EP2961988A1 - Screw pump with at least two parts - Google Patents
Screw pump with at least two partsInfo
- Publication number
- EP2961988A1 EP2961988A1 EP14723689.7A EP14723689A EP2961988A1 EP 2961988 A1 EP2961988 A1 EP 2961988A1 EP 14723689 A EP14723689 A EP 14723689A EP 2961988 A1 EP2961988 A1 EP 2961988A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- screw pump
- pressure
- base body
- pressure chamber
- low
- 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
Links
- 238000005086 pumping Methods 0.000 claims abstract description 5
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 4
- 230000006835 compression Effects 0.000 claims description 16
- 238000007906 compression Methods 0.000 claims description 16
- 239000012530 fluid Substances 0.000 claims description 15
- 238000004891 communication Methods 0.000 claims description 4
- 230000008859 change Effects 0.000 claims description 2
- 230000001050 lubricating effect Effects 0.000 claims description 2
- 239000000725 suspension Substances 0.000 claims description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 2
- 238000002485 combustion reaction Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 239000003082 abrasive agent Substances 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000834 fixative Substances 0.000 description 1
- 239000011796 hollow space material Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 230000003319 supportive effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- 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
-
- 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
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
- the shape of the rotating displacer is similar to a spindle screw.
- the screw pump consists of two or more counter-rotating rotors and a pump housing that encloses the rotors.
- the rotors are formed with a regular, thread-shaped profiling and engage gear-like in one another.
- 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.
- This type of pump is particularly suitable for incompressible, also viscous media and for generating high pressures.
- Screw pumps are used both for transporting single-phase and multi-phase liquids.
- the three-spindle screw pump is mainly used for pumping lubricating fluids that are free of abrasives. It is characterized in particular by the fact that it is possible to produce high pressures of up to 160 bar.
- the three spindles are usually arranged so that a central drive spindle (also referred to as a main rotor) drives two laterally engaging follower spindles.
- the drive spindle in turn 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 in known from the prior art embodiments of the drive spindle via the spindle profile on the driven spindles.
- the interlocking spindle profiles produce closed delivery chambers, in which the fluid is enclosed and transported in the axial direction from the suction to the pressure side.
- the auxiliary rotors may be positioned at 180 ° in the pump housing from the axis of rotation of the main rotor, which balances the radial force on the main rotor.
- Inlet liquid is transported by the pump under pressure to an outlet.
- Such a pump is known for example from WO 201 1/063870 A2.
- the WO patent publication shows a screw pump with a pump housing and a flange portion, wherein the flange portion is formed as a fixed part of the pump housing.
- the pump housing must therefore be oriented together with its flange portion with respect to the position of a corresponding counter flange.
- the object of the invention is therefore to provide a screw pump available, which has an increased flexibility in terms of their possible installation.
- the invention relates to a screw pump formed from at least two parts for pumping fluids.
- the delivery media are formed by fluid media such as lubricants, water, suspensions, or the like.
- the term "pumps" 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 rotatably movable.
- the spindle system comprises a main drive spindle, which is coupled to one or more additional secondary spindles which can be driven rotationally movably by the main drive spindle.
- the main drive spindle is coupled via the respective spindle profile following the toothing law with the respective sub spindle.
- the main drive spindle is driven by one or more actuators.
- the one or more actuators may be formed, for example, as an electric and / or internal combustion engine.
- the rotational frequency of the main drive spindle can be predetermined via the one or more actuators and can optionally be adapted to the respective delivery medium and the desired delivery rate.
- the first part comprises a pressure region downstream of the spindle system and at least one outlet opening communicating therewith, which discharges the conveying medium from the pressure region.
- the fluid is thus transported via the spindle system in the pressure range.
- the outlet opening may be formed, 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 formed as an angle against the axis of rotation of the main drive spindle employed and opening into the pressure area through hole in the housing. According to a further embodiment, the outlet opening is designed as a passage bore perpendicular to the axis of rotation of the main drive spindle and opening into the pressure area.
- the second part of the screw pump comprises at least one low-pressure chamber 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 identical or different.
- the second part and the first part are preferably sealed together, so that no fluid can escape unintentionally from the low pressure chamber of the screw pump. According to the invention, it is provided that the first part and the second part of the
- Screw pump for taking at least two different relative positions are preferably rotatably coupled together.
- the inlet opening and the outlet opening are formed as an inlet channel and as an outlet channel, wherein a parallel course of the inlet channel and the outlet channel is formed at a first relative position.
- first part and the second part are releasably connected to one another in the respective relative position.
- the detachable connection via screw or the like.
- the first and the second part are held in the respective relative position, for example via shrinkage and / or adhesive and / or welding connections.
- the first part and the second part are releasably connected together in their respective relative position during operation of the screw pump.
- the first part and the second part are rotatably coupled together.
- the housing at least partially has a cylindrical shape and the relative rotational movement of the first and second part about a longitudinal axis of the cylindrically shaped housing or housing part can be produced. It is also conceivable that the second part of the screw pump rotatably seated on the first part.
- one of the two parts has contact means for this purpose and the other of the two parts has corresponding counter-contact means, wherein the contact means and counter-contact means optionally engage with one another. It is also conceivable that a change from a first of the at least two
- Relative positions in a second of the at least two relative positions by means of a relative rotational movement of the first part relative to the second part about a longitudinal axis is effected, which longitudinal axis is formed as a rotation axis of a main drive spindle of the spindle system.
- the main drive spindle may, as previously mentioned, be defined as the spindle which is coupled to the drive with an actuator, such as an electric and / or internal combustion engine.
- an actuator such as an electric and / or internal combustion engine.
- the longitudinal axis is formed as a rotation axis of a further of the spindles.
- the first part comprises at least one return duct, which at least one return duct is fluidically connected to the pressure area and to the low-pressure chamber.
- the return channel for guiding the pumped medium is formed by the pressure region in the low-pressure chamber.
- a plurality of such return channels are present, which optionally run parallel to each other.
- one or more return channels are oriented parallel to a rotation axis of one or more drive spindles.
- the return duct leads from the pressure region in the direction of the low-pressure chamber and is closed at an end pointing in the direction of the low-pressure chamber. It is also conceivable that the return channel has, for example, a branching and / or deflection, which leads deflection in the direction of one or more means described in more detail below for limiting a predefined desired pressure level in the pressure range.
- the at least one return channel In order to be able to integrate the at least one return channel in the simplest possible manner during production of the screw pump, it is possible, for example, for the at least one return channel to be formed by the housing of the first part.
- the at least one return channel In order to be able to integrate the at least one return channel in the simplest possible manner during production of the screw pump, it is possible, for example, for the at least one return channel to be formed by the housing of the first part.
- the at least one return channel In order to be able to integrate the at least one return channel in the simplest possible manner during production of the screw pump, it is possible, for example, for the at least one return channel to be formed by the housing of the first part.
- the at least one return channel In order to be able to integrate the at least one return channel in the simplest possible manner during production of the screw pump, it is possible, for example, for the at least one return channel to be formed by the housing of the first part.
- the at least one return channel In order to be able to integrate
- Return channel formed as a bore in the housing, which extends from the pressure region 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 range such that a predefined maximum pressure level in the pressure chamber can be set by one or more means when a predefined pressure level in the pressure chamber is exceeded. It is conceivable that such means are arranged in the region of the low-pressure chamber. It is also conceivable that the means comprise one or more pressure relief valves. In particular, in embodiments with the previously described at least one return channel, there is the possibility that the means be brought into operative connection with the low-pressure chamber and the pressure region and formed as part of the second part of the screw pump. Thus, in this embodiment, the means are movable with relative rotational movement of the first part and the second part as part of the second part together with the second part.
- the one or more means may have a base body with a cavity in which a piston is mounted for lifting against the restoring force of a compression spring and at least one end face arranged in the base body bore.
- a piston coupled to the piston may be preferably guided coaxially to the piston and are in contact with the respective fluid.
- the maximum cross section of the bolt is preferably reduced in area to the maximum cross section of the piston.
- the maximum cross-section of the bolt is formed reduced in area to the minimum cross section of the piston.
- the bore is formed as part of a front cover of the base body and the lid has one or more further and preferably radially arranged around the bore openings for entry of the pumped medium into the cavity of the base body.
- the pumped medium can after entering via the one or more further holes directly with the piston and in particular with a subsequently described further head portion of the piston in contact and push the bolt supportive against the restoring force of the spring away from the one or more holes.
- the fluid can penetrate into a cavity of the base body which becomes accessible from the lifting movement, resulting in a pressure reduction in the pressure region or in the low-pressure chamber.
- the valve is composed of a base body, a piston, a compression spring and a so-called pilot system.
- the pilot system is used here to control the pressure in a pressure range when a maximum pressure is exceeded. Reduce pressure levels on opening and closing of the valve.
- the opening takes place in this embodiment under pressure of a control pin. If pressure is applied to an opening bore of the valve, a pressure relief in the pressure range is achieved by means of an opening of the valve via the control bolt.
- the control pin is in this case brought into connection with the previously mentioned piston and preferably has a smaller cross-sectional area than the piston, resulting in a reinforcing effect when the valve is opened.
- the piston is moved in the embodiment described by the force of the compression spring in a seat of the valve and closes a pressure port through which the control pin is guided.
- a laterally arranged in the base body breakthrough or channel is opened, which is in communication with the low pressure chamber.
- the pressure level in the base body is thus reduced at the opening of the aperture or the channel and adapted to the pressure level of the low-pressure chamber.
- Means comprise a base body with cavity, in which a piston is mounted in a liftable against the restoring force of a compression spring and a bolt connected to the piston whose maximum cross-section is reduced in area reduced to the maximum cross section of the piston is at a predefined maximum pressure levels in the hub Base body is guided.
- a lateral opening of the base body for the return flow of the conveying medium from the pressure region into the low-pressure chamber is preferably released from the lifting movement.
- the one or more means one or more externally accessible and preferably actuated by means of tool adjustment means for specifying the restoring force of the compression spring.
- tool adjustment means for specifying the restoring force of the compression spring.
- an external square or the like for example, an external square or the like .
- FIG. 1 shows a schematic perspective view of an embodiment of a screw pump according to the invention
- FIG. 2 shows a schematic perspective view of the second part of FIG
- Figures 3 show a schematic plan view and a schematic side view of the second part of Figure 2;
- Figures 4 show a schematic frontal view of the second part of Figures 2 and 3 and a cross section through the second part;
- Figure 5 shows a valve for setting a maximum pressure level in the pressure range of the screw pump of Figure 1;
- Figures 6 show a possibility of arranging the valve of Figure 5 in a second part of an embodiment of a screw pump according to the invention. Identical or equivalent elements of the invention will be identical
- 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 consists of a main drive spindle 9 and two further secondary spindles, of which a secondary spindle 10 can be seen in FIG.
- the first secondary spindle 10 and the additional secondary spindles are rotatably coupled to the main drive spindle 9 and form under operative connection with the main drive spindle moving delivery chambers for transporting a pumped medium in the conveying direction FR.
- the main drive spindle 9 is at its free and from the housing 7 of the first part 3 exiting end 1 1 to an actuator (not shown), such as an electric motor, coupled. Also indicated is the axis of rotation R of the main drive spindle 9.
- the first part 3 comprises a pressure region 15 and an outlet opening 13, which is conveyed from the pressure region 15 to the pressure region 15 in connection with the conveying medium.
- the conveying medium thus flows out of the pressure region 15 and out of the housing 7 of the first part 3 via the outlet opening 13.
- the pressure region 15 is defined as the region over which the conveying medium is passed from the spindle system 4 to the outlet opening 13.
- a screw pump 1 may also have one or more pressure chambers, which are arranged upstream of the outlet opening 13.
- the embodiment of FIG. 1 also has 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 introduced during a manufacturing process of the housing 7 as a bore in the housing 7. Shown is merely such a return channel 21, in further embodiments, however, several such return channels 21 may be introduced into the housing 7.
- the return channel 21 connects the pressure region 15 of the first part 3 with the low pressure chamber 16 of the second part 5, but is closed in the region of the low pressure chamber 16, so that the fluid from the pressure region 15 can not flow back into the low pressure chamber 16.
- the fluid is passed through the return channel 21 in a pressure chamber 43 or 43 ', which is designed as an annular channel, with each pressure chamber 43 or 43', a valve 2 (see Figure 5) in Connection stands.
- 1 shows an embodiment in which the outlet opening 13 is formed as an outlet channel, wherein the return channel 21 has an orthogonal orientation to the outlet channel or to the outlet opening 13 and is in communication with the outlet opening 13 and the outlet channel.
- the pressure region 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-spindle pump 1 comprises at least one low-pressure chamber 16 which precedes the spindle system 4 and is cup-shaped in FIG.
- the flow behavior of the 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 Via the inlet opening 14, the delivery medium enters the low-pressure chamber 16. In the region of the inlet opening 14 and in the region of the outlet opening 13, a respective flange section 18 or 19 for fixing to a corresponding counter flange (not shown) is formed.
- FIG. 1 shows a first relative position of the first and second parts 3 and 5, in which the medium flows in a first flow direction SR1 through the inlet opening 14 into the low-pressure chamber 16 and in a second flow direction SR2 through the outlet opening 13 from the housing 7 of the first part 3 flows out, wherein the first flow direction SR1 and the second flow direction SR2 parallel to each other.
- Main drive spindle 9 is also formed as a rotation axis D for relative rotation of the first and second parts 3 and 5.
- the flange portions 18 and 19 of the first and second parts 3 and 5 can thus be adapted by means of a relative rotation of the first and the second part 3 and 5 to the position of a corresponding counter-flange.
- Figure 2 shows a schematic perspective view of the second part 5 of the screw pump 1 of Figure 1. Good to see in Figure 2 again the flange portion 18 and the inlet opening 14 of the second part 5.
- a valve 2 is shown, which is also part of the second Part 5 is formed and which valve 2 is discussed in detail below in Figure 5.
- the valve 2, the inlet opening 14 and the flange portion 18 are in relative rotational movement of the first part 3 (see Figure 1) to the second part 5 as part of the second part 5 together with the second part 5 rotatable.
- FIG. 3 shows a schematic top view (FIG. 3A) and a schematic side view (FIG. 3B) of the second part 5 from FIG. 2.
- the flange section 18 and the inlet opening 14 of the second part 5 are again shown in FIG. 3A
- the rear cover 23 is arranged on an outer side of the second part 5 and may optionally there via connections such as screws or the like fixed and / or positively in the second part. 5 be included.
- the adjusting means 25 which is accessible from the outside and formed as a square, a restoring force of the compression spring 27 of the valve 2 shown in Figure 5 can be specified or adjusted.
- FIG. 4 shows in FIG. 4A a schematic frontal view of the second part 5 from FIGS. 2 and 3. Furthermore, FIG. 4B shows a cross section through the second part 5 along the section line B-B on FIG. 4A.
- FIG. 4B The cross-section of Figure 4B illustrates again the arrangement of the valve 2 in the second part 5.
- the low-pressure chamber 16 and the valve for the transfer of the pumped medium are fluidly connected with each other.
- the fluid can, for example via a return channel 21st
- valve 5 shows a valve 2 for setting a maximum pressure level in the pressure region 15 of the screw pump 1.
- the valve 2 is designed as a so-called pressure relief valve or safety valve.
- the valve 2 is part of the second part 5. In relative rotation of the first part 3 and the second part 5 as well as a rotational movement of the valve 2 takes place together with the second part. 5
- the function of the valve 2 is such that when a predefined pressure level in the pressure range 15 is exceeded, a predefined maximum pressure level in the pressure range 15 can be established via the valve 2.
- the valve 5 comprises a base body 35 with cavity H.
- a piston 31 is mounted for lifting against the restoring force of a compression spring 27.
- a front cover 41 of the base body 35 a plurality of holes 44 are shown, wherein a guided through the cover 41 control pin 39, the piston 31 leads coaxially over the frontally present bore.
- the control bolt 39 is fastened by a middle bore 44 in the cover 41, wherein a plurality of further openings or bores 44 are provided radially around the central bore in the cover 41 of the base body 35.
- the maximum cross-section of the bolt 39 is reduced in area perpendicular to the respective longitudinal axis to the maximum cross-section of the piston 31.
- the piston 31 comprises at a pointing in the direction of the bore 44 free end a head portion 33.
- the head portion 33 is received in the assembled state of the valve 2 and the pressure relief valve play in the cavity H of the base body 35.
- a lateral opening 37 is shown in the base body 35, on which the head portion 33 of the piston 31 is guided past when performing a stroke movement.
- the head portion 33 is hereby arranged from a restoring force of the compression spring 27 resulting in a seat S of the front cover 41.
- the seat S of the front cover 41 may be such that the head portion 33 is substantially free of play in the seat S can be accommodated.
- the pressure level of the conveying medium entering 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 performs a stroke movement by exceeding the maximum pressure level and the head portion 33 of the piston 37 leaves the seat S can convey medium with pressure through the return channel 21, the bore 44 and the radially mounted openings of the control pin 39 penetrate and the lifting movement of the Support piston 31 against the restoring force of the compression spring 27 complementary to Subsequently, the medium to be opened in the cavity H of the base body 35 via the opening 37 in the low-pressure chamber 16 the medium.
- the rear cover 23 is arranged on an outer side of the second part 5.
- the restoring force of the compression spring 27 can be specified.
- FIG. 6 shows a possibility of arranging the valve 2 from FIG. 5 in a second part 5 of an embodiment of a screw pump 1 according to the invention.
- FIG. 6A illustrates a possible option of the flow of the pumped medium by means of an arrow.
- the delivery medium enters the low-pressure chamber 16 of the second part 5 as a volume flow via the inlet opening 14 and is subsequently transported in the direction of the arrow via the spindle system 4 (cf. FIG. 1) to the outlet opening 13.
- the embodiment of 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 or 43', wherein with each pressure chamber 43 and 43 'in each case a valve 2, as exemplified in Figure 5, is in communication.
- FIG. 6B also shows that the conveying medium can flow directly into the low-pressure space 16 of the second part 5 via the opening 37 of the valve 2 shown in FIG. Furthermore, the hollow space H of the valve 2 or of the base body 35 is fluidically connected via the opening 37 directly to the low-pressure chamber 16.
Landscapes
- 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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013102031.3A DE102013102031B4 (en) | 2013-03-01 | 2013-03-01 | From at least two parts formed screw pump |
PCT/DE2014/000088 WO2014131393A1 (en) | 2013-03-01 | 2014-02-25 | Screw pump with at least two parts |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2961988A1 true EP2961988A1 (en) | 2016-01-06 |
EP2961988B1 EP2961988B1 (en) | 2020-10-07 |
Family
ID=50721524
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14723689.7A Active EP2961988B1 (en) | 2013-03-01 | 2014-02-25 | Screw pump with at least two parts |
Country Status (10)
Country | Link |
---|---|
US (1) | US9759214B2 (en) |
EP (1) | EP2961988B1 (en) |
JP (1) | JP6101367B2 (en) |
KR (1) | KR101788952B1 (en) |
CN (1) | CN105143675B (en) |
AR (1) | AR094938A1 (en) |
BR (1) | BR112015020824B1 (en) |
DE (1) | DE102013102031B4 (en) |
RU (1) | RU2638706C2 (en) |
WO (1) | WO2014131393A1 (en) |
Families Citing this family (8)
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DE102018109866A1 (en) | 2018-04-24 | 2019-10-24 | Nidec Gpm Gmbh | Controllable lubricating oil conveyor system for internal combustion engines |
DE102019128602B3 (en) * | 2019-10-23 | 2021-02-11 | Leistritz Pumpen Gmbh | Screw pump |
DE102021101111A1 (en) * | 2021-01-20 | 2022-07-21 | Netzsch Pumpen & Systeme Gmbh | screw pump |
DE102021133114A1 (en) | 2021-12-14 | 2023-06-15 | Leistritz Pumpen Gmbh | screw pump |
DE102021133112A1 (en) * | 2021-12-14 | 2023-06-15 | Leistritz Pumpen Gmbh | screw pump |
DE102022131167A1 (en) | 2022-11-24 | 2024-05-29 | Dürr Systems Ag | Spindle metering pump and associated operating procedure |
KR102688160B1 (en) * | 2022-12-23 | 2024-07-24 | 주식회사 코아비스 | Pump apparatus |
KR102697715B1 (en) | 2023-03-07 | 2024-08-23 | 주식회사 코아비스 | Water pump |
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US2321498A (en) * | 1940-05-06 | 1943-06-08 | Leo S Madlem | Pump |
US2592476A (en) * | 1948-02-07 | 1952-04-08 | Laval Steam Turbine Co | Series arrangement of positive and nonpositive screw pumps |
US2924181A (en) * | 1957-05-13 | 1960-02-09 | Laval Steam Turbine Co | Screw pumps or motors |
US3759636A (en) * | 1972-03-13 | 1973-09-18 | Dunham Busa Inc | Composite variable oil pressure relief and compressor unload valve assembly |
SE407839B (en) * | 1977-09-15 | 1979-04-23 | Imo Industri Ab | SCREWDRIVER |
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2013
- 2013-03-01 DE DE102013102031.3A patent/DE102013102031B4/en active Active
-
2014
- 2014-02-25 WO PCT/DE2014/000088 patent/WO2014131393A1/en active Application Filing
- 2014-02-25 JP JP2015559423A patent/JP6101367B2/en not_active Expired - Fee Related
- 2014-02-25 KR KR1020157026977A patent/KR101788952B1/en active IP Right Grant
- 2014-02-25 EP EP14723689.7A patent/EP2961988B1/en active Active
- 2014-02-25 BR BR112015020824-0A patent/BR112015020824B1/en active IP Right Grant
- 2014-02-25 CN CN201480010046.XA patent/CN105143675B/en active Active
- 2014-02-25 RU RU2015141528A patent/RU2638706C2/en not_active IP Right Cessation
- 2014-02-28 AR ARP140100652A patent/AR094938A1/en unknown
-
2015
- 2015-08-27 US US14/837,028 patent/US9759214B2/en active Active
Non-Patent Citations (1)
Title |
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See references of WO2014131393A1 * |
Also Published As
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BR112015020824A2 (en) | 2017-07-18 |
US9759214B2 (en) | 2017-09-12 |
KR101788952B1 (en) | 2017-10-20 |
DE102013102031B4 (en) | 2016-05-12 |
CN105143675A (en) | 2015-12-09 |
WO2014131393A1 (en) | 2014-09-04 |
AR094938A1 (en) | 2015-09-09 |
JP6101367B2 (en) | 2017-03-22 |
DE102013102031A1 (en) | 2014-09-04 |
EP2961988B1 (en) | 2020-10-07 |
RU2638706C2 (en) | 2017-12-15 |
US20150369239A1 (en) | 2015-12-24 |
CN105143675B (en) | 2018-01-12 |
BR112015020824B1 (en) | 2022-06-21 |
KR20150121221A (en) | 2015-10-28 |
RU2015141528A (en) | 2017-04-06 |
JP2016508575A (en) | 2016-03-22 |
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