WO2021203638A1 - 涡旋压缩机的配重组件及涡旋压缩机 - Google Patents

涡旋压缩机的配重组件及涡旋压缩机 Download PDF

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Publication number
WO2021203638A1
WO2021203638A1 PCT/CN2020/118016 CN2020118016W WO2021203638A1 WO 2021203638 A1 WO2021203638 A1 WO 2021203638A1 CN 2020118016 W CN2020118016 W CN 2020118016W WO 2021203638 A1 WO2021203638 A1 WO 2021203638A1
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Prior art keywords
oil
scroll compressor
counterweight
counterweight assembly
scroll
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PCT/CN2020/118016
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English (en)
French (fr)
Inventor
贾祥敏
刘强
秦岩
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.)
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Priority claimed from CN202010266516.6A external-priority patent/CN113494457B/zh
Priority claimed from CN202020493852.XU external-priority patent/CN212389528U/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 WO2021203638A1 publication Critical patent/WO2021203638A1/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

Definitions

  • the present disclosure relates to a counterweight assembly of a scroll compressor and a scroll compressor including the counterweight assembly.
  • Scroll compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems.
  • the scroll compressor includes a compression mechanism for compressing working fluid (such as refrigerant).
  • the compression mechanism includes a movable scroll and a fixed scroll. When the scroll compressor is running, the drive shaft drives the movable scroll relative to the fixed scroll. The orbiting relative motion enables the movable scroll and the fixed scroll to maintain dynamic engagement with each other, thereby forming a series of compression chambers between the movable scroll and the fixed scroll to compress the working fluid.
  • an eccentric pin is provided at the drive shaft to use the principle of eccentricity to make the movable scroll relative to The fixed scroll performs circular translation.
  • this eccentric configuration may cause unbalanced motion of moving parts, thereby increasing motion noise and unnecessary friction.
  • it is usually used in scroll compressors.
  • the drive shaft and other places are equipped with counterweights for balancing.
  • the counterweight is also provided with an oil stirring surface, that is, when the counterweight rotates with the drive shaft, the oil stirring surface can stir nearby lubricating oil to promote the flow of lubricating oil to the surrounding moving parts. And its relative motion contact surface to achieve better lubrication.
  • the oil stirring surface is usually set to have a larger inclination.
  • this inclined surface design will significantly change the position of the center of mass of the counterweight. Especially the inclined surface design at certain angles will cause the center of mass of the counterweight to move along the direction of the longitudinal axis and deviate from the center of mass of the drive bushing matched with the eccentric pin, which may result in a larger deflection moment and cause the lining
  • the relative offset and wear of the sleeve and the drive bearing is not conducive to the stability of operation. Therefore, it is necessary to improve the counterweight in order to ensure the dynamic balance and further improve the oil stirring efficiency and reduce the oil stirring power consumption while avoiding the bushing and the drive The relative offset and wear of the bearing.
  • one aspect of the present disclosure provides a counterweight assembly of a scroll compressor, the scroll compressor including a compression mechanism adapted to compress a working fluid and a drive shaft adapted to drive the compression mechanism
  • the compression mechanism includes a movable scroll having a driving coupling portion, the driving shaft includes a driving portion, and the driving coupling portion is drivingly engaged with the driving portion so that the driving shaft can drive the movable scroll, so
  • the counterweight components include:
  • a bushing provided between the driving coupling part and the driving part
  • the counterweight member includes a base mounted to the bushing or integrally formed with the bushing and a counterweight portion extending from the base, and the counterweight portion follows The rotation of the drive shaft rotates so as to have an oil stirring surface as a windward surface,
  • At least one oil inlet is provided on the oil stirring surface
  • at least one oil outlet is provided on the top end surface of the counterweight portion
  • at least one oil inlet is provided inside the counterweight portion, and extends from the at least one oil inlet At least one oil passage to the at least one oil outlet.
  • the oil can be stirred and the lubricating oil can be further targeted to the specific position-the thrust surface, so that the counterweight component can simultaneously play the role of stirring The role of oil and oil transportation.
  • the at least one oil passage extends along the direction of the rotation axis of the counterweight assembly.
  • the at least one oil passage is inclined with respect to the rotation axis of the counterweight assembly such that the at least one oil inlet is located in the rotation direction of the counterweight part.
  • the at least one oil passage includes a plurality of oil passages, which are independent of each other or communicate with each other.
  • the at least one oil inlet is positioned close to the base in the direction of the rotation axis of the counterweight assembly.
  • the height of the counterweight part is set such that: in the installation state of the counterweight component, in the direction of the rotation axis of the counterweight component, the at least one oil outlet
  • the distance between the port and the thrust surface of the main bearing seat of the scroll compressor that is in sliding contact with the movable scroll is less than or equal to 5.5 mm.
  • the oil droplets will be thrown out along the direction of rotation, and then the height of the oil droplets will not continue to increase because it is no longer affected by the rotating force.
  • the distance between the oil outlet and the thrust surface is too large, a large amount of oil is thrown onto the inner wall of the main bearing cover and cannot reach the thrust surface.
  • the height of the counterweight part is set such that: in the installation state of the counterweight component, in the direction of the rotation axis of the counterweight component, the at least one oil outlet
  • the distance between the port and the thrust surface of the main bearing seat of the scroll compressor that is in sliding contact with the movable scroll is less than or equal to 3 mm.
  • the weight portion has an upper end portion away from the base and a lower end portion adjacent to the base, and the upper end portion faces the weight portion relative to the lower end portion.
  • the front side of the rotation direction protrudes.
  • This configuration can lift the center of mass of the weight portion upward, thereby avoiding the center of mass of the weight portion from moving down along the longitudinal axis and deviating from the center of mass of the bushing, so it can avoid the generation of a larger center of mass in the bushing.
  • the deflection moment improves the operation stability, and the oil stirring surface of this inclined surface design can also significantly reduce the oil stirring resistance, thereby improving the oil stirring efficiency and reducing the oil stirring power consumption.
  • the angle formed by each part of the oil stirring surface and the lower edge of the weight portion is greater than 90°.
  • the oil stirring surface includes a convex arc surface, a concave arc surface, a flat surface, a step surface or a combination thereof.
  • the base is a ring-shaped mounting portion, and the ring-shaped mounting portion is sleeved on the outside of the bush to be fixedly installed with the bush.
  • Another aspect of the present disclosure provides a scroll compressor, which is characterized in that the scroll compressor includes the aforementioned counterweight assembly.
  • the counterweight assembly is configured such that: when the counterweight assembly is installed in the scroll compressor, the at least one oil outlet is located in the scroll compressor The radial inner side of the thrust surface of the main bearing housing.
  • the counterweight assembly and scroll compressor of the scroll compressor according to the present disclosure provide at least the following beneficial technical effects: the counterweight assembly and scroll compressor of the scroll compressor according to the present disclosure can perform scroll compression
  • the movement of the internal parts of the machine provides a good balance of movement, and can achieve good oil stirring and oil transport effects, and has a simple structure and easy processing and manufacturing, with high cost-effectiveness.
  • Fig. 1 shows a longitudinal sectional view of a scroll compressor according to the present disclosure
  • Figures 2a to 2c show a first embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 2a shows a perspective view of the counterweight member, and Figure 2b shows a front view of the counterweight member, Figure 2c shows a perspective view of the counterweight assembly when it is mounted to the drive shaft of the scroll compressor;
  • Figures 3a and 3b show a second embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 3a shows a perspective view of the counterweight member, and Figure 3b shows a front view of the counterweight member;
  • Figures 4a and 4b show a third embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 4a shows a perspective view of the counterweight assembly, and Figure 4b shows a side view of the counterweight assembly;
  • Figures 5a and 5b show examples of the counterweight assembly of the prior art scroll compressor, wherein Figure 5a shows a perspective view of the counterweight assembly, and Figure 5b shows a side view of the counterweight assembly;
  • Figures 6a to 6d show a fourth embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 6a shows a perspective view of the counterweight assembly, Figure 6b shows a side view of the counterweight assembly, and Figure 6c A front view of the counterweight member is shown, and FIG. 6d shows a perspective view when the counterweight assembly is mounted to the eccentric pin of the drive shaft.
  • Scroll compressor 1 housing 12; stator 14; rotor 15; drive shaft 16
  • Fixed scroll 22 Fixed scroll 22; fixed scroll end plate 221; fixed scroll scroll S2; orbiting scroll 24
  • Counterweight member 50 Annular mounting part 501; Counterweight part 502; Oil stirring surface 5022
  • the scroll compressor shown in FIG. 1 is exemplarily shown as a low-pressure side scroll compressor—that is, the electric motor is located in a low-pressure space, but the scroll compressor according to the present disclosure is not limited to this Type, the present disclosure is also applicable to other suitable types of scroll compressors such as the high-pressure side scroll compressor-the electric motor is located in the high-pressure space.
  • FIG. 1 shows a longitudinal cross-sectional view of a scroll compressor 1 according to the present disclosure.
  • the overall structure of the scroll compressor 1 according to the present disclosure will be briefly described with reference to FIG. 1.
  • the scroll compressor 1 includes a substantially cylindrical casing 12, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 40, and a working fluid suitable for compressing a working fluid (such as a refrigerant). ) Compression mechanism CM.
  • the cover 26 at the top of the housing 12 and the base 28 at the bottom of the housing 12 may be mounted to the housing 12 so as to define the internal volume of the scroll compressor 1.
  • Lubricant such as lubricating oil
  • the drive shaft 16 is provided with an upward extension from the oil sump O.
  • the oil supply path (not specifically shown in the figure) to the upper end of the drive shaft 16 facilitates further supply of lubricating oil to the main bearing housing 40 and the compression mechanism CM to provide lubrication.
  • the scroll compressor 1 further includes a partition 19 arranged between the top cover 26 and the casing 12 to partition the internal space of the scroll compressor 1 into a high-pressure space A2 and a low-pressure space A1, specifically, the partition 19 and the cover A high-pressure space A2 is formed between 26, and a low-pressure space A1 is formed between the partition 19, the housing 12, and the base 28.
  • the housing 12 in the low-pressure space A1 is provided with an intake pipe 18 for introducing the low-pressure working fluid to be compressed, and the high-pressure space A2 is provided with a device for discharging the compressed high-temperature and high-pressure fluid to the outside of the scroll compressor 1.
  • Exhaust pipe 17. As mentioned above, the embodiment shown in FIG. 1 is an example of a low-pressure side scroll compressor. Therefore, as shown in FIG. 1, the motor and the compression mechanism CM are located in the low-pressure space A1.
  • the compression mechanism CM includes a movable scroll 24 and a fixed scroll 22.
  • the fixed scroll 22 includes a fixed scroll end plate 221 and a fixed scroll scroll S2;
  • the movable scroll 24 includes a movable scroll end plate 241, a movable scroll scroll S4 extending from the first side surface of the movable scroll end plate 241, and
  • a hub 240 (the hub corresponds to the drive coupling according to the present disclosure) extending from the second side surface of the movable scroll end plate 241.
  • the fixed scroll scroll S2 and the movable scroll scroll S4 are joined to form an open suction chamber in fluid communication with the outside of the compression mechanism CM.
  • the low-pressure space A1 is in fluid communication so as to introduce the working fluid to be compressed in the low-pressure space A1 into the compression mechanism CM; a series of compression chambers whose volumes gradually decrease from the radially outer side to the radially inner side (including the following row The central compression chamber connected to the port C).
  • the compression mechanism CM also includes an exhaust port C located at the radial center of the fixed scroll end plate 221. The exhaust port C can be in fluid communication with the high-pressure space A2 in the housing 12 and will be compressed with high temperature and high pressure. The fluid is discharged into the high-pressure space A2.
  • the motor and the compression mechanism CM are located in the high-pressure space.
  • the compression mechanism CM directly introduces low-pressure working fluid from the outside, for example, through a suction fluid pipe, and discharges the compressed high-temperature and high-pressure fluid into the internal volume of the housing.
  • the entire internal volume forms a high-pressure space. Therefore, the operating principles of the high-pressure side scroll compressor and the low-pressure side scroll compressor are basically the same.
  • a part of the drive shaft 16 is supported by a main bearing provided in the main bearing housing 40.
  • the upper end of the drive shaft 16 is formed with an eccentric crank pin (not specifically shown in the figure), and the eccentric crank pin is fitted into the hub 240 of the movable scroll 24 via a bush (for example, an unloading bush) 51 to drive the movable scroll 24 .
  • the eccentric crank pin corresponds to the driving part according to the present disclosure.
  • the main bearing housing 40 includes a main bearing cover plate 420 as a thrust plate.
  • the main bearing cover 420 may be fixed on the body of the main bearing seat 40 by a fixing device.
  • a space is formed between the body of the main bearing housing 40 and the main bearing cover plate 420 (it can also be said that the main bearing housing 40 defines a cavity).
  • the back side (second side surface) of the movable scroll 24 is supported by the main bearing cover plate 420.
  • the annular end surface 422 of the main bearing cover plate 420 is used to support the movable scroll 24.
  • the thrust surface 422 maintains contact with the back side of the movable scroll 24 and performs sliding movement relative to each other.
  • 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 around its longitudinal axis L, and the drive shaft 16 is coupled to the movable scroll 24 to drive the movable scroll 24.
  • the fixed scroll 22 is mounted to the main bearing housing 40 using mechanical fasteners, for example, to restrict the radial and circumferential movement of the fixed scroll 22 but allow the fixed scroll 22 to perform a certain degree of axial translation, and the movable scroll
  • the orbiting 24 is driven by the electric motor via the drive shaft 16, so that it can perform translational rotation relative to the fixed scroll 22 by means of, for example, an Oldham ring—that is, orbit (that is, the axis of the movable scroll 24 is relative to the fixed scroll 22).
  • the axis revolves, but the orbiting scroll 24 itself does not rotate around its axis—that is, spinning), so that the fixed scroll S2 and the orbiting scroll S4 are joined to form a series of volumes that gradually decrease from the radial outside to the radial inside. Small compression cavity.
  • the scroll compressor 1 The counterweight assembly 5 according to the embodiment of the present disclosure is provided. As shown in FIG. 1, the counterweight assembly 5 can be mounted to the upper end of the drive shaft 16 (in particular, the eccentric crank pin) and located in the space (cavity) defined by the main bearing housing 40, the counterweight assembly 5 is configured as It can rotate with the drive shaft 16 and the centrifugal force caused by the rotation of the counterweight assembly 5 acts on the drive shaft 16 to improve dynamic balance and force balance.
  • lubricating oil can be supplied to the space defined by the main bearing housing 40 where the counterweight assembly 5 is located via the oil passage in the drive shaft 16.
  • lubricating oil will accumulate in this space, so that the weight assembly 5 will whip the lubricating oil during the rotation (especially, the windward surface of the weight portion of the weight assembly 5 will whip the lubricating oil). Therefore, the windward surface of the counterweight assembly 5 is also called the oil stirring surface (not specifically shown in FIG. 1 and will be described in detail below).
  • the oil stirring surface agitates the surrounding lubrication while the counterweight assembly 5 rotates with the drive shaft 16
  • the oil arouses oil droplets and oil mist, so that the lubricating oil can be more fully dispersed to the surrounding moving parts-such as the orbiting scroll end plate of the scroll mechanism CM-and the contact surfaces of the parts in contact with the moving parts,
  • the thrust surface 422 of the main bearing cover 420 for supporting the movable scroll 24 provides better lubrication.
  • the counterweight assembly 5 is defined as including the aforementioned bushing 51 and a counterweight member 50 mounted to the bushing 51 or integrally formed with the bushing 51. It should be understood that, in some applications, the counterweight assembly 5 may not include the bushing 51, that is, it can be manufactured and used separately without the limitation of the structure of the bushing 51 itself.
  • Figures 2a to 2c show a first embodiment of the counterweight assembly 5 of the scroll compressor 1 according to the present disclosure, wherein Figure 2a shows a perspective view of the counterweight member 50, and Figure 2b shows the counterweight member 50 Figure 2c shows a perspective view of the counterweight assembly 5 installed to the main bearing housing 40 of the scroll compressor 1.
  • the weight assembly 5 includes a bush 51 (the bush 51 is removed in this embodiment) and a weight member 50 mounted to the bush 51, and the weight member 50 includes: a base — It is preferably configured as the ring-shaped mounting portion 501 shown in the figure, the ring-shaped mounting portion 501 is sleeved on the outside of the bushing 51 to be fixedly installed with the bushing 51; and from the base—the ring-shaped mounting portion 501— -A counterweight 502 extending to one side.
  • the weight portion 502 may be configured to extend radially outward to one side and then axially upward.
  • One side surface of the weight portion 502 is configured as an oil stirring surface 5022.
  • the oil stirring surface 5022 extends as a flat surface along the longitudinal axis (rotation axis) of the weight assembly 5, and is formed on the oil stirring surface 5022 of the weight portion 502.
  • Two oil inlets 5027 are provided on the upper part, the oil inlet 5027 is positioned close to the base in the direction of the longitudinal axis of the counterweight assembly 5, and two oil outlets are provided on the top end surface 5023 of the counterweight part 502 5028, and two separate oil passages (not visible in the figure) extending from the two oil inlets 5027 to the two oil outlets 5028 are respectively provided in the counterweight portion 502.
  • the lubricating oil can reach the two oil outlets 5028 through the two oil inlets 5027 and two separate oil passages, thereby removing the lubricating oil from the counterweight part.
  • the lower end 5026 of the 502 is supplied to the upper end 5024 (top end surface 5023) to reach other components and surfaces located near the top end surface 5023, such as the thrust surface 422 of the main bearing cover 420, as shown in Figure 2c,
  • the counterweight assembly 5 is installed in the scroll compressor 1
  • the counterweight assembly 5 is installed in the space defined by the main bearing housing 40, and the top end surface 5023 of the counterweight portion 502 abuts the thrust of the main bearing cover 420 Therefore, through the above-mentioned two oil inlets 5027, two separate oil passages and two oil outlets 5028, lubricating oil can be supplied to the thrust surface 422 of the main bearing cover 420 to the thrust surface
  • the frictional sliding contact between the 422 and the movable scroll 24 provides lubrication.
  • the counterweight assembly 5 is configured such that: in the state where the counterweight assembly 5 is mounted to the scroll compressor 1, in the direction of the longitudinal axis of the counterweight assembly 5 (ie, scroll compression In the direction of the longitudinal axis L of the machine 1, the distance between the oil outlet 5028 and the thrust surface 422 is less than or equal to 5.5 mm, so that the lubricant can be supplied to the thrust surface 422 more efficiently. Specifically, when the lubricating oil comes out of the oil outlet 5028, the oil droplets will be thrown out along the direction of rotation, and then the height of the oil droplets will not continue to increase because it is no longer affected by the rotating force.
  • the counterweight assembly 5 is configured such that the oil passage extends vertically upward along the direction of the longitudinal axis of the counterweight assembly 5 (ie, the direction of the longitudinal axis L of the scroll compressor 1) When the counterweight assembly 5 rotates, the centrifugal force causes the lubricating oil to flow upward in the oil path to the top end surface 5023, and then to the thrust surface 422.
  • the oil circuit of this configuration can be easily processed and manufactured by various methods well known in the prior art. However, the present disclosure is not limited to this. It should be understood that the oil circuit may also be relative to the longitudinal direction of the counterweight assembly 5.
  • the axis is inclined, or is a curved, wavy, step-like or other arbitrary shape of the oil path, as long as the purpose of supplying lubricating oil can be achieved, in the case that the oil path is inclined with respect to the rotation axis of the counterweight assembly 5
  • the oil passage is inclined such that the oil inlet 5027 is located on the front side of the oil outlet 5028 in the rotation direction of the counterweight portion 502.
  • the above two oil passages are not necessarily completely independent of each other, but may also be partially overlapped or staggered.
  • Figures 3a and 3b show a second embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 3a shows a perspective view of the counterweight member, and Figure 3b shows a front view of the counterweight member.
  • the second embodiment has substantially the same configuration as the first embodiment shown in FIGS. 2a to 2c, and further improvements have been made on this basis. The difference is: based on the configuration of the first embodiment, the second embodiment
  • the size of the oil stirring surface 5022 is specifically optimized.
  • the oil stirring surface 5022 of the counterweight portion 502 includes a lower surface F2 adjacent to the base (annular mounting portion 501) and a lower surface away from the base.
  • the upper surface F1 of the seat, wherein the oil stirring surface 5022 is preferably configured such that the projected area of the upper surface F1 in the circumferential direction of the counterweight member 50 is larger than the projected area of the lower surface F2 in the circumferential direction.
  • the projected area of the upper surface F1 and the lower surface F2 along the circumferential direction of the weight member 50 refers to the direction of rotation of the upper surface along the weight member.
  • the projection reference plane may be: a virtual plane parallel to the rotation axis of the counterweight member and passing through the intersection line of the oil stirring surface and the top surface of the base.
  • the points on the oil stirring surface will pass through the projection reference plane vertically.
  • the projection reference surface coincides with the oil stirring surface, that is, the entire oil stirring surface is located at the projection reference Surface. At this time, the projected areas of the upper surface and the lower surface are the largest and are respectively equal to their real areas.
  • the ratio of the projected area of the upper surface F1 in the circumferential direction of the counterweight member 50 to the projected area of the lower surface F2 in the circumferential direction is greater than or equal to 1.15, and more preferably, the ratio of the projected area of the upper surface F1 along the circumferential direction
  • the ratio of the projected area of the member 50 in the circumferential direction to the projected area of the lower surface F2 in the circumferential direction is greater than or equal to 1.3.
  • the purpose of this configuration is to further raise the center of mass of the counterweight portion 502 upward, and appropriately reduce the area of the lower surface F2 of the oil stirring surface 5022 that is usually in the lubricating oil, so as to reduce the oil stirring resistance and reduce Stirring power consumption.
  • the boundary between the upper surface F1 and the lower surface F2 may be defined such that the upper surface F1 and the lower surface F2 correspond to the oil level of the lubricating oil accumulated in the space defined by the main bearing housing 40 under normal circumstances.
  • the oil level is generally basically determined for a specific scroll compressor, but only according to the different actual operating conditions of the specific scroll compressor (such as high-speed/low-speed operation) or Some unexpected conditions (such as unexpected fuel shortage) and some changes.
  • the scroll compressor 1 is also provided with an oil drain path 11 to discharge the lubricating oil accumulated in the space of the main bearing housing 40 outward.
  • the opening of the oil drain path 11 provided at the peripheral wall of the main bearing housing 40 is roughly aligned with the position of the counterweight 502. Therefore, in this particular case where the oil drain path 11 for draining oil from the space (cavity) of the main bearing housing is provided, the oil level under normal circumstances is aligned with the opening of the oil drain path 11.
  • the boundary line between the upper surface F1 and the lower surface F2 according to the present embodiment is aligned with the opening of the oil discharge path 11.
  • the boundary D between the upper surface F1 and the lower surface F2 is located slightly above the step T of the oil stirring surface 5022. Then, it is also conceivable that the dividing line D exactly coincides with the step T, and it may even be better in some cases that the dividing line D is located below the step T.
  • the step portion T of the oil stirring surface 5022 is exactly aligned with the opening of the oil discharge path 11 so that the portion above the step portion T becomes the upper surface F1 and the portion below the step portion T becomes the lower surface F2.
  • the projected area of the upper face F1 can be made sufficiently larger than the projected area of the lower face F2.
  • most of the upper face F1 in the axial direction ie from the dividing line D to the top end face 5023
  • the lower face F2 has a relatively small thickness from the base (annular mounting portion 501) to most of the dividing line D. In this way, it is ensured that the projected area of the upper face F1 is larger than the projected area of the lower face F2.
  • Figures 4a and 4b show a third embodiment of the counterweight assembly of the scroll compressor according to the present disclosure, wherein Figure 4a shows a perspective view of the counterweight assembly, and Figure 4b shows a side view of the counterweight assembly.
  • the third embodiment has roughly the same configuration as the first embodiment shown in FIGS. 2a to 2c, and further improvements have been made on this basis. The difference is that: based on the configuration of the first embodiment, the third embodiment
  • the oil stirring surface 5022 is configured such that the upper end 5024 of the counterweight part 502 faces the circumferential direction of the counterweight part 502 (that is, the rotation direction of the counterweight part 502) relative to the lower end 5026 of the counterweight part 502.
  • the front side protrudes, and preferably, in this embodiment, the oil stirring surface 5022 is configured to be opposite to the lower edge 5021 of the counterweight portion 502 (the lower edge 5021 can be regarded as being in a plane perpendicular to the longitudinal axis L of the drive shaft 16
  • the upper is a plane inclined at an obtuse angle, that is, the angles formed by the various parts of the oil stirring surface 5022 and the lower edge 5021 of the weight portion 502 are all greater than 90°, and more preferably all are less than 150°.
  • This configuration can raise the center of mass of the weight portion 502 upward, thereby preventing the center of mass of the weight portion 502 from moving downward along the longitudinal axis L and deviating from the center of mass of the bushing 51 (for example, as shown in FIGS. 5a and 5b)
  • the oil stirring surface 5022 of this inclined surface design can also be used.
  • Figs. 5a and 5b show examples of the counterweight assembly P5 of the prior art scroll compressor, wherein Fig. 5a shows a perspective view of the counterweight assembly P5, and Fig. 5b shows a side view of the counterweight assembly P5.
  • the oil stirring surface P5022 of the counterweight component P5 in the prior art is generally configured as a plane inclined at an acute angle with respect to the lower edge P5021 of the counterweight part P502, which is completely contrary to the above-mentioned embodiment of the present disclosure.
  • the design of the oil stirring surface P5022 will cause the center of mass of the counterweight P502 to move down along the longitudinal axis L and deviate from the center of mass of the bushing P51, resulting in a larger deflection moment in the bushing P51 relative to
  • the drive bearing provided between the bush P51 and the hub 240 of the movable scroll 24 is offset.
  • the above-mentioned configuration of the present disclosure can avoid this problem in the prior art, and at the same time can ensure high oil stirring efficiency.
  • the oil stirring surface 5022 is configured in a planar shape, the present disclosure is not limited to this, and the oil stirring surface 5022 may include a convex arc surface, a concave arc surface, a flat surface, and a stepped surface. (Surface composed of multiple planes with different inclination angles) or any combination thereof.
  • the base of the weight member 50 is configured as an annular mounting portion 501 that is sleeved on the outside of the bushing 51 to be fixedly mounted with the bushing 51, the present invention The disclosure is not limited to this.
  • the base of the weight member 50 may also be integrally formed with the bush 51.
  • Figures 6a to 6d show a fourth embodiment of the counterweight assembly 5 of the scroll compressor 1 according to the present disclosure, wherein Figure 6a shows a perspective view of the counterweight assembly 5, and Figure 6b shows a side view of the counterweight assembly 5 Fig. 6c shows a front view of the counterweight assembly 5, and Fig. 6d shows a perspective view of the counterweight assembly 5 when it is mounted to the drive shaft 16 of the scroll compressor 1.
  • the fourth embodiment includes the features of the foregoing various embodiments according to the present disclosure, and is a combination of the foregoing various embodiments.
  • one side surface of the weight portion 502 is configured as an oil stirring surface 5022, and the upper end portion 5024 of the weight portion 502 faces the circumferential direction of the weight portion 502 relative to the lower end portion 5026 of the weight portion 502 (that is, the weight portion 502
  • the front side of the rotating direction of the weight portion 502) protrudes so that the oil stirring surface 5022 is configured as a plane inclined at an obtuse angle with respect to the lower edge 5021 of the weight portion 502, and the oil stirring surface 5022 of the weight portion 502 is provided with Two oil inlets 5027, two oil outlets 5028 are provided on the top end surface 5023 of the counterweight portion 502, and the counterweight portion 502 is provided with two oil inlets 5027 extending from the two oil inlets 5027 to two oil outlets respectively Two separate oil passages of 5028, so that the thrust surface 422 supplies lubricating oil (see Figure 6d), and preferably, the distance between the oil outlet 5028 and the thrust surface 422 is less than or equal to 6mm
  • the ratio of the projected area of the upper surface F1 of the oil stirring surface 5022 in the circumferential direction of the counterweight assembly 5 to the projected area of the lower surface F2 in the circumferential direction is greater than or equal to 1.3.
  • the scroll compressor 1 includes the counterweight assembly of the scroll compressor according to the foregoing embodiment of the present disclosure. .

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Abstract

一种涡旋压缩机的配重组件及涡旋压缩机（1），涡旋压缩机（1）包括压缩机构和驱动轴（16），配重组件（5）包括：衬套，衬套（51）设置在驱动联接部与驱动部之间；以及配重构件（50），配重构件（50）包括安装至衬套（51）或者与衬套（51）一体地形成的基座以及从基座延伸的配重部（502），配重部（502）随着驱动轴（16）转动，从而具有作为迎风面的搅油面（5022），在搅油面（5022）上设置至少一个进油口（5027），在配重部（502）的顶部端面（5023）上设置至少一个出油口（5028），在配重部（502）内部设置从至少一个进油口（5027）延伸到至少一个出油口（5028）的至少一个油路（5029）。该结构能够提供更好的运动平衡，能够实现更好的搅油和输油效果，同时显著降低搅油功耗，并且结构简单且易于加工制造。

Description

涡旋压缩机的配重组件及涡旋压缩机
本申请要求以下中国专利申请的优先权：于2020年4月7日提交中国专利局的申请号为202010266516.6、发明创造名称为“涡旋压缩机的配重组件及涡旋压缩机”的中国专利申请；于2020年4月7日提交中国专利局的申请号为202020493852.X、发明创造名称为“涡旋压缩机的配重组件及涡旋压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种涡旋压缩机的配重组件及包括该配重组件的涡旋压缩机。
背景技术
本部分提供了与本公开相关的背景信息，这些信息并不必然构成现有技术。
涡旋压缩机可以应用于例如制冷系统、空调系统和热泵系统中。涡旋压缩机包括用于压缩工作流体(例如制冷剂)的压缩机构，压缩机构包括动涡旋和定涡旋，在涡旋压缩机运转时，驱动轴驱动动涡旋相对于定涡旋进行绕动式相对运动，使得动涡旋涡卷与定涡旋涡卷彼此保持动态的接合从而在动涡旋涡卷与定涡旋涡卷之间形成一系列压缩腔，以压缩工作流体。
为了实现动涡旋相对于定涡旋进行绕动式相对运动，在涡旋压缩机中，在设置防自转机构的同时，在驱动轴处设置偏心销以利用偏心原理来使动涡旋相对于定涡旋进行圆周平动，然而，这种偏心构型可能会导致运动部件的运动不平衡，进而增大运动噪音以及不必要的摩擦，为了抑制这种运动不平衡，通常在涡旋压缩机的驱动轴等处设置配重来进行平衡。并且，对于一些特定的配重，配重还设置有搅油面，即，在配重随着驱动轴转动时，其搅油面能够搅动附近的润滑油以促进润滑油流动至周围的运动部件及其相对运动接触面之间，以实现更好的润滑作用。
在实际应用中，为了减小搅油面的搅油阻力以降低功耗，通常将搅油面设置为具有较大的倾斜度，但是，这种斜面设计将显著改变配重的质量中心位置，特别是在某些角度下的斜面设计将导致配重的质量中心沿着纵向轴线的方向 移动而偏离与偏心销配合的驱动衬套的质量中心，因此可能导致较大的偏转力矩，并且导致衬套与驱动轴承相对偏移及磨损，不利于操作稳定性，因此，需要对配重进行改进，以期在确保动平衡以及进一步改善搅油效率和减小搅油功耗的同时避免衬套与驱动轴承的相对偏移及磨损。
发明内容
在本部分中提供本公开的总体概要，而不是本公开完全范围或本公开所有特征的全面公开。
本公开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，本公开的一方面提供了一种涡旋压缩机的配重组件，所述涡旋压缩机包括适于对工作流体进行压缩的压缩机构以及适于驱动所述压缩机构的驱动轴，所述压缩机构包括具有驱动联接部的动涡旋，所述驱动轴包括驱动部，所述驱动联接部与所述驱动部驱动地接合使得所述驱动轴能够驱动所述动涡旋，所述配重组件包括：
衬套，所述衬套设置在所述驱动联接部与所述驱动部之间；以及
配重构件，所述配重构件包括安装至所述衬套或者与所述衬套一体地形成的基座以及从所述基座延伸的配重部，在所述配重部随着所述驱动轴的旋转而旋转从而具有作为迎风面的搅油面，
其中，在所述搅油面上设置至少一个进油口，在所述配重部的顶部端面上设置至少一个出油口，在所述配重部内部设置从所述至少一个进油口延伸至所述至少一个出油口的至少一个油路。
通过设置上述构型的进油口、出油口和油路，能够搅油的同时进一步有针对性地将润滑油输送至特定的位置——止推面，从而使得配重组件能够同时发挥搅油和输油的作用。
根据本公开的一个优选实施方式，所述至少一个油路沿着所述配重组件的旋转轴线的方向延伸。
根据本公开的一个优选实施方式，所述至少一个油路相对于所述配重组件的旋转轴线倾斜成使得所述至少一个进油口在所述配重部的旋转方向上位于所述至少一个出油口的前侧。
根据本公开的一个优选实施方式，所述至少一个油路包括多个油路，所述 多个油路彼此独立或者彼此连通。
根据本公开的一个优选实施方式，所述至少一个进油口定位成在所述配重组件的旋转轴线的方向上靠近所述基座。
根据本公开的一个优选实施方式，所述配重部的高度设置为使得：在所述配重组件的安装状态下，在所述配重组件的旋转轴线的方向上，所述至少一个出油口与所述涡旋压缩机的主轴承座的与所述动涡旋滑动接触的止推面的距离小于等于5.5mm。
具体来讲，当润滑油从出油口出来时，油滴会沿着旋转方向被甩出来，随后因为不再受到旋转力的作用，油滴的高度基本不会继续增加。当出油口与止推面的距离过大时，大量的油被甩到主轴承盖板的内壁上，而不能到达止推面。实验显示：当出油口与止推面的距离小于等于时是较优的，能够确保足够的润滑油被输送至止推面，可以改善止推面的润滑和并降低磨损；当大于时，只有比较少的润滑油到达止推面，对改善止推面的润滑和降低磨损没有帮助。
根据本公开的一个优选实施方式，所述配重部的高度设置为使得：在所述配重组件的安装状态下，在所述配重组件的旋转轴线的方向上，所述至少一个出油口与所述涡旋压缩机的主轴承座的与所述动涡旋滑动接触的止推面的距离小于等于3mm。
根据本公开的一个优选实施方式，所述配重部具有远离所述基座的上端部和邻近所述基座的下端部，所述上端部相对于所述下端部朝向所述配重部的旋转方向的前侧突出。
这种构型能够向上提升配重部的质量中心，从而避免配重部的质量中心沿着纵向轴线的方向向下移动而偏离衬套的质量中心，因此可以避免在衬套中产生较大的偏转力矩，改善操作稳定性，并且这种斜面设计的搅油面也能够显著减小搅油阻力从而提高搅油效率并减小搅油功耗。
根据本公开的一个优选实施方式，所述搅油面的各部分与所述配重部的下边缘所成的角度均大于90°。
根据本公开的一个优选实施方式，所述搅油面包括凸出的弧面、内凹的弧面、平面、台阶面或其组合。
根据本公开的一个优选实施方式，所述基座为环状安装部，所述环状安装部套置在所述衬套的外部以与所述衬套固定安装。
本公开的另一方面提供一种涡旋压缩机，其特征在于，所述涡旋压缩机包括如前所述的配重组件。
根据本公开的一个优选实施方式，所述配重组件构造成使得：当所述配重组件安装在所述涡旋压缩机中时，所述至少一个出油口位于所述涡旋压缩机的主轴承座的止推面的径向内侧。
综上可知，根据本公开的涡旋压缩机的配重组件及涡旋压缩机至少提供以下有益技术效果：根据本公开的涡旋压缩机的配重组件及涡旋压缩机能够为涡旋压缩机内部部件的运动提供良好的运动平衡，并且能够实现良好的搅油和输油效果，并且结构简单且易于加工制造，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，本公开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示出根据本公开的涡旋压缩机的纵向截面图；
图2a至图2c示出根据本公开的涡旋压缩机的配重组件的第一实施方式，其中，图2a示出配重构件的立体图，图2b示出配重构件的正视图，图2c示出配重组件安装至涡旋压缩机的驱动轴时的立体图；
图3a和图3b示出根据本公开的涡旋压缩机的配重组件的第二实施方式，其中，图3a示出配重构件的立体图，图3b示出配重构件的正视图；
图4a和图4b示出根据本公开的涡旋压缩机的配重组件的第三实施方式，其中，图4a示出配重组件的立体图，图4b示出配重组件的侧视图；
图5a和图5b示出现有技术的涡旋压缩机的配重组件的示例，其中，图5a示出配重组件的立体图，图5b示出配重组件的侧视图；
图6a至图6d示出根据本公开的涡旋压缩机的配重组件的第四实施方式，其中，图6a示出配重组件的立体图，图6b示出配重组件的侧视图，图6c示出配重构件的正视图，图6d示出配重组件安装至驱动轴的偏心销时的立体图。
参考标记列表
涡旋压缩机1；壳体12；定子14；转子15；驱动轴16
主轴承座40；压缩机构CM；盖26；基部28；油池O
高压空间A2；低压空间A1；隔板19；排气管17；动涡旋24
定涡旋22；定涡旋端板221；定涡旋涡卷S2；动涡旋24
动涡旋端板241；动涡旋涡卷S4；毂部240；排气口C；衬套51
主轴承盖板420；止推面422；纵向轴线L；配重组件5
配重构件50；环状安装部501；配重部502；搅油面5022
上端部5024；下端部5026；下边缘5021；顶部端面5023
现有技术的配重组件P5；现有技术的搅油面P5022
现有技术的配重部P502；现有技术的下边缘P5021
现有技术的衬套P51
进油口5027；出油口5028；下部面F2；上部面F1
分界线D；台阶部T；排油路径11
具体实施方式
现在将结合附图1-6d并对照现有技术来对本公开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公开及其应用或用途。
为了便于描述，如图1所示的涡旋压缩机示例性地示出为低压侧涡旋压缩机——即，电动马达位于低压空间中，然而根据本公开的涡旋压缩机并不限于此类型，本公开也适用于诸如高压侧涡旋压缩机——电动马达位于高压空间中——等其他合适类型的涡旋压缩机。
图1示出了根据本公开的涡旋压缩机1的纵向截面图。首先，参照图1概要地描述根据本公开的涡旋压缩机1的总体结构。
如图1所示，涡旋压缩机1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40、适于压缩工作流体(例如制冷剂)的压缩机构CM。
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内部容积的底部内的油池O中以用于润滑涡旋压缩机1的各个相关部件，具体地，例如，驱动轴16中设置有从油池O向上延伸至驱动轴16的上 端部的供油油路(图中未具体示出)，从而便于进一步将润滑油供送至主轴承座40和压缩机构CM，以提供润滑作用。
涡旋压缩机1还包括设置在顶部盖26和壳体12之间以将涡旋压缩机1的内部空间分隔成高压空间A2和低压空间A1的隔板19，具体地，隔板19与盖26之间构成高压空间A2，而隔板19、壳体12和基部28之间构成低压空间A1。在低压空间A1处的壳体12上设置有用于引入待被压缩的低压工作流体的进气管18，在高压空间A2内设置有用于将被压缩的高温高压流体排出至涡旋压缩机1外部的排气管17。如前所述，图1中所示的实施方式是以低压侧涡旋压缩机为例，因此，如图1中所示，马达以及压缩机构CM位于该低压空间A1中。
压缩机构CM包括动涡旋24、定涡旋22。定涡旋22包括定涡旋端板221和定涡旋涡卷S2；动涡旋24包括动涡旋端板241、从动涡旋端板241的第一侧面延伸的动涡旋涡卷S4和从动涡旋端板241的第二侧面延伸的毂部240(毂部对应于根据本公开的驱动联接部)。压缩机构CM中由定涡旋涡卷S2与动涡旋涡卷S4接合而形成有：与压缩机构CM外部流体连通的开放的吸气腔，所述吸气腔的进气口与壳体12内的所述低压空间A1流体连通从而将低压空间A1中的待压缩的工作流体引入压缩机构CM中；一系列体积从径向外侧向径向内侧逐渐减小的压缩腔(包括能够与下述的排气口C连通的中央压缩腔)。另外，压缩机构CM还包括位于定涡旋端板221的径向中心处的排气口C，排气口C能够与壳体12内的所述高压空间A2流体连通并将被压缩的高温高压流体排出至高压空间A2中。
相反，对于高压侧涡旋压缩机，马达以及压缩机构CM位于高压空间中，压缩机构CM例如通过吸入流体管从外部直接引入低压工作流体并且将压缩后的高温高压流体排出至壳体内的内部容积而使整个内部容积形成高压空间，因此，高压侧涡旋压缩机与低压侧涡旋压缩机的操作原理大体相同而区别主要在于压缩机构CM所处的空间压力不同，对此不再赘述。
驱动轴16的一部分由设置在主轴承座40中的主轴承支撑。驱动轴16的上端部形成有偏心曲柄销(图中未具体示出)，偏心曲柄销经由衬套(例如卸载衬套)51配合在动涡旋24的毂部240中以驱动动涡旋24。这里，需要说明的是，偏心曲柄销对应于根据本公开的驱动部。
主轴承座40包括作为止推板的主轴承盖板420。主轴承盖板420可以通过固定装置固定在主轴承座40的本体上。在主轴承座40的本体和主轴承盖板420之间形成空间(也可以说，主轴承座40限定有凹腔)。动涡旋24的背侧(第二侧面)由主轴承盖板420支承，主轴承盖板420的用于支承动涡旋24的环形端面为止推面422，在涡旋压缩机1运转期间，该止推面422与动涡旋24的背侧保持接触并且相对于彼此进行滑动运动。
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绕其纵向轴线L旋转，驱动轴16联接至动涡旋24以驱动动涡旋24。具体地，定涡旋22例如使用机械紧固件安装至主轴承座40以例如限制定涡旋22的径向运动和周向运动但是允许定涡旋22进行一定程度的轴向平移，动涡旋24经由驱动轴16被电动马达驱动，从而借助例如十字滑环而能够相对于定涡旋22进行平动转动——即绕动(亦即，动涡旋24的轴线相对于定涡旋22的轴线公转，但是动涡旋24本身并未绕其轴线旋转——即自转)，从而由定涡旋涡卷S2与动涡旋涡卷S4接合形成一系列体积从径向外侧向径向内侧逐渐减小的压缩腔。
为了避免或减小运动不平衡，并且为了降低定涡旋22的定涡旋涡卷S2的侧表面与动涡旋24的动涡旋涡卷S4的侧表面之间的接触力，涡旋压缩机1设置有根据本公开的实施方式的配重组件5。如图1中所示，配重组件5可以安装至驱动轴16的上端部(特别地，偏心曲柄销)并且位于由主轴承座40限定的空间(凹腔)中，配重组件5构造成能够随驱动轴16旋转并且配重组件5由于旋转而造成的离心力作用在驱动轴16上，以改善动平衡和受力平衡。
另外，如前所述，润滑油能够经由驱动轴16中的油路而被供给至配重组件5所在的由主轴承座40限定的空间中。通常，在该空间中会积聚有润滑油，从而配重组件5在旋转过程中会搅打润滑油(特别地，配重组件5的配重部的迎风面会搅打润滑油)。因此，配重组件5的迎风面也称为搅油面(图1中未具体示出，将在下文具体说明)，在配重组件5随驱动轴16转动的同时搅油面搅动周围的润滑油以激起油滴和油雾，以使润滑油能够更充分地分散至周围的运动部件——如涡旋机构CM的动涡旋端板——以及与运动部件接触的部件的接触面，尤其是主轴承盖板420的用于支承动涡旋24的止推面422，从而提供更好的润滑作用。
优选地，在本公开的各实施方式中，将配重组件5定义为包括前述衬套51以及安装至衬套51或与衬套51一体成型的配重构件50。应当理解的是，在一些应用中，配重组件5也可以不包括衬套51，也就是说，其可以脱离衬套51本身结构的限制而被单独制造和应用。
下面将结合附图2a至图6d具体描述根据本公开的涡旋压缩机的配重组件的优选实施方式。
图2a至图2c示出根据本公开的涡旋压缩机1的配重组件5的第一实施方式，其中，图2a示出配重构件50的立体图，图2b示出配重构件50的正视图；图2c示出配重组件5安装至涡旋压缩机1的主轴承座40时的立体图。如图所示，配重组件5包括衬套51(在此实施方式中移除了衬套51)以及安装至衬套51的配重构件50，并且，配重构件50包括：基座——优选地构造为图中所示的环状安装部501，环状安装部501套置在衬套51的外部以与衬套51固定安装；以及从基座——环状安装部501——向一侧延伸的配重部502。特别地，配重部502可以构造为向一侧径向向外延伸然后再轴向向上延伸。配重部502的一个侧面构造为搅油面5022，搅油面5022沿着配重组件5的纵向轴线(旋转轴线)的方向延伸成平直表面，并且在配重部502的搅油面5022上设置有两个进油口5027，进油口5027定位成在配重组件5的纵向轴线的方向上靠近所述基座，在配重部502的顶部端面5023上设置有两个出油口5028，并且在配重部502内部设置有分别从两个进油口5027延伸至两个出油口5028的两个单独的油路(图中不可见)。由此，当配重组件5随着驱动轴16旋转时，润滑油能够经由两个进油口5027、两个单独的油路到达两个出油口5028处，从而将润滑油从配重部502的下端部5026供应至上端部5024(顶部端面5023)，以到达位于顶部端面5023附近的其他部件和表面，例如主轴承盖板420的止推面422，如在图2c中示出的，当配重组件5安装在涡旋压缩机1中时，配重组件5安装在由主轴承座40限定的空间中，并且，配重部502的顶部端面5023邻接主轴承盖板420的止推面422，因此，通过上述两个进油口5027、两个单独的油路和两个出油口5028，能够将润滑油供送至主轴承盖板420的止推面422，以为止推面422与动涡旋24之间的摩擦滑动接触提供润滑。优选地，在本实施方式中，将配重组件5构造为使得：在配重组件5安装至涡旋压缩机1的状态下，在配重组件5的纵向轴线的方向(即，涡旋压缩机1 的纵向轴线L的方向)上，出油口5028与止推面422的距离小于等于5.5mm，从而能够更高效地向止推面422供送润滑油。具体来讲，当润滑油从出油口5028出来时，油滴会沿着旋转方向被甩出来，随后因为不再受到旋转力的作用，油滴的高度基本不会继续增加。当出油口5028与止推面422的距离过大时，大量的油被甩到主轴承盖板420的内壁上，而不能到达止推面422。实验显示：当出油口5028与止推面422的距离小于等于5.5mm时是较优的，能够确保足够的润滑油被输送至止推面422，可以改善止推面422的润滑和并降低磨损；当大于5.5mm时，只有比较少的润滑油到达止推面422，对改善止推面422的润滑和降低磨损没有帮助。
进一步，优选地，在本实施方式中，配重组件5构造为使得油路沿着配重组件5的纵向轴线的方向(即，涡旋压缩机1的纵向轴线L的方向)竖直向上延伸，当配重组件5旋转时，通过离心力的作用，使得润滑油在油路中向上流动至顶部端面5023，进而到达止推面422。这种构型的油路易于通过现有技术所熟知的各种方法简单地被加工制造，但是，本公开不限于此，应当理解的是，该油路也可以相对于配重组件5的纵向轴线倾斜、或者是弯曲的、波形的、台阶状或其他任意形状的油路，只要能够实现供送润滑油的目的即可，在所述油路相对于配重组件5的旋转轴线倾斜的情况下，该油路倾斜成使得进油口5027在配重部502的旋转方向上位于出油口5028的前侧。此外，应当理解的是，上述两个油路不一定是完全彼此独立的，也可以是部分重叠或交错的，例如，基于上述两个进油口5027和两个出油口5028，完全可以设置仅一条油路，该油路仅在两个进油口5027和两个出油口5028处分支以分别连通两个进油口5027和两个出油口5028，等等，可以根据实际需要设置不同构型的油路；并且进油口和出油口的数目，以及相应的油路的数目都可以是任意数目，可以根据实际需要进行设置。
图3a和图3b示出根据本公开的涡旋压缩机的配重组件的第二实施方式，其中，图3a示出配重构件的立体图，图3b示出配重构件的正视图。第二实施方式与图2a至图2c所示的第一实施方式具有大致相同的构型，并在此基础上做了进一步改进，其区别在于：基于第一实施方式的构型，第二实施方式对搅油面5022的尺寸进行了具体优化，如图3b中最佳示出的，配重部502的搅油面5022包括临近基座(环状安装部501)的下部面F2和远离基座的上部面F1， 其中，搅油面5022优选地构造为使得：上部面F1的沿配重构件50的周向方向的投影面积大于下部面F2的沿周向方向的投影面积。此处需要说明的是，上部面F1和下部面F2的沿配重构件50的周向方向(即旋转方向/自转方向)的投影面积是指：上部面的沿配重构件的自转方向投影至投影基准面的投影面积以及下部面的沿该自转方向投影至该投影基准面的投影面积。其中，投影基准面可以为：平行于配重构件的旋转轴线并且经过所述搅油面与所述基座的顶部面的相交线的虚拟平面。在搅油面自转时搅油面上的各点将会垂直地通过该投影基准面。另外，在整个搅油面竖向地延伸从而平行于配重构件的旋转轴线并且面向自转方向的前方的示例中，投影基准面与搅油面重合，亦即，整个搅油面位于投影基准面上。此时，上部面和下部面的投影面积最大并且分别等于它们的真实面积。优选地，上部面F1的沿配重构件50的周向方向的投影面积与下部面F2的沿周向方向的投影面积之比值大于等于1.15，更优选地，上部面F1的沿配重构件50的周向方向的投影面积与下部面F2的沿周向方向的投影面积之比值大于等于1.3。这种构型目的在于进一步将配重部502的质量中心向上提升，并且适当减小搅油面5022中的通常处在润滑油中的下部面F2的面积，以减小搅油阻力，减小搅油功耗。上部面F1与下部面F2的分界可以如此限定，即，上部面F1与下部面F2对应于通常情况下的由主轴承座40限定的空间中所积聚的润滑油的油位。通常情况下的油位对于特定的涡旋压缩机而言一般是基本上确定的，而仅仅会根据该特定的涡旋压缩机的不同的实际运行工况(比如高转速/低转速运行)或一些意外状况(比如意外的缺油状况)而有些变化。
现在，重新参照图1所示的涡旋压缩机1的视图，可知，涡旋压缩机1中还设置有排油路径11以将积聚在主轴承座40的空间中的润滑油向外排出而返回至油池O，排油路径11的设置在主轴承座40的周壁处的开口大致对准配重部502的位置。因此，在设置有用于从主轴承座的空间(凹腔)排油的排油路径11的这种特定情况下，通常情况下的油位即与排油路径11的开口对齐。由此，根据本实施方式的上部面F1与下部面F2的分界线即与排油路径11的开口对齐。
如图3b最佳示出的，上部面F1与下部面F2的分界线D位于搅油面5022的台阶部T的稍微上方。然后，还可以想到的是，使得分界线D正好与台阶 部T重合，甚至可能在某些情况下更优的是，分界线D位于台阶部T的下方。具体地，通过适当地设置台阶部T在搅油面5022中所处的轴向位置，并且/或者通过适当地调整配重组件5安装在涡旋压缩机1中时所处的轴向位置，使得搅油面5022的台阶部T正好与排油路径11的开口大致对齐，从而使台阶部T以上的部分成为上部面F1而使台阶部T以下的部分成为下部面F2。以这种方式，可以使上部面F1的投影面积能够充分地大于下部面F2的投影面积。另外，如图3b最佳示出的，优选地，上部面F1在轴向方向上(即从分界线D至顶部端面5023)的大部分均具有较大的(径向)厚度，而下部面F2从基座(环状安装部501)至分界线D的大部分则具有较小的厚度。以此方式，确保了上部面F1的投影面积大于下部面F2的投影面积。
图4a和图4b示出根据本公开的涡旋压缩机的配重组件的第三实施方式，其中，图4a示出配重组件的立体图，图4b示出配重组件的侧视图。第三实施方式与图2a至图2c所示的第一实施方式具有大致相同的构型，并在此基础上做了进一步改进，其区别在于：基于第一实施方式的构型，在第三实施方式中，搅油面5022构造成使得：配重部502的上端部5024相对于配重部502的下端部5026朝向配重部502的周向方向(即配重部502的转动方向)的前侧突出，并且优选地，在本实施方式中，搅油面5022构造为相对于配重部502的下边缘5021(下边缘5021可以视为处在与驱动轴16的纵向轴线L垂直的平面上)呈钝角倾斜的平面，即，使得搅油面5022的各处与配重部502的下边缘5021所成的角度均大于90°，且更优选地均小于150°。这种构型能够向上提升配重部502的质量中心，从而避免配重部502的质量中心沿着纵向轴线L的方向向下移动而偏离衬套51的质量中心(例如图5a和图5b示出的现有技术的涡旋压缩机的配重组件的情况)，因此可以避免在衬套51中产生较大的偏转力矩，改善操作稳定性，并且这种斜面设计的搅油面5022也能够显著减小搅油阻力从而提高搅油效率并减小搅油功耗。
具体地，图5a和图5b示出现有技术的涡旋压缩机的配重组件P5的示例，其中，图5a示出配重组件P5的立体图，图5b示出配重组件P5的侧视图。如图所示，现有技术中的配重组件P5的搅油面P5022通常构造为相对于配重部P502的下边缘P5021呈锐角倾斜的平面，这与本公开的上述实施方式完全相悖，这种搅油面P5022的设计会使配重部P502的质量中心沿着纵向轴线L的 方向向下移动而偏离衬套P51的质量中心，导致在衬套P51中产生较大的偏转力矩而相对于设置在衬套P51与动涡旋24的毂部240之间的驱动轴承偏移。而本公开的上述构型则能够避免现有技术中的这种问题，同时能够确保高的搅油效率。
进一步，尽管在本公开的上述实施方式中，搅油面5022构造为平面形状，但是本公开不限于此，搅油面5022可以包括凸出的弧面、内凹的弧面、平面、台阶面(由倾斜角度不同的多个平面构成的表面)或其任意组合。只要能够确保配重部502的上端部5024相对于配重部502的下端部5026朝向配重部502的周向方向(即配重部502的转动方向)的前侧突出即可，由此可以避免配重部502的质量中心沿着纵向轴线L的方向向下移动而偏离衬套51的质量中心。
通过将上述构型的搅油面5022与上述构型的进油口、出油口和油路进行结合，能够在实现高效搅油和减小搅油功耗的同时，进一步有针对性地将润滑油输送至特定的位置——止推面422，从而使得配重组件5能够同时发挥搅油和输油的作用。
此外，尽管在上述实施方式中，配重构件50的基座构造为环状安装部501，该环状安装部501套置在衬套51的外部以与衬套51固定安装，但是，本公开不限于此，例如配重构件50的基座也可以与衬套51一体成型。
图6a至图6d示出根据本公开的涡旋压缩机1的配重组件5的第四实施方式，其中，图6a示出配重组件5的立体图，图6b示出配重组件5的侧视图，图6c示出配重组件5的正视图，图6d示出配重组件5安装至涡旋压缩机1的驱动轴16时的立体图。第四实施方式包括了根据本公开的前述各个实施方式的特征，是前述各实施方式的结合。如图所示，配重部502的一个侧面构造为搅油面5022，配重部502的上端部5024相对于配重部502的下端部5026朝向配重部502的周向方向(即配重部502的转动方向)的前侧突出，以使得搅油面5022构造为相对于配重部502的下边缘5021呈钝角倾斜的平面，并且，在配重部502的搅油面5022上设置有两个进油口5027，在配重部502的顶部端面5023上设置有两个出油口5028，并且在配重部502内部设置有分别从两个进油口5027延伸至两个出油口5028的两个单独的油路，以便为止推面422供送润滑油(参见图6d所示)，并且优选地，出油口5028与止推面422的距离小于等于6mm，优选地小于等于5.5mm，更优选地小于等于3mm。进一步， 参照图6c，搅油面5022的上部面F1的沿配重组件5的周向方向的投影面积与下部面F2的沿周向方向的投影面积之比值大于等于1.3。
通过将上述各个实施方式的结构特征进行结合，能够最优地实现配重组件5的实现动平衡、高效搅油和润滑油输送并且降低搅油功耗的有益技术效果，从而改善涡旋压缩机1的整体运行表现。
本领域普通技术人员应当理解的是，上述各个特征能够进行适当的变化和修改，并且其之间的结合方式可以是任意的，而不限于上述具体实施方式。
此外，根据本公开的另一方面，还提供了一种涡旋压缩机1，该涡旋压缩机1如图1所示地包括根据本公开的前述实施方式的涡旋压缩机的配重组件。
尽管在前述实施方式中描述了根据本公开的涡旋压缩机的配重组件以及涡旋压缩机的示例性实施方式，但是，本公开并不限于此，而是在不背离本公开的保护范围的情况下，可以进行各种改型、替换和组合。
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公开的优选实施方式的涡旋压缩机的配重组件以及涡旋压缩机。可以理解，以上描述仅为示例性的而非限制性的，在不背离本公开的范围的情况下，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公开的保护范围内。

Claims (13)

  1. 一种涡旋压缩机的配重组件，所述涡旋压缩机(1)包括适于对工作流体进行压缩的压缩机构(CM)以及适于驱动所述压缩机构的驱动轴(16)，所述压缩机构包括具有驱动联接部(240)的动涡旋(24)，所述驱动轴包括驱动部，所述驱动联接部与所述驱动部驱动地接合使得所述驱动轴能够驱动所述动涡旋，所述配重组件(5)包括：
    衬套(51)，所述衬套设置在所述驱动联接部与所述驱动部之间；以及
    配重构件(50)，所述配重构件包括安装至所述衬套或者与所述衬套一体地形成的基座以及从所述基座延伸的配重部(502)，在所述配重部随着所述驱动轴的旋转而旋转从而具有作为迎风面的搅油面(5022)，
    其特征在于，在所述搅油面上设置至少一个进油口(5027)，在所述配重部的顶部端面(5023)上设置至少一个出油口(5028)，在所述配重部内部设置从所述至少一个进油口延伸至所述至少一个出油口的至少一个油路(5029)。
  2. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述至少一个油路沿着所述配重组件的旋转轴线的方向延伸。
  3. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述至少一个油路相对于所述配重组件的旋转轴线倾斜成使得所述至少一个进油口(5027)在所述配重部的旋转方向上位于所述至少一个出油口(5028)的前侧。
  4. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述至少一个油路包括多个油路，所述多个油路彼此独立或者彼此连通。
  5. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述至少一个进油口定位成在所述配重组件的旋转轴线的方向上靠近所述基座。
  6. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述配重部的高度设置为使得：在所述配重组件的安装状态下，在所述配重组件的旋 转轴线的方向上，所述至少一个出油口与所述涡旋压缩机的主轴承座(40)的与所述动涡旋滑动接触的止推面(422)的距离小于等于5.5mm。
  7. 根据权利要求1所述的涡旋压缩机的配重组件，其特征在于，所述配重部的高度设置为使得：在所述配重组件的安装状态下，在所述配重组件的旋转轴线的方向上，所述至少一个出油口与所述涡旋压缩机的主轴承座(40)的与所述动涡旋滑动接触的止推面(422)的距离小于等于3mm。
  8. 根据权利要求2至7中任一项所述的涡旋压缩机的配重组件，其特征在于，所述配重部具有远离所述基座的上端部(5024)和邻近所述基座的下端部(5026)，所述上端部(5024)相对于所述下端部(5026)朝向所述配重部的旋转方向的前侧突出。
  9. 根据权利要求8所述的涡旋压缩机的配重组件，其特征在于，所述搅油面的各部分与所述配重部的下边缘(5021)所成的角度均大于90°。
  10. 根据权利要求8所述的涡旋压缩机的配重组件，其特征在于，所述搅油面包括凸出的弧面、内凹的弧面、平面、台阶面或其组合。
  11. 根据权利要求1至7中任一项所述的涡旋压缩机的配重组件，其特征在于，所述基座为环状安装部(501)，所述环状安装部套置在所述衬套的外部以与所述衬套固定安装。
  12. 一种涡旋压缩机，其特征在于，所述涡旋压缩机(1)包括根据权利要求1至11中任一项所述的配重组件。
  13. 根据权利要求12所述的涡旋压缩机，其特征在于，所述配重组件构造成使得：当所述配重组件安装在所述涡旋压缩机中时，所述至少一个出油口位于所述涡旋压缩机的主轴承座(40)的止推面(422)的径向内侧。
PCT/CN2020/118016 2020-04-07 2020-09-27 涡旋压缩机的配重组件及涡旋压缩机 WO2021203638A1 (zh)

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