WO2001066950A1 - Pompe-compresseur sous vide a circulation de liquide et a tambour - Google Patents

Pompe-compresseur sous vide a circulation de liquide et a tambour Download PDF

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Publication number
WO2001066950A1
WO2001066950A1 PCT/CN2001/000001 CN0100001W WO0166950A1 WO 2001066950 A1 WO2001066950 A1 WO 2001066950A1 CN 0100001 W CN0100001 W CN 0100001W WO 0166950 A1 WO0166950 A1 WO 0166950A1
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WO
WIPO (PCT)
Prior art keywords
rotor
liquid ring
drum
liquid
gas
Prior art date
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PCT/CN2001/000001
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English (en)
Chinese (zh)
Inventor
Zigang Jiang
Original Assignee
Zigang Jiang
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 Zigang Jiang filed Critical Zigang Jiang
Priority to AU23438/01A priority Critical patent/AU2343801A/en
Publication of WO2001066950A1 publication Critical patent/WO2001066950A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F04C19/002—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids with rotating outer members

Definitions

  • Liquid ring vacuum pump / compressor is a gas conveying compression machine that pumps gaseous medium at a given inlet and outlet pressure, or continuously works for obtaining a specified volume of vacuum or maintaining pressure. It is mainly confined by the casing and the liquid ring. It is composed of an impeller rotor and other auxiliary components installed eccentrically in the cavity. When the rotor rotates, the working fluid is driven to flow in a circular manner in the constrained cavity. The liquid ring seals, sucks, compresses, discharges, and cools the gas between the rotor blades.
  • Liquid ring vacuum pumps / compressors have been designed, manufactured and used for nearly a century. Several improvements have been made during this period, and performance has continued to improve. As this machine has the characteristics of stable performance, reliable operation, easy maintenance, low noise and high efficiency, it is widely used. In many industries such as chemical industry, petroleum, metallurgy, machinery, energy, food, medicine, environmental protection, etc., it has become a key equipment in production lines that include gas phase operations.
  • liquid ring vacuum pump / compressor has the following disadvantages.
  • the end-face gas distribution plate mechanism generates mechanical friction loss and local resistance loss due to its poor flow channel characteristics, and also causes complex problems such as machine parts wear and compensation control, so that the liquid ring vacuum pump / compressor has no wear,
  • the advantage of high stability is discounted. Due to the limitation of the degree of sealing, the friction of the parts of the valve plate mechanism is difficult to eliminate. In addition, the flow field characteristics of this structure are not good, and it is difficult to make large improvements.
  • the invention of the rubber one-way exhaust valve can reduce the turbulence caused by the differential pressure of the pulsation pressure, and can improve the efficiency of the machine, but at the same time introduces additional pressure loss.
  • the improvement of the gas distribution mechanism is not the main technical issue concerned by the present invention. Therefore, the literature in this regard is not a comparative document of the present invention.
  • the friction loss between the liquid ring and its confined cavity is ranked first, and the flow path characteristic loss and gas distribution loss are the second and third problems to be solved respectively.
  • the main objectives of the present invention are: 1. Design a new liquid ring accommodating and restraining mechanism for a liquid ring vacuum pump / compressor, which can eliminate the friction between the liquid ring and the casing, and greatly reduce energy loss. Improve the efficiency of the machine; 2. Design a new gas distribution and air compression mechanism without the need for a gas distribution plate mechanism, which can fundamentally improve the flow field characteristics near the intake and exhaust ports, reduce friction and turbulence losses In order to eliminate the wear of the parts, smooth the air flow and make the pressurization process continuous, in order to further reduce energy consumption and improve the performance of the machine.
  • the solution for achieving the first object of the present invention is to use a rotating drum that rotates synchronously with the liquid ring.
  • the rotating drum is installed in the casing, and the rotor is eccentrically installed in the rotating drum.
  • the center of the end plates on both sides of the drum is open to serve as a space for air flow and other supporting mechanisms such as support, transmission and gas distribution plates.
  • the end plate on one side of the drum is removable for rotor loading and unloading and maintenance.
  • the rotating drum, the rotor and the casing according to the present invention are connected by two bearings each. Since the distance between the drum shaft and the rotor shaft is small, it is necessary to install certain independent bearings without interfering with each other, and to install other mechanisms that may be required, which requires certain space planning skills.
  • the design of the present invention is: two opposite shaft piers are arranged on the axis of the drum, and the shaft piers are rigidly connected with the casing.
  • the shaft piers have an outer cylindrical surface pedestal and an inner cylindrical surface pedestal, or an end face of the shaft pedestal is also provided with a valve plate that contacts the center of the rotor end surface.
  • the outer cylindrical surface pedestal is axially inboard and coaxial with the drum.
  • the size of the outer cylindrical shaft platform is large enough to allow the airflow channel and the eccentric rotor shaft to pass through in the middle countersink. If no closed duct is used for the airflow channel, the size of the outer cylindrical surface pillow can be reduced, and only the eccentric rotor shaft is allowed to pass, while the airflow flows from the bearing through the ribs at the center of the end face of the rotating drum.
  • the inner cylindrical surface of the abutment is staggered outward by an axial distance to arrange the airflow channels and other accessories.
  • the inner cylindrical bearing can be simplified as a shaft hole, a sliding bearing sleeve, or staggered inward.
  • a small inner cylindrical surface abutment with axial distance, and an outer cylindrical surface abutment is arranged on the outside.
  • the inner cylindrical bearing is coaxial with the rotor and is used to install the outer shell of the rotor bearing.
  • the outer sleeve of the drum bearing is inserted into the bearing sleeve at the center of the end face of the drum, so that the drum can rotate freely about the axis of the shaft pier.
  • the inner sleeve of the rotor bearing is sleeved on the rotor shaft passing through the inner pillow block, or the rotor shaft is directly inserted into the sleeve, so that the rotor can rotate freely about the eccentric axis. .
  • the other main structure layout of the machine is:
  • the rotating shaft of the rotor protrudes from the bearing at one end, and is connected to the power equipment such as the motor through the transmission mechanism.
  • the air inlet and exhaust are located at both ends of the drum, and lead out of the casing from the axial or radial direction.
  • the power machine drives the rotor to rotate in the drum, and the liquid in the drum is driven by the rotor to quickly form a liquid ring.
  • the initial disturbance of the working fluid by the rotor starting and the tangential component of the working fluid velocity during the formation of the liquid ring are all applied to the drum by the viscous force medium to form a continuous acting momentum moment, which makes the drum start and Gradually accelerate.
  • the drum is stabilized at a constant speed, and the linear velocity on the inner wall of the drum is only slightly different from the linear velocity on the outer layer of the liquid ring.
  • Another important improvement of the second invention achieved by the present invention is to replace the cylindrical blade rotor with a spiral rotor.
  • the specific solution is as follows: the valve valve mechanism and the cylindrical blade rotor at both ends are eliminated, and a spiral rotor is eccentrically installed in the drum.
  • the rotor consists of a rotating shaft, a hub, and two or more spiral blades wound on the hub. When the machine is working, two or more spiral flow channels are formed between adjacent spiral blades, the surface of the liquid ring and the surface of the hub, which are isolated from each other.
  • each spiral flow channel is closed on the eccentric side by a liquid ring to form a liquid seal, and the liquid seal line advances from the air inlet to the air outlet with the rotation of the spiral flow channel. Therefore, each spiral flow channel becomes an automatic gas distribution and compression channel, which can transport and compress the gas unidirectionally and continuously.
  • the design scheme of the dynamic seal of the present invention is: a dynamic seal ring is provided at one end of the rotary drum (usually at the end of the exhaust port), and the ring is a stationary annular ring coaxial with the rotary drum and perpendicular to the shaft; Flakes.
  • the ring is rigidly connected to the casing by connecting the neck tube, and is in sealed communication with the wall of the airflow duct at the same end.
  • the outer diameter of the connecting neck tube is slightly smaller than the opening of the end face of the rotating drum, and the opening extends into the gap outside the end face of the inner rotor of the rotating drum to make a sealing connection with the dynamic seal ring.
  • the outer edge of the dynamic seal ring is immersed in the liquid ring, and the minimum depth Hmin of the radial immersion in the liquid ring should meet the inequality
  • AP max is the upper limit of the pressure difference between inlet and outlet
  • P is the density of the working fluid
  • ⁇ is the rotational angular velocity of the liquid ring
  • r is the surface radius of the liquid ring.
  • the working fluid forming the liquid ring may be taken away by the pumped gas and needs to be replenished. It may be contaminated by the pumped gas with dust, fibers and other impurities and need to be cleaned. In addition, the working fluid needs to be cooled to release the compressed gas. The heat transferred to it from time to time, so circulation is essential. Liquid ring level control is more important. It is a prerequisite for the normal operation of the liquid ring pump, so the control should be stable and reliable. The rotation of the liquid ring restraint container brings certain difficulties to the connection of the circulation pipeline and the liquid ring level control.
  • a solution of the present invention is: circulate the working fluid into the pipe to lead to the stationary shaft piers, and Fortunately, on the shaft pier of the air intake port, it enters the drum through the axial through hole on the shaft pier, and turns 90 degrees in the gap outside the end face of the rotor to flow out to the position of the liquid ring design surface.
  • the pipeline is stationary.
  • the working fluid outlet tube in the drum is connected from the outer edge of the end cap on the other side of the drum. After the end cap is turned 90 degrees to point to the center, the opening is released when it reaches the position of the liquid ring design surface.
  • the position of the opening can be fine-tuned, and the depth of the liquid ring can be fine-tuned by adjusting this position.
  • This solution can automatically stabilize the depth of the liquid ring, solve the problem of liquid level control by the way, and is simple and reliable without the need for additional power and control.
  • this pipeline is rotating with the drum, and the outflow liquid will be thrown out along the tangent direction of the surroundings.
  • a liquid collecting tank can be opened at a corresponding position in the casing, and the liquid is thrown out by gravity to the lower part, and then drawn out through a stationary pipe.
  • the rotating outlet pipe should be arranged symmetrically in two ways, or a symmetrical balance pipe should be arranged.
  • the working fluid circulation outlet in the drum can also be set at the designed liquid level position on the dynamic seal ring.
  • the drum is led out through the inner cavity of the neck tube through a pipe, and then passes through the neck tube for external circulation connection.
  • This is a static pipeline all the way, the structure is simpler.
  • a two-phase negative pressure source with lower pressure is required to work. In this case, its simplicity, reliability and stability are inferior to the former.
  • the central part of the helical rotor according to the present invention is a cylindrical or slightly tapered dome-shaped hub.
  • Cylindrical hub rotors are suitable for horizontal liquid ring vacuum pumps / compressors.
  • Slightly tapered dome-shaped hub rotors are suitable for vertical models. Its taper depends on the ratio of the acceleration of gravity to the average value of the centripetal acceleration of the liquid ring.
  • the blades of the helical rotor are helical curved sheets of equal width, integrated with the hub, and are perpendicular to the axis of the rotor everywhere. In each plane perpendicular to the axis, the spiral blades have the same cross-section and are distributed at equal angles.
  • the rotation angle of each spiral around the hub is not less than (l + 1 / n) X 360 ° so that there is at least one liquid ring seal line in the flow path between adjacent blades Isolate the air inlet and the air outlet.
  • the inner diameter of the rotating barrel, the outer diameter of the spiral rotor, the diameter of the hub and the eccentricity of the rotating shaft should be properly designed in accordance with the requirements basically the same as those of the cylindrical impeller rotor, and the liquid level of the liquid ring should be controlled so that There is only a small gap between the outer edge of the spiral blade of the rotor and the inner wall of the drum when it is far away from the liquid ring axis, and it can still be submerged into the liquid ring when it is closest to the liquid ring axis.
  • the minimum depth of the spiral blade immersed in the liquid ring is also The conditions for effective sealing of the maximum pressure differential that can occur in the flow channels on both sides of the blade.
  • a major constraint in the inequality group is: When the rotor is operating, the outer edge of the blade should always be immersed in the liquid ring.
  • this constraint condition should be modified as follows: When the spiral rotor is operating, the outer edge of the blade should always be immersed in the liquid ring, and at the closest point to the axis of the drum, the minimum depth of immersion h min should satisfy both sides of the blade Conditions to achieve sealing when the maximum pressure difference occurs between the runners, that is, 11 1 ⁇ > [2 11 ⁇ / ( ⁇ 2 ) + r 2 ] 1/2 ⁇ r, where A p max is likely to occur between the runners on both sides
  • the maximum pressure difference is determined by the maximum pressure difference between the inlet and outlet gas, the working angle of the spiral flow channel and the local parameter design of the compression zone.
  • P is the density of the working fluid
  • ⁇ is the angular velocity of the liquid ring
  • r is the surface of the liquid ring. radius.
  • a further improvement of the present invention is: the spiral blades are made to have a variable pitch, so that the cross-sectional area of the flow channels between the spiral blades gradually becomes larger and smaller, and the number of seal lines in the spiral flow channels is increased so that the same flow channel
  • the pressure difference of each sealing section is reduced, and its distribution is made uniform. In this way, the dynamic range of the pressure difference on both sides of the spiral blade can be reduced to a suitable level, so as to reduce the requirements for blade sealing.
  • the specific method is: Make the spiral rotor blades have a larger working angle, which should generally exceed (l + 1 / n) X 360 ° (n ⁇ 2) several times, and according to the pumped gas at the inlet and outlet
  • the overall adjustment of the diameter and speed of the rotating drum and the helical rotor can compensate for the decrease of the pitch due to the increase of the working angle to meet the requirements of displacement design.
  • a formula for calculating displacement is
  • Q is the displacement (cubic meters / second)
  • n is the number of spiral heads
  • ⁇ is the angular velocity of the rotor (radians / second)
  • V is the volume of the first closed section of the runner, which is determined by the rotor diameter and the rotor shaft relative to the rotor shaft
  • a volume fraction determined by factors such as the eccentricity (independent variable) and the function of the pitch as a function of axial distance. It can be seen from this formula that the displacement is proportional to the number of screw heads, the volume of the first closed joint of the flow channel, and the speed of the rotor.
  • the volume of the first closed section of the flow channel is proportional to the axial distance of the first 360 ° advance of the spiral blade, and inversely proportional to the number of spiral heads, if the volume of the spiral blades is ignored, the displacement is actually independent of the number of spiral heads , Which is directly equal to the product of the three factors: the number of revolutions per second, the difference between the hollow area of the cross section of the liquid ring and the cross-sectional area of the hub, and the axial distance of the helical blade in the first 360 °.
  • the increase of the number of screw heads and the increase of the screw working angle are only measures taken to increase the compression ratio and reduce the requirements of adjacent channel sealing.
  • Adjacent channel seal depth is inversely proportional to the surface radius of the liquid ring, inversely proportional to the square of the speed of rotation, inversely proportional to the number of screw heads, and generally inversely proportional to the working angle of the screw. In most cases, increasing the number of screw heads and the working angle of the screw is the first choice to increase the design compression ratio.
  • the invention also specifically includes a structural design that reduces the difficulty of processing the spiral rotor, and an inexpensive spiral rotor processing method made possible by the structural design.
  • a structural design that reduces the difficulty of processing the spiral rotor, and an inexpensive spiral rotor processing method made possible by the structural design.
  • the machining of helical blade rotors is difficult, and the machining of multi-helix and variable pitch rotors is even more difficult. Since there is no direction to release the mold, it is not possible to use an inexpensive mold forming process, but only Manufactured using expensive CNC cutting methods, which is not conducive to mass production and cost reduction.
  • the spiral rotor is assembled by axially fastening multiple segments, wherein the working angle of the rotor blades in each segment is equal to 360 ° / n (n is the number of heads), and On the setting position of the end face, there are yin and yang positioning pins that can ensure that the spiral blades accurately kiss during assembly.
  • the matching manufacturing method of the present invention is: According to the standardization and serialization planning, all the spiral rotor segments with an operating angle equal to 360 ° / n (n is the number of heads) are decomposed into an accessory series. These rotor sections are manufactured by two-clamping or partial forming. Prepare two molds for the corresponding process, use plastic or metal materials to make a series of accessories through injection molding, precision casting or powder metallurgy, or use a blanking mold to punch the sheet into a rotary leaf, and then use a special tire to punch it. The method of connecting to the hub makes a series of accessories.
  • Rotor segments with different pitches and different pitch change rates are connected in series, and can be assembled into a rotor suitable for any specific volume ratio of inlet and outlet gases.
  • the rotor segments with different pitches and fixed pitches can also be connected in series, which can be assembled into variable-pitch spiral rotors with approximate optimal variation rules suitable for any specific volume ratio of gas at the inlet and outlet.
  • the above series of accessories can also be provided to the user, so that they can replace parts during use, and change the working parameters and performance of the equipment on the spot.
  • the inventions such as the rotating drum, helical rotor, and variable pitch helical rotor that rotate with the liquid ring are important improvements to the liquid ring vacuum pump / compressor, and their effects are more significant.
  • the large-area high-speed friction between the liquid ring and the casing is eliminated due to the function of the drum mechanism, and the angular velocity difference between the laminar flows inside the liquid ring is also greatly reduced.
  • the friction loss between the two and the laminar flow inside the liquid ring becomes very small, which can be almost ignored.
  • the efficiency of rotary liquid ring vacuum pumps / compressors can thus be taken to a new level.
  • the design of helical rotors especially variable-pitch helical rotors, adopts the method of segmented manufacturing and axial assembly of the die forming process, which is not difficult. This method can make the design and production of the helical rotor easy, the cost is reduced, it is conducive to standardization and serialization, and it is conducive to increasing the type of the machine and expanding the scope of use of the machine.
  • the present invention also has some flaws which constitute disadvantages and problems from a certain perspective.
  • the introduction of spiral rotors especially the introduction of spiral rotors with large working angles, lengthens the flow channel, which increases The friction path and loss of gas.
  • Another example is the change from radial compression to axial compression, which requires the liquid ring seal depth to increase, which results in increased friction loss between the blade and the liquid ring.
  • the small gas viscosity coefficient (2 to 3 orders of magnitude smaller than liquid) and the small amount of static pressure equilibrium (2 to 3 orders of magnitude smaller than in the standard state) in an overweight state in a liquid ring, this increase It is smaller in number.
  • the invention includes the design of a class of uses and usage of the rotary liquid ring vacuum pump / compressor under the conditions. Its content is: at a lower temperature of not more than 100 ° C or at ordinary temperature, at a lower pressure of not more than 10OKPa or at normal pressure, when the density of the gas produced during the process is higher than the density of air under standard conditions (1.29Kg / m 3 ) is much smaller, for example, when it is less than 60%, especially when the gas density is smaller than that of air, or when the temperature and pressure of the gas are very unstable during the process, the rotary vacuum pump / compressor In this type of process, it is used as a pump with constant current characteristics suitable for low density and large specific volume gas. This type of process includes vacuum acquisition of containers operating at normal temperature and pressure, material fractions, liquid degassing, material drying, tail gas condensation, pressurized circulating gas, bag dust removal, and so on.
  • the present invention also includes a method for selecting a working fluid in the above-mentioned uses.
  • the method is: when the pumping medium needs to be recovered and has a high affinity with water, and it is not suitable to use water as a working fluid, a water-insoluble and incompatible working medium (non-volatile to working medium, insoluble working medium) )
  • Oily substances such as vegetable oil to air or water vapor
  • this mixed oil is used as the working fluid to allow the oil to participate in the circulation and control the proportion of oil so that it forms a surface on the surface of the water ring. Thinner insulation film.
  • Water has a high density, high specific heat, a small viscosity coefficient, and is safe and non-toxic. Therefore, it is a liquid ring pump working fluid with the best working characteristics, and water is the cheapest and most widely distributed. Therefore, water can be used as a working fluid. At this time, other liquids are never considered.
  • the affinity of the pumped medium and water is large, such as high solubility, or some undesired physical and chemical reactions will occur, according to the considerations of the prior art, it is generally not necessary to use water as a working fluid and to find other liquids instead. The cost is therefore rise.
  • the benefits of using oil-doped water as a working fluid are self-evident if feasible.
  • the reason why the method of the present invention is feasible is that the liquid ring is in an overweight state with hundreds or even thousands of gravitational accelerations. In such a supergravitational field, the buoyancy of oil that is 20% less than the specific gravity of water is large. Amazing (about 10 times the buoyancy of mercury to vacuum), so the oil floating on the water The membrane is like a sturdy rubber membrane that surrounds the surface of the liquid ring so that the pumped medium cannot come into contact with water. Although the impact and friction of the rotor blade on the working fluid will emulsify the oiling water, especially the tendency to produce oil-in-water emulsification, it may cause the oil seal to fail.
  • hydrophilic gases such as carbon dioxide, ammonia gas, various kinds of acid and tritium gas, and even pump water vapor.
  • Figure 1 is a schematic diagram of a vertical design of a rotary liquid ring vacuum pump / compressor in a specific application, where the rotor is a double-headed helical rotor.
  • Figure 2 is a schematic diagram of a horizontal design of a rotary-liquid-type liquid ring vacuum pump / compressor of a variable-pitch helical rotor assembled axially with a fixed-pitch rotor section.
  • the rotary liquid ring vacuum pump / compressor is mainly composed of three parts: a casing 14, a rotary drum 10 and a 540 degree double-headed screw rotor 9.
  • the drum 10 has a cylindrical inner cavity for receiving and restraining the liquid ring, which is a cavity that can rotate in the casing.
  • the rotating drum is installed between the casing and the rotor, and the end plates of the two end plates are open at the center, and the bearings are connected through the upper bearing support ribs 6 and the lower bearing support ribs 15, respectively.
  • the upper end cover 4 is detachable.
  • the spiral rotor 9 can be inserted from the detachable upper end cover of the drum, and can be rotated therein.
  • each of the shaft piers 0 and 17 has an outer cylindrical bearing platform, which is fitted with the inner surfaces of the upper and lower bearings 7 and 13 of the drum, respectively.
  • Bearing sleeve for transitional mating assembly.
  • a hole is formed in each of the shaft piers 0 and 17 where the eccentric axis of the helical rotor passes, and the hole is fitted with a sliding bearing sleeve through a tight fit to install the upper end 8 and the lower end 12 of the helical rotor shaft. In this way, the drum can be installed around the rotor and can rotate independently.
  • the shaft piers 0 and 17 are rigidly connected to the housing through the upper and lower shaft piers 3 and 16 of the housing.
  • the intake airflow channel is the space between the ribs of the lower shaft piers 16 of the casing and the lower bearing ribs 15 of the rotor, and the airflow enters directly through the air inlets at the lower part of the casing.
  • the exhaust airflow channel is the space between the ribs 3 on the casing and the bearing ribs 6 on the drum, and the airflow passes directly between them to the exhaust port 2 on the upper part of the casing.
  • the lower end 12 of the rotating shaft of the spiral rotor extends out of the casing from the inside of the sleeve, and is connected to the motor through a coupling.
  • the air intake and exhaust are led axially from below and above the enclosure.
  • the screw rotor rotates at a high speed in the drum, which drives the working fluid to form a liquid ring.
  • the working fluid enters from the circulation inlet pipe 1, flows through the channel in the center of the rotor, and flows into the drum from the working fluid circulation inlet 11.
  • the rotor accelerates it and throws it towards the drum wall. The moment formed by the tangential component of the impulse is enough to start the drum slowly.
  • the dynamic seal ring 5 of this embodiment is directly mounted on an adjustable neck tube where the upper shaft pier and the casing are threaded.
  • the neck tube can be adjusted in position axially, so that the dynamic seal ring and the lower surface of the upper end cover 4 of the drum and the There is a protective distance between the upper surfaces of the upper bearing ribs.
  • the outer diameter of the movable seal ring has sufficient dimensions to ensure that the maximum pressure difference between the space between the exhaust port 2 and the drum 10 and the casing 14 communicating with the air inlet 16 is sealed.
  • the liquid seal depth calculated according to the above inequality is very small, because the liquid ring is in an overweight state with hundreds of gravitational accelerations.
  • the center portion of the helical rotor in FIG. 1 is a slightly tapered dome-shaped hub, whose taper is equal to the ratio of the acceleration of gravity to the average value of the centripetal acceleration of the liquid ring.
  • the hub has a double-headed spiral blade 9 and the rotation angle around the hub is 540 °. Therefore, no matter what angle the rotor rotates, each spiral flow channel has at least one liquid ring seal line to isolate the air inlet and the air outlet, and the isolation line is always Advancing from the air inlet to the air outlet, the air can be continuously sucked into the flow channel from the air inlet, and the sucked gas can be continuously pushed to the air outlet, and its volume can be compressed.
  • the speed difference with the blade will be adaptively reduced.
  • the diameter of the rotor is smaller than the outer diameter of the liquid ring (slightly larger than 4/5) and its angular velocity is greater than the angular velocity of the liquid ring, the linear velocity difference corresponding to the same radius difference is also greater than the liquid ring. Therefore, on the eccentric side, the outer edge of the rotor blade has a large linear velocity difference with the liquid ring, and the linear velocity difference at the root is small or may be negative, so the force of the rotor blade on the liquid ring is mainly concentrated outside Along, that is, the deep part of the liquid ring.
  • the result of this external force acting in the deep part is the driving of a balance drum resistance torque, and the rest of the disturbance will rapidly decay under the action of the super-stability mechanism of the super gravity field.
  • the effect mode that can accumulate its effects during the transient state and participate in the moment equilibrium during the steady state is the side friction of the blade. It can be seen that when the drag torque is small, the liquid ring has good stability, and all the functions of the liquid ring can function normally.
  • variable-pitch helical-rotor-type liquid ring vacuum pump / compressor and the manufacturing method of the variable-pitch helical rotor axially assembled with a fixed-pitch rotor section are described below with reference to FIG. 2.
  • variable-pitch screw rotor rotary liquid ring vacuum pump / compressor is mainly composed of a casing 14, a rotary drum 10, and a double-headed screw rotor 9, which are horizontal models.
  • the drum 10 has a cylindrical inner cavity for receiving and restraining the liquid ring.
  • the drum is installed between the casing and the rotor.
  • the center of the end plates at both ends is open, and its bearings are connected by the right bearing support ribs 6 and the left bearing support ribs 15.
  • the right end plate 4 is detachable.
  • the spiral rotor 9 can be inserted from the detachable right end cover of the drum, and can be rotated therein.
  • the left end 12 of the rotating shaft of the spiral rotor extends out of the casing from the shaft sleeve, and is connected to the motor through a coupling.
  • the air inlets and exhausts are led axially from the left and right sides of the cabinet.
  • the dynamic seal ring 5 is directly mounted on the adjustable neck tube where the right shaft pier is threaded to the casing, and the outer diameter of the ring is sufficient to ensure that the exhaust port 2 and the rotor communicating with the air inlet port 16 are sealed. Large pressure difference in the space between 10 and cabinet 14.
  • the hub of the helical rotor in FIG. 2 is cylindrical, and the hub has a double-headed spiral blade 9 surrounding the wheel.
  • the rotation angle of the hub is 1440 ° (around 4 revolutions).
  • the direction of the demolding is axial.
  • the helical rotor in Fig. 2 shares 8 helical segments.
  • the pitch of each spiral segment is fixed, but the pitch of each segment is different from each other. They were selected from a series of 2-head helical rotor segments prepared according to a standardized and serialized plan and manufactured using a die-forming process.
  • the pitch of each segment can form an L / (m + i) sequence, i is the assembly serial number of the rotor segment, and its value ranges from 1 to 8, L is the axial length of the entire rotor, and m is the ratio of the inlet and outlet gas. Coefficient to be determined by volume or pressure ratio.
  • the helical rotor is assembled axially in series from a rotor segment with a large pitch to a rotor segment with a small pitch.
  • the pitch of the spiral rotor segment constitutes a L / (m + i) sequence
  • the volume of each spiral flow channel segment divided by the liquid seal line also generally constitutes a V / (m + i) sequence (V is constant.
  • V is constant.
  • the two spiral flow channels can only form 7 divided flow channel segments, so the value of i ranges from 1 to 7).
  • the specific volume of the contained gas is inversely proportional to the axial direction. Decreases, so the gas pressure will increase linearly in the axial direction during operation. This pattern of change has two benefits.
  • the outlet liquid seal line of each flow channel when the outlet liquid seal line of each flow channel is opened, its pressure is exactly equal to the outlet pressure, there is no sudden change in pressure and pulsation of air velocity, and the turbulence and inertial loss caused by it will be eliminated;
  • the exhaust port The pressure difference from the air inlet is evenly distributed between the sealed flow channel sections, thereby minimizing the liquid seal depth. For example, if the pressure difference between the inlet and outlet is 203KPa (2 atmospheres), the pressure difference between the runner sections on either side of the blade is roughly 1/7, which is 29KPa.
  • the surface acceleration of the liquid ring hypergravity field is 500g (g is gravity acceleration) and the working fluid is water
  • the calculation of the liquid seal depth based on the surface acceleration only takes about 5.9 millimeters.
  • the centripetal acceleration increases linearly in the radial direction. The value for accurate calculation is even smaller. It can be seen that the required liquid seal depth is very small under the action of the liquid ring supergravity field.
  • the present invention makes many improvements to the structure and working principle of the liquid ring vacuum pump / compressor, and outlines the prototype of a new generation of machines.
  • the elimination of friction between the liquid ring and the cavity wall, the omission of the gas distribution mechanism and the realization of the continuous intake and exhaust mechanism, the characteristics of the flow channel with few turbulence and the formation of the air-flow speed compressor mechanism can make the efficiency of the new machine much larger.
  • the maintenance requirements will be reduced, its operation will be more stable, and its application range will be wider.
  • the invention can not only exert its benefits in the traditional application fields of existing models such as chemical industry, petroleum, metallurgy, machinery, energy, food, medicine, environmental protection, etc., but also can be used as a composition in the fields of construction, fire protection, flood resistance, and desalination. Use of new technology functional devices.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe-compresseur sous vide à circulation de liquide et à tambour rotatif se composant d'un tambour, d'un rotor excentrique et d'un boîtier. La circulation de liquide entraîne la rotation du tambour, réduisant ainsi l'usure et la consommation d'énergie. Si on utilise un rotor hélicoïdal présentant une fermeture hydraulique s'étendant le long du côté excentrique du passage d'écoulement, on confère à la pompe une poussée en continu dans le sens axial et on assure une amenée d'air en déplacement unilatéral tout en jugulant le flux turbulent et la consommation de pompage sans faire appel à une distribution de gaz ni à des pièces d'usure. La compression progressive de la section du passage d'écoulement du rotor à pas réglable génère une compression à vitesse moyenne haute fréquence. Les rotors sont assemblés par deux moules ce qui assure un rapport de compression élevé tout en n'impliquant pas de coûts élevés. Cette pompe-compresseur est spécialement indiquée pour fonctionner en cas d'instabilité à basse température, faible compression et faible densité. Le fluide de travail est un dopant qui, dans des conditions de surcharge, génère une membrane imperméable résistante de manière à assurer une amenée d'air et de liquide.
PCT/CN2001/000001 2000-01-03 2001-01-03 Pompe-compresseur sous vide a circulation de liquide et a tambour WO2001066950A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU23438/01A AU2343801A (en) 2000-01-03 2001-01-03 Rotating drum liquid ring vacuum pump/compressor and its using method

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN00100007.1 2000-01-03
CN 00100007 CN1258817A (zh) 2000-01-03 2000-01-03 转筒式液环真空泵/压缩机

Publications (1)

Publication Number Publication Date
WO2001066950A1 true WO2001066950A1 (fr) 2001-09-13

Family

ID=4575167

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2001/000001 WO2001066950A1 (fr) 2000-01-03 2001-01-03 Pompe-compresseur sous vide a circulation de liquide et a tambour

Country Status (3)

Country Link
CN (1) CN1258817A (fr)
AU (1) AU2343801A (fr)
WO (1) WO2001066950A1 (fr)

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CN112377410A (zh) * 2020-11-10 2021-02-19 湖南创源生物科技有限公司 一种密封效果好的机械真空泵

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CN102808772B (zh) * 2012-08-14 2014-12-31 东北大学 一种等齿顶宽的单头变螺距螺杆转子
CN103062056B (zh) * 2012-12-29 2015-03-18 中国科学院沈阳科学仪器股份有限公司 一种具有组合式螺杆转子的螺杆型干式真空泵
WO2015109048A1 (fr) * 2014-01-15 2015-07-23 Eaton Corporation Procédé d'optimisation de performances d'un compresseur d'alimentation
KR101450507B1 (ko) 2014-06-19 2014-10-15 김학률 스크류날개와 냉각수가 접촉하는 구조의 진공펌프
WO2016206064A1 (fr) * 2015-06-26 2016-12-29 威海凌云流体传动科技有限公司 Pompe à anneau liquide
CN107940526A (zh) * 2017-12-14 2018-04-20 汪弘轩 一种电磁无轴向心式连续涡叶吸排油烟机
CN108131300A (zh) * 2017-12-14 2018-06-08 汪弘轩 一种电磁无轴涡叶向心式高压水泵
CN108105112A (zh) * 2017-12-14 2018-06-01 汪弘轩 一种电磁无轴向心式涡叶高压油泵
CN108105118A (zh) * 2017-12-14 2018-06-01 汪弘轩 一种电磁无轴涡叶向心式燃气加压机
GB2580423B (en) * 2019-01-11 2022-10-05 Fuel Active Ltd Fuel pick-up device
CN111934495B (zh) * 2020-10-12 2020-12-22 南京晨荣环保设备制造有限公司 一种干湿两用油水冷却电机及其冷却方法

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Publication number Priority date Publication date Assignee Title
US4484457A (en) * 1982-02-11 1984-11-27 Siemens Aktiengesellschaft Liquid-ring vacuum pump preceded by a precompressor
US4946349A (en) * 1989-07-19 1990-08-07 National Space Development Agency Of Japan Water ring vacuum pump
EP0494041A1 (fr) * 1991-01-02 1992-07-08 Berendsen Teknik A/S Pompe à anneau liquide
CN2148200Y (zh) * 1992-11-01 1993-12-01 胡平 同步液环泵

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4484457A (en) * 1982-02-11 1984-11-27 Siemens Aktiengesellschaft Liquid-ring vacuum pump preceded by a precompressor
US4946349A (en) * 1989-07-19 1990-08-07 National Space Development Agency Of Japan Water ring vacuum pump
EP0494041A1 (fr) * 1991-01-02 1992-07-08 Berendsen Teknik A/S Pompe à anneau liquide
CN2148200Y (zh) * 1992-11-01 1993-12-01 胡平 同步液环泵

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112377410A (zh) * 2020-11-10 2021-02-19 湖南创源生物科技有限公司 一种密封效果好的机械真空泵

Also Published As

Publication number Publication date
CN1258817A (zh) 2000-07-05
AU2343801A (en) 2001-09-17

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