WO2020052418A1 - 泵体组件及具有其的压缩机 - Google Patents

泵体组件及具有其的压缩机 Download PDF

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Publication number
WO2020052418A1
WO2020052418A1 PCT/CN2019/102052 CN2019102052W WO2020052418A1 WO 2020052418 A1 WO2020052418 A1 WO 2020052418A1 CN 2019102052 W CN2019102052 W CN 2019102052W WO 2020052418 A1 WO2020052418 A1 WO 2020052418A1
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WO
WIPO (PCT)
Prior art keywords
groove
oil
pump body
back pressure
section
Prior art date
Application number
PCT/CN2019/102052
Other languages
English (en)
French (fr)
Inventor
徐嘉
罗发游
万鹏凯
吴飞
丁宁
郭霜
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 US17/254,378 priority Critical patent/US11519270B2/en
Priority to EP19860387.0A priority patent/EP3798446A4/en
Publication of WO2020052418A1 publication Critical patent/WO2020052418A1/zh

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    • 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
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
    • 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
    • F04C18/3445—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 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
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present application relates to the field of compressors, and in particular, to a pump body assembly and a compressor having the same.
  • this application claims the priority of a patent application filed on September 12, 2018 with the State Intellectual Property Office of China, with an application number of 201811062779.4, and an invention name of "Pump Body Component and Compressor With It".
  • sliding vane compressors Compared with other types of compressors, sliding vane compressors have the advantages of simple parts, no eccentric structure, and low torque and stable vibration. At the same time, sliding vane compressors also have a disadvantage that affects their energy efficiency, namely the power consumption of the sliding vane head. is too big.
  • the sliding vane compressor pushes the sliding vane out of the sliding vane groove by centrifugal force or sliding vane back pressure and forms a seal against the inner wall of the cylinder. Due to the large rotation radius of the sliding vane head, the linear speed is large during operation, which causes the sliding vane head.
  • the frictional power consumption caused by the contact between the engine and the cylinder is very large, and the number of sliding blades is large, so the power consumption of the sliding head is the main source of mechanical power consumption of the sliding vane compressor.
  • the main purpose of the present application is to provide a pump body assembly and a compressor having the same, in order to solve the problem of large power consumption of the sliding head of the pump body assembly in the suction stage in the prior art.
  • a pump body assembly including: an oil supply channel, the oil supply channel is used to circulate an oil body; two back pressure members, two back pressure members, at least one back pressure
  • a back pressure groove is provided on the piece.
  • the back pressure groove includes a first groove section and a second groove section spaced from the first groove section.
  • the first groove section is connected to the oil supply channel, and the second groove section is connected to the oil supply channel.
  • the area where the first groove section communicates with the oil supply channel is a, and the area where the second groove section communicates with the oil supply channel is b, a ⁇ b.
  • the oil supply channel includes: a flow channel, the flow channel is arranged on at least one back pressure member, the flow channel includes a first flow channel and a second flow channel, the first flow channel communicates with the first groove section, and the second flow channel communicates with The second slot section is in communication; wherein the area of the first opening where the first flow channel is in communication with the first slot section is a, and the area of the second opening in which the second flow channel is in communication with the second slot section is b.
  • the pump body assembly further includes a rotating shaft, the rotating shaft passes through the two back pressure members, and the oil supply channel further includes: an oil passage, the oil passage is arranged on the rotating shaft, the oil passage is connected with the first flow passage, and the oil passage is connected with the second flow The roads are connected.
  • the oil supply passage further includes: an oil cavity, the oil cavity is disposed on at least one back pressure member, the oil cavity is communicated with the oil passage, and the oil cavity is communicated with the flow passage, so that the oil passage passes through the oil cavity and the first flow passage The oil passage communicates with the second flow passage through the oil cavity; wherein the flow passage is located between the oil cavity and the back pressure groove.
  • the back pressure groove further includes: a third groove section, and the second groove section is located between the third groove section and the first groove section; wherein the width of the third groove section is smaller than the width of the second groove section.
  • the third groove section is in communication with the oil supply passage.
  • the third slot section is in communication with the second slot section.
  • the cross section of the first flow channel is circular or polygonal
  • / or the cross section of the second flow channel is circular or polygonal
  • first groove section is an arc-shaped groove
  • second groove section is an arc-shaped groove
  • the two back pressure members are an upper flange and a lower flange, respectively, and the back pressure groove is provided on an end surface of the upper flange facing the lower flange; and / or the back pressure groove is provided on an end surface of the lower flange facing the upper flange. on.
  • a back pressure groove is provided on the upper flange and the lower flange, and the projection of the back pressure groove on the upper flange on the lower flange coincides with the back pressure groove on the lower flange.
  • the two back pressure members are an upper flange and a lower flange, respectively.
  • the back pressure grooves are provided on the end faces of the upper flange facing the lower flange, and the back pressure grooves are provided on the end faces of the lower flange facing the upper flange.
  • the flange is provided with at least a part of the oil supply channel.
  • the pump body assembly further includes: a pump body, and an oil outlet of the pump body is in communication with the oil supply channel, so that the pump body transmits the oil body in the oil tank to the oil supply channel.
  • a compressor including a pump body component, and the pump body component is the above-mentioned pump body component.
  • the pump body assembly of the present application can reduce the amount of oil in the tail groove of the sliding blade during the suction phase of the pump body component, thereby reducing the pressure difference across the sliding blade. Therefore, the power consumption of the slider head can be reduced.
  • the sliding blade tail groove is in communication with the first groove segment, and the oil body enters the sliding blade groove through the oil supply channel and the first groove segment in sequence.
  • the first groove segment and the The area where the oil supply channels communicate is small, thereby reducing the amount of oil in the tail groove of the sliding blade, thereby reducing the pressure difference across the sliding blade.
  • the sliding vane groove is in communication with the second groove segment, and the oil body enters the sliding vane groove through the oil supply channel and the second groove segment in sequence.
  • the second groove segment is connected to the oil supply channel
  • the area of the passage is larger than the area where the first groove segment communicates with the oil supply channel, thereby increasing the amount of oil in the tail groove of the sliding blade, thereby ensuring that the pressure difference between the two sides of the sliding blade is sufficient to make the sliding blade in a reliable position.
  • the pump body assembly of the present application can reduce the amount of oil in the tail groove of the sliding blade during the suction phase of the pump body component, thereby reducing the pressure difference across the sliding blade. Therefore, the power consumption of the sliding blade head can be reduced, and the problem that the power consumption of the sliding blade head during the suction phase of the pump assembly in the prior art is large is solved.
  • FIG. 1 is a schematic cross-sectional structure diagram of a pump body component in the prior art
  • FIG. 2 shows an exploded structure diagram of an embodiment of a pump body assembly according to the present application
  • FIG. 3 shows a schematic cross-sectional structure of a pump body assembly according to the present application
  • FIG. 4 shows a partially enlarged structure diagram of the pump body component A at FIG. 3;
  • FIG. 5 is a schematic structural diagram of a first state of a pump body assembly according to the present application.
  • FIG. 6 is a schematic structural diagram of a second state of a pump body assembly according to the present application.
  • FIG. 7 is a schematic structural diagram of a third state of a pump body assembly according to the present application.
  • FIG. 8 is a schematic structural diagram of a fourth state of a pump body assembly according to the present application.
  • FIG. 9 is a schematic structural view of a first perspective of an upper flange of a pump body assembly according to the present application.
  • FIG. 10 shows a schematic structural view of a second perspective of an upper flange of a pump body assembly according to the present application
  • FIG. 11 is a schematic structural view of a first perspective of a lower flange of a pump body assembly according to the present application.
  • FIG. 12 shows a schematic structural view of a second perspective of a lower flange of a pump body assembly according to the present application
  • FIG. 13 is a schematic structural view of a third perspective of a lower flange of a pump body assembly according to the present application.
  • FIG. 14 is a schematic structural view of a fourth perspective of a lower flange of a pump body assembly according to the present application.
  • FIG. 15 is a schematic cross-sectional structure diagram of a lower flange of a pump body assembly according to the present application.
  • FIG. 16 is a schematic structural diagram of a rotating shaft of a pump body assembly according to the present application.
  • FIG. 17 shows a schematic cross-sectional structure diagram of a rotating shaft of a pump body assembly according to the present application
  • FIG. 18 is a schematic structural view of a first perspective of a pump body of a pump body assembly according to the present application.
  • FIG. 19 is a schematic structural view of a second perspective of a pump body of a pump body assembly according to the present application.
  • FIG. 20 shows a schematic cross-sectional structure of a pump body of a pump body assembly according to the present application.
  • the pump body assembly includes: an oil supply channel, the oil supply channel is used to circulate the oil body; two back pressure members, at least one back pressure member
  • the pressure piece is provided with a back pressure groove 10.
  • the back pressure groove 10 includes a first groove section 11 and a second groove section 12 spaced from the first groove section 11.
  • the first groove section 11 communicates with the oil supply channel.
  • the slot section 12 is in communication with the oil supply channel; wherein the area where the first slot section 11 is in communication with the oil supply channel is a, and the area where the second slot section 12 is in communication with the oil supply channel is b, a ⁇ b.
  • the pump body assembly of the present application reduces the area where the first groove section 11 communicates with the oil supply passage, and can reduce the amount of oil in the tail groove 31 of the sliding blade during the suction phase of the pump body component, thereby reducing the The pressure difference can reduce the power consumption of the head of the sliding plate 30.
  • the sliding vane tail groove 31 communicates with the first groove segment 11, and the oil body enters the sliding vane groove 21 through the oil supply channel and the first groove segment 11 in sequence.
  • the area of a groove section 11 communicating with the oil supply channel is relatively small, thereby reducing the amount of oil in the tail groove 31 of the sliding blade, thereby reducing the pressure difference across the sliding blade 30.
  • the sliding blade tail groove 31 communicates with the second groove section 12, and the oil body enters the sliding groove 21 through the oil supply channel and the second groove section 12 in sequence.
  • the area communicating with the oil supply channel is larger than the area where the first groove section 11 communicates with the oil supply channel, thereby increasing the amount of oil in the tail groove 31 of the vane, thereby ensuring that the pressure difference between the two sides of the vane 30 is sufficient Position the slide 30 in a reliable position.
  • the pump body assembly of the present application reduces the area where the first groove section 11 communicates with the oil supply passage, and can reduce the amount of oil in the tail groove 31 of the sliding blade during the suction phase of the pump body component, thereby reducing the The pressure difference can reduce the power consumption of the head of the sliding blade 30, and solves the problem that the power consumption of the sliding head of the pump body component in the prior art is large during the suction phase.
  • the pump body assembly further includes: a rotating shaft 20 that passes through two back pressure members.
  • the rotating shaft 20 is provided with a sliding blade groove 21; the sliding blade 30 is slidably disposed in the sliding blade groove.
  • a sliding blade tail groove 31 is formed between the sliding blade 30 and the sliding blade groove 21.
  • the sliding blade tail groove 31 and the first groove segment 11 can be provided on and off, and the sliding blade tail groove 31 and the second groove segment 12 can be provided on and off.
  • the sliding plate tail groove 31 communicates with the first groove segment 11. Accordingly, during the compression phase, the sliding plate tail groove 31 communicates with the first groove section 11.
  • the second groove section 12 communicates.
  • the oil supply channel includes: The channel 40 is disposed on at least one back pressure member.
  • the flow channel 40 includes a first flow channel 41 and a second flow channel 42.
  • the first flow channel 41 is in communication with the first groove section 11, and the second flow channel 42 is in communication with the second groove section 12.
  • the area of the first opening communicating with the first flow channel 41 and the first groove section 11 is a, and the area of the second opening communicating with the second flow channel 42 and the second groove section 12 is b.
  • the area of the first opening communicating with the first flow passage 41 and the first groove section 11 is a, that is, the area of the oil outlet of the first flow passage 41 is a, and the second flow passage 42 and the second groove
  • the area of the second opening communicating with the segment 12 is b, that is, the area of the oil outlet of the second flow channel 42 is b.
  • the pump body assembly further includes a rotating shaft 20, the rotating shaft 20 passes through two back pressure members, and the oil supply channel further includes:
  • the oil passage 22 is arranged on the rotating shaft 20.
  • the oil passage 22 is in communication with the first flow passage 41 and the oil passage 22 is in communication with the second flow passage 42.
  • an oil passage 22 is provided on the rotating shaft 20, and an oil inlet of the oil passage 22 flows into the lubricating oil, and an oil outlet of the oil passage 22 communicates with both the first flow passage 41 and the second flow passage 42, so that The lubricating oil in the pump body component is caused to flow into the first flow passage 41 and the second flow passage 42 through the oil passage 22, and then enter the corresponding first groove section 11 and the second groove section 12.
  • the oil supply channel further includes: an oil chamber 50, the oil chamber 50 is disposed on at least one back pressure member, and the oil chamber 50 and the oil passage 22 communicates, the oil cavity 50 communicates with the flow passage 40, so that the oil passage 22 communicates with the first flow passage 41 through the oil cavity 50, and the oil passage 22 communicates with the second flow passage 42 through the oil cavity 50;
  • the channel 40 is located between the oil chamber 50 and the back pressure groove 10.
  • an oil cavity 50 is provided on the back pressure member, and the oil cavity 50 is in communication with the oil passage 22, and the oil cavity 50 is in communication with the flow passage 40, so that the oil passage 22 passes through the oil cavity 50 and the first
  • the first channel 41 communicates, and the oil channel 22 communicates with the second flow channel 42 through the oil chamber 50, that is, the lubricant in the oil channel 22 enters the oil chamber 50 for storage, and then flows into the first flow channel 41 and the second flow channel.
  • the flow passage 40 is located between the oil cavity 50 and the back pressure groove 10, and the inner wall of the oil cavity 50 is a circular arc.
  • the back pressure groove 10 further includes a third groove section 13, and the second groove section 12 is located in the third groove. Between the segment 13 and the first slot segment 11, wherein the width of the third slot segment 13 is smaller than the width of the second slot segment 12.
  • a third groove section 13 is provided on the back pressure groove 10, and the width of the third groove section 13 is smaller than the width of the second groove section 12.
  • the inside of the sliding groove 21 can be guaranteed. It has sufficient oil pressure, that is, simmer oil is generated in the vane groove 21.
  • the third groove section 13 and the sliding blade tail groove 31 can be provided on and off, that is, in the exhaust phase, the third groove section 13 and the sliding blade tail groove 31 communicate with each other.
  • the second slot section 12 is located between the third slot section 13 and the first slot section 11.
  • the third groove segment 13 is in communication with the oil supply channel.
  • the third groove segment 13 is connected to the oil supply channel. So that the lubricating oil in the sliding blade groove 21 can be partially leaked through the oil supply channel.
  • the third groove section 13 is in communication with the second groove section 12.
  • the third groove section 13 is in communication with the second flow channel 42.
  • the third groove section 13 is spaced apart from the second groove section 12, and the flow channel 40 further includes a third flow channel.
  • the third groove section 13 is in communication with the third flow channel, so that the third groove section 13 passes the first
  • the three flow passages communicate with the oil passage 22.
  • the third groove section 13 is an arc-shaped groove.
  • the cross section of the first flow passage 41 is circular or polygonal
  • the cross section of the second flow passage 42 is circular or polygonal
  • the cross sections of the first flow passage 41 and the second flow passage 42 are quadrangular.
  • the first groove section 11 is an arc-shaped groove
  • the second groove section 12 is an arc-shaped groove
  • the two back pressure pieces are an upper flange 60 and a lower flange 70, respectively.
  • the back pressure groove 10 is provided in the upper flange 60 facing the lower flange. 70 on the end surface; the back pressure groove 10 is provided on the end surface of the lower flange 70 facing the upper flange 60.
  • the two back pressure members are an upper flange 60 and a lower flange 70, respectively, and the sliding plate 30 is located between the upper flange 60 and the lower flange 70.
  • the back pressure groove 10 is provided on an end surface of the upper flange 60 facing the lower flange 70
  • the back pressure groove 10 is provided on an end surface of the lower flange 70 facing the upper flange 60, that is, in the upper flange 60 and the lower flange 70. At least one of them is provided with a back pressure groove 10.
  • both the upper flange 60 and the lower flange 70 are provided with a back pressure groove 10, and the projection of the back pressure groove 10 on the upper flange 60 on the lower flange 70 is the same as the back pressure groove 10 on the lower flange 70. coincide.
  • both the upper flange 60 and the lower flange 70 are provided with a back pressure groove 10, and the specific structure of the back pressure groove 10 on the upper flange 60 and the back pressure groove 10 on the lower flange 70 are consistent .
  • the lower flange 70 and the upper flange 60 are provided with a flow channel 40.
  • the two back pressure members are an upper flange 60 and a lower flange 70, respectively.
  • the back pressure groove 10 is provided on an end surface of the upper flange 60 facing the lower flange 70.
  • the back pressure groove 10 The lower flange 70 is disposed on an end surface of the lower flange 70 facing the upper flange 60. At least a part of the oil supply channel is provided on the lower flange 70.
  • the upper flange 60 and the lower flange 70 are both provided with a back pressure groove 10, and the lower flange 70 is provided with a flow channel 40 and an oil cavity 50.
  • the pump body assembly further includes: a pump body 80, and an oil outlet of the pump body 80 communicates with the oil supply passage so that the pump body 80 transfers the oil body in the fuel tank to the oil supply channel.
  • the pump body 80 is provided on the pump body assembly, and the oil outlet of the pump body 80 is communicated with the oil supply channel, so that the pump body 80 can transport the oil body in the oil tank to the oil supply channel. To ensure that the sliding groove 21 is filled with lubricating oil.
  • the pump body 80 is an oil pump, and the oil pump is a gear oil pump.
  • the oil passage 22 includes a central hole 221 and a radial hole 222 communicating with the central hole 221, and the central hole 221 and the pump
  • the oil outlet of the body 80 is in communication, and the radial hole 222 is in communication with the oil cavity 50.
  • the present application also provides a compressor including a pump body component, and the pump body component is the above-mentioned pump body component.
  • the suction of the sliding vane compressor is an angle, and because the head of the sliding vane is under the suction pressure during the suction stage, the pressure difference between the tail of the sliding vane and the head (F back-F head) is the largest.
  • the radius of rotation of the sliding head is increasing, that is, the linear velocity of the sliding head is getting larger and larger.
  • W f ⁇ v
  • the consumption in the inhalation phase is not only large, but also an increasing process. Therefore, the power consumption of the slider head in the inhalation phase occupies a larger proportion in the entire operating cycle of the slider. Reducing the power consumption there will reduce the overall machine. Power consumption has a significant effect.
  • the back pressure at the tail of the sliding vane in the conventional exhaust stage may not meet the requirements of ensuring that the sliding vane is always close to the inner wall of the cylinder.
  • the risk is likely to cause the impact of the sliding blades, affecting the reliability of the sliding blades and the noise and vibration of the compressor. Therefore, increasing the back pressure of the exhaust section and ensuring that the sliding blades do not return are important to the reliability of the compressor and the noise and vibration.
  • the compressor of the present application is a brand new sliding vane compressor.
  • the tail back pressure control method of the sliding vane compressor is to divide the traditional back pressure groove into an intake section, a compression section, and an exhaust section.
  • the back pressure corresponding to the section is different, so that the lower back pressure is provided in the suction section where the head pressure of the slider is lower, and the back pressure higher than the exhaust pressure is provided in the exhaust section where the head pressure is higher than the exhaust pressure. Pressure.
  • This application divides the sliding blade back pressure groove into three sections, the suction section, the compression section, and the exhaust section, wherein the suction section is separated from the compression section and the exhaust section by a transition section to prevent the latter's high-pressure oil from communicating with The suction section affects the back pressure in the suction section.
  • the sliding blade back pressure tank uses three stages of back pressure, the suction section uses low back pressure to reduce power consumption, the compression section uses high back pressure of the exhaust pressure, and the exhaust section uses an oil tank design to generate back pressure higher than the exhaust pressure. .
  • the pressure control of the three-stage back pressure of the present application is through: the back pressure oil (P) is divided from the main path into two paths respectively leading to the back pressure groove of the suction section (the first groove section 11) and the back pressure groove of the compression section (the second section) The groove section 12) and the exhaust section back pressure groove (the third groove section 13).
  • the oil passage (the first flow passage 41) leading to the suction section back pressure groove is narrow, and the oil flow through the small-diameter oil passage is realized. Throttle and reduce pressure ( ⁇ P1) to achieve low back pressure (P- ⁇ P1) in the intake section.
  • the oil path to the back pressure groove of the compression and exhaust section is a large-diameter oil path (second flow path 42), which prevents oil from being lost along the way, ensures that the back pressure oil does not generate a pressure drop, and achieves high back pressure in the compression section.
  • P The sliding section of the exhaust section is retracted, and the space of the sliding section at the tail of the sliding section is reduced with the sliding section.
  • the back pressure groove here is designed to be a shallow, narrow groove. At the end of the sliding vane groove, a back pressure ( ⁇ P2) will be generated to achieve an ultra-high back pressure (P + ⁇ P2) in the exhaust section.
  • the shallow narrow back pressure groove can both realize the return of the sliding vane to the pressure of the oil to increase the back pressure. The effect can also give an appropriate oil drain path to prevent excessive oil pressure.
  • the suction section of this application is from the start of suction to the start of compression, the compression section is from the start of compression to the start of exhaust, and the exhaust section is from the start of exhaust to the end of exhaust.
  • Their respective angle ranges vary depending on the compressor.
  • the structure of the pump body varies.
  • the cross-sectional area design of the oil passage leading to the suction section of this application is determined by its oil passage length and minimum operating frequency to ensure that the ideal pressure drop ⁇ P1 can be achieved under the condition of the minimum oil speed and the minimum oil flow rate.
  • This application leads to compression
  • the cross-sectional area of the oil circuit in the exhaust section is designed to ensure that no oil pressure drop along the route is generated under the highest operating frequency and maximum oil flow rate.
  • the design of the oil tank in the exhaust section of this application should be able to ensure sufficient oil pressure ⁇ P2 at the lowest operating frequency, and sufficient oil leakage at the highest operating frequency to prevent ⁇ P2 from being too high.
  • symmetrical back pressure grooves are provided on both the upper and lower flanges to ensure the stability of the back pressure, and can effectively prevent the upper and lower ends of the sliding plate from being unevenly biased.
  • the oil supply in this application is actively supplied by the oil pump at the bottom of the main shaft (rotary shaft 20), which guarantees that the entire amount of oil can fill the entire back pressure chamber of the sliding blade at any time, and provides the prerequisites for the degreasing of the exhaust section.
  • This application can reduce the back pressure of the sliding blade through the three-stage back pressure structure, thereby reducing the power consumption of the head of the sliding blade.
  • By increasing the back pressure of the sliding blade during the exhaust phase it is ensured that the sliding blade does not detach and realize the sliding blade back pressure.
  • Flexible control improving the reliability of sliding vanes, compressor noise and vibration, and improving the overall performance of the compressor.
  • the application has a simple structure, and the processing and assembly of parts are simple and easy to implement.
  • FIG. 2 is an exploded view of a pump body assembly of the present application, including parts such as a main shaft (rotating shaft 20), a cylinder 90, an upper flange 60, a lower flange 70, an oil pump, a sliding plate 30, a screw 100, an exhaust valve 110, and the like.
  • the flange end surface is provided with a back pressure groove 10.
  • the back pressure groove is an annular groove with a certain depth.
  • the back pressure groove is divided into a suction section and a compression section. And the exhaust section.
  • the back pressure groove of the exhaust section is a relatively shallow and narrow oil tank.
  • the main shaft is provided with a central hole 221 and a radial hole 222 for supplying oil
  • the oil pump is a gear oil pump, which is assembled with the main shaft through a D-type small shaft at the bottom of the main shaft.
  • the intake section oil passage (flow channel 40), the intake section oil passage, the compression and exhaust section oil passages are straight holes with a certain length and cross section, and are all arranged on the lower flange 70, as shown in FIG. 15 As shown.
  • Phase 1 When the compressor runs the main shaft, the oil pump installed at the bottom of the main shaft will rotate to pump the oil into the center hole. As the main shaft rotates, the oil in the center hole will pass through the radial holes on the main shaft under the action of centrifugal force. It enters the oil cavity formed by the lower flange and the oil pump, and then enters the back pressure groove of the flange through the oil circuit in the suction section and the oil circuit in the compression and exhaust sections, respectively. The oil pressure in the suction section is lowered to P- ⁇ P1 due to the throttle pressure ⁇ P1 passing through the oil passage in the suction section. The refrigerant enters the compression chamber through the air inlet 120.
  • FIG. 5 to 8 are the actual movements of the pump body.
  • One of the sliding plates 30 is used as the object (the sliding plate with the number 30 in the figure).
  • the sliding blade tail groove sliding blade groove 21
  • the sliding plate 30 reached the position of FIG. The air section back pressure groove is disconnected and will enter the transition zone.
  • Phase 3 As the sliding blade continues to move past Figure 6, the sliding blade tail groove will leave the transition zone and communicate with the back pressure groove of the compression section. After an angle, the refrigerant in the pump body will be exhausted after being compressed. At this time, the sliding blade tail groove It will leave the compression section and enter the exhaust section.
  • Phase 4 When the sliding blade continues to move in the direction of rotation, the sliding blade enters the exhaust section and reaches the position of Figures 7 and 8. During this whole process, the volume V of the tail groove of the slider is gradually reduced. The oil inside the tail groove of the sliding vane is compressed and flows out of the oil tank. However, due to the fast rotation speed of the sliding van, the volume change rate of the V tail is large, coupled with the small cross-sectional area of the oil tank and the incompressibility of the oil. A higher pressure (P- ⁇ P2) is formed in the tail groove than the original pressure, so the back pressure is higher than the conventional scheme.
  • the pump body assembly of the present application reduces the area where the first groove section 11 communicates with the oil supply passage, and can reduce the amount of oil in the tail groove 31 of the sliding blade during the suction phase of the pump body component, thereby reducing the The pressure difference can reduce the power consumption of the head of the sliding plate 30.
  • the sliding vane tail groove 31 communicates with the first groove segment 11, and the oil body enters the sliding vane groove 21 through the oil supply channel and the first groove segment 11 in sequence.
  • the area of a groove section 11 communicating with the oil supply channel is relatively small, thereby reducing the amount of oil in the tail groove 31 of the sliding blade, thereby reducing the pressure difference across the sliding blade 30.
  • the sliding blade tail groove 31 communicates with the second groove section 12, and the oil body enters the sliding groove 21 through the oil supply channel and the second groove section 12 in sequence.
  • the area communicating with the oil supply channel is larger than the area where the first groove section 11 communicates with the oil supply channel, thereby increasing the amount of oil in the tail groove 31 of the vane, thereby ensuring that the pressure difference between the two sides of the vane 30 is sufficient Position the slide 30 in a reliable position.
  • the pump body assembly of the present application reduces the area where the first groove section 11 communicates with the oil supply passage, and can reduce the amount of oil in the tail groove 31 of the sliding blade during the suction phase of the pump body component, thereby reducing the The pressure difference can reduce the power consumption of the head of the sliding blade 30, and solves the problem that the power consumption of the sliding head of the pump body component in the prior art is large during the suction phase.
  • spatially relative terms such as “above”, “above”, “above”, “above”, etc. can be used here to describe as shown in the figure Shows the spatial position relationship between one device or feature and other devices or features. It should be understood that spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device as described in the figures. For example, if a device in the figure is turned over, devices described as “above” or “above” other devices or constructions will then be positioned “below the other devices or constructions” or “under Other devices or constructs. " Thus, the exemplary term “above” may include both directions “above” and “below”. The device can also be positioned in other different ways (rotated 90 degrees or at other orientations), and the relative description of space used here is explained accordingly.

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Abstract

一种泵体组件及具有其的压缩机，泵体组件包括：供油通道，供油通道用于流通油体；背压件，背压件为两个，至少一个背压件上设置有背压槽（10），背压槽（10）包括第一槽段（11）和与第一槽段（11）间隔设置的第二槽段（12），第一槽段（11）与供油通道相连通，第二槽段（12）与供油通道相连通；其中，第一槽段（11）与供油通道相连通的面积为a，第二槽段（12）与供油通道相连通的面积为b，a＜b，该泵体组件解决了现有技术中的泵体组件在吸气阶段滑片头部功耗较大的问题。

Description

泵体组件及具有其的压缩机 技术领域
本申请涉及压缩机领域，具体而言，涉及一种泵体组件及具有其的压缩机。其中，本申请要求于2018年9月12日提交至中国国家知识产权局、申请号为201811062779.4、发明名称为“泵体组件及具有其的压缩机”的专利申请的优先权。
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，但同时滑片式压缩机也有一个影响其能效的缺点，即滑片头部功耗过大。滑片式压缩机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，由于滑片头部的旋转半径大，因此运行时线速度较大，导致滑片头部与气缸接触时产生的摩擦功耗很大，加上滑片数量多，因此滑片头部功耗是滑片式压缩机的主要机械功耗来源。
在具体使用时，如图1所示，为了使滑片在运行过程中始终贴紧气缸内壁，一般会在滑片槽尾部引入壳体腔中的高压油来提供背压，从而保证滑片在运行中不会被头部压力退回。滑片机滑片头部功耗的计算公式可简单表述为：W＝f·v，其中，v为滑片头部线速度在摩擦力方向的分量，与滑片机泵体结构及转速有关，f为滑片头部对气缸摩擦力，是滑片背压力F1与滑片头部气体力F2差值的分量与摩擦系数μ的乘积。因此，滑片头部功耗计算可表示为：W＝μv(F1-F2)cost。
其中，在吸气段，由于此时滑片头部压力F2为吸气压力提供，即(F1-F2)值较大，这就使吸气段的滑片头部功耗W较大，会影响滑片可靠性及压缩机性能。在排气段，由于排气过压缩的存在，此时滑片头部的实际压力F2≥F排气压力，由于滑片背压油是壳体内高压油经过一定长度的通道到达滑片尾部，因此必定会造成一定的沿程压降，即F1≤F排气压力，因此F1-F2的值接近零甚至为负值，且此时滑片的离心力相对于气体力来说非常小，当腔体内有过压缩时或背压有波动时就有可能造成滑片尾部压力不足，即滑片有脱离气缸内壁退回滑片槽的风险，容积造成滑片撞击，影响压缩机性能及噪音，同时对滑片可靠性也非常不利。
发明内容
本申请的主要目的在于提供一种泵体组件及具有其的压缩机，以解决现有技术中的泵体组件在吸气阶段滑片头部功耗较大的问题。
为了实现上述目的，根据本申请的一个方面，提供了一种泵体组件，包括：供油通道，供油通道用于流通油体；背压件，背压件为两个，至少一个背压件上设置有背压槽，背压槽包括第一槽段和与第一槽段间隔设置的第二槽段，第一槽段与供油通道相连通，第二槽段与 供油通道相连通；其中，第一槽段与供油通道相连通的面积为a，第二槽段与供油通道相连通的面积为b，a＜b。
进一步地，供油通道包括：流道，流道设置在至少一个背压件上，流道包括第一流道和第二流道，第一流道与第一槽段相连通，第二流道与第二槽段相连通；其中，第一流道与第一槽段相连通的第一开口的面积为a，第二流道与第二槽段相连通的第二开口的面积为b。
进一步地，泵体组件还包括转轴，转轴穿过两个背压件，供油通道还包括：油道，油道设置在转轴上，油道与第一流道相连通，油道与第二流道相连通。
进一步地，供油通道还包括：油腔，油腔设置在至少一个背压件上，油腔与油道相连通，油腔与流道相连通，以使油道通过油腔与第一流道相连通，油道通过油腔与第二流道相连通；其中，流道位于油腔与背压槽之间。
进一步地，背压槽还包括：第三槽段，第二槽段位于第三槽段与第一槽段之间；其中，第三槽段的宽度小于第二槽段的宽度。
进一步地，第三槽段与供油通道相连通。
进一步地，第三槽段与第二槽段相连通。
进一步地，第一流道的截面为圆形或多边型，和/或第二流道的截面为圆形或多边型。
进一步地，第一槽段为弧形槽，和/或第二槽段为弧形槽。
进一步地，两个背压件分别为上法兰和下法兰，背压槽设置在上法兰朝向下法兰的端面上；和/或背压槽设置在下法兰朝向上法兰的端面上。
进一步地，上法兰和下法兰上均设置有背压槽，上法兰上的背压槽在下法兰上的投影与下法兰上的背压槽相重合。
进一步地，两个背压件分别为上法兰和下法兰，背压槽设置在上法兰朝向下法兰的端面上，背压槽设置在下法兰朝向上法兰的端面上，下法兰上设置有至少部分的供油通道。
进一步地，泵体组件还包括：泵体，泵体的出油口与供油通道相连通，以使泵体将油箱内的油体输送到供油通道内。
根据本申请的另一方面，提供了一种压缩机，包括泵体组件，泵体组件为上述的泵体组件。
本申请的泵体组件通过减小第一槽段与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽内的进油量，以此降低滑片两端的压差，从而可以降低滑片头部的功率消耗。在泵体组件吸气阶段，滑片尾槽与第一槽段相连通，油体依次通过供油通道和第一槽段进入到滑片槽内，在进油过程中，由于第一槽段与供油通道相连通的面积较小，从而减少了滑片尾槽内的进油量，以此降低滑片两端的压差。在压缩阶段，滑片尾槽与第二槽段相连通，油体依次通过供油通道和第二槽段进入到滑片槽内，在进油过程中，由于第二槽段与供油通道 相连通的面积相要大于第一槽段与供油通道相连通的面积，从而增加了滑片尾槽内的进油量，以此保证滑片两侧的压差足以使滑片位于可靠位置。本申请的泵体组件通过减小第一槽段与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽内的进油量，以此降低滑片两端的压差，从而可以降低滑片头部的功率消耗，解决了现有技术中的泵体组件在吸气阶段滑片头部功耗较大的问题。
附图说明
构成本申请的一部分的说明书附图用来提供对本申请的进一步理解，本申请的示意性实施例及其说明用于解释本申请，并不构成对本申请的不当限定。在附图中：
图1示出了现有技术中的泵体组件的剖面结构示意图；
图2示出了根据本申请的泵体组件的实施例的分解结构示意图；
图3示出了根据本申请的泵体组件的剖面结构示意图；
图4示出了图3的泵体组件的A处的局部放大结构示意图；
图5示出了根据本申请的泵体组件的第一个状态的结构示意图；
图6示出了根据本申请的泵体组件的第二个状态的结构示意图；
图7示出了根据本申请的泵体组件的第三个状态的结构示意图；
图8示出了根据本申请的泵体组件的第四个状态的结构示意图；
图9示出了根据本申请的泵体组件的上法兰的第一个视角的结构示意图；
图10示出了根据本申请的泵体组件的上法兰的第二个视角的结构示意图；
图11示出了根据本申请的泵体组件的下法兰的第一个视角的结构示意图；
图12示出了根据本申请的泵体组件的下法兰的第二个视角的结构示意图；
图13示出了根据本申请的泵体组件的下法兰的第三个视角的结构示意图；
图14示出了根据本申请的泵体组件的下法兰的第四个视角的结构示意图；
图15示出了根据本申请的泵体组件的下法兰的剖面结构示意图；
图16示出了根据本申请的泵体组件的转轴的结构示意图；
图17示出了根据本申请的泵体组件的转轴的剖面结构示意图；
图18示出了根据本申请的泵体组件的泵体的第一个视角的结构示意图；
图19示出了根据本申请的泵体组件的泵体的第二个视角的结构示意图；
图20示出了根据本申请的泵体组件的泵体的剖面结构示意图。
其中，上述附图包括以下附图标记：
10、背压槽；11、第一槽段；12、第二槽段；13、第三槽段；20、转轴；21、滑片槽；22、油道；221、中心孔；222、径向孔；30、滑片；31、滑片尾槽；40、流道；41、第一流道；42、第二流道；50、油腔；60、上法兰；70、下法兰；80、泵体；90、气缸；100、螺钉；110、排气阀；120、吸气口。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本申请。
应该指出，以下详细说明都是例示性的，旨在对本申请提供进一步的说明。除非另有指明，本文使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
本申请提供了一种泵体组件，请参考图2至图20，泵体组件包括：供油通道，供油通道用于流通油体；背压件，背压件为两个，至少一个背压件上设置有背压槽10，背压槽10包括第一槽段11和与第一槽段11间隔设置的第二槽段12，第一槽段11与供油通道相连通，第二槽段12与供油通道相连通；其中，第一槽段11与供油通道相连通的面积为a，第二槽段12与供油通道相连通的面积为b，a＜b。
本申请的泵体组件通过减小第一槽段11与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽31内的进油量，以此降低滑片30两端的压差，从而可以降低滑片30头部的功率消耗。在泵体组件吸气阶段，滑片尾槽31与第一槽段11相连通，油体依次通过供油通道和第一槽段11进入到滑片槽21内，在进油过程中，由于第一槽段11与供油通道相连通的面积较小，从而减少了滑片尾槽31内的进油量，以此降低滑片30两端的压差。在压缩阶段，滑片尾槽31与第二槽段12相连通，油体依次通过供油通道和第二槽段12进入到滑片槽21内，在进油过程中，由于第二槽段12与供油通道相连通的面积相要大于第一槽段11与供油通道相连通的面积，从而增加了滑片尾槽31内的进油量，以此保证滑片30两侧的压差足以使滑片30位于可靠位置。本申请的泵体组件通过减小第一槽段11与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽31内的进油量，以此降低滑片30两端的压差，从而可以降低滑片30头部的功率消耗，解决了现有技术中的泵体组件在吸气阶段滑片头部功耗较大的问题。
在本实施例中，泵体组件还包括：转轴20，转轴20穿过两个背压件，转轴20上设置有滑片槽21；滑片30，滑片30可滑动地设置在滑片槽21内，滑片30与滑片槽21之间形成滑片尾槽31，滑片尾槽31与第一槽段11可通断地设置，滑片尾槽31与第二槽段12可通断地设置。
在本实施例中，在转轴20带动滑片30转动过程中，在泵体组件吸气阶段，滑片尾槽31与第一槽段11相连通，相应地，在压缩阶段，滑片尾槽31与第二槽段12相连通。
为了能够使得第一槽段11与供油通道相连通的面积小于第二槽段12与供油通道相连通的面积，如图4和图13所示，供油通道包括：流道40，流道40设置在至少一个背压件上，流道40包括第一流道41和第二流道42，第一流道41与第一槽段11相连通，第二流道42与第二槽段12相连通；其中，第一流道41与第一槽段11相连通的第一开口的面积为a，第二流道42与第二槽段12相连通的第二开口的面积为b。
在本实施例中，第一流道41与第一槽段11相连通的第一开口的面积为a，即第一流道41的出油口的面积为a，第二流道42与第二槽段12相连通的第二开口的面积为b，即第二流道42的出油口的面积为b。
为了能够将泵体组件内的润滑油引入到流道40内，如图2和图4所示，泵体组件还包括转轴20，转轴20穿过两个背压件，供油通道还包括：油道22，油道22设置在转轴20上，油道22与第一流道41相连通，油道22与第二流道42相连通。
在本实施例中，通过在转轴20上设置有油道22，油道22的进油口流入润滑油，油道22的出油口与第一流道41和第二流道42均连通，从而使得泵体组件内的润滑油通过油道22流入到第一流道41和第二流道42内，然后进入相应的第一槽段11和第二槽段12内。
为了能够在背压件内存储一定的润滑油，如图4和图12所示，供油通道还包括：油腔50，油腔50设置在至少一个背压件上，油腔50与油道22相连通，油腔50与流道40相连通，以使油道22通过油腔50与第一流道41相连通，油道22通过油腔50与第二流道42相连通；其中，流道40位于油腔50与背压槽10之间。
在本实施例中，通过在背压件上设置有油腔50，且油腔50与油道22相连通，油腔50与流道40相连通，以使油道22通过油腔50与第一流道41相连通，油道22通过油腔50与第二流道42相连通，即油道22内的润滑油进入油腔50内进行存储，然后流入到第一流道41和第二流道42内。
在本实施例中，流道40位于油腔50与背压槽10之间，油腔50的内壁为圆弧。
为了能够防止滑片30在排气阶段出现回退量过大而造成碰撞的现象，如图13所示，背压槽10还包括：第三槽段13，第二槽段12位于第三槽段13与第一槽段11之间；其中，第三槽段13的宽度小于第二槽段12的宽度。
在本实施例中，通过在背压槽10上设置有第三槽段13，且第三槽段13的宽度小于第二 槽段12的宽度，在排气阶段，可以保证滑片槽21内具有足够的油压，即滑片槽21内产生憋油。
在本实施例中，第三槽段13与滑片尾槽31可通断地设置，即在排气阶段，第三槽段13与滑片尾槽31相连通，为了满足泵体组件的各个阶段，第二槽段12位于第三槽段13与第一槽段11之间。
为了防止滑片槽21内憋油过高，第三槽段13与供油通道相连通。
在本实施例中，由于第三槽段13的宽度小于第二槽段12的宽度，即在排气阶段，滑片槽21内产生憋油。但考虑到滑片槽21内憋油过高时会使得滑片30两端的压差过高，从而造成滑片30头部的功率消耗过大，故将第三槽段13与供油通道相连通，从而可以使得滑片槽21内的润滑油可以通过供油通道进行部分的泄露。
优选地，第三槽段13与第二槽段12相连通。
在本实施例中，第三槽段13与第二流道42相连通。
可选地，第三槽段13与第二槽段12间隔设置，流道40还包括第三流道，第三槽段13与第三流道相连通，以使第三槽段13通过第三流道与油道22相连通。
在本实施例中，第三槽段13为弧形槽。
针对第一流道41和第二流道42的具体结构，第一流道41的截面为圆形或多边型，第二流道42的截面为圆形或多边型。
可选地，第一流道41和第二流道42的截面为四边形。
优选地，第一槽段11为弧形槽，和/或第二槽段12为弧形槽。
针对两个背压件的具体分布，如图2和图3所示，两个背压件分别为上法兰60和下法兰70，背压槽10设置在上法兰60朝向下法兰70的端面上；背压槽10设置在下法兰70朝向上法兰60的端面上。
在本实施例中，两个背压件分别为上法兰60和下法兰70，滑片30位于上法兰60和下法兰70之间。其中，背压槽10设置在上法兰60朝向下法兰70的端面上，背压槽10设置在下法兰70朝向上法兰60的端面上，即上法兰60和下法兰70中的至少一个设置有背压槽10。
优选地，上法兰60和下法兰70上均设置有背压槽10，上法兰60上的背压槽10在下法兰70上的投影与下法兰70上的背压槽10相重合。
在本实施例中，上法兰60和下法兰70上均设置有背压槽10，且上法兰60上的背压槽10和下法兰70上的背压槽10具体结构相一致。其中，下法兰70和上法兰60上设置有流道40。
针对泵体组件的一个具体实施例，两个背压件分别为上法兰60和下法兰70，背压槽10 设置在上法兰60朝向下法兰70的端面上，背压槽10设置在下法兰70朝向上法兰60的端面上，下法兰70上设置有至少部分的供油通道。
在本实施例中，上法兰60和下法兰70上均设置有背压槽10，且下法兰70上设置有流道40和油腔50。
为了能够保证供油通道内具有充足的润滑油，如图2和图4所示，泵体组件还包括：泵体80，泵体80的出油口与供油通道相连通，以使泵体80将油箱内的油体输送到供油通道内。
在本实施例中，通过在泵体组件上设置有泵体80，且泵体80的出油口与供油通道相连通，从而可以使泵体80将油箱内的油体输送到供油通道内，以此保证滑片槽21内充满润滑油。
针对泵体80的具体结构，如图18至20所示，泵体80为油泵，油泵为齿轮油泵。
在本实施例中，针对转轴20的具体结构，如图16和图17所示，其中，油道22包括：中心孔221和与中心孔221相连通的径向孔222，中心孔221与泵体80的出油口相连通，径向孔222与油腔50相连通。
本申请还提供了一种压缩机，包括泵体组件，泵体组件为上述的泵体组件。
滑片式压缩机吸气是一段角度，且由于吸气阶段滑片头部处在吸气压力下，因此滑片尾部和头部的压差力(F背-F头)最大，另外，吸气阶段滑片随着滑片槽是伸出运动，滑片头部的旋转半径是增大过程，即滑片头部线速度越来越大，根据W＝f·v，滑片头部功耗在吸气阶段不仅较大，且是个增大的过程，因此吸气阶段的滑片头部功耗在滑片整个运行周期中占有较大的比重，降低该处的功耗对降低整机功耗有显著的作用。
此外，由于滑片背压油流道的沿程压降及过压缩的存在，常规方案排气阶段滑片尾部背压可能无法满足保证滑片始终贴紧气缸内壁的要求，滑片有脱离的风险，容易造成滑片撞击，影响滑片可靠性及压缩机整机的噪音振动，因此提高排气段背压，保证滑片不退回对压缩机可靠性和噪音振动至关重要。
本申请的压缩机是一种全新的滑片式压缩机，滑片式压缩机的尾部背压控制方式就是通过将传统背压槽分为吸气段、压缩段、排气段三段，每段对应的背压不一样，从而实现在滑片头部压力较低的吸气段提供较低的背压，在头部压力高于排气压力的排气段提供高于排气压力的背压。
本申请将滑片背压槽分为三段，吸气段、压缩段、排气段，其中吸气段与压缩段和排气段有过渡段分隔开，避免后者的高压油连通到吸气段，影响吸气段背压。
滑片背压槽采用三段背压，吸气段采用低背压降低功耗，压缩段采用排气压力的高背压，排气段采用憋油槽设计，产生高于排气压力的背压。
本申请三段背压的压力控制是通过：背压油(P)从主路分为两路分别通往吸气段背压槽(第一槽段11)、压缩段背压槽(第二槽段12)和排气段背压槽(第三槽段13)，其中，通往吸气段背压槽的油路(第一流道41)狭小，通过小口径的油路实现对油的节流降压(ΔP1)， 实现吸气段的低背压(P-ΔP1)。而通往压缩、排气段背压槽的油路是大口径油路(第二流道42)，防止油产生沿程损失，保证背压油不产生压降，实现压缩段的高背压(P)；排气段滑片做退回运动，此次滑片尾部滑片槽空间随着滑片运动而减小，设计此处的背压槽为浅窄的小槽，由于油的不可压性，滑片槽尾部会产生一个憋压(ΔP2)，实现排气段的超高背压(P+ΔP2)，浅窄背压槽既能实现滑片退回对油的憋压提升背压的效果，又能给予适当的泄油通路，防止油压憋的过高。
本申请的吸气段为从吸气开始到压缩开始的阶段，压缩段为压缩开始到排气开始阶段，排气段为排气开始到排气结束阶段，其各自的角度范围因不同压缩机泵体结构而有所不同。
本申请通往吸气段的油路截面积设计通过其油路长度和最低运行频率来确定，保证在油最低转速、最低油流速情况下还能实现理想的压降ΔP1，本申请通往压缩、排气段的油路截面积设计保证在最高运行频率、最高油流速的情况下也不产生油的沿程压降。
本申请排气段憋油槽设计应满足在最低运行频率时能保证足够的憋油压ΔP2，在最高运行频率时能保证足够的泄油量，防止ΔP2过高。
本申请在上、下法兰均开设对称的背压槽，以保证背压的稳定性，能有效防止滑片上下端受力不均偏斜。
本申请供油由主轴(转轴20)底部油泵主动供应，保证每时每刻油量都能充满整个滑片背压腔，为排气段的憋油提供前提条件。
本申请通过三段背压结构能实现降低吸气阶段滑片背压，从而降低滑片头部功耗，排气阶段通过提高滑片背压，保证滑片不脱离，实现滑片背压的灵活控制，改善滑片可靠性和压缩机噪音振动，提高压缩机整机性能。
本申请结构简单，零部件加工和装配简单易于实现。
如图2是本申请的泵体组件的爆炸图，包括主轴(转轴20)、气缸90、上法兰60、下法兰70、油泵、滑片30、螺钉100、排气阀110等零件。
在本实施例中，如图9至图15所示，法兰端面上均开设有背压槽10，背压槽是具有一定深度的环状槽，背压槽分为吸气段、压缩段和排气段三段，其中，排气段背压槽是相对浅窄的憋油槽，另外吸气段前后分别有与压缩段和排气段隔离的过渡段。
在本实施例中，主轴上开设有供油流通的中心孔221和径向孔222，油泵为齿轮油泵，与主轴通过主轴底部的D型小轴装配。
本申请的吸气段油路(流道40)，吸气段油路、压缩、排气段油路为具有一定长度和横截面的直孔，且均设置在下法兰70上，如图15所示。
具体实施方式：
阶段一：当压缩机运行主轴旋转时，装配在主轴底部的油泵会旋转将油泵入到中心孔内， 随着主轴的旋转，中心孔的油会在离心力的作用下通过主轴上的径向孔进入下法兰与油泵构成的油腔中，再分别通过吸气段油路和压缩、排气段油路进入法兰的背压槽。吸气段的油压由于经过吸气段油路的节流降压ΔP1，其油压较低为P-ΔP1。其中，冷媒经过吸气口120进入压缩腔。
阶段二：图5至图8是泵体实际运动过程，以其中一个滑片30为对象(图中具有30标号的滑片)，如图5当滑片在吸气槽起始处，即零度角附近时，滑片尾槽(滑片槽21)刚与吸气段背压槽连通，随着主轴旋转运动，滑片30到达图6位置，此时为吸气结束，滑片尾槽即将与吸气段背压槽断开，并将进入过渡区。
阶段三：随着滑片继续运动经过图6，滑片尾槽将脱离过渡区并与压缩段背压槽连通，经过一段角度后，泵体内冷媒经过压缩后即将进行排气，此时滑片尾槽将脱离压缩段并进入排气段。
阶段四：当滑片继续随着旋转方向运动，滑片进入排气段并到达图7、图8位置，这整个过程滑片尾槽容积V尾是逐渐减小的，这个过程随着V尾的减小，滑片尾槽内部的油会被压缩并从憋油槽流出，但由于滑片旋转速度较快V尾容积变化率大，加上憋油槽横截面积较小和油的不可压性，滑片尾槽内会形成比原始压力较高的一个压力(P-ΔP2)，因此背压比常规方案有所提高。
随着滑片继续运动，滑片到达图5位置，完成一个完整周期，即完成一个吸气-压缩-排气过程。
从以上的描述中，可以看出，本申请上述的实施例实现了如下技术效果：
本申请的泵体组件通过减小第一槽段11与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽31内的进油量，以此降低滑片30两端的压差，从而可以降低滑片30头部的功率消耗。在泵体组件吸气阶段，滑片尾槽31与第一槽段11相连通，油体依次通过供油通道和第一槽段11进入到滑片槽21内，在进油过程中，由于第一槽段11与供油通道相连通的面积较小，从而减少了滑片尾槽31内的进油量，以此降低滑片30两端的压差。在压缩阶段，滑片尾槽31与第二槽段12相连通，油体依次通过供油通道和第二槽段12进入到滑片槽21内，在进油过程中，由于第二槽段12与供油通道相连通的面积相要大于第一槽段11与供油通道相连通的面积，从而增加了滑片尾槽31内的进油量，以此保证滑片30两侧的压差足以使滑片30位于可靠位置。本申请的泵体组件通过减小第一槽段11与供油通道相连通的面积，在泵体组件吸气阶段可以减少滑片尾槽31内的进油量，以此降低滑片30两端的压差，从而可以降低滑片30头部的功率消耗，解决了现有技术中的泵体组件在吸气阶段滑片头部功耗较大的问题。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式例如能够以除了在这里图示或描述的那些以外的顺序实施。此外，术语“包括”和“具有”以及他们的任何变形，意图在于 覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、系统、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
以上所述仅为本申请的优选实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (20)

  1. 一种泵体组件，其特征在于，包括：
    供油通道，所述供油通道用于流通油体；
    背压件，所述背压件为两个，至少一个所述背压件上设置有背压槽(10)，所述背压槽(10)包括第一槽段(11)和与所述第一槽段(11)间隔设置的第二槽段(12)，所述第一槽段(11)与所述供油通道相连通，所述第二槽段(12)与所述供油通道相连通；
    其中，所述第一槽段(11)与所述供油通道相连通的面积为a，所述第二槽段(12)与所述供油通道相连通的面积为b，a＜b。
  2. 根据权利要求1所述的泵体组件，其特征在于，所述供油通道包括：
    流道(40)，所述流道(40)设置在至少一个所述背压件上，所述流道(40)包括第一流道(41)和第二流道(42)，所述第一流道(41)与所述第一槽段(11)相连通，所述第二流道(42)与所述第二槽段(12)相连通；
    其中，所述第一流道(41)与所述第一槽段(11)相连通的第一开口的面积为a，所述第二流道(42)与所述第二槽段(12)相连通的第二开口的面积为b。
  3. 根据权利要求2所述的泵体组件，其特征在于，所述泵体组件还包括转轴(20)，所述转轴(20)穿过两个所述背压件，所述供油通道还包括：
    油道(22)，所述油道(22)设置在所述转轴(20)上，所述油道(22)与所述第一流道(41)相连通，所述油道(22)与所述第二流道(42)相连通。
  4. 根据权利要求3所述的泵体组件，其特征在于，所述供油通道还包括：
    油腔(50)，所述油腔(50)设置在至少一个所述背压件上，所述油腔(50)与所述油道(22)相连通，所述油腔(50)与所述流道(40)相连通，以使所述油道(22)通过所述油腔(50)与所述第一流道(41)相连通，所述油道(22)通过所述油腔(50)与所述第二流道(42)相连通；
    其中，所述流道(40)位于所述油腔(50)与所述背压槽(10)之间。
  5. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述背压槽(10)还包括：
    第三槽段(13)，所述第二槽段(12)位于所述第三槽段(13)与所述第一槽段(11)之间；
    其中，所述第三槽段(13)的宽度小于所述第二槽段(12)的宽度。
  6. 根据权利要求5所述的泵体组件，其特征在于，所述第三槽段(13)与所述供油通道相连通。
  7. 根据权利要求5所述的泵体组件，其特征在于，所述第三槽段(13)与所述第二槽段(12)相连通。
  8. 根据权利要求2所述的泵体组件，其特征在于，所述第一流道(41)的截面为圆形或多边型，所述第二流道(42)的截面为圆形或多边型。
  9. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述第一槽段(11)为弧形槽，所述第二槽段(12)为弧形槽。
  10. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，两个所述背压件分别为上法兰(60)和下法兰(70)，所述背压槽(10)设置在所述上法兰(60)朝向所述下法兰(70)的端面上；所述背压槽(10)设置在所述下法兰(70)朝向所述上法兰(60)的端面上。
  11. 根据权利要求10所述的泵体组件，其特征在于，所述上法兰(60)和所述下法兰(70)上均设置有所述背压槽(10)，所述上法兰(60)上的背压槽(10)在所述下法兰(70)上的投影与所述下法兰(70)上的所述背压槽(10)相重合。
  12. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，两个所述背压件分别为上法兰(60)和下法兰(70)，所述背压槽(10)设置在所述上法兰(60)朝向所述下法兰(70)的端面上，所述背压槽(10)设置在所述下法兰(70)朝向所述上法兰(60)的端面上，所述下法兰(70)上设置有至少部分的所述供油通道。
  13. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述泵体组件还包括：
    泵体(80)，所述泵体(80)的出油口与所述供油通道相连通，以使所述泵体(80)将油箱内的油体输送到所述供油通道内。
  14. 根据权利要求2所述的泵体组件，其特征在于，所述第一流道(41)的截面为圆形或多边型。
  15. 根据权利要求2所述的泵体组件，其特征在于，所述第二流道(42)的截面为圆形或多边型。
  16. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述第一槽段(11)为弧形槽。
  17. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述第二槽段(12)为弧形槽。
  18. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，两个所述背压件分别为上法兰(60)和下法兰(70)，所述背压槽(10)设置在所述上法兰(60)朝向所述下法兰(70)的端面上。
  19. 根据权利要求1至4中任一项所述的泵体组件，其特征在于，所述背压槽(10)设置在所述下法兰(70)朝向所述上法兰(60)的端面上。
  20. 一种压缩机，包括泵体组件，其特征在于，所述泵体组件为权利要求1至18中任一项所述的泵体组件。
PCT/CN2019/102052 2018-09-12 2019-08-22 泵体组件及具有其的压缩机 WO2020052418A1 (zh)

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