Pump-and-valve assembly
Patent Information
- Application Number
- EP2024712170
- Authority / Receiving Office
- EP · EP
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2023-03-08
- Filing Date
- 2024-03-08
- Publication Date
- 2026-01-14
Smart Images
Figure EP2024056230_12092024_PF_FP_ABST
Abstract
Description
[0001] Pump valve arrangement
[0002] 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.
[0003] To regulate fluid flow in a fluid circuit, it is known to use valve elements that cooperate with valve seats. Flow cross-sections of lines through which the fluid flow flows are assigned to the valve seats. To at least partially open or close the flow cross-sections, the valve elements can be positioned within the line. Electromagnetic drives with electric motors are increasingly being used to position 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 valve housing, 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 must be overcome, which result from the sealing between the actuating rod and the housing opening.
[0004] To solve these problems, it is already known in the prior art to arrange the electric drive of the valve within the housing or to use the electromagnetic drive of the pump connected to the valve as the drive for the valve member. DE 10 2017 208 134 Ai discloses such a pump valve arrangement in which the valve member is driven by the pump motor in order to position the valve member. However, it has been found that the solution in DE 10 2017 208 134 Ai requires a complex structure within the pump valve arrangement to move the valve member. This structure comprises different components, each of which can wear out and / or be damaged individually. In addition, the additional components increase the assembly effort and the cost of the pump valve arrangement.
[0005] 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.
[0006] This problem is solved by the subject matter of claim i.
[0007] According to this, a pump valve assembly comprising a pump and a valve in a common housing is provided. The pump valve assembly according to the invention can be used, for example, in motor vehicles, in particular in the motor vehicle engine sector and / or in the motor vehicle battery sector in electric motor-driven motor vehicles, for their thermal management, i.e., for example, for distributing, mixing, shutting off, and the like, fluid flows, such as coolant flows.
[0008] The pump valve arrangement in a common housing comprises a pump with an impeller for generating a pump flow; a valve for at least partially opening and / or blocking at least two pressure outlets leading 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 impeller, 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 has a first operating state in which it is stationary relative to the impeller to generate the pump flow, and a second operating state in which it rotates together with the impeller in the opposite direction to the impeller's direction of rotation to force a valve actuating movement.
[0009] The pressure outputs 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 for coupling to a line system can be connected to the inlet and / or the multiple pressure outputs. The fluid can enter 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. For this purpose, the individual pressure outputs can each be at least partially opened and / or closed using the valve or the intermediate control valve element. Partial opening and / or closing means that a pressure output can be fully opened, in other words 100% open or 100% closed.100% flow is possible and can be completely closed, in other words it can be opened 0% or 0% flow is possible, but any intermediate position between 0% and 100%, in other words a flow rate between 0 and 100%, can also be set. This makes it possible to specifically respond to the needs and requirements in thermal management. The impeller and the intermediate control valve member can be arranged in the interior of the housing. The impeller can rotate to generate the impeller flow and set the process fluid in motion through the rotation. In the pump valve arrangement according to the invention, the intermediate control valve member can direct the fluid flow or pump flow generated by the pump with the aid of the impeller from the common inlet to a desired pressure outlet in the first operating state. It is also conceivable that the fluid flow or pump flow is directed through the intermediate control valve member.Pump flow from the common inlet is divided into two or more pressure outlets. In the first operating state, the pump impeller 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 also does not rotate about the longitudinal axis of the pump valve arrangement or the axis of rotation of the pump impeller. In the second operating state of the intermediate control valve member, 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.For this purpose, the intermediate control valve member can be rotatable about a rotational axis until the intermediate control valve member has reached a desired valve position. The rotational axis of the intermediate control valve member is oriented in particular coaxially to a rotational axis of the impeller. The rotational axis of the intermediate control valve member and / or the impeller can define a longitudinal direction of the pump valve arrangement. In the second operating state, the intermediate control valve member thus rotates together with the impeller. In particular, the impeller and the intermediate control valve member can rotate at the same speed. For this purpose, the impeller and the intermediate control valve member can in particular be arranged on a common shaft and / or connected to a common shaft. In particular, the intermediate control valve member can be driven by the pump drive or pump motor in the second operating state.In the pump valve arrangement according to the invention, the pump wheel thus rotates in the first and second operating states, while the intermediate control valve member rotates only in the second operating state and is fixed or stationary in the first operating state.
[0010] By accommodating the pump valve assembly in the common housing or by accommodating the valve in the pump housing, a separate actuator (electric servomotor) for the intermediate control valve element is no longer necessary. The pump valve assembly can be driven by the pump motor. This saves weight due to additional components (actuator, motor, etc.) and also reduces costs. An electrical connection for the separate servomotor can also be omitted, which simplifies integration into the overall system, e.g. the vehicle, both on the assembly and / or software side. In particular, a control address for the unnecessary servomotor can be omitted in a control system for the overall system. Furthermore, by integrating the valve into the pump housing, the installation space is optimized. The size of the pump valve assembly can be adapted to specific customer applications.
[0011] Alternatively, for specific customer applications, the housing, i.e., the pump head, can already be included in the application, allowing the pump valve assembly to be provided without a housing. In this case, a housing is virtually unnecessary.
[0012] The intermediate control valve member may have a base region and a circumferential wall extending radially and axially. At least one fluid passage opening may be formed in the radially 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.
[0013] It is advantageous that the intermediate control valve member is designed as a single component and has a spiral geometry. In one exemplary development, the spiral geometry is designed as a fluid channel and corresponds to a recess in a wall region of the circumferential wall of the intermediate control valve member. The recess in the wall region can be rotated to align with 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 rotated 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. not entirely, along an inner side of the circumferential wall and forms a spiral contour. This means that the cross-section of the fluid channel tapers from its opening, which corresponds to the recess in the wall area, to its end area and therefore forms the geometric spiral shape. The advantage is that the spiral geometry, on the one hand, ensures the necessary geometry for conveying the flow medium through the pump with sufficient efficiency. On the other hand, 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 formed in the intermediate control valve element.
[0014] In a further development, the pump impeller is accommodated in the intermediate control valve element. This allows for particularly effective use of the available installation space and, in particular, a reduction in the longitudinal length of the pump valve arrangement by nesting the pump impeller and the intermediate control valve element. This also has the advantage that the pump impeller can deliver the fluid directly into an inlet of the fluid geometry, which, viewed longitudinally, can be arranged at the same height as the pump impeller.
[0015] Alternatively or additionally, the pump impeller and the intermediate control valve element are arranged on a common shaft in the housing. This arrangement on a common shaft also allows for particularly efficient use of the available installation space, 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 impeller is housed.
[0016] It is also advantageous that 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 region 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 makes it possible to implement both operating states of the intermediate control valve member in a structurally simple manner, with the freewheel allowing movement in one direction of rotation and blocking movement against the direction of rotation. The freewheel can be made of plastic, for example. In particular, the freewheel can be made of a plastic material that is specifically adapted to a water-glycol application or is water-glycol resistant.For example, the plastic material can be adapted so that it has low water absorption.
[0017] The freewheel is advantageously designed as a bearing. This eliminates the need for 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 those skilled in the art could conceivably be used as a freewheel.
[0018] In a further embodiment, the freewheel can rotate in one direction of impeller rotation and blocks against the impeller rotation. In other words, the freewheel can only rotate in one direction of impeller rotation. This allows the impeller to rotate freely in the "normal" impeller rotation direction without rotating the intermediate control valve element. If the freewheel of the intermediate control valve element blocks against this direction of rotation, the impeller and the intermediate control valve element are then rotated simultaneously.
[0019] It can be provided that the pump flow into at least one pressure output is controlled via the position of the intermediate control valve element. This allows for targeted control of a selected pressure output.
[0020] Another advantage is that the at least two pressure outlets are arranged radially on the common housing. This eliminates the need for axially arranged pressure outlets on the housing. For customer applications without a housing, the at least two pressure outlets are located in the customer housing.
[0021] In an exemplary embodiment, the at least two pressure outlets are arranged tangentially to a housing interior. In particular, the pressure outlets are also designed tangentially to the housing or to a radial outer side of the housing. This allows for a particularly low-pressure-loss and efficient flow guidance.
[0022] In a further development, a sealing element is arranged at each pressure outlet in the common housing. The sealing element is preferably formed as an elastomer or made of a suitable sealing material known to those skilled in the art. A thin layer of PTFE (Teflon) can be applied, in particular vulcanized, to the elastomer. The PTFE layer can achieve improved sliding properties between the intermediate control valve member and the sealing element. Furthermore, the PTFE layer can reduce the torque required to rotate the intermediate control valve member and / or improve the durability of the sealing element.
[0023] In a further embodiment, 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 shape of the sealing contour can be adapted to the opening in the wall of the intermediate control valve member and / or completely surround it. This ensures that the entire fluid flow can be directed to the desired pressure outlet without any risk of leakage or pressure loss.
[0024] Preferably, the position of the intermediate control valve member is switched via a pump motor. Instead of a separate actuator for switching the valve positions, the motor used to operate the pump is also used for the intermediate control valve member. In other words, in the second operating state, the intermediate control valve member can be connected to the pump motor and / or to the common shaft for power transmission in order to enable rotation of the intermediate control valve member to position the intermediate control valve member. In this way, a separate actuator and a separate shaft for the intermediate control valve member can be dispensed with, thus saving space, weight, and / or costs. At the same time, assembly of the pump valve arrangement according to the invention is faster and less prone to errors due to the reduced number of components.
[0025] In an exemplary further development, the pump motor is operated with a torque in the range between 0.4 and 0.6 Nm and / or at a speed in the range of 20 to 50 rpm to enable adjustment of the intermediate control valve element. In this range with a low speed and high torque, adjustment of the intermediate control valve element is reliably possible. The low speed also enables particularly precise adjustment of the intermediate control valve element. In contrast, to rotate the pump impeller, the pump motor can be operated in a much higher speed range, in particular at 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.
[0026] In a further embodiment, 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 attached to the intermediate control valve member and connected to the circuit board. However, the Hall sensor can also be arranged at another location in the pump or in the pump valve arrangement that is obvious to a person skilled in the art and is technically feasible. Other position sensors known to a person skilled in the art are also possible. To position the intermediate control valve member, for example, a coil of the pump motor can be energized and the intermediate control valve member can thus be rotated against the direction of rotation of the pump impeller until the Hall sensor signals a desired switching position. Subsequently, by reversing the energization, the pump impeller can be driven in the direction of rotation of the pump impeller in order to generate the pump flow.
[0027] It can further be provided that the intermediate control valve member is operatively connected to a gear, preferably a planetary gear. This gear can have a drive wheel arranged coaxially with 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.
[0028] Alternatively, the intermediate control valve element can also be operated without a gearbox. This simplifies the modular design, manufacturing, and sealing concept of the pump valve assembly.
[0029] According to the invention, a pump comprises a rotor mounted on a shaft and a stator arranged around the rotor. Such a pump can be used in a pump-valve assembly according to the previously described aspect of the invention and / or according to the preceding exemplary and preferred embodiments. The pump shaft can then, in particular, be the common shaft of the pump-valve assembly.
[0030] In an exemplary embodiment, the intermediate control valve member has a circumferential wall and a base extending perpendicular to the wall. The base can in particular adjoin one end of the wall, so that the wall and the base are arranged perpendicular to one another in cross-section. The wall of the intermediate control valve member can be circumferential only in certain regions, in other words can be interrupted at one or more points in the circumferential direction. A completely circumferential wall offers the advantage that the wall and thus the intermediate control valve member is more stable, but an opening or aperture must be formed at one or more points on the circumferential wall to ensure fluid delivery. The base of the intermediate control valve member can in particular have a constant wall thickness.In an exemplary development, the base of the intermediate control valve member is arranged in a longitudinal direction of the pump valve arrangement between the impeller and a drive of the impeller. The wall of the intermediate control valve member can then extend in particular away from the drive of the impeller. In this way, the drive can be sealed against the impeller or the pump flow. If the common inlet of the pump valve arrangement is arranged in the longitudinal direction opposite the drive of the impeller, 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 strikes the impeller 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.In addition, the flow path of the process fluid can be optimized and pressure losses reduced.
[0031] In a further exemplary embodiment, 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 impeller. In other words, the impeller is arranged within the circumferential wall of the intermediate control valve member, so that the installation space available within the shared housing can be used particularly efficiently.
[0032] In an exemplary development, 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 extent of the impeller between the housing and the impeller. In other words, at least half of a longitudinal extent of the impeller is accommodated in the intermediate valve member in that the wall of the intermediate control valve member is arranged between the impeller and the common housing over at least half of the longitudinal extent of the impeller. It can also be provided that the impeller is completely accommodated in the intermediate control valve member or that the wall of the intermediate control valve member even extends beyond the impeller in the longitudinal direction.
[0033] According to an exemplary embodiment, the impeller has, on a side facing the pump drive, a particularly conical recess for accommodating the bearing, in particular the freewheel, of the intermediate control valve member. In other words, in a central region around the common shaft, the intermediate control valve member or an inner region of the intermediate control valve member can be arranged in the recess of the impeller and thus within the impeller. In other words, the impeller 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.
[0034] According to another exemplary embodiment, the impeller is connected to the common shaft in a rotationally fixed manner. In particular, the impeller is connected to the common shaft in a form-fitting manner and / or via a press fit. This ensures, at low cost, that the impeller can be reliably rotated together with the intermediate control valve element both in the impeller's direction of rotation to generate the pump flow and in the opposite direction to the impeller's direction of rotation.
[0035] In a further exemplary embodiment, the intermediate control valve member is freely rotatable with respect 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. In particular, in the first operating state, the intermediate control valve member is also freely rotatable with respect to the pump impeller. In the first operating state, the intermediate control valve member therefore remains fixed or 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. In the second operating state, the intermediate control valve member rotates together with the common shaft and thus together with the pump impeller due to the force-transmitting connection, so that the position of the intermediate control valve member can be changed.
[0036] According to another exemplary embodiment, the common inlet is arranged on one end face of the housing, in particular coaxially with the common shaft. In this way, the fluid impinges centrally on the impeller, allowing a particularly uniform and efficient pump flow to be generated.
[0037] In an exemplary embodiment, 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.
[0038] In a further exemplary embodiment, 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.
[0039] Preferred embodiments are specified in the dependent claims.
[0040] In the following, further properties, features and advantages of the invention will become clear by describing preferred embodiments of the invention with reference to the accompanying exemplary drawings, in which:
[0041] Figure 1: an exploded view of an exemplary embodiment of a pump valve arrangement according to the invention;
[0042] Figure 2: a perspective view of an exemplary embodiment of an intermediate control valve member according to the invention; and
[0043] Figure 3: a sectional view of an exemplary embodiment of a pump valve arrangement according to the invention.
[0044] In the following description of exemplary embodiments of pump valve arrangements according to the invention with reference to the accompanying figures, a pump valve arrangement according to the invention is generally provided with the reference number 1.
[0045] The pump valve assembly 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 regulate fluid flows. The pump valve assembly 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 opening and / or shutting off at least two pressure outlets 9 of the pump valve assembly 1.
[0046] 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 an impeller 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 stationary relative to the impeller 13 to generate the pump flow, and a second operating state in which it rotates together with the impeller 13 opposite to the impeller rotation direction in order to force a valve actuating 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 at each pressure outlet 9, in particular at all pressure outlets 9, in the common housing 11. 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.
[0047] In the embodiment in Fig. 1, the housing 11 has a circumferential wall 12 on which four pressure outlets 9 are arranged radially to the common housing 11, wherein the pressure outlets 9 are arranged at equal distances from one another in the circumferential direction. The common pressure inlet 17 is formed centrally on an end face 15 of the housing 11 and 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.For fastening the sealing elements 23 in the housing 11, a rib-shaped fastening projection 28 extending in the longitudinal direction L is formed on an inner side of the circumferential housing wall 12 for each pressure outlet 9 on both sides of each opening 26, between which the respective sealing element 23 can be inserted or to which the respective sealing element 23 can be fastened.
[0048] The housing 11 also has a plurality of radial projections 29 on the outer side 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 to connect the common housing 11 and the motor housing 31 in another way. An electrical connection point 35 is also formed on the motor housing 31 in order to supply the pump motor 27 with power and to be able to control it.
[0049] 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 designated 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 entirely, 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. It is advantageous that the spiral geometry 37, on the one hand, ensures the necessary geometry for conveying the flow medium through the pump 3 with sufficient efficiency.Secondly, the spiral shape acts as a valve piston (spiral piston). Due to these advantages, the spiral geometry 37 is not integrated into the housing (pump head), as is often the case in the prior art, but rather 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, through which pressure equalization can take place between the drive chamber of the pump motor 27 and the housing interior 51.
[0050] The pump impeller 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 impeller 13 is accommodated. A receptacle 53 for the shaft 19 and the freewheel 21 is formed in the center of the base region 45 of the intermediate control valve member 7. The freewheel 21 allows the intermediate control valve member 7 and the pump impeller 13 to be operated, adjusted, or moved independently of one another.
[0051] Figure 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 numeral 49. Through the inlet 17, the flow fluid reaches a housing interior or valve chamber or pump chamber delimited by the housing 11, which is designated by the reference numeral 51. Depending on the position of the intermediate control valve member 7, the flow fluid then exits the housing 11 and thus the pump valve arrangement 1 through one or more of the pressure outlets 9. The pressure outlets 9 are each arranged tangentially to the housing interior 51 in the embodiment in Figure 1 and in the embodiment in Figure 3.In Figure 3, the intermediate control valve member 7 is rotated such that the left pressure outlet 9a in Figure 3 is completely closed and the right pressure outlet 9b is opened, so that the flow medium exits the pump valve arrangement 1 again through the pressure outlet 9b, which is indicated in Figure 3 by the arrow with the reference number 50.
[0052] The sectional view also shows that 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. To accommodate the freewheel 21, a bearing projection 53 in the form of a circumferential wall is formed centrally on the intermediate control valve member 7, which wall 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 received in the bearing projection 53 and connected to the intermediate control valve member 7 for force transmission. The freewheel 21 can have a structure known in principle 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, they slide over the common shaft 19 in the direction of pump impeller rotation, so that the shaft 19 can rotate freely with respect to the intermediate control valve member 7 when the shaft 19 rotates in the direction of pump impeller rotation. When the common shaft 19 rotates counter to the direction of pump impeller rotation, 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 for force transmission and rotates together with the shaft 19 when the shaft 19 rotates counter to the direction of pump impeller rotation.The pump impeller 13 is connected to the common shaft 19 in a rotationally fixed manner via an injection-molded sleeve 55 and thus rotates together with the shaft 19 both when rotating in the pump impeller's direction of rotation and when rotating counter to the pump impeller's direction of rotation. This allows both operating states of the intermediate control valve member 7 to be easily realized. The pump impeller 13 for generating the pump flow is arranged in the housing interior 51. The intermediate control valve member 7 for adjusting the pump flow is also arranged in the housing interior 51. In order to be able to better utilize the installation space available in the housing interior 51, the intermediate control valve member 7 and the pump impeller 13 are nested within one another in a pump valve arrangement 1 according to the invention.
[0053] Firstly, 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 impeller 13. The base 45 of the intermediate control valve member 7 is arranged in the longitudinal direction L between the impeller 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 impeller 13 or in the direction of the inlet 17. In this way, the pump drive 27 can be sealed off from the impeller 13 or the pump flow. In addition, in the embodiment in Figure 3, such an arrangement of the base 45 results in increased efficiency of the pump valve arrangement 1 because the incoming process fluid strikes the impeller 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.In addition, the flow path of the process fluid can be optimized and pressure losses reduced.
[0054] On the other hand, the pump wheel 13 has a conical recess 57 in the center, in which the bearing projection 53 of the intermediate control valve member 7 is received, 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 received in the intermediate control valve member 7 and the available installation space can be better utilized.
[0055] The features disclosed in the above description, the figures, and the claims may be important both individually and in any combination for the realization of the invention in its various embodiments. List of reference symbols
[0056] 1 pump valve arrangement
[0057] 3 Pump
[0058] 5 Valve
[0059] 7 Intermediate control valve element
[0060] 9, 9a, 9b Pressure outlet ii Housing
[0061] 12 Housing wall
[0062] 13 Pump wheel
[0063] 15 Housing front side
[0064] 17 shared entrance
[0065] 19 common wave
[0066] 21 Freewheel
[0067] 23 Sealing element
[0068] 25 Sealing contour
[0069] 26 Opening
[0070] 27 Pump motor
[0071] 28 Mounting projection
[0072] 29 Radial projection
[0073] 31 Engine housing
[0074] 33 Mounting flange
[0075] 35 electrical connection point
[0076] 37 Spiral geometry
[0077] 39 Fluid channel
[0078] 41 recess
[0079] 43 Wall
[0080] 45 Floor
[0081] 47 Opening 49 Inlet flow
[0082] 50 Outlet flow
[0083] 51 Housing interior
[0084] 53 Bearing projection
[0085] 54 clamping bodies
[0086] 55 sleeve
[0087] 57 Recording Room
[0088] L longitudinal direction
[0089] R Radial direction
Claims
Claims 1. A pump valve arrangement (1) in a common housing(s), comprising a pump (3) with a pump impeller (13) for generating a pump flow; a valve (5) for at least partially opening and / or blocking at least two pressure outlets (9) leading from the common housing (11), which is supplied with the flow medium from at least one common inlet (17); and an intermediate control valve member (7) arranged between the housing (11) and the pump impeller (13), which is assigned to the pressure outlets (9) in such a way that it can at least partially open / block them, wherein the intermediate control valve member (7) has a first operating state in which it is stationary relative to the pump impeller (13) to generate the pump flow, and a second operating state in which it rotates together with the pump impeller (13) opposite to the pump impeller's direction of rotation to force a valve actuating movement.
2. Pump valve arrangement (1) according to claim 1, wherein the intermediate control valve member (7) is designed as a single component and has a spiral geometry (37).
3. Pump valve arrangement (1) according to claim 2, wherein the spiral geometry (37) is designed as a fluid channel (39) and corresponds to a recess (41) in a wall region (43) of the intermediate control valve member (7).
4. Pump valve arrangement (1) according to claim 1, 2 or 3, wherein the pump wheel (13) is accommodated in the intermediate control valve member (7).
5. Pump valve arrangement (1) according to one of the preceding claims, wherein the pump wheel (13) and the intermediate control valve member (7) are arranged on a common shaft (19) in the housing (11).
6. Pump valve arrangement (1) according to claim 5, wherein the intermediate control valve member (7), in particular with the received pump wheel (13), is connected to the common shaft (19) via a freewheel (21).
7. Pump valve arrangement (1) according to claim 6, wherein the freewheel (21) is designed as a bearing, in particular as a plain bearing bush.
8. Pump valve arrangement (1) according to claim 6 or 7, wherein the freewheel (21) is rotatable in a pump wheel rotation direction and blocks against the pump wheel rotation direction.
9. Pump valve arrangement (1) according to one of the preceding claims, wherein the pump flow into at least one pressure outlet (9) is controlled via the position of the intermediate control valve member (7).
10. Pump valve arrangement (1) according to one of the preceding claims, wherein the at least two pressure outlets (9) are arranged radially on the common housing (11).
11. Pump valve arrangement (1) according to claim 10, wherein the at least two pressure outlets (9) are arranged tangentially to a housing interior (51).
12. Pump valve arrangement (1) according to one of the preceding claims, wherein a sealing element (23) is arranged in the common housing (11) at each pressure outlet (9), in particular at all pressure outlets (9).
13. Pump valve arrangement (1) according to claim 12, wherein the sealing element (23) has a circumferential sealing contour (25) on a side facing the intermediate control valve member (7).
14. Pump valve arrangement (1) according to one of the preceding claims, wherein the position of the intermediate control valve member (7) is switched via a pump motor (27).
15. Pump valve arrangement (1) according to claim 14, wherein the pump motor (27) 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 member.
16. Pump valve arrangement (1) according to one of the preceding claims, wherein the current operating state of the intermediate control valve member (7) is determined by means of at least one Hall sensor.
17. Pump valve arrangement (1) according to one of the preceding claims, wherein the intermediate control valve member (7) is operatively connected to a gear, preferably a planetary gear.
18. Pump valve arrangement (1) according to one of the preceding claims, wherein the intermediate control valve member (7) has a particularly circumferential wall (43) and a base (45) extending particularly perpendicular to the wall (43).
19. Pump valve arrangement (1) according to claim 18, wherein the bottom (45) of the intermediate control valve member (7) in a longitudinal direction (L) of the pump valve arrangement (1) is arranged between the pump wheel (13) and a drive (27) of the pump wheel (13).
20. Pump valve arrangement (1) according to one of the preceding claims, wherein the intermediate control valve member (7), in particular the wall (43) of the intermediate control valve member (7), is arranged in the radial direction (R), perpendicular to the longitudinal direction (L) of the pump valve arrangement (1), between the housing (11) and the pump wheel (13).
21. Pump valve arrangement (1) according to claim 20, wherein the intermediate control valve member (7) is arranged in the longitudinal direction (L) in a region between 50% and 150% of a longitudinal extent of the pump wheel (13) between the housing (11) and the pump wheel (13).
22. Pump valve arrangement (1) according to one of the preceding claims, wherein the pump wheel (13) has, on a side facing the pump drive (27), a particularly conical recess (55) for receiving the bearing, in particular the freewheel (21), of the intermediate control valve member (7).
23. Pump valve arrangement (1) according to one of claims 4 to 22, wherein the pump wheel (13) is connected in a rotationally fixed manner to the common shaft (19), in particular in a form-fitting manner and / or via a press fit.
24. Pump valve arrangement (1) according to one of claims 4 to 23, wherein the intermediate control valve member (7) is freely rotatable with respect to the common shaft (19) in the first operating state and / or is connected to the common shaft (19) in a force-transmitting manner in the second operating state.
25. Pump valve arrangement (1) according to one of the preceding claims, wherein the common inlet (17) is arranged on an end face of the housing (11), in particular coaxially to the common shaft (19).
26. Pump valve arrangement (1) according to one of the preceding claims, wherein at least one pressure outlet (9), in particular at all pressure outlets (9), a sealing element (23) is arranged between the intermediate control valve member (7) and the common housing (11).
27. Pump valve arrangement (1) according to one of the preceding claims, wherein the current operating state of the intermediate control valve member (7) is determined by means of at least one optical sensor.