DE1553248A1 - Rotary lobe pump - Google Patents

Description

DR. ING. P. WUESTHOFF ⁸ MUNICH 90 DIPL. ING. G. PTTLS SCHWEI & EHSTHASSE B

DÄE 22 06 51

PATENT LAWYERS tjeükohammadkbbsb: PHOTEOTPATENT MUNICH

1A-30 965 Description "" - "

to the patent application

- TEiV IHC,
Cleveland 17, Ohio, usa,

concerning
Rotary lobe pump

Lie invention relates to an oil burner system with a furnace or furnace pump, in which a rotatably mounted pump ring is used, which delimits a pump chamber for a two-stage sliding shoe pump in such a way that it is possible with the help of a pivoting movement of the pump ring, the displacement volume and thus also vary the delivery rate of the pump in direct proportion to the eccentricity in order to maintain a certain pressure drop across a fixed nozzle or restrictor while the pump operates with a minimal bypass flow.

With an oil burner system of the usual type the delivery rate of the combustion pump usually with the help of a Overpressure and bypass valve regulated. Apart from the need for the fixed nozzle or throttle, the excess flow rate becomes diverted by the pump and returned to the reservoir. There If this excess liquid has to be conveyed through the pump, energy is consumed unnecessarily.

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The invention now provides a shoe type pump before, in which one or more sliding blocks, which are supported by a rotatable runner, allow unhindered radial movements run and can be pivoted while following the outline shape of a pump bore in the middle part of a pivotally mounted pump ring is formed, which is within the by the geometric relationships dea pump mechanism given range is continuously adjustable. If the pump ring is adjusted, the stroke volume and thus also the delivery rate of the pump varies in direct proportion to the eccentricity. This adjustability enables the to operate the oil burner system at the smallest delivery rate, the is required to maintain a certain pressure drop across a fixed nozzle or throttle without creating an excess pumped liquid needs to be discharged via a bypass channel.

Furthermore, the invention makes it possible to use a nozzle of a different size as required, and to adjust the system so that that the pressure drop across the new nozzle again corresponds to the respective requirements, and during normal operation the The amount of liquid or oil to be diverted is always the same Is zero.

In the event that the fixed nozzle or throttle is out of any kind Basically clogged, measures have been taken to discharge the oil via a bypass route and into the bypass line a flow- or pressure-sensitive warning device can be switched on, by means of which the fact can be displayed

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it is possible that the nozzle has clogged.

An object of the invention is thus to provide an adjustable Provide sliding shoe pump, which comprises a pivotable pump ring which can be adjusted to the displacement volume and thus also the delivery rate of the pump directly proportional to vary the eccentricity of the pump ring.

Another object of the invention is to provide an oil burner system be provided in which the pump can be easily adjusted to match the fixed nozzle or throttle.

The invention also provides an oil burner system which essentially avoids the diversion of an excess amount of liquid conveyed or the liquid to be diverted s amount is reduced as much as possible.

Furthermore, the invention provides a two-stage sliding shoe pump in which the pump chamber can be pivoted in one direction supported pump ring is delimited, which is infinitely adjustable, so that the displacement volume and thus also the delivery rate the pump can be varied, the performance of the two pump stages is selected so that optimal operating conditions result.

The invention is illustrated below with reference to schematic drawings * Explained in more detail using an exemplary embodiment.

Fig. 1 shows partially in a schematic representation Oil burner system with a pump according to the invention for supply

of the burner. BATHROOM _{0 RIGINAL}

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Fig. 2 is a side view of the invention Pump.

Pig. 3 is a section along the line III-III in Fig.

4 shows the rear end of the pump according to FIGS. 2 and 3 in an end view.

FIG. 5 is a section along the line V-V in FIG. 4.

Fig. 6 is an enlarged fragmentary section taken along the line VI-VI in Fig. 4.

Fig. 7 is an enlarged fragmentary section taken along the line VII-VII in Fig. 4.

In Fig. 1 can be seen at 10, an oil reservoir is supported on a floor surface 12 with the aid of a substructure 11. The container 10 is filled with heating oil up to the level indicated at 13! a removal line 14 is so in the Container installed so that its open end 16 is located near the bottom of the container. The extraction or suction line 14 is connected by a further line 17 to the burner paper pump according to the invention, denoted as a whole by 18. According to the invention, a so-called sliding shoe "is used as the pump 18"

pump used in the case of several sliding shoes, which are guided by one

I runners are supported, radial movements and unhindered

Can perform angular movements while in touch ι

move with the adjacent wall of a pump chamber or bore. !

The sliding shoe pump can advantageously have two separate ί

Form pump circles, namely an outer circle and a \

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inner circle, which can be kept in a row. According to Pig. 1, the pump 18 has an inlet 19 '- and the After entering the pump 18, liquid flows duroh a total of 20 designated sieve or filter unit, whereupon the! liquid the inlet of the first stage designated by 21 achieved.

After an initial pressure generation, the liquid emerges from the outlet 22 of the first stage, and any existing one Excess amount of liquid reaches a bypass or bypass line 23 under the regulating effect of a bypass control valve 24 to the container 10, in the pump 18 is a channel section 26 is provided, in which a ball 27 is pressed, so that a line 28 connected to the channel section 26 allows the returned liquid to reach a return pipe 29 leaves, which opens in the container TO, so that the returned liquid at 30 above the liquid level 13 near the upper end of the container 10 can get back into the container.

The liquid delivered by the first stage of the pump then enters the second stage inlet at 31 and thereafter the liquid has experienced a further increase in pressure, it will discharged via the outlet 32 of the second stage to through a line or a channel 33 to be directed to the Yerwendungsstelle, which in the case of an oil burner system is a fixed nozzle or throttle 34 acts. According to FIG. 1, at 36 is a

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The pressure regulating and shut-off valve is switched on in the delivery line 33.

According to Mg. 1, a pump chamber is defined by a pump ring 37 delimited. which is pivotable about an axis 38; for this purpose, the pump ring 37 is mounted in a housing 39 in such a way that that it can be adjusted with the help of two diametrically opposed screws 40 and 41, which serve the Adjust the eccentricity of the pump ring.

Because the pump ring 37 can be pivoted about the axis 38, it is possible to adjust the pump ring so that that the center of the pump rotor and the center of the pump ring 37 coincide; however, one can do both of these points within the by the geometrical relationships of the pump mecJaanismua infinitely adjust against each other in the given range. Such an adjustment increases the stroke volume and thus also the delivery rate of the pump varies in direct proportion to the eccentricity. This adjustability enables the oil burner system to operate with the smallest displacement volume of the pump that is necessary to achieve a certain pressure drop at nozzle 34 * case to maintain it, it is not necessary · to maintain an excess to return the amount of liquid pumped. If necessary, the system can easily be attached to one nozzle of another Adjust the size, and it is possible to adjust the pressure drop at the ■ new nozzle according to the changed operating conditions reset. This ensures that only a minimal amount of oil to the suction side of the during normal operation Pump must be returned.

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If one considers the oil burner system according to FIG. 1 as a whole, it can be seen that the pump 18 comprises a section designated inagesamt 42, which is switched into the delivery line. This section includes a stepped bore 43 * in one Verachlußkugel 44 is pressed. So there is a second exit zone 46 which is connected by a conduit or channel 47 to the outlet 32 of the second stage; further is a connector 48 is provided which enables the system to be connected to to connect a suitable warning device. The warning device could either respond to a flow or to a pressure, to indicate that the nozzle has clogged or that another faulty operating condition has occurred.

Further details of the pump 18 can be found in FIGS. 2 to 7 forth; the pump comprises an outer housing 39 with a cover 50 through which a shaft 51 protrudes to the outside, which with a flat 52 is provided to with a suitable drive device to be able to be connected. The housing 39 and the cover 50 are held together by a plurality of screws 53.

According to FIG. 3, the housing 39 is provided with two threaded bores 54 and 56, of which the screws 41 and 40 for adjusting the eccentricity of the pump ring are received. The screws 40 and 41 are provided with a slot at their outer end so that they can be adjusted with the aid of a suitable tool, for example a screwdriver; Furthermore, protective caps 57 with threaded bores 58 are provided which are screwed onto the associated adjusting screws, with BADORIGJNAL ₁₀ 9823/0067

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the protective caps 57 and the housing 39 seals 59 are arranged to prevent the escape of liquid from the pump.

The pump ring 37 has an outer peripheral surface 60, and it is provided with a bore 61 which defines a pump chamber. In the bore 61, a rotor 62 is arranged, which can be driven by the shaft 51. The runner has a plurality of recesses 63, each of which is through a floor surface 64 and side walls 66 and 67 is delimited.

In each recess 63 there is arranged a sliding shoe, designated as a whole by 68. Each of these sliding shoes has one curved outer sealing surface 69 »which is profiled to match the wall of the bore. Because the radius of curvature of the sealing surface each sliding shoe is slightly smaller than the radius of curvature of the bore 61, exists between the mutually facing surfaces practically a touch within a narrow zone.

Each slide shoe 68 is on one side surface with a Provided cutout, the total of 70 designated sealant records. Because of the presence of these sealants, the pump is capable of performing a double pumping action, in such a way that an inner and an outer pumping circuit are present. Here the pump is using in a suitable manner Inlet and outlet openings provided with a working chamber 71 are connected, which is delimited by the wall of the bore 61 and the outer peripheral surface of the rotor 62,

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so that the first pump circuit on the outside of the sealant 70 lies. Furthermore, the pump is provided with openings, di e are in communication with the inner parts of the recesses 63, so that a second pump circuit within the sealing means 70 is available. The sealing means 70 are brought into effect by the centrifugal forces that occur when the runner moves 62 rotates so that a good seal between the sliding blocks 68 and the adjacent walls 67 of the cutouts of the rotor is achieved will.

TJm to pretension the sliding shoes 68 outwards already in the boom state, a helical spring 72 is assigned to each sliding shoe, which is supported on the bottom surface 64 of the relevant recess and on the inner surface of the associated sliding shoe.

It should be noted that the inlet 21 of the first stage and the Outlet 22 of the first stage are connected to the working chamber 71, while inlet 31 and outlet 32 of the second stage are in connection with the parts of the rotor recesses 63 lying further inward.

It is preferably ensured that the delivery rate of the outer pump circuit is greater than that of the inner one Pump circuit, so that there is a charging effect for the second • stage and the excess amount of liquid to the fuel tank is returned. The regulation of the delivery rate is made by suitable dimensioning of the wing cross-sections the relationship ^^ spftan ^ fyer eccentricity and the

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Width causes so that the width of the sliding shoes 68 and the associated recesses 63 can be adjusted to suit the delivery rate of the inner and outer pump circuit to vary.

From Fig. 6 in connection with Figs. 1, 2 and 4 it can be seen that that at 76 a cleaning of the filter enables Screw plug is provided which is inserted into a threaded hole 77 of the housing 39 is screwed in and provided with a seal 78 is; by removing the screw plug 76, the filter designated as a whole by 20 can be made easily accessible; to the The filter is removed from its installation opening for cleaning purposes. The filter unit 20 comprises a cup-shaped Holding part 79 »a sealing ring 80 engages on the circumferential surface, which is installed in an annular groove 81 within an opening 82 of a face plate 83. The end wall of the holding part 79 is depressed at 83 to hold in place a generally tubular screen 84, which is known as the The filter element acts and the entire amount of fuel flows through it, which is taken from the fuel tank by the pump is sucked in.

The end plate 83 has a fiing groove on its peripheral surface 84, in which a sealing ring 86 is located, which engages the inner surface 87 of the housing part 39 and thus the interior of the housing is divided into two separate zones on either side of the sealing ring 86.

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The face plate 85 forms a beatand part of a Stack-forming unit, which also has an apertured plate 90, a support plate 91, the pump ring 37 and the Runner 62 includes. About this' aggregate that forms a stack Several coil springs are to be exposed to a compressive force in the boo state 93 is provided, which according to FIG. 7 at circumferential intervals are distributed; one end of each coil spring 93 is supported on the end wall of the housing 39, while the other end in a Recess 94 of an actuating surface 96 engages through a "face of the face plate 83 is formed.

According to FIG. 7, one of the recesses 94 is extended through the face plate 83 and provided with a valve seat 97, with which a valve ball 24 cooperates to regulate the flow returned to the fuel container 10. According to Fig. 7, the yentilkugel 24 is constantly biased by a coil spring 98, which is located on a shoulder 99 within an opening 100 of the plate 90 is supported, the opening 100 is in communication with a continuous channel 101 in the Pump ring 37 is formed, and from which the liquid via an opening 102 of the support plate 91 to one in the cover 50 formed channel 103 arrives. The channel 103 corresponds to the line 28 according to FIG. 1 and can according to FIG. 4 in a system be connected with two lines by a connector 104 with a suitable bypass line.

As described with reference to FIG. 1, the connection piece 26 forms the cover part 50 of the pump, and on the

End 104 facing away from the end is another line connection

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provided, by means of which the line 17 can be connected to um.die pump with the fuel tank 10 and the suction pipe 14 to connect. According to FIG. 6, the inlet, again designated by 19, in the cover 50 guides the supplied liquid via the channel 107 to an inlet 108 which has the pump ring 37, the support plate 91, the apertured plate 90 and parts of the face plate 83 surrounds. The sucked in liquid flows through filter 84 and then via inlet 21 in plate 90 to working chamber 71 of the first stage or des outer pumping circuit. After the liquid in the working chamber 71 has been brought to a certain pressure at which it If the pressure is medium, the liquid becomes a zone between the end wall which is exposed to this medium pressure of the housing 39 and the actuating surface 96 of the face plate 83 are supplied.

The medium-pressure liquid is stressed the actuating surface 96 and thereby contributes to the to hold united parts together in a stack to increase the efficiency of the pump, without the need for special Provide clamping devices or other mechanical aids.

The liquid flows from the tree behind the actuating surface 96 via a channel 109 in the end plate 83 and a channel 110 in the plate 90 according to FIG. 1 to the inlet of the second stage. The pressure of this liquid is then increased in the second stage, whereupon the liquid leaves the second stage via the outlet 32. According to FIG. 6, the end plate has 33

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a through opening 112 in which a valve member 36 is displaceable is. The yentilorgan 36 is generally cup-shaped and

/ an includes a side wall 113t which delimits a recess, the One end of a helical spring 114 is supported at the bottom. The other End of coil spring 114 engages a pressure adjustment screw

116 to the ig. a nut part 117 is screwed in »the nut part

117 is in a threaded hole in the end wall of the housing 39 installed, and a cap 118 is screwed onto the free end of the pressure adjustment screw. The valve member 115 carries an end section 119 of smaller diameter with a recess, in which a seal 120 made of rubber is arranged. The face plate 83 has a channel 85, which is normally is kept closed by the side wall 113 of the valve member; however, the valve 36 opens so far that the channel 85 is released, this channel acts as a pressure relief ■ or Bypass channel through which the liquid is under the delivery pressure to the low pressure inlet zone 108; *} may.

In a; Opening 122 of the plate 90, a hollow bearing bolt 121 is installed, which also protrudes through an opening 123 in the pump ring 37, the pump ring being mounted on the bolt 121, the? thus the beautiful Iiage the mentioned axis of rotation 38 determined * The one bearing pin 121 further extends into the bore 124 egg neck tubular member 126 into "the dta in an opening 127? Stützplaite 91 is installed * Daa component 126 eratreolEt eioh ·· 128 further into, 4 is in a "channel with a" designated in fig, 1 with 33 »passage, which has a Aueίaß-

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Forms channel of the pump, which are connected via an outlet connection 129 with a consumer for the pumped liquid can·

The hollow bearing pin 121 has a central channel on, and according to FIG. 6, the seal 120 acts on the left end of the hollow bearing journal, so that the valve 36 acts as a shut-off valve works with an accompanying effect · The surfaces of the valve member 36, which are exposed to the delivery pressure, and the force of the Coil springs 114 are dimensioned so that the pressure control and Shut-off valve 36 within normal operating range for Effect comes. In Fig. 6, the valve 36 is shown completely closed, while Fig. 1 shows the valve in completely shows open state.

In order to ensure a good seal of the inlet zone 108, the cover 50 is provided with a Bingnut 131 in which a Sealing ring 132 is that engages the inner surface of the housing. ,

The rotor 62 is rotatably connected to the shaft 51 by a key 133, and the end of the shaft 51 is in the with Plate 90 provided with openings is guided in a recess 134.

According to FIG. 5, a β timsei tiger is on the cover 50 Closure arranged by a resiliently aufeetzbaren cap i 140 is held in its position, with a shaft seal designated as a whole by 141 being installed in the VersohluSaggregat is.

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In order to limit the extent of the adjustment, I ¹ Ig. 6, a stop pin 146 is provided which is built into the support plate 91 and protrudes into an enlarged opening 147 of the pump ring 37.

In a typical system, the burner nozzle 34 is chosen so that that it is suitable for operation .with a pressure of about 6.35 atmospheres, and the flow control valve 36 is controlled by a suitable Set the pressure adjustment screw 116 to the correct one Opening pressure set. Since the pump ring 37 is adjustable according to the invention, the delivery rate of the pump can be adjusted optionally vary so that the system can be operated with the smallest displacement of the pump that is required to to maintain a certain pressure drop across a nozzle of certain dimensions without the need to return excess liquid

It should be noted that various changes and modifications can be made to the embodiment described above can provide without departing from the scope of the invention.

claims 10982370067

Claims (5)

Claims 1 J rotary lobe pump, especially for use in oil firing systems, in which Puiapengehäusering is normal to the axis of the pump roller movable, characterized in, that in the slots - (63) of the pump roller (67) movably and sealingly mounted, under centrifugal force the pump housing ring '(37) applying tiltable and displaceable Pistons (68) have a shorter length than the slot depth corresponds, and that in addition to the inlet (21) and outlet (22) arranged in a known manner on one end face of the roller for through the outer pump chamber (71) between the alze and the pump housing ing formed pumping stage on one end face each a further inlet (31) and outlet (32) is provided, which one through the inner pumping spaces between each bottom (64) of the sole seats and each radially inward side of the sliders formed further pumping stage are assigned and d ^ ß the Pump housing ring to change the eccentricity and thus Delivery rate etes? around one lying outside the pump axis Axis pivotable and arretierbax is arranged in its position. 2. Rotary lobe pump according to claim 1, characterized in that the pistons (68) in iiiren slots so are arranged that the conveyor voluinen of the outer first Pump stage slightly larger than that of the inner time You pump life is, and dai.i eggs in the connection between the two outer outlet (22) uriu "the inner ^ ■ i.inla.3 (31) eiu ^ bIa." ,, aros sei- 109823/0087 _B ad original valve (24) switched on for the excess flow rate is 5. Drelikrorbenpußipe according to claim 1 or 2, characterized g e Ic e η η a e i c h n e t. that each piston (68) in Umiangsrichtimg somewhat narrower than its slot (63) is, has curved sides and at least on its one side has a cylindrical seal (70) receiving recess, the radially outside part of the boundary wall lying at its greatest depth converges towards the side wall of the slot. BATH ORIGINAL 1Q982370067 Vt Blank page