EP2961988B1 - Pompe à vis se composant d'au moins deux parties - Google Patents

Pompe à vis se composant d'au moins deux parties Download PDF

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Publication number
EP2961988B1
EP2961988B1 EP14723689.7A EP14723689A EP2961988B1 EP 2961988 B1 EP2961988 B1 EP 2961988B1 EP 14723689 A EP14723689 A EP 14723689A EP 2961988 B1 EP2961988 B1 EP 2961988B1
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EP
European Patent Office
Prior art keywords
screw pump
pressure
base body
low
pressure chamber
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.)
Active
Application number
EP14723689.7A
Other languages
German (de)
English (en)
Other versions
EP2961988A1 (fr
Inventor
Eduardo Nuss
Arthur Zinke
Aluisio Loth
Klaus Heizinger
Lorenz Lessmann
Sérgio Krahn
Rui Keunecke
Silvio Beneduzzi
Egon Weege
André THEILACKER
Sidney Guedes
Petra Lutke
Robert Kurz
Josef Strassl
Johann Kreidl
Hisham Kamal
Horst ENGL
George Balcerczyk
Mathias Gradl
Gunther Herr
André Nijmeh
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.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme GmbH
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Application filed by Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP2961988A1 publication Critical patent/EP2961988A1/fr
Application granted granted Critical
Publication of EP2961988B1 publication Critical patent/EP2961988B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the present invention relates to a screw pump formed from at least two parts.
  • a screw pump is a so-called positive displacement pump, in which the shape of the rotating displacement resembles that of a spindle screw.
  • the screw pump consists of two or more rotors rotating in opposite directions and a pump housing that encloses the rotors.
  • the rotors are designed with a regular, thread-shaped profile and mesh like a gear.
  • the rotors are also referred to as screw spindles and have at least a first shaft section and a profile section with a helical screw profile.
  • the cavities which are formed by the three construction elements pump housing, first screw spindle and second screw spindle, form the pumping spaces for the pumping medium.
  • This type of pump is particularly suitable for incompressible, also viscous media and for generating high pressures.
  • Screw pumps are used to transport both single-phase and multi-phase liquids.
  • the three-spindle screw pump is mainly used for pumping lubricating fluids that are free from abrasives. It is characterized in particular by the fact that it is possible to generate high pressures of up to 160 bar with it.
  • the three spindles are usually arranged in such a way that a drive spindle located in the middle (also known as the main rotor) drives two laterally engaging secondary spindles.
  • the drive spindle for its part, is connected to a drive motor, which can be designed both as an electric motor and as an internal combustion engine.
  • the torque generated by the drive is transmitted from the drive spindle to the driven spindles via the spindle profile.
  • the interlocking spindle profiles create closed pumping chambers in which the pumping medium is enclosed and transported in the axial direction from the suction to the pressure side.
  • the secondary rotors can be positioned in the pump housing at an angle of 180 ° from the axis of rotation of the main rotor, which balances the radial force acting on the main rotor.
  • Such a pump is for example from the WO 2011/063870 A2 known.
  • the WO-Offenlegungsschrift shows a screw spindle pump with a pump housing and a flange section, the flange section being designed as a stationary component of the pump housing.
  • the pump housing must therefore be oriented together with its flange section with regard to the position of a corresponding counter-flange.
  • the object of the invention is therefore to provide a screw pump which has increased flexibility with regard to its possible installation.
  • the invention relates to a screw spindle pump formed from at least two parts for pumping conveying media.
  • the delivery media are formed by fluid media, such as lubricants, water, suspensions or the like.
  • the term “pumping” is to be understood as a process in which the conveying medium is transported and pressurized.
  • the first of the at least two parts of the screw pump comprises a housing and at least one spindle system arranged in the housing and drivable in a rotationally movable manner.
  • the spindle system comprises a main drive spindle, which is coupled to one or more further auxiliary spindles which can be driven in a rotationally movable manner by the main drive spindle.
  • the main drive spindle is coupled to the respective auxiliary spindle via the respective spindle profile that follows the toothing law.
  • the main drive spindle is preferably driven by one or more actuators.
  • the one or more actuators can be designed, for example, as an electric and / or internal combustion engine.
  • the rotation frequency of the main drive spindle can be predefined in a defined manner via the one or more actuators and, if necessary, can be adapted to the respective delivery medium and the desired delivery rate.
  • the first part further comprises a pressure area downstream of the spindle system and at least one outlet opening connected to it, which discharges the conveying medium from the pressure area.
  • the pumped medium is thus conveyed into the pressure area via the spindle system.
  • the outlet opening is designed, for example, as a bore in the housing and / or as a channel in the housing. It is conceivable, for example, that the outlet opening is designed as a through-hole in the housing, which is angled against the axis of rotation of the main drive spindle and opens into the pressure area. According to a further embodiment, the outlet opening is designed as a through-hole which is perpendicular to the axis of rotation of the main drive spindle and opens into the pressure area.
  • the second part of the screw pump further comprises at least one low-pressure chamber arranged upstream of the spindle system and at least one inlet opening for the fluid medium into the low-pressure chamber.
  • the at least one outlet opening and the at least one inlet opening are designed to be identical or different.
  • the second part and the first part are preferably connected to one another in a sealed manner, so that no conveying medium can inadvertently escape from the low-pressure chamber of the screw pump.
  • the first part and the second part of the screw pump are coupled to one another so as to be rotatable in order to assume at least two different relative positions.
  • the inlet opening and the outlet opening are designed as an inlet channel and as an outlet channel, with a parallel course of the inlet channel and the outlet channel in a first relative position. It can further be the case that in a second relative position a skewed course of the inlet channel and of the outlet channel is formed.
  • first part and the second part are releasably connected to one another in the respective relative position.
  • the detachable connection takes place via screw connections or the like.
  • the first and the second part are held in the respective relative position, for example by means of shrink and / or adhesive and / or welded connections.
  • the first part and the second part are releasably connected to one another in their respective relative positions during operation of the screw pump.
  • the first part and the second part are rotatably coupled to one another.
  • the housing has a cylindrical shape, at least in sections, and the relative rotational movement of the first and second parts about a longitudinal axis of the cylindrically shaped housing or housing part can be produced.
  • the second part of the screw pump sits rotatably on the first part.
  • one of the two parts has contact means for this purpose and the other of the two parts has corresponding mating contact means, the contact means and mating contact means possibly engaging with one another.
  • a change from a first of the at least two relative positions to a second of the at least two relative positions can be brought about by means of a relative rotational movement of the first part with respect to the second part about a longitudinal axis, which longitudinal axis is designed as the axis of rotation of a main drive spindle of the spindle system.
  • the main drive spindle can be defined as that spindle which is coupled to an actuator, such as an electric motor and / or internal combustion engine, for driving purposes.
  • the longitudinal axis is designed as the axis of rotation of another of the spindles.
  • embodiments have proven themselves in practice in which the low-pressure chamber of the second part has a shell-like shape at least in some areas. Such a shape improves the flow behavior of the delivery medium in the second part of the screw pump.
  • a flange section for fixing to a corresponding counter flange is formed in the area of the inlet opening and / or in the area of the outlet opening .
  • the flange section in the area of the inlet opening or the flange section of the second part is thus preferably rotated together with the first part when the second part is rotated relative to the first part.
  • the first part comprises at least one return channel, which at least one return channel is fluidically connected to the pressure area and to the low-pressure chamber.
  • the return channel is designed to guide the conveying medium from the pressure area into the low-pressure chamber.
  • there are several return channels of this type which optionally run parallel to one another.
  • the return channel leads from the pressure area in the direction of the low-pressure chamber and is closed at an end pointing in the direction of the low-pressure chamber.
  • the return channel has, for example, a branching and / or deflection, which deflection leads in the direction of one or more means, which are described in more detail below, for limiting a predefined setpoint pressure level in the pressure area.
  • the at least one return channel is formed by the housing of the first part.
  • the at least one return channel is designed as a bore in the housing which extends from the pressure area to the low-pressure chamber.
  • the screw pump comprises one or more means which are brought into operative connection with the low-pressure chamber and the pressure area in such a way that when a predefined pressure level in the pressure chamber is exceeded, a predefined maximum pressure level in the pressure chamber can be set via one or more means. It is conceivable that such means are arranged in the area of the low-pressure chamber.
  • the means comprise one or more pressure relief valves.
  • the means are brought into operative connection with the low-pressure chamber and the pressure area and are designed as part of the second part of the screw pump.
  • the means can be moved together with the second part as part of the second part when the first part and the second part are rotated relative to each other.
  • the previously mentioned at least one return channel has a branch, with one branch continuing the conveying medium to the one or more means.
  • the one or more means can have a base body with a cavity, in which a piston is mounted such that it can move in a stroke against the restoring force of a compression spring, and have at least one bore arranged on the end face in the base body.
  • a bolt coupled to the piston can be guided through the bore, preferably coaxially to the piston, and can be in contact with the respective conveying medium.
  • the maximum cross section of the bolt is preferably designed to be reduced in area compared to the maximum cross section of the piston.
  • the maximum cross-section of the bolt is designed to be reduced in area to the minimum cross-section of the piston.
  • the bore is designed as part of a front cover of the base body and the cover has one or more further openings, preferably arranged radially around the bore, for the delivery medium to enter the cavity of the base body.
  • the conveying medium can come into direct contact with the piston and in particular with a head section of the piston described further below and push the bolt away from the one or more bores in a supporting manner against the restoring force of the spring.
  • the delivery medium can penetrate into a cavity of the base body that becomes accessible from the stroke movement, which results in a pressure reduction in the pressure area or in the low-pressure chamber.
  • the one or more means as a valve, the valve being composed of a base body, a piston, a compression spring and a so-called pilot system.
  • the pilot system is used to increase the pressure in a pressure range when a maximum pressure level is exceeded by opening and closing the valve.
  • the opening takes place under pressure from a control bolt. If there is pressure at an opening bore of the valve, pressure relief in the pressure area is achieved by opening the valve via the control bolt.
  • the control bolt is connected to the aforementioned piston and preferably has a smaller cross-sectional area than the piston, which results in a reinforcing effect when the valve is opened.
  • the piston in the described embodiment is moved into a seat of the valve by the force of the compression spring and closes a pressure opening through which the control pin is guided.
  • an opening or channel arranged laterally in the base body is opened, which is connected to the low-pressure chamber. The pressure level in the base body is thus reduced when the opening or the channel is opened and adapted to the pressure level of the low-pressure chamber.
  • the one or more means comprise a base body with a cavity in which a piston is mounted so as to be movable against the restoring force of a compression spring and a bolt connected to the piston, whose maximum cross-section is reduced in area to the maximum cross-section of the Piston is formed when a predefined maximum pressure level is exceeded, is guided in the base body in a stroke-movable manner.
  • a lateral opening of the base body is preferably released for the return flow of the conveying medium from the pressure area into the low-pressure chamber.
  • the one or more means are designed as a component of the second part and have a rear cover which can be removed via one or more screw connections and which is arranged on an outside of the second part.
  • the one or more means have one or more setting means, accessible from the outside and preferably actuatable by means of a tool, for specifying the restoring force of the compression spring.
  • a tool for specifying the restoring force of the compression spring.
  • the maximum pressure level in the low-pressure chamber or in the pressure area is adjusted by simply actuating the one or more setting means from outside, without having to replace components.
  • FIG. 1 shows a schematic perspective view of an embodiment of a screw pump 1 according to the invention.
  • the screw pump 1 is formed from a first part 3 and a second part 5.
  • the first part 3 comprises a housing 7.
  • a spindle system 4 is arranged, which in the present case is composed of a main drive spindle 9 and two further auxiliary spindles, of which one auxiliary spindle 10 in Figure 1 is recognizable.
  • the first secondary spindle 10 and the further secondary spindles are coupled to the main drive spindle 9 in a rotationally movable manner and form moving conveying chambers for transporting a conveying medium in the conveying direction FR, with an operative connection with the main drive spindle.
  • the main drive spindle 9 is coupled to an actuator (not shown), such as an electric motor, at its free end 11 emerging from the housing 7 of the first part 3.
  • the axis of rotation R of the main drive spindle 9 is also indicated.
  • the first part 3 comprises a pressure area 15 and an outlet opening 13, which is brought into connection with the pressure area 15 in a way that removes the conveying medium from the pressure area 15.
  • the delivery medium thus flows out of the pressure area 15 and out of the housing 7 of the first part 3 via the outlet opening 13.
  • the pressure area 15 is defined as that area via which the conveying medium is passed on from the spindle system 4 to the outlet opening 13.
  • a screw pump 1 can also have one or more pressure chambers which are arranged upstream of the outlet opening 13.
  • the embodiment of the Figure 1 also knows a return channel 21 as part of the screw pump 1.
  • the return channel 21 is formed by the housing 7 of the first part 3 and is made as a bore in the housing 7 during a manufacturing process of the housing 7. Only one such return channel 21 is shown, but in further embodiments several such return channels 21 can also be introduced into the housing 7.
  • the return channel 21 connects the pressure area 15 of the first part 3 with the low-pressure chamber 16 of the second part 5, but is closed in the area of the low-pressure chamber 16 so that the conveying medium cannot flow back from the pressure area 15 into the low-pressure chamber 16.
  • the delivery medium is guided through the return channel 21 into a pressure chamber 43 or 43 ', which is designed as an annular channel, with a valve 2 (cf. Figure 5 ) is in communication.
  • Figure 1 shows an embodiment in which the outlet opening 13 is designed as an outlet channel, the return channel 21 having an orthogonal orientation to the outlet channel or to the outlet opening 13 and being connected to the outlet opening 13 or the outlet channel.
  • the pressure area thus extends into the outlet opening 13 or into the outlet channel.
  • the return channel 21 runs as a bore parallel to the axis of rotation R of the main drive spindle 9.
  • the screw pump 1 further comprises at least one low-pressure chamber 16 arranged upstream of the spindle system 4, which is shown in FIG Figure 1 Is shell-shaped.
  • the shell-shaped configuration By means of the shell-shaped configuration, the flow behavior of the conveying medium entering the low-pressure chamber 16 as a volume flow and its transfer to the spindle system 4 are optimized.
  • An inlet opening 14 of the second part 5 is also shown.
  • the conveying medium enters the low-pressure chamber 16 via the inlet opening 14.
  • a respective flange section 18 or 19 is formed for fixing to a corresponding counter-flange (not shown).
  • the first part 3 and the second part 5 are rotatably coupled to one another in order to assume two different relative positions.
  • the second part 5 sits on the first part 3 in the present case.
  • Figure 1 shows a first relative position of the first and second parts 3 and 5, in which the conveying medium flows in a first flow direction SR1 through the inlet opening 14 into the low-pressure chamber 16 and flows out in a second flow direction SR2 through the outlet opening 13 from the housing 7 of the first part 3 , wherein the first flow direction SR1 and the second flow direction SR2 run parallel to one another.
  • the axis of rotation R of the main drive spindle 9 is also designed as an axis of rotation D for the relative rotation of the first and second parts 3 and 5.
  • the flange sections 18 and 19 of the first and second parts 3 and 5 can thus be adapted to the position of a corresponding counter flange by means of a relative rotation of the first and second parts 3 and 5. A higher flexibility with such a configuration of a screw pump 1 according to the invention is guaranteed.
  • FIG. 10 shows a schematic perspective view of the second part 5 of the screw pump 1 from FIG Figure 1 . It is easy to see in Figure 2 Again the flange section 18 and the inlet opening 14 of the second part 5.
  • a valve 2 is shown, which is also designed as a component of the second part 5 and to which valve 2 is shown in detail below in Figure 5 is received.
  • the valve 2, the inlet opening 14 and the flange section 18 are in the relative rotational movement of the first part 3 (cf. Figure 1 ) to the second part 5 as part of the second part 5 together with the second part 5.
  • Figures 3 show a schematic top view ( Figure 3A ) and a schematic side view ( Figure 3B ) of the second part 5 Figure 2 .
  • Figure 3A The flange section 18 and the inlet opening 14 of the second part 5 are again clearly visible in FIG Figures 3 a rear cover 23 and adjustment means 25 of the in Figure 5 valve 2 shown in detail.
  • the rear cover 23 is arranged on an outside of the second part 5 and can optionally be fixed there via connections such as screws or the like and / or received in the second part 5 in a form-fitting manner.
  • Via the setting means 25, which is accessible from the outside and designed as an external square a restoring force of the in Figure 5 illustrated compression spring 27 of the valve 2 can be specified or adjusted.
  • Figures 4 show in Figure 4A a schematic front view of the second part 5 from FIG Figures 2 and 3 .
  • Figure 4B a cross section through the second part 5 along the section line BB Figure 4A shown.
  • FIG. 4B The cross section of the Figure 4B again clarifies the arrangement of the valve 2 in the second part 5.
  • the low-pressure chamber 16 and the valve for the transfer of the conveying medium are shown fluidically connected to one another.
  • the conveying medium can, for example, via a return channel 21 (comparatively Figure 1 ) are passed on to valve 2.
  • Figure 5 shows a valve 2 for setting a maximum pressure level in the pressure area 15 of the screw pump 1.
  • the valve 2 is designed as a so-called overpressure valve or safety valve.
  • the valve 2 is part of the second part 5. When the first part 3 and the second part 5 are rotated relative to each other, the valve 2 also rotates together with the second part 5.
  • the valve 2 is designed in such a way that when a predefined pressure level is exceeded in the pressure area 15, a predefined maximum pressure level can be produced in the pressure area 15 via the valve 2.
  • the valve 5 comprises a base body 35 with a cavity H.
  • a piston 31 is mounted such that it can move in a stroke against the restoring force of a compression spring 27.
  • a plurality of bores 44 are shown in a front cover 41 of the base body 35, a control bolt 39 guided through the cover 41 guiding the piston 31 coaxially over the bore provided at the end.
  • the control bolt 39 is fastened through a central bore 44 in the cover 41, several further openings or bores 44 being provided radially around the central bore in the cover 41 of the base body 35.
  • the piston 31 comprises a head section 33 at a free end pointing in the direction of the bore 44.
  • the head section 33 is received in the cavity H of the base body 35 without play.
  • a lateral opening 37 is shown in the base body 35, through which the head section 33 of the piston 31 is guided when a lifting movement is carried out.
  • the head section 33 is arranged in a seat S of the front cover 41 resulting from a restoring force of the compression spring 27.
  • the seat S of the front cover 41 can be such that the head section 33 can be received in the seat S essentially without play.
  • the conveying medium can penetrate through the lateral opening 37.
  • the pressure level of the delivery medium penetrating into the lateral opening 37 is always identical to the actual pressure level in the low-pressure chamber 16 or in the pressure region 15. If the piston 31 executes a stroke movement by exceeding the maximum pressure level and the head section 33 of the piston 37 leaves the seat S, the conveying medium with excess pressure can penetrate through the return duct 21, the bore 44 and the radially attached openings of the control pin 39 and the stroke movement of the Support piston 31 against the restoring force of the compression spring 27 in addition to to open the path into the cavity H of the base body 35 via the opening 37 into the low-pressure chamber 16 following the conveying medium.
  • the rear cover 23 is arranged on an outside of the second part 5.
  • the restoring force of the compression spring 27 can be specified via the setting means 25.
  • Figures 6 show one possibility of the arrangement of the valve 2 from Figure 5 in a second part 5 of an embodiment of a screw pump 1 according to the invention.
  • First clarified Figure 6A a possible option for the flow of the pumped medium by means of an arrow representation.
  • the conveyed medium enters the low-pressure chamber 16 of the second part 5 as a volume flow via the inlet opening 14 and is then transferred in the direction of the arrow via the spindle system 4 (cf. Figure 1 ) transported to the outlet opening 13.
  • the embodiment of the Figures 6 has two return channels 21 and 21 ', which return channels 21 and 21' have a parallel course.
  • Each of the return channels 21 and 21 ' leads in the direction of a pressure chamber 43 and 43', respectively, with each pressure chamber 43 and 43 'having a valve 2, as in FIG Figure 5 exemplified, is in connection.
  • Figure 6B also shows that the pumped medium is transferred directly to the in Figure 5
  • the opening 37 of the valve 2 shown can flow into the low-pressure chamber 16 of the second part 5.
  • Next is the cavity H of the valve 2 respectively. of the base body 35 is fluidically connected directly to the low-pressure chamber 16 via the opening 37.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (14)

  1. Pompe à broche hélicoïdale (1) constituée en au moins deux parties (3, 5), destinée à pomper des fluides tels que des fluides lubrifiants, de l'eau, des suspensions ou similaires, sur laquelle
    - la première partie (3) comprend un carter (7) ainsi qu'au moins un système de broche (4) placé dans le carter (7) et susceptible d'être entraîné de manière mobile en rotation, une zone de pression (15) placée en aval du système de broche (4), ainsi qu'au moins un orifice de sortie (13), lequel en évacuant le fluide hors de la zone de pression (15) est amené en liaison avec la zone de pression (15) et sur laquelle
    - la deuxième partie (5) comporte au moins une chambre basse pression (16) placée en amont du système de broche (4), ainsi qu'au moins un orifice d'entrée (14) pour le fluide dans la chambre basse pression (16), pour adopter au moins deux positions relatives différentes, la première partie (3) et la deuxième partie (5) étant accouplées l'une à l'autre de manière mobile en rotation, la pompe à broche hélicoïdale (1) caractérisée en ce que
    la pompe à broche hélicoïdale (1) comprend un ou plusieurs moyens (2) qui détiennent une ou plusieurs soupapes de surpression et qui sont amenés en liaison active avec la chambre basse pression (16) et la zone de pression (15), de telle sorte que lors d'un dépassement d'un niveau de pression prédéfini dans la zone de pression (15), par l'intermédiaire de l'un ou des plusieurs moyens (2), un niveau de pression maximal prédéfini est réglable dans la zone de pression (15).
  2. Pompe à broche hélicoïdale (1) selon la revendication 1, sur laquelle la deuxième partie (5) de la pompe à broche hélicoïdale (1) repose de manière mobile en rotation sur la première partie (3).
  3. Pompe à broche hélicoïdale (1) selon la revendication 1 ou la revendication 2, sur laquelle un changement d'une première des au moins deux positions relatives dans une deuxième des au moins deux positions relatives de la première partie (3) vers la deuxième partie (5) est susceptible d'être provoqué autour d'un axe longitudinal (D), ledit axe longitudinal étant conçu sous la forme d'un axe de rotation (R) d'une broche d'entraînement principale (9) du système de broches (4).
  4. Pompe à broche hélicoïdale (1) selon l'une quelconque ou plusieurs des revendications 1 à 3, sur laquelle la chambre basse pression (16) de la deuxième partie (5) détient au moins par endroits une conformation en coque.
  5. Pompe à broche hélicoïdale (1) selon l'une quelconque ou plusieurs des revendications 1 à 4, sur laquelle dans la zone de l'orifice d'entrée (14) et/ou dans la zone de l'orifice de sortie (13) est conçu un segment de bride (18, 19) destiné à être fixé sur une contre-bride correspondante.
  6. Pompe à broche hélicoïdale (1) selon l'une quelconque ou plusieurs des revendications 1 à 5, sur laquelle la première partie (3) comprend au moins un canal de retour (21), lequel canal de retour (21) est amené en liaison fluidique avec la zone de pression (15) et avec la chambre basse pression (16).
  7. Pompe à broche hélicoïdale (1) selon la revendication 6, sur laquelle l'au moins un canal de retour (21) est conduit à travers le carter (7) de la première partie (3).
  8. Pompe à broche hélicoïdale (1) selon la revendication 6 ou la revendication 7, sur laquelle l'au moins un canal de retour (21) s'écoule à la parallèle de l'axe de rotation (R) d'une ou de plusieurs broches (9, 10) du système de broches (4).
  9. Pompe à broche hélicoïdale (1) selon la revendication 1, sur laquelle les moyens (2) sont conçus sous la forme de partie intégrante de la deuxième partie (5) de la pompe à broche hélicoïdale (1).
  10. Pompe à broche hélicoïdale (1) selon l'une quelconque des revendications 1 à 9, qui comporte un ou plusieurs moyens (2) comprenant un corps de base (35) pourvu d'une cavité (H), dans lequel un piston (31) est logé en étant mobile en course à l'encontre de la force de rappel d'un ressort de pression (27) et au moins un goujon de commande (39) qui est en liaison avec le piston (31), dont la section transversale maximale est conçue en étant réduite en surface vers la section transversale maximale du piston (31) et qui lors du dépassement d'un niveau de pression maximal dans la zone de pression (15) guide le piston (31) en étant mobile en course dans le corps de base (35) à l'encontre de la force de rappel du ressort de pression (27), au résultat du mouvement en course, un orifice (37) latéral du corps de base (35) étant libéré pour l'écoulement en retour du fluide de la zone de pression (15) dans la chambre basse pression (16).
  11. Pompe à broche hélicoïdale (1) selon la revendication 10, sur laquelle l'au moins un perçage (43) est conçu sous la forme de partie intégrante d'un couvercle (41) antérieur du corps de base (35) et le couvercle (41) antérieur comportant au moins un ou plusieurs ajours additionnels et placés de préférence en direction radiale autour du perçage (43) pour l'entrée du fluide dans la cavité (H) du corps de base (35).
  12. Pompe à broche hélicoïdale (1) selon la revendication 10 ou 11, lorsque le niveau de pression maximale n'est pas dépassé dans la zone de pression (15), un segment de tête (33) du piston (31) étant guidé au moyen du ressort de pression (27) dans un siège (S) et la cavité (H) du corps de base (35) étant amenée en liaison fluidique avec la chambre basse pression (16) par l'intermédiaire de l'orifice (37) conçu latéralement dans le corps de base (35), de telle sorte que le niveau de pression dans la cavité (H) du corps de base (35) soit conçu sensiblement à l'identique du niveau de pression dans la chambre basse pression (16).
  13. Pompe à broche hélicoïdale (1) selon l'une quelconque des revendications 1 à 12, sur laquelle l'un ou les plusieurs moyens (2) sont conçus en tant que partie intégrante de la deuxième partie (5) et sur laquelle le corps de base (35) comporte un couvercle (23) postérieur susceptible d'être retiré par un ou plusieurs assemblages vissés (29), qui est placé sur une face extérieure de la deuxième partie (5).
  14. Pompe à broche hélicoïdale (1) selon l'une quelconque des revendications 10 à 13, sur laquelle l'un ou les plusieurs moyens (2) comprennent un ou plusieurs moyens de réglage (25) accessibles par l'extérieur et susceptibles d'être actionnés de préférence au moyen d'un outil, pour prédéfinir la force de rappel du ressort de pression (27).
EP14723689.7A 2013-03-01 2014-02-25 Pompe à vis se composant d'au moins deux parties Active EP2961988B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013102031.3A DE102013102031B4 (de) 2013-03-01 2013-03-01 Aus wenigstens zwei Teilen gebildete Schraubenspindelpumpe
PCT/DE2014/000088 WO2014131393A1 (fr) 2013-03-01 2014-02-25 Pompe à vis se composant d'au moins deux parties

Publications (2)

Publication Number Publication Date
EP2961988A1 EP2961988A1 (fr) 2016-01-06
EP2961988B1 true EP2961988B1 (fr) 2020-10-07

Family

ID=50721524

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14723689.7A Active EP2961988B1 (fr) 2013-03-01 2014-02-25 Pompe à vis se composant d'au moins deux parties

Country Status (10)

Country Link
US (1) US9759214B2 (fr)
EP (1) EP2961988B1 (fr)
JP (1) JP6101367B2 (fr)
KR (1) KR101788952B1 (fr)
CN (1) CN105143675B (fr)
AR (1) AR094938A1 (fr)
BR (1) BR112015020824B1 (fr)
DE (1) DE102013102031B4 (fr)
RU (1) RU2638706C2 (fr)
WO (1) WO2014131393A1 (fr)

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DE102018109866A1 (de) 2018-04-24 2019-10-24 Nidec Gpm Gmbh Regelbares Schmierölfördersystem für Verbrennungsmaschinen
DE102019128602B3 (de) * 2019-10-23 2021-02-11 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021101111A1 (de) * 2021-01-20 2022-07-21 Netzsch Pumpen & Systeme Gmbh Schraubenspindelpumpe
DE102021133112A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
DE102021133114A1 (de) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe
KR102688160B1 (ko) * 2022-12-23 2024-07-24 주식회사 코아비스 펌프 장치
KR102697715B1 (ko) 2023-03-07 2024-08-23 주식회사 코아비스 워터 펌프

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DE102022131167A1 (de) 2022-11-24 2024-05-29 Dürr Systems Ag Spindeldosierpumpe und zugehöriges Betriebsverfahren
WO2024110168A1 (fr) 2022-11-24 2024-05-30 Dürr Systems Ag Pompe doseuse à broche et procédé de fonctionnement associé

Also Published As

Publication number Publication date
AR094938A1 (es) 2015-09-09
WO2014131393A1 (fr) 2014-09-04
DE102013102031B4 (de) 2016-05-12
KR101788952B1 (ko) 2017-10-20
RU2015141528A (ru) 2017-04-06
JP6101367B2 (ja) 2017-03-22
CN105143675A (zh) 2015-12-09
KR20150121221A (ko) 2015-10-28
EP2961988A1 (fr) 2016-01-06
US9759214B2 (en) 2017-09-12
US20150369239A1 (en) 2015-12-24
DE102013102031A1 (de) 2014-09-04
RU2638706C2 (ru) 2017-12-15
CN105143675B (zh) 2018-01-12
BR112015020824A2 (pt) 2017-07-18
BR112015020824B1 (pt) 2022-06-21
JP2016508575A (ja) 2016-03-22

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