JP3129737B2 - Vane machine - Google Patents

Abstract

In order to compensate in an efficient manner the radial and axial forces in a vane cell machine, and at the same time to increase its service life, the vane cell machine for liquids has a slotted rotor (1) mounted in a stator (4), and in which radially movable vanes (9) are slidingly mounted in such a way that they can be pressed against a stator inner wall by centrifugal, elastic or other pressure forces. Expanding or narrowing sickle-shaped feeding cells are formed and the liquid enters through a hollow, central stator, so that the vane cells are filled from the inside towards the outside. The rotor (1) is tubular and designed without a shaft; its two sides are prolonged beyond the working area determined by the vanes and the rotor is mounted in the outer stator by means of its prolongations. The rotor has vane slits that extend from its inner to its outer diameter. In the area of the rotor prolongations, the casing of the stator has hydraulic working surfaces oriented towards the rotor and on whose surface the operation pressure is applied and/or not applied in order to at least partially compensate or avoid radial forces.

Description

Description: FIELD OF THE INVENTION The present invention comprises a rotor supported in a stator, the rotor comprising a radially extending guide slit in which a radially slidable blade is slidably arranged. The blades are urged by centrifugal force and can be pressed against the inner wall of the stator, so that a blade compartment that expands or contracts in a crescent shape when the rotor rotates is formed. The invention relates to a liquid vane machine that runs from inside to outside through a filling port in a compartment.

State of the art The blade machine is formed as a constant displacement pump or a constant displacement motor or as a variable displacement pump or a variable displacement motor. However, vane machines can be used as capacity meters. The advantages of the vane machine are its uniform transport flow and low rotational noise. The problem is caused by the respective radial and axial bearing loads due to the hydraulic pressure.

In the case of a bladed machine with a rotor of the same length as the working range of the blade, the radial bearing load due to hydraulic pressure acts on the product of the projected area of the rotor and the protruding blade and the hydraulic pressure, i.e. on the rotor. Resulting from differential pressure. The small radial load is caused by blade friction on the stator and in the rotor slit and the weight of the rotor. The rotor shafts and bearings are either rigidly formed or costly in terms of the hydraulically disadvantageous multi-stroke type in order to accommodate the radial forces which occur as a whole and the large forces already occurring at low pressure differentials. An attempt is made to offset the forces by a pump or motor structure.

Axial bearing loads due to hydraulic pressure can be prevented by forming the axial hydraulic working surface of the rotor symmetrically. In this case, the hydraulic pressure on the working surface must be equal. In an embodiment with an axially displaceable rotor, which is advantageous for manufacturing and cost reasons, the rotor contacts the stator in one area.
In this case, the balance of the axial forces is not achieved because of the strong hydraulic pressure on the opposite side. As a countermeasure, the rotor was supported so as not to move in the axial direction, and the rotor gap on the end face side was adjusted exactly the same. However, this comes at a cost. For example, for a pneumatic compressor or motor in connection with the subject of the present application, a pneumatic cushioning material is formed on the end face of the rotor, DE-A-41 199
It is provided in some recesses according to 2133455. This recess is between the rotor blades and is supplied with compressible air via a passage. This passage is formed in an arc shape in the cover on the side of the casing. Thus, as the rotor slides axially, a pressure differential is created between the air compression cushions on both sides of the rotor. This pressure difference applies a push-back force towards the center position.

German Patent No. 3120350 also proposes a relatively costly solution for a blade machine. In this case, the shaft-equipped rotor is provided with a bush that is largely slidable in the axial direction. This bush is urged by the conveying pressure in the pressure-urged gap in the axially slidable bearing bush provided on the back surface and the end face, thereby balancing the pressure of the shaft-equipped rotor, Bearing load and friction loss can be minimized. Many precision parts in the hydraulic working range are large and costly,
The disadvantage is that the gap length between the high-pressure range and the low-pressure range must be made relatively long, which results in poor efficiency of the bladed machine. In addition, the shaft projecting from the rotary piston machine for driving and driven causes an axial bearing load due to the differential pressure in the shaft seal and, in the case of slip ring seals, also its spring force. If the balancing is achieved on the opposite side by a symmetrical structure, this bearing load does not occur.

Furthermore, rotary piston pumps are known, for example, from DE-A-123 66 41.
In this rotary piston pump, a rotating cylindrical rotor having a large number of slits in a substantially radial direction is supported in a stator cavity having a uniform cross section, and the blades slide in the slits. In this case, by forming the cross-sectional profile of the stator cavity into an axial shape, a large number of blade compartments are formed between the stator and the rotor. In this vane compartment,
The transport or working medium is supplied and discharged via a tangentially open passage. Of these passages, the suction side or the low pressure side passage is a hole on one side of the blade and leading to the central rotor hollow chamber, and the high pressure side passage on the other side of the blade is respectively connected to each blade. It is connected to an attached axial passage through the rotor. The longitudinal passage communicates with an annular groove formed in the stator side wall. This annular groove is connected to a connection port on the high pressure side of the pump or the motor.

It is known to provide a passage in the rotor that opens into the vane compartment for direct supply and discharge of the transport medium.
This passage is connected to the passage of the stationary casing part. The use of such a rotor passage is advantageous, for example, if one or more working chambers are provided between the outer peripheral surface of the rotor and the outer peripheral wall of the stator cavity. This is because, when a large number of inlets and outlets are provided in the stator wall, the large parts of the working chamber do not act as a range for closing the displacement compartment from the suction side and the discharge side. When a large number of dispensing operations are performed, which reduce the available working chamber and cause a high friction loss, a large part of the working chamber acts as an area closing the displacement compartment.

In order to be able to make the supply and discharge passages in the rotor sufficiently wide, on the other hand to avoid significant weakening of the rotor by the passages, and to reduce the axial thrust from the delivery passages, which exerts an opposing effect on the pressure. To avoid
German Offenlegungsschrift DE 1236941 further proposes to provide, on the pressure side of each blade, a number of grooves extending in the blade sliding direction as passages on the pressure side. This groove is formed in the wall of the associated rotor slit. Further, on both sides of the rotor, one annular groove is provided on each side wall of the stator near the rotor end wall.
A longitudinal passage on the pressure side of the rotor opens in this annular groove. In this case, the annular groove is connected to the pressure connection of the pump or the motor. The rotor cavity into which the low pressure side hole of the rotor communicates is a part of the central longitudinal hole of the shaft connected to the rotor. However, this rotary piston machine is structurally expensive due to the large number of radial holes and holes outside the blade slits and the large number of outlets.

U.S. Pat. No. 3,361,076 describes a vane motor having a rotor mounted on a stator and having a slit in its operating range. This rotor is constructed by bolting a housing for a blade, an end member and a flow bush to each other. The receptacle for the blade has an end flange. This end flange, like the end member, protrudes radially from the outer circumference of the slit rotor and the inner circumference of the stator element, thereby defining a hydraulic working range from the side. The housing for the blades is axially formed as a shaft, is supported by rolling bearings in the stator, is sealed, and is guided out of the bladed motor for housing the drive elements. In this case, the end members are provided with short shaft projections for accommodating the rolling bearings. The filling of the blade compartments takes place from the inside to the outside. In this case, in order to center the movable suction ring complementarily in the axial direction, a rotor having a large outer diameter is provided on both sides beyond the slitted range. Both extensions are mounted on the casing via tapered roller bearings in order to receive radial and axial hydraulic forces. in this case,
The extension as a rotationally sealed shaft is guided out of the machine for a drive connection. A pressure adjustable overflow valve limits the clearance pressure in the clearance created by operating pressure leaks. This gap pressure creates an axial pressure balance over this gap range to the seal diameter at the same pressure. Axial fluid pressure above the unbalanced surface below the seal inner circumference is received by the bearing. In this blade type motor, the blades are biased by springs. As a result, when the spring pressing force is weakened, the blade is not guided along the inner wall of the stator in the operating state, so that the blade is very likely to be broken. Furthermore, the rotor must rotate relative to the stator so that the blades can penetrate into its receiving slit of the rotor against the spring. Therefore, the rotor composed of three members is not formed so as not to have a shaft and is not formed in a tubular shape. The rotor does not have a blade slit penetrating from the inner circumference to the outer circumference. This is because the inner circumference is formed by the distribution bush. The pressure biasing chamber of the stator does not contribute in the region of the rotor extension to offset the radial forces acting only on the rotor part by the operating pressure.
The same pressure that is present in the gap is regulated and limited by the valve, avoiding axial forces due to this pressure due to the working surface coming out of the seal diameter. However, the working surface cannot be offset by pressure in the axial direction below the seal diameter.

U.S. Pat. No. 3,153,384 describes a bladed machine. In the case of this vane type machine, two rotors, two support rotors, two spacer bushes and two balancing disks are provided fixed on the common shaft in the axial direction, separated by spacer disks. ing.
The support rotor is slidably mounted in the housing on a bearing bush. In the bearing bush there is formed a suitable recess which is biased by the operating pressure in order to offset the radial hydraulic forces. The operating pressure is guided from the pressure side to the recess of the bearing bush through an outer conduit. In the case of this vane pump, a working surface biased by the operating pressure and facing the rotor is provided in the stator. In order to offset radial hydraulic forces in the case of vanes with sliding bearings, it is known to provide an additional sliding bearing area with a working surface which is biased by the operating pressure. I have. In the case of this vane pump, there is the disadvantage that an additional gap inflow passage with a relatively short gap length, which is loaded by the operating pressure, is formed and the efficiency is reduced due to an increased capacity loss. In addition, the formation of a dynamic pressure support surface is hindered. This is because the narrow gaps required for this in the bearing area are eliminated by the operating surface provided at this point which is biased by the operating pressure.

From DE-A 1 395 435 a blade-type machine is known in which a rotor supported by a shaft rotates in a stator. In this case, the inner peripheral surface of the stator has three partially circular concave portions. The wall surfaces of the recess are guided so that the connection range of the two wall surfaces is provided in the outer circumference range of the rotor. The rotor has radially extending guide slits for four blades. In this case, the guide stators are arranged in such a way that the two opposing guide slits are offset from one another with respect to the imaginary radial line, so that only one blade is present in each partial circular recess. do not do. In this case, no transport-lubricated sliding bearing for the rotor shaft is provided.

German Offenlegungsschrift 202 284 1 describes a rotary piston pump with circular rotary blades for transport and without a valve. The pump comprises a casing, two or more blades formed as rotating pistons and mounted on a drive hollow shaft, and a fixed profile shaft. This profile axis determines the blade market in the individual working phases. In this case, the drive hollow shaft is eccentrically supported in the pump casing as follows. In other words, a sufficient conveying cross section is formed between the hollow shaft and the casing in the operating range, and the hollow shaft is in sealing contact with the casing in the separation range and is supported to separate the discharge side and the suction side. The blades for sucking and conveying the medium project in the operating range from the hollow shaft to the casing wall. In this case, the drive shaft is formed as a hollow shaft, on which blades are slidably supported in the radial direction and supported by a profile shaft fixedly supported inside the hollow shaft. In this case, the hollow shaft is supported on the pump housing. Thus, no bearing without a shaft is provided.

In the case of rotary piston machines for liquids as transfer pumps with vane compartments, as known from the state of the art, positive inflow by an effective suction head having a high vapor pressure and increasing rapidly with rotation speed For liquids with a head, operation with an economical drive speed of, for example, 1450 rpm is no longer possible.

The volumetric efficiency and dry suction capacity (in the case of an empty pump) of a vane pump are determined by gap losses. The order of the gap depends on the length of the gap, assuming that the product to be conveyed has the same manufacturing accuracy and pressure difference. Thus, for comparable transport flows, a slowly rotating pump with a large periodic discharge and a long gap length has a greater volumetric efficiency than a rapidly rotating pump with a small periodic discharge and a short gap length. And dry inhalation ability is small. This technical relationship limits the potential for structural improvements in volumetric efficiency and dry suction capacity due to the required rotational speed limitation by the effective suction head.

In addition, liquid rotary piston machines require dimensioned shafts and bearings due to the large differential pressure biased large projected area formed by the rotor and the protruding blades. If the rotary piston machine is formed as a double-stroke vane pump or vane motor, it does not require a measured shaft and bearings, but this pump or motor has two inlets and outlets respectively for the liquid. Equipped with means that are costly in terms of manufacturing technology, and in the case of a pump, the effective suction head is raised and exacerbated.

Problem, Solution, Effect The problem of the present invention is that the balance of radial and axial forces is achieved completely or fully, the wear is minimized in view of the long service life and a high high rate is achieved. It is an improvement of the known vane type machine. When the vane machine is a volume meter, the measurement accuracy should be improved. Another object of the present invention is to extend the application as a pump by reducing the effective suction head and to improve the efficiency in the case of a machine used as a pump or a motor. It is a further object of the present invention to improve at least some or all of the axial and radial hydraulic loads by means of structural measures without significant structural costs.

This object is achieved by a bladed machine according to claim 1.

In accordance with this, a blade-shaped machine is characterized in that the rotor is formed tubular without a shaft and extends on both sides beyond the working range of the blade, this extension being supported by the outer stator, and the rotor being moved from the inner circumference to the outer circumference. A penetrating vane slit, in which case the peripheral wall of the stator is biased and / or biased by pressure on its surface in the region of the rotor extension in order to at least partially offset or avoid radially occurring forces. It is characterized in that it comprises a hydraulically actuated surface which is released and faces towards the rotor. However, in the case of a rotor having no shaft and extending from the operating range to both sides, pressure acts on the bearing gap between the rotor and the outer stator. This results in other bearing loads. On the other hand, the radially unloaded portion is significantly reduced by the recess (working surface) in the stator peripheral wall which has been unloaded from the pressure.

According to another embodiment, in a vane-shaped machine, the passage for filling the vane compartment, in which liquid flows through a hollow concentric stator, is provided by radial recesses in the vanes and / or vane slits. The concentric stator has on its surface a pressure-biased working surface towards the rotor for at least partially offsetting the radial forces. In this case, the hydraulically energizable recess can be replaced by a small hole which is energized by pressure. This bore creates a large pressure-working surface in the bearing gap between the rotor and the outer stator, facing away from the rotor. This measure is simple to produce and has relatively low gap losses, thereby improving volumetric efficiency. This vane machine is advantageous because it is simple to construct. In this case, the relatively expensive additional bearings and the frictional forces which occur during these bearings are initially minimized, such as the axial and radial hydraulic forces.

The radial passage is then formed by a radial recess in the blade and / or in the blade slit to fill the blade compartment, which radial recess extends from the outer periphery to both sides beyond the operating range of the blade. As the inner circumference of the protruding shaftless rotor extends through to the rotor longitudinal bore, liquid flows axially into the hollow rotor shaft and fills the expanding vane compartment with a radius through a window opening in the rotor shaft. Direction and through the holes in the rotor slits and / or blades.

The rotor part or the rotor parts on both sides projecting beyond the operating range are rotatable relative to the stator and are sealed in. In the case of a pump, significant advantages are associated with the effective suction head. This is because only the loss of introduction of liquid into the rotor slit is relevant to the effective absorption head, and other pressure losses up to the filling of the vane compartments, and hence the speed increase of the liquid associated with centrifugal force, cause energy to be lost by the drive. In addition, it occurs. Furthermore, when the blade compartment is filled with liquid in the radial direction from the inside via the rotor slit, the stroke volume of the blade in the rotor slit is taken into account in the periodic working volume of the pump or motor, with the known state of the art. As such, the advantage is that there is no need to specially fill this stroke volume against centrifugal forces, as is the case for filling the vane compartments from the outside, tangentially or axially. In the case of pumps and motors, the rotor shaft, which at the same time serves as a liquid inlet and as a bearing for the rotor, is hydraulically supported with respect to the rotor shaft, in particular at low cost to balance hydraulic pressure in the radial direction. Advantageously, it is possible.

 Further embodiments of the invention are described in the dependent claims.

No other pressure source or control is required, for example, because the recess is energized in particular by the pressure of the liquid.

In a first embodiment, the recesses in the stator peripheral wall are arranged opposite the rotor peripheral wall outside the operating range of the blades, ie symmetrically with respect to a vertical plane passing through the operating range of the blades. In another embodiment, the recess is provided on the outer peripheral surface of the stator shaft. The stator shaft is inserted into a concentric hole in the rotor tube and is in sealing contact with the rotor tube. This embodiment has the advantage that the recess can be provided at the same height as the operating range of the blade, thereby possibly reducing the structural height. Furthermore, combinations of the above embodiments are possible.

In another embodiment of the invention, the rotor portion projecting beyond the operating range of the blade has the same outer diameter or outer diameter as compared to its diameter within the operating range of the blade. By reducing the diameter outside the operating range of the vanes, the advantage is that the rotor is axially centered during the rotary operation of the vane machine.

When the blade machine is stopped, the blade is sinking in the rotor slit. This allows the rotor to slide axially since the entire rotor has the same diameter. If the rotor has a reduced diameter and the rotor is freely movable in the axial direction, the difference in diameter serves to center the rotor with respect to the working chamber. In this case, the above-described disadvantage that the hydraulic pressure acts strongly on one side due to the contact on the opposite side does not occur. This is because the working surface is reduced by a small diameter difference. Due to the centering of this rotor in the working chamber, a gap is formed between the end face of the rotor and the stators on both sides for the balancing of the hydrostatic forces at the same pressure.

If the rotor has the same diameter and extends on both sides, the necessary centering of the rotor with respect to the working chamber is provided by the vanes. The space in the guide slit below the blades communicates with the blade compartment which is short in the direction of rotation, for example by radial recesses of the blades and / or the rotor. The blades that are moved radially outward by the centrifugal force sink into the rotor when the blade machine is stopped, and the freely moving rotor can slide to one side in the axial direction toward the stator on the end face side. As the stator of the blade-type machine starts, the stator prevents or tilts the blade from popping out, so that the stator portion that defines the working chamber from the side moves toward the rotation axis in the range of the blade that is not loaded by the pressure difference. The room is slightly tapered to enlarge it. This taper is formed on both sides to be somewhat wider than the axial movement distance of the rotor in the stator, so that when the blade-shaped machine starts rotating, the centrifugal force causes the vanes to move out of the rotor immediately relative to the working chamber. Since the centering takes place and there is no axial force, this centering is kept free of additional friction with the blades.

In a special embodiment of the bladed machine according to the invention, the rotor is formed in a tubular shape and has a longitudinal hole in which an even number of blade slits are opened, each diametrically opposed blade being connected to one another. It is fixedly connected or integrally formed.

But instead, the rotor is formed in a tubular shape, the stator shaft is inserted into the bore of this tube, the inside of this stator shaft is hollow, for the vanes on which the stator shaft can slide,
A window opening may be provided in the area of the slit passing through the rotor in the radial direction, and the blade and / or the rotor slit may have a radial recess. This embodiment balances the radial hydraulic force partially on the rotor.

The rotor is preferably connected at one end face to an axially fixed shaft as a drive connection or a driven connection. In this case, the shaft is housed in the stator casing.

In particular, in the filling area of the blade compartment, the stator bore is formed radially outward in a partial circle over the range of the maximum radial run-out of the blade, and through the recess formed thereby, the two or more blades The compartments communicate. The blades facilitate filling of the blade compartment.

Furthermore, a guide for the blades in the stator peripheral wall transition area between the expanding blade section and the narrowing blade section or in the area between the two blade sections is provided coaxially with the rotor rotation axis, whereby the blades rotate during rotation. It does not move radially in this transition range, which is loaded with differential pressure.

According to another embodiment, the inner rotor outer peripheral wall at least partially offsets the radial hydraulic bearing load.
A recess is provided which can be hydraulically biased by pumping pressure or motor inlet pressure. Due to this measure, which is simple in construction, a rigidly formed bearing can be dispensed with.

The rotor part protruding from the operating range of the blade has, in particular, a smaller outer diameter compared to the rotor diameter in the operating range of the blade. Thereby, the rotor is centered in the axial direction during operation.

The blade sinks into the rotor slit when the rotor stops. Thereby, the rotor can slide in the axial direction without reducing the outer diameter. When the rotor is restarted, the stator peripheral wall which defines the operating range of the blade from the side is not biased by pressure to prevent the blade from being accidentally tilted by the inner circumferential surface of the stator outside the operating range. Due to the tapered shape in the region, the blades are forcibly guided to an axial centering position at start-up.

According to another embodiment, the rotor is connected at its end face opposite the inlet directly to the drive or driven shaft or via a coupling. In this case, the shaft is sealed and guided in the stator housing.

BRIEF DESCRIPTION OF THE DRAWINGS Next, an embodiment of the present invention will be described in detail with reference to the drawings.

1 is a vertical sectional view of a blade-type machine, FIG. 2 is a vertical sectional view taken along a line II-II of FIG. 1, and FIG. 3 is a cone formed between an operating range of a blade and an adjacent stator peripheral wall. FIG. 4 is a partial longitudinal sectional view of a bladed machine having a limited range of movement, FIG. 4 is a sectional view of a bladed machine provided with a tubular rotor, and diametrically opposed blades are connected to each other; FIG. 6 is a vertical sectional view taken along line VV, FIG. 6 is a sectional view of a bladed machine having a rotor having a central hole into which a stator shaft is fitted, and FIG. 7 is a vertical section taken along line VII-VII in FIG. FIG. 8, FIG. 8 is a vertical sectional view of an embodiment in which an inlet connection portion is formed at the center of the stator, FIG. 9 is a vertical sectional view taken along line IX-IX of FIG. 8, and FIG. FIG. 11 is a longitudinal sectional view of the embodiment, FIG. 11 is a transverse sectional view at a height position of an operating range of the blade perpendicular to the section of FIG. 10, and FIG. Vertical cross-sectional view of FIG. 13 is a vertical sectional view taken along line XIII-XIII in FIG.

DETAILED DESCRIPTION OF THE INVENTION AND BEST MODE FOR CARRYING OUT THE INVENTION A vane machine, preferably formed as a single-stroke vane machine, is formed as a pump in the embodiment shown in FIGS. . This pump has a shaftless rotor 1. The rotor may have, in the axial direction, an outer diameter 2 having the same outer circumference as the operating range 15 of the blade, or an outer diameter having an outer circumference 3 that is smaller than this.
Outside the operating range of the blades, the rotor 1
It is fitted so as to be hermetically supported inside. The stator has a recess 5 in this fitting range. This recess is formed in the following position and size. That is, the pressure of the liquid acting therein is formed so as to provide a partial or complete liquid pressure balance, taking into account frictional forces and gravity. In the embodiment shown in FIG. 2, the recesses 5 are arranged axially in front of or behind the operating range 15 of the blade and symmetrically with respect to the operating range of the blade.

If the rotor 1 has a difference in diameter, as shown in the upper half of FIG. 2, the vertical step surface, ie the end face with the difference in diameter 6, simultaneously serves for axial centering of the rotor. This results in a gap 7 of the same size between the rotor end and the opposing stator end during rotation. For rotors with reduced diameter,
The end face having the diameter difference 6 serves for positioning the rotor with respect to the working chamber. In this case, by contacting on both sides, the aforementioned disadvantage of the hydraulic pressure acting strongly on one side can be accepted. This is because the end face 6 as the working surface is kept small by a small diameter difference. By positioning the rotor with respect to the working chamber in this manner, between the end face of the rotor 1 and the stators 4 on both sides,
In the case of the same pressure, the gap 7 for balancing the static pressure force is reliably formed.

The rotors 1 each have a slit 8 extending in the radial direction. The blade 9 is slidably guided in this slit. Each space in the guide slit 8 below the blade 9 communicates with a blade compartment located on the near side in the rotation direction. In the present embodiment, they are communicated by a radial recess 10 in the blade and / or a recess 11 in the rotor. During operation, the blades that move outward due to centrifugal force can sink into the rotor when the blade pump is stopped, as shown in FIG. 4 is slidable to one side in the axial direction toward the end face. This prevents the blades 9 from going out when starting the blade machine. Since this can cause the blades to tilt on the stator inner wall, the stator inner peripheral wall portion 12 that defines the working chamber 15 from the side within the range of the blades 9 that is not biased by the differential pressure is moved toward the rotation axis. It is tapered or slightly inclined to widen the working chamber. The tapered or inclined stator inner peripheral wall portion 12 is formed on both sides thereof over a range slightly larger than the axial movement distance of the rotor 1 in the stator. Thus, at the start of the rotation of the blade-type machine, the blades going out by centrifugal force immediately center the rotor 1 with respect to the working chamber 15 and do not exert any axial force and produce additional friction on the blades 9. Do not maintain this centering position.

The connection of the drives and driven devices of the bladed machine takes place via a shaft 13 which reaches into the stator housing 4 and is sealed there. This shaft is connected to the rotor via a joint 14 so that no reaction occurs in the axial direction.

6 and 7, the rotor 1 is formed in a tubular shape, extending on both sides beyond the operating range determined by the blades 9, having extensions 1 ′, 1 ″. In this case, the stator shaft 16 is concentrically inserted into the hole of the tube, and the stator shaft 16 is fixedly connected to the other stator portions.With this configuration, the hydraulic pressure in the range of the tube slit is applied to the rotor. Hydraulic forces and radial forces caused by weight and friction are not actuated by hydraulically biased, concentric recesses 17 or
18 partially or completely offset depending on the position and size of the recess. In the case of a pump, the recess 17 is provided in a range where the blade compartment is small, and in the case of a motor or a volume meter, the recess 18 is provided in a range where the blade compartment is large.

In the case of the above-described embodiment, the filling of the expanding blade compartment is performed almost tangentially from the outside, but in the embodiment shown in FIGS. 8 and 9, the inlet is formed hollow to the end of the working chamber width 20. Provided on the fixed stator shaft 16. This stator has a window 21 in the working range 15 of the spreading blade 9. In this case, the blade 9 and / or the rotor 1 has a radial recess 1.
0 and 11 are provided. With the aid of centrifugal force, the filling of the blade compartment expanding from this recess takes place. Recess 1
0,11 are provided on the rotor at the rear of the blade and / or just behind the blade, viewed in the direction of rotation.

The blade-shaped machine shown in FIGS. 10 and 11 includes a rotor 111 supported on a hollow shaft 110 as a tubular concentric stator 100. The rotor is rotatably disposed and surrounds a central axis within the stator 112. Stator 112
As can be seen from 10, there are two parts, especially the hollow shaft 11
It has a component 113 integrated with 0. Rotor 111
Outside the operating range of the blade 124 (FIG. 10), each has a diameter reduced laterally from the operating range, and its outer peripheral surface is in sealing contact with the inner peripheral surface of the stator. End face of rotor 114,115
A gap 116 is provided between the
Or 117 is formed. This gap is urged by pressure. An axial hole 118 and a radial hole 118 'are provided to balance the pressure between the gaps 116 and 117. The rotor is driven or driven by a shaft 119
Or directly through a joint (not shown). The shaft 119 is rotatably and sealingly supported on a stator casing or a driving machine or a driven machine. The hollow shaft 110 has an end face-side entrance accessible from the direction of arrow 120. The inlet communicates with the groove-shaped recess 112 extending in the radial direction of the rotor and the recess 123 of the blade via the window opening 121 of the hollow shaft and the corresponding recess of the rotor. The blades 124 are in radial slits 125 of the rotor 111. The concentric tubular stator 100 has a recess 1 on its rotating surface.
It has 26. This recess 126 is hydraulically biased by the pumping pressure of the pump or the inlet pressure of the motor and is arranged so that the radial hydraulic bearing load is partially or completely canceled.

Spaces between the rotor 111 and the stator 112 and including the crescent-shaped blade compartments 127 are divided by the blades 124, respectively. The vanes rotate along the area indicated by arcs 128 at their ends. Furthermore, the inner circumferential surface of the stator is provided with an additional recess 129. This recess projects in a crescent shape from the maximum radial runout (arc 128).

A transition area 130 is provided between the expanding blade compartment and the narrowing blade compartment 127. In this transition range, the blade does not move in the radial direction when rotating in the direction of arrow 131.

 The blade-shaped machine shown in FIGS. 10 and 11 operates as follows.

The liquid flowing from the direction of the arrow 120 is guided radially outward into the blade compartment 127 through the window opening 121 and the groove-shaped radial concave portions 122 and 123, and is discharged almost in the tangential direction toward the arrow 32. . Thereby, in the case of a pump, the inflow of the liquid from the hollow shaft and the filling of the expanding vane compartment from inside to outside are performed by the energy supply from the drive, which has a low efficiency even at high rotational speeds. It becomes a suction head. At the same time, hydraulic balancing can be achieved by simple structural measures.

FIGS. 12 and 13 show, on the basis of the example of a pump, a functionally and technically highly advantageous embodiment of the radial hydraulic force balancing device acting on the rotor.

The tubular rotor 201 is slidably supported on both bearings 202,203. The single-stroke suction ring 204 forms a working chamber 205 and is fixedly connected to bearings 202 and 203. An outer cylindrical stator composed of these three members 202, 203, 204 is inserted into a pump casing 207 having a gap 206 for guiding or flowing liquid, and is sealed at both ends to the pump casing by O-rings 208. A pressure outlet 209 in the suction ring is
When shifting to 218, the pump pressure
Reach 06.

In opposition to radial hydraulic forces acting on the rotor substantially in the direction of the section line in FIG.
02,203. This bore allows an opposing pressure to be exerted on the rotor within the bearing area, balancing the pressure partially or completely.

The inner rotor 213 is fitted inside the rotor 201 in a non-contact and narrow gap. Via the inlet 214 of the inner rotor 213 which continues to the drive side and the window opening 215 in the area of the expanding blade compartment, the blade compartment is filled. Via the through holes 214 and 216, the inlet pressure acts on both end faces of the rotor.

In order to limit the hydraulic radial pressure to the working range, i.e. the axial length of the suction ring 204, the bearing is mounted in the hydraulic radial compressive force working area with a recess 21.
Has one. Since the recess communicates with the gap 217 on the low pressure side via the holes 214 and 218, a short bearing 212 is formed in the area of the recess 211, which is sufficient for the seal and the bearing.

Through the slit 217 in the rotor, the hydraulic operating pressure acts directly on the tubular concentric stator without biasing the rotor, and further through the rotor stator a gap between the rotor and the tubular concentric stator is formed. Energized by pressure. This pressure further contributes to a partial pressure balance.

Continuation of the front page (51) Int.Cl. ⁷ Identification symbol FI G01F 3/10 G01F 3/10 C (56) References JP-A-60-95197 (JP, A) JP-A-64-73179 (JP, A JP-A-56-96196 (JP, A) JP-A-1-1555091 (JP, A) JP-A-57-70982 (JP, A) JP-A-60-187783 (JP, A) JP-A 61-96 87990 (JP, A) Japanese Utility Model Showa 61-99688 (JP, U) Japanese Utility Model Showa 64-25486 (JP, U) Japanese Patent Publication 57-38792 (JP, B2) Japanese Patent Publication 61-47316 (JP, B2) (58) Field surveyed (Int.Cl. ⁷ , DB name) F04C 2/30-2/352 F03C 2/30 G01F 3/10

Claims (21)

(57) [Claims] 1. A rotor (1) mounted in a stator (4), said rotor having a radially extending guide slit (8) in which a radially slidable blade (8) is provided. 9) is slidably disposed, the blades are urged by centrifugal force and can be pressed against the inner wall of the stator (4), so that a blade compartment that expands or contracts in a crescent shape when the rotor rotates is formed, and the inflow of liquid is prevented. A liquid vane machine, which runs from the inside to the outside through a tubular concentric stator (16,100) and a vane compartment, a) penetrating from the inner circumference to the outer circumference within the working range (15) of the blade (9) A shaftless, tubularly formed rotor (1) provided with a radial guide slit (8) extending beyond the working range (15) of the blade (9) to both sides, this extension being The operating range of the blade (15) is smaller than the rotor diameter A small gap is formed between the surface of the extension and the outer concentric stator (4), b) the rotor extensions (1 ', 1 ") on both sides are fixed to the stator (4)
C) The rotor (1) is slidably mounted on its inner circumference on a stator (16,100) concentric over the entire length of the rotor, d) The circumferential wall of the stator (4) is laterally attached to the rotor (1). Wing-shaped machine, characterized in that, in the area of its extension (1 ', 1 "), the surface thereof is provided with a hydraulically actuated surface facing the rotor (1) which is unloaded. 2. Transfer of the inlet pressure to the bearing gap between the rotor (1) and the stator (4) within the two extensions (1 ', 1 ") of the rotor whose bearing is loaded by the inlet pressure. 2. A blade according to claim 1, characterized in that a bore (216) is provided in the concentric stator (213) in the region of the two extensions (1 ', 1 ") of the rotor. machine. 3. A stator (112) having a slit rotor (111) supported therein, and a radially slidable blade (124) provided in the rotor, wherein the rotor is A longitudinal hole is provided from which the grooved radial recesses (122,123) extend into the blade compartment (127), and the stator comprises a tubular concentric stator (100) to fill the blade compartment. A groove-shaped radial recess (122, 123) is formed in the blade (124) and / or the blade slit (125) to allow the radial recess to extend from the outer periphery beyond the operating range of the blade (124). The liquid extends into the hollow rotor shaft (110) from the axial direction and penetrates to the rotor vertical hole as the inner periphery of the shaftless rotor (111) protruding on both sides, and spreads to the expanding blade compartment (127). Filling takes place radially through a window opening (121) in the rotor shaft. The recess of the rotor (111) and or vanes (124) (12
Claim 1 characterized by being performed through 2)
Item or the bladed machine according to item 2. 4. The rotor (1) is hermetically supported outside the operating range of the blade and is fitted into the stator (4), the stator (4) having a recess (5, 17, 18) in the fitting range. This recess faces the rotor outer peripheral wall outside the operating range (15) of the blade and / or the stator shaft (16).
The blade shape according to any one of claims 1 to 3, wherein the stator shaft is inserted into a central hole of the tubular rotor and is in sealing contact with the tubular rotor. machine. 5. The rotor (1) is hermetically supported outside the operating range of the blades and fitted into the stator (4), in which fitting the stator (4) is recessed (5, 17, 1).
8) The blade-type machine according to any one of claims 1 to 4, further comprising (8), wherein a liquid pressure is applied to the recess. 6. The rotor part projecting beyond the operating range of the blade (15) has the same outer diameter or a smaller outer diameter (2,3) compared to its diameter in the operating range (15) of the blade. The blade-shaped machine according to any one of claims 1 to 5, characterized by having: 7. A stator peripheral wall (12) defining a side of an operating range (15) of a blade is tapered so as to widen an operating chamber toward a rotation axis in a range of the blade which is not biased by pressure. 7. The method as claimed in claim 1, wherein the slope is extended on both sides longer than a distance corresponding to the axial movement of the rotor (1). Or one vane machine. 8. The rotor (1) is formed in a tubular shape and has a longitudinal hole, in which an even number of blade slits (8) are opened, each of which has a diametrically opposed blade (9). The blade machine according to any one of claims 1 to 7, which is fixedly connected to each other or integrally formed. 9. A rotor (1) is formed in a tubular shape, and a stator shaft (16) is inserted into a hole of the tube. The inside of the stator shaft is hollow, and the stator shaft is slidable in a radial direction. Window opening (21) in the area of the slit (8) for (9)
9. A blade-type machine according to claim 1, wherein the blades (9) and / or the slits (8) are provided with radial recesses (10, 11). 10. A shaftless rotor (1) extends on both sides beyond the operating range of the blades (9), this extension having the same diameter or a reduced diameter, and the flame spread (1 ', 1 "). ) Is easily rotatably fitted into the area of the stator (4) so as to seal the gap, and the stator (4) is biased on both sides by pressure in the area of the rotor extension (1 ', 1 "). 2. The method according to claim 1, wherein the position and size of the recess are determined so as to partially or completely cancel the radial hydraulic force and gravity.
Item 10. The blade-shaped machine according to any one of Items 9 to 9. 11. The rotor (1) is connected at one end to an axially fixed shaft (13) as a drive connection or a driven connection. 11. The bladed machine according to any one of items 1 to 10. 12. A stator hole is formed in a partially circular shape radially outward beyond a range of a maximum deflection (128) in the radial direction of the blade (124) in a range in which the blade compartment (127) is filled with liquid. 12. The blade-shaped machine according to claim 1, wherein two or more blade compartments (127) communicate with each other via a recess (129) formed thereby. . 13. A guide for a blade (124) in a stator peripheral wall transition area (130) between an expanding blade section and a narrowing blade section (127) or in a range between two blade sections (127), 13. The bladed machine according to claim 1, wherein the blade is arranged coaxially with the axis of rotation of the rotor, so that the blades do not move radially in this transition region during rotation. . 14. A tubular concentric stator (100) having a recess (126) for offsetting at least a portion of a radial and / or axial hydraulic bearing load. The vane machine according to any one of claims 1 to 13. 15. The stator according to claim 1, wherein the peripheral wall defining the side of the operating range of the blade is tapered in the range of the blade which is not biased by pressure. Any one vane machine. 16. A blade according to any one of claims 1 to 15, characterized in that the gaps (116, 117) on the end face side are balanced in pressure via hydraulic connections (118, 118 '). Shape machine. 17. The rotor (111) has an end face opposite to the inlet, which is connected directly to a shaft (119) as a driving device or a driven device, or is connected via a joint. A bladed machine according to any one of claims 1 to 16. 18. A suction ring (2) having an outlet (209).
04) is fixedly connected to the bearings (202, 203) on both sides, inserted as a cylindrical unit into the casing (207), and both ends are sealed to the casing. Any one of the bladed machines of paragraph 17. 19. A suction ring (204) and a bearing (202, 203).
A cylindrical unit having a diameter smaller than that of the casing hole, and the entire circumference of the cylindrical unit being a suction ring (20).
19. The bladed machine according to claim 1, wherein the blade is urged by the pressure of the outlet (209). 20. The bearing according to claim 20, wherein one or more radial holes (210) are provided in the bearings (202, 203) substantially opposite the hydraulic force in the radial direction with respect to the axis of rotation. Item 19. The blade machine according to any one of Items 1 to 19. 21. The method according to claim 1, wherein the tubular concentric stator (213) is fitted into the inner periphery of the rotor (201) without contact and with a narrow gap. One vane machine.