WO2017012098A1 - 活塞式压缩机以及具有其的制冷系统 - Google Patents

活塞式压缩机以及具有其的制冷系统 Download PDF

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Publication number
WO2017012098A1
WO2017012098A1 PCT/CN2015/084825 CN2015084825W WO2017012098A1 WO 2017012098 A1 WO2017012098 A1 WO 2017012098A1 CN 2015084825 W CN2015084825 W CN 2015084825W WO 2017012098 A1 WO2017012098 A1 WO 2017012098A1
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WIPO (PCT)
Prior art keywords
crankshaft
thrust bearing
piston type
type compressor
compressor according
Prior art date
Application number
PCT/CN2015/084825
Other languages
English (en)
French (fr)
Inventor
严志奇
黄刚
Original Assignee
安徽美芝制冷设备有限公司
美的集团股份有限公司
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 CN201510427823.7A external-priority patent/CN105089982B/zh
Priority claimed from CN201520527820.6U external-priority patent/CN204783552U/zh
Application filed by 安徽美芝制冷设备有限公司, 美的集团股份有限公司 filed Critical 安徽美芝制冷设备有限公司
Priority to US15/503,538 priority Critical patent/US10309384B2/en
Priority to DE112015006715.9T priority patent/DE112015006715T5/de
Publication of WO2017012098A1 publication Critical patent/WO2017012098A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • F16C19/12—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly for supporting the end face of a shaft or other member, e.g. footstep bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/08—Crankshafts made in one piece
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons

Definitions

  • the present invention relates to the field of compressors, and more particularly to a piston type compressor and a refrigeration system having the same.
  • the high-efficiency compressor generally adopts a rolling thrust bearing, and the lubrication of the ball of the thrust bearing is mainly by the non-continuous lubrication of the splash.
  • the splash non-continuous lubrication cannot fully lubricate the ball, and the heat generated by the friction between the ball and the upper and lower support pieces cannot be completely completed.
  • the friction coefficient between the balls and the upper and lower support pieces becomes large, and the power consumption of the compressor becomes large.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • the present invention proposes a piston type compressor in which the lubricating oil can continuously lubricate the thrust bearing, so that the performance of the piston type compressor can be made good.
  • the invention further proposes a refrigeration system.
  • a piston type compressor includes: a crankcase having a crank hole provided therein, and an upper end of the crankcase is provided with a mounting boss, the crank hole extending upward through the mounting boss; a bearing, the thrust bearing sleeve is disposed outside the mounting protrusion; a crankshaft, the crankshaft is rotatably disposed in the crankshaft hole, and the crankshaft is provided with a thrust portion, the lower portion of the thrust portion An end surface is abutted on an upper end surface of the thrust bearing, and an oil passage is formed in the crankshaft, wherein a cavity is formed between the mounting protrusion, the thrust bearing and the thrust portion, A through hole for communicating the oil passage and the cavity is formed in a peripheral wall of the crankshaft.
  • the oil passage in the crankshaft can continuously supply oil to the thrust bearing
  • the lubricating oil can continuously lubricate the balls, reduce the friction work of the balls and the upper support piece, and the balls and the lower support piece.
  • the frictional work can improve the performance of the piston compressor
  • the lubricating oil can continuously take away the heat of the ball, further reduce the heat transferred by the ball to the cage, and improve the service life of the thrust bearing, thereby improving the piston.
  • the service life of the compressor can continuously supply oil to the thrust bearing
  • the lubricating oil can continuously lubricate the balls, reduce the friction work of the balls and the upper support piece, and the balls and the lower support piece.
  • the frictional work can improve the performance of the piston compressor
  • the lubricating oil can continuously take away the heat of the ball, further reduce the heat transferred by the ball to the cage, and improve the service life of the thrust bearing, thereby improving the piston.
  • the service life of the compressor can continuously supply oil to the thrust bearing, the lubricating oil
  • piston type compressor according to the present invention may have the following additional technical features:
  • the upper end surface of the mounting boss is higher than the upper end surface of the thrust bearing in the axial direction of the crankshaft.
  • the lower surface of the thrust portion is formed with an upwardly concave groove that is disposed over the mounting projection to form at least a portion of the cavity.
  • the top wall of the groove is higher than the upper end surface of the mounting boss in the axial direction of the crankshaft.
  • the horizontal projection of the groove is annular and the center of the ring coincides with the axis of the crankshaft bore.
  • the longitudinal projection of the groove is tapered and the tapered opening faces the thrust bearing.
  • the mounting boss and the thrust bearing are in a clearance fit.
  • the oil passage includes a sloped section that is disposed obliquely within the crankshaft from the crankshaft axis toward the outer circumferential wall of the crankshaft, the through hole communicating with the inclined section.
  • the angled segments are helically disposed.
  • a refrigeration system according to the present invention includes the above-described piston type compressor.
  • the piston type compressor of the refrigeration system having the above-described piston type compressor has good performance and long service life.
  • FIG. 1 is a cross-sectional view of a piston type compressor in accordance with an embodiment of the present invention
  • Figure 2 is a partial cross-sectional view of a piston type compressor in accordance with an embodiment of the present invention
  • FIG 3 is a cross-sectional view of a crankshaft of a piston type compressor in accordance with an embodiment of the present invention.
  • crankcase 10 crankshaft hole 11; mounting boss 12;
  • Thrust bearing 20 upper support piece 21; ball 22; lower support piece 23; retainer 24;
  • Cavity 40 through hole 41; inclined section 42.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • connection In the description of the present invention, it should be noted that the terms “installation”, “connected”, and “connected” are to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or integrally connected; may be mechanically connected or electrically connected; may be directly connected, or may be indirectly connected through an intermediate medium, may be internal communication of two elements or an interaction relationship of two elements. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • the first feature "on” or “under” the second feature may include direct contact of the first and second features, and may also include first and second features, unless otherwise specifically defined and defined. It is not in direct contact but through additional features between them.
  • the first feature "above”, “above” and “above” the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature includes the first feature directly below and below the second feature, or merely the first feature level being less than the second feature.
  • a piston type compressor 100 according to an embodiment of the present invention will be described below with reference to Figs.
  • a piston compressor 100 may include a crankcase 10, a thrust bearing 20, and a crankshaft 30.
  • the crankcase 10 is provided with a crank hole 11, and the upper end of the crankcase 10 is provided with a mounting boss 12, and the crank hole 11 extends upward through the mounting boss 12, and the crankshaft 30 is rotatably disposed in the crankshaft hole. 11 inside.
  • the thrust bearing 20 is sleeved outside the mounting boss 12, and optionally, the mounting boss 12 and the thrust bearing 20 can be clearance fit.
  • the present invention is not limited thereto, and the mounting boss 12 and the thrust bearing 20 may also be a transition fit.
  • the crankshaft 30 is provided with a thrust portion 31, and the lower end surface of the thrust portion 31 is abutted against the upper end surface of the thrust bearing 20, and an oil passage 32 is formed in the crankshaft 30.
  • the oil passage 32 in the crankshaft 30 can draw oil from the bottom up, and then the lubricating oil can be extracted from the upper end of the crankshaft 30 to lubricate other components in the piston compressor 100 (eg, connecting rods, pistons). And cylinder wall, etc.).
  • a cavity 40 is formed between the mounting boss 12, the thrust bearing 20, and the thrust portion 31, and a through hole 41 for connecting the oil passage 32 and the cavity 40 is formed in the peripheral wall of the crankshaft 30.
  • the oil passage 32 in the crankshaft 30 can continuously absorb oil from the bottom to the top.
  • a part of the lubricating oil can continue to flow upward by the centrifugal force, and another part of the lubricating oil can enter through the through hole 41.
  • Within the cavity 40 at least a portion of the lubricating oil can flow onto the thrust bearing 20, and the lubricating oil flowing onto the thrust bearing 20 can further flow into the gap between the mounting boss 12 and the thrust bearing 20.
  • the thrust bearing 20 includes: an upper support piece 21, a ball 22, a lower support piece 23, and a holder 24, the balls 22 are disposed in the holder 24, and the upper support piece 21 is located in the holder 24 and Above the balls 22, the lower support piece 23 is located below the cage 24 and the balls 22, and the lubricating oil flowing into the cavity 40 can flow onto the upper support piece 21 of the thrust bearing 20, and the lubricating oil on the upper support piece 21 It can flow downward into the ball 22 and the cage 24 through the gap between the mounting boss 12 and the thrust bearing 20, so that the lubricating oil can continuously lubricate the ball 22, reducing the friction work of the ball 22 and the upper support piece 21, and The frictional work between the ball 22 and the lower support piece 23 can improve the performance of the piston compressor 100, and the lubricating oil can continue to carry away the heat of the ball 22, further reducing the heat transferred by the ball 22 to the cage 24.
  • the service life of the thrust bearing 20 is increased, so that the service life of the piston compressor 100 can
  • the continuously rotating crankshaft 30 can smash the lubricating oil to different positions of the cavity 40 through the through hole 41, so that the lubricating oil can quickly fill the upper supporting piece of the supporting bearing. 21, and the oil on the upper support sheet 21 can continue to flow downward to the balls 22.
  • the oil passage 32 in the crankshaft 30 can continuously supply oil to the thrust bearing 20, and the lubricating oil can continuously lubricate the balls 22, lowering the balls 22 and the upper support piece 21
  • the frictional work and the frictional work between the ball 22 and the lower support piece 23 can improve the performance of the piston compressor 100, and the lubricating oil can continue to carry away the heat of the ball 22, further reducing the transfer of the ball 22 to the cage.
  • the heat of 24 increases the service life of the thrust bearing 20, thereby increasing the service life of the piston compressor 100.
  • the upper end surface of the mounting boss 12 may be higher than the upper end surface of the thrust bearing 20 in the axial direction of the crankshaft 30 (i.e., the up and down direction shown in FIG. 2). It can be understood that when the upper end surface of the mounting boss 12 is higher than the upper end surface of the thrust bearing 20 in the up and down direction, the lubricating oil flowing into the cavity 40 can be at least partially stored in the upper support piece of the thrust bearing 20. On the upper surface of 21, it is thereby further facilitated that the lubricating oil continuously lubricates the balls 22.
  • an upwardly concave groove 33 may be formed on the lower surface of the thrust portion 31, and the groove 33 is disposed on the mounting protrusion 12 to constitute at least the cavity 40. portion.
  • the through hole 41 in the oil passage 32 may be opposed to the groove 33, and the lubricating oil flowing out from the through hole 41 may flow into the cavity 40.
  • the top wall of the recess 33 may be higher than the upper end surface of the mounting boss 12 in the axial direction of the crankshaft 30, so that the lubricating oil flowing out of the through hole 41 may be facilitated to flow into the cavity 40.
  • the horizontal projection of the recess 33 may be annular and the center of the ring coincides with the axis of the crankshaft bore 11. That is, the groove 33 forms an annular structure around the crank hole 11, and the groove 33 of the annular structure can facilitate the flow of the lubricating oil flowing out of the through hole 41 to different positions of the upper support piece 21 of the thrust bearing 20 in the cavity 40. .
  • the longitudinal projection of the groove 33 may be tapered and the tapered opening faces the thrust bearing 20. It can be understood that when the lubricating oil flowing out from the through hole 41 splashes onto the outer peripheral wall of the groove 33, the lubricating oil flows from the outer peripheral wall of the groove 33 to the upper support piece 21 of the thrust bearing 20 located below the outer peripheral wall. Thereby, it is further possible to facilitate the lubricating oil to fill the upper surface of the support piece 21 so that the lubricating oil continuously lubricates the balls 22.
  • the oil passage 32 may include a slanted section 42 that is disposed within the crankshaft 30 from the axis L of the crankshaft 30 toward the outer peripheral wall of the crankshaft 30, and the through hole 41 communicates with the slanted section 42.
  • the inclined section 42 may be disposed in a spiral shape. It can be understood that the inclined portion 42 can increase the lift of the lubricating oil, and the helical inclined portion 42 can further increase the lift of the lubricating oil, so that the lubricating oil flows from the bottom to the top under the centrifugal force.
  • the amount of lubricating oil of the piston compressor 100 can be adjusted by adjusting the position of the through hole 41 and the parameter L.
  • the position of the through hole 41 can be adjusted by the inclination angle ⁇ of the inclined section 42 with respect to the bearing hole 11 and the distance L1 between the end surface of the mounting boss 12 and the end surface of the thrust bearing 20, and the inclination angle ⁇ is adjusted.
  • the L1 value can adjust the size of the oil discharge cross section of the through hole 41, and the oil output amount of the through hole 41 can be further adjusted.
  • the parameter L is the distance between the outer peripheral wall of the groove 33 adjacent to the thrust bearing 20 to the outer end surface of the mounting boss 12, and the lubrication speed of the ball 22 of the lubricating oil lubrication thrust bearing 20 can be adjusted by adjusting the parameter L. .
  • the balls 22 can be sufficiently lubricated, and at the same time, the oil passages 32 can be sufficiently lubricated to the other moving friction pairs of the piston compressor 100.
  • a refrigeration system according to an embodiment of the present invention includes the piston compressor 100 of the above embodiment.
  • the piston type compressor 100 of the refrigeration system having the piston type compressor 100 of the above embodiment has good performance and long service life.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Abstract

一种活塞式压缩机（100）以及具有其的制冷系统，活塞式压缩机包括：曲轴箱（10），曲轴箱（10）上设有曲轴孔（11），曲轴箱（10）的上端设有安装凸起（12），曲轴孔（11）向上贯穿安装凸起（12）；止推轴承（20），止推轴承（20）套设在安装凸起（12）外部；曲轴（30），曲轴（30）可转动地设在曲轴孔（11）内，曲轴（30）上设有止推部（31），止推部（31）的下端面止抵在止推轴承（20）的上端面上，曲轴（30）内形成有油路（32），其中，安装凸起（12）、止推轴承（20）和止推部（31）之间形成有空腔（40），曲轴（30）的周壁上形成有用于连通油路（32）和空腔（40）的通孔（41）。

Description

活塞式压缩机以及具有其的制冷系统 技术领域
本发明涉及压缩机领域，尤其是涉及一种活塞式压缩机以及具有该活塞式压缩机的制冷系统。
背景技术
相关技术中，高效压缩机普遍采用滚动止推轴承，止推轴承的滚珠的润滑主要靠飞溅非连续地润滑，飞溅非连续润滑不能充分润滑滚珠，滚珠与上下支撑片摩擦产生的热量不能完全的带走，导致滚珠与上下支撑片的摩擦系数变大，压缩机功耗变大。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明提出一种活塞式压缩机，该活塞式压缩机内的润滑油可以持续地润滑止推轴承，从而可以使得活塞式压缩机的性能好。
本发明进一步地提出了一种制冷系统。
根据本发明的活塞式压缩机，包括：曲轴箱，所述曲轴箱上设有曲轴孔，所述曲轴箱的上端设有安装凸起，所述曲轴孔向上贯穿所述安装凸起；止推轴承，所述止推轴承套设在所述安装凸起外部；曲轴，所述曲轴可转动地设在所述曲轴孔内，所述曲轴上设有止推部，所述止推部的下端面止抵在所述止推轴承的上端面上，所述曲轴内形成有油路，其中，所述安装凸起、所述止推轴承和所述止推部之间形成有空腔，所述曲轴的周壁上形成有用于连通所述油路和所述空腔的通孔。
根据本发明实施例的活塞式压缩机，曲轴内的油路可以持续地向止推轴承供油，润滑油可以不断地润滑滚珠，降低滚珠和上支撑片的摩擦功以及滚珠和下支撑片之间的摩擦功，从而可以提高活塞式压缩机的性能，而且润滑油可以持续带走滚珠的热量，进一步地可以降低滚珠传递给保持架的热量，提高止推轴承的使用寿命，从而可以提高活塞式压缩机的使用寿命。
另外，根据本发明的活塞式压缩机还可具有如下附加技术特征：
在本发明的一些示例中，所述安装凸起的上端面在所述曲轴的轴向方向上高于所述止推轴承的上端面。
在本发明的一些示例中，所述止推部的下表面上形成有向上凹入的的凹槽，所述凹槽罩设在所述安装凸起上以构成所述空腔的至少一部分。
在本发明的一些示例中，所述凹槽的顶壁在所述曲轴的轴向方向上高于所述安装凸起的上端面。
在本发明的一些示例中，所述凹槽的水平投影为环形且所述环形的中心与所述曲轴孔的轴线重合。
在本发明的一些示例中，所述凹槽的纵向投影呈锥形且所述锥形的开口朝向所述止推轴承。
在本发明的一些示例中，所述安装凸起和所述止推轴承间隙配合。
在本发明的一些示例中，所述油路包括倾斜段，所述倾斜段在所述曲轴内从所述曲轴轴线朝向所述曲轴外周壁倾斜设置，所述通孔连通所述倾斜段。
在本发明的一些示例中，所述倾斜段呈螺旋状倾斜设置。
根据本发明的制冷系统，包括上述的活塞式压缩机。具有上述的活塞式压缩机的制冷系统的活塞式压缩机的性能好，而且使用寿命长。
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明的实践了解到。
附图说明
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是根据本发明实施例的活塞式压缩机的剖视图；
图2是根据本发明实施例的活塞式压缩机的局部剖视图；
图3是根据本发明实施例的活塞式压缩机的曲轴的剖视图。
附图标记：
活塞式压缩机100；
曲轴箱10；曲轴孔11；安装凸起12；
止推轴承20；上支撑片21；滚珠22；下支撑片23；保持架24；
曲轴30；止推部31；油路32；凹槽33；
空腔40；通孔41；倾斜段42。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征之“上”或之“下”可以包括第一和第二特征直接接触，也可以包括第一和第二特征不是直接接触而是通过它们之间的另外的特征接触。而且，第一特征在第二特征“之上”、“上方”和“上面”包括第一特征在第二特征正上方和斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”包括第一特征在第二特征正下方和斜下方，或仅仅表示第一特征水平高度小于第二特征。
下面参考图1-图3描述根据本发明实施例的活塞式压缩机100。
如图1所示，根据本发明实施例的活塞式压缩机100可以包括曲轴箱10、止推轴承20和曲轴30。如图1和图2所示，曲轴箱10上设有曲轴孔11，曲轴箱10的上端设有安装凸起12，曲轴孔11向上贯穿安装凸起12，曲轴30可转动地设在曲轴孔11内。止推轴承20套设在安装凸起12外部，可选地，安装凸起12和止推轴承20可以间隙配合。但是本发明并不限于此，安装凸起12和止推轴承20还可以是过渡配合。
如图2所示，曲轴30上设有止推部31，止推部31的下端面止抵在止推轴承20的上端面上，曲轴30内形成有油路32。具体地，如图3所示，曲轴30内的油路32可以从下向上吸油，然后润滑油可以从曲轴30的上端甩出以润滑活塞式压缩机100内的其他元件(例如连杆、活塞和气缸壁等)。其中，安装凸起12、止推轴承20和止推部31之间形成有空腔40，曲轴30的周壁上形成有用于连通油路32和空腔40的通孔41。 可以理解的是，曲轴30内的油路32可以从下向上持续地吸油，在通孔41处，一部分润滑油可以靠着离心力的作用继续向上流动，另一部分润滑油可以通过通孔41进入到空腔40内，从而可以至少一部分润滑油流动至止推轴承20上，流动到止推轴承20上的润滑油可以进一步地流动到安装凸起12和止推轴承20的间隙内。
具体地，如图2所示，止推轴承20包括：上支撑片21、滚珠22、下支撑片23和保持架24，滚珠22设置在保持架24内，上支撑片21位于保持架24和滚珠22的上方，下支撑片23位于保持架24和滚珠22的下方，流入到空腔40内的润滑油可以流动到止推轴承20的上支撑片21上，上支撑片21上的润滑油可以通过安装凸起12和止推轴承20之间的间隙向下流动到滚珠22和保持架24内，从而使得润滑油可以持续地润滑滚珠22，降低滚珠22和上支撑片21的摩擦功以及滚珠22和下支撑片23之间的摩擦功，从而可以提高活塞式压缩机100的性能，而且润滑油可以持续带走滚珠22的热量，进一步地可以降低滚珠22传递给保持架24的热量，提高止推轴承20的使用寿命，从而可以提高活塞式压缩机100的使用寿命。
需要说明的是，当活塞式压缩机100工作时，不断旋转的曲轴30可以通过通孔41将润滑油甩到空腔40的不同位置，从而润滑油可以快速地布满支撑轴承的上支撑片21，进而上支撑片21上的油可以持续地向下流动到滚珠22处。由此，根据本发明实施例的活塞式压缩机100，曲轴30内的油路32可以持续地向止推轴承20供油，润滑油可以不断地润滑滚珠22，降低滚珠22和上支撑片21的摩擦功以及滚珠22和下支撑片23之间的摩擦功，从而可以提高活塞式压缩机100的性能，而且润滑油可以持续带走滚珠22的热量，进一步地可以降低滚珠22传递给保持架24的热量，提高止推轴承20的使用寿命，从而可以提高活塞式压缩机100的使用寿命。
在本发明的一些示例中，如图2所示，安装凸起12的上端面可以在曲轴30的轴向方向(即图2所示的上下方向)上高于止推轴承20的上端面。可以理解的是，当安装凸起12的上端面在上下方向上高于止推轴承20的上端面时，流动到空腔40内的润滑油可以至少一部分储存在止推轴承20的上支撑片21的上表面上，从而可以进一步地便于润滑油持续地润滑滚珠22。
可选地，如图2和图3所示，止推部31的下表面上可以形成有向上凹入的凹槽33，凹槽33罩设在安装凸起12上以构成空腔40的至少一部分。如图2所示，油路32上的通孔41可以与凹槽33相对，从通孔41流出的润滑油可以流动到空腔40内。通过设置凹槽33，可以增加空腔40的体积，而且便于通孔41的设置，进一步地便于润滑油流动到空腔40内。可选地，凹槽33的顶壁可以在曲轴30的轴向方向上高于安装凸起12的上端面，从而可以便于从通孔41流出的润滑油流动到空腔40内。
可选地，凹槽33的水平投影可以为环形，而且环形的中心与曲轴孔11的轴线重合。也就是说，凹槽33围绕曲轴孔11形成环形结构，环形结构的凹槽33可以便于从通孔41流出的润滑油流动到空腔40内的止推轴承20的上支撑片21的不同位置。
可选地，如图2所示，凹槽33的纵向投影可以呈锥形，而且锥形的开口朝向止推轴承20。可以理解的是，当从通孔41流出的润滑油飞溅到凹槽33的外周壁上时，润滑油从凹槽33的外周壁流动到位于外周壁下方的止推轴承20的上支撑片21，从而可以进一步地便于润滑油布满上支撑片21的上表面以便于润滑油持续地润滑滚珠22。
在本发明的一些具体示例中，油路32可以包括倾斜段42，倾斜段42在曲轴30内从曲轴30轴线L朝向曲轴30外周壁倾斜设置，通孔41连通倾斜段42。具体地，倾斜段42可以呈螺旋状倾斜设置。可以理解的是，倾斜设置的倾斜段42可以增加润滑油的升力，而且螺旋状的倾斜段42可以进一步地增加润滑油的升力，便于润滑油在离心力的作用下从下向上流动。
需要说明的是，活塞式压缩机100的润滑油量分配可以通过调整通孔41的位置和参数L来调节。如图2所示，通孔41的位置可以通过倾斜段42相对轴承孔11的倾斜角度θ和安装凸起12的端面到止推轴承20的端面之间的距离L1调节，调节倾斜角度θ和L1值可以调整通孔41的出油截面的大小，进一步地可以调节通孔41的出油量。其中，参数L为凹槽33的邻近止推轴承20的外周壁到安装凸起12的外端面之间的距离，通过调节参数L可以实现调节润滑油润滑止推轴承20的滚珠22的润滑速度。通过合理调整参数L、角度θ和L1值，可以使得滚珠22得到充分润滑，同时还可以保证油路32给活塞式压缩机100的其他运动摩擦副充分润滑。根据本发明实施例的制冷系统，包括上述实施例的活塞式压缩机100。具有上述实施例的活塞式压缩机100的制冷系统的活塞式压缩机100的性能好，而且使用寿命长。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (10)

  1. 一种活塞式压缩机，其特征在于，包括：
    曲轴箱，所述曲轴箱上设有曲轴孔，所述曲轴箱的上端设有安装凸起，所述曲轴孔向上贯穿所述安装凸起；
    止推轴承，所述止推轴承套设在所述安装凸起外部；
    曲轴，所述曲轴可转动地设在所述曲轴孔内，所述曲轴上设有止推部，所述止推部的下端面止抵在所述止推轴承的上端面上，所述曲轴内形成有油路，
    其中，所述安装凸起、所述止推轴承和所述止推部之间形成有空腔，所述曲轴的周壁上形成有用于连通所述油路和所述空腔的通孔。
  2. 根据权利要求1所述的活塞式压缩机，其特征在于，所述安装凸起的上端面在所述曲轴的轴向方向上高于所述止推轴承的上端面。
  3. 根据权利要求2所述的活塞式压缩机，其特征在于，所述止推部的下表面上形成有向上凹入的的凹槽，所述凹槽罩设在所述安装凸起上以构成所述空腔的至少一部分。
  4. 根据权利要求3所述的活塞式压缩机，其特征在于，所述凹槽的顶壁在所述曲轴的轴向方向上高于所述安装凸起的上端面。
  5. 根据权利要求3所述的活塞式压缩机，其特征在于，所述凹槽的水平投影为环形且所述环形的中心与所述曲轴孔的轴线重合。
  6. 根据权利要求3所述的活塞式压缩机，其特征在于，所述凹槽的纵向投影呈锥形且所述锥形的开口朝向所述止推轴承。
  7. 根据权利要求1所述的活塞式压缩机，其特征在于，所述安装凸起和所述止推轴承间隙配合。
  8. 根据权利要求1所述的活塞式压缩机，其特征在于，所述油路包括倾斜段，所述倾斜段在所述曲轴内从所述曲轴轴线朝向所述曲轴外周壁倾斜设置，所述通孔连通所述倾斜段。
  9. 根据权利要求8所述的活塞式压缩机，其特征在于，所述倾斜段呈螺旋状倾斜设置。
  10. 一种制冷系统，其特征在于，包括根据权利要求1-9中任一项所述的活塞式压缩机。
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