JP2013127249A - Multi-discharge port hydraulic vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make first and second wear disks slidable in an axial direction to provide for thermal expansion of a rotor and a vane.SOLUTION: A cam ring is disposed within the interior pumping chamber and defines a continuous peripheral cam surface. The rotor is mounted for axial rotation within the interior pumping chamber. A plurality of vanes are mounted for radial movement within slots formed in the rotor. The pump includes axially opposed first and second wear disks 50, 60 disposed within the interior pumping chamber. The first wear disk is a floating wear disk and 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 the vane. The second wear disk 60 is positioned adjacent to a second end surface of the rotor.

Description

Government License Rights This invention was made with government support under contract number AATD W911W6-06-D-0005-0004 awarded by the US Army. The government has certain rights in the invention.

1. TECHNICAL FIELD OF THE INVENTION The present invention relates to rotary vane pumps and, more particularly, balanced split discharge that supplies a combined discharge flow rate at high fluid demand conditions and a first (main) flow rate at low fluid demand conditions. Related to vane pumps. More particularly, in a multi-outlet fluid vane pump having one inlet port and four discharge ports, a floating side wear disc, a cam ring with an internal flow passage, and a rotor assembly with improved under-vane pumping characteristics. Related.

2. 2. Description of Related Art Rotating fluid vane pumps are well known in the prior art as disclosed in Sakamaki et al. US Pat. No. 4,274,817 and Hansen US Pat. No. 5,064,362. is there. A typical rotary vane pump includes a circular rotor mounted and rotated within a larger circular pumping chamber. The centers of these two circles are typically offset to cause eccentricity. The vanes are slidably mounted in and out of the rotor, creating a plurality of volume chambers or vane buckets that perform pumping work. On the blow side of the pump, the volume of the vane bucket increases. These vane buckets of increasing volume are filled with fluid that is pushed into the pumping chamber by inlet pressure. On the discharge side of the pump, the vane bucket whose volume is reduced pushes the pressurized fluid out of the pumping chamber.

  The fluid volume of the vane pump is preferably matched to the operating characteristics of the system with which the pump is associated. For example, the maximum volume of the fuel pump must be tuned to the maximum fuel requirement of the relevant engine application. However, system requirements typically vary with operating conditions. As a result, fixed volume fuel pumps designed as a function of the most severe engine operating conditions can operate at lower efficiency than is desirable in other operating conditions.

  In the case of fuel pumps associated with aircraft gas turbine engines, fuel flow demands quantified by pump volume per rotational speed are other engines that are less demanding, such as cruise, idle, descent and taxiing when the engine is started. Significantly exceed fuel flow requirements during operating conditions. Various attempts have been made to improve fuel pump efficiency in the operating range of gas turbine engines by utilizing different valve structures at the pump outlet to adjust some of the pump discharge to the engine as a function of engine demand. It was. However, these prior art devices are typically complex and therefore add cost to the pump system. In other implementations, variable displacement pumps have been utilized to match the pump output flow to system requirements. However, these implementations increase the pump radial / axial load and involve the addition of moving parts, at the expense of pump size / weight and reliability.

  US 2010/0316507 entitled Split Discharge Vane Pump and its Fluid Flow Control System is a positive displacement vane pump adapted and configured to more closely match the operating characteristics of the system to which it relates. And a valve structure that effectively controls fluid flow from the pump in response to the fluid requirements of the system with which it is associated. The disclosure of US Patent Application Publication No. 2010/0316507 is incorporated herein in its entirety by this reference.

  The pump disclosed in US 2010/0316507 solves many of the problems described above with respect to prior art pump structures. However, there is a need for a positive displacement vane pump design that further increases pump efficiency over the operating range of fuel requirements and reduces component degradation by more effectively balancing the forces inside the pumping chamber.

  The present invention, among other things, defines an inner pumping chamber and an inlet port that allows fluid to be supplied to the inner pumping chamber and at least one discharge that allows pressurized fluid to be discharged from the inner pumping chamber. Directed to a fluid vane pump with a pump body defining a port. The pump is disposed within the inner pumping chamber and defines a continuous peripheral cam surface; a rotor mounted within the inner pumping chamber for rotation about an axis and defining a pump shaft; Is further provided. A plurality of circumferentially spaced and radially extending vanes are mounted for radial movement within slots formed in the rotor, the plurality of vanes being arranged on the outer periphery of the rotor. And an equal number of volume chambers extending in the circumferential direction and extending between the cam surfaces and moving the pressurized fluid. The pump further includes axially opposed first and second wear discs disposed within the inner pumping chamber. The first wear disc has an outer periphery disposed radially inward of the cam surface and is adapted and configured to slide axially relative to the cam surface to provide for thermal expansion of the rotor and vanes. ing. The second wear disk is fixedly disposed adjacent to the second end face of the rotor. However, as will be described below, the second wear disc can also be a floating disc (adapted for axial sliding).

  In a preferred embodiment, the vane pump is a multiple outlet fluid vane pump, the pump body defines four radially oriented discharge ports, each of which discharges pressurized fluid from the inner pumping chamber. I try to do it.

  It is envisioned that the first wear disk is biased against the first end face of the rotor using a spring element. Furthermore, the first wear disc can be biased toward the first end face of the rotor using pressurized fluid discharged from a volume chamber defined by the vanes.

  In a particular configuration of the invention, the pump body further comprises a rear side plate and the inlet port extends axially through the rear side plate and into the inner pumping chamber.

  Preferably, the cam surface has four quadrant cam portions, the diametrically opposed cam portions have the same cam profile, and each cam portion has an inlet arc, a discharge arc and Defines two seal arcs

  In a preferred embodiment, the cam ring has 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 portion. The cam ring also has a plurality of discharge chambers that are arranged and configured to communicate with the discharge arc of each cam portion and to facilitate the discharge of pressurized fluid from the inner pumping chamber.

  It is presently preferred that each vane slot has a lower vane pocket that receives pressurized fluid depending on the angular position of the rotor. In addition, in a specific embodiment, the rotor has a plurality of lower vane channels extending in the axial direction, and each lower vane channel communicates with the lower vane pocket via the connector channel.

  Preferably, each wear disc has a channel below the vane pocket associated with each vane slot and a channel in fluid communication with the interior of the channel below the vane. The pressure in the lower vane pocket is determined according to the angular position of the rotor. Preferably, the fluid in the lower vane passage of the rotor while disposed in the inlet arc portion is approximately equal to the pump inlet pressure, and the fluid in the lower vane passage of the rotor while disposed in the discharge arc portion is pumped. It is almost equal to the discharge pressure.

  A particular configuration of the vane pump of the present invention includes a fluid flow regulation system that draws fluid flow from the discharge arcs of the four cam portions. It is envisioned that the fluid flow regulation system has a first operating state in which fluid is extracted from the discharge arcs of all four cam portions and combined for supply to a fluid demand source. The fluid flow regulation system also draws fluid from a first (main) set of diametrically opposed discharge arcs for supply to a fluid demand source, and a second diametrically opposed discharge arc. The fluid from the set may have a second operating state that bypasses the fluid demand source and returns to the inner pumping chamber.

  The present invention also has, among other elements, an inner pumping chamber and an axially extending inlet port that allows fluid to be supplied to the inner pumping chamber and pressurized fluid is expelled from the inner pumping chamber. It is directed to a multiple outlet fluid vane pump with a pump body defining four radially extending discharge ports. The vane pump includes a cam ring disposed within the inner pumping chamber and defining a continuous peripheral cam surface; a rotor mounted within the inner pumping chamber for rotation about an axis and defining a pump shaft; Is further provided. A plurality of circumferentially spaced vanes extending radially are mounted for radial movement within slots formed in the rotor. The plurality of vanes define an equal number of circumferentially spaced volume chambers that move between the outer circumference of the rotor and the cam surface to move the pressurized fluid. The pump further comprises first and second wear discs that are axially opposed and disposed within the inner pumping chamber.

  In a preferred embodiment, the first wear disc has an outer peripheral surface disposed radially inward of the cam surface and attached for sliding relative to the cam surface to provide for thermal expansion of the rotor and vanes. The second wear disk is disposed adjacent to the second end face of the rotor.

  It is envisioned that the first wear disk is biased against the first end face of the rotor using a spring element. Furthermore, the first wear disc can be biased towards the first end face of the rotor using pressurized fluid discharged from a volume chamber defined by the vanes.

  In a particular configuration of the invention, the pump body has a rear housing with an inlet port extending axially through the rear side plate and into the inner chamber.

  Preferably, the cam surface has four quadrant cam portions, the diametrically opposed cam portions have the same cam profile, and each cam portion has an inlet arc, a discharge arc and two seals Define an arc.

  In a preferred embodiment of the present invention, the cam ring has 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 portion. The cam ring also has a plurality of discharge chambers that are arranged and configured to communicate with the discharge arc of each cam portion and to facilitate the discharge of pressurized fluid from the inner pumping chamber.

  It is presently preferred that each vane slot has a lower vane pocket that accepts or discharges high pressure pressurized fluid that depends on the angular position of the rotor. In addition, in a specific embodiment, the rotor has a plurality of lower vane channels extending in the axial direction, and each lower vane channel communicates with the lower vane pocket via the connector channel.

  It is envisioned that each wear disk has a channel below the vane pocket associated with each vane slot and a fluid path communicating the interior of the channel below the vane. The pressure in the lower vane pocket is determined according to the angular position of the rotor. Preferably, the pressurized fluid in the rotor vane passage while being disposed in the inlet arc portion is approximately equal to the pump inlet pressure, and the fluid in the rotor vane passage while being disposed in the discharge arc portion is It is almost equal to the pump discharge pressure.

  A particular configuration of the vane pump of the present invention includes a fluid flow regulation system that draws fluid flow from the discharge arcs of the four cam portions. It is envisioned that the fluid flow regulation system has a first operating state in which fluid is extracted from the discharge arcs of all four cam portions and combined for supply to a fluid demand source. The fluid flow regulation system is configured to draw fluid from a first set of diametrically opposed discharge arcs for supply to a fluid demand source, while fluid from a second set of diametrically opposed discharge arcs There may be a second operating state that bypasses the fluid demand source and returns to the inner pumping chamber.

  The fluid vane pump to which the present invention is directed includes, among other things, a pump body that defines an inner pumping chamber, an inlet port that allows fluid to be supplied to the inner pumping chamber, and fluid pressurized from the inner pumping chamber. And at least one discharge port for discharging. The fluid vane pump includes a cam ring disposed within the inner pumping chamber and defining a continuous peripheral cam surface, the cam ring defining a plurality of inlet chambers and discharge chambers. The inlet chamber is arranged and configured to receive fluid from the inlet port and distribute the fluid to the inner pumping chamber. The discharge chamber is arranged and configured to communicate with the inner pumping chamber and to facilitate the discharge of pressurized fluid from the inner pumping chamber.

  The rotor is mounted inside the inner pumping chamber for rotation about an axis to define a pump shaft. A plurality of vanes disposed circumferentially spaced apart and extending radially are mounted for radial movement within slots formed in the rotor. The plurality of vanes define an equal number of volume chambers spaced circumferentially and extending between the outer circumferential surface of the rotor and the cam surface to move the pressurized fluid. Each vane slot has a lower vane pocket for fluid communication. The pressure inside the lower vane pocket is determined according to the angular position of the rotor.

  Axially opposed first and second wear discs are disposed within the inner pumping chamber, the first wear disc having an outer circumferential surface disposed radially inward of the cam surface, and a rotor and To prepare for the thermal expansion of the vane, it is biased in the axial direction toward the first end face of the rotor. The second wear disk is disposed adjacent to the second end face of the rotor. Preferably, each wear disk has a flow path that allows fluid to communicate with the interior of the lower vane pocket associated with each vane slot. The pressure in the lower vane pocket is determined according to the angular position of the rotor.

  These and other features and advantages of the present invention, as well as the manner in which it is assembled and used, will be understood by those skilled in the art from the description of the preferred embodiments of the present invention made in conjunction with the several drawings described below. It will be readily apparent to

  Those skilled in the art to which the present invention pertains will readily understand without undue experimentation how to make and use the methods, apparatus and systems of the present invention. Preferred embodiments thereof are described in detail below with reference to specific drawings.

1 is a perspective view of a multiple outlet pump assembly configured in accordance with a preferred embodiment of the present invention. FIG. FIG. 2 is an exploded perspective view of the pump assembly of FIG. 1 with the front side plate removed for simplicity of illustration. FIG. 2 is an exploded perspective view of a cam ring, a rotor assembly, an annular spacer, and a rear side plate used in the pump assembly of FIG. 1. FIG. 3 is an end view of a rear side plate used in the pump assembly of FIG. 1. Sectional drawing of the back side plate along the broken line 5-5 in FIG. Sectional drawing of the back side plate along the broken line 6-6 in FIG. FIG. 2 is an exploded perspective view of a portion of the pump assembly of FIG. 1 showing the front fixed wear plate, rotor assembly, cam ring, and rear slide wear plate. The perspective view of the rotor assembly used for the pump assembly of FIG. FIG. 9 is a cross-sectional view of the rotor assembly taken along the broken line 9-9 in FIG. The perspective view of the cam ring used for the pump assembly of FIG. FIG. 11 is an end view of the cam ring of FIG. 10. FIG. 2 is a perspective view of a rear floating disk used in the pump assembly of FIG. 1. FIG. 13 is a front end view of the floating wear disc of FIG. 12. FIG. 13 is a rear end view of the floating wear disc of FIG. 12. FIG. 15 is a cross-sectional view of the floating wear disc of FIG. FIG. 8 is a perspective view of a front fixed wear disc used in the pump assembly of FIG. 7. FIG. 17 is a front end view of the fixed wear disc of FIG. 16. FIG. 17 is a rear end view of the fixed wear disc of FIG. 16. FIG. 2 is a cross-sectional view of the pump assembly shown in FIG. 1, showing a state where a vane is in a seal arc and a lower vane cavity is connected to a pump discharge passage. FIG. 20 is a cross-sectional view of the pump assembly shown in FIG. 1 taken along section line 20-20 of FIG. FIG. 2 is a cross-sectional view of the pump assembly shown in FIG. 1 taken along the broken line 21-21, showing the vane in the discharge ramp / arc and the upper and lower vane cavities connected to the pump discharge passage. Figure. FIG. 22 is a cross-sectional view of the pump assembly shown in FIG. 1 taken along the broken line 22-22, with the vane in the suction ramp / arc and the vane upper and lower vane cavities connected to the pump suction passage. FIG. Sectional drawing of a rotor assembly and a cam ring.

  Those skilled in the art can more readily understand these or other aspects of the present invention by reference to the following detailed description of the invention in conjunction with the drawings.

  Detailed descriptions of specific embodiments of the apparatus, systems and methods of the present invention are disclosed herein. It is to be understood that the disclosed embodiments are merely examples of how certain aspects of the invention can be implemented, and do not represent an exhaustive list of all the ways in which the invention may be embodied. It is. It will be appreciated that the systems, devices and methods described herein may be embodied in various and other alternative forms. The drawings are not necessarily to scale, and some features may be exaggerated or minimized to show details of particular components. Well-known parts, materials or methods are not necessarily described in detail to avoid obscuring the present disclosure. The specific structural and functional details disclosed herein are not intended to be limiting, but merely as a basis for the claims and to teach one of ordinary skill in the art using the present invention in various ways. It should be interpreted as a representative basis.

  For ease of description, the components of the present invention are described in an upright operating position, and terms such as upper, lower, front, rear, horizontal, etc. are used in connection with this position. However, it is to be understood that the components of the present invention can be manufactured, stored, moved, used and sold in orientations other than those described.

  The drawings depicting the components show some mechanical elements known and recognized by those skilled in the art. A detailed description of such elements is essential to an understanding of the invention and is therefore presented herein to the extent necessary to facilitate an understanding of the new features of the invention.

  Referring now to the drawings, like reference numerals identify similar structural features or elements of the present invention. One embodiment of the hydrostatically balanced multiple outlet fluid vane pump of the present invention shown in FIG. 1 is indicated generally by the reference numeral 10 and includes a cartridge assembly pump element (item 90 in FIG. 7). ). The cartridge assembly 90 is configured to fit inside a reusable housing (annular spacer 16). In other words, the pump element 90 can be easily replaced when it wears out or requires repair. 2-18 show the various parts forming the pump element 90, and FIGS. 19-23 show cross-sectional and elevation views of the pump assembly 10 in various operating states.

  The pump assembly 10 has a single inlet port 24 (see FIGS. 19-22) that receives low pressure fluid within the pump assembly 10. The pump assembly 10 also has four discharge ports 30 a to 30 d for discharging pressurized fluid from the pump assembly 10. The discharge ports 30a and 30c are opposed to each other in the diametrical direction. Similarly, the discharge ports 30b and 30d face each other in the diametrical direction. Normally, 30a / 30c or 30b / 30d is provided for one of the two pumps.

  By passing through the pump assembly 10, the low pressure fluid becomes a high pressure fluid and exits the pump assembly through any two of the diametrically opposed discharge ports 30a-30d or all of the discharge ports. The state in which the low pressure fluid proceeds from the inlet port 24 to the inner pumping chamber 42, is pressurized and supplied to the discharge ports 30a-30d is described in detail below. Due to the diametrical opposition of the discharge ports 30a-30d, the forces generated in the pumping process are thereby effectively canceled, resulting in a balanced pump assembly 10.

  The pump assembly 10 also includes fixed front and rear side plates 80 a, 80 b that are separated from each other by an annular spacer 16. The inlet port 24 is formed in the rear side plate 80b. The discharge ports 30 a to 30 d are formed in the annular spacer 16.

  The end plate 22 is fixed to the front side plate 80a using a series of bolts 27a to 27f, and defines an axial passage 26 through which the drive shaft 28a passes and attaches to the rotor assembly 70. The front and rear side plates 80a, 80b are assembled with the annular spacer 16 to form an inner pumping chamber 42 that houses the cam ring 90, the floating side wear disc 50, the fixed side wear disc 60, and the rotor assembly 70 (FIG. 3). See).

  Referring to FIG. 2, the pump with the front side plate 80a removed to show the rotor assembly 70 and cam ring 90 housed inside the inner pumping chamber 42 and having a front end abutting against the fixed side wear disc 60. A perspective view of the assembly 10 is shown. In the additional exploded perspective view of FIG. 3, the cam ring 90, the fixed side wear disc 60, the floating side wear disc 50 and the rotor assembly 70 have been removed from the interior of the inner pumping chamber 42.

  The rotor assembly 70 best shown in FIGS. 8 and 9 is attached to the drive shaft 28b for rotation about an axis within the inner pumping chamber 42. FIG. The rotor assembly 70 is rotatably supported within the inner pumping chamber 42 by two journal bearings associated with the side wear discs 50/60. As shown in FIG. 19, the rotor drive shaft 28b is engaged with a drive shaft 28a extending outside the front side plate 80a.

  The rotor assembly 70 has a rotor body 71 that fits inside a pumping chamber surface 35 (best shown in FIG. 11) defined by a cam ring 90. The rotor body 71 has a plurality of vane elements 36 that act radially outward and contact a generally elliptical pumping chamber surface 35. As will be described in more detail below, a plurality of peripheral vane buckets or volume chambers 44 are formed between the rotor body 71, the elliptical pumping chamber surface 35, the vane assembly 36, and the wear disc 50/60. See FIG.

  For each vane element 36, the rotor body 71 has a vane slot 38 that slidably receives the vane element, an axially extending lower vane pumping pocket 73, and an axially extending lower vane pumping passage 75. An angled and radially extending connector passage 77 provides fluid communication between the lower vane pumping pocket 73 and the lower vane pumping passage 75. The conditions associated with subvane pumping and the advantages associated with the subvane pumping structure of the present invention are described below.

  Reference is now made to FIGS. 4-6 which provide several views of the rear housing plate 80b. The eight through holes 82 provided in the outer flanges of the front and rear housing plates 80a / 80b allow the rear housing plate 80b and the front housing plate 80a to be fixed to the annular spacer 16 with through bolts and accompanying nuts. (See FIG. 1). As described above, the axial inlet port 24 of the pump assembly 10 branches into an inlet channel 84 formed in the rear side plate 80b and inclined diametrically opposed. These inlet channels 84, as seen in FIG. 3 and described below, are arranged and configured to distribute fluid entering the four axially extending inlet chambers 92 formed in the cam ring 90. Has been.

  Referring now to FIGS. 10 and 11, in addition to the axially extending inlet chamber 92, the cam ring 90 defines an axially extending discharge chamber 94. In addition, the outer periphery 96 of the cam ring 90 has a plurality of access slots 108 that allow the formation of ports 104/106 that extend radially through the inner wall 102 of the cam ring 90 to the pumping chamber surface 35. Used to do. The port 104 extends radially inward from the inlet chamber 92 and the port 106 extends radially inward from the discharge chamber 94. The purpose of the flow port 104/106 is described below.

  The cam ring 90 is provided with a number of seal grooves. For example, the outer periphery 96 of the cam ring 12 has a plurality of sealing grooves 98 that are adapted and configured to receive linear sealing elements. Each end of the cam ring 90 has a circular seal groove 99 and the pumping chamber surface 35 has front and rear outer peripheral seal grooves 97. Those skilled in the art will appreciate that the seal inserted into the seal groove 97/98/99 is designed to prevent crossport leakage throughout the pump assembly 10.

  With reference now to FIGS. 12-15, a floating wear disc 50 is depicted. As shown in FIG. 19, unlike the prior art wear disc located outside the cam ring and fixedly located adjacent to the end of the cam ring, the floating wear disc 50 comprises a cam ring 90 in its entirety. And is adapted to slide axially to permit thermal expansion of the rotor assembly during operation. However, unlike conventional devices where the axial clearance between the wear disk and the rotor must be minimized to prevent cross-port leakage, the pump assembly 10 must be sealed with a floating wear disk. A circumferential clearance between 50 and the pumping chamber surface 35. This circumferential clearance is less susceptible to thermal expansion during pump operation, so it is easier to maintain the seal in this position.

  Similar to the cam ring 90, the floating wear disk 50 has a plurality of fluid ports that allow fluid to communicate with the pump assembly 10. For example, eight radial holes 52 extending from the outer periphery of the floating wear disc 50 are provided. Four of these radial holes 52 are connected to four axially extending outlet fluid ports 54 and the other four radial holes 52 are connected to four axially extending inlet fluid ports 56. Yes. As will be described in detail later, the outlet fluid port 54 allows pressurized and discharged fluid to be supplied to the lower vane slot and the lower vane flow path for use in lower vane pumping, and the inlet fluid port 56 The fluid flowing in is supplied to the lower vane slot and the lower vane flow path so as to be used for lower vane pumping.

  A journal bearing 58 provided on the floating wear disk 50 supports one end of the rotor assembly 70 inside the pumping chamber 52. The four seal grooves 53 are provided on the rear surface of the floating wear disk 50 and are configured to receive end face seals. In addition, eight spring cavities 55 are formed in the rear surface of the floating wear disc 50 and contain spring elements or biasing mechanisms that press the floating wear disc 50 toward the rotor assembly 70. In addition, a small hole 59 extends from each discharge fluid port 54 to the rear surface of the floating wear disc 50. As a result, pressurized discharge fluid is supplied to the rear surface of the floating wear disc 50 to further press / bias the floating wear disc 50 in the direction of the rotor assembly 70. The structure and position of the seal groove 53 define a load region in which a pressurized discharge fluid that presses the floating wear disc 50 toward the rotor assembly 70 acts. As a result, the total pressure applied to the rear surface of the wear disc 50 can be adjusted by adjusting the load area where the discharged fluid acts.

  Referring now to FIGS. 16-18, there is depicted a fixed side wear disc 60 for use in the pump assembly 10 of the present invention. Similar to the floating wear disc 50, this fixed side wear disc 60 has 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. . As with the floating wear disc 50, the discharge fluid port 64 and the inlet fluid port 66 are used to supply fluid for subvane pumping.

  The rear surface of the fixed side wear disc 60 has circular pressure relief grooves 67a / 67b and four pressure relief grooves 69a to 69d extending in the radial direction. It should be noted that the floating side wear disc and the fixed side wear disc 50/60 have a slot that receives a pin to prevent rotation relative to the cam ring 90.

  Referring now to FIGS. 19-23, the arrangement of components used in the pump assembly 10 and the manner in which the pump assembly 10 operates to increase the pressure of the inlet fluid is illustrated. In operation, fluid is received at the inlet port 24 and redirected to the four inlet channels 84. Four inlet channels 84 supply fluid to four inlet chambers 92 formed in cam ring 90 and extending axially. Fluid from the inlet chamber 92 is directed radially inward through a radially extending inlet port 104. When the two end ports 104 each supply fluid to the four radial holes 52/62 formed in the wear disk 50/60, this fluid is used for under-vane pumping. Fluid traveling through the remaining ports 104 formed in the cam ring 90 is supplied to the vane buckets 44 in the four inlet arc regions “I” shown in FIG. As the rotor assembly 70 rotates, fluid moves and exits the vane bucket 44 in the discharge arc region “D” through the innermost port 106 formed in the cam ring 90 and includes four discharge chambers 94 extending in the axial direction. To be accepted. A portion of the pressurized fluid contained in the discharge chamber 94 is supplied to the discharge fluid port 54/64 of the wear disc 50/60 via the radial holes 52/62 and used for under-vane pumping. The remaining pressurized fluid contained in the four discharge chambers 94 formed in the cam ring 90 and extending in the axial direction is supplied to the four discharge ports 30 a to 30 d of the pump assembly 10.

  FIG. 19 is a cross-sectional view of the pump assembly shown in FIG. 1, wherein when the vane 36 is within the seal arc “S”, the lower vane slot 75 and the lower vane flow path 73 have the wear disk 50/60 and cam ring 90. It is shown that it is connected to the pump discharge passage formed. 20 is a cross-sectional view of the pump assembly 10 shown in FIG. 1 taken along the broken line 20-20 in FIG.

  FIG. 21 is a cross-sectional view of the pump assembly 10 shown in FIG. 1, wherein the vane upper cavity 44 and the lower vane cavity 73/75/77 when the vane 36 is within the discharge ramp / arc "D". Is connected to the pump discharge passage formed in the wear disc 50/60 and the cam ring 90.

  Finally, FIG. 22 is a cross-sectional view of the pump assembly 10 shown in FIG. 1, wherein when the vane 36 is in the inlet ramp / arc “I”, the upper and lower vane cavities are worn by the wear disk 50. / 60 and the cam ring 90 are connected to the pump inlet channel.

  Typically, wear disks in prior art vane pumps are fixedly mounted inside the pumping chamber and abut the axial ends of the cam rings and rotor blades. As shown in these figures, the front side wear disc 50 is a floating wear disc disposed radially inside the pumping chamber surface 35 defined by the cam ring 90.

  The vane pump design already disclosed has an axial clearance fixed between the wear disc and the rotor. Furthermore, the wear plates / disks on both sides of the rotor / vane are fixed. In the design of a fixed axial clearance, the longer the rotor, the greater the axial clearance is required, considering the free thermal expansion of the rotor and vanes. At high operating temperatures, the size of the gap available between the rotor and the wear disk can be significantly reduced by rotor / vane expansion. As a result, mechanical wear and premature wear can occur at the rotor ends if the axial clearance is not sufficient.

  Furthermore, as described above, cross port leakage occurs due to the fixed axial clearance described above. Excessive leakage occurs when the pump operating pressure is high. This leakage has a significant impact on the minimum allowable operating speed of the pump, in addition to significant energy loss of the pump. In other words, when the input speed of the pump is low, there is little or no discharge flow rate due to excessive crossport leakage that circulates internally.

  Accordingly, the vane pump preferably has at least one pressure compensated side wear disc. In the present invention, while the pump is operating, the side wear disc 50 receives a net clamping force that presses the wear disc tightly against the rotor / vane (rotating group) due to the pressure differential. This net force results from the mechanical spring force and / or fluid pressure acting on the rear surface of the floating wear disk 50 facing the rotor 70. Usually, the higher the operating pressure, the higher the net clamping force. In a well-designed pump, this clamping force closes the axial gap and minimizes the mechanical contact between the two parts rotating in close proximity to the oil film between the rotor and the wear disc. Crush to the limit thickness.

  In order to allow the floating wear disc 50 to move freely within the cam ring 90 as a result of the net biasing force described above, the outer shape of the wear disc 50 is in accordance with the shape of the inner pumping chamber surface 35 of the cam ring 90 (free relative Are generally the same (with sufficient radial clearance for movement). Thus, the floating wear disc 50 requires precise manufacture, as does the inner diameter 35 of the cam ring.

  Typically, in a single balance (dual action) fixed volume vane pump, the shape of the inner pumping chamber surface of the cam ring is elliptical. As shown in FIG. 23, in the present invention, because the same pumping element has two balanced pumps, the cross-sectional shape of the inner pumping chamber surface 35 is substantially circular. Centering pins can be used to ensure proper orientation of the wear disc and cam profile.

  One skilled in the art will readily appreciate that the fixed side wear disc 60 can be a floating wear disc when there is no cost concern. Preferably, both discs 50/60 are manufactured from steel, aluminum or other lightweight material for weight reduction and have a hard coating layer applied to the wear surface (rotor side). It should also be understood here that the rear face of the floating wear disc 50 is always connected to the corresponding pump discharge pressure.

  It is expected that contact between the vane and the inner surface of the cam ring will be maintained as the rotor rotates. Since the radius of the cam ring inner surface varies at different angular positions, each vane acting as a piston slides inside and out of the rotor vane groove. This radial movement of the vane causes fluid to enter and exit the cavity below it. A porting device is required for each vane to function as a positive displacement piston pump. This porting device connects the pump flow path under the vane to the pump inlet pressure when the cavity volume increases, and conversely, when the bucket volume decreases, the pump flow path under the vane Ensure that it is connected to the line.

  Conventional vane pumps typically incorporate a flow path that directly connects the lower vane cavity to the corresponding upper vane volume chamber. This allows the under-vane cavities to be connected simultaneously to the inlet and discharge ports of the pump as their corresponding vane upper volume chamber. These flow channels can be inside the rotor, or an interface can be used between the rotor and the side wear plate. The disadvantage of the conventional design is that when the pump operates at very high speeds, there is a significant loss of dynamic pressure along or through the flow path, and cavitation erosion occurs in these areas. .

  The vane pump assembly 10 provides a separate porting mechanism that connects the inlet and discharge ports of each pump (on the vane) to its corresponding sub-vane cavity. When the cavity volume increases, it is connected to the pump inlet pressure. When the cavity volume decreases, it is connected to the corresponding discharge line.

  Volume chambers on the vanes (16 total in pump assembly 10) are separated by vane / cam seals. As shown in FIG. 19, when the vane 36 strokes a seal arc “S” (a portion where the radius of the contour of the cam ring arranged between the inlet port and the discharge port is constant), the vane underflow passage 73 and the vane below The slot / pocket 75 is connected to the pump discharge pressure port to ensure that the vane 36 is pushed out by the fluid pressure under the vane. When the vane 36 strokes the inlet slope “I”, as shown in FIG. 22, the lower vane flow path 73 and the lower vane slot 75 are connected to the inlet pressure. When the vane 36 strokes the discharge slope, as shown in FIG. 21, the vane lower flow path 73 and the vane lower slot 75 are connected to the corresponding discharge line. As a result, the pressure port on the wear disc is longer than the inlet port 56/66 in the circumferential direction of the discharge port 54/64.

  As explained above, there are radial holes 52/62 in the outer surface of the wear disc 50/60. These radial holes 52/62 connect the lower vane channel 73 and lower vane slot 75 (for pump porting under the vane) to the pump inlet line 92 and the discharge line 94 which are integrated into the cam ring 90. Used to connect.

  The vane pumps the fluid in the subvane cavity at a very fast rate. One axial slot for connecting the lower vane cavity to the pump system port or volume chamber on the vane to avoid excessive pressure build-up or decompression due to resistance in the lower vane cavity and flow path Unlike conventional designs, which have only a single vane pump element, the pump assembly 10 has a lower vane flow path 73 and a lower vane slot 75. This structure reduces pressure loss in the subvane cavities and flow paths.

  The outer axial slot 75 is the connection to the first sub-vane cavity and pump port, the first and inner axial flow path 73 being the second. The second flow path 73 is connected to a first slot inside the rotor via many radial connection flow paths 77. These radial connection channels 77 reduce the energy loss of the flow that merges at an angle.

  As will be readily appreciated, the pump assembly 10 is a split delivery pump and is essentially the main fuel pump composed of four separate pumps. Each pump can discharge flow from an upper vane volume chamber and a lower vane volume chamber. All volume chambers require separate timely porting to ensure they are connected to the inlet line when their volume increases and to the pump discharge line when their volume decreases. To do.

  As previously described, the cam ring 90 is designed to receive fluid from the pump inlet 24 (four pumps having the same pump inlet together) and porting for the vane upper volume chamber. Carry the fluid to the wear disc inlet port 56/66. In addition, it accepts the discharge flow from the wear plate 56/60 and combines it with the discharge flow on the corresponding vane and supplies it as a discharge flow from one of the four corresponding discharge ports 94 on the cam ring. .

  In order to ensure minimal timing errors in porting on the vanes, the angular position of the ports on the inner surface of the cam ring is extremely important and requires precise manufacturing. These ports are machined from the outer surface of the cam ring 90 to reduce manufacturing costs. When the cam ring is inserted into its housing / annular spacer 16, several structural openings on the outer surface are covered by the inner surface of the annular spacer 16. As discussed above, a plurality of seal straps are used to seal the circumferential crossport leak between the cam ring and the housing.

  Those skilled in the art will readily appreciate that the cam ring 90 can be of different designs with multiple portions to facilitate manufacture. For example, a hardened sleeve / ring can be used as a wear surface on which the vane slides and can be inserted into a separate block containing the flow port, thereby facilitating the manufacture of the cam sliding surface and flow path.

  Further, unlike the vane pump structure of the prior art, the vane pump assembly 10 of the present invention has one inlet port 24 oriented in the axial direction and a plurality of discharge ports 30a-30d oriented in the radial direction. doing. There are a total of four vane pumps in this divided discharge vane pump. All four pumps have the same pump inlet volume. The volume chamber above the vane of each pump discharges flow into the cam ring. There, the flow merges with the corresponding flow from the subvane cavity. The total flow from the pump discharge port is then consumed from the pump. There are a total of four discharge ports, one for each pump.

  To form two balanced dual action vane pumps, the flow from the two discharge ports on opposite sides of the main pump diagonal can be combined by external piping. Alternatively, the two ports may be designed inside the main pump housing, along with the necessary control valves, as disclosed in U.S. Patent Application Publication No. 2010/0316507, the disclosure of which is incorporated herein by reference. Can connect.

  While the invention has been described in terms of preferred embodiments, those skilled in the art will readily appreciate that changes and modifications can be made without departing from the spirit and scope of the invention as defined by the appended claims. By the way.

DESCRIPTION OF SYMBOLS 10 Pump assembly 16 Annular spacer 50 Floating wear disc 60 Fixed wear disc 70 Rotor assembly 80a Front side plate 80b Rear side plate 90 Pump element

Claims (34)

a) having an inner pumping chamber and defining an inlet port allowing fluid to be supplied to the inner pumping chamber and at least one discharge port allowing pressurized fluid to be discharged from the inner pumping chamber The pump body to
b) a cam ring disposed in the inner pumping chamber and defining a continuous peripheral cam surface;
c) a rotor mounted within the inner pumping chamber for rotation about an axis to define a pump shaft;
d) a plurality of circumferentially spaced vanes extending radially within a slot formed in the rotor for radial movement, the outer periphery of the rotor; A plurality of vanes defining an equal number of volume chambers extending circumferentially and spaced between the cam surfaces to move pressurized fluid;
e) first and second wear disks disposed in the inner pumping chamber and facing each other in the axial direction, wherein the first wear disk has an outer periphery disposed radially inward of the cam surface. And adapted and configured to slide axially relative to the cam surface to provide for thermal expansion of the rotor and the vane, and the second wear disc is a first of the rotor. First and second wear discs disposed adjacent to the two end faces;
A fluid vane pump comprising:   The vane pump is a multi-discharge fluid vane pump, and the pump body defines four discharge ports oriented in a radial direction, and each port discharges pressurized fluid from the inner pumping chamber. The fluid vane pump according to claim 1.   The fluid of claim 1, wherein the first wear disk is biased against the first end surface of the rotor using a spring element toward the first end surface of the rotor. Vane pump.   The first wear disk is urged toward the first end face of the rotor using pressurized fluid discharged from the volume chamber defined by the vane. Item 2. The fluid vane pump according to Item 1.   The fluid vane pump of claim 1, wherein the pump body further includes a rear housing plate, and the inlet port extends axially through the rear housing plate and into the inner chamber.   The cam surface has four quadrant cam portions, the diametrically opposed cam portions have the same cam profile, and each cam portion has an inlet arc, a discharge arc and two The fluid vane pump according to claim 1, wherein a seal arc is defined.   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 portion. The fluid vane pump described.   The cam ring has a plurality of discharge chambers that are arranged and configured to communicate with the discharge arc of each cam portion and to facilitate the discharge of pressurized fluid from the inner pumping chamber. The fluid vane pump according to claim 6.   The fluid vane pump according to claim 1, wherein each vane slot has a lower vane pocket for receiving fluid, and the pressure of the lower vane pocket is determined according to the angular position of the rotor.   The fluid according to claim 9, wherein the rotor includes a plurality of vane lower passages extending in the axial direction, and each vane lower passage communicates with the lower vane pocket via a connector passage. Vane pump.   Each wear disc has a channel that communicates fluid to the interior of the lower vane pocket and the lower vane channel associated with each vane slot, and the pressure in the lower vane pocket depends on the angular position of the rotor. The fluid vane pump according to claim 10, wherein the fluid vane pump is fixed.   The fluid vane pump according to claim 9, wherein the pressure of the fluid in the lower vane flow path of the rotor is substantially equal to a pump inlet pressure while being disposed in the inlet arc portion.   10. The fluid vane pump according to claim 9, wherein the pressure of the fluid in the lower vane flow path of the rotor is substantially equal to the pump discharge pressure while being disposed in the discharge arc portion.   The fluid vane pump according to claim 6, further comprising a fluid flow rate adjusting system for extracting a fluid flow from the discharge arcs of the four cam portions.   15. The fluid flow regulation system has a first operating condition wherein fluid is withdrawn from the discharge arcs of all four cam portions and combined for supply to a fluid demand source. The fluid vane pump described.   The fluid flow regulation system is configured to draw fluid for supply to a fluid demand source from a first set of diametrically opposed discharge arcs and to provide fluid from a second set of diametrically opposed discharge arcs. The fluid vane pump of claim 14, wherein the fluid vane pump has a second operating state that bypasses the fluid demand source and returns to the pumping chamber. a) An axially extending inlet port having an inner pumping chamber and allowing fluid to be supplied to the inner pumping chamber and four discharge ports allowing pressurized fluid to be discharged from the inner pumping chamber A pump body that defines
b) a cam ring disposed within the inner pumping chamber and defining a continuous peripheral cam surface;
c) a rotor mounted within the inner pumping chamber for rotation about an axis to define a pump shaft;
d) a plurality of circumferentially spaced vanes extending radially in a slot formed in the rotor for radial movement and moving the pressurized fluid A plurality of vanes defining an equal number of volume chambers spaced circumferentially extending between an outer periphery of the rotor and the cam surface;
e) first and second wear discs axially opposed disposed within the inner pumping chamber;
A multi-discharge port fluid vane pump comprising:   The first wear disc is disposed radially inward of the cam surface and has an outer periphery attached for sliding relative to the cam surface to provide for thermal expansion of the rotor and the vane; and The multiple discharge fluid vane pump of claim 17, wherein two wear discs are disposed adjacent to the second end face of the rotor.   The plurality of claim 18, wherein the first wear disk is biased toward the first end surface of the rotor using a spring element toward the first end surface of the rotor. Discharge port fluid vane pump.   The first wear disk is biased toward a first end face of the rotor using pressurized fluid discharged from the volume chamber defined by the vane. A multiple discharge fluid vane pump according to claim 18.   The multiple outlet fluid of claim 17, wherein the pump body has a rear housing plate and the inlet port extends axially through the side plate toward the inner chamber. Vane pump.   The cam surface has four quadrant cam portions, the diametrically opposed cam portions have the same cam profile, and each cam portion has an inlet arc, a discharge arc and two seal arcs. The multi-discharge port fluid vane pump according to claim 17, wherein the multi-discharge port fluid vane pump is defined.   18. 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 portion. Multiple outlet fluid vane pump.   The cam ring includes a plurality of discharge chambers arranged and configured to communicate with the discharge arc of each cam portion and facilitate discharge of pressurized fluid from the inner pumping chamber. Item 18. A multiple discharge fluid vane pump according to Item 17.   18. The multi-outlet fluid of claim 17, wherein each vane slot has a lower vane pocket for receiving fluid, and the pressure in the lower vane pocket is determined according to the angular position of the rotor. Vane pump.   The multiple discharge port according to claim 25, wherein the rotor has a plurality of vane lower passages extending in the axial direction, and each vane lower passage communicates with the vane lower pocket through the connector passage. Fluid vane pump.   Each wear disk has a lower vane pocket associated with each underlying vane slot and a flow path for fluid communication in the lower vane flow path, and the pressure in the lower vane pocket is an angle of the rotor. 27. The multi-discharge port fluid vane pump according to claim 26, which is determined according to a position.   26. The multiple outlet fluid vane pump of claim 25, wherein the pressurized fluid in the rotor vane lower pocket while disposed in the inlet arc portion is approximately equal to a pump inlet pressure.   26. The multi-discharge port fluid vane pump according to claim 25, wherein the pressurized fluid in the rotor vane lower pocket while being disposed in the discharge arc portion is substantially equal to a pump discharge pressure.   23. The multi-discharge fluid vane pump of claim 22, further comprising a fluid flow rate adjustment system for extracting fluid from the discharge arcs of the four cam portions.   31. The fluid flow control system of claim 30, wherein the fluid flow regulation system has a first operating condition wherein fluid is extracted from the discharge arcs of all four cam portions and combined for supply to a fluid demand source. Multiple discharge fluid vane pump as described.   The fluid flow regulation system draws fluid from a first set of diametrically opposed discharge arcs and supplies fluid from a second set of diametrically opposed discharge arcs for supply to a fluid demand source 32. The multiple outlet fluid vane pump of claim 30, having a second operational state that bypasses the fluid demand source and returns to the pumping chamber. a) having an inner pumping chamber and defining an inlet port for allowing fluid to be supplied to the inner pumping chamber and at least one discharge port for allowing pressurized fluid to be discharged from the inner pumping chamber; A pump body,
b) a cam ring disposed within the inner pumping chamber and defining a continuous peripheral cam surface, wherein the cam ring also defines a plurality of inlet chambers and discharge chambers, the inlet chamber comprising the Arranged and configured to receive fluid from an inlet port and distribute the fluid to the inner pumping chamber, the discharge chamber being in communication with the inner pumping chamber and pressurized from the inner pumping chamber A cam ring arranged and configured to facilitate fluid ejection;
c) a rotor mounted within the inner pumping chamber for rotation about an axis to define a pump shaft;
d) a plurality of circumferentially spaced vanes extending radially in a slot formed in the rotor for radial movement and moving the pressurized fluid Therefore, an equal number of volume chambers spaced circumferentially extending between the outer periphery of the rotor and the cam surface are defined, and each vane slot is added based on the angular position of the rotor. A plurality of vanes having a lower vane pocket for receiving the pressurized fluid;
e) first and second axially opposed wear discs disposed within the inner pumping chamber, wherein the first wear disc is disposed radially inward of the cam surface And is biased axially toward the first end surface of the rotor in preparation for thermal expansion of the rotor and vane, and the second wear disk is adjacent to the second end surface of the rotor A first and a second wear disc,
A fluid vane pump comprising:   Each wear disk has a flow path for fluid to be fed into the lower vane pocket associated with each vane slot, and the pressure in the lower vane pocket is determined according to the angular position of the rotor. 34. A fluid vane pump according to claim 33.

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