WO2001016465A1 - Pump - Google Patents
Pump Download PDFInfo
- Publication number
- WO2001016465A1 WO2001016465A1 PCT/US2000/020317 US0020317W WO0116465A1 WO 2001016465 A1 WO2001016465 A1 WO 2001016465A1 US 0020317 W US0020317 W US 0020317W WO 0116465 A1 WO0116465 A1 WO 0116465A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- housing
- driven
- pump
- input shaft
- 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
- 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
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
-
- 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
- F01C21/02—Arrangements of bearings
-
- 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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for rotary-piston 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
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
Definitions
- the present invention relates to a pump such as a hydraulic pump, and particularly to a pump that maintains balanced axial forces on the pumping mechanism, even in the event of high inlet and outlet pump pressures.
- the hydraulic system disclosed in Tieben U.S. Patent No. 5,916,139 includes a pump, an actuator and a reservoir. In one mode of operation, the pump inlet is connected to the reservoir and the pump outlet is connected to the actuator. In another mode of operation, the pump inlet is connected to the actuator and the pump outlet is connected to the reservoir.
- This system encounters relatively high fluid pressures at both the pump inlet and the pump outlet. As explained in the Tieben patent, such pressures can result in undesired axial loads on the pumping mechanism, due to the high internal pressure of the pump.
- the pump disclosed in the Tieben patent overcomes this potential problem by providing high-pressure seals at both ends of the driven shaft of the pump. In this way, hydraulic axial forces on the driven shaft are balanced, and friction and associated wear are reduced.
- the present invention is directed to an improved pump that is well- suited for use in applications having high internal pump pressures and that overcomes the potential disadvantages described above.
- the preferred embodiment described below includes a pump mechanism having a driven shaft.
- the driven shaft is connected to an input shaft of the pump via a flexible coupling such as a splined coupling.
- a housing is disposed around the driven shaft, and this housing supports both the driven shaft and the input shaft for rotation.
- a high-pressure seal such as a mechanical seal is disposed between the housing and the input shaft, and a thrust bearing is disposed between the housing and the input shaft.
- the flexible coupling transmits fluid pressure within the housing to the outer end of the driven shaft. In this way, fluid pressure on the outer end of the driven shaft tends to balance fluid pressure on the inner end of the driven shaft, thereby reducing or eliminating asymmetrical axial loads.
- Figure 1 is a cross-sectional view of a pump that incorporates a preferred embodiment of this invention.
- Figure 2 is a cross-sectional view taken along line 2-2 of Figure 1.
- Figure 3 is an enlarged view of portions of the input shaft, the mechanical seal, and the thrust bearings of Figure 1.
- Figures 1 and 2 show respective cross- sectional views of a pump 10 that includes a pump mechanism 12.
- the pump mechanism 12 includes a gear set comprising a driven gear 14 mounted on a driven gear shaft 16 having an inner end 18 and an outer end 20.
- the driven gear 14 is in meshing engagement with a follower gear 22 that is mounted on a follower gear shaft 24 having an inner end 26 and an outer end 28.
- the pump 10 includes a housing 30 having a first portion 32 that defines an inlet passage 34 and an outlet passage 36 in fluid communication with a gear chamber 38.
- the gears 14, 22 are mounted for rotation in the gear chamber 38 by means of bushings 40 that receive and position the shafts 16, 24 ( Figure 1 ).
- the bushings 40 are held in place by wear plates 42 positioned adjacent to inner retainer plates 44. Also provided is an insert 46 that is held in place by an outer retainer plate 48.
- the inner retainer plates 44 and the wear plates 42 are conventionally used in gear pumps, and are well known to those skilled in the art.
- the wear plates 42 may for example be formed of brass, and the inner retainer plates 44 may be formed of steel.
- the pump 10 also includes an input shaft 50 having an inner end 52 and an outer end 54.
- the inner end 52 forms a hub 56, and the hub 56 supports a radially extending flange 58.
- the outer end 20 of the driven gear shaft 16 defines a first splined surface
- the hub 56 defines a second splined surface shaped to receive and mesh with the first splined surface.
- the splined surfaces of the driven gear shaft 16 and the input shaft 50 form a flexible coupling between the two shafts.
- the driven gear shaft 16 forms a shoulder 60 between the driven gear 14 and the outer end 20.
- the housing 30 also includes a second portion 64 that supports the input shaft 50 for rotation. Radial bearings 70 are mounted between the input shaft 50 and the second portion 64 of the housing 30.
- a thrust bearing 72 is mounted between the flange 58 and the second portion 64 of the housing 30.
- a high pressure seal such as a mechanical seal 74 is mounted between the input shaft 50 and the second portion 64 of the housing 30.
- Figure 3 provides an enlarged view of the mechanical seal 74 of Figure 1.
- the seal 74 includes a retainer 92 sealed to the second portion 64 of the housing 30 (not shown in Figure 3), and the retainer 92 holds a first annular sealing element 96 that extends around the input shaft 50.
- the seal 74 also includes a second retainer 94 sealed to the input shaft 50, and the second retainer 94 holds a second annular sealing element 98 in sliding, sealing contact with the first sealing element 96 by means of springs 100.
- Mechanical seals such as the seal 74 are well known to those skilled in the art. A suitable seal can be obtained from John Crane Co. (Kansas City, Missouri).
- a lip seal 78 is mounted between the input shaft 50 and the second portion 64 of the housing 30, and a weep hole 76 is formed in the second portion 64 between the mechanical seal 74 and the lip seal 78 ( Figure 1 ).
- the specific embodiment shown in the drawings also includes a direction control valve 80 that performs the function of the valve 16 of the above-identified Tieben patent, and a bypass valve 82 that performs the function of the valve 24 of the above-identified Tieben patent. Though useful in some applications, the direction control valve 80 and the bypass valve 82 are not essential aspects of this invention.
- the housing 30 defines a chamber 90 in which the hub 56 rotates.
- Fluid pressure in the chamber 90 is substantially equal to fluid pressure in other portions of the pump, as for example adjacent the inner ends 18, 26 of the shafts 16, 24.
- the flexible coupling comprising the splined surfaces of the driven gear shaft 16 and the input shaft 50 forms a relatively loose connection that ensures that the hydraulic pressure in the chamber 90 is transmitted to the extreme end surface of the driven gear shaft 16.
- the reference symbol is used for the area of the inner end 18 of the driven gear shaft 16.
- the area Ai is also equal to the area of the inner end 26 and to the area of the outer end 28 of the follower gear shaft 24.
- the reference symbol A 2 is used for the area of the shoulder 60, and the symbol A 3 is used for the area of the outer end 20 of the driven gear shaft 16. In all cases, area is measured in a plane transverse to the longitudinal axis of the respective shafts.
- the area Ai is equal to the sum of the area A 2 and the area A 3 . Since all of the areas, A-i, A 2 , A 3l are subjected to substantially the same hydraulic pressure within the pump 10, axial hydraulic forces on the driven shaft 16 are substantially balanced and axial faces on the follower shaft 24 are substantially balanced. Axial hydraulic forces on the input shaft 50 are carried by the thrust bearing 72 in a manner that substantially reduces wear and friction. Because the splined connection between the driven shaft 16 and the input shaft 50 allows axial as well as limited radial movement therebetween, the driven gear shaft 16 and the driven gear 14 are free to float in the housing 30 in a way that minimizes wear and friction. Since both of the ends of the driven gear shaft 16 and both of the ends of the follower gear shaft 24 are situated within the housing and subjected to the internal hydraulic pressure of the pump, axial forces on these shafts are balanced and wear and friction are minimized.
- the pump 10 operates efficiently and reliably even when subjected to a high pressure at the inlet passage 34.
- the pump 10 can be used in the hydraulic system described in Tieben U.S. Patent 5,916,139.
- pressure in the reservoir is selectively applied to the pump inlet to substantially reduce the power needed to drive the pump.
- high inlet pressure can result in undesired axial loads on the pumping mechanism, due to the high internal pressure of the pump.
- the pump 10 overcomes this problem by balancing axial forces on the gear shafts as described above.
- the pump 10 is well- suited for use in a wide variety of applications, and it is not limited to the specific applications described above.
- the splined connection between the input shaft 50 and the driven shaft 16 is only one example of a flexible coupling.
- Other flexible couplings can be used, including for example chain couplers and flexible couplings known under the trade names Browning, Para-flex and Lovejoy.
- the thrust bearing 72 shown in the drawings is only one example of a thrust bearing, and other thrust bearings can be substituted.
- roller bearings can be used instead of ball bearings, or bushing-type thrust bearings can be used.
- the thrust bearing can be formed as part of a radial bearing.
- the thrust bearing can be positioned at other places along the input shaft than the position shown in the drawings.
- the thrust bearing can be combined with a radial bearing and positioned at any desired point along the input shaft.
- ball bearings, bushing-type radial bearings or other types of roller bearings may be substituted for the illustrated radial bearings.
- the mechanical seal 74 may be replaced with other types of high pressure seals, including cup seals, for example.
- high pressure seal is intended to refer to a seal capable of sealing hydraulic fluid pressurized to a pressure of at least 500 psi.
- the housing 30 is shown in the preferred embodiment as including two separate portions held together by threaded fasteners.
- first and second portions of the housing can be defined by a single integrated structure rather than the separable structure shown.
- junction between the first and second portions of the housing can be placed at any desired point to facilitate fabrication and assembly.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MXPA01004187A MXPA01004187A (en) | 1999-08-27 | 2000-07-26 | Pump. |
CA002349007A CA2349007C (en) | 1999-08-27 | 2000-07-26 | Pump |
BRPI0007043-2A BR0007043B1 (en) | 1999-08-27 | 2000-07-26 | bomb. |
AU64948/00A AU766733B2 (en) | 1999-08-27 | 2000-07-26 | Pump |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16006399P | 1999-08-27 | 1999-08-27 | |
US60/160,063 | 1999-08-27 | ||
US09/436,413 | 1999-11-09 | ||
US09/436,413 US6244842B1 (en) | 1999-11-09 | 1999-11-09 | Pump |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001016465A1 true WO2001016465A1 (en) | 2001-03-08 |
Family
ID=26856564
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2000/020317 WO2001016465A1 (en) | 1999-08-27 | 2000-07-26 | Pump |
Country Status (8)
Country | Link |
---|---|
CN (1) | CN1120286C (en) |
AR (1) | AR025859A1 (en) |
AU (1) | AU766733B2 (en) |
BR (1) | BR0007043B1 (en) |
CA (1) | CA2349007C (en) |
ID (1) | ID29521A (en) |
MX (1) | MXPA01004187A (en) |
WO (1) | WO2001016465A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1653083A1 (en) * | 2004-10-29 | 2006-05-03 | Saurer GmbH & Co. KG | Gear pump with radial and axial support bearing |
US11662011B2 (en) | 2017-06-16 | 2023-05-30 | Gkn Sinter Metals Ag | Pump assembly and method for producing a pump assembly |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009029293A1 (en) * | 2009-09-09 | 2011-03-10 | Robert Bosch Gmbh | Gear pump with a drive shaft, a drive gear and a driven gear |
JP6271992B2 (en) * | 2013-12-13 | 2018-01-31 | Ntn株式会社 | Internal gear pump |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2587838A (en) * | 1950-09-20 | 1952-03-04 | Hub City Iron Company | Spline adapter coupler |
US3990550A (en) * | 1975-07-10 | 1976-11-09 | Recker Florian B | Shaft coupling |
US4402654A (en) * | 1980-03-13 | 1983-09-06 | Robert Bosch Gmbh | Fluid-operated gear machine |
JPH03130593A (en) * | 1989-10-12 | 1991-06-04 | Anlet Co Ltd | Shaft sealing device for vacuum pump or blower for gas |
US5772520A (en) * | 1996-07-11 | 1998-06-30 | Ford Motor Company | Vented studyoke on slip-between-center driveshaft |
US5957677A (en) * | 1996-04-03 | 1999-09-28 | Alfa Laval Flow Gmbh | Rotary lobe pump with magnetic rotor retention system |
-
2000
- 2000-07-26 BR BRPI0007043-2A patent/BR0007043B1/en not_active IP Right Cessation
- 2000-07-26 ID IDW20010923A patent/ID29521A/en unknown
- 2000-07-26 WO PCT/US2000/020317 patent/WO2001016465A1/en active Application Filing
- 2000-07-26 AU AU64948/00A patent/AU766733B2/en not_active Ceased
- 2000-07-26 CA CA002349007A patent/CA2349007C/en not_active Expired - Fee Related
- 2000-07-26 CN CN00801799A patent/CN1120286C/en not_active Expired - Fee Related
- 2000-07-26 MX MXPA01004187A patent/MXPA01004187A/en active IP Right Grant
- 2000-08-23 AR ARP000104341 patent/AR025859A1/en active IP Right Grant
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2587838A (en) * | 1950-09-20 | 1952-03-04 | Hub City Iron Company | Spline adapter coupler |
US3990550A (en) * | 1975-07-10 | 1976-11-09 | Recker Florian B | Shaft coupling |
US4402654A (en) * | 1980-03-13 | 1983-09-06 | Robert Bosch Gmbh | Fluid-operated gear machine |
JPH03130593A (en) * | 1989-10-12 | 1991-06-04 | Anlet Co Ltd | Shaft sealing device for vacuum pump or blower for gas |
US5957677A (en) * | 1996-04-03 | 1999-09-28 | Alfa Laval Flow Gmbh | Rotary lobe pump with magnetic rotor retention system |
US5772520A (en) * | 1996-07-11 | 1998-06-30 | Ford Motor Company | Vented studyoke on slip-between-center driveshaft |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1653083A1 (en) * | 2004-10-29 | 2006-05-03 | Saurer GmbH & Co. KG | Gear pump with radial and axial support bearing |
US7495575B2 (en) | 2004-10-29 | 2009-02-24 | Saurer Gmbh & Co. Kg | Gear pump |
US11662011B2 (en) | 2017-06-16 | 2023-05-30 | Gkn Sinter Metals Ag | Pump assembly and method for producing a pump assembly |
Also Published As
Publication number | Publication date |
---|---|
BR0007043A (en) | 2001-07-31 |
AR025859A1 (en) | 2002-12-18 |
AU766733B2 (en) | 2003-10-23 |
AU6494800A (en) | 2001-03-26 |
CA2349007A1 (en) | 2001-03-08 |
CN1321216A (en) | 2001-11-07 |
MXPA01004187A (en) | 2003-06-06 |
CA2349007C (en) | 2005-03-22 |
CN1120286C (en) | 2003-09-03 |
ID29521A (en) | 2001-09-06 |
BR0007043B1 (en) | 2010-01-26 |
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