WO2016086396A1 - 低背压旋转式压缩机 - Google Patents

低背压旋转式压缩机 Download PDF

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Publication number
WO2016086396A1
WO2016086396A1 PCT/CN2014/093060 CN2014093060W WO2016086396A1 WO 2016086396 A1 WO2016086396 A1 WO 2016086396A1 CN 2014093060 W CN2014093060 W CN 2014093060W WO 2016086396 A1 WO2016086396 A1 WO 2016086396A1
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WO
WIPO (PCT)
Prior art keywords
oil supply
chamber
cylinder
oil
rotary compressor
Prior art date
Application number
PCT/CN2014/093060
Other languages
English (en)
French (fr)
Inventor
高斌
喻继江
郭宏
Original Assignee
广东美芝制冷设备有限公司
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 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to PCT/CN2014/093060 priority Critical patent/WO2016086396A1/zh
Priority to KR1020157023406A priority patent/KR101710350B1/ko
Priority to EP14907244.9A priority patent/EP3228868B1/en
Priority to AU2014413252A priority patent/AU2014413252B2/en
Priority to KR1020177004260A priority patent/KR101751901B1/ko
Priority to US15/318,942 priority patent/US10458410B2/en
Publication of WO2016086396A1 publication Critical patent/WO2016086396A1/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
    • 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
    • F04C29/026—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
    • 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
    • F04C18/356—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 outer member
    • 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
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • 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
    • F01C21/08—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
    • F04C18/356—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 outer member
    • F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces 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
    • F04C18/356—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 outer member
    • F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/0092—Removing solid or liquid contaminants from the gas under pumping, e.g. by filtering or deposition; Purging; Scrubbing; Cleaning
    • 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
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2240/30—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
    • F04C2240/50—Bearings

Definitions

  • This invention relates to the field of compressors, and more particularly to a low back pressure rotary compressor.
  • the tail end of the slider needs to be located.
  • the area is designed to form a vane cavity that is sealed from the inner diameter of the housing and provides a relatively high pressure environment for the vane cavity to ensure intimate contact of the vane tip with the outer diameter of the piston.
  • the sliding vane cavity needs to be sealed from the inside of the casing, lubrication cannot be achieved by the oil pool inside the casing. Therefore, it is also necessary to design a reasonable oil passage of the vane cavity to ensure lubrication and sealing of the sliding vane.
  • the volume of the vane chamber will also change periodically.
  • the vane cavity There is a maximum pressure, and when the volume of the vane chamber is maximum, the pressure in the vane chamber has a minimum. If the structural volume design of the sliding vane cavity is unreasonable, it may occur that when the maximum pressure of the sliding vane chamber is too large, the power consumption of the compressor rises, and even the current is abnormally large, causing the motor to trip, and may also appear as a sliding vane.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • Ben The invention proposes a low back pressure rotary compressor in which the pressure fluctuation of the sliding vane chamber is not excessive or too small.
  • a low back pressure rotary compressor includes: a housing having an exhaust port and a return air port; a compression mechanism, the compression mechanism being disposed in the housing, the compressing
  • the mechanism includes a cylinder assembly, a piston, a sliding piece, a main bearing and a sub-bearing, the main bearing and the sub-bearing being respectively disposed on both end faces of the cylinder assembly, the cylinder assembly including at least one cylinder, each of the a piston is disposed in the cylinder, a front end of the sliding plate is abutted against an outer peripheral wall of the piston, the cylinder further has a sliding plate cavity, the sliding piece cavity has an oil supply hole, and the sliding piece reciprocates The trailing end of the slider projects into or out of the slider cavity when moving such that the internal volume of the slider cavity changes between a maximum volume V2 and a minimum volume V1; for discharging from the cylinder
  • An oil separator for separating oil and gas; an oil pool for containing lubricating oil separated by the oil separator
  • the low back pressure rotary compressor according to the embodiment of the present invention satisfies the following relationship by making the ratio of the maximum volume V2 of the slider chamber to the minimum volume V1: 35% ⁇ V1/V2 ⁇ 85%, so the pressure fluctuation of the slider chamber It will not be too large or too small, and it can ensure the close sealing of the sliding piece and the piston, so as to better meet the force requirements of the sliding piece, achieve better compressor performance.
  • the ratio of the maximum volume V2 to the minimum volume V1 satisfies the following relationship: 50% ⁇ V1/V2 ⁇ 70%.
  • a vertical distance from a lowermost end of the oil supply hole to a bottom wall of the sliding chamber is d, and a corresponding height of the cylinder is H, wherein 0 ⁇ d ⁇ 0.8H .
  • the ratio of the area S3 of the oil supply hole to the minimum volume V1 of the slider cavity satisfies the following relationship: 0.1 ⁇ S3 / V1 ⁇ 10.5.
  • the ratio of the area S3 of the oil supply hole to the minimum volume V1 of the slider cavity The following relationship is satisfied: 2 ⁇ S3 / V1 ⁇ 6.5.
  • an area of the inlet of the oil supply path is S1
  • a minimum flow area of the oil supply path is S2
  • the S1, S2, and S3 satisfy the following relationship: S2 ⁇ S1, S2 ⁇ S3 .
  • the oil supply hole is disposed at a top of the sliding chamber, and a ratio of an area S3 of the oil supply hole to a minimum volume V1 of the sliding chamber cavity satisfies the following relationship: S3/ V1 ⁇ 4.5.
  • the oil separator is arranged outside the housing and/or in the compression mechanism.
  • the cylinder assembly includes an upper cylinder, a lower cylinder, and a middle partition, the middle partition being disposed between the upper cylinder and the lower cylinder, the upper cylinder sliding
  • the vane chambers and the vane chambers of the lower cylinder are in communication with the oil sump, respectively.
  • the slider chamber of the upper cylinder and the slider chamber of the lower cylinder communicate through an intermediate oil supply path penetrating the intermediate partition.
  • an opening area of the sliding chamber of the upper cylinder of the intermediate oil supply path is S4, and an opening area of the sliding chamber of the intermediate oil supply path of the lower cylinder is S5, the S4 ⁇ S5.
  • FIG. 1 is a schematic view of a low back pressure rotary compressor in which a compressor is a single cylinder compressor, in accordance with one embodiment of the present invention
  • FIG. 2 is a schematic view of a slide oil supply path on a sub-bearing according to an embodiment of the present invention
  • FIG. 3 is a schematic view of the cooperation of a cylinder, a sliding piece and a piston according to an embodiment of the present invention, wherein the internal volume of the sliding chamber is in a minimum volume state;
  • FIG. 4 is a schematic view of the cooperation of a cylinder, a sliding piece and a piston according to an embodiment of the present invention, wherein the sliding piece cavity The internal volume is in the maximum volume state;
  • Figure 5 is a schematic view of a low back pressure rotary compressor in accordance with another embodiment of the present invention, wherein the compressor is a single cylinder compressor;
  • Figure 6 is a schematic view of a low back pressure rotary compressor in accordance with one embodiment of the present invention, wherein the compressor is a two cylinder compressor;
  • Figure 7 is a schematic view of a low back pressure rotary compressor in accordance with another embodiment of the present invention, wherein the compressor is a two cylinder compressor;
  • Figure 8 is a schematic view of a low back pressure rotary compressor in accordance with still another embodiment of the present invention, wherein the compressor is a two cylinder compressor;
  • Figure 9 is a schematic view of a low back pressure rotary compressor in accordance with still another embodiment of the present invention, wherein the compressor is a two cylinder compressor;
  • Figure 10 is a graph showing the change in the volume of the slider cavity
  • Figure 11 is a schematic view showing the fluctuation trend of the pressure in the sliding chamber
  • Figure 12 is a schematic view of the force of the crankshaft
  • Figure 13 is a graph showing the relationship between the ratio of the maximum volume V2 and the minimum volume V1 of the vane chamber to the energy efficiency ratio of the compressor according to an embodiment of the present invention.
  • 100 is a low back pressure rotary compressor
  • 1 is the internal space of the casing
  • 2 is the sliding cavity
  • 3 is the oil supply path of the sliding plate
  • 4 is the sliding groove
  • 5 is the oil pool
  • 6 is the exhaust hole
  • 10 is Housing
  • 11 is the main bearing
  • 12 is the cylinder
  • 13 is the piston
  • 14 is the sliding piece
  • 15 is the auxiliary bearing
  • 16 is the crankshaft
  • 17 is the cover plate
  • 18 is the oil separator
  • 21 is the stator
  • 22 is the rotor
  • H is the height of the cylinder
  • d is the distance from the oil supply hole of the sliding chamber to the bottom of the sliding chamber
  • P is the exhaust pressure.
  • P1 is the minimum pressure of the sliding cavity
  • P2 is the maximum pressure of the sliding cavity
  • V1 is the minimum volume of the sliding cavity
  • V2 is the maximum volume of the sliding cavity.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one piece; it may be a mechanical connection, or it may be an electrical connection or a communication with each other; it may be directly connected or indirectly connected through an intermediate medium, and may be an internal connection of two elements or an interaction relationship between two elements. Unless otherwise expressly defined. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • a low back pressure rotary compressor 100 according to an embodiment of the present invention will be described in detail below with reference to FIGS. 1-9, wherein the low back pressure rotary compressor 100 may be a single cylinder compressor or a two cylinder compressor.
  • a low back pressure rotary compressor 100 includes a housing 10, a compression mechanism, an oil separator 18, and an oil sump 5.
  • the casing 10 is provided with an exhaust port 6 and a return air port (not shown).
  • the compression mechanism is disposed in the housing 10, and the compression mechanism includes a cylinder assembly, a piston 13, a slide 14, a main bearing 11 and a sub-bearing 15, respectively, the main bearing 11 and the sub-bearing 15 are respectively disposed on both end faces of the cylinder assembly, and the cylinder assembly includes At least one cylinder 12 is provided with a piston 13 in each cylinder 12.
  • the front end of the slide 14 is abutted against the outer peripheral wall of the piston 13.
  • the cylinder 12 also has a vane chamber 2, and the vane chamber 2 has an oil supply hole and slides.
  • the trailing end of the slider 14 projects into or out of the slider chamber 2 as the sheet 14 reciprocates to cause the internal volume of the slider chamber 2 to vary between the maximum volume V2 and the minimum volume V1.
  • the oil separator 18 is for separating oil and gas from the refrigerant discharged from the cylinder 12.
  • the oil pool 5 is for holding the lubricating oil separated by the oil separator 18, and since the refrigerant discharged from the cylinder 12 is a high-pressure refrigerant, it is understood that the oil pool 5 is in a high-pressure environment.
  • the oil pool 5 communicates with the oil supply hole through the sliding oil supply path 3, wherein the ratio of the maximum volume V2 to the minimum volume V1 satisfies the following relationship: 35% ⁇ V1/V2 ⁇ 85%. Since the vane chamber 2 communicates with the oil pool 5, it can be seen that the vane chamber 2 is in a high pressure environment, so that the tip end of the vane 14 can be stopped against the outer peripheral wall of the piston 13.
  • the low back pressure rotary compressor 100 further includes an electric motor, a crankshaft 16 and the like.
  • the electric motor includes a stator 21 and a rotor 22, the stator 21 is fixed on the inner wall of the casing 10, and the stator 21 is jacketed on the rotor 22, and the rotor 22 is sleeved on the crankshaft 16 to drive the crankshaft 16 to rotate.
  • the piston 13 of each cylinder 12 is jacketed on the eccentric portion of the crankshaft 16.
  • the slider 14 is disposed in the vane slot 4 of the cylinder 12 and the leading end of the slider 14 is stopped.
  • the outer peripheral wall of the piston 13 partitions the inside of the cylinder 12 into an air suction chamber and a compression chamber.
  • the crankshaft 16 drives the piston 13 to perform eccentric motion in the corresponding cylinder 12.
  • the slide 14 reciprocates in the sliding slot 4, and when the slider 14 reciprocates, the tail of the slider 14 The end projects into the vane chamber 2 or projects out of the vane chamber 2, so that the internal volume of the vane chamber 2 also periodically changes with the reciprocating motion of the vane 14.
  • Figure 10 is a schematic view showing the change in the volume of the slider chamber 2 as the reciprocating motion of the slider 14 during the operation of the compressor.
  • the volume of the slider chamber 2 varies from V1 to V2, wherein the abscissa is the angle of rotation of the piston 13 with respect to the cylinder center.
  • the rotation angle of the crankshaft 16 is 0 degrees at this time, the volume of the slider chamber 2 is the smallest, and the minimum volume is V1, and as shown in FIG.
  • the crankshaft 16 rotates at an angle of 180 degrees, the volume of the slider chamber 2 is the largest, and the maximum volume is V2.
  • crank angle of the crankshaft 16 is 360 degrees (radial 2 ⁇ ), and the volume of the slider chamber 2 is returned to the minimum volume V1.
  • What is shown in Fig. 10 is the ideal pressure change period. In the actual compressor, due to the pressure loss and the pressure transfer process, the pressure fluctuation and the abscissa crankshaft 16 rotation angle may have a delay, but the periodic fluctuation The change attribute does not change.
  • V2 V1+2e*H*T
  • the sliding chamber 2 With the reciprocating motion of the slider 14, considering that the leakage gap of the sliding surface of the sliding plate 14 and the cylinder is extremely small, the sliding chamber 2 can be assumed to be a closed space except for the sliding oil supply path 3. .
  • the pressure in the vane chamber 2 fluctuates with the change of the volume of the vane chamber 2, and if the pressure of the inlet oil pool 5 of the vane oil supply path 3 is P, the volume of the vane chamber 2 changes.
  • Slide The pressure in the chamber 2 will have pressure fluctuations ranging from P1 to P2, which is completely different from the conventional high-pressure rotary compressor in which the vane chamber is open to the internal space of the casing.
  • the outlet of the slide oil supply path 3 in the vane chamber 2 may have a certain influence on the pressure fluctuation, but in general, the vane chamber 2
  • the trend of internal pressure fluctuations is shown in Figure 11.
  • Fig. 11 in general, with the reciprocating motion of the slider 14, when the volume of the slider chamber 2 is the smallest, the pressure reaches the maximum P2, and when the volume of the slider chamber 2 is the largest, the pressure reaches the minimum value P1, as opposed to
  • the oil supply pressure P of the vane chamber 2 has a relationship of P1 ⁇ P ⁇ P2.
  • fluctuations in pressure and the angle of rotation of the crankshaft 16 may also cause delays, the fluctuations of which are primarily affected by volume changes.
  • crankshaft 16 is rotated by the rotational torque input by the motor, and the crankshaft 16 also has a resistance moment M during operation, and the resistance torque M is composed of several parts, as shown in FIG. ,include:
  • Mn the resistance torque formed by the force Fn of the apex 14 acting on the outer diameter of the piston 13
  • Mn is the resistance torque formed by the force Fn of the tip end of the slider 14 acting on the outer diameter of the piston 13, and in the low back pressure rotary compressor, the force analysis of the slider 14 is known to be slippery.
  • the gas force Fc at the end of the sheet 14 is one of the important factors affecting the force Fn of the tip end of the slider 14 acting on the outer diameter of the piston 13.
  • the gas force Fc at the tail of the slider 14 is obtained as follows:
  • the gas force Fc at the tail portion of the slider 14 is mainly determined by the pressure Pc of the slider chamber 2 in a certain configuration. According to the above analysis, the gas pressure of the slider chamber 2 fluctuates within the range of P1 to P2, and therefore, the gas force Fc at the tail of the slider 14 also fluctuates.
  • the force of the slide 14 pressing the piston 13 is kept within a suitable range, so as to avoid excessive or excessive resistance and leakage and collision at the time of excessive rotation, and therefore, for the tail portion of the slider 14
  • a suitable range for gas pressure there is also a suitable range for gas pressure.
  • the gas pressure of the vane chamber 2 that is, the range of the gas pressure at the tail of the vane 14 is mainly affected by the supply pressure P and the volume change ranges V1 and V2 of the vane chamber 2, the condition can be adjusted by adjusting P and V1, V2.
  • Fig. 13 is a view showing the relationship between the running performance of the low back pressure rotary compressor 100, that is, the ratio of the COP to the volume change range V1 and V2 of the vane chamber 2, i.e., V1/V2, as follows:
  • V1 is the minimum volume of the vane chamber 2
  • V2 is the vane.
  • the maximum volume of the cavity 2 can be designed by structure so that the relationship between V1 and V2 is set to:
  • V1/V2 The relationship between the energy efficiency ratio (COP) of the low pressure rotary compressor of the housing 10 is as shown in Fig. 13:
  • a suitable force Fn of the flank 14 acting on the outer diameter of the piston 13 can be obtained to ensure better performance of the compressor under most working conditions. And it can ensure the close sealing of the sliding piece 14 and the piston 13, because in the case of the maximum volume and the minimum volume ratio of the sliding piece chamber 2, the pressure fluctuation of the sliding piece chamber 2 is not excessive or too small.
  • the amplitudes of P2 and P1 with respect to P are within a reasonable range, so that better compressor performance is achieved while better meeting the force requirements of the slider 14.
  • the slider chamber 2 is designed such that the ratio of the maximum volume V2 to the minimum volume V1 satisfies the following relationship: 50% ⁇ V1/V2 ⁇ 70%.
  • the low back pressure rotary compressor 100 satisfies the following relationship by making the ratio of the maximum volume V2 of the vane chamber 2 to the minimum volume V1: 35% ⁇ V1/V2 ⁇ 85 Therefore, the pressure fluctuation of the sliding vane chamber 2 is not excessively large or too small, and the sealing and sealing of the sliding piece 14 and the piston 13 can be ensured, so that the better satisfying the force requirement of the sliding piece 14 is achieved. Compressor performance.
  • the oil storage condition in the vane chamber 2 also affects the pressure fluctuation of the vane chamber 2. This is because the lubricating oil is a liquid and is an incompressible product. If the oil content of the sliding vane chamber 2 is excessive and the sliding piece 14 reciprocates, the resistance of the compressed lubricating oil will be extremely large, thereby affecting the compression. The performance and wear of the machine, in extreme cases, even caused the compressor to run out due to excessive resistance during the operation.
  • the second type the oil supply hole is disposed in the middle of the sliding chamber 2, mainly considering that the proper oil storage of the sliding chamber 2 can improve the lubrication of the sliding piece 14 and the sealing of the mating surface.
  • the opening height d of the oil supply hole of the vane chamber 2 is designed. It is 0 ⁇ d ⁇ 0.8 * H.
  • the oil supply hole may be disposed at the bottom or the middle of the sliding chamber 2, the vertical distance from the lowermost end of the oil supply hole to the bottom wall of the sliding chamber 2 is d, and the height of the corresponding cylinder 12 is H, wherein 0 ⁇ d ⁇ 0.8H.
  • the oil stored in the vane chamber 2 can be recovered and buffered through the oil supply hole, thereby avoiding the performance and reliability problems of the compressor caused by the sliding of the lubricating oil of the vane 14. Therefore, the size design of the oil supply hole will also affect the recovery buffer of the oil storage.
  • the design of the opening area of the reasonable oil supply hole is related to the volume of the sliding chamber 2.
  • the oil supply hole of the sliding chamber 2 and the oil supply path of the sliding oil supply path 3 are realized. Recycling buffer.
  • the oil supply hole is disposed at the bottom or the middle of the sliding chamber 2, in general, if the area of the oil supply hole is S3 (unit: mm 2 ), when it is the smallest volume V1 of the sliding chamber 2: cm 3
  • the numerical ratio is 0.1 ⁇ S3 / V1 ⁇ 10.5
  • the pressure fluctuation of the vane chamber 2 of the low back pressure rotary compressor 100 will be within an acceptable range, and the stable and reliable operation of the compressor can be ensured.
  • the numerical ratio of the area S3 (unit: mm 2 ) of the oil supply hole to the minimum volume V1 (unit: cm 3 ) of the slider chamber 2 can be designed to be 2 ⁇ S3 / V1 ⁇ 6.5.
  • the oil supply hole of the slider chamber 2 is disposed at the top of the slider chamber 2, it is necessary to ensure good oil return performance of the oil supply hole.
  • the area of the oil supply hole S3 can be designed (unit: mm 2
  • the numerical ratio of the minimum volume V1 (unit: cm 3 ) to the vane chamber 2 is: S3 / V1 ⁇ 4.5, so that the area of the oil supply hole is sufficiently larger than the minimum volume of the vane chamber 2.
  • the vane oil supply path 3 as shown in FIG. 2, if the inlet area of the vane oil supply path 3 is S1, the minimum flow area of the vane oil supply path 3 is S2, and the vane oil supply path 3
  • the outlet of the oil supply hole is S3
  • the lubricating oil input and output oil supply paths can be more easily realized, thereby ensuring that the sliding oil supply path 3 is provided to the sliding chamber 2
  • the role of oil quantity and recovery buffer That is, the design requires that the area relationship of each part of the oil supply path 3 is: S2 ⁇ S1, and S2 ⁇ S3. When the equal sign is established, the processing and manufacture of the slide oil supply path 3 can be simplified.
  • the oil separator 18 can be disposed external to the housing 10 and/or within the compression mechanism. Specifically, the setting of the oil separator 18 is divided into the following cases:
  • the oil separator 18 is one and disposed outside the casing 10
  • the oil pool 5 is located at the bottom of the oil separator 18, and the oil separator 18 is in communication with the vent hole 6 of the compressor, and each of the vane chambers 2 is in communication with the oil pool 5.
  • the low back pressure rotary compressor 100 is a single cylinder compressor.
  • the oil supply hole is located at the bottom of the slide chamber 2, and the oil separator 18 is disposed at the sub bearing 15 and the cover plate 17. Defined inside the exhaust chamber.
  • the low back pressure rotary compressor 100 is a single cylinder compressor, and the oil supply hole is located at the top of the vane chamber 2, and the oil separator 18 is disposed in the exhaust chamber in the main bearing 11.
  • the low back pressure rotary compressor 100 is a two-cylinder compressor, and the main bearing 11 and An oil separator 18 and an oil pool 5 are provided on the sub-bearings 15, respectively.
  • the low back pressure rotary compressor 100 is a two-cylinder compressor, and the first oil separator is disposed in the exhaust chamber of the main bearing or the auxiliary bearing and is used to separate the first oil separator.
  • the first oil pool of the lubricating oil is provided, and a second oil separator is arranged outside the casing 10, and a second oil pool is arranged at the bottom of the second oil separator, and the sliding chambers of the two cylinders are respectively first
  • the oil pools are connected to the second oil pool.
  • a low back pressure rotary compressor 100 in accordance with several different embodiments of the present invention will now be described in detail with reference to FIGS. 1 and 5-9.
  • a low back pressure rotary compressor 100 includes a housing 10, a motor, and a compression mechanism.
  • the housing 10 defines an internal space 1 in communication with the intake port.
  • the motor is disposed at an upper portion of the internal space 1.
  • the motor is composed of a stator 21 and a rotor 22, wherein the rotor 22 is coupled to the crankshaft 16 to drive the crankshaft 16 for rotational movement.
  • the compression mechanism includes a cylinder 12, a piston 13 and a slider 14 disposed in the cylinder 12, a crankshaft 16 that drives the piston 13 to rotate eccentrically, and a main bearing 11 and a sub-bearing 15 that support the crankshaft 16.
  • the slider 14 reciprocates along the vane slot 4 disposed in the cylinder 12, and the leading end of the vane 14 closely conforms to the outer diameter of the piston 13 to form a compression chamber.
  • An exhaust chamber is disposed at a lower portion of the auxiliary bearing 15 , and the exhaust chamber is a chamber formed by the auxiliary bearing 15 and the cover 17 and is pressure-tightly sealed with the internal space 1 of the housing, wherein the pressure in the exhaust chamber is a compression mechanism. Exhaust pressure P.
  • the oil separator 18 is disposed in the exhaust chamber, and at the bottom of the exhaust chamber, an oil pool 5 is provided for collecting the lubricating oil separated by the oil separator 18 in the exhaust chamber.
  • a vane chamber 2 which is pressure-tightly separated from the inner space 1 of the housing 10, the vane chamber 2 having an internal volume V and, due to the vane chamber 2 is separated from the internal space of the housing by a pressure seal, so that with the reciprocation of the slide 14, the slide
  • the size of the internal space V of the cavity 2 also varies, ranging from V1 to V2, where V1 is the minimum volume of the slider cavity 2 when the slider 14 is completely received into the slider slot 4, and V2 is slippery.
  • the sheet 14 extends the maximum volume of the slider chamber 2 when the slider slot 4 is the longest.
  • the minimum volume V1 and the maximum volume V2 of the vane chamber volume V have the following relationship: 35% ⁇ V1/V2 ⁇ 85%.
  • V1/V2 the range of more suitable V1/V2 can be reduced to: 50% ⁇ V1/V2 ⁇ 70%.
  • the low back pressure rotary compressor 100 is further provided with a slide oil supply path 3, and the inlet of the slide oil supply path 3 communicates with the oil pool 5 in the exhaust chamber, and the slide oil supply path 3 is disposed on the sub-bearing 15.
  • the outlet of the oil supply path 3, that is, the vane chamber oil supply hole is provided at the bottom of the vane chamber 2, as shown in FIG.
  • the inlet area of the oil supply path 3 is S1
  • the minimum cross-sectional area of the oil supply path 3 is S2
  • the area of the outlet, that is, the oil supply hole is S3.
  • the ratio of the area S3 (unit: mm 2 ) of the oil supply hole outlet of the sliding plate oil supply path 3 to the minimum volume V1 (unit: cm 3 ) of the sliding chamber 2 is: 0.1 ⁇ S3 / V1 ⁇ 10.5 .
  • the range of S3/V1 can be reduced to: 2 ⁇ S3 / V1 ⁇ 6.5.
  • the relationship between the inlet of the slide oil supply path 3, the minimum cross-sectional area S2 of the oil supply path 3, and the area S3 of the outlet is set to S2 ⁇ S1 and S2 ⁇ S3.
  • the oil separator 18 of the low back pressure rotary compressor 100 is disposed outside the casing 10, and the oil separator 18 is in communication with the exhaust hole 6.
  • the oil pool 5 is disposed at the bottom of the oil separator 18, and the inlet of the vane oil supply path 3 communicates with the oil pool 5 disposed in the oil separator 18, and the vane oil supply path 3 is connected to the oil bath 5 and the vane chamber 2.
  • the oil supply pipe, the outlet of the slide oil supply path 3, that is, the oil supply hole of the slide chamber 2 is located at the center of the slide chamber 2.
  • the distance between the oil supply hole and the bottom of the sliding chamber 2 is d, and the height of the sliding chamber 2 is H, which has:
  • the compression mechanism has two upper and lower cylinders, that is, the cylinder assembly includes an upper cylinder 12a, a lower cylinder 12b, and a middle partition.
  • the intermediate partition is disposed between the upper cylinder 12a and the lower cylinder 12b.
  • the slider chamber 2 also includes an upper slider chamber 2a and a slider chamber 2b, and a slider chamber 2a of the upper cylinder 12a and a slider of the lower cylinder 12b.
  • the chamber 2b is in communication with the oil sump, respectively, and the oil supply path 3 of the vane chamber also includes an upper oil supply path 3a and a lower oil supply path 3b, .
  • the upper cylinder 12a and the lower cylinder 12b are respectively analyzed by independent cylinders, and the volume V of the vane chamber of the two cylinders, the pressure P, and the area S3 of the oil supply hole are
  • the slider cavity structure of each cylinder is correspondingly analyzed, and a parameter is added after the corresponding parameter of the upper cylinder 12a, such as 12a, V1a, V2a, S3a, etc., and b is added after the parameter corresponding to the lower cylinder 12b, such as 12b, V2b. , S3b, etc.
  • the volume range of the upper cylinder vane chamber is V1a to V2a
  • the pressure fluctuation range is P1a to P2a
  • the inlet of the upper vane oil supply path 3a the minimum cross-sectional area of the oil supply path, and the area of the outlet.
  • S1a, S2a and S3a the distance from the oil supply hole to the bottom of the upper slide chamber is da
  • the height of the upper cylinder is Ha.
  • S2b ⁇ S1b
  • S2b ⁇ S3b.
  • the oil separator 18 is disposed outside the casing 10, the oil pool 5 is located at the bottom of the oil separator 18, the oil supply hole of the upper cylinder vane chamber 2a is located at the middle portion, and the lower cylinder vane chamber 2b is The oil supply hole is located in the middle, that is, the outlet of the upper slide oil supply path 3a is located in the middle of the upper cylinder slide chamber 2a, and the outlet of the slide supply oil supply path 3b is located in the middle of the lower cylinder slide chamber 2b, the upper slide The oil supply path 3a and the slide oil supply path 3b are in communication with the oil pool 5, respectively.
  • an oil pool is respectively disposed in the exhaust chambers of the main bearing 11 and the sub-bearing 15.
  • the oil supply hole of the upper cylinder vane chamber 2a is located in the middle of the vane chamber 2a, and the upper slide oil supply path 3 is
  • the oil supply pipe communicates with the oil pool in the main bearing 11 and the lower end projects into the vane chamber 2a.
  • the oil supply hole of the lower cylinder vane chamber 2b is located at the bottom of the vane chamber 2b.
  • the oil supply hole in the slider chamber 2a of the upper cylinder 12a is disposed at the top, and the oil supply hole of the slider chamber 2b is disposed at the bottom or the middle portion, at this time, in the upper slider chamber 2a and the slide piece
  • An intermediate oil supply path 3m is provided between the chambers 2b, wherein the opening area of the intermediate oil supply path 3m in the upper vane chamber 2a is S4, and the opening area in the slide chamber 2b is S5, and S4 ⁇ S5.
  • the slider chamber 2a of the upper cylinder 12a and the slider chamber 2b of the lower cylinder 12b communicate with each other through the intermediate oil supply path 3m penetrating the intermediate partition.
  • the opening area of the vane chamber 2a of the upper cylinder 12a of the intermediate oil supply path 3m is S4, and the opening area of the vane chamber 2b of the intermediate oil supply path 3m of the lower cylinder 12b is S5, S4 ⁇ S5.
  • the volume range of the upper cylinder sliding vane chamber is V1a to V2a
  • the pressure fluctuation range is P1a to P2a
  • the inlet of the upper sliding vane oil supply path 3a is respectively
  • the minimum cross-sectional area of the oil supply path is respectively
  • the distance between the oil supply hole and the bottom of the upper slide chamber is da
  • the height of the upper cylinder is Ha.
  • S2b ⁇ S1b
  • S2b ⁇ S3b.
  • the present embodiment is different from the fourth embodiment in that the intermediate oil supply path 3m is not provided, and the outlet of the oil supply path 3a of the upper vane chamber 2a, that is, the area S3a of the oil supply hole (unit : mm 2 )
  • the numerical ratio of the minimum volume V1a (unit: cm 3 ) to the vane cavity is: S3a / V1a ⁇ 4.5.
  • connection relationship between the slide oil supply path 3 and the slider chamber 2 is not limited to the above, for example, when the slider chamber 2a of the upper cylinder 12a and the slider chamber 2b of the lower cylinder 12b pass through the middle.
  • the oil separator 18 may be located outside the casing 10, the oil supply hole of the slider chamber 2a of the upper cylinder 12a is located at the center, and the oil supply hole of the slider chamber 2b of the lower cylinder 12b is also located at the center.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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Abstract

一种低背压旋转式压缩机（100），包括：壳体（10）、压缩机构、用于对从气缸（12）排出的冷媒进行油气分离的油分离器（18）、用于盛放油分离器（18）分离出来的润滑油的油池（5）。压缩机构包括气缸组件、活塞（13）、滑片（14）、主轴承（11）和副轴承（12），气缸（12）具有滑片腔（2），滑片腔（2）具有供油孔，滑片（14）往复移动时滑片（14）的尾端伸入或伸出滑片腔（2）以使得滑片腔（2）的内部容积在最大容积V2和最小容积V1之间发生变化。油池（5）通过滑片供油路径（3）与供油孔连通，其中最大容积V2和最小容积V1的比值满足如下关系：35％≤V1/V2≤85％。

Description

低背压旋转式压缩机 技术领域
本发明涉及压缩机领域，尤其是涉及一种低背压旋转式压缩机。
背景技术
低背压旋转式压缩机中，由于壳体内部为低压的吸气压力环境，作用于滑片尾端的气体力不足以保证滑片先端与活塞外径的紧密接触，因此，需要将滑片尾端所在的区域设计形成与壳体内径密封分隔的滑片腔，并给滑片腔提供相对的高压环境，以保证滑片先端与活塞外径的紧密接触。并且，由于滑片腔需要与壳体内部密封分隔，无法利用壳体内部的油池实现润滑，因此，还需要设计合理的滑片腔供油路径，来保证滑片的润滑与密封。
另外，在密闭的滑片腔中，由于滑片的往复运动，滑片腔的容积也会随之周期性变化，在这种变化过程中，当滑片腔的容积最小时，滑片腔的压力存在最大值，而当滑片腔的容积最大时，滑片腔的压力存在最小值。若滑片腔的结构容积设计不合理，可能会出现当滑片腔的最大压力过大时，带来压缩机的功耗上升，甚至导致电流异常大使电机跳停，也可能会出现当滑片腔的最小压力过小时，无法保证滑片先端与活塞外径的紧密接触，导致滑片与活塞出现撞击产生异常音和异常磨损，并且出现泄漏导致压缩机性能恶化。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本 发明提出一种低背压旋转式压缩机，滑片腔的压力波动不会过大或过小。
根据本发明实施例的低背压旋转式压缩机，包括：壳体，所述壳体上设有排气口和回气口；压缩机构，所述压缩机构设在所述壳体内，所述压缩机构包括气缸组件、活塞、滑片、主轴承和副轴承，所述主轴承和所述副轴承分别设在所述气缸组件的两端面上，所述气缸组件包括至少一个气缸，每个所述气缸内设有一个所述活塞，所述滑片的先端止抵在所述活塞的外周壁上，所述气缸还具有滑片腔，所述滑片腔具有供油孔，所述滑片往复移动时所述滑片的尾端伸入或伸出所述滑片腔以使得所述滑片腔的内部容积在最大容积V2和最小容积V1之间发生变化；用于对从所述气缸排出的冷媒进行油气分离的油分离器；用于盛放所述油分离器分离出来的润滑油的油池，所述油池通过滑片供油路径与所述供油孔连通，其中所述最大容积V2和所述最小容积V1的比值满足如下关系：35％≤V1/V2≤85％。
根据本发明实施例的低背压旋转式压缩机，通过使得滑片腔的最大容积V2和最小容积V1的比值满足如下关系：35％≤V1/V2≤85％，因此滑片腔的压力波动不会过大或过小，能保证滑片与活塞的紧贴密封，从而在较好的满足滑片的受力需要的同时，实现较好的压缩机性能。
优选地，所述最大容积V2和所述最小容积V1的比值满足如下关系：50％≤V1/V2≤70％。
在本发明的一些实施例中，所述供油孔的最下端到所述滑片腔的底壁的竖向距离为d，相应的所述气缸的高度为H，其中0≤d≤0.8H。
优选地，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值满足如下关系：0.1≤S3/V1≤10.5。
进一步优选地，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值 满足如下关系：2≤S3/V1≤6.5。
根据本发明的一些实施例，所述供油路径的入口的面积为S1，所述供油路径的最小流通面积为S2，所述S1、S2和S3满足如下关系：S2≤S1，S2≤S3。
在本发明的一些实施例中，所述供油孔设置在所述滑片腔的顶部，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值满足如下关系：S3/V1≥4.5。
根据本发明的具体实施例，所述油分离器设置在所述壳体外和/或设在所述压缩机构内。
在本发明的一些具体实施例中，所述气缸组件包括上气缸、下气缸和中隔板，所述中隔板设在所述上气缸和所述下气缸之间，所述上气缸的滑片腔和所述下气缸的滑片腔分别与所述油池连通。
进一步地，所述上气缸的滑片腔和所述下气缸的滑片腔通过贯穿所述中隔板的中间供油路径连通。
优选地，所述中间供油路径的位于所述上气缸的滑片腔的开口面积为S4，所述中间供油路径的位于所述下气缸的滑片腔的开口面积为S5，所述S4≥S5。
附图说明
图1为根据本发明一个实施例的低背压旋转式压缩机的示意图，其中压缩机为单缸压缩机；
图2为根据本发明实施例的副轴承上的滑片供油路径的示意图；
图3为根据本发明实施例的气缸、滑片和活塞的配合示意图，其中滑片腔的内部容积处于最小容积状态；
图4为根据本发明实施例的气缸、滑片和活塞的配合示意图，其中滑片腔 的内部容积处于最大容积状态；
图5为根据本发明另一个实施例的低背压旋转式压缩机的示意图，其中压缩机为单缸压缩机；
图6为根据本发明一个实施例的低背压旋转式压缩机的示意图，其中压缩机为双缸压缩机；
图7为根据本发明另一个实施例的低背压旋转式压缩机的示意图，其中压缩机为双缸压缩机；
图8为根据本发明再一个实施例的低背压旋转式压缩机的示意图，其中压缩机为双缸压缩机；
图9为根据本发明又一个实施例的低背压旋转式压缩机的示意图，其中压缩机为双缸压缩机；
图10为滑片腔容积变化曲线图；
图11为滑片腔压力波动趋势示意图；
图12为曲轴的受力示意图；
图13为根据本发明实施例的滑片腔的最大容积V2和最小容积V1的比值与压缩机的能效比之间的关系示意图。
附图标记：
100为低背压旋转式压缩机，1为壳体内部空间，2为滑片腔，3为滑片供油路径，4为滑片槽，5为油池，6为排气孔，10为壳体，11为主轴承，12为气缸，13为活塞，14为滑片，15为副轴承，16为曲轴，17为盖板，18为油分离器，21为定子，22为转子
H为气缸高度，d为滑片腔供油孔距离滑片腔底部距离，P为排气压力， P1为滑片腔最小压力，P2为滑片腔最大压力，V1为滑片腔最小容积，V2为滑片腔最大容积。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本发明的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
下面参考图1-图9详细描述根据本发明实施例的低背压旋转式压缩机100，其中低背压旋转式压缩机100可以为单缸压缩机也可以为双缸压缩机。
如图1-图9所示，根据本发明实施例的低背压旋转式压缩机100，包括：壳体10、压缩机构、油分离器18和油池5。其中壳体10上设有排气口6和回气口(图未示出)。
压缩机构设在壳体10内，压缩机构包括气缸组件、活塞13、滑片14、主轴承11和副轴承15，主轴承11和副轴承15分别设在气缸组件的两端面上，气缸组件包括至少一个气缸12，每个气缸12内设有一个活塞13，滑片14的先端止抵在活塞13的外周壁上，气缸12还具有滑片腔2，滑片腔2具有供油孔，滑片14往复移动时滑片14的尾端伸入或伸出滑片腔2以使得滑片腔2的内部容积在最大容积V2和最小容积V1之间发生变化。
油分离器18用于对从气缸12排出的冷媒进行油气分离。油池5用于盛放油分离器18分离出来的润滑油，由于从气缸12排出的冷媒为高压冷媒，由此可知油池5处于高压环境。
油池5通过滑片供油路径3与供油孔连通，其中最大容积V2和最小容积V1的比值满足如下关系：35％≤V1/V2≤85％。其中由于滑片腔2与油池5连通，由此可知滑片腔2处于高压环境，从而可以使得滑片14的先端止抵在活塞13的外周壁上。
可以理解的是，低背压旋转式压缩机100还包括电机、曲轴16等元件，电机包括定子21和转子22，定子21固定在壳体10的内壁上，定子21外套在转子22上，转子22外套在曲轴16上以驱动曲轴16转动，每个气缸12的活塞13外套在曲轴16的偏心部上，滑片14设在气缸12的滑片槽4内且滑片14的先端止抵在活塞13的外周壁上以将气缸12内分隔成吸气腔和压缩腔， 其中曲轴16带动活塞13在相应的气缸12内做偏心运动，在活塞13偏心转动的过程中，滑片14在滑片槽4内做往复运动，滑片14往复运动时，滑片14的尾端伸入到滑片腔2内或者伸出滑片腔2，从而滑片腔2的内部容积也随着滑片14的往复运动发生周期性变化。
图10所示为压缩机运转过程中，随着滑片14的往复运动，滑片腔2的容积变化情况示意图。如图10所示，滑片腔2容积在V1～V2范围内变化，其中，横坐标为活塞13相对于气缸中心的旋转角度。如图3所示，当滑片14完全收纳于滑片腔2内时，此时曲轴16旋转角度为0度，滑片腔2的容积最小，最小容积为V1，而如图4所示，当滑片14伸出滑片腔2最长时，此时曲轴16旋转角度为180度，滑片腔2的容积最大，最大容积为V2，当曲轴16旋转一圈后，滑片14再次完全收纳于滑片腔2内时，此时曲轴16旋转角度为360度(弧度2π)，滑片腔2的容积变回最小容积V1。图10中所示的是理想情况下的压力变化周期，在实际的压缩机中，由于压力损失及压力传递的过程影响，压力波动与横坐标曲轴16旋转角度可能存在延迟，但周期性的波动变化属性不变。
根据旋转式压缩机的工作原理，如图3和图4所示，若活塞13偏心旋转的半径为e，则滑片14往复运动的最大行程为2e，若气缸高度为H，滑片14厚度为T，则近似有：
V2＝V1+2e*H*T
随着滑片14的往复运动，考虑到滑片14与气缸配合面的泄漏间隙极小，因此，滑片腔2除了连通滑片供油路径3外，其内部容积可以假定为一个密闭的空间。这样的话，滑片腔2内的压力会随着滑片腔2容积的变化而产生波动，若滑片供油路径3的入口油池5的压力为P，随着滑片腔2的容积变化，滑片 腔2内的压力会存在范围为P1～P2的压力波动，这一点与传统的滑片腔开放于壳体内部空间的高背压旋转式压缩机是完全不同的。一般来说，滑片腔2的滑片供油路径3的位于滑片腔2内的出口即供油孔的大小会对此压力波动产生一定的影响，但总的来说，滑片腔2内压力波动的趋势如图11所示。根据图11，一般情况下，随着滑片14的往复运动，滑片腔2容积最小时，其压力达到最大P2，而当滑片腔2容积最大时，其压力达到最小值P1，相对于滑片腔2的供油压力P，存在关系P1＜P＜P2。同样的，压力的波动与曲轴16的旋转角度也可能产生延迟，其波动主要受到容积变化的影响。
在旋转式压缩机运转过程中，曲轴16在电机输入的转动力矩的带动下进行转动，而曲轴16在运转过程中也存在阻力矩M，阻力矩M由几个部分组成，如图12所示，包括：
M＝Mg+Mn+Mc+Mj
其中，：
Mg：压缩气体力产生的阻力矩
Mn：滑片14先端作用在活塞13外径上的力Fn形成的阻力矩
Mc：滚动活塞13与偏心曲轴16之间的摩擦力矩
Mj：曲轴16与上、副轴承15产生的阻力矩
在这些阻力矩中，Mn是滑片14先端作用在活塞13外径上的力Fn形成的阻力矩，而在低背压旋转式压缩机中，通过对滑片14的受力分析可知，滑片14尾部的气体力Fc是影响滑片14先端作用在活塞13外径上的力Fn的重要因素之一，滑片14尾部的气体力Fc越大，滑片14先端作用于活塞13外径上的力Fn越大。而滑片14尾部的气体力Fc是这样得到的：
Fc＝Pc*Sc
其中，
Pc：滑片14尾部的气体压力
Sc：滑片14尾部的受力面积
在低背压旋转式压缩机100中，由于滑片14尾部位于滑片腔2中，在结构一定的情况下，滑片14尾部的气体力Fc主要由滑片腔2的压力Pc来决定。根据上面的分析可知，滑片腔2的气体压力在P1～P2范围内波动，因此，滑片14尾部的气体力Fc也存在波动。
在旋转式压缩机运转过程中，滑片14压紧活塞13的力要保持在合适的范围内，避免过大时的阻力过大或过小时出现泄漏和碰撞，因此，对于滑片14尾部的气体压力来说，也存在一个合适的范围。
由于滑片腔2的气体压力即滑片14尾部的气体压力的范围主要受供油压力P和滑片腔2的容积变化范围V1和V2影响，因此，可以通过调节P和V1、V2来条件滑片14尾部的气体压力范围。
在稳定运转工况下，供油压力P一定，因此，可以通过设计滑片腔2的容积变化范围V1和V2的关系来使压力波动尽可能的出现在合适的P1～P2范围内。图13显示了低背压旋转式压缩机100的运转性能即COP与滑片腔2的容积变化范围V1和V2的比例即V1/V2的关系，说明如下：
在压缩机运转过程中，若滑片腔2的内部容积V随着滑片14的往复运动具有周期性变化的范围V1～V2，其中，V1为滑片腔2的最小容积，V2为滑片腔2的最大容积，则可以通过结构设计，使V1与V2的关系设置为：
0.25％≤V1/V2≤95％，可以保证在低背压旋转式压缩机100的绝大多数情况运行条件下，保证滑片14先端作用于活塞13外径的力，以确保滑片14与活塞13能够紧密贴合，不会出现分离，从而保证压缩机的性能及可靠性。V1/V2 与壳体10低压力旋转式压缩机的能效比(COP)的关系如图13所示：
若设置35％≤V1/V2≤85％时，能够获得合适的滑片14先端作用于活塞13外径的力Fn，以保证在大多数工况下，压缩机能够获得更好的性能表现，并能保证滑片14与活塞13的紧贴密封，这是因为，在这种滑片腔2的最大容积和最小容积比的情况下，滑片腔2的压力波动不会过大或过小，参考图11中，即P2和P1相对P的振幅在合理范围内，从而在较好的满足滑片14的受力需要的同时，实现较好的压缩机性能。
根据图13中的结果可知，当V1/V2的范围为50％≤V1/V2≤70％，可以更好的满足压缩机的性能要求。因此在本发明的优选实施例中，将滑片腔2设计成使得最大容积V2和最小容积V1的比值满足如下关系：50％≤V1/V2≤70％。
在图13中，当V1/V2过小时，如V1/V2＜20％，由于滑片腔2加工工艺及滑片14弹簧避让孔的存在，从结构上来说难以实现，因此，图13中以虚线表示可能的情况。而当V1/V2过大时，由于滑片腔2的容积变化小导致滑片腔2的压力波动小，可能会导致滑片腔2的供油困难，带来润滑性能的恶化，导致压缩机的COP下降。
因此，综上分析可知，根据本发明实施例的低背压旋转式压缩机100，通过使得滑片腔2的最大容积V2和最小容积V1的比值满足如下关系：35％≤V1/V2≤85％，因此滑片腔2的压力波动不会过大或过小，能保证滑片14与活塞13的紧贴密封，从而在较好的满足滑片14的受力需要的同时，实现较好的压缩机性能。
其中，在滑片腔2容积变化过程中，滑片腔2中存油状况也会影响到滑片腔2的压力波动。这是因为润滑油是液体，属于不可压缩品，若滑片腔2的存油量过多，滑片14往复运动时，压缩润滑油的阻力会极大，从而影响到压缩 机的性能和磨损，极端情况下甚至导致压缩机运转过程中由于阻力过大而卡死停机。
为了避免这种情况的发生，必须要使滑片腔2内的润滑油在滑片腔2容积变小时可以根据实际情况适当的缓冲减少，在本发明中，可以通过以下方案来实现：
第一种：也是最可靠的，就是将滑片腔2的供油孔设置在滑片腔2的底部，即供油孔最下端到滑片腔2底部的距离d设置为d＝0。
第二种：将供油孔设置在滑片腔2的中部，主要是考虑到滑片腔2的适当存油能改善滑片14的润滑及配合面的密封，在滑片14往复运动时，当滑片腔2容积减小时，滑片腔2内的润滑油会部分保留，不会被完全压回至供油孔内，因此，这里，设计滑片腔2的供油孔的开口高度d为0＜d≤0.8*H。
简言之，供油孔可以设置在滑片腔2的底部或者中部，供油孔的最下端到滑片腔2的底壁的竖向距离为d，相应的气缸12的高度为H，其中0≤d≤0.8H。
另外，滑片腔2内的存油可以通过供油孔来实现回收缓冲，从而避免滑片14压缩润滑油带来压缩机的性能和可靠性问题。因此，供油孔的大小设计也会对存油的回收缓冲带来影响。
合理的供油孔的开口面积设计与滑片腔2的容积有关，通过设计合理的滑片腔2供油孔的面积，实现滑片腔2供油孔及滑片供油路径3的存油回收缓冲作用。对于供油孔设置在滑片腔2的底部或中部时，一般情况下，若供油孔的面积为S3(单位：mm2)，当其与滑片腔2的最小容积V1单位：cm3)的数值比为0.1≤S3/V1≤10.5时，低背压旋转式压缩机100的滑片腔2的压力波动将处于可接受的范围内，能保证压缩机的稳定可靠运转。
进一步地，供油孔的面积S3(单位：mm2)与滑片腔2的最小容积V1(单 位：cm3)的数值比可设计为2≤S3/V1≤6.5。
最后，若滑片腔2的供油孔设置在滑片腔2的顶部时，就需要保证供油孔有良好的回油性能，这时，可以设计供油孔的面积S3(单位：mm2)与滑片腔2的最小容积V1(单位：cm3)的数值比为：S3/V1≥4.5，使得相比滑片腔2的最小容积，供油孔的面积足够大。
另外，对于滑片供油路径3来说，如图2所示，若滑片供油路径3的入口面积为S1，滑片供油路径3的最小流通面积为S2，滑片供油路径3的出口即供油孔的面积为S3时，设计成进口及出口略大时，能更容易的实现润滑油输入和输出供油路径，从而保证滑片供油路径3给滑片腔2提供的油量和回收缓冲的作用。即设计上，要求滑片供油路径3各部位的面积关系为：S2≤S1，且S2≤S3。当等号成立时，可以简化滑片供油路径3的加工和制造。
在本发明的具体实施例中，油分离器18可以设置在壳体10外和/或设在压缩机构内。具体而言，油分离器18的设置情况分成如下几种情况：
第一种情况是，如图5和图7所示，当低背压旋转式压缩机100为单缸压缩机或者双缸压缩机时，油分离器18为一个且设置在壳体10外，油池5位于油分离器18的底部，油分离器18与压缩机的排气孔6连通，每个滑片腔2与油池5连通。
第二种情况是：低背压旋转式压缩机100为单缸压缩机，如图1所示，供油孔位于滑片腔2的底部，油分离器18设置在副轴承15和盖板17限定出的排气腔内。
第三种情况是：低背压旋转式压缩机100为单缸压缩机，供油孔位于滑片腔2的顶部，则油分离器18设置在主轴承11内的排气腔内。
第四种情况是：低背压旋转式压缩机100为双缸压缩机，则主轴承11和 副轴承15上分别设有油分离器18和油池5。
第五种情况是：低背压旋转式压缩机100为双缸压缩机，主轴承或副轴承的排气腔内设有第一个油分离器和用于盛接第一个油分离器分离出来的润滑油的第一个油池，壳体10外还设有第二个油分离器，第二油分离器的底部设有第二油池，两个气缸的滑片腔分别与第一个油池和第二油池连通。
下面参考图1、图5-图9详细描述根据本发明几个不同实施例的低背压旋转式压缩机100。
实施例1：
如图1所示，根据本发明实施例的低背压旋转式压缩机100，包括：壳体10、电机和压缩机构。壳体10内限定出与吸气口连通的内部空间1，电机设在内部空间1的上部，电机由定子21和转子22组成，其中，转子22与曲轴16连接，驱动曲轴16做旋转运动。
压缩机构包括：气缸12、设置在气缸12内的活塞13和滑片14、驱动活塞13做偏心转动的曲轴16、以及支撑曲轴16的主轴承11和副轴承15。
在压缩机运转过程中，滑片14沿着设置在气缸12上的滑片槽4作往复运动，并且，滑片14的先端与活塞13的外径紧密贴合形成压缩腔室。
在副轴承15下部设置有排气腔，该排气腔是由副轴承15及盖板17配合形成的与壳体内部空间1压力性密封的腔室，其中排气腔内的压力为压缩机构的排气压力P。油分离器18设置在排气腔内，在排气腔底部，设置有油池5，用来收集排气腔内油分离器18分离出来的润滑油。
在滑片14的尾部，位于气缸12的外缘部位，设置有与壳体10内部空间1压力性密封分隔的滑片腔2，该滑片腔2具有内部容积V，并且，由于滑片腔2与壳体内部空间1压力性密封分隔，因此，随着滑片14的往复运动，滑 片腔2的内部空间V的大小也随着变化，变化范围为V1～V2，其中，V1为滑片14完全收纳至滑片槽4中时滑片腔2的最小容积，而V2则为滑片14伸出滑片槽4最长时滑片腔2的最大容积。
其中，滑片腔容积V的最小容积V1和最大容积V2具备以下关系：35％≤V1/V2≤85％。
进一步地，更合适的V1/V2的范围可缩小至：50％≤V1/V2≤70％。
另外，如图1所示，低背压旋转式压缩机100还设置有滑片供油路径3，该滑片供油路径3的入口连通排气腔内的油池5，滑片供油路径3设置在副轴承15上，在本实施例中，供油路径3的出口即滑片腔供油孔设置在滑片腔2的底部，如图1中所示。如图2所示，供油路径3入口面积为S1，供油路径3最小截面积为S2，出口即供油孔的面积为S3。
其中，滑片供油路径3的出口即供油孔的面积S3(单位：mm2)与滑片腔2的最小容积V1(单位：cm3)的数值比为：0.1≤S3/V1≤10.5。
进一步地，S3/V1的范围可缩小至：2≤S3/V1≤6.5。
并且，该滑片供油路径3的入口、供油路径3的最小截面积S2、出口的面积S3关系设置为：S2≤S1，且S2≤S3。
实施例2：
如图5所示，在该实施例中，低背压旋转式压缩机100的油分离器18设置在壳体10的外部，该油分离器18与排气孔6连通。油池5设置在油分离器18的底部，滑片供油路径3的入口连通设置在油分离器18中的油池5，滑片供油路径3为连通油池5和滑片腔2的供油管，滑片供油路径3的出口即滑片腔2的供油孔位于滑片腔2的中部。
其中，供油孔距离滑片腔2的底部的距离为d，滑片腔2的高度为H，有：
0＜d≤0.8*H
其余与实施例1相同，不再赘述。
实施例3：
如图7和图9所示，在本实施例中，与实施例1和实施例2的差别在于压缩机构具有上下两个气缸，即气缸组件包括上气缸12a、下气缸12b和中隔板，中隔板设在上气缸12a和下气缸12b之间，相应地，滑片腔2也包括上滑片腔2a和下滑片腔2b，上气缸12a的滑片腔2a和下气缸12b的滑片腔2b分别与油池连通，并且，滑片腔的供油路径3也包括上供油路径3a和下供油路径3b，……。
也就是说，在本实施例中，将上气缸12a和下气缸12b相应的分别以独立气缸的方法来分析，两个气缸的滑片腔的容积V，压力P以及供油孔的面积S3与各自气缸的滑片腔结构对应分析，并在上气缸12a对应的参数后面加a表示，如12a，V1a，V2a，S3a等，而在下气缸12b对应的参数后面加b来表示，如12b，V2b，S3b等。
因此，在本实施例中，上气缸滑片腔的容积范围为V1a～V2a，压力波动范围为P1a～P2a，上滑片供油路径3a的入口、供油路径的最小截面面积及出口的面积分别为S1a，S2a及S3a，供油孔距离上滑片腔底部的距离为da，上气缸的高度为Ha，这些参数也具备实施例1中所述的对应参数关系：
35％≤V1a/V2a≤85％，更进一步的优化选择是50％≤V1a/V2a≤70％；
0.1≤S3a/V1a≤10.5，进一步的：2≤S3a/V1a≤6.5；
并且，S2a≤S1a，且S2a≤S3a。
同样的，下气缸的参数和关系也类似上气缸的要求，有：
35％≤V1b/V2b≤85％，更进一步的优化选择是50％≤V1b/V2b≤70％；
0.1≤S3b/V1b≤10.5，进一步的：2≤S3b/V1b≤6.5；
并且，S2b≤S1b，且S2b≤S3b。
其中，如图7所示，油分离器18设置在壳体10外，油池5位于油分离器18的底部，上气缸滑片腔2a的供油孔位于中部，下气缸滑片腔2b的供油孔位于中部，也就是说，上滑片供油路径3a的出口位于上气缸滑片腔2a的中部，下滑片供油路径3b的出口位于下气缸滑片腔2b的中部，上滑片供油路径3a和下滑片供油路径3b分别与油池5连通。
如图9所示，主轴承11和副轴承15的排气腔内分别设有油池，上气缸滑片腔2a的供油孔位于滑片腔2a的中部，上滑片供油路径3为与主轴承11内的油池连通且下端伸入到滑片腔2a内的供油管。下气缸滑片腔2b的供油孔位于滑片腔2b的底部。
实施例4：
如图8所示，上气缸12a的滑片腔2a中的供油孔设置于顶部，而下滑片腔2b的供油孔设置在底部或中部，此时，在上滑片腔2a和下滑片腔2b之间设置有中间供油路径3m，其中该中间供油路径3m在上滑片腔2a内的开口面积为S4，在下滑片腔2b内的开口面积为S5，有S4≥S5。换言之，上气缸12a的滑片腔2a和下气缸12b的滑片腔2b通过贯穿中隔板的中间供油路径3m连通。中间供油路径3m的位于上气缸12a的滑片腔2a的开口面积为S4，中间供油路径3m的位于下气缸12b的滑片腔2b的开口面积为S5，S4≥S5。
在本实施例中，S4与S5的关系可以详细分为两部分：
第一，当S5的面积设置的较小时，考虑到上滑片腔2a内的压力缓冲作用，要通过中间供油路径3m来实现，因此，要求S4＞S5，以保证上滑片腔2a内的油能更容易的进入到中间供油路径3m中，此时S5≤3.5mm2；
第二，当S5的面积设置的较大时，如S5＞3.5mm2时，可以设置S4＝S5。
同时在本实施例中，上气缸滑片腔的容积范围为V1a～V2a，压力波动范围为P1a～P2a，上滑片供油路径3a的入口、供油路径的最小截面面积及出口的面积分别为S1a，S2a及S3a，供油孔距离上滑片腔底部的距离为da，上气缸的高度为Ha，这些参数也具备如下的对应参数关系：
35％≤V1a/V2a≤85％，更进一步的优化选择是50％≤V1a/V2a≤70％；
S3a/V1a≥4.5；
并且，S2a≤S1a，且S2a≤S3a。
同样的，下气缸的参数和关系也类似上气缸的要求，有：
35％≤V1b/V2b≤85％，更进一步的优化选择是50％≤V1b/V2b≤70％；
0.1≤S3b/V1b≤10.5，进一步的：2≤S3b/V1b≤6.5；
并且，S2b≤S1b，且S2b≤S3b。
实施例5：
如图6所示，本实施例与实施例4的不同之处在于，未设置中间供油路径3m，并且，上滑片腔2a的供油路径3a的出口即供油孔的面积S3a(单位：mm2)与滑片腔的最小容积V1a(单位：cm3)的数值比为：S3a/V1a≥4.5。
其余与实施例4相同，不再赘述。
需要进行说明的是，上述四种具体实施例只是对根据本发明的低背压旋转 式压缩机100的示例性说明，滑片供油路径3与滑片腔2的连接关系不限于上述几种，例如当上气缸12a的滑片腔2a和下气缸12b的滑片腔2b通过中间供油路径3m连通时，油分离器18可以位于壳体10外，上气缸12a的滑片腔2a的供油孔位于中部，下气缸12b的滑片腔2b的供油孔也位于中部。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (11)

  1. 一种低背压旋转式压缩机，其特征在于，包括：
    壳体，所述壳体上设有排气口和回气口；
    压缩机构，所述压缩机构设在所述壳体内，所述压缩机构包括气缸组件、活塞、滑片、主轴承和副轴承，所述主轴承和所述副轴承分别设在所述气缸组件的两端面上，所述气缸组件包括至少一个气缸，每个所述气缸内设有一个所述活塞，所述滑片的先端止抵在所述活塞的外周壁上，所述气缸还具有滑片腔，所述滑片腔具有供油孔，所述滑片往复移动时所述滑片的尾端伸入或伸出所述滑片腔以使得所述滑片腔的内部容积在最大容积V2和最小容积V1之间发生变化；
    用于对从所述气缸排出的冷媒进行油气分离的油分离器；
    用于盛放所述油分离器分离出来的润滑油的油池，所述油池通过滑片供油路径与所述供油孔连通，其中所述最大容积V2和所述最小容积V1的比值满足如下关系：35％≤V1/V2≤85％。
  2. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述最大容积V2和所述最小容积V1的比值满足如下关系：50％≤V1/V2≤70％。
  3. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述供油孔的最下端到所述滑片腔的底壁的竖向距离为d，相应的所述气缸的高度为H，其中0≤d≤0.8H。
  4. 根据权利要求3所述的低背压旋转式压缩机，其特征在于，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值满足如下关系：0.1≤S3/V1≤10.5。
  5. 根据权利要求4所述的低背压旋转式压缩机，其特征在于，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值满足如下关系：2≤S3/V1≤ 6.5。
  6. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述供油路径的入口的面积为S1，所述供油路径的最小流通面积为S2，所述S1、S2和S3满足如下关系：S2≤S1，S2≤S3。
  7. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述供油孔设置在所述滑片腔的顶部，所述供油孔的面积S3与所述滑片腔的最小容积V1的比值满足如下关系：S3/V1≥4.5。
  8. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述油分离器设置在所述壳体外和/或设在所述压缩机构内。
  9. 根据权利要求1所述的低背压旋转式压缩机，其特征在于，所述气缸组件包括上气缸、下气缸和中隔板，所述中隔板设在所述上气缸和所述下气缸之间，所述上气缸的滑片腔和所述下气缸的滑片腔分别与所述油池连通。
  10. 根据权利要求9所述的低背压旋转式压缩机，其特征在于，所述上气缸的滑片腔和所述下气缸的滑片腔通过贯穿所述中隔板的中间供油路径连通。
  11. 根据权利要求10所述的低背压旋转式压缩机，其特征在于，所述中间供油路径的位于所述上气缸的滑片腔的开口面积为S4，所述中间供油路径的位于所述下气缸的滑片腔的开口面积为S5，所述S4≥S5。
PCT/CN2014/093060 2014-12-04 2014-12-04 低背压旋转式压缩机 WO2016086396A1 (zh)

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PCT/CN2014/093060 WO2016086396A1 (zh) 2014-12-04 2014-12-04 低背压旋转式压缩机
KR1020157023406A KR101710350B1 (ko) 2014-12-04 2014-12-04 저배압 회전식 압축기
EP14907244.9A EP3228868B1 (en) 2014-12-04 2014-12-04 Low-backpressure rotary compressor
AU2014413252A AU2014413252B2 (en) 2014-12-04 2014-12-04 Low-backpressure rotary compressor
KR1020177004260A KR101751901B1 (ko) 2014-12-04 2014-12-04 저배압 회전식 압축기
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CN113250642A (zh) * 2021-05-25 2021-08-13 张梦 一种固井用封隔器

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CN108916045B (zh) * 2018-07-18 2024-04-02 珠海格力电器股份有限公司 泵体组件、流体机械及换热设备

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EP3228868A1 (en) 2017-10-11
KR101751901B1 (ko) 2017-07-11
KR20160082351A (ko) 2016-07-08
EP3228868A4 (en) 2018-05-23
AU2014413252B2 (en) 2019-02-14
KR20170021362A (ko) 2017-02-27
US20170138360A1 (en) 2017-05-18
AU2014413252A1 (en) 2016-10-06
US10458410B2 (en) 2019-10-29
KR101710350B1 (ko) 2017-02-27

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