EP0204263A2 - Pompe à piston avec piston rotatif - Google Patents

Pompe à piston avec piston rotatif Download PDF

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Publication number
EP0204263A2
EP0204263A2 EP86107301A EP86107301A EP0204263A2 EP 0204263 A2 EP0204263 A2 EP 0204263A2 EP 86107301 A EP86107301 A EP 86107301A EP 86107301 A EP86107301 A EP 86107301A EP 0204263 A2 EP0204263 A2 EP 0204263A2
Authority
EP
European Patent Office
Prior art keywords
piston
axis
troughs
crank
pump according
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.)
Granted
Application number
EP86107301A
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German (de)
English (en)
Other versions
EP0204263A3 (en
EP0204263B1 (fr
Inventor
Franz Orlita
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT86107301T priority Critical patent/ATE48677T1/de
Publication of EP0204263A2 publication Critical patent/EP0204263A2/fr
Publication of EP0204263A3 publication Critical patent/EP0204263A3/de
Application granted granted Critical
Publication of EP0204263B1 publication Critical patent/EP0204263B1/fr
Expired 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the invention relates to a piston pump with a rotating piston which can reciprocate in a cylinder bore and with a rotating crank with which the piston is connected in an articulated manner, the piston axis and the axis of rotation of the crank intersecting one another and the crank and piston coupled to one another in terms of rotational drive are and wherein the joint has rolling surfaces, which are located on the crank and on the piston.
  • Pumps with a rotatable piston have the advantage that they can be designed as control piston pumps in which the piston acts as a rotary slide valve.
  • Such pumps have a minimum of moving parts and are extremely robust.
  • the joint between the crank and the piston must be designed in such a way that changes in angle are possible, but the piston is set into a rotary movement safely and with as little play as possible. This places special demands on the joint.
  • EP-OS 0 116 165 Pumps of the type mentioned at the beginning (EP-OS 0 116 165) are also known, in which sliding movements are largely avoided in the articulated connection between the crank and the piston, as a result of which a long service life is achieved.
  • a conical surface rolls on a flat surface.
  • Favorable pressure ratios between the rolling surfaces are obtained, but only at a certain inclination angle. The delivery stroke of this pump can therefore not be changed easily by changing the axis inclination.
  • EP-OS 0 116 165 also describes a solution (FIGS. 4, 5 of this document) which allows the inclination to be changed.
  • a rolling surface as T orus and the other is formed as a groove in which engages the toric surface.
  • a spring is provided to transmit the forces during the suction stroke, which presses the toric rolling surface into the groove.
  • the pressure ratios are not particularly favorable since the cross-section of the torus is small for design reasons. It is too not possible to transfer the forces occurring during the suction stroke via the rolling surfaces.
  • the invention has for its object to design a piston pump of the type mentioned in such a way that the angle between the piston axis and the crank axis can be adjustable for the purpose of changing the delivery stroke and there are favorable pressure conditions in all setting positions.
  • the pump should also be executable so that the forces occurring during the suction stroke can also be transmitted via the rolling surfaces.
  • the rolling surfaces on the crank and piston are formed as troughs and in that a convex rolling element engages in the troughs, the surface curvature of which is greater than the curvature of the trough surface, the edges of the troughs being oriented such that with all relative positions between the troughs, the trough edges do not touch each other and there is a positive engagement between troughs and rolling elements in the circumferential direction of the rotary movement and forces can be transmitted in the pressure stroke direction via the rolling elements.
  • the pump is also advantageous if one Adjustment is not provided because the rolling element and the troughs can be easily manufactured. Because of the difference in the curvature of the rolling elements and trough surfaces, the rolling element performs a rolling movement in both troughs at the same time, sliding friction being avoided.
  • the pressure ratios are favorable for all settings. Since the curvatures of the trough surfaces and the curvature of the rolling element can be brought very close to one another, the Hertzian pressure is relatively low, which means that the joint has a long service life even with poor lubrication.
  • edges of the troughs are preferably oriented such that there is a positive engagement between the troughs and rolling elements also in the direction of the suction stroke, so that tensile forces can be transmitted from the crank to the piston (claim 2).
  • Such an embodiment has the advantage that a spring is not required to overcome the suction forces.
  • the invention can also be carried out with an orientation of the troughs which does not allow the transfer of forces during the suction stroke. In this case, as in the known pump of the type mentioned, a spring must be provided which absorbs the forces occurring during the suction stroke.
  • the troughs are preferably elongated and oriented as stated in claim 3. With such elongated troughs, the difference between the width of the circular crank path and the small axis of the ellipse is bridged, along which the trough, which is located on the piston, moves. With a small angle between the crank axis and the piston axis, an elongated design of the troughs can be omitted, since the difference between the The diameter of the crank track and the length of the small axis of the ellipse is vanishingly small. An elongated design of the troughs can also be dispensed with in the tangential arrangement of the troughs to be explained.
  • the rolling element is preferably a ball (claim 4).
  • a spherical rolling element is particularly easy to produce. Balls with good strength properties are commercially available. Balls, such as those used in ball bearings, are particularly suitable. Shapes of the rolling element deviating from a spherical shape are possible. For example, B. a disc-shaped rolling element.
  • a preferably elastic clamp element is provided in order to hold the trough bodies containing the troughs against the rolling bodies (claim 5). It is thus avoided with certainty that the troughs stand out from the rolling element.
  • a clamp element is not always necessary.
  • a clamp element is used when a positive engagement is not provided for the transmission of the lifting forces.
  • Appropriate training for a bracket element and for its arrangement are given in claims 6 to 8.
  • a clamp element also has a special support between the crank and piston may be present, which has a distance from the piston axis and serves to transmit a negative torque, as during the suction - stroke may occur under certain circumstances.
  • the pump has a housing 1, a drive motor 2, a pump shaft 3, a cylinder body 4 and a piston 5.
  • the drive motor 2 is an electric motor, which is only shown in part and from whose housing one end of the motor shaft 6 protrudes.
  • An intermediate ring 7 is flanged to the motor 2 by means of screws 8.
  • the pump housing 1 is in turn flanged to the intermediate ring 7 by means of screws 9.
  • a coupling piece 10 sits on the motor shaft 6 and is clamped on the shaft 6 by means of screws 11.
  • the coupling piece 10 has a cylindrical projection 12, on which a driving surface 13 is located. On the driving surface 13 there is a pin 14 which is inserted through a bore in the pump shaft 3.
  • the pump shaft 3 is mounted in the pump housing 1 by means of a ball bearing 15, which is axially secured in the pump housing by means of a snap ring 16.
  • a snap ring 17 on the pump shaft and a shoulder 18, which is located on the pump shaft, serve to axially fix the pump shaft 3.
  • the bearing is sealed to the motor 2 by means of a shaft seal 19 and to the interior of the pump housing 1 by means of a shaft seal 20.
  • the arrangement 22 includes a slide ring 23 which bears against a shoulder in the pump housing via an elastic O-ring seal 24. On the slide ring 23 slides a sealing ring 25 which is sealed off from the pump shaft 3 by an elastic O-ring seal 26.
  • a helical compression spring 27 presses on the sealing ring 25 and is supported with its right end on a component 28.
  • Component 28 is to be referred to as a crank because of its function, which is yet to be explained.
  • a joint arrangement generally designated 29, which is the subject of the invention in the narrower sense.
  • the already mentioned crank 28, a ball 30, a trough body 31 and a spring ring 32 belong to the joint arrangement.
  • the trough body 31 is inserted into a head 33 of the piston 5 and secured by means of a threaded pin 34.
  • the cylinder body 4 is received in an oblique bore 35 of the pump housing 1.
  • the axis 36 of this bore which coincides with the axis of the cylinder body 4, is at an angle to the axis 37 of the pump shaft 3.
  • the axes 36 and 37 intersect.
  • the cylinder body 4 is secured in the axial direction to the left by abutment on a shoulder 38 of the pump housing and to the right by a ring 39 which is screwed onto the pump housing by means of screws 40.
  • the space 21 is sealed off to the right by two sealing rings 41, 42.
  • a bore 43 in which the piston 5 is slidable In the cylinder body 4 there is a bore 43 in which the piston 5 is slidable.
  • the bore 43 is sealed to the right by a plug 44 which partially engages in the cylinder bore 43 and has an annular groove in the engaging part for receiving a sealing ring 45.
  • the cylinder bore 43 is smooth.
  • the axis 46 of the cylinder bore 43 with the axis of the piston 5 coincides with the axis 36 of the cylinder body.
  • the inclination angle between the axes 36 and 46 is the same size as the angle between the axes 36 and 37.
  • the cylinder body 4 there is also a bore 47 which cuts through the cylinder bore 43.
  • the entry point forms a suction opening 48 and the exit point forms a pressure opening 49.
  • In the piston there is a longitudinal slot 50 which can be congruent with both the suction opening 48 and the pressure opening 49.
  • the pressure opening 49 communicates via a bore 51 with a groove 52 which extends over the circumference of the cylinder body 4. At each rotational position of the cylinder body 4, the groove 52 communicates with a connection bore 53 to which a pressure line can be connected.
  • the suction opening 48 communicates with the space 21, into which a connection bore 54 for a suction line opens.
  • An adjusting ring 55 is placed on the cylinder body 4 and axially secured by means of a screw 56.
  • the adjusting ring 55 allows the cylinder body 4 to be rotated in a convenient manner.
  • Fig. 7 the pump shaft 3 and the piston 5 are shown schematically. Only the ball 30 of the joint arrangement is shown in two different positions.
  • the piston axis 46 intersects the axis 37 of the pump shaft 3.
  • the inclination angle is designated by ⁇ .
  • the joint rotates about the axis 37 on a circular path with the radius r ⁇ .
  • the piston 5 rotates in the same direction as the pump shaft 3.
  • the direction of rotation is indicated by arrows 57, 58.
  • the shaft 3 can be driven with a torque M K.
  • the piston is also set in rotation via the joint arrangement, namely at the same speed as the pump shaft 3.
  • An axial force F K acts on the piston, which is symbolized in FIG. 7 by an arrow.
  • the part of the joint arrangement 29 which is fixedly connected to the pump shaft 3 moves on a circular path. This circular path is shown in FIG. 8 and labeled 59.
  • the part of the joint arrangement which is connected to the piston describes an elliptical path 60 in the plane defined by line 84, the major axis 61 of which has a length of 2. r ⁇ .
  • the total difference in the width of web 59 and 60 is thus 2 r ⁇ (1- cos ⁇ ).
  • the ellipse 60 can also be seen as an oblique section of a cylinder jacket which has a radius of - r ⁇ - cös a.
  • the piston stroke at the drawn angle ⁇ is identified by the dimension line 63 in the drawing. From Fig. 7 it is readily apparent that the stroke changes depending on the angle ⁇ . The smaller the angle ⁇ , the smaller the stroke. If ⁇ has the value zero, the piston 5 is only rotated, but no longer back and forth moves. The funding is then zero.
  • the difference between the tracks 59 and 60 requires a special design of the joint, which will be explained in more detail.
  • the joint arrangement 29 is shown enlarged.
  • the crank 28 is rotatable about the axis 37.
  • the bowl bodies 64 and 66 are pressed against the ball 30 by a cut-open spring ring 68.
  • the spring ring 68 engages in these grooves.
  • FIG. 5 shows the trough 65 "from FIG. 6 in a top view.
  • the length 1 of the trough 65" is greater than the width b of the trough, namely at least and the amount r ⁇ (1 - cos ⁇ ).
  • the radius r of the trough shown in Fig.
  • the trough cross section parallel to the longitudinal direction of the trough in the area of the dash-dotted lines 72, 73 consists of a short straight piece, the length of which is at least r ⁇ (1 - cos ⁇ ). This straight section is followed by radii with a radius r M.
  • the trough In the area between the lines 72, 73, the trough has the shape of a channel with a circular cross section, the radius of the circle being only slightly larger than the radius of the ball.
  • the longitudinal direction of the troughs must be oriented so that they can compensate for the difference a (see Fig. 8) between the circular path and the elliptical path, ie essentially radially to the axes of the crank and piston.
  • the ball 30 executes a rolling movement in the two troughs 65, 67, whereby it rolls around in the trough 65 and in the trough 67 at the same time.
  • the roller body 30 rolls within the two troughs 65 and 67.
  • the rolling motion is favored in that the direction of force is reversed during the transition from the suction stroke to the pressure stroke. It is also essential for the rolling that the curvatures in the troughs 65, 67 are a little weaker than the curvature of the spherical surface. The difference across the longitudinal direction of the troughs is slight and is shown in a greatly exaggerated manner in FIG. 2.
  • edges 65a and 67a of the troughs 65, 67 each lie in one plane and are at such a distance from one another that they do not collide with one another in the possible relative positions between the trough bodies 64, 66. If the Are M uldenr sections 65a, 67a, which have the 5 seen in FIG. Shape, parallel to each other, they have from one have to M uldenr sectionn parallel equator of the ball 30 at the same distance, ie they form approximately circles of latitude of the sphere 30. However, the Trough edges 65a, 67a are not exactly a circular shape, but are somewhat elongated (see FIG. 5). The elongation is exaggerated in Fig. 5, however.
  • the ball 30 At the front dead center, the ball 30 "was in contact with the inner end of the trough 65", while in the rear dead center it was against the outer end of the trough 65 " Accordingly, the ball 30 "lies at the front dead center (VT) at the outer end of the trough and at the rear dead center at the inner end of the trough. After a further rotation by 90 °, the position C is reached, in which the ball 30" again in the Longitudinal center of the troughs. Due to the elongated design of the troughs, the deviation of the elliptical path 60 from the circular path 59 is taken into account.
  • the ball 30 can also be used to transmit forces to the piston 5 which arise during the suction stroke.
  • the engagement of the ball 30 in the troughs 65, 67 is such that there is also a positive engagement in the suction stroke direction S (see FIG. 2), which is additionally secured by the spring ring 68.
  • the plane of the spring ring 68 passes approximately through the center M of the ball 30.
  • the ball 77 engages in depressions 78, 79 which are oriented differently than the depressions 65, 67.
  • the depressions 78, 79 are also elongated in order to differentiate between the circular path of the crank 80 and to be able to bridge the Elli p senbahn des Pistons 81.
  • the ball cannot transmit forces with which the piston can be pulled in the direction of the suction stroke F. 3 shows this clearly. Thanks to a spring ring 82, which presses the troughs 78, 79 against the ball 77, a suction stroke is nevertheless possible. The forces occurring here must take over the spring ring 82. 3 has the advantage that there are particularly favorable conditions for the pressure stroke.
  • FIG. 2 shows an embodiment in which the edge 65a of the trough 65 lies in a plane which tangential to an imaginary cone about the crank axis 37 along a cone surface line.
  • the edge 67a of the trough 67 lies in a plane tangent to an imaginary cone about the axis 5a of the piston 5 along a cone surface line.
  • the levels in which the trough edges 65a, 67a lie can also be oriented differently, e.g. B. also so that they touch imaginary cylinders about the axes 37 and 5a. In these cases, a spring ring 68 and an elongated design of the troughs can be dispensed with.
  • Fig. 3 37 'and the piston axis is substantially blunt 5'a shows a "tangential position", which corresponds to the principle of FIG. 2, but with the imaginary cone urbelachse the K (larger cone angle) as in the embodiment of Fig. 2. Because of the very obtuse cone angle, a spring ring 82 is useful here.
  • the pump works as follows.
  • the motor shaft 6 rotates, the pump shaft 3 is taken along via the coupling piece 10.
  • the crank 28 is also rotated and takes the piston 5 with it via the ball 30.
  • Fig. 1 the front dead center of the piston is shown, in which the groove 50 of the piston communicates with the suction opening 48.
  • the piston is withdrawn and finally reaches the rear dead center HT via the position B, the cylinder space being filled with the delivery medium via the bore 47, the longitudinal slot 50 and a bore 83 within the piston 5.
  • the space inside the cylinder bore 43 is reduced again and the pumped medium reaches the connecting bore 53 via the longitudinal slot 50 and the bore 51.
  • the slot 50 communicates with the pressure opening 49.
  • a rotational position of the cylinder body 4 is shown in which the angle between the axis 37 of the pump shaft and the axis 46 of the piston is greatest. By rotating the cylinder body 4, the angle can be reduced and finally brought to zero. This parallel alignment is possible because the angle between the axes 36 and 46 is the same as the angle between the axes 36 and 37.
  • Embodiments with elastic, cut rings 68 and 82 are shown. However, closed rings can also be used. Such rings can be subjected to much higher tensile stress.
  • the invention was described using an example in which the rolling element 30 is designed as a ball. However, a body can also be used as the rolling element, which has a shape deviating from a sphere with a convex surface, e.g. B. a discus.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP86107301A 1985-06-05 1986-05-29 Pompe à piston avec piston rotatif Expired EP0204263B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86107301T ATE48677T1 (de) 1985-06-05 1986-05-29 Kolbenpumpe mit rotierendem kolben.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3520233 1985-06-05
DE3520233A DE3520233C1 (de) 1985-06-05 1985-06-05 Kolbenpumpe mit rotierendem Kolben

Publications (3)

Publication Number Publication Date
EP0204263A2 true EP0204263A2 (fr) 1986-12-10
EP0204263A3 EP0204263A3 (en) 1988-07-27
EP0204263B1 EP0204263B1 (fr) 1989-12-13

Family

ID=6272552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107301A Expired EP0204263B1 (fr) 1985-06-05 1986-05-29 Pompe à piston avec piston rotatif

Country Status (5)

Country Link
US (1) US4708605A (fr)
EP (1) EP0204263B1 (fr)
JP (1) JPH0641748B2 (fr)
AT (1) ATE48677T1 (fr)
DE (2) DE3520233C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464301A1 (fr) * 1990-05-16 1992-01-08 Dennis Pinkerton Pompe doseuse à phase réglable et méthode pour régler son débit
EP0482774A3 (en) * 1990-10-24 1992-07-15 Hypro Corporation Positive displacement pump with rotating reciprocating piston
EP0686767A3 (fr) * 1991-04-15 1996-01-10 Baxter Int

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4398487A (en) * 1981-06-26 1983-08-16 Exxon Production Research Co. Fairing for elongated elements
US5096394A (en) * 1990-10-24 1992-03-17 Gerlach C Richard Positive displacement pump with rotating reciprocating piston and improved pulsation dampening
US5074767A (en) * 1990-10-24 1991-12-24 Hypro Corporation Positive displacement pump with rotating reciprocating piston and improved lubrication feature
US5022831A (en) * 1990-10-24 1991-06-11 Hypro Corporation Positive displacement pump with rotating reciprocating piston
US5494420A (en) * 1994-05-31 1996-02-27 Diba Industries, Inc. Rotary and reciprocating pump with self-aligning connection
JP2002349424A (ja) * 2001-05-23 2002-12-04 Tokyo Kikai Seisakusho Ltd 印刷機用ポンプ
WO2007070035A1 (fr) * 2005-12-12 2007-06-21 Carrier Commerical Refrigeration, Inc. Plaque d'adaptation dans une pompe de systeme de production de boisson
US20080187449A1 (en) * 2007-02-02 2008-08-07 Tetra Laval Holdings & Finance Sa Pump system with integrated piston-valve actuation
EP2222957B1 (fr) * 2007-12-10 2017-01-25 Bayer Healthcare LLC Système et procédé de distribution en continu de fluide
ES3030489T3 (en) 2015-01-09 2025-06-30 Bayer Healthcare Llc Multiple fluid delivery system with multi-use disposable set and features thereof
EP3241611B1 (fr) * 2016-05-02 2020-03-04 Borealis AG Procédé d'alimentation d'un catalyseur de polymérisation
CN117469307A (zh) * 2022-07-20 2024-01-30 广东超流精密科技有限公司 一种联轴器组件

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE509222C (de) 1926-08-05 1930-10-06 Alex Friedmann Fa Antriebsanordnung fuer Pumpen kleiner Fluessigkeitsmengen
EP0116165A1 (fr) 1983-01-13 1984-08-22 Franz Orlita Pompe alternative à piston tournant

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2485893A (en) * 1945-10-29 1949-10-25 Kost Alwin Universal joint
US2921451A (en) * 1958-07-14 1960-01-19 Emil A Helmke Constant velocity universal joint structure
FR1229148A (fr) * 1959-06-30 1960-09-05 Dispositif mécanique de transformation de mouvement formant compresseur, moteur <<deux temps>> ou analogue
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump
US4008003A (en) * 1975-06-27 1977-02-15 Pinkerton Harry E Valveless positive displacement pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE509222C (de) 1926-08-05 1930-10-06 Alex Friedmann Fa Antriebsanordnung fuer Pumpen kleiner Fluessigkeitsmengen
EP0116165A1 (fr) 1983-01-13 1984-08-22 Franz Orlita Pompe alternative à piston tournant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464301A1 (fr) * 1990-05-16 1992-01-08 Dennis Pinkerton Pompe doseuse à phase réglable et méthode pour régler son débit
EP0482774A3 (en) * 1990-10-24 1992-07-15 Hypro Corporation Positive displacement pump with rotating reciprocating piston
EP0686767A3 (fr) * 1991-04-15 1996-01-10 Baxter Int
EP0512688B1 (fr) * 1991-04-15 1996-09-18 Baxter International Inc. Pompe de dosage

Also Published As

Publication number Publication date
JPH0641748B2 (ja) 1994-06-01
US4708605A (en) 1987-11-24
JPS6238881A (ja) 1987-02-19
ATE48677T1 (de) 1989-12-15
EP0204263A3 (en) 1988-07-27
DE3520233C1 (de) 1986-07-31
EP0204263B1 (fr) 1989-12-13
DE3667524D1 (de) 1990-01-18

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