EP2604790A2 - Pompe hydraulique à palettes à écoulements multiples - Google Patents

Pompe hydraulique à palettes à écoulements multiples Download PDF

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Publication number
EP2604790A2
EP2604790A2 EP12250181.0A EP12250181A EP2604790A2 EP 2604790 A2 EP2604790 A2 EP 2604790A2 EP 12250181 A EP12250181 A EP 12250181A EP 2604790 A2 EP2604790 A2 EP 2604790A2
Authority
EP
European Patent Office
Prior art keywords
fluid
rotor
discharge
vane
pump
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.)
Withdrawn
Application number
EP12250181.0A
Other languages
German (de)
English (en)
Inventor
Xingen Dong
Paul J. Paluszewski
Mihir C. Desai
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.)
Triumph Engine Control Systems LLC
Original Assignee
Goodrich Pump and Engine Control Systems Inc
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 Goodrich Pump and Engine Control Systems Inc filed Critical Goodrich Pump and Engine Control Systems Inc
Publication of EP2604790A2 publication Critical patent/EP2604790A2/fr
Withdrawn legal-status Critical Current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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear 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
    • F04C15/0096—Heating; Cooling
    • 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
    • F04C2220/00—Application
    • F04C2220/24—Application for metering throughflow
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/801—Wear plates

Definitions

  • the subject disclosure is directed to rotary vane pumps, and more particularly, to a balanced split discharge vane pump that provides a combined discharge flow for high fluid demand conditions and a first (primary) discharge flow for low fluid demand conditions, and stili more particularly to a multi-discharge vane pump that has an inlet port and four discharge ports, includes a floating side wear disk and a cam ring with internal flow passages, and a rotor assembly with improved under-vane pumping features.
  • Rotary hydraulic vane pumps are well known in the art, as disclosed for example in U.S. Patent No. 4,274,817 to Sakamaki et al. and U.S. Patent No. 5,064,362 to Hansen.
  • a typical rotary vane pump includes a circular rotor mounted for rotation within a larger circular pumping chamber. The centers of these two circles are typically offset, causing eccentricity. Vanes are mounted to slide in and out of the rotor to create a plurality of volume chambers or vane buckets that perform the pumping work. On the intake side of the pump, the vane buckets increase in volume. These increasing volume vane buckets are filled with fluid that is forced into the pumping chamber by an inlet pressure. On the discharge side of the pump, the vane buckets decrease in volume, forcing pressurized fluid out of the pumping chamber.
  • U.S. Patent Application Publication No. 2010/0316507 entitled Split Discharge Vane Pump and Fluid Metering System Therefor, discloses a positive displacement vane pump that is adapted and configured to more closely match the operating characteristics of the system with which it is associated, as well as, a valving arrangement for effectively managing the flow of fluid from the pump depending upon the fluid demand conditions of the system with which it is associated.
  • the disclosure of U.S. Patent Application Publication No. 2010/0316507 is hereby incorporated by reference in its entirety.
  • the present invention is directed to a hydraulic vane pump that includes, inter alia, a pump body that defines an interior pumping chamber and an inlet port for allowing fluid to be provided to the interior pumping chamber and at least one discharge port for allowing pressurized fluid to be discharged from the interior pumping chamber.
  • the pump further includes a cam ring that is disposed within the interior pumping chamber and defines a continuous peripheral cam surface; and a rotor mounted for axial rotation within the interior pumping chamber and defining a pump axis.
  • a plurality of circumferentially spaced apart radially extending vanes are mounted for radial movement within slots formed in the rotor, the plurality of vanes define an equal number of circumferentially spaced apart volume chambers which extend between an outer periphery of the rotor and the cam surface for carrying pressurized fluid.
  • the pump includes axially opposed first and second wear disks disposed within the interior pumping chamber.
  • the first wear disk has an outer periphery which is positioned radially inward of the cam surface and is adapted and configured to slide axially with respect to the cam surface, so as to provide for thermal expansion of the rotor and vanes.
  • the second wear disk is fixedly positioned adjacent to a second end surface of the rotor.
  • the second wear disk can also be a floating disk (i.e., adapted for sliding in the axial direction).
  • the pump is a multi-discharge hydraulic vane pump and the pump body defines four radially-oriented discharge ports, each discharge port allowing pressurized fluid to be discharged from the interior pumping chamber.
  • first wear disk is biased towards the first end surface of the rotor using a spring element.
  • first wear disk can be biased towards the first end surface of the rotor using pressurized fluid discharged from the volume chambers defined by the vanes.
  • the pump body further includes a rear side plate and the inlet port extends axially through the rear side plate to the interior chamber.
  • the cam surface includes four quadrantal cam segments, wherein diametrically opposed cam segments have identical cam profiles, and each cam segment defines an inlet arc, a discharge are and two seal arcs.
  • the cam ring includes a plurality of inlet chambers arranged and configured to receive fluid from the inlet port and distribute the fluid to the inlet arc of each cam segment.
  • the cam ring can also includes a plurality of discharge chambers which communicate with the discharge arc of each cam segment and are arranged and configured to facilitate the discharge of pressurized fluid from the interior pumping chamber.
  • each vane slot has an under-vane pocket for receiving pressurized fluid based on an angular position of the rotor.
  • the rotor includes a plurality of axially-extending under-vane passages, each under-vane passage communicating with an under-vane pocket through a connector passage.
  • each wear disk includes flow passages for communicating fluid into the under-vane pockets and under-vane passages associated with each vane slot.
  • the pressure of the undervane pocket is dependent on an angular position of the rotor.
  • the fluid in the rotor under-vane passage whilst positioned in the inlet arc segment is about equal to pump inlet pressure and the fluid in the rotor under-vane passage whilst positioned in the discharge arc segment is about equal to pump discharge pressure.
  • Certain constructions of the vane pump of present invention include a fluid metering system for extracting fluid flow from the discharge arcs of the four cam segments. It is envisioned that the metering system has a first operating condition in which fluid is extracted from the discharge arcs of all four cam segments and combined for delivery to a source of fluid demand.
  • the fluid metering system can also include a second operating condition wherein fluid is extracted from a first (primary) pair of diametrically opposed discharge arcs for delivery to a source of fluid demand and fluid from a second pair of diametrically opposed discharge arcs bypasses the source of fluid demand and returns to the pumping chamber.
  • the present invention is also directed to a multi-discharge hydraulic vane pump that includes, among other elements, a pump body that has an interior pumping chamber and defines a axially extending inlet port for allowing fluid to be provided to the interior pumping chamber and four radially-extending discharge ports for allowing pressurized fluid to be discharged from the interior pumping chamber.
  • the vane pump further includes a cam ring disposed within the interior pumping chamber that defines a continuous peripheral cam surface and a rotor mounted for axial rotation within the interior pumping chamber that defines a pump axis.
  • a plurality of circumferentially spaced apart and radially extending vanes are mounted for radial movement within slots formed in the rotor.
  • the plurality of vanes define an equal number of circumferentially spaced apart volume chambers which extend between an outer periphery of the rotor and the cam surface for carrying pressurized fluid.
  • the pump further includes axially opposed first and second wear disks which are disposed within the interior pumping chamber.
  • the first wear disk has an outer periphery which is positioned radially inward of the cam surface and is mounted for sliding movement with respect to the cam surface, so as to provide for thermal expansion of the rotor and vanes.
  • the second wear disk is positioned adjacent to a second end surface of the rotor.
  • first wear disk is biased towards the first end surface of the rotor using a spring element.
  • first wear disk can be biased towards the first end surface of the rotor using pressurized fluid discharged from the volume chambers defined by the vanes.
  • the pump body further includes a rear housing with an inlet port that extends axially through the rear side plate to the interior chamber.
  • the cam surface includes four quadrantal cam segments, wherein diametrically opposed cam segments have identical cam profiles, and each cam segment defines an inlet arc, a discharge arc and two seal arcs.
  • the cam ring includes a plurality of inlet chambers arranged and configured to receive fluid from the inlet port and distribute the fluid to the inlet arc of each cam segment.
  • the cam ring also includes a plurality of discharge chambers which communicate with the discharge arc of each cam segment and are arranged and configured to facilitate the discharge of pressurized fluid from the interior pumping chamber.
  • each vane slot has an under-vane pocket for receiving either low inlet or discharging high outlet pressurized fluid based on an angular position of the rotor.
  • the rotor includes a plurality of axially-extending under-vane passages, each under-vane passage communicating with an under-vane pocket through a connector passage.
  • each wear disk can includes flow passages for communicating fluid into the under-vane pockets and under-vane passages associated with each vane slot.
  • the pressure of the undervane pocket in dependent on an angular position of the rotor.
  • the pressurized fluid in the rotor under-vane passage whilst positioned in the inlet arc segment is about equal to pump inlet pressure and the fluid in the rotor under-vane passage whilst positioned in the discharge arc segment is about equal to pump discharge pressure.
  • Certain constructions of the vane pump of present invention include a fluid metering system for extracting fluid flow from the discharge arcs of the four cam segments. It is envisioned that the metering system has a first operating condition in which fluid is extracted from the discharge arcs of all four cam segments and combined for delivery to a source of fluid demand.
  • the fluid metering system can also include a second operating condition wherein fluid is extracted from a first pair of diametrically opposed discharge arcs for delivery to a source of fluid demand and fluid from a second pair of diametrically opposed discharge arcs bypasses the source of fluid demand and returns to the pumping chamber.
  • the present invention is further directed to a hydraulic vane pump that includes, inter atia, a pump body that defines an interior pumping chamber, an inlet port for allowing fluid to be provided to the interior pumping chamber and at least one discharge port for allowing pressurized fluid to be discharged from the interior pumping chamber.
  • the hydraulic vane pump further includes a cam ring disposed within the interior pumping chamber that defines a continuous peripheral cam surface, the cam ring also defining a plurality of inlet chambers and discharge chambers.
  • the inlet chambers are arranged and configured to receive fluid from the inlet port and to distribute the fluid to the interior pumping chamber and the discharge chambers communicate with the interior pumping chamber and are arranged and configured to facilitate the discharge of pressurized fluid from the interior pumping chamber.
  • a rotor is mounted for axial rotation within the interior pumping chamber and defines a pump axis.
  • a plurality of circumferentially spaced apart and radially extending vanes are mounted for radial movement within slots formed in the rotor.
  • the plurality of vanes define an equal number of circumferentially spaced apart volume chambers which extend between an outer periphery of the rotor and the cam surface for carrying pressurized fluid.
  • Each vane slot has an under-vane pocket for communicating fluid. The pressure in the undervane pockets are dependent on an angular position of the rotor.
  • first and second wear disks are disposed within the interior pumping chamber, the first wear disk has an outer periphery which is positioned radially inward of the cam surface and is axially biased towards a first end surface of the rotor, so as to provide for thermal expansion of the rotor and vanes.
  • the second wear disk is positioned adjacent to a second end surface of the rotor.
  • each wear disk includes flow passages for communicating fluid into the under-vane pockets associated with each vane slot. The pressure of the undervane pockets is dependant on an angular position of the rotor.
  • FIG. 1 is a perspective view of a multi-discharge pump assembly which has been constructed in accordance with a preferred embodiment of the present invention
  • FIG. 2 is a partially exploded perspective view of the pump assembly of FIG. 1 in which a front side plate has been removed for ease of illustration;
  • FIG. 3 is an exploded perspective view of the cam ring, the rotor assembly, the annular spacer and the rear side plate used in the pump assembly of FIG. 1 ;
  • FIGS. 4 provides a end view of a rear side plate used in the pump assembly of FIG. 1 ;
  • FIG. 5 provides a cross-sectional view of the rear side plate shown in FIG. 4 taken along cut line 5-5;
  • FIG. 6 provides a cross-sectional view of the rear side plate shown in FIG. 4 taken along cut line 6-6;
  • FIG. 7 is an exploded view of a portion of the pump assembly of FIG. 1 which illustrates the front side fixed wear plate, the rotor assembly, the cam ring and the rear side sliding wear plate;
  • FIG. 8 is a perspective view of the rotor assembly used in the pump assembly of FIG. 1 ;
  • FIG. 9 is a cross-sectional view of the rotor assembly of FIG. 8 taken along cut line 9-9;
  • FIG. 10 is a perspective view of the cam ring used in the pump assembly of FIG. 1 ;
  • FIG. 11 is an end view of the cam ring of FIG. 10 ;
  • FIG. 12 provides a perspective view of the rear side floating disk used in the pump assembly of FIG. 1 ;
  • FIG. 13 is a front end view of the floating wear disk of FIG. 12 ;
  • FIG. 14 is a rear end view of the floating wear disk of FIG. 12 ;
  • FIG. 15 is a cross-sectional view taken along cut line 15-15 of the floating wear disk of FIG. 12 ;
  • FIG. 16 provides a perspective view of the front side fixed wear disk used in the pump assembly of FIG. 7 ;
  • FIG. 17 is a front end view of the fixed wear disk of FIG. 16 ;
  • FIG. 18 is a rear end view of the fixed wear disk of FIG. 16 ;
  • FIG. 19 is sectional view of the pump assembly shown in FIG. 1 which illustrates that when the vanes are within the seal arc, the under-vane cavities are connected to pump discharge passages;
  • FIG. 20 is a cross-sectional view of the pump assembly shown in FIG. 1 taken along cut line 20-20 in FIG. 19 ;
  • FIG. 21 is sectional view of the pump assembly shown in FIG. 1 taken along cut line 21-21 which illustrates that when the vanes are within the discharge ramp/arc, the over-vane and under-vane cavities are connected to pump discharge passages;
  • FIG. 22 is sectional view of the pump assembly shown in FIG. 1 taken along cut line 22-22 which illustrates that when the vanes are within the inlet ramp/are, the over-vane and under-vane cavities are connected to pump inlet passages; and
  • FIG. 23 provides a cross-sectional view of the rotor assembly and a portion of the cam ring.
  • FIG. 1 an embodiment of the hydrostatically-balance, multi-discharge hydraulic vane pump of the present invention designated generally by reference numeral 10 which includes a cartridge assembly pumping element (item 90 in Fig. 7 ).
  • the cartridge assembly 90 is configured to fit within a reusable housing (annular space 16).
  • the pump element 90 can be readily replaced when worn or in need of repair.
  • FIGS. 2 through 18 provide views of the various component parts that form the pump element 90 and FIGS. 19 through 23 provide cross-sectional and elevational views for pump assembly 10 in a variety of operating configurations.
  • Pump assembly 10 includes a single inlet port 24 (see FIGS. 19-22 ) for admitting low pressure fluid into the pump assembly 10.
  • Pump assembly 10 also includes four discharge ports 30a-d for discharging pressurized fluid from the pump assembly 10.
  • Discharge ports 30a and 30c diametrically oppose each other.
  • discharge ports 30b and 30d diametrically oppose each other. Normally, 30a/30c or 30b/30d for one of two pumps.
  • the low pressure fluid By passing through the pump assembly 10, the low pressure fluid becomes high pressure fluid and exits the pump assembly through either two diametrically opposed discharge ports 30a-d or through all of the discharge ports.
  • the manner in which the low pressure fluid proceeds from the inlet port 24 into the interior pump chamber 42, is pressurized and is supplied to the discharge ports 30a-d will be discussed in detail herein below.
  • the forces generated in the pumping process thereby effectively cancel to provide a balanced pump assembly 10.
  • the pump assembly 10 also includes fixed front and rear side plates 80s, 80b, which are separated from one another by an annular spacer 16.
  • the inlet port 24 is formed in the rear side plate 80b.
  • the discharge ports 30a-30d are formed in the annular spacer 16.
  • An end plate 22 is fixed to the front side plate 80a using a series of bolts 27a-f and defines an axial passageway 26 through which a drive shaft 28a passes to attach to a rotor assembly 70.
  • the front and rear side plates 80a, 80b, along with the annular spacer 16, combine to form an interior or pumping chamber 42 that houses a cam ring 90, a floating side wear disk 50, a fixed side wear disk 60 and the rotor assembly 70 (see FIG. 3 ).
  • FIG. 2 a perspective view of the pump assembly 10 is shown with the front side plate 80a removed to illustrate the rotor assembly 70 and the cam ring 90 housed in the pumping chamber 42 and having a front end abutting the fixed side wear disk 60.
  • FIG. 3 provides an additional exploded perspective view in which the cam ring 90, fixed side wear disk 60, floating wear disk 50 and the rotor assembly 70 have been removed from within the interior pumping chamber 42.
  • the rotor assembly 70 which is best viewed in FIGS. 8 and 9 , is mounted on a drive shaft 28b for axial rotation within the pumping chamber 42.
  • the rotor assembly is supported for rotation within the pumping chamber 42 by two journal bearings which are associated with the side wear disks 50/60.
  • rotor drive shaft 28b engages with drive shaft 28a which extends outside of the front side plate 80a.
  • Rotor assembly 70 includes a rotor body 71, which fits within a pumping chamber surface 35 defined by cam ring 90 (best shown in FIG. 11 ).
  • the rotor body 71 includes a plurality of radially outwardly acting vane elements 36 which normally contact the elliptical pumping chamber surface 35.
  • a plurality of circumferential vane buckets or volume chambers 44 are formed between the rotor body 71, the elliptical pumping chamber surface 35, the vane assemblies 36 and the wear disks 50/60 (see FIG. 20 ).
  • rotor body 71 For each vane element 36, rotor body 71 includes a vane slot 38 into which the vane element is slidably received, an axially extending under-vane pumping pocket 73 and an axially extending under-vane pumping passage 75. Radially extending, but angled, connector passages 77, allow fluid to communicate between the under-vane pumping pocket 73 and under-vane pumping passage 75.
  • FIGS. 4 through 6 provide several views of rear housing plate 80b.
  • Eight through holes 82 are provided in the outer flanges of the front and rear housing plates 80a/80b which allow the rear housing plate 80b and the front housing plate 80a to be secured to the annular spacer 16 using through bolts and associated nuts (see FIG. 1 ).
  • the axial inlet port 24 for the pump assembly 10 is formed in the rear side plate 80b and branches off into four diametrically opposed angled inlet channels 84.
  • These inlet channels 84 can also been viewed in FIG. 3 and as will be discussed below are arranged and configured so as to distribute the incoming fluid into four axially extending inlet chambers 92 formed in cam ring 90.
  • cam ring 90 in addition to the axially extending inlet chambers 92, cam ring 90 also defines axially extending discharge chambers 94. Still further, the outer periphery 96 of the cam ring 90 also includes a plurality of access slots 108 which are used to enable the formation of radially extending ports 104/106 which extend through the inner wall 102 of the cam ring 90 to the pumping chamber surface 35. Ports 104 extend radially inward from the inlet chambers 92 and ports 106 extend radially inward from the discharge chambers 94. The purpose of the flow ports 104/106 will also be discussed below.
  • the cam ring 90 is also provided with a number of seal grooves.
  • the outer periphery 96 of the cam ring 12 includes a plurality of seal grooves 98 which are adapted and configured for receiving linear sealing elements.
  • Each end of the cam ring 90 also includes a circular seal groove 99 and the pumping chamber surface 35 includes front and rear circumferential seal grooves 97.
  • the seals inserted into the seal grooves 97/98/99 are designed to prevent cross port leakage throughout the pump assembly 10.
  • floating wear disk 50 As shown in FIG. 19 , unlike prior art wear disks, which are fixedly positioned outside and adjacent to the end of the cam ring, floating wear disk 50 is positioned entirely within the inside profile of the cam ring 90 and is adapted for sliding in an axial direction to allow for thermal expansion of the rotor assembly during operation. However, unlike prior art devices wherein the axial gap between the wear disk and the rotor must be minimized in order to prevent cross port leakage, in pump assembly 10 it is the circumferential gap between the floating wear disk 50 and the pumping chamber surface which must be sealed. Since the circumferential gap is much less impacted by thermal expansion during operation of the pump, it is easier to maintain the seal in this location.
  • floating wear disk 50 includes a plurality of fluid ports which allow fluid to communicate with pump assembly 10.
  • eight radial holes 52 are provided which extend from the outer periphery of the floating wear disk 50.
  • Four of the radial holes 52 connect with four axially extending discharge fluid ports 54 and the other four radial holes 52 connect with four axially extending inlet fluid ports 56.
  • the discharge fluid ports 54 are used to allow pressurized discharge fluid to be provided to the under-vane slots and under-vane passages to used for under-vane pumping and the inlet fluid ports 56 are used to allow low pressure inlet fluid to be provided to the under-vane slots and under-vane passages to be used for under-vane pumping.
  • the floating wear disk 50 is also provided with a journal bearing 58 which supports one end of the rotor assembly 70 within the pumping chamber 52.
  • Four seal grooves 53 are provided on the rear face of the floating wear disk 50 and are adapted for receiving a face seal
  • eight spring cavities 55 are formed in the rear face of the floating wear disk 50 and contain a spring element or biasing mechanism for urging the floating wear disk 50 in the direction of the rotor assembly 70.
  • a small hole 59 extends from each of the discharge fluid ports 54 to the rear face of the floating wear disk 50.
  • the configuration and location of the seal grooves 53 defines a load area against which the pressurized discharge fluid works in order to urge the floating wear disk 50 towards the rotor assembly 70.
  • the amount of pressure applied to the back side of the wear disk 50 can be adjusted by adjusting the load area upon which the discharge fluid works.
  • FIGS. 16 through 18 illustrate the fixed side wear disk 60 used in the pump assembly 10 of the present invention.
  • the fixed side wear disk 60 includes a journal bearing 68 and a plurality of radial holes 62.
  • Four axially extending discharge fluid ports 64 communicate with four of the radial holes 62 and four radially extending inlet fluid ports 66 communicate with the remaining four radial holes 62.
  • discharge fluid ports 64 and inlet fluid ports 66 are used to provide fluid in support of under-vane pumping.
  • the back side of the fixed side wear disk 60 includes circular pressure relief groves 67a/67b and four radially extending pressure relief grooves 69a-d. It should be noted that both the floating side wear disk and the fixed side wear disk include slots for receiving a pin which prevents the disks 50/60 from rotating with respect to the cam ring 90.
  • FIGS. 19 through 23 illustrate the arrangement of the component parts used in pump assembly 10 and the manner in which the pump assembly operates to increase the pressure of the inlet fluid.
  • fluid is received in inlet port 24 and is diverted into the four inlet channels 84.
  • the four inlet channels 84 provide the fluid to the four axially extending inlet chambers 92 formed in the cam ring 90. From the inlet chambers 92 the fluid is directed radially inward through the radially extending inlet ports 104.
  • the end two ports 104 provide fluid to four radial holes 52/62 formed in the wear disks 50 and 60 respectively, and this fluid is used for under-vane pumping.
  • the fluid proceeding through the remaining ports 104 formed in the cam ring 90 is supplied into vane buckets 44 which are in the four inlet arc regions "I" shown in FIG. 23 .
  • the fluid is displaced and exits the vane buckets 44 in the discharge arc region "D" through the interior-most ports 106 formed in the cam ring 90 and is received into the four axially extending discharge chambers 94.
  • a portion of the pressurized fluid contained in the discharge chamber 94 is provided to the discharge fluid ports 54/64 of the wear disks 50/60 via radial holes 52/62 and is used for under-vane pumping.
  • the remaining pressurized fluid contained with the four axially extending discharge chambers 94 formed in the cam ring 90 is provided to the four discharge ports 30a-d of the pump assembly 10.
  • FIG. 19 is sectional view of the pump assembly shown in FIG. 1 which illustrates that when the vanes 36 are within the seal are "S", the under-vane slot 75 and the under-vane passage 73 are connected to pump discharge passages which are formed in the wear disks 50/60 and the cam ring 90.
  • FIG. 20 is a cross-sectional view of the pump assembly shown in FIG. 1 taken along cut line 20-20 in FIG. 19 .
  • FIG. 21 is sectional view of the pump assembly shown in FIG. 1 which illustrates that when the vanes 36 are within the discharge ramp/are "D", the over-vane 44 and under-vane cavities 73/75/77 are connected to pump discharge passages which are formed in the wear disks 50/60 and the cam ring 90.
  • FIG. 22 is sectional view of the pump assembly shown in FIG. 1 which illustrates that when the vanes 36 are within the inlet ramp/are "I", the over-vane and under-vane cavities are connected to pump inlet passages which are formed in the wear disks 50/60 and the cam ring 90.
  • the wear disks are fixedly mounted within the interior pumping chamber and abut the axial ends of the cam ring and rotor blade.
  • the front side wear disk 50 is a floating wear disk which is located radially inside of the pumping chamber surface 35 defined by the cam ring 90.
  • Previously disclosed vane pump designs usually have a fixed axial clearance between the wear disk and the rotor. Moreover, the wear plates/disks at both side of the rotor/vane are fixed. For a fixed axial clearance design, the longer the rotor, the more axial clearance is needed considering free thermal expansion of the rotor and vanes. At high operating temperatures, the amount of available clearance between the rotor and wear disks could be significantly reduced due to rotor/vane expansion. As a result, mechanical galling and premature wear could occur at rotor ends if the axial clearance is not sufficient
  • cross-port leakage occurs due to above described fixed axial clearance. Excessive leakage could then take place at high pump operating pressures. This leakage could have significant effect on the minimum allowable operation speed of the pump, in addition to significant energy loss of the pump. In other terms, the pump could have little or no discharge flow due to its excessive internal re-circulated cross-port leakage at a low input speed.
  • a vane pump with at least one pressure compensated side wear disk.
  • the pressure overbalanced side wear disk 50 is subject to a net clamping force that pushes the wear disk against the rotor/vanes (rotating group) tightly.
  • This net force comes from mechanical spring force and/or hydraulic pressure acting on the back side of the floating wear disk 50 at the side opposite to the rotor 70.
  • the higher the operating pressure the higher the net clamping force.
  • the clamping force closes the axial gap and squeezes the oil film between rotor and the wear disk to a minimum film thickness without mechanical contact between two parts that rotate close to each other.
  • the outer shape of the wear disk 50 generally has the same shape (with adequate radial clearance for free relative movement) as the inner pumping chamber surface 35 of the cam ring 90.
  • the floating wear disk 50 requires precision manufacturing similar to the cam ring inner diameter 35.
  • the inner pumping chamber surface of a cam ring has an elliptical shape for a single balance (dual action) fixed displacement vane pump.
  • the cross-section of the inner pumping chamber surface 35 is close to a circle because it has two balanced pumps in a same pumping element. Alignment pins could be used to ensure proper orientation of the wear disk and the cam profile.
  • both disks 50/60 are made of steel, alumiaum, or other light weight materials for weight reduction and have hard coated layers applied on the wear surfaces (rotor side). It also should be appreciated that the back side of the floating wear disk 50 is connected to corresponding pump discharge pressure all the time.
  • vanes When a rotor rotates, vanes are expected to maintain contact with the inner surface of the cam ring. Since the inner surface of the cam ring has a varying radius at different angular positions, each vane, which behaves as a piston, will slide into and out of the rotor inside the rotor vane slot. This radial movement of the vane stokes fluid into and out the cavity beneath it. To let each vane work as a positive displacement piston pump, a porting device is needed. The porting device assures that when the cavity volume increases, the under-vane pumping passages are linked to a pump inlet pressure; and conversely, when the bucket volume is reduced, the under-vane pumping passages are linked to its corresponding pump discharge line.
  • Vane pump assembly 10 provides a separate porting mechanism to link inlet and discharge ports of each pump (over-vane) to its corresponding under-vane cavities. When a cavity volume increases, it is linked to pump inlet pressure. When the cavity is reduced, it is linked to a corresponding discharge line.
  • Over vane volume chambers (16 total for pump assembly 10) are separated by vane/cam sealing.
  • FIG. 19 when a vane 36 is sweeping on the seal arc "S" (the constant radius portion of the cam ring profile located between inlet and discharge ports), its under-vane passage 73 and under-vane slot/pocket 75 are linked to a pump discharge pressure port to assure that the vane 36 can be pushed out by under-vane hydraulic pressure forces.
  • a vane 36 is sweeping on the inlet ramp "I"
  • its under-vane passage 73 and under-vane slot 75 are connected to inlet pressure.
  • radial holes 52/62 are used to connect the under-vane passage 73 and under-vane slot 75 (for under-vane pump porting) to pump inlet lines 92 and discharge lines 94, which are integrated into the cam ring 90.
  • Vanes pump under-vane cavity fluid at very rapid speed.
  • the pump assembly 10 has both an under-vane passage 73 and an under-vane slot 75 for a single under-vane pumping element. This arrangement reduces the pressure loss inside the under-vane cavity and flow passages.
  • the outer axial slot 75 is a primary one and the inner axial passage 73 is the second link to under-vane cavities and pump ports.
  • the second passage 73 is linked to the primary slot inside the rotor via a number of radial connector passages 77. Those radial connector passages 77 are slanted with an angle to reduce the energy loss of merging flow.
  • pump assembly 10 is a split discharge pump and is essentially a main fuel pump that consists of four separate pumps. Each pump can discharge flow both from over-vane volume chambers and under-vane volume chambers. All volume chambers need separate timely porting to assure volume chambers are connected to an inlet line when their volume is expanding and connected to a pump discharge line when its volume is contracting.
  • the cam ring 90 is designed to receive fluid from a common pump inlet 24 (four pumps share the same pump inlet) and it ports it to the inlet ports 56/66 of the wear disk, along with performing porting for the over-vane volume chambers. In addition, it receives discharge flow from the wear plates 56/60 and combines the flow with corresponding over-vane discharge flow and then provides for discharge from one of the four corresponding discharge ports 94 in the cam ring.
  • the angular location of the ports on the inner surface of the cam ring is very critical and requires precision manufacturing. To reduce the manufacturing cost, these ports are machined from the outer surface of the cam ring 90. When the cam ring is inserted into its housing/annular space 16, some construction openings on the outer surface will be covered by the inner surface of the annular spacer 16. As discussed previously, multiple seal cords are used to seal circumferential cross-port leakage between the cam ring and the housing.
  • cam ring 90 could have been designed differently with multiple pieces for ease of manufacturing.
  • a hardened sleeve/ring could be used as vane running wear surface and inserted into a separate block inclusive of the flow ports, thereby simplifying manufacturing of the cam running surface and the flow passages.
  • vane pump assembly 10 includes single inlet port 24 oriented in the axial direction and multiple discharge ports 30a-30d oriented in the radial direction.
  • vane pumps for this split-discharge vane pump. All four pumps share the same pump inlet volume.
  • the over-vane volume chamber discharges flow into the cam ring. There, flow merges with the discharge flow from its corresponding under-vane cavity. Then, the total flow is expended from the pump from a pump discharge port.
  • the flow from two diagonally opposite discharge ports of the main pump could be combined by external plumbing.
  • the two ports could be linked internally inside a main pump housing by design, along with necessary control valves, as illustrated in U.S. Patent Application Publication No. 2010/0316507 , the disclosure of which is incorporated by reference.

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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)
EP12250181.0A 2011-12-16 2012-12-14 Pompe hydraulique à palettes à écoulements multiples Withdrawn EP2604790A2 (fr)

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US13/328,060 US20130156564A1 (en) 2011-12-16 2011-12-16 Multi-discharge hydraulic vane pump

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EP2604790A2 true EP2604790A2 (fr) 2013-06-19

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CN106014965A (zh) * 2016-07-20 2016-10-12 常州市恒泰源盛减速机配件厂 结构稳固型油泵

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GB0603099D0 (en) * 2006-02-16 2006-03-29 Lontra Environmental Technolog Rotary piston and cylinder devices
JP6358033B2 (ja) * 2014-10-14 2018-07-18 株式会社デンソー ベーン式ポンプ、及び、それを用いる燃料蒸気漏れ検出装置
KR101740610B1 (ko) * 2015-06-11 2017-06-08 명화공업주식회사 베인펌프

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US5064362A (en) 1989-05-24 1991-11-12 Vickers, Incorporated Balanced dual-lobe vane pump with radial inlet and outlet parting through the pump rotor
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US5064362A (en) 1989-05-24 1991-11-12 Vickers, Incorporated Balanced dual-lobe vane pump with radial inlet and outlet parting through the pump rotor
US20100316507A1 (en) 2009-06-11 2010-12-16 Goodrich Pump & Engine Control Systems, Inc. Split discharge vane pump and fluid metering system therefor

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Publication number Priority date Publication date Assignee Title
CN106014965A (zh) * 2016-07-20 2016-10-12 常州市恒泰源盛减速机配件厂 结构稳固型油泵

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