US3794449A - Viscosity pump - Google Patents

Viscosity pump Download PDF

Info

Publication number
US3794449A
US3794449A US00283213A US3794449DA US3794449A US 3794449 A US3794449 A US 3794449A US 00283213 A US00283213 A US 00283213A US 3794449D A US3794449D A US 3794449DA US 3794449 A US3794449 A US 3794449A
Authority
US
United States
Prior art keywords
rotor
housing
grooves
liquid
shallowness
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00283213A
Other languages
English (en)
Inventor
G Brouwer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
US Philips Corp
Original Assignee
US Philips Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by US Philips Corp filed Critical US Philips Corp
Application granted granted Critical
Publication of US3794449A publication Critical patent/US3794449A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/105—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one bearing surface providing angular contact, e.g. conical or spherical bearing surfaces

Definitions

  • ABSTRACT A viscosity pump for dosing small quantities of liquid including a rotor and driving shaft, and a housing surrounding the rotor, the cooperating surfaces of rotor or housing being provided with at least one pattern of shallow pumping grooves which communicate on one side with a liquid supply and on the other side with a liquid outlet, the side of the grooves communicating with the outlet being shallower than the rest of the groove.
  • the invention relates to a viscosity pump for dosing small quantities of liquid, the pump including a rotor provided with a driving shaft as well as a housing surrounding the rotor.
  • the surfaces of the rotor and of the housing facing each other comprise at least one pattern of shallow pumping grooves which communicate at one end with a liquid inlet and at the other end with a liquid outlet.
  • Viscosity pumps of the above-described type are known and are used as dosing pumps for the accurate dosing of small quantities of liquid, for example, in micro-analysis and in automated chemical analysis.
  • the quantities to be dosed in these cases are very small and cover the range of 30 cm/sec to quantitites smaller than lcmm/sec.
  • This type of pump gives a continuous, pulse-free supply which is proportional to the number of revolutions of the rotor and independent of the viscosity of the relevant liquid.
  • These types of pumps may be constructed as cylindrical, conical or flat disk pumps and also as double acting conical or disk pumps.
  • the viscosity pump according to the invention is characterized in that the part of each of the pumping grooves communicating with the outlet is shallower than the rest ofthe groove.
  • the pressure in the liquid is inversely proportional to the distance between the faces in which the patterns of grooves are present, it has now become possible in viscosity pumps in which an axial movement of the rotor and the housing produces a distance variation between the relevant surfaces, to control the liquid pressure supplied by the pump.
  • a favourable embodiment of the viscosity pump according to the invention includes the rotor having a surface which encloses an angle with the rotor axis, and the housing having a surface cooperating therewith, and one of the said surfaces comprising a pattern of grooves.
  • the pump is characterized in that the rotor and the housing are movable axially relative to each other, and means are present to exert on the rotor or the housing a control force which may be controllable and is directed opposite to the liquid pressure.
  • control force may be exerted, for example, by a spring, a hydraulic or pneumatic pressure, and
  • a further favourable embodiment of the viscosity pump according to the invention is constructed as a double acting pump; its rotor has two surfaces which enclose an angle with the rotor axis and the housing comprises two surfaces cooperating therewith, and in which each of the said two surfaces of the rotor or the housing is provided with a pattern of grooves.
  • the pump is characterized in that the housing has such a construction that the relevant two surfaces thereof are movable axially relative to each other.
  • the magnitude of the clearance between the rotor and the housing can be varied by varying the distance between the two relevant surfaces which, as described above, produces a variation in the pressure supplied-by the pump.
  • one of the said two surfaces forms part of a structural component which is connected to the housing via a flexible diaphragm, means being present to exert pressure on said diaphragm.
  • the pressure exerted on the diaphragm makes equilibrium with the pressure exerted on the housing by the liquid in the pump so that the pressure exerted on the diaphragm is a reference pressure for the pressure of the liquid supplied by the pump.
  • a pressure controlled by means of a viscosity pump is obtained with structurally very simple means.
  • FIGS. 1, 2 and 3 show diagrammatically the housing, the rotor and the combination thereof, respectively, of a cylindrical viscosity pump.
  • FIG. 4 is a diagrammatic cross-sectional view of a disk-shaped viscosity pump not drawn to scale
  • FIG. 5 is a perspective view of the rotor and one of the parts of the housing of the pump shown in FIG. 4,
  • FIG. 6 shows diagrammatically a conical viscosity pump not drawn to scale.
  • FIG. 7 shows diagrammatically a disk-shaped viscosity pump of which one of the parts of the housing is axially movable relative to the rotor to control the pressure.
  • FIG. 8 shows the control principle of FIG. 7 applied to a single-acting conical pump of the type in FIG. 6.
  • FIGS. 1, 2 and 3 show the housing, the rotor and a cross-sectional view of the combination of housing and rotor, respectively.
  • the rotor is denoted by reference numeral 1.
  • This rotor 1 comprises a shaft 2 which can be coupled to a driving mechanism not shown.
  • the rotor comprises three shallow pumping grooves 3 and three shallow pumping grooves 4.
  • the pumping grooves 3 are separated from each other by dams 6, and the pumping grooves 4 are separated from each other by dams 7.
  • the rotor 1 furthermore comprises a much deeper liquid collecting duct 5 and two liquid supply ducts 8 and 9.
  • the liquid supply duct communicates with one side of the pumping grooves 3, while the supply duct 9 communicates with one side of the pumping grooves 4 via axially extending recesses 9.
  • the housing furthermore comprises liquid supply apertures and 21 which communicate with the pumping grooves 3 and 4, respectively, and a liquid outlet 13 which communicates with the liquid collecting duct 5.
  • the rotor 1 fits in the housing 12 with a small amount of play.
  • the liquid in the grooves 3 and 4 is forced, by viscous forces, from the inlets 8' and 9' to the outlets 10 and 11. Since the same pressures prevail at the area of the inlets 8 and 9 on the one hand and of the outlets l0 and 11 on the other hand, and the pressure variation in the grooves 3 and 4 is the same for all the grooves, the forces exerted on the rotor will compensate each other as a result of the uniform distribution of the grooves 3 and 4 over the rotor circumfer- Bl'lCe.
  • each of the grooves 3 and 4 comprises a shallower portion 22 on the side where said grooves communicate with the outlets 10 and 11; i.e., the outlet part 10 of the groove is more shallow than the central and inlet parts.
  • FIG. 4 shows a double-acting disk-shaped pump in which reference numeral 41 denotes a disk-shaped rotor which includes a driving shaft 42.
  • the rotor 41 is surrounded by the parts 43 and 44 of the housing.
  • surfaces of the parts 43 and 44 of the housing facing the rotor 41 are each provided with a pattern of shallow pumping grooves 45 and 46, respectively, which communicate at one side with the liquid supply chambers 47 and 48, respectively, and communicate on the other side with a common liquid collecting duct 49 which communicates with a liquid outlet 50.
  • the liquid supply chambers 47 and 48 communicate with each other through ducts 51 in the rotor 41, the chamber 48 communicating with a liquid supply duct 52.
  • each of the grooves 45, 46 which communicates with the collecting duct 49, is shallower than the rest of the groove. All this is shown in greater detail in the perspective view of the rotor 41 and the part 43 of the housing shown in FIG. 5.
  • the part 44 of the housing is not shown to improve clarity; however, how the portion 53 of each groove becomes gradually shallower in the direction of the collecting duct is shown. Although in this embodiment a gradual transition from the portion 53 to the rest of the groove has been chosen, an abrupt transition may also be used.
  • the pressure in the supply chambers 47 and 48 on the one hand and in the collecting duct 49 on the other hand is the same for all the grooves, the pressure variation, supposing the shallow portion 53 were not present, would be the same in all the grooves independently of the position of the rotor 41 relative to the housing walls. This means that the forces exerted on the rotor in the axial direction are always equal to each other so that no stabilizing effect, that is to say an automatic searching of the central position of the rotor relative to the housing, occurs. In the case of a large deviation from the central position of the rotor, quadratic influences start to influence the dosing accuracy of the pump. In order to prevent this, the shallow portions 53 are provided.
  • FIG. 4 shows a disk-shaped flat viscosity pump by way of example, it will be obvious that other constructions are also possible. By way of illustration,
  • FIG. 6 shows diagrammatically a conical viscosity pump according to the same principle.
  • the parts are referred to by the same reference numerals as in the pump shown in FIG. 4 but with suffix a.
  • the liquid supply 52a communicates with only one supply chamber 48 a, while on the other side of each pattern of grooves 45a and 46a, respectively, a collection duct 49a is present with which liquid outlet 50a communicates.
  • each of the grooves 45a and 460, respectively is again provided with a shallower portion 53a so that again a stabilizing effect of rotor 41 is obtained which therefore will alwaysbe in its central position again.
  • FIG. 7 finally shows a viscosity pump of the same disk-shaped type as in FIG. 4.
  • the same reference numerals are used but with suffix b.
  • the only difference with the construction shown in FIG. 4 is that the pattern of grooves 45b is now provided on a structural part 55 which communicates, via
  • chamber 57 is present below the diaphragm 56 and contains liquid the pressure of which can be controlled.
  • the space 57 communicates, via a duct 58, with a pressure-supplying control device not shown.
  • the position of the structural part 55 can now be adjusted by means of the liquid in the space 57, a variation of the play between the rotor 41b and the patterns of grooves 45b and 46b thus occurring.
  • This variation will involve a pressure variation namely such that the pressure exerted on the structural part 55 by the liquid in the pump is equal to and opposite to the pressure which is exerted on said part by the liquid in the space 57. So in this manner a viscosity pump is obtained with structurally very simple means and in which liquid can be dosed with a given desirable pressure.
  • the reference force on the structural part 55b in this case is obtained hydraulically, this may also be effected, if desirable, mechanically, for example, with spring force, pneumatically, and so on.
  • FIG. 8 shows diagrammatically how the control principle according to FIG. 7 can also be applied to a single-acting pump.
  • the conically constructed rotor 81 is incorporated in housing 82 which is arranged on a spring 83 the resilience of which can be adjusted by means of an adjusting screw 84.
  • the liquid to be pumped is supplied on the top at 85 and transported to space 87 through the grooves 86 and then to outlet 88.
  • the side of the grooves 86 communicating with the space 87 again comprises a shallower portion. In the liquid pumped to space 87 a pressure will adjust such that an equilibrium of forces is achieved with the force of the spring 83.
  • the desirable liquid pressure can thus be adjusted; it will be obvious that this is associated with a given distance between the rotor 81 and the housing 82.
  • the housing and the rotor are slightly forced apart as a result of which the distance between the co-operating surfaces becomes larger. As a result of this the internal leak will increase and the pressure will drop until the desirable pressure is achieved.
  • the spring 83 may be replaced by a hydraulic or pneumatic force. It is also possible to exert the force on the rotor instead of on the housing, although this will present a few problems structurally.
  • a viscosity pump for closing small quantities of liquid. and operable with a source of control fluid comprising, a rotor and drive shaft, a housing that surrounds the rotor, the rotor and housing having at least one pair of adjacent, facing surfaces, which define between them a pattern of continuous shallow pumping grooves comprising an inlet part, a central part, and an outlet part more shallow than the other parts, liquid inlet means communicating with said inlet part, and liquid outlet means communicating with said outlet part, the rotor rotatable and axially movable relative to said housing, whereby the shallowness of said grooves is variable, control means for exerting a selectively, variable axial force on at least one of said housing and rotor members relative to the other, for controlling the shallowness of said grooves, said control means comprising a flexible diaphragm, one side of which supports a part of the housing that defines one of said surfaces, the other side of the diaphragm defining with the housing a chamber, and means communicating said control fluid into
  • a viscosity pump for dosing small quantities of liquid, and operable with a source of control fluid comprising, a rotor and drive shaft, a housing that surrounds the rotor, the rotor and housing having at least one pair of adjacent, facing surfaces, which define be- .tween them a pattern of continuous shallow pumping grooves comprising an inlet part, a central part, and an outlet part more shallow than the other parts, said pair of adjacent surfaces define two generally conical configurations positioned coaxially with their base parts adjacent, liquid inlet means communicating with said inlet part, and liquid outlet meanscommunicating with said outlet part, the rotor rotatable and axially movable relative to said housing, whereby the shallowness of said grooves is variable, control means for exerting a selectively, variable axial force on at least one of said housing and rotor members relative to the other, for controlling the shallowness of said grooves, said control means comprising a flexible diaphragm, one side of which supports a part of the housing that defines
  • a viscosity pump for dosing small quantities of liquid, and operable with a source of control fluid'comprising, a rotor and drive shaft, a housing that surrounds the rotor, the rotor and housing having at least one pair of adjacent, facing surfaces, which define between them a pattern of continuous shallow pumping grooves comprising an inlet part, a central part, and an outlet part more shallow than the other parts, liquid inlet means communicating with said inlet part, and liquid outlet means communicating with said outlet part, the rotor rotatable and axially movable relative to said housing, whereby the shallowness of said grooves is variable, control means for exerting a selectively, variable axial force on at least one of said housing and rotor members relative to the other, for controlling the shallowness of said grooves.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
US00283213A 1971-08-31 1972-08-23 Viscosity pump Expired - Lifetime US3794449A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL7111948A NL7111948A (zh) 1971-08-31 1971-08-31

Publications (1)

Publication Number Publication Date
US3794449A true US3794449A (en) 1974-02-26

Family

ID=19813914

Family Applications (1)

Application Number Title Priority Date Filing Date
US00283213A Expired - Lifetime US3794449A (en) 1971-08-31 1972-08-23 Viscosity pump

Country Status (9)

Country Link
US (1) US3794449A (zh)
JP (1) JPS4833407A (zh)
AT (1) AT321255B (zh)
BE (1) BE788140A (zh)
DE (1) DE2239857A1 (zh)
FR (1) FR2152023A5 (zh)
GB (1) GB1400531A (zh)
IT (1) IT964321B (zh)
NL (1) NL7111948A (zh)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924962A (en) * 1973-09-14 1975-12-09 Cit Alcatel Molecular pumps of the drum type
WO1980002058A1 (en) * 1979-03-19 1980-10-02 L Kalashnikov Vane pump
US4227816A (en) * 1978-08-21 1980-10-14 Usm Corporation Rotary processor
WO1981000276A1 (en) * 1979-07-12 1981-02-05 P Staebler Lubricant metering pump
US4408966A (en) * 1979-12-27 1983-10-11 Matsushita Electric Industrial Co., Ltd. Pump for supplying liquid fuel
DE3347471A1 (de) * 1983-12-29 1985-07-11 Technion Research & Development Foundation Ltd., Haifa Hochdruckrotationspumpe niedriger kapazitaet
US4543037A (en) * 1984-01-16 1985-09-24 Technion Research & Development Foundation Limited Rotary high-pressure, low-capacity pump
US4899704A (en) * 1989-05-08 1990-02-13 Tecumseh Products Company Self-lubricating bearing
US5056715A (en) * 1990-02-21 1991-10-15 Pfizer Inc. Apparatus for mixing and spraying a slurry
US6506025B1 (en) * 1999-06-23 2003-01-14 California Institute Of Technology Bladeless pump
US20140308112A1 (en) * 2011-11-10 2014-10-16 Eagleburgmann Germany Gmbh & Co. Kg Slide ring seal arrangement with tesla pump
US20150292468A1 (en) * 2013-03-05 2015-10-15 Yugen Kaisha Nakanoseisakusho Rotation drive apparatus

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5834227A (ja) * 1981-08-26 1983-02-28 Nippon Seiko Kk 動圧形流体軸受
EP0220628B1 (en) * 1985-10-22 1992-09-23 Ebara Corporation Thrust bearing
DE3918844A1 (de) * 1989-06-09 1990-12-13 Vorwerk Co Interholding Staubsaugermotor
JP2563543Y2 (ja) * 1991-05-28 1998-02-25 三菱自動車工業株式会社 粘性ポンプ
IT1260461B (it) * 1992-01-28 1996-04-09 Fiat Auto Spa Dispositivo a pompa per un fluido viscoso
GB9525972D0 (en) 1995-12-19 1996-02-21 Domino Printing Sciences Plc Pump

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US649546A (en) * 1899-04-28 1900-05-15 Edwin F Porter Motor.
US760776A (en) * 1903-09-09 1904-05-24 Ben J Campbell Fluid-viscosity motor or turbine.
US1003020A (en) * 1907-11-14 1911-09-12 Samuel J Webb Rotary pump.
US1586160A (en) * 1926-02-20 1926-05-25 Mauron Francois Molecular vacuum pump
FR1266131A (fr) * 1960-08-25 1961-07-07 Thomson Houston Comp Francaise Perfectionnements aux pompes rotatives à haute pression
US3328094A (en) * 1964-02-29 1967-06-27 Philips Corp Axial bearings of the pump type
US3376083A (en) * 1965-03-27 1968-04-02 Philips Corp Axial bearing
US3497273A (en) * 1967-03-31 1970-02-24 Philips Corp Hydrodynamic bearing for axial and radial loads
US3663074A (en) * 1969-05-27 1972-05-16 Skf Ind Trading & Dev Arrangement in spiral groove bearings
US3712754A (en) * 1969-12-05 1973-01-23 Philips Corp Dosing device

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US649546A (en) * 1899-04-28 1900-05-15 Edwin F Porter Motor.
US760776A (en) * 1903-09-09 1904-05-24 Ben J Campbell Fluid-viscosity motor or turbine.
US1003020A (en) * 1907-11-14 1911-09-12 Samuel J Webb Rotary pump.
US1586160A (en) * 1926-02-20 1926-05-25 Mauron Francois Molecular vacuum pump
FR1266131A (fr) * 1960-08-25 1961-07-07 Thomson Houston Comp Francaise Perfectionnements aux pompes rotatives à haute pression
US3328094A (en) * 1964-02-29 1967-06-27 Philips Corp Axial bearings of the pump type
US3376083A (en) * 1965-03-27 1968-04-02 Philips Corp Axial bearing
US3497273A (en) * 1967-03-31 1970-02-24 Philips Corp Hydrodynamic bearing for axial and radial loads
US3663074A (en) * 1969-05-27 1972-05-16 Skf Ind Trading & Dev Arrangement in spiral groove bearings
US3712754A (en) * 1969-12-05 1973-01-23 Philips Corp Dosing device

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924962A (en) * 1973-09-14 1975-12-09 Cit Alcatel Molecular pumps of the drum type
US4227816A (en) * 1978-08-21 1980-10-14 Usm Corporation Rotary processor
WO1980002058A1 (en) * 1979-03-19 1980-10-02 L Kalashnikov Vane pump
WO1981000276A1 (en) * 1979-07-12 1981-02-05 P Staebler Lubricant metering pump
US4408966A (en) * 1979-12-27 1983-10-11 Matsushita Electric Industrial Co., Ltd. Pump for supplying liquid fuel
DE3347471A1 (de) * 1983-12-29 1985-07-11 Technion Research & Development Foundation Ltd., Haifa Hochdruckrotationspumpe niedriger kapazitaet
US4543037A (en) * 1984-01-16 1985-09-24 Technion Research & Development Foundation Limited Rotary high-pressure, low-capacity pump
US4899704A (en) * 1989-05-08 1990-02-13 Tecumseh Products Company Self-lubricating bearing
US5056715A (en) * 1990-02-21 1991-10-15 Pfizer Inc. Apparatus for mixing and spraying a slurry
US6506025B1 (en) * 1999-06-23 2003-01-14 California Institute Of Technology Bladeless pump
US20140308112A1 (en) * 2011-11-10 2014-10-16 Eagleburgmann Germany Gmbh & Co. Kg Slide ring seal arrangement with tesla pump
US20150292468A1 (en) * 2013-03-05 2015-10-15 Yugen Kaisha Nakanoseisakusho Rotation drive apparatus
US10267285B2 (en) * 2013-03-05 2019-04-23 Yugen Kaisha Nakanoseisakusho Rotation drive apparatus

Also Published As

Publication number Publication date
BE788140A (fr) 1973-02-28
NL7111948A (zh) 1973-03-02
IT964321B (it) 1974-01-21
DE2239857A1 (de) 1973-03-08
GB1400531A (en) 1975-07-16
AT321255B (de) 1975-03-25
FR2152023A5 (zh) 1973-04-20
JPS4833407A (zh) 1973-05-10

Similar Documents

Publication Publication Date Title
US3794449A (en) Viscosity pump
US2678607A (en) Constant pressure variable displacement pump
US3271086A (en) Device for maintaining constant the distance between adjacent surfaces of a reference body and a movable body subject to a variable external force
US2915985A (en) Pump
US3918855A (en) Adjustable vane pump
US4679995A (en) Variable capacity type pump with damping force on cam ring
US3669570A (en) Power regulation for fluid machines
US3442560A (en) Hydrostatic bearings
US4437819A (en) Controllable vane pump
US2842064A (en) Hydraulic pressure unit
GB1343518A (en) Journal support bearings for rotating shafts
US3221665A (en) Hydraulic pump or motor with hydraulic pressure-responsive vane
GB1069874A (en) Variable ratio transmission
US3729014A (en) Flow divider
US4222718A (en) Linear motion thrust block for hydraulic pumps and motors
US4118040A (en) Contactless seal
US3664776A (en) Variable volume vane pump
US3604823A (en) Vane tracking in rotary devices
US3126233A (en) royle
US3252423A (en) Variable volume vane type pump
US4340338A (en) Hydraulic pressure biased linear motion thrust block for hydraulic pumps and motors
US3788652A (en) Sealing devices for rotating shafts
EP0333278A1 (en) Static bearing
US3089427A (en) Hydraulic machines
US3583423A (en) Dosing device for gaseous or liquid substances