CN108252915B - Centrifugal oil-gas separator - Google Patents
Centrifugal oil-gas separator Download PDFInfo
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- CN108252915B CN108252915B CN201810045856.9A CN201810045856A CN108252915B CN 108252915 B CN108252915 B CN 108252915B CN 201810045856 A CN201810045856 A CN 201810045856A CN 108252915 B CN108252915 B CN 108252915B
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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
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- Separating Particles In Gases By Inertia (AREA)
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Abstract
The invention provides a centrifugal oil-gas separator, which adds a plurality of layers of centrifugal separation sleeves on the traditional centrifugal separator so as to keep higher separation efficiency of the centrifugal separator under the condition that the working condition of the centrifugal separator is changed in a large range and improve the separation performance of the centrifugal separator when the centrifugal separator is applied to a variable frequency compressor. Meanwhile, a derotator is added at an inlet of a filter element of the separator so as to despin and rectify the oil-gas mixture which is about to enter the filter element for fine separation, and part of kinetic energy is recovered and converted into pressure energy, so that the total pressure loss of the oil-gas separator is reduced; meanwhile, the air flow entering the filter element is distributed more uniformly, and the separation efficiency and the service life of the filter element are improved.
Description
Technical Field
The invention relates to oil-gas separation equipment, in particular to a cyclone type oil-gas separator applied to an oil-injection compressor.
Background
Air compressors, which are used to produce compressed air and to effect remote transport of gases, have become increasingly popular in recent years. The most widely used by the current industry is the oil-injected screw compressor. The working principle of the double-screw air compressor is that air is compressed by a cavity formed by meshing a pair of rotor systems consisting of a female rotor and a male rotor. During working, compressor oil is required to be continuously sprayed to the male rotor and the female rotor, so that leakage of compressed gas is reduced, and the effect of sealing the cavity is achieved. Meanwhile, the oil drops sprayed into the main engine also take away heat in the main engine, the temperature of the rotor is reduced, the oil drops are mixed with compressed gas, compressed air is cooled, and the exhaust temperature is reduced. The oil drops attached to the main body and the rotor lubricate the rotor in the main body, reduce friction and reduce noise of the main body.
Cyclone separators are one of the important components of oil-injected air compressors. The method has the functions of treating gas containing a small amount of liquid mist, purifying gas phase, ensuring the purity of the gas and simultaneously realizing secondary recycling of compressor oil. In order to reduce the oil content in the unit exhaust and to recycle the lubricating oil in the unit, the lubricating oil must be efficiently separated from the compressed gas by means of an oil-gas separator.
At present, an inlet of a cyclone type oil-gas separator commonly adopted is tangent to a separator cylinder, an oil-gas mixture enters the separator and then is converted into centrifugal motion, larger oil drops are attached to the wall surface under the action of centrifugal force, and the oil drops flow downwards along the wall surface under the action of gravity after being condensed. The cyclone oil-gas separator has many problems in the use process: the application working condition range is narrow, and the separation effect on the variable frequency compressor which is applied more and more is not ideal; the low separation efficiency can increase the oil drop concentration of the oil-gas mixture entering the filter element, shorten the service life of the filter element and increase the system operation cost; improving the separation efficiency of existing cyclone separators generally results in increased drag loss and increased energy consumption.
Disclosure of Invention
The invention aims to overcome the defects of the existing cyclone oil-gas separator, and provides an energy-saving centrifugal oil-gas separator to improve the separation performance of the cyclone separator when the cyclone separator is used in a variable frequency compressor, namely, the resistance loss of the separator is reduced while the oil-gas separation efficiency is improved, and the power consumption of the compressor is reduced.
In order to achieve the purpose, the invention adopts the following technical scheme:
the oil-gas mixed gas separation device comprises a barrel, an oil-gas mixed gas inlet, an oil discharge port and a clean gas outlet, wherein the oil-gas mixed gas inlet, the oil discharge port and the clean gas outlet are arranged on the barrel, a single shunt barrel or a plurality of shunt barrels which are nested with one another are arranged in the barrel, the separation sleeves are arranged at the lower ends of the shunt barrels and are the same as the shunt barrels in number, each shunt barrel is connected with the upper end of a corresponding separation sleeve (if the shunt barrels and the separation sleeves are a plurality of shunt barrels and are connected in one-to-one correspondence), the lower ends of the separation sleeves are positioned above the oil discharge port, an inner barrel is arranged in the separation sleeve or the innermost separation sleeve, a centrifugal separation region is formed in an annular region between the inner barrel and the shunt barrel (and the separation sleeve connected with the inner barrel) or the innermost shunt barrel (and the separation sleeve connected with the inner barrel), another centrifugal separation region is formed in an annular region between the barrel and the shunt barrel (and the separation sleeve, the annular area between any two adjacent inner and outer shunt cylinders (and the separation sleeve correspondingly connected with the inner and outer shunt cylinders) forms a corresponding Mth centrifugal separation area, M is more than or equal to 3, and each shunt cylinder is provided with a notch for guiding the oil-gas mixed gas entering the cylinder body through the inlet into each centrifugal separation area; the filter is arranged in the inner barrel, the bottom of an annular interval area between the inner barrel and the filter core is provided with a deswirler, and the top of the filter core is opposite to the clean gas outlet.
The notch is formed by locally and radially swinging the side wall surface of the splitter cylinder outwards by a certain angle.
The gap and the oil-gas mixed gas inlet are spaced in the horizontal direction, and the gap is gradually increased (for example, by increasing the swing angle) along the sequence of the plurality of flow distribution cylinders arranged from outside to inside and the spacing of the inlets.
The despin device adopts a derotator with inverted blades.
The inlet angle of the blades of the deswirler is tangent to the direction of the airflow outside the inner cylinder, and the outlet angle of the blades is the axial direction of the inner cylinder.
The cylinder, each centrifugal separation area, the inner cylinder and the filter element are coaxially arranged.
The oil discharge port is communicated with a liquid collection area at the bottom of the barrel, and the despin device and the separation sleeve are positioned above the liquid collection area.
The invention has the beneficial effects that:
the invention adds a multilayer shunt cylinder and a separation sleeve on the traditional centrifugal separator, and a multilayer centrifugal separation area is formed, so that the centrifugal separator can keep higher separation efficiency under the condition of large-range change of working conditions, and the separation performance of the centrifugal separator when applied to a variable frequency compressor is improved. Meanwhile, a derotator is added at an inlet of a filter element of the separator so as to despin and rectify the oil-gas mixture which is about to enter the filter element for fine separation, and part of kinetic energy is recovered and converted into pressure energy, so that the total pressure loss of the oil-gas separator is reduced; meanwhile, the air flow entering the filter element is distributed more uniformly, and the separation efficiency and the service life of the filter element are improved. Finally, the resistance loss of the separator is reduced while the oil-gas separation efficiency is improved, and the energy consumption is reduced.
Drawings
FIG. 1 is an isometric view of a centrifugal oil-gas separator for venting a conventional compressor;
FIG. 2 is an isometric view of a centrifugal oil-gas separator according to the present invention;
FIG. 3 is a schematic diagram of a separation region of the centrifugal oil-gas separator according to the invention;
FIG. 4 is an isometric view of the first inlet splitter cylinder and the first splitter sleeve;
FIG. 5 is an isometric view of a second inlet splitter cylinder and a second splitter sleeve;
FIG. 6 is an isometric view of the derotator of the present invention;
FIG. 7 is a schematic diagram showing the movement locus of liquid droplets moving radially from the inner cylindrical wall to the cylindrical surface in a conventional centrifugal separator;
FIG. 8 is a schematic diagram of the radial movement locus of liquid drops in the centrifugal oil-gas separator according to the invention;
FIG. 9 is a comparison graph of simulation calculation results of the centrifugal oil-gas separator according to the present invention and a conventional separator;
in the figure: 1. the centrifugal separation device comprises a liquid collection area, a cylinder body, a second separation sleeve, a filter element, a second inlet flow-dividing cylinder, a first outlet, an inlet, a second inlet flow-dividing cylinder, a second separation sleeve, a second inlet flow-dividing cylinder, a second separation sleeve, a second inlet flow-dividing cylinder, a second separation sleeve, a second inlet.
Detailed Description
The invention is further illustrated with reference to the following figures and examples.
As shown in fig. 1, a centrifugal separator (i.e., a centrifugal oil-gas separator) is generally used in a conventional cyclone oil-gas separator for an oil-injected compressor, and an air flow enters the separator through a tangential inlet 7 to generate centrifugal motion, so as to achieve the purpose of coarse separation, and then the mixed air flow enters a filter element 4 to perform fine separation. It is less effective when applied to a variable frequency compressor and the rotational flow into the filter element 4 also increases the drag loss of the system. The separation efficiency in the rough separation stage is low, so that the concentration of the oil-gas mixture entering the filter element 4 is high, the service life of the filter element 4 can be shortened, and the operation cost of the system is increased. Therefore, the invention provides an energy-saving centrifugal oil-gas separator.
Referring to fig. 2, the energy-saving centrifugal oil-gas separator of the present invention includes a cylindrical barrel 2, the upper end of the outer surface of the barrel 2 is provided with an inlet 7 for tangential air intake, and an oil-gas mixture enters the separator from the inlet 7, is split by a multi-stage inlet splitter cylinder, and enters each centrifugal separation region. The lower end of each inlet shunt cylinder is closely connected with a corresponding separation sleeve. The inlet shunt cylinder and the separating sleeve at each level are respectively in an internal and external nested arrangement mode, the filter element 4 for fine separation and the inner cylinder 9 positioned on the outer side of the filter element are coaxially arranged at the center of the inner part, and the bottom of an annular space formed by the inner cylinder 9 and the filter element 4 is provided with a derotator 11. The bottom of the cylinder body 2 is a liquid collecting area 1, and the center of the top of the cylinder body 2 is provided with a clean gas outlet 6. The cylinder body 2 is provided with an oil discharge port 12 communicated with the liquid collecting area 1 and used for guiding separated lubricating oil out of the separator, and the oil can be recycled and enter the compressor again for lubrication through the pressure difference between the inside of the separator and the oil injection position.
The oil-gas separation process of the energy-saving centrifugal oil-gas separator is specifically described below (taking a two-stage inlet flow-splitting cylinder and a separation sleeve as examples).
Referring to fig. 2, the incoming flow direction and size of the oil-gas mixture are uniform, and when the mixture enters the separator from the mixed gas inlet 7 tangential to the cylinder 2, the flow direction is converted into centrifugal motion centering on the central axis of the cylinder 2.
Coarse separation: referring to fig. 3, 4 and 5, the oil-gas mixture entering the separator tangentially along the cylinder 2 is split at the notches formed by swinging a certain angle outwards along the radial direction on the side wall surfaces of the first inlet splitter cylinder 8 and the second inlet splitter cylinder 5, and the mixed gas flow enters three centrifugal separation areas 13, 14 and 15 simultaneously. The mixed airflow is divided into three airflows which move centrifugally by one airflow moving at high speed, and the three airflows move centrifugally in three centrifugal separation areas 13, 14 and 15 respectively to carry out oil-gas separation. Because the oil-gas mixture continuously enters the separator through the inlet 7, the original split air flow does centrifugal motion downwards along the central axis of the cylinder 2, and oil drops in the oil-gas mixture are thrown to the wall surface to achieve the purpose of oil-gas separation. Oil drops separated from the oil-gas mixture in the centrifugal separation area 15 on the outermost side are gathered on the inner surface of the cylinder 2 and flow downwards to the liquid collection area 1 at the bottom along the inner wall surface of the cylinder 2; oil drops separated from the oil-gas mixture in the middle centrifugal separation region 14 and the innermost centrifugal separation region 13 are respectively gathered on the inner surfaces of the second separation sleeve 3 and the first separation sleeve 10, flow downwards along the inner wall surfaces of the second separation sleeve 3 and the first separation sleeve 10, and enter the liquid collection region 1 at the bottom of the barrel 2. The lubricating oil collected in the sump 1 at the bottom of the separator bowl 2 exits the separator via the oil drain 12.
Referring to fig. 2, the mixed gas flow after the first step of coarse separation is a downward gas flow which performs centrifugal motion, and when the mixed gas flow continues to move downward and contacts the bottom of the cylinder 2, the mixed gas flow is changed into a motion direction, namely, an upward rotary motion. Referring to fig. 6, the vane outlet 16 of the deswirler 11 is 90 ° and the vane inlet 17 is at an angle tangential to the direction of rotation of the air flow. When the airflow moves upwards to the derotator 11, the movement direction of the airflow is changed from the upward rotary motion along the central axis of the cylinder 2 to the upward motion along the central axis of the cylinder 2, and the circumferential centrifugal motion is not performed any more.
The mixed gas flow changes the movement direction and then moves upwards along the annular space formed between the filter element 4 and the inner cylinder 9 and enters the filter element 4, and the second step of fine separation is carried out in the filter element 4. The separated oil particles adhere to the inside of the filter element 4 and the clean gas exits the separator from the centre of the filter element 4 along the outlet 6. Since the pressure loss of the separator is mainly concentrated in the filter element 4 part, the pressure loss is in direct proportion to the square of the airflow speed, and the way of reducing the pressure loss of the airflow in the filter element 4 and improving the fine separation efficiency is mainly to reduce the speed of the airflow flowing through the filter element 4. When the mixed gas flow flows through the deswirler 11, high-speed centrifugal motion is converted into low-speed axial motion, so that the separation efficiency of fine separation of the mixed gas flow in the filter element 4 can be improved, and the kinetic energy of the gas flow can be converted into pressure energy, thereby achieving the purposes of energy recovery and energy consumption reduction of the separator.
The following compares the oil-gas separation performance of the centrifugal separator for the traditional compressor and the energy-saving centrifugal separator of the invention to verify the improvement of the energy-saving centrifugal separator of the invention on the application status of the separator for the traditional compressor. Firstly, the theoretical analysis of the multi-stage separation sleeve is beneficial to improving the separation efficiency of the centrifugal separator; next, numerical simulation calculations were performed comparing the separation performance of the centrifugal separator with the derotator and the existing separator to illustrate the effective function of the derotator.
(1) Theoretical analysis of multistage separation sleeve for improving separation efficiency of centrifugal separator
The addition of multi-stage sleeves to the centrifugal separator can improve the separation efficiency of the separator when the gas flow rate is changed in a large range. Comparing FIGS. 7 and 8, the radial distance for droplet separation in a conventional centrifugal separator is R-R; in separators with multi-layer separating sleeves, the droplets being separated by a radial distance of
S represents the number of the separation sleeves, and is, for example, 2. The key quantity in the process of settling the liquid drops is the settling velocity v of the liquid drops, and the settling velocity calculation formula of the liquid drops can be obtained by analyzing the stress of the liquid drops in the separator:
wherein:
w-angular velocity of the droplet
rLRadius of centrifugal movement of the droplets
v-settling velocity of liquid droplets
d-droplet diameter
ρL-droplet density
ρgDensity of gas
Viscosity of mu-gas
It can be seen from the formula that the settling velocity of the droplets is only related to the diameter of the droplets, the gas density, the droplet density and the velocity of the gas stream (angular velocity) entering the separator, and the addition of multiple layers of separation sleeves does not affect the settling velocity of the droplets. When the air flow velocity in the centrifugal separator bowl increases, the droplet particles sink due to the greater centrifugal force to which they are subjectedThe reduction rate is also increased, so that the separation efficiency is kept constant or increased appropriately. When the gas flow in the cylinder is reduced, the gas flow speed is reduced, and the centrifugal force applied to the liquid drops is reduced, so that the settling speed is reduced. Referring to fig. 7, the path of the droplet particles moving along the radial direction is R-R, when the gas flow is reduced, the speed of the droplet moving along the radial direction is also reduced, the settling time for the droplet moving to the inner surface of the cylinder to be separated is longer, and the separation efficiency is reduced. Referring to fig. 8, if two layers of sleeves are added to the separator drum, the distance of the liquid drop moving along the radial direction is reduced
Even if the settling velocity of the liquid drops is reduced due to the reduction of the gas flow, the liquid drops can move to the inner surface of the cylinder (and the sleeve) in a short time and be separated. Therefore, the centrifugal separator with the multi-layer sleeve can keep high separation efficiency under the condition that the working conditions are changed in a wide range.
In addition, referring to fig. 3, the distance between the gap positions and the level of the oil-gas mixed gas inlet (usually, the gap and the inlet are located on the same horizontal plane) is gradually increased according to the sequence of 2 flow-dividing cylinders arranged from outside to inside, so that the centrifugal motion of the gas flow is ensured to be formed, and the flow-dividing is completed as soon as possible, thereby further improving the separation efficiency.
(2) Comparison of the separation Performance of a centrifugal separator with a deswirler with an existing separator
Principle analysis of the despin device: referring to fig. 6, the arrangement of the deswirler in the barrel essentially forms an axial flow cyclone separator with inverted inlet swirl vanes, the vane inlet angle of the deswirler is tangential to the direction of the air flow velocity in the separator, and the vane outlet angle is vertical. The purpose is to despin the oil-gas mixture that will get into the filter core and carry out the fine separation, has reduced the motion route of mixture to reduce the pressure loss of air current.
In order to verify the function of the despin device, a numerical simulation calculation model of the traditional centrifugal separator is established, and the despin device is additionally arranged on the separator model to respectively perform numerical simulation calculation and compare calculation results. The results show that:
the derotator rectifies the rotating airflow, and after the airflow passes through the derotator, the tangential velocity of the airflow is reduced, and a part of kinetic energy is converted into pressure energy. The velocity profiles of the two separators are compared as shown in fig. 9. The diameter of the inner cylinder of the separator is 3/4 of the diameter of the cylinder of the separator, and when the deswirler is added into the traditional separator, the airflow speed of the inner cylinder is greatly reduced and can be reduced by about 33 percent. The reduced kinetic energy is converted into pressure energy, so that the energy recovery of the pressure energy is realized, and the aim of saving energy is fulfilled. Static pressure losses at the inlet and the outlet of the separator are calculated according to a mass weighted average method, and when the operating pressure is 0.8MPa, the static pressure loss of the centrifugal separator is reduced by 45.44% compared with that of the traditional separator under the same working condition, so that the kinetic energy of airflow can be effectively recovered.
Claims (7)
1. A centrifugal oil-gas separator is characterized in that: comprises a cylinder body (2), an oil-gas mixed gas inlet (7), an oil discharge port (12) and a clean gas outlet (6), wherein the oil-gas mixed gas inlet (7), the oil discharge port (12) and the clean gas outlet (6) are arranged on the cylinder body (2), a single shunt cylinder or a plurality of shunt cylinders which are mutually nested are arranged in the cylinder body (2), and separation sleeves which are positioned at the lower ends of the shunt cylinders and have the same number with the shunt cylinders, each shunt cylinder is connected with the upper end of a corresponding separation sleeve, the lower end of each separation sleeve is positioned above the oil discharge port (12), an inner cylinder (9) is arranged in each separation sleeve or the innermost separation sleeve, the inner cylinder (9) and the single shunt cylinder or an annular region between the innermost shunt cylinders in the plurality of shunt cylinders which are mutually nested form a centrifugal separation region, and the cylinder (2) and the single shunt cylinder or an annular region between the outermost shunt cylinders in the plurality of, the annular area between any two adjacent inner and outer shunt cylinders forms a corresponding Mth centrifugal separation area, M is more than or equal to 3, and each shunt cylinder is provided with a notch for enabling the oil-gas mixed gas entering the cylinder body (2) through the inlet (7) to flow into each centrifugal separation area; the filter is characterized in that a filter element (4) is arranged in the inner barrel (9), a derotation device (11) is arranged at the bottom of an annular interval area between the inner barrel (9) and the filter element (4), and the top of the filter element (4) is opposite to the clean gas outlet (6).
2. The centrifugal oil-gas separator according to claim 1, wherein: the notch is formed by locally and radially swinging the side wall surface of the splitter cylinder outwards by a certain angle.
3. A centrifugal oil-gas separator according to claim 1 or 2, wherein: the gap and the oil-gas mixed gas inlet (7) are spaced in the horizontal direction, and the gap is gradually increased along the sequence of the plurality of flow distribution cylinders distributed from outside to inside and the distance between the plurality of flow distribution cylinders and the inlet (7).
4. The centrifugal oil-gas separator according to claim 1, wherein: the despin device (11) adopts a spinner with an inverted blade.
5. The centrifugal oil-gas separator according to claim 4, wherein: the angle of a blade inlet (17) of the deswirler (11) is tangential to the direction of the airflow outside the inner cylinder (9), and the angle of a blade outlet (16) is the axial direction of the inner cylinder (9).
6. The centrifugal oil-gas separator according to claim 1, wherein: the cylinder body (2), each centrifugal separation area, the inner cylinder (9) and the filter element (4) are coaxially arranged.
7. The centrifugal oil-gas separator according to claim 1, wherein: the oil drain port (12) is communicated with the liquid collecting area (1) positioned at the bottom of the cylinder body (2).
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| CN109236658B (en) * | 2018-10-26 | 2024-02-09 | 南京晨光森田环保科技有限公司 | Oil-gas separator |
| CN109798238A (en) * | 2018-12-18 | 2019-05-24 | 西安交通大学 | A kind of cyclone type oil-gas separator and separation method |
| CN114183362A (en) * | 2021-11-03 | 2022-03-15 | 杰瑞石油天然气工程有限公司 | Oil-gas separation device and oil injection screw compressor unit |
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| US4388087A (en) * | 1981-08-07 | 1983-06-14 | Tipton Joe D | Cyclonic separator-filter |
| CN1804514A (en) * | 2005-01-11 | 2006-07-19 | 东元电机股份有限公司 | Rotary and centrifugal type flash vaporization groove energy saving device |
| RU2454266C1 (en) * | 2011-02-04 | 2012-06-27 | Эдуард Владимирович Юрьев | Vortex-type gas separator (versions) |
| RU2452555C1 (en) * | 2011-05-03 | 2012-06-10 | Эдуард Владимирович Юрьев | Vortex-type gas-fluid separator |
| CN102168677A (en) * | 2011-05-17 | 2011-08-31 | 上海优耐特斯压缩机有限公司 | Combined structure of vertical oil-gas separating cylinder and inside-admission and outside-exit type oil-gas separating core |
| CN202195631U (en) * | 2011-08-24 | 2012-04-18 | 李元超 | Oil separation device for air conditioner |
| CN203362453U (en) * | 2013-06-18 | 2013-12-25 | 宁波欣达螺杆压缩机有限公司 | Structure for installing safety valve in air compressor separator |
| CN203420850U (en) * | 2013-06-19 | 2014-02-05 | 聚才实业(深圳)有限公司 | Oil-gas separator of air compressor and air compressor |
| CN203710815U (en) * | 2013-12-25 | 2014-07-16 | 潍柴动力股份有限公司 | Oil-gas separator |
| CN205340359U (en) * | 2015-12-31 | 2016-06-29 | 广西玉林卓越动力发电设备有限公司 | Novel dehydration of cyclone formula device |
| CN106621582A (en) * | 2016-12-19 | 2017-05-10 | 四川雷鸣环保装备有限公司 | Multi-polar vortex separator |
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Denomination of invention: A centrifugal oil gas separator Effective date of registration: 20230516 Granted publication date: 20200317 Pledgee: China Wuping of Longyan Branch Bank of Limited by Share Ltd. Pledgor: Fujian ipsi Industry Co.,Ltd. Registration number: Y2023980040691 |
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