EP3670918A1 - Drehmechanismus - Google Patents

Drehmechanismus Download PDF

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Publication number
EP3670918A1
EP3670918A1 EP18846743.5A EP18846743A EP3670918A1 EP 3670918 A1 EP3670918 A1 EP 3670918A1 EP 18846743 A EP18846743 A EP 18846743A EP 3670918 A1 EP3670918 A1 EP 3670918A1
Authority
EP
European Patent Office
Prior art keywords
discharge
oil
end surface
rotating member
compressor
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.)
Pending
Application number
EP18846743.5A
Other languages
English (en)
French (fr)
Other versions
EP3670918A4 (de
Inventor
Genhui ZHAO
Shi Wang
Qiming ZHOU
Anbing MAO
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.)
Copeland Climate Technologies Suzhou Co Ltd
Original Assignee
Emerson Climate Technologies Suzhou Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201710701301.0A external-priority patent/CN109404289B/zh
Priority claimed from CN201721025170.0U external-priority patent/CN207437367U/zh
Application filed by Emerson Climate Technologies Suzhou Co Ltd filed Critical Emerson Climate Technologies Suzhou Co Ltd
Publication of EP3670918A1 publication Critical patent/EP3670918A1/de
Publication of EP3670918A4 publication Critical patent/EP3670918A4/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/98—Lubrication

Definitions

  • the present disclosure relates to a rotary machinery.
  • a compressor typically includes a compression mechanism, a drive shaft and a motor.
  • the drive shaft is supported by a bearing in a bearing housing and is driven to rotate by the motor.
  • the rotation of the drive shaft further drives the movable components of the compression mechanism (for example, an orbiting scroll of the scroll compressor, a rotor of the rotor compressor or the like) to move so as to compress working fluid (for example, refrigerant).
  • Each of movable components of the compressor (for example, the orbiting scroll of the scroll compressor, the rotor of the rotor compressor, the bearing or the like) needs to be lubricated by lubricating oil to maintain the operation stability and reliability of the movable component and the entire compressor. Therefore, a lubricating oil circulation system for the compressor is an important part of the compressor.
  • the lubricating oil When the compressor is operated, the lubricating oil is transported from an oil pool to each movable component of the compressor under differential pressure or by an oil pumping mechanism, for example, to lubricate each component so as to maintain the normal operation of each movable component, and finally returns to the oil pool.
  • an oil pumping mechanism for example, to lubricate each component so as to maintain the normal operation of each movable component, and finally returns to the oil pool.
  • it may also take away impurities between the contact surfaces of components to reduce abrasion, and heat generated by each component due to friction or current.
  • the lubricating oil discharged from the compressor along with the working fluid will also adhere to, for example, coils of condensers and evaporators, thereby affecting the heat exchange efficiency of the working fluid with the ambient air. Therefore, it is necessary for the compressor to properly control the lubricating oil circulation rate (also called an oil circulation rate).
  • the oil circulation rate may be understood as the (mass) ratio of the lubricating oil contained in unit working fluid discharged from the compressor.
  • an oil-gas separating device may be disposed in the compressor.
  • the internal space of the compressor casing is limited, it is desired to provide a compressor with a simple structure and small space occupation, and capable of efficiently controlling the oil circulation rate.
  • An object of the present disclosure is to provide a rotary machinery with a simple structure and small space occupation and capable of efficiently controlling the oil circulation rate.
  • Another object of the present disclosure is to provide a compressor with simplified manufacture and assembly and low cost and capable of reasonably controlling the oil circulation rate of the compressor.
  • a rotary machinery including a casing, a rotating member, and a discharge member.
  • the casing contains an oil-gas mixture therein.
  • the rotating member is disposed in the casing and is rotatable around a rotating axis to drive the oil-gas mixture to form a cyclone flow, whereby under a centrifugal force, an oil content in the oil-gas mixture decreases as it approaches the rotating member.
  • the discharge member is disposed on the casing and extends radially inward from the casing to a position where the oil content is less than or equal to a predetermined content.
  • the rotating machinery according to the present disclosure can well control the lubricating oil circulation rate.
  • a predetermined distance exists between an end portion of the discharge member located inside the casing and an outer peripheral surface of the rotating member, the ratio of the predetermined distance to the diameter of a circular discharge passage of the discharge member is less than 1.5.
  • the ratio of the predetermined distance to the diameter of the circular discharge passage of the discharge member is greater than 0.25.
  • the ratio of the predetermined distance to the diameter of the circular discharge passage is between 0.4 and 0.5.
  • the rotating member has a first axial end surface and a second axial end surface in an axial direction, and the discharge member is positioned between a first axial position and a second axial position. If the discharge member is in the first axial position, a one radial side of the discharge passage of the discharge member is located axially outside of the first axial end surface and the other radial side opposite to the one radial side of the discharge passage is aligned with the first axial end surface. If the discharge member is in the second axial position, the other radial side of the discharge passage is located axially outside of the second axial end surface and the one radial side of the discharge passage is aligned with the second axial end surface.
  • the discharge member is positioned to be substantially aligned with an axial central portion of the rotating member.
  • an end portion of the discharge member adjacent to the rotating member linearly extends in a horizontal direction perpendicular to the rotating axis, and an end surface of the end portion is oriented obliquely with respect to an outer peripheral surface of the rotating member.
  • an end portion of the discharge member adjacent to the rotating member is bent in a circumferential direction of the rotating member and / or in a vertical direction parallel to the rotating axis
  • a discharge opening of the discharge member is oriented to face a downstream side of a rotating direction of the rotating member, and the oil-gas mixture in the casing enters the discharge member via the discharge opening.
  • the rotating member has a first axial end surface and a second axial end surface in an axial direction
  • the discharge member is positioned axially outside of the first axial end surface or of the second axial end surface, and an end portion of the discharge member located in the casing extends inward to be flush with an outer peripheral surface of the rotating member or to be radially inside of the outer peripheral surface of the rotating member.
  • the rotating member is in the form of a cam, an eccentric part, or a counterweight
  • the discharge member is in the form of a discharge pipe or a discharge passage.
  • the rotatory machinery further includes a compression mechanism, a drive shaft, and a motor.
  • the compression mechanism is located in the casing and is configured to compress working fluid.
  • the drive shaft is adapted to drive the compression mechanism.
  • the motor includes a stator and a rotor rotatable with respect to the stator and configured to drive the drive shaft to rotate.
  • the rotating member is disposed on the drive shaft or disposed on the rotor.
  • the rotating member is located between the compression mechanism and the motor or between the motor and an oil sump.
  • the rotary machinery is a high side scroll compressor.
  • the lubricating oil may be separated from the oil-gas mixture under the centrifugal force before the oil-gas mixture exits from the compressor, so as to well control the lubricating oil circulation rate.
  • the oil level of the oil pool in the compressor may be maintained at a desired level.
  • the amount of the lubricating oil exiting from the compressor and entering the compressor system may be reduced, for example, the amount of the lubricating oil entering the heat exchanger may be reduced, thereby improving the overall working efficiency of the compressor system.
  • the "longitudinal direction” or “axial direction” mentioned for the component herein refers to the direction parallel to the rotating axis
  • the “radial direction” mentioned for the component herein refers to the direction perpendicular to the rotating axis.
  • the compressor 10 includes a casing 11, and a compression mechanism 12, a motor 13 and a drive shaft (also referred to as a rotating shaft or a crankshaft) 14 which are disposed in the casing 11.
  • the motor 13 includes a stator 13b fixed to the casing 11 and a rotor 13a located at the inner side of the stator 13b and fixed to the drive shaft 14.
  • the rotor 13a rotates and drives the drive shaft 14 to rotate with it.
  • the drive shaft 14 is fitted with the compression mechanism 12 so as to drive the compression mechanism 12 to compress the working fluid (usually gaseous) when the drive shaft 14 rotates.
  • an eccentric crank pin 14b of the drive shaft 14 is fitted in an orbiting scroll 12b of the compression mechanism 12 to drive the orbiting scroll 12b to rotate.
  • the compressor 10 further includes a main bearing housing 15 fixed to the casing 11.
  • the main bearing housing 15 rotatably supports the drive shaft 14 via the main bearing 15a, and supports the compression mechanism 12, particularly the orbiting scroll component 12b.
  • the compression mechanism 12 includes a non-orbiting scroll component 12a fixed to the casing 11 or the main bearing housing 15, and the orbiting scroll component 12b movable with respect to the non-orbiting scroll component 12a.
  • the orbiting scroll component 12b orbits relative to the non-orbiting scroll component 12a (that is, the central axis of the orbiting scroll component moves around the central axis of the non-orbiting scroll component, but the orbiting scroll component itself does not rotate around its own central axis).
  • a series of compression chambers whose volume gradually decreases from the radial outer side to the radial inner side are formed between the spiral vanes of the non-orbiting scroll component 12a and the spiral vanes of the orbiting scroll component 12b.
  • the working fluid is compressed in these compression chambers, and then discharged through a discharge hole 17 of the compression mechanism 12.
  • the discharge hole 17 of the compression mechanism 12 is generally disposed at approximately the center of the end plate of the non-orbiting scroll component 12a.
  • a centrifugal force or centrifugal torque generated by the rotation of the eccentric component causes the compressor to vibrate.
  • a counterweight is disposed on a rotating component to provide a reverse centrifugal force or centrifugal torque to counteract the imbalance generated by the eccentric component.
  • a counterweight 110 is fixed on the outer peripheral surface of the drive shaft 14 and is adjacent to the main bearing housing 15; a counterweight 210 is disposed on an end surface of the rotor 13a of the motor 13 facing the compression mechanism 12; and a counterweight 310 is disposed on an end surface of the rotor 13a of the motor 13 facing away from the compression mechanism 12.
  • the compressor in the figure includes three counterweights, it should be understood that the number of counterweights may vary according to specific application requirements.
  • an oil sump 20 for storing lubricating oil is disposed at the bottom of the compressor casing 11.
  • the drive shaft 14 may be formed therein with a passage 14a extending substantially along the axial direction of the drive shaft 14.
  • the lubricating oil in the oil sump 20 is supplied to each bearing of the compressor, the bearing surface of the main bearing housing 15 and the orbiting scroll component 12b, the compression mechanism and the like through this passage 14a. After various components of the compressor are lubricated, the lubricating oil returns to the oil sump 20.
  • the compressor 10 is a high side scroll compressor.
  • a discharge pipe (a discharge member) 130 is disposed on the casing 11.
  • the low pressure working fluid is directly supplied into a suction chamber or a low pressure chamber of the compression mechanism 12 through an intake pipe (not shown) and a suction hole (not shown) of the compression mechanism, and then is compressed and discharged from the discharge hole 17 of the compression mechanism 12 into a space surrounded by the casing 11 of the compressor.
  • the discharge pipe 130 is hermetically installed in the casing 11 to discharge the compressed gas out of the compressor 10.
  • the working fluid discharged from the discharge hole 17 is mixed with lubricating oil, and the lubricating oil supplied from the passage 14a of the drive shaft 14 is distributed in a space within the compressor casing 11 in the form of oil mist, due to the movement of the orbiting scroll component 12b, the rotor 13a of the motor 13, and the like. Therefore, the high pressure working fluid to be discharged through the discharge pipe 130 out of the compressor often contains lubricating oil, and thus it is necessary to control the amount of lubricating oil in the working fluid discharged out of the compressor via the discharge pipe 130, thereby controlling the oil circulation rate (OCR) of the entire compressor.
  • OCR oil circulation rate
  • an oil-gas separating device may be disposed in the compressor 10.
  • the additional oil-gas separating device requires a certain space and complicates the manufacturing and assembly process. Especially when the internal space of the compressor is limited, it is not suitable to additionally install the oil-gas separating device.
  • the inventors of the present disclosure have conceived a solution in which the lubricating oil may be separated from the high pressure working fluid with a centrifugal force by using members that already exist in the compressor and only by reasonably configuring the relative positional relationship between the members, and the working fluid containing a reduced content of lubricating oil or even containing no lubricating oil is discharged, thereby reasonably controlling the oil circulation rate (OCR) of the compressor.
  • OCR oil circulation rate
  • the oil-gas separating device includes the counterweight 110 and the discharge pipe 130.
  • the counterweight 110 is fixed to the outer peripheral surface of the drive shaft 14 and may be rotated together with the drive shaft 14.
  • the rotating axis of the counterweight 110 is also the rotating axis of the drive shaft 14, that is, the longitudinal central axis of the drive shaft 14.
  • the discharge pipe 130 is located outside the counterweight 110 in the radial direction and is fixed on the casing 11 hermetically.
  • the counterweight 110 has an outer peripheral surface 111 adjacent to and facing the discharge pipe 130, and a first axial end surface 115 and a second axial end surface 117 opposite to each other.
  • the counterweight may have a radial protrusion 112 protruding radially outward, and an axial protrusion 114 extending axially from the second axial end surface 117.
  • the structure of the counterweight (especially the position, size and number of the protrusions) may vary according to the specific application.
  • the counterweight may have only one of a radial protrusion and an axial protrusion.
  • the counterweight may have an axial protrusion extending axially from the first axial end surface.
  • the radial protrusion 112 and the axial protrusion 114 of the counterweight 110 may agitate the oil-gas mixture surrounding them and discharged from the discharge hole 17 and force the oil-gas mixture surrounding them to form a cyclone flow.
  • the lubricating oil in the oil-gas mixture is thrown radially outward to the casing 11 and flows down along the casing 11 back into the oil sump 20 under gravity. In this way, the content of lubricating oil in the oil-gas mixture close to the counterweight 110 is low, while the content of lubricating oil in the oil-gas mixture close to the casing 11 is high.
  • the content of the lubricating oil in the oil-gas mixture increases in a direction from the counterweight 110 to the casing 11.
  • the content of lubricating oil in the oil-gas mixture on the radial inner side of the cyclone flow is smaller than the content of lubricating oil in the oil-gas mixture on the radial outer side of the cyclone flow. Therefore, the inventors propose positioning an end portion of the discharge pipe provided inside the casing within the area of the cyclone flow generated by the rotation of the counterweight, and particularly within the radial inner side of the cyclone flow.
  • the desired content of the lubricating oil in the oil-gas mixture to be discharged may be predetermined according to a desired oil circulation rate.
  • the position of the discharge pipe may be determined according to the predetermined desired content (also referred to as a "predetermined content"). That is, the discharge pipe may be extended radially inward from the casing to a position where the content of the lubricating oil in the oil-gas mixture is less than or equal to the predetermined content.
  • predetermined desired content also referred to as a "predetermined content”
  • the inventive concept of the present disclosure is based on the principle that the cyclone flow generated by the rotation of counterweight 110 causes the gradient change in the content of lubricating oil between the counterweight 110 and the casing 11 and the relative positional relationship between the discharge pipe 130 and the counterweight 110 is determined to obtain the desired and reduced oil circulation rate.
  • a length of the discharge pipe may extend into the compressor casing. In this case, the extension length of the discharge pipe only needs to meet the installation requirements, and thus the extension end of the discharge pipe tends to be closer to the compressor casing.
  • a length of the discharge pipe may also extend into the compressor casing to prevent the lubricating oil from flowing into the discharge pipe.
  • the setting of the extension length of the discharge pipe in the conventional compressor has nothing to do with the rotation of the counterweight, the cyclone flow generated by the rotation of counterweight, and the like.
  • the discharge pipe 130 may be positioned closer to the counterweight 110 according to the inventive concept of the present disclosure.
  • the discharge pipe 130 is disposed adjacent to the counterweight 110, that is, positioned at a predetermined distance from the outer peripheral surface of the counterweight 110 to discharge the working fluid containing a reduced content of lubricating oil, or even containing no lubricating oil, as required.
  • the discharge pipe 130 is a circular tubular member and has a circular discharge passage 133.
  • the discharge pipe 130 also has an end surface 131 adjacent to the counterweight 110.
  • the end surface 131 of the discharge pipe 130 located inside the casing extends inward from a wall of the casing to the vicinity of the counterweight 110.
  • the distance L may be determined according to the working conditions, for example, the rotating speed of the counterweight 110, the ambient pressure, the distance from the counterweight 110 to the casing 11, the content of lubricating oil in the working fluid discharged via the discharge hole 17, and the desired content of lubricating oil in the working fluid to be discharged via the discharge pipe 130 and the like.
  • the distance L may be predetermined or may vary according to the operation condition of a compressor.
  • the end surface 131 of the discharge pipe 130 is as close as possible to the outer peripheral surface 111 of the counterweight 110 to provide a better oil-gas separating effect, and it is also desirable that the distance between the end surface 131 of the discharge pipe 130 and the outer peripheral surface 111 of the counterweight 110 should not be too small to disadvantageously reduce a flow area of the discharge pipe 130.
  • “Lower content of lubricating oil” or “reduced content of lubricating oil” or the like mentioned herein refers to that the content of lubricating oil in the working fluid discharged via the discharge pipe 130 is less than the content of lubricating oil in the working fluid in the compressor casing 11 and is within a suitable range of lubricating oil circulation rate (OCR).
  • OCR lubricating oil circulation rate
  • a ratio L / D of the distance L to the diameter D may be less than about 1.5. In some examples, the ratio L / D of the distance L to the diameter D may be greater than about 0.25. In some examples, the ratio L / D of the distance L to the diameter D may be between about 0.25 and 1.25, between about 0.4 and 1, between about 0.4 and 0.75, preferably between about 0.4 and 0.5. More preferably, the ratio of the distance L to the diameter D may be about 0.5.
  • FIG. 7 a graph showing the distance between the discharge pipe and the counterweight versus the circulation rate when a compressor is operated at 5400 RPM (revolutions per minute) is illustrated.
  • the abscissa represents the radial distance L between the end surface of the discharge pipe and the outermost peripheral surface of the counterweight, where D represents the inner diameter of the discharge pipe; the ordinate represents an oil circulation rate OCR of the compressor.
  • L is about 1/2 D
  • the oil circulation rate of the compressor is the lowest, about 1.08%.
  • the compressor in the prior art when the compressor is operated at 5400 RPM, its oil circulation rate exceeds 5%.
  • the oil circulation rate of the compressor can be significantly reduced, which achieves significantly unexpected technical effects.
  • the conventional compressor and the compressor according to the present disclosure are tested by the inventors, and test results are listed in the following table.
  • the test is performed on one set of conventional compressors (C1) and three sets of compressors of the present disclosure (T1, T2, and T3) under different working conditions (different rotating speeds of the counterweight), and in the test, the ratio of the distance L to the diameter D is 0.4 in the compressor of the present disclosure.
  • Test results in the table are the content of lubricating oil in the separated working fluid.
  • the discharge pipe extends into the compressor casing only for convenience of assembly, but is far away from the counterweight, that is, the distance between the discharge pipe and the counterweight is far greater than the inner diameter of the discharge pipe.
  • Figure 8a is a cross sectional view illustrating the oil-gas distribution of the oil-gas separating device according to the present disclosure
  • Figure 8b is a cross sectional view illustrating the oil-gas distribution of the oil-gas separating device in a comparison example.
  • Figure 8b there is a region with higher lubricating oil content at the vicinity of the outer peripheral surface of the counterweight, and there is also a region with higher lubricating oil content at the vicinity of the compressor casing, and the content of lubricating oil contained in the working fluid discharged from the discharge pipe is higher.
  • the region with higher lubricating oil content is concentrated at the vicinity of the casing. Therefore, a smaller content of lubricating oil is contained in the working fluid discharged from the discharge pipe adjacent to the counterweight, thereby reducing the oil circulation rate of the compressor.
  • the counterweight is used as an active rotating member, and when it rotates, oil-gas mixture surrounding it is forced to form a cyclone flow, whereby throwing radially outward the lubricating oil with a larger specific gravity under the action of centrifugal force. Therefore, the working fluid close to the counterweight contains therein less lubricating oil, and is easily discharged from the discharge pipe disposed close to the counterweight.
  • the end surface 131 of the discharge pipe 130 may not be parallel to the outer peripheral surface 111 of the counterweight 110 in the direction of the rotating axis of the counterweight 110, but may face the counterweight 110 and is oblique with respect to the outer peripheral surface 111 of the counterweight 110.
  • a discharge opening of the discharge pipe 130 may be oriented to face the downstream side in the rotating direction of the counterweight, and oil-gas mixture inside the compressor casing enters the discharge pipe via the discharge opening and is discharged from the compressor via the discharge pipe. In this way, the amount of lubricating oil entering the discharge pipe 130 can be decreased, and a better oil-gas separating effect can be implemented.
  • the discharge pipe 130 may linearly extend from the compressor casing in a horizontal direction perpendicular to the direction of the rotating axis of the counterweight 110.
  • the end surface 131 of the discharge pipe 130 is oriented toward the outer peripheral surface 111 of the counterweight 110 and is oblique with respect to the outer peripheral surface 111 of the counterweight 110.
  • the angle between the end surface 131 of the discharge pipe 130 and the central longitudinal axis of the discharge pipe 130 is greater than 0 degree but less than 90 degrees.
  • an end portion of the discharge pipe 130 adjacent to the counterweight 110 may be bent in a circumferential direction of the counterweight 110 and / or in a vertical direction parallel to the rotating axis of the counterweight 110. That is, the discharge pipe 130 may include a bent end portion located in the casing. The bent end portion may be a curved arc shape or may be bent at a constant angle.
  • a bent end portion 230 of the discharge pipe 130 is bent in the circumferential direction of the counterweight 110.
  • a discharge opening at the end surface 231 of the bent end portion 230 may face downstream in the rotating direction of the counterweight 110. Therefore, a better oil-gas separating effect can be achieved.
  • a bent end portion 330 of the discharge pipe 130 is bent in a vertical direction parallel to the rotating axis of a counterweight 110.
  • an end surface 331 of the bent end portion 330 may be oriented downward.
  • the end surface 331 of the bent end portion 330 may be oriented downward or may be oriented in any other suitable direction capable of reducing the amount of the lubricating oil entering the discharge pipe.
  • the discharge pipe 130 may be positioned within a range of a cyclone flow caused by the rotation of the counterweight 110.
  • the discharge pipe 130 may be positioned between a first axial position P1 and a second axial position P2.
  • the discharge pipe 130 is located on an axial outer side of a first axial end surface 115 of a counterweight 110 and is substantially aligned with the first axial end surface 115.
  • one radial side of a discharge passage 133 of the discharge pipe 130 is located axially outside of the first axial end surface 115, and the other radial side opposite to the one radial side of the discharge passage 133 is substantially aligned with the first axial end surface 115.
  • the discharge pipe 130 in the first axial position PI, is located below the first axial end surface 115 of the counterweight 110 in the axial direction, and an axially uppermost portion of the discharge passage of the discharge pipe 130 is substantially aligned with the first axial end surface 115.
  • the discharge pipe 130 is located on an axial outer side of the second axial end surface 117 of the counterweight 110 and is substantially aligned with the second axial end surface 117.
  • said other radial side of the discharge passage of the discharge pipe 130 is located axially outside of the second axial end surface 117, and said one radial side of the discharge passage is substantially aligned with the second axial end surfaces 117.
  • the discharge pipe 130 in the second axial position P2, is located above the second axial end surface 117 of the counterweight 110 in the axial direction, and an axially lowermost portion of the discharge passage of the discharge pipe 130 is substantially aligned with the second axial end surface 117.
  • the discharge pipe 130 may also be positioned on an axial outer side of the first axial position P1 or an axial outer side of the second axial position P2 (that is, lower than the first axial position P1 or higher than the second axial position P2) and may further extend inward in the radial direction, for example, to be flush with the outer peripheral surface 111 of the counterweight 110, or even to a radial inside of the outer peripheral surface 111 of the counterweight 110. Due to the cyclone flow caused by the rotation of the counterweight 110, the working fluid discharged from the discharge pipe 130 can still maintain a lower oil circulation rate (OCR).
  • OCR oil circulation rate
  • the counterweight 110 is disposed on the outer peripheral surface of the drive shaft 14.
  • the oil-gas separating device may include a counterweight disposed on any other suitable rotating members and a discharge pipe.
  • an oil-gas separating device may include a counterweight 210 disposed on an end surface 1301 of a rotor 13a of a motor 13 facing the compression mechanism.
  • an oil-gas separating device may include a counterweight 310 disposed on an end surface 1302 of the rotor 13a of the motor 13 facing away from the compression mechanism. The mutual positional relationship and dimensional relationship between the discharge pipe 130 and the counterweight may be appropriately set with reference to the above description.
  • the oil-gas separating device is disposed between the main bearing housing 15 and the motor 13.
  • the oil-gas separating device may be disposed in any suitable position of an internal space defined by the compressor casing 11.
  • the oil-gas separating device may be located between the motor 13 and the oil sump 20.
  • the counterweight may have any suitable structure, as long as the counterweight can rotate and force the oil-gas mixture surrounding it to form a cyclone flow.
  • the counterweight may have a constant radial dimension or a variable radial dimension, and / or may have a constant axial dimension or a variable axial dimension.
  • the counterweight may have a cylindrical outer peripheral surface, a tapered outer peripheral surface, or any other outer peripheral surfaces with suitable shape capable of implementing the above effect.
  • the counterweight illustrated in the figure may be replaced by a cam, an eccentric part, or any other suitable members capable of implementing the above effect.
  • the discharge pipe may have any suitable structure and / or number, as long as it can facilitate the discharge of the working fluid.
  • the discharge pipe may include a flared end portion.
  • the discharge pipe may include an end portion disposed obliquely with respect to the outer peripheral surface of the counterweight.
  • an end portion of the discharge pipe adjacent to the counterweight is obliquely downward, which may facilitate the outflow of the lubricating oil on the inner wall of the discharge pipe.
  • the compressor in the figure includes one discharge pipe; however, the number of discharge pipes may be plural.
  • the discharge pipe illustrated in the figure may also be replaced by a discharge passage disposed in a fixed structure.
  • the oil-gas separating device may have no a bottom portion, thus the lubricating oil may be dropped directly into the oil sump along the wall.
  • Other variations and modifications can be implemented by those skilled in the art without departing from the essence and scope of the present disclosure. All the variations and modifications are within the scope of the present disclosure.
  • all of the members described herein may be replaced by other technically equivalent members.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP18846743.5A 2017-08-16 2018-07-19 Drehmechanismus Pending EP3670918A4 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CN201710701301.0A CN109404289B (zh) 2017-08-16 2017-08-16 旋转机械
CN201721025170.0U CN207437367U (zh) 2017-08-16 2017-08-16 旋转机械
PCT/CN2018/096240 WO2019033894A1 (zh) 2017-08-16 2018-07-19 旋转机械

Publications (2)

Publication Number Publication Date
EP3670918A1 true EP3670918A1 (de) 2020-06-24
EP3670918A4 EP3670918A4 (de) 2021-04-28

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EP18846743.5A Pending EP3670918A4 (de) 2017-08-16 2018-07-19 Drehmechanismus

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EP (1) EP3670918A4 (de)
JP (3) JP2020531728A (de)
KR (1) KR20200040802A (de)
WO (1) WO2019033894A1 (de)

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KR102500686B1 (ko) * 2021-03-19 2023-02-17 엘지전자 주식회사 밀폐형 압축기

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Also Published As

Publication number Publication date
WO2019033894A1 (zh) 2019-02-21
JP2020531728A (ja) 2020-11-05
EP3670918A4 (de) 2021-04-28
JP3242528U (ja) 2023-06-22
JP2022183232A (ja) 2022-12-08
KR20200040802A (ko) 2020-04-20

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