WO2021082627A1 - 主轴承座组件以及具有该主轴承座组件的涡旋压缩机 - Google Patents

主轴承座组件以及具有该主轴承座组件的涡旋压缩机 Download PDF

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Publication number
WO2021082627A1
WO2021082627A1 PCT/CN2020/108769 CN2020108769W WO2021082627A1 WO 2021082627 A1 WO2021082627 A1 WO 2021082627A1 CN 2020108769 W CN2020108769 W CN 2020108769W WO 2021082627 A1 WO2021082627 A1 WO 2021082627A1
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WO
WIPO (PCT)
Prior art keywords
oil
thrust plate
main bearing
bearing housing
scroll
Prior art date
Application number
PCT/CN2020/108769
Other languages
English (en)
French (fr)
Inventor
张跃
钱源
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 CN201911052915.6A external-priority patent/CN112746964A/zh
Priority claimed from CN201921862906.9U external-priority patent/CN211144809U/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
Priority to US17/772,904 priority Critical patent/US11835046B2/en
Publication of WO2021082627A1 publication Critical patent/WO2021082627A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/801—Wear plates
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

Definitions

  • the present disclosure relates to a main bearing seat assembly used in a scroll compressor, and in particular, to a main bearing seat assembly with a shower-type oil distribution path.
  • the present disclosure also relates to a scroll compressor including the main bearing housing assembly.
  • Scroll compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems.
  • Scroll compressors usually include: a compression mechanism for compressing working fluid (such as refrigerant), the compression mechanism includes a movable scroll and a fixed scroll; a thrust plate located on one side of the end plate of the movable scroll, the thrust plate The thrust surface is kept in surface contact with the end surface of the end plate of the movable scroll to support the movable scroll so that the movable scroll maintains stable engagement with the fixed scroll; and a lubricating oil source storing and supplying to each moving part Lubricating oil for lubrication.
  • working fluid such as refrigerant
  • the movable scroll When the scroll compressor is in operation, the movable scroll performs an orbiting relative movement with respect to the fixed scroll, and the movable scroll also performs an orbiting relative movement with respect to the thrust plate. Therefore, there is a relative frictional movement between the end surface of the end plate of the movable scroll and the thrust surface of the thrust plate, which will produce abrasion of the end plate of the movable scroll and the thrust plate and a large amount of frictional heat, and thus increase the work. Consumption. In order to reduce wear and reduce power consumption, it is necessary to provide lubrication (such as supply of lubricating oil) between the end surface of the end plate of the orbiting scroll and the thrust surface of the thrust plate to reduce friction.
  • lubrication such as supply of lubricating oil
  • the purpose of the present disclosure is to provide a thrust plate that can promote lubrication between the thrust surface and the end surface of the movable scroll.
  • Another object of the present disclosure is to provide a scroll compressor capable of reducing the friction between the thrust surface and the end surface of the movable scroll.
  • a main bearing housing assembly for a scroll compressor comprising: a main bearing housing; and a thrust plate provided on the top of the main bearing housing, It also includes a thrust surface at the top that is in surface contact with the bottom end surface of the scroll assembly of the scroll compressor.
  • the thrust plate includes: at least one oil inlet hole; a closed oil cavity formed in the thrust plate; and at least one oil outlet hole, the orifice of the at least one oil outlet hole is exposed to the thrust surface .
  • at least one oil inlet hole is communicated with at least one oil outlet hole via the closed oil cavity.
  • the enclosed oil cavity is a single annular oil cavity formed along the circumferential direction of the thrust plate; or the enclosed oil cavity is a plurality of discrete oil cavities arranged along the circumferential direction of the thrust plate.
  • a groove connecting the orifices of the oil outlet holes is formed on the thrust surface.
  • it further includes a pressure relief valve arranged on the thrust plate for adjusting the pressure in the closed oil chamber.
  • oil inlet holes there are a plurality of oil inlet holes, and the oil inlet holes are arranged at equal intervals around the center axis of the thrust plate.
  • the number of oil outlet holes is more than the number of oil inlet holes, and the oil outlet holes are arranged at equal intervals around the central axis of the thrust plate.
  • the thrust plate is integrally formed on the main bearing housing; or the thrust plate is an independent member arranged on the top of the main bearing housing, wherein the thrust plate has a structure adapted to be closed from the bottom to form a closed oil cavity Oil tank.
  • the oil groove of the thrust plate is sealed by the top surface of the main bearing housing to form a closed oil cavity; or the main bearing housing assembly further includes a structure that is adapted to interact with the thrust plate A cover plate is tightly fitted at the bottom of the thrust plate. When the thrust plate and the cover plate are assembled together, the cover plate closes the oil groove of the thrust plate to form a closed oil cavity.
  • a scroll compressor comprising: a scroll assembly including a fixed scroll component and a movable scroll component for the purpose of opposing a working fluid Perform compression, and the main bearing housing assembly according to the previous aspect of the present disclosure.
  • the scroll compressor further includes a pumping mechanism that can provide lubricant to the moving parts of the scroll compressor including the scroll assembly, and the oil inlet hole of the thrust plate and the pumping mechanism Connected so that the pumping mechanism directly and actively provides lubricant to the thrust plate.
  • a pumping mechanism that can provide lubricant to the moving parts of the scroll compressor including the scroll assembly, and the oil inlet hole of the thrust plate and the pumping mechanism Connected so that the pumping mechanism directly and actively provides lubricant to the thrust plate.
  • the pumping mechanism is a positive displacement pump.
  • the thrust plate and the scroll compressor having the main bearing housing assembly according to the embodiment of the present disclosure, compared to the prior art, by additionally supplying oil to the thrust surface via the thrust plate, the thrust can be improved.
  • the lubrication between the surface and the end surface of the movable scroll component, especially the shower-type distribution path of the thrust plate, can directly and actively supply oil to the thrust surface through the pumping mechanism, which can be more evenly and efficiently stopped
  • the thrust surface provides additional lubrication and cooling.
  • the thrust plate and the scroll compressor according to the present disclosure have a simple structure, easy processing and manufacturing, and high cost-effectiveness.
  • Fig. 1 shows a longitudinal cross-sectional view of a scroll compressor according to the present disclosure.
  • FIG. 2 shows an enlarged partial longitudinal cross-sectional view of the scroll compressor in FIG. 1 including a compression mechanism, a thrust plate, and a main bearing housing, which shows the configuration of the thrust plate according to the first embodiment of the present disclosure .
  • FIG. 3 shows a longitudinal cross-sectional view of the thrust plate according to the first embodiment of the present disclosure.
  • Fig. 4 shows a longitudinal cross-sectional view of the thrust plate and the cover plate in an assembled state according to the first embodiment of the present disclosure.
  • Fig. 5 shows an exploded perspective view of the thrust plate and the cover plate according to the first embodiment of the present disclosure.
  • Fig. 6 shows a plan view of a thrust plate according to a second embodiment of the present disclosure.
  • Fig. 7 shows a longitudinal sectional view of a thrust plate according to a second embodiment of the present disclosure.
  • Fig. 8 shows a plan view of a thrust plate with a pressure relief valve according to the present disclosure.
  • the scroll compressor is exemplarily shown as a vertical scroll compressor.
  • the scroll compressor according to the present disclosure is not limited to this type, but may be any type of scroll compressor such as a horizontal scroll compressor.
  • Fig. 1 shows a longitudinal cross-sectional view of a scroll compressor according to the present disclosure.
  • Fig. 1 shows a longitudinal cross-sectional view of a scroll compressor according to the present disclosure.
  • the scroll compressor 1 may include a substantially cylindrical housing 10, an electric motor, a drive shaft 36, a main bearing housing 40, a fixed scroll (or called a fixed scroll member) 22, and a movable scroll. Swirl (or referred to as a movable scroll member) 24.
  • the movable scroll 24 and the fixed scroll 22 together constitute a compression mechanism 20 for compressing a working fluid (such as a refrigerant), wherein the fixed scroll 22 includes a fixed scroll end plate, a fixed scroll scroll and a center located at the fixed scroll 22
  • the orbiting scroll 24 includes the orbiting scroll end plate 244, the orbiting scroll scroll extending from the orbiting scroll end plate 244 facing the surface of the fixed scroll 22 and the orbiting scroll end plate 244
  • the hub 242 on the opposite side of the scroll scroll (hereinafter referred to as the "end surface") P extends, and the compression mechanism 20 defines an open suction chamber in fluid communication with the air inlet of the compression mechanism 20, and A closed compression chamber formed by joining the fixed scroll scroll and the movable scroll scroll for compressing the working fluid.
  • a top cover 12 may be installed at the top of the housing 10, and a base 14 may be installed at the bottom of the housing 10, so as to define the internal volume of the scroll compressor 1.
  • Lubricants such as lubricating oil can be stored in the oil pool 16 at the bottom for lubricating various moving parts of the scroll compressor 1, for example, including the movable scroll 24, the fixed scroll 22, and the thrust plate 50.
  • the oil pool 16 serves as a lubricant source.
  • the electric motor includes a stator 32 and a rotor 34.
  • the rotor 34 is used to drive the drive shaft 36 so that the drive shaft 36 rotates relative to the housing about its rotation axis.
  • the drive shaft 36 may include an eccentric pin 362 that is mounted to the first end (top end) of the drive shaft 36 or is formed integrally with the first end of the drive shaft 36.
  • the drive shaft 36 also includes a central hole 364 and an eccentric hole (not shown).
  • the central hole 364 is formed at the second end (bottom end) of the drive shaft 36.
  • the eccentric hole extends upward from the central hole 364 to the end of the eccentric pin 362 surface.
  • the end (lower end) of the center hole 364 can be immersed in the oil sump 16 at the bottom of the scroll compressor 1, so that, for example, the lubricating oil can be transported from the oil sump 16 at the bottom under the action of the centrifugal force generated by the rotation of the drive shaft 36 , And the lubricating oil flows upward through the center hole 364 and the eccentric hole and flows out from the end surface of the eccentric pin 362.
  • the lubricating oil flowing out from the end surface of the eccentric pin 362 may flow into, for example, a lubricating oil supply area formed between the eccentric pin 362 and the movable scroll 24 and between the main bearing housing 40 and the movable scroll 24.
  • the lubricating oil in the lubricating oil supply area can lubricate, for example, the rotating joints and sliding surfaces between the eccentric pin 362 and the movable scroll 24 and between the main bearing housing 40 and the movable scroll 24.
  • the lubricating oil in the lubricating oil supply area may also be supplied to the compression mechanism 20.
  • the movable scroll 24 is axially supported by the main bearing housing 40 and is supported by the main bearing housing 40 so as to be capable of orbiting.
  • the hub 242 of the movable scroll 24 may be rotatably coupled to the eccentric pin 362.
  • the hub 242 may be rotatably coupled to the eccentric pin 362 via a sleeve or bearing.
  • the lubricating oil supplied to the eccentric pin 362 and flowing out from the eccentric pin 362 through the above-mentioned exemplary eccentric oil supply scheme or the like can then enter the space in the hub 242.
  • the lubricating oil accumulates in the recess of the main bearing housing 40 after lubricating the hub 242, the eccentric pin 362, the bearing, or the like.
  • the lubricating oil in the recessed portion of the main bearing housing 40 adheres to the movable scroll end plate 244 and the main bearing in the form of oil mist.
  • the thrust surface above the seat 40 thus realizes lubrication between the movable scroll end plate 244 and the thrust surface T that provides axial support for the movable scroll 24.
  • the thrust surface T is provided by a separately provided thrust plate 50 arranged between the movable scroll end plate 244 and the main bearing housing 40.
  • Fig. 2 shows an enlarged partial longitudinal cross-sectional view of the scroll compressor according to the present disclosure.
  • the thrust plate 50, the movable scroll 24, and the main bearing housing 40 according to an aspect of the present disclosure are clearly shown, and for ease of description, components such as a housing and a motor are omitted.
  • the thrust plate 50 is a disc-shaped member and has a central through hole 502 at the center through which the hub 242 of the orbiting scroll 24 passes.
  • the upper surface of the thrust plate 50 surrounding the central through hole 502 is the thrust surface T makes surface contact with the end surface P of the movable scroll 24.
  • the thrust plate 50 has an oil supply passage communicating from the side to the thrust surface T inside.
  • Fig. 3 shows a longitudinal sectional view of a thrust plate according to the present disclosure.
  • the thrust plate 50 includes an oil inlet 50a, an oil groove 504, and an oil outlet 50b.
  • the oil groove 504 is formed on the side opposite to the thrust surface T, and the oil inlet 50a passes through the thrust plate 50.
  • the outer side wall of the oil groove 504 is connected to the oil groove 504, and the oil outlet hole 50b passes through the top wall of the thrust plate 50 from the top of the oil groove 504 to the thrust surface T.
  • the thrust plate 50 is installed between the movable scroll 24 and the main bearing housing 40 and the opening of the oil groove 504 is closed by the surface of the element closely fitting with the bottom of the thrust plate 50
  • a closed oil chamber C is formed, and the oil inlet 50a is connected to the pumping mechanism 18 in the oil sump 16 at the bottom of the compressor via the oil pipe L, so that the pumping mechanism 18 directly and actively supplies oil.
  • the pumping mechanism 18 and the oil pipe L can continuously provide lubricating oil to the oil inlet hole 50a of the thrust plate 50 during the operation of the compressor, and the lubricating oil entering the thrust plate 50 can accumulate in the sealed oil chamber.
  • the lubricating oil can further flow upward to the thrust surface T, thereby providing the orbiting scroll end surface P and the thrust surface T of the thrust plate 50 Effective lubrication.
  • the lubricating oil that enters the oil cavity C through the oil inlet 50a flows out through the oil outlet 50b, and reciprocates in this way, the lubricating oil in the oil cavity C is always in a stable flow state, which can provide stable lubrication.
  • the fast lubricating oil flow speed and the higher oil flow rate can more efficiently take away the heat generated by the friction between the orbiting scroll end plate 244 and the thrust plate 50, thereby forming the orbiting scroll 24 And thrust plate 50 bring additional cooling effect.
  • the thrust plate there is at least one oil outlet hole in the thrust plate, and preferably, the number of oil outlet holes 50b is greater than the number of oil inlet holes, more preferably, the number of oil outlet holes
  • the number of oil inlet holes is doubled (here, "doubled” means doubled or more, for example, 3, 4, 5... etc.), so that a "shower type" is formed in the thrust plate Fuel supply path.
  • the thrust plate may include at least one oil inlet hole, or as shown in FIGS. 3 and 4 of the present disclosure, two oil inlet holes radially symmetrical about the center axis of the thrust plate may be provided, and include Six oil outlet holes are arranged at equal intervals on the central axis.
  • the number of oil outlet holes in the thrust plate more than especially double the number of oil inlet holes (for example, each oil inlet hole corresponds to or communicates with 3 oil outlet holes), it is possible to provide only a small amount of oil inlet holes.
  • the lubricating oil can reach all parts of the thrust surface more evenly after overflowing the oil outlet holes without uneven oil film distribution or local hysteresis.
  • the lubricating oil can be used more efficiently, uniformly and fully to provide lubrication and cooling for the contact surface between the orbiting scroll end plate and the thrust plate.
  • FIGS. 4 and 5 it also includes a bottom flange 508 at the bottom of the thrust plate 50 adapted to tightly fit with the bottom flange 508 of the thrust plate 50 (including but not limited to interference fit ), and a gasket 62 for enhancing the sealing effect is also provided between the cover plate and the thrust plate 50.
  • the upper surface of the gasket 62 abuts against the opening of the oil groove 504 and closes the opening of the oil groove 504 so that the oil groove 504 becomes a sealed oil chamber C.
  • the thrust plate 50, the washer 62 and the cover plate 60 are arranged in order from top to bottom and are fixed together with fasteners F such as screws.
  • the thrust plate 50, the washer 62 and the cover plate 60 may be installed as a whole above the main bearing housing 40 to support the orbiting scroll end plate 244.
  • the number of oil inlet holes and oil outlet holes forming the "shower type" oil supply path of the thrust plate is not fixed, and the number of oil inlet holes and oil outlet holes can be changed according to actual conditions.
  • the number and location of the oil outlet holes can be determined according to specific requirements, such as failure conditions, wear locations, and locations for deliberately enhanced lubrication or cooling.
  • the oil outlet hole can be provided at the radially outer side of the thrust surface T (for example, as shown in FIG.
  • the oil outlet can be set in the thrust surface
  • the surface T is close to the radial inner side; if necessary, the oil outlet hole can also be provided at the radial inner side and the radial outer side of the thrust surface T at the same time.
  • the oil outlet hole is arranged to be inclined radially outward from the top of the oil cavity C to the thrust surface T, the orientation of the oil outlet hole may be optional according to needs, for example, it may also be vertically upward. , Inclined radially inward or inclined along the circumferential direction.
  • the thrust plate 50 is shown as including an oil groove 504.
  • the oil groove 504 By providing the oil groove 504, the flow rate or circulation efficiency of lubricating oil in the thrust plate 50 can be increased, thereby helping to strengthen the thrust surface. Lubrication and cooling effects of T and the end face P of the movable scroll.
  • the form of the oil groove 504 is not fixed.
  • the oil groove 504 may be an annular groove extending along the entire circumference of the thrust plate 50. The advantage of this structure lies in the fluidity of the lubricating oil in the thrust plate 50.
  • the oil groove 504 may be a plurality of discrete grooves arranged along the entire circumference of the thrust plate 50, wherein each groove is connected to at least one oil inlet 50a and The multiple oil outlet holes 50b are in communication.
  • the advantage of this configuration is that it can improve the lubrication and cooling effects of the thrust surface T and the orbiting scroll end surface P while better ensuring the rigidity of the thrust plate 50.
  • the longitudinal cross-sectional shape of the oil groove 504 is also optional, and does not need to be rectangular as shown in FIG. 3, and it may also be any optional shape such as a semicircle or a trapezoid.
  • each oil inlet 50a can also be directly Connecting a plurality of oil outlet holes 50b to form a "shower type" oil supply path, which can also obtain a more uniform and efficient lubrication and lubrication between the thrust surface T and the orbiting scroll end surface P compared to the prior art. cool down.
  • FIGS. 6 and 7 show an improved form of the thrust plate 150 according to the present disclosure (ie , The thrust plate 150 according to the second embodiment of the present disclosure).
  • an annular groove 150c extending in the circumferential direction of the thrust surface T is provided on the thrust surface T, and the annular groove 150c connects the orifices of the oil outlet holes 150b in series .
  • the lubricating oil that flows out onto the thrust surface T through the shower-type distribution path of the thrust plate 150 can be stored and circulated in the groove 150c.
  • the groove 150c has a smaller depth.
  • the groove 150c may also have other shapes that can connect all the orifices in series, or may According to the position of the orifice, it is arranged in two or more concentric circles.
  • the sealing gasket between the thrust plate and the cover plate does not necessarily exist, and the top surface of the cover plate can be used to seal the oil groove opening of the thrust plate to form a closed oil chamber.
  • the cover plate may not be provided, but the thrust plate is directly installed on the top of the main bearing housing, and the bottom of the thrust plate is closely matched with the top of the main bearing housing (for example, interference fit) The oil groove opening of the thrust plate is sealed to form a closed oil cavity.
  • the thrust plate can be integrally formed on the main bearing housing, that is, the oil cavity is a cavity directly formed in the main bearing housing, which will have a better sealing effect.
  • the pumping mechanism is a positive displacement oil pump with a pressure relief function.
  • a pressure relief valve V communicating with the oil chamber can be arranged on the side wall of the thrust plate (as shown in Figure 8). Show). In this way, when the pressure in the oil cavity of the thrust plate reaches a certain height, part of the lubricating oil can be discharged through the positive displacement oil pump and/or the pressure relief valve V to avoid failures such as oil pipe rupture and oil pump damage.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

一种用于涡旋压缩机（1）的主轴承座组件及具有主轴承座组件的涡旋压缩机（1），主轴承座组件包括：主轴承座（40）；以及止推板（50；150），止推板（50；150）设置在主轴承座（40）顶部，并且包括位于顶部的与涡旋压缩机（1）的涡旋组件的底部端面形成面接触的止推面（T），止推板（50；150）包括：至少一个进油孔（50a）；封闭油腔（C），封闭油腔（C）形成在止推板（50；150）中；以及至少一个出油孔（50b；150b），至少一个出油孔（50b；150b）的孔口暴露于止推面（T）；至少一个进油孔（50a）与至少一个出油孔（50b；150b）经由封闭油腔（C）连通。

Description

主轴承座组件以及具有该主轴承座组件的涡旋压缩机
本公开要求于2019年10月31日提交中国国家知识产权局、申请号为201911052915.6、名称为“主轴承座组件以及具有该主轴承座组件的涡旋压缩机”的中国专利申请的优先权以及要求于2019年10月31日提交中国国家知识产权局、申请号为201921862906.9、名称为“主轴承座组件以及具有该主轴承座组件的涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本公开中。
技术领域
本公开涉及一种用于涡旋压缩机中的主轴承座组件，具体地，涉及一种具有花洒式油分配路径的主轴承座组件。另外，本公开还涉及包括该主轴承座组件的涡旋压缩机。
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。涡旋压缩机通常包括：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；位于动涡旋的端板一侧的止推板，该止推板的止推面与动涡旋的端板的端面保持面接触从而支撑动涡旋以使动涡旋保持与定涡旋的稳定接合；以及润滑油源，该润滑油源储存供应至各个运动部件进行润滑的润滑油。涡旋压缩机在运转时，动涡旋相对于定涡旋进行绕动式相对运动，并且，动涡旋也相对于止推板进行绕动式相对运动。因此动涡旋的端板的端面与止推板的止推面之间存在相对摩擦运动，由此会产生动涡旋端板和止推板的磨损以及大量的摩擦热，并因此增大功耗。为了减轻磨损并降低功耗，需要向动涡旋的端板的端面与止推板的止推面之间提供润滑(例如供给润滑油)以减轻摩擦。
但是，在实际应用过程中发现，特别是在高负载条件下，根据现有技术的涡旋压缩机往往存在动涡旋与止推板之间磨损严重并导致润滑油发黑的问题。
因此，存在改善动涡旋的端面与止推板的止推面之间的润滑的需要。
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。
本公开的目的在于提供一种能够促进止推面与动涡旋的端面之间的润滑的止推板。
本公开的另一目的在于提供一种能够减轻止推面与动涡旋的端面之间的摩擦的涡旋压缩机。
根据本公开的一方面，提供了一种用于涡旋压缩机的主轴承座组件，该主轴承座组件包括：主轴承座；以及止推板，该止推板设置在主轴承座顶部，并且包括位于顶部的与涡旋压缩机的涡旋组件的底部端面形成面接触的止推面。其中，止推板包括：至少一个进油孔；封闭油腔，该封闭油腔形成在止推板中；以及至少一个出油孔，所述至少一个出油孔的孔口暴露于止推面。其中，至少一个进油孔与至少一个出油孔经由所述封闭油腔连通。
可选地，封闭油腔为沿着止推板的周向方向形成的单个环形油腔；或者封闭油腔为沿着止推板的周向方向布置的多个离散油腔。
优选地，出油孔为多个，在止推面上形成有将出油孔的孔口连通的沟槽。
优选地，还包括设置在止推板上用于调节封闭油腔中的压力的泄压阀。
优选地，进油孔为多个，并且进油孔围绕止推板的中心轴线等间距布置。
优选地，出油孔的数目多于进油孔的数目，并且出油孔围绕止推板的中心轴线等间距布置。
可选地，止推板一体地形成在主轴承座上；或者止推板为设置在主轴承座的顶部的独立构件，其中，止推板具有适于从底部被封闭而形成封闭油腔的油槽。
可选地，在止推板为独立构件的情况下，止推板的油槽被主轴承座的顶表面密封而形成封闭油腔；或者，主轴承座组件还包括构造成适于与止推板的底部紧密配合的盖板，在止推板与盖板组装在一起的状态下，盖板封闭止推板的油槽从而形成封闭油腔。
根据本公开的另一方面，还提供了一种涡旋压缩机，该涡旋压缩机包括：涡旋组件，该涡旋组件包括定涡旋部件和动涡旋部件，以用于对工作流体进行压缩，以及根据本公开的前一方面所述的主轴承座组件。
优选地，涡旋压缩机还包括泵送机构，该泵送机构能够向涡旋压缩机的包括涡旋组件在内的运动部分提供润滑剂，并且，止推板的进油孔与泵送机构连通，从而由泵送机构直接且主动地为止推板提供润滑剂。
优选地，泵送机构为容积泵。
利用根据本公开的实施方式的主轴承座组件和具有该主轴承座组件的涡旋压缩机，相对于现有技术而言，通过经由止推板向止推面额外供油，能够改善止推面与动涡旋部件的端面之间的润滑，特别是止推板的花洒式分配路径能够经由泵送机构向止推面直接且主动地供油，能够更均匀、更有效率地向止推面提供额外的润滑和冷却，此外，根据本公开的止推板和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示出了根据本公开的涡旋压缩机的纵向截面图。
图2示出了图1中的涡旋压缩机的包括压缩机构、止推板和主轴承座的局部纵向截面放大图，其中示出了根据本公开的第一实施方式的止推板的构造。
图3示出了根据本公开的第一实施方式的止推板的纵向截面图。
图4示出了根据本公开的第一实施方式的止推板与盖板在组装状态下的纵向截面图。
图5示出了根据本公开的第一实施方式的止推板与盖板的分解立体图。
图6示出了根据本公开的第二实施方式的止推板的平面图。
图7示出了根据本公开的第二实施方式的止推板的纵向截面图。
图8示出了根据本公开的带有泄压阀的止推板的平面图。
具体实施方式
现在将结合附图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。
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。然而根据本公开的涡旋压缩机并不限于此类型，而可以是诸如卧式涡旋压缩机的任何类型的涡旋压缩机。
图1示出了根据本公开的涡旋压缩机的纵向截面图。首先，参照图1概 要地描述根据本公开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10、电动马达、驱动轴36、主轴承座40、定涡旋(或称为定涡旋部件)22和动涡旋(或称为动涡旋部件)24。动涡旋24和定涡旋22共同构成用于压缩工作流体(例如制冷剂)的压缩机构20，其中，定涡旋22包括定涡旋端板、定涡旋涡卷和位于定涡旋22中心处的排气口；动涡旋24包括动涡旋端板244、从动涡旋端板244的面向定涡旋22的表面延伸的动涡旋涡卷和从动涡旋端板244的与动涡旋涡卷相反一侧的表面(在下文中，简称为“端面”)P延伸的毂部242，在压缩机构20内限定有与压缩机构20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。
在壳体10的顶部处可以安装有顶盖12，并且在壳体10的底部安装有底座14，从而限定涡旋压缩机1的内部容积。例如润滑油的润滑剂可以储存在底部的油池16中以用于润滑涡旋压缩机1的各种运动部件，例如包括动涡旋24、定涡旋22和止推板50等。在此，油池16用作润滑剂源。
电动马达包括定子32和转子34。转子34用于对驱动轴36进行驱动以使驱动轴36绕其旋转轴线相对于外壳旋转。驱动轴36可以包括偏心销362，偏心销362安装至驱动轴36的第一端(顶端)或者与驱动轴36的第一端一体地形成。驱动轴36还包括中心孔364和偏心孔(未示出)，中心孔364形成在驱动轴36的第二端(底端)处，偏心孔从中心孔364向上延伸至偏心销362的端部表面。中心孔364的端部(下端)可以浸入在涡旋压缩机1底部的油池16中，从而例如在因驱动轴36的旋转而产生的离心力的作用下能够从底部的油池16输送润滑油，并且使润滑油向上流动经过中心孔364和偏心孔并且从偏心销362的端部表面流出。
从偏心销362的端部表面流出的润滑油可以流动至例如形成在偏心销362与动涡旋24之间以及主轴承座40与动涡旋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362与动涡旋24之间以及主轴承座40与动涡旋24之间的旋转接合部和滑动表面进行润滑。而且，如将在下文进一步描述地，润滑油供应区域中的润滑油还可以被供给至压缩机构20。
动涡旋24由主轴承座40轴向地支撑并且被主轴承座40支撑成能够进行绕动。动涡旋24的毂部242可以可旋转地联接至偏心销362。替代性地，毂部242可以经由套管或轴承可旋转地联接至偏心销362。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362并从偏心销362流出的润滑油进而能够进入毂部242内的空间。润滑油在对毂部242、偏心销362或轴承等润滑之后积聚在主轴承座40的凹部中。在诸如动涡旋24的毂部242和/或平衡块(未示出)的旋转搅动下，主轴承座40的凹部中的润滑油以油雾形式附着在动涡旋端板244和主轴承座40上方的止推面上，由此实现动涡旋端板244与对动涡旋24提供轴向支撑的止推面T之间的润滑。
特别地，在根据本公开的实施方式中，如图1所示，止推面T由单独设置的布置在动涡旋端板244与主轴承座40之间的止推板50提供。如图2示出了根据本公开的涡旋压缩机的局部纵向截面放大图。其中清楚示出了根据本公开的一方面的止推板50、动涡旋24以及主轴承座40，并且为了便于描述，省略了壳体、马达等部件。总体上，止推板50为盘状部件并且于中心处具有供动涡旋24的毂部242穿过的中心通孔502，止推板50的围绕中心通孔502的上表面即止推面T与动涡旋24的端面P进行面接触。
结合图1和图2可见，根据本公开的止推板50内部具有从侧面连通至止推面T的供油通路。图3示出了根据本公开的止推板的纵向剖视图。如图3所示，在止推板50包括进油孔50a、油槽504和出油孔50b，其中油槽504形成在与止推面T相反的一侧，进油孔50a穿过止推板50的外侧壁连通至油槽504，并且出油孔50b从油槽504的顶部穿过止推板50的顶壁连通至止推面T。在使用中，如图1和图2所示，止推板50安装在动涡旋24与主轴承座40之间并且油槽504的开口被与止推板50的底部紧密配合的元件的表面封闭从而形成密闭的油腔C，进油孔50a经由油管L连通至压缩机底部油池16中的泵送机构18从而由泵送机构18直接且主动地供油。这样一来，通过泵送机构18和油管L可以在压缩机工作的过程中源源不断地为止推板50的进油孔50a提供润滑油，进入止推板50的润滑油可以积聚在密闭油腔C中，并且由于进油孔50a与出油孔50b之间的压力差，润滑油可以进一步向上流至止推面T，从而为动涡旋端面P和止推板50的止推面T提供有效的润滑。此外，由于经进油孔50a进入油腔C中的润滑油经由出油孔50b流出，如此循环往复，因此油腔C中的润滑油始终处于稳定的流动状态，由此可以在提供稳定的润滑的同时，通过快速的润滑油流动速度以及较高的油流量可以更有效率地带走因动涡旋端板244与止推板50之间的摩擦而产生的热量，由此为动涡旋24和止推板50带来额外的冷却效果。
特别地，作为根据本公开的优选实施方式，止推板中具有至少一个出油 孔，并且优选地，出油孔50b的数量多于进油孔的数量，更优选地，出油孔的数量成倍于进油孔的数量(此处，“成倍”意指成2倍以上，例如，成3、4、5…..倍等)，使得在止推板中形成“花洒式”供油路径。例如，止推板可以包括至少一个进油孔，或者如本公开图3和图4所示，可以设置关于止推板的中心轴线径向对称的两个进油孔，并且包括围绕止推板的中心轴线等间距布置的六个出油孔。通过使止推板中的出油孔的数量多于特别是成倍于进油孔的数量(例如每个进油孔对应于或连通于3个出油孔)，可以在仅设置少量进油孔的情况下，通过设置多个均匀分布的出油孔，使得润滑油溢出出油孔后能够更均匀地到达止推面的各个部分，而不会出现油膜分布不均匀或局部滞后的现象，并且能够更高效、更均匀、更充分地利用润滑油来为动涡旋端板和止推板之间的接触面提供润滑和冷却。
在根据本公开的实施方式中，如图4和图5所示，还包括位于止推板50底部的适配成与止推板50的底部凸缘508紧密配合(包括但不限于过盈配合)的盖板60，并且在盖板与止推板50之间还设置有用于加强密封效果的垫圈62。垫圈62的上表面抵接油槽504的开口并将油槽504的开口封闭，从而使油槽504成为密闭的油腔C。止推板50、垫圈62和盖板60由上至下依序排列并且利用诸如螺钉等紧固件F固定在一起。在涡旋压缩机中，止推板50、垫圈62和盖板60可以作为一个整体安装在主轴承座40上方来支撑动涡旋端板244。
然而，本领域技术人员可以理解的是，以上实施方式仅是示例。在实践中，可以对其作各种适应性变形。
在此，形成止推板的“花洒式”供油路径的进油孔和出油孔的数量不是固定的，可以根据实际情况改变进油孔和出油孔的数量。特别地，出油孔的数量和位置可以根据具体需求——比如失效工况、磨损位置以及用于有意加强润滑或冷却的位置——来确定。例如，在止推面T的靠近径向外侧处的磨损较为严重的情况下，可以将出油孔设置在止推面T的靠近径向外侧处(例如在图3中示例性示出的)，以加强对止推面T的靠近径向外侧的表面的润滑和冷却；同理，在止推面T的靠近径向内侧处的摩擦较为严重的情况下，出油孔可以设置在止推面T的靠近径向内侧处；如果需要，还可以将出油孔同时设置在止推面T的靠近径向内侧和靠近径向外侧处。此外，尽管出油孔在此被设置成从油腔C顶部径向向外倾斜通向止推面T，然而出油孔的取向可以是根据需要任选的，例如其也可以是竖直向上的、径向向内倾斜或是沿周向方向倾斜等。
在上述实施方式中，止推板50被示出为包括油槽504，通过设置该油槽 504，可以增大润滑油在止推板50中的流量或循环效率，从而有助于增强对止推面T和动涡旋端面P的润滑和冷却效果。在此，油槽504的形式不是固定的，例如，油槽504可以是沿止推板50的整个周向延伸的一个环形凹槽，这种构造的优点在于润滑油在止推板50中的流动性强，使得润滑和冷却效果好；或者可选地，油槽504可以是沿止推板50的整个周向布置的多个离散的凹槽，其中每个凹槽均与至少一个进油孔50a以及多个出油孔50b连通，这种构造的优点在于可以在改善对止推面T和动涡旋端面P的润滑和冷却效果的同时更好地保证止推板50的刚度。另外，油槽504的纵向截面形状也是可选的，而无需如图3中所示的那样为矩形，其也可以是例如半圆形、梯形等任何可选的形状。
尽管在本公开的止推板的实施方式中包括油槽504，但本领域技术人员可以理解的是，油槽是优选的但并非必要的，例如可以设想到的，每个进油孔50a也可以直接连通多个出油孔50b从而形成“花洒式”供油路径，这同样能够获得在止推面T与动涡旋端面P之间的相对于现有技术而言更加均匀、高效的润滑和冷却。
区别于如图2至图5(特别是图5)所示的不具有环形沟槽的第一实施方式，图6和图7示出了具有改进形式的根据本公开的止推板150(即，根据本公开第二实施方式的止推板150)。如图6和图7中所示，在止推面T上设置有沿止推面T的周向延伸的环形沟槽150c，并且该环形沟槽150c将各出油孔150b的孔口串联起来。这样经由止推板150的花洒式分配路径流出到止推面T上的润滑油能够在该沟槽150c中存储并循环流动。通过以这种方式促进润滑油在止推面T上的流动，能够进一步加强止推面T与动涡旋端面P之间的润滑、更大程度地带走摩擦热。优选地，该沟槽150c具有较小的深度。另外，可以设想到，当在止推板150上的出油孔150b的孔口以不同的径向位置排列时，该沟槽150c也可以是能够将所有孔口串联起来的其他形状，或者可以根据孔口位置而设置为两个或更多个同心圆环形。
尽管未示出，止推板与盖板之间的密封垫圈并非必须存在的，可以利用盖板顶面将止推板的油槽开口密封形成密闭的油腔。进一步地，作为一种替代方案，可以不设置盖板，而是将止推板直接安装在主轴承座的顶部，并且通过止推板底部与主轴承座顶部的紧密配合(例如过盈配合)而将止推板的油槽开口密封形成密闭的油腔。作为又一种替代方案，止推板可以一体地形成在主轴承座上，即油腔为直接形成在主轴承座中的腔体，这样将会具有更好的密封效 果。
根据本公开的优选实施方式，泵送机构为具有泄压功能的容积式油泵，替代性地或附加地，可以在止推板的侧壁布置连通油腔的泄压阀V(如图8所示)。这样，当止推板的油腔内压力达到一定高度时，可以通过该容积式油泵和/或泄压阀V来泄放掉部分润滑油，以避免油管破裂、油泵损坏等故障。
然而，本领域技术人员应当理解的是，通过压缩机底部油池中的泵送机构为止推板的进油口直接、主动地供送润滑油仅是一种示例形式。也可以采用任何其他可行的方式为止推板的进油口提供润滑油。
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。这些变型和修改同样包含在本公开的保护范围内。

Claims (12)

  1. 一种用于涡旋压缩机的主轴承座组件，所述主轴承座组件包括：
    主轴承座(40)，以及
    止推板(50；150)，所述止推板(50；150)设置在所述主轴承座(40)顶部，并且包括位于顶部的与所述涡旋压缩机的涡旋组件的底部端面形成面接触的止推面(T)，
    其特征在于，
    所述止推板(50；150)包括：
    至少一个进油孔(50a)；
    封闭油腔(C)，所述封闭油腔(C)形成在所述止推板中；以及
    至少一个出油孔(50b；150b)，所述至少一个出油孔(50b；150b)的孔口暴露于所述止推面(T)，
    所述至少一个进油孔(50a)与所述至少一个出油孔(50b；150b)经由所述封闭油腔(C)连通。
  2. 根据权利要求1所述的主轴承座组件，其中：
    所述封闭油腔(C)为沿着所述止推板(50；150)的周向方向形成的单个环形油腔；或者
    所述封闭油腔(C)为沿着所述止推板(50；150)的周向方向布置的多个离散油腔。
  3. 根据权利要求1所述的主轴承座组件，其中，所述出油孔为多个，在所述止推面(T)上形成有将所述出油孔(50b；150b)的孔口连通的沟槽(150c)。
  4. 根据权利要求1所述的主轴承座组件，其中，还包括设置在所述止推板上用于调节所述封闭油腔(C)中的压力的泄压阀(V)。
  5. 根据权利要求1所述的主轴承座组件，其中，所述进油孔(50a)为多个，并且所述进油孔(50a)围绕所述止推板的中心轴线等间距布置。
  6. 根据权利要求1所述的主轴承座组件，其中，所述出油孔(50b；150b)的数目多于所述进油孔的数目，并且所述出油孔围绕所述止推板(50；150)的中心轴线等间距布置。
  7. 根据权利要求1至6中任一项所述的主轴承座组件，其中：
    所述止推板(50；150)一体地形成在所述主轴承座(40)上，或者
    所述止推板(50；150)为设置在所述主轴承座(40)的顶部的独立构件，其中，所述止推板(50；150)具有适于从底部被封闭而形成所述封闭油腔(C)的油槽(504)。
  8. 根据权利要求7所述的主轴承座组件，其中，在所述止推板(50；150)为独立构件的情况下，所述止推板的所述油槽(504)被所述主轴承座(40)的顶表面密封而形成所述封闭油腔(C)。
  9. 根据权利要求7所述的主轴承座组件，其中，在所述止推板(50；150)为独立构件的情况下，所述主轴承座组件还包括构造成适于与所述止推板(50；150)的底部紧密配合的盖板(60)，在所述止推板(50；150)与所述盖板(60)组装在一起的状态下，所述盖板(60)封闭所述止推板(50；150)的油槽(504)从而形成所述封闭油腔(C)。
  10. 一种涡旋压缩机，所述涡旋压缩机包括：
    涡旋组件(20)，所述涡旋组件(20)包括定涡旋部件(22)和动涡旋部件(24)，以用于对工作流体进行压缩，以及
    如权利要求1至9中任一项所述的主轴承座组件。
  11. 根据权利要求10所述的涡旋压缩机，其中，所述涡旋压缩机还包括泵送机构(18)，所述泵送机构(18)能够向所述涡旋压缩机(1)的包括所述涡旋组件(20)在内的运动部分提供润滑剂，并且，所述止推板(50；150)的进油孔与所述泵送机构(18)连通，从而由所述泵送机构(18)直接且主动地为所述止推板(50；150)提供润滑剂。
  12. 根据权利要求11所述的涡旋压缩机(1)，其中，所述泵送机构(18)为容积泵。
PCT/CN2020/108769 2019-10-31 2020-08-13 主轴承座组件以及具有该主轴承座组件的涡旋压缩机 WO2021082627A1 (zh)

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