JP2008526610A - Hydrodynamic turbomachine with axially displaceable vane wheels - Google Patents

Abstract

The present invention relates to a hydrodynamic turbomachine, in particular to a retarder having a bladed primary wheel (1) and a bladed secondary wheel (2) which together form a working chamber (3) filled with a working medium. . At least one of the two wheels (1, 2) at least in the partial region (1.1) with its blades as opposed to the other as follows, ie directly opposite the other wheel in the axial direction, Displaceable in the axial direction so that it can be switched between a close position of 1 and a second distant position, which is arranged with a larger axial distance relative to the other wheel than the first position Is possible. The hydrodynamic turbomachine, in particular the retarder, according to the invention has the following characteristics: a working chamber (3) arranged on the axially front side of the displaceable wheel (1) and a displaceable wheel ( A pressure compensation connection (4) for guiding the flow is provided between the compensation chambers (5) arranged on the rear side of the front side in the axial direction of 1); When the displaceable wheel is in the first position in the compensation chamber, the pressure compensation connection is at least indirectly completely or substantially completely blocked by the displaceable wheel, as opposed to Thus, when the displaceable wheel is in the second remote position, the pressure compensating connection is arranged open so that it is at least indirectly released by the displaceable wheel.
[Selection] Figure 1

Description

  The present invention relates to a hydrodynamic turbomachine having two blade wheels, a primary wheel and a secondary wheel, at least one of which is axially displaceable relative to the other. The present invention particularly relates to retarders.

  The fact that at least one of the two blade wheels is displaceable is used to reduce the loss output in the idling of the hydrodynamic turbomachine. DE10219753A1 describes, for example, a retarder, in which the rotor is mounted on a hollow shaft by means of screw bolts and is moved away from the stator when moving from a brake drive to a non-brake drive, i.e. idling. Moved. In order to shift to brake driving again, the rotor is moved closer to the stator again, so that a flow circulation can be formed in the working chamber between the rotor and the stator, and torque from the rotor can be formed using the flow circulation. Is transmitted to the stator, so that the rotor is braked.

  The transition from idling to work drive, i.e., in the retarder from non-brake drive to brake drive, can be easily understood, e.g. a brake command is given by the driver of the vehicle in which the retarder is incorporated for braking. Once done, it should be done as quickly as possible. Thus, as quickly as possible, the two blade wheels are directly opposed in the axial direction, thereby creating a desired working medium circulation between the two blade wheels in the working chamber and starting torque transmission by the working medium. It is necessary to make such a configuration. There is room for improvement in terms of the actual speed or the required length of time when shifting from idling drive to work drive based on inertia in the system.

  The object of the present invention is to provide a hydrodynamic turbomachine, in particular a retarder, having an axially displaceable vane wheel in which the transition from idling to work drive takes place more quickly compared to known specifications. At the same time, the structural changes of the known machine are kept small and no additional energy consumption is required for switching.

  The object of the invention is solved by a hydrodynamic turbomachine having the features of claim 1. The dependent claims describe preferred and particularly advantageous forms of the invention.

  The hydrodynamic turbomachine according to the invention has a primary wheel with blades and a secondary wheel with blades, which together form a working chamber that can be filled with a working medium. In that case, at least one of the two wheels is slidable in the axial direction with respect to the other. This axial slidability, in the context of the invention, relates to at least a partial region of the axially slidable wheel, so that in the first close position both wings of the two wheels are present. The partial areas are directly opposed in the axial direction. Thereafter, when one of the two wheels, for example, the primary wheel is driven to rotate, the working medium in the working chamber formed by the partial region of the two blades is accelerated radially outward by the driven wheel blades. Then, it flows into a partial region where the blades of the opposite wheel are present, and is decelerated radially inward there, so that a circulation of the working medium is formed in the working chamber.

  In a second remote position, i.e. in a position where the vane part of the axially displaceable vane wheel is separated from the part area of the other wheel vane, between the two vane areas Since no flow circulation can be formed in the working chamber based on this distance, torque is not transmitted between the regions where the blades are present, or substantially no torque is transmitted. Thereby, undesirable losses in idling drive are substantially or completely avoided.

  In order to facilitate the process of moving one of the two wheels closer together or moving the two wheels closer together, a turbomachine according to the invention flows between the working medium and the pressure compensation chamber. Pressure compensating connection for guiding The pressure-compensating connection that guides this flow opens on the one hand in the working chamber arranged on the axially front side of the displaceable wheel, and on the other hand on the rear side that is axially opposed to the front side of the displaceable wheel. Opened in the guarantee room located on the side. Thus, if the displaceable wheel, for example the primary wheel or retarder rotor, moves closer to the opposite wheel, for example the secondary wheel or retarder stator, the medium in the working chamber that has been enlarged before it For example, since air flows from the working chamber, which becomes smaller when moving closer, into the compensation chamber through the pressure compensation connection, the counter pressure to be overcome that antagonizes the wheel displacement when moving closer is Not formed.

  In order to prevent the working medium from flowing out of the working chamber through the pressure compensation connection in the working state, for example in a brake drive, according to the invention, the pressure compensating connection is arranged in the working chamber and the compensation chamber as follows: Arranged such that when the displaceable wheel is in the first close position, its pressure compensating connection is at least indirectly blocked by the displaceable wheel completely or substantially completely. ing. In order to enable the above-described flow compensation when the wheel moves closer, according to the invention, the pressure compensation connection is simultaneously performed by the displaceable wheel or the displaceable subregion of the wheel at the second distant position. Or when generally outside the first close position.

  The pressure-compensating connection can be used, for example, when a displaceable wheel or a partial region of a displaceable wheel occupies the first close position described above, the displaceable wheel or the displaceable partial region of the corresponding wheel is hydrodynamic. It can be shut off by contacting other parts of the turbomachine.

  In particular, the pressure compensating connection is guided through a displaceable wheel and / or a displaceable partial region in the form of one or more shaft holes. Alternatively or additionally, the pressure compensating connection can be formed along the outer peripheral surface of the displaceable wheel or displaceable partial area.

  In the following, the invention will be described in detail by means of two embodiments schematically shown in the figures.

  In FIG. 1 a retarder having a primary wheel 1 and a secondary wheel 2 can be seen. The primary wheel 1 is a retarder rotor, and the secondary wheel 2 is a stator. The two wheels 1, 2 have a partial area with vanes, ie the rotor has a partial area 1.1 and the stator has a partial area 2.1.

  The stator, that is, the secondary wheel 2 is supported at a fixed position in the housing 7. The housing 7 surrounds the primary wheel 1 together with the stator to form an internal space, and the internal space is substantially separated from each other by two regions 1.1 with the blades of the primary wheel 1, that is, the working chamber 3. And is divided into compensation chambers 5.

  The partial region 1.1 of the primary wheel 1 that supports the blades 1.4 is axially displaceable, as suggested by the double arrow 12. This axial displacement is achieved by the partial area 1.1 displaceable on the axially fixed area 1.3 of the primary wheel being mounted in a toothed or screw-shaped manner. This bearing is indicated by the reference numeral 9 in FIG. Of course, the axially displaceable partial region 1.1 of the primary wheel and the axially fixed region 1.3 are also arranged to be rotatable in the circumferential direction so that the primary wheel 1 performs its desired function. Can be exercised.

  Instead of the display shown in the drawing, the entire primary wheel 1 can be slidably arranged in the axial direction.

  A number of axial holes 6 are formed in the axially slidable partial region 1.1 of the primary wheel 1 and represent the pressure compensating connection 4 according to the invention.

  In FIG. 1, the position of the slidable partial area 1.1 is shown inside the space enclosed by the housing 7 and the secondary wheel 2, and the slidable partial area 1.1 at that position is It is arranged axially away from the partial area 2.1 having the blades of the secondary wheel 2. Thus, the space formed by the regions 1.1 and 2.1 with the blades of both the primary wheel 1 and the secondary wheel 2, respectively, is interrupted by a clear gap in its axial direction, from the primary wheel 1 No output is transmitted to the secondary wheel 2. This state is referred to as idling because the primary wheel 1 rotates without being braked. Even in this state, the working chamber is formed between the primary wheel 1 and the secondary wheel 2 or by the region 1.1 and 2.1 with the blades of the primary and secondary wheels, with an axial gap located between them. The space designated 3 is preferably completely or emptied to a predetermined residual amount of working medium and is filled with air accordingly.

  In order to switch to the brake drive as quickly as possible, the primary wheel 1 is such that the torus-shaped working chamber 3 is formed by the region 1.1 with the blades of the primary wheel and the region 2.1 with the blades of the secondary wheel. This partial area 1.1 must be quickly switched to the position shown in FIG. Since the working chamber 3 is filled with the working medium, the working medium is accelerated radially outward by the vanes 1.4 in the primary wheel 1 and decelerated radially inward by the vanes 2.4 in the secondary wheel 2. As shown by the arrow 11, a circulating flow for transmitting torque is formed.

  While the partial region 1.1 of the primary wheel 1 moves towards the partial region 2.1 with the blades of the secondary wheel 2, the front side of the primary wheel 1, i.e. the bottom of the blades of the primary wheel 1 and the secondary wheel 2 The medium in the space between the bottoms of the blades flows out into the compensation chamber 5 through the shaft hole 6 as indicated by the arrow 10, thus preventing the subregion 1.1 from approaching the work chamber 3. No pressure is formed. In the state shown in FIG. 2, i.e. when the partial area 1.1 is in its first close position relative to the partial area 2.1, i.e. the blades 1.4 of the primary wheel 1 and the secondary wheel 2. For the first time at the position where 4 directly faces in the axial direction, the partial region 1.1 that can be displaced in the axial direction has a partial region 1.3 that is fixed in the axial direction. The pressure compensation connection 4 is cut off. For this purpose, as can be seen in FIGS. 1 and 2, the shaft is formed to have a substantially or completely cylindrical outer peripheral surface in the region supporting the axially displaceable region 1.1. A radial protrusion is formed in the partial area 1.3 fixed in the direction so as to be adjacent to the axially displaceable partial area in the axial direction, and the protrusion can be displaced in the axial direction. When the partial region 1.1 is moved so as to approach the first close position, the partial region 1.1 is fitted into the radially inner notch 13 formed in the axially displaceable partial region 1.1.

  The radial protrusion of the fixed partial area 1.3 can be formed integrally with the cylindrical area of the axially fixed part 1.3 or mounted on this cylindrical part. it can. In particular, as suggested in FIGS. 1 and 2, the radial protrusion is formed in the shape of a disc mounted in a stepped peripheral area of a cylindrical area. The radial protrusion may be formed from a material that is preferred for the seal it is to form.

  3 and 4 show the second specification of the retarder. This retarder is shown in FIGS. 1 and 2 except that the pressure compensating connection 4 is formed along the radially outer peripheral surface 1.2 of the axially displaceable partial region 1.1. It is almost equivalent to the specifications. For this purpose, a step is provided on the inner peripheral surface of the housing 7, so that the inner peripheral surface of the housing 7 starts from the radially outer side of the secondary wheel 2 and widens stepwise in the direction of the primary wheel 1. Therefore, as shown in FIG. 3, when the partial region 1.1 is located far from the secondary wheel 2, it is between the outer peripheral surface of the partial region 1.1 and the inner peripheral surface of the housing 7. When a relatively large radial gap is formed, whereas, as shown in FIG. 4, the partial gap 1.1 is in a nearby position, this annular gap is significantly narrowed.

  Thus, when the partial area 1.1 begins to move closer to the secondary wheel 2, the medium in the working chamber 3 passes through a still relatively large annular gap representing the pressure compensating connection 4. As shown in FIG. 4, this flow flows into the compensation chamber 5 into the axial region in which the partial region 1.1 is formed with a relatively small inner circumference radially inward of the housing 7, ie When entering a position close to the secondary wheel 2, it is completely or almost interrupted.

  In the illustrated embodiment, a seal member 8 is further inserted in the stepped region of the inner peripheral surface of the housing 7, and the seal member is brought into contact with the outer periphery 1.2 of the partial region 1.1 or remains. The pressure compensation connection 4 is sealed by significantly narrowing the annular gap. Of course, to omit the step shown in the region of the inner peripheral surface of the housing 7, and thus to form the inner peripheral surface of the housing 7 in a cylindrical shape, and to seal or narrow the pressure compensation connection 4 as desired. It is also possible to provide only one or more sealing members. FIG. 3a shows another embodiment for possible sealing member arrangements. Viewed from top to bottom, the first configuration has a number of seal tips of equal length disposed one after the other on the outer peripheral surface 1.2 of the primary wheel, the tips of the housing 7. Acting in the inner peripheral surface, which is cylindrical in this region; the second configuration has a number of equal length seal tips on the inner peripheral surface of the housing 7, which Are arranged one after the other and act on the cylindrical region of the outer peripheral surface 1.2 of the primary wheel 1; the third configuration has a tip-tip-seal; The form is a point on the outer peripheral surface 1.2 of the primary wheel 1 or on the inner peripheral surface of the housing 7 and is fitted into a groove formed in a cylindrical surface facing it. Other seal configurations are also conceivable.

  The pressure compensating connection shown in FIGS. 1 and 2 and the pressure compensating connection shown in FIGS. 3 and 4 can also be provided simultaneously in a particularly preferred embodiment of the invention.

1 shows a first embodiment of a retarder formed in accordance with the present invention, with a second remotely located rotor. The retarder according to FIG. 1 is shown with the rotor in a first close position. A second embodiment of a retarder formed in accordance with the present invention is shown with a second remotely located rotor. FIG. 4 shows a retarder according to FIG. 3 with a rotor in a first close position.

Claims (9)

1.1 having a winged primary wheel (1) and a winged secondary wheel (2), which together form a working chamber (3) that can be filled with a working medium;
1.2 At least one of the two wheels (1, 2) faces the other wheel in the following direction, ie directly in the axial direction, at least in the partial region (1.1) with its blades The shaft is switchable between a first close position and a second distant position, which is arranged with a greater axial distance relative to the other wheel relative to the first position. Can be displaced in the direction,
In hydrodynamic turbomachines, especially retarders:
1.3 A work chamber (3) arranged on the front side in the axial direction of the displaceable wheel (1) and a rear side of the displaceable wheel (1) facing the front side in the axial direction. A pressure compensation connection (4) for guiding the flow is provided between the compensation chamber (5);
1.4 When the displaceable wheel (1) is in the first position in the working chamber (3) and the compensation chamber (5) as follows: If at least indirectly completely or substantially completely blocked by the displaceable wheel (1), whereas the displaceable wheel (1) is in the second remote position, the pressure compensation Arranged open so that the connection is at least indirectly released by the displaceable wheel (1),
A hydrodynamic turbomachine, especially a retarder.   The pressure compensating connection (4) is interrupted by the displaceable wheel (1) or the displaceable partial area (1.1) of the wheel (1) abutting against other parts of the hydrodynamic turbomachine The hydrodynamic turbomachine according to claim 1.   The pressure-compensating connection (4) is guided through a displaceable wheel (1) or a displaceable partial area (1.1) in the form of one or more shaft holes (6) The hydrodynamic turbomachine according to claim 2.   3. The pressure-compensating connection (4) is formed along the outer peripheral surface (1.2) of the displaceable wheel (1) or the displaceable partial area (1.1). The hydrodynamic turbomachine described.   The hydrodynamic turbomachine has a housing (7) circumferentially surrounding a displaceable wheel (1) and the displaceable wheel (1) or displaceable partial area (1.1) In the first close position, it abuts the housing (7) or the sealing member (8) connected to the housing (7) or the flow of the pressure compensating connection (4) together with the housing (7) or the sealing member (8). The hydrodynamic turbomachine according to claim 4, wherein the cross section is narrowed compared to the second distant position.   The displaceable wheel (1) has an axially fixed partial region (1.3) and an axially displaceable partial region (1.1), and one or more axial holes ( The hydrodynamic turbomachine according to claim 3, characterized in that 6) is closed by the two partial areas (1.1, 1.3) abutting each other.   Hydrodynamic turbomachine according to claim 6, characterized in that the one or more axial holes (6) are arranged in the axially displaceable partial area (1.1).   The hydrodynamic turbomachine according to claim 7, wherein the hydrodynamic turbomachine is a retarder having a rotor and a stator.   The hydrodynamic turbomachine according to claim 8, wherein the rotor is axially displaceable with respect to the stator.

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