CN1140805A - Rotary vane type hydraulic machines - Google Patents
Rotary vane type hydraulic machines Download PDFInfo
- Publication number
- CN1140805A CN1140805A CN96105456A CN96105456A CN1140805A CN 1140805 A CN1140805 A CN 1140805A CN 96105456 A CN96105456 A CN 96105456A CN 96105456 A CN96105456 A CN 96105456A CN 1140805 A CN1140805 A CN 1140805A
- Authority
- CN
- China
- Prior art keywords
- mentioned
- cylinder
- rotor
- compressor
- pump chamber
- Prior art date
- Legal status (The legal status 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 status listed.)
- Pending
Links
- 238000007789 sealing Methods 0.000 claims abstract description 51
- 239000007788 liquid Substances 0.000 claims abstract description 18
- 239000012530 fluid Substances 0.000 claims description 56
- 230000005855 radiation Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 abstract description 17
- 238000007906 compression Methods 0.000 abstract description 17
- 238000005461 lubrication Methods 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 45
- 238000001816 cooling Methods 0.000 description 6
- 238000009434 installation Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
The invention provides a mini-type rotary vane type compressor which is not reduced in volumetric efficiency and a vacuum pump. An approximately oval cylinder 23 is arranged inside a shell22; a vane29 which can move in the radial direction and a rotor27 of the vane29 are arranged at the eccentric position of the cylinder; the rotor27 divides the cylinder 23 into an airproof gas compression chamber30 with a large volume and a pump chamber 31 with a large volume to carry seal liquid; seal liquid discharged from a discharge outlet(36) of the pump chamber 31 is sent to the parts of the compressor and vacuum pump, which require sealing and lubrication. Since the seal liquid needs no extra pump to be pressurized, the invention can be structurally miniaturized and the invention can also prevent the reduction of the volumetric efficiency caused by internal leakage.
Description
The present invention relates to fluid compression engine devices such as gas compressor and vacuum pump, relate to the rotary vane type hydraulic machines device of band sliding-vane rotor in more detail.
Gas compressor is a kind of rotary vane type hydraulic machines device.It is to dispose the rotors that have a plurality of blades that slide in the radiation direction in the cylinder that forms on housing freely rotationally, because of the rotation of rotor sucks gas the above-mentioned cylinder from suction port, by means of the compression of above-mentioned blade it is discharged from exhaust port.
In this rotary sliding-vane compressor, be subjected to blade compresses and the gas that becomes high pressure is easy to leak to the low suction side of pressure, because this leakage and easily cause volumetric efficiency to reduce.In addition, owing to gas elevates the temperature by compression, thus need cooling, so, generally will be conducted to the sealing fluid that has sealing and greasy property and cooling performance concurrently on the revolution sliding parts of compressor.
Hitherto known method is to utilize the head pressure of pressurized gas to be used as supplying with the means of above-mentioned sealing fluid.Yet this head pressure method of utilizing has the air pressure that makes in the pressing chamber identical with sealed fluid pressure or be higher than the situation of its pressure in a flash, thereby the handlebar sealing fluid pushes back and causes the problem of temporary transient poor sealing easily.
For head it off, have in the prior art and on compressor, set up gear pump, supply with the structure of sealing fluid forcibly with this gear pump.
Fig. 5 and Fig. 6 show an example of the rotary sliding-vane compressor of setting up this gear pump.This rotary sliding-vane compressor 1 is in the cylinder 3 that forms in housing 2, can dispose rotationally freely with a plurality of rotors 5 with eccentric position along the blade 4 that radiates the direction slip, compress owing to the rotation of rotor 5 from gases such as suction port 6 inhaled airs with above-mentioned blade 4, gas after the compression is discharged from exhaust port 8 through valve opening 7, and be stored in the jar 9, the gas that is stored in the jar 9 is delivered to the place that will go by direction shown in the solid arrow, is provided with only to allow the pressurized gas outflow and can prevent the safety check 7a of backflow in above-mentioned valve opening 7.
Install gear pump 11 in the gearhousing 10 on being installed on housing 2.The suction port 12 of gear pump 11 is connected to jars 9 bottom by pipeline 13, and exhaust port 15 links to each other with aperture 17 on the housing 2 by pipeline 16, and handle is conducted on the revolution sliding parts of compressor from the sealing fluid in aperture 17.The sealing fluid that is conducted to the revolution slide part of compressor 1 is discharged in the jar 9 with the gas with blade 4 compressions, but it is stored in the bottom of jar owing to the proportion difference.
Sequence number 18 is motor of rotary rotor 5 and gear pump 11 among Fig. 6.
This compressor 1 that does not have a gear pump 11 is to force to the sealing fluid pressurization to deliver on the revolution slide part of compressor 1 with gear pump 11, so the structure that it is pressed with the discharge that utilizes pressurized gas specific energy is mutually supplied with sealing fluid more reliably, thereby revolution slide part poor sealing and cooling bad phenomenon that compressor seldom occurs, but owing to must assemble said gear pump 11 in addition, so make compressor 1 whole the change greatly, and because problem that gear meshing strengthens noise and vibration.
This problem occurs in equally by means of the rotation of the rotor of band blade and sucks, compresses and discharge in the rotary vane vacuum pump of gas.
Main purpose of the present invention provides a kind of rotary vane type hydraulic machines, it in addition the Assembling gear pump just can be reliably supply with sealing fluid to the revolution sliding parts, body is little and noise is little with vibration, can't cause the volumetric efficiency reduction because of leakage.
Other purpose of the present invention is by making it have the design rationalization that the function that sealed hydraulic is delivered to the rotor of pressurized gas and the pump on the cylinder makes above-mentioned fluid compression engine concurrently.
In order to achieve the above object, the formation of rotary vane type hydraulic machines provided by the invention is: the rotor that can dispose a plurality of blades that slide in housing in the cylinder that forms freely rotationally on the radiation direction, turning handle gas by this rotor and blade is drawn in the pressing chamber from suction port, compressed and discharged from exhaust port, and above-mentioned cylinder is divided into by above-mentioned rotor suck, the above-mentioned pressing chamber of pressurized gas, sealing fluid is sucked from liquid sucting port, press and from exhaust port row pump chamber to the revolution slide part.
Specific constructive form of the present invention is that to make above-mentioned cylinder be elliptical shape, forms above-mentioned pressing chamber and pump chamber between the two end part of transverse direction and rotor.At this moment, because above-mentioned rotor is arranged on the position of being partial to pump chamber one side in the cylinder, just can become the desirable little state of volume ratio compression chamber volume that makes pump chamber.
As one embodiment of the present invention, it is provided with to comprise to separate sneaks into the filter of the sealing fluid in the pressurized gas or at least one the segregating unit in the cooler.
The fluid compression engine of the present invention that said structure is arranged, owing on the part of cylinder, form pump chamber, by blade rotation sealing fluid is sucked in the pump chamber, simultaneously its pressurization is sent to the desired position, so can not establish existing such gear pump in addition, the pump-unit that rotor of using with pressurized gas and blade and cylinder are used as the force feed sealing fluid also can supply to required place to sealing liquid reliably, prevents gas leakage in view of the above and reliably, prevents that volumetric efficiency from reducing.
And, owing to omitted the said gear pump, can make the whole miniaturization of compressor, simultaneously owing to do not have the noise of gear engagement and the compressor that vibrational energy makes it to become low noise, low vibration.
In addition, because the pump-unit of above-mentioned rotor and blade and cylinder double as gas compressing apparatus and force feed sealing fluid makes fluid compression engine simple, form reasonably design.
And then, owing to be initiatively to pressurize its force feed to sealing fluid,, thereby can with posture more freely this fluid compression engine be set corresponding to the pipe arrangement space so the mobile of sealing liquid is subjected to the influence that posture is set of fluid compression engine little with above-mentioned blade.
Fig. 1 is the sectional view of the present invention's the 1st embodiment's gas compressor, is the sectional view along A-A line among Fig. 2.
Fig. 2 is the sectional view along the B-B line of Fig. 1.
Fig. 3 is the sectional view of the present invention's the 2nd embodiment's vacuum pump, is the sectional view along C-C line among Fig. 4.
Fig. 4 is that the figure that cuts open along D-D line among Fig. 3 looks.
Fig. 5 is the major component longitudinal section of known compressor.
Fig. 6 is the major component sectional elevation of known compressor.
Fig. 1 and Fig. 2 illustrate an example as rotary vane type hydraulic machines of the present invention, and it is the compressor of gases such as pressurized air, and this compressor 21 is provided with housing 22 and the prime mover 25 (example is a motor among the figure) that is tightly connected with suitable way.
Above-mentioned housing 22 is made of airtight the 1st continuous parts 22a and the 2nd parts 22b, forms cylinder 23 between two parts 22a, 22b.This cylinder 23 is an approximate ellipsoidal, and its concrete shape is to be semicircle substantially in the halves of transverse direction, and links these semi-circular portion with the big circular-arc part of radius of curvature.
Round rotor 27 can be provided in the above-mentioned cylinder 23 freely rotationally.Rotor 27 usefulness key 27a are connected on the axle 28 of prime mover 25, and rotate by the driving of prime mover 25.Be on the periphery of above-mentioned rotor 27 and be formed on circumferencial direction equally spaced a plurality of (example is 2 among the figure) blade installation groove radially, blade 29 inserts respectively in each blade installation groove movably in the radiation direction.Above-mentioned rotor 27 is configured in the above-mentioned cylinder 23 to be had to a side on the position of certain off-centre along transverse, in view of the above this cylinder is divided into voltage supply the contract capacious pressing chamber 30 of usefulness of gas and the little pump chamber 31 of volume that voltage supply send sealing fluid to use.
The axial length l of above-mentioned rotor 27 and the degree of depth L of cylinder 23 will set size minimum allowable except l for greater than the size relationship the maximum allowable size situation (stationary fit) of L, so that they can cooperate with the dimensional accuracy of the best.Specifically, be set at the maximum allowable undersized that makes l in the relation (movingly) of the minimum size allowable of L or for not belonging to the size relationship (transition fit) of above-mentioned virtually any size relation (stationary fit and movingly), best with the size relationship of " transition fit " therein.Like this, above-mentioned rotor 27 just to keep the state of micro-gap respectively between the bottom surface of its axial bi-side and cylinder 23 and the 2nd parts 22b inner side surface, can be disposed in the above-mentioned cylinder 23 freely rotationally.
Above-mentioned blade 29,29 is at the sealed fluid pressure that flows into above-mentioned blade installation groove or be located at the wall that is pressed towards cylinder 23 under the effect of the helical spring jack units such as (omitting among the figure) in this groove.
And then above-mentioned blade is not limited to 2 shown in the figure, and the blade that equally spaced is provided with more than 3 also is fine in a circumferential direction.
The suction port 33 that gases such as air is sucked the inlet side of pressing chamber 30 is set on the 1st parts 22a of above-mentioned housing 22, at the outlet side of pressing chamber 30 exhaust port 34 that the gas that is compressed by blade 29,29 is discharged is set then, this exhaust port 34 is connected with exhaust port 38 on the 2nd parts 22b by valve pocket 34a.In above-mentioned valve pocket 34a, be provided with spring 37a and carry out the safety check 37 of roof pressure to stop compressed gas backstreaming.
In addition, also on the 1st parts 22a of above-mentioned housing 22, be provided with the liquid sucting port 35 that the sealing fluid that is made of water or oil is drawn into the inlet side of pump chamber 31, then be provided with the exhaust port 36 that is used to discharge by the sealing fluid of blade 29,29 pressurizations at the outlet side of pump chamber 31, this exhaust port 36 is communicated with exhaust port 42 on the 2nd parts 22b through valve pocket 36a.In above-mentioned valve pocket 36a, be provided with spring 37a and carry out the safety check 37 that roof pressure refluxes with the sealing fluid that stops pressurization.
Between above-mentioned exhaust port 34 and liquid sucting port 35, and between exhaust port 36 and the suction port 33, between pressing chamber 30 and pump chamber 31, separate airtightly in other words by rotor 27.
Above-mentioned gas suction port 33 is communicated with outer gas, and pressurized gas exhaust port 38 39 is connected on the basin 40 by the road.And the liquid sucting port 35 of sealing fluid is 41 bottoms that are connected in the above-mentioned basin 40 by the road, sealing fluid exhaust port 42 is then linked respectively on formed supplying mouth 44 and 45 on the 1st parts 22a and the 2nd parts 22b by pipeline 43, and above-mentioned supplying mouth 44 is through supplying with sealing fluid at the slip surface of formed runner 46 on the 1st parts 22a between axle 28 and the 1st parts 22a; 45 of supplying mouths are fed to sealing fluid on the face of the 2nd parts 22b cylinder 23 sides.
And then, though in illustrating, omitted, runner needs to seal so that the sealing fluid after the pressurization is supplied to, position lubricated and cooling connects the mode that is located at above-mentioned each aperture 42,44,45 on the housing 22 to replace with the above-mentioned pipeline 43 outside the compressor 21 but also can directly form in housing 22, the pipe arrangement that does not so just have outside trouble, and the profile of the further compresses machine 21 of energy.
Certainly, when the gas beyond the air is compressed, be connected to suction port 33 on this gas source.
Sequence number 48 is spring seats of the spring 37a of roof pressure safety check 37 among Fig. 1, and sequence number 49 is the seal rings that seal between housing 22 and prime mover 25 among Fig. 2.
In above-mentioned the 1st embodiment's compressor, if rotor 27 is when the direction of arrow is rotated in Fig. 1 under the effect of prime mover 25, each blade 29,29 is subjected to centrifugal action and outstanding from the blade installation groove, and the state that is crimped on cylinder 23 walls with its front end rotates with rotor 27.The result, just gas is sucked pressing chamber 30 from suction port 33, rotate its compression by blade 29 again, by the blade 29 in the above-mentioned pressing chamber 30, the gas that is compressed flows out from exhaust port 34, and press off arrival exhaust port 38 by the safety check 37 of spring 37a institute roof pressure, be housed in the jar 40 by pipeline 39 again.The pressurized gas of being stored in the jar 40 then is conducted in the suitable fluid press device not shown in the figures.
Before compressor 21 running, infeed a small amount of sealing fluid in jars 40 in advance, suck in the pump chambers 21 from liquid sucting port 35, and be used in blade 29 in this pump chamber 21 its pressurization by pipeline 41.Sealing fluid after the pressurization presses off by the safety check 37 of spring 37a roof pressure and is discharged in the exhaust port 42,43 delivers to supplying mouth 44 and 45 by the road again, to sealing around axle 28 and the blade 29,29 with lubricated, simultaneously pressing chamber 30 is cooled off.
To blade 29,29 etc. seal, the major part of the above-mentioned sealing fluid of lubricated and cooling has been sneaked into pressurized gas and flow into simultaneously in jars 40 with this gas, separate in gas in this jar 40 internal cause proportions difference, be stored on the bottom surface of jar 40, the sealing fluid of being store sucks the pump chamber 31 once more from liquid sucting port 35, and the part of sealing fluid circulates and is back to pump chamber 31 inlet sides in cylinder 23 with the rotation of rotor 27 and blade 29 and pressurizes.
In the case, the cooler of the gas of discharging by known oil separation filter device of assembling on jar 40 or cooling, perhaps both are double establishes, and then can further improve the function that it separates sealing fluid and gas.
Though omit in the drawings, but gas-liquid separating apparatus such as the filter of above-mentioned separating oil and cooler can be installed on housing 22 also, by this segregating unit pressurized gas is conducted to basin 40, so just can be omitted in the pipe arrangement 41 between above-mentioned basin 40 and the liquid sucting port 35.
There are the compressor 21 usefulness rotors 27 of said structure that cylinder 23 is divided into pressing chamber 30 and pump chamber 31, pressurize with the sealing fluid in 29 pairs of suction pump chambers 31 of blade, and deliver on sealing that needs compressor 21 and the revolution slide part that lubricates part, need not to establish in addition existing such gear pump and just can be conducted to required position to sealing fluid reliably, whereby, can prevent reliably that the volumetric efficiency that causes because of gas leakage is low.And, owing to omitted the said gear pump, can also make the compressor integral miniaturization, and since the noise that does not exist gear engagement to cause become low noise with vibration, hang down the compressor that vibrates.
In addition, because above-mentioned sealing fluid pressurizes in pump chamber 31 and sends, it sends sealing fluid with the head pressure of utilizing pressurized gas structure is different, and its sealed fluid pressure increases, thereby can seal reliably and lubricated, also can reduce internal leakage as much as possible.
And then the delivery volume of above-mentioned sealing fluid can be lacked than the gas of compression in pressing chamber 30, so the volume of the pump chamber 31 that sealing fluid is pressurizeed can be littler than the volume of pressing chamber 30.And be engaged on the part of cylinder 23 of approximate ellipsoidal above-mentioned pump chamber 31 is set, even when on compressor 21 pump chamber 31 being set, these compressor 21 whole sizes are compared with the structure that does not have above-mentioned pump chamber 31 with the volume of this pressing chamber does not almost have any variation.
Vacuum pump as the other embodiment of rotating fluid compressor of the present invention has been shown among Fig. 3 and Fig. 4.This vacuum pump 51 have with above-mentioned the 1st embodiment in the identical structure of compressor 21 essence, its difference is only for to be connected to suction port 33 on the vacuum chamber 52 of vacuum compressor, exhaust port 38 is to atmosphere opening, liquid sucting port 35 links to each other with sealing fluid basin 55.
In this vacuum pump 51, the gas from suction port 33 inspiration vacuum chambers 52 is discharged to the outside from exhaust port 38, and sealing fluid is drawn into the liquid sucting port 35 from basin 55.
Because other structure of above-mentioned vacuum pump 51 is all identical with above-mentioned compressor 21 with effect, so main same area gives identical sequence number among the figure, detailed description is omitted.
The fluid compression engine of the present invention of this form is to form pump chamber on the part of cylinder, by blade rotation sealing fluid is sucked in this pump chamber, required position is delivered in pressurization simultaneously, need not to adorn in addition existing the sort of gear pump and just can be conducted to required place to sealing fluid reliably, can prevent gas leakage reliably in view of the above, prevent that volumetric efficiency is low.
And, owing to omitted the said gear pump, thus can make the whole miniaturization of compressor, also since the noise that does not exist gear engagement to form become a kind of low noise and hang down the compressor that vibrates with vibration.
And then, implement feed flow owing to sealing fluid initiatively being pressurizeed by means of pump, the mobile of sealing liquid is subjected to the influence that posture is set of fluid compression engine little, thereby can with attitude more freely this fluid compression engine be set corresponding to the space of pipe arrangement.
Claims (4)
1. rotary vane type hydraulic machines, its structure is to dispose the rotor of a plurality of blades that can slide on the radiation direction in the cylinder that forms in housing freely rotationally, turning handle gas by this rotor and blade is compressed in suction port suction pressing chamber, and, it is characterized in that from the exhaust port discharge:
Above-mentioned cylinder be divided into utilize above-mentioned rotor and suck, the above-mentioned pressing chamber of pressurized gas, from liquid sucting port suction seal liquid pressurization back from the pump chamber of exhaust port row to the revolution slide part.
2. the rotary vane type hydraulic machines described in claim 1, it is characterized in that: above-mentioned cylinder is essentially ellipse, forms above-mentioned pressing chamber and pump chamber between the two end part of this long axis of ellipse direction and rotor.
3. the rotary vane type hydraulic machines described in claim 2 is characterized in that:
By above-mentioned rotor is arranged on the position of being partial to pump chamber one side in the cylinder, make the volume of pump chamber volume less than pressing chamber.
4. as the rotary vane type hydraulic machines described in the claim 1 to 3 each, it is characterized in that:
Be provided with on the above-mentioned housing and comprise filter that the sealing fluid of sneaking in the pressurized gas is separated or one segregating unit in the cooler at least.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7124390A JPH08296575A (en) | 1995-04-25 | 1995-04-25 | Rotary vane type compressor and vacuum pump |
| JP124390/95 | 1995-04-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1140805A true CN1140805A (en) | 1997-01-22 |
Family
ID=14884243
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN96105456A Pending CN1140805A (en) | 1995-04-25 | 1996-04-24 | Rotary vane type hydraulic machines |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPH08296575A (en) |
| KR (1) | KR100186875B1 (en) |
| CN (1) | CN1140805A (en) |
| DE (1) | DE19614329A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597525A (en) * | 2009-09-28 | 2012-07-18 | 泰康产品公司 | Rotary compressor |
| CN114787517A (en) * | 2019-12-19 | 2022-07-22 | 莱宝法国有限责任公司 | Lubricant sealed vacuum pump, lubricant filter and method |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100482859B1 (en) * | 2002-10-14 | 2005-04-14 | 현대자동차주식회사 | Integration device with compressor and vacuum pump |
| CN100432439C (en) * | 2005-01-20 | 2008-11-12 | 株式会社日立制作所 | Hand-held vacuum pump and automated urinary drainage system using that vacuum pump |
| TWI274105B (en) | 2005-01-20 | 2007-02-21 | Hitachi Ltd | Portable vacuum pump and automatic urination treatment apparatus using thereof |
| ITMI20051008A1 (en) | 2005-05-30 | 2006-11-30 | O M P Officine Mazzocco Pagnon | MOTOR DEPRESSOR FOR MOTOR VEHICLES AND NON-RETURN VALVE FOR THIS HEADER |
| CN101652546B (en) * | 2007-11-30 | 2011-09-07 | 阿尔法动力系统公司 | Rotary mechanically reciprocated sliding metal vane air pump and boundary layer gas turbines integrated with a pulse gas turbine engine system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1553034A1 (en) * | 1965-02-03 | 1969-11-06 | Eriksson Sven Gustav | Suction pump for liquid, air and solid particles |
| DE2223156C2 (en) * | 1972-05-12 | 1985-02-14 | Robert Bosch Gmbh, 7000 Stuttgart | Vane compressors |
| DE3430353A1 (en) * | 1983-08-20 | 1985-03-07 | Mitsubishi Denki K.K., Tokio/Tokyo | WING CELL PUMP |
-
1995
- 1995-04-25 JP JP7124390A patent/JPH08296575A/en active Pending
-
1996
- 1996-04-11 DE DE19614329A patent/DE19614329A1/en not_active Withdrawn
- 1996-04-23 KR KR1019960012410A patent/KR100186875B1/en not_active IP Right Cessation
- 1996-04-24 CN CN96105456A patent/CN1140805A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597525A (en) * | 2009-09-28 | 2012-07-18 | 泰康产品公司 | Rotary compressor |
| CN114787517A (en) * | 2019-12-19 | 2022-07-22 | 莱宝法国有限责任公司 | Lubricant sealed vacuum pump, lubricant filter and method |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100186875B1 (en) | 1999-05-01 |
| DE19614329A1 (en) | 1996-10-31 |
| JPH08296575A (en) | 1996-11-12 |
| KR960038127A (en) | 1996-11-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1261692C (en) | Sealed rotor duplex compressor and manufacturing method thereof | |
| CN1081754C (en) | Compression engine | |
| CN1022772C (en) | Combined blade rotary engine | |
| MY119733A (en) | Rotary compressor | |
| CN1249350C (en) | Vacuum-protective device for vortex compressor | |
| CN1140805A (en) | Rotary vane type hydraulic machines | |
| CN112922836A (en) | Gas compressor | |
| CN1620554A (en) | Suction mechanism of rotary compressor | |
| CN1608173A (en) | Hermetic compressor | |
| US12018686B2 (en) | Rotary compressor | |
| CN1637298A (en) | Compressor | |
| CN1548753A (en) | Closed rotary compressor | |
| CN1061131C (en) | Method for pumping high-vacuum degree | |
| CN2769556Y (en) | Vortex compressor | |
| CN214998208U (en) | Gas compressor | |
| CN1107792C (en) | Reciprocative moving type compressor | |
| CN1757928A (en) | Orbiting vane compressor with side-inlet structure | |
| CN111188753A (en) | No-load starting valve of compressor | |
| CN1094567C (en) | Fluid compressor | |
| CN221299478U (en) | Single-vane air pressure pump | |
| CN210440211U (en) | Sliding vane type power and air compressor capable of being used as power compensation equipment | |
| CN1106896A (en) | An oil pump for a closed type compressor | |
| US11891995B2 (en) | Rotary compressor having improved vane chattering performance | |
| CN201206551Y (en) | Single-stage cantalever radial air intake and exhaust double-action liquid ring pump | |
| CN202338474U (en) | Chord-variable type compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |