EP4677231A1 - Ensemble pompe et soupape - Google Patents

Ensemble pompe et soupape

Info

Publication number
EP4677231A1
EP4677231A1 EP24712170.0A EP24712170A EP4677231A1 EP 4677231 A1 EP4677231 A1 EP 4677231A1 EP 24712170 A EP24712170 A EP 24712170A EP 4677231 A1 EP4677231 A1 EP 4677231A1
Authority
EP
European Patent Office
Prior art keywords
pump
control valve
intermediate control
valve member
valve arrangement
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.)
Pending
Application number
EP24712170.0A
Other languages
German (de)
English (en)
Inventor
Dennis VAN DEKKEN
Bertram Baudler
Petr Nemec
Fabian KUPFER
Domenico Solazzo
Nils Gehring
Alexander Krimm
Klaus Weiske
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.)
Woco Industrietechnik GmbH
Original Assignee
Woco Industrietechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Woco Industrietechnik GmbH filed Critical Woco Industrietechnik GmbH
Publication of EP4677231A1 publication Critical patent/EP4677231A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0088—Testing machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0686—Mechanical details of the pump control unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet

Definitions

  • the invention relates to a pump valve arrangement comprising a pump for generating a fluid flow, in particular of a motor vehicle, and a valve for adjusting the fluid flow.
  • valve elements that cooperate with valve seats.
  • the valve seats are assigned flow cross sections of lines through which the fluid flow flows.
  • the valve elements can be positioned within the line.
  • Electromagnetic drives with electric motors are increasingly being used to adjust the valve elements.
  • the electromagnetic drive of a valve element usually has a rotor that is connected to the valve element via coupling elements, such as an actuating rod.
  • the electromagnetic drive can be arranged outside the housing of the valve, which requires complex sealing in the area of the housing opening and leads to high energy consumption. This is particularly due to the fact that high frictional forces that result from the sealing between the actuating rod and the housing opening must be overcome.
  • DE 10 2017 208 134 Ai discloses such a pump valve arrangement in which the valve member is driven by the motor of the pump in order to position the valve member.
  • the disadvantage of the solution in DE 10 2017 208 134 Ai has been It has been found that a complex structure within the pump valve assembly is required to move the valve member. This includes different components, each of which can wear out and/or become damaged individually. In addition, the additional components increase the assembly effort and the cost of the pump valve assembly.
  • An object of the present invention is to overcome the disadvantages of the known prior art, in particular to provide a cost-effective pump valve arrangement with a simpler structure.
  • a pump valve arrangement comprising a pump and a valve in a common housing.
  • the pump valve arrangement according to the invention can be used, for example, in motor vehicles, in particular in the motor vehicle engine area and/or in the motor vehicle battery area in electric motor-driven motor vehicles, for their thermal management, that is, for example, for distributing, mixing, shutting off and the like of fluid flows, such as coolant flows.
  • the pump valve arrangement in a common housing comprises a pump with a pump wheel for generating a pump flow; a valve for at least partially opening and/or blocking at least two pressure outlets that lead from the common housing, which is supplied with the flow medium from at least one common inlet; and an intermediate control element arranged between the housing and the pump wheel, which is assigned to the pressure outlets in such a way that it can at least partially open/block them.
  • the intermediate control valve element comprises a first operating state in which it is stationary relative to the pump wheel to form the pump flow, and a second operating state in which it rotates together with the pump wheel in the opposite direction to the pump wheel rotation in order to force a valve control movement.
  • the pressure outlets and the common inlet of the pump valve arrangement can open into a common housing interior or valve chamber or pump chamber, which is delimited or formed by the common housing.
  • a fluid inlet nozzle and/or fluid outlet nozzle can be connected to the inlet and/or the multiple pressure outlets for coupling to a line system.
  • the fluid can flow into the common housing via the fluid inlet nozzle or the inlet. and the fluid can leave the common housing again via the fluid outlet nozzles.
  • the valve or the intermediate control valve member can be used to at least partially open and/or close the individual pressure outlets.
  • Partial opening and/or closing means that a pressure outlet can be fully opened, in other words 100% open or 100% flow is possible, and fully closed, in other words 0% open or 0% flow is possible, but any intermediate position between 0% and 100%, in other words a flow between 0 and 100%, can also be set.
  • the impeller and the intermediate control valve member can be arranged inside the housing. The impeller can rotate to generate the impeller flow and set the process fluid in motion through the rotation.
  • the intermediate control valve member can, in the first operating state, direct the fluid flow or pump flow generated by the pump with the aid of the pump wheel from the common inlet to a desired pressure outlet.
  • the fluid flow or pump flow from the common inlet is divided into two or more pressure outlets by the intermediate control valve member.
  • the pump wheel In the first operating state, the pump wheel is driven and rotated by a pump drive or pump motor, so that a pump flow is generated.
  • the intermediate control valve member is fixed or stationary in the first operating state. This means that in the first operating state, the intermediate control valve member essentially does not move in the longitudinal direction of the valve arrangement and does not rotate about the longitudinal axis of the pump valve arrangement or the axis of rotation of the pump wheel.
  • the pump flow or fluid flow can be changed accordingly by moving the intermediate control valve member and the fluid can be directed to one or more other pressure outlets.
  • the intermediate control valve member can be rotatable about a rotation axis until the intermediate control valve member has reached a desired valve position.
  • the rotation axis of the intermediate control valve member is oriented in particular coaxially to a rotation axis of the pump wheel.
  • the rotation axis of the intermediate control valve member and/or the pump wheel can define a longitudinal direction of the pump valve arrangement.
  • the intermediate control valve member thus rotates together with the pump wheel.
  • the pump wheel and the intermediate control valve member can rotate at the same speed.
  • the pump wheel and the intermediate control valve member can in particular be arranged on a common shaft and/or connected to a common shaft.
  • the intermediate control valve member is driven by the pump drive or pump motor.
  • the pump wheel thus rotates in the first and second operating states, while the intermediate control valve member only rotates in the second operating state and is fixed or stationary in the first operating state.
  • a separate actuator for the intermediate control valve element is not required.
  • the pump valve arrangement can be driven by the pump motor. This saves weight through additional components (actuator, motor, etc.) and also saves costs.
  • An electrical connection to the separate servomotor can also be omitted, which makes integration into the overall system, for example the motor vehicle, easier on the assembly side and/or on the software side.
  • a control address for the servomotor that is not required can be omitted in a control system for the overall system.
  • the installation space is optimized by integrating the valve into the pump housing.
  • the size of the pump valve arrangement can be adapted to specific customer applications.
  • the housing i.e. the pump head
  • the pump valve arrangement can be provided without a housing.
  • a housing can be dispensed with.
  • the intermediate control valve member can have a base region and a circumferential wall in the radial and axial direction. At least one fluid passage opening can be formed in the radial circumferential wall, which transports the flow medium into the pump via the at least one inlet and out of the pump via a valve outlet.
  • the intermediate control valve member is designed as a single component and has a spiral geometry.
  • the spiral geometry is designed as a fluid channel and corresponds to a recess in a wall area of the circumferential wall of the intermediate control valve member.
  • the recess in the wall area can be rotated to an opening of a pressure outlet in order to open and close a pressure outlet.
  • the pressure outlet can be fully open if the recess on the intermediate control valve member completely covers the opening or only partially open if the recess on the Intermediate control valve member only partially covers the opening. If the recess is turned away from the opening or does not cover it, the corresponding pressure outlet is closed.
  • the spiral geometry in particular the fluid channel, runs at least partially, i.e.
  • the spiral geometry ensures the necessary geometry for conveying the flow medium through the pump with sufficient efficiency.
  • the spiral shape acts as a valve piston (spiral piston). Due to these advantages, the spiral geometry is not integrated in the housing (pump head), but is formed in the intermediate control valve member.
  • the pump wheel is accommodated in the intermediate control valve member.
  • This allows the available installation space to be used particularly well and, in particular, the length of the pump valve arrangement in the longitudinal direction can be reduced by arranging the pump wheel and the intermediate control valve member in a nested manner.
  • This also has the advantage that the pump wheel can convey the fluid directly into an inlet of the fluid geometry, which can be arranged at the same height as the pump wheel when viewed in the longitudinal direction.
  • the pump wheel and the intermediate control valve element are arranged on a common shaft in the housing.
  • the arrangement on a common shaft also allows the available installation space to be used particularly well, as no second shaft is required for the intermediate control valve element.
  • the base area and the surrounding wall of the intermediate control valve element can form a receiving space in which the pump wheel is accommodated.
  • the intermediate control valve member in particular with the pump wheel mounted thereon, is connected to the common shaft via a freewheel.
  • a receptacle for the shaft and the freewheel can be formed in the center of the base area of the intermediate control valve member.
  • the freewheel allows the intermediate control valve member and the pump wheel to be operated, adjusted or moved independently of one another.
  • the freewheel allows both operating states of the intermediate control valve member to be realized in a structurally simple manner, in which the freewheel allows movement in one direction of rotation and blocks it against the direction of rotation.
  • the freewheel can be made of plastic, for example.
  • the Freewheels are made of plastic material that is specifically adapted to a water-glycol application or is water-glycol resistant.
  • the plastic material can be adapted so that it has low water absorption.
  • the freewheel is advantageously designed as a bearing. This saves a separate component, as the freewheel can be used as a bearing.
  • the freewheel is preferably designed as a plain bearing and has a sleeve shape. However, any bearing known to the person skilled in the art can conceivably be used as a freewheel.
  • the freewheel can be rotated in one direction of pump wheel rotation and blocks against the direction of pump wheel rotation.
  • the freewheel can only rotate in one direction of pump wheel rotation. This allows the pump wheel to run freely in the "normal" direction of pump wheel rotation without rotating the intermediate control valve element. The freewheel of the intermediate control valve element blocks against this direction of rotation. The pump wheel and the intermediate control valve element are then rotated simultaneously.
  • the pump flow in at least one pressure output is controlled via the position of the intermediate control valve element.
  • a targeted control of a selected pressure output can thus be achieved.
  • the at least two pressure outlets are arranged radially on the common housing. This means that no axially arranged pressure outlets are formed on the housing. In customer applications without a housing, the at least two pressure outlets are formed in the customer housing.
  • the at least two pressure outlets are arranged tangentially to a housing interior.
  • the pressure outlets are also designed tangentially to the housing or to a radial outer side of the housing. In this way, a particularly low-pressure loss and efficient flow guidance can be realized.
  • a sealing element is arranged at each pressure outlet in the common housing.
  • the sealing element is preferably designed as an elastomer or made of a suitable material for seals known to those skilled in the art.
  • a thin layer of PTFE Teflon
  • the PTFE layer can provide improved sliding properties between the intermediate control valve member and the sealing element.
  • the PTFE layer can reduce the torque required to rotate the intermediate control valve member and/or improve the durability of the sealing element.
  • the sealing element has a circumferential sealing contour on a side facing the intermediate control valve member.
  • the sealing contour can be designed, for example, as a bead, sealing lip or other sealing shape.
  • the course of the sealing contour can be adapted to the opening in the wall of the intermediate control valve member and/or completely surround it. In this way, it can be ensured that the entire fluid flow can be directed to the desired pressure outlet without any leakage or pressure loss occurring.
  • the position of the intermediate control valve member is switched via a pump motor.
  • the motor that is used to operate the pump is also used for the intermediate control valve member.
  • the intermediate control valve member in the second operating state, can be connected to the pump motor and/or to the common shaft in a force-transmitting manner in order to enable rotation of the intermediate control valve member to position the intermediate control valve member.
  • a separate actuator and a separate shaft for the intermediate control valve member can be dispensed with, thus saving installation space, weight and/or costs.
  • assembly of the pump valve arrangement according to the invention is faster and less prone to errors due to the reduced number of components.
  • the pump motor is operated with a torque in the range between 0.4 and 0.6 Nm and/or with a speed in the range of 20 to 50 rpm to enable adjustment of the intermediate control valve element.
  • a torque in the range between 0.4 and 0.6 Nm and/or with a speed in the range of 20 to 50 rpm to enable adjustment of the intermediate control valve element.
  • the low speed also enables particularly precise positioning of the intermediate control valve element.
  • the pump motor can be operated in a much higher speed range, in particular with a speed in the range of 5000 to 7000 rpm, in order to generate the pump flow or to convey the fluid through the pump valve arrangement.
  • the current operating state of the intermediate control valve member is determined by means of at least one Hall sensor.
  • the Hall sensor can be attached to or on a circuit board or to the intermediate control valve member attached and connected to the circuit board.
  • the Hall sensor can also be arranged at another location in the pump or in the pump valve arrangement that is obvious to the person skilled in the art and is technically feasible.
  • Other position sensors known to the person skilled in the art are also possible.
  • a coil of the pump motor can be energized and the intermediate control valve element can be rotated in the opposite direction to the pump wheel rotation until the Hall sensor signals a desired switching position.
  • the pump wheel can then be driven in the pump wheel rotation direction by reversing the energization in order to generate the pump flow.
  • the intermediate control valve member is operatively connected to a gear, preferably a planetary gear.
  • a gear preferably a planetary gear.
  • This can have a drive wheel arranged coaxially to the pump shaft, which drives several planetary gears, which in turn drive a ring gear.
  • the ring gear can in particular be connected to the intermediate control valve member.
  • a pump comprises a rotor which is mounted on a shaft and a stator which is arranged around the rotor.
  • a pump can be used in a pump valve arrangement according to the aspect of the invention described above and/or according to the preceding exemplary and preferred embodiments.
  • the shaft of the pump can then in particular be the common shaft of the pump valve arrangement.
  • the intermediate control valve member has a particularly circumferential wall and a base that extends particularly perpendicular to the wall.
  • the base can in particular be connected to one end of the wall, so that the wall and the base are arranged perpendicular to each other in cross-section.
  • the wall of the intermediate control valve member can only be circumferential in some areas, in other words it can be interrupted in the circumferential direction at one or more points.
  • a completely circumferential wall offers the advantage that the wall and thus the intermediate control valve member is more stable, but an opening or an opening must be formed at one or more points on the circumferential wall in order to ensure the fluid conveyance.
  • the base of the intermediate control valve member can in particular have a constant wall thickness.
  • the base of the intermediate control valve member is arranged in a longitudinal direction of the pump valve arrangement between the pump wheel and a drive of the pump wheel.
  • the wall of the intermediate control valve member can then extend in particular away from the drive of the pump wheel. In this way, the drive can be sealed against the pump wheel or the pump flow.
  • the common inlet of the pump valve arrangement is arranged in the longitudinal direction opposite the drive of the pump wheel, such an arrangement of the base or such an orientation of the intermediate control valve member also results in increased efficiency of the pump valve arrangement because the incoming process fluid hits the pump wheel directly without having to flow past the base of the intermediate control valve member. In this way, turbulence in the process fluid can be prevented.
  • the flow path of the process fluid can be optimized and pressure losses reduced.
  • the intermediate control valve member in particular the wall of the intermediate control valve member, is arranged in the radial direction, perpendicular to the longitudinal direction of the pump valve arrangement, between the housing and the pump wheel.
  • the pump wheel is arranged within the circumferential wall of the intermediate control valve member, so that the installation space available within the common housing can be used particularly efficiently.
  • the intermediate control valve member is arranged in the longitudinal direction in a range between 50% and 150%, in particular between 60% and 130%, between 70% and 110%, between 80% and 90% or approximately 84% of a longitudinal extension of the pump wheel between the housing and the pump wheel.
  • at least half of a longitudinal extension of the pump wheel is accommodated in the intermediate valve member in that the wall of the intermediate control valve member is arranged between the pump wheel and the common housing over at least half of the longitudinal extension of the pump wheel.
  • the pump wheel is completely accommodated in the intermediate control valve member or that the wall of the intermediate control valve member even extends beyond the pump wheel in the longitudinal direction.
  • the pump wheel has a particularly conical recess on a side facing the pump drive for receiving the bearing, in particular the freewheel, of the intermediate control valve member.
  • the The intermediate control valve member or an inner region of the intermediate control valve member can be arranged in the recess of the pump wheel and thus within the pump wheel.
  • the pump wheel extends around a bearing point of the intermediate control valve member, at which additional material can be provided on the intermediate control valve. The further nesting allows the available installation space to be used even more efficiently.
  • the pump wheel is connected to the common shaft in a rotationally fixed manner.
  • the pump wheel is connected to the common shaft in a form-fitting manner and/or via a press fit. In this way, it is ensured in a cost-effective manner that the pump wheel can be reliably rotated together with the intermediate control valve member both in the direction of rotation of the pump wheel to generate the pump flow and against the direction of rotation of the pump wheel.
  • the intermediate control valve member is freely rotatable in relation to the common shaft in the first operating state and/or is connected to the common shaft in a force-transmitting manner in the second operating state.
  • the intermediate control valve member in the first operating state, is also freely rotatable in relation to the pump wheel. In the first operating state, the intermediate control valve member therefore remains stationary when the common shaft rotates and does not rotate with the common shaft, so that the pump flow can be directed to a desired pressure outlet.
  • the intermediate control valve member rotates together with the common shaft and thus together with the pump wheel due to the force-transmitting connection, so that the position of the intermediate control valve member can be changed.
  • the common inlet is arranged on a front side of the housing, in particular coaxially to the common shaft. In this way, the fluid hits the pump wheel centrally, so that a particularly uniform and efficient pump flow can be generated.
  • a sealing element is arranged between the intermediate control valve member and the common housing at at least one pressure outlet, in particular at all pressure outlets.
  • the current operating state of the intermediate control valve member is determined by means of at least one optical sensor.
  • the At least one optical sensor can be used alternatively or in addition to at least one Hall sensor.
  • Figure 1 an exploded view of an exemplary embodiment of a pump valve arrangement according to the invention
  • Figure 2 a perspective view of an exemplary embodiment of an intermediate control valve member according to the invention.
  • Figure 3 a sectional view of an exemplary embodiment of a pump valve arrangement according to the invention.
  • a pump valve arrangement according to the invention is generally provided with the reference numeral 1.
  • the pump valve arrangement 1 according to the invention is used, for example, in a motor vehicle for its thermal management and serves to distribute, mix, shut off and/or adjust fluid flows.
  • the pump valve arrangement 1 according to the invention comprises the following main components: a pump 3 for generating a pump flow and a valve 5 with an intermediate control valve member 7 for releasing and/or shutting off at least two pressure outlets 9 of the pump valve arrangement 1.
  • Fig. 1 shows an exploded view of an exemplary embodiment of a pump valve arrangement 1 according to the invention.
  • the pump valve arrangement 1 is arranged in a common housing 11 and comprises a pump 3 with a pump wheel 13 for generating a pump flow and a valve 5 for at least partially opening and/or blocking at least two pressure outlets 9.
  • the pump valve arrangement 1 also comprises an intermediate control valve member 7, which is assigned to the pressure outlets 9 in such a way that it can at least partially open and/or block them, wherein the intermediate control valve member 13 has a first operating state in which it is used to form the pump flow is stationary relative to the pump wheel 13, and a second operating state in which it rotates together with the pump wheel 13 in the opposite direction to the pump wheel rotation in order to force a valve adjustment movement.
  • the intermediate control valve member 7 is designed as a single component.
  • the pump wheel 13 is accommodated in the intermediate control valve member 7 and both are arranged on a common shaft 19 in the housing 11 and the intermediate control valve member 7 is connected to the common shaft 19 via a freewheel 21.
  • the freewheel 21 is designed as a bearing.
  • At least two pressure outlets 9 are arranged radially on the housing 11.
  • a sealing element 23 is arranged in the common housing 11 at each pressure outlet 9, in particular at all pressure outlets 9.
  • the sealing element 23 has a circumferential sealing contour 25 on a side facing the intermediate control valve member 7. The position of the intermediate control valve member 7 is switched via a pump motor 27.
  • the housing 11 has a circumferential wall 12 on which four pressure outlets 9 are arranged radially to the common housing 11, the pressure outlets 9 being arranged at equal distances from one another in the circumferential direction.
  • the common pressure inlet 17 is formed in the middle of an end face 15 of the housing 11, which extends in the longitudinal direction L of the pump valve arrangement 1 and is arranged coaxially to the common shaft 19 (see in particular Figure 3).
  • the fluid flow or pump flow reaches the interior of the housing 11 and thus the interior of the pump valve arrangement 1 through the inlet 17.
  • the pressure inlet 17 and the pressure outlets 9 are designed as hollow, cylindrical pipe sections.
  • the course of the sealing element 23 and in particular of the sealing contour 25 is adapted to the shape of the openings 26 of the pressure outlets 9 and completely surrounds the openings 26.
  • a rib-shaped fastening projection 28 extending in the longitudinal direction L is formed on both sides of each opening 26 on an inner side of the circumferential housing wall 12 for each pressure outlet 9, between which the respective sealing element 23 can be inserted or to which the respective sealing element 23 can be fastened.
  • the housing 11 also has several radial projections 29 on the outside of the circumferential wall 12, which are also evenly distributed in the circumferential direction and are each arranged between two pressure outlets 9. Corresponding connecting flanges 33 are formed on a housing 31 of the pump motor 27.
  • the common housing 11 of the pump 3 and the valve 5 can then be screwed to the motor housing 31, for example using screws (not shown). However, it is also conceivable that the common housing 11 and the motor housing 31 are connected to other An electrical connection point 35 is also formed on the motor housing 31 in order to be able to supply the pump motor 27 with power and to control it.
  • Fig. 2 shows a perspective view of the intermediate control valve member 7.
  • the intermediate control valve member 7 is designed as a single component and has a spiral geometry, which is generally identified by the reference numeral 37.
  • the spiral geometry 37 is designed as a fluid channel 39 and corresponds to a recess 41 (see Figure 3) in a wall region 43 of the intermediate control valve member 7.
  • the fluid channel 39 runs at least partially, i.e. not completely, on the inside of the circumferential wall 43 and forms a spiral contour. This means that the cross-section of the fluid channel tapers from its opening, which corresponds to the recess 41 in the wall region 43, to its end region and therefore forms the geometric spiral shape.
  • the spiral geometry 37 ensures the necessary geometry for conveying the flow medium through the pump 3 with sufficient efficiency.
  • the spiral shape acts as a valve piston (spiral piston). Due to these advantages, the spiral geometry 37 is not integrated in the housing (pump head), as is often the case in the prior art, but is formed in the intermediate control valve member 7.
  • the intermediate control valve member 7 also has a base 45 in which several openings 47 are formed, via which pressure equalization can take place between the drive chamber of the pump motor 27 and the housing interior 51.
  • the pump wheel 13 is accommodated in the intermediate control valve member 7, which will be explained in more detail later with reference to Figure 3.
  • the base region 45 and the circumferential wall 43 of the intermediate control valve member 7 form a receiving space 57 in which the pump wheel 13 is accommodated.
  • a receptacle 53 for the shaft 19 and the freewheel 21 is formed in the center. The freewheel 21 allows the intermediate control valve member 7 and the pump wheel 13 to be operated, adjusted or moved independently of one another.
  • FIG. 3 shows an exemplary embodiment of a pump valve arrangement 1 according to the invention in a sectional view.
  • the flow fluid enters the housing 11 of the pump valve arrangement 1 through the inlet 17, which is indicated in Fig. 3 by the arrow with the reference number 49.
  • the flow fluid enters a housing interior or valve chamber or pump chamber delimited by the housing 11 through the inlet 17, which is marked with the reference number 51.
  • the flow fluid then exits the intermediate control valve member 7 through one or more of the pressure outlets 9 from the housing 11 and thus from the pump valve arrangement 1.
  • the pressure outlets 9 are arranged tangentially to the housing interior 51 in the embodiment in Figure 1 and in the embodiment in Figure 3.
  • the intermediate control valve member 7 is connected to the common shaft 19 via the freewheel 21.
  • the common shaft 19 is driven by the pump motor 27, which is shown in simplified form in the sectional view.
  • a bearing projection 53 in the form of a circumferential wall is formed in the middle of the intermediate control valve member 7, which extends from the base 45 of the intermediate control valve member 7 in the same direction as the wall 43 of the intermediate control valve member 7.
  • the freewheel 21 or a sleeve of the freewheel 21 is accommodated in the bearing projection 53 and connected to the intermediate control valve member 7 in terms of force transmission.
  • the freewheel 21 can have a structure that is basically known from the prior art, with an outer race of the freewheel 21 being formed by the sleeve of the freewheel 21 and an inner race being formed by the common shaft 19.
  • the freewheel sleeve and the common shaft 19 are connected via spring-loaded clamping bodies 54. Due to the geometric design of the clamping bodies 54, these slide over the common shaft 19 in the direction of rotation of the pump wheel, so that the shaft 19 can rotate freely in relation to the intermediate control valve member 7 when the shaft 19 rotates in the direction of rotation of the pump wheel.
  • the clamping bodies 54 position themselves through a slight twist and thus create a clamping effect between the common shaft 19 and the freewheel sleeve, so that the intermediate control valve member 7 is connected to the common shaft 19 in terms of force transmission and rotates together with the shaft 19 when the shaft 19 rotates against the direction of rotation of the pump wheel.
  • the pump wheel 13 is connected to the common shaft 19 in a rotationally fixed manner via an injected sleeve 55 and thus rotates together with the shaft 19 both when rotating in the pump wheel rotation direction and when rotating against the pump wheel rotation direction.
  • the pump wheel 13 for generating the pump flow is arranged in the housing interior 51.
  • the intermediate valve member 7 for adjusting the pump flow is also arranged in the housing interior 51.
  • the intermediate valve member 7 and the pump wheel 13 are nested in one another in a pump valve arrangement 1 according to the invention.
  • the circumferential wall 43 of the intermediate control valve member 7 is arranged in a radial direction R, perpendicular to the longitudinal direction L of the pump valve arrangement 1, between the housing 11 and the pump wheel 13.
  • the base 45 of the intermediate control valve member 7 is arranged in the longitudinal direction L between the pump wheel 13 and the pump motor 27 and the wall 43 of the intermediate control valve member 7 extends from the base 45 in the direction of the pump wheel 13 or in the direction of the inlet 17.
  • the pump drive 27 can be sealed against the pump wheel 13 or the pump flow.
  • such an arrangement of the base 45 results in increased efficiency of the pump valve arrangement 1 because the incoming process fluid hits the pump wheel 13 directly without having to flow past the base 45 of the intermediate control valve member 7. In this way, turbulence in the process fluid can be prevented.
  • the flow path of the process fluid can be optimized and pressure losses reduced.
  • the pump wheel 13 has a conical recess 57 in the middle, in which the bearing projection 53 of the intermediate control valve member 7 is accommodated, so that the pump wheel 13 and the intermediate control valve member 7 can be nested even further into one another or a larger part of a longitudinal extension of the pump wheel 13 is accommodated in the intermediate control valve member 7 and the available installation space can be better used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Multiple-Way Valves (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

La présente invention concerne un ensemble pompe-et-soupape dans un boîtier commun, comprenant une pompe dotée d'une roue de pompe pour produire un écoulement de pompe ; une soupape pour découvrir et/ou bloquer au moins partiellement au moins deux sorties de pression s'étendant hors du boîtier commun qui est alimenté avec le milieu d'écoulement provenant d'au moins une entrée commune ; et un élément de soupape de commande intermédiaire qui est disposé entre le boîtier et la roue de pompe et qui est associé aux sorties de pression de telle sorte que l'élément de soupape de commande intermédiaire puisse au moins partiellement ouvrir/bloquer les sorties de pression, l'élément de soupape de commande intermédiaire présentant un premier état de fonctionnement dans lequel, pour la formation de l'écoulement de pompe, il est fixe par rapport à la roue de pompe, et un second état de fonctionnement dans lequel il tourne conjointement avec la roue de pompe à l'encontre du sens de rotation de la roue de pompe afin de forcer un mouvement de commande de soupape.
EP24712170.0A 2023-03-08 2024-03-08 Ensemble pompe et soupape Pending EP4677231A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023105784.7A DE102023105784B4 (de) 2023-03-08 2023-03-08 Pumpenventilanordnung
PCT/EP2024/056230 WO2024184527A1 (fr) 2023-03-08 2024-03-08 Ensemble pompe et soupape

Publications (1)

Publication Number Publication Date
EP4677231A1 true EP4677231A1 (fr) 2026-01-14

Family

ID=90366106

Family Applications (1)

Application Number Title Priority Date Filing Date
EP24712170.0A Pending EP4677231A1 (fr) 2023-03-08 2024-03-08 Ensemble pompe et soupape

Country Status (4)

Country Link
EP (1) EP4677231A1 (fr)
CN (1) CN120187955A (fr)
DE (1) DE102023105784B4 (fr)
WO (1) WO2024184527A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4474650B1 (fr) 2023-06-09 2026-03-25 Illinois Tool Works Inc. Pompe à vis et ses composants
US12533995B2 (en) 2023-08-31 2026-01-27 Illinois Tool Works Inc. Battery electric vehicle temperature-regulation system

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3006386C2 (de) * 1980-02-21 1985-10-17 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG, 7000 Stuttgart Drehzahlabhängig steuerbares Rotations-Ventil
DE3317155C1 (de) * 1983-05-11 1984-09-06 Ford-Werke AG, 5000 Köln Scheibenwaschanlage eines Fahrzeuges
DE10133130A1 (de) 2001-07-07 2003-01-16 Miele & Cie Umwälzpumpe mit/ohne Heizungseinrichtung
EP1353072B1 (fr) 2002-04-09 2005-06-29 Kautex Textron GmbH & Co. KG. Pompe de lavage
DE102006034960B4 (de) 2006-07-28 2008-05-15 Audi Ag Kühlmittelpumpe für einen Kühlkreislauf einer Verbrennungskraftmaschine
DE102011090208A1 (de) 2011-12-30 2013-07-04 Dr. Ing. H.C. F. Porsche Ag Wasserpumpe
GB201307257D0 (en) 2013-04-22 2013-05-29 Flowork Systems Ii Llc Conrollable variable flow coolant pump and flow management mechanism
DE102015106639A1 (de) 2015-04-29 2016-11-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pumpe
EP3376050B1 (fr) * 2017-03-14 2026-01-21 Grundfos Holding A/S Groupe pompe centrifuge
DE102017208134B4 (de) 2017-05-15 2022-07-07 Hanon Systems Efp Deutschland Gmbh Fördereinrichtung
DE102019202975A1 (de) * 2019-03-05 2020-09-10 Hanon Systems Efp Deutschland Gmbh Elektrisch angetriebene Fluidmaschine

Also Published As

Publication number Publication date
DE102023105784B4 (de) 2024-10-31
WO2024184527A1 (fr) 2024-09-12
DE102023105784A1 (de) 2024-09-12
CN120187955A (zh) 2025-06-20

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