WO2020093924A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2020093924A1
WO2020093924A1 PCT/CN2019/114651 CN2019114651W WO2020093924A1 WO 2020093924 A1 WO2020093924 A1 WO 2020093924A1 CN 2019114651 W CN2019114651 W CN 2019114651W WO 2020093924 A1 WO2020093924 A1 WO 2020093924A1
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WO
WIPO (PCT)
Prior art keywords
scroll
oil
fixed scroll
passage
lubricating oil
Prior art date
Application number
PCT/CN2019/114651
Other languages
English (en)
French (fr)
Inventor
贾祥敏
赵小冬
周启明
Original Assignee
艾默生环境优化技术(苏州)有限公司
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 CN201821822846.3U external-priority patent/CN209244821U/zh
Priority claimed from CN201811312810.5A external-priority patent/CN111140495B/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2020093924A1 publication Critical patent/WO2020093924A1/zh

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    • 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
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present application relates to a scroll compressor, and in particular to a scroll compressor that improves the oil supply lubrication of the contact portion between the outer peripheral end surface of the fixed scroll and the end plate of the movable scroll.
  • Compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems.
  • the scroll compressor includes: a compression mechanism including a fixed scroll and a movable scroll, the fixed scroll and the movable scroll are engaged with each other to define a series of working fluid receiving chambers; and a main bearing housing, the main bearing housing The movable scroll is supported and fixedly connected with the fixed scroll. The movable scroll is located between the main bearing seat and the fixed scroll and can perform orbital motion relative to the fixed scroll.
  • the peripheral wall of the fixed scroll The end face of the end plate of the movable scroll and the area on the one side of the end plate of the movable scroll located radially outside of the movable scroll wrap contact each other to form a contact portion.
  • the movable scroll orbits relative to the fixed scroll Relative motion, there is relative friction between the two contact surfaces of the contact part to generate more heat, and when there are impurities between the two contact surfaces, it will greatly accelerate the movable scroll and the fixed scroll Failure due to wear.
  • Existing compressors cannot effectively remove impurities between the contact surfaces and cannot effectively discharge heat generated by friction between the contact surfaces.
  • the present application provides a scroll compressor as described below, which can significantly improve the oil supply lubrication performance and the lubricating performance in the contact portion between the outer peripheral end surface of the fixed scroll and the end plate of the movable scroll
  • the heat dissipation performance of the compression mechanism can take away impurities in the contact portion, thereby significantly reducing the risk of the fixed scroll and the movable scroll being worn and failing.
  • a scroll compressor including:
  • the fixed scroll includes a fixed scroll end plate, and a side surface from the fixed scroll end plate A fixed scroll wrap extending from the side and a peripheral wall extending from the side and radially outward of the fixed scroll wrap
  • the movable scroll plate includes a movable scroll disk end plate, and a movable scroll disk end A movable scroll wrap extending from the first side of the plate and a hub extending from the second side of the movable scroll end plate, the fixed scroll wrap and the movable scroll wrap engage each other to define a series of operations Fluid receiving chamber;
  • a main bearing seat which supports the movable scroll and is fixed with the fixed scroll such that the movable scroll is located between the fixed scroll and the main bearing seat and is The orbiting scroll is capable of orbiting relative to the fixed scroll;
  • the peripheral wall of the fixed scroll and the first side surface of the movable scroll end plate are in contact with each other to form a contact portion
  • the scroll compressor is further provided with an oil delivery passage
  • the oil delivery passage includes: Fluid communication from the lubricating oil source to at least one first oil delivery path at the contact portion; fluid communication with the at least one first oil delivery path to guide at least one oil delivery in the contact portion An oil sump; and at least one second oil transfer passage in fluid communication with the at least one oil transfer sump to discharge lubricating oil directly to the outside of the compression mechanism.
  • the oil delivery passage supplies lubricating oil to the contact portion, guides the flow of lubricating oil in the contact portion, and then directly discharges the lubricating oil at the contact portion to From the outside of the compression mechanism, it can be seen that with this configuration, sufficient lubricating oil can be supplied to the contact area between the outer peripheral end surface of the fixed scroll and the end plate of the movable scroll, not only to ensure Good lubricating performance under conditions, and the lubricating oil supplied to the contact area can also carry impurities that may be present in the contact area and the heat in the entire compression mechanism is discharged to compression through the oil delivery passage Outside the mechanism, the lubricating oil supplied to the contact area will not enter the closed compression chamber formed by the fixed scroll and the movable scroll under the guidance of the oil tank, thereby preventing impurities from entering the compression chamber In order to prevent the scroll from being worn and failing, and by taking away the heat, the compression mechanism can be prevented from overheating.
  • the first oil delivery passage includes: a first inlet fluidly connected to the lubricating oil source; a first outlet opening toward the contact portion; and extending from the first inlet to all A first passage of the first outlet, and the second oil delivery passage includes: a second inlet opening toward the contact portion; a second outlet opening toward the outside of the compression mechanism; and from the second inlet A second channel extending to the second outlet.
  • the contact portion includes an annular first contact area located on an end face of the peripheral wall of the fixed scroll and an annular first contact area located on the first side of the movable scroll end plate Two contact areas, each of the first outlet, the oil delivery tank, and the second inlet is provided in any one of the first contact area and the second contact area.
  • the first outlet, the oil trough and the second inlet are all provided in the first contact area or are all provided in the second contact area, the first outlet The second inlet is positioned at a position diametrically opposed to the first contact area or the second contact area.
  • the first passage includes at least one of a passage provided in the fixed scroll, a passage provided in the movable scroll, and an independent pipe, or includes a passage provided in A combination of at least one of the passage in the fixed scroll, the passage provided in the movable scroll, and the independent pipe and the passage provided in the main bearing housing;
  • the second channel includes at least one of a channel provided in the fixed scroll, a channel provided in the movable scroll, and an independent pipe, or a channel provided in the fixed scroll A combination of at least one of the channel, the channel provided in the movable scroll, and the independent tube and the channel provided in the main bearing seat.
  • the oil delivery groove is formed as an arc-shaped, spiral-shaped or annular groove.
  • At least a portion of the oil delivery groove is immediately adjacent to the radially outermost outer side wall of the fixed scroll or the movable scroll.
  • the first contact area includes a first sub-area that remains in contact with the second contact area during work and a second sub-area that intermittently contacts the second contact area during work,
  • the first outlet, the oil tank and / or the second inlet are provided in the first sub-region.
  • the lubricating oil source includes at least one of the following items: an oil sump at the bottom of the casing of the scroll compressor, an oil storage recess of the main bearing housing, defined in The space between the end plate of the movable scroll and the end surface of the drive shaft for driving the hub, and the compression chamber in the working fluid receiving chamber.
  • the main bearing housing includes an oil reservoir extending along an edge of the central through hole adjacent to the hub, and the first inlet is in communication with the oil reservoir.
  • the at least one second oil transfer passage is provided to directly discharge the lubricating oil to the outside of the space formed by the compression mechanism and the main bearing housing.
  • the scroll compressor is a high-pressure side scroll compressor.
  • the scroll compressor according to the present application provides at least the following beneficial effects: the scroll compressor according to the present application can directly face the outer peripheral end surface of the fixed scroll and the movable scroll by providing the above-mentioned oil delivery passage Lubricating oil is supplied in the contact portion between the end plates, and the lubricating oil supplied to the contact portion can be discharged to the outside of the compression mechanism.
  • the scroll compressor of the present application can significantly improve the supply of the contact portion Oil lubrication performance and heat dissipation performance of the compression mechanism, and can remove impurities in the contact portion and prevent impurities from entering the closed compression chamber formed by the fixed scroll and the movable scroll scroll, thereby significantly reducing the fixed scroll and The risk of the orbiting scroll being worn and failing, and the scroll compressor of the present application has a simple structure, is easy to process and manufacture, and has high cost efficiency.
  • FIG. 1 shows a longitudinal sectional view of a scroll compressor according to the present application, which shows the arrangement of a fixed scroll and a movable scroll;
  • FIG. 2 shows an enlarged view of a partial longitudinal cross-section of the scroll compressor in FIG. 1 including a compression mechanism, which shows the arrangement of an oil supply passage according to a preferred embodiment of the present application;
  • FIG. 3 shows a schematic cross-sectional perspective view of the fixed scroll of FIG. 2 with the end plate of the fixed scroll removed, wherein the arrangement of the oil supply passage in FIG. 2 is shown in detail;
  • 4a and 4b show the arrangement of oil supply passages according to other embodiments of the present application.
  • FIG. 5 shows a cross-sectional view of an orbiting scroll according to the present application, in which the arrangement of an oil supply passage according to another embodiment of the present application is shown.
  • Scroll compressor 1 housing 12; drive shaft 16; main bearing housing 11; cover 26; base 28
  • Oil delivery passage 13 ; first oil delivery passage 131; first inlet 131A; first outlet 131B
  • Second oil passage 132 Second oil passage 132; second inlet 132A; second outlet 132B; oil tank 130
  • FIGS. 1-5 The preferred embodiments of the present application will now be described in detail with reference to FIGS. 1-5.
  • the following description is merely exemplary in nature and is not intended to limit the application and its applications or uses.
  • the scroll compressor is exemplarily shown as a vertical scroll compressor.
  • the scroll compressor according to the present application is not limited to this type, but may be any suitable type of scroll compressor, for example, a horizontal scroll compressor, a high-pressure side scroll compressor, a low-pressure side scroll compressor, etc. .
  • the “high-pressure side scroll compressor” described herein refers to a scroll compressor in which the motor is in the discharge pressure region (high-pressure region) of the casing.
  • the “low-pressure side scroll compressor” described herein refers to a scroll compressor in which the motor is in the suction pressure region (low-pressure region) of the casing.
  • FIG. 1 shows a longitudinal sectional view of a scroll compressor according to the present application.
  • the overall structure of the scroll compressor according to the present application will be briefly described with reference to FIG. 1.
  • the scroll compressor 1 may include a substantially cylindrical housing 12, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 11, a movable scroll 24, and a fixed scroll ⁇ ⁇ 22.
  • the movable scroll 24 and the fixed scroll 22 constitute a compression mechanism CM suitable for compressing a working fluid (eg, refrigerant), wherein the fixed scroll 22 includes a fixed scroll end plate, a fixed scroll scroll, and a fixed scroll
  • the hub portion G extending from the second side of the compressor defines an open suction chamber in fluid communication with the intake port of the compression mechanism CM in the compression mechanism CM, and is formed by a fixed scroll and a movable scroll that are joined together A closed compression chamber that compresses the working fluid.
  • the cover 26 at the top of the casing 12 and the base 28 at the bottom of the casing 12 may be mounted to the casing 12, thereby defining the internal volume of the scroll compressor 1.
  • Lubricants such as lubricating oil may be stored in an oil sump OR in the bottom of the housing 12 for lubricating various components of the scroll compressor 1 (such as the movable scroll 24, fixed scroll 22, and thrust plate) Or the thrust surface of the main bearing housing 11, etc.).
  • the oil sump OR can be used as a lubricant source (lubricant source) according to the present application.
  • the electric motor includes a stator 14 and a rotor 15.
  • the rotor 15 is used to drive the drive shaft 16 to rotate the drive shaft 16 relative to the housing 12 about its axis of rotation.
  • the drive shaft 16 may include an eccentric pin mounted to the first end (top end) of the drive shaft 16 or formed integrally with the first end of the drive shaft 16.
  • the drive shaft 16 may include a center hole 52 formed at the second end (bottom end) of the drive shaft 16 and an eccentric hole 56 that extends upward from the center hole 52 to the end surface of the eccentric pin.
  • the end (lower end) of the center hole 52 may be immersed in the oil sump OR at the bottom of the casing 12 of the scroll compressor 1, so that, for example, the centrifugal force generated by the rotation of the drive shaft 16 can be removed from the casing 12
  • the oil sump OR at the bottom conveys the lubricating oil and causes the lubricating oil to flow upward through the center hole 52 and the eccentric hole 56 and flow out from the end surface of the eccentric pin.
  • the lubricating oil flowing out from the end surface of the eccentric pin can flow into, for example, the lubricating oil supply region formed between the eccentric pin and the movable scroll 24 and between the main bearing housing 11 and the movable scroll 24.
  • the lubricating oil in the lubricating oil supply region can lubricate, for example, the rotary joint and the sliding surface between the eccentric pin and the orbiting scroll 24 and between the main bearing housing 11 and the orbiting scroll 24.
  • the lubricating oil in the lubricating oil supply area can also be supplied to the compression mechanism CM, and thus these lubricating oil supply areas can also be used as a lubricating oil source according to the present application.
  • the movable scroll 24 is axially supported by the main bearing housing 11 and supported by the main bearing housing 11 so as to be able to orbit.
  • the hub G of the movable scroll 24 may be rotatably coupled to the eccentric pin.
  • the hub G may be rotatably coupled to the eccentric pin via a sleeve or bearing.
  • the lubricating oil that is supplied to the eccentric pin and flows out of the eccentric pin through the above-described exemplary eccentric oil supply scheme and the like can further enter the space in the hub G.
  • the lubricating oil accumulates in the recessed portion, the oil reservoir V, on the inner side wall of the central through hole O of the main bearing housing 11.
  • the lubricating oil after lubricating the hub G, the eccentric pin or the bearing, etc. may be accumulated in the main bearing housing 11 for accommodating and allowing the hub G and the eccentric pin to rotate In the recess.
  • the above-mentioned oil storage tank V or recess can be used as a lubricant source according to the present application.
  • the lubricating oil in the concave portion of the main bearing housing 11 adheres to the peripheral wall of the fixed scroll, the movable scroll in the form of oil mist It can be lubricated on the disk end plate and the main bearing housing.
  • the fixed scroll 22 is attached to the main bearing housing 11 using, for example, mechanical fasteners such as screw fastening members.
  • the orbiting scroll 24 is driven by an electric motor via a drive shaft 16 (specifically, an eccentric pin), so that it can perform a translational rotation relative to the fixed scroll 22 by virtue of the cross slip ring—that is, orbiting (that is, moving).
  • the axis of the scroll 24 revolves relative to the axis of the fixed scroll 22, but both the movable scroll 24 and the fixed scroll 22 themselves do not rotate about their respective axes).
  • each holding chamber defined by the fixed scroll and the movable scroll wraps from the radially outer to the radially inner side from the radially closed suction chamber to the outer low-pressure compression chamber and then to the intermediate medium pressure
  • the compression chamber then becomes the central high-pressure compression chamber (with the highest pressure), and the volume of the containing chamber gradually changes from large to small.
  • the pressure in the accommodating chamber also gradually increases, so that the working fluid (for example, refrigerant) in the accommodating chamber (compression chamber) is compressed and finally exhausted from the radial center located at the end plate of the fixed scroll 22
  • the port is discharged and then discharged to the outside of the casing 12 of the scroll compressor 1 through the discharge fitting, thereby achieving a working cycle of suction, compression, and discharge of working fluid.
  • FIG. 2 shows an enlarged view of a partial longitudinal section of the scroll compressor 1 in FIG. 1 including the compression mechanism CM, which shows the arrangement of the oil supply passage 13 according to a preferred embodiment of the present application
  • FIG. 3 shows the diagram 2 is a schematic cross-sectional perspective view of the fixed scroll 22 with the fixed scroll end plate removed, in which the arrangement of the oil supply passage 13 in FIG. 2 is shown in detail.
  • the compression mechanism CM includes a fixed scroll 22 and a movable scroll 24, and the movable scroll end plate 241 of the movable scroll 24 faces the main bearing housing 11
  • the central area of the second side of the cylinder has a cylindrical hub G
  • the fixed scroll 22 includes a peripheral wall S extending from one side of the end plate of the fixed scroll and surrounding the fixed scroll wrap
  • the peripheral wall of the fixed scroll 22 S abuts and is fastened to the main bearing housing 11 to securely connect the fixed scroll 22 and the main bearing housing 11 to each other
  • the main bearing housing 11 and the fixed scroll 22 are fixed so that the movable vortex
  • the orbiting disk 24 is located between the fixed scroll 22 and the main bearing housing 11 and the orbiting scroll 24 can perform orbital motion relative to the fixed scroll 22.
  • main bearing housing 11 and the fixed scroll 22 may be installed in any other suitable manner, for example, the main bearing housing 11 and the fixed scroll 22 may each be directly mounted to the housing 12.
  • the main bearing housing 11 includes a central through hole O that communicates with the hub G of the orbiting scroll 24 to form a shaft cavity, and the drive shaft 16 is fitted in the shaft cavity, as described above, from the drive shaft 16 Of lubricating oil enters the shaft cavity (as shown by the arrow in Figure 1).
  • the end surface of the peripheral wall S of the fixed scroll 22 and the region on the first side surface of the movable scroll end plate 241 on the radially outer side of the movable scroll wrap contact each other to form a contact portion P P includes a first contact area P1 located on the end surface of the peripheral wall S of the fixed scroll 22 and a second contact area P2 located on the first side surface of the movable scroll end plate 241, the first contact area P1 and the second contact
  • the regions P2 are respectively formed into annular contact regions around the scrolls.
  • the scroll compressor 1 is also provided with an oil delivery passage 13, as shown by the arrow in the figure, the oil delivery passage 13 is configured to supply the lubricating oil in the shaft cavity to the contact portion P, guide the lubricating oil to flow in the contact portion P, and then The lubricating oil at the contact portion P is output to the outside of the compression mechanism CM.
  • the oil transfer passage 13 includes: a first oil transfer passage 131 in fluid communication from the shaft cavity to the contact portion P; and a fluid communication from the contact portion P to the outside of the compression mechanism CM A second oil delivery passage 132; and an oil delivery tank 130 provided in the contact portion P to fluidly communicate the first oil delivery passage 131 and the second oil delivery passage 132.
  • the first oil transfer passage 131 is configured to supply the lubricating oil at the lubricating oil source to the contact portion P.
  • the oil transfer groove 130 is configured to guide the flow and distribution of the lubricating oil at the contact portion P at the contact portion P.
  • the second oil transfer passage 132 is configured to directly discharge the lubricating oil from the oil transfer tank 130 to the outside of the compression mechanism CM.
  • the "direct discharge” described herein means that the lubricating oil in the oil transfer tank 130 is discharged out of the compression mechanism without entering the compression chamber.
  • the "not entering the compression chamber” described here is not absolute.
  • the lubricating oil in the oil transfer tank 130 may leak into the compression chamber between the first contact area P1 and the second contact area P2 in.
  • the present disclosure does not consider lubricant oil leaking into the compression chamber between the first contact area P1 and the second contact area P2.
  • the oil transfer passage 13 to form a lubricating oil circuit at the contact portion P to allow the lubricating oil to actively flow through the contact portion P, the heat generated by friction in the contact area can also be reduced while satisfying lubrication Impurities are taken away.
  • the first oil passage 131 includes a first inlet 131A located on the side wall of the shaft cavity and opening toward the space in the shaft cavity and a first outlet 131B opening toward the contact portion P, wherein
  • the first inlet 131A is provided on the inner side wall of the central through hole O of the main bearing housing 11 and communicates with the oil reservoir V on the inner side wall of the central through hole O, as shown in FIG.
  • the oil storage groove V is located at the edge of the inner side wall of the central through hole O adjacent to the hub G, and preferably, the first outlet 131B is provided in the first contact area P1 of the fixed scroll 22 and toward the movable scroll end
  • the second contact area P2 of the plate 241 is open, and the first passage 131C extends from the first inlet 131A through the main bearing housing 11 and into the fixed scroll 22 via the peripheral wall S, and then extends to the first outlet 131B.
  • the second oil passage 132 includes a second inlet 132A located on the first contact area P1 and opening toward the second contact area P2, and a second outlet 132B opening toward the outside at the peripheral wall S, and the second passage 132C extends from the second inlet 132A It extends through the peripheral wall S to reach the second outlet 132B.
  • the oil delivery tank 130 is provided in the first contact area P1 and extends from the first outlet 131B to the second inlet 132A.
  • a large amount of lubricating oil can be supplied to the contact area P, so in addition to the above-mentioned improved lubricating performance, a large amount of lubricating oil supplied to the contact area P can also flush out the contact area P and take away the contact area Impurities that may exist in P, and can exchange heat with the compression mechanism CM to take away the heat generated by its work, and finally is discharged to the outside of the compression mechanism CM through the second oil passage 132, thereby not only preventing impurities from entering In the fluid receiving chamber formed by the fixed scroll and the movable scroll, the scroll is prevented from being worn out, and the compression mechanism CM can be prevented from overheating.
  • the impurities in the contact area P are usually concentrated in the area immediately adjacent to the fixed vortex wrap. Therefore, preferably, in this embodiment (as shown in FIG. 3), a larger portion of the oil delivery tank 130 It is arranged immediately adjacent to the radially outer side wall of the fixed vortex wrap, so as to remove as much impurities as possible in the contact area P.
  • the present application is not limited to this, specifically, the first oil delivery passage 131, the second oil delivery passage 132, and the oil delivery tank 130 are each not limited to one, but A plurality of first oil transfer passages 131, a plurality of second oil transfer passages 132, a plurality of oil transfer tanks 130, and a plurality of first inlets 131A and / or first outlets 131B, a plurality of second Inlet 132A and / or second outlet 132B.
  • FIGS. 4a and 4b show the arrangement of oil supply passages according to other embodiments of the present application.
  • FIG. 4a and 4b show the arrangement of the first outlet 131B, the second inlet 132A, and the oil delivery tank 130 provided in the first contact area P1 of the fixed scroll.
  • a first outlet 131B and a second inlet 132A are provided in the first contact area P1
  • the first outlet 131B and the second inlet 132A are substantially at diametrically opposed positions.
  • Two oil transfer grooves 130 are provided between the first outlet 131B and the second inlet 132A. The two oil transfer grooves 130 respectively extend from the first outlet 131B to the second inlet 132A and together form a closed ring shape.
  • two first outlets 131B and two second inlets 132A, and two oil transfer grooves 130 are provided in the first contact area P1.
  • the two oil transfer grooves 130 respectively correspond to The first outlets 131B extend to the respective second inlets 132A, and are respectively formed in an arc shape.
  • the two oil transfer tanks 130 do not intersect each other, and deliver the lubricant independently of each other.
  • a closed annular oil delivery groove in the entire annular first contact area P1 around the scroll not only can the contact portion P be sufficiently lubricated, but also impurities in the contact portion P can be removed as much as possible and the compression mechanism can be taken away CM heat.
  • FIGS. 4a and 4b a person of ordinary skill in the art can conceive of any other variations and modifications and other arbitrary combinations.
  • the first outlet 131B and the oil delivery tank 130 are both provided on the fixed scroll 22 (specifically, in the first contact area P1). Therefore, the first outlet 131B, the oil delivery tank 130, and the first The two inlets 132A are always in communication with each other, thereby continuously supplying lubricating oil to the contact portion P and continuously outputting the lubricating oil in the contact portion P to the outside of the compression mechanism CM.
  • the present application is not limited to this.
  • the first outlet 131B and the oil delivery tank 130 may also be provided on the movable scroll 24, specifically in the second contact area P2. In the present disclosure, the position, shape, size, number, etc.
  • the oil transfer tank 130, and the second inlet 132A may be changed as long as the first outlet 131B and the oil transfer tank 130 are in fluid communication (including always-on and intermittent communication) And the oil delivery tank 130 and the second inlet 132A can be in fluid communication (including always communicating and intermittent communicating) to form a circuit for the lubricating oil flow at the contact portion P.
  • FIG. 5 shows the arrangement of an oil supply passage according to another embodiment of the present application.
  • the first outlet 131B is provided in the second contact area P2 of the movable scroll 24 and opens toward the first contact area P1, and accordingly, the first inlet 131A is provided in the movable vortex
  • the inner wall of the hub G of the turntable 24 opens toward the internal space of the hub G, thereby supplying the lubricating oil from the drive shaft 16 and into the internal space of the hub G to the contact portion P, the first passage 131C It extends from the first inlet 131A through the movable scroll end plate 241 and to the first outlet 131B.
  • the oil transfer groove 130 may be provided in the first contact area P1 of the fixed scroll 22, and at this time, the oil transfer groove 130 is positioned to be able to operate during the operation of the compression mechanism CM (ie, during the orbiting motion of the movable scroll) Intermittently corresponds to the first outlet 131B-that is, in fluid communication to receive the lubricating oil from the first oil transfer passage 131, and the oil transfer groove 130 extends to the second inlet 132A in the first contact area P1, thereby continuously Lubricating oil is conveyed in the second oil conveying passage 132; alternatively, the oil conveying groove 130 may also be provided in the second contact area P2 of the movable scroll 24.
  • the oil conveying groove 130 extends to the first in the second contact area P2
  • the outlet 131B so as to be able to continuously receive the lubricating oil from the first oil delivery passage 131
  • the oil delivery groove 130 is positioned to be intermittent with the second inlet 132A during the operation of the compression mechanism CM (ie, during the orbiting motion of the orbiting scroll) Corresponding—that is, in fluid communication to intermittently deliver lubricating oil into the second oil delivery passage 132.
  • the oil tank 130 also It may be provided in the second contact area P2 of the orbiting scroll 24.
  • the oil transfer groove 130 is positioned to be able to intermittently communicate with the first outlet 131B during the operation of the compression mechanism CM (ie, during the orbiting motion of the orbiting scroll)
  • the second inlet 132A- that is, fluidly communicated to intermittently receive the lubricating oil from the first oil delivery passage 131 and intermittently deliver the lubricating oil to the second oil delivery passage 132.
  • the oil delivery groove 130 is provided in an arc shape or a closed circular ring around the scroll, but the present application is not limited thereto, and the oil delivery groove 130 may be any shape, such as a wave shape, a broken line shape, or even A multi-turn spiral is formed around the scroll.
  • the first contact area P1 located on the fixed scroll 22 during operation has a first sub-region that is always in contact with the second contact region P2 and a second sub-region that is intermittently in contact with the second contact region P2, preferably in a preferred implementation according to the present application
  • the first contact area includes a sub-area that always remains in contact with the second contact area during operation, and the first outlet 131B, the second inlet 132A, and the oil transfer tank 30 are all disposed in the first sub-area, thereby achieving higher lubrication Oil supply efficiency.
  • the present application is not limited to this. In some practical applications, the first outlet 131B, the second inlet 132A, and the oil tank 30 may all be disposed or partially disposed in the second sub-region.
  • the present application is not limited to this, but various modifications can be made without departing from the scope of protection of the present application Type, replacement and combination.
  • the first channel 131C and the second channel 132C are not limited to the above-mentioned extended path, as long as the first channel 131C can communicate from the first inlet 131A to the first outlet 131B, and similarly, the second channel 132C can only communicate from the second inlet 132A It is sufficient to connect to the second outlet 132B.
  • the oil delivery passage is not limited to various channels formed in the components of the compressor (for example, the first channel 131C or the second channel 132C), and for example, may also include an independent pipeline. It should be pointed out that according to the present application, it is most preferable to discharge the lubricating oil directly to the outside of the space formed by the compression mechanism and the main bearing seat by reasonably setting the position of the second passage and the second outlet, so as to ensure that impurities and heat are kept away Compression mechanism and main bearing seat.
  • the source of lubricating oil in the present disclosure is not limited to the specific embodiment described above, as long as any area capable of accumulating lubricating oil can be used as the source of lubricating oil, for example, the compression chamber, the housing of the scroll compressor The oil sump at the bottom, the space defined between the end plate of the orbiting scroll and the end face of the drive shaft, etc. It should be understood that when the position of the lubricating oil source is different, the arrangement of the first channel and / or the second channel may be appropriately changed.
  • a first inlet opening toward the selected compression chamber may be provided on the end plate of the movable scroll, and provided in the end plate of the movable scroll A first passage extending from the first inlet to the first outlet opening toward the contact portion, thereby guiding the lubricating oil in the compression chamber to the contact portion.
  • the first passage and / or the second passage may be formed by a passage provided in the fixed scroll, or may be formed by a passage provided in the fixed scroll At least one of the channels in the movable scroll is formed in any combination with the channels provided in the main bearing seat.
  • the lubricating oil in the oil sump OR can be introduced to the outer peripheral contact portion between the movable scroll and the fixed scroll through a separate pipe and / or The lubricating oil is discharged from the outer peripheral contact portion to the outside of the compression mechanism.
  • the first channel and / or the second channel include independent pipes.
  • the first channel and / or the second channel may include any possible combination of the following: an independent pipe, a channel in the rotating shaft, a channel in the movable scroll, or a main bearing housing And the channels in the fixed vortex.
  • the first passage and / or the second passage may include any possible combination of the following: The channel, the channel in the fixed scroll, and the channel in the main bearing housing.

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Abstract

一种涡旋压缩机，包括：压缩机构（CM），压缩机构（CM）包括定涡旋盘（22）和动涡旋盘（24），定涡旋盘（22）包括定涡旋盘端板、定涡旋涡卷以及在定涡旋涡卷的径向外侧的周壁（S）；动涡旋盘（24）包括动涡旋盘端板（241）、动涡旋涡卷和毂部；以及主轴承座，主轴承座的中心通孔与动涡旋盘的毂部连通形成轴腔，定涡旋盘（22）的周壁与动涡旋盘端板（241）的第一侧面接触而形成接触部分，输油通路将轴腔内的润滑油供给至接触部分并且再将接触部分处的润滑油输出至压缩机构外部。该涡旋压缩机能够改善接触部分中的供油润滑性能和压缩机构的散热性能，并能够清除接触部分中的杂质，其结构简单、易于制造且成本效益高。

Description

涡旋压缩机
本申请要求于2018年11月6日提交中国专利局、申请号为201811312810.5、名称为“涡旋压缩机”的中国专利申请以及于2018年11月6日提交中国专利局、申请号为201821822846.3、名称为“涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及一种涡旋压缩机，具体地，涉及一种对定涡旋盘外周端面与动涡旋盘端板之间的接触部分的供油润滑等方面进行改进的涡旋压缩机。
背景技术
本部分提供了与本申请相关的背景信息，这些信息并不必然构成现有技术。
压缩机(例如涡旋压缩机)可以应用于例如制冷***、空调***和热泵***中。涡旋压缩机包括：压缩机构，压缩机构包括定涡旋盘和动涡旋盘，定涡旋涡卷和动涡旋涡卷彼此接合以限定一系列工作流体接纳室；以及主轴承座，主轴承座支承动涡旋盘并与定涡旋盘固定连接，动涡旋盘位于主轴承座与定涡旋盘之间并能够相对于定涡旋盘进行绕动运动，其中，定涡旋盘的周壁的端面与动涡旋盘端板的一侧面上的位于动涡旋涡卷的径向外侧的区域彼此接触而形成接触部分，在工作期间，由于动涡旋盘相对于定涡旋盘进行绕动式相对运动，该接触部分的两个接触面之间存在相对摩擦运动从而产生较多的热量，并且当两个接触面之间存在杂质时，会大大加速动涡旋盘和定涡旋盘的磨损而导致失效。现有压缩机不能有效地排出接触面之间的杂质并且不能有效地将接触面之间摩擦产生的热量排出。
为了解决上述可能的发热和杂质磨损等问题，期望的是能够便于压缩机构散热以及将上述两个接触面之间的杂质排出。
因此，需要提供一种在上述方面进行改进的涡旋压缩机。
发明内容
在本部分中提供本申请的总体概要，而不是本申请完全范围或本申请所有特征的全面公开。
本申请的目的是在上面提到的一个或多个技术问题方面进行改进。总体 而言，本申请提供了一种如下文所述的涡旋压缩机，其能够显著改善定涡旋盘的外周端面与动涡旋盘端板之间的接触部分中的供油润滑性能和压缩机构的散热性能，并能够带走所述接触部分中的杂质，从而显著降低定涡旋盘和动涡旋盘被磨损而失效的风险。
根据本申请的一个方面，提供了一种涡旋压缩机，包括：
压缩机构，所述压缩机构适于压缩工作流体并且包括定涡旋盘和动涡旋盘，所述定涡旋盘包括定涡旋盘端板、从所述定涡旋盘端板的一个侧面处延伸的定涡旋涡卷以及从所述侧面延伸并在所述定涡旋涡卷的径向外侧的周壁，所述动涡旋盘包括动涡旋盘端板、从所述动涡旋盘端板的第一侧面延伸的动涡旋涡卷和从所述动涡旋盘端板的第二侧面延伸的毂部，所述定涡旋涡卷和所述动涡旋涡卷彼此接合以限定一系列工作流体接纳室；
主轴承座，所述主轴承座支承所述动涡旋盘并与所述定涡旋盘固定成使得所述动涡旋盘位于所述定涡旋盘与所述主轴承座之间并且所述动涡旋盘能够相对于所述定涡旋盘进行绕动运动；以及
润滑油源，所述润滑油源用于向所述压缩机构供送润滑油，
其中，所述定涡旋盘的周壁与所述动涡旋盘端板的第一侧面彼此接触而形成接触部分，所述涡旋压缩机还设置有输油通路，所述输油通路包括：从所述润滑油源流体连通至所述接触部分处的至少一个第一输油通路；与所述至少一个第一输油通路流体连通以引导润滑油在所述接触部分中流动的至少一个输油槽；以及与所述至少一个输油槽流体连通以将润滑油直接排出至所述压缩机构的外部的至少一个第二输油通路。
在根据本申请的上述涡旋压缩机中，输油通路将润滑油供给至所述接触部分、引导润滑油在所述接触部分中的流动并且再将所述接触部分处的润滑油直接排出至所述压缩机构的外部，可见，通过这种构型，能够确保将足够多的润滑油供给至定涡旋盘的外周端面与动涡旋盘端板之间的接触区域，不仅确保在任何工况条件下的良好的润滑性能，并且，被供给至所述接触区域中的润滑油还能够携带接触区域中可能存在的杂质以及整个压缩机构中的热量通过所述输油通路而被排出至压缩机构的外部，被供给至所述接触区域中的润滑油在输油槽的导引下基本不会进入由定涡旋涡卷和动涡旋涡卷形成的封闭的压缩 腔中，从而防止杂质进入压缩腔中，避免涡卷被磨损失效，并且通过带走热量，能够防止压缩机构过热。
根据本申请的一个方面，所述第一输油通路包括：流体连通至所述润滑油源的第一入口；朝向所述接触部分开口的第一出口；以及从所述第一入口延伸至所述第一出口的第一通道，并且所述第二输油通路包括：朝向所述接触部分开口的第二入口；朝向所述压缩机构的外部开口的第二出口；以及从所述第二入口延伸至所述第二出口的第二通道。
根据本申请的一个方面，所述接触部分包括位于所述定涡旋盘的周壁的端面上的环形的第一接触区域和位于所述动涡旋盘端板的第一侧面上的环形的第二接触区域，所述第一出口、所述输油槽以及所述第二入口中的每一者设置在所述第一接触区域和所述第二接触区域中的任一区域中。
根据本申请的一个方面，所述第一出口、所述输油槽以及所述第二入口均设置在所述第一接触区域中或者均设置在所述第二接触区域中，所述第一出口和所述第二入口定位在所述第一接触区域或所述第二接触区域的径向相对的位置处。
根据本申请的一个方面，所述第一通道包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者，或者包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者与设置在所述主轴承座中的通道的组合；以及
所述第二通道包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者，或者包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者与设置在所述主轴承座中的通道的组合。
根据本申请的一个方面，所述输油槽形成为弧形、螺旋形或环形的凹槽。
根据本申请的一个方面，所述输油槽的至少一部分紧邻所述定涡旋涡卷或所述动涡旋涡卷的径向最外侧的外侧壁。
根据本申请的一个方面，所述第一接触区域包括在工作期间始终保持接触所述第二接触区域的第一子区域以及在工作期间间歇地接触所述第二接触区域的第二子区域，所述第一出口、所述输油槽和/或所述第二入口设置于所 述第一子区域内。
根据本申请的一个方面，所述润滑油源包括下列项中的至少一者：在所述涡旋压缩机的壳体的底部处的油池、所述主轴承座的储油凹部、限定在所述动涡旋盘端板与用于驱动所述毂部运动的驱动轴的端面之间的空间、所述工作流体接纳室中的压缩腔。
根据本申请的一个方面，所述主轴承座包括沿着所述中心通孔的与所述毂部相邻的边缘延伸的储油槽，所述第一入口与所述储油槽连通。
根据本申请的一个方面，所述至少一个第二输油通路设置为将润滑油直接排出至所述压缩机构与所述主轴承座构成的空间的外部。
根据本申请的一个方面，所述涡旋压缩机为高压侧涡旋压缩机。
综上可知，根据本申请的涡旋压缩机至少提供以下有益效果：根据本申请的涡旋压缩机通过设置上述输油通路而能够直接向所述定涡旋盘的外周端面与动涡旋盘端板之间的接触部分中供送润滑油，并能够将供送至该接触部分中的润滑油排出至压缩机构外部，因此，本申请的涡旋压缩机能够显著改善该接触部分中的供油润滑性能和压缩机构的散热性能，并能够清除所述接触部分中的杂质且避免杂质进入由定涡旋涡卷和动涡旋涡卷形成的封闭的压缩腔中，从而显著降低定涡旋盘和动涡旋盘被磨损而失效的风险，并且，本申请的涡旋压缩机结构简单、易于加工制造，具有较高的成本效益。
附图说明
根据以下参照附图的详细描述，本申请的前述及另外的特征和特点将变得更加清楚，这些附图仅作为示例并且不一定是按比例绘制。在附图中采用相同的附图标记指示相同的部件，在附图中：
图1示出根据本申请的涡旋压缩机的纵向截面图，其中示出了定涡旋盘与动涡旋盘的布置；
图2示出图1中的涡旋压缩机的包括压缩机构的局部纵向截面放大图，其中示出了根据本申请的一个优选实施方式的供油通路的布置；
图3示出图2中的定涡旋盘的去除了定涡旋盘端板后的示意性剖视立体图，其中详细示出了图2中的供油通路的布置；以及
图4a和4b示出根据本申请的其他实施方式的供油通路的布置。
图5示出根据本申请的动涡旋盘的截面图，其中示出了根据本申请的另一个实施方式的供油通路的布置。
参考标记列表
涡旋压缩机1；壳体12；驱动轴16；主轴承座11；盖26；基部28
定子14；转子15；中心孔52；偏心孔56；压缩机构CM
定涡旋盘22；动涡旋盘24；动涡旋盘端板241；油池OR
毂部G；定涡旋盘的周壁S；储油槽V
中心通孔O；接触部分P；第一接触区域P1；第二接触区域P2
输油通路13；第一输油通路131；第一入口131A；第一出口131B
第二输油通路132；第二入口132A；第二出口132B；输油槽130
第一通道131C；第二通道132C
具体实施方式
现在将结合附图1-5对本申请的优选实施方式进行详细描述。以下的描述在本质上只是示例性的而非意在限制本申请及其应用或用途。
在下述示例性实施方式中，所述涡旋压缩机示例性地示出为立式涡旋压缩机。然而根据本申请的涡旋压缩机并不限于此类型，而可以是任何合适类型的涡旋压缩机，例如，卧式涡旋压缩机、高压侧涡旋压缩机、低压侧涡旋压缩机等。本文中所述的“高压侧涡旋压缩机”指的是马达处于壳体的排出压力区域(高压区域)中的涡旋压缩机。本文中所述的“低压侧涡旋压缩机”指的是马达处于壳体的吸入压力区域(低压区域)中的涡旋压缩机。
图1示出了根据本申请的涡旋压缩机的纵向截面图。首先，参照图1概要地描述根据本申请的涡旋压缩机的总体结构。
如图1所示，涡旋压缩机1可以包括呈大致筒状的壳体12、电动马达(包括定子14和转子15)、驱动轴16、主轴承座11、动涡旋盘24、定涡旋盘22。动涡旋盘24和定涡旋盘22构成适于压缩工作流体(例如制冷剂)的压缩机构CM，其中，定涡旋盘22包括定涡旋盘端板、定涡旋涡卷和位于定涡旋盘中心处的排气口；动涡旋盘24包括动涡旋盘端板241、从动涡旋盘端板241的第 一侧面延伸的动涡旋涡卷和从动涡旋盘端板241的第二侧面延伸的毂部G，在压缩机构CM内限定有与压缩机构CM的进气口流体连通的开放的吸气腔，以及由定涡旋涡卷与动涡旋涡卷接合形成的用于对工作流体进行压缩的封闭的压缩腔。
位于壳体12的顶部处的盖26和位于壳体12的底部处的基部28可以安装至壳体12，从而限定了涡旋压缩机1的内部容积。例如润滑油的润滑剂可以储存在壳体12的底部内的油池OR中以用于润滑涡旋压缩机1的各种部件(例如动涡旋盘24、定涡旋盘22和止推板或主轴承座11的止推面等)。这里，需要指出的是，油池OR可以用作根据本申请的润滑油源(润滑剂源)。
电动马达包括定子14和转子15。转子15用于对驱动轴16进行驱动以使驱动轴16绕其旋转轴线相对于外壳12旋转。驱动轴16可以包括偏心销，偏心销安装至驱动轴16的第一端(顶端)或者与驱动轴16的第一端一体地形成。
驱动轴16可以包括中心孔52和偏心孔56，中心孔52形成在驱动轴16的第二端(底端)处，偏心孔56从中心孔52向上延伸至偏心销的端部表面。中心孔52的端部(下端)可以浸入在涡旋压缩机1的壳体12的底部的油池OR中，从而例如在因驱动轴16的旋转而产生的离心力的作用下能够从壳体12底部处的油池OR输送润滑油，并且使润滑油向上流动经过中心孔52和偏心孔56并且从偏心销的端部表面流出。
从偏心销的端部表面流出的润滑油可以流动至例如形成在偏心销与动涡旋盘24之间以及主轴承座11与动涡旋盘24之间的润滑油供应区域中。该润滑油供应区域中的润滑油可以对例如偏心销与动涡旋盘24之间以及主轴承座11与动涡旋盘24之间的旋转接合部和滑动表面进行润滑。而且，如将在下文做进一步描述，润滑油供应区域中的润滑油还可以被供给至压缩机构CM，因而这些润滑油供应区域也可以用作根据本申请的润滑油源。
动涡旋盘24由主轴承座11轴向地支承并且被主轴承座11支承成能够进行绕动。动涡旋盘24的毂部G可以可旋转地联接至偏心销。替代性地，毂部G可以经由套管或轴承可旋转地联接至偏心销。如上所述，通过上述示例性偏心供油方案等被供送至偏心销并从偏心销流出的润滑油进而能够进入毂部G内的空间。润滑油在对毂部G、偏心销或轴承等润滑之后积聚在主轴承座11 的中心通孔O的内侧壁上的凹部——储油槽V——中。在另一示例中，即使没有储油槽V，对毂部G、偏心销或轴承等润滑之后的润滑油也可以积聚在主轴承座11的用于容置且允许毂部G和偏心销旋转的凹部中。上述储油槽V或凹部可以用作根据本申请的润滑油源。在诸如动涡旋的毂部G和/或平衡块(未示出)的旋转搅动下，主轴承座11的凹部中的润滑油以油雾形式附着在定涡旋盘的周壁、动涡旋盘端板和主轴承座等构件上，由此可以进行润滑。
定涡旋盘22例如使用机械紧固件——如螺钉紧固构件——安装至主轴承座11。动涡旋盘24经由驱动轴16(具体为偏心销)通过电动马达而被驱动，从而借助十字滑环而能够相对于定涡旋盘22进行平动转动——即绕动(亦即，动涡旋盘24的轴线相对于定涡旋盘22的轴线公转，但是动涡旋盘24和定涡旋盘22二者本身并未绕它们各自的轴线旋转)。由此，由定涡旋涡卷与动涡旋涡卷限定的各容纳室在从径向外侧向径向内侧移动的过程中从未封闭的吸气腔变为外侧低压压缩腔再变为中间中压压缩腔再变为中心高压压缩腔(具有最高压力)，并且容纳室的容积逐渐由大变小。这样，容纳室中的压力也逐渐升高，从而容纳室(压缩腔)中的工作流体(例如制冷剂)被压缩并最终从位于定涡旋盘22的端板的径向中心处的排气口排出并进而经由排出配件排出至涡旋压缩机1的壳体12外部，由此实现工作流体的吸入、压缩和排出的工作循环。
下面将参照图2至图4b详细描述根据本申请的涡旋压缩机1。
图2示出图1中的涡旋压缩机1的包括压缩机构CM的局部纵向截面放大图，其中示出了根据本申请的一个优选实施方式的供油通路13的布置；图3示出图2中的定涡旋盘22的去除了定涡旋盘端板后的示意性剖视立体图，其中详细示出了图2中的供油通路13的布置。参照附图2-3可知，根据本申请，总体上，压缩机构CM包括定涡旋盘22和动涡旋盘24，动涡旋盘24的动涡旋盘端板241的朝向主轴承座11的第二侧面的中心区域处具有筒状的毂部G，定涡旋盘22包括从定涡旋盘端板的一个侧面延伸并环绕定涡旋涡卷的周壁S，定涡旋盘22的周壁S与主轴承座11抵接并紧固至主轴承座11，从而将定涡旋盘22与主轴承座11彼此固定连接，并且，主轴承座11与定涡旋盘22固定成使得动涡旋盘24位于定涡旋盘22与主轴承座11之间并且动涡旋盘 24能够相对于定涡旋盘22进行绕动运动。应理解的是，主轴承座11和定涡旋盘22可以以其他任何合适的方式进行安装，例如，主轴承座11和定涡旋盘22可以各自直接安装至壳体12。主轴承座11包括中心通孔O，中心通孔O与动涡旋盘24的毂部G连通形成轴腔，驱动轴16配装在所述轴腔中，如前所述，来自驱动轴16的润滑油进入所述轴腔中(如图1中箭头所示)。
如图所示，定涡旋盘22的周壁S的端面与动涡旋盘端板241的第一侧面上的位于动涡旋涡卷的径向外侧的区域彼此接触而形成接触部分P，接触部分P包括位于定涡旋盘22的周壁S的端面上的第一接触区域P1和位于动涡旋盘端板241的第一侧面上的第二接触区域P2，第一接触区域P1和第二接触区域P2分别围绕涡卷形成为环形接触区域。涡旋压缩机1还设置有输油通路13，如图中箭头所示，输油通路13构造成将轴腔内的润滑油供给至接触部分P，引导润滑油在接触部分P中流动，再将接触部分P处的润滑油输出至压缩机构CM的外部。在图2-3所示的优选实施方式中，输油通路13包括：从轴腔流体连通至接触部分P处的第一输油通路131；从接触部分P处流体连通至压缩机构CM的外部的第二输油通路132；以及设置在接触部分P中的将第一输油通路131与第二输油通路132流体连通的输油槽130。
第一输油通路131构造成将润滑油源处的润滑油供应至接触部分P处。输油槽130构造成引导接触部分P处的润滑油在接触部分P处的流动和分布。第二输油通路132构造成将润滑油从输油槽130中直接排出至压缩机构CM的外部。本文中所述的“直接排出”指的是使输油槽130中的润滑油不进入压缩腔中而被排出压缩机构的外部。当然，应理解的是，这里所述的“不进入压缩腔”不是绝对的，例如，输油槽130中的润滑油可以在第一接触区域P1和第二接触区域P2之间渗漏至压缩腔中。本公开不考虑在第一接触区域P1和第二接触区域P2之间渗漏至压缩腔中的润滑油。换言之，在本公开中，通过设置输油通路13在接触部分P处形成润滑油回路以使润滑油积极流动通过接触部分P，从而在满足润滑的同时还可以将接触区域因摩擦产生的热以及杂质等带走。
具体地，如图所示，第一输油通路131包括位于所述轴腔的侧壁上并朝向轴腔内的空间开口的第一入口131A和朝向接触部分P开口的第一出口 131B，其中，在本实施方式中，优选地，第一入口131A设置在主轴承座11的中心通孔O的内侧壁上并与中心通孔O的内侧壁上的储油槽V连通，如图2所示，储油槽V位于中心通孔O的内侧壁的邻接毂部G的边缘处，并且优选地，第一出口131B设置在定涡旋盘22的第一接触区域P1中并朝向动涡旋盘端板241的第二接触区域P2开口，并且第一通道131C从第一入口131A开始延伸穿过主轴承座11并经由周壁S到达定涡旋盘22中，进而延伸至第一出口131B。通过设置上述构型的第一输油通路131，能够将主轴承座11的中心通孔O内的大量的润滑油——尤其是被收集在储油槽V中的大量润滑油——输送至接触部分P中，从而确保向接触部分P处供送足够的润滑油。
第二输油通路132包括位于第一接触区域P1上且朝向第二接触区域P2开口的第二入口132A以及于周壁S处朝向外部开口的第二出口132B，第二通道132C从第二入口132A延伸穿过周壁S而到达第二出口132B。并且，如图3所示，输油槽130设置于第一接触区域P1中并从第一出口131B延伸至第二入口132A。通过这种构型，被供送至接触区域P处的润滑油经由输油槽130而流动至第二入口132A，进而通过第二通道132C而被输送至第二出口132B并被排除至压缩机构CM外部。
根据上述优选实施方式，能够将大量润滑油供送至接触区域P处，因此，除了上述改进的润滑性能，被供给至接触区域P的大量润滑油还能够冲刷该接触区域P并带走接触区域P中可能存在的杂质，并且能够与压缩机构CM进行热交换从而带走其工作产生的热量，并最终通过第二输油通路132而被排出至压缩机构CM的外部，从而不仅防止杂质进入由定涡旋涡卷和动涡旋涡卷形成的流体接纳室中，避免涡卷被磨损失效，并且能够防止压缩机构CM过热。
另外，在实际应用中，接触区域P中的杂质通常集中在紧邻定涡旋涡卷的区域中，因此，优选地，在本实施方式中(如图3所示)，输油槽130的较大部分设置为紧邻定涡旋涡卷的径向外侧壁，从而尽可能多地清除接触区域P中的杂质。
尽管本实施方式中的输油通路13具有上述构型，但是本申请不限于此，具体地，第一输油通路131、第二输油通路132以及输油槽130各自均不限于一个，而是可以分别设置有多个第一输油通路131、多个第二输油通路132、 多个输油槽130，以及相应地设置多个第一入口131A和/或第一出口131B、多个第二入口132A和/或第二出口132B。例如，图4a和4b示出根据本申请的其他实施方式的供油通路的布置。图4a和4b示出了设置在定涡旋盘的第一接触区域P1中的第一出口131B、第二入口132A和输油槽130的布置。具体地，参照图4a，在第一接触区域P1中设置有一个第一出口131B和一个第二入口132A，第一出口131B和第二入口132A大致处于径向相对的位置处。在第一出口131B和第二入口132A之间设置有两条输油槽130，这两条输油槽130分别从第一出口131B延伸至第二入口132A并且共同形成为一个闭合的环形。参照图4b，在第一接触区域P1中设置有两个第一出口131B和两个第二入口132A，以及两条输油槽130，如图中所示，这两条输油槽130分别从各自相应的第一出口131B延伸至各自相应的第二入口132A，并且分别形成为弧形，这两条输油槽130彼此间没有交集，彼此独立地输送润滑油。优选地，通过在围绕涡卷的整个环形的第一接触区域P1中形成闭合的环形输油槽，不仅能够充分润滑接触部分P，而且能够尽可能地清除接触部分P中的杂质以及带走压缩机构CM的热量。根据图4a和4b示出的替代性实施方式，本领域普通技术人员可以设想出任何其他变形和修改以及其他任意的组合。
根据本申请的上述各实施方式，第一出口131B和输油槽130均设置在定涡旋盘22上(具体地，第一接触区域P1中)，因此，第一出口131B、输油槽130和第二入口132A彼此始终保持连通，从而保持持续不断地向接触部分P供送润滑油并且持续不断地将接触部分P中的润滑油输出至压缩机构CM外部。但是本申请并不限于此，在实际应用中，第一出口131B和输油槽130也可以分别设置在动涡旋盘24上，具体地设置在第二接触区域P2中。在本公开中，第一出口131B、输油槽130和第二入口132A的位置、形状、大小以及数量等可以变化，只要第一出口131B与输油槽130能够流体连通(包括始终连通和间歇连通)并且输油槽130和第二入口132A能够流体连通(包括始终连通和间歇连通)以在接触部分P处形成供润滑油流动的回路。
例如，图5示出根据本申请的另一个实施方式的供油通路的布置。参照图5可知，在本实施方式中，第一出口131B设置在动涡旋盘24的第二接触区域P2中并朝向第一接触区域P1开口，并且相应地，第一入口131A设置在 动涡旋盘24的毂部G的内壁上并朝向毂部G的内部空间开口，从而将来自驱动轴16并进入毂部G的内部空间中的润滑油供送至接触部分P，第一通道131C因此从第一入口131A开始延伸穿过动涡旋盘端板241并延伸至第一出口131B。在此情况下，输油槽130可以设置在定涡旋盘22的第一接触区域P1中，此时，输油槽130定位成能够在压缩机构CM工作期间(即，动涡旋盘绕动运动期间)间歇地与第一出口131B对应——即，流体连通，从而接收来自第一输油通路131的润滑油，并且输油槽130延伸至第一接触区域P1中的第二入口132A，从而持续地向第二输油通路132中输送润滑油；或者，输油槽130也可以设置在动涡旋盘24的第二接触区域P2中，此时，输油槽130延伸至第二接触区域P2中的第一出口131B，从而能够持续地接收来自第一输油通路131的润滑油，并且输油槽130定位成能够在压缩机构CM工作期间(即，动涡旋盘绕动运动期间)间歇地与第二入口132A对应——即，流体连通，从而间歇地将润滑油输送至第二输油通路132中。
同样地，尽管附图中未示出，但本领域普通技术人员通过阅读上述内容可知，在第一出口131B设置于定涡旋盘22的第一接触区域P1中的情况下，输油槽130也可以设置在动涡旋盘24的第二接触区域P2中，此时，输油槽130定位成能够在压缩机构CM工作期间(即，动涡旋盘绕动运动期间)分别间歇地与第一出口131B和第二入口132A对应——即，流体连通，从而间歇地接受来自第一输油通路131的润滑油以及间歇地向第二输油通路132输送润滑油。
另外，在上述优选实施方式中，输油槽130围绕涡卷设置为弧形形状或闭合的圆环形，但本申请不限于此，输油槽130可以是任意形状，如波浪形、折线形，甚至围绕涡卷形成多圈式的螺旋形。
并且，参照图1和图2可知，在定涡旋盘22与动涡旋盘24彼此相接触形成的接触部分P中，位于定涡旋盘22上的第一接触区域P1在工作期间由于动涡旋盘24的绕动运动而具有始终与第二接触区域P2保持接触的第一子区域以及间歇地与第二接触区域P2接触的第二子区域，优选地，在根据本申请的优选实施方式中，第一接触区域包括在工作期间始终保持接触第二接触区域的子区域，第一出口131B、第二入口132A和输油槽30均设置于第一子区域内， 从而实现更高的润滑油供送效率。但本申请不限于此，在一些实际应用中，第一出口131B、第二入口132A和输油槽30均可以设置在或部分地设置在第二子区域中。
尽管在前述实施方式中描述了根据本申请的涡旋压缩机的示例性实施方式，但是，本申请并不限于此，而是在不背离本申请的保护范围的情况下，可以进行各种改型、替换和组合。例如，第一通道131C和第二通道132C不限于上述延伸路径，只要第一通道131C能够从第一入口131A连通至第一出口131B即可，同样，第二通道132C只要能够从第二入口132A连通至第二出口132B即可。并且，输油通路也不局限于在压缩机的部件中形成的各种通道(例如，第一通道131C或第二通道132C)，例如，还可以包括独立的管道。需指出的是，根据本申请，最优选地是通过合理设置第二通道以及第二出口的位置来将润滑油直接排出至压缩机构与主轴承座构成的空间的外部，从而确保杂质和热量远离压缩机构和主轴承座。
此外，本公开中的润滑油源不限于上面所述的具体实施方式，只要是能够积聚润滑油的任何区域均可以用作润滑油源，例如，压缩腔、在涡旋压缩机的壳体的底部处的油池、限定在动涡旋盘端板与驱动轴的端面之间的空间等。应理解的是，当润滑油源的位置不同时，第一通道和/或第二通道的设置可以适当变化。
例如，当将压缩腔作为润滑油源时，可以在动涡旋盘端板上设置朝向选定的压缩腔(例如中压腔)开口的第一入口，并且在动涡旋盘端板中设置从所述第一入口延伸至朝向所述接触部分开口的第一出口的第一通道，从而将压缩腔中的润滑油引导至所述接触部分处。并且，类似地，在压缩腔作为润滑油源的情况下，第一通道和/或第二通道可以由设置在定涡旋中的通道形成，或者可以由设置在定涡旋中的通道和设置在动涡旋中的通道中的至少一者与设置在主轴承座中的通道的任意组合形成。
例如，当将壳体底部处的油池OR作为润滑油源时，可以通过独立的管道将油池OR中的润滑油引入至动涡旋与定涡旋之间的外周接触部分处并且/或者将润滑油从所述外周接触部分排出至压缩机构外部。这种情况下，第一通道和/或第二通道包括独立的管道。在未示出的示例中，第一通道和/或第二通道 可以包括下述项中的任何可能的组合：独立的管道、旋转轴中的通道、动涡旋中的通道或主轴承座中的通道以及定涡旋中的通道。
例如，在将动涡旋盘端板与驱动轴端面之间的空间作为润滑油源时，第一通道和/或第二通道可以包括下述项中的任何可能的组合：动涡旋中的通道、定涡旋中的通道以及主轴承座中的通道。
显而易见的是，通过将不同的实施方式及各个技术特征以不同的方式进行组合或者对其进行改型，可以进一步设计得出各种不同的实施方式。
上文结合具体实施方式描述了根据本申请的优选实施方式的涡旋压缩机。可以理解，以上描述仅为示例性的而非限制性的，在不背离本申请的范围的情况下，本领域技术人员参照上述描述可以想到多种变型和修改。这些变型和修改同样包含在本申请的保护范围内。

Claims (12)

  1. 一种涡旋压缩机(1)，包括：
    压缩机构(CM)，所述压缩机构适于压缩工作流体并且包括定涡旋盘(22)和动涡旋盘(24)，所述定涡旋盘包括定涡旋盘端板、从所述定涡旋盘端板的一个侧面处延伸的定涡旋涡卷以及从所述侧面延伸并在所述定涡旋涡卷的径向外侧的周壁(S)，所述动涡旋盘包括动涡旋盘端板(241)、从所述动涡旋盘端板的第一侧面延伸的动涡旋涡卷和从所述动涡旋盘端板的第二侧面延伸的毂部(G)，所述定涡旋涡卷和所述动涡旋涡卷彼此接合以限定一系列工作流体接纳室；
    主轴承座(11)，所述主轴承座支承所述动涡旋盘并与所述定涡旋盘固定成使得所述动涡旋盘位于所述定涡旋盘与所述主轴承座之间并且所述动涡旋盘能够相对于所述定涡旋盘进行绕动运动；以及
    润滑油源，所述润滑油源用于向所述压缩机构供送润滑油，
    其中，所述定涡旋盘的周壁与所述动涡旋盘端板的第一侧面彼此接触而形成接触部分(P)，所述涡旋压缩机还设置有输油通路(13)，所述输油通路(13)包括：从所述润滑油源流体连通至所述接触部分处的至少一个第一输油通路(131)；与所述至少一个第一输油通路(131)流体连通以引导润滑油在所述接触部分(P)中流动的至少一个输油槽(130)；以及与所述至少一个输油槽(130)流体连通以将润滑油直接排出至所述压缩机构的外部的至少一个第二输油通路(132)。
  2. 根据权利要求1所述的涡旋压缩机，其中，所述第一输油通路包括：流体连通至所述润滑油源的第一入口(131A)；朝向所述接触部分开口的第一出口(131B)；以及从所述第一入口延伸至所述第一出口的第一通道(131C)，并且所述第二输油通路包括：朝向所述接触部分开口的第二入口(132A)；朝向所述压缩机构(CM)的外部开口的第二出口(132B)；以及从所述第二入口延伸至所述第二出口的第二通道(132C)。
  3. 根据权利要求2所述的涡旋压缩机，其中，所述接触部分(P)包括位 于所述定涡旋盘的周壁的端面上的环形的第一接触区域(P1)和位于所述动涡旋盘端板的第一侧面上的环形的第二接触区域(P2)，所述第一出口、所述输油槽(130)以及所述第二入口中的每一者设置在所述第一接触区域和所述第二接触区域中的任一区域中。
  4. 根据权利要求3所述的涡旋压缩机，其中，所述第一出口、所述输油槽(130)以及所述第二入口均设置在所述第一接触区域中或者均设置在所述第二接触区域中，所述第一出口和所述第二入口定位在所述第一接触区域或所述第二接触区域的径向相对的位置处。
  5. 根据权利要求2所述的涡旋压缩机，其中，所述第一通道包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者，或者包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者与设置在所述主轴承座中的通道的组合；以及
    所述第二通道包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者，或者包括设置在所述定涡旋盘中的通道、设置在所述动涡旋盘中的通道和独立的管道中的至少一者与设置在所述主轴承座中的通道的组合。
  6. 根据权利要求1至5中任一项所述的涡旋压缩机，其中，所述输油槽形成为弧形、螺旋形或环形的凹槽。
  7. 根据权利要求6所述的涡旋压缩机，其中，所述输油槽的至少一部分紧邻所述定涡旋涡卷或所述动涡旋涡卷的径向最外侧的外侧壁。
  8. 根据权利要求3所述的涡旋压缩机，其中，所述第一接触区域包括在工作期间始终保持接触所述第二接触区域的第一子区域以及在工作期间间歇地接触所述第二接触区域的第二子区域，所述第一出口、所述输油槽和/或所述第二入口设置于所述第一子区域内。
  9. 根据权利要求1至5中任一项所述的涡旋压缩机，其中，所述润滑油源包括下列项中的至少一者：在所述涡旋压缩机的壳体的底部处的油池(OR)、所述主轴承座的储油凹部、限定在所述动涡旋盘端板与用于驱动所述毂部运动的驱动轴的端面之间的空间、所述工作流体接纳室中的压缩腔。
  10. 根据权利要求1至5中任一项所述的涡旋压缩机，其中，所述主轴承座包括沿着所述中心通孔的与所述毂部相邻的边缘延伸的储油槽，所述第一入口与所述储油槽连通。
  11. 根据权利要求1至5中任一项所述的涡旋压缩机，其中，所述至少一个第二输油通路设置为将润滑油直接排出至所述压缩机构与所述主轴承座构成的空间的外部。
  12. 根据权利要求1至5中任一项所述的涡旋压缩机，其中，所述涡旋压缩机为高压侧涡旋压缩机。
PCT/CN2019/114651 2018-11-06 2019-10-31 涡旋压缩机 WO2020093924A1 (zh)

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