US3787151A - Stack-up assembly - Google Patents

Stack-up assembly Download PDF

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Publication number
US3787151A
US3787151A US00269766A US3787151DA US3787151A US 3787151 A US3787151 A US 3787151A US 00269766 A US00269766 A US 00269766A US 3787151D A US3787151D A US 3787151DA US 3787151 A US3787151 A US 3787151A
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United States
Prior art keywords
plate
pressure
pump
separator
pressure plate
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
US00269766A
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English (en)
Inventor
R Carlson
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.)
Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
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Filing date
Publication date
Application filed by TRW Inc filed Critical TRW Inc
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Publication of US3787151A publication Critical patent/US3787151A/en
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Expired - Lifetime legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • the pressure plate is relieved in areas under the 3,549,288 12/1970 Nichols et al... 418/133 sepamof P 2,3l2,89l 3/1943 Ferris 4. 418/133 3,057,304 10/1962 Rohde 418/133 7 Clam, 5 Drawmg 39 1/ 38 F3. 01 II II 42 29 H371 30 17 26 I I 34 a! 1 I 4 :1 ,a 33 60 12 I I: I 65 0 ,1
  • This invention relates to pumps and more particularly to a rotary slipper type pump.
  • Prior Art Rotary slipper pumps are well known and have found use in numerous embodiments. A particularly useful embodiment for such pumps, and one in which the instant invention will be described, is in automotive power steering pumps.
  • Such pumps include a pumping chamber defining member, commonly a ring with a varying radius inner diameter.
  • a pumping chamber defining member commonly a ring with a varying radius inner diameter.
  • a rotor having a plurality of radial slots therein which receive slippers disposed for radial movement.
  • the slippers move radially of the slots and the chambers defined between the inner diameter of the chamber-defining member and the outer diameter of the rotor and between adjacent slippers changes to compress fluid received between adjacent slippers.
  • the compressed fluid is ported through an end plate lying on one or both ends of the chamber-defining member and exits as a higher pressure fluid. It has been known, and it is common, to provide a separator plate adjacent one of the end plates.
  • the separator plate has orifices therethrough and the high pressure fluid passes through the orifices to chambers defined in a valve plate or closure plate located on the other side of the separator plate. These chambers then become high pressure channels and act to press the separator plate against the end plates.
  • the end plates in such instances may be referred to as pressure plates in that they are forced against the side walls of the chamber-defining member to create a tight seal. Because their opposed faces, which define the side walls of the pumping chamber, are in contact with both low and high pressure areas of the pumping chamber, the presence of a high pressure on the opposite side pressure balances them into maintaining a seal with the chamber-defining member.
  • the pump pressure can be extremely high and can therefore press the separator plate against the end plate or pressure plate to such a degree as to cause a bending or bowing in the center of the pressure plate which is not supported by contact with the ring-like chamber-defining member.
  • the pressure plate can be bowed into contact with the rotor or the slippers to an extent sufficient to increase the degree of torque necessary to rotate the rotor; In certain instances, this pressure against the rotor can be so excessive as to cause seizing of the rotor.
  • FIG. 1 is a cross-sectional view of a pump incorporating the teachings of this invention
  • FIG. 2 is a cross-sectional view taken along the lines IIII of FIG. 1, illustrating the separator plate;
  • FIG. 3 is a plan view of the one surface of the top pressure plate
  • FIG. 4 is a plan view of the other surface of the top pressure plate.
  • FIG. 5 is a simplified view of a pump equipped with the invention and illustrating force vectors.
  • FIG. 5 illustrates the forces at work in a pump of the type in which this invention may be practised.
  • the pump includes elements received in a pressure housing 90.
  • a pumping chamber defining member 91 Disposed within the pressure housing is a pumping chamber defining member 91 which has a continuous wall 92 surrounding a cavity, the wall being formed as a continuous closed curve having varying inner diameters.
  • a rotor 93 Disposed within the pumping chamber defining member.
  • the chamber 94 is closed at either end by pressure plates 95 and 96.
  • the lower pressure plate 95 is generally bottomed against a housing closure member, while the upper pressure plate 96 has its outer surface bottomed against a separator plate 97 which in turn has its outer surface bottomed against a valve body 98 received in the pressure housing 90.
  • Pressure developed in the chamber 94 is ported through at least the upper pressure plate and separator plate to the interior of the valve body and also to the interior of the pressure housing exterior of the valve body. The pressure thus developed, represented by the arrows P acts to force the valve body against the separator plate 97.
  • This pressure P representing a hydraulic pressure
  • This pressure P is transformed to a mechanical pressure at the interface between the valve body and the separator plate as indicated by the arrows F
  • the mechanical force F acting against the separator plate will be transmitted directly against the pressure plate if the two plates mate completely.
  • This pressure can tend to bow the pressure plate into the cavity 94 to the extent that there is an allowed end clearance 99. This can bring the pressure plate into contact with the rotor.
  • This invention overcomes this problem by providing a relief area 100 in a mating surface between the separator plate and upper pressure plate.
  • the relief area in FIG. 5 is illustrated as being in the upper pressure plate and is centrally disposed thereof.
  • the mechanical force P will be transmitted through the upper pressure plate at its periphery against the body of the pumping chamber defining member 92 as indicated by the arrows F Since at this point, the upper pressure plate 96 is supported directly by the wall of the pumping chamber defining member, the tendency of the upper pressure plate to bow inwardly towards the rotor in the central sections is minimized.
  • valve body separator plate and upper pressure plate Although the invention will hereinafter be disclosed in connection with a specific pump embodiment which utilizes a valve body separator plate and upper pressure plate, it is to be understood that the invention can be practised in other pumps which may eliminate one or more of these elements or which may substitute others in their place.
  • a pump could be designed where the valve body acts directly against the upper pressure plate. In such an instance, the forces would still be the same inasmuch as the force F would act against the upper pressure plate without the intermediary of the separator plate. This could still, however, cause the bowing of the upper pressure plate.
  • FIG. 1' illustrates a specific embodiment of this invention and shows an automotive power steering pump which includes a cup-shaped housing member 11 closed at its open end by a cap member 12 having a central bore 13 therethrough.
  • the bore 13 may include a sleeve bearing 14 and a shaft 15 is supported through the closure 12 in the opening 13.
  • the external end of the shaft 17 may be fitted with a driving means such as, by way of example, a pulley wheel 18 which may be operated by the vehicle engine drive belt.
  • the pumping section 20 of the pump 10 includes, in axial stacked-up relation, the closure cap 12, a first or bottom pressure plate 21, a chamber-defining ring member 22 which has a lobed or varying radius inner diameter 23 and which surrounds a rotor 24 carrying a plurality of slippers 25 in radial slots in the rotor, the slippers being positioned for radial and rocking movement in the grooves of the rotor and being expanded into contact with the inner diameter 23 by springs 26.
  • the rotor is splined onto the shaft 15.
  • the end 29 of the chamber-defining member 22 remote from the first pressure plate 21 is closed by a second pressure plate 30.
  • the opposite side of the pressure plate 30 from the chamber-defining member is contacted by a separator plate 31 which in turn has its outer surface 32 contacted by a valve plate 33.
  • An inner cup-shaped housing 34 has a flanged open end 35 riding on a radial face 36 which extends radially outwardly from the pressure plate contacting face 37 of the end cap 12.
  • the inner cup-shaped housing 34 encloses the stacked first pressure plate 21, the pumping chamber defining member 22, and its enclosed rotor 24 and slippers 25, the second pressure plate 30, separator plate 31 and valve plate 33 while providing an area 37 beyond the valve plate 33.
  • the entire assemblage is received within the cup-shaped housing 11 which contacts an outer diameter surface 38 of the end cap 12. Seals 39 may be interposed between the end cap 12 and the cup-shaped housing 11 and gasket seals 40 may be interposed between the radial face 36 and the flange 35 of the inner cup-shaped housing 34.
  • a seal 42 is interposed between the inner cup-shaped housing 34 and the outer diameter surface of the valve plate 33 which divides the inner cupshaped housing into a high pressure area 37 and a lower pressure area 44 radially outwardly of the pressure plates and pumping chamber.
  • a discharge outlets 45 is communicated through the outer 11 and inner cup-shaped housings 34 to 'an area 46 interior of the valve plate 33.
  • a port 47 communicates the area 37 to the conduit 48 between the valve plate and the outlets 45.
  • a return 49 communicates the exterior to the low pressure area 50 between the outer 11 and inner 34 cup-shaped housings and a fill cap 51 is also provided communicating to the area 50.
  • the area 50 is also communicated to the area 44 to provide a flow of low-pressure fluid to the area 44.
  • the area 50 is maintained in a flooded state with low-pressure fluid which is ported through the first and second pressure plates 21 and 30 to low pressure areas of the pumping chamber inwardly of the pumping chamber defining member 22.
  • the pressure of the fluid is increased and then ported again through the pressure plates to channel 60 in the valve plate.
  • the channel 60 opens to a valve area 61 which in turn is communicated to the discharge conduit 48 through a port 62.
  • the channels 60 are open to the separator plate 32 which in turn has discharge ports to open to the outlet openings in the pressure plates.
  • the outlet openings of the first pressure plate 21 are in communication with outlet openings in the second pressure plate through axially extending channels in the ring-shaped chamberdefining member 22.
  • the pressure in the channels 60 can become quite large. At times this pressure can become so large as to press the separator plate 31 against the second pressure plate 30 to an extent sufficient to bow or bend the second pressure plate 30 inwardly towards the rotor. Because the outer peripheral areas of the pressure plate 30 are supported on the radial face of the chamber-defining member, the central section of the pressure plate will be pressed into contact with the rotor and slippers. When this pressure becomes excessive, it can increase frictional contact between the pressure plate and the rotating rotor and slippers to an extent sufficient to adversely affect the operation of the pump and, in extreme circumstances, can cause the rotor to seize. It is a primary object of this invention to prevent this from occurring.
  • FIG. 3 illustrates the second pressure plate 30 and is a plan view of the face 58 thereof which contacts the separator plate 31 illustrated in FIG. 2.
  • FIG. 4 is a plan view of the pressure plate 30 illustrating the face 59 and the back side of the view of FIG. 3.
  • the separator plate 30 includes inlet openings circumferentially spaced from one another and open to the periphery 71 of the pressure plate.
  • Minor inlet openings 72 are disposed radially inwardly of the opening 70 and are in communication therewith through a reduced axial thickness area 73.
  • the minor inlets 72 communicate to the slipper receiving grooves in the rotor.
  • circumferentially spaced from the inlets 70 are outlet openings 74 which are aligned with the highpressure portions of the chambers defined by the lobed or varying radius inner diameter of the chamberdefining member and the outer diameter of the rotor.
  • Minor outlets 75 are disposed radially inwardly of the outlet 74 and communicate to the bottoms of the slipper receiving grooves.
  • the outlets 74 and 75 are ported to the discharge ports of the separator plate 31 which in turn is open to the channels 60 in the valve plate.
  • the separator plate contacts the surface 58 of the pressure plate and separates the inlet openings and outlet openings and is pressed against the face 58 to maintain the separation of the openings.
  • the portions which I have chosen to recess are those areas which do not include or surround the high pressure outlet openings and the dowel pin receiving openings 86 which align the members.
  • two circumferentially spaced lands 87 and 88 are therefore provided which are raised above the recessed area 85.
  • the lands 87, 88 are diametrically opposed from one another and contain the opposed outlet 74 and minor outlet 75 as well as the dowel pin openings 86.
  • the remainder of the surface 58 is recessed which results in a communication of the inlet openings 72 and 73 with each other across the diameter of the pressure plate.
  • the separator plate 31 may bow inwardly towards the rotor without contacting the central section of the pressure plate. Therefore, the pressure plate will not be forced against the rotor in the central section. At the same time, the separator plate is maintained in continuous contact with peripheral areas of the pressure plate and particularly in the raised areas 87, 88.
  • my invention provides a stack-up slipper pump wherein a recess area is provided between the pressure plate and the separator plate to prevent the separator plate from being forced into contact with the outer surface of the pressure plate to an extent sufficient to bend the pressure plate into excessive seizing.
  • a fluid pressure loaded pump having a stack of pump components loaded by an end plate and including a member defining a pumping chamber with fluid inlet and outlet passages, a rotor in the pumping chamber, a pressure plate bottomed on said member and covering the rotor, a separator plate overlying the pressure plate receiving the end plate thereagainst, said end plate having outlet channels, said pressure and separator plates having outlet ports registering with said channels, and said pressure and separator plates having surfaces in sealed mated engagement around the ports thereof together with a gap between the separator and pressure plates in the central portion thereof vented to the fluid inlet effective to prevent bowing of the pressure plate against the rotor under fluid pressure loading of the stack of components.
  • a pump having a stack of pressure loaded pump components including a member defining a pump chamber, a pump rotor rotatably mounted in said chamber, a pressure plate bottomed on the member providing an end wall for the pump chamber and having inlet and outlet ports conveying fluid to and from the pump chamber, a separator plate overlying the pressure plate having outlet ports registering with the outlet ports of the pressure plate, and an end plate bottomed on the separator plate having outlet ports communicating with the outlet ports of said separator plate, the improvements of land areas surrounding the outlet ports of the pressure plate seated on the separator plate around the outlet ports of the separator plate to seal the outlet ports from the inlet ports and a gap between the separator and pressure plates communicating with the inlet ports of the pressure plate and effective to prevent deformation of the pressure plate against the rotor under pressures developed by the pump.
  • Arotary pump comprising a housing, and end cap for the housing, a shaft rotatably supported in said end cap extending into the housing, an axial stack-up of pump parts in said housing including a bottom pressure plate bottomed on the end cap, a pumping chamber defining ring bottomed on the bottom pressure plate, a pump rotor in said ring coupled to said shaft, a second pressure plate bottomed on said ring, a separator plate bottomed on said second pressure plate, and a valve plate with an outlet passage bottomed on said separator plate, slippers carried by said rotor riding in said ring, seal means between the valve plate and housing separating the interior of the housing into an inlet chamber and a pressure chamber, said second pressure plate having inlets joining the inlet chamber of the housing with the interior of the chamber defining ring to supply fluid to be pumped by said slippers, said second pressure plate and separator plate having outlet ports joining the interior of the chamber defining ring with the outlet passage of the valve plate, means venting said pressure chamber in said housing

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US00269766A 1972-07-07 1972-07-07 Stack-up assembly Expired - Lifetime US3787151A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US26976672A 1972-07-07 1972-07-07

Publications (1)

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US3787151A true US3787151A (en) 1974-01-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00269766A Expired - Lifetime US3787151A (en) 1972-07-07 1972-07-07 Stack-up assembly

Country Status (7)

Country Link
US (1) US3787151A (enrdf_load_stackoverflow)
JP (1) JPS5330363B2 (enrdf_load_stackoverflow)
BR (1) BR7305048D0 (enrdf_load_stackoverflow)
CA (1) CA984672A (enrdf_load_stackoverflow)
FR (1) FR2192622A5 (enrdf_load_stackoverflow)
GB (1) GB1424077A (enrdf_load_stackoverflow)
IT (1) IT991048B (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4201521A (en) * 1978-03-20 1980-05-06 Trw Inc. Pump and motor assembly
US4207033A (en) * 1976-12-06 1980-06-10 Trw Inc. Pump and motor assembly for use in regulating a flow of fuel from a source of fuel to an operating chamber of an engine of a vehicle
US4416598A (en) * 1980-05-16 1983-11-22 Zahnradfabrik Friedrichshafen, Ag. Rotary vane pump with pressure biased flow directing end plate
US5380178A (en) * 1994-02-10 1995-01-10 Trw Inc. Rotary device and method of assembly
US6152716A (en) * 1996-06-21 2000-11-28 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Vane pump
CN106030111A (zh) * 2014-01-27 2016-10-12 Ｋｙｂ株式会社 叶片泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4072450A (en) * 1976-01-12 1978-02-07 Trw Inc. Pump assembly
US20140083478A1 (en) * 2011-04-19 2014-03-27 Hokkaido Tokushushiryou Kabushikikaisha Combustion Device, Combustion Method, and Electric Power-Generating Device and Electric Power-Generating Method Using Same

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2312891A (en) * 1939-05-19 1943-03-02 Oilgear Co Hydrodynamic machine
US3029794A (en) * 1960-03-02 1962-04-17 Ammco Tools Inc Rotary fluid motors
US3057304A (en) * 1960-02-03 1962-10-09 Gen Motors Corp Vane pump
US3200752A (en) * 1963-05-16 1965-08-17 Thompson Ramo Wooldridge Inc Stack-up slipper pump with integral flow control valve
US3430574A (en) * 1967-05-17 1969-03-04 Webster Electric Co Inc Plural rotary hydraulic apparatus
US3549288A (en) * 1969-03-05 1970-12-22 Ford Motor Co Positive displacement slipper pump with flangeless drive shaft

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2312891A (en) * 1939-05-19 1943-03-02 Oilgear Co Hydrodynamic machine
US3057304A (en) * 1960-02-03 1962-10-09 Gen Motors Corp Vane pump
US3029794A (en) * 1960-03-02 1962-04-17 Ammco Tools Inc Rotary fluid motors
US3200752A (en) * 1963-05-16 1965-08-17 Thompson Ramo Wooldridge Inc Stack-up slipper pump with integral flow control valve
US3430574A (en) * 1967-05-17 1969-03-04 Webster Electric Co Inc Plural rotary hydraulic apparatus
US3549288A (en) * 1969-03-05 1970-12-22 Ford Motor Co Positive displacement slipper pump with flangeless drive shaft

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4207033A (en) * 1976-12-06 1980-06-10 Trw Inc. Pump and motor assembly for use in regulating a flow of fuel from a source of fuel to an operating chamber of an engine of a vehicle
US4201521A (en) * 1978-03-20 1980-05-06 Trw Inc. Pump and motor assembly
US4416598A (en) * 1980-05-16 1983-11-22 Zahnradfabrik Friedrichshafen, Ag. Rotary vane pump with pressure biased flow directing end plate
US5380178A (en) * 1994-02-10 1995-01-10 Trw Inc. Rotary device and method of assembly
US6152716A (en) * 1996-06-21 2000-11-28 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Vane pump
CN106030111A (zh) * 2014-01-27 2016-10-12 Ｋｙｂ株式会社 叶片泵
US9897086B2 (en) 2014-01-27 2018-02-20 Kyb Corporation Vane pump
CN106030111B (zh) * 2014-01-27 2018-03-13 Ｋｙｂ株式会社 叶片泵

Also Published As

Publication number Publication date
JPS5330363B2 (enrdf_load_stackoverflow) 1978-08-26
DE2334484B2 (de) 1976-06-10
JPS4944304A (enrdf_load_stackoverflow) 1974-04-26
FR2192622A5 (enrdf_load_stackoverflow) 1974-02-08
BR7305048D0 (pt) 1974-08-15
GB1424077A (en) 1976-02-04
CA984672A (en) 1976-03-02
DE2334484A1 (de) 1974-01-24
IT991048B (it) 1975-07-30

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