WO2016173801A1 - Pumpenvorrichtung - Google Patents
Pumpenvorrichtung Download PDFInfo
- Publication number
- WO2016173801A1 WO2016173801A1 PCT/EP2016/057158 EP2016057158W WO2016173801A1 WO 2016173801 A1 WO2016173801 A1 WO 2016173801A1 EP 2016057158 W EP2016057158 W EP 2016057158W WO 2016173801 A1 WO2016173801 A1 WO 2016173801A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- clamping member
- eccentric
- ring
- pump ring
- Prior art date
Links
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
- F01C5/00—Rotary-piston machines or engines with the working-chamber walls at least partly resiliently deformable
- F01C5/02—Rotary-piston machines or engines with the working-chamber walls at least partly resiliently deformable the resiliently-deformable wall being part of the inner member, e.g. of a rotary piston
-
- 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
- F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2610/00—Adding substances to exhaust gases
- F01N2610/14—Arrangements for the supply of substances, e.g. conduits
- F01N2610/1433—Pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
-
- 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
- F04C2210/00—Fluid
- F04C2210/10—Fluid working
- F04C2210/1083—Urea
-
- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
Definitions
- the invention relates to a pump device for pumping a liquid.
- a pump device or pump is understood here to mean a working machine which serves to convey liquids. This also applies
- Liquid-solid mixtures, pastes and low-gas liquids During operation of the pump device, the drive work is converted into the kinetic energy of the transported liquid.
- the pumping device shown is also referred to as orbital pump, rotary diaphragm pump or peristaltic pump.
- the pump device can be used to direct a liquid from a reservoir, for example a tank, into a desired environment, for example into an exhaust tract of an internal combustion engine.
- a pump device which is designed as an orbital pump, which has a pump housing with at least one inlet and at least one outlet, wherein on the
- an eccentric is arranged rotatably relative to the pump housing.
- an electric drive is provided between the eccentric and the pump housing.
- a deformable membrane which, together with the pump housing, delimits a delivery path from the at least one inlet to the at least one outlet and forms at least one seal of the delivery path.
- the at least one seal is displaceable by a movement of the eccentric for conveying along the conveying path.
- the publication WO 2012/126544 A1 describes a metering system for metering a liquid with a pump device, which via a with an electric motor drivable eccentric drive has.
- the pump device which has two directions of delivery, has a pump ring and a stationary ring, which is arranged relative to the pump ring and the eccentric drive so that between the stationary ring and the pump ring, a pump chamber is formed, which changes its shape upon rotation of the electric motor, to pump a liquid to be dispensed through the pump chamber.
- the document describes the operating principle of an orbital pump.
- a pump device for pumping a fluid comprising a pump housing which comprises an annular section, a pump ring which is deformable and an annular pump chamber at least
- first port and a second port which first port and which second port are respectively in fluid communication with the pump chamber, an eccentric which is rotatable relative to the pump housing and arranged in the pump device such that the eccentric in response to a current rotational position of the eccentric the
- the pump ring has at least one recess for receiving at least a portion of the clamping member, and wherein the recess is dimensioned such that at each rotational position of the eccentric at least partially a distance between the radially inner side of Clamping member and the pump ring is provided.
- Pump device comprises a clamping member which is in a recess of the
- Such a clamping member often has an opposite the pump ring increased rigidity, so that the clamping member in a compression of the pump ring changes a stretching or compression behavior of the pump ring partially. It is envisaged that the clamping member, while the eccentric rotates in the pump device and the pump ring deformed or
- the volume of the recess in the region between the radially inner side of the clamping member and the pump ring in dependence on the current rotational position of the eccentric change reversibly, so the recess there deform dynamically depending on the rotational position of the eccentric and so the compression behavior of the pump ring or affect its rigidity.
- the pump ring in the clamping member region is stronger in the second state compressed as in the first state.
- the volume of the changes Recess of the pump ring from the first state to the second (compressed) state, wherein the volume is preferably greater in the first state than in the second (compressed) state.
- the recess at each rotational position of the eccentric on the radially inner side of the clamping member has a predetermined minimum volume, and preferably the clamping member on the radially inner side at each rotational position of the eccentric at least partially no contact with the pump ring to the rotation of the eccentric to the area to facilitate the clamping member.
- the pump chamber is formed between the pump chamber and the annular portion.
- the pump chamber in which the fluid to be conveyed moves, between the pump ring and the annular
- Section of the pump device is formed so that a movement of the pump ring and a region-wise compression of the pump ring, the
- the clamping member is designed to statically press at least a part of the pump ring in the clamping member region between the first port and the second port against the annular portion and, as a result, fluid flow between the reduce or prevent the first port and the second port via the clamp member area.
- the pump ring carrier has at least one
- the pump ring carrier recess can influence the rigidity of the pump ring or of the entire system in the clamping member region, and this makes it possible for the eccentric to be better rotated past the clamping member region.
- the PumpenringtragrungsEnglishung may be configured such that the
- Clamping member engages at least at predetermined rotational positions of the eccentric in the at least one Pumpenringtrag Vogels Principleung, the
- Pump ring carrier recess thus provides space for the clamping member, in particular for a rotational position of the eccentric to the clamping member area, so that there is no collision between the clamping member and the pump ring carrier.
- the at least one pump ring support recess is rounded off at respective ends or corners. Investigations have shown that in the area of the pump ring bearing recess strong stresses can occur in the pump ring, and the risk of damage to the pump ring is caused by the
- the PumpenringicaausANSung is flattened or rounded in their inner corners, so that sharp edges are avoided and possibly also the risk of damage to the pump ring is reduced.
- the clamping member on both axial sides of the pump ring on Pump housing is supported. This allows a well-defined hold of the clamping member.
- the clamping member is chamfered at a first axial end on the radially outer side, to allow a gentle insertion of the clamping member into the recess.
- the clamping member is chamfered at a first axial end on the radially inner side in order to enable a successive alignment of the clamping member on the pump housing upon insertion of the clamping member.
- Influenced pump ring so that the clamping member by the chamfer and the pressure by the pumping ring initially slightly obliquely (in particular slightly towards the axis of rotation of the eccentric out) introduced into the recess and then sets up in the course of movement.
- the clamping member has a conical cross section, a curved outer surface and / or a radial outer surface. This reduces the risk of damaging the portion of the pump ring compressed by the clamping member.
- the clamping member is rounded in the region of respective contact points with the pump ring at respective radially outer sides and / or curved. By avoiding sharp corners and edges, the risk of damage to the pump ring is prevented, wherein the design of the clamping member is still freely selectable in other areas.
- the recess has a contour in the area radially inside the clamping member, which contour in each case has a bulge in both circumferential directions. As a result, the recess in this area in
- the contour of the recess in the area radially inside the clamping member has a greater maximum extent in the circumferential direction than the radial extent of the radially inner side of the clamping member. This makes it possible to increase the extent of the recess in the circumferential direction relative to the extension of the clamping member on the radially inner side and thus to increase the effect of the recess spatially.
- the contour of the recess in the area radially inside the clamping member has a greater maximum extent in the circumferential direction than the maximum extent of the clamping member in the circumferential direction. This can lead to an even greater spatial effect of the recess.
- the eccentric on its way along the pump ring in the clamping member area must be brought opposite. It can also be done considering the rigidity of the pump ring.
- the rigidity of the pump ring in the clamping member region can be selected to be lower than in the region outside of the clamping member region in order to facilitate positioning of the eccentric towards the clamping member region or to facilitate the rotation of the eccentric.
- Pump Ring predominantlyaussianung include a catch and snap mechanism by means of which the Pumpenringicaaus supraung is guided in selected positions of the eccentric outside of the clamping member portion in the clamping member portion.
- the pump device with a
- Exhaust gas treatment system of an internal combustion engine is in fluid communication.
- the exhaust treatment system may thus regulate catalytic combustion processes based on urea pumped by the pump device.
- FIG. 2 shows a side view of the pump device of FIG. 1, FIG.
- FIG. 3 is a sectional view of the pump device of Fig. 1,
- Fig. 4 in a sectional view of the pump device of Fig. 1 in a first
- Fig. 5 in a sectional view of the pump device of Fig. 1 in one
- Fig. 6 is a pump ring of the pump device of FIG. 1 on a
- FIG. 8 in a cross section a possible embodiment of a clamping member of
- FIG. 9 is a longitudinal section of the clamping member of Fig. 8,
- Fig. 1 1 in a three-dimensional view of a possible embodiment of the
- FIG. 12 is a plan view of the radially outer side of the clamping member of Fig. 1 1,
- Fig. 12, and 14 shows a section through the clamping member along the section line XIV-XIV of FIG. 12.
- Fig. 1 shows a sectional view of an embodiment of the presented
- Pumping device which is generally designated by the reference numeral 10 and designed as an orbital pump.
- the illustration shows a hydraulic housing 12, a pump ring 14, a pump ring support 16, an eccentric 18, a shaft 20, a drive 140, a first bearing 1 10, a second bearing 1 18, a bush 1 12, which also serves as a ring 1 12th can be referred to, a clamping member 1 14, which also as
- Separating chamber pin can be designated, an eccentric bearing 1 16, and a sealing ring 120, which can also be referred to as a sealing disc 120.
- the first bearing 1 10 is mounted in this embodiment as a floating bearing, and the second bearing 1 18 as a fixed bearing. This results in a good storage.
- eccentric bearing 1 16 a needle bearing can be used. This has a small extent in the radial direction. There are also other types of bearings such as bearings possible.
- the eccentric bearing 1 16 allows a low-friction transmission of forces between the rotating eccentric 18 and the rotatably mounted pump ring 14 and pump ring carrier 16th
- the hydraulic housing 12 includes an annular portion 22 and a first lateral portion 24, which may also be referred to as a pump cover, and a second lateral portion 26, which also serves as a motor flange or
- the two lateral sections 24, 26 are arranged opposite one another.
- the pump ring 14 is at least partially between the two side portions 24, 26 of the hydraulic housing 12.
- the annular portion 22 has a first collar 74 and a second collar 75th
- the drive 140 has a stator assembly 145 and a rotor assembly 146.
- the driver 140 is partially attached to a tubular portion 170 of the second lateral portion 26
- the pump housing 12 has a locking member 27 which is adapted to lock during insertion of the clamping member 1 14 in the pump housing 12 and the clamping member 1 14 axially secure. The insertion of the clamping member 1 14 can be done prior to assembly of the drive 140.
- the pump ring 14 is deformable and may be formed of an elastomeric material or other deformable material.
- FIG. 2 shows a side view of the pump device 10 of FIG. 1.
- FIG. 3 shows a cross-section through the pump device 10, as seen along the section line III - III of FIG. 2.
- a first port 51 and a second port 52 are provided, and these ports 51, 52 are in fluid communication with a pumping chamber 57 between the annular portion 22 of the
- Hydraulic housing and a running surface 46 of the pump ring is formed and annular in the illustration of FIG. 3 from the first port 51 in
- the pump chamber 57 is deactivated in the portion extending from the first port 51 counterclockwise to the second port 52 through the clamping member 1 14 by the
- Clamping member 1 14 14 presses the tread 46 of the pump ring 14 statically against the annular portion 22 of the hydraulic housing 12 and thereby prevents fluid flow through this section or at least greatly reduced.
- the area in which the clamping member 1 14 presses the running surface 46 of the pump ring 14 against the annular portion 22 is also referred to below as clamping member area 45.
- the operation of the orbital pump is described below with reference to FIGS. 1 and 3.
- the eccentric 18 sits on the shaft 20 and is driven by this.
- the shaft 20 In turn serves the drive 140, typically a motor or
- a controllable drive 140 is provided as drive 140.
- the shaft 20 is thereby rotated about its longitudinal axis 21, which defines an axial direction of the pump device 10.
- the eccentric 18 is thus also moved in a rotational movement about the longitudinal axis of the shaft 20.
- This movement of the eccentric 18 is transmitted via the bearing 1 16 and the pump ring carrier 16 to the pump ring 14.
- the pump ring carrier 16 and the pump ring 14 are rotationally fixed relative to the hydraulic housing 12, but they are locally moved closer to the annular portion 22 or further depending on the rotational position of the eccentric 18.
- the eccentric 18 in a direction indicated by an arrow 19 direction, in the example shown in the direction 9 o'clock, d. H. the area of the eccentric 18 with the greatest radial extent points in the direction of the arrow 19.
- the pump ring 14 is moved in this direction 19 and is pressed in the area 58 against the annular portion 22.
- the pump channel 57 is reduced in area 58 or completely blocked.
- the pump device 10 also works in the reverse direction by the direction of rotation of the eccentric 18 is reversed.
- Fig. 4 shows a cross section through the pump housing 12 of the pump device
- Zero position 19 are designated, the position of the zero position is basically arbitrary. In the selected illustration, the eccentric 18 in the direction 12 o'clock.
- the pump ring 14 has a recess 47, in which at least partially the clamping member 1 14 is provided.
- the recess 47 is so large in the exemplary embodiment that even at the position shown on the radially inner side 50 (see Fig. 6) of the clamping member 1 14 at least partially a distance 48 between the clamping member 1 14 and the pump ring 14 is provided.
- This distance 48 facilitates rotation of the eccentric 18 over the zero position, since the pump ring is easily deformed or compressible by the distance 48 generated by the recess 47, as if no such distance 48 would be provided. In other words, the mechanical resistance that opposes the eccentric 18 during its rotation is reduced by the recess 47.
- the fluid 13 is shown schematically at the port 51.
- the box 130 denotes the internal combustion engine with the exhaust gas treatment system.
- FIG. 5 shows a representation analogous to FIG. 4, the position of the eccentric 18 being rotated by 180 ° relative to the zero position of FIG. 4, so that the pump ring 14 is pulled away from the clamping member 14 in the clamping member region 45.
- Recess 47 is in an uncompressed state and has increased its volume from the state shown in Fig. 4.
- the distance 48 between the pump ring 14 and the clamping member 1 14 on the radially inner side of the clamping member 1 14 is greater than in Fig. 4. In this way, the rotation of the eccentric 1 16 is facilitated even in the illustrated rotational position, since the pump ring carrier 16 due the recess 47 with the distance 48 lighter from the clamping member area 45 can be pulled away as a connected on all sides with the clamping member 1 14 14 pump ring.
- the clamping member portion 45 is flexible, and the pump ring 14 can move well in the clamping member portion 45 with the rotation of the eccentric 18. Without the provided on the radially inner side of the clamping member 1 14 distance 48 between the clamping member 1 14 and the pump ring 14 of the pump ring 14 would be stiffer, since the pump ring 14 on the inside of the clamping member 1 14 would possibly be narrower in the radial direction than in the rest Area of the pump ring 14th
- Fig. 6 the pump ring 14 is shown, which is attached to the pump ring carrier 16 and fixed.
- the eccentric 18 is in the zero position, cf. Fig. 4.
- Pump ring carrier 16 has a Pumpenringicaaus principleung 49, which is highlighted by a thicker line.
- the pump ring carrier 16 thus has in
- Clamping member portion 45 has a smaller radial extent than at least partially in areas outside of the clamping member portion 45.
- the outer contour of the pump ring carrier outside of the clamping member portion 45 in the cross section shown is circular, but it can also be slightly oval, for example.
- the provision of the pump ring carrier recess 49 on the one hand has the advantage that a collision between the pump ring carrier 16 and the clamping member 1 14 is prevented.
- Pump ring carrier can be reduced over the entire circumference of the pump ring carrier 16 and a circular shape can be selected. Due to the greater distance of the pump ring carrier 16 from the annular portion 22, the power of the
- the zero position is advantageous because in the other positions the risk is greater that from the pressure difference between the outlet and inlet a moment is exerted on the eccentric, which leads to a rotation of the eccentric 18, if it is not by the shaft 20 (see. Fig. 1) is held.
- the recess 47 projects beyond the radially inner side of the clamping member 1 14 in both circumferential directions, so it is laterally larger than the clamping member on the radially inner side. This leads to a jump in stiffness of the pump ring 14 in these areas with the extensions, even before the clamping member 1 14 affects the rigidity of the pump ring in the clamping member portion 45. This affects as a snap effect, wherein the eccentric 18 in the
- Clamping member 1 14 has a contour, which in each case has a bulge 53 in both circumferential directions.
- the contour of the recess 47 in the region radially within the clamping member 1 14 has a larger maximum in the embodiment
- Extension in the circumferential direction has as the radial extent of the radially inner side 50 of the clamping member 1 14th
- the rigidity of the pump ring 14 may also or additionally by the
- Design of the Pumpenringehrnianung be influenced such that the rigidity in the region of the zero position is lower than in the regions located outside, so as to favor a rotational position of the eccentric 18 to the clamping member region 45.
- FIG. 7 shows a longitudinal section through the pump ring 14, that is to say a section along the axis 21 defined by the shaft 20 (see FIG.
- the pump ring 14 is held in position by the pump housing 12.
- the pump ring 14 has projections 28 and the pump housing 12 has cavities 60, wherein the projections 28 are pressed in the cavities 60 and so the
- Arrows 25 indicate how the pump housing 12 laterally supports the pump ring 14 so that it does not escape to the outside when the force 54 acts and thus reduces the pump performance.
- Fig. 8 is a cross section through the pump ring 14 and the clamping member 1 14 is shown.
- the clamping member 1 14 has a conical cross-section with a radial or generally a curved contact surface 1 15, so that upon introduction of the clamping member 1 14 in the pump ring 14, a destruction of the
- the maximum extent 142 of the radially inner side 50 of the clamping member 1 14 is located.
- Fig. 9 is a longitudinal section of the pump ring 14 and the Klennnnglieds 1 14 is shown. It can be clearly seen that the Klennnnglied 1 14 is chamfered at its axial end 1 17, as illustrated by arrows 59.
- the Klennnnglied 1 14 has at its first axial end 1 17 on the radially outer side of a chamfer 121, and this allows a material-friendly insertion of the clamping member 1 14 in the recess 47 of the pump ring 14, since this at
- the clamping member 1 14 has at its first axial end 1 17 on the radially inner side a chamfer 122, and this allows an oblique insertion of the clamping member 1 14 in the recess 47, wherein the clamping member 1 14 upon reaching the lateral portion 24 of the pump housing 12th through the chamfer 122 at least
- Section 24 is aligned like a ramp.
- FIG. 10 shows a longitudinal section through the pump housing 12 with the pump ring 14.
- the pump housing 12 has in the axial direction recesses 58 on the pump ring 14 surrounding parts to a movement of the
- Fig. 11 shows an embodiment of the clamping member 1 14.
- the clamping member 1 14 has a first axial end 1 17 and an oppositely disposed second axial end 124, wherein the axial direction is oriented to the direction of the shaft 20, see.
- the clamping member 1 14 has a groove-shaped recess 61, which simplifies the production of the clamping member 1 14.
- the chamfer 122 at the first axial end 1 17 on the radially inner side can be seen.
- FIG. 12 shows the radially outer side of the clamping member 14 with the chamfer 121.
- the clamping member has at the first axial end 1 17 in the respective circumferential direction, again relative to the shaft 20 of FIG. 1, a chamfer 123, in the plan view of FIG. 12 thus the clamping member 1 14 tapers to the first axial end 1 17th out. This facilitates the installation of the Klennnnglieds 1 14 in the assembly
- the chamfer 123 has in the embodiment an angle 133 of 23 ° to
- the angle 133 can be selected for example in the range of 20 ° to 26 °.
- a region 128 is marked on the first axial end 17 of the clamping member, and the clamping member preferably has no corners or "sharp" edges in this region 128. This can be achieved, for example, by rounding all edges in this region 128, for example by a radius of 0.5 mm or 0.7 mm.
- Fig. 13 shows in section the chamfers 121 and 122 at the first axial end, which is first introduced into the pumping ring 14 during assembly.
- the chamfer 121 has in the embodiment an angle 131 of 20 ° to
- the angle 131 can be selected for example in the range of 15 ° to 25 °.
- the chamfer 122 has in the embodiment an angle 132 of 20 ° to
- the angle 132 can be selected for example in the range of 15 ° to 25 °.
- Two support points 151, 152 are shown, and at these support points 151, 152 which lie on both axial sides of the pump ring 14, the clamping member 1 14 is supported on the pump housing 12.
- Fig. 14 shows the profile of the clamping member 1 14th
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Exhaust Gas After Treatment (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112016001964.5T DE112016001964A5 (de) | 2015-04-29 | 2016-03-31 | Pumpenvorrichtung |
CN201680022349.2A CN107532591B (zh) | 2015-04-29 | 2016-03-31 | 泵设备 |
US15/557,125 US10677059B2 (en) | 2015-04-29 | 2016-03-31 | Rotary pump with deformable pump ring |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015106613.0A DE102015106613A1 (de) | 2015-04-29 | 2015-04-29 | Pumpenvorrichtung |
DE102015106613.0 | 2015-04-29 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016173801A1 true WO2016173801A1 (de) | 2016-11-03 |
Family
ID=55661418
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2016/057158 WO2016173801A1 (de) | 2015-04-29 | 2016-03-31 | Pumpenvorrichtung |
Country Status (4)
Country | Link |
---|---|
US (1) | US10677059B2 (de) |
CN (1) | CN107532591B (de) |
DE (2) | DE102015106613A1 (de) |
WO (1) | WO2016173801A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019238351A1 (de) * | 2018-06-15 | 2019-12-19 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Pumpenvorrichtung sowie verfahren zum zumindest lokalen abdichten der pumpenvorrichtung |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017116468A1 (de) | 2017-07-21 | 2019-01-24 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Pumpenvorrichtung |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140017094A1 (en) * | 2011-03-19 | 2014-01-16 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Metering system |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB583578A (en) * | 1944-11-04 | 1946-12-20 | Kenneth Albert Braybrook | Improvements in rotary pumps and engines |
US2544628A (en) * | 1946-06-15 | 1951-03-06 | Coca Cola Co | Peristaltic pump |
US3408947A (en) * | 1967-03-14 | 1968-11-05 | William J Easton Jr | Diaphragm pump with single compression roller |
US4332534A (en) * | 1978-12-14 | 1982-06-01 | Erich Becker | Membrane pump with tiltable rolling piston pressing the membrane |
GB2495937A (en) * | 2011-10-25 | 2013-05-01 | Watson Marlow Ltd | Peristaltic pump head with auxiliary leakage chamber |
JP5861474B2 (ja) * | 2012-01-30 | 2016-02-16 | セイコーエプソン株式会社 | ポンプ装置 |
DE102013104245A1 (de) | 2013-04-26 | 2014-10-30 | Emitec Gesellschaft Für Emissionstechnologie Mbh | Verfahren zum Betrieb einer Vorrichtung zur dosierten Bereitstellung einer Flüssigkeit |
JP2017509825A (ja) | 2014-03-19 | 2017-04-06 | コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツングContinental Automotive GmbH | 液体、特に排ガス浄化添加剤の圧送用ポンプ |
US9889876B2 (en) | 2015-11-23 | 2018-02-13 | Ford Global Technologies, Llc | Methods and systems for controlling steering response and steering torque feedback based on steering position |
-
2015
- 2015-04-29 DE DE102015106613.0A patent/DE102015106613A1/de not_active Withdrawn
-
2016
- 2016-03-31 US US15/557,125 patent/US10677059B2/en active Active
- 2016-03-31 CN CN201680022349.2A patent/CN107532591B/zh active Active
- 2016-03-31 DE DE112016001964.5T patent/DE112016001964A5/de active Pending
- 2016-03-31 WO PCT/EP2016/057158 patent/WO2016173801A1/de active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140017094A1 (en) * | 2011-03-19 | 2014-01-16 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Metering system |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019238351A1 (de) * | 2018-06-15 | 2019-12-19 | Ebm-Papst St. Georgen Gmbh & Co. Kg | Pumpenvorrichtung sowie verfahren zum zumindest lokalen abdichten der pumpenvorrichtung |
Also Published As
Publication number | Publication date |
---|---|
CN107532591A (zh) | 2018-01-02 |
DE112016001964A5 (de) | 2018-02-08 |
DE102015106613A1 (de) | 2016-11-03 |
US10677059B2 (en) | 2020-06-09 |
CN107532591B (zh) | 2019-06-21 |
US20180045050A1 (en) | 2018-02-15 |
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