EP2910875B1 - Séparateur d'huile - Google Patents

Séparateur d'huile Download PDF

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Publication number
EP2910875B1
EP2910875B1 EP15153295.9A EP15153295A EP2910875B1 EP 2910875 B1 EP2910875 B1 EP 2910875B1 EP 15153295 A EP15153295 A EP 15153295A EP 2910875 B1 EP2910875 B1 EP 2910875B1
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EP
European Patent Office
Prior art keywords
pressure container
refrigerant
inlet pipe
refrigerant inlet
gas phase
Prior art date
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Active
Application number
EP15153295.9A
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German (de)
English (en)
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EP2910875A1 (fr
Inventor
Osamu Ogawa
Satoshi Imai
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP2910875A1 publication Critical patent/EP2910875A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • 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 an oil separator that separates refrigerating machine oil by inertia force and centrifugal force, from a gas phase refrigerant containing the refrigerating machine oil that is discharged from a compressor.
  • a compressor is used for a heat pump cycle of an air conditioner and the like.
  • refrigerating machine oil is typically used.
  • the refrigerating machine oil circulates through a refrigerant circulating system with a refrigerant flowing through the refrigerant circulating system.
  • the refrigerating machine oil suctioned from an intake side of the compressor or the refrigerating machine oil stored in a shell container including the compressor is supplied to the sliding portions inside the compressor and used to lubricate the sliding portions.
  • the refrigerating machine oil is supplied to an operation chamber of the compressor and used to prevent leakage of a vaporized refrigerant by sealing a gap inside the operation chamber.
  • the refrigerating machine oil tends to attach to an inner wall of a heat transfer pipe of a heat exchanger.
  • the refrigerating machine oil attaching to the inner wall of the heat transfer pipe is a factor that hampers heat transfer in the heat transfer pipe, worsens the heat-transfer efficiency of the heat exchanger, and increases pressure loss.
  • an oil separator is provided inside the refrigerant circulating system.
  • the oil separator separates the refrigerating machine oil from the refrigerant discharged from the compressor, and returns the refrigerating machine oil to the intake side of the compressor.
  • an oil separator which is provided with a refrigerant inlet pipe and a refrigerant outlet pipe in an upper end plate of a pressure container, and is provided with an oil return pipe in a lower end plate of the pressure container.
  • the oil separator After a mixture of a gas phase refrigerant and refrigerating machine oil from a compressor flows in trough the refrigerant inlet pipe, the oil separator causes the mixture to collide against a cylindrical inner wall of the pressure container and separates the refrigerating machine oil by inertia force. Then, after the mixture of the gas phase refrigerant and refrigerating machine oil collides against the inner wall, the oil separator causes the mixture to rotate at a high speed along the inner wall and separates the refrigerating machine oil by centrifugal force.
  • Document JP-H09-210509 discloses an oil separator that separates refrigerating machine oil contained in a gas phase, according to the preamble of claim 1.
  • One non-limiting and exemplary embodiment provides an improved oil separator according to claim 1.
  • the oil separator separates refrigerating machine oil contained in a gas phase refrigerant by inertia force and centrifugal force.
  • the oil separator includes a cylindrical pressure container, a refrigerant inlet pipe that leads the gas phase refrigerant containing the refrigerating machine oil into the cylindrical pressure container, and a refrigerant outlet pipe that discharges the gas phase refrigerant from which the refrigerating machine oil is separated.
  • An angle ⁇ between a straight line along the direction of the opening of a delivery port at a tip of the refrigerant inlet pipe introduced into the cylindrical pressure container and a plane perpendicular to the central axis of the cylindrical pressure container satisfies 45° ⁇ ⁇ ⁇ 90°.
  • the present invention can reduce an influence of variations in the machining accuracy of the refrigerant inlet pipe of the oil separator, enhance an effect of impingement separation and an effect of centrifugal separation for the refrigerating machine oil at the same time, and make a path length of a rotational flow longer than a conventional one.
  • the inventor has conducted a thorough study of the conventional oil separator and has obtained the following knowledge.
  • the refrigerant inlet pipe is introduced through the upper end plate of the pressure container.
  • a delivery port of the refrigerant inlet pipe is curved, and the direction of the opening of the delivery port is faced toward a portion of the inner wall of the oil separator slightly below the delivery port.
  • a gas phase refrigerant delivered from the delivery port collides against the inner wall of the pressure container and rotates within the pressure container.
  • FIG. 7 illustrates a configuration of a conventional oil separator 1.
  • Fig. 7 is a cross sectional view of the oil separator 1 including a cylindrical pressure container 20 when the oil separator 1 is cut by a plane perpendicular to the central axis of the pressure container 20.
  • the oil separator 1 includes the pressure container 20, a refrigerant inlet pipe 11, and a refrigerant outlet pipe 14. As described above, the direction of the opening of a delivery port 13 is faced toward a portion of the inner wall of the oil separator 1 slightly below the delivery port 13.
  • a distance X is large to some extent and a distance Y is small.
  • the distances X and Y are distances from the delivery port 13 to the inner wall of the oil separator 1 in the direction of the opening and in a direction perpendicular to the direction of the opening, respectively.
  • the rotational flow of the gas phase refrigerant reaches a bottom part of the pressure container 20 quickly and the path length of the rotational flow is shortened. Therefore, the refrigerating machine oil may not be separated sufficiently.
  • the inventor has thus conceived the following oil separator.
  • the oil separator of the present invention separates refrigerating machine oil contained in a gas phase refrigerant.
  • the oil separator includes a cylindrical pressure container, a refrigerant inlet pipe that leads the gas phase refrigerant containing the refrigerating machine oil into the cylindrical pressure container, and a refrigerant outlet pipe that discharges the gas phase refrigerant from which the refrigerating machine oil is separated.
  • An angle ⁇ between a straight line along the direction of the opening of a delivery port at a tip of the refrigerant inlet pipe introduced into the cylindrical pressure container and a plane perpendicular to the central axis of the cylindrical pressure container satisfies 45° ⁇ ⁇ ⁇ 90°.
  • the direction of the opening of the delivery port comes closer to a ceiling surface of the cylindrical pressure container or faces the ceiling surface, and the distance X can be made still larger. That is, it becomes possible to enhance an effect of impingement separation and an effect of centrifugal separation for the refrigerating machine oil at the same time.
  • Fig. 1 is a refrigerant circuit diagram illustrating an overall configuration of an outdoor unit 100 of an air conditioner according to an embodiment of the present disclosure.
  • the outdoor unit 100 illustrated in Fig. 1 is an example of an air conditioner to which an oil separator 10 according to the present invention is applicable, and a range of application of the oil separator 10 is not limited to such an air conditioner.
  • the outdoor unit 100 includes a variable capacity compressor (DC inverter compressor) 30, the oil separator 10, an outdoor heat exchanger 31, an expansion valve 32, a four-way valve 33, a receiver tank 34, and an accumulator 35.
  • DC inverter compressor DC inverter compressor
  • a suction pipe 41 extending through the accumulator 35 is connected to a suction opening of the compressor 30.
  • a discharge pipe 42A is connected to a discharge opening of the compressor 30.
  • the discharge pipe 42A is connected to the oil separator 10, and a discharge pipe 42B extending through the oil separator 10 is connected to the four-way valve 33.
  • the four-way valve 33 communicates one end of the outdoor heat exchanger 31 with the discharge pipe 42B or communicates one end of the outdoor heat exchanger 31 with a duct 43 linking to the suction pipe 41 of the compressor 30. Further, the four-way valve 33 communicates the discharge pipe 42B extending through the oil separator 10 with a gas pipe 46 or communicates the duct 43 linking through the accumulator 35 to the suction pipe 41 of the compressor 30 with the gas pipe 46.
  • the other end of the outdoor heat exchanger 31 is connected to the expansion valves 32 and the receiver tank 34, and further connected through a refrigerant pipe 44 to a liquid tube 45.
  • An oil return pipe 47 is connected to the oil separator 10; the oil return pipe 47 returns refrigerating machine oil stored in the oil separator 10 to the suction pipe 41 of the compressor 30.
  • the above refrigerating machine oil is lubricating oil for the compressor 30 contained in a gas phase refrigerant discharged from the compressor 30.
  • the oil separator 10 separates the refrigerating machine oil from the refrigerant discharged from the compressor 30, returns the separated refrigerating machine oil to a suction side of the compressor 30, and supplies the gas phase refrigerant from which the refrigerating machine oil is removed to the four-way valve 33.
  • the outdoor unit 100 is connected through the liquid tube 45 and the gas pipe 46 to an indoor unit (not illustrated).
  • the air conditioner in the embodiment is configured such that a refrigerant is circulated between the outdoor unit 100 and the indoor unit and the four-way valve 33 is switched, thereby enabling cooling operation or air-heating operation.
  • Fig. 2 illustrates an inside of the oil separator 10 when the oil separator 10 is viewed from the upper direction.
  • Fig. 3 illustrates the inside of the oil separator 10 when the oil separator 10 is viewed from the direction of arrow III in Fig. 2 .
  • Fig. 4 illustrates the inside of the oil separator 10 when the oil separator 10 is viewed from the direction of arrow IV in Fig. 2 .
  • the oil separator 10 includes a pressure container (oil separator main body) 20, which is a cylindrical sealed container.
  • the pressure container 20 is configured with a container upper section 21, a container lower section 22, and a container barrel section 29.
  • the container upper section 21 and the container barrel section 29 are joined, and the container lower section 22 and the container barrel section 29 are joined, by welding or the like.
  • the openings are sealed with each other.
  • An upper end plate 23 is formed on an upper surface of the container upper section 21 in an integrated manner.
  • a lower end plate 24 is formed on a lower surface of the container lower section 22 in an integrated manner.
  • the upper end plate 23 is provided with a refrigerant inlet pipe 11 and a refrigerant outlet pipe 14.
  • Figs. 2 , 3 , and 4 illustrate not only outer walls of the refrigerant inlet pipe 11 and the refrigerant outlet pipe 14, but also their inner walls.
  • the discharge pipe 42A extending from the discharge opening of the compressor 30 is connected to the refrigerant inlet pipe 11.
  • the gas phase refrigerant that is discharged from the compressor 30 and contains the refrigerating machine oil is led into the pressure container 20 by the refrigerant inlet pipe 11.
  • the discharge pipe 42B linking to the four-way valve 33 is connected to the refrigerant outlet pipe 14.
  • the gas phase refrigerant from which the refrigerating machine oil is separated is discharged to the outside of the pressure container 20 by the refrigerant outlet pipe 14.
  • the lower end plate 24 is provided with an oil outlet pipe 25.
  • the oil outlet pipe 25 is connected to the oil return pipe 47.
  • the refrigerating machine oil in the pressure container 20 is discharged to the outside of the pressure container 20 by the oil outlet pipe 25.
  • the container lower section 22 of the pressure container 20 is provided with two leg portions 26.
  • the upper end part of each leg portion 26 is joined to a peripheral surface of the container lower section 22 by welding or the like.
  • the lower end part of each leg portion 26 is bent so as to be parallel with a contact surface (bottom plate of the outdoor unit 100). That is, the leg portions 26 are formed in a substantially L shape.
  • the pressure container 20 is configured to be longitudinally mounted with a spacing from the contact surface while standing with the leg portions 26.
  • Two leg portions 26 are assumed here, but three or more leg portions 26 may be used.
  • the refrigerant inlet pipe 11 and the refrigerant outlet pipe 14 are provided substantially parallel with a central axis AX of the cylindrical pressure container 20 and penetrate the upper end plate 23 substantially vertically.
  • the refrigerant inlet pipe 11 is introduced through the upper end plate 23 at a position deviated from a center C of the pressure container 20.
  • the refrigerant outlet pipe 14 is introduced through the upper end plate 23 at the position of the center C of the pressure container 20.
  • through-holes 27 and 28 are formed through which the refrigerant inlet pipe 11 and the refrigerant outlet pipe 14 are introduced, respectively.
  • the refrigerant inlet pipe 11 and the refrigerant outlet pipe 14 are introduced through the through-holes 27 and 28, respectively, and the entire peripheries of the refrigerant inlet pipe 11 and the refrigerant outlet pipe 14 are sealed by brazing.
  • the refrigerant inlet pipe 11 has a curved portion 12.
  • the direction of the opening may also be referred to as the direction in which the gas phase refrigerant flows out of the delivery port 13.
  • the refrigerant inlet pipe 11 is formed such that an angle ⁇ between a straight line along the direction of the opening of the delivery port 13 and a plane H perpendicular to the central axis AX of the pressure container 20 falls within a range of 45° ⁇ ⁇ ⁇ 90°.
  • Fig. 3 illustrates a case in which the direction of the opening of the delivery port 13 is faced toward a curved portion of the upper end plate 23 of the pressure container 20.
  • the gas phase refrigerant delivered from the delivery port 13 collides against the curved portion of the pressure container 20. Then, a flow of the gas phase refrigerant is separated to a flow F1 moving further upward and a flow F2 moving further downward in the pressure container 20.
  • the flow F1 is dominant over the flow F2.
  • the path length for an outflow from the refrigerant outlet pipe 14 is longer than that for the flow F2, and therefore more refrigerating machine oil can be separated.
  • the angle ⁇ is greater than or equal to 45°
  • the vertical component of velocity of the gas phase refrigerant delivered from the delivery port 13 is greater than or equal to the horizontal component of velocity of the gas phase refrigerant. Therefore, when the gas phase refrigerant collides against a side face inner wall of the pressure container 20, the gas phase refrigerant is efficiently directed further upward in the pressure container 20. Moreover, loss of kinetic energy of the flow of the gas phase refrigerant is suppressed.
  • the angle ⁇ is a value within the above range, when the curved portion 12 is formed in the refrigerant inlet pipe 11, the gas phase refrigerant collides against the inner wall at the outward side of the curved portion 12. This also enables separation of the refrigerating machine oil from the gas phase refrigerant.
  • the refrigerant inlet pipe 11 is formed such that the angle ⁇ falls within a range of 45° ⁇ ⁇ ⁇ 90°.
  • a reticulated member such as a mesh filter may be provided inside the refrigerant inlet pipe 11 at the upstream side of the curved portion 12. This enables the reticulated member to separate the refrigerating machine oil from the gas phase refrigerant to some extent, and the oil separation efficiency of the entire oil separator 10 can be further improved.
  • the refrigerant inlet pipe 11 is placed at a position where a distance x from the inner wall of the pressure container 20 to the center position of the delivery port 13 satisfies a relationship of D/2 ⁇ x ⁇ 1.6D.
  • D is an inner diameter of the refrigerant inlet pipe 11.
  • Fig. 5 illustrates an influence of the position of the delivery port 13 of the refrigerant inlet pipe 11 on a separation rate of refrigerating machine oil.
  • the vertical axis represents the refrigerating machine oil separation rate
  • the horizontal axis represents a ratio of the distance x to an inner diameter L of the pressure container 20.
  • D in Fig. 5 is the inner diameter of the refrigerant inlet pipe 11. This result was obtained by Monte Carlo simulation.
  • Fig. 5 shows that as the ratio x/L becomes smaller, the refrigerating machine oil separation rate becomes larger. This is because when the gas phase refrigerant rotates along the inner wall and the refrigerating machine oil is separated by centrifugal force, the closer the delivery port 13 to the inner wall of the pressure container 20, the shorter the time for refrigerating machine oil to reach the inner wall and the more easily the refrigerating machine oil is captured on the inner wall.
  • the refrigerating machine oil separation rate indicates the maximum value 100% when the distance x is D/2 (the ratio x/L is 7.3). This is a case in which the refrigerant inlet pipe 11 is in contact with the inner wall of the pressure container 20.
  • the separation rate required for the oil separator 10 according to the specifications is a value greater than or equal to 85%. This separation rate is achieved when the distance x is smaller than or equal to 1.6D (the ratio x/L is 23.0). Accordingly, a range of D/2 ⁇ x ⁇ 1.6D is set.
  • the refrigerating machine oil is separated from the gas phase refrigerant, mainly when the gas phase refrigerant passes through the curved portion 12 of the refrigerant inlet pipe 11, when the gas phase refrigerant flowing out of the refrigerant inlet pipe 11 collides against the upper end plate 23, and when the gas phase refrigerant rotates within the pressure container 20.
  • the separation rate of the entire oil separator 10 is about 85%.
  • the above lower limit value of 85% for the separation rate according to the specifications has been determined based on these factors.
  • the direction of the opening of the delivery port 13 of the refrigerant inlet pipe 11 is not parallel with a surface normal direction of the inner wall of the pressure container 20 in the direction of the opening. If the direction of the opening of the delivery port 13 is parallel with the surface normal direction of the inner wall of the pressure container 20 in the direction of the opening, the gas phase refrigerant delivered from the delivery port 13 collides against the inner wall from the vertical direction, causing larger loss of kinetic energy of the gas phase refrigerant.
  • the gas phase refrigerant delivered from the delivery port 13 flows while deviating in a direction other than the delivery port 13. As a result, a high-speed rotational flow can be generated without loss of kinetic energy.
  • the refrigerant outlet pipe 14 penetrates the center C of the upper end plate 23 and a tip 15 of the refrigerant outlet pipe 14 extends further downward than the delivery port 13 of the refrigerant inlet pipe 11.
  • the direction of the opening of the tip 15 is a vertically downward direction. In this way, the refrigerant outlet pipe 14 is placed so as not to interfere with the refrigerant inlet pipe 11.
  • the operation of the oil separator 10 will next be described.
  • the gas phase refrigerant discharged from the compressor 30 is led into the pressure container 20 of the oil separator 10 through the discharge pipe 42A and the refrigerant inlet pipe 11.
  • the gas phase refrigerant contains refrigerating machine oil.
  • the curved portion 12 of the refrigerant inlet pipe 11 is curved such that a high-temperature gas phase refrigerant discharged from the compressor 30 is delivered along an inner peripheral surface of the pressure container 20. Therefore, the gas phase refrigerant delivered from the delivery port 13 of the refrigerant inlet pipe 11 becomes a collision flow colliding against the upper end plate 23, and then becomes a flow rotating hard along the inner peripheral surface of the pressure container 20.
  • the refrigerating machine oil contained in the gas phase refrigerant that has become the collision flow has a higher density than the gas phase refrigerant, and therefore is separated from the gas phase refrigerant by inertia force upon collision against the container wall. Still-unseparated refrigerating machine oil scatters in an outside radius direction of the pressure container 20 and is separated from the gas phase refrigerant by centrifugal force generated from rotation of the gas phase refrigerant.
  • the refrigerant inlet pipe 11 is formed such that the angle ⁇ falls within a range of 45° ⁇ ⁇ ⁇ 90°.
  • the collision flow of the gas phase refrigerant collides against a ceiling surface of the upper end plate 23, and a rotational flow is generated from the ceiling surface. Therefore, because the height of the pressure container 20 can be used to make the path length of the rotational flow longer, the refrigerating machine oil separation rate can be improved.
  • the delivery port 13 may face further downward than the horizontal direction to some extent due to variations in the machining accuracy. In this case, there is a possibility that a rotational flow of the gas phase refrigerant delivered from the delivery port 13 also faces downward, the path length of the rotational flow of the gas phase refrigerant is insufficient, and the refrigerating machine oil is not separated sufficiently.
  • the direction of the opening of the delivery port 13 of the refrigerant inlet pipe 11 faces further upward than the horizontal direction and the angle ⁇ is a value within a range of 45° ⁇ ⁇ ⁇ 90°. Therefore, because it is possible to prevent the direction of the opening of the delivery port 13 from facing further downward than the horizontal direction due to variations in the machining accuracy, the path length of the rotational flow of the gas phase refrigerant is longer than was previously possible, and the refrigerating machine oil separation rate can be improved.
  • the delivery port 13 of the refrigerant inlet pipe 11 can be close to the inner wall of the pressure container 20. Therefore, centrifugal force generated from a rotational flow enables reduction in the time before particles of the refrigerating machine oil move to the inner wall of the pressure container 20 and are captured on the inner wall. Accordingly, the refrigerating machine oil separation rate can be further improved.
  • the refrigerant inlet pipe 11 is placed in contact with the inner wall of the pressure container 20, it is desirable to weld the refrigerant inlet pipe 11 and the pressure container 20. Accordingly, occurrence of vibrations can be suppressed.
  • the oil separator 10 it is possible to keep a sufficient distance between the opening face of the delivery port 13 of the refrigerant inlet pipe 11 and the ceiling surface of the upper end plate 23. Accordingly, it is possible to diffuse the gas phase refrigerant delivered from the delivery port 13 of the refrigerant inlet pipe 11 before the gas phase refrigerant reaches the ceiling surface of the upper end plate 23.
  • the refrigerating machine oil separated from the gas phase refrigerant by centrifugal force falls under its own weight and is stored in the container lower section 22 of the pressure container 20. Then, the refrigerating machine oil is led out of the oil outlet pipe 25 provided in the bottom part of the pressure container 20 to the outside of the pressure container 20 and returned to the suction opening of the compressor 30 via the oil return pipe 47.
  • the gas phase refrigerant from which the refrigerating machine oil is separated inside the pressure container 20 is stored in a space higher than the liquid level of the refrigerating machine oil stored in the container lower section 22 of the pressure container 20. Then, the gas phase refrigerant enters the refrigerant outlet pipe 14 and is supplied to the four-way valve 33 through the discharge pipe 42B.
  • the refrigerant outlet pipe 14 is placed at the center of the pressure container 20, and does not disturb a flow rotating along the inner peripheral surface of the pressure container 20. Because the tip 15 of the refrigerant outlet pipe 14 is placed at the center of the flow rotating along the inner peripheral surface of the pressure container 20, it is possible to prevent scattered refrigerating machine oil from being led out of the tip 15, and it is possible to direct, to the discharge pipe 42B, the gas phase refrigerant from which most of the refrigerating machine oil is removed.
  • Fig. 6 is a streamline diagram illustrating an example of a flow of the gas phase refrigerant.
  • the streamline diagram was obtained as a result of numerical simulation.
  • the gas phase refrigerant flowing out of the refrigerant inlet pipe 11 collides against the ceiling surface of the oil separator 10. Then, the gas phase refrigerant falls within the oil separator 10 while rotating, and rises again. In this process, the refrigerating machine oil is separated from the gas phase refrigerant, and the gas phase refrigerant from which the refrigerating machine oil is separated flows out of the oil separator 10 through the refrigerant outlet pipe 14.
  • the refrigerant inlet pipe 11 is introduced into the pressure container 20 through the upper end plate 23.
  • the refrigerant inlet pipe 11 may be introduced into the pressure container 20 through the side wall or the lower part (lower end plate 24) of the pressure container 20, provided that the angle ⁇ between a straight line along the direction of the opening of the delivery port 13 and a plane perpendicular to the central axis of the pressure container 20 satisfies 45° ⁇ ⁇ ⁇ 90° : such an oil separator is not within the scope of the present invention.
  • the oil separator 10 separates refrigerating machine oil contained in a gas phase refrigerant.
  • the oil separator 10 includes the cylindrical pressure container 20, the refrigerant inlet pipe 11 that leads the gas phase refrigerant containing the refrigerating machine oil into the pressure container 20, and the refrigerant outlet pipe 14 that discharges the gas phase refrigerant from which the refrigerating machine oil is separated.
  • the angle ⁇ between a straight line along the direction of the opening of the delivery port 13 at a tip of the refrigerant inlet pipe 11 introduced into the pressure container 20 and a plane perpendicular to the central axis of the pressure container 20 satisfies 45° ⁇ ⁇ ⁇ 90°.
  • the gas phase refrigerant flows out of the refrigerant inlet pipe 11 obliquely upward and collides against the pressure container 20, and a high rate of gas phase refrigerant reaches the ceiling of the pressure container 20. Then, the gas phase refrigerant flows downward from the ceiling of the pressure container 20 while rotating.
  • the second embodiment of the present disclosure provides an oil separator in which, in the first embodiment, when D is the inner diameter of the refrigerant inlet pipe 11, the distance x from the inner wall of the pressure container 20 to the center position of the delivery port 13 of the refrigerant inlet pipe 11 satisfies a relationship of D/2 ⁇ x ⁇ 1.6D.
  • the oil separation rate can be improved significantly.
  • the third embodiment of the present disclosure provides an oil separator in which, in the first or second embodiment, the direction of the opening of the delivery port 13 of the refrigerant inlet pipe 11 is not parallel with the surface normal direction of the inner wall of the pressure container 20 in the direction of the opening.
  • the gas phase refrigerant delivered from the delivery port 13 flows while deviating in a direction other than the delivery port 13, loss of kinetic energy can be suppressed, and as a result, a high-speed rotational flow can be generated.
  • the fourth embodiment of the present disclosure provides an oil separator in which, in any one of the first to third embodiments, the direction of the opening of the delivery port 13 is faced toward a curved portion of the upper end plate 23 of the pressure container 20.
  • the gas phase refrigerant can be smoothly directed upward in the pressure container 20, and loss of kinetic energy of the gas phase refrigerant can be suppressed.
  • the fifth embodiment of the present disclosure provides an oil separator in which, in any one of the first to fourth embodiments, the refrigerant inlet pipe 11 has the curved portion 12, and a reticulated member is provided inside the refrigerant inlet pipe 11 at the upstream side of the curved portion 12.
  • the reticulated member can be used to separate the refrigerating machine oil from the gas phase refrigerant to some extent, and the oil separation efficiency can be further improved.
  • the sixth embodiment of the present disclosure assumes that, in any one of the first to fifth embodiments, the refrigerant outlet pipe 14 is connected to the pressure container 20 on the central axis AX of the pressure container 20, and the refrigerant inlet pipe 11 is connected to the pressure container 20 at a position deviated from the central axis AX of the pressure container 20.
  • the refrigerant outlet pipe 14 is connected to the pressure container 20 on the central axis AX of the pressure container 20
  • the refrigerant inlet pipe 11 is connected to the pressure container 20 at a position deviated from the central axis AX of the pressure container 20.
  • the oil separator 10 is used for an air conditioner that includes one inverter compressor 30, but this is not a limitation; the oil separator 10 may be used for an air conditioner that includes a plurality of inverter compressors and constant-speed compressors. In addition, the oil separator 10 may also be used for a gas heat pump air conditioner.
  • the oil separator according to the present disclosure is useful as an oil separator that separates refrigerating machine oil contained in a gas phase refrigerant.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
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Claims (5)

  1. Séparateur d'huile (10) qui sépare l'huile de machine frigorifique contenue dans un fluide frigorigène en phase gazeuse par une force d'inertie et une force centrifuge, comprenant :
    un récipient cylindrique sous pression (20) comprenant une plaque d'extrémité supérieure (23) présentant une partie incurvée ;
    un tuyau d'entrée de fluide frigorigène (11) qui conduit le fluide frigorigène en phase gazeuse contenant l'huile de machine frigorifique dans le récipient cylindrique sous pression, le tuyau d'entrée de fluide frigorigène présentant un orifice de distribution (13), le sens de l'ouverture de l'orifice de distribution (13) étant tourné vers la partie incurvée de la plaque d'extrémité supérieure (23) du récipient cylindrique sous pression (20) ; et
    un tuyau de sortie de fluide frigorigène (14) qui évacue le fluide frigorigène en phase gazeuse à partir duquel l'huile de machine frigorifique est séparée,
    un angle α entre une ligne droite le long d'une direction d'une ouverture d'un orifice de distribution (13) au niveau d'une pointe du tuyau d'entrée de fluide frigorigène (11) introduite dans le récipient cylindrique sous pression (20) et un plan perpendiculaire à un axe central du récipient cylindrique sous pression satisfaisant à 45°≤ α < 90°,
    le tuyau d'entrée de fluide frigorigène (11) et le tuyau de sortie de fluide frigorigène (14) étant disposés sensiblement parallèlement à un axe central (AX) du récipient cylindrique sous pression (20) et pénétrant sensiblement verticalement la plaque d'extrémité supérieure (23),
    le tuyau d'entrée de fluide frigorigène (11) pénétrant la plaque d'extrémité supérieure (23) en une position écartée d'un centre (C) de la plaque d'extrémité supérieure (23),
    le tuyau d'entrée de fluide frigorigène (11) présentant une partie incurvée en forme de U à l'intérieur du récipient sous pression (20), de telle sorte que le sens de l'ouverture de l'orifice de distribution (13) est orienté vers le haut,
    caractérisé en ce que
    un tuyau de sortie d'huile (25) est disposé dans une plaque d'extrémité inférieure (24) du récipient sous pression (20) et
    le tuyau de sortie de fluide frigorigène (14) pénètre dans le centre (C) de la plaque d'extrémité supérieure (23) et
    une pointe (15) du tuyau de sortie de fluide frigorigène (14) s'étend davantage vers le bas que l'orifice de distribution (13) du tuyau d'entrée de fluide frigorigène (11) et le sens de l'ouverture de la pointe (15) est un sens verticalement vers le bas.
  2. Séparateur d'huile selon la revendication 1,
    dans lequel, lorsque D est un diamètre interne du tuyau d'entrée de fluide frigorigène (11), une distance x à partir d'une paroi interne du récipient cylindrique sous pression (20) jusqu'à une position centrale de l'orifice de distribution (139) satisfait à une relation de D/2 ≤ x ≤ 1,6D.
  3. Séparateur d'huile selon la revendication 1,
    dans lequel la direction de l'ouverture de l'orifice de distribution n'est pas parallèle à une direction normale de surface de la paroi interne du récipient cylindrique sous pression (20) dans la direction de l'ouverture (13).
  4. Séparateur d'huile selon la revendication 1,
    dans lequel le tuyau d'entrée de fluide frigorigène (11) présente une partie incurvée (12) et un élément réticulé est disposé à l'intérieur du tuyau d'entrée de fluide frigorigène au niveau d'un côté en amont de la partie incurvée (12).
  5. Séparateur d'huile selon la revendication 1,
    dans lequel le tuyau de sortie de fluide frigorigène (14) est relié au récipient cylindrique sous pression (20) sur l'axe central du récipient cylindrique sous pression et le tuyau d'entrée de fluide frigorigène (11) est relié au récipient cylindrique sous pression en une position écartée de l'axe central du récipient cylindrique sous pression.
EP15153295.9A 2014-02-13 2015-01-30 Séparateur d'huile Active EP2910875B1 (fr)

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Publication number Priority date Publication date Assignee Title
CN108168165B (zh) * 2018-02-13 2020-04-24 天津商业大学 一种氟制冷系统气液油分离器
JP7358833B2 (ja) * 2019-08-13 2023-10-11 富士電機株式会社 油分離装置
JP7453517B2 (ja) 2020-02-27 2024-03-21 東亜ディーケーケー株式会社 砂濾過装置の砂濾過ユニット

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JPH0610562B2 (ja) * 1987-08-31 1994-02-09 三菱電機株式会社 ヒートポンプ式冷暖房装置
JPH09210509A (ja) * 1996-02-07 1997-08-12 Sanyo Electric Co Ltd アキュムレータ

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JPH07218009A (ja) * 1994-02-01 1995-08-18 Hitachi Ltd 冷蔵庫用冷凍サイクル
JPH07260292A (ja) * 1994-03-23 1995-10-13 Matsushita Refrig Co Ltd 冷却システム
FR2718833B1 (fr) * 1994-04-19 1997-04-11 Daewoo Electronics Co Ltd Accumulateur destiné à être utilisé dans un réfrigérateur.
JPH11173706A (ja) * 1997-12-08 1999-07-02 Mitsubishi Electric Corp オイルセパレータ
JP4294764B2 (ja) * 1998-09-10 2009-07-15 三菱電機株式会社 冷凍サイクル
KR100613505B1 (ko) * 2004-02-25 2006-08-17 엘지전자 주식회사 냉동 사이클 장치
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JP2011058431A (ja) * 2009-09-10 2011-03-24 Toshiba Carrier Corp 密閉型回転式圧縮機および冷凍サイクル装置
KR20110119553A (ko) * 2010-04-26 2011-11-02 니찌레이 고오교오 가부시끼가이샤 기액 분리 장치 및 기액 분리 장치를 구비한 냉동 장치
JP6296322B2 (ja) * 2013-02-20 2018-03-20 パナソニックＩｐマネジメント株式会社 オイルセパレータ

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JPH0610562B2 (ja) * 1987-08-31 1994-02-09 三菱電機株式会社 ヒートポンプ式冷暖房装置
JPH09210509A (ja) * 1996-02-07 1997-08-12 Sanyo Electric Co Ltd アキュムレータ

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KR102183547B1 (ko) 2020-11-26
CN104848615B (zh) 2019-05-14
JP2015166668A (ja) 2015-09-24
JP6403061B2 (ja) 2018-10-10
CN104848615A (zh) 2015-08-19
EP2910875A1 (fr) 2015-08-26

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