DE1528935A1 - Universal joint arrangement and sealing device for screw pumps - Google Patents

Description

Aktiebolaget Flygts Pumpar Jelelon 2? 55 2t iUddargatan 12 .- ". '.

Stockholm 0 / Sweden __—— * ~ - Ί 23rd September 1964

Universal joint assembly and sealing device for

Screw pumps
(Inventor: lR Lindberg).

The invention relates to a universal joint assembly and Sealing device for screw pumps with a housing, that on its inner surface surrounding the pump chamber with screw threads wersehen and one on its outside with Screw pistons provided with screw threads, but an intermediate shaft with universal joints of one in the housing wall rotatably mounted drive shaft is driven.

A known pump of this type is described in the Swedish patent ..ί ?? .... ίΤ. · .... (patent application 4-421 / 63) in which a rotating screw piston with an external simple screw thread (ie a thread with a single thread) rotates with simultaneous eccentric movement in a stationary pump housing, which has an inner double screw thread cooperating with the rotating screw piston (i.e. _r »in thread with two turns), the pitch of which is twice that of the rotating screw piston "bps Pumptngthäuae is from a elaetisohen .Material, generally au" rubber manufactured ,, and awiaohen the two puapen-leilen ^^ nd ^ ^ EACN oaaen · HohXJrlüme separated,

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which is continuously and smoothly fed axially by the pump will.

On the basis of the fact that the rotating screw jacks during his Rotation carries out an eccentric movement on the same side, the drive must take place via a deflection arrangement, vvoüei usually a short one with universal joints at the ends Intermediate shaft between the rotating piston and the drive shaft is used.

Known pumps of this type are almost without exception manufactured with their pressure side on the stuffing box side, ie the side where the passage of the drive shaft is located in the pump housing. The reason for this is that the conventional stuffing box is difficult to seal against the negative pressure prevailing on the suction side, ie against the air penetrating from the outside. This air only needs to penetrate in small quantities, ufa to worsen the suction capacity of the pump or to cancel it completely, in order not to speak of the disadvantages and the risk associated with the air penetrating the medium being pumped . The leakage is primarily due to the fact that the stuffing box will run dry under negative pressure , which results in overheating and ultra-tightness.

Attaching the pressure side to the drive side, however, has significant disadvantages. The axial force exerted by the pump pressure on d # | i rotating piston, which is several

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Surprised ic. '/ em- be canoe * receives such a direction that the swivel shaft and the universal joints are exposed on the same side to a force and the three necessary for the drive of the rotating piston in the oiiient .-- The tree between the drive shaft and the rotating piston is limited »and therefore the force-transmitting pins in the universal joints are not always designed as strong as is desirable. The ^ aeigt also _r that the joint coupling in these

It is the weakest point from a mechanical point of view and it is the jusaciie for operational disruptions and interruptions. Another ITaehteil is _r that "this creates erhebliciier ausütslicher power requirement at ents ^ rec-iend strong formation of the stuffing box.

Pie invention has the dual task of creating a safe and reliable device that seals against negative pressure on the passage of the drive shaft in the pump house and thus to enable the suction side to be attached to the drive side, and on the other hand, one for this disconnection To create suitable articulated coupling on the suction and pressure side, which is subjected to pressure instead of suction. According to the invention, this joint (: K: ardan-) coupling is formed by 'j \ -i- & i universal joints, which are arranged in such a way that the axial force acting on the rotating piston is entirely of' iieö .-- 'νοώ torque conditional; Forces is separated, where

ftegruppen each for themselves from separate parts of the

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Universal joints are included. The goals are thereby achieved that in a device of the aforementioned type of the drive shaft passage in the pump housing with one with the Shaft circumferential sealing device is provided and that the universal joints of the intermediate shaft are two separate Have force-transmitting and -absorbing parts, namely a ball joint, which is exclusively on the rotating Piston absorbs axial forces, and a transverse pin that only acts on the rotating piston absorbs acting torques.

In the drawing is an exemplary embodiment of the object of the invention shown schematically It shows:

E ¹ Ig. 1 shows an embodiment of a screw pump with a universal joint and sealing device according to the invention in a vertical longitudinal center section.

Fig. 2 shows an embodiment of. power-transmitting intermediate shaft on a larger scale.

3 shows a cross section along the line III-III of FIG. 1 and

4 shows a part of FIG. 1 on a larger scale, namely a longitudinal center section through one end of the rotating screw piston with the one universal joint according to the invention.

The pump housing of the screw pump shown in FIG. 1 consists of three parts, namely an inlet part 10, one

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Outlet part 12 and a clamped between "the same sleeve-shaped stator housing part 14, these parts by (not inclined) tension bolts between the inlet and outlet parts 10 and. 12 are held together in the sleeve-shaped Stator housing part 14 is an elastic stator 16 (preferably made of a fairly hard quality plastic rubber) used with a snug fit, with an am-a linden of the stator formed outer flange 16a between the one iCnde of the stator housing 14 and the housing part 10 is clamped with a seal. At the opposite end is the stator housing 14 sealed by an O-ring 14a. The flange 16a is between the inlet 10a of the stator 16 facing face of the same and its outer I.lantelflache a channel immediately near the flange I6a 18 arranged. This channel 18 serves the purpose of an existing one '' hydraulic grip "to modify the outer surface of the stator 16 and thereby achieve a kind of automatic hydraulic compensation of the stator 16 (as in the Patent ............ ο (filed simultaneously herewith Patent application ...........) is explained).

The inner surface or the inner circumferential surface of the stator 16, which limits the actual pump chamber to the outside as a flat rounded screw thread with two turns educated. With, this inner sun surface acts ■ rotating screw piston 20 together, its outer surface is also designed as a screw thread, however

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has only one helix and one pitch that is only "corresponds to half that of the stator thread. Furthermore, the tip of the visual piston thread is pointed more sharply as the tips of the stator thread, between the rotating ones Piston 20 and the stator 16 are closed Cavities, which during the rotation of the rotating Piston 20 continuously moves axially from the bin to the run-out during the transport of the unpopped podium move. Simultaneously with the rotation of the rotating piston 20 about its axis, it performs an eccentric movement in the stator 16 with the Hadius e. A more detailed explanation the interaction of the stator 16 with the rotating Piston 20 in a screw pipe of this type and the pumping action is listed in the introduction to the description Patent included. .

The necessary eccentric movement of the rotating piston 20 in the stator has, as already mentioned, the inevitable complication that its drive from "a fixed V / elle on some kind of joint coupling the rotating piston 20 is transmitted. In the drawn execution plan, the rotor 20 is made hollow, wherein the inner cavity 22 is closed to the outlet side 12a of the pump, however, the inlet side 10a, which is also the drive side, is open, which is everything from the IPig. 1 can be seen is. The special feature of the hollow rotating piston 20 has. not only result in the total length of the pump see abbreviated, but also that the rotating piston 20 of

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the pumped medium is cooled from the inside, which in many Cases of great importance ". An intermediate shaft 24 is connected between the rotor and the drive shaft 26, this intermediate shaft 24 at its ends with the rotating Piston 20 at its outlet end b: sw. with the drive shaft by special, trained according to the invention IZardan- or universal joints 30 is connected, which the through caused the eccentric movement of the rotating piston 20 Record the conical oscillation of the intermediate shaft 24. These universal joints essential for the invention are described below to be described in more detail.

Tie was already highlighted in the introduction to the description, this screw pump is particularly characterized by that its drive side coincides with its suction side, why to the seal on the implementation of the drive shaft In the pump house, among other things, the great demand is made that no outside air in this way into the pump sucked in, which would have various unpleasant consequences. The Y / ell lead-through is extremely important for safe and reliable operation of the pump shown on the right in Pig »1. If you follow them from the right Side, you will only find one that is driven by a single drive Shaft coupling half 50 »which by means of a wedge or bolt connection 50a is firmly connected to the outer end of the relatively short drive shaft 26. Inside the coupling half 50 there is a two-row, angular contact ball

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bearing 52 and on its inside one with the same outer diameter Executed combined guide and sealing ring 54 made of metal, with both parts 52 and 54 in an end bore 56 of the pump housing part 10 are housed. Of the ■ Ring 54 is in contact with the interposition of an O-ring 54a ″ a shoulder 56a at the bottom of the bore 56, and the parts ball bearing 52 and ring 54 are by a clamping ring 58 with Screws 58a pressed against the shoulder 56a. At his after outwardly directed end is the ring 54 with an enlarged provided annular recess 54b, which is a conventional Sealing sleeve 60 for shielding the ball bearing 52 records. The driving and sealing ring 54 is in the rest not in contact with the intermediate shaft 26, and between the At the bottom of the recess 54b and the cuff 60 there is an intermediate space which is open to the environment, so that at, for example When the pump is at a standstill, liquid pumping medium may leak out.

As mentioned above, the outer ring is the ball bearing 52 and the guide sleeve 54 in the pump housing part 10 clamped. The drive shaft 26 is in turn axially fixed in the inner ring of the ball bearing that a spacer ring 62 and the hub 50 b of the coupling flange 50 by a at the outer end, the drive shaft 26 centrally mounted screw 50c with washer that engages hub 50b is pressed against a shoulder 26a on the drive shaft will. The drive shaft 26 is thus fixed but rotatable in the. pump housing part 10 fixed, and it can be seen that the

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Shaft .26 with the bearing and one-piece construction described, and extremely precise alignment and centering thanks to the use of conventional installation technology. in the .pump housing, especially in relation to the Eührungs-. and the lit unbaring 5 4 can be veLKCedißht. . . ... - _;

This is of great importance for a seamless way of working the pumps and the drive shaft exhaust 3meQhanisrii, us, as explained in more detail below. . .

The often difficult problem of a seal between a solid and your rotating one. ¹ PeIl is solved in this case with the help of a circumferential planar seal, in which the circumferential part is made from xahle in a well-known tYaia-e. "* ■ _". ·:>: ■,. . ■ .... ,

On the inside of the Mlirungs- and sealing ring 54 there is an Eohlering 64 which can slide on the 'Velle 26 is attached against which it seals (e.g. lelrS-catfish by an O-iÜng 64a) while he is at the same time rotates with the shaft 26. The inner end of the drive shaft.,

• 26 is seen with a thickening or a head 26b. and ζ wischen ^ this and the Kaiilering 64 a high pressure spring JS6 is inserted, which presses the Kötilering 64 to rest against the Büirungs- and sealing ring 54. The two surfaces of the rings 64, 54 which meet one another are flat

»- gesehliffe ^ i and together form an almost perfect botox ^ poetry. : So that this, especially in the case of long-lasting

90983.4 / 0106 bad original

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der Untdreliung / on: dfer .-; while. = 26 au; sf »iii _: g ^ g (. ''FressJae.vegunjjeii; ¹¹¹ -) ■ work 'slGti eel" the

DleMwngBfäMäk. Since both of them _; iiinge; ii 54, ^> 4 as außii Äwiiachen the coal ring 64. imä idea *:! felle 26 scliad-;. borrowed, from ... The ^ BiGiiiKnü ^S; fis ^G fee zmiaohen U ^ m Mn ^ en SA.iVA :: mQ thus exactly in the right- ϊ / inkel; for: 3todr ^ ün, gsacja3e verlixafen * ITun are the ends of the combined FLOatrangs- and Diclitungsringes 54 .öder iünsiuantelf igpher.-. flat sanded, '-. waa siGli simply bBv / ernstelligen ^ liäßi;, and with- a bed action of the -from Sing 54 -----, ball bearings 52 ^ -iaitatLebswalle 26 Ue -, -stellenden-, system is laielit to erseiiiaii, especially with . ; Hin- ~ .. looks at the tremendous accuracy: ait welclier a Ku ^ eJs- :: bearing usually: is manufactured. ;that the

54-64 see (exactly. At right angles to the üdishiaigsaclise becomes, .weshal% ^r de ^ J ^ hleriimg -: ^

whole time: in the same plane, run & en ^

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the FigU 5 - 4 referenced. V / ie ^ from Eig. 2 ersiciitliidni,.; - is: the ZwisGlienwelle ZA at ο each end with a feugßlföiriaigen. ϊμ & £, - 32: with a ^ hemispherical f'rMgeji IPIaG ^ 28 ^

K0pif 52: Is * reciitwinkellg to the Xä ^ satiise ait one-Bonrang ^; 54 provided _; , whose Liittelachs © durcli deii la ^ telßunk * the half-. 28 goes, in gedea löhrtüigsloiBJi 54 is * a

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wendting ,, auvarlüssig: and _: operation ssiehes *: work aodl ;; - io / fc ..es -: - · -.-

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however, Vienna. that, dex: Kohrle ring :; £ 4 _; loeiä & - ^ yaneb ^ or; Ivii> p-- '

both ends; with: -a '". threaded pin 56 inserted, Two hatches 38 are screwed onto the threads, which are opposite to. to the. Taper head 32 conically at 38a. The ends of the cones. 38a engage opposite conical seat surfaces 40 at the end of the rotating piston 20 (Pig. 4) and in the end head 26b of the drive shaft 26 (Fig.I). The holes 34 can preferably be attached at right angles to each other as can be seen from FIG.

According to the invention, the closed end of the hollow rotating piston 20 opposite the head 32 of the intermediate shaft 24 is provided with a hollow spherical surface 28. The bores 34 are widened somewhat conically from the center to the ends, so that the axial force acting on the rotating piston 20 is certainly taken up by the actual Luge Ige lenkfläclie and not by the pin, while the pin 36 only. shear stress resulting from the torque applied to the piston 20. The small conical widening of the bores 34 towards their ends creates a pivoting deflection between the piston 20 and the intermediate shaft corresponding to "Yinkel α in rig» 2 and Y / inkel f \ in Fig. 3. The '.Vinkela and I? Are of the .Jröüe order 4 or 1.5 ° · When the pump is operated, the intermediate shaft 24 performs a pendulous l'egel movement with the entire angular deflection 2 arc sin e / L, which movement is partly a small rotation around the pin 36 , partly a small lateral rash in the one caused by the

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Cone shape rait the angle Ot creates space. The cone shape with the angle β has been applied so that the torque during the line contact between the pin 36 and the walls of the bores 34, as in Ii ¹ Ig. 3 indicated, is transmitted. During the movement there is of course a slight sliding between the surfaces 28 and 42 in the ball joint, but the surface pressure is relatively low.

In this way it is achieved that the developed during operation of the pump to drive the rotating piston 20 required forces thanks to extremely robust universal joints are transmitted in which the axial and momentary forces are completely separate from one another and each taken up by one element v / earth. As mentioned earlier, this is a new universal joint device according to the invention thereby enables a secure vacuum seal in the further pursuit of the invention at the passage of the drive shaft 26 into the pump housing is guaranteed.

The illustrated and described embodiment of the invention is of course not limited to this example, but can be adapted to the respective cases of the Practice experienced numerous changes without affecting the area

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the invention is abandoned. V

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Claims (1)

- claims. . 1 . \ £ adapter arrangement with sealing device for screw pumps with a housing that is attached to its pump chamber surrounding inner surface is provided with screw threads and one provided on its outer surface with screw threads The screw piston surrounds the via an intermediate shaft Universal joints are driven by a drive shaft rotatably mounted in the housing wall, characterized in that that the drive shaft passage in the pump housing (10,12,14) with a shielding device that runs around the shaft (p4,6O) is provided, and that the universal joints (30 of the intermediate shaft (24.) two separate power transferring and - have receiving parts, namely a. löigelgeienk (28.42), that only acts on the rotating piston (20) Absorbs axial forces, and one, uerzapfen (56), the exclusively those acting on the rotating piston (20) Absorbs torques. 2. Apparatus according to claim 1, characterized in that the intermediate shaft (24) is formed with spherical surface ends (28,32) which are provided with transverse bores (34) for receiving transverse pins (36) whose i.ättelachse the longitudinal axis of the Zv / ischenwelle (24) in the center of the associated spherical surface (28) of the corresponding shaft end (32) • cut, the transverse pin of one universal joint being connected to the rotating piston (2q) χ _η and 903834/0106. ■ »« «» · * «■ > 14 - ■: '■■■ the spherical surface (28) rait dem.Ilugelsitz- (42) .. in the piston- · (20) which: forms a ball bearing range * wüurend. u-er. other cones ("^ 6) Eiit the end head (26a) .der: Aiiti'iebaweil (26). stands in ^ itniJiiäe-connection and aas ziißer.ori ^ e ^ u ^ elcursing end (26) with the opposite ilugelsitz i ;; i. Jexienenakß, .x- (^ Gb) is formed _λ . der - Susanen;:. it der.r>;i'.chot. lying 3ade of the Zv / isciienwelle forms the second .ICu ^ eila ^ örun ^, 5ο Device according to claim 2, dadurcn _{: j} ekenrioClehnet, aaij die. ;; overbores - (i4) and .die> or: -: y ei'en. (;> υ) in -de-π, yr.u of the Zvvisciienwelle. (24) in the right v / inicel iiuein-. are arranged. 4. Device "dadarch according to claim 2, · in that the rotating Zolben (20) is provided with an internal cavity [ '2Z) having the outlet (12a) d.er Pum ^ e closed end facing and with the Hugels. itzflache is equipped. "i>. Device according to one of claims 2-4, characterized in that that the transverse pin (36) in the sliding piston (20) bzv /. in the inner band head (26b) of the drive shaft (26) on aejren Ends of screwed-on Haiterauttern (38) are, v; elche with tapered inner ends. (38a) in: matching conical ^ seats (40) in the rotating piston (20) ^ or: in Engage the drive shaft end head. ..; . . 6 ₀ device according to one of claims 2-4, characterized in that - ;;:, -.- 909834/0106. kenn ^ eicmiet, aaiJ ale .; Bores (34) in the ends (32) of the intermediate v / elle (24) are widened from their Lürigsiaitten to the ■■ linden- to conical in order for the, uerzapfen ('5G) the to errriüglichen for the pivotal movements of the SchraubenkoTberis (20) of motion required, in the direction of rotation but the ürehrriomenti.bertragung of the Antriebswe_lle (26) on the uersapfen Scliraircbenkolben (20) through the LinienberUhrung _H (36) the räit. bores (34) is ensured (Jj ¹ Xg. 3). 7. The device according to claim 1, characterized in that the umlümte sealing device of the Yfelldurchganges consists of an xland seal, which comprises a known plane-ground lCohlring (64) which is firmly attached with seal (64a) on the drive shaft (26) and of this in Drüiirichtung η is taken it, wherein the carbon ring (64) egen by a spring (66) with its surface-ground face ^ a face-ground end face of a combined guide and sealing ring (54) _o epreßt v / ith which, together with einem.Kugel - or .Rollerlager (52) is inserted into a bore (56) made from the outer surface of the pump housing part (10) and is pressed against a shoulder (56a) at the bottom of the bore (56) by holding members (58,58a), wherein the continuous drive shaft (26), which is fixed in the inner ring of the ball or roller bearing (52) during assembly and with its axis exactly at right angles to the sealing plane between the guide - and sealing ring (54) and the ^T : ohlering (64) is held and a 'chattering is avoided with constant rotary movement. . 90 9 83 4/0 106 8. Apparatus according to claim 7 »characterized in that the Müirungs- and sealing ring (b4) at his your ball or Hollenlager (52) facing end with an annular cavity (^ 4b) is provided | which is a known sealing cuff (60) around the drive shaft (26) to protect the adjacent ball or roller bearing (52), wherein in the ring (54) between the bottom of the cavity (i? 4b) and the sealing cuff (Go) is provided with a gap which is in free connection with the environment, so that possibly leaking pump medium v / uring the standstill of the Pumps can drain to the outside. 9 0 9 8 3 A / 0 10 6 _gAD original ;. Le e.r s e i t e