Hydraulic converter

Abstract

The present invention relates to a high-speed hydraulic regulating converter, which has a working space for constructing a circulation of a hydraulic working medium, wherein at least one pump wheel, at least one turbine and at least one guide wheel are positioned in the working space, wherein the working medium flows through the pump wheel centrifugally or centrifugally-diagonally, and the working medium flows through the turbine centripetally or centripetally-diagonally; wherein, relative to the rotation axes of the pump wheel and the turbine, the radius of the inlet grille edge of the turbine is less than or equal to the radius of the inlet grille edge of the pump wheel. The hydraulic converter according to the present invention is characterized in that a first guide wheel is arranged in the working space in front of the pump wheel along the flow direction of the working medium, and the pump wheel is arranged for a purely centrifugal or diagonally-centrifugal flow of the working medium and for influencing power transmission.

Description

Technical Field

[0001] The invention relates to a hydrodynamic converter having at least one pump wheel, at least one turbine wheel and at least one stator wheel in a working space for forming a circulation of a hydraulic working medium. Background Art

[0002] Hydrodynamic converters have been known for decades. Hydrodynamic converters are provided, for example, as starting converters or traveling converters or medium / high speed converters in the hydraulic transmission of rail vehicles. Thus, an automatic two-speed or multi-speed transmission can be provided, depending on the number of converters used as hydraulic power transmitters. The design point of the starting converter is usually the speed ratio of the turbine speed to the pump speed, i.e. the speed ratio between the speed of the turbine and the speed of the pump wheel, which is between 0.4 and 0.6, and extreme starting converters also have a speed ratio of about 0.3. Travel converters usually have a corresponding speed ratio of between 0.8 and 0.9. Therefore, the turbine runs slower than the pump wheel at the design point, i.e. at the rated speed of the vehicle. In the traveling converter, depending on the design of the cooling facility, a turbine with a maximum speed ratio of between 1.3 and about 1.5 can be used in the rail vehicle.

[0003] For example, DE 10 2010 018 160 B3 discloses such a hydraulic converter, in which a circulating working medium in a working space flows at least partially centrifugally through a pump wheel, a circulating working medium flows at least partially centrifugally through a guide wheel, and the circulating working medium extends in a flow direction toward the turbine in parallel to the axis of rotation along the axial direction of the hydraulic converter, while conversely, a flow direction of the circulating working medium away from the turbine extends partially centrifugally and partially in an axial direction, i.e. diagonally. The guide wheel is also called a guide vane ring in the converter because, unlike the pump wheel and the turbine, the guide wheel does not rotate.

[0004] For industrial applications, hydrodynamic converters are usually implemented as influenceable converters with adjustable guide wheels. It is also possible to provide multiple guide wheels, one of which is adjustable and the other of which is fixed. In adjustable guide wheels, the blades are adjustable during operation in order to thus continuously vary the power consumption and power transmission of the converter.

[0005] An exemplary embodiment for such a hydrodynamic converter is disclosed, for example, in DE 10 2007 005 426 B3.

[0006] Even in conventional hydrodynamic converters for industrial applications, the speed ratio is usually limited in order to favour a high torque transmission, the design of which corresponds to the starting and running converter shown.

[0007] WO 02 / 14706A2 discloses a hydraulic converter for use in a unit, wherein the drive is a gas turbine and the working machine is a compressor. This involves very high power, which is on the order of 20 MW or more. Due to this extreme power, these machines also have very large rotating masses. The hydraulic converter has a very small lambda value. The speed ratio between the rotational speed of the turbine and the rotational speed of the pump wheel is on the order of 1. The efficiency is on the order of 0.75 and higher. The pump wheel is essentially centrifugal and the turbine is essentially flowed through centripetally, wherein the inlet edge of the pump wheel blades and the outlet edge of the turbine blades are opposite to each other. The inlet edge of the pump wheel blades and the outlet edge of the turbine blades are closer to the axis of rotation of the converter than the outlet edge of the pump wheel blades and the inlet edge of the turbine blades.

[0008] DE 10 2004 011 033 B3 discloses a hydrodynamic converter having a pump wheel through which a centrifugal flow flows and a turbine wheel through which a centripetal flow flows, wherein the outlet edge of the pump wheel has a larger radius than the inlet edge of the turbine wheel. In addition, the inlet edge of the blades of the pump wheel has a larger radius than the inlet edge of the blades of the turbine wheel. Guide vanes are arranged in a radially outer region between the pump wheel and the turbine wheel, and guide vanes are arranged in a radially inner region between the turbine wheel and the pump wheel, wherein the flow flows through the guide vanes axially.

[0009] WO 2010 / 062269 A1 is based on a hydrodynamic converter of the type shown above and proposes arranging the pump wheel radially outside the turbine wheel with flow passing through it centrifugally or axially. The guide vanes can then also be positioned in front of the pump wheel with flow passing through it centrifugally. Summary of the invention

[0010] The technical problem to be solved by the present invention is to provide a hydrodynamic converter which is particularly suitable for high speed ratios at the design point, speed ratios above the speed ratios of previously known hydraulic converters, and for a wide operating range near the design point.

[0011] The technical problem according to the present invention is solved by a hydraulic converter according to the present invention, namely a hydraulic converter having a working space for constructing a circulation of a hydraulic working medium, wherein at least one pump wheel, at least one turbine and at least one guide wheel are positioned in the working space, wherein the working medium flows through the pump wheel centrifugally or centrifugally-diagonally, and the working medium flows through the turbine centripetally or centripetally-diagonally; wherein, relative to the rotation axes of the pump wheel and the turbine, the radius of the edge of the inlet grille of the turbine is less than or equal to the radius of the edge of the inlet grille of the pump wheel, a first guide wheel is arranged in front of the pump wheel in the flow direction of the working medium in the working space, and the pump wheel is arranged for purely centrifugal or diagonal-centrifugal flow of the working medium.

[0012] A device having a drive machine and a multiphase pump driven by the drive machine, wherein a hydrodynamic converter according to the invention is arranged in the drive connection between the drive machine and the multiphase pump.

[0013] Advantageous and particularly suitable embodiments of the present invention include at least one of the following technical features:

[0014] The edge of the inlet grille of the first stator is located at a radius at least substantially corresponding to the radius of the edge of the inlet grille of the turbine relative to the rotation axes of the pump impeller and the turbine;

[0015] The radius of the inlet grille edge of the first guide wheel is 0.8 to 1.2 times, 0.9 to 1.1 times, or 0.95 to 1.05 times the radius of the inlet grille edge of the turbine;

[0016] The first guide wheel is arranged directly before the pump wheel along the flow direction of the working medium;

[0017] A second guide wheel is arranged in the working space, and the second guide wheel is arranged for a purely axial flow or a diagonal-axial flow or an axial-diagonal flow of the working medium;

[0018] The first stator is designed with guide vanes which are adjustable about a stator rotation axis and are variably adjustable relative to the flow of the working medium, wherein the stator rotation axis extends in particular parallel or obliquely relative to the rotation axes of the pump wheel and the turbine wheel;

[0019] The second guide wheel is designed as a fixed guide wheel;

[0020] The second guide wheel has a plurality of guide vanes, which are divided into two groups and positioned in sequence adjacent to each other in the working space, wherein the number of guide vanes in the first group is smaller than the number of guide vanes in the second group;

[0021] Three guide wheels are arranged in the working space;

[0022] A third guide wheel is arranged in the working space and positioned for purely axial flow of the working medium;

[0023] The second guide wheel is positioned at a larger diameter than the first guide wheel, and the third guide wheel is positioned at a smaller diameter than the first guide wheel;

[0024] The first guide wheel or the third guide wheel is designed with guide vanes which are adjustable about the guide wheel rotation axis and are adjustable relative to the working medium flow during operation of the converter, wherein in particular the guide wheel of the two guide wheels without adjustable guide vanes carries a wall element which delimits the working space radially inwardly relative to the working medium circulation;

[0025] The ratio of the inner diameter of the working space to the outer diameter of the working space is less than 0.2 or 0.1;

[0026] The ratio of the width of the working space along the direction of the rotation axis of the pump wheel and the turbine to the outer diameter of the working space is less than 0.5 or 0.4;

[0027] The radius of the inlet grille edge of the pump wheel is 1.1 to 1.3 times, in particular 1.2 times, the radius of the inlet grille edge of the turbine wheel;

[0028] The impeller is arranged, in particular the pump wheel and the turbine are positioned, in such a way that a design speed ratio between the turbine speed and the pump wheel speed in the range of 1.8 to 2.0 and a maximum operating range of 2.3 are achieved.

[0029] The hydraulic converter according to the present invention has a working space for constructing a hydraulic working medium circulation of a working medium. In particular, oil is considered, but other media, such as water or a water mixture, in particular a water-glycol mixture, can also be used as the working medium. At least one pump wheel, at least one turbine and at least one guide wheel are positioned in the working space in sequence along the flow direction of the working medium. Here, along the flow direction, the guide wheel usually follows the pump wheel, and the turbine usually follows the guide wheel. In addition, another guide wheel can be arranged in front of the pump wheel in the flow direction, for example, wherein the guide wheel is advantageously adjustable, that is, its guide vanes or at least a part of the guide vanes can be rotated around the rotation axis (also referred to as the blade rotation axis) respectively, so that the guide wheel can be variably adjusted relative to the flow of the working medium. If an adjustable guide wheel is provided, it is also called an influenceable hydraulic converter.

[0030] The converter according to the invention is designed in particular as a so-called high-speed converter, ie a converter with a particularly large design speed ratio, which will be discussed further below.

[0031] According to the invention, the working medium flows through the pump wheel centrifugally, in particular purely centrifugally or centrifugally-diagonally, and the working medium flows through the turbine wheel centrifugally, in particular purely centrifugally or centrifugally-diagonally.

[0032] The working medium thus enters the turbine wheel centrifugally and flows out of the turbine wheel centrifugally or partially centrifugally and partially axially.

[0033] The radius of the inlet grille edge of the turbine is less than or equal to the radius of the inlet grille edge of the pump wheel. This inlet grille edge of the turbine can also be called the inlet edge of the blades of the turbine and represents the edge of the turbine blades that is incident on the flow. The outlet grille edge or outlet edge represents the edge of the turbine blades that is out of the flow. The corresponding situation also applies to the other wheels, namely the pump wheel and one or more guide wheels.

[0034] Advantageously, the hydrodynamic converter is designed as a single-stage hydrodynamic converter having a single turbine.

[0035] Preferably, only one single pump wheel is also provided, which is arranged for a pure centrifugal or centrifugal-diagonal flow of the working medium through it. Accordingly, the working medium flows centrifugally into the pump wheel and flows out of the pump wheel centrifugally or flows into the pump wheel centrifugally and flows out of the pump wheel partly centrifugally and partly axially.

[0036] According to the invention, a first guide wheel is provided, for example a guide wheel adjustable about an axis of rotation, wherein the guide wheel is preferably arranged in the working space for a purely centrifugal or diagonal centrifugal flow through of the working medium. Accordingly, the working medium flows into the first guide wheel centrifugally or partially centrifugally and partially axially and flows out of the first guide wheel centrifugally. The regulating vanes are arranged in the region of the guide wheel through which the purely centrifugal flow flows.

[0037] The first guide wheel is arranged in the working space in front of the pump wheel in the flow direction of the working medium, in particular, directly in front of the pump wheel. When the first guide wheel is arranged directly in front of the pump wheel, no additional impeller or no additional blades are arranged between the outlet of the first guide wheel and the inlet of the pump wheel, that is, the outlet grating edge of the guide wheel or the outlet edge of the blades of the guide wheel is directly opposite to the inlet grating edge of the pump wheel or the inlet edge of the blades of the pump wheel.

[0038] Furthermore, preferably a second guide wheel is provided, which is arranged in the working space for a purely axial, diagonal-axial or axial-diagonal flow of the working medium. Accordingly, the working medium flows into the second guide wheel partially radially and partially axially or only axially and flows out of the second guide wheel only axially or partially axially and partially radially.

[0039] The second stator is arranged, in particular, behind the pump wheel in the flow direction of the working medium in the working medium circuit.

[0040] The inlet grille edge of the first stator or the inlet edge of the blades of the first stator preferably has a radius with respect to the axis of rotation of the pump wheel and the turbine which at least substantially corresponds to the radius of the inlet grille edge of the turbine or the inlet edge of the blades of the turbine. The radius of the inlet grille edge of the first stator is, for example, 0.8 to 1.2 times, in particular 0.9 to 1.1 times or 0.95 to 1.05 times, the radius of the inlet grille edge of the turbine. Preferably, the radius of the inlet grille edge of the first stator is 0.9 times the radius of the inlet grille edge of the turbine.

[0041] The radius of the inlet grille edge of the pump wheel or the inlet edges of the blades of the pump wheel is preferably 1.1 to 1.3 times, in particular 1.2 times, the radius of the inlet grille edge of the turbine wheel or the inlet edges of the blades of the turbine wheel.

[0042] The second stator can be designed in particular as a fixed stator, respectively without blades which are adjustable about the axis of rotation or relative to the flow of the working medium.

[0043] According to one embodiment, the second guide wheel is equipped with splitter blades in the outlet region. This means that the second guide wheel has a plurality of guide blades or guide vanes, which are arranged in two groups adjacent to each other in the working space, wherein the number of guide vanes of the first group is less than or can also be equal to the number of guide vanes of the second group. The guide vanes of the first group can, for example, have a relatively long axial extension, in particular an axial extension that is longer than the radial extension. The guide vanes can have a predetermined thickness in order to guide the working medium.

[0044] According to one embodiment of the present invention, three guide wheels are arranged in the working space, for example, the first guide wheel is arranged in the radial flow-through region of the working space, the second guide wheel is arranged on the outer diameter in the axial flow-through region of the working space, and the third guide wheel is arranged in the axial flow-through region, on the radial inner diameter of the working space, and behind the turbine in the flow direction of the working medium. The third guide wheel can, for example, have a bearing function of a component or wall part for radially delimiting the working space inwardly relative to the working medium circulation, that is, the component or wall part forms the meridian profile of the working space.

[0045] The working space is in particular hollow annular, i.e. the working space has an annular shape in an axial cross-section on each side of the axis of rotation of the hydraulic converter, wherein the annular shape may be different from a circular ring and may have a variable thickness or a variable cross-section on the periphery of the annular shape. In other words, the working space of the converter through which the working medium flows is bounded by inner and outer annular meridian profiles, which symmetrically construct the working space of the converter around the axis of rotation of the converter, wherein the impeller is arranged. The channel width, i.e. the distance between the outer meridian profile and the inner meridian profile, is changed in an appropriate form in accordance with the requirements in the individual sections of the converter along the throughflow direction.

[0046] If the above-described adjustable first guide wheel and the fixed second guide wheel are provided, and if a third guide wheel is also provided in the working space, the third guide wheel is advantageously positioned for a purely axial throughflow of the working medium.

[0047] Preferably, the second guide wheel is positioned on a larger diameter than the first guide wheel, and the third guide wheel is positioned on a smaller diameter than the first guide wheel.

[0048] According to one embodiment of the invention, at least one fourth guide wheel is arranged in the working space. Such a fourth guide wheel is preferably flowed through by the working medium diagonally-centripetally or purely centripetally. The fourth guide wheel is preferably positioned between the second guide wheel and the turbine, in particular directly in front of the turbine, so that the outlet grille edge of the fourth guide wheel or the outlet edges of the blades of the fourth guide wheel are directly opposite the inlet grille edge of the turbine without any further wheels or blades being arranged in between.

[0049] Such a fourth stator wheel can be combined in particular, but not necessarily, with a simple second stator wheel without splitter blades.

[0050] It is of course also possible to design the second stator as a simple stator without splitter blades and to position the fourth stator behind the second stator with axial or diagonal flow through it.

[0051] Advantageously, the ratio of the inner diameter of the working space to the outer diameter of the working space is less than 0.2 or less than 0.1. According to one embodiment, the ratio of the inner diameter (on the ascending side (German: Hubseite) of the meridian profile) to the outer diameter is respectively 0.1.

[0052] Preferably, the ratio of the width of the working space in the direction of the rotation axis of the pump wheel and the turbine to the outer diameter of the working space is smaller than 0.5 or smaller than 0.4, for example, 0.38 or 0.485.

[0053] The device with the hydrodynamic converter according to the invention has, for example, a drive machine and a multiphase pump, wherein the multiphase pump is driven by the drive machine. The hydrodynamic converter according to the invention is arranged in the drive connection between the drive machine and the multiphase pump.

[0054] Multiphase pumps are particularly suitable for conveying liquid-gas mixtures and measures are taken so that no gas bubbles are formed upstream of the pump impeller of the multiphase pump. Dry running of the pump is thus excluded.

[0055] Preferably, the suction side of the multiphase pump is throttled to a certain extent, so that the multiphase pump can automatically suck in the gas.

[0056] According to one embodiment of the invention, such a multiphase pump is used in particular for transporting oil and / or gas.

[0057] The hydrodynamic converter according to the invention can have, for example, a design speed ratio of between 1.8 and 2.0 and a maximum operating range of 2.3.

[0058] The blades of the adjustable stator are preferably individually rotatable within a certain rotation range, suitable for presenting a maximum open up to completely closed flow channel in the stator. If an axially inner stator is provided, it can be provided for forming the desired meridian profile in the region between the turbine wheel and the pump wheel and, moreover, for accommodating components for adjusting the guide vanes of the adjustable stator.

[0059] The number of blades of each impeller of the hydrodynamic converter can be designed to be relatively small while taking all requirements into account.

[0060] The converter according to the invention has a good integrity, which means a wide variation of the efficiency. Thus, in the speed ratio range between 1.3 and 2.2, the efficiency can be, for example, higher than 75%. Furthermore, in the speed ratio range between 1.4 and 2.4, the efficiency can be higher than 75%. The speed ratio describes the speed of the turbine relative to the speed of the pump wheel. The peak efficiency can be between 80% and 82% or even higher.

[0061] The design speed ratio range with a maximum efficiency of, for example, more than 78% or 80% is, for example, 1.8 to 2.2.

[0062] The pressure factor psi for the pump wheel can be, for example, between 1.25 and 3, and the delivery factor phi is at least approximately 1.1. The power consumption (λ value) of the pump wheel is preferably at least approximately 0.6×10 3 .

[0063] The lambda curve can be designed to decrease slightly with increasing speed ratio.

[0064] According to one embodiment of the present invention, the converter is designed so that the conversion is always less than 0.7, that is, there is no coupling point and the torque of the turbine is less than the torque of the pump wheel in the entire speed ratio range.

[0065] The preferred arrangement of the adjustable stator directly in front of the pump wheel enables a particularly well graded characteristic curve and thus good influencing of the power transmission of the converter. Grading is understood to mean that the distance between the individual characteristic curves of the power consumption of the pump wheel and the turbine torque is proportional to the rotation angle of the regulating wheel blades (blades of the first stator). In this case, the arrangement of the adjustable stator directly in front of the pump wheel can be achieved not only by a stator through which a purely centrifugal flow passes, but also by a stator through which an axial flow passes, with corresponding positioning in the working medium circuit.

[0066] The hydrodynamic converter is preferably speed-limited, that is, at an increase in speed above the upper operating range speed ratio, the turbine causes a disruption of the surrounding mass flow of the working medium and, in connection therewith, immediately reaches the through-point. Above speed ratio 3, the hydrodynamic converter itself is particularly speed-limited.

[0067] The impeller is arranged, in particular the pump wheel and the turbine are positioned, such that a design speed ratio between the turbine speed and the pump wheel speed in the range of 1.8 to 2.0 and a maximum operating range of 2.3 are achieved. This converter is therefore a high-speed converter. BRIEF DESCRIPTION OF THE DRAWINGS

[0068] The invention will be explained below by way of example with reference to exemplary embodiments and figures.

[0069] in:

[0070] Figure 1 An embodiment of a high-speed hydraulic converter according to the present invention is shown;

[0071] Figure 2 An embodiment of a device according to the invention having a drive machine, a hydrodynamic converter and a multiphase pump is shown;

[0072] Figure 3 Shows the corresponding Figure 1 , which has a modified arrangement of the impeller;

[0073] Figure 4 Shows the corresponding Figure 3 , which has an arrangement of an impeller with splitter blades having a second guide wheel. DETAILED DESCRIPTION

[0074] Figure 1 A schematic axial section through a working space 10 of a hydrodynamic converter 11 is shown laterally from the axis of rotation 8. The working space has an inner diameter DI, an outer diameter DA and a width B relative to the outer contour of the hollow annular working space 10 or its meridian profile.

[0075] The pump wheel 1 through which the centrifugal flow passes and the turbine 2 through which the centripetal-diagonal flow passes are arranged in the working space 10. The inlet grille edge 7 of the turbine 2 is located at a smaller radius than the inlet grille edge 9 of the pump wheel 1. The pump wheel 1 is arranged approximately on the average diameter of the working space 10, and the turbine 2 extends at least substantially to the inner diameter DI of the working space 10.

[0076] The fixed stator 5 is arranged between the turbine 2 and the pump wheel 1, i.e. in the radially inner region of the working space 10, followed by the adjustable stator 3, which is positioned radially approximately further outwards before the inlet grille edge 9 of the pump wheel 1. In addition, a further stator 4 is arranged in the radially outer region of the working space 10.

[0077] In the present case, the guide wheel 3 in front of the pump wheel 1 is referred to as the first guide wheel 3, which is adjustable about the guide wheel rotation axis 6. The guide wheel 4 arranged in the radially outer region of the working space 10 is referred to as the second guide wheel 4, which has two groups of guide vanes 4.1, 4.2, wherein the number of guide vanes 4.2 of the second group is greater than or equal to the number of guide vanes 4.1 of the first group. The guide wheel 5 arranged in the radially inner region of the working space 10 is referred to as the third guide wheel 5.

[0078] The first stator 3 has an inlet grating edge 14 and an outlet grating edge 15. The outlet grating edge 15 is directly opposite the inlet grating edge 7 of the pump wheel 1. The inlet grating edge 14 of the first stator 3 is positioned parallel to the axis of rotation 8, so that the working medium flows through the first stator 3 purely centrifugally.

[0079] Figure 2 The arrangement of a driving machine 12 and a multiphase pump 13 driven by the driving machine 12, which transports a liquid-air mixture or a liquid-gas mixture. The multiphase pump 13 is driven by a hydraulic converter 11 according to the invention, for example schematically in FIG. Figure 1 A hydraulic converter is shown in FIG.

[0080] according to Figure 3 , the second guide wheel 4 is implemented as a simple guide wheel, that is, without splitter blades. Alternatively, the fourth guide wheel 16 is connected after the second guide wheel 4 in the flow direction of the working medium. The fourth guide wheel 16 is positioned directly before the turbine 2 and is flowed through purely centripetally in the embodiment shown. Alternatively, however, a diagonal-centripetal flow can also be provided.

[0081] In accordance with Figure 4 Alternatively, the second guide wheel 4 is implemented with splitter blades, including a first set of guide blades 4.1 and a second set of guide blades 4.2, wherein the orientation and / or the number of the first set of guide blades 4.1 is different from the orientation and / or the number of the second set of guide blades 4.2.

[0082] List of Reference Numerals

[0083] 1 Pump wheel

[0084] 2 Turbine

[0085] 3First guide wheel

[0086] 4 Second guide wheel

[0087] 4.1 The first set of guide vanes

[0088] 4.2 The second set of guide vanes

[0089] 5Third guide wheel

[0090] 6 Guide wheel rotation axis

[0091] 7 Inlet grille edge

[0092] 8Rotation axis

[0093] 9 Inlet grille edge

[0094] 10. Workspace

[0095] 11Hydraulic converter

[0096] 12 Driving Machine

[0097] 13Multiphase pump

[0098] 14 Inlet grille edge

[0099] 15 outlet grill edge

[0100] 16Fourth guide wheel

Claims

1. A hydraulic converter (11) having a working space (10) for forming a circulation of a hydraulic working medium, wherein at least one pump wheel (1), at least one turbine wheel (2) and at least one guide wheel (3, 4, 5) are positioned in the working space (10), wherein: The working medium flows through the pump wheel (1) centrifugally or centrifugally-diagonally, and the working medium flows through the turbine (2) centripetally or centrifugally-diagonally; wherein, relative to the rotation axis (8) of the pump wheel (1) and the turbine (2), the radius of the inlet grille edge (7) of the turbine (2) is less than or equal to the radius of the inlet grille edge (9) of the pump wheel (1), characterized in that the first guide wheel (3) is arranged in the working space (10) before the pump wheel (1) along the flow direction of the working medium, and the pump wheel is arranged for pure centrifugal or diagonal-centrifugal flow of the working medium.

2. The hydraulic converter (11) according to claim 1, characterized in that: With respect to the rotational axes (8) of the pump wheel (1) and the turbine wheel (2), the inlet grille edge (14) of the first guide wheel (3) is located at a radius which at least substantially corresponds to the radius of the inlet grille edge (7) of the turbine wheel (2).

3. The hydraulic converter (11) according to claim 2, characterized in that: The radius of the inlet grille edge (14) of the first guide wheel (3) is 0.8 to 1.2 times the radius of the inlet grille edge (7) of the turbine (2).

4. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The first guide wheel (3) is arranged directly before the pump wheel (1) along the flow direction of the working medium.

5. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: A second guide wheel (4) is arranged in the working space (10), which is designed for a purely axial or diagonal-axial or axial-diagonal flow of the working medium.

6. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The first guide wheel (3) is designed with guide vanes which are adjustable about a guide wheel rotation axis (6) and which are variably adjustable relative to the flow of the working medium.

7. The hydraulic converter (11) according to claim 5, characterized in that: The second guide wheel (4) is designed as a fixed guide wheel (4).

8. The hydraulic converter (11) according to claim 5, characterized in that: The second guide wheel (4) has a plurality of guide vanes (4.1, 4.2), which are divided into two groups and positioned adjacent to each other in the working space (10) in sequence, wherein the number of guide vanes (4.1) in the first group is smaller than the number of guide vanes (4.2) in the second group.

9. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: Three guide wheels (3, 4, 5) are arranged in the working space (10).

10. The hydraulic converter (11) according to claim 5, characterized in that The third guide wheel (5) is arranged in the working space (10) and is positioned for a purely axial flow of the working medium.

11. The hydraulic converter (11) according to claim 10, characterized in that The second guide wheel (4) is positioned on a larger diameter than the first guide wheel (3), and the third guide wheel (5) is positioned on a smaller diameter than the first guide wheel (3).

12. The hydraulic converter (11) according to claim 11, characterized in that The first guide wheel (3) or the third guide wheel (5) is designed with guide vanes which are adjustable about the guide wheel rotation axis (6) and are adjustable relative to the flow of the working medium during operation of the converter (11).

13. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The ratio of the inner diameter (DI) of the working space (10) to the outer diameter (DA) of the working space (10) is less than 0.

2.

14. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The ratio of the width (B) of the working space (10) in the direction of the rotation axis (8) of the pump wheel (1) and the turbine (2) to the outer diameter (DA) of the working space (10) is less than 0.

5.

15. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The radius of the inlet grille edge (9) of the pump wheel (1) is 1.1 to 1.3 times the radius of the inlet grille edge (7) of the turbine (2).

16. The hydraulic converter (11) according to claim 6, characterized in that The stator rotation axis (6) extends parallel or obliquely relative to the rotation axes (8) of the pump wheel (1) and the turbine wheel (2).

17. The hydraulic converter (11) according to claim 12, characterized in that The guide wheel of the first guide wheel (3) and the third guide wheel (5) without adjustable guide vanes carries a wall part which delimits the working space (10) radially inwardly with respect to the working medium circulation.

18. The hydraulic converter (11) according to claim 15, characterized in that The radius of the inlet grille edge (9) of the pump wheel (1) is 1.2 times the radius of the inlet grille edge (7) of the turbine (2).

19. The hydraulic converter (11) according to claim 2, characterized in that: The radius of the inlet grille edge (14) of the first guide wheel (3) is 0.95 to 1.05 times the radius of the inlet grille edge (7) of the turbine (2).

20. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that: The ratio of the inner diameter (DI) of the working space (10) to the outer diameter (DA) of the working space (10) is less than 0.

1.

21. The hydraulic converter (11) according to any one of claims 1 to 3, characterized in that The ratio of the width (B) of the working space (10) in the direction of the rotation axis (8) of the pump wheel (1) and the turbine (2) to the outer diameter (DA) of the working space (10) is less than 0.

4.

22. An arrangement having a drive machine (12) and a multiphase pump (13) driven by the drive machine, characterized in that A hydrodynamic converter (11) according to any one of claims 1 to 21 is arranged in the drive connection between the drive machine (12) and the multiphase pump (13).

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