US20130022487A1 - Vane pump - Google Patents
Vane pump Download PDFInfo
- Publication number
- US20130022487A1 US20130022487A1 US13/521,878 US201113521878A US2013022487A1 US 20130022487 A1 US20130022487 A1 US 20130022487A1 US 201113521878 A US201113521878 A US 201113521878A US 2013022487 A1 US2013022487 A1 US 2013022487A1
- Authority
- US
- United States
- Prior art keywords
- vane
- vane pump
- pump
- housing body
- cover
- 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.)
- Abandoned
Links
Images
Classifications
-
- 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
-
- 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
- F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/001—Radial sealings for working fluid
- F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear pumps
Definitions
- the invention relates to a vane pump with a pump housing having a sleeve-shaped housing body, a bottom, and a cover, with the bottom and the cover axially closing the housing body, a rotor arranged eccentrically in the housing body and rotatably mounted in the bottom and cover, and one or more vanes which are mounted in the rotor for movement in axial direction.
- Vane pumps are known in many configurations. They are intended to seal gaseous media, to produce a negative pressure, or to transport gaseous or liquid media.
- a rotor is eccentrically arranged in the pump housing and has several vanes which are movably mounted so as to form between the vanes and between the rotor and the inner circumferential surface of the pump housing forming the stator, work spaces that have continuously changing volumes, i.e. expand and contract.
- the vanes are hurled outwards by the centrifugal force when the rotor rotates and sweep on the inner circumferential surface of the pump housing. As a result, the respective work space is sealed against the neighboring work spaces.
- the sealing action is assisted by wetting the surface of the components with lubricating oil.
- This lubricating oil also serves to reduce frictional forces so that the power loss of the pump is reduced. It is considered disadvantageous however that the transported fluid becomes necessarily wetted with lubricant and possibly has to be cleaned before being either used again or released into the atmosphere. Moreover, lubricant is consumed.
- the invention is based on the object to provide a vane pump which exhibits a lesser consumption of lubricant and in which the transported fluid is free of lubricant.
- this object is attained by a vane pump of the afore-described type by providing each vane at its axial end faces with bearing pins which engage in the bottom and the cover.
- the vane is not only mounted in the rotor for movement in radial direction so as to be able to oscillate in radial direction in relation to the rotor in accordance with the eccentric disposition of the rotor in the pump housing but also has bearing pins which engage in the bottom and the cover so that the vane can be deliberately controlled via these bearing pins. This is possible because the bottom and the cover are stationary and the bearing pins revolve in the bottom and the cover.
- the bottom and the cover have each a guideway for the bearing pins, with the bearing pins engaging in the guideways free of clearance or at slight clearance.
- the guideways are configured as groove, with the guideway exhibiting in particular a circular shape and lying in coaxial relationship to the inner circumferential surface of the housing body.
- the bearing pin is formed by a bolt mounted in the vane.
- the vane can be produced as usually, for example as injection-molded part or a die-case part, which needs only to be provided with the bearing pin. The latter may, for example, be injected directly into the injection-molded part.
- the free end of the bolt which end extends axially beyond the vane, supports a bearing, in particular a deep groove ball bearing.
- This deep groove ball bearing engages in the guideway and revolves in the bottom and the cover.
- the deep groove ball bearing is self-lubricating so that the need for an additional lubrication can be omitted.
- An essential feature of the invention resides in the presence of a gap between the radially outer vane tip and the inner circumferential surface of the housing body. This gap ensures that no frictional forces can establish between vane and housing body so that the vane is not exposed to wear on one hand, and the power loss of the pump is small on the other hand.
- the gap lies hereby at a range between 5 ⁇ m to 100 ⁇ m, and in particular between 10 ⁇ m and 50 ⁇ m.
- a sealing bar may be arranged on the radially outer vane tip.
- a groove extends in the radially outer vane tip in length direction of the vane and receives a sealing bar which projects beyond the vane tip.
- This sealing bar is floatingly supported in the groove so as to be able to execute relative movements in relation to the vane. When the rotor rotates, this sealing bar is forced or hurled against the inner circumferential surface of the housing body to thereby completely seal the work space. As the weight of the sealing bar is virtually negligible in comparison to the vane, the frictional forces are minimal.
- the sealing bar is made of metal, especially light metal or of a plastic which is fiber-reinforced for example.
- Such sealing bars have a slight weight on one hand and are sufficiently wear-resistant on the other hand.
- the vane pump according to the invention is operated in the absence of lubricant, i.e. running dry.
- This has the advantage that the transported medium is not contaminated so that the need for oil separator or the like at the outlet of the vane pump is eliminated.
- FIG. 1 a perspective view of the vane pump according to the invention
- FIG. 2 a side view in direction of the arrow II according to FIG. 1 ;
- FIG. 3 a perspective view according to FIG. 1 with detached housing cover
- FIG. 4 a section IV-IV according to FIG. 2 ;
- FIG. 5 a section V-V according to FIG. 4 ;
- FIG. 6 a section VI-VI according to FIG. 4 ;
- FIG. 7 a perspective view of a vane, cut open in part.
- FIG. 1 depicts a vane pump 10 which essentially includes a housing body 12 with cooling fins 14 , a bottom 16 with fastening brackets 18 , and a cover 20 with a fastening bracket 22 . Further shown are outlet and inlet openings 24 and 26 in the cover 20 as well as a flange 28 for attachment of a (not shown) drive which is connected to a driveshaft 30 .
- the housing body 12 has a substantially sleeve-like configuration in surrounding relationship to a rotor 32 which is mounted eccentrically in the housing body 12 and from which the driveshaft 30 projects out.
- the rotor 32 is substantially cylindrical in shape and provided with receiving slots 34 which extend in axial direction and have open edges at the circumference of the rotor 32 and the end faces thereof.
- the rotor 32 is provided with a multiplicity of axial bores 36 and 38 , with the bores 38 lying at the base of the receiving slots 34 and the bores 36 lying between the receiving slots 34 . These bores 36 and 38 reduce the weight of the rotor 32 and thus its moment of inertia.
- Vanes 40 are located in the receiving slots 34 and mounted in such a way as to be able to move in radial direction. Two adjacent vanes 40 , the circumferential surface 42 of the rotor 32 , and the inner circumferential surface 44 of the housing body 12 form each a work space 46 in which the trapped fluid is transported from the inlet opening 26 to the outlet opening 24 .
- the inlet opening 26 and the outlet opening 24 are connected via overflow channels 48 in the housing body 12 having crescent-shaped inlets and outlets 50 and 52 feeding into the work spaces 46 .
- FIG. 5 clearly shows that the work spaces 46 permanently expand and contract and that the vanes 40 project more or less far into the receiving slots 34 of the rotor 32 .
- FIG. 7 shows such a vane 40 which is provided on both its end faces 54 with bearing pins 56 that are formed by bolts 58 which engage in the vanes 40 and project beyond the end face 54 and which support a bearing 60 , for example a deep groove ball bearing 62 .
- the cover 20 has a guideway 66 configured in the shape of a groove 64 for guiding the deep groove ball bearing 62 .
- the groove 64 thus forms a forced control for the vanes 40 as the groove 64 lies coaxially to the inner circumferential surface of the housing body 12 and thus eccentrically to the rotor 32 and the driveshaft 30 thereof.
- the position of the guideway 66 and the radial extent of the vanes 40 as well as the position thereof in the rotor 32 are so dimensioned that the vane tip 68 ( FIG. 7 ) has a constant distance to the inner circumferential surface 44 of the housing body 12 in the range of 5 ⁇ m to 100 ⁇ m.
- the guideway 66 is thus situated such as to ensure this gap or distance to the inner circumferential surface 44 , with consideration that the vanes 40 although radially arranged in the rotor 32 are inclined to the orthogonal in relation to the housing body 12 , in particular the inner circumferential surface 44 thereof.
- This means that the inner circumferential surface 44 and/or the guideway 66 has or have a configuration which deviates from the circular shape as the gap is constantly of same size.
- the gap may also fluctuate within certain limits.
- FIG. 7 further shows that the vane tip 68 has a groove 70 which extends in length direction of the vane 40 and in which a sealing bar 72 is placed and slightly extends beyond the vane tip 68 .
- the sealing bar 72 floats in the groove 70 and is able to move especially in direction of the inner circumferential surface 44 of the housing body 12 .
- the sealing bar 72 has the task to bridge and seal the gap between the vane 40 and the inner circumferential surface 44 of the housing body 12 .
- the gap is effectively closed, in particular when the gap continuously changes, and it is ensured that the vane tip 68 does not touch the inner circumferential surface 44 of the housing body 12 .
- the sealing bar 72 is made of plastic in particular, the weight is low so that the frictional forces become negligibly small. Moreover, the sealing bar 72 can easily be exchanged.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The invention relates to a vane pump comprising a pump housing that has a sleeve-shaped housing body, a bottom, and a cover, with the bottom and cover axially closing the housing body. The vane pump also has a rotor, which lies eccentrically in the housing body and which is rotatably mounted in the bottom and the cover, and one or more vanes which are movably mounted in the rotor in an axial direction. Each vane has bearing pins on the axial end faces thereof, with the bearing pins engaging in the bottom and the cover.
Description
- The invention relates to a vane pump with a pump housing having a sleeve-shaped housing body, a bottom, and a cover, with the bottom and the cover axially closing the housing body, a rotor arranged eccentrically in the housing body and rotatably mounted in the bottom and cover, and one or more vanes which are mounted in the rotor for movement in axial direction.
- Vane pumps are known in many configurations. They are intended to seal gaseous media, to produce a negative pressure, or to transport gaseous or liquid media. In these vane pumps, a rotor is eccentrically arranged in the pump housing and has several vanes which are movably mounted so as to form between the vanes and between the rotor and the inner circumferential surface of the pump housing forming the stator, work spaces that have continuously changing volumes, i.e. expand and contract. The vanes are hurled outwards by the centrifugal force when the rotor rotates and sweep on the inner circumferential surface of the pump housing. As a result, the respective work space is sealed against the neighboring work spaces. The sealing action is assisted by wetting the surface of the components with lubricating oil. This lubricating oil also serves to reduce frictional forces so that the power loss of the pump is reduced. It is considered disadvantageous however that the transported fluid becomes necessarily wetted with lubricant and possibly has to be cleaned before being either used again or released into the atmosphere. Moreover, lubricant is consumed.
- The invention is based on the object to provide a vane pump which exhibits a lesser consumption of lubricant and in which the transported fluid is free of lubricant.
- In accordance with the invention, this object is attained by a vane pump of the afore-described type by providing each vane at its axial end faces with bearing pins which engage in the bottom and the cover.
- In the vane pump according to the invention, the vane is not only mounted in the rotor for movement in radial direction so as to be able to oscillate in radial direction in relation to the rotor in accordance with the eccentric disposition of the rotor in the pump housing but also has bearing pins which engage in the bottom and the cover so that the vane can be deliberately controlled via these bearing pins. This is possible because the bottom and the cover are stationary and the bearing pins revolve in the bottom and the cover.
- For that purpose, the bottom and the cover have each a guideway for the bearing pins, with the bearing pins engaging in the guideways free of clearance or at slight clearance. Preferably, the guideways are configured as groove, with the guideway exhibiting in particular a circular shape and lying in coaxial relationship to the inner circumferential surface of the housing body. As a result, the vanes always assume a defined position in relation to the inner circumferential surface of the housing body. This has the advantage that this position is assumed even when the rotor does not revolve. As a result, when the rotation speeds are low and thus the centrifugal force is also small, it is ensured that the vanes still assume a defined position so that optimum transport results are achieved, already when the rotation speeds are low. This is of advantage e.g. when starting a combustion engine and the vane pump operates as lubricant pump. In this case, the lubricant is transported already at the start of the engine and not when higher rotation speeds are involved.
- In a preferred exemplary embodiment, the bearing pin is formed by a bolt mounted in the vane. As a result, the vane can be produced as usually, for example as injection-molded part or a die-case part, which needs only to be provided with the bearing pin. The latter may, for example, be injected directly into the injection-molded part.
- According to a refinement, the free end of the bolt, which end extends axially beyond the vane, supports a bearing, in particular a deep groove ball bearing. This deep groove ball bearing engages in the guideway and revolves in the bottom and the cover. Preferably, the deep groove ball bearing is self-lubricating so that the need for an additional lubrication can be omitted.
- An essential feature of the invention resides in the presence of a gap between the radially outer vane tip and the inner circumferential surface of the housing body. This gap ensures that no frictional forces can establish between vane and housing body so that the vane is not exposed to wear on one hand, and the power loss of the pump is small on the other hand. The gap lies hereby at a range between 5 μm to 100 μm, and in particular between 10 μm and 50 μm.
- In the event a complete sealing is desired or required, a sealing bar may be arranged on the radially outer vane tip. In an exemplary embodiment, a groove extends in the radially outer vane tip in length direction of the vane and receives a sealing bar which projects beyond the vane tip. This sealing bar is floatingly supported in the groove so as to be able to execute relative movements in relation to the vane. When the rotor rotates, this sealing bar is forced or hurled against the inner circumferential surface of the housing body to thereby completely seal the work space. As the weight of the sealing bar is virtually negligible in comparison to the vane, the frictional forces are minimal.
- Preferably, the sealing bar is made of metal, especially light metal or of a plastic which is fiber-reinforced for example. Such sealing bars have a slight weight on one hand and are sufficiently wear-resistant on the other hand.
- Preferably, the vane pump according to the invention is operated in the absence of lubricant, i.e. running dry. This has the advantage that the transported medium is not contaminated so that the need for oil separator or the like at the outlet of the vane pump is eliminated.
- Further advantages, features and details of the invention are set forth in the sub-claims and the following description which describes in greater detail a particularly preferred exemplified embodiment with reference to the drawing. The features illustrated in the drawing and set forth in the description and the claims may be relevant individually or in any combination
- The drawing shows in:
-
FIG. 1 a perspective view of the vane pump according to the invention; -
FIG. 2 a side view in direction of the arrow II according toFIG. 1 ; -
FIG. 3 a perspective view according toFIG. 1 with detached housing cover; -
FIG. 4 a section IV-IV according toFIG. 2 ; -
FIG. 5 a section V-V according toFIG. 4 ; -
FIG. 6 a section VI-VI according toFIG. 4 ; and -
FIG. 7 a perspective view of a vane, cut open in part. -
FIG. 1 depicts avane pump 10 which essentially includes ahousing body 12 withcooling fins 14, abottom 16 withfastening brackets 18, and acover 20 with afastening bracket 22. Further shown are outlet andinlet openings cover 20 as well as aflange 28 for attachment of a (not shown) drive which is connected to adriveshaft 30. - As can be seen from
FIG. 3 , thehousing body 12 has a substantially sleeve-like configuration in surrounding relationship to arotor 32 which is mounted eccentrically in thehousing body 12 and from which thedriveshaft 30 projects out. Therotor 32 is substantially cylindrical in shape and provided with receivingslots 34 which extend in axial direction and have open edges at the circumference of therotor 32 and the end faces thereof. Moreover, therotor 32 is provided with a multiplicity ofaxial bores 36 and 38, with the bores 38 lying at the base of thereceiving slots 34 and thebores 36 lying between thereceiving slots 34. Thesebores 36 and 38 reduce the weight of therotor 32 and thus its moment of inertia. Vanes 40 are located in thereceiving slots 34 and mounted in such a way as to be able to move in radial direction. Twoadjacent vanes 40, thecircumferential surface 42 of therotor 32, and the innercircumferential surface 44 of thehousing body 12 form each awork space 46 in which the trapped fluid is transported from the inlet opening 26 to the outlet opening 24. - As can be seen from
FIG. 4 , the inlet opening 26 and the outlet opening 24 are connected viaoverflow channels 48 in thehousing body 12 having crescent-shaped inlets andoutlets work spaces 46. -
FIG. 5 clearly shows that thework spaces 46 permanently expand and contract and that thevanes 40 project more or less far into thereceiving slots 34 of therotor 32. -
FIG. 7 shows such avane 40 which is provided on both itsend faces 54 with bearing pins 56 that are formed by bolts 58 which engage in thevanes 40 and project beyond theend face 54 and which support a bearing 60, for example a deep groove ball bearing 62. - As can be seen from
FIG. 6 , thecover 20 has a guideway 66 configured in the shape of a groove 64 for guiding the deep groove ball bearing 62. The groove 64 thus forms a forced control for thevanes 40 as the groove 64 lies coaxially to the inner circumferential surface of thehousing body 12 and thus eccentrically to therotor 32 and thedriveshaft 30 thereof. The position of the guideway 66 and the radial extent of thevanes 40 as well as the position thereof in therotor 32 are so dimensioned that the vane tip 68 (FIG. 7 ) has a constant distance to the innercircumferential surface 44 of thehousing body 12 in the range of 5 μm to 100 μm. The guideway 66 is thus situated such as to ensure this gap or distance to the innercircumferential surface 44, with consideration that thevanes 40 although radially arranged in therotor 32 are inclined to the orthogonal in relation to thehousing body 12, in particular the innercircumferential surface 44 thereof. This means that the innercircumferential surface 44 and/or the guideway 66 has or have a configuration which deviates from the circular shape as the gap is constantly of same size. The gap may also fluctuate within certain limits. -
FIG. 7 further shows that thevane tip 68 has agroove 70 which extends in length direction of thevane 40 and in which a sealingbar 72 is placed and slightly extends beyond thevane tip 68. The sealingbar 72 floats in thegroove 70 and is able to move especially in direction of the innercircumferential surface 44 of thehousing body 12. The sealingbar 72 has the task to bridge and seal the gap between thevane 40 and the innercircumferential surface 44 of thehousing body 12. The gap is effectively closed, in particular when the gap continuously changes, and it is ensured that thevane tip 68 does not touch the innercircumferential surface 44 of thehousing body 12. As the sealingbar 72 is made of plastic in particular, the weight is low so that the frictional forces become negligibly small. Moreover, the sealingbar 72 can easily be exchanged.
Claims (18)
1-14. (canceled)
15. A vane pump, comprising:
a pump housing having a sleeve-shaped housing body, a bottom, and a cover, with the bottom and the cover axially closing the housing body;
a rotor arranged eccentrically in the housing body and rotatably mounted in the bottom and cover;
at least one vane mounted in the rotor for movement in a radial direction, said vane having axial end faces; and
bearing pins provided on the axial end faces of the vane and engaging in the bottom and the cover.
16. The vane pump of claim 15 , wherein each said bearing pin is formed by a bolt formed in the vane.
17. The vane pump of claim 16 , wherein the bolt has a free end which extends axially beyond the vane, and further comprising a bearing supported by the free end of the bolt.
18. The vane pump of claim 17 , wherein the bearing is a deep groove ball bearing.
19. The vane pump of claim 15 , wherein each of the bottom and the cover has a guideway for receiving the bearing pins.
20. The vane pump of claim 19 , wherein the guideway is configured as a groove.
21. The vane pump of claim 19 , wherein the guideway is configured as a circular track.
22. The vane pump of claim 19 , wherein the guideway lies in coaxial relationship to an inner circumferential surface of the housing body.
23. The vane pump of claim 15 , wherein the vane has a radially outer vane tip which defines a gap with an inner circumferential surface of the housing body.
24. The vane pump of claim 23 , wherein the gap has a size of 5 μm to 100 μm.
25. The vane pump of claim 23 , wherein the gap has a size of 10 λm to 50 μm.
26. The vane pump of claim 15 , wherein the vane has a radially outer vane tip which is formed with a groove extending in a length direction of the vane.
27. The vane pump of claim 26 , further comprising a sealing bar arranged in the groove and sized to extend beyond the vane tip.
28. The vane pump of claim 27 , wherein the sealing bar is floatingly supported in the groove.
29. The vane pump of claim 27 , wherein the sealing bar is made of metal or plastic.
30. The vane pump of claim 27 , wherein the sealing bar is made of light metal.
31. The vane pump of claim 15 , constructed in the form of a dry running pump.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010000947.4 | 2010-01-15 | ||
DE102010000947.4A DE102010000947B4 (en) | 2010-01-15 | 2010-01-15 | Vane pump |
PCT/EP2011/050069 WO2011086013A2 (en) | 2010-01-15 | 2011-01-04 | Vane pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130022487A1 true US20130022487A1 (en) | 2013-01-24 |
Family
ID=44304719
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/521,878 Abandoned US20130022487A1 (en) | 2010-01-15 | 2011-01-04 | Vane pump |
Country Status (6)
Country | Link |
---|---|
US (1) | US20130022487A1 (en) |
EP (1) | EP2524111A2 (en) |
KR (1) | KR20120112790A (en) |
CN (1) | CN102844525A (en) |
DE (1) | DE102010000947B4 (en) |
WO (1) | WO2011086013A2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017107228A1 (en) * | 2015-12-25 | 2017-06-29 | 常州市金坛翰广科技有限公司 | Rotary-vane vacuum pump |
CN108005900A (en) * | 2017-11-23 | 2018-05-08 | 陈永辉 | A kind of eccentric curve rotor arrangement |
US20200072215A1 (en) * | 2018-08-28 | 2020-03-05 | Pfeiffer Vacuum Gmbh | Rotary vane vacuum pump |
US11174863B2 (en) * | 2018-11-16 | 2021-11-16 | Lg Electronics Inc. | Vane rotary compressor |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITUB20159158A1 (en) * | 2015-12-23 | 2017-06-23 | Vhit Spa | Volumetric vane pump |
CN106640648A (en) * | 2017-01-13 | 2017-05-10 | 南通荣恒环保设备有限公司 | Rotary draught fan for limiting of wheels at roots of slip sheets |
CN107218213B (en) * | 2017-08-03 | 2018-10-26 | 太原科技大学 | Swing vane-type pump |
DE102017117988A1 (en) * | 2017-08-08 | 2019-02-14 | Kameliya Filipova Ganeva | Pneumatic or hydraulic device |
CN108590772A (en) * | 2018-03-20 | 2018-09-28 | 罗德凯 | A kind of anti-wear blade rotor mechanical structure improving mechanical efficiency |
CN108501915B (en) * | 2018-04-25 | 2021-02-02 | 罗德凯 | Blade type brake system |
KR102370499B1 (en) | 2020-03-25 | 2022-03-04 | 엘지전자 주식회사 | Rotary compressor |
KR102370523B1 (en) | 2020-03-25 | 2022-03-04 | 엘지전자 주식회사 | Rotary compressor |
KR102301479B1 (en) | 2020-03-27 | 2021-09-13 | 엘지전자 주식회사 | Rotary compressor |
KR102349747B1 (en) | 2020-05-22 | 2022-01-11 | 엘지전자 주식회사 | Rotary compressor |
KR102387189B1 (en) | 2020-05-22 | 2022-04-15 | 엘지전자 주식회사 | Rotary compressor |
KR102367895B1 (en) * | 2020-05-22 | 2022-02-25 | 엘지전자 주식회사 | Rotary compressor |
KR102378399B1 (en) | 2020-07-03 | 2022-03-24 | 엘지전자 주식회사 | Rotary compressor |
CN117212143B (en) * | 2023-10-31 | 2024-02-13 | 福力德泰克(上海)泵业有限公司 | Vane pump capable of inhibiting clearance backflow |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4212603A (en) * | 1978-08-18 | 1980-07-15 | Smolinski Ronald E | Rotary vane machine with cam follower retaining means |
US4799867A (en) * | 1986-11-21 | 1989-01-24 | Eagle Industry Co., Ltd. | Vane pump with brittle vanes and rough finished housing surface |
US4859163A (en) * | 1987-06-25 | 1989-08-22 | Steven Schuller Performance Inc. | Rotary pump having vanes guided by bearing blocks |
US4955985A (en) * | 1986-07-22 | 1990-09-11 | Eagle Industry Co., Ltd. | Vane pump with annular ring for engaging vanes and drive means in which the rotor drives the annular ring |
US5051078A (en) * | 1989-07-05 | 1991-09-24 | Lew Hyok S | Rotary pump-flowmeter |
US5087183A (en) * | 1990-06-07 | 1992-02-11 | Edwards Thomas C | Rotary vane machine with simplified anti-friction positive bi-axial vane motion control |
US5160252A (en) * | 1990-06-07 | 1992-11-03 | Edwards Thomas C | Rotary vane machines with anti-friction positive bi-axial vane motion controls |
US5181843A (en) * | 1992-01-14 | 1993-01-26 | Autocam Corporation | Internally constrained vane compressor |
US5242285A (en) * | 1989-12-12 | 1993-09-07 | Acd, Inc. | Cryogenic vane pump |
US7077098B2 (en) * | 2003-08-26 | 2006-07-18 | Shuba Yaroslav M | Vane-type piston, four-cycle multi-chamber rotary internal combustion engine |
US20070292297A1 (en) * | 2004-09-20 | 2007-12-20 | Ulrich Fromm | Vane Pump Consisting A Two-Part Stator |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3294454A (en) * | 1964-09-30 | 1966-12-27 | Eugene E Foerster | Reciprocating vane type rotary pump |
DE2742217A1 (en) * | 1977-09-20 | 1979-03-22 | Josef Bertrams | Hydraulic pump and motor acting on differential pressure - have single rotor working as motor and pump on opposite sides |
EP0048415A1 (en) * | 1980-09-11 | 1982-03-31 | RMC Rotary-Motor Company AG | Rotary-piston machine |
DE3108819A1 (en) * | 1981-03-09 | 1982-11-25 | Kommanditgesellschaft RMC Rotationsmaschinen GmbH + Co, 2000 Hamburg | Method for forming a compression chamber in a rotary piston engine |
DE8313036U1 (en) * | 1983-05-03 | 1985-09-26 | Kathmann, Peter B., Solothurn | Rotary piston machine |
EP0158064B1 (en) * | 1984-03-23 | 1989-12-27 | Volkswagen Aktiengesellschaft | Sealing for a positive-displacement machine for compressible fluids |
US6821099B2 (en) * | 2002-07-02 | 2004-11-23 | Tilia International, Inc. | Rotary pump |
-
2010
- 2010-01-15 DE DE102010000947.4A patent/DE102010000947B4/en not_active Expired - Fee Related
-
2011
- 2011-01-04 EP EP11700120A patent/EP2524111A2/en not_active Withdrawn
- 2011-01-04 US US13/521,878 patent/US20130022487A1/en not_active Abandoned
- 2011-01-04 WO PCT/EP2011/050069 patent/WO2011086013A2/en active Application Filing
- 2011-01-04 KR KR1020127021239A patent/KR20120112790A/en not_active Application Discontinuation
- 2011-01-04 CN CN2011800062816A patent/CN102844525A/en active Pending
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4212603A (en) * | 1978-08-18 | 1980-07-15 | Smolinski Ronald E | Rotary vane machine with cam follower retaining means |
US4955985A (en) * | 1986-07-22 | 1990-09-11 | Eagle Industry Co., Ltd. | Vane pump with annular ring for engaging vanes and drive means in which the rotor drives the annular ring |
US5044910A (en) * | 1986-07-22 | 1991-09-03 | Eagle Industry Co., Ltd. | Vane pump with rotatable drive means for vanes |
US4799867A (en) * | 1986-11-21 | 1989-01-24 | Eagle Industry Co., Ltd. | Vane pump with brittle vanes and rough finished housing surface |
US4859163A (en) * | 1987-06-25 | 1989-08-22 | Steven Schuller Performance Inc. | Rotary pump having vanes guided by bearing blocks |
US5051078A (en) * | 1989-07-05 | 1991-09-24 | Lew Hyok S | Rotary pump-flowmeter |
US5242285A (en) * | 1989-12-12 | 1993-09-07 | Acd, Inc. | Cryogenic vane pump |
US5087183A (en) * | 1990-06-07 | 1992-02-11 | Edwards Thomas C | Rotary vane machine with simplified anti-friction positive bi-axial vane motion control |
US5160252A (en) * | 1990-06-07 | 1992-11-03 | Edwards Thomas C | Rotary vane machines with anti-friction positive bi-axial vane motion controls |
US5181843A (en) * | 1992-01-14 | 1993-01-26 | Autocam Corporation | Internally constrained vane compressor |
US7077098B2 (en) * | 2003-08-26 | 2006-07-18 | Shuba Yaroslav M | Vane-type piston, four-cycle multi-chamber rotary internal combustion engine |
US20070292297A1 (en) * | 2004-09-20 | 2007-12-20 | Ulrich Fromm | Vane Pump Consisting A Two-Part Stator |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017107228A1 (en) * | 2015-12-25 | 2017-06-29 | 常州市金坛翰广科技有限公司 | Rotary-vane vacuum pump |
CN108005900A (en) * | 2017-11-23 | 2018-05-08 | 陈永辉 | A kind of eccentric curve rotor arrangement |
US20200072215A1 (en) * | 2018-08-28 | 2020-03-05 | Pfeiffer Vacuum Gmbh | Rotary vane vacuum pump |
US11174863B2 (en) * | 2018-11-16 | 2021-11-16 | Lg Electronics Inc. | Vane rotary compressor |
US11619230B2 (en) | 2018-11-16 | 2023-04-04 | Lg Electronics Inc. | Vane rotary compressor |
Also Published As
Publication number | Publication date |
---|---|
CN102844525A (en) | 2012-12-26 |
DE102010000947A1 (en) | 2011-07-21 |
EP2524111A2 (en) | 2012-11-21 |
KR20120112790A (en) | 2012-10-11 |
WO2011086013A2 (en) | 2011-07-21 |
WO2011086013A3 (en) | 2012-05-10 |
DE102010000947B4 (en) | 2015-09-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20130022487A1 (en) | Vane pump | |
US5022842A (en) | Vane pump with rotatable annular ring means to control vane extension | |
RU2374494C2 (en) | Blade pump | |
RU2741681C2 (en) | Blade air-driven engine | |
JP6014757B2 (en) | Blade type fluid transmission device | |
EP3103959B1 (en) | Scroll compressor | |
US7566211B2 (en) | Vane pump having vanes with a cutout portion | |
JP2011231675A (en) | Vane pump | |
JP2010127318A (en) | Lubricating structure of rotating shaft | |
KR101629899B1 (en) | Rotor and rotary fluid machine | |
JP2008128201A (en) | Vane pump | |
JP2004011421A (en) | Vane type vacuum pump | |
US6135742A (en) | Eccentric-type vane pump | |
US10443599B2 (en) | Mechanical vacuum pump for a motor vehicle | |
EP2242927B1 (en) | A displacement pump with a barrier against the fluid leakage | |
CN105604781B (en) | Hydraulic vane formula machine | |
JP5812722B2 (en) | Structure of lubricating device for internal combustion engine | |
JP5484717B2 (en) | Rotary airfoil oil rotary vacuum pump | |
JP2010101202A (en) | Variable displacement type compressor | |
US4558999A (en) | Vane type pump device | |
KR20200045426A (en) | Compressor | |
FI123314B (en) | A method for improving the operation of a reciprocating piston machine and an arrangement implementing the method | |
EP2103778A1 (en) | Rotary vane volumetric compressor or expender | |
JP2013064510A (en) | Floating bush bearing | |
EP2441915B1 (en) | Vane pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: JOMA-POLYTEC GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HELLE, TORSTEN;PYRDOK, BENJAMIN;SCHNEIDER, WILLI;AND OTHERS;SIGNING DATES FROM 20120703 TO 20120723;REEL/FRAME:028791/0005 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |