WO1997047885A1 - Bidirectionally operable, unidirectionally feeding pump - Google Patents
Bidirectionally operable, unidirectionally feeding pump Download PDFInfo
- Publication number
- WO1997047885A1 WO1997047885A1 PCT/DK1997/000255 DK9700255W WO9747885A1 WO 1997047885 A1 WO1997047885 A1 WO 1997047885A1 DK 9700255 W DK9700255 W DK 9700255W WO 9747885 A1 WO9747885 A1 WO 9747885A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear wheel
- ring
- shaft
- axis
- bearing unit
- 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
-
- 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
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Definitions
- the invention concerns a bidirectionally operable, unidi ⁇ rectionally feeding pump comprising a housing with an inlet and an outlet, an internally toothed ring having a ring axis, and an externally toothed gear wheel having a gear wheel axis, the gear wheel being arranged inside and mesh ⁇ ing with the ring, a cylindrical bore being provided in the gear wheel coaxially with the gear wheel axis, a bearing unit being arranged in the cylindrical bore for rotatable bedding of the gear wheel with respect to a rotation axis arranged eccentrically in relation to the ring axis, the bearing unit being pivotable around the gear wheel axis; and with a limiter for limiting the pivotation of the bear- mg unit to substantially 180 degrees.
- One em ⁇ bodiment comprises a housing with a shaft.
- An outer inter ⁇ nally toothed gear wheel is fixed to the housing and an inner externally toothed gear wheel is fixed to the shaft.
- the shaft comprises a first section and a second section.
- the second section has a centre, which is displaced by an eccentricity in relation to a centre of the first section.
- the centre of the first section is arranged in a rotation axis for the shaft. On shaft rotation the inner gear wheel will make an orbiting movement around the rotation axis.
- the pump described in this document has one con ⁇ siderable disadvantage. It requires starting of the shaft with a fixed rotation direction, either clockwise or anti ⁇ clockwise. If the shaft starts in the opposite direction of the one fixed, the pump will work oppositely. Small pumps driven by small motors may experience that the motor starts the shaft in a random direction, either clockwise or anti- clockwise. This is not critical for small centrifugal pumps, ordinarily known from domestic appliances. However, if these small motors are used together with gear wheel pumps, special means are required to ensure the pump func ⁇ tion.
- EP 0 486 164 Al describes a bidirectionally drivable gero- tor pump, which comprises a lobed annulus containing a lobed rotor journalled on a cylindrical boss, which is free to turn on an eccentric pin between two positions.
- the pump is driven by a shaft, which drives the lobed annulus and by meshing with the rotor, it rotates around the pin.
- the pressure difference between the one side of the pump and the other due to the direction of turning causes the boss to rotate between fixed positions. In this way the inlet and outlet ports have a fixed position independent of rota- tional direction of the drive shaft, causing the motor to have unidirectional feed.
- the purpose of the invention is to provide a pump with small frictional power loss and small starting torque, where only simple means are required to ensure unidirec ⁇ tional pumping independently of the rotation direction of the driving shaft.
- This task can be solved by means of a pump as described in the introduction, m that the ring is fixed m relation to the housing, and that the pump comprises driving means for driving the inner gear wheel into an orbiting movement within and in relation to the r ng to create between gear wheel and ring a number of expanding chambers and a number of contracting chambers, a commutator plate being arranged next to gear wheel and ring in a space m the housing, connected m a way that the commutator plate rotates at the speed of the orbiting motion around the ring axis, and that the commutator plate has channels connecting the expanding chambers with the inlet and the contracting chambers with the outlet.
- the driving means may be a rotating shaft having within the cylindrical bore of the gear wheel a semicircular cross section with a first plane surface co-operating with a second plane surface on the bearing unit also having a semicircular cross section, such that the plane surface of the bearing unit bears against the plane surface of the shaft in a first position during clockwise shaft rotation, whereas the plane surface of the plane unit bears m a second position against the plane surface of the shaft during anticlockwise shaft rotation.
- the torque required will be limited to a torque corresponding to a switching of the semicircular bearing unit from a first position to a second position. Only when the bearing unit has moved to a different position will the pump start displacement of a medium to be pumped. During the switching from the first position to the second position the motor reaches a rotation torque, which is able to overcome the starting torque of the pump.
- the required starting torque may be higher than the torque which the motor is able to supply.
- Many inexpensive motors will automatically turn the rotation direction and try to start in the opposite direc ⁇ tion. The required starting torque will then, as mentioned above, be limited. Thus it is possible to use smaller and less expensive motors for the pump operation.
- the cylindrical bore in the gear can have a first diameter D and the shaft can have a second diameter d and the ring axis is merging with the rotation centre of the shaft, the gear wheel axis during operation being displaced by an eccentricity e in relation to the rotation centre of the shaft. This enables displacement of the gear wheel by the eccentricity e in two opposite directions in relation to a neutral position.
- the diameter D of the cylindrical bore in the gear wheel may be at least the shaft diameter d plus two times the eccentricity e. This gives a simple dimensioning of shaft and cylindrical bore.
- the inlet can lead to a centrally arranged opening in a side plate connected via a first channel in the commutator plate to the expanding chambers between the ring and the gear wheel, also the contracting chambers might be con ⁇ nected to the outlet via a second channel in the commutator plate.
- the inlet flow communication is inde ⁇ pendent of the rotional position of the commutator plate.
- the second channel can comprise a cut-out in the commutator plate and a ring-shaped channel encircling the commutator plate and communicating with the cut-out, as set forth in claim 6.
- the ring-shaped channel is always in fluid commu ⁇ nication with the outlet independent of the position of the commutator plate.
- the second channel can communicate with the outlet through an eccentric bore in a side plate of the pump.
- the first channel can comprise a second cut-out in the commutator plate.
- the second cut-out makes a fluid communi- cation from a central bore in the side plate to the expand ⁇ ing chambers.
- the inlet and the outlet communicate with the channels via the driving shaft. This causes that the shaft is both the driving element of the pump and forms the basis of an inlet channel and/or an outlet channel.
- the rotation of the gear wheel in relation to the ring may take place on a rotation of shaft and gear wheel, while the ring stands still.
- the rotation of the gear wheel in rela- tion to the ring may be caused by a rotation of the ring during standstill of shaft and gear wheel.
- the pump and the motor driving the pump be parts of a complete unit, in which the motor can be an electromotor, and motor and pump have a common flange containing means for sealing along a common axis, and the flange may contain a common bearing.
- the ring might be part of the pump housing.
- the ring will stand still in relation to the side walls of the pump. Thus friction between the ring and the side walls will be elimi ⁇ nated. Friction between ring and pump housing, a common fact in a gerotor machine, is also eliminated.
- FIG. 1 A schematic view of a pump embodiment according to the invention in a resting position for mounting
- FIG. 2 A schematic view of a pump embodiment in a posi ⁇ tion for switching from mounting position to a first operating situation
- FIG. 3 A schematic view of the pump embodiment in the first operating position
- FIG. 4 A schematic view of the pump embodiment in a position for switching from the first operating position to a second operating position
- Fig. 5 A schematic view of the pump embodiment in the second operating position
- FIG. 6 A first detailed drawing of a preferred pump embodiment according to the invention
- Fig. 7 A second detailed drawing of the preferred pump embodiment according to the invention
- Fig. 1 shows an embodiment of a pump according to the in ⁇ vention in a position for mounting.
- the figure shows an externally toothed gear wheel 1, 2, an internally toothed ring 3,4, a shaft 5 and a bearing unit 6.
- the shaft 5 ex- tends into a cylindrical bore 7 in the gear wheel 1.
- the shaft 5 has a plane surface 8, being plane in the shown embodiment.
- the shaft has a diameter d, and the cylindrical bore has a diameter D.
- the bearing unit 6 is arranged in the bore 7 in the gear wheel 1, and also has a semicircular cross section t 6 .
- the cross section t 6 of the bearing unit 6 is approximately half as big as the diameter of the hole 7 in the gear wheel 1.
- the bearing unit 6 has a plane surface 9, being plane in the shown embodiment.
- the shaft 5 has a rotation axis A displaced by an eccentricity e in relation to a centre C of the bore 7 in the gear wheel 1.
- FIG. 2 shows a switching from the mounting position in fig. 1 to a first operating position (see fig. 3) .
- the shaft 5 has started anticlock ⁇ wise rotation and has rotated by an angle rotation ⁇ .
- a first edge of the plane surface 8 of the shaft 5 bears against the plane surface 9 of the bearing unit 6.
- Fig. 3 shows a first operating position for the pump ac ⁇ cording to the invention.
- the shaft 5 has rotated one angle rotation ⁇ anticlockwise in relation to the position shown in fig. 1.
- the angle ⁇ is approximately 90°.
- One rotation of the shaft 5 has brought along the bearing unit 6, and the whole plane bearing surface 8 of the shaft 5 now bears in a first position against the plane bearing surface 9 of the bearing unit 6.
- the shaft rotation ⁇ of about 90° has not yet made the gear wheel 1 rotate. Only a further anticlockwise rotation of the shaft 5 will make the gear wheel 1 rotate.
- the shaft 5 and the bearing unit 6 have thus already started rotating, when the gear wheel 1 starts rotating.
- the shaft has made a rotation of 90° at a low torque. This position will remain unchanged during operation.
- Fig. 4 shows a switching from the first operating position shown in fig. 3 to a second operating position (see fig. 5) .
- the shaft 5 has started clockwise rotation and has rotated one angle rotation ⁇ .
- a second edge 11 of the plane surface 8 of the shaft 5 bears against the plane surface 9 of the bearing unit 6.
- the angle ⁇ is 90°.
- Fig. 5 shows a second operating position for the pump ac ⁇ cording to the invention.
- the shaft 5 has rotated one angle rotation ⁇ clockwise in relation to the position shown in fig. 3.
- the angle ⁇ is 180°.
- the shaft 5 has brought along the bearing unit 6, and the whole plane surface 8 of the shaft 5 now bears in a different position against the plane surface 9 of the bearing unit 6.
- the switching shown in fig. 4 from a first operating posi ⁇ tion to a second operating position will take place, if the shaft 5 of the pump according to the invention starts ro ⁇ tating in a direction, which is opposite to the direction in a previous, first operating situation.
- the switching from the first operating position to the second operating position depends on a distance between the plane surface 8 of the shaft 5 and the plane surface 9 of the bearing unit 6 in a position, where the plane surfaces 8, 9 are paral ⁇ lel, as shown in fig. 1.
- the bearing unit 6 has a cross section t 6 , which is half the diameter ti of the bore 7, and where the shaft has a semi ⁇ circular cross section, the distance between the plane surface 8 of the shaft 5 and the plane surface 9 of the bearing unit 6 is equal to the eccentricity e between the rotation axis A of the shaft 5 and the centre C of the bore 7.
- Fig. 6 and 7 show two different sections, at right angles to each other, of a possible embodiment of the pump. It comprises a housing 12 having a suction pipe branch 17 and a pressure pipe branch 19.
- the housing comprises a side plate 14 to which the ring 3 is fixed, and inside the ring 3, also bearing on the side plate 14, the gear wheel 1 is arranged.
- the gear wheel 1 has a cylindrical bore 7, partly filled by the semicircular bearing unit 6, and by a shaft 5 arranged in a bore in the side wall 14.
- the gear wheel 1 and the ring 3 are supported by a commutator plate 20 driven by the shaft 5.
- a circular pas ⁇ sage 31 extends around the commutator plate 20 and is con ⁇ nected with a recess 22 in the commutator plate.
- the commutator plate 20 also comprises a recess 21, from which two channels 32, 33 form the connection to a third recess in the commutator plate 20 for admission of the semicircular end of the shaft 5. From the commutator plate centre through a side plate 13 there is a bore 25 having connection to the suction pipe branch 17. A spacer 30 having the same thickness as the ring 3 and the gear wheel 1 is also arranged between the side plates 13 and 14. A spacer 29 with the same thickness as the commuta ⁇ tor plate 20 is also available. Together with the spacers 30 and 29 the side plates 13 and 14 are joined by the bolts 15 and 28 to one unit. Sealmgs m the shape of O-rings 27 are available around the flow connections 23, 25 and 24, 26 between the side plate 13 and the housing 12.
- the pump 12 has a suction pipe branch 17 from which a suction connection 23 forms fluid communication through an opening 25 in the side plate 13 to a central recess m the side plate 13 for admission of the extension of the rotating shaft 5.
- a suction connection 23 forms fluid communication through an opening 25 in the side plate 13 to a central recess m the side plate 13 for admission of the extension of the rotating shaft 5.
- From the recess channels 32, 33 in the commutator plate 20 are connected with the recess 21 m the commutator plate 20.
- From the recess 21 there is a fluid connection to the expanding volume between the orbit ⁇ ing gear wheel 1 and the stationary ring 3.
- the recess 21 will remain across the expanding cham ⁇ bers between gear wheel 1 and ring 3.
- a medium transport will take place between the orbiting gear wheel 1 and the stationary ring 3 to the contracting chamber, from which an additional recess 22 forms the pres ⁇ sure connection from the contracting chamber to the ring channel 31.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU31656/97A AU3165697A (en) | 1996-06-14 | 1997-06-12 | Bidirectionally operable, unidirectionally feeding pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DK0663/96 | 1996-06-14 | ||
DK66396A DK66396A (en) | 1996-06-14 | 1996-06-14 | Pump with device for switching between a first operating position and a second operating position |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997047885A1 true WO1997047885A1 (en) | 1997-12-18 |
Family
ID=8096120
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DK1997/000255 WO1997047885A1 (en) | 1996-06-14 | 1997-06-12 | Bidirectionally operable, unidirectionally feeding pump |
Country Status (3)
Country | Link |
---|---|
AU (1) | AU3165697A (en) |
DK (1) | DK66396A (en) |
WO (1) | WO1997047885A1 (en) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2871831A (en) * | 1959-02-03 | Internal gear machines | ||
US3561893A (en) * | 1967-12-14 | 1971-02-09 | Danfoss As | Hydrostatic control equipment' partic-ularly for steering systems |
DE1703346A1 (en) * | 1967-05-04 | 1972-03-09 | Reliance Electric & Eng Co | Gear pump or motor |
EP0098682A1 (en) * | 1982-04-07 | 1984-01-18 | Sumitomo Heavy Industries, Ltd | Planetary rotation machine |
-
1996
- 1996-06-14 DK DK66396A patent/DK66396A/en not_active Application Discontinuation
-
1997
- 1997-06-12 WO PCT/DK1997/000255 patent/WO1997047885A1/en active Application Filing
- 1997-06-12 AU AU31656/97A patent/AU3165697A/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2871831A (en) * | 1959-02-03 | Internal gear machines | ||
DE1703346A1 (en) * | 1967-05-04 | 1972-03-09 | Reliance Electric & Eng Co | Gear pump or motor |
US3561893A (en) * | 1967-12-14 | 1971-02-09 | Danfoss As | Hydrostatic control equipment' partic-ularly for steering systems |
EP0098682A1 (en) * | 1982-04-07 | 1984-01-18 | Sumitomo Heavy Industries, Ltd | Planetary rotation machine |
Also Published As
Publication number | Publication date |
---|---|
DK66396A (en) | 1997-09-22 |
AU3165697A (en) | 1998-01-07 |
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