Rotary hydraulic machine

Abstract: A rotary hydraulic machine having particular utility as a fuel pump for aircraft turbine engines that combines the desirable features of vane-type and centrifugal-type machines of similar character -ie, high pressure positive displacement at low speed combined with improved reliability, package size and weight. This is accomplished, in accordances with a presently preferred embodiment of the invention, by providing a combined vane- and centrifugal-type pump that is configured to function as a pressure-compensated single-lobe vane pump for engine starting, and as a centrifugal pump at normal operating speed.

Description: The present invention relates to a rotary hydraulic machine of the vane-type according to the preamble of claim 1. Variable displacement vane-type hydraulic pumps of that kind are well known (US-A 2,064,421). Fluid inlet and fluid outlet is through a valve shaft having an inlet port and a discharge port, which communicate with passages in the rotor. No centrifugal pumping is effected by these rotor passages, since they carry the fluid to and from the widening and narrowing working spaces of the pump. Also fixed displacement vane-type pumps are known (DE-A 16 53 932) and are widely used as steering pumps. Positive displacement pumps are conventionally employed as fuel pumps for aircraft turbine engines in order to obtain sufficient fuel pressure for the engine during low speed starting conditions. Recent requirements to improve pump reliability, package size and weight have increased need to employ centrifugal-type pumps in applications of this type. However, centrifugal hydraulic pumps, which rely upon high-speed rotation to obtain high output pressure, do not provide sufficient fuel pressure at the ten percent to fifteen percent speed range to permit engine starting. System designs specifications typically require fuel pumps to operate at a specified flow rate with a vapor/liquid inlet ratio of 0.45, and with a net positive suction pressure or NPSP, which is the pressure at the pump inlet above true vapor pressure of the fuel, of 0.35 bar (5 psi). Newer system specifications, however, require the 0.45 vapor/liquid inlet ratio capability over a wider engine flow range, and may even require a 1.0 vapor/liquid ratio with intermittent all-liquid or all-vapor operation. Furthermore, the NPSP requirements have been increased to 0.35 bar (5 psi) over the entire engine flow range, and in some cases even 0.21 bar (3 psi) over the engine flow range. It is therefore a general object of the present invention to provide a rotary hydraulic machine of the subject type that provides sufficient output pressure for use during low speed starting of aircraft turbine engines and other applications of similar type, while retaining desirable features of centrifugal pumps in terms of reliability, package size and weight. It is another object of the present invention to provide a rotary hydraulic pump that is capable of satisfying flow requirements in aircraft turbine engine fuel delivery systems over an extended engine operating range. A further object of the present invention is to provide a fuel pump of the described character that is economical and efficient in construction in terms of the stringent weight and volume requirements in aircraft applications, and that provides reliable service over an extended operating lifetime. The teaching of the invention can be taken from claim 1. The dependent claims contain further features and developments of the invention. Briefly stated, the present invention contemplates a rotary hydraulic machine having particular utility as a fuel pump for aircraft turbine engines that combines the desirable features of vane-type and centrifugal-type machines of similar characteristic high pressure positive displacement at low speed combined with improved reliability, package size and weight. This is accomplished, in accordances with a presently preferred embodiment of the invention, by providing a combined vane- and centrifugal-type pump that is configured to function as a pressure-compensated single-lobe vane pump for engine starting, and as a centrifugal pump at normal operating speeds. In accordance with a first important aspect to the present invention, a pressure-compensated rotary hydraulic machine comprises a housing, a rotor mounted for rotation within the housing and having a plurality of radially extending peripheral slots, and a plurality of vanes individually slidably mounted in the slots. An annular track ring is mounted within the housing and forms a radially inwardly directed vane track surrounding the rotor, and a fluid pressure cavity between the track and the rotor periphery. Fluid inlet and outlet passages in the housing are coupled to the cavity. A spring actuator is carried by the housing and engages the track ring so as to urge the ring to a position eccentric to the axis of rotation of the rotor. A fluid actuator is mounted within the housing at a position diametrically opposed to the spring actuator, and is responsive to fluid pressure at one of the inlet and outlet passages for moving the track ring against the force of the spring actuator toward a position coaxial with the rotor. The fluid actuator thus controls displacement of the machine as a function of fluid pressure. In the preferred application of the subject machine as a rotary hydraulic pump, the fluid actuator is coupled to the pump output so as to decrease displacement of the pump as pump output pressure increases to a pressure limit at which the track ring is coaxial with the rotor and the pump exhibits zero displacement. In accordance with a second important aspect of the present invention, the rotor includes a plurality of internal passages extending radially between the vanes slots from an open outer end at the periphery of the rotor to an inner end that receives inlet fluid. The track ring has a plurality of radial passages extending through the ring, preferably at an angle with respect to the axis of rotor rotation. Thus, in the zero-displacement position of the track ring coaxial with the rotor, the machine operates as a centrifugal machine, with the rotor vanes functioning to seal the rotor discharge from the rotor inlet and the track ring functioning as a diffuser. In the preferred implementation of the invention as a fuel pump for aircraft turbine engines, the pump shaft extends from the rotor housing for coupling to a source of motive power, and the fuel inlet is coaxial with the pump shaft and disposed on the opposite side of the rotor. A spiral fluid inducer is coupled to the pump drive shaft within the inlet for pressurizing inlet fluid fed to the rotor internal passages and thence to the rotor/ring fluid pressure cavity. Such fluid prepressurization helps urge the rotor vanes into sliding sealing engagement with the track ring and side backup plates, and also helps obtain high fluid pressure at low pump speed. Brief Description of the Drawings The invention, together with additional objects, features and advantages thereof, will be best understood from the following description, the appended claims and the accompanying drawings in which: Fig. 1 is a sectional side elevational view of a rotary hydraulic machine in accordance with a presently preferred embodiment of invention, Figs. 2 and 3 are sectional views taking substantially along the respective lines 2-2 and 3-3 in Fig. 1, Fig. 4 is a graphic illustration useful in describing operation of the invention, and Fig. 5 is a sectional view taken along line 3-3 and passing in axial direction and along slots 52, 52 to line 3-3. Detailed Description of Preferred Embodiment The drawings illustrate an aircraft engine fuel pump 10 in accordance with a presently preferred implementation of the invention as comprising a housing 12 formed by a hollow cup-shaped enclosure or shell 14 having a base 16 and an outwardly stepped sidewall 18. A drive shaft 20 projects from base 16 coaxially with shell 14 and has a disc-shaped pump rotor 22 formed integrally therewith. A rear backup plate 24 is affixed by bolts 26 to the open edge or lip of shell 14. A front backup plate 28 is slidably positioned within shell 14 in opposition to rear backup plate 24, and is resiliently urged toward backup plate 24 by the preload spring 30 positioned between front backup plate 28 and base 16 of shell 14. The periphery of backup plate 28 is stepped identically with the surrounding shell, and is slidably sealed with respect thereto by a plurality of O-rings 32. Likewise rear backup plate 24 is sealed with respect to shell 14 by an O-ring 34. A pump mounting flange 36 integrally projects radially outwardly from base 16 of shell 14 coaxially with the axis of rotation of shaft 20. A shaft seal 38 carried by shell base 16 cooperates with a mating ring 40 on shaft 20 for sealing the shaft opening through shell 14. A front port plate 42 is affixed by suitable pins (not shown) to front backup plate 28. A complementary rear port plate 44 is affixed to rear backup plate 24. Port plates 42, 44 are parallel to each other and slidably engage the parallel side faces of rotor 22, port plate 24 being resiliently urged against the opposing rotor face and the rotor being urged against port plate 44, by spring 30 and fluid pressure in cavities between backup plate 28 and shell 14, as will be described. Rotor 22 has a plurality of radially extending slots 46 disposed in an array about the periphery of the rotor. A flat generally rectangular vane 48 is slidably disposed within each slot 46. An undervane fluid pressure chamber 50 is formed at the radially inner edge of each slot 46 at a radius from the axis of rotation of rotor 20 for registry with a circumferential array of kidney slots 52, 53 in port plates 42, 44. A fluid passage 54 (FIG. 1) in backup plate 28 couples slots 52 to an annular cavity 56 between plate 28 and shell 14 for feeding fluid at intermediate pressure to undervane chambers 50 and thereby urging vanes 48 radially outwardly with respect to rotor 22. Likewise, a fluid passage (not shown) in backup plate 28 couples slots 53 (FIG. 3) to the fluid outlet for feeding fluid at outlet pressure to the undervane chambers. A plurality of radially extending passages 60 are formed internally of rotor 22 in a uniform circumferential array, one passage 60 being positioned midway between a pair of adjacent vane slots 46, as best seen in Fig. 2. The outer end 61 of each rotor passage 60 flares outwardly and opens onto the periphery of rotor 22. The radially inner end of each rotor passage 60 is open to an axial passage 62 that extends entirely through the rotor body. Rotor passages 62 alternately register as the rotor rotates with slots 64, 65 (FIGS. 1 and 3) in ports plates 42, 44. Slots 64 are key-shaped, while slots 65 are kidney-shaped. Slots 64 communicate through a passage 67 in backup plate 28 with a annular cavity 66 surrounding shaft 20 adjacent to base 16 of shell 14 for feeding fluid at inlet pressure to cavity 66 and thereby assisting spring 30 in urging backup plate 28 against rotor 22. Slots 52 are connected through passage 54 to annular cavity 56, as previously described. A third passage 70 couples slots 65 in port plate 42 to a third annular cavity 72 between backup plate 28 and shell 14. As will be observed in FIG. 1, the cavities 72, 56 and 66 are sealed from each other by the O-rings 32. A circumferential array of passages 74 extend radially inwardly from axial passages 62 in rotor 22 and interconnect rotor passages 60 with the hollow interior 76 of shaft 20. A one-piece annular track ring 78 is captured between port plates 42, 44 surrounding the periphery of rotor 22. Track ring 78 is free to slide laterally of the axis of rotation of rotor 22, having diametrically opposed flats 80 (FIG. 2) that cooperate with opposing ledges 82 on shell 14 for guiding and restraining such lateral motion. A plurality of passages 84 are formed in ring 78, each passage 84 flaring outwardly of the ring body and being disposed at an angle with respect to the ring diameter. A spring actuator 86 (FIG. 2) comprises a collar 88 integral with shell 18 and having a radially orientated passage 90 extending therethrough. A cup-shaped piston 92 has a sidewall slidably captured within opening 90 and a base coupled by a sealing vane 94 to the opposed periphery of track ring 78. A cup-shaped spring seat 96 is adjustably threadably received into the outer end of opening 90, and captures a coil spring 98 in compression between seat 96 and piston 92. A guide pin 100 has a base captured between spring 98 and seat 96, and a pin body that extends coaxially through spring 98 for restraining lateral motion of the spring. A fluid actuator 102 (FIG. 2) comprises a hollow collar 104 integral with shell 14 and having a radial through-passage 105 diametrically aligned with passage 90 of collar 86 with respect to the axis of rotation of rotor 22. A hollow cup-shaped sleeve 106 is adjustably threadably received within passage 105. A fluid piston 108 is slidably carried in passage 107 at the inner end of sleeve 106 and is coupled by a sealing vane 110 to the opposing periphery of ring 78 diametrically opposite to vane 94 of spring actuator 86. An internal stop 111 within sleeve 106, cooperates with piston 108 for limiting outward motion of the latter and thereby limiting motion of ring 78 eccentrically of rotor 22 under force of spring actuator 86. A pair of diametrically opposed cavities 122 between ring 78 and shell 14 are connected to annulus 56 and to rotor undervane chambers 50 by passages 54. A second pair of diametrically opposed cavities 112 between ring 78 and shell 14 are interconnected by a channel 114 (FIG. 1) in rear backup plate 24 and feed fluid under pressure to the control through passage 116. Passage 116 extends from this channel into collar 104 from the cavity 112, and through openings 118 in sleeve 106 into the hollow interior 119 thereof, so that pressurized fluid within cavities 112 is fed to actuator 102 and operates on actuator piston 108. An annular opening 120 in sleeve 106 is uncovered by motion of piston 108 to feed fluid from the hollow 119 to an outlet passage 121 through a pump filter and to the pump outlet port (not shown). An open collar 124 on rear backup plate 24 forms the pump fluid inlet coaxially with shaft 20. An inducer 126 comprises a substantially cylindrical body 128 threadably received into shaft 20 coaxially therewith and positioned within inlet collar 124. A series of spiral vanes 130 radially integrally projects from body 128 to adjacent the inside diameter of collar 124. In operation, with the pump initially at rest, ring 78 is biased by spring actuator 86 to the upper right in the orientation shown in Fig. 2, so that piston 108 abuts stop 111 and track ring 78 is positioned eccentrically of rotor 22. Thus, a sickle-shaped or crescent cavity 23a, 23b (Fig. 5) is formed between rotor 22 and ring 78. Vanes 48 engage the opposing ring surface 78, which effectively forms a vane track. Undervane chambers 50 are connected by slots 52 to low pressure through cavity 56 during vane rise (sweeping half cavity 23a) and by slots 53 to the pump output during vane fall (sweeping half cavity 23b). Upon initial rotation of drive shaft 20, inlet fluid at collar 124 is prepressurized by rotation of inducer 126 and is fed through slots 64 and passages 62, 67 to cavity 66 to urge plate 28 against rotor 22. Furthermore, vanes 48 act as pistons moving in slots 46 so that undervane chambers 50 at slots 52 increase and suck fluid whereas undervane chambers 50 at kidney slots 53 decrease and press the fluid through a further passage (not shown) into cavity 120. Prepressurized fluid is also fed through rotor passage 62, 60 radially outwardly into the crescent cavity 23a, 23b and through passages 84 in the cavity 112. Thus, the piston action of the vanes raises pump output pressure during the vane-pump mode of operation. The pressurized fluid in cavity 112 is fed by passages 116, 118 to cavity 120, the pump filter and to the pump outlet. The piston pumping mode continues up to about 10% of nominal operating speed N(Fig.4). As pump speed increases and centrifugal outlet fluid pressure correspondingly increases, actuator piston 108 is urged by fluid pressure to move ring 78 against the force of spring actuator 86 toward a position coaxial with rotor 22. Thus, the stroke of vanes 48 communicating through cavities 52 and 53 decreases, and therefore pump displacement correspondingly decreases. In the meantime, as rotor speed increases, effective centrifugal pump output pressure correspondingly increases. At about 60% of design speed N (FIG. 4), rotor 22 functions as a two-stage impeller. At a first stage, fluid from inducer 126 to plate slots 64 is pumped by centrifugal action to the rotor periphery, and thence through diffuser 84 into chambers 122 connected to annulus 72. Such first stage impeller output, at intermediate pressure, is returned by passage 70 to slots 65, and is again centrifugally pumped by rotor/impeller 22. Thus, rotor passages 60, 62 cooperate with port plate slots 64, 65 and backup plate passages 70 to function alternately as first and second stage impeller passages as the impeller rotates. Moreover, passages 74 in shaft 20 feed fluid at intermediate pressure to the passages 62 in registry with plate slots 65, and thereby function as an injector stage for boosting first stage fluid flow to the impeller. FIG. 4 is a graphic illustration of effective vane-pump output pressure 150 regulated by a pressure control valve (not shown) to the engine required pressure, vane pump displacement 152 controlled by actuator 108, centrifugal pump output pressure 154 determined by rotor (impeller) speed, and total pump output pressure 156, all as a function of pump speed (rpm). At a speed threshold 158, total pressure of outlet fluid is sufficient at actuator 102 to overcome spring actuator 86 and to position ring 78 coaxially with rotor 22, so that displacement 152 and effective vane pump output pressure 150 are zero.

Claims: A rotary hydraulic machine of the vane-type comprising: a housing (12) having a fluid inlet (124) and a fluid outlet (121); a rotor (22) mounted for rotation within said housing (12) and having a plurality of radially extending peripheral slots (46); a plurality of vanes (48) individually slidably mounted in said slots (46) and determining each an undervane chamber (50) at the respective radial inner end of each slot (46); a drive shaft (20) coupled to said rotor (22) and extending out of said housing (12); a track ring (78) movably mounted within said housing (12), said track ring (78) having a radially inner surface surrounding said rotor (22) and forming a fluid cavity (23a, 23b) between said surface and said rotor (22); passage means (64, 65, 66, 67) for feeding inlet fluid to said fluid cavity (23a, 23b) and fluid outlet passage means (112, 116, 118, 120, 122) for feeding outlet fluid from said cavity (23a, 23b); means (50, 52, 53) urging said vanes (48) radially outwardly into sliding engagement with said track ring (78); and displacement adjusting means (86, 102) coupled to said track ring (78) and responsive to pressure of fluid fed to said outlet (121) for adjustably positioning said track ring (78) within said housing (12), and thereby controlling displacement of said machine, as a function of fluid pressure, characterized in that said rotor has a plurality of internal passages (60) extending radially between said slots (46) form an open outer end (61) at a periphery of said rotor to an inner end (62), said track ring (78) has a plurality of passages (84) extending radially therethrough, said fluid inlet passage means (64, 65, 66, 67) lead to said inner ends (62) of said rotor passages (60), and said fluid outlet passage means (112, 116, 118, 120, 122) includes outlet cavity means (112, 122) which is arranged between said housing (12) and said track ring (78) and is connected to said outlet (121) such that fluid pressure at said outlet (121) varies as a combined function of piston pumping of said vanes (48) through radial displacement in said slots (46) and centrifugal pumping of fluid through said rotor passages (84). The machine set forth in claim 1 wherein said housing (12) includes opposed backup plate means (24, 28) including port means (42, 44) in facing engagement with said rotor (22), said track ring (78) being movably positioned between said backup plate means (24, 28) surrounding said rotor (22). The machine set forth in claim 1 or 2 wherein said passages (84) in said track ring (78) are angulated radially of said rotor (22). The machine set forth in any of claims 1 to 3 wherein said slots (46) and said passages (60) in said rotor (22) alternate with each other circumferentially of said rotor (22) at uniform spacing. The machine set forth in any of claims 1 to 4 wherein said outlet cavity means (112, 122) includes a diametrically opposed pair of first cavities (122) and second cavities (112) staggered around said rotor (22). The machine set forth in claim 5 wherein said first cavities (122) are connected to a first annular chamber (56) and to said vane urging means (50, 52, 53) by passages (54). The machine set forth in claim 5 or 6 wherein said second cavities (112) are connected (116, 118) to said displacement adjusting means (86, 102). The machine set forth in any of claims 1 to 7 wherein said displacement adjusting means (86, 102) comprises a spring actuator (86) including a first piston (92) radially slidably mounted in said housing (12) and coupled to said track ring (78), and a coil spring (98) having a radially oriented axis and captured in compression between a spring seat (96) in said housing (12) and said first piston (92). The machine set forth in any of claims 1 to 8 wherein said displacement adjusting means (86, 102) comprises a hydraulic fluid actuator (102) including a second piston (108) radially slidably mounted in said housing (12) and coupled to said track ring (78) in diametric opposition to said first piston (92). The machine set forth in claim 9 wherein said fluid actuator (102) further includes a radial passage (107) having said second piston (108) slidable therewithin, and means (106) received in said passage (107) to form a seat (111) for said second piston (108) to limit radially outward motion thereof. The machine set forth in claim 10 wherein said seat forming means (106) is adjustably positioned to said passage (107). The machine set forth in claim 11 wherein said seat forming means (106) is a hollow cup-shaped sleeve adjustably threadably received in a passage (105) of the housing (12) and having a side port (120) for receiving fluid from said second cavities (112) of claim 7. The machine set forth in any of claims 2 to 12 wherein said vane-urging means (50, 52, 53) comprises a fluid chamber (50) at the radially inner end of each said slot (46) beneath the associated said vane (48), and kidney slots(52, 53) in said port means (42, 44) for feeding fluid to said chambers (50). The machine set forth in claim 13 wherein said rotor (22) further includes internal passages means (74, 76) interconnecting all of said internal ends (62). The machine set forth in any of claims 2 to 14 wherein said shaft (20) extends from said housing (12) through one (28) of said backup means, and said fluid inlet (124) is coaxial with said shaft (20) in the other (24) of said backup means. The machine set forth in claim 15 further comprising a spiral inducer (126) coupled to said shaft (20) and positioned in said inlet (124) for pressurizing fluid at said inlet.

Inventors: HANSEN LOWELL D, HANSEN, LOWELL D.
Applicants: VICKERS INC, VICKERS INCORPORATED
Application year: 1990
Main classification: F04C2
IPC codes: F04C14, F02M37, F04D13, F04D29, F04C2