Vane type positive displacement pump

Abstract: Vane type positive displacement pump includes three separate vane type pump units (2,3,4) on a single shaft (5), with spacers (54,55) between the middle pump unit (3) and both end pump units (2,4) for axially positioning the pump vanes (15,16) for the middle pump (3) unit at both ends and axially positioning the pump vanes (17,18;19,20) for the two end pump units (2,4) at one end. The shaft has reduced diameter journal portions (27,29) adjacent opposite ends of the barrel portion (28) for the middle pump unit (3) on which the spacers (54,55) are mounted. Also, the outer diameter of the barrel portions (27,29) for the two end pump units (2,4) corresponds to the outer diameter of the journal portions for the spacers. At the other end of the end pump units are end bearings (8,9) for axially positioning the vanes (15,16;19,20) for the end pump units (2,4) at such other ends.

Description: This invention relates generally, as indicated, to a vane type positive displacement pump (or motor), and, more particularly, to a single shaft, multiple pump unit vane type positive displacement pump (or motor) which does not compromise the efficiency of the pump units or the mechanical integrity of the overall pump design. Vane type positive displacement pumps and motors use mechanical power to compress a fluid when operating as a pump and compressed fluid as a power source when operating as a motor. To avoid complication of description, these devices will be described herein as pumps, it being understood that the reverse operation as a motor is equally possible. Typically these pumps comprise a housing containing a liner with a bore and a pair of end bearings which support a rotor shaft with its axis parallel to but offset from the axis of the liner. Vanes or blades slide radially in and out in slots through the shaft to define pockets which expand and contract with each shaft revolution. Axial positioning and sealing of the ends of the vanes or blades of prior art pumps have been accomplished in different ways, each with accompanying advantages and disadvantages. One technique permits maximum volumetric efficiency but limits design and construction flexibility, whereas another technique has reduced volumetric efficiency but enhanced design flexibility. In this context, volumetric efficiency is increased when the rotor shaft is mounted as nearly tangent to the liner bore as practically possible. Also, mechanical integrity is enhanced when multiple pump units are mounted on a single rotor shaft. The first of these prior art techniques involves the provision of stepped journals on the rotor shaft at opposite ends of the liner. This permits the end bearings that are mounted on the shaft journals to overlap radially the shaft outer diameter surrounded by the liner (hereinafter sometimes referred to as the "rotor barrel"), thus serving to position the vanes or blades axially even when the innermost retracted position of the blade tips substantially corresponds to the outer diameter of the rotor barrel. However, this design prohibits more than one pump unit per shaft because the end bearings for the pump unit must be assembled from opposite ends of the shaft. Accordingly, to provide a multiple pump unit utilizing this design requires interconnecting the shafts of a plurality of individual pump units using various types of drive couplings, thereby compromising the mechanical integrity of the pump design and increasing the overall cost. Another prior art technique for axial positioning of vanes or blades in this type of pump utilizes a shaft of uniform diameter which permits multiple pump units to be mounted on a single shaft. However, this is accomplished at the expense of volumetric efficiency, in that in order to position the vanes or blades axially when the blade tips are at their innermost retracted positions, the rotor barrel is mounted short of tangent to the liner bore. Thus, the blade tips never retract completely, leaving as a minimum a small amount of the end faces of each blade projecting radially outwardly beyond the outer diameter of the rotor barrel which bear against a respective end bearing to position the blades axially. Because the rotor barrel is not tangent to the liner bore, the blades never retract completely into the barrel, whereby volumetric efficiency is reduced. Still another prior art technique which permits multiple pump units to be mounted on a single shaft is disclosed in U.S. Patent No. 4,619,594. In this patent, which is assigned to the same assignee as the present application and is incorporated herein by reference, the axial positioning of the blades (vanes) is accomplished by providing each blade with a radially extending tab at one axial end thereof. The tabs fit in an annular groove formed either by a counterbore in each pump liner or by a separate wafer at one end of each pump liner having an internal diameter that is greater than the liner internal diameter. While the volumetric efficiency of this pump design is greater than the prior art technique of mounting the rotor barrel short of tangent to the liner bore, it still lacks the volumetric efficiency of the single pump unit per shaft design previously described because of the small volume of fluid, termed the carryover volume, in the pockets in the counterbore between the tabs which in effect is never expelled from the pump. The pump of this invention comprises a single shaft, multiple pump unit vane type positive displacement pump which does not compromise the efficiency of any of the pump units or the mechanical integrity of the overall pump design. According to the present invention there is provided a vane type positive displacement pump comprising a housing, a shaft mounted for rotation in said housing, an intermediate vane type pump unit and two end vane type pump units mounted on said shaft in axially spaced relation with said intermediate pump unit located intermediate said end pump units, each said pump unit including a cavity which is located in said housing and has an axis parallel to and offset from the axis of said shaft and a set of vanes mounted in and radially slidable with respect to said shaft, said vanes engaging the walls of said cavities as said shaft rotates, and positioning means for positioning said vanes axially in said cavities, said positioning means including spacer means between said intermediate and end pump units, characterized in that said shaft has reduced diameter journal portions adjacent opposite ends of said cavity for said intermediate pump unit and on which said spacer means are mounted for axially positioning said vanes of said intermediate pump unit therebetween. Preferably, each pump unit is sized such that the running clearance between the respective rotor barrel and surrounding cavity is substantially the same as for current conventional single pump unit per shaft designs. Preferably, the journal size of the middle pump unit on which the spacers are mounted is used to determine the outer diameter of the rotor barrels for the two end pump units. Preferably, the innermost retracted position of the vanes of the end pump units substantially corresponds to the inner diameter of the spacers between the middle and end pump units. To prevent possible interference of the vanes with the spacers in the event that the vanes protrude into the spacer inner diameters in the extreme tolerance stack-up condition, the inner diameters of the spacers are desirably chamfered to guide the vane tips smoothly out from within the spacer inner diameters during outward movement of the vanes beyond their innermost retracted positions. An embodiment of the invention will now be described by way of example, with reference to the accompanying drawings, in which: - Fig. 1 is a longitudinal section through a preferred form of vane type positive displacement pump in accordance with this invention; Figs. 2 and 3 are reduced transverse sections through the pump of Fig. 1, taken generally along the lines 2-2 and 3-3 thereof; Fig. 4 is an enlarged longitudinal section showing the rotor shaft portion of the pump of Fig. 1; and Fig. 5 is a further enlarged longitudinal section showing one of the spacers of the pump of Fig. 1. Referring now in detail to the drawings, and initially to Fig. 1, there is shown a positive displacement pump 1 in accordance with this invention including three vane type pump units 2, 3 and 4 which share a common rotor shaft 5. The shaft 5 is mounted for rotation within a cylindrical bore 6 in a pump housing 7 as by means of a pair of sleeve bearings 8, 9 at opposite ends of the shaft. At one end of the bore 6 is a retaining ring 10 to retain the various parts in assembled relation, whereas at the other end of the bore is a spring tension washer 11 that provides a desired preload on the various pump parts to maintain the desired fluid seal therebetween. Each of the pump units 2 through 4 includes its own set of vanes or blades 15, 16; 17, 18 and 19, 20 which extend through respective slots 21, 22; 23, 24 and 25, 26 in longitudinally spaced barrel portions 27, 28 and 29 of the rotor shaft 5. Surrounding the barrel portions 27, 28 and 29 are respective liners 30, 31 and 32. The respective slots 21 through 26 and barrel portions 27 through 29 can best be seen in Fig. 4, which is a longitudinal section showing the rotor shaft 5 by itself. Each liner 30, 31 and 32 may be retained within the housing bore 6 as by means of a set screw 33 extending through a bore 34 in the housing wall 35 into an external recess 36 in each of the liners as schematically shown in Figs. 2 and 3. Two mutually perpendicular slots 21, 22; 23, 24 and 25, 26 extend longitudinally through each barrel portion 27, 28 and 29 for receipt of two pairs of blades 15, 16; 17, 18 and 19, 20. Also, each pair of blades 15, 16; 17, 18 and 19, 20 may be formed as a single unit in a generally C-shape, with each pair facing in opposite directions in the respective slots as shown, or formed separately as desired. The size of the middle pump unit 3 is desirably selected using a conventional single pump unit per shaft design and standard journal size for that particular pump unit . Also, the liner 31 for the middle pump unit 3 has an eccentric bore 40 whose axis is parallel to but offset with respect to the axis of the rotor shaft 5 as shown in Fig. 2, with the rotor barrel portion 28 as nearly tangent to the liner bore 40 as is practicable. Any clearance that does exist between the rotor barrel portion 28 and liner bore 40 is due to machining tolerances on the rotor shaft 5 and liner 31. As in prior art pump designs, the blade tips 41 for the middle pump unit 3 engage the liner bore 40 to define pockets 42 through 45 which expand and contract as the rotor shaft 5 rotates. As the pockets move past the liner passages 46, 47 and associated ports 48, 49 in the pump housing 7, fluid is drawn in from one port and expelled out through the other port. Assuming the rotor shaft 5 is rotated in a clockwise direction as viewed in Fig. 2, the fluid will enter pump unit 3 through the port 48 and associated liner passage 46 and will be discharged from the pump under pressure through the liner passage 47 and associated housing port 49. Rotation of the rotor shaft 5 in the opposite direction will cause a reverse flow of fluid through the pump 3. Each of the other pump units 2, 4 operates in a similar manner. The rotor slots 21 through 26 for the respective pump units 2 through 4 are axially longer than the respective blades 15 through 20 which are substantially the same length as the respective liners 30 through 32. The middle pump unit 3 is separated from the two end pump units 3, 4 by spacers 54, 55 which are mounted on the rotor shaft 5 adjacent opposite ends of the barrel portion 28 of the middle pump unit 3 preferably using the standard journal size for that particular pump unit. To that end, the outer diameters of the journals 56, 57 for the two spacers 54, 55 are somewhat less than the outer diameter of the middle pump unit barrel portion 28 whereby the opposed end faces 58, 59 of the spacers 54, 55 radially overlap opposite ends of both the liner 31 and barrel portion 28, thus serving to position the blades 17, 18 axially within the slots 23, 24 even when the blades 17, 18 are in their radial innermost retracted positions. The blades 15, 16 and 19, 20 of the respective end pump units 2, 4 are positioned axially within the respective slots 21, 22 and 25, 26 (which are longer than the blades) by the spacers 54, 55 at one end and the end bearings 8, 9 at the opposite end. The barrel diameters 27, 29 for the two end pump units 2, 4 are made to correspond to the journal diameters 56, 57 for the middle pump unit 3. Also, the liners 30, 32 for the two end pump units 2, 4 are sized such that the running clearance between the respective barrel portions 27, 29 and liner bores 60, 61 is substantially the same as for current conventional single pump unit per shaft designs, whereby the efficiency of the two end pump units 2, 4, like that of the middle pump unit 3, may be substantially the same as for current conventional single pump unit per shaft designs. In such a pump construction, the travel of the blades 15, 16 and 19, 20 in the respective liner bores 60, 61 of the two end pump units 2, 4, which are substantially identical, is such that the innermost retracted position of the blade tips 62 of the end pump units is very close to the inner diameter of the spacers 54, 55 (see Figs. 1 and 3). In the extreme tolerance stack-up condition, it is feasible that the blades 15, 16 and 19, 20 will protrude into the spacer inner diameters, causing interference. To avoid this, special chamfers 65 are desirably provided on the inner diameters of the spacers 54, 55 on the ends facing the end pump units 2, 4 to guide the blade tips 61 out smoothly during outward movement of the blades 15, 16 and 19, 20 beyond their innermost retracted positions. If desired, the chamfers 65 on the spacers 54, 55 need only be provided in the regions of the innermost retracted positions of the blades 15, 16 and 19, 20 for the end pump units 2, 4. However, for reasons of economy, the chamfers 65 desirably extend all the way around the spacers at an angle of approximately 18 to 20° as measured from the end face of the spacers (see Fig. 5). Also, the height of the chamfers 65 is desirably kept to a minimum size of between approximately 0.5 mm (0.020 inch) and 1.5 mm (0.060 inch) to restrict internal leakage. The diameter of the journals 66, 67 for the two end bearings 8, 9 is also preferably sized using the standard journal size for the two end pump units 2, 4, which is somewhat less than the barrel 27, 29 diameter for the two end pump units 2, 4 so that the end bearings 8, 9 serve to position the adjacent ends of the blades 15, 16 and 19, 20 within the slots 21, 22 and 25, 26 even when the blades are in the radial innermost retracted positions. Moreover, the opposed ends of the end bearings 8, 9 as well as that of the spacers 54, 55 may be chamfered to accommodate inside corner radius on the rotor shaft 5. As previously indicated, the two end pump units 2, 4 operate in substantially the same manner as the middle pump unit 3. That is, assuming as before that the shaft 5 is rotated in a clockwise direction as viewed in Fig. 3, fluid will enter pump unit 2 through housing port 70 and associated liner passage 71 and will be discharged from the pump under pressure through liner passage 72 and housing port 73. At the same time, fluid will enter pump unit 4 through housing port 74 and associated liner passage 75 and will be discharged from the pump under pressure through liner passage 76 and housing port 77 (see Fig. 1). Rotation of the shaft 5 in the opposite direction will cause a reverse flow through the two end pump units 2, 4.

Claims: A vane type positive displacement pump comprising a housing (7), a shaft (5) mounted for rotation in said housing, an intermediate vane type pump unit (3) and two end vane type pump units (2, 4) mounted on said shaft in axially spaced relation with said intermediate pump unit located intermediate said end pump units, each said pump unit (2, 3, 4) including a cavity (40, 60, 61) which is located in said housing and has an axis parallel to and offset from the axis of said shaft and a set of vanes (15, 16, 17, 18, 19, 20) mounted in and radially slidable with respect to said shaft, said vanes engaging the walls of said cavities as said shaft rotates, and positioning means for positioning said vanes axially in said cavities, said positioning means including spacer means (54, 55) between said intermediate and end pump units, characterized in that said shaft (5) has reduced diameter journal portions (56, 57) adjacent opposite ends of said cavity (40) for said intermediate pump unit (3) and on which said spacer means (54, 55) are mounted for axially positioning said vanes (17, 18) of said intermediate pump unit therebetween. The pump of claim 1, wherein said shaft (5) has a larger diameter barrel portion (28) disposed between said reduced diameter journal portions (56, 57) and surrounded by a liner (31) containing said cavity (40) for said intermediate pump unit (3), and each of said spacer means (54, 55) radially overlaps said larger diameter barrel portion (28) and said liner (31) for said intermediate pump unit. The pump of claim 2, wherein said vanes (17, 18) for said intermediate pump unit (3) are received in longitudinal slots (23, 24) in said larger diameter barrel portion (28), and said slots (23, 24) are longer than said larger diameter barrel portion and said vanes contained in said slots whereby said spacer means (54, 55) serve to position said vanes axially within said slots. The pump of any of claims 1 to 3, wherein said shaft (5) includes reduced diameter barrel portions (27, 29) for said end pump units (2, 4) and corresponding in diameter to the diameter of said journal portions (56, 57) for said spacer means (54, 55). The pump of claim 4, wherein said spacer means (54, 55) also axially position said vanes (15, 16, 19, 20) for said end pump units (2, 4) at one end of each of said cavities (60, 61) for said end pump units, and said positioning means includes end bearings (8,9) adjacent the other ends of said cavities for said end pump units for axially positioning said vanes (15, 16, 19, 20) for said end pump units at said other ends. The pump of claim 5, wherein said shaft (5) includes additional journal portions (66, 67) adjacent said other ends of said cavities (60, 61) for said end pump units (2, 4) and on which said end bearings (8, 9) are mounted, and the outer diameter of said additional journal portions (66, 67) is less than the outer diameter of said barrel portions (27, 29) for said end pump units (2, 4). The pump of claim 6, wherein said barrel portions (27, 29) for said end pump units (2, 4) are surrounded by liners (30, 32) containing said cavities (60, 61) for said end pump units (2, 4), and said end bearings (8, 9) radially overlap said barrel portions (27, 29) and liners (30, 32) for said end pump units. The pump of claim 7, wherein said vanes (15, 16, 19, 20) for said end pump units (2, 4) are received in longitudinal slots (21, 22, 25, 26) which (i) are disposed in said barrel portions (27, 29) for said end pump units and (ii) are longer than said vanes for said end pump units whereby said spacer means (54, 55) and said end bearings (8, 9) serve to position said vanes for said end pump units axially within said slots for said end pump units. The pump of any of claims 4 to 8, wherein said barrel portions (27, 29) for said end pump units (2, 4) are mounted substantially tangentially to the walls of said cavities (60, 61) for said end pump units, and the inner diameters of said spacer means (54, 55) have chamfer means (65) on the ends facing said end pump units to guide said vanes (15, 16, 19, 20) for said end pump units smoothly out from within said inner diameters of said spacer means during outward movement of said vanes for said end pump units in the event of said vanes for said end pump units protruding into said inner diameters of said spacer means when in their innermost retracted positions. The pump of claim 9, wherein said chamfer means (65) extend all the way around the inner diameters of said spacer means (54, 55). The pump of claim 9 or 10, wherein said chamfer means (65) extend at an angle of approximately 18 to 20° as measured from said ends of said spacer means facing said end pump units (2, 4) and have a height of between approximately 0.020 inch and 0.060 inch to restrict internal leakage. The pump of any of claims 9 to 11, wherein the inner diameters of the other ends of said spacer means (54, 55) have additional chamfer means to facilitate assembly of said spacer means onto said shaft (5).

Inventors: JOHNSON DUANE C, KAPUR DESH K, JOHNSON, DUANE C., KAPUR, DESH K.
Applicants: LEAR ROMEC CORP, LEAR ROMEC CORP.
Application year: 1990
Main classification: F04C11
IPC codes: F04C2, F04C11