EP0116165A1 - Pompe alternative à piston tournant - Google Patents

Pompe alternative à piston tournant Download PDF

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Publication number
EP0116165A1
EP0116165A1 EP83112972A EP83112972A EP0116165A1 EP 0116165 A1 EP0116165 A1 EP 0116165A1 EP 83112972 A EP83112972 A EP 83112972A EP 83112972 A EP83112972 A EP 83112972A EP 0116165 A1 EP0116165 A1 EP 0116165A1
Authority
EP
European Patent Office
Prior art keywords
piston
crank
axis
rolling
rolling surface
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.)
Ceased
Application number
EP83112972A
Other languages
German (de)
English (en)
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
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 Individual filed Critical Individual
Publication of EP0116165A1 publication Critical patent/EP0116165A1/fr
Ceased 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18024—Rotary to reciprocating and rotary
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18232—Crank and lever
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18248—Crank and slide

Definitions

  • the invention relates to a piston pump with a rotating piston which can be moved back and forth in a cylinder bore and with a 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 being coupled to one another in terms of rotational drive .
  • Pumps with a rotatable piston have the advantage that they can be designed as control piston pumps in which the piston is effective as a rotary valve.
  • Such pumps have a minimum of moving parts and are extremely robust.
  • the joint between the connecting rod and the piston must be designed in such a way that changes in the angle between the connecting rod and the piston 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.
  • the invention has for its object to design a piston pump of the type mentioned so that movements causing sliding friction are largely avoided.
  • annular piston rolling surface is arranged on the piston or on a part rigidly connected to it, which cooperates with an annular crank rolling surface arranged on the crank, the ring axes being inclined to one another and the rolling surfaces through the forces occurring during the pressure stroke can be pressed against one another along a line-shaped or point-shaped contact point, which point of contact moves rolling around the circumference of the ring-shaped rolling surfaces when the crank is rotated, and that the piston and crank are connected to one another by a train connection with which the forces occurring during the suction stroke the crank can be transferred to the piston.
  • the design of the piston rolling surface as a conical jacket is particularly advantageous (claim 2).
  • Such a surface can be produced precisely with little manufacturing effort. It is particularly advantageous if, according to claim 3, both of the cooperating annular rolling surfaces are designed as conical surfaces, a particularly advantageous embodiment according to claim 4 being that the cone angles of both conical surfaces are the same. This continues to reduce sliding friction to a minimum.
  • Such a train connection is particularly reliable and also suitable when the forces on the piston are relatively large even during the suction stroke.
  • conical surfaces can be provided for the retraction of the piston according to claims 6 and 7.
  • the train connection can also consist of a spring arrangement according to claims 8 and 9, through which the rolling surfaces are drawn against each other.
  • the spring can both lie within the rolling surfaces and also surround them.
  • a rotary drive connection between the crank and piston can be formed according to claim 10 by positive engagement of the piston or a part firmly connected to the crank.
  • a rotary drive Establish connection by a coil spring arranged centrally to the crank axis and the piston axis (claim 11).
  • a conical surface is less suitable as a rolling surface. In this case, toroidal surfaces are advantageous.
  • the 1 has an electric drive motor 1 and a pump housing 2.
  • a pump housing 2 In the pump housing 2 there is a cylinder bore 3 into which a piston 4 engages in a sealing manner.
  • a suction hole 5 and a drain hole 6 open into the cylinder bore 3.
  • the suction holes 5 open into a cavity 7 inside the pump housing 2, while the drain hole 6 opens onto the outer surface 2a of the pump housing 2, where a pressure line can be connected.
  • the piston is cut in its front area by a cutting surface 8, the edges of which act as control edges, so that depending on the rotary position of the piston, either the suction bore 5 opens into the cylinder bore 3 or the drain bore.
  • the cutting surface 8 is shown offset by 90 °, to make them clearly visible in the drawing. Rotation and longitudinal movement of the piston are coordinated with one another in such a way that the suction bore 5 is open during the suction stroke (movement to the left in FIG. 1) and the drain hole 6 during the pressure stroke (piston movement to the right in FIG. 1).
  • This pump principle is known per se .
  • the clutch 9 has an arm 14 which is rigidly connected to the piston 4.
  • a screw 15 is used for fixation, which is screwed into a threaded hole of the arm 14 and presses on an inclined surface 16 which is located on the piston 4.
  • the screw is oriented so that a pressure component in the longitudinal direction of the piston 4 is created by the pressure on the surface 16, which pulls the crank arm 14 against the piston.
  • the arm 14 has a shoulder 19 which engages in a cavity 20 which is located in the crank 10.
  • the cavity 20 has on the front surface 10 an opening 20a of such a diameter that the projection 19 engages in the cavity 20 without any significant play, which widens starting from the opening 20a.
  • a helical tension spring 21 is used to pull the conical surface 17 against the flat front surface 18 of the crank 10. This is held by means of screws 22 and 23. Both screws have a thread that corresponds to the spring 21 and are screwed into the spring ends.
  • the head of the screw 22 is located on a support surface 24 of the crank and the head of the screw 23 on a support surface 25 of the arm 14.
  • the spring 21 is under a certain preload with which the conical surface 17 is pulled against the flat surface 1.8.
  • Fig. 2 the kinematic relationships are shown schematically and enlarged compared to Fig. 1.
  • Two positions are shown, namely the position in which the piston is at its front (pressure side) dead center and the position in which the piston is at its suction side dead center.
  • the rolling plane 18 has the position 0 ° at the pressure side dead center and the position 180 ° at the suction side dead center.
  • the central axis of the cone 17 is designated 26; it intersects the piston axis 13 at a point 27.
  • the central axis 26 of the cone 17 intersects the piston axis 13 at a point 28.
  • the distance between the points 27 and 28 is equal to the stroke H.
  • the central axes 26 close in both positions with the piston axis 13 an angle ⁇ .
  • the connecting line 29 between the points P, P ' closes the angle with the plane 18 in both extreme positions shown.
  • the condition ⁇ ⁇ must be met if a rolling motion is to take place between the conical surface 17 and the flat surface 18.
  • Fig. 1 shows the position in which the piston is in the dead center on the pressure side.
  • the force required for this is transmitted by the spring 21.
  • the spring 21 has such a large preload that it is not further stretched under the influence of the forces mentioned, so that the conical surface 17 lies firmly against the flat surface 18 during the suction stroke.
  • the cone jacket 17 rolls on the surface 18. The rolling motion is continuous. After turning the crank by 180 °, half of the circumference of the cone jacket 17 has rolled on the surface 18, which can also be seen in Fig Crank 10 presses on the conical surface 17.
  • an elastic intermediate member is therefore not effectively available.
  • the rolling process allows the transmission of large forces without significant wear on the rolling surfaces.
  • the recess 20 is shaped so that the neck 19 of the arm 14 has sufficient freedom of movement in any position.
  • the torque is transmitted to the piston in that the shoulder -19 abuts the edge 20a of the recess 20.
  • the piston cooperates with the bores 5 and 6 for controlling the inlet and outlet, as has already been described above.
  • the suction line is connected to the bore 30, which opens into the housing cavity 7. So this space is constantly flooded.
  • the funding therefore also acts as a lubricant on the rolling surfaces.
  • the motor 1 is a so-called canned motor.
  • This motor contains a tube 31 which is arranged in the gap between the stator winding 32 and the rotor 33.
  • the space 34 inside the tube 31 is also flooded with the conveying medium, since the housing cavity 7 is connected to the space 34 via bores 35.
  • the pumped medium thus also serves to lubricate the motor bearings 36 and 37.
  • the piston force occurring during the suction stroke is achieved by positive engagement between the crank and the piston.
  • the crank 38 is pierced by a hole 39.
  • the fixation of the arm 41 on the piston 42 is designed accordingly, as in the embodiment according to FIG. 1.
  • a fixing screw 43 is provided which is arranged obliquely and presses on an inclined surface 44 on the piston.
  • Hole 39 consists of two conical sections that collide at 48. This ridge line 48 defines the narrowest point of the opening 39. The diameter at this point is such that the cylindrical portion 40 reaches through the bore without any play.
  • a hollow cylindrical guide surface 50 is arranged on the pump housing 49.
  • a cylindrical surface 51 is guided on this surface and is located on a part which is fixedly connected to the drive motor 52. With each pivot position of the motor 52, the crank axis 12 intersects the piston axis 13 at point A, which is located in the center of the cylindrical surfaces 50, 51.
  • a conical surface is less suitable as a rolling surface.
  • Toric surfaces are therefore provided as the rolling surfaces, namely a convex piston rolling surface 53 and a concave rolling surface 54 on the crank 55. The cross sections of these surfaces are shown in FIG. 5 shown enlarged.
  • the convex surface 53 is located on an arm 56 which is firmly connected to the piston 57.
  • a helical tension spring 58 which pulls the parts 53, 55 against each other, extends again within the toric surfaces 53, 54.
  • the method of operation is the same as for the pump according to FIG. 1.
  • the pressure lifting forces are transmitted via the rolling surfaces, while the suction lifting forces are transmitted via the helical tension spring 58.
  • the angle oG can be changed within wide limits.
  • the piston stroke is also O, ie. funding is no longer available.
  • the stroke of the piston increases with increasing angle ⁇ .
  • the toric surfaces 53, 54 allow different inclinations between the arm 56 and the crank 55.
  • the engagement of the toric surfaces in one another results in a positive connection, with which a rotational drive coupling between the crank 55 and the piston 57 also takes place. In this case, a special element for the rotary drive need not be provided.
  • the driver connection is formed by a spring arranged centrally to the crank axis and piston axis.
  • a kind of cap 60 is screwed onto the piston 59, the end face of which forms a rolling surface.
  • the crank is here, so to speak, formed by a surface 62 which is arranged obliquely to the crank axis 12. This surface is located on a cap 63 which is placed on the drive shaft 64 of an engine.
  • Both surfaces 61 and 62 are surrounded by a helical tension spring 65.
  • the caps 60, 63 are screwed into the ends of the coil tension spring.
  • corresponding threads are provided on the peripheral surfaces of the caps.
  • the helical tension spring 65 has both the task of pulling the two parts 60, 63 against one another and the task of transmitting torque from the part 63 to the part 60 in order to effect the rotary drive of the piston.
  • the torque transmission is achieved in that the spring is always contracted so far that further twisting is no longer possible. Thereafter, twisting changes between the two parts 60, 63 are no longer possible.
  • FIG. 7 largely corresponds to the embodiment according to FIG. 3.
  • a crank disk 67 is seated on a motor shaft 66.
  • a hat-shaped part 68 is firmly connected to the crank disk 67. This hat-shaped part extends over the front surface 67a of the crank disk and has a rolling surface 69 in the projecting area, which is conical.
  • the hat-shaped part 48 has a central opening 70 which is cylindrical and opens into a cavity 71. Another conical surface 72 is located on the hat-shaped part within the cavity.
  • driver pin 77 there is a driver pin, generally designated 77, on the arm 74.
  • the driver pin has a projection 78 which is inserted through the rolling part 75 and the arm 74 and on the end of which a retaining nut 79 is screwed on and secured by means of a spring ring 80. By tightening the nut 79, the rolling part 75 is also pulled firmly against the arm 74.
  • the driver pin 77 has at its front end a tapered rolling surface 81, which with the tapered rolling surface 72 interacts. Both conical surfaces 81 and 72 have the same cone angle. In the area that extends through the opening 70, the driver pin has two conical surfaces 82 and 83, which lie against one another with their respective large bases. The cone angles are dimensioned such that in the two extreme positions, one of which is shown in FIG. 7, surface lines of the cone surfaces 82, 83 are parallel to surface lines of the cylindrical opening 70.
  • the pump according to FIG. 7 works in principle the same as the pump according to FIG. 3.
  • the interacting rolling surfaces are conical surfaces with the same cone angles, sliding movements are further reduced, since the rolling surfaces are the same size. This does not exactly apply to the rolling of a conical surface on a flat ring surface, so that in this case sliding movements occur which are somewhat larger.
  • the driver structure in FIG. 7 is designed equivalent to FIG. 3. While a bore with two conical surfaces is used according to FIG. 3, which cooperates with a cylindrical pin, the bore is cylindrical according to FIG. 7 and the driver pin has two conical surfaces for this. The same effect is achieved in each case.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP83112972A 1983-01-13 1983-12-22 Pompe alternative à piston tournant Ceased EP0116165A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3300847 1983-01-13
DE3300847 1983-01-13

Publications (1)

Publication Number Publication Date
EP0116165A1 true EP0116165A1 (fr) 1984-08-22

Family

ID=6188140

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83112972A Ceased EP0116165A1 (fr) 1983-01-13 1983-12-22 Pompe alternative à piston tournant

Country Status (3)

Country Link
US (1) US4531897A (fr)
EP (1) EP0116165A1 (fr)
JP (1) JPS59150986A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3520233C1 (de) * 1985-06-05 1986-07-31 Franz 6305 Buseck Orlita Kolbenpumpe mit rotierendem Kolben
WO1986006794A1 (fr) * 1985-05-10 1986-11-20 Bergman, Manfred Pompe a piston sans soupapes
WO1987004497A1 (fr) * 1986-01-24 1987-07-30 M & T Chemicals Inc. Pompe submersible a piston a deplacement positif
EP0464301A1 (fr) * 1990-05-16 1992-01-08 Dennis Pinkerton Pompe doseuse à phase réglable et méthode pour régler son débit
EP0482774A2 (fr) * 1990-10-24 1992-04-29 Hypro Corporation Pompe à déplacement positif à piston alternatif rotatif
EP0512688A2 (fr) * 1991-04-15 1992-11-11 Baxter International Inc. Pompe de dosage

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3516867A1 (de) * 1985-05-10 1986-11-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5439360A (en) * 1991-07-22 1995-08-08 Carrier Corporation Self-adjusting crankshaft drive
US5492457A (en) * 1994-06-21 1996-02-20 Lee; W. Ken Unidirectional flow pump with rotary drive
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
EP3241611B1 (fr) * 2016-05-02 2020-03-04 Borealis AG Procédé d'alimentation d'un catalyseur de polymérisation
JP6905442B2 (ja) * 2017-09-29 2021-07-21 株式会社イワキ プランジャポンプ
DE112018006550A5 (de) * 2017-12-21 2020-09-03 WS Wieländer + Schill Engineering GmbH & Co. KG Hydraulikwerkzeug für eine Zug- und/oder Pressvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1244160A (en) * 1916-01-07 1917-10-23 Charles A Anderson Engine or pump construction.
CH128278A (de) * 1926-08-05 1928-10-16 Friedmann Alex Fa Antriebsvorrichtung an Pumpen, insbesondere zur Förderung kleiner Flüssigkeitsmengen.
US2517645A (en) * 1947-07-11 1950-08-08 Nathan Mfg Co Pumping mechanism
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump

Family Cites Families (3)

* 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
FR981580A (fr) * 1948-12-11 1951-05-28 Pompe d'injection à piston
US3382812A (en) * 1966-09-27 1968-05-14 Gorman Rupp Ind Inc Variable positive displacement pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1244160A (en) * 1916-01-07 1917-10-23 Charles A Anderson Engine or pump construction.
CH128278A (de) * 1926-08-05 1928-10-16 Friedmann Alex Fa Antriebsvorrichtung an Pumpen, insbesondere zur Förderung kleiner Flüssigkeitsmengen.
US2517645A (en) * 1947-07-11 1950-08-08 Nathan Mfg Co Pumping mechanism
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986006794A1 (fr) * 1985-05-10 1986-11-20 Bergman, Manfred Pompe a piston sans soupapes
DE3520233C1 (de) * 1985-06-05 1986-07-31 Franz 6305 Buseck Orlita Kolbenpumpe mit rotierendem Kolben
EP0204263A2 (fr) 1985-06-05 1986-12-10 Franz Orlita Pompe à piston avec piston rotatif
US4708605A (en) * 1985-06-05 1987-11-24 Franz Orlita Piston pump with rotating piston having a universal joint
WO1987004497A1 (fr) * 1986-01-24 1987-07-30 M & T Chemicals Inc. Pompe submersible a piston a deplacement positif
EP0464301A1 (fr) * 1990-05-16 1992-01-08 Dennis Pinkerton Pompe doseuse à phase réglable et méthode pour régler son débit
EP0482774A2 (fr) * 1990-10-24 1992-04-29 Hypro Corporation Pompe à déplacement positif à piston alternatif rotatif
EP0482774A3 (en) * 1990-10-24 1992-07-15 Hypro Corporation Positive displacement pump with rotating reciprocating piston
EP0512688A2 (fr) * 1991-04-15 1992-11-11 Baxter International Inc. Pompe de dosage
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
US4531897A (en) 1985-07-30
JPS59150986A (ja) 1984-08-29

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