DE1403890A1 - Rotary vane pump - Google Patents

Description

'140389Q

P 14 03 890.5 Munich, November 22, 1968

Ro / He.

Pacific Press & Shear Corporation, Oakland / Calif. (V.St.Ao)

"Rotary vane pump"

The invention relates to a reversible rotary vane pump variable capacity, with a housing which has a cylindrical chamber and from there an opening through it the wall of this housing has, with a ring smaller outside diameter than the housing chamber, with a partially A pump chamber delimited by a cylindrical inner wall, with a pivot pin opening arranged outside this pump chamber opposite the housing, with a web whose Cross-section is smaller than the housing opening and which extends from the ring into the housing opening! with a Means for pivotally mounting the ring in the housing, the ring through a neutral position of can pivot with a matching diameter, with a

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axially to the cylindrical housing chamber through the housing extending shaft and with a rotor provided on the shaft in the pump chamber, this rotor having a has narrow cylinder with substantially radial vane slots on its periphery, with feed and Discharge channels, which in the periphery of this cylinder between these vane slots end, with a vane slidably provided in each of the vane slots, with one slidable provided between the ring and the rotor Storage device, each outermost edge of the blade with this storage device for the purpose of forming Uinfangkammer around the rotor can be brought into engagement, with a device for supplying and removing the liquid to the rotor, which comprises a control rotor wedged onto the shaft at one end for engagement with the rotor, this control rotor near its other end with a number of radial flow passages correspondingly the number of pump rotor supply and discharge channels has, with each of these radial passages with one of these supply and discharge channels of the rotor connecting longitudinally extending passage, with means for driving the pump and optional adjustment of the pump and the ring from a position of maximum pump capacity in one direction through the aforementioned neutral Position in a position of maximum pump capacity in the opposite direction.

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The rotary bucket pump according to the invention is thereby characterized in that a front housing surrounding the control rotor is provided, which is attached to one end of the pump housing and arranged in pairs diametrically Has radial openings which extend towards the control rotor and essentially in the plane of these radial passages open so that when the control rotor rotates, each of these radial passages alternates with each of the radial openings in the front housing, the liquid alternating through one of the radial openings at low pressure added and this through the other of the radial openings can be delivered with higher pressure

Appropriately, the device for the optional adjustment of the ring around the joint includes a cylinder on each side of the plunger at a distance therefrom, in each of the cylinders a piston and a push rod extending from the piston to the abutment on the plunger and each cylinder having one Acting connection has ₉ which led behind the piston

A device for balancing the radial pressures is advantageous to the shaft provided regardless of the position of this Radialdrüoke, this device one the

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Shaft surrounding bearing ring on each side of the rotor includes! each storage on the inside two ' similarly arranged grooves at diametrically located points have a device is provided for creating a hydraulic fluid connection from one of the input-output passages, if the latter acts as an exit passage, to the corresponding grooves in the bearing rings, which ensure a balance of the hydraulic pressures under prevailing working conditions and where a Similar device is provided which has a hydraulic fluid connection from the remaining entrance-exit passage to the remaining groove in each of these Bearing rings creates when this remaining input-output passage works as an exit passage.

The essential advantages of the proposal according to the invention are"

1.) Can the performance or delivery rate of the pump be changed? »

2.) the performance or flow rate is not only adjustable, but the flow of liquid through the pump can also be reversed;

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3.) The friction losses are reduced to such an extent that the performance of the pump is significant is increased;

4o) the pump can run at a high speed and a promote high pressure

5 ·) the pump blades are continuous and radial at the pump pressure to a circumferential stop assembly of the rotor printed in such a way that the pump losses are reduced and the pump pressure and the delivery speed can be increased j

6.) With the rotary vane pump, each pump part can work as a reversible, variable displacement pump

The invention is explained in more detail below using a preferred exemplary embodiment with reference to the accompanying drawings explained

In the drawings shows?

1 shows a sectional view of the pump,

Fig. 2 is a sectional view along the line 2-2 in Pig. 1,

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Fig. 3 is a sectional view along the line 3-3 in Fig. Ij Fig. 4- is a sectional view along the line 4-4 in Fig. 1;

Figure 5 is an end view of a bored hole Pump rotor;

Fig. 6 is a fragmentary representation of a valve detail of that of Fig. 3 in faint lines valve shown;

FIG. 7 shows a cross section of a pump structure different from FIG. 1; FIG.

8 shows another illustration of the embodiment of FIG. 7 with the pump housing omitted;

FIG. 9 is a sectional view of the embodiment shown in FIG. 7.

The rotary vane pump has a generally cylindrical pump housing 1 with a lateral extension 3 on o The pump housing 1 consists of side walls 5 »7 and a common partition 9 for

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Formation of the two accuracy chambers 11, 13. The walls of the Housing chambers 11, 13 have concentric wall openings, their centers on a common axis ljsjen.

In each housing chamber 11, 13 there is a rotating ring 15, the outside diameter of which is smaller than the inside diameter the associated housing chamber is to perform an adjustment movement of the rotary ring in the chamber to be able to. The rotating ring 15 has a tapered to-running Circumferential lead 1? on, which extends into the space of the extension 3 of the housing chamber. The chamber walls and the circumferential projection have aligned Openings for mounting an axis of rotation 19, by means of which each rotating ring can be pivoted within its housing chamber is"

At a point diametrically opposite the pivot each rotating ring is provided with a plunger 21, the end of which is button-shaped. It extends into a common opening, which includes both! pump chambers, this common opening by a protruding edge is limited. If each rotating ring is arranged in its housing chamber, it can be pivoted about a neutral position.

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Each rotating ring 15 "forms with its cylindrical inner wall in part the pump chamber for the pump rotor 31. It is keyed onto a shaft 33 which, axially extends through the two housing chambers. The two Pump rotors 31 are separated from one another by a separating piece 35 which is arranged on shaft 33.

Each pump rotor has a disk-shaped or narrow cylinder 37. It has an axial opening for the continuous shaft 33 and a split pin 39, whereby it is keyed onto this shaft.

Each rotor cylinder 37 has a number of radial blades - slots 41 and a number of recesses 4-3 for the Absorption and delivery of the liquid. Both the slots 4-1 and the recesses 4-3 end at the circumference of the cylinder 37, the recesses 43 being located between the slots 41.

A paddle 47 is slidably mounted in each slot 41. Their storage is such that they are with their outer edges can come into engagement with slidable stop pieces 51, which the outer edges of the blades 47 are circular Enclose inside the pump chamber.

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The stop pieces 51 can have various shapes. In the embodiment shown, the stop piece has 51 an outer raceway 53, which is within the Pump chamber ■ is located on the surface of the rotating ring 15. In addition, the stop piece has an inner raceway 55. It extends around the outer edges of the blades 47 and can be engaged with it. A number of roller bearing pieces 59 are located between these raceways «

The supply and discharge of the liquid takes place through a control rotor 61 which has bores and which consists of a cylindrical piece with an axial bore and has a recess Wedge piece onto the pump shaft 33 by means of a key, one end of the pump piece in engagement with the next pump rotor is at a standstill.

A number of flow passages extend through the Roto * 61 63 · They correspond in number to the recesses 43 in the cylinder 37. Each flow passage 63 stands with one of these recesses 43 in connection.

If the control rotor 61 is keyed onto the pump shaft, can

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it rotates with the pump rotor 31, where «& · the: Fluid passage between each rotor bore 63 with its associated recess 43 for receiving and Delivery of the liquid is maintained

The control rotor 61 is in order to rotate freely a bearing 69 supported, which has an inner race 70, whose function also depends on the outer surface 71 of the Rotor 61 can be taken over, and has an outer race 73 »In between are the rotor bearing parts 75.

The outer race 73 is mounted within an overhanging, lateral extension 79 of a housing 81. The extension 79 is provided with a laterally extending, projecting edge 83 that is flush within the adjacent side opening of the pump housing 1 is arranged. The surface of the lateral extension lies here 79 of the housing 8l on the adjacent side wall of the pump housing 1. The housing can be in this arrangement 81 can be screwed to the pump housing 1 with the aid of a number of screws 87 »By grooving the enclosed Edge of the pump housing and by placing an O-ring seal 91 with pressure within the so formed The connection point between the

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Seal the pump housing and the end housing in such a way that that the liquid is prevented from leaking at this point.

The housing 81 has an axial opening in correspondence with the outer diameter of the adjacent end of the control rotor 61 provided with bores. At diametrical An opening 95 is located opposite points for the supply and discharge of the liquid, which extends vadially through the inner circumference of the 8l from the end. The opening 95 expands as a recess 97 the inner periphery of the housing 81. The recess 97 ends at a short distance from the corresponding recess the opposite opening 95. The one opening is used for the supply of the liquid, while the other opening takes care of the drainage, which of the two openings has to take over the relevant functions depends on the respective position of the rotary ring 15.

For fluid communication between each opening 95 and the associated pump rotor 31 via the intermediate control rotor 61 is provided with bores Plate 101 within the axial opening of the end housing 81 provided. This plate 101 has an opening whose

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Diameter is larger than that of the pump shaft. the Plate 101 also has upper and lower arcuate grooves 103. These grooves form an angle that is approximately corresponds to the angle which is formed by the recess 97 of each discharge opening 95 at its inner end » The opposing recesses are connected to one another by a number of holes, which are individually on the The periphery of the plate 101 opens into a radial bore 107.

The plate 101 is within the end housing 81 by a Wedge 109 held. Such a wedge prevents one Relative rotation of the plate 101 within the end housing. In contrast, the plate 101 can unhindered in the axial Direction can be adjusted.

This adjustment is also made by means of an intermediate ring 111 allows, which is located on the shaft 33 within the axial bore of the plate 101. The intermediate ring 111 has a length which is slightly larger than the corresponding dimension of the plate 101 and is between the control rotor 61 and a compensating plate 115 held, which is on the shaft within the end housing 81 is located.

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This plate 115 at the drive motor end of the pump shaft is secured by a protruding edge 117 on the shaft and held at the other end of the engine by a Sing 121. The rotatable part of the pump assembly is under large Pressure held by a nut 123, which is screwed onto the relevant shaft end in engagement with the ring 121 is.

A support 125 », which is screwed to the housing 81 at the motor end of the pump, is used to mount a drive motor 127, to accommodate a shaft seal 129 and a further seal 131 between the carrier 125 and the adjacent housing 81

At the other end of the pump, a cover 135 is on the housing 81 screwed on by means of screws 137, which protects the fastening nut 123 and serves to cover it. An annular seal 139 is provided between the housing 81 and the cover 135, which the pressures within the Cover 135 is exposed and seal the connection point between the cover · and the adjacent housing should so that no liquid can escape at this end of the pump assembly.

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After starting the engine 127, all pumps turn on components with the shaft 33 »which are pinned to it. Furthermore, other parts of the pump also rotate, the are fastened between the protruding edge 117 at the shaft motor end and the nut 123 at the other shaft end. to These parts include the pump rotors 31, the separating piece 35, the control rotors 61 with bores, the intermediate rings 111 and the balancing plates 115 'is each rotating ring 15 in its neutral position, i.e. in the In the position in which its center point coincides with the center point of the rotor 31, the pump is in "symmetry". All rotor chambers have the same efficiency and convey the same amount of fluid · As a result there is a hydraulic equilibrium state for the associated discharge openings 95. In this case, therefore not pumped.

If, however, the rotating ring is moved to another position in which its center point does not coincide with the rotor axis, the blades can extend outwards on one side of the rotor cylinder circumference, while this happens to a lesser extent on the diametrically opposite side. When the rotor rotates, these blades are pushed inwards, which reduces the capacity of the ^k """" formed by these blades

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Chamber is decreased. On the other hand, those blades adhere that previously assumed a position that is closer to one another at the center of the rotor cylinder ", the possibility of to move outwards, thereby enlarging the chambers between these wings «Below these Under certain circumstances, when the rotor is rotating it becomes a subatmospheric one Pressure condition in the circumferential chambers of the rotor thawing produced when the chambers expand in volume. After the same chambers begin their volume later to decrease, which is the case when the concerned If the blades are pushed in towards the cylinder, the fluid pressure in the chamber increases. This liquid is gradually released at the rotor openings and to the associated main pipe for the supply line ftzw. Discharge of the liquid conducted. By doing In the case described, this main passage is used for delivery of the liquid for that part of the pump ftaues. In contrast, the diametrically opposite main bore wM for the supply ftzw. Deriving the liquid at the suction or receiving end for the liquid ftetBeffenden part of the pump defrosting

By shifting the rotating ring 15 from the position explained by being "neutral position" into a new position

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on the other side of the rotor axis, the state is reversed, i.e. the main bore that was previously used served to drain the liquid, now becomes the suction end of the relevant pump part. The other main bore, on the other hand, becomes the liquid discharge opening.

The Drtioke, with which the rotary pump the liquid delivers change according to the extent to which the rotary ring 15 is set beyond its neutral position will o On the other hand, the direction of the fluid flow depends by the pump depends on which side the rotating ring is moved with respect to its neutral length has been.

Since jefttr rotating ring 15 moved independently of others can be, both sides of the pump structure can be independent work from each other, so that the direction of liquid flow in each pitch half and the generated Pressures can be different from each other.

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Balanced path ο This creates between the plate and the rotating control rotor 61 or plate 115 has very little friction and very little hydraulic Resistance",

In order for the pump structure to be efficient, the Blades 4-7 are subjected to an outward pressure so that they are in contact with the inner raceway of the bearing structure are kept. This is done on hydraulic Way achieved by the inner edges of the blades of the liquid in the respective prevailing liquid the delivery pressure of the relevant pump part is continuously applied «,

For this purpose, each control rotor 61 has a circular recess 141 in that end which is located opposite the adjacent pump rotor. The diameter of this recess 141 is such that it can be aligned with the inner ends of the radial blade slots 41 . A number of bores 145 extend in the longitudinal direction through the control rotor 61 and connect the space around the associated intermediate ring 111 with the circular recess. 141 .... "- - ^~}::;": · "■■■.." - . ■■ "" - .. '·. ■ ^:; ^.:' - - '.

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So that in this space 144 around each intermediate ring 111 to each Time during pumping liquid with a Druok is present, so that the blades correspond to one Are subjected to pressure by which they are pushed outwards, a radial bore 147 is in the Plate 101 is provided. Also in this record is a further bore 149 is provided which crosses the radial bore 147 and at one end with one of the radial openings 107 is connected. This bore 149 has a portion lying between its ends, the Diameter is slightly larger. So there is a valve chamber formed with a valve seat 151 at each end of this chamber.

In this valve chamber there is a ball valve 155, that from one valve seat 151 to the other depending on the direction in which a pressure is applied to this ball valve 153 is exercised, can commute. Thus becomes independent of which of the two grooves 103 currently has the high pumping pressure, the given low-pressure side through the Ball valve 153 completed while the liquid was high Pressure through radial bore 147 to space 144 each intermediate ring 111 occurs from where it passes through the bores 145 and into the Sohaufel braid 41 behind the innermost Edges of the Schaifeln can flow. As a result will be

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during operation all blades under a continuous, hydraulic bridge held through which it to the outside are pressed into pressure contact with the inner raceway 55 of the attachment piece 51 of the associated pump rotor 31

one

the seal between the vanes 47 and the surface adjoining them, which prevents the liquid from leaking sustained with essentially no heat loss occur at the points of contact.

Not only are these frictional losses suppressed, but also the bending stresses that normally occur in connection with the frictional drag that arises in a conventional construction in which the blades slide along a fixed surface engaging them. All of this contributes to the fact that the rotary pump operates with considerably higher pressures, with lower Y * rlus.ten _s with finer smaller; Beanjpr ^ ohun ^ g and strain and consequently with a greater efficiency

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Ea are two pairs of opposed cylinders 161 in the Band 23 is provided, which surrounds the opening of the Pampen housing 1. Each cylinder 161 is in correspondence with the protruding plunger 21 of one of the rotating rings 15, a piston is slidably located in each cylinder 161 with an extension 165 »the end of which is completed · This extension 165 can come into engagement with the plunger. A recess 167 on each piston is used for Storage of a Q-sealing ring 169 for sealing the Piston in its cylindrical bore.

The piston can come out of its cylinder as a result of a cover 171 doesn’t emerge, which covers the adjacent cylinder bores ein.e S, screw opening 173, in which a loading 175 can be skated "

EJ.nj fgder 3.77 b, can be found behind each piston, 163 and h§tj <| i§ ATifgjbj, ei | ie slight contact between the 4f » ^m fi ^ Sf ^ iiB * I- ¹ ^ naughty ^ uerhallif» if no Dr | ßJ | s j

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If hydraulic fluid gets into a cylinder, it will an adjustment of the relevant rotary ring and a corresponding setting of the associated pump works. A flow of the liquid into the other cylinder causes an adjustment of the associated pump in the opposite one This makes sense · As a result, each of the two pumps can be set in this way independently of the other that it conveys a maximum amount of liquid either in one direction or in the other direction, whereby this adjustment of the pump takes place through a neutral position.

The liquid flows out of the housing chambers 11, 13 and the associated spaces within the pump structure through a pipe 185, which is only for one or also provided for both chambers o

Instead of the stop piece 51 between the pump rotor and the rotating ring 15, a stop ring made of brass, for example, can also be used * This stop ring is hydraulically through on its outer surface Pump pressure equalized this becomes any Time prevailing on the inner surface of the stop ring Pressure balanced The "result is," that ^ this stop ring ^

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in oil or in another liquid to be pumped swims.

Reference is made to FIGS. 7, 8 and 9. There is a rotary ring 193 is also provided, which corresponds to the rotary ring 15 of the first embodiment. Both forms of execution differ in that, in the second embodiment, a soling ring 194 made of brass, bronze or another suitable metal. This stop ring 194 has diametrically opposite recesses 195, which are located in the inner circumferential surface of the stop ring "and from each other by the short Intermediate parts 197 are separated. Concentrate on this Stop ring 194 is a rotor ring 198, which blades 47 touch. The openings 199,? in the rotor ring 198 bring the recesses 195 in connection with the associated rotor chamber, so that the pressures along the inner surface of the rotor ring substantially through the pressures are equalized at the appropriate Places occur along the outer surface of the rotor ring. The rotor ring can thus move through unhindered the rotary motion of the rotor blades turn, wee being the Liquid serves as a lubricant. This reduces friction to a minimum.

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Auoh can the bearing ring 69 around each control rotor 61 in the The first embodiment is replaced by a bearing ring 205 · This bearing ring 205 is in its end housing 81 preferably arranged with the application of pressure. On the inside of the bearing ring 205 ″ are located diametrically opposite recesses 209, which with the Recesses 195 of the Ansohlagringes are comparable and are also separated from each other by short intermediate parts 211

Each of the two recesses 209 is in communication with the opening 95 for the supply and discharge of the Liquid that is not immediate in the example shown Connection is, WJiI bores 215 are provided, which is through the front face, ha * u # e 81 and the bearing ring 205 Extensive and a connection with the Iqhrleitunien hera, telle.n »

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served and now as an opening for the derivation from the Pump is used and now a compensation pressure in the other Recess of the "relevant bearing ring 205 builds up. As a result, the unbalanced pressures that a Characteristics of positive displacement pumps are always essentially balanced, whatever is independent of the magnitude or direction of these pressures happens.

Claims

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Claims (2)

Claims Q Reversible rotary vane pump with variable capacity a housing which is a cylindrical chamber and from there an opening through the wall of this housing AL. " has, with a ring of smaller outer diameter than the housing chamber, with a partially cylindrical Inner wall "limited pump chamber, with one outside this pump chamber opposite the housing arranged pivot bolt opening, with a web whose cross section is smaller than the housing opening and which extends from the ring into the housing opening; with means for pivotably securing the ring in the housing, the ring being replaced by a neutral Can pivot position of matching diameter, with an axially to the cylindrical housing chamber through the housing extending shaft and with a rotor provided on the shaft in the pump chamber, wherein this rotor has a narrow cylinder with substantially radial blade slots on its periphery Supply and discharge channels, which in the periphery of this Cylinder end between these vane slots, a vane being slidably provided in the springs of the vane slots is, with a slidable between the ring and, 909827 / ΟΟ & β- UQ3890 the rotor provided bearing device, each outermost edge of the blade with this bearing device for the purpose of forming. Umf angskammem engaged around the rotor can be brought, with a device for supplying and conveying the liquid to the rotor, which one for the purpose of engagement comprising the rotor with one end keyed on the shaft, this control rotor in the vicinity its other end with a number of radial flow passages corresponding to the number of pump rotor inlet round Has discharge channels, with each of these radial passages with one of these supply and discharge channels of the The longitudinally extending passage connecting the rotor, with means for driving the pump and optionally Adjustment of the pump and the ring from one position maximum pump capacity in one direction through the aforementioned neutral position to a position of maximum Pump capacity in the opposite direction, characterized in that a End housing (81) is provided, which is attached to one end of the pump housing (1) and in pairs diametrically arranged radial openings (1o5), which look to the control rotor (61) and essentially in the plane of this open radial passages (63) so that upon rotation of the Control rotor (61) each of these radial passages alternately?. · with each of the radial openings (1o5) in the front housing (81) ■■ - -27-909827 / 0008 140389Q aligns, with the liquid alternating through a of the radial openings (1o5) "at low pressure and this through the other of the radial openings (to5) with higher pressure can be delivered. 2.) Rotary vane pump according to claim 1, characterized in that that the means for selectively adjusting the ring around the joint have a cylinder on each side of the Includes plunger (21) at a distance from this, wherein in each of the cylinders (161) a piston (163) and one extending from the piston (163) into contact with the plunger (21) Push rod lies and each cylinder has a loading connection (175) which leads behind the piston. 3 ·) Rotary bucket pump according to one of claims 1-2, characterized characterized in that a device for equalizing the radial pressures around the shaft (33) regardless of the position of this Radial pressures is provided that this device has a bearing ring surrounding the shaft (69) on each side of the rotor (31) includes, each bearing ring (69) on the inside two similarly arranged grooves (1o3) at diametrically located Has bodies that means is provided for providing a pressurized fluid connection from one of the entrance-exit passages, if the latter is the exit passage acts to the corresponding grooves in the bearing -28- 909827/0008 U0389Q wrestle, which for a compensation of the hydraulic Pressures under prevailing working conditions and that a similar facility is provided which a pressurized fluid connection from the remaining one Creates inlet-outlet passage to the remaining groove in each of these bearing rings, if this one remains Entrance-exit passage works as JLoading passage. 90982 7/0008 Blank page