WO1980002057A1 - Pump - Google Patents
Pump Download PDFInfo
- Publication number
- WO1980002057A1 WO1980002057A1 PCT/GB1980/000048 GB8000048W WO8002057A1 WO 1980002057 A1 WO1980002057 A1 WO 1980002057A1 GB 8000048 W GB8000048 W GB 8000048W WO 8002057 A1 WO8002057 A1 WO 8002057A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- channel
- pump
- inlet
- outlet
- stator
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1085—Channels or passages to recirculate the liquid in the bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/001—Shear force pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/36—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication
Definitions
- This invention relates to viscosity pumps, which comprise a rotor and stator ring, the rotor having a surface co-operating with an inner surface of the stator and being capable of rotation with respect to the stator ring, one of the surfaces having a channel for pressurising fluid between an inlet and an outlet Background Art
- such a pump comprises a thrust collar on a driving shaft, whose external cylindrical surface moves in close co-operation with an internal cylindrical surface of a surrounding stator ring in which the channel is formed. Viscous drag enables the rotor to pull the fluid from the channel and to pressurise it.
- the collar may be a collar provided as a shaft to co-operate with thrust pads to carry shaft thrust loads. Since such pads require forced lubrication, a viscosity pump may be eminently suitable for providing that lubrication, and indeed may also provide auxiliary lubrication for the motor driving the shaft.
- a viscosity pump is characterised in that the channel has a substantially constant cross-sectional area, and is of such a shape that its width changed smoothly from being comparatively wide in the area of the inlet to being comparatively narrow in a region displaced from the inlet.
- the collar conveniently constitutes a part of a thrust bearing for the driving shaft so that the pump may provide lubricant to the bearing surfaces as well as to auxiliary equipment, and also possibly to an oil cooler.
- the depth of the channel at its deepest point may be between 1.5 and 3 times the depth at its most shallow point.
- an inlet and/or an outlet passage may lead into the channel tangentially and may be of converging shape as it approaches the channel to act as a diffuser so that there is little turbulence where the. oil enters and leaves the channel.
- a sharp edge may be formed to act as a scraper for removing oil which has been pressurised in the channel and is about to leave by way of the outlet.
- a thrust bearing may comprise a thrust collar on a shaft, and thrust bearing surfaces against which the collar bears during shaft rotation, so that the thrust collar may act a rotor of a pump for providing pressurised lubricant for the bearing surfaces.
- Figure 1 is an end view of a viscosity pump whose rotor is a thrust collar on a shaft;
- Figure 2 is a section on the line A-A in Figure 1. Best Mode for Carrying out the Invention
- the pump is for providing a pressurised lubricant supply from a bath indicated generally at 11 in Figure 2, to various lubricant channels and galleries in the engine shown generally at 12, and especially to thrust pads 4 forming part of a thrust bearing for the shaft.
- the pump comprises essentially a rotor constituted by a cylindrical thrust collar 3 on an extension 13 of the engine shaft, and a ring 6 within whose inner cylindrical surface 25 the collar rotates with just sufficient clearance to establish a hydro-dynamic lubricant film between the co-operating cylindrical surfaces.
- the internal cylindrical surface of the ring 6 is formed with a pumping channel 7 extending around the ring between a pair of apertures 1 and 2 which are arranged to communicate with the bath 11, and with a passage 26 leading to a lubricant gallery in the engine.
- the collar 3 bears against a ring of thrust pads (one is shown at 4) of a conventional thrust bearing for the engine shaft.
- the pads 4 are mounted conventionally on a support, generally at 14, fast with the ring 6 which is itself mounted on the engine 12.
- each of the apertures 1 and 2 there is a passage formed in the body of the ring 6 which first converges as indicated at 15, and then opens smoothly tangentially into the ann ⁇ lar channel 7.
- the channel 7 is of constant cross sectional area, but where it joins the passages 15, it is shallow and wide as indicated at 16, and at the mid-way position diametrically opposite the apertures 1 and 2 is narrow and deep as indicated at 17.
- the lubricant at 15 (assuming rotation is clockwise in Figure 1), is driven viscously around with the rotating cylindrical surface of the collar, and an increased pressure is established by the time the lubricant reaches the passage leading to the aperture 2, where it is scraped from the surface of the collar 3 by the edge 18 of a land extending between the openings from the passages leading to the apertures 1 and 2. Between the two edges 18 is an uninterrupted area 5.
- the smooth change in the cross sectional shape (but not the area) of the channel 7 ensures that there is maximum viscous drag near the apertures 1 and 2, where the channel section is wide and shallow, whereas there is the maximum load bearing area on the lands 8 and 9 on either side of the channel at the region 17 opposite 5 where substantial loads have to be carried. Where the channel is wide to give high viscous drag, so that the lands 8 and 9 are quite narrow, there is the adjacent substantial area 5 which is uninterruptedby the channel 7 for supporting substantial loads there.
- the ring 6 would be fixed to the engine, but if it were possible for the collar 3 to be rotated, in either sense, then the ring 6 could be mounted for limited rotation about the shaft axis between two positions defined on each side by an external lug 10 on the ring, and a pair of stop surfaces 27 on the engine in which respective positions the bath 11 and the passage 26 would be in communication with different ones of the apertures 1 and 2. Rotation of the collar 3 and the viscous drag of the lubricant would hold the ring 6 against one or other of the stop surfaces 27 on each side, and reversal of the direction of rotation would automatically move the ring against the other stop surfaces.
- the depth of the channel 7 at 17 is between 1.5 and 3 times the depth of the channel at 16.
- the arcuate extent of the area 5 may be between about 5° and about 30°.
- the smooth reduction in cross sectional area of the diffuser passages 15 helps to ensure that a minimum of turbulence occurs in those areas with acceleration and deceleration of the lubricant occuring smoothly, and that gives the pump a high efficiency, and also enables it to be primed quickly and easily so that there is unlikely to be wear at starting up before a lubricant film is established. It may be noted that this is achieved while having a substantial load supporting land area on either side of the channel 7 at the region 17, and that may be conveniently about one third or one half of the width of the ring 6.
- a rotating shaft will have angular positions of maximum transverse load, for example the vertical directions for heavy shafts or for shafts carrying heavy loads, or the direction of piston movement in the case of a shaft driven by a reciprocating engine.
- the pump ring will be orientated so that the larger bearing area at 17 and 5 are where the maximum loads are experienced.
- the bath 11 is arranged so that the lowest part of the collar will be under oil in the bath when the collar is stationary. Thus, at starting, there will be oil on the area 5 to provide lubrication before pumping pressure has been built up.
- the thrust bearing collar is used to provide pressurised lubricant for the thrust pads, and can also be used for other auxiliary purposes.
- the main load driven by the shaft might be turbine or a main pump, for example, for pumping oil from the sea bed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
- Rotary Pumps (AREA)
- Lubricants (AREA)
- Fluid-Driven Valves (AREA)
- Eye Examination Apparatus (AREA)
- Reciprocating Pumps (AREA)
Abstract
A viscosity pump in which a cylindrical collar (3) constituted by a part of a thrust bearing rotates in a co-operating surrounding ring (6) in which is formed an annular channel (7) in which oil or other fluid can be pressurised by viscous drag as the collar rotates. In order to reduce wear and to make it easier to prime the pump, the cross sectional of the channel is of constant area but of smoothly changing shape so that the viscous drag is a maximum at the inlet (1) but the channel is at its narrowest at a point (17) displaced from the inlet where substantial transverse loads have to be carried. The pump provides pressurised lubricant for the pads (4) of the thrust bearing.
Description
PUMP
Technical Field
This invention relates to viscosity pumps, which comprise a rotor and stator ring, the rotor having a surface co-operating with an inner surface of the stator and being capable of rotation with respect to the stator ring, one of the surfaces having a channel for pressurising fluid between an inlet and an outlet Background Art
In one known application such a pump comprises a thrust collar on a driving shaft, whose external cylindrical surface moves in close co-operation with an internal cylindrical surface of a surrounding stator ring in which the channel is formed. Viscous drag enables the rotor to pull the fluid from the channel and to pressurise it. The collar may be a collar provided as a shaft to co-operate with thrust pads to carry shaft thrust loads. Since such pads require forced lubrication, a viscosity pump may be eminently suitable for providing that lubrication, and indeed may also provide auxiliary lubrication for the motor driving the shaft.
Difficulties with viscosity pumps are that there can be an unacceptable amount of wear between co- operating surfaces of the stator and rotor other than at the channel with consequent leakage and also that priming of the pump at starting is not easy, and wear may occur before the pump has been fully primed. It is an object of the present invention to overcome these disadvantages.
Disclosure of Invention
According to the invention, a viscosity pump is characterised in that the channel has a substantially constant cross-sectional area, and is of such a shape that its width changed smoothly from being comparatively wide in the area of the inlet to being comparatively narrow in a region displaced from the inlet.
The collar conveniently constitutes a part of a thrust bearing for the driving shaft so that the pump may provide lubricant to the bearing surfaces as well as to auxiliary equipment, and also possibly to an oil cooler.
There will thus be maximum viscous forces adjacent the inlet where the channel is wide and shallow, while at a position displaced from the inlet the channel is narrower and deeper, so that it will be possible at that position to have comparatively wide lands on the stator ring on either side of the channel. This may then provide a substantial area for carrying bearing loads through the medium of a hydro-dynamic lubricant film between the co-operating surfaces.
Conveniently the depth of the channel at its deepest point may be between 1.5 and 3 times the depth at its most shallow point.
Preferably there is an area of the stator surface between the inlet and the outlet which does not have any part of the channel formed in it so that the whole of that area is available for taking bearing loads.
An inlet and/or an outlet passage may lead into the channel tangentially and may be of converging shape as it approaches the channel to act as a diffuser so that there is little turbulence where the. oil enters and leaves the channel.
Where a converging passage merges tangentially into the cylindrical co-operating surface of the stator ring, a sharp edge may be formed to act as a scraper for removing oil which has been pressurised in the channel and is about to leave by way of the outlet.
The stator ring may be capable of taking up either of two positions in relation to supply and discharge lines so that the functions of the inlet and outlet apertures can be changed over if the sense of rotation of the rotor changes. Thus the pump ring could be symmetrical about a plane containing the axis of rotation.
In accordance with the invention, a thrust bearing may comprise a thrust collar on a shaft, and thrust bearing surfaces against which the collar bears during shaft rotation, so that the thrust collar may act a rotor of a pump for providing pressurised lubricant for the bearing surfaces. Brief Description of Drawings.
The invention may be carried into practice in various ways, and one embodiment willnow be described by way of example, with reference to the accompanying drawings, in which Figure 1 is an end view of a viscosity pump
whose rotor is a thrust collar on a shaft; and
Figure 2 is a section on the line A-A in Figure 1. Best Mode for Carrying out the Invention
In the example being described, the pump is for providing a pressurised lubricant supply from a bath indicated generally at 11 in Figure 2, to various lubricant channels and galleries in the engine shown generally at 12, and especially to thrust pads 4 forming part of a thrust bearing for the shaft. The pump comprises essentially a rotor constituted by a cylindrical thrust collar 3 on an extension 13 of the engine shaft, and a ring 6 within whose inner cylindrical surface 25 the collar rotates with just sufficient clearance to establish a hydro-dynamic lubricant film between the co-operating cylindrical surfaces.
The internal cylindrical surface of the ring 6 is formed with a pumping channel 7 extending around the ring between a pair of apertures 1 and 2 which are arranged to communicate with the bath 11, and with a passage 26 leading to a lubricant gallery in the engine. The collar 3 bears against a ring of thrust pads (one is shown at 4) of a conventional thrust bearing for the engine shaft. The pads 4 are mounted conventionally on a support, generally at 14, fast with the ring 6 which is itself mounted on the engine 12.
From each of the apertures 1 and 2 there is a passage formed in the body of the ring 6 which first converges as indicated at 15, and then opens smoothly
tangentially into the annμlar channel 7. The channel 7 is of constant cross sectional area, but where it joins the passages 15, it is shallow and wide as indicated at 16, and at the mid-way position diametrically opposite the apertures 1 and 2 is narrow and deep as indicated at 17.
As the collar 3 is driven around, the lubricant at 15 (assuming rotation is clockwise in Figure 1), is driven viscously around with the rotating cylindrical surface of the collar, and an increased pressure is established by the time the lubricant reaches the passage leading to the aperture 2, where it is scraped from the surface of the collar 3 by the edge 18 of a land extending between the openings from the passages leading to the apertures 1 and 2. Between the two edges 18 is an uninterrupted area 5.
The smooth change in the cross sectional shape (but not the area) of the channel 7 ensures that there is maximum viscous drag near the apertures 1 and 2, where the channel section is wide and shallow, whereas there is the maximum load bearing area on the lands 8 and 9 on either side of the channel at the region 17 opposite 5 where substantial loads have to be carried. Where the channel is wide to give high viscous drag, so that the lands 8 and 9 are quite narrow, there is the adjacent substantial area 5 which is uninterruptedby the channel 7 for supporting substantial loads there.
Where the collar 3 can only rotate in one sense, the ring 6 would be fixed to the engine, but if it were possible for the collar 3 to be rotated, in either
sense, then the ring 6 could be mounted for limited rotation about the shaft axis between two positions defined on each side by an external lug 10 on the ring, and a pair of stop surfaces 27 on the engine in which respective positions the bath 11 and the passage 26 would be in communication with different ones of the apertures 1 and 2. Rotation of the collar 3 and the viscous drag of the lubricant would hold the ring 6 against one or other of the stop surfaces 27 on each side, and reversal of the direction of rotation would automatically move the ring against the other stop surfaces.
In many cases, it is convenient if the depth of the channel 7 at 17 is between 1.5 and 3 times the depth of the channel at 16. The arcuate extent of the area 5 may be between about 5° and about 30°.
The smooth reduction in cross sectional area of the diffuser passages 15 helps to ensure that a minimum of turbulence occurs in those areas with acceleration and deceleration of the lubricant occuring smoothly, and that gives the pump a high efficiency, and also enables it to be primed quickly and easily so that there is unlikely to be wear at starting up before a lubricant film is established. It may be noted that this is achieved while having a substantial load supporting land area on either side of the channel 7 at the region 17, and that may be conveniently about one third or one half of the width of the ring 6. Often, a rotating shaft will have angular
positions of maximum transverse load, for example the vertical directions for heavy shafts or for shafts carrying heavy loads, or the direction of piston movement in the case of a shaft driven by a reciprocating engine. The pump ring will be orientated so that the larger bearing area at 17 and 5 are where the maximum loads are experienced.
The bath 11 is arranged so that the lowest part of the collar will be under oil in the bath when the collar is stationary. Thus, at starting, there will be oil on the area 5 to provide lubrication before pumping pressure has been built up.
It will be seen that the thrust bearing collar is used to provide pressurised lubricant for the thrust pads, and can also be used for other auxiliary purposes.
The main load driven by the shaft might be turbine or a main pump, for example, for pumping oil from the sea bed.
Claims
1. A viscosity pump comprising a rotor (3) and stator ring (6), the rotor having a surface co-operating with an inner surface (25) of the stator and being capable of rotation with respect to the stator ring, one of the surfaces having a channel (7) for pressurising fluid between an Inlet (1) and an outlet (2) characterised in that the channel (7) has a substantially constant cross-sectional area, and is of such a shape that its width changes smoothly from being comparatively wide (16) in the area of the inlet to being comparatively narrow (17) in a region displaced from the inlet.
2. A pump as claimed in Claim 1 characterised in that the channel is in the inner cylindrical surface of the stator.
3. A pump as claimed in Claim 2 characterised by comparatively wide lands on either side of channel where the channel is comparatively narrow.
4. A pump as claimed in Claim 3 characterised by an area (5) of the inner cylindrical surface of the stator which does not have any part of the channel formed in it, and is located generally between the inlet and the outlet.
5. A pump as claimed in Claim 4 characterised In that the arcuate extent of the said area is between 5° and 30°.
6. A pump as claimed in Claim 5 characterised In that the inlet and/or outlet (1) and/or (2) leads into the channel tangentially.
7. A pump as claimed in Claim 6 characterised by a sharp edge where the channel meets the tangential opening to the outlet.
8. A pump as claimed in any of Claims 1 to 7 characterised in that, at its deepest point, the depth of the channel is between 1.5 and 3 times the depth of the channel at its most shallow point.
9. A pump as claimed in Claim 8 characterised in that the stator ring is capable of taking up either of two positions in relation to the Inlet and outlet whereby the functions of the inlet and outlet are reversed when the direction of rotation of the rotor is reversed.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE8080900496T DE3067921D1 (en) | 1979-03-27 | 1980-03-20 | Pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB7910694 | 1979-03-27 | ||
GB7910694 | 1979-03-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1980002057A1 true WO1980002057A1 (en) | 1980-10-02 |
Family
ID=10504165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB1980/000048 WO1980002057A1 (en) | 1979-03-27 | 1980-03-20 | Pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US4396348A (en) |
EP (1) | EP0026765B1 (en) |
JP (1) | JPH0135198B2 (en) |
AT (1) | ATE7622T1 (en) |
DE (1) | DE3067921D1 (en) |
FR (1) | FR2452612B1 (en) |
IT (1) | IT1127008B (en) |
WO (1) | WO1980002057A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5266003A (en) * | 1992-05-20 | 1993-11-30 | Praxair Technology, Inc. | Compressor collector with nonuniform cross section |
GB2295864B (en) * | 1994-12-06 | 1998-07-01 | Glacier Metal Co Ltd | Vertical bearing assembly lubrication |
JP5964207B2 (en) * | 2012-11-01 | 2016-08-03 | 三菱重工業株式会社 | Self-lubricating bearing device |
JP5964206B2 (en) * | 2012-11-01 | 2016-08-03 | 三菱重工業株式会社 | Self-lubricating bearing device |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE336410C (en) * | 1918-07-18 | 1921-04-30 | Aeg | Lubricating device for shafts or journals |
DE720485C (en) * | 1936-10-07 | 1942-05-07 | Gustav Stromeier | Conveyor device for liquids |
FR1439499A (en) * | 1965-06-25 | 1966-05-20 | Thomson Houston Comp Francaise | Self-contained pump lubrication system |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL6704587A (en) * | 1967-03-31 | 1968-10-01 | ||
US3617148A (en) * | 1970-05-18 | 1971-11-02 | Carrier Corp | Thrust bearing for refrigeration compressor |
GB1373955A (en) * | 1971-04-03 | 1974-11-13 | Bullough W A | Combined viscosity pump and electric motor |
-
1980
- 1980-03-20 AT AT80900496T patent/ATE7622T1/en not_active IP Right Cessation
- 1980-03-20 US US06/212,732 patent/US4396348A/en not_active Expired - Lifetime
- 1980-03-20 WO PCT/GB1980/000048 patent/WO1980002057A1/en active IP Right Grant
- 1980-03-20 DE DE8080900496T patent/DE3067921D1/en not_active Expired
- 1980-03-20 EP EP80900496A patent/EP0026765B1/en not_active Expired
- 1980-03-20 JP JP55500623A patent/JPH0135198B2/ja not_active Expired
- 1980-03-25 IT IT48257/80A patent/IT1127008B/en active
- 1980-03-26 FR FR8006725A patent/FR2452612B1/en not_active Expired
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE336410C (en) * | 1918-07-18 | 1921-04-30 | Aeg | Lubricating device for shafts or journals |
DE720485C (en) * | 1936-10-07 | 1942-05-07 | Gustav Stromeier | Conveyor device for liquids |
FR1439499A (en) * | 1965-06-25 | 1966-05-20 | Thomson Houston Comp Francaise | Self-contained pump lubrication system |
Also Published As
Publication number | Publication date |
---|---|
DE3067921D1 (en) | 1984-06-28 |
ATE7622T1 (en) | 1984-06-15 |
JPS56500304A (en) | 1981-03-12 |
EP0026765B1 (en) | 1984-05-23 |
IT8048257A0 (en) | 1980-03-25 |
US4396348A (en) | 1983-08-02 |
IT1127008B (en) | 1986-05-21 |
FR2452612A1 (en) | 1980-10-24 |
JPH0135198B2 (en) | 1989-07-24 |
EP0026765A1 (en) | 1981-04-15 |
FR2452612B1 (en) | 1985-09-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6446976B1 (en) | Hydrodynamic face seal with grooved sealing dam for zero-leakage | |
JPS6261797B2 (en) | ||
US4789317A (en) | Rotary vane oil pump and method of operating | |
US3818803A (en) | Pumps | |
US4396348A (en) | Viscosity pump | |
CN111601949B (en) | Rotary sliding vane machine | |
US4421321A (en) | Hydrodynamic non-contacting seal for rotary machines | |
EP0835400B1 (en) | Seal/bearing apparatus | |
US5964584A (en) | Vane pump having a shaftless balanced rotor | |
EP3783240B1 (en) | Bearing assembly and compressor comprising same | |
US20150377233A1 (en) | Integrated lubrication pump | |
US4392795A (en) | Wear resistant rotor slots for vane-type pumps or motors | |
JPH0578691B2 (en) | ||
JPH0652114B2 (en) | Self-lubricating bearing | |
US3299825A (en) | Hydraulic pump | |
US3002463A (en) | Rotary pump of the liquid ring type with side channels | |
US3733144A (en) | Viscosity pump | |
JP4115401B2 (en) | Swash plate type fluid pressure equipment | |
US1964244A (en) | Variable delivery radial pump | |
JPH0626447A (en) | Hydraulic pump motor | |
US3065707A (en) | Vane type oil pump lubrication system | |
JPH0467045B2 (en) | ||
US5863133A (en) | Vertical bearing assembly lubrication | |
JP2003343424A (en) | Swash plate type fluid pump/motor | |
US4543037A (en) | Rotary high-pressure, low-capacity pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Designated state(s): JP US |
|
AL | Designated countries for regional patents |
Designated state(s): AT CH DE GB LU NL SE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1980900496 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 1980900496 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 1980900496 Country of ref document: EP |