JPH1030579A - Rotary turning vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure stable operation for a long period by arranging a surface profile shape part which is displaced from a straight line matched with the shape of the control rim of a reversing element at a horizontal cross sectional surface which is perpendicular to a turning axial line, in a turning contact range where the pressure surface of a vane is brought into contact with the control rim of a reversing member. SOLUTION: In a pump 20 in which four turning vanes 35 are arranged in a ring shaped passage 30 freely to turn, in an annular passage 30, its feed passage part 54 is formed on a horizontal cross sectional surface corresponding to the shape of a vane 70 arranged in a horizontal direction to a rotational direction. A reversing member 90.1 formed by a cylindrical rod which is bent about 90 deg. is arranged on a part which is transferred from the feed passage part 54 to a seal passage part 55 due to turn a turning vane 35. A change member is arranged on a position which is symmetrically with the change member 90.1 in the range of a flow-in part 31, and an invasion member 91.2 is arranged on the change member to help turning of the vane 70 in the case where a pump is operated in a direction reverse to a rotary direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary swirl vane pump having a driving device and an annular passage having a suction connection and a pressure connection, wherein a feed passage portion of the passage is fixed. A swirl vane formed with a plurality of flat vanes, the swirl vane being coupled to the drive device, the swirl vane having a cross section of The swirl vane is pivotable about a pivot axis in a plane positioned in the rotational direction, and the swirl vane is located in a direction substantially orthogonal to the rotational direction in a pressure plane at a feed passage portion; A seal passage portion is provided in the passage between the suction connection and the pressure connection, the seal passage portion having a lateral shape corresponding to the shape of a swirl vane swiveled in the rotational direction. Has a surface and further wherein the seal passage portion are constantly sealed by at least one swirl vane passes, provided further from the feed passage portion at the transition to the sealing passage portion,
It is of the type provided with at least one deflection member for pivoting the vane, having a control edge or surface.

[0002]

2. Description of the Related Art Two types of rotary swivel vane pumps are known from the viewpoint of the type of support of the swirl vane. In a first configuration, the swirl vanes are swivelable about a swivel axis located radially or perpendicular to the rotational axis. The disk-shaped vane is located in a direction orthogonal to the rotation direction in the feed passage portion, and is located parallel to the rotation direction in the seal passage portion. Based on the disc-shaped configuration,
Regarding the cross section of the vane in the plane including the rotation axis, the cross section in the feed passage portion is formed larger than the cross section in the seal passage portion. The vanes are in particular often formed by flat circular disks, but may also be formed by flat rectangular disks. Pumps of this type are described, for example, in DE-OS 2 160 162 and 23 543.
No. 75, No. 2,553,192 and No. 3,046,155.

[0003] In a second configuration, the swirl vane's swivel axis is not located radially or at right angles to the rotational axis, but rather is parallel to the rotational axis. In many arrangements formed according to this principle, the swirl vane is swiveled into a notch formed in the hub in the seal passage, so that the cross-section of the swirl vane in the plane containing the axis of rotation is zero in the seal passage. Becomes An axial swirl vane pump of this type is disclosed, for example, in DE-A-28 45 658.

[0004] In order to swivel the swirl vane, there are also known two principal configurations of a swivel mechanism. In the first configuration, the support pins of the swirl vane are driven such that the vanes occupy predetermined positions in the feed passage portion and the seal passage portion, respectively. Rotary swirl vane pumps provided with such a swivel mechanism are disclosed, for example, in German Patent Application Publication Nos. 2553192 and 2845.
No. 658, Austrian Patent No. 9304 and German Patent DE 230 929.

In the second configuration of the swivel mechanism, the vane must be displaced from this constriction by swirling, since the feed passage or a part thereof is often formed so as to narrow from the side of the swivel axis. The return of the swirl vanes is effected by means of a spring, as described, for example, in U.S. Pat. No. 2,135,161, or by coupling with a swirl vane located on the opposite side with respect to the axis of rotation. The swirl vane, upon climbing over the constriction, causes the opposite swivel vane coupled to the swirl vane to swirl together by its swiveling motion. Such a configuration is described, for example, in DE-OS 2 160 162 and EP-A 2 354 37.
No. 5 and No. 3046155.

In particular, rotary swirl vane pumps of the last-mentioned type, in which swirling of the swirl vanes is effected by contact of the vanes in a constriction provided at the transition from the feed passage section to the seal passage section. In the case of, wear on the pressure surface of the vane cannot be avoided particularly during long-time operation. This can lead to inconveniences when turning the vanes, which can eventually lead to complete pump failure.

For example, many rotary swirl vane pumps, such as those disclosed in US Pat. Nos. 2,135,161, 7,136,63 and DE-A-2,160,162, force the swirl of the vanes. The constriction is formed in the form of a relatively long contact lamp with a gentle rising angle. This requires a relatively large range of the pump passage or a relatively large rotation angle range for swiveling the swirl vanes. As a result, the delivery power of the pump is correspondingly limited. Therefore, it would be advantageous to limit the constriction to a relatively small area of the pump passage, i.e., to use as much of a deflection member as possible to allow the swivel vane to swivel only to a small angle of rotation. Seem. Further, in order to obtain a high conveyance output, it is necessary to form the swirl vane so that the swirl vane reliably seals the seal passage portion. In this case, however, undesirable trapping of the vanes in the region of the constriction can occur, which can lead to vane destruction and, consequently, complete failure of the pump. Since only relatively rigid vanes made of steel or plastics of corresponding properties are used for reliable operation, to mitigate this problem, flexible flexible vanes which allow relatively large elastic deformations have hitherto been used. The narrow portion is formed by a deflection member, for example, a deflection member made of rubber. Such an arrangement is known from DE-A 30 46 155. This pump has hitherto proved to be particularly advantageous for the pumping of highly abrasive substances and / or corrosive media, for example liquids or vinegar containing fruit acid. In such a pump configuration, the entire annular passage is completely lined with plastic or rubber, which ensures that corrosive substances do not come into contact with the metal parts of the pump casing. However, in this configuration, a relatively large amount of energy is absorbed when the swirl vane is swirled in the narrow area. Therefore, operation of this pump requires relatively high drive energy.

[0008]

SUMMARY OF THE INVENTION The object of the invention is to improve a rotary swirl vane pump of the type mentioned at the outset, so that a reliable operation over a long period of time is possible, while at the same time a large transfer power and an energy-saving operation type. It is another object of the present invention to provide a rotary swirl vane pump capable of performing the above-mentioned operations.

[0009]

SUMMARY OF THE INVENTION In order to solve this problem, according to an embodiment of the present invention, the pressure surface of the vane has a swivel contact area where it contacts the control edge or control surface of the deflection member.
The cross section perpendicular to the pivot axis has a surface profile which is adapted to the shape of the control edge or control surface of the deflecting element and is displaced from a straight line.

[0010]

With the design according to the invention, on the one hand, advantageous sliding and moment properties are obtained, so that the vanes are reliably prevented from catching in the area of the deflecting element forming the constriction. You. On the other hand, the arrangement according to the invention makes it possible to limit the swirling of the vanes to a small area or a small angular range of the pump chamber, so that a maximum transport output is possible. further,
The design of the swirl vanes according to the invention makes it possible to dispense with the use of energy-absorbing materials in the swivel contact area, which makes it possible to operate the pump with low drive energy.

In a preferred embodiment of the invention, the pressure surface of the vane is concave at least in a partial region.
With this configuration, an optimal sealing of the seal passage portion in relation to an optimal transport output is possible, together with advantageous sliding characteristics and moment characteristics during the turning of the blade.

In another advantageous embodiment of the invention, the surface contour of the pressure surface is continuous, preferably elliptical or circular, in the cross-section perpendicular to the pivot axis in the pivot contact area. Is formed by the cam shape formed in the above. This means a uniform swivel movement of the burn with favorable moment and power action characteristics.

In a further advantageous embodiment of the invention, there is provided an intrusion member having a control edge or a control surface, which is associated with the deflecting member and which pivots the swirl vane during rotation of the swirl vane. In relation to the plane of rotation described by the axis, it is located opposite the diverting member and is circumferentially offset from this diverting member. With this configuration, a reliable swirling of the vane is possible even after a long operation of the pump.

In another advantageous embodiment of the invention, the deflecting member and the penetrating member are such that the turning angle corresponding to the turning of the vane at the diverting member is greater than the penetrating turning angle corresponding to the turning of the vane at the penetrating member. It is designed to be very large, so that the pivot angle is preferably greater than 60 °. With this configuration, the vane can be relatively quickly turned, and the acceleration force generated in this case can be considered at the same time. In this case, a reliable inward swiveling of the vane into the sealing passage is ensured, despite wear which cannot be avoided during relatively long running.

In another advantageous embodiment of the invention, the pressure surface of the vane and the control edge or control surface of the penetrating and / or deflecting member have a revolving angle of rotation corresponding to approximately 90 ° rotation of the swirl vane. They are aligned with each other so as to be less than 40 °. Such a measure enables a large transport output with a reliable operation for a long time.

In an advantageous embodiment of the invention, the deflecting member is 9
It is formed by a cross-section circular rod or a cross-section circular tube curved at an angle of 0 °. With this configuration, the diverter occupies a minimum amount of space in the pump passage without obstructing the transport flow. This is especially true
It is advantageous when conveying a sensitive liquid medium containing flake-like components, so that the liquid medium is not exposed to undesired compression or shearing in this area.

In a preferred embodiment of the deflecting element, the surface profile of the control edge or the control surface of the deflecting element is circular in a cross section which is formed perpendicular to the pivot axis. This ensures a sufficiently fast swirling of the vanes in a small space.

In a preferred embodiment of the invention, the pressure surface of the vane has a radius of curvature greater than the radius of curvature of the control edge or control surface of the deflecting member in the swiveling contact area.

In a further advantageous embodiment of the invention, the pressure surfaces of the vanes extend flat and parallel to one another outside the swiveling contact area, and are in this case substantially square in the plane having the axis of rotation. It has a shape. In this way, a very good sealing of the sealing channel is possible, and on the one hand a complete sealing is already guaranteed immediately after the vane enters the sealing channel, and on the other hand a sealing The passage portion is sealed until the vane has left the seal passage portion almost completely. As a result, the sealing passage can be designed to be relatively short, i.e., occupy only a relatively small rotational angle range. This provides the advantage of the feed passage section extending over a large rotational angle range in the context of the high transport power obtained. This is advantageously facilitated by the fact that the radial circumference of the burn is formed parallel to the pivot axis.

[0020]

Embodiments of the present invention will now be described in detail with reference to the drawings.

The pump 20 has a pump casing 21 which is divided along a partition surface 28 into two casing parts 22, 23. The casing parts are intimately assembled with one another by means of a seal 24, for which purpose a clamping screw 25 is used, which extends through a hole 26 in the eye 27. The pump casing 21 has a ring-shaped passage 30, and the passage is constituted by a feed passage portion 54 and a seal passage portion 55. Both connections 31, 32 are tangentially open in the passage 30 and are provided with connection flanges 33 for connection of the inlet or outlet conduit.
Regardless of whether the pump is turned clockwise and counterclockwise or forward or backward, connection 31 is shown for simplicity as an inlet or suction connection and connection 32 is shown as an outlet or pressure connection. Have been. The connection fulfills such a function when the pump is operating clockwise according to arrow 34 in FIG.

A swirl vane 35 circulates in the ring-shaped passage 30. Four swirl vanes 35 are provided, the swirl vanes being arranged at an angle of 90 ° to each other. In this embodiment, the swirl vanes 35 are each formed integrally with a vane 70, a journal 37, and a stopper collar 50 provided at a transition between the journal 37 and the vane 70. Unlike this, swirl vane 35
May be constituted by two separate swirl vane sections, wherein one swirl vane section is constituted by the journal 37 and another swirl vane section is provided by a vane 70 and within said vane. And a stopper flange 50 integrally formed with the stopper. The two swirl vane sections are advantageously releasably connected to one another again by means of two bayonet pins which are closely inserted in a bore extending parallel to one another and parallel to the swivel axis 75. Instead of a bayonet pin and a correspondingly shaped hole, it is also possible to use a flat-shaped member which is plugged closely, but again separably, into a correspondingly formed opening. If the swirl vane 35 is formed by two swirl vane sections as described above, the vane 70 can be easily replaced without removing and replacing the journal 37.

The swirl vane 35 is arranged so as to be rotatable about a swivel axis 75, which is defined by the rotation of the swirl vane 35 about the rotary axis 29, and which is indicated by the partition surface 28. Is located in the plane,
It extends radially with respect to the axis of rotation 29 of the pump.
The journal 37 is provided with a bearing hole 3 provided in the boss body 40.
9 is supported. The boss body 40 is formed integrally with the drive sleeve 41 in a flange shape and opens the control hollow chamber 42. The journal diameter 78 is chosen as large as possible to obtain a good turning torque ratio. The boss body 40 is slidably tightly connected to the casing part 2 via cylindrical slide seal rings 43.1 and 43.2.
It is supported by 2,23 cylindrical bearing shoulders 44.1, 44.2. For another seal of the drive sleeve 41,
A shaft seal 45 is provided. Drive shaft (not shown)
Are non-rotatably connected to the drive sleeve 41 and the boss body 40 in a manner not shown by using a fitting key engaged in the groove 46.

The swirl vane 35 is supported on a cylindrical bearing shoulder 51 by a stopper collar 50 toward the inside. The journals 37 projecting inward of the opposing swirl vanes 35, as is apparent from FIGS. 1, 2 and 5,
Here, they are non-rotatably connected to each other using linear connecting rods 47, 48 but can be disengaged,
In this case, the vanes 70 of the pair of swirling vanes 35 that are opposed to each other are shifted by about 90 degrees about the swivel axis 75. A connecting rod 47 also formed in a tubular shape,
Reference numeral 48 has a predetermined outer diameter at least in both end regions. 2 and 3 (a) to 3 (c), the connection rod is closely engaged in a hole 73 of a predetermined diameter 107 provided in the journal 37. The hole 37 is formed in the center plane 8 of the vane 70, as is apparent particularly from FIG.
Displaced by an angle 74 with respect to zero and outwardly by a distance 104 relative to the pivot axis 75 of the vane. This allows both vane pairs to be pivotable independently of one another. The connecting rods 47, 48
Two anti-rotation pins 8 which are arranged at a distance from one another and are perpendicular to the connecting rod axis 89 in the same plane
7.1, 87.2, and the rotation preventing pins are arranged at the same distance from the center of the rod. Rotation prevention pin 87.
1, 87.2 are closely engaged in the respective anti-rotation grooves 76 in the assembled state, the anti-rotation grooves being arranged at the inward facing end of the journal 37. For axial positioning, the connecting rods 47, 48 have both stopper collars 88.1, 88.2, respectively, which directly contact the anti-rotation pins 87.1, 87.2. Thus, it is arranged between the rotation preventing pins. The stopper collars 88.1 and 88.2 are for connecting rods 47 and 48,
The opposite sides of the anti-rotation pins 87.1, 87.2 are chamfered in a circular shape so that the connecting rods 47, 48 can move outwardly with respect to the pivot axis 75 at the maximum possible distance without impeding the pivoting movement. Swivel vanes 3 which can be arranged and connected to each other
The lever ratio as good as possible when turning 5 is possible. Instead of the anti-rotation pins 87.1, 87.2 and the narrow stop collars 88.1, 88.2, further auxiliary elements may be provided for fixing the position and preventing rotation. For example, instead of a stopper collar, a supportive wide stopper support pin arranged perpendicular to the connecting rod axis 89 may be provided. Such a stopper support pin has an anti-rotation rod extending in parallel to the connection rod axis 89 at an end remote from the connection rod 47 to prevent rotation. Connecting rod 4
7 has substantially the same outer diameter as the outer diameter 106. Such an anti-rotation rod is closely engaged in a corresponding hole provided in the journal 37 of the swivel vane 35, which is provided outwardly with respect to the swivel axis 75 and opposite the hole 73. Have been. With such a structure, it is possible to transmit large swirl vane forces and moments, which is particularly advantageous for large pumps.

If more than two swirl vane pairs or four swirl vanes, for example three swirl vane pairs or six swirl vanes 35 are used, advantageously at least two of the three connecting rods alternate. The third connecting rod may be configured linearly, whereas the different sides are bent in a crank shape. by this,
Even in embodiments with more than two swirl vane pairs, it is possible to swirl all three swirl vane pairs independently of one another.

For the purpose of cleaning the pump 30 and / or replacing the swirl vanes 35, the three clamping screws 25
After unscrewing and removing the casing part 23, the entire boss body together with the swivel vane 35 mounted in the boss body can be easily removed without any loosening. Due to the disassembly of the swirl vanes 35 or 70, the swirl vanes or vanes are easily pulled out. It is only necessary to loosen the three clamping screws 25 for cleaning the pump and / or for replacing worn vanes. All other components can be easily removed or withdrawn without loosening any screws or other fixing elements, thereby making it easier and easier for the whole pump or the worn pump part after prolonged operation. Quick disassembly or assembly is possible.

The annular passage 30 has its feed passage portion 5
4 has a cross section corresponding to the shape of the vanes 70 arranged transversely to the direction of rotation. Inflow section 31
In the part of the seal passage extending over a shorter rotational angle region between the outlet 32 and the outlet 32, the passage 30 has a cross section corresponding to the vane 70 which is swiveled in the direction of rotation, in which region the thickness of the vane 70 The dimensions have been reduced to 92. For this purpose, the seal members 56 and 57 are inserted into the passage 30 extending annularly over the entire circumference. These sealing members are fixed to the casing parts 22; 23 by screws or the like (not shown).

At the transition from the feed passage portion 54 to the seal passage portion 55, a turning member 90.1 for turning the swirl vane 35 is arranged. The diverter is formed by a cylindrical rod that is bent by about 90 °. One end 93 of this rod is fixed to the starting end face 53 of the sealing member 57, and the other end 94 is fixed to the casing part 21. The connection between the deflection member and the passage wall is made by welding, but
For the purpose of easy replacement of the deflecting member, it may be performed by coupling means not shown. Turned to the partition surface 28,
In the curved region of the diverting member 90.1, the diverting member has a curved radius of curvature 96 adapted to obtain rapid turning of the swirl vane 35. The relative spatial arrangement of the diverting member 90.1 with respect to the swirl vane 35 is such that the diverting edge 98 of this diverting member is
Contacting the pressure surface 72 for the first time in an area as close to
The swivel / contact area is selected to be located near the bearing of the swirl vane 35. Thereby, a suitable moment characteristic (Momentenverha) for rotating the swirl vane 35 is obtained.
eltnisse) and force-action properties (Kraftangriffsverhaeltnis
se) is obtained.

The upper edge 97 of the deflecting member 90.1 extends linearly and transitions into alignment with the sealing surface 60 of the sealing member 57. The seal member passes through the entire seal passage portion 55 and moves from the start end face 53 arranged in the area of the outflow section 32 to the end face 5 formed in the area of the inflow section 31.
Has reached eight.

During operation of the pump for a relatively long time, the area of the pressure surface 72 of the vane 70, particularly the radial edge 102 provided at the transition to the radial outer peripheral surface 82, will wear to some extent. Can not be avoided. As a result, the vane is not completely swung in the rotational direction 34 before entering the seal passage portion 55, and the vane is moved from the starting end face 5.
There is a risk of collision with 3 or being caught at this location.

In order to avoid the inconvenience at the time of intrusion due to such wear, or to enable the operation of the pump for a long time without inconvenience, the sealing member 56 needs to be provided with the end face 58. At the transition of the sealing surface 60 there is provided an intrusion member 91.1 formed by a wedge-shaped climbing ramp 101. This penetrating member is located opposite the turning member 90.1 with respect to the rotation surface 28 described by the turning axis 75 of the turning vane when the turning vane 35 rotates, and In the rotational direction 34 (FIG. 4).

The climbing inclined portion 101 forms an acute angle 103 with respect to the sealing surface 60, and is formed by a notch of the sealing member 57 in this embodiment.
The notch is arranged so as to be shifted by a predetermined angle 59 with respect to the terminal surface 58 (FIG. 1). In order to facilitate swiveling, the vanes 70 are at least partially rounded or flattened at the radial edge 102 so that the vanes 70 Directional edge 102.

Intrusion member 91.1 is disposed on deflection member 90.1 in connection with the turning of vane 70 during operation of pump 20 in the direction of rotation indicated by arrow 34 in FIG. (FIG. 4). In contrast, the intrusion element 91.2 causes the vane 70 to run when the pump 20 is operated in a direction opposite to the direction of rotation indicated by the arrow 34 in FIG.
Are disposed on the diverting member 90.2 in relation to the turning (FIG. 2).

The sealing surface 60 is formed on the partition surface 2 except for the area of the intruding member 91.2 and the area immediately following the boss body 40.
At a distance corresponding to half the thickness 100 of the vane 70 with respect to 8, it extends flat and parallel.

A similar, but mirror-image or symmetrically formed sealing element 56 is inserted into the sealing channel section 55 of the housing section 23. Deflection member 90.1
Are located in the region of the outlet 32. A similar diverting member 90.2 is arranged in the area of the inflow part 31 in a mirror image or symmetrically with respect to the diverting member 90.1. According to this, one diverting member 90.1, 90.2 is provided on each side of the seal passage portion 55, which is arranged at the transition from the feed passage portion 54 to the seal passage portion 55. I have. In this case, one diverting member 90.1 is arranged on one side of the turning surface 28 described by its turning axis 75 when the turning vane 35 rotates, while the other turning member 90.2 is It is located on the other side of surface 28. Thus, such a mirror or symmetrical arrangement is selected so that the pump can be operated clockwise or counterclockwise, that is to say both forward and backward. Both sealing members 56, 57
A seal constricted portion 61 is formed between the two seal surfaces 60. The contour of the surface of the seal constriction corresponds to the shape of the vane 70 that is swung in the circumferential direction.

The shape of the vane 70 of the swirl vane 35 will be described below in more detail with reference to FIGS. 3 (a), 3 (b), 3 (c) and 4.

The relatively flat vane 70 mainly has a plate-like shape. The outer peripheral surface 81 in the axial direction facing the casing 30 has a spherical radius 77 similar to the outer peripheral surface 52 of the casing 30 which is directly opposed to these outer peripheral surfaces.
, And the radially outer peripheral surfaces 82.1 and 82.2 of the vane 70 are formed into a partially cylindrical shape so as to have a radius of curvature 83. ing. By such means, in all possible positions of the swirl vanes 35, satisfactory contact and sealing inside the passage 30 is obtained. Furthermore, the swirl vane 35 has a predetermined transition radius 79 at the transition from the stopper collar 50 to the vane 70. This transition radius is formed according to the specific material requirements and load conditions given in each case. Accordingly, the sealing members 56 and 57 are chamfered in a convex shape at an edge portion facing the vane 70.

The pressure surface and suction surface of the swirl vane 35 are as follows:
For the sake of simplicity and on the basis of the possibility of operating the pump in clockwise and counterclockwise rotations, the pressure surfaces 72.1 and 72.
Call it 2. Thus, each vane 70 has two pressure surfaces 72.
1 and 72.2. Vane 70 has a pressure surface 72.
The radius of curvature 96 of the diverting member 90.1 in the swivel / contact area of 1,72.2, i. An elliptical or arc-shaped groove having a larger radius of curvature 84 is provided. Furthermore, the pressure surfaces 72.1, 72.2 of the vanes 70, which are arranged symmetrically with respect to the pivot axis, are formed as flat surfaces parallel to one another.

Accordingly, as shown in FIG. 4, the vane 70 has a barbell-like cross-sectional shape in the range of the swivel / contact region, when viewed in a cross section perpendicular to the swivel axis 75 of the vane. The groove 71 has a groove depth 85, which is selected as follows: on the one hand, the leverage or moment ratio (Hebel ratio) occurring at the diverting member 90.1 during the turning of the vane 70. bzw. Momentenverhaeltnisse)
And load acting ratio or force ratio (Lastangriff-bzw. Kr
The locking of the vanes 70 is reliably avoided on the basis of the aftverhaeltnisse, and on the other hand, the groove depth is chosen to be adapted to the material-specific requirements and application conditions. The width 86 of the concave groove 71 is selected to be sufficiently large according to the diameter 95 of the deflecting member 90.1 or according to the actual contact state.

Since the pump 20 is defined in particular for aggressive media, beverages and foodstuffs in the chemical industry, all parts which come into contact with the media are made of correspondingly resistant materials. In this case, for a luxury item to be pumped, the physiological safety of the luxury item is particularly problematic. In this case, special stainless steel is used for the pump casing or the feed passage section 54, but also bronze, gray cast iron and possibly cast steel. Seal passage portion 55 or seal member 5
The 6,57 are advantageously made of a similarly hardenable stainless steel, but can also be made of another material, in particular a plastic with suitable properties. The swirl vanes 35 are advantageously made of a rigid, wear-resistant material, in particular a plastic with corresponding physiologically safe properties. However, the swirl vanes can also be manufactured from rigid cores, preferably made of metal, which are coated with a plastic having corresponding properties. With this suitable material pair, the anticipated wear is almost completely concentrated on the swivel vanes 35 which can be manufactured inexpensively and are easily exchangeable. In another embodiment, the pressure surfaces 72.1, 72.2 of the swirl vanes at least partially
A surface structure or a surface layer or a spare member that enables reliable turning for a long time is provided. For this purpose, the vane 70
The pressure surfaces 72.1, 72.2 of the
In the region 02, it has a rigid, wear-resistant coating or insert, which can also be formed as a peripherally injected metal core of a suitable plastic, which extends to the surface. .

Next, the operation mode of the pump will be described.

The individual operating steps are clearly illustrated in FIG. Starting from vane position 63 for explanation of the mode of operation. If the boss 40 is rotated by a motor (not shown) via a shaft (also not shown) in the direction of arrow 34, the boss will carry all the swirl vanes 35. The vane 70 of the swirl vane is located at a right angle or perpendicular to the rotation direction at the vane positions 63 and 64. The vane 70 located at the vane position 63 causes the feed medium occupying between the vane 70 and the vane 70 located at the vane position 64 to move the feed medium 32 along the rotation direction (see the arrow 34).
While reaching the vane position 64. In this case, the feed medium is transported toward the outlet 32. This is particularly assisted by the vane 70 moving from the vane position 64 to the vane position 65 by sealingly closing the seal passage portion after it has penetrated into the seal passage portion 55, whereby the vane position 63
The feed medium conveyed by the position exchange from the to the vane position 64 is almost completely conveyed to the outlet 32. However, a small amount of feed medium is, in this embodiment, entrained between the two vanes 70, each of which is swiveled in the direction of rotation, via the sealing passage portion 55 towards the inlet 31.

Immediately after reaching vane position 64, vane 70
Reaches the diverting member 90.1 located in the transition region from the feed passage portion 54 to the seal passage portion 55 and is displaced by this diverting member so that the vane pivots about the pivot axis 75 and Before reaching the position 65, in particular before entering the seal passage section 55, the diverter 90.1 occupies a position pivoted in the direction of rotation 34 (see FIG. 4) and thus extends in parallel with the sealing surface 60. Contacts the upper edge 97 of Accordingly, when the swirl vane 35 rotates about the rotation axis 29, the swivel angle that is forcibly generated by the contact with the deflection member 90.1 is substantially 90 degrees when the vane 70 is not worn.

However, if the pressure surface 72 has worn to some extent after the pump 20 has been running for a long time, the vane 70 does not occupy the position swiveled in the rotational direction 34 before entering the seal passage portion 55, Rather, it occupies a position slightly inclined with respect to the rotation plane 28. In this case, the vane 70
Strikes the ramp 101 of the penetrating member 91.1 in the region of the edge 102 located at the transition of the pressure surface 72.1 with respect to the radial outer circumference 82.2 and this ramp 10
At 1, it rotates in the rotational direction 34 by a sliding motion during rotation to completely seal the seal passage portion 55 formed between the seal members 56 and 57. Seal passage portion 55
Has a thickness 92 of the vane 70 over its entire length, except for the region provided with the intrusion members 91.1, 91, 2.

Vane 7 penetrating into seal passage portion 55
When 0 enters the seal passage portion until it completely seals the seal passage portion 55, the leading vane 70 travels a small stroke in the sealed seal passage portion 55 and then projects out of the seal passage portion 55. If the vane is fully extended, the vane is brought to a position pivoted at right angles or perpendicular to the direction of rotation, i.e., the opposing vane 70, which is non-rotatably connected to the vane, is turned by the diverter 90.1. By colliding with and turning at this time,
The vanes are brought to a position swiveled perpendicular or perpendicular to the direction of rotation. During this pivoting movement, in particular, the vanes 70 are still in contact with the subsequent
Assisted by sealing 5 sucks the feed medium through inlet 31. Then, two swirl vanes 35 located at right angles or perpendicular to the rotation direction.
The feed medium trapped between them is guided through the feed passage 54 in a protected, i.e. without significant compression.

An opposing vane 70 non-rotatably coupled to the vane contacts the upper edge 97 of the diverter 90.1 or is prevented from pivoting between the two sealing surfaces 60 at the seal passage portion 55. By contacting the upper edge 97 of the diverting member 90.2, which is arranged symmetrically with respect to the diverting member 90.1, the vanes 70 rotate in the rotational direction during rotation through the feed passage portion 54. It is held at a right angle or perpendicular to it. In this way, the automatic control performed in the pump chamber for the swirl of the swirl vane 35 is performed.

Based on the mode of operation of the pump 20 in the form of a piston pump, this pump 20 is self-priming. However, the pump 20 is, on the other hand, designed as a rotary pump or a rotary pump, so that a very uniform flow is obtained in the pressure line with almost no pulsation.

Next, the swivel motion of the vane 70 about the swivel axis 75 after climbing on the deflection members 90.1 and 90.2, the load acting characteristic or force characteristic generated in this case, and the lever arm Characteristics or moment characteristics (Lasta
ngriffs- bzw.Kraft- sowieHebelarm- bzw.Momentenv
erhaeltnisse) will be described in detail. In order to clarify the advantageous configuration of the vane 70, it is compared below with a vane of an unfavorable configuration, i.e. a vane with a pressure surface formed in the form of a flat surface over its entire width. In this case, since the swirl vane 35 rotates at a constant rotation speed, it is assumed that the swirl vanes advance the same distance or the same rotation angle in the same time segment. A correspondingly positioned lever arm (Hebelarme) should likewise be considered.
The leverage arm lies in a plane perpendicular to the pivot axis, on the one hand is limited by the intersection with the pivot axis 75 and, on the other hand, its position changes in each case depending on the individual position. It is limited by the diverting edges of the diverting members 90.1, 90.2 or the points of contact on the diverting surface 98.

During the turning of the vane 70, the length of the lever arm is continuously changed, that is, from the maximum length at the position where the vane 70 is located in a direction transverse or perpendicular to the rotation direction, Fully rotated in the direction of rotation, ie 9
It changes to the minimum length at the position rotated by 0 °. This means, first of all, that the moment properties are progressively degraded starting from the starting point due to the continuous shortening of the lever arm. On the other hand, during the entire turning time required for a complete turning of 90 °, a force action is generated which is directed in the direction of the turning edge or turning surface 98.
This force action also causes a force action that is directed away from the direction of rotation 34. This is especially true when rigid, wear-resistant vanes 70 are used.
This can lead to inconvenient locking of the vanes 70 in one area. This causes various major damages on the pressure surface 71 of the vane 70 and the deflecting member 90.1, and this damage may also cause the pump 20 to be completely damaged due to the complete destruction of the above-mentioned functional parts. There is.
This problem is not reliably solved by increasing the radius of curvature 96 of the deflection member 90.1 or by a gently rising or otherwise formed deflection member.

On the other hand, the advantageous configuration of the pressure surfaces 72.1, 72.2 of the vanes 70 in the swivel / contact area provides good leverage or moment properties during the entire swivel time. The lever arm that occurs in this case is larger than the lever arm that occurs under a vane with an unfavorable pressure surface configuration that is pivoted completely in the direction of rotation 34. Furthermore, it can be seen that during the critical turning time, good loading or force properties are obtained, which are diametrically opposed to those under unfavorable pressure surface profiles. Thus, starting from the position where the lever arm is perpendicular to the direction of rotation 34, the pressure surface 72 of the vane 70 on the diverting edge or diverting surface 98 of the main diverting member 90.1 A pure sliding is performed. This ensures that inconvenient locking of the vanes 70 in this region is avoided. The short turning time to reach the last mentioned position does indeed produce a load or force characteristic which is also directed to the deflecting member 90. 1, which results in a thickness 92 of the vane 70. In this connection, it does not matter in this case, based on the extremely large lever arm length and the angle adjusted with respect to the deflection member 90.1 in the pivot and contact area.

In this case, in particular, due to the appropriate shape of the pressure surfaces 72.1, 72.2 of the vanes 70 in the swivel / contact area, good properties with regard to the forces and force directions occurring at this location and good leverage properties or the resulting leverage characteristics are obtained. Moment characteristics can be obtained. In this case, the combined effect of these effects should also be considered.

An important part of this description will be repeated below.

The rotary swirl vane pump (20) has a drive and a ring-shaped passage (30) with a suction connection and a pressure connection (31, 32). The feed passage portion (54) of this passage has a constant cross section. The pump (20) has a swirl vane (35) formed by a flat vane (70). This swirl vane (35) is connected to the drive and is connected to the passage (3).
0), it is rotatable about a rotation axis (29). The swirl vane (35) is swivelable about a swivel axis (75) in a plane lying in the direction of rotation (34) and in its feed passage portion (54) its pressure surface (7).
2) is located substantially orthogonal to the rotation direction (34). The pump (20) has a seal passage portion (55) formed in the passage (30) between the suction connection (31) and the pressure connection (32). This sealing passage part (55) has a cross section corresponding to the shape of the swirl vane (35) swiveled in the direction of rotation (34) and is always sealed by at least one continuous swirl vane (35). Have been. The transition from the feed passage section (54) to the seal passage section (55) is provided with a diverting member (90) with at least one control edge or surface for turning the vane (70). Have been. The pressure surface (72) of the vane (70) enables good swivel characteristics in the control edge of the deflection member (90) or in the swivel / contact area in contact with the control surface and enables the control edge of the deflection member (90). It has a surface profile adapted to the shape of the part or control surface.

[Brief description of the drawings]

FIG. 1 is a plan view showing an open rotary swirl vane pump having two casing parts.

FIG. 2 shows the closed rotary swirl vane pump in FIG.
FIG. 3 is a cross-sectional view taken along two lines.

3A and 3B are diagrams showing a swirl vane, wherein FIG. 3A is a view of the swirl vane as viewed from above, FIG. 3B is a side view of the swirl vane,
(C) is the figure which looked at the turning vane from the bottom.

FIG. 4 is a sectional view of the swivel vane taken along line 4-4 in FIG. It is a fragmentary sectional view which expands and shows.

FIG. 5 is a top plan view of a reduced connecting pin for connecting each of the two swirl vanes in a non-rotatable and releasable manner;

[Explanation of symbols]

20 pump, 21 pump casing, 22, 2
3 Casing part, 24 seal, 25 tightening screw, 26 hole, 27 eye, 28 partition / rotation surface, 29 rotation axis, 30 passage, 31 connection / inflow / suction connection, 32 connection / outflow /
Pressure connection, 33 connection flange, 34 arrow / rotation direction, 35 swivel vane, 37 journal, 3
9 bearing hole, 40 boss body, 41 drive sleeve,
42 control cavity, 43.1, 43.2 slide seal ring, 44.1, 44.2 bearing shoulder,
45 shaft seal, 46 groove, 47, 48 connecting rod, 50 stopper collar, 51 bearing shoulder,
52 outer peripheral surface, 53 start end surface, 54 feed passage portion, 55 seal passage portion, 56, 57 seal member, 58 end surface, 59 angle, 60 seal surface, 61 seal constricted portion, 63, 64, 65, 66
Vane position, 70 vanes / outer circumference, 71 grooves,
72, 72.1, 72.2 pressure surface, 73 holes,
74 angle, 75 pivot axis, 76 anti-rotation groove,
77 spherical radius, 78 diameter, 79 transition radius, 8
0 center plane, 81 axial outer peripheral surface, 82, 8
2.1, 82.2 radial outer peripheral surface, 83, 84
Radius of curvature, 85 groove depth, 86 width, 87.1
87.2 anti-rotation pin, 88.1, 88.2 stopper collar, 89 connecting rod axis, 90, 90.1,
90.2 Deflection member, 91, 91.1, 91.2 Penetration member, 92 Thickness, 93, 94 End, 95
Diameter, 96 radius of curvature, 97 upper edge, 9
8 turning edge / turning surface, 100 half thickness, 101
Ramp, 102 rim, 103 angle,
104 spacing, 106 outer diameter, 107 diameter

Claims (14)

[Claims] 1. A rotary swirl vane pump, comprising a drive and an annular passage (30) provided with a suction connection and a pressure connection (31, 32). The feed passage section (54) has a constant cross-section and has a rotation axis (2) in said passage (30).
Flat vanes (7) that can be rotated about 9)
0), provided by a swivel vane (35), connected to a drive and swiveling the swirl vane (35) in a plane lying in the direction of rotation (34). It is swivelable about an axis (75) and the pressure surface (72) of the swirl vane (35) is located in the feed passage portion (54) substantially transverse to the direction of rotation (34). And suction connection (31)
Swivel vane having a seal passage portion (55) formed in a passage (30) between the pressure connection (32) and the seal passage portion (55) in a rotational direction (34). Has a cross section corresponding to the shape of (35),
Vane (70), which is always sealed by at least one swirl vane (35) passing therethrough and has a control circle or control surface provided at the transition from the feed passage section (54) to the seal passage section (55). ) Is provided with at least one deflecting member (90) for pivoting the diverting member (90).
In the cross-section perpendicular to the pivot axis (75) in the pivot contact area contacting the control edge or the control surface of the deflection edge (90) of the deflection edge (90). A rotary swirl vane pump characterized by having a matched surface profile. 2. The rotary swirl vane pump according to claim 1, wherein the pressure surface (72) of the vane (70) is concave at least in a partial region. 3. The surface profile of the pressure surface (72) is formed by a continuous cam profile in a cross section perpendicular to the pivot axis (75) in the pivot contact area. 3. The rotary swirl vane pump according to 1 or 2. 4. The surface contour of the pressure surface (72) is designed to be elliptical or circular in a cross section perpendicular to the pivot axis (75) in the pivot contact area.
A rotary swirl vane pump as described. 5. An intrusion member (91) having a control edge or a control surface assigned to the deflecting member (90) is provided, the intrusion member (91) being turned when the swirl vane (35) rotates. In relation to the turning surface (28) described by the turning axis (75) of this turning vane (35), the turning member (9)
2. The deflecting member (90) is positioned opposite to the deflecting member (90) in the circumferential direction (34).
The rotary swirl vane pump according to any one of claims 1 to 4. 6. The turning angle corresponding to the turning of the vane (70) in the turning member (90) is determined by the turning angle of the vane (91) in the turning member (90). 6. The rotary swirl vane pump according to claim 5, wherein the rotary swirl vane pumps are configured so as to be significantly larger than a corresponding intrusion swivel angle. 7. The rotary swirling vane pump according to claim 5, wherein the swirling angle is larger than 60 °. 8. The pressure surface (72) of the vane (70) and the control edge or control surface of the entry and / or deflection members (90, 91) correspond to a 90 ° turn of the swirl vane (35). So that the circulation rotation angle is smaller than 40 °
A rotary swirl vane pump according to any one of claims 5 to 7, which is adapted to one another. 9. Rotation according to claim 1, wherein the deflecting element (90) is formed by a circular cross-section rod or a cross-section circular tube curved at an angle of 90 °. Swirl vane pump. 10. The surface contour of the control edge or control surface of the deflecting element (90) is circular in a cross section perpendicular to the pivot axis (75) in the deflecting contact area. The rotary swirl vane pump according to any one of claims 1 to 9, wherein the rotary swirl vane pump is provided. 11. The pressure surface (72) of the vane (70)
11. The rotary swivel according to claim 1, wherein the swivel contact area has a radius of curvature greater than the radius of curvature of the control edge or control surface of the deflecting member. Vane pump. 12. The pressure surface (72) of the vane (70)
12. The rotary swirl vane pump according to claim 1, wherein the rotary swirl vane pump extends flat and parallel to each other outside the swirl contact area. 13. The pressure surface (72) of the vane (70)
13. The rotary swirling vane pump according to claim 1, which has a substantially rectangular shape in a plane having a rotation axis (29). 14. Rotation according to claim 1, wherein the radially outer circumferential surface (82) of the vane (70) is formed substantially parallel to the pivot axis (75). Swirl vane pump.