EP0425567B1 - Dispositif tubulaire de separation pour pompes a deux cylindres de liquides epais - Google Patents

Dispositif tubulaire de separation pour pompes a deux cylindres de liquides epais Download PDF

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Publication number
EP0425567B1
EP0425567B1 EP89908693A EP89908693A EP0425567B1 EP 0425567 B1 EP0425567 B1 EP 0425567B1 EP 89908693 A EP89908693 A EP 89908693A EP 89908693 A EP89908693 A EP 89908693A EP 0425567 B1 EP0425567 B1 EP 0425567B1
Authority
EP
European Patent Office
Prior art keywords
ring
pipe
axial
rubber
pivot
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89908693A
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German (de)
English (en)
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EP0425567A1 (fr
Inventor
Karl Schlecht
Hartmut Benckert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Putzmeister Concrete Pumps GmbH
Original Assignee
Putzmeister Werk Maschinenfabrik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Putzmeister Werk Maschinenfabrik GmbH filed Critical Putzmeister Werk Maschinenfabrik GmbH
Publication of EP0425567A1 publication Critical patent/EP0425567A1/fr
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Publication of EP0425567B1 publication Critical patent/EP0425567B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0084—Component parts or details specially adapted therefor
    • F04B7/0088—Sealing arrangements between the distribution members and the housing
    • F04B7/0096—Sealing arrangements between the distribution members and the housing for pipe-type distribution members

Definitions

  • the invention relates to a pipe switch of a two-cylinder thick matter pump with a swivel tube pivotable in front of a cylinder-side spectacle plate, with an axially displaceably arranged on the spectacle-side end of the swivel tube, which can be pressed against the spectacle plate by means of the hydrostatic internal pressure in the swivel tube and with a wear ring between the swivel tube and the A rubber-elastic ring arranged on the wear ring, the wear ring having at its end on the swivel tube side an axial guide surface guided on a radially outward-pointing cylindrical centering surface of the swivel tube, together with the centering surface delimiting a sealing gap, and on its spectacle-side end an annular shoulder pointing radially inward from the axial guide surface, whose front outer surface rests against the eyeglass plate and its inner surface serving the rubber-elastic ring as an axial abutment by an axial through which elastic ring bridged.,
  • the space is separated from the end face of the swivel tube and the swivel tube has at its front end a recess which preferably has the shape of a rectangular step and is open towards the axial guide surface and engages under the sealing ring on the inside.
  • Pipe switches of this type which referred to an automatic hydrostatic adjustment, called an automatic ring Wear wear ring are known (DE-C-26 14 895 and DE-A-31 03 321).
  • DE-C-26 14 895 and DE-A-31 03 321 in order to accommodate the rubber-elastic ring, mutually facing ring rotations, which engage under the ends of the rubber-elastic ring, are provided both in the swivel tube and in the wear ring.
  • Abrasive material can penetrate into the area of the ring twists and migrate behind the rubber-elastic ring.
  • this material can reach the radial gap between the wear ring and the swivel tube and exit through the radial gap, while the material penetrating the backward rotation between the wear ring and the sealing ring can no longer escape to the inside of the tube when the pressure is released.
  • the latter leads to an axial bracing of the pipe switch and thus to a heavy, wear-promoting switching.
  • the backward rotation is gradually filled with the hardening material, so that the elastic sealing ring can be drawn towards the inside of the pipe with increasing wear and increasing axial air and can be lost in the process. This is particularly the case if the thick matter pump draws vacuum during the backward conveyance.
  • the axial relative movement between the swivel tube and the wear tube can also lead to premature wear there under the action of the hardening material that escapes to the outside.
  • the axial movement mentioned is between, depending on the elasticity of the surrounding pump housing 1 and 3 mm.
  • the object of the invention is to create a pipe switch for two-cylinder thick matter pumps of the type specified at the outset, which ensures a reliable seal against material leakage and a low-wear axial guidance between the wear ring and the pipe switch.
  • the wear ring In practical operation, it is particularly important that when switching the pipe switch and clamping solid particles such as stones and the like between the wear ring and the glasses, the wear ring can spring back somewhat both in the axial and in the radial direction and can also tilt slightly. Furthermore, care must be taken to ensure that the abrasive material does not reach the sealing gap as far as possible and is deposited in the area of the sealing ring and can grow there gradually after hardening.
  • the inner surface of the ring shoulder formed on the wear ring is designed to be stepless in its region serving the rubber-elastic ring as an axial abutment towards the pipe interior and that the turning in the swivel pipe over at least the rubber-elastic ring engages under one third, preferably over more than half or even two thirds of its axial extent.
  • the rubber-elastic ring rests with its radial outer surface while performing an axial guide function, against the part of the axial guide surface of the wear ring bridging the recess and with its front end face against the axial inner surface of the ring shoulder arranged on the wear ring.
  • the rubber-elastic ring is supported with its radial inner surface by bridging the front space between the swivel tube and the ring shoulder against the radial boundary surface of the recess and with its rear end surface against the axial boundary surface of the recess of the swivel tube.
  • the arrangement according to the invention When pressurized, the arrangement according to the invention has the effect that the material to be conveyed, which tends to harden from the inside of the tube and pressures under elastic deformation, presses into the rubber-elastic ring in the region of its end face on the spectacle side.
  • the elastic ring in its rear part is pressed firmly against the sealing gap in the area of the axial guide surface between the wear ring and the swivel tube.
  • the tube switch can spring back in the direction of the spectacle plate due to the elastic deformation of the elastic ring.
  • radially continuous axially open grooves can also be arranged on the end face of the swivel tube, which grooves only have to be about 1 to 2 mm deep.
  • Another possibility of resilience in the sense described above and the access of material to be conveyed for the purpose of hydrastatic loading can be achieved in that bevels or preferably wedge-shaped ring grooves are arranged on the elastic ring towards the inside of the pipe. If the chamfers or ring grooves are provided at both ends, the sealing ring can be inserted regardless of the direction and turned over in the event of wear, thus doubling its service life. The chamfer on both sides also increases the resilience volume.
  • the swivel tube can be provided with a step stop for the wear ring at the rear end of the cylindrical axial guide surface, which ensures that the The gap remains open even when the wear ring is struck.
  • the part of the axial guide surface of the wear ring opposite the pivot tube or in the part of the wear ring can be used opposite part of the axial guide surface of the swivel tube, an annular groove for receiving an O-ring can be left out.
  • the diameter of the axial guide surface of the wear ring is larger than the effective diameter or even larger than the front outer diameter of the ring shoulder with which the wear ring rests on the spectacle plate. It is particularly advantageous if the ring surfaces of the wear ring acted upon by the hydrostatic pressure are designed such that the effective diameter of the force acting between the tube switch and the wear ring in the pressing direction is greater than the effective diameter of the force acting between the spectacle plate and the wear ring in the lifting direction Force.
  • the pipe switch shown in the drawing is intended for a two-cylinder thick matter pump, the delivery cylinders, not shown, of which are covered by a replaceable spectacle plate 5 on their mouths on the side of a material feed container.
  • a swivel tube 2 is arranged with its end face in front of the spectacle plate 5 so that it can swivel back and forth about a horizontal axis in such a way that its opening 20 alternately reaches one or the other of the two openings 4 of the spectacle plate 5 and the other opening 4 releases to the material feed container.
  • the swivel tube 2 opens into a delivery line, not shown.
  • a wear ring 1 With its cylindrical axial guide surface 21 is axially displaceably mounted on the cylindrical guide and centering surface 7 of the shoe tube 2.
  • the wear ring 1 At its front end, the wear ring 1 has a radially inwardly facing ring shoulder 22, the outer end face 23 of which against the surface 24 of the spectacle plate 5 rests and the annular inner surface 17 of which lies opposite the end face 16 of the swivel tube 2.
  • the ring 3 lies with its radial inner surface against the radial boundary surface 8 and with its rear end face 12 'against the axial step 6 of the turn in the pipe switch 2, while it with its radial outer surface against the part of the axial guide surface 21 of the wear ring bridging the turn 1 and rests with its front end face 12 against the radially outer part of the inner ring face 17 of the wear ring 1.
  • the end face 16 of the swivel tube 2 is separated from the inner surface 17 of the wear ring 1 by radially continuous, axially open grooves 11 or an annular gap 18, so that the viscous conveyed material conveyed under pressure by the swivel tube 2 directly from the inside to the grooves 11 or can reach the gap 18 bridging part of the elastic ring 3.
  • the swivel tube 2 strikes with the upper edge of the grooves 11 in the region of the inner surface 17 against the wear ring 1, while in the case of FIGS. 2 and 3 a step 15 is provided in the rear region of the swivel tube 2 as a limit stop for the wear ring 1.
  • the rubber-elastic ring 3 with its essentially rectangular cross-section takes on not only a sealing function due to its var tension but also the function of automatic tracking of the wear ring 1 in the event of wear.
  • its radial outer surface represents an extension of the axial guide and centering surface 21.
  • the axial extent of the ring 3 is at least twice, preferably one Multiple of the axial extent of the guide and centering surface 21 on the swivel tube 2, there is the possibility within the necessary play between the wear ring 1 and the swivel tube 2 in the area of the centering surface 21 that the wear ring 1 due to the elastic properties of the ring 3 can tilt easily if solid particles get into the gap area between the contact surfaces 23 and 24 of the wear ring 1 and the spectacle plate 5. This results in a considerable reduction in wear and thus a longer service life of the wear ring 1 and the spectacle plate 5.
  • the ring surfaces 23 and 17 of the wear ring 1, which are acted upon by the hydrostatic pressure, are arranged and designed such that the force 31 acting in the pressing direction is greater than the lifting force 30.
  • the effective diameter 10 of the force 31 acting between the swivel tube 2 and the wear ring 1 in the pressing direction is greater than the effective diameter 9 of the force 30 acting between the spectacle plate 5 and the wear ring 1 in the lifting direction.
  • the axial guide - And centering diameter 7 of the wear ring 1 larger than the effective diameter 9, with which the wear ring 1 rests on the eyeglass plate 5 and even larger than the end outer diameter of the ring shoulder 22, with which the wear ring 1 rests on the eyeglass plate 5.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Joints Allowing Movement (AREA)
  • Reciprocating Pumps (AREA)
  • Sealing Devices (AREA)

Abstract

Un dispositif tubulaire de séparation pour pompes à deux cylindres de liquides épais comprend un tuyau pivotable (2) qui présente à son extrémité frontale une gorge (6, 8) à profil rectangulaire de réception d'une bague (3) en caoutchouc élastique dont la face externe radiale s'appuie contre la partie de la face de guidage axial (21) d'une bague d'usure (1) qui s'étend sur la gorge (6, 8) et dont la face frontale antérieure (12) s'appuie contre la face axiale interne (17) d'une pièce rapportée annulaire (22) agencée sur la bague d'usure (1). La face radiale interne de la bague (3) en caoutchouc élastique s'appuie contre la face (8) de délimitation radiale, en surmontant une fente située entre la bague d'usure (1) et le tuyau pivotable (2), et sa face frontale postérieure (12') s'appuie contre la face (6) de délimitation axiale de la gorge du tuyau pivotable (2). La bague d'usure (1) axialement mobile sur le tuyau pivotable (2) et réglable au moyen de la bague élastiquement précontrainte (3) est sollicitée par la pression hydrostatique régnant à l'intérieur du tuyau pivotable (2) contre une plaque à lunette (5), devant laquelle le tuyau pivotable (2) peut pivoter de façon à mettre les orifices (4) reliés aux cylindres de refoulement de la pompe de liquides épais alternativement en communication avec le tuyau pivotable (2) et avec un récipient distributeur de matériau.

Claims (11)

1 - Conduit de dérivation, ou by-pass, d'une pompe à deux cylindres pour liquides épais, comprenant un tube basculant (2) susceptible de basculer devant une plaque à deux ouvertures (5) côté cylindres, une bague d'usure (1) montée de manière axialement déplaçable sur l'extrémité, côté plaque à deux ouvertures, du tube basculant (2) et pouvant être appuyée contre la plaque à deux ouvertures (5) à l'aide de la pression hydrostatique interne dans le tube basculant (2), et une bague élastique (3) en caoutchouc ou analogue montée entre le tube basculant et la bague d'usure, la bague d'usure présentant, d'une part, à son extrémité côté tube basculant une surface de guidage axiale qui, guidée sur une surface de centrage cylindrique du tube basculant orientée radialement vers l'extérieur, limite conjointement avec la surface de centrage une fente d'étanchéité et, d'autre part, à son extrémité côté plaque à deux ouvertures, un prolongement annulaire (22) s'étendant à partir de la surface de guidage axiale radialement vers l'intérieur et dont la surface frontale extérieure prend appui contre la plaque à deux ouvertures et dont la surface interieure servant de butée axiale à la bague élastique (3) est séparée de la face frontale du tube basculant (2) par un intervalle axial franchi par la bague élastique et ouvert vers l'intérieur du tube, tandis que le tube basculant (2) présente à son extrémité frontale un évidement obtenu par tournage et qui, présentant de préférence la forme d'un gradin rectangulaire, est ouvert en direction de la surface de guidage axiale et s'engage du côté intérieur sous la bague d'étanchéité élastique, caractérisé en ce que le prolongement annulaire (22) est réalisé, dans la région de sa surface intérieure (17) servant de butée axiale à la bague élastique (3), de façon à être exempt de gradin en direction de l'intérieur du tube et en ce que l'évidement (6, 8) obtenu par tournage dans le tube basculant (2) s'engage sous la bague élastique (3) sur au moins un tiers de son étendue axiale.
2 - Conduit de dérivation selon la revendication 1, caractérisé en ce que l'évidement (6, 8) dans le tube basculant s'engage sous la bague élastique (3) sur au moins la moitié et, de préférence, sur au moins les deux tiers de son étendue axiale.
3 - Conduit de dérivation selon la revendication 1 ou 2, caractérisé en ce qu'à l'extrémité frontale du tube basculant (2) sont disposées des rainures radialement continues et axialement ouvertes (11) dont les bords supérieurs forment une butée frontale du tube basculant (2) au contact du prolongement annulaire (22) de la bague d'usure (1).
4 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube basculant (2) présente à l'extrémité arrière de sa surface de guidage et de centrage cylindrique (7) une butée (15) en forme de gradin pour la bague d'usure (1) et en ce que l'intervalle (18) entre le prolongement annulaire (22) de la bague d'usure (1) et la face frontale (16) du tube basculant (2) reste ouvert lorsque la bague d'usure (1) est en contact avec la butée (15).
5 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que dans la partie de la surface de guidage axiale (21) de la bague d'usure (1) qui se trouve en regard du tube basculant (2) ou dans la partie de la surface de guidage et de centrage axiale (7) du tube basculant (2) qui se trouve en regard de la bague d'usure (1) est ménagée une rainure annulaire (14) destinée à recevoir un joint torique (27).
6 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que le diamètre (7) de la surface de guidage axiale (21) de la bague d'usure (1) est supérieur au diamètre actif (9) au moyen duquel la bague d'usure (1) prend appui contre la plaque à deux ouvertures (5).
7 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que le diamètre (7) de la surface de guidage axiale (21) de la bague d'usure (1) est supérieur au diamètre frontal extérieur du prolongement annulaire (22) au moyen duquel la bague d'usure (1) prend appui contre la plaque à deux ouvertures (5).
8 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que les surfaces annulaires (23, 17) de la bague d'usure (1) soumises à la pression hydrostatique sont réalisées de telle manière que le diamètre actif (10) de la force (31) s'exerçant entre le tube basculant (2) et la bague d'usure (1) dans le sens d'appui est supérieur au diamètre actif (9) de la force (30) s'exerçant entre la plaque à deux ouvertures (5) et la bague d'usure (1) dans le sens de soulèvement.
9 - Conduit de dérivation selon l'une quelconque des revendications précédentes, caractérisé en ce que l'étendue longitudinale de la surface de guidage axiale dans la région de la bague élastique (3) est au moins le double de celle de la surface de guidage et de centrage axiale (7) dans la région du tube basculant (2).
10 - Conduit de dérivation selon l'une quelconque des revendications 3 à 9, caractérisé en ce que la bague élastique (3) présente, à son extrémité franchissant l'intervalle, ou fente annulaire, (18) ou les rainures (11), un chanfrein (25) ou une rainure annulaire (26) en forme de coin disposé radialement à l'intérieur.
11 - Conduit de dérivation selon la revendication 10, caractérisé en ce que la bague élastique (3) présente à chacune de ses extrémités un chanfrein (25) ou une rainure annulaire (26) en forme de coin disposé radialement à l'intérieur.
EP89908693A 1988-07-19 1989-07-08 Dispositif tubulaire de separation pour pompes a deux cylindres de liquides epais Expired - Lifetime EP0425567B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3824466A DE3824466A1 (de) 1988-07-19 1988-07-19 Mehrzylinder-dickstoffpumpe
DE3824466 1988-07-19

Publications (2)

Publication Number Publication Date
EP0425567A1 EP0425567A1 (fr) 1991-05-08
EP0425567B1 true EP0425567B1 (fr) 1992-10-07

Family

ID=6359025

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89908693A Expired - Lifetime EP0425567B1 (fr) 1988-07-19 1989-07-08 Dispositif tubulaire de separation pour pompes a deux cylindres de liquides epais

Country Status (4)

Country Link
EP (1) EP0425567B1 (fr)
JP (1) JP2514729B2 (fr)
DE (2) DE3824466A1 (fr)
WO (1) WO1990001117A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3905355C2 (de) * 1989-02-22 1994-06-23 Schlecht Karl Rohrweiche für Zweizylinder-Dickstoffpumpen
US5302094A (en) * 1988-07-19 1994-04-12 Putzmeister-Werk Maschinenfabrik Gmbh Tube switch for a double-cylinder sludge pump
KR100390483B1 (ko) * 1995-12-13 2003-09-06 엘지전자 주식회사 티브이의고스트제거방법
DE10131784A1 (de) * 2001-07-04 2003-01-16 Putzmeister Ag Vorrichtung zum Fördern von fließ- und schüttfähigem Fördergut
EP1580035B1 (fr) 2004-03-26 2007-05-30 Continental Aktiengesellschaft Bandage pneumatique
GB2416569A (en) 2004-07-27 2006-02-01 Clarke Uk Ltd Method of and a pump for pumping drill cuttings
DE102013215990A1 (de) * 2013-08-13 2015-02-19 Putzmeister Engineering Gmbh Zweizylinder-Dickstoffpumpe mit Rohrweiche

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2614895A1 (de) * 1976-04-07 1977-10-20 Schlecht Karl Beton-rohrweiche
DE2829181A1 (de) * 1978-07-03 1980-01-17 Scheele Maschf W Rohrweiche fuer eine betonpumpe
DE2921735A1 (de) * 1979-05-29 1980-12-04 Teka Baumaschinen Gmbh Vorrichtung zum dichten einer betonpumpe
DE3103321A1 (de) * 1981-01-31 1982-08-12 Friedrich Wilh. Schwing Gmbh, 4690 Herne "zweizylinder-dickstoffpumpe, vorzugsweise betonpumpe mit einem von einer zylinderseitigen brillenplatte abwechselnd schwenkenden schaltorgan"
JPS59172287U (ja) * 1983-05-06 1984-11-17 石川島播磨重工業株式会社 コンクリ−トポンプのシ−ル構造

Also Published As

Publication number Publication date
JPH03506060A (ja) 1991-12-26
WO1990001117A1 (fr) 1990-02-08
JP2514729B2 (ja) 1996-07-10
DE58902434D1 (de) 1992-11-12
EP0425567A1 (fr) 1991-05-08
DE3824466A1 (de) 1990-01-25

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