WO2022001033A1 - 法兰及具有其的泵体组件 - Google Patents

法兰及具有其的泵体组件 Download PDF

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Publication number
WO2022001033A1
WO2022001033A1 PCT/CN2020/139110 CN2020139110W WO2022001033A1 WO 2022001033 A1 WO2022001033 A1 WO 2022001033A1 CN 2020139110 W CN2020139110 W CN 2020139110W WO 2022001033 A1 WO2022001033 A1 WO 2022001033A1
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WO
WIPO (PCT)
Prior art keywords
back pressure
flange
shaft hole
pressure groove
sliding vane
Prior art date
Application number
PCT/CN2020/139110
Other languages
English (en)
French (fr)
Inventor
董明珠
胡余生
魏会军
徐嘉
任丽萍
万鹏凯
Original Assignee
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 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to EP20942831.7A priority Critical patent/EP4098878A4/en
Priority to JP2022552521A priority patent/JP2023530803A/ja
Priority to US17/908,383 priority patent/US20230332600A1/en
Priority to KR1020227030425A priority patent/KR20230026298A/ko
Publication of WO2022001033A1 publication Critical patent/WO2022001033A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C18/3441—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 one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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 one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2240/10—Stators
    • 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
    • F04C2240/20—Rotors
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/60—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/60—Shafts

Definitions

  • the present disclosure relates to the technical field of pump body equipment, and in particular, to a flange and a pump body assembly having the same.
  • the sliding vane compressor Compared with other types of compressors, the sliding vane compressor has the advantages of simple parts, no eccentric structure, stable torque, and low vibration. Withstanding the inner wall of the cylinder to form a seal, the stable and reliable back pressure of the sliding vane is an important factor affecting the quality of the sliding vane machine.
  • a back pressure cavity is generally set at the tail of the sliding vane (the sliding vane tail cavity formed by the sliding vane and the main shaft sliding vane groove, the upper flange Back pressure groove, lower flange back pressure groove), and the introduction of high-pressure oil from the oil pool to provide power for the back of the sliding vane, which is used to overcome the gas pressure in the front and rear chambers of the sliding vane head and the frictional force on the side of the sliding vane groove, etc., to realize the entire operation.
  • the vane head is always in contact with the inside of the cylinder.
  • the oil under the back pressure of the sliding vane is mainly pumped from the oil pool by the gear oil pump, and then enters the flange back pressure groove through the central hole of the main shaft and the main shaft side hole connected to the central hole of the main shaft, and then fills the back pressure cavity.
  • the oil coming out of the side hole of the main shaft needs to pass through a certain gap to enter, as shown in Figure 1.
  • the sliding vane reciprocates in the sliding vane groove, and the speed changes periodically.
  • the volume of the tail cavity of the sliding vane increases rapidly, and it is difficult to replenish the back pressure oil in time.
  • the back pressure of the sliding vane will drop, resulting in insufficient back pressure of the sliding vane.
  • the head is detached from the inner wall of the cylinder, resulting in leakage, which affects the performance of the compressor.
  • a flange comprising: a flange body, a shaft hole is formed on the flange body, a back pressure groove is provided on one side of the shaft hole, and a side of the back pressure groove close to the shaft hole is provided A communication part is opened on the side wall of the back pressure groove, and the communication part communicates the back pressure groove with the shaft hole;
  • the communicating portion includes a notch provided on the sidewall of the back pressure groove, and/or the communicating portion includes a through hole structure provided on the sidewall.
  • the communicating portion includes a first notch, a side wall of the back pressure groove close to the shaft hole has a first position, and a first notch is opened at the first position, and both ends of the first notch are connected to the shaft hole.
  • the included angle formed by the connection line between the hole centers is ⁇ 1, where A-50° ⁇ 1 ⁇ A+50°, A is the speed at which the slider starts to extend from the slider slot from the first initial position until the slider The angle of rotation when the maximum is reached.
  • the communicating portion further includes a second notch, the second notch is spaced apart from the first notch, a side wall of the back pressure groove on the side close to the shaft hole has a second position, and a first notch is opened at the second position.
  • the communicating portion is configured in an arc shape, and an included angle formed by a line between two ends of the communicating portion and the center of the shaft hole is ⁇ , where A-50° ⁇ B+50°, or, A-30° ⁇ B+30°, A is the angle that the slider rotates from the beginning of the slider slot until the speed of the slider reaches the maximum; B is the sliding blade from the beginning to retract and slide The angle at which the slot turns until the speed of the slide reaches maximum.
  • the communicating portion is a notch formed on the side wall of the back pressure groove, the height difference between the notch and the flange plane is H1, the depth of the back pressure groove is H2, and the thickness of the flange body is H,
  • the ratio of H2 to H ranges from 0.1 to 0.6
  • the ratio of H1 to H2 ranges from 0.1 to 1.
  • H1 > 1 mm.
  • a pump body assembly including the flanges in the above embodiments.
  • the pump body assembly further includes: a cylinder, the flange body is located on one side of the cylinder; and a main shaft, the main shaft has a central part, the central part is provided with at least one sliding vane groove, and each sliding vane groove is provided with a sliding plate groove
  • the main shaft is penetrated in the shaft hole, and the central part is located in the cylinder, and the main shaft drives the sliding plate to rotate to perform the compression operation in the cylinder.
  • the lubricating oil can be input into the back pressure groove in time through the communication part, avoiding the use of the related art.
  • the flange of this structure enables the lubricating oil to enter the back pressure groove smoothly, and can provide stable and reliable oil pressure at the tail of the sliding vane at all angles of the sliding vane extending, even at the maximum extending and retracting speeds Stable operation can also be maintained, which effectively improves the stability and reliability of the pump body assembly with the flange.
  • FIG. 1 shows a schematic diagram of lubricating oil supplying oil through the gap between the flange and the main shaft in the related art
  • FIG. 2 shows a schematic structural diagram of the first embodiment of the flange according to the present disclosure
  • Fig. 3 shows the sectional structure schematic diagram of the A-A direction in Fig. 2;
  • FIG. 4 shows a schematic structural diagram of a second embodiment of the flange according to the present disclosure
  • FIG. 5 shows a schematic structural diagram of a third embodiment of the flange according to the present disclosure
  • FIG. 6 shows a schematic structural diagram of a fourth embodiment of the flange according to the present disclosure
  • Fig. 7 shows the sectional structure schematic diagram of the direction B-B in Fig. 6;
  • FIG. 8 shows a schematic structural diagram of a fifth embodiment of the flange according to the present disclosure.
  • FIG. 9 is a schematic diagram showing the comparison of the pressure in the back pressure groove formed on the flange provided according to some embodiments of the present disclosure and the flange in the related art;
  • FIG. 10 shows a schematic structural diagram of a pump body assembly provided according to some embodiments of the present disclosure
  • FIG. 11 is a schematic diagram illustrating the relationship between the moving speed of the slider and the rotation angle according to some embodiments of the present disclosure.
  • Some embodiments of the present disclosure provide a flange and a pump body assembly having the same, so as to alleviate the problem of poor oil supply to the sliding vane back pressure chamber in the related art.
  • a flange is provided.
  • the flange includes a flange body 10 .
  • the flange body 10 is provided with a shaft hole 11, one side of the shaft hole 11 is provided with a back pressure groove 12 around the shaft hole 11, and a communication part 13 is opened on the side wall of the back pressure groove 12 on the side close to the shaft hole 11.
  • the communication part 13 communicates the back pressure groove 12 with the shaft hole 11 , and the communication portion 13 is configured to supply or drain lubricating oil to the back pressure groove 12 .
  • the lubricating oil can be input into the back pressure groove 12 in time through the communication portion 13, avoiding the need of using
  • the flange of this structure enables the lubricating oil to enter the back pressure groove 12 smoothly, and can provide stable and reliable oil pressure at the tail of the sliding vane at all angles of the sliding vane extending, even when the sliding vane is extended and retracted at its maximum. It can also maintain stable operation at high speed, which effectively improves the stability and reliability of the pump body assembly with the flange.
  • the communicating portion 13 may be a notch formed on the side wall of the back pressure groove 12 .
  • the communicating portion 13 may also be a through hole formed on the side wall.
  • a notch and a through hole may also be formed on the side wall of the back pressure groove 12 as required.
  • the communicating portion 13 is a notch formed on the side wall of the back pressure groove 12 . This setting is convenient for processing.
  • a plurality of communicating portions 13 may be provided, and the plurality of communicating portions 13 are provided at intervals along the circumferential direction of the shaft hole 11 .
  • the position of the corresponding communication part can be set according to the movement state of the sliding vane, so that the sliding vane is always in a stable compression state under the action of the back pressure groove during the compression operation of the entire pump body assembly, which improves the The reliability of the pump body assembly with this flange.
  • the communicating portion 13 is a notch structure opened on the side wall, and the number of the notch is one.
  • the communicating portion 13 includes a first notch 131 , a side wall of the back pressure groove 12 on the side close to the shaft hole 11 has a first position, and a first notch 131 is opened at the first position.
  • the included angle formed by the connecting line between the two ends of the notch 131 and the center of the shaft hole 11 is ⁇ 1, where A-50° ⁇ 1 ⁇ A+50°, A is the sliding vane from the first initial position (ie When the working chamber of the sliding vane starts to inhale), the sliding vane starts to extend from the sliding vane groove until the speed of the sliding vane reaches the maximum, and the angle with which the main shaft of the pump body assembly rotates.
  • the speed can be obtained by mathematical calculation according to the dimensions of the rotating shaft, the sliding vane, the cylinder, etc. As shown in Figure 11, when the sliding vane extends along the sliding vane groove at the maximum speed, the rotation angle is 105°. Wherein, the moving speed of the sliding vane in FIG. 11 includes the speed at which the sliding vane extends out of the sliding vane slot and the speed at which the sliding vane retracts from the sliding vane slot.
  • the communicating portion 13 further includes a second notch 132 , which is arranged at an interval from the first notch 131 , a side wall of the back pressure groove 12 on the side close to the shaft hole 11 has a second position, and a second position is opened at the second position.
  • Two notches 132 the included angle formed by the connecting line between the two ends of the second notches 132 and the center of the shaft hole 11 is ⁇ 2, where B-50° ⁇ 2 ⁇ B+50°, B is the sliding plate from the first
  • the second initial position that is, within one suction compression cycle of the working chamber, the sliding vane extends from the beginning, and the sliding vane will gradually retreat into the sliding vane slot after the preset value is extended, and the second initial position is that the sliding vane starts to realize the retraction sliding movement.
  • the sliding vane is retracted from the sliding vane groove until the speed of the sliding vane retracting reaches the maximum, it will follow the rotation angle of the main shaft of the pump body assembly.
  • the sliding vane will return to the sliding vane groove and reach the maximum speed according to the The dimensions of the shaft, vane, cylinder, etc. are obtained by mathematical calculation.
  • This setting makes it possible to provide stable and reliable oil pressure at the tail of the sliding vane at all angles of the sliding vane, even when the sliding vane extends out of the sliding vane groove to the maximum speed, and the sliding vane retracts into the sliding vane groove to the maximum speed can also maintain stable operation.
  • the communicating portion 13 is arranged in an arc shape around the shaft hole 11 , and the included angle formed by the connection line between the two ends of the communicating portion 13 and the center of the shaft hole 11 is ⁇ , where A-50° ⁇ ⁇ B+50°, or, A-30° ⁇ B+30°.
  • the communicating portion 13 is a notch structure, and the angle between the two ends of the notch and the hole center of the shaft hole 11 is ⁇ , A-50° ⁇ B+50°, or, A -30° ⁇ B+30°.
  • A is the angle that the sliding vane rotates with the main shaft of the pump body assembly from the beginning of the sliding vane out of the sliding vane groove until the speed of the sliding vane reaches the maximum;
  • B is the sliding vane from the beginning to retract the sliding vane groove until the speed of the sliding vane reaches the maximum, with The angle of rotation of the main shaft of the pump body assembly.
  • the communicating portion 13 is a notch formed on the side wall of the back pressure groove 12 , the height difference between the notch and the flange plane is H1, the depth of the back pressure groove 12 is H2, and the The thickness is H, wherein the ratio of H2 to H ranges from 0.1 to 0.6, the ratio of H1 to H2 ranges from 0.1 to 1, and H1 ⁇ 1mm.
  • This setting can ensure the timeliness of oil supply and oil discharge of the back pressure, and at the same time reduce the resistance to the flow of lubricating oil at the gap.
  • a flange can be used for a pump body equipment assembly, that is, according to another aspect of some embodiments of the present disclosure, a pump body assembly is provided, including a flange, and the flange is the flange in the above-mentioned embodiments .
  • the pump body assembly includes a cylinder 20 and a main shaft 30 .
  • the flange body 10 is located on one side of the cylinder 20 .
  • the main shaft 30 has a central portion 31 , at least one sliding vane groove is formed on the central portion 31 , each sliding vane groove is provided with a sliding vane 40 , the main shaft 30 is inserted into the shaft hole 11 , and the central portion 31 is located in the cylinder 20 , the main shaft 30 is located in the cylinder 20 .
  • 30 drives the sliding vane 40 to rotate to perform the compression operation in the cylinder 20 .
  • a back pressure cavity is formed at the back pressure groove 12 on the flange body 10 .
  • the central portion 31 is provided with three sliding vane grooves, and each of the three sliding vane grooves is provided with a first sliding vane 41, a second sliding vane 42 and a third sliding vane 43.
  • first initial position is the position of the first sliding vane 41 in FIG. 10 .
  • first sliding vane 41 has completed the compression operation, and starts to protrude from the sliding vane groove for the next cycle of compression operation.
  • the second initial position is the position when the third sliding piece 43 extends to the farthest position and starts to retreat from the sliding piece groove.
  • the pressure variation range P2-P3 of the back pressure groove solution provided by the embodiment of the present disclosure is smaller than that of P1-P4 in the whole rotation cycle, indicating that the back pressure groove provided by the embodiment of the present disclosure has a
  • the pressure change is relatively gentle and the fluctuation is small, wherein at the position of the maximum extension speed and the maximum retraction speed of the sliding vane, the pressure of the back pressure groove provided by the embodiment of the present disclosure is larger than the pressure of the back pressure groove in the related art, which can better Provide stable support to the tail of the slide.

Abstract

一种法兰及具有其的泵体组件。其中，法兰包括法兰本体(10)，法兰本体(10)上开设轴孔(11)，轴孔(11)的一侧设置有背压槽(12)，背压槽(12)的靠近轴孔(11)一侧的侧壁上开设有连通部(13)，连通部(13)将背压槽(12)与轴孔(11)连通，连通部(13)被配置为向背压槽(12)供润滑油或排润滑油。通过在法兰本体(10)的背压槽(12)的靠近轴孔(11)一侧的侧壁上开设连通部(13)，通过连通部(13)可以向背压槽(12)内及时的输入润滑油，避免了采用相关技术中通过法兰与主轴(30)之间形成的间隙供油造成的供油不畅的问题。采用该结构的法兰，使得润滑油能够顺畅的进入背压槽(12)内，在滑片(40)伸出的各个角度都可以在滑片(40)尾部提供稳定可靠的油压，即使在最大伸出和退后速度下也能保持稳定的运行，有效提高了具有该法兰的泵体组件的稳定性和可靠性。

Description

法兰及具有其的泵体组件
本公开是以CN申请号为202010606496.2，申请日为2020年6月29日的申请为 基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及泵体设备技术领域，尤其涉及一种法兰及具有其的泵体组件。
背景技术
滑片式压缩机相比于其他类型的压缩机有着零件简单、无偏心结构、力矩平稳、振动小等优点，其中的滑片是通过离心力或是滑片背压将滑片推出滑片槽并顶住气缸内壁形成密封，稳定可靠的滑片背压是影响滑片机质量的重要因素。
相关技术中的旋叶式压缩机，为保证在运行过程中滑片能够顺利伸出，一般会在滑片尾部设置背压腔(滑片与主轴滑片槽形成的滑片尾腔、上法兰背压槽、下法兰背压槽)，并引入油池高压油为滑片背部提供动力，用于克服滑片头部前后腔体的气体压力和滑片槽侧面摩擦力等，实现整个运行过程中，滑片头部与气缸内部始终接触。
滑片背压的油主要通过齿轮油泵从油池泵油，然后通过主轴中心孔、与主轴中心孔相连的主轴侧孔进入法兰背压槽，进而充满背压腔。
相关技术中的背压结构，从主轴侧孔出来的油需要经过一定的间隙才能进入，如图1所示。根据滑片的运动规律，滑片在滑片槽中做往复运动，且速度在周期性变化。当滑片伸出速度较快时，该滑片尾腔容积增加较快，背压油难以及时得到补充。特别是压缩机高频运行时，当油补充不及时时，滑片背压会下降，导致滑片背压不足，进而滑片在滑片头部两侧腔体的气体压力作用下，滑片头部与气缸内壁发生脱离，进而发生泄漏，影响压缩机性能，同时滑片再次伸出时与气缸内壁发生撞击，影响压缩机可靠性。同时当滑片退回速度较快时，该滑片尾腔油不能得到及时排出会引起背压过高，滑片头部和气缸内壁摩擦力增加，功耗增加，进而影响压缩机能效及可靠性。
发明内容
根据本公开实施例的一个方面，提供了一种法兰，包括：法兰本体，法兰本体上开设轴孔，轴孔的一侧设置有背压槽，背压槽的靠近轴孔一侧的侧壁上开设有连通部，连通部将背压槽与轴孔连通，连通部被配置为向背压槽供润滑油或排润滑油。
在一些实施例中，连通部包括设于背压槽的侧壁上的缺口，和/或，连通部包括设于侧壁上的通孔结构。
在一些实施例中，连通部为多个，多个连通部沿轴孔的周向间隔地设置。
在一些实施例中，连通部包括第一缺口，背压槽的靠近轴孔一侧的侧壁上具有第一位置，第一位置处开设有第一缺口，第一缺口的两端与轴孔的孔心之间的连线形成的夹角为α1，其中，A-50°≤α1≤A+50°，A为滑片从第一初始位置处开始伸出滑片槽直至滑片的速度达到最大时转动的角度。
在一些实施例中，连通部还包括第二缺口，第二缺口与第一缺口间隔地设置，背压槽的靠近轴孔一侧的侧壁上具有第二位置，第二位置处开设有第二缺口，第二缺口的两端与轴孔的孔心之间的连线形成的夹角为α2，其中，B-50°≤α2≤B+50°，B为滑片从第二初始位置处开始退回滑片槽直至滑片的速度达到最大时转动的角度。
在一些实施例中，连通部被构造成弧形，所述连通部的两端与所述轴孔的孔心之间的连线形成的夹角为θ，其中，A-50°≤θ≤B+50°，或者，A-30°≤θ≤B+30°，A为滑片从开始伸出滑片槽直至滑片的速度达到最大时转动的角度；B为滑片从开始退回滑片槽直至所述滑片的速度达到最大时转动的角度。
在一些实施例中，连通部为形成在背压槽的侧壁上的缺口，缺口与法兰平面之间的高度差为H1，背压槽的深度为H2，法兰本体的厚度为H，其中，H2与H的比值范围为0.1～0.6，H1与H2的比值范围为0.1～1。
在一些实施例中，H1≥1mm。
根据本公开实施例的另一个方面，提供了一种泵体组件，包括上述实施例中的法兰。
在一些实施例中，泵体组件还包括：气缸，法兰本体位于气缸的一侧；以及主轴，主轴具有中心部，中心部上开设有至少一个滑片槽，各滑片槽内设置有滑片，主轴穿设于轴孔内，且中心部位于气缸内，主轴带动滑片转动以在气缸内进行压缩作业。
在一些实施例中，通过在法兰本体的背压槽的靠近轴孔一侧的侧壁上开设连通部，通过连通部可以向背压槽内及时的输入润滑油，避免了采用相关技术中通过法兰与主轴之间形成的间隙供油造成的供油不畅的问题。采用该结构的法兰，使得润滑油能够 顺畅的进入背压槽内，在滑片伸出的各个角度都可以在滑片尾部提供稳定可靠的油压，即使在最大伸出和退后速度下也能保持稳定的运行，有效地提高了具有该法兰的泵体组件的稳定性和可靠性。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本公开的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1示出了相关技术中润滑油通过法兰与主轴之间的间隙进行供油的示意图；
图2示出了根据本公开的法兰的第一实施例的结构示意图；
图3示出了图2中的A-A向的剖视结构示意图；
图4示出了根据本公开的法兰的第二实施例的结构示意图；
图5示出了根据本公开的法兰的第三实施例的结构示意图；
图6示出了根据本公开的法兰的第四实施例的结构示意图；
图7示出了图6中的B-B向的剖视结构示意图；
图8示出了根据本公开的法兰的第五实施例的结构示意图；
图9示出了根据本公开一些实施例提供的法兰与相关技术中法兰上形成的背压槽内的压力的对比示意图；
图10示出了根据本公开一些实施例提供的泵体组件的结构示意图；
图11示出了根据本公开一些实施例提供的滑片移动速度与转动角度关系的示意图。
具体实施方式
下面将结合本公开实施例中的附图，对实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本公开的一部分实施例，而不是全部的实施例。基于本公开的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”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公 开和简化描述，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公开保护范围的限制。
本公开的一些实施例提供了一种法兰及具有其的泵体组件，以缓解相关技术中滑片背压腔供油不畅的问题。
结合图2至图10所示，根据本公开的一些实施例，提供了一种法兰。
法兰包括法兰本体10。法兰本体10上开设轴孔11，轴孔11的一侧围绕轴孔11设置有背压槽12，背压槽12的靠近轴孔11一侧的侧壁上开设有连通部13，连通部13将背压槽12与轴孔11连通，连通部13被配置为向背压槽12供润滑油或排润滑油。
在本实施例中，通过在法兰本体10的背压槽12的靠近轴孔一侧的侧壁上开设连通部13，通过连通部13可以向背压槽12内及时输入润滑油，避免了采用相关技术中通过法兰与主轴之间形成的间隙供油造成的供油不畅的问题。采用该结构的法兰，使得润滑油能够顺畅的进入背压槽12内，在滑片伸出的各个角度都可以在滑片尾部提供稳定可靠的油压，即使在滑片最大伸出和退回速度下也能保持稳定的运行，有效地提高了具有该法兰的泵体组件的稳定性和可靠性。
其中，连通部13可以是形成在背压槽12的侧壁上的缺口。或者，连通部13也可以是开设在侧壁上的通孔，当然，也可以根据需要，在背压槽12的侧壁上同时开设缺口和通孔。
在一些实施例中，如图2和图3所示，连通部13为形成在背压槽12的侧壁上的缺口。这样设置方便加工。
在一些实施例中，连通部13可以设置为多个，多个连通部13沿轴孔11的周向间隔地设置。这样设置能够根据滑片的运动状态设置对应的连通部的位置，使得整个泵体组件在压缩工作中，滑片在背压槽的作用下，能够保证滑片始终处于稳定的压缩状态，提高了具有该法兰的泵体组件的可靠性。其中，如图2至图5所示，连通部13为开设在侧壁上的缺口结构，该缺口为一个。
如图6至图8所示，连通部13包括第一缺口131，背压槽12的靠近轴孔11一侧的侧壁上具有第一位置，第一位置处开设有第一缺口131，第一缺口131的两端与轴孔11的孔心之间的连线形成的夹角为α1，其中，A-50°≤α1≤A+50°，A为滑片从第一初始位置(即该滑片的工作腔开始吸气时的位置)处开始伸出滑片槽直至滑片的速度达到最大时，随泵体组件的主轴转动的角度，其中，滑片伸出滑片槽的最大速度可以根据转轴、滑片、气缸等尺寸通过数学计算得到，如图11中，示出了滑片沿滑 片槽伸出速度达到最大时，转动的角度为105°的实施例。其中，图11中的滑片移动速度包括滑片伸出滑片槽的速度和滑片缩回滑片槽的速度。
连通部13还包括第二缺口132，第二缺口132与第一缺口131间隔地设置，背压槽12的靠近轴孔11一侧的侧壁上具有第二位置，第二位置处开设有第二缺口132，第二缺口132的两端与轴孔11的孔心之间的连线形成的夹角为α2，其中，B-50°≤α2≤B+50°，B为滑片从第二初始位置(即在工作腔一个吸气压缩周期内，滑片从开始伸出，伸出预设值后滑片会逐渐退回滑片槽内，而第二初始位置为滑片开始实现退回滑片槽内时的位置)处开始退回滑片槽直至滑片退回的速度达到最大时，随泵体组件的主轴转动的角度，同样地，滑片退回至滑片槽内达到最大速度也可以根据转轴、滑片、气缸等尺寸通过数学计算得到。这样设置使得在滑片伸出的各个角度都可以在滑片尾部提供稳定可靠的油压，即使在滑片伸出滑片槽至最大速度时，以及滑片退回至滑片槽内至最大速度时也能保持稳定的运行。
在一些实施例中，连通部13围绕轴孔11设置呈弧形，连通部13的两端与轴孔11的孔心之间的连线形成的夹角为θ，其中，A-50°≤θ≤B+50°，或者，A-30°≤θ≤B+30°。如图2和图4所示，连通部13为缺口结构，缺口两端与轴孔11的孔心之间连线的角度为θ，A-50°≤θ≤B+50°，或者，A-30°≤θ≤B+30°。A为滑片从开始伸出滑片槽直至滑片的速度达到最大时，随泵体组件的主轴转动的角度；B为滑片从开始退回滑片槽直至滑片的速度达到最大时，随泵体组件的主轴转动的角度。
如图3所示，连通部13为形成在背压槽12的侧壁上的缺口，缺口与法兰平面之间的高度差为H1，背压槽12的深度为H2，法兰本体10的厚度为H，其中，H2与H的比值范围为0.1～0.6，H1与H2的比值范围为0.1～1，H1≥1mm。这样设置能够保证背压的供油和排油及时性，同时降低了缺口处润滑油流动的阻力。
在一些实施例中，法兰可以用于泵体设备组件，即根据本公开一些实施例的另一个方面，提供了一种泵体组件，包括法兰，法兰为上述实施例中的法兰。
在一些实施例中，泵体组件包括气缸20和主轴30。法兰本体10位于气缸20的一侧。主轴30具有中心部31，中心部31上开设有至少一个滑片槽，各滑片槽内设置有滑片40，主轴30穿设于轴孔11内，且中心部31位于气缸20内，主轴30带动滑片40转动以在气缸20内进行压缩作业。其中，法兰本体10上的背压槽12处形成背压腔。
在一些实施例中，如图10所示，中心部31上开设有三个滑片槽，三个滑片槽内 各设置有第一滑片41、第二滑片42和第三滑片43。其中，上述的第一初始位置为图10中第一滑片41所处的位置，此时第一滑片41为进行压缩作业完成，开始从滑片槽内伸出进行下一周期的压缩作业。第二初始位置为第三滑片43伸出至最远位置开始退回滑片槽时的位置。
如图9所示，从中可以看出，本公开实施例提供的背压槽方案在整个旋转周期内的压力变化范围P2-P3均小于P1-P4，说明本公开实施例提供的背压槽的压力变化比较平缓，波动小，其中在滑片最大伸出速度和最大退回速度位置，本公开实施例提供的背压槽的压力比相关技术中的背压槽的压力更大，可以更好的对滑片的尾部进行平稳支撑。
在本公开的描述中，需要理解的是，使用“第一”、“第二”、“第三”等词语来限定零部件，仅仅是为了便于对上述零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本公开保护范围的限制。
另外，在没有明确否定的情况下，其中一个实施例的技术特征可以有益地与其他一个或多个实施例相互结合。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (10)

  1. 一种法兰，包括：
    法兰本体(10)，所述法兰本体(10)上开设轴孔(11)，所述轴孔(11)的一侧设置有背压槽(12)，所述背压槽(12)的靠近所述轴孔(11)一侧的侧壁上开设有连通部(13)，所述连通部(13)将所述背压槽(12)与所述轴孔(11)连通，所述连通部(13)被配置为向所述背压槽(12)供润滑油或排润滑油。
  2. 根据权利要求1所述的法兰，其中，所述连通部(13)包括设于所述背压槽(12)的侧壁上的缺口，和/或，所述连通部(13)包括设于所述背压槽(12)的侧壁上的通孔。
  3. 根据权利要求1或2所述的法兰，其中，所述连通部(13)为多个，多个所述连通部(13)沿所述轴孔(11)的周向间隔地设置。
  4. 根据权利要求1至3任一项所述的法兰，其中，所述连通部(13)包括第一缺口(131)，所述背压槽(12)的靠近所述轴孔(11)一侧的侧壁上具有第一位置，所述第一位置处开设有所述第一缺口(131)，所述第一缺口(131)的两端与所述轴孔(11)的孔心之间的连线形成的夹角为α1，其中，A-50°≤α1≤A+50°，A为滑片从第一初始位置处开始伸出滑片槽直至滑片的速度达到最大时转动的角度。
  5. 根据权利要求4所述的法兰，其中，所述连通部(13)还包括第二缺口(132)，所述第二缺口(132)与所述第一缺口(131)间隔地设置，所述背压槽(12)的靠近所述轴孔(11)一侧的侧壁上具有第二位置，所述第二位置处开设有所述第二缺口(132)，所述第二缺口(132)的两端与所述轴孔(11)的孔心之间的连线形成的夹角为α2，其中，B-50°≤α2≤B+50°，B为滑片从第二初始位置处开始退回滑片槽直至所述滑片的速度达到最大时转动的角度。
  6. 根据权利要求1至3中任一项所述的法兰，其中，所述连通部(13)被构造成弧形，所述连通部(13)的两端与所述轴孔(11)的孔心之间的连线形成的夹角为θ，其中，A-50°≤θ≤B+50°，或者，A-30°≤θ≤B+30°；A为滑片从开始伸出滑片槽直至滑片的速度达到最大时转动的角度；B为滑片从开始退回滑片槽直至所述滑片的速度达到最大时转动的角度。
  7. 根据权利要求1至6任一项所述的法兰，其中，所述连通部(13)为形成在所述背压槽(12)的侧壁上的缺口，所述缺口与法兰平面之间的高度差为H1，所述背压 槽(12)的深度为H2，所述法兰本体(10)的厚度为H，其中，H2与H的比值范围为0.1～0.6，H1与H2的比值范围为0.1～1。
  8. 根据权利要求7所述的法兰，其中，H1≥1mm。
  9. 一种泵体组件，包括根据权利要求1至8中任一项所述的法兰。
  10. 根据权利要求9所述的泵体组件，还包括：
    气缸(20)，所述法兰本体(10)位于所述气缸(20)的一侧；以及
    主轴(30)，所述主轴(30)具有中心部(31)，所述中心部(31)上开设有至少一个滑片槽，各所述滑片槽内设置有滑片(40)，所述主轴(30)穿设于所述轴孔(11)内，且中心部(31)位于所述气缸(20)内，所述主轴(30)带动所述滑片(40)转动以在所述气缸(20)内进行压缩作业。
PCT/CN2020/139110 2020-06-29 2020-12-24 法兰及具有其的泵体组件 WO2022001033A1 (zh)

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