CN104204522B - Pump installation - Google Patents
Pump installation Download PDFInfo
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- CN104204522B CN104204522B CN201380017010.XA CN201380017010A CN104204522B CN 104204522 B CN104204522 B CN 104204522B CN 201380017010 A CN201380017010 A CN 201380017010A CN 104204522 B CN104204522 B CN 104204522B
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- piston
- pump
- pumping section
- drive shaft
- pump chamber
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- 238000009434 installation Methods 0.000 title claims abstract description 36
- 238000005086 pumping Methods 0.000 claims abstract description 70
- 230000001360 synchronised effect Effects 0.000 claims description 6
- 230000008859 change Effects 0.000 description 9
- 230000000694 effects Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 3
- 230000000740 bleeding effect Effects 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
Classifications
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
-
- 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
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
- F04B2201/0201—Position of the piston
- F04B2201/02011—Angular position of a piston rotating around its own axis
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/08—Cylinder or housing parameters
- F04B2201/0802—Vibration
-
- 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
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0201—Current
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The present invention provides a kind of pump installation that can reduce power consumption further.Pump installation (1) involved by an embodiment of the invention has: drive motor M, there is the 1st pump chamber and the 1st piston (21v), the 1st pumping section (11) for vacuum exhaust, and there is the 2nd pump chamber and the 2nd piston (21c), the 2nd pumping section for pressurization.2nd piston (21c) is ahead of the 1st piston (21v) with the poor Φ of rotatable phase being less than 80 ° more than 0 °.
Description
Technical field
The present invention relates to a kind of pump installation with vavuum pump and force (forcing) pump.
Background technology
People are known as the oscillating plunger pump of a kind of vavuum pump, and it is to be moved back and forth in cylinder by piston, carries out the air-breathing of pump indoor gas and the reciprocating pump of exhaust alternately, and it is widely used as such as vavuum pump and force (forcing) pump.
On the other hand, having and simultaneously driven by common motor, the compound pump installation for vacuum exhaust with for two pistons of pressurization is also known by people.The known driving method of this kind of pump installation is, makes the method that this two pistons move reciprocatingly with mutually opposite phase place, and makes the method (such as, with reference to following patent document 1) that these two pistons move reciprocatingly with same-phase.
The former method, i.e. make the rotatable phase of two-piston stagger 180 °, the driving method moved reciprocatingly, there is the dynamic equilibrium preferably keeping each piston, the advantage reducing pump installation body vibration.On the other hand, the method for the latter, i.e. the driving method simultaneously making two-piston move to top dead centre or lower dead center, can reduce the load change in driving source, it is achieved the steady running of pump installation.
Prior art literature
Patent document 1: flat No. 7-310651 of Japanese invention Patent Publication No
Summary of the invention
In recent years, having the requirement of the power consumption reducing pump installation, above-mentioned compound pump installation is with greater need for reducing power consumption.
In view of the above circumstances, it is an object of the invention to, it is provided that a kind of pump installation being capable of reducing power consumption further.
For reaching above-mentioned purpose, the pump installation involved by a technical scheme of the present invention, have and drive motor, the 1st pumping section for vacuum exhaust, the 2nd pumping section for pressurization.
Above-mentioned driving motor has the 1st drive shaft and the 2nd drive shaft.Above-mentioned driving motor enables above-mentioned 1st drive shaft and above-mentioned 2nd drive shaft around the 1st axle synchronous rotary.
Above-mentioned 1st pumping section has: the 1st piston, and it is rotarily driven by above-mentioned 1st drive shaft, moves reciprocatingly along the 2nd direction of principal axis vertical with above-mentioned 1st axle；1st pump chamber, its internal pressure changes corresponding to the reciprocating motion of above-mentioned 1st piston.
Above-mentioned 2nd pumping section has: the 2nd piston, and it is rotarily driven by above-mentioned 2nd drive shaft, moves reciprocatingly along above-mentioned 2nd direction of principal axis；2nd pump chamber, its internal pressure changes corresponding to the reciprocating motion of above-mentioned 2nd piston.Above-mentioned 2nd piston is ahead of above-mentioned 1st piston so that the rotatable phase being less than 80 ° more than 0 ° is poor.
Accompanying drawing explanation
Fig. 1 is the stereogram when the front unilateral observation of the pump installation involved by an embodiment of the invention.
Fig. 2 is the stereogram when the reverse side of said pump device is observed.
Fig. 3 is the right view of said pump device.
Fig. 4 is the left view of said pump device.
Fig. 5 is the profilograph of a part of structure representing the vacuum pumping section of said pump device and drive division.
Fig. 6 is the eccentric shaft schematic diagram with the relation of the eccentric shaft of pressurization pumping section side of the vacuum pumping section side of explanation said pump device, and (A) is front view, side view when (B) is to see from vacuum pumping section side.
Fig. 7 is for driving pump installation, making the pump chamber internal pressure of vacuum zone and the pump chamber internal pressure of pressurized segment is experimental result during same-phase, (A) the pump chamber internal pressure of vacuum zone and piston position are represented over time, (B) representing the pump chamber internal pressure of pressurized segment and piston position over time, (C) represents the synthetic waveform of the pressure waveform of the pressure waveform of the pump chamber of vacuum zone and the pump chamber of pressurized segment.
Fig. 8 is for driving pump installation, making the pump chamber internal pressure of vacuum zone and the pump chamber internal pressure of pressurized segment is experimental result during antiphase, (A) the pump chamber internal pressure of vacuum zone and piston position are represented over time, (B) representing the pump chamber internal pressure of pressurized segment and piston position over time, (C) represents that synthetic waveform Fig. 9 of the pressure waveform of the pressure waveform of the pump chamber of vacuum zone and the pump chamber of pressurized segment is an experimental result of the effect that said pump device is described.
Fig. 9 is the experimental result of the relation representing power consumption with motor poor relative to the rotatable phase of the piston of the pressurized segment of the piston of vacuum zone.
Symbol description
1: pump installation；
11: vacuum pumping section；
12: pressurization pumping section；
21,21v, 21c: piston；
26: pump chamber；
51,52: counterweight；
131: drive shaft；
232,232v, 232c: eccentric shaft；
M: motor
Detailed description of the invention
The internal pressure of the pump chamber of oscillating plunger pump with piston reciprocation period change.Such as, piston is by lower dead center when top dead centre moves, and because of the volume reducing of pump chamber, internal pressure is stepped up, and piston is from top dead centre when lower dead center is moved, and because the volume of pump chamber increases, internal pressure gradually reduces.Now, in the case of vavuum pump, change in being pressed in atmospheric pressure pressure below scope (negative pressure) in pump chamber, in the case of force (forcing) pump, change in being pressed in the pressure limit (malleation) of more than atmospheric pressure in pump chamber.
But, according to the experiment of inventor, inventor confirms the following fact, even if making the piston for vavuum pump described above and the piston for force (forcing) pump move reciprocatingly with same-phase, the internal pressure of two pump chambers also and asynchronous is changed, and the pressure change between two pump chambers can produce phase difference.It addition, further acknowledge that, even if controlling the rotatable phase of two-piston, making the internal pressure of two pump chambers of vavuum pump and force (forcing) pump be changed to same-phase, the load of motor can not minimize value.
Then, for realizing reducing further the power consumption of pump installation, the present invention uses following manner such as to constitute pump installation.
That is, the pump installation involved by an embodiment of the invention has driving motor, the 1st pumping section for vacuum exhaust, the 2nd pumping section for pressurization.
Above-mentioned driving motor has the 1st drive shaft and the 2nd drive shaft.Above-mentioned driving motor enables above-mentioned 1st drive shaft and above-mentioned 2nd drive shaft around the 1st axle synchronous rotary.
Above-mentioned 1st pumping section has: the 1st piston, and it is rotarily driven by above-mentioned 1st drive shaft, moves reciprocatingly along the 2nd direction of principal axis vertical with above-mentioned 1st axle；1st pump chamber, its internal pressure changes corresponding to the reciprocating motion of above-mentioned 1st piston.
Above-mentioned 2nd pumping section has: the 2nd piston, and it is rotarily driven by above-mentioned 2nd drive shaft, moves reciprocatingly along above-mentioned 2nd direction of principal axis；2nd pump chamber, its internal pressure changes corresponding to the reciprocating motion of above-mentioned 2nd piston.Above-mentioned 2nd piston is ahead of above-mentioned 1st piston so that the rotatable phase being less than 80 ° more than 0 ° is poor.
Experiment according to inventor, although in the 1st pumping section of vacuum exhaust, the top dead centre of piston and the pressure peak position of pump chamber are basically identical, but in the 2nd pumping section for pressurization, the top dead centre of piston and the pressure peak position of pump chamber are not consistent.Particularly it was determined that in the 2nd pumping section, before piston arrives top dead centre, pump chamber reaches pressure peak.
Above-mentioned rotatable phase difference can take the circumstances into consideration to set in the range of more than 0 ° less than 80 °, such as, the scope of 40 ° ± 30 °, can obtain the effect that stable power consumption reduces, the scope of 40 ° ± 15 °, can obtain the effect that power consumption reduces further.Poor by so optimizing rotatable phase, pump installation can be made stably to operate with low power consumption.
Below, referring to the drawings, embodiments of the present invention are described.
Fig. 1～Fig. 4 is the outside drawing representing the pump installation involved by an embodiment of the invention, and stereogram when Fig. 1 is to see from side, front, Fig. 2 is the stereogram when reverse side is seen, and Fig. 3 is right view, and Fig. 4 is left view.
The pump installation 1 of present embodiment has the vacuum pumping section 11 (the 1st pumping section) as vacuum zone, as the pressurization pumping section 12 (the 2nd pumping section) of pressurized segment and for driving vacuum pumping section 11 and the drive division 13 of pressurization pumping section 12.Pump installation 1 such as can use as the vacuum and the force (forcing) pump that use in the booster fan of the gas used in the fuel cell system, medical treatment analysis meter.
Vacuum pumping section 11 and pressurization pumping section 12 typically have identical structure, are oscillating plunger pump in the present embodiment.
Pump installation 1 has pump case 100, it the 3rd hood 103 including constituting a part for the 1st hood 101 of a part for vacuum pumping section 11, the 2nd hood 102 constituting a part for pressurization pumping section 12 and composition drive division 13.
Fig. 5 is the profilograph of a part of structure representing vacuum pumping section 11 and drive division 13.In Fig. 5 X-axis, Y-axis and Z axis represent respectively orthogonal 3 axially.It addition, because pressurization pumping section 12 has identical structure with vacuum pumping section 11, therefore vacuum pumping section 11 is mainly described at this.
Vacuum pumping section 11 has the 1st hood 101, piston 21, connecting rod 22 (linkage component) and eccentric part 23.
1st hood 101 has pump case main body 110, cylinder 111, pump head 112 and pump cover 113.Pump case main body 110, cylinder 111, pump head 112 and pump cover 113 form as one mechanism in the way of overlapping each other in the Z-axis direction.
Pump case main body 110 is connected with the 3rd hood 103 receiving dress motor M, and has the through hole 110h run through by connecting rod 22.Pump case main body 110 has: fixed part 110a, and it is fixed with can the drive shaft 131 of supporting motor M be allowed to rotatable bearing 32 (the 2nd bearing)；Cylinder portion 110b, it receives the coil 132 of dress motor M.Drive shaft 131 and Y direction (the 1st is axial) configured in parallel, and made it rotate around Y-axis by motor M driving.Bearing 32 is configured between the main body of motor M and eccentric part 23.
Cylinder 111 is configured between pump case main body 110 and pump head 112, receives dress piston 21 therein, and makes this piston 21 can along Z-direction slidably.Pump head 112 is configured between cylinder 111 and pump cover 113, and has inlet valve 112a and air bleeding valve 112b.Pump cover 113 is configured on pump head 112, has inside it: induction chamber 113a, and it is connected with air entry 114a；Exhaust chamber 113b, it is connected with exhaust outlet 114b.As shown in Figure 1 and Figure 2, air entry 114a and exhaust outlet 114b is separately positioned on each pumping section 11,12 side in opposite directions.
Piston 21, in discoideus, is fixed on the 1st end 221 of connecting rod 22 by screw component 25.Piston 21 forms pump chamber 26 between this piston 21 and pump head 112.Piston 21 moves back and forth, so that the internal pressure of pump chamber 26 changes along the direction parallel with the Z-direction (the 2nd is axial) within cylinder 111.And, piston 21, by inlet valve 112a and air bleeding valve 112b, the mutual gas sucked and discharge in pump chamber 26, plays the effect of predetermined pump.
Connecting rod 22 makes piston 21 and eccentric part 23 interconnect.Connecting rod 22 has: the 1st end 221, and it is connected with piston 21；2nd end 222, it is connected with eccentric part 23.1st end 221 is formed as the circle roughly the same with piston 21 diameter.Between these piston the 21 and the 1st ends 221, discoideus seal member 24 is installed.The circumference of seal member 24 is can be folded into connecting rod 22 side in the way of the inner peripheral surface of sliding contact cylinder 111.
It addition, in pressurization pumping section 12, in contrast with the previous embodiment, the circumference of described seal member is folded into pump chamber side.
The embedded hole 222a of the eccentric shaft 232 of chimeric eccentric part 23 it is formed with on 2nd end 222 of connecting rod 22.Being provided with bearing 31 in embedded hole 222a, it can support eccentric shaft 232 so that it is rotates freely.
Eccentric part 23 makes the drive shaft 131 of the 3rd interior motor M receiving dress of hood 103 and connecting rod 22 interconnect.Eccentric part 23 has roughly cylindrical base block 230.The face of the motor M side of base block 230 is connected with drive shaft 131, and the face of connecting rod 22 side is formed with eccentric shaft 232.The axle center of eccentric shaft 232 is eccentric relative to drive shaft 131, thus the rotation along with drive shaft 131 is partial to.Drive shaft 131 is threadingly attached to the fixing screw 41 of the lateral circle surface of base block 230, is connected with base block 230.
Eccentric part 23 is provided with counterweight 51.Counterweight 51 is threadingly attached to the fixing screw 42 of the lateral circle surface of base block 230, is fixed on the side perimembranous of eccentric part 23.Counterweight 51 rotates together with eccentric part 23, has the effect eliminating the vibration that connecting rod 22 produced when eccentric shaft 232 rotates along with the rotation of drive shaft 131.Counterweight 51 is configured at the eccentric shaft 232 rightabout position relative to the eccentric direction of drive shaft 131.
In vacuum pumping section 11 as constituted above, motor M drives eccentric part 23 to rotate around drive shaft 131, and thus eccentric shaft 232 is along having the circumference of itself and the radius corresponding relative to the offset of drive shaft 131, revolves round the sun around drive shaft 131.The rotation of drive shaft 131 is converted to the reciprocating motion of the piston 21 within cylinder 111 by the connecting rod 22 being connected to eccentric shaft 232.I.e., in Figure 5, piston 21, while the inside of cylinder 111 swings along X-direction, also moves back and forth along Z-direction.So, by carrying out air-breathing and the exhaust of pump chamber 26 alternately, predetermined vacuum exhaust effect can be produced by vacuum pumping section 11.
On the other hand, pressurization pumping section 12 is identical with the structure of vacuum pumping section 11, and drive shaft 131 is also prominent to the side of pressurization pumping section 12, is connected with the eccentric shaft (omitting diagram) of pressurization pumping section 12.So, pressurization pumping section 12 and vacuum pumping section 11, driven by same motor M simultaneously, produced predetermined pressurization (boosting) effect.
Here, vacuum pumping section 11 and pressurization pumping section 12 are driven in mutually different phase place.I.e., in the present embodiment, the piston 21c (the 2nd piston) of pressurization pumping section 12 is with the poor piston 21v (the 1st piston) being ahead of vacuum pumping section 11 of rotatable phase being less than 80 ° more than 0 °.
Poor for making above-mentioned each piston have above-mentioned rotatable phase, in the present embodiment, the position making the eccentric shaft 232 of each pump 11,12 is different.According to present embodiment, only eccentric part 23 can be fixed in drive shaft 131 by the connection of fixing screw 41, therefore can be easily adjusted the respective relative position of eccentric shaft 232 in two pumps 11,12.
It addition, the position of counterweight because being fixed on eccentric part 23 is relevant to the eccentric direction of eccentric shaft 232, therefore the outside of self-pumping apparatus 1 also is able to easily verify that the rotatable phase of two-piston 21 is poor.I.e., as shown in Figure 1 to 4, counterweight 51 relative to vacuum pumping section 11, the counterweight 52 of pressurization pumping section 12 is fixed on, position along direction of rotation (clockwise direction centered by Y-axis in Fig. 3, counter clockwise direction centered by Y-axis in Fig. 4) the advanced above-mentioned predetermined rotatable phase poor (more than 0 ° less than 80 °) of drive shaft 131.
Fig. 6 (A), (B) are the eccentric shaft 232v schematic diagram with the relation of the eccentric shaft 232c of pressurization pumping section 12 side of explanation vacuum pumping section 11 side, (A) it is front view, side view when (B) is to see from vacuum pumping section 11 side.As shown in Fig. 6 (B), the eccentric shaft 232c of force (forcing) pump side is arranged at, than the position of the most predetermined for the 232v rotatable phase Φ of vacuum pumping section 11 side.Therefore, the piston 21c of the piston 21v of vacuum pumping section 11 side and pressurization pumping section 12 side is driven in the way of mutually having phase difference Φ, and piston 21c early arrives top dead centre and is equivalent to the time of phase difference Φ compared with piston 21v.
Rotatable phase difference Φ is set in more than 0 ° less than in the suitable scope of 80 °.Therefore, compared with the situation driving two-piston 21v, 21c in same-phase (Φ=0), it is possible to reduce the power consumption of motor M.It addition, by setting Φ=40 ° ± 15 °, can stably maintain the operation of above-mentioned motor M low power consumption.
Fig. 7 (A) is to represent the experimental result that the pump chamber internal pressure of vavuum pump and piston position produce change in time, and Fig. 7 (B) be the experimental result that the pump chamber internal pressure of expression force (forcing) pump and piston position produce change in time.In figure, solid line is experimental result during 50Hz operating, and dotted line is experimental result during 60Hz operating.
It addition, the lift of the pump installation used in Shi Yan, it is 40 [kPa (absolute pressures)] in vacuum zone (vavuum pump), is 220 [kPaG (gauge pressures)] in pressurized segment (force (forcing) pump).The internal pressure of pump chamber obtains by sealing the inner tube mensuration inserting pump chamber.Piston position uses the output of the accelerometer being installed on connecting rod bottom.The cylinder bore of the pump of each section is Φ 37mm, and the offset of eccentric shaft is 3.3mm, and the rotation number of motor is about 1400rpm/1700rpm (50Hz/60Hz).The condition of the experimental result represented by Fig. 8, Fig. 9 is the most identical.
At vacuum zone, pump chamber internal pressure changes (Fig. 7 (A)), on the other hand, in pressurized segment with piston position so that same-phase is Tong Bu, pump chamber internal pressure and piston position asynchronous change, produce therebetween phase difference (Fig. 7 (B)).More specifically, before the piston of pressurized segment arrives top dead centre, pressure peak occurs in pump chamber.
Be may determine that by above experimental result: even if driving vacuum zone and the respective piston of pressurized segment in the most synchronous mode mutually, vacuum zone and pressurized segment respective pump chamber internal pressure the most do not change with same-phase, and the pump chamber of pressurized segment reaches Pressure maximum value earlier compared with the pump chamber of vacuum zone.
Additionally, be may determine that by experiment: constituted pump installation by the form being changed to antiphase with the internal pressure of two pump chambers of the 1st pumping section and the 2nd pumping section, compared with in the case of the piston driving each pumping section in the most synchronous mode mutually, it is possible to reduce the power consumption driving motor.
Here, internal pressure refers to typically for antiphase over time, the pressure waveform in two pump chambers has the phase difference of 180 °.But it is also not limited to this, as long as having the phase relation can being construed on essential meaning as antiphase.Here, the antiphase on essential meaning can be defined as, such as, relatively two-piston, the phase relation of amount capable of reducing power consumption are driven in same-phase.
Predetermined phase difference is set between the piston and the piston of vacuum zone of pressurized segment, so that the pressure waveform of the pump chamber internal pressure of the pressure waveform of the pump chamber internal pressure of vacuum zone and pressurized segment is same-phase, in the case of adopting and constituting pump installation in this way, the rotatable phase difference of the piston of pressurized segment and the piston of vacuum zone is set greater than 180 ° less than 260 ° the phase place of piston of vacuum zone (phase places of the piston of pressurized segment be ahead of).Fig. 7 (A)～(C) represent that this rotatable phase difference is experimental result when 220 °.Fig. 7 (C) represents the synthetic waveform of the pressure waveform of the pressure waveform of the pump chamber of vacuum zone and the pump chamber of pressurized segment.
On the other hand, predetermined phase difference is set between the piston and the piston of vacuum zone of pressurized segment, so that the pressure waveform of the pump chamber internal pressure of the pressure waveform of the pump chamber internal pressure of vacuum zone and pressurized segment is antiphase, in the case of adopting and constituting pump installation in this way, the piston of pressurized segment and the piston of vacuum zone rotatable phase difference be set greater than 0 ° less than 80 ° the phase place of piston of vacuum zone (phase places of the piston of pressurized segment be ahead of).Fig. 8 (A)～(C) represent that this rotatable phase difference is experimental result when 40 °.Over time, the pump chamber internal pressure of Fig. 8 (B) expression pressurized segment and piston position are over time for the pump chamber internal pressure of Fig. 8 (A) expression vacuum zone and piston position.Additionally, Fig. 8 (C) represents the synthetic waveform of the pressure waveform of the pressure waveform of the pump chamber of vacuum zone and the pump chamber of pressurized segment.
Then, Fig. 9 is the experimental result representing the relation between and the power consumption of motor poor relative to the rotatable phase of the piston of the pressurized segment of the piston of vacuum zone.The rotatable phase difference of transverse axis represents the phase advance angle degree (along the direction of rotation of drive shaft, pressurization side piston is ahead of the phase angle of vacuum side piston) of the piston of the pressurized segment of the piston relative to vacuum zone.
As shown in Figure 9, it is known that: the current value of motor changes corresponding to relative to the poor Φ of the rotatable phase of the piston of the pressurized segment of the piston of vacuum zone.The harmony that this is to the pressure between the pump chamber of each section changes is relevant.
In this experimental example, the rotatable phase difference that current value is minimum is 40 °, and the pressure waveform of the pump chamber of each section now is Fig. 8 (A), (B) shown, the relation of antiphase each other.Now, the synthetic waveform of the internal pressure of the pump chamber of each section becomes as shown in Fig. 8 (C), and the pump chamber internal pressure of each section is cancelled out each other, so that the power consumption of motor is minimum.
On the other hand, under the most synchronous drive condition of internal pressure (poor relative to the rotatable phase of the piston of the pressurized segment of the piston of vacuum zone be+220 °) of the pump chamber of each section, as shown in Fig. 7 (C), the internal pressure superposition of the pump chamber of each section changes with causing the load period of motor, and this is the reason that power consumption increases.
Additionally it is possible to determine: as it is shown in figure 9, in the case of supply frequency is 50Hz or 60Hz, when rotatable phase difference Φ is in the range of more than 0 ° less than 80 °, reduce during driving current ratio rotatable phase difference Φ=0 ° (360 °) of motor.Particularly, when rotatable phase difference is in the range of Φ=40 ° ± 30 °, unrelated with supply frequency, current value is always the least than current value during Φ=0 °.It addition, in the scope of Φ=40 ° ± 15 °, it is possible to reduce power consumption further, during 50Hz, about reduce by 4.1%, during 60Hz, about reduce the current value of 2.2%.
Additionally, by above-mentioned phase difference Φ is set in 40 ° ± 15 °, amount the most capable of reducing power consumption, it is possible to reduce the vibration produced when pump installation 1 drives.Inventor passes through experimental verification, such as, during Φ=40 °, when each piston of relatively vacuum zone and pressurized segment is same-phase (Φ=0 °), the vibration acceleration on each direction of principal axis (with reference to Fig. 1) of X, Y and Z all decreases.
The effect of this reduction vibration, all can be confirmed in arbitrary supply frequency of 50Hz and 60Hz.
This concludes the description of embodiments of the present invention, but the present invention not shall be limited only to the extent above-mentioned embodiment, the deformation such as any amendment without departing from the spirit and scope of the invention, equivalent, improvement, should be included within the scope of the present invention.
Such as, in the above embodiment, the vacuum pumping section 11 and the pressurization pumping section 12 that constitute pump installation are made up of oscillating plunger pump respectively, but are not limited to this, such as, it is possible to by membrane pump etc., other move back and forth type piston pump and constitute each pump.
Additionally, in the above embodiment, illustrate that there is a driving motor and the pump installation of two pumping section, but there are many groups (such as, two groups) pump installation of pump unit that is made up of above-mentioned driving motor and two pumping section, it is possible to the application present invention.
Claims (3)
1. a pump installation, has: drive motor, the 1st pumping section and the 2nd pumping section, its
In,
Described driving motor, it has the 1st drive shaft and the 2nd drive shaft, it is possible to make described
1 drive shaft and described 2nd drive shaft are around the 1st axle synchronous rotary；
1st pumping section, its be used for vacuum exhaust, have: the 1st piston, it is by the described 1st
Rotarily driving of drive shaft, moves reciprocatingly along the 2nd direction of principal axis vertical with described 1st axle；
1st pump chamber, its internal pressure changes corresponding to the reciprocating motion of described 1st piston；
2nd pumping section, it is used for pressurizeing, has: the 2nd piston, it is by described 2nd drive shaft
Rotarily drive, move reciprocatingly along described 2nd direction of principal axis；2nd pump chamber, its internal pressure phase
The reciprocating motion of the 2nd piston described in Ying Yu changes, and described 2nd piston is with little more than 0 °
It is ahead of described 1st piston in the rotatable phase differences of 80 °.
Pump installation the most according to claim 1, it is characterised in that
Described rotatable phase difference is 40 ° ± 15 °.
Pump installation the most according to claim 1, it is characterised in that
Described 1st pumping section also has the 1st counterweight, and described 1st counterweight is around described 1st drive shaft
Rotate；
Described 2nd pumping section also has the 2nd counterweight, and described 2nd counterweight is relative to the described 1st
Counterweight, poor with described rotatable phase, rotate around described 2nd drive shaft.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-082015 | 2012-03-30 | ||
| JP2012082015 | 2012-03-30 | ||
| PCT/JP2013/001436 WO2013145576A1 (en) | 2012-03-30 | 2013-03-07 | Pump device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104204522A CN104204522A (en) | 2014-12-10 |
| CN104204522B true CN104204522B (en) | 2016-08-24 |
Family
ID=49258896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380017010.XA Active CN104204522B (en) | 2012-03-30 | 2013-03-07 | Pump installation |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20150086402A1 (en) |
| EP (1) | EP2832998B1 (en) |
| JP (1) | JP5878625B2 (en) |
| KR (1) | KR101602089B1 (en) |
| CN (1) | CN104204522B (en) |
| TW (1) | TWI619883B (en) |
| WO (1) | WO2013145576A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150147202A1 (en) * | 2013-11-27 | 2015-05-28 | Gardner Denver Thomas, Inc. | Pump having interchangeable heads |
| CN107076125A (en) * | 2014-09-11 | 2017-08-18 | 赫梅蒂克水力公司 | Gearshift |
| CN104612937B (en) * | 2015-03-06 | 2017-08-04 | 宁波捷美进出口有限公司 | Automobile inflator pump |
| CN111255666B (en) * | 2018-12-03 | 2023-11-28 | 广东美的白色家电技术创新中心有限公司 | Booster pump and water purification equipment |
| CN112032022B (en) * | 2020-09-10 | 2024-04-26 | 北京通嘉宏瑞科技有限公司 | Dry vacuum pump without dead angle purge gas and use method thereof |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5584675A (en) * | 1995-09-15 | 1996-12-17 | Devilbiss Air Power Company | Cylinder sleeve for an air compressor |
| US6126410A (en) * | 1998-02-12 | 2000-10-03 | Gast Manufacturing Corporation | Head cover assembly for reciprocating compressor |
| CN1740566A (en) * | 2004-08-26 | 2006-03-01 | Ulvac机工株式会社 | Diaphragm vacuum pump |
| CN1865700A (en) * | 2005-05-17 | 2006-11-22 | 托马斯工业公司 | Pump improvements |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3190233A (en) * | 1963-03-05 | 1965-06-22 | Welch Harold George | Pumps |
| US5564908A (en) * | 1994-02-14 | 1996-10-15 | Phillips Engineering Company | Fluid pump having magnetic drive |
| JP3640412B2 (en) * | 1994-05-17 | 2005-04-20 | 芝浦メカトロニクス株式会社 | Reciprocating pump unit |
| GB2314593B (en) * | 1996-06-28 | 1999-11-10 | Thomas Industries Inc | Two-cylinder air compressor |
| JP2008190517A (en) * | 2007-02-05 | 2008-08-21 | Kazumori Otogao | Portable air compressor |
| US8128382B2 (en) * | 2007-07-11 | 2012-03-06 | Gast Manufacturing, Inc. | Compact dual rocking piston pump with reduced number of parts |
-
2013
- 2013-03-07 WO PCT/JP2013/001436 patent/WO2013145576A1/en active Application Filing
- 2013-03-07 EP EP13768264.7A patent/EP2832998B1/en active Active
- 2013-03-07 KR KR1020147026361A patent/KR101602089B1/en active Active
- 2013-03-07 US US14/386,641 patent/US20150086402A1/en not_active Abandoned
- 2013-03-07 CN CN201380017010.XA patent/CN104204522B/en active Active
- 2013-03-07 JP JP2014507375A patent/JP5878625B2/en active Active
- 2013-03-15 TW TW102109327A patent/TWI619883B/en active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5584675A (en) * | 1995-09-15 | 1996-12-17 | Devilbiss Air Power Company | Cylinder sleeve for an air compressor |
| US6126410A (en) * | 1998-02-12 | 2000-10-03 | Gast Manufacturing Corporation | Head cover assembly for reciprocating compressor |
| CN1740566A (en) * | 2004-08-26 | 2006-03-01 | Ulvac机工株式会社 | Diaphragm vacuum pump |
| CN1865700A (en) * | 2005-05-17 | 2006-11-22 | 托马斯工业公司 | Pump improvements |
Also Published As
| Publication number | Publication date |
|---|---|
| TWI619883B (en) | 2018-04-01 |
| CN104204522A (en) | 2014-12-10 |
| KR20140126757A (en) | 2014-10-31 |
| JP5878625B2 (en) | 2016-03-08 |
| TW201400702A (en) | 2014-01-01 |
| US20150086402A1 (en) | 2015-03-26 |
| KR101602089B1 (en) | 2016-03-09 |
| EP2832998A4 (en) | 2016-01-20 |
| EP2832998A1 (en) | 2015-02-04 |
| WO2013145576A1 (en) | 2013-10-03 |
| JPWO2013145576A1 (en) | 2015-12-10 |
| EP2832998B1 (en) | 2017-01-18 |
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