SE509659C2 - Disc Piston Compressor - Google Patents
Disc Piston CompressorInfo
- Publication number
- SE509659C2 SE509659C2 SE9703628A SE9703628A SE509659C2 SE 509659 C2 SE509659 C2 SE 509659C2 SE 9703628 A SE9703628 A SE 9703628A SE 9703628 A SE9703628 A SE 9703628A SE 509659 C2 SE509659 C2 SE 509659C2
- Authority
- SE
- Sweden
- Prior art keywords
- rotor
- disc piston
- piston
- disc
- housing
- Prior art date
Links
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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
-
- 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
- F04C18/3441—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 one line or continuous surface substantially parallel to the axis of rotation
- F04C18/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Compressor (AREA)
Abstract
Description
15 20 25 30 35 509 659 ventilskivan ligger an mot fångaren och stängd när den lig- ger an mot sätet. Fjädrarnas uppgift är att minska backström- ningen genom att påskynda ventilernas stängningsförlopp. 15 20 25 30 35 509 659 the valve disc rests against the catcher and closes when it rests against the seat. The task of the springs is to reduce the backflow by speeding up the closing process of the valves.
För skivkolvkompressorer med självverkande ventil i huset på utloppssidan har det, speciellt vid höga varvtal, visat sig vara ett problem att begränsa backströmningen genom ventilen till acceptabel mängd arbetsmedium per tidsenhet.For disc piston compressors with self-acting valve in the housing on the outlet side, it has, especially at high speeds, proved to be a problem to limit the reverse flow through the valve to an acceptable amount of working medium per unit time.
Med hjälp av ventilfjädrar kan man minska backströmningen men inte eliminera den. Styvare fjädrar ger verkningsgrads- vinst genom minskad backströmning men förlust genom högre mottryck. Ändamålet med föreliggande uppfinning är att åstadkomma en skivkolvkompressor utan ventilfjädrar som är helt fri från backströmning.With the help of valve springs, you can reduce the reverse flow but not eliminate it. Stiffer springs provide efficiency gains through reduced reverse flow but losses through higher back pressure. The object of the present invention is to provide a disc piston compressor without valve springs which is completely free from reverse flow.
Detta åstadkommes enligt uppfinningen genom kombinationen att rotorn innefattar från dess mantelyta utgående utloppskanaler för utledning av arbetsmediet från arbetsrummen och självver- kande ventiler anordnade att i stängt läge förhindra back- strömming av arbetsmediet i utloppskanalerna samt att tvär- snittsformen på husets inre mantelväggyta är så utformad att den under en viss vinkel tätt följer rotorns mantelyta för att förhindra backströmning av arbetsmediet i utloppskanaler- na under de självverkande ventilernas stängningsperioder.This is achieved according to the invention by the combination that the rotor comprises outlet ducts emanating from its jacket surface for discharging the working medium from the working rooms and self-acting valves arranged to prevent backflow of the working medium in the outlet ducts in closed position and that the cross-sectional shape of the housing that it closely follows the mantle surface of the rotor at a certain angle in order to prevent backflow of the working medium into the outlet ducts during the closing periods of the self-acting valves.
Ett utföringsexempel på uppfinningen kommer i det följande att beskrivas med hänvisning till den bilagda ritningen.An embodiment of the invention will be described in the following with reference to the accompanying drawing.
Fig 1 visar ett axialsnitt genom en skivkolvkompressor enligt uppfinningen.Fig. 1 shows an axial section through a disc piston compressor according to the invention.
Fig 2 visar en sektion tagen utmed I-I i figur 1.Fig. 2 shows a section taken along I-I in Fig. 1.
Skivkolvkompressorn innefattar ett hus 1 med ett kolvrum som är definierat av en mantelvägg 2 och två parallella 10 15 20 25 30 35 3 509 659 gavelväggar 3 och 4. En cirkulärcylindrisk rotor 5 är pla- cerad excentriskt i kolvrummet. Rotorns 5 geometriska axel markeras med 51. Rotorn 5 har en lagringsaxel 52 som är lagrad i lagringar 60, 61 i gavelväggen 4.The disc piston compressor comprises a housing 1 with a piston space defined by a jacket wall 2 and two parallel end walls 3 and 4. A circular-cylindrical rotor 5 is placed eccentrically in the piston space. The geometric axis of the rotor 5 is marked with 51. The rotor 5 has a bearing shaft 52 which is mounted in bearings 60, 61 in the end wall 4.
Rotorn 5 har en central kavitet 54 som är öppen mot gavel- väggen 3. Gavelväggen 3 uppbär en axeltapp 31 som sträcker sig in i det centrala inre området av huset 1 och bär vid sin fria ände ett rullningslager 32 vars geometriska axel indikeras med 321. Rotorn 5 har ett diametralt spår 55 som sträcker sig genom den skålformade rotorns 5 geometriska axel 51.The rotor 5 has a central cavity 54 which is open to the end wall 3. The end wall 3 carries a shaft pin 31 extending into the central inner area of the housing 1 and carries at its free end a rolling bearing 32 whose geometric axis is indicated by 321. The rotor 5 has a diametrical groove 55 which extends through the geometric axis 51 of the cup-shaped rotor 5.
En skivkolv 7 är emottagen i rotorns 5 diametrala spår 55.A disc piston 7 is received in the diametrical groove 55 of the rotor 5.
Skivkolven 7 omfattar en kolvskiva 71 som med ringa spel sträcker sig genom rotorns 5 diametrala spår 55 för att vara förskjutbar i radiell riktning relativt rotorn 5 i det dia- metrala spåret 55. Kolvskivan 71 har en bredd motsvarande avståndet mellan husets 1 gavelväggar 3 och 4. Den allmänt flata och rektangulära kolvskivan 71 har två axiella kanter 72 som löper parallella med mantelväggens 2 inre mantelvägg- yta 21 och har vidare radiella kanter 73 och 74 som löper på ringa avstånd från och parallellt med gavelväggarnas 3 och 4 innerytor. Husets 1 inre mantelväggyta 21 är så utformad att den inom en vinkel 4% , vars mittlinje 22 skär rotorns 5 ge- ometriska axel 51 och rullningslagrets 32 geometriska axel 321 och vars spets ligger på rotorns 5 geometriska axel 51, följer tätt intill rotorn 5 och under resten av varvet föl- jer den bana som skivkolvens 7 axiella kanter 72 avgränsar under rotorns 5 rotation.The disc piston 7 comprises a piston disc 71 which with small clearance extends through the diametrical groove 55 of the rotor 5 to be displaceable in radial direction relative to the rotor 5 in the diametrical groove 55. The piston disc 71 has a width corresponding to the distance between the end walls 3 and 4 of the housing 1 The generally flat and rectangular piston plate 71 has two axial edges 72 which run parallel to the inner shell wall surface 21 of the casing wall 2 and further has radial edges 73 and 74 which run at short distances from and parallel to the inner surfaces of the end walls 3 and 4. The inner casing wall surface 21 of the housing 1 is designed so that it adjoins the geometric axis 51 of the rotor 5 and the geometric axis 321 of the rolling bearing 32 at an angle of 4%, the center line of which follows the geometric axis 51 of the rotor 5, closely follows the rotor 5 and during the rest of the revolution follows the path which the axial edges 72 of the disc piston 7 delimit during the rotation of the rotor 5.
Vid sin mot gavelväggen 3 vända ände har skivkolven 7 ett mot gavelväggen 3 öppet styrspår 75 vars sidoväggar 76 är planparallella och ligger i plan som är vinkelräta mot kolvskivans 71 huvudplan. Avståndet mellan sidoväggarna 76 motsvarar ytterdiametern för rullningslagret 32, så att kolvskivan 71 kan parallellförskjutas i förhållande till rullningslagret 32. Skivkolven 7 är symetrisk i förhållande 10 15 20 25 30 35 509 659 4 till ett plan som innefattar rullningslagrets 32 geometriska axel 321 och som är vinkelrätt mot kolvskivans 71 huvudplan.At its end facing the end wall 3, the disc piston 7 has a guide groove 75 open towards the end wall 3, the side walls 76 of which are plane-parallel and lie in planes which are perpendicular to the main plane of the piston disc 71. The distance between the side walls 76 corresponds to the outer diameter of the rolling bearing 32, so that the piston disc 71 can be displaced in parallel with the rolling bearing 32. The disc piston 7 is symmetrical in relation to a plane comprising the geometric axis 321 of the rolling bearing 32 and which is perpendicular to the main plane of the piston plate 71.
Skivkolvkompressorn har en inloppsöppning 81 i husets 1 mantelvägg 2 och en utloppsöppning 82 i gavelväggen 3.The disc piston compressor has an inlet opening 81 in the casing wall 2 of the housing 1 and an outlet opening 82 in the end wall 3.
Inloppsöppningen 81 sträcker sig i husets 1 inre mantel- väggyta 21, räknat i rotorns 5 rotationsriktning enligt pi- len 56, från vinkelns 0( mittlinje 22. Sett i axiell riktning täcks från där vinkeln of slutar till cirka 90 grader utloppsöppningens 82 tvärsnittsarea av den centrala kavi- teten 54 i rotorn 5.The inlet opening 81 extends in the inner jacket wall surface 21 of the housing 1, calculated in the direction of rotation of the rotor 5 according to the arrow 56, from the angle 0 (center line 22. Seen in the axial direction from where the angle of ends to about 90 degrees the cross-sectional area of the outlet opening 82). central cavity 54 in the rotor 5.
För utledning av arbetsmediet från arbetsrummen har rotorn 5 två utloppskanaler 91 som utgår från rotorns 5 mantelyta 53 är placerade en på vardera sidan om det diametrala spå- 55. utloppskanalerna 91 belägna strax före det diametrala spå- och ret Räknat i rotationsriktningen enligt pilen 56 är ret 55. Utloppskanalerna 91 är riktade radiellt inåt i ro- torn 5 och leder från arbetsrummen in till rotorns 5 centra- la kavitet 54 som utmynnar ur rotorn 5 mot utloppsöppningen 82. I båda utloppskanalerna 91 är självverkande ventiler 92 anordnade för att förhindra backströmning av arbetsmediet i utloppskanalerna 91.For discharging the working medium from the working spaces, the rotor 5 has two outlet channels 91 emanating from the mantle surface 53 of the rotor 5, one is located on each side of the diametrical groove 55. the outlet ducts 91 located just before the diametrical groove and counted in the direction of rotation according to arrow 56 are 55. The outlet channels 91 are directed radially inwards in the rotor 5 and lead from the working spaces into the central cavity 54 of the rotor 5 which opens from the rotor 5 towards the outlet opening 82. In both outlet channels 91 self-acting valves 92 are arranged to prevent backflow of the working medium in the outlet ducts 91.
En självverkande ventil 92 har ett säte 94 och en fångare 95 mellan vilka en ventilskiva 93 är fritt rörlig och utformad så att när den ligger an mot sätet 94 och täcker sätesöpp- ningen 96 är ventilen stängd och när den ligger an mot fångaren 95 är ventilen öppen. Förutom av tryckskillnaden på sidorna om ventilskivan 93 påverkas denna av den radiellt utåt riktade centrifugalkraften när rotorn roterar.A self-acting valve 92 has a seat 94 and a catcher 95 between which a valve disc 93 is freely movable and designed so that when it abuts the seat 94 and covers the seat opening 96 the valve is closed and when it abuts the catcher 95 the valve is open. In addition to the pressure difference on the sides of the valve disc 93, this is affected by the radially outwardly directed centrifugal force when the rotor rotates.
Om kolvskivan 71 under rotorns 5 rotation i riktning enligt pilen 56 befinner sig i det i figur 2 visade läget börjar, strax efter det att rotorn 5 vridits en vinkel GX/2, ett nytt arbetsrum att växa fram, vilket är begränsat av husets 1 inre mantelväggyta 21, rotorn 5, gavelväggarna 3 och 4 samt skivkolven 7. Detta arbetsrum kommer strax i kontakt 10 15 20 25 30 35 5 509 659 med inloppsöppningen 81. Under rotorns 5 vidare rotation ökar arbetsrummet hela tiden i volym under det att arbets- medium strömmar in i arbetsrummet. Sin största volym uppnår arbetsrummet efter 270 graders vridning av rotorn 5. Strax därefter har arbetsrummet ej längre kontakt med inlopps- öppningen 81 och intern kompression börjar under minskning av arbetsrummets volym. När trycket i arbetsrummet är så mycket högre än trycket i rotorns 5 centrala kavitet 54 att det övervinner centrifugalkraften på ventilskivan 93 öppnar den självverkande ventilen 92 och arbetsmedium strömmar genom den utloppskanal som står i förbindelse med arbets- rummet. Under rotorns 5 vidare rotation pressas allt arbets- medium i arbetsrummet ut genom utloppskanalen 91 och via den centrala kaviteten 54 vidare ut genom utloppsöppningen 82.If the piston disc 71 is in the position shown in Figure 2 during the rotation of the rotor 5 in the direction of the arrow 56, shortly after the rotor 5 has been turned an angle GX / 2, a new working space begins to emerge, which is limited by the interior of the housing 1 jacket wall surface 21, rotor 5, end walls 3 and 4 and the disc piston 7. This working space comes into immediate contact with the inlet opening 81. During the further rotation of the rotor 5, the working space constantly increases in volume while the working medium flows into the workroom. The working space reaches its largest volume after 270 degrees of rotation of the rotor 5. Shortly thereafter, the working space no longer has contact with the inlet opening 81 and internal compression begins while reducing the volume of the working space. When the pressure in the working space is so much higher than the pressure in the central cavity 54 of the rotor 5 that it overcomes the centrifugal force on the valve disc 93, the self-acting valve 92 opens and working medium flows through the outlet channel communicating with the working space. During the further rotation of the rotor 5, all working medium in the working space is forced out through the outlet channel 91 and via the central cavity 54 further out through the outlet opening 82.
När sätesöppningen 96, som varit i kontakt med arbetsrummet, kommit in helt inom vinkeln a¥ tätar husets 1 inre mantel- väggyta 21 mot sätets 94 radiellt utåt riktade del och ar- betsmedium kan då inte strömma i någon riktning i utlopps- kanalen 91. Om således den självverkande ventilen 92 stänger helt med hjälp av centrifugalkraften på ventilskivan 93 un- der den tid som sätesöppningen 96 befinner sig helt inom vinkeln ai kan backströmning ej förekomma under den själv- verkande ventilens 92 stängningsförlopp.When the seat opening 96, which has been in contact with the working space, has entered completely within the angle that the inner casing wall surface 21 of the housing 1 seals against the radially outwardly directed part of the seat 94 and working medium can then not flow in any direction in the outlet channel 91. Thus, if the self-acting valve 92 closes completely by the centrifugal force on the valve disc 93 during the time that the seat opening 96 is completely within the angle α, backflow cannot occur during the closing process of the self-acting valve 92.
Genom att rullningslagret 32 uppbär skivkolven 7 i styr- spåret 75 är skivkolven 7 radiellt orörlig i dess plan men då den är förskjutbar i normalriktningen kan den medfölja rotorn 5 i dess rotation under det att skivkolven 7 enbart är rörlig relativt rotorn 5 i radiell led. Under rotorns 5 rotation kommer skivkolvens 7 axiellt riktade kanters 72 rörelsebana att vara entydigt bestämd. Om således husets 1 inre mantelväggytas 21 tvärsnittsform utanför vinkeln âf överenstämmer med de axiella kanternas 72 avgränsande rörelsebana tätar skivkolven 7 direkt mot mantelväggytan 21.Because the roller bearing 32 supports the disc piston 7 in the guide groove 75, the disc piston 7 is radially immovable in its plane, but when it is displaceable in the normal direction it can follow the rotor 5 in its rotation while the disc piston 7 is only movable relative to the rotor 5 in radial direction. During the rotation of the rotor 5, the axially directed edges 72 of the disc piston 7 will be unambiguously determined. Thus, if the cross-sectional shape 21 of the inner casing wall surface 21 of the housing 1 corresponds to the defining path of movement of the axial edges 72, the disc piston 7 seals directly against the casing wall surface 21.
Om husets 1 inre mantelväggytas 21 tvärsnittsform, även utanför vinkeln af, avviker något från de axiella kanter- 10 15 20 509 659 6 nas 72 avgränsande bana och t ex är en cirkelbåge kan avståndet mellan skivkolven 7 och mantelväggytan 21 över- bryggas med konventionella lameller som i radiell riktning är fritt rörliga i spår i skivkolven 7.If the cross-sectional shape of the inner casing wall surface 21 of the housing 1, also outside the angle of, deviates slightly from the defining path 72 of the axial edges and is, for example, an arc of a circle, the distance between the disc piston 7 and the casing wall surface 21 can be bridged with conventional slats which in the radial direction are freely movable in grooves in the disc piston 7.
Mantelväggytan 21 är företrädesvis cylindrisk men fackman- nen inser att man kan välja en mer eller mindre konisk form eller en form som definieras av en icke rak generatris.The jacket wall surface 21 is preferably cylindrical, but those skilled in the art will appreciate that one can choose a more or less conical shape or a shape defined by a non-straight generator.
Fackmannen inser också att skivkolvkompressorns arbets- område innefattar tryck från långt under till högt över atmosfärstrycket.Those skilled in the art will also appreciate that the working range of the disc reciprocating compressor includes pressures from far below to high above atmospheric pressure.
Utföringsexemplet ovan visar en skivkolvkompressor där backströmning förhindrats, där friktion mellan skivkolven och husets mantelvägg eliminerats och där kompressions- graden automatiskt anpassas för optimal verkningsgrad obe- roende av trycken på inlopps- och utloppssidan. Uppfin- ningen är dock ej begränsad till detta utföringsexempel utan ändringar kan vidtagas inom ramen för efterföljande patentkrav.The embodiment above shows a disc piston compressor where reverse flow is prevented, where friction between the disc piston and the casing wall of the housing is eliminated and where the compression ratio is automatically adjusted for optimal efficiency regardless of the pressures on the inlet and outlet side. However, the invention is not limited to this exemplary embodiment, but changes can be made within the scope of the appended claims.
Claims (8)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE9703628A SE509659C2 (en) | 1997-10-06 | 1997-10-06 | Disc Piston Compressor |
PCT/SE1999/000208 WO2000049295A1 (en) | 1997-10-06 | 1999-02-17 | Rotary vane compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE9703628A SE509659C2 (en) | 1997-10-06 | 1997-10-06 | Disc Piston Compressor |
PCT/SE1999/000208 WO2000049295A1 (en) | 1997-10-06 | 1999-02-17 | Rotary vane compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
SE9703628D0 SE9703628D0 (en) | 1997-10-06 |
SE9703628L SE9703628L (en) | 1999-02-22 |
SE509659C2 true SE509659C2 (en) | 1999-02-22 |
Family
ID=26663096
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE9703628A SE509659C2 (en) | 1997-10-06 | 1997-10-06 | Disc Piston Compressor |
Country Status (2)
Country | Link |
---|---|
SE (1) | SE509659C2 (en) |
WO (1) | WO2000049295A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8113805B2 (en) * | 2007-09-26 | 2012-02-14 | Torad Engineering, Llc | Rotary fluid-displacement assembly |
EP3350447B1 (en) | 2015-09-14 | 2020-03-25 | Torad Engineering, LLC | Multi-vane impeller device |
CN105201828B (en) * | 2015-10-14 | 2017-05-10 | 珠海凌达压缩机有限公司 | Roller and rotary compressor comprising same |
CN112412786B (en) * | 2020-10-26 | 2022-12-30 | 珠海格力节能环保制冷技术研究中心有限公司 | High-efficient compressor exhaust structure |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60147591A (en) * | 1984-01-11 | 1985-08-03 | Hitachi Ltd | Hydraulic machine |
US4568257A (en) * | 1984-04-13 | 1986-02-04 | Moore Jesse C | Rotary pump |
US4673343A (en) * | 1984-04-13 | 1987-06-16 | Moore Jesse C | Rotary vane pump |
ES2019910B3 (en) * | 1986-08-06 | 1991-07-16 | Barmag Barmer Maschf | VACUUM PUMP WITH FINS |
-
1997
- 1997-10-06 SE SE9703628A patent/SE509659C2/en not_active IP Right Cessation
-
1999
- 1999-02-17 WO PCT/SE1999/000208 patent/WO2000049295A1/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
SE9703628L (en) | 1999-02-22 |
WO2000049295A1 (en) | 2000-08-24 |
SE9703628D0 (en) | 1997-10-06 |
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Legal Events
Date | Code | Title | Description |
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NUG | Patent has lapsed |