a triangular pyramid shape.
  • the second guide 37 has slopes 37a, 37b, 37c, a convex vertex 327, and three ridge lines.
  • Three apex portions of the bottom surface of the triangular pyramid-shaped second guide 37 are fixed to the guide mounting flange 29, and the guide mounting flange 29 is fixed to the accumulator sealed container 11 by welding.
  • Three communication ports 307a, 307b, and 307c are formed between the second guide 37 and the cylindrical body 11b, and the refrigerant is guided from the upstream space 21 to the outlet pipe openings 13a and 14a.
  • the refrigerant compressor provided with the accumulator 10 according to the eleventh embodiment has the same effect as the fifth to ninth embodiments, and reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator. It is possible to improve the compressor efficiency.
  • the second bend guide (second guide) of the accumulator 10 has the shape of an axis that combines slopes made of solid plates.
  • the effects similar to those of the first to eleventh embodiments can also be obtained when a curved guide shape is manufactured by combining slopes made of wire mesh.
  • the structure of the second bend guide (second guide) of the accumulator 10 is an axial target shape combining the same slope shape and material.
  • a structure example of a bending guide (second guide) having a shape of an axis that combines a plurality of slope shapes and materials will be described.
  • FIG. 22 is a longitudinal sectional view (upstream from the discharge pipe) of “accumulator 10 attached to refrigerant compressor” according to Embodiment 12.
  • FIG. 23 shows a view (excluding the first guide) as seen directly from the AA cross section representing the bending flow guide of the accumulator 10 of FIG. 22 according to the twelfth embodiment. Since the structure of the bending flow guide (second guide) 38 is different from that of the above-described second embodiment, the twelfth embodiment will be mainly described. As the first guide, the same first guide 42 as in the second embodiment is used.
  • FIG. 22 is a longitudinal sectional view (upstream from the discharge pipe) of “accumulator 10 attached to refrigerant compressor” according to Embodiment 12.
  • FIG. 23 shows a view (excluding the first guide) as seen directly from the AA cross section representing the bending flow guide of the accumulator 10 of FIG. 22 according to the twelfth embodiment. Since the structure of the bending flow guide (second guide) 38 is different from that
  • ASHRAE-T condition is “ASHRAE Standard 23-1993, Methods of Testing for Rating Positive Displacement Compressor Compressors and Condensing Units” (AS93).
  • a flat disk is recessed by pressing at three locations to form three inclined surfaces 38a, 38b, 38c and communication ports 308a, 308b, 308c adjacent to these inclined surfaces.
  • the ratio of the inclined surface of the second guide 38 and the communication port to the disk is very large. Therefore, after cutting out the outer peripheral arcs of the three communication ports from the disk, the three inclined surfaces 38a, 38b, and 38c are formed by deforming the three locations by press working.
  • the center of the disk is protruded to the hemispherical protrusion 88 to form a protrusion vertex 328.
  • the non-deformed portion remains as a flat portion 38r orthogonal to the central axis 9, and is shaped like a bicycle wheel with a hub and three spokes.
  • the first guide first half 42a constitutes the outer peripheral portion of the diffuser-type flow path (40-2) having a gentle angle 2 ⁇ and the flow path cross-sectional inner diameter extending to D2.
  • the spread angle 2 ⁇ increases rapidly and the outer peripheral portion spreads in a trumpet shape, reaching the vicinity of the inner wall 411 of the cylindrical body 11b of the accumulator sealed container.
  • the trumpet-shaped first guide rear portion 42b forms a three-way curved flow path (30-12) with the inclined surfaces 38a, 38b, 38c of the second guide 38 inside the trumpet-shaped first guide portion 42b. Smooth conversion from the axial direction to the radial direction.
  • the second guide 38, the wire mesh 89, and the “terminal portion of the first guide 42” are laminated on the guide mounting flange 29, and are fixed with a small screw bolt 87.
  • the metal mesh 89 has a conical shape extending in a mountain shape with the position of the convex vertex 328 as a vertex, and has a function of assisting the gas-liquid separation function of the accumulator. In addition to preventing the dust flowing into the accumulator from being sucked into the compression cylinder, it functions to prevent liquid refrigerant having a large particle size from adhering and scattered in the radial direction to enter the openings 13a and 14a of the outlet pipe. is there.
  • the first guide front half 42a of the diffuser-type flow path (40-2) has a spread angle 2 ⁇ , and the flow path cross-sectional inner diameter gradually widens from D1 to D2.
  • the axial flow that has spread to D2 in the first guide front half 42a flows from the diffuser-shaped flow path (40-2) substantially downstream in the axial direction without being separated, and the convex portion of the second guide 38 After colliding with the vicinity of the apex 328 (substantially in a circular region having a radius D2 / 2), the flow is changed in a direction parallel to the inclined surfaces 38a, 38b, 38c having an inclination angle ⁇ with respect to the central axis 9 and spread in the radial direction, The refrigerant flows toward the three communication ports 308a, 308b, and 308c on the extension of the slope.
  • regions corresponding to the inclined surfaces 38a, 38b and 38c and regions corresponding to the hemispherical projection 88 are indicated by wavy lines.
  • the axial flow entering this wavy region has a relatively small pressure resistance and is smoothly converted to a radial flow.
  • the region other than this is orthogonal to the axial flow, the pressure resistance increases and the momentum loss of the axial flow is large.
  • the ratio of the inclined surface of the curved flow guide (second guide) 38 according to the twelfth embodiment (diffuser flow path area end portion as a reference 1) and the total pressure loss coefficient ⁇ (total when the inlet pipe flows in). And the ratio of the total pressure loss after passing through the second guide 38 to the pressure). Plotted from measured and calculated values when a compressor equivalent to 1 horsepower using propane refrigerant was operated at 60 Hz under the Ashrae-T condition.
  • FIG. 25 shows the divergence angle (2 ⁇ ) of the inlet pipe flow guide 42 of the twelfth embodiment and the total pressure loss coefficient ⁇ (second guide (curved flow guide) 38 with respect to the total pressure when the inlet pipe flows).
  • the operating conditions are the same as in FIG.
  • the second guide that covers the outlet pipe openings 13a and 14a is not provided, the total pressure loss coefficient ⁇ is the smallest and a characteristic close to that of a single diffuser type flow path is exhibited.
  • the divergence angle 2 ⁇ increases, the total pressure loss coefficient ⁇ increases, and the increase rate increases in a range of about 20 degrees to about 40 degrees, and converges to a substantially constant value at 60 degrees or more.
  • the total pressure loss coefficient ⁇ increases from 0.15 to 0.75.
  • the divergence angle 2 ⁇ is sufficiently small (around 20 degrees)
  • the influence of the inclined surface of the second guide is large, and the total pressure loss coefficient ⁇ when there is no inclined surface is the same even with the same communication port area.
  • the slope increases about twice as much as when the inclined surface is 100% (corresponding to FIG. 21).
  • the second guide is not provided at all and the outlet pipe openings 13a and 14a are not covered at all, the liquid refrigerant directly enters the outlet pipes 13 and 14, and there is a high risk of impairing the reliability. That's not true. Therefore, it is necessary to take measures such as covering the outlet pipe openings 13a and 14a with a coarse wire mesh or providing a guide having a slightly inclined surface on the extension of the refrigerant inflow direction from the inlet pipe and having a large opening ratio. For example, in FIG. 23, a structure in which the three slopes 38a, 38b, and 38c are eliminated and the communication port is enlarged can be considered.
  • the pressure loss reduction effect and reliability can be secured to some extent.
  • the opening ratio that the communication port and the wire mesh occupy in the cross section of the closed container have a trade-off relationship between reliability and efficiency. In actual design, the structure is simple (low cost) as long as the reliability can be verified by actual operation. Therefore, it is determined so that the pressure loss can be reduced most.
  • the refrigerant compressor provided with the accumulator 10 according to the twelfth embodiment is inferior to the second embodiment, but reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator and improves the compressor efficiency. It is possible.
  • the accumulator used in the two-cylinder compressor provided with the two compression cylinders 3 and 4 in parallel has been described.
  • the same effect can be obtained even when there is a single accumulator discharge pipe used in a single cylinder compressor having one compression cylinder or a multistage compressor having a plurality of compression cylinders in series.
  • FIG. FIG. 26 is a longitudinal sectional view showing a configuration of a “refrigerant compressor with an accumulator” according to the thirteenth embodiment. Only parts different from the accumulator 10 shown in FIG. 1, which is a CC longitudinal sectional view of FIG. 2, will be described.
  • the accumulator 10 according to the thirteenth embodiment is different from the accumulator 10 according to the first embodiment in that the first guide 41 of the accumulator 10 is eliminated, and the upper end plate 11a of the accumulator sealed container 11 forms a conical diffuser type flow path.
  • FIG. 32 is a longitudinal sectional view showing the configuration of the inlet shape of the accumulator 10 of FIG.
  • the upper end plate 11a of the accumulator sealed container 11 that is a high-pressure container is usually hemispherical or dish-shaped.
  • the inner wall shape of the upper end plate 11a is brought close to a conical diffuser type flow path (40-13) having a cylindrical hole at the same position as the central axis 9.
  • the upper end plate 11a having a round hole in the central shaft 9 is stretched by drawing to the upper side of the central shaft 9 to form a cylindrical hole whose inner diameter is more plus tolerance than the outer diameter of the inlet pipe 12, and is welded through the inlet pipe 12 here. To do.
  • the upper end plate 11a extends from the opening 12a of the inlet tube in a trumpet shape (the curvature at this time is about R1) with a length L2 in the direction of the central axis 9.
  • the divergence angle 2 ⁇ 1 0 degree at the inlet pipe opening 12a and the divergence angle 2 ⁇ in the AA cross section is about 45 degrees. In the vicinity of the inlet pipe opening 12a in this range, the loss reduction effect by the diffuser can be obtained.
  • the divergence angle (2 ⁇ ) is about 120 degrees and is in a peeled state.
  • the inner wall of the upper end plate 11a extends in the trumpet shape to the vicinity of the cylindrical body 11b, then spreads in a spindle shape (the curvature at this time is about R2) with a length L3 toward the central axis 9, and the angle 2 ⁇ is reduced.
  • 11b is connected to the inner wall.
  • a bent flow path (30-13) is formed between the second half of the upper end plate 11a and the second guide 31 (a rectangular conical shape similar to FIG. 1), and communicates with the communication ports 301a and 301b.
  • the length L2 of the diffuser type flow path (40-13) extends from the opening 12a of the inlet pipe to the inflection point (the point at which the trumpet type is switched to the spindle type).
  • the spread angle 2 ⁇ spreads to 45 degrees or more on the downstream side of the AA cross section, so that the effect of reducing the pressure loss by the diffuser becomes small.
  • the first guide first half part configured independently of the accumulator sealed container 11 in FIG. 22 of the twelfth embodiment the first guide first half part from the opening 12a of the diffuser inlet pipe to the vicinity of the AA cross section is as follows.
  • the diffuser length of the first half of the first guide is redefined as L2 ′ (FIG. 32) and the outlet cross-sectional inner diameter is defined as D2 ′ (FIG. 32), it is independent of the accumulator sealed container 11 in FIG.
  • the divergence angle 2 ⁇ is in the range of 0 to 45 degrees, and a diffuser effect is obtained.
  • Average divergence angle 2 ⁇ m 2 ⁇ tan ⁇ 1 ⁇ [(D2′ ⁇ D1) / 2] / L2 ′ ⁇
  • the average spread angle 2 ⁇ is also in the range of 0 to 45 degrees.
  • the spread angle 2 ⁇ of the diffuser flow path can be gradually increased.
  • the accumulator 10 of the single cylinder compressor 5 has one compression cylinder 6 and one discharge pipe, and in order to operate so as to ensure the same capacity as the two cylinder compressor, the suction volume of the compression cylinder is doubled. And the pressure loss generated at the outlet pipe of the accumulator becomes large.
  • in order to reduce the pressure loss of the outlet pipe 16 it is effective to increase the inner diameter of the outlet pipe.
  • the inner diameter of the outlet pipe rear half portion 16c connected to the compression cylinder 6 is limited due to restrictions on the thickness and arrangement of the compression cylinder. Therefore, the pipe diameter of the outlet pipe front half 16b disposed in the accumulator internal space 20 is wider than that of the outlet pipe rear half 16c.
  • the inlet pipe flow guides (41, 42) constituting an ideal diffuser type flow path are used independently of the accumulator sealed container 11. Is desirable.
  • a structure that also serves as the upper end plate 11a of the accumulator sealed container 11 as in the thirteenth embodiment is effective.
  • the refrigerant compressor provided with the accumulator 10 according to the thirteenth embodiment has the same effect as the first guide (inlet pipe flow guide) of the first to twelfth embodiments, and maintains the gas-liquid separation function of the accumulator. It is possible to reduce losses and improve compressor efficiency.
  • FIG. 27 is a longitudinal sectional view (a CC longitudinal sectional view of FIG. 28) showing a configuration of “accumulator 10 attached to the refrigerant compressor” according to the fourteenth embodiment.
  • FIG. 28 is a view of the accumulator 10 of FIG. 27 as viewed from directly above the AA cross section of FIG. Only differences from the thirteenth embodiment will be described.
  • the accumulator 10 according to the fourteenth embodiment is different from the thirteenth embodiment in that a fourth guide 83 is added.
  • the conical diffuser type flow path is configured by the upper end plate 11a of the accumulator hermetically sealed container 11.
  • the fourth guide 83 along the diffuser flow is provided on the inner side of the upper end plate 11a in order to suppress the separation in a wider range and obtain a loss reduction effect by the diffuser.
  • the shape is a conical diffuser shape made of a thin plate. The length is about half of the length L2 of the diffuser channel (40-14).
  • the fourth guide 83 is disposed on the upstream side of the second guide 31, the flow flowing into the curved flow path 30-14 is not easily disturbed, and the flow resistance is reduced.
  • the fourth guide 83 is welded and fixed by making cuts 351 at four positions overlapping the ridgeline 311 of the third guide at the end portion.
  • the refrigerant compressor provided with the accumulator 10 according to the fourteenth embodiment is more effective than the thirteenth embodiment, and reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator, thereby improving the compressor efficiency. Is possible.
  • the accumulator sealed container 11 has a cylindrical shape that is an axial object with respect to the central axis 9 and the refrigerant flows into the central axis from the inlet pipe 12 has been described.
  • the fifteenth embodiment below shows an example in which the compressor efficiency improving effect according to the first to fourteenth embodiments can be obtained even when the axial direction in which the refrigerant flows from the inlet pipe does not coincide with the central axis of the sealed container. .
  • the larger the non-target elements the less the pressure loss reduction effect, but the compressor efficiency improvement effect according to the first to fourteenth embodiments can be obtained.
  • the accumulator sealed container 11 does not necessarily have an axial target shape, and the cylindrical body is not necessarily a cylindrical body and may have a flat shape.
  • the axial direction in which the refrigerant flows from the inlet pipe 12 does not have to be directly below the central axis. It may deviate from the central axis, and does not necessarily have to be in the downward direction. That is, if a diffuser-type flow path and a chevron-shaped distribution flow path that are axially symmetric with respect to the refrigerant inflow direction are formed on the downstream side in the axial direction in which the refrigerant flows from the inlet pipe 12, the same improvement effect can be obtained.
  • the fifteenth embodiment when there are non-target elements will be described below.
  • FIG. 29 is a longitudinal sectional view (a CC longitudinal sectional view of FIG. 30) showing a configuration of “accumulator 10 attached to refrigerant compressor” according to the fifteenth embodiment.
  • FIG. 30 is a view of the accumulator 10 of FIG. 29 as viewed from directly above the AA cross section (except for the accumulator sealed container 11).
  • the accumulator sealed container 11 has a cylindrical shape that is an axial object with respect to the central axis 9, and the refrigerant flows from the inlet pipe to the central axis.
  • the diffuser is formed by the first guide 45 that extends in the axial direction in which the refrigerant flows into the hermetic container from the inlet pipe 12 attached to the side of the cylindrical body 11b.
  • the liquid refrigerant passes through the shaped flow path (4-15) through the curved flow path (30-15) that changes the flow in the radial direction by the two-forked second guide 39 that blocks the inflow direction. Collides with the inner wall 411. After the gas-liquid separation, the gas refrigerant passes through the communication ports 309a and 309b and is guided to the opening 16a of the outlet pipe.
  • 309a and 309b have the smallest flow resistance and are easy to flow.
  • the first guide is fixed to the guide mounting flange 29 by welding.
  • 329 of FIG. 30 is a ridgeline of the convex vertex.
  • the second guide 34 of FIG. 16 is arranged vertically and the apex of the convex portion is directed toward the refrigerant outlet of the first guide 45.
  • the refrigerant compressor provided with the accumulator 10 according to the fifteenth embodiment has an improvement effect according to the first to fourteenth embodiments, reduces the pressure loss while maintaining the gas-liquid separation function of the accumulator, and improves the compressor efficiency. It is possible to improve.
  • the accumulator 10 is provided with both a diffuser-type flow path and a curved flow guide (second guide) in a sealed container. Due to the synergistic effect of the mutual combination, an effect of reducing the pressure loss while maintaining the gas-liquid separation function of the accumulator and improving the compressor efficiency can be obtained.
  • the diffuser-type flow path is provided in the accumulator sealed container and the partition plate orthogonal to the axial direction as in the conventional patent document 1 is provided on the downstream side thereof, the pressure loss compared with the conventional accumulator.
  • the effect of improving the compressor efficiency can be obtained, but the improvement effect is limited.
  • the diffuser type flow path and the curved flow guide (second guide) The improvement effect is significantly inferior to the case where both are provided.
  • the lower end plate 11c attached with the inlet pipe and the upstream space of the accumulator remain in the conventional example, and a mountain-shaped bent flow guide (second guide) is provided on the downstream side thereof.
  • a mountain-shaped bent flow guide (second guide)
  • the pressure loss is reduced compared to the conventional accumulator and the compression is performed. The effect of improving the efficiency is obtained.
  • the refrigerant flows as shown in FIGS. 14 to 16 in the eighth embodiment.
  • the compressor efficiency improvement effect obtained by the accumulators of Embodiments 1 to 15 described above varies depending on the type of refrigerant used in the vapor compression refrigeration cycle. As the refrigerant operating at the compressor has a lower pressure and density, the power loss due to the pressure loss that occurs during suction of the accumulator accounts for a larger proportion of the compressor input, so the effect of improving the compressor efficiency is greater.
  • Low GWP refrigerants such as HC refrigerants (isobutane, propane, propylene) and HFO1234yf operate at a low pressure and low density compared to CFC refrigerants (R410A, R22) currently used in the global market for air conditioning equipment. With the accumulator of the embodiment, a particularly large compressor efficiency improvement effect can be obtained.
  • other rotary compressors such as a swing piston type, a sliding vane type, and a compressor type other than the rotary type are used.
  • the reciprocating type and the scrolling type when the accumulator is provided on the suction side, the effect of improving the compressor efficiency can be obtained as in the first to fifteenth embodiments.
  • the high-pressure shell type single-stage compressor in which the pressure in the high-pressure vessel 8 is equal to the pressure in the high-stage compression section has been described.
  • the accumulator is used in exactly the same manner as the high pressure shell type, and the same compressor efficiency improvement effect as in the first to fifteenth embodiments can be obtained. Further, even in the case of a low-pressure shell type refrigerant compressor, the same effect can be obtained when the accumulator of the above embodiment is attached to the suction side of the refrigerant compressor.
  • the effect of improving the compressor efficiency can be obtained in exactly the same manner as in the first to fifteenth embodiments.
  • the accumulator shown in the first to fifteenth embodiments is used at a place other than the suction side of the refrigerant compressor in the vapor compression refrigeration cycle, for the purpose of improving gas-liquid separation (or oil separation) efficiency and liquid storage.
  • a conical diffuser-type channel (including a trumpet shape other than a straight wall and a bell shape) is used as the diffuser-type channel. Even if it is a flat ellipse or a rectangle, the effect according to the first to fifteenth embodiments can be obtained as long as it is a diffuser-type flow channel that extends straight from the inlet pipe 12 in the inflow direction.
  • the circular diffuser-shaped channel having both the inlet and the outlet has been described as the diffuser-shaped channel.
  • P61 and p147 of Non-Patent Document 1 show a diffuser-type channel that changes from a circular inlet to an elliptical outlet, and a diffuser-type channel that changes from a flat rectangular inlet to an elliptical outlet.
  • the diffuser-type flow channel extends straight from the inlet pipe 12 in the inflow direction
  • the first guide that forms the diffuser-shaped flow path is designed so that it gradually changes from an inlet having the same circular cross section as the inlet pipe to a shape close to the bottom shape of the curved flow guide (second guide), It is possible to obtain the effects of reducing the pressure loss and improving the compressor efficiency, equivalent to or better than the first to fifteenth aspects.
  • Embodiments 5 to 9 of the present invention or in the fourteenth and fifteenth embodiments specific configurations excellent from a practical viewpoint are shown.
  • a specific configuration in which auxiliary means for providing a suction channel is appropriately combined has been described.
  • a specific configuration in which auxiliary means for providing intermediate guide vanes are appropriately combined is shown.
  • a specific configuration in which auxiliary means for providing a wire mesh in the diffuser type flow path is appropriately combined has been shown.
  • FIG. 31 is a configuration diagram of a vapor compression refrigeration cycle 70 (vapor compression refrigeration cycle apparatus) according to the sixteenth embodiment.
  • the vapor compression refrigeration cycle 70 includes a compressor 71 (3 and 4 in the case of a two-cylinder compression cylinder) that compresses refrigerant with a single-cylinder compression cylinder 6 in the compressor hermetic container 2, and a suction side of the compressor 71.
  • the accumulator 10 according to any one of the first to fifteenth embodiments, the radiator 72, the expansion mechanism 73, and the evaporator 74 are provided. By using the accumulator 10 in the vapor compression refrigeration cycle 70, the efficiency of the vapor compression refrigeration cycle 70 can be improved.
  • the “refrigerant compressor with an accumulator” as an apparatus has been described, but the function of the accumulator 10 can also be grasped as a gas-liquid separation method.
  • the function of the accumulator 10 is to introduce a two-phase gas-liquid two-phase refrigerant into the accumulator sealed container and guide the flow of the two-phase refrigerant flowing in the inner circumferential direction while expanding in the inner circumferential direction of the accumulator sealed container.
  • a first guide, a second guide for guiding the flow of the refrigerant guided in the inner circumferential direction by the first guide in the radial direction of the accumulator sealed container, and a flow of the refrigerant guided in the radial direction by the second guide for the outlet pipe It is also possible to grasp as a gas-liquid separation method for passing through the communication port.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

La présente invention se rapporte à un compresseur frigorifique équipé d'un accumulateur avec lequel la perte de pression est réduite tout en conservant une performance de séparation gaz/liquide. Le compresseur frigorifique (10) équipé d'un accumulateur est équipé : d'un contenant fermé hermétiquement du type à accumulateur (11) ; d'un tuyau d'admission (12) par lequel circule le fluide frigorigène allant d'une partie d'ouverture (12a) au niveau d'une partie d'extrémité de ce dernier vers le récipient fermé hermétiquement du type à accumulateur (11) ; d'un tuyau de sortie (13) par lequel le fluide frigorigène est aspiré depuis une partie d'ouverture (13) au niveau d'une partie d'extrémité de ce dernier ; d'un guide d'écoulement de tuyau d'admission (41) qui est agencé dans un espace situé en amont (21), formant un trajet d'écoulement en forme de diffuseur (40-1) dont la coupe transversale augmente petit à petit depuis une position se trouvant près de l'ouverture du tuyau d'admission (12) vers la partie aval de la direction d'écoulement (335c) du fluide frigorigène, le fluide frigorigène qui s'écoule à l'intérieur, s'écoulant par le trajet d'écoulement en forme de diffuseur (40-1), ce qui permet de séparer l'espace intérieur en un espace situé en amont (21) et en un espace situé en aval (22) et de bloquer l'écoulement dans la direction d'écoulement du fluide frigorigène provenant du tuyau d'amenée qui s'écoule par le trajet d'écoulement en forme de diffuseur (40-1).
PCT/JP2011/069066 2010-08-25 2011-08-24 Compresseur frigorifique équipé d'un accumulateur et d'un dispositif de cycle de réfrigération du type à compression de vapeur Ceased WO2012026496A1 (fr)

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CN103940160A (zh) * 2014-03-14 2014-07-23 安徽美芝精密制造有限公司 储液器
CN105202831A (zh) * 2015-10-10 2015-12-30 安徽美芝精密制造有限公司 储液器和具有其的压缩机、空调系统
CN106907882A (zh) * 2017-02-23 2017-06-30 广州市粤联水产制冷工程有限公司 制冷系统
CN109140845A (zh) * 2018-08-23 2019-01-04 特灵空调系统(中国)有限公司 储液器和具有其的热泵系统
WO2020181764A1 (fr) * 2019-03-13 2020-09-17 珠海格力电器股份有限公司 Séparateur gaz-liquide, ensemble compresseur, et climatiseur
CN112513545A (zh) * 2018-08-22 2021-03-16 翰昂汽车零部件有限公司 可选地与共享壳体中的内部热交换器组合的蓄能器
US20220275986A1 (en) * 2019-08-22 2022-09-01 Danfoss A/S Refrigeration system
WO2022230101A1 (fr) * 2021-04-28 2022-11-03 三菱電機株式会社 Récepteur de liquide et dispositif à cycle frigorifique
WO2022239211A1 (fr) * 2021-05-14 2022-11-17 三菱電機株式会社 Récipient de stockage de fluide frigorigène, et dispositif à cycle frigorifique doté dudit récipient de stockage de fluide frigorigène
WO2025232338A1 (fr) * 2024-10-22 2025-11-13 上海海立电器有限公司 Ensemble admission d'air de compresseur et système de réfrigération

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EP3690376B1 (fr) * 2019-02-04 2021-07-21 Carrier Corporation Échangeur de chaleur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103940160A (zh) * 2014-03-14 2014-07-23 安徽美芝精密制造有限公司 储液器
CN103940160B (zh) * 2014-03-14 2016-08-31 安徽美芝精密制造有限公司 储液器
CN105202831A (zh) * 2015-10-10 2015-12-30 安徽美芝精密制造有限公司 储液器和具有其的压缩机、空调系统
CN106907882B (zh) * 2017-02-23 2022-10-11 广州市粤联水产制冷工程有限公司 制冷系统
CN106907882A (zh) * 2017-02-23 2017-06-30 广州市粤联水产制冷工程有限公司 制冷系统
CN112513545A (zh) * 2018-08-22 2021-03-16 翰昂汽车零部件有限公司 可选地与共享壳体中的内部热交换器组合的蓄能器
CN109140845A (zh) * 2018-08-23 2019-01-04 特灵空调系统(中国)有限公司 储液器和具有其的热泵系统
CN109140845B (zh) * 2018-08-23 2020-10-02 特灵空调系统(中国)有限公司 储液器和具有其的热泵系统
WO2020181764A1 (fr) * 2019-03-13 2020-09-17 珠海格力电器股份有限公司 Séparateur gaz-liquide, ensemble compresseur, et climatiseur
US20220275986A1 (en) * 2019-08-22 2022-09-01 Danfoss A/S Refrigeration system
WO2022230101A1 (fr) * 2021-04-28 2022-11-03 三菱電機株式会社 Récepteur de liquide et dispositif à cycle frigorifique
WO2022239211A1 (fr) * 2021-05-14 2022-11-17 三菱電機株式会社 Récipient de stockage de fluide frigorigène, et dispositif à cycle frigorifique doté dudit récipient de stockage de fluide frigorigène
JP7433522B2 (ja) 2021-05-14 2024-02-19 三菱電機株式会社 冷媒貯留容器及び該冷媒貯留容器を備えた冷凍サイクル装置
WO2025232338A1 (fr) * 2024-10-22 2025-11-13 上海海立电器有限公司 Ensemble admission d'air de compresseur et système de réfrigération

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