CN104514719A - Multi-Stage Pump Having Reverse Bypass Circuit - Google Patents
Multi-Stage Pump Having Reverse Bypass Circuit Download PDFInfo
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- CN104514719A CN104514719A CN201410461237.XA CN201410461237A CN104514719A CN 104514719 A CN104514719 A CN 104514719A CN 201410461237 A CN201410461237 A CN 201410461237A CN 104514719 A CN104514719 A CN 104514719A
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Classifications
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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
- 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
- F04C23/003—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 having complementary function
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage 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
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
- F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
-
- 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
-
- 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
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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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C2/025—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents the moving and the stationary member having co-operating elements in spiral form
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A multi-stage pump (1) having a reverse bypass circuit includes a pump (1) head having at least two compression stages (270a) disposed in series with espect to the direction of flow of fluid through the pump (1), and a reverse fluid bypass circuit (290) including a fluid passageway (295) through which fluid flowing between upstream and downstream ones of the compression stages (270a) can he circulated back upstream of the upstream compression stage (270a). The reverse fluid bypass circuit (290) may restrict or stop the flow of fluid through the fluid passageway (295) as long as the pressure differential across the fluid passage (295) is below a predetermined value. To this end, the reverse fluid bypass circuit (290) may be configured to restrict the flow of fluid while the fluid is in its transitional or molecular flow regime, and allow the flow of fluid while the fluid is in its viscous flow regime.
Description
Technical field
The present invention relates to the multistage displacement pump comprising multistage scroll-type vacuum pump.Specifically, the present invention relates to the multistage displacement pump with bypath system comprising vacuum pump, wherein, this bypath system departs from the proper flow path of liquid by pump for impelling the liquid leaving certain grade.
Background technique
Various types of displacement pump (positive displacement pump), such as screw pump, vane pump, Roots's claw pump, scroll-type pump, can be configured to multistage pump.Multistage pump provides multistage compression, thinks the capacity (discharge capacity) that pump provides larger and/or pressure ratio performance.The example of multistage vortex pump is disclosed in U. S. Patent 6068459,5855473,5616015 and 6884047, and the content of these patents is incorporated fully by reference by reference.
In multistage pump, liquid is introduced in first (upstream) level of pump by the entrance of pump, and wherein in the first order of pump, liquid is compressed; Left the first order by the liquid compressed and be directed and enter second (downstream) level, wherein in the second level of pump, liquid is compressed again; Then, in the second level, flowed out the second level by compress liquid and flow to delivery side of pump (directly flow to delivery side of pump or flow to delivery side of pump via pump for the extra downstream stage compressed further) subsequently.Multistage pump can be equipped with forward direction bypass circulation, and under some abnormal operating conditions of pump, the liquid that forward direction bypass circulation makes great majority leave upstream stage gets around one or more downstream stages of pump.
Such as, forward direction bypass circulation is arranged in multistage vacuum pump usually, and wherein the entrance discharge capacity of the first order is much larger than the entrance discharge capacity of the second level.When pump is activated first or when pump is communicated to air, high inlet pressure (that is, atmospheric pressure) can be run in a first stage.In this case, forward direction bypass circulation is by the most liquid around the second level of diverter pump.
Such bypass circulation can be avoided producing excess pressure in the liquid between upstream stage and one or more downstream stage, therefore can prevent the too much power consumption in downstream stage and excessive temperature.Too high power consumption can cause the grease viscosity in the bearing of pump and/or motor overload and the bearing that caused by too high temperature to decline.
But the forward direction bypass circulation of the liquid around one or more downstream stages of this shunting does not solve all potential problem causing the too much power consumption in multistage pump and excessive temperature.In addition, when being applied to multistage scroll-type vacuum pump, such forward direction bypass circulation may cause extra problem.
Summary of the invention
One object of the present invention is, provides a kind of multistage displacement pump preventing the upstream stage of pump and back to back downstream stage from becoming the source of the excessive power consumption of pump.
Another object of the present invention is, provides a kind of multistage displacement pump guaranteeing to reach its design speed.
Another object of the present invention is, provides a kind of and has the end seal (tip seal) of each compression stage for it and guarantee the multistage scroll-type vacuum pump of the device that the end seal of downstream stage is reinforced.
According to an aspect of the present invention, provide a kind of multistage pump, this multistage pump has intake section and discharge section, and comprises pump head and reversed liquid bypass circulation, wherein, this pump head has relative at least two compression stages flowing to tandem arrangement of liquid by pump.
Intake section has pump intake and forms the low voltage side of pump, and wherein liquid is inhaled into pump in this low voltage side.Discharge section has pump discharge and forms compressed side, wherein liquid this compressed side by with than liquid at the high pressure venting from pump of the pressure of low voltage side.Pump head also has the inlet opens (inlet opening) that pump intake extends to and the discharge aperture (exhaust opening) leading to pump discharge.
Each compression stage of compressing mechanism has introducing port and export mouth, and liquid enters this level by introducing port and leaves this level by export mouth.Liquid from pump intake flow to pump discharge extend between the flow path of the process upstream compression stage pump in pump intake and compression stage, extend between the introducing port of the downstream compression stage in the export mouth of the upstream compression stage in compression stage and compression stage, and extend between the export mouth of downstream compression stage in compression stage and pump discharge.Reversed liquid bypass circulation (reversefluid bypass circuit) defines fluid passage, and this fluid passage and flow path are separated and the second position of the upstream of the introducing port of primary importance between the export mouth of a compression stage and the introducing port of a back to back compression stage in this compression stage downstream and this compression stage is connected to flow path.
According to a further aspect in the invention, reversed liquid bypass circulation comprises flow of fluid control gear, flows through fluid passage for restriction or stop liquid.
According to another aspect of the invention, reversed liquid bypass circulation comprises flow of fluid control gear, for being in transition or Molecular flow limit flow of fluid at liquid, and allows flow of fluid when fluid is in viscosity fluidised form.
Accompanying drawing explanation
From the detailed description to the preferred embodiments of the present invention made with reference to the accompanying drawings, these and other aspect of the present invention, Characteristics and advantages will become can clearly, wherein:
Fig. 1 is according to the schematic longitudinal section figure comprising the multistage pump of an example of reverse bypass circulation of the present invention;
Fig. 2 is according to the schematic longitudinal section figure with the pump head component of the multistage scroll-type pump of reverse bypass circulation of the present invention;
Fig. 3 A is the enlarged view of a part for the pump head component of the multistage scroll-type pump of Fig. 2;
Fig. 3 B is the enlarged view of another part of the pump head component of the multistage scroll-type pump of Fig. 2;
Fig. 4 A is the schematic diagram of the layout of reversed liquid bypass circulation according to two stage pump of the present invention;
Fig. 4 B is the schematic diagram of the layout of reversed liquid bypass circulation according to triplex of the present invention;
Fig. 4 C is the schematic diagram of the layout of reversed liquid bypass circulation according to another triplex of the present invention;
Fig. 5 A is according to the schematic diagram with a part for the multistage pump of the reversed liquid bypass circulation of another kind of version of the present invention;
Fig. 5 B is according to the schematic diagram with a part for the multistage pump of the reversed liquid bypass circulation of another kind of version of the present invention;
Fig. 5 C is according to the schematic diagram with a part for the multistage pump of the reversed liquid bypass circulation of another kind of version of the present invention;
Fig. 5 D is according to the schematic diagram with a part for the multistage pump of the reversed liquid bypass circulation of another kind of version of the present invention.
Embodiment
Hereinafter with reference to the accompanying drawings to the present invention design various embodiment and embodiment's example describe more fully.In the accompanying drawings, for clarity, the size of element and relative size may be exaggerated.Similarly, in order to clear and easy to understand, the shape of element may be exaggerated and/or be simplified.Further, run through the identical numeral of institute's drawings attached to be used to specify identical element with reference character.
In addition, the term of the concrete example or embodiment for describing the present invention's design used herein will be put and consider within a context.Such as, show to exist specific characteristic or process when term " comprises " or " comprising " is used in specification but do not get rid of and there is extra feature or process.Term " pump " can refer to the device of the pressure driving or promote or reduce liquid etc.The term " upstream stage " be combined with the compressing mechanism of pump will refer to any compression stage of pump, namely relative to the upstream compression stage that flow at least one other compression stage of pump of liquid by compressing mechanism.That is, if pump has three or more compression stage, so term " upstream stage " might not refer to the first order of compressing mechanism.Similarly, any compression stage in the downstream of at least one other grade that will refer to as pump of term " downstream stage ".Therefore, unless otherwise mentioned, do not mean that these grades are directly series connection when term " upstream " and " downstream " level are used together.
Referring now to Fig. 1, multistage pump 1 of the present invention can be applied and generally include shell 100 and the pump head component 200 be disposed in shell 100 and pump motor 300.Pump can also comprise the cooling fan 400 for cooling pump head component 200 and/or pump motor 300.In this example, shell 100 defines suction port 100A and relief opening 100B in its opposite end respectively, and cooling fan 400 is arranged in suction port 100A, to make cooling-air by shell and to go out from relief opening 100B.
Shell 100 can also comprise the cowling 110 covering pump head component 200 and pump motor 300 and the bottom 120 supporting pump head component 200 and pump motor 300.Cowling 110 can have one or more part and be detachably connected to bottom 120, thus pump head component 200 carries out safeguarding, repairing etc. to make cowling 110 to be removed from bottom 120 to enter.
Scroll vacuum pump 1 also has intake section and discharge section, and wherein, intake section has pump intake 140 and forms the low voltage side (as inlet side) of pump, and liquid is inhaled into pump in this low voltage side; Discharge section has pump discharge 150 and forms compressed side, and liquid by discharge at the pressure that the pressure of low voltage side is high than liquid from pump.Pump head component 200 also has the inlet opens (inletopening) 260 of the inlet side being positioned at pump, the compressing mechanism 270 of compressed liquid and discharge aperture (exhaustopening) 280.The entrance 140 of pump is connected to the compressing mechanism 270 of pump by inlet opens 260.The compressing mechanism 270 of pump is connected to pump discharge 150 by discharge aperture 280.
Compressing mechanism 270 has multiple compression stage, comprises relative at least two compression stages flowing to tandem arrangement of liquid along the flow path defined by pump.Each compression stage has intake and drawing-off mouth, and wherein liquid enters this level by intake and leaves this level by drawing-off mouth.In the example shown in fig. 1, pump 1 is the two stage pump with upstream compression stage 270a and downstream compression stage 270b.Flow path (as being with shown in the solid line of arrow) extends between pump intake 140 and upstream compression stage 270a, extend between the drawing-off mouth and the intake of downstream compression stage 270b of upstream compression stage 270a, and extend between the drawing-off mouth and pump discharge 150 of downstream compression stage 270b.
Pump 1 also has the reversed liquid bypass circulation 290 combined with pump head component 200.Reversed liquid bypass circulation 290 defines fluid passage 295, this fluid passage and flow path are separated, and the second place ' B ' place of the upstream of the intake of primary importance ' A ' between the drawing-off mouth and the intake of back to back downstream compression stage 270b of (upstream) compression stage 270a and this (upstream) compression stage 270a is connected to flow path.Reversed liquid bypass circulation 290 also has flow of fluid control gear 299.Reversed liquid bypass circulation 290 will be explained in more detail below.
But the example according to the pump head component 200 of multistage scroll-type pump of the present invention is described with reference to Fig. 2 first.
Pump head component 200 comprises framework 210, inner (first) fixed plate volute (scroll) 220A, orbital motion plate volute (orbiting plate scroll) 230, outside (second) fixed plate volute 220B, as the driven eccentric drive mechanism 240 of result that the rotation of motor 300 exports, tubular member 250, and fixed plate volute 220A and 220B be fixed to framework 210 and tubular member 250 be fixed to the fastening piece (not shown) of framework 210 and orbital motion plate volute 230.As shown in the figure, external stability plate volute 220B can be fixed to framework 210 by inner this medium of fixed plate volute 220A.
Inner fixed plate volute 220A comprises the first fixing scroll blade (scroll blade) 221 of pump and has first fixed plate 222 of outer (front) side and interior (afterwards) side.First fixing scroll blade 221 stretches out vertically (with the longitudinal axis of pump) at first direction from the outside of the first fixed plate 222.External stability plate volute 220B comprises the second fixing scroll blade 223 of pump and has second fixed plate 224 of outer (afterwards) side and interior (front) side.Second fixing scroll blade 223 stretches out vertically in the second direction relative with first direction from the inner side of the second fixed plate 224.
Orbital motion plate volute 230 to be axially inserted between inner fixed plate volute 220A and external stability plate volute 220B and to be coupled to eccentric drive mechanism 240, to be driven on the track of the longitudinal axis around pump by eccentric drive mechanism 240 at pump.Orbital motion plate volute 230 comprise the orbital motion plate 231 with outside and inner side, the first orbital motion scroll blade 232 stretched out in second direction vertically from the inner side of orbital motion plate 231 and from the outside of orbital motion plate 231 vertically at the second orbital motion scroll blade 233 that first direction stretches out.First orbital motion scroll blade 232 and the first fixing scroll blade 221 side by side, thus make the first fixing scroll blade 221 be nested with the first orbital motion scroll blade 232 in the radial direction of pump.Second orbital motion scroll blade 233 is arranged side by side in the radial direction of pump with the second fixing scroll blade 223 of pump, thus makes the second fixing scroll blade 223 be nested with the second orbital motion scroll blade 233.In these areas, fixing with orbital motion scroll blade 223,233 with 221,232 by nested with predetermined relative angular position with space, thus one or more little space (pocket) is limited between nested scroll blade by nested scroll blade.
Eccentric drive mechanism 240 comprises transmission shaft and bearing 246.In this example, transmission shaft has to be connected to motor 300 and the major component 242 rotated around the longitudinal axis of pump 100 by motor 300 and its center longitudinal axis depart from the crankshaft of the crank 243 of the longitudinal axis in radial direction.Bearing 246 can comprise organizes rolling member more.
In addition, in this example, the major component 242 of crankshaft is supported by framework 210 by one or more groups bearing 246, thus can rotate relative to framework 210.Orbital motion plate volute 230 is installed to crank 243 by one or more groups bearing 246 another.Therefore, orbital motion plate volute 230 is carried by crank 243, and with the longitudinal axis orbiting when main shaft 242 is rotated by motor 300 at pump, and orbital motion plate volute 230 is supported by crank 243, thus can rotate around the center longitudinal axis of crank 243.
Along with orbital motion scroll blade 232,233 respectively relative to fixing scroll blade 221,223 moved by the volume organizing the little space that nested scroll blade 221,232 and 223,233 limits more and change.The motion of orbital motion scroll blade 232,233 also makes to move in pump head component 200 in the one or more little space limited between nested scroll blade 221,232 and 223,233 of organizing more, thus little space is placed with pump intake (by inlet opens 260) and the open phase earthing of pump discharge (by discharge aperture 280) selectively.Therefore, as shown by the arrow, liquid is drawn along the flow path extending through pump head component 200.
In this example, at least two compression stages that pumping occurs are had.Such as, the downstream compression stage (the level 270b corresponding in Fig. 1) of pump can be defined between orbital motion plate volute 230 and inner fixed plate volute 220A.The upstream compression stage (the compression stage 270a corresponding in Fig. 1) of pump can be defined between orbital motion plate volute 230 and external stability plate volute 220B.
Alternatively, same pump can be configured to triplex.Such as, upstream (or first) compression stage of pump and centre (or second) compression stage can be defined between orbital motion plate volute 230 and external stability plate volute 220B.In this respect, with reference to above-mentioned U. S. Patent 6,884,047, can this patent illustrate and provide two levels between track running plate volute and fixed plate volute.In a first stage, liquid is pumped by the fixing action with the radially outer of orbital motion scroll blade.In the second level, liquid is pumped by the fixing action with the inner radial of orbital motion scroll blade.Inner radial that is fixing and orbital motion scroll blade has the height of the radially outer being less than fixing and orbital motion scroll blade.Therefore, the first order has the axial depth being greater than the second level.
On the other hand, downstream (or 3rd) compression stage of pump can be defined between orbital motion plate volute 230 and inner fixed plate volute 220A.Therefore, in downstream compression stage, liquid is pumped by the action of the fixing scroll blade 221 of inner fixed plate volute 220A and the first orbital motion scroll blade 232 of orbital motion plate volute 230.
Still with reference to Fig. 2, tubular member 250 has the first end and the second end, and wherein this tubular member is fixed to orbital motion plate volute 230 at the first end, and is fixed to framework 210 at the second end.Tubular member 250 also extends around the part and bearing 246 of the crankshaft 243 of eccentric drive mechanism 240.Like this, tubular member 250 can also stuffing box bearing 246 and bearing surface.Therefore, the oiling agent that can prevent bearing 246 from using and/or the particulate matter generated by bearing surface enter flow path.Tubular member 250 is enough radial when allowing the second end when it to be still fixed on framework 210 flexibly, and its first end can follow orbital motion plate volute 230 moves.
In the example shown in the series of figures, tubular member 250 is metal bellowss, its torsional stiffness prevents its first end from rotating significantly around the center longitudinal axis of bellows, namely prevents its first end from significantly rotating at its circumferencial direction when the second end of bellows is still fixed on framework 210.Therefore, metal bellows 250 can, in the operation period of pump, provide angle synchronous at fixing scroll blade 221 with between 223 and first and second orbital motion scroll blade 232 and 233 respectively.
In addition, although not shown in Figure 2 for the sake of simplicity, but vortex pump is the dry vortex pump comprising end seal (tip seal), wherein each end seal is sealed in the groove that the length along the end (axial end) of a corresponding scroll blade extends.
Fig. 3 A shows end seal 220AS, 230S of being associated with the first fixed plate volute 220A and orbital motion plate volute 230 respectively.Fig. 3 B shows end seal 220BS, 230S of being associated with the second fixed plate volute 220B and orbital motion plate volute 230 respectively.Each end seal in this example be inserted in the first fixing and orbital motion plate volute 220A, 230 one of them the end of scroll blade 221,232 and the first fixing and orbital motion plate volute 220A, 230 in plastic member between another plate 231,222.
Multistage scroll-type pump also has the reversed liquid bypass circulation of the reversed liquid bypass circulation 290 shown in corresponding diagram 1.Reversed liquid bypass circulation plays a part as follows.Here with reference to the pump 1 in Fig. 1.
Usually, when the pressure at the pressure difference (being called interstage pressure) of the liquid between compression stage and the intake place of the first order exceedes predetermined value, reverse bypass fluid loop 290 makes the liquid-circulating along the diverted flow of the flow path directly connecting the first and second compression stages turn back to the upstream of the intake of the first compression stage.Such as, when shown in Fig. 1 two stage pump 1, when interstage pressure exceeds prearranging quatity (such as relative to inlet pressure, high 1-2 pound/square inch) time, reverse bypass fluid loop 290 will turn back to the upstream of the intake of the first compression stage 270a along the direct liquid-circulating connecting the diverted flow of the flow path of first and second compression stage 270a, 270b, and then turns back to the entrance 140 of pump.
For this reason, flow of fluid control gear 299 can comprise valve, the safety check of such as loading spring, and when interstage pressure exceeds predetermined value than inlet pressure, the cracking pressure of this safety check is set to open.In the example of the interstage pressure provided above than inlet pressure height 1-2 pound/square inch, the cracking pressure of safety check can be 1-1.5 pound/square inch.The valve of other type, such as gas charging valve or solenoid-operated valve can substitute and be used.In these cases, reversed liquid bypass circulation can also comprise and is one or morely connected to fluid passage 295 and is operably connected to the pressure transducer of valve, to open valve when predetermined pressure or pressure difference being detected in passage 295.
This provide following advantage.Maximum consumption of power in first and second grades of 270a, 270b is all reversed the operation constraint in Liquid refrigerant by-pass loop 290.Maximum consumption of power in constraint first order 270a and second level 270b, causes driving moment significantly to reduce, pump 1 is started, and protect the adverse effect that bearing and motor 300 are transshipped.
Secondly, the end seal of the unloaded spring as shown in Fig. 2, Fig. 3 A and 3B and as described in reference Fig. 2, Fig. 3 A and 3B must keep " being reinforced ", mean that it must keep engaging to provide sufficient sealing with relative plate, such as, even if end seal is through the wearing and tearing of some during use.If second and the end seal of any extra downstream compression stage do not have " being reinforced ", the larger pressure difference through the first order so combined with relatively large first order discharge capacity may make motor overload.These other parts that can stop pump startup conversely or damage such as bearing and so in pump.
In order to strengthen each end seal, usually require that the pressure difference through end seal impels end seal to compress the relative plate will sealed needed for providing.But in order to generate the necessary pressure of " reinforcement " end seal, first end seal must move forward to create sufficient sealing relative to relative plate.Therefore, when pump startup, end seal is not likely correctly strengthened, particularly when pump is equipped with the forward direction Liquid refrigerant by-pass loop stoping the space of pressure between first and second grades to produce (otherwise it will be used for strengthening end seal).
When there is certain interstage pressure difference between the intake and the intake of back to back downstream compression stage of upstream compression stage, by the upstream making liquid-circulating turn back to the intake of upstream compression stage, reversed liquid bypass circulation 290 of the present invention contributes to guaranteeing that the end seal of back to back downstream compression stage and any extra downstream compression stage is by " reinforcement ".
Fig. 4 A, 4B and 4C show the different layouts of reversed liquid bypass circulation 290.Any one layout in these layouts can be applied to the multistage scroll-type pump described shown in Fig. 2 and with reference to Fig. 2, also can be applied to the multistage displacement pump of other type any.
Fig. 4 A shows two stage pump, and wherein compressing mechanism is made up of the first (upstream) compression stage and second (downstream) compression stage.At this, the interstage pressure difference that reversed liquid bypass circulation 290 controls is the pressure difference between the intake of the first order and the intake of the second level.
Fig. 4 B shows triplex, and wherein first, second, third compression stage is by the continuous-flow paths in series connection extending to pump discharge from pump intake of pump.In this example, second compression stage is upstream compression stage, 3rd compression stage is back to back downstream compression stage, and reversed liquid bypass circulation makes fluid circulate turns back to the upstream position B of the intake of the first compression stage, and then turns back to the upstream of intake of the second compression stage.At this, the interstage pressure difference that reversed liquid bypass circulation 290 controls is the pressure difference between the drawing-off mouth of the second level and the intake of the first order.That is, upstream compression stage is this example illustrated not necessarily along the first compression stage of flow path.
Fig. 4 C shows triplex, wherein first, second, third compression stage arranged in parallel.In this case, the continuous-flow path of pump directly extends to the second compression stage from pump intake, directly extends to the 3rd compression stage and directly extend to pump discharge from the 3rd compression stage from the second compression stage.In this example, the second compression stage is upstream compression stage, and the 3rd compression stage is back to back downstream compression stage, and reversed liquid bypass circulation makes fluid circulation turn back to the upstream position B of the intake of the second compression stage.At this, the interstage pressure difference that reversed liquid bypass circulation 290 controls is the pressure difference between the drawing-off mouth of the second level and intake.
Certainly, these layouts can expand to the multistage pump being applied to and having more than three compression stages.
In addition, although reversed liquid bypass circulation 290 is described to the fluxus formae control gear of the valve of the safety check with such as loading spring and so on above, Fig. 5 A-5D shows the alternative form of flow control apparatus.
Fig. 5 A shows the reversed liquid bypass circulation 290 of the capillary tube 299a comprised as flow control apparatus.
Fig. 5 B shows the reversed liquid bypass circulation 290 comprising the hole 299b coaxially arranged with fluid passage 295.
Fig. 5 C shows the reversed liquid bypass circulation 290 comprising flexible tube, and wherein, when the low certain value of the pressure outside the pressure ratio flexible tube in flexible tube, flexible tube caves in.When internal pressure drops to lower than predetermined value, barometric pressure or other reference pressure provide strength that flexible tube is caved in.
Fig. 5 D shows for being in transition or Molecular flow limit flow of fluid at liquid, and allows the example of the flow of fluid control gear of flow of fluid when liquid is in viscosity fluidised form.In this example, reversed liquid bypass circulation 290 comprises labyrinth sealing 299d.But other flow of fluid control gear can be used to the flowing limiting transition or molecular state, allows the flowing of viscosity state simultaneously.
Finally, the present invention design embodiment and example in above-detailed.But the present invention's design can embody in many different forms and should not be understood to be confined to above-described embodiment.Certainly, describe these embodiments to make the disclosure thorough and complete, and given full expression to design of the present invention to those skilled in the art.Therefore, the true spirit of the present invention's design and scope are defined by the following claims not by the restriction of above-described embodiment and example.
Claims (10)
1. a multistage pump (1), comprising:
Entrance (140) part, this intake section has pump intake (140) and forms the low voltage side of pump (1), and wherein, liquid is inhaled into described pump (1) in described low voltage side;
Discharge section, this discharge section has pump discharge (150) and forms compressed side, wherein, liquid in described compressed side by discharge from described pump (1) at the pressure that the pressure of described low voltage side is high than liquid; And
Pump (1) head, this pump head has inlet opens (260) that described pump intake (140) extends to, lead to described in pump (150) discharge aperture (280), relative to liquid by least two compression stages (270a) flowing to tandem arrangement of described pump (1) and Liquid refrigerant by-pass loop, and
Wherein, each compression stage in described compression stage (270a) has introducing port and export mouth, and wherein liquid enters this level (270b) by this introducing port and leaves this level (270b) by this export mouth,
Extend between the export mouth of the described downstream compression stage between the introducing port of the downstream compression stage in the export mouth of the described upstream compression stage between the upstream compression stage of the flow path that liquid flows to described pump discharge (150) process from described pump intake (140) described pump (1) in described pump intake (140) and described compression stage (270a), in described compression stage (270a) and described compression stage (270a) and in described compression stage (270a) and described pump discharge (150), and
Described Liquid refrigerant by-pass loop defines fluid passage (295), this fluid passage (295) and described flow path are separated, and the second position of the upstream of the introducing port of the export mouth of a compression stage in described compression stage (270a) and the primary importance between the introducing port of the back to back compression stage (270b) in a described compression stage downstream and a described compression stage (270a) is connected to described flow path.
2. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises the valve coaxially arranged with described fluid passage (295).
3. pump (1) as claimed in claim 2, wherein, described valve is the safety check of loading spring, wherein, when by described fluid passage (295), pressure difference between described second and primary importance higher than predetermined value time, this safety check is opened.
4. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises the labyrinth sealing (299d) providing flow restriction between the first and second positions.
5. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises the capillary tube (299a) providing flow restriction between the first and second positions.
6. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises the hole (299b) be disposed in described fluid passage (295) providing flow restriction between the first and second positions.
7. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises flexible tube, and the pressure difference of this flexible tube therein and between outside is caved in lower than during predetermined value.
8. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises flow of fluid control gear, for when by described fluid passage (295), pressure difference between described second and primary importance lower than predetermined value, restriction or stop liquid flow through described fluid passage (295).
9. pump (1) as claimed in claim 1, wherein, described Liquid refrigerant by-pass loop comprises flow of fluid control gear, for preventing liquid from flowing to the described second place from described primary importance when liquid is in transition or Molecular flow between the export mouth of a described compression stage (270a) and the introducing port of the described back to back compression stage (270a) in a described compression stage downstream, and allow liquid to flow to the described second place from described primary importance when liquid is in viscosity fluidised form between the export mouth of a described compression stage (270a) and the introducing port of the described back to back compression stage (270a) in a described compression stage downstream.
10. pump (1) as claimed in claim 1, wherein, a described compression stage (270a) be along described flow path with respect to the flow direction of described pump (1) closest to the compression stage of entrance (140) position of described pump (1).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US14/026,550 US20150078927A1 (en) | 2013-09-13 | 2013-09-13 | Multi-Stage Pump Having Reverse Bypass Circuit |
| US14/026,550 | 2013-09-13 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104514719A true CN104514719A (en) | 2015-04-15 |
Family
ID=51796500
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410461237.XA Pending CN104514719A (en) | 2013-09-13 | 2014-09-11 | Multi-Stage Pump Having Reverse Bypass Circuit |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20150078927A1 (en) |
| CN (1) | CN104514719A (en) |
| GB (1) | GB2520140A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107044417A (en) * | 2017-04-18 | 2017-08-15 | 王旭明 | A kind of compressed air cycle power device |
| CN107084134A (en) * | 2017-06-26 | 2017-08-22 | 湖北维斯曼新能源科技有限公司 | New two stages of compression scroll type air compressor |
| CN113431781A (en) * | 2021-08-05 | 2021-09-24 | 临海市谭氏真空设备有限公司 | Dry type vortex vacuum pump |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2572958C (en) * | 2018-04-16 | 2021-06-23 | Edwards Ltd | A multi-stage vacuum pump and a method of differentially pumping multiple vacuum chambers |
| US12015320B2 (en) | 2020-05-07 | 2024-06-18 | Agilent Technologies, Inc. | Air gap magnetic coupling with counterbalanced force |
| GB2600716B (en) * | 2020-11-05 | 2023-05-03 | Edwards Ltd | Scroll pump |
| GB2606224B (en) * | 2021-04-30 | 2024-01-31 | Edwards Ltd | Stator for a vacuum pump |
| EP4420220A1 (en) | 2021-10-22 | 2024-08-28 | Agilent Technologies, Inc. | Air gap magnetic coupling with thermal isolation |
| US12006937B2 (en) | 2022-06-07 | 2024-06-11 | Agilent Technologies, Inc. | Fluid pump with integrated cowling and discharge muffler |
| US11686311B1 (en) | 2022-06-07 | 2023-06-27 | Agilent Technologies, Inc | Drive shaft connector with counterweight and blades for cooling pump motor |
| US20240200558A1 (en) | 2022-12-15 | 2024-06-20 | Agilent Technologies, Inc. | Fluid pump and enclosure providing stator holder and cooling for motor and electronics |
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| CN113431781A (en) * | 2021-08-05 | 2021-09-24 | 临海市谭氏真空设备有限公司 | Dry type vortex vacuum pump |
Also Published As
| Publication number | Publication date |
|---|---|
| US20150078927A1 (en) | 2015-03-19 |
| GB201416031D0 (en) | 2014-10-22 |
| GB2520140A (en) | 2015-05-13 |
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