WO2019061892A1 - 一种压缩机的油路结构和压缩机 - Google Patents

一种压缩机的油路结构和压缩机 Download PDF

Info

Publication number
WO2019061892A1
WO2019061892A1 PCT/CN2017/118247 CN2017118247W WO2019061892A1 WO 2019061892 A1 WO2019061892 A1 WO 2019061892A1 CN 2017118247 W CN2017118247 W CN 2017118247W WO 2019061892 A1 WO2019061892 A1 WO 2019061892A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
bearing
hole
rolling
compressor
Prior art date
Application number
PCT/CN2017/118247
Other languages
English (en)
French (fr)
Inventor
胡余生
徐嘉
张振江
杨国蟒
万鹏凯
梁社兵
Original Assignee
格力电器（武汉）有限公司
珠海格力电器股份有限公司
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
Application filed by 格力电器（武汉）有限公司, 珠海格力电器股份有限公司 filed Critical 格力电器（武汉）有限公司
Priority to US16/617,033 priority Critical patent/US11248609B2/en
Priority to EP17926432.0A priority patent/EP3690248B1/en
Publication of WO2019061892A1 publication Critical patent/WO2019061892A1/zh

Links

Images

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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F04C18/3447—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface the vanes having the form of rollers, slippers or the like
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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

Definitions

  • the invention belongs to the technical field of compressors, and in particular relates to an oil circuit structure and a compressor of a compressor.
  • the existing suction and exhaust structure of the conventional rotary vane compressor is mainly arranged on the side of the cylinder.
  • the mechanical power consumption of the compressor is too large, and the overall energy efficiency is poor. Reliability issues such as abnormal wear.
  • Korean Patent Application No. KR1020100076562 discloses a rolling bearing scheme: by adding a rolling body and an inner ring (similar to a roller) structure to the inner wall of the cylinder, the relative sliding of the sliding head and the inner wall of the inner ring is ensured to be the inner ring and the rolling body. Rolling motion, which reduces the mechanical power consumption of the compressor and improves the energy efficiency of the compressor.
  • the disclosed structure does not lubricate the rolling bearing.
  • the heat generated by the friction of the rolling element cannot be discharged in time.
  • the long-term operation easily causes the temperature of the part to rise, which causes the reliability of the rolling bearing.
  • the temperature is too high.
  • the wall surface heating heatating the refrigerant during the compression process, more deviating from the adiabatic compression, increasing the power consumption
  • the rolling bearing rolling elements have no lubricating oil for lubrication during operation, and are prone to dry friction.
  • Metal contact causes adhesive wear, etc., which causes the entire compressor to be abnormal.
  • the present invention has devised a circuit structure and a compressor for a compressor.
  • the technical problem to be solved by the present invention is to overcome the defects that the heat generated by the friction of the rolling element in the prior art cannot be discharged in time, thereby providing an oil passage structure and a compressor of the compressor.
  • the invention provides an oil passage structure of a compressor, comprising:
  • the rolling bearing is internally enclosed with a cylinder bore for performing compression, the rolling bearing comprising a rolling body;
  • the spindle is internally provided with a spindle oil hole, and the upper flange is provided with an oil groove, and the oil groove is connected with the spindle oil hole to introduce oil into the rolling body to lubricate the same.
  • the oil sump comprises:
  • the bearing lubrication oil inlet passage has one end communicating with the straight oil groove and the other end communicating with the bearing rolling body oil inlet hole.
  • the straight oil groove is opened on a radially inner side of the upper flange and extends along an axial direction of the upper flange, and the bearing lubrication oil inlet passage extends in a radial direction of the upper flange
  • the bearing rolling element oil inlet hole extends along an axial direction of the upper flange.
  • the straight oil groove is an annular oil groove or an arc oil groove.
  • the bearing lubrication oil inlet passage is two or more, distributed along the circumferential direction of the upper flange;
  • Each of the bearing lubrication oil inlet passages is connected with one bearing rolling element oil inlet hole, and two or more of the bearing lubrication oil inlet passages are connected with one of the straight oil grooves, or each of the bearings is lubricated into The oil passage connects one of the straight oil grooves.
  • the method further includes an upper oil reservoir disposed on the upper flange, the upper oil reservoir being in communication with the bearing rolling body oil inlet hole and simultaneously communicating with the bearing lubrication oil inlet passage.
  • the upper oil reservoir is located axially above the oil inlet hole of the bearing rolling body and extends in a circumferential direction of the upper flange.
  • a gasket is further disposed between the upper flange and the rolling bearing, and the gasket is provided with a plurality of oil guiding holes along the axial direction of the main shaft, and the plurality of oil guiding holes are arranged along the circumferential direction of the main shaft And feeding the bearing rolling element oil inlet hole and the rolling body.
  • At least two of the plurality of oil guiding holes have different aperture sizes, and an oil guiding hole close to the rolling bearing vent hole has a larger diameter than the oil guiding hole of the rolling bearing.
  • the pore size of the hole is not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to, but not limited to the rolling bearing vent hole.
  • a lower flange is further included, and a lower oil groove capable of communicating with the rolling body is further disposed on the lower flange, and oil can be extracted from the lower flange or oil from the lower oil groove
  • the rolling bearing is derived.
  • the lower oil groove is located axially below the rolling body, and the lower oil groove extends radially to a circumferential end surface of the lower flange, and the oil is led out at the circumferential end surface.
  • the lower oil grooves are two or more, and are distributed at different circumferential positions of the lower flange.
  • a lower oil reservoir disposed on the lower flange, the lower oil reservoir being in communication with the lower oil groove.
  • the lower oil reservoir is an annular structure circumferentially surrounding the main shaft.
  • the rolling bearing further includes a bearing inner ring and a bearing outer ring
  • the bearing outer ring is provided with an outer ring oil groove
  • the lower oil groove can simultaneously communicate the rolling body and the outer ring oil groove, through the outer
  • the oil groove can discharge oil from the outer ring of the bearing.
  • the outer ring oil groove comprises an axial oil hole extending axially along the outer ring of the bearing and at least one radial oil hole extending radially along the outer ring, the axial oil hole communicating with the lower oil groove And the radial oil hole is in communication with the axial oil hole, and oil can be discharged from the circumferential surface of the bearing outer ring through the radial oil hole.
  • the lower oil groove extends in a radial direction of the lower flange
  • the plurality of radial oil holes are plural, and the plurality of the radial oil holes are disposed in parallel and each extend in a radial direction of the outer ring of the bearing.
  • the spindle oil hole includes a main shaft radial oil hole opened inside the main shaft and in a radial direction.
  • the present invention also provides a compressor comprising the aforementioned compressor oil passage structure.
  • the compressor is a rotary vane compressor.
  • the oil passage structure and compressor of the compressor of the present invention by providing an oil groove on the upper flange, the oil sump being in communication with the spindle oil hole and capable of introducing oil into the rolling body to Lubrication can effectively guide the oil in the oil hole of the compressor main shaft through the upper flange to the rolling element of the rolling bearing, and lubricate it, so that the heat generated by the rolling body friction can be discharged in time to prevent the bearing temperature from rising. High, and reduce wear, thereby improving the energy efficiency of the compressor and ensuring the normal operation of the compressor;
  • the oil passage structure and the compressor of the compressor of the present invention and by the oil groove provided on the upper flange, the oil can be introduced from the top to the bottom into the rolling elements of the rolling bearing by gravity, thereby ensuring the lubricating oil in the rolling bearing. Adequate to ensure the normal operation of the compressor;
  • the oil circuit structure and the compressor of the compressor of the present invention can also enter the oil passing through the bearing lubrication oil passage before entering the bearing rolling body oil inlet hole through the upper oil storage groove provided on the upper flange.
  • Storage in the oil storage tank so as to achieve the role of oil storage when the amount of oil is too much, in the case of too little oil, the lubricating oil can be released through the oil storage tank, ensuring good lubrication and cooling effect of the rolling bearing, and improving the compressor Performance; oil can be recycled and recycled by discharging the oil through the lower oil groove provided on the lower flange and discharging the lubricating oil into the casing of the compressor.
  • Figure 1 is an exploded perspective view showing the structure of a pump body of the compressor of the present invention
  • Figure 2 is a schematic cross-sectional view of the longitudinal section of Figure 1;
  • Figure 3 is an enlarged schematic view of a portion A of Figure 2;
  • Figure 4 is a top plan view of the upper flange of Figure 1;
  • Figure 5 is a top plan view of the upper flange of the alternative embodiment of Figure 4.
  • Figure 6 is a top plan view of the upper flange of Figure 4 with the oil reservoir of the first embodiment
  • Figure 7 is a top plan view of the upper flange of Figure 4 with the oil reservoir of the second embodiment
  • Figure 8 is a structural view showing the lower flange of the compressor of the present invention having the oil groove of the first embodiment
  • Figure 9 is a structural view showing the lower flange of the compressor of the present invention having the oil groove of the second embodiment
  • Figure 10 is a structural view showing the lower flange of the compressor of the present invention having a lower oil reservoir
  • Figure 11 is a longitudinal sectional view showing the structure of the outer ring of the bearing of the compressor of the present invention.
  • Figure 12 is a top plan view of the lower flange of Figure 11;
  • Figure 13 is a longitudinal cross-sectional view of the first embodiment of the rolling bearing of Figure 11;
  • Figure 14 is a longitudinal cross-sectional view of a second embodiment of the rolling bearing of Figure 11;
  • Figure 15 is a front cross-sectional view showing the compressor of the present invention having a gasket
  • Figure 16 is a perspective view showing the structure of the gasket of Figure 15.
  • the present invention provides an oil passage structure of a compressor, which includes:
  • the rolling bearing 3 (cylinder) is enclosed by a cylinder chamber for compression, the rolling bearing 3 comprises a rolling body 33;
  • the spindle 1 is internally provided with a spindle oil hole 10, and the upper flange 2 is provided with an oil groove 20, and the oil groove 20 is in communication with the spindle oil hole 10 and can introduce oil into the rolling body 33. Lubricate it.
  • An oil sump is disposed on the upper flange, the oil sump is in communication with the spindle oil hole, and oil can be introduced into the rolling body to lubricate the oil, and the oil in the oil hole of the compressor main shaft can be effectively
  • the upper flange is introduced into the rolling element of the rolling bearing, and is lubricated and cooled, so that the heat generated by the rolling body friction can be discharged in time, the bearing temperature is prevented from rising, and the wear is reduced, thereby improving the energy efficiency value of the compressor and ensuring Normal operation of the compressor;
  • the oil sump 20 comprises:
  • the bearing lubrication oil inlet passage 20b has one end communicating with the straight oil groove 20a and the other end communicating with the bearing rolling element oil inlet hole 20c.
  • the straight oil sump can introduce lubricating oil from the oil hole of the main shaft, further guide the lubricating oil passage through the bearing, and finally lead to the bearing rolling body oil. In the hole, the oil is transported to the position of the rolling element of the rolling bearing to complete the effect and effect on the lubrication of the bearing rolling element.
  • Figure 1 shows the basic structure of the compressor pump body.
  • the oil circuit is shown in Figure 2.
  • the gear oil pump is forced to supply the oil in the oil pool to the center hole of the spindle as the spindle rotates.
  • the upper end of the main shaft is closed, and the lower end is opened.
  • the lubricating oil enters from the central hole and reaches the height of the upper flange, it will flow to the radial oil hole of the main shaft by oil pressure, and then flow to the main shaft retreating groove and the upper flange straight oil groove.
  • Small oil storage space (as shown in Figure 3).
  • the straight oil groove 20a is opened radially inward of the upper flange 2 and extends along an axial direction of the upper flange 2, and the bearing lubricates the oil inlet passage 20b along the upper flange The radial direction of 2 extends, and the bearing rolling element oil inlet hole 20c extends in the axial direction of the upper flange 2.
  • the bearing rolling body oil inlet hole extends axially along the upper flange, and can transport the lubricating oil from the top to the bottom vertically to the rolling body, thereby effectively utilizing the action of gravity and reducing the pump
  • the power of the oil delivery flow improves the efficiency of the lubricating oil.
  • the straight oil groove 20a is an annular oil groove or an arc oil groove.
  • This is a preferred structural form of the straight oil groove of the present invention, and it is provided that the annular oil groove or the curved oil groove is correspondingly arranged according to the shape of the cylindrical body of the main shaft, and the lubricating oil can be introduced from a plurality of circumferential positions of the main shaft and opened.
  • the annular oil groove can connect a plurality of bearing lubrication oil passages to the one annular oil groove, which makes the structure simpler and more practical.
  • the bearing lubrication oil inlet passages 20b are two or more, distributed along the circumferential direction of the upper flange 2;
  • Each of the bearing lubrication oil inlet passages 20b is connected to one of the bearing rolling element oil inlet holes 20c, and two or more of the bearing lubrication oil inlet passages 20b are connected to one of the straight oil grooves 20a, or each of the The bearing lubrication oil inlet passage 20b is connected to one of the straight oil grooves 20a.
  • the bearing lubrication oil inlet passage is provided in two or more, and can conduct oil and oil in the radial direction in different circumferential directions of the upper flange, thereby improving the transmission.
  • the flow rate of the oil increases the amount of oil delivered, improves the lubrication and cooling effect on the bearing rolling elements, improves the operational reliability and stability of the compressor, and allows the compressor to operate at higher frequencies and higher rotational speeds.
  • This embodiment is a further improvement based on the embodiment 1, as shown in FIGS. 6-7, preferably, further comprising an upper oil reservoir 21 disposed on the upper flange 2, the upper oil reservoir 21 and The bearing rolling element oil inlet hole 20c is in communication while being in communication with the bearing lubrication oil inlet passage 20b.
  • the oil passing through the bearing lubrication oil inlet passage can be stored in the upper oil storage tank before entering the bearing rolling body oil inlet hole, thereby realizing oil storage when the oil quantity is too much.
  • the function in the case of too little oil, can release the lubricating oil through the oil storage tank, ensuring good lubrication and cooling effect of the rolling bearing and improving the performance of the compressor.
  • the upper oil reservoir 21 is located above the axial direction of the bearing rolling body oil inlet hole 20c and extends in the circumferential direction of the upper flange 2. This can change the direction of the oil that is about to enter the bearing rolling element oil inlet and enter the upper oil storage tank to complete the oil storage.
  • the upper oil storage tank is a straight section groove, as shown in FIG. 6, and may also be a curved section groove. As shown in FIG. 7, the cross-sectional area of the upper oil storage tank in FIG. 7 is significantly larger than that of FIG.
  • this embodiment is a further improvement based on the embodiment 1 and/or 2, preferably a spacer 8 is further disposed between the upper flange 2 and the rolling bearing 3.
  • a plurality of oil guiding holes 81 are arranged on the gasket 8 along the axial direction of the main shaft, and the plurality of oil guiding holes 81 are arranged along the circumferential direction of the main shaft, and the bearing rolling body oil inlet holes 20c and the The rolling elements 33 are in communication.
  • the lubricating oil directly enters the bearing cavity rolling body 33 through the upper flange bearing rolling body oil inlet hole 20c.
  • the oil is supplied from one point to the entire bearing chamber, so that the oil supply position is relatively fixed, although The inner ring is rotated, but the temperature difference of the oil temperature is large for the entire bearing cavity.
  • the gasket is added, the oil supply in the range of 360° of the entire bearing cavity can be realized, and different diameters can be set as needed to achieve lubrication of the rolling elements; after the gasket, the lubrication and cooling of the rolling elements can be more fully performed;
  • the gasket can improve the wear of the inner ring of the rolling bearing and the end face of the upper flange.
  • At least two of the plurality of oil guiding holes 81 have different aperture sizes, and an oil guiding hole 81 close to the exhaust hole of the rolling bearing 3 has a larger diameter than the rolling bearing 3
  • oil guiding holes 81 of different diameters are mainly opened, and the size of the oil guiding holes is set according to the lubrication requirement, and the pressure of the rolling elements due to the pressure difference of the inner ring is in the vicinity of the exhaust side (exhaust holes).
  • oil hole diameter here should be designed to be larger, and the oil guide hole of the upper flange bearing rolling element oil inlet hole 20c is due to the suction of the compressor.
  • the side is not subject to a lot of force, so the amount of oil required here is smaller, and the diameter of the oil hole is designed to be smaller. It is preferred to include oil guide holes of three pore sizes:
  • This embodiment is a further improvement based on the embodiment 1-3, and preferably further includes a lower flange 4, and the lower flange 4 is further provided with a lower oil groove which can communicate with the rolling body 41. Oil can be withdrawn from the lower flange 4 via the lower oil groove 41 or the oil can be discharged from the rolling bearing 3. The oil can be transported and diverted through the lower oil groove provided on the lower flange, and the lubricating oil is discharged into the casing of the compressor to realize oil recovery and recycling.
  • the rolling bearing lubricating oil road solution connects the main shaft, the upper flange, the rolling bearing and the lower flange, which not only enables the lubricating oil to be recycled in the casing oil pool, but also ensures that the rolling elements of the rolling bearing are fully lubricated and can also be brought in time. Walk the heat generated by friction during this process. Through such an oil passage method, the effect of sufficient lubrication of the rolling bearing is achieved, the wear of the pump body during the operation of the compressor is reduced, and the reliability of the operation is increased.
  • the lower oil groove 41 is located below the axial direction of the rolling element 33 and extends in the radial direction to a circumferential end surface of the lower flange 4, and the oil is led out at the circumferential end surface.
  • the oil can be directly guided to the circumferential end surface of the lower flange through the oil sump, and the purpose and function of discharging the oil out of the compressor pump body to the oil pool at the bottom of the compressor casing are completed.
  • the lower oil grooves 41 are two or more and distributed at different circumferential positions of the lower flange 4. This is an extended form of the lower oil sump.
  • the oil discharge amount of the lubricating oil can be increased by two or more lower oil grooves, the circulation speed of the lubricating oil is accelerated, and the cooling lubrication rate of the bearing is improved.
  • a lower oil reservoir 42 is provided on the lower flange 4, and the lower oil reservoir 42 is in communication with the lower oil groove 41.
  • the lower oil storage tank provided at the above position can be stored in the lower oil storage tank before entering the lower oil tank 41, so that the oil storage effect can be achieved when the oil quantity is too large, and the oil can be passed when the oil quantity is too small.
  • the oil storage tank releases the lubricating oil to ensure good lubrication and cooling of the rolling bearing and improve the performance of the compressor.
  • the lower oil reservoir 42 is an annular structure circumferentially surrounding the main shaft 1. This is a preferred shape of the lower oil sump of the present invention, which maximizes the ability to store oil.
  • the rolling bearing 3 further includes a bearing inner ring 31 and a bearing outer ring 32.
  • the bearing outer ring 32 is provided with an outer ring oil groove 321 which can simultaneously communicate the rolling
  • the body 33 and the outer ring oil groove 321 can discharge oil from the bearing outer ring 32 through the outer ring oil groove 321 .
  • the position of the lower oil groove 41 in the axial direction of the outer ring oil groove is enlarged, and it can be used for oil storage.
  • the upper flange radial bearing lubricates the position of the oil inlet passage and the oil inlet hole (opening position at different angles), the number of radial bearing lubrication oil passages 20b, and the bearing rolling element oil inlet hole 20c can be adjusted; in addition, the upper flange end structure can also be added with different lengths of annular oil storage tank for oil storage, as shown in Figures 6 and 7.
  • the oil discharge position can be increased from the oil outlet of the lower flange end face to the side hole of the rolling bearing to replace the oil groove of the lower flange.
  • the specific oil passage is as shown in FIG. 10, and the lubricating oil in the rolling element region flows into the oil groove of the lower flange end face (as shown in FIG. 11), and the groove communicates with the through hole of the upper and lower end faces of the rolling bearing (as shown in FIG. 12). It flows to the through hole and then flows out of the rolling bearing radial oil hole 321b(s) into the housing oil sump.
  • the side holes of the rolling bearing may be opened at different height positions, or one or more may be opened.
  • the outer ring oil groove 321 includes an axial oil hole 321a extending axially along the bearing outer ring 32 and at least one radial oil hole 321b extending radially along the outer ring, the axial oil hole 321a and The lower oil groove 41 is in communication, and the radial oil hole 321b communicates with the axial oil hole 321a, and oil can be discharged from the circumferential surface of the bearing outer ring 32 through the radial oil hole 321b.
  • This is a specific structural form of the outer ring oil groove formed on the outer ring of the bearing of the present invention.
  • the oil in the lower oil groove is axially sucked through the axial oil hole, and is guided into the radial oil hole and passes through the radial oil hole. It is discharged from the outer peripheral surface of the outer ring of the bearing to achieve the function and purpose of lubricating oil discharge.
  • the lower oil groove 41 extends in a radial direction of the lower flange 4;
  • the plurality of radial oil holes 321b are plural, and the plurality of the radial oil holes 321b are disposed in parallel and each extend in a radial direction of the bearing outer ring 32.
  • the spindle oil hole 10 includes a main shaft radial oil hole 13 which is opened radially outward of the radial direction.
  • the oil in the oil hole of the main shaft can be introduced into the oil groove 20 in the radial direction to realize the oil guiding and outputting of the lubricating oil.
  • the invention provides a novel structure for lubricating a rolling bearing for a compressor.
  • different oil holes and oil grooves are formed in the upper flange, the lower flange and the rolling bearing, so that the rolling bearing and the upper and lower flange oil passages are penetrated.
  • this lubrication method has the advantages of simple structure and simple processing. The lubrication degree of the pump body bearing is ensured, the wear and heat of the rolling bearing are effectively solved, and the reliability and energy efficiency of the compressor are improved.
  • the upper flange By opening different holes and slots in the upper flange, it is connected with the oil outlet hole of the main shaft of the pump body and the gap region of the rolling element of the rolling bearing, and the lower flange groove is communicated with the lower gap region of the rolling element, so that the four parts
  • the oil passage is connected (the rolling element is between the outer ring and the inner ring, and its height is smaller than the bearing height, so there is a gap between the upper and lower end faces, and the gap between the rolling element and the upper end surface of the bearing is the clearance area on the rolling element, and the rolling element and the lower end surface of the bearing
  • the clearance is the lower clearance area of the rolling element), so as to ensure that the rolling body part of the rolling bearing has lubricating oil flowing, not only lubricating the rolling bearing, but also taking away the heat generated by the rolling friction in time, reducing the power consumption of the compressor, thereby improving The energy efficiency of the compressor itself.
  • the present invention also provides a compressor comprising the aforementioned compressor oil passage structure.
  • An oil sump is disposed on the upper flange, the oil sump is in communication with the spindle oil hole, and oil can be introduced into the rolling body to lubricate the oil, and the oil in the oil hole of the compressor main shaft can be effectively
  • the upper flange is introduced into the rolling element of the rolling bearing, and is lubricated and cooled, so that the heat generated by the rolling body friction can be discharged in time, the bearing temperature is prevented from rising, and the wear is reduced, thereby improving the energy efficiency value of the compressor and ensuring Normal operation of the compressor;
  • the compressor is a rotary vane compressor. This is a preferred construction of the compressor of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

一种压缩机的油路结构，包括：主轴（1）、上法兰（2）和滚动轴承（3），滚动轴承（3）内部围成用于进行压缩的气缸腔，滚动轴承（3）包括滚动体（33）；其中主轴（1）内部设置有主轴油孔（10），上法兰（2）上设置有上油槽（20），上油槽（20）与主轴油孔（10）连通且能将油导入滚动体（33）中以对其进行润滑。该油路结构能够有效地将压缩机主轴油孔（10）中的油通过上法兰（2）导入到滚动轴承（3）的滚动体（33）部位，对其进行润滑降温，使得滚动体（33）摩擦产生的热量得以及时地被排出，防止轴承温度升高，并且降低磨损，从而提高压缩机的能效值，保证压缩机的正常运行。还包括一种设置有该油路结构的压缩机。

Description

一种压缩机的油路结构和压缩机 技术领域
本发明属于压缩机技术领域，具体涉及一种压缩机的油路结构和压缩机。
背景技术
现有传统旋叶式压缩机吸气和排气结构主要布置在气缸侧面，但由于滑片头部和气缸内壁磨损严重，造成压缩机机械功耗偏大，整体能效较差，严重时甚至引起异常磨损等可靠性问题。
韩国专利申请号KR1020100076562专利公开了一种滚动轴承方案：通过在气缸内壁增加滚动体和内圈(类似滚子)结构，保证滑片头部与内圈内壁的相对滑动转为内圈与滚动体的滚动运动，从而降低压缩机机械功耗，提高压缩机能效。
但其公开的结构未对滚动轴承进行润滑，在压缩机运行过程中，滚动体摩擦产生的热量无法及时排出，长时间运行容易导致该部位温度升高引起滚动轴承可靠性问题；同时温度过高会导致压缩过程中壁面加热(对压缩过程中的冷媒加热，更加偏离绝热压缩，功耗增加)严重，引起压缩机能效变差；另外，滚动轴承滚动体在运行过程没有润滑油进行润滑，容易产生干摩擦金属接触引起粘着磨损等，进而引起整个压缩机异常。
由于现有技术中的旋叶压缩机存在未对滚动轴承进行润滑，在压缩机运行过程中，滚动体摩擦产生的热量无法及时排出，长时间运行容易导致该部位温度升高引起滚动轴承可靠性问题，压缩机能效变差等技术问题，因此本发明研究设计出一种压缩机的油路结构和压缩机。
发明内容
因此，本发明要解决的技术问题在于克服现有技术中的压缩机存在滚动体摩擦产生的热量无法及时排出的缺陷，从而提供一种压缩机的油路结构和压缩机。
本发明提供一种压缩机的油路结构，其包括：
主轴、上法兰和滚动轴承，所述滚动轴承内部围成有用于进行压缩的气缸腔，所述滚动轴承包括滚动体；
其中所述主轴内部设置有主轴油孔，所述上法兰上设置有上油槽，所述上油槽与所述主轴油孔连通以能将油导入所述滚动体中以对其进行润滑。
优选地，所述上油槽包括：
直油槽，与所述主轴油孔连通；
轴承滚动体进油孔，与所述滚动体相连通；
轴承润滑进油通道，其一端与所述直油槽连通、另一端与所述轴承滚动体进油孔连通。
优选地，所述直油槽开设于所述上法兰的径向内侧、沿着所述上法兰的轴向延伸，所述轴承润滑进油通道沿着所述上法兰的径向方向延伸，所述轴承滚动体进油孔沿着所述上法兰的轴向方向延伸。
优选地，在所述上法兰的横截面上，所述直油槽为环形油槽或弧形油槽。
优选地，所述轴承润滑进油通道为两个以上、沿着所述上法兰的周向进行分布；
每个所述轴承润滑进油通道均连接有一个所述轴承滚动体进油孔，两个以上所述轴承润滑进油通道均与一个所述直油槽相连通、或者每个所述轴承润滑进油通道连接一个所述直油槽。
优选地，还包括设置在所述上法兰上的上储油槽，所述上储油槽与所述轴承滚动体进油孔相连通、同时还与所述轴承润滑进油通道相连通。
优选地，所述上储油槽位于所述轴承滚动体进油孔的轴向上方、且沿着所述上法兰的周向方向延伸。
优选地，在所述上法兰和所述滚动轴承之间还设置有垫片，所述垫片上沿主轴轴向开设有多个导油孔，多个所述导油孔沿主轴周向排布、且能将所述轴承滚动体进油孔与所述滚动体进行连通。
优选地，多个所述导油孔中，至少两个所述导油孔的孔径大小不同，且靠近所述滚动轴承排气孔的导油孔的孔径大于靠近所述滚动轴承吸气孔的导油孔的孔径。
优选地，还包括下法兰，在所述下法兰上还开设有能与所述滚动体连通的 下油槽，经由所述下油槽能将油从所述下法兰导出、或者将油从所述滚动轴承导出。
优选地，所述下油槽位于所述滚动体的轴向下方，且所述下油槽沿径向延伸至所述下法兰的周向端面，在所述周向端面将油导出。
优选地，所述下油槽为两个以上、在所述下法兰的不同周向位置进行分布。
优选地，还包括设置在所述下法兰上的下储油槽，所述下储油槽与所述下油槽相连通。
优选地，所述下储油槽为围绕所述主轴周向环绕的环形结构。
优选地，所述滚动轴承还包括轴承内圈和轴承外圈，所述轴承外圈上设置有外圈油槽，所述下油槽能同时连通所述滚动体和所述外圈油槽，通过所述外圈油槽能将油从轴承外圈排出。
优选地，所述外圈油槽包括沿所述轴承外圈轴向延伸的轴向油孔和沿外圈径向延伸的至少一个径向油孔，所述轴向油孔与所述下油槽连通、且所述径向油孔与所述轴向油孔连通，能通过所述径向油孔将油从所述轴承外圈的周面排出。
优选地，所述下油槽沿所述下法兰的径向延伸；
和/或，所述径向油孔为多个，多个所述径向油孔平行设置、均沿所述轴承外圈的径向方向延伸。
优选地，所述主轴油孔包括在所述主轴内部、沿径向方向开设的主轴径向油孔。
本发明还提供一种压缩机，其包括前述的压缩机油路结构。
优选地，所述压缩机为旋叶式压缩机。
本发明提供的一种压缩机的油路结构和压缩机具有如下有益效果：
1.本发明的压缩机的油路结构和压缩机，通过在上法兰上设置有上油槽，所述上油槽与所述主轴油孔连通且能将油导入所述滚动体中以对其进行润滑，能够有效地将压缩机主轴油孔中的油通过上法兰导入到滚动轴承的滚动体部位、对其进行润滑降温，使得滚动体摩擦产生的热量得以及时地被排出，防止轴承温度升高，并且降低磨损，从而提高压缩机的能效值，保证压缩机的正常运行；
2.本发明的压缩机的油路结构和压缩机，并且通过在上法兰上设置的上油 槽，能够利用重力将油从上往下地导入到滚动轴承的滚动体中，保证了滚动轴承中润滑油的充足，保证压缩机的正常运行；
3.本发明的压缩机的油路结构和压缩机，通过在上法兰上设置的上储油槽还能对经过轴承润滑进油通道中的油在进入轴承滚动体进油孔之前进入到上储油槽中进行储存，从而在油量过多的时候实现储油的作用、在油量过少的情况下可以通过该储油槽进行释放润滑油，保证滚动轴承良好的润滑降温作用，提升压缩机的性能；通过在下法兰上设置的下油槽能够对油进行储存的同时、还能通过其将润滑油排出至压缩机的壳体中，实现了油的回收利用和循环利用。
附图说明
图1是本发明的压缩机的泵体结构的分解示意图；
图2是图1中的纵向截面的截面示意图；
图3是图2中A部分的放大结构示意图；
图4是图1中上法兰的俯视结构示意图；
图5是图4的替代实施例的上法兰的俯视结构示意图；
图6是图4的上法兰具有第一种实施方式上储油槽的俯视结构示意图；
图7是图4的上法兰具有第二种实施方式上储油槽的俯视结构示意图；
图8是本发明的压缩机的下法兰具有第一种实施方式下油槽的结构图；
图9是本发明的压缩机的下法兰具有第二种实施方式下油槽的结构图；
图10是本发明的压缩机的下法兰具有下储油槽的结构图；
图11是本发明的压缩机的轴承外圈上设置外圈油槽时的结构纵向截面图；
图12是图11的下法兰的俯视结构示意图；
图13是图11中的滚动轴承的第一种实施方式的纵向截面图；
图14是图11中的滚动轴承的第二种实施方式的纵向截面图；
图15是本发明的压缩机具有垫片时的正面截面示意图；
图16是图15中垫片的立体结构示意图。
图中附图标记表示为：
1、主轴；10、主轴油孔；11、主轴中心部；12、主轴退刀槽；13、主轴径向油孔；2、上法兰；20、上油槽；20a、直油槽；20b、轴承润滑进油通道； 20c、轴承滚动体进油孔；21、上储油槽；3、滚动轴承(气缸)；31、轴承内圈；32、轴承外圈；321、外圈油槽；321a、轴向油孔；321b、径向油孔；33、滚动体；4、下法兰；41、下油槽；42、下储油槽；5、叶片；6、下盖板；7、齿轮油泵；8、垫片；81、导油孔。
具体实施方式
如图1所示，本发明提供一种一种压缩机的油路结构，其包括：
主轴1、上法兰2和滚动轴承3，所述滚动轴承3(气缸)内部围成用于进行压缩的气缸腔，所述滚动轴承3包括滚动体33；
其中所述主轴1内部设置有主轴油孔10，所述上法兰2上设置有上油槽20，所述上油槽20与所述主轴油孔10连通且能将油导入所述滚动体33中以对其进行润滑。
通过在上法兰上设置有上油槽，所述上油槽与所述主轴油孔连通且能将油导入所述滚动体中以对其进行润滑，能够有效地将压缩机主轴油孔中的油通过上法兰导入到滚动轴承的滚动体部位、对其进行润滑降温，使得滚动体摩擦产生的热量得以及时地被排出，防止轴承温度升高，并且降低磨损，从而提高压缩机的能效值，保证压缩机的正常运行；
还能够利用重力将油从上往下地导入到滚动轴承的滚动体中，保证了滚动轴承中润滑油的充足，保证压缩机的正常运行。
如图2-4，优选地，所述上油槽20包括：
直油槽20a，与所述主轴油孔10连通；
轴承滚动体进油孔20c，与所述滚动体33相连通；
轴承润滑进油通道20b，其一端与所述直油槽20a连通、另一端与所述轴承滚动体进油孔20c连通。
这是本发明的上法兰上开设的上油槽的具体结构形式，通过直油槽能够从主轴油孔中引入润滑油、进一步通过轴承润滑进油通道对其进行引导、最终导致轴承滚动体进油孔中，再将油输送至滚动轴承的滚动体的位置，完成对轴承滚动体润滑的作用和效果。
图1为压缩机泵体的基本结构，油路情况具体如图2。齿轮油泵随着主轴转动，把油池中的油强制提供到主轴中心孔。主轴上端封闭，下端开孔，当润 滑油从中心孔进入后到达上法兰高度处，受油压作用将流向主轴径向油孔，再流向主轴退刀槽和上法兰直油槽形成的一小储油空间(如局部放大图图3所示)。
因压缩机工作时，油会源源不断吸入，因此当该小储油空间充满后，润滑油则会进入到上法兰直油槽，经过径向轴承润滑进油通道，再到轴承滚动体进油孔，具体如图4所示。因上法兰不随主轴转动，而滚动轴承的滚动体会随着主轴转动且还能自转，油便会在上法兰开设的进油孔在该固定位置持续地为滚动体供油，这样就能对每个滚动体起到润滑的效果。
优选地，所述直油槽20a开设于所述上法兰2的径向内侧、且沿着所述上法兰2的轴向延伸，所述轴承润滑进油通道20b沿着所述上法兰2的径向方向延伸，所述轴承滚动体进油孔20c沿着所述上法兰2的轴向方向延伸。这是本发明的直油槽20a、轴承润滑进油通道20b和轴承滚动体进油孔20c的进一步的结构形式，能够完成对润滑油从主轴油孔至滚动轴承的滚动体的输油和导油的作用，尤其地、轴承滚动体进油孔沿着上法兰轴向延伸，能够将润滑油从上而下竖直方向地输送至滚动体，从而有效地利用了重力的作用，减小了泵送油流动的动力，提高了润滑油的输送效率。
如图4-7，优选地，在所述上法兰2的横截面上，所述直油槽20a为环形油槽或弧形油槽。这是本发明的直油槽的优选结构形式，将其设置为环形油槽或弧形油槽是根据主轴的柱体形状而相应地设置的，能够从主轴的多处周向位置引入润滑油，并且开设环形油槽能够将多个轴承润滑进油通道与该一个环形油槽连通，使得结构更为简单和实用。
优选地，所述轴承润滑进油通道20b为两个以上、沿着所述上法兰2的周向进行分布；
每个所述轴承润滑进油通道20b均连接一个所述轴承滚动体进油孔20c，两个以上所述轴承润滑进油通道20b均与一个所述直油槽20a相连通、或者每个所述轴承润滑进油通道20b连接一个所述直油槽20a。
这是本发明的轴承润滑进油通道的优选手段，将该轴承润滑进油通道设置为两个以上，能够沿上法兰的不同周向方向沿径向进行导油和输油，从而提高输油的流量，增大输送油量，提高对轴承滚动体的润滑冷却的效果，提高压缩机的运行可靠性和稳定性，且可以使得压缩机可以运行得更加的高频、转速更高。
实施例2
本实施例是在实施例1的基础上做出的进一步改进，如图6-7，优选地，还包括设置在所述上法兰2上的上储油槽21，所述上储油槽21与所述轴承滚动体进油孔20c相连通、同时还与所述轴承润滑进油通道20b相连通。通过在上述位置设置的上储油槽能够对经过轴承润滑进油通道中的油在进入轴承滚动体进油孔之前进入到上储油槽中进行储存，从而在油量过多的时候实现储油的作用、在油量过少的情况下可以通过该储油槽进行释放润滑油，保证滚动轴承良好的润滑降温作用，提升压缩机的性能。
优选地，所述上储油槽21位于所述轴承滚动体进油孔20c的轴向上方、且沿着所述上法兰2的周向方向延伸。这样能够对即将进入轴承滚动体进油孔中的油改变方向而进入上储油槽中完成储油的作用。所述上储油槽为直段槽，如图6所示，也可以为弧形段槽，如图7所示，图7中的上储油槽的横截面积明显大于图6。
实施例3
如图15-16，本实施例是在实施例1和/或2的基础上做出的进一步改进，优选地，在所述上法兰2和所述滚动轴承3之间还设置有垫片8，所述垫片8上沿主轴轴向开设有多个导油孔81，多个所述导油孔81沿主轴周向排布、且能将所述轴承滚动体进油孔20c与所述滚动体33进行连通。在没有添加垫片之前，润滑油通过上法兰轴承滚动体进油孔20c直接进入到轴承腔滚动体33，原理上是从一点供油到整个轴承腔，这样供油的位置比较固定，虽然内圈是旋转的，但是对于整个轴承腔内来说，油温的温差较大。增加垫片以后，可以实现整个轴承腔360°范围内的供油，并且根据需要可以设置不同的孔径，实现滚动体的润滑；垫片后可以使滚动体的润滑和冷却更加充分；另外，该垫片可以改善滚动轴承内圈与上法兰端面的磨损情况。
优选地，多个所述导油孔81中，至少两个所述导油孔81的孔径大小不同，且靠近所述滚动轴承3排气孔的导油孔81的孔径大于靠近所述滚动轴承3吸气孔的导油孔81的孔径。在垫片上主要开设有不同直径的导油孔81，导油孔的大小根据润滑的需要进行设置，在排气侧(排气孔)附近，滚动体由于内圈压差作用所承受的压力最大，就需要更多的润滑油，所以此处的油孔直径就要设计的大一点，而正对上法兰轴承滚动体进油孔20c的导油孔，由于处在压缩 机的吸气侧，并没有受很大的力，所以此处需要的油量就小一些，油孔的直径设计的就要小一些。优选包括三种孔径大小的导油孔：
Figure PCTCN2017118247-appb-000001
实施例4
本实施例是在实施例1-3的基础上做出的进一步改进，优选地，还包括下法兰4，在所述下法兰4上还开设有能与所述滚动体连通的下油槽41，经由所述下油槽41能将油从所述下法兰4导出、或者将油从所述滚动轴承3导出。通过在下法兰上设置的下油槽能够对油进行输送和导流，将润滑油排出至压缩机的壳体中，实现了油的回收利用和循环利用。
然后，润滑油经过滚动体后，因自身重力和油压作用则会往下法兰流，集中流向下法兰的下油槽(如图8所示)，该下油槽直接通向泵体之外，油便会随着端面出油槽流出至壳体油池中去。
此滚动轴承润滑油路方案连通了主轴、上法兰、滚动轴承和下法兰，不仅使得润滑油在壳体油池能循环使用，而且还保证了滚动轴承的滚动体得到充分润滑，同时也能及时带走在此过程中因摩擦产生的热量。通过这样的一种油路方式，实现了滚动轴承充分润滑的效果，减少压缩机运行时泵体的磨损，增加其运行的可靠性。
优选地，所述下油槽41位于所述滚动体33的轴向下方、且沿径向延伸至所述下法兰4的周向端面，在所述周向端面将油导出。这样能够通过下油槽直接将油导流至下法兰的周向端面，完成将油排出压缩机泵体外、至压缩机壳体底部油池的目的和作用。
优选地，所述下油槽41为两个以上、在所述下法兰4的不同周向位置进行分布。这是下油槽的扩展形式，通过两个以上的下油槽能够增大润滑油的排油量，加快润滑油的循环速度，提高对轴承的冷却润滑速率。
如图10，优选地，还包括设置在所述下法兰4上的下储油槽42，所述下储油槽42与所述下油槽41相连通。通过在上述位置设置的下储油槽能够对进入下油槽41之前进入到下储油槽中进行储存，从而在油量过多的时候实现储油的作用、在油量过少的情况下可以通过该储油槽进行释放润滑油，保证滚动轴承良好的润滑降温作用，提升压缩机的性能。
优选地，所述下储油槽42为围绕所述主轴1周向环绕的环形结构。这是本发明的下储油槽的优选形状，能够最大程度地增大储油的能力。
参见图11-15，优选地，所述滚动轴承3还包括轴承内圈31和轴承外圈32，所述轴承外圈32上设置有外圈油槽321，所述下油槽41能同时连通所述滚动体33和所述外圈油槽321，通过所述外圈油槽321能将油从轴承外圈32排出。下油槽41与外圈油槽轴向相对的位置流通面积扩大，能够用于储油。
通过在轴承外圈上设置外圈油槽，能够将下法兰上下油槽流过来的油进行导向和输送至外圈外部，从而实现将润滑油排出的作用，这是相对于在下法兰上将油排出的方案而言的替换方式。
如图5所示，对比图4，上法兰径向轴承润滑进油通道和进油孔的位置(不同角度的开设位置)、径向轴承润滑进油通道数量20b、轴承滚动体进油孔20c均可调整；另外上法兰端面结构也可增加不同长度的环形储油槽用于储油，如图6、7所示，
如图9所示，对比图8，下法兰端面出油槽位置(不同角度开设槽)、数量(1个、2个或多个)均可以调整；
出油位置可从下法兰端面出油孔提高至滚动轴承侧孔处，来代替下法兰下油槽。具体油路如图10所示，滚动体区域的润滑油流至下法兰端面储油槽(如图11所示)内，该槽和滚动轴承的上下端面通孔(如图12)连通，润滑油便流向该通孔，之后从滚动轴承径向油孔321b(一个或多个)流出至壳体油池内。另外，如图13所示，滚动轴承的侧孔可以在不同高度位置开设，也可开设一个或多个。
优选地，所述外圈油槽321包括沿所述轴承外圈32轴向延伸的轴向油孔321a和沿外圈径向延伸的至少一个径向油孔321b，所述轴向油孔321a与所述下油槽41连通、且所述径向油孔321b与所述轴向油孔321a连通，能通过所述径向油孔321b将油从所述轴承外圈32的周面排出。这是本发明的轴承外圈上开设的外圈油槽的具体结构形式，通过轴向油孔将下油槽中的油沿轴向吸入，并导至径向油孔中，并通过径向油孔从轴承外圈外周面排出，实现润滑油排出的作用和目的。
优选地，所述下油槽41沿所述下法兰4的径向延伸；
和/或，所述径向油孔321b为多个，多个所述径向油孔321b平行设置、均沿所述轴承外圈32的径向方向延伸。
这是本发明的油路结构中下油槽的优选延伸方向，以及径向油孔的多个设 置方式，能够从下法兰上径向地导油，从轴承外圈上径向地排油。
优选地，所述主轴油孔10包括在其径向外侧、沿径向方向开设的主轴径向油孔13。通过主轴径向油孔能够将主轴油孔中的油沿径向方向导入至上油槽20中，实现润滑油的导油和输出的作用。
本发明提供一种压缩机用滚动轴承润滑的新型结构，根据压缩机泵油特点，通过在上法兰、下法兰和滚动轴承开设不同的油孔和上油槽，使滚动轴承与上下法兰油路贯通，实现滚动轴承充分润滑的效果，减少压缩机运行时泵体的磨损，增加其运行的可靠性。另外此润滑方式具有结构简单、加工简便等优点。保证压缩机泵体轴承的润滑程度，有效解决滚动轴承的磨损及发热问题，提高压缩机的可靠性及能效。
通过在上法兰内部开设不同的孔与槽，使之与泵体主轴的出油孔和滚动轴承的滚动体上间隙区域相通，并在下法兰开槽与滚动体下间隙区域相通，使得四部分油路连通(滚动体在外圈和内圈之间，其高度小于轴承高度，因此和上下端面均存在一个间隙，滚动体与轴承上端面的间隙为滚动体上间隙区域，滚动体与轴承下端面的间隙为滚动体下间隙区域)，如此可保证滚动轴承的滚动体部分有润滑油流过，不仅润滑了滚动轴承，而且可及时带走因滚动摩擦产生的热量，降低压缩机运行功耗，从而提高压缩机自身的能效。
本发明还提供一种压缩机，其包括前述的压缩机油路结构。通过在上法兰上设置有上油槽，所述上油槽与所述主轴油孔连通且能将油导入所述滚动体中以对其进行润滑，能够有效地将压缩机主轴油孔中的油通过上法兰导入到滚动轴承的滚动体部位、对其进行润滑降温，使得滚动体摩擦产生的热量得以及时地被排出，防止轴承温度升高，并且降低磨损，从而提高压缩机的能效值，保证压缩机的正常运行；
还能够利用重力将油从上往下地导入到滚动轴承的滚动体中，保证了滚动轴承中润滑油的充足，保证压缩机的正常运行。
优选地，所述压缩机为旋叶式压缩机。这是本发明的压缩机的优选结构形式。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。以上所述仅是本发明的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本发明的保护范围。

Claims (21)

  1. 一种压缩机的油路结构，其特征在于：包括：
    主轴(1)、上法兰(2)和滚动轴承(3)，所述滚动轴承(3)内部围成用于进行压缩的气缸腔，所述滚动轴承(3)包括滚动体(33)；
    其中所述主轴(1)内部设置有主轴油孔(10)，所述上法兰(2)上设置有上油槽(20)，所述上油槽(20)与所述主轴油孔(10)连通以能将油导入所述滚动体(33)中以对其进行润滑。
  2. 根据权利要求1所述的油路结构，其特征在于：所述上油槽(20)包括：
    直油槽(20a)，与所述主轴油孔(10)连通；
    轴承滚动体进油孔(20c)，与所述滚动体(33)相连通；
    轴承润滑进油通道(20b)，其一端与所述直油槽(20a)连通、另一端与所述轴承滚动体进油孔(20c)连通。
  3. 根据权利要求2所述的油路结构，其特征在于：所述直油槽(20a)开设于所述上法兰(2)的径向内侧、沿着所述上法兰(2)的轴向延伸，所述轴承润滑进油通道(20b)沿着所述上法兰(2)的径向方向延伸，所述轴承滚动体进油孔(20c)沿着所述上法兰(2)的轴向方向延伸。
  4. 根据权利要求3所述的油路结构，其特征在于：在所述上法兰(2)的横截面上，所述直油槽(20a)为环形油槽或弧形油槽。
  5. 根据权利要求2-4中任一项所述的油路结构，其特征在于：所述轴承润滑进油通道(20b)为两个以上、沿着所述上法兰(2)的周向进行分布；
    每个所述轴承润滑进油通道(20b)均连接有一个所述轴承滚动体进油孔(20c)，两个以上所述轴承润滑进油通道(20b)均与一个所述直油槽(20a)相连通、或者每个所述轴承润滑进油通道(20b)连接一个所述直油槽(20a)。
  6. 根据权利要求2-5中任一项所述的油路结构，其特征在于：还包括设置在所述上法兰(2)上的上储油槽(21)，所述上储油槽(21)与所述轴承滚动体进油孔(20c)相连通、同时还与所述轴承润滑进油通道(20b)相连通。
  7. 根据权利要求6所述的油路结构，其特征在于：所述上储油槽(21)位于所述轴承滚动体进油孔(20c)的轴向上方、且沿着所述上法兰(2)的周向方向延伸。
  8. 根据权利要求2-7中任一项所述的油路结构，其特征在于：在所述上法兰(2)和所述滚动轴承(3)之间还设置有垫片(8)，所述垫片上沿主轴轴向开设有多个导油孔(81)，多个所述导油孔(81)沿主轴周向排布、且能将所述轴承滚动体进油孔(20c)与所述滚动体(33)进行连通。
  9. 根据权利要求8所述的油路结构，其特征在于：多个所述导油孔(81)中，至少两个所述导油孔(81)的孔径大小不同，且靠近所述滚动轴承(3)排气孔的导油孔(81)的孔径大于靠近所述滚动轴承(3)吸气孔的导油孔(81)的孔径。
  10. 根据权利要求1-9中任一项所述的油路结构，其特征在于：还包括下法兰(4)，在所述下法兰(4)上还开设有能与所述滚动体(33)连通的下油槽(41)，经由所述下油槽(41)能将油从所述下法兰(4)导出、或者将油从所述滚动轴承(3)导出。
  11. 根据权利要求10所述的油路结构，其特征在于：所述下油槽(41)位于所述滚动体(33)的轴向下方，且所述下油槽(41)沿径向延伸至所述下法兰(4)的周向端面，在所述周向端面将油导出。
  12. 根据权利要求11所述的油路结构，其特征在于：所述下油槽(41)为两个以上、两个以上的所述下油槽(41)在所述下法兰(4)的不同周向位置进行分布。
  13. 根据权利要求10-12中任一项所述的油路结构，其特征在于：还包括设置在所述下法兰(4)上的下储油槽(42)，所述下储油槽(42)与所述下油槽(41)相连通。
  14. 根据权利要求13所述的油路结构，其特征在于：所述下储油槽(42)为围绕所述主轴(1)周向环绕的环形结构。
  15. 根据权利要求10所述的油路结构，其特征在于：所述滚动轴承(3)还包括轴承内圈(31)和轴承外圈(32)，所述轴承外圈(32)上设置有外圈油槽(321)，所述下油槽(41)能同时连通所述滚动体(33)和所述外圈油槽(321)，通过所述外圈油槽(321)能将油从轴承外圈(32)排出。
  16. 根据权利要求15所述的油路结构，其特征在于：所述外圈油槽(321)包括沿所述轴承外圈(32)轴向延伸的轴向油孔(321a)和沿外圈径向延伸的至少一个径向油孔(321b)，所述轴向油孔(321a)与所述下油槽(41)连通、 且所述径向油孔(321b)与所述轴向油孔(321a)连通，能通过所述径向油孔(321b)将油从所述轴承外圈(32)的周面排出。
  17. 根据权利要求16所述的油路结构，其特征在于：所述下油槽(41)沿所述下法兰(4)的径向延伸；
    和/或，所述径向油孔(321b)为多个，多个所述径向油孔(321b)平行设置、均沿所述轴承外圈(32)的径向方向延伸。
  18. 根据权利要求1-17中任一项所述的油路结构，其特征在于：所述主轴油孔(10)包括在所述主轴(1)内部、沿径向方向开设的主轴径向油孔(13)。
  19. 一种压缩机，其特征在于：包括权利要求1-18中任一项所述的压缩机油路结构。
  20. 根据权利要求19所述的压缩机，其特征在于：所述压缩机为旋叶式压缩机。
  21. 一种空调器，其特征在于：包括权利要求1-18中任一项所述的压缩机油路结构。
PCT/CN2017/118247 2017-09-29 2017-12-25 一种压缩机的油路结构和压缩机 WO2019061892A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US16/617,033 US11248609B2 (en) 2017-09-29 2017-12-25 Oil line structure of compressor and compressor
EP17926432.0A EP3690248B1 (en) 2017-09-29 2017-12-25 Oil line structure of compressor and compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201710907160.8 2017-09-29
CN201710907160.8A CN107701447B (zh) 2017-09-29 2017-09-29 一种压缩机的油路结构和压缩机

Publications (1)

Publication Number Publication Date
WO2019061892A1 true WO2019061892A1 (zh) 2019-04-04

Family

ID=61175556

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2017/118247 WO2019061892A1 (zh) 2017-09-29 2017-12-25 一种压缩机的油路结构和压缩机

Country Status (4)

Country Link
US (1) US11248609B2 (zh)
EP (1) EP3690248B1 (zh)
CN (1) CN107701447B (zh)
WO (1) WO2019061892A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108843570B (zh) * 2018-08-17 2023-08-25 珠海格力电器股份有限公司 压缩机和具有其的空调器
CN109026715B (zh) * 2018-08-21 2024-02-27 珠海格力节能环保制冷技术研究中心有限公司 泵体及具有其的压缩机
CN108825663B (zh) * 2018-08-21 2023-10-24 珠海格力电器股份有限公司 泵体及具有其的压缩机
CN109737065B (zh) 2019-02-27 2024-04-16 珠海格力电器股份有限公司 泵体组件、压缩机及空调设备
CN113790157A (zh) * 2021-10-22 2021-12-14 珠海格力电器股份有限公司 轴承气缸、压缩机和空调器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000337281A (ja) * 1999-03-24 2000-12-05 Seiko Seiki Co Ltd 気体圧縮機
CN101265893A (zh) * 2008-02-04 2008-09-17 加西贝拉压缩机有限公司 一种往复活塞式密封压缩机
KR20100076562A (ko) 2008-12-26 2010-07-06 엘지이노텍 주식회사 아이피티브이용 튜너 모듈 및 그의 구동방법
EP2520802A1 (en) * 2009-12-29 2012-11-07 Valeo Japan Co., Ltd. Lubricating oil supply structure of vane-type compressor
CN203404081U (zh) * 2013-07-17 2014-01-22 广东美芝制冷设备有限公司 旋转式压缩机及具有其的制冷系统
CN204572458U (zh) * 2015-01-15 2015-08-19 珠海格力节能环保制冷技术研究中心有限公司 泵体及转缸压缩机
CN105952642A (zh) * 2016-06-15 2016-09-21 珠海格力节能环保制冷技术研究中心有限公司 气缸轴承润滑结构及滑片式压缩机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2737341A (en) * 1950-02-25 1956-03-06 Trico Products Corp Rotary pump
KR101159455B1 (ko) 2010-08-09 2012-06-25 아스펜 컴프레서 엘엘씨. 회전저항을 감소시킨 소형 로터리 베인 압축기
CN204239241U (zh) * 2014-11-07 2015-04-01 广东美芝制冷设备有限公司 旋转式压缩机及其泵组件
CN105987004B (zh) * 2015-01-28 2018-02-06 珠海格力节能环保制冷技术研究中心有限公司 滑片式压缩机及其排气结构
CN106481555B (zh) 2015-08-25 2018-09-07 珠海格力节能环保制冷技术研究中心有限公司 一种卧式压缩机及调温设备
CN205677829U (zh) 2016-06-15 2016-11-09 珠海格力节能环保制冷技术研究中心有限公司 气缸轴承润滑结构及滑片式压缩机
CN207363876U (zh) * 2017-09-29 2018-05-15 珠海格力电器股份有限公司 一种压缩机的油路结构和压缩机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000337281A (ja) * 1999-03-24 2000-12-05 Seiko Seiki Co Ltd 気体圧縮機
CN101265893A (zh) * 2008-02-04 2008-09-17 加西贝拉压缩机有限公司 一种往复活塞式密封压缩机
KR20100076562A (ko) 2008-12-26 2010-07-06 엘지이노텍 주식회사 아이피티브이용 튜너 모듈 및 그의 구동방법
EP2520802A1 (en) * 2009-12-29 2012-11-07 Valeo Japan Co., Ltd. Lubricating oil supply structure of vane-type compressor
CN203404081U (zh) * 2013-07-17 2014-01-22 广东美芝制冷设备有限公司 旋转式压缩机及具有其的制冷系统
CN204572458U (zh) * 2015-01-15 2015-08-19 珠海格力节能环保制冷技术研究中心有限公司 泵体及转缸压缩机
CN105952642A (zh) * 2016-06-15 2016-09-21 珠海格力节能环保制冷技术研究中心有限公司 气缸轴承润滑结构及滑片式压缩机

Also Published As

Publication number Publication date
CN107701447A (zh) 2018-02-16
EP3690248B1 (en) 2021-09-08
EP3690248A1 (en) 2020-08-05
CN107701447B (zh) 2019-08-06
EP3690248A4 (en) 2020-10-14
US11248609B2 (en) 2022-02-15
US20210131437A1 (en) 2021-05-06

Similar Documents

Publication Publication Date Title
WO2019061892A1 (zh) 一种压缩机的油路结构和压缩机
CN104797822B (zh) 具有油冷却马达的涡旋压缩机
CN105952642B (zh) 气缸轴承润滑结构及滑片式压缩机
CN207363876U (zh) 一种压缩机的油路结构和压缩机
CN106715864A (zh) 增压机
TW201128147A (en) Oil free lubrication centrifugal refrigerant compressor and lubrication method thereof
CN209990681U (zh) 一种皮托管泵轴承润滑系统
CN104421214A (zh) 一种高温泵轴承冷却装置
CN205677829U (zh) 气缸轴承润滑结构及滑片式压缩机
CN207647779U (zh) 压缩机及具有其的空调系统
WO2016067715A1 (ja) 過給機およびこれを備えたエンジン
CN112412799A (zh) 一种曲轴、压缩机、压缩机的供油方法以及电器
US3804202A (en) Compressor lubrication system
CN208996942U (zh) 涡旋压缩机
CN104074793B (zh) 离心泵的双润滑式止推轴承装置
CN211343689U (zh) 一种提升可靠性的压缩机曲轴
CN104696227B (zh) 旋转式压缩机
CN216894808U (zh) 轴承冷却结构及轴承及压缩机及制冷设备
CN206908435U (zh) 一种带凸台的电机轴承
CN217712951U (zh) 压缩机的曲轴及压缩机
CN112483358B (zh) 回油结构、压缩机和冰箱
CN216477857U (zh) 润滑轴承、压缩机及空调器
CN117212172A (zh) 一种压缩机油路结构、压缩机
CN216241282U (zh) 一种全封涡旋压缩机
US11885335B2 (en) Oil supply mechanism of rotating machinery and rotating machinery having oil supply mechanism

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17926432

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2017926432

Country of ref document: EP

Effective date: 20200429