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Description  |
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BACKGROUND OF THE INVENTION
The present invention relates to an impeller wheel for conveying a medium
of the type including a plurality of vanes spaced from each other.
The effect of a non-uniform distribution of intervals between the vanes of
the impeller on the noise generation is determined in a frequency range.
With a uniform distribution of vanes in the impeller a tone or a sound
with frequency N f.sub.o and high harmonics thereof are produced wherein N
is the number of vanes and f.sub.o is the rotation frequency of the
impeller wheel. Without taking into consideration the uppertone the
intensity/frequency spectrum of this noise consists of a discrete line
which indicates the entire sound energy (FIG. 1a). The purpose of the
non-uniform or irregular vane distribution is that the sound intensity of
the single spectrum line be uniformly subdivided into many discrete lines
in the frequency range so that each partial tone would be below the
audible threshold of hearing.
An impeller has been known from DE-AS 1253402, in which the instructions
have been given as to how the vane positions should be distributed on the
periphery of the impeller wheel. Thereby a mathematical equation between
the succession of the intervals between the vanes and the resulting noise
spectrum has not been considered so that, for example the subdivision of
the output spectrum can develop as shown in FIG. 1b, in which individual
tones dominate. The degree of irregularity for a given successions of the
vane intervals is defined in that the difference between the maximal and
minimal interval is divided by the middle interval. This definition does
not take into consideration the succession of different intervals which
are very important for the aforementioned irregularity.
SUMMARY OF THE INVENTION
It is an object of this invention to provide an improved impeller.
The irregularity of a function or sequence can be read off as a function of
its autocorrelation of its amplitude/frequency spectrum. In this invention
efforts have been made to obtain a flat or leveled amplitude/frequency
spectrum (FIG. 1c), which is typical for white or blank noise. With a vane
interval distribution of this invention, a flat discrete wide-band noise
spectrum has been obtained, in which no spectrum portion is apperceived
(FIG. 1c).
The stimulation processes are repeated periodically after each rotation of
the impeller wheel, that is the noise signal has an initial frequency
f.sub.o which is identical with an inverse rotation period. The intensity
or amplitude/frequency spectrum of noise is thus discrete. Despite such
deterministic repetitions a signal can be obtained which would have all
the properties of a white or blank noise, namely a flat (discrete)
amplitude/frequency spectrum or a quickly dropping autocorrelation
function. Such properties are expressed by a so-called pseudo-noise
sequence, i.e. a mathematical sequence of numbers which are calculated
according to certain rules described below.
An example for a pseudo-noise sequence is a binary maximal length sequence
which can be generated with a shift register. For clarification one
assumes that the vane noise generated by an impeller with the uniform vane
distribution, be sinusoidal with a single amplitude:
##EQU1##
This sinusoidal function (1) is multiplied in beat with a maximum length
sequence {a.sub.k } by +1 or -1, which can be conceived also as a phase
shifting by 0.degree. or 180.degree.. The following function is obtained:
##EQU2##
whereby rect
##EQU3##
otherwise, is a rectangle function and T.sub.c =T.sub.o /N is the cycle
time, that is the time of a rotation divided by the number of vanes.
In the spectral range the function (2), indicates a uniform distribution of
a linear energy within frequency f.sub.o and its multiples. The
distribution is in this case weighted with an interval function. The phase
jumps in accordance with the maximum length sequence {a.sub.k } are, with
the position of N vanes on the periphery of the impeller wheel realized so
that the K-th vane would be positioned in the angle range:
##EQU4##
Since the binary maximal length sequences have always the length
N=2M-1(M=3, 4, 5, . . . ), the number of vanes with this distribution
would be only 7, 15, 31, 63, etc.
When another number of vanes N are necessary the intervals between the
vanes are distributed in accordance with primitive-root- or
quadratic-residue sequences which have aforementioned pseudo-noise
properties. These sequences are not binary.
The chief advantage of the present invention resides in that pump sounds or
noises arising from the impeller wheel are reduced to an absolute minimum.
The objects of this invention are attained by an impeller wheel for
conveying a medium, including a plurality of vane-shaped conveying
elements positioned on a peripheral surface of the wheel and spaced from
each other in a peripheral direction of the wheel at non-uniform intervals
which are determined in accordance with mathematical interrelations of a
pseudonoise sequence.
The pseudonoise sequence may be the binary maximal length sequence (3) or a
primitive root sequence or a quadratic residue sequence which will be
described later.
The impeller wheel has a middle rotation plane, and two crowns of conveying
elements or vanes are positioned at two opposite sides of the middle
plane, the conveying elements being arranged so that an arrangement
thereof in one crown corresponds to that of the other crown.
An arrangement sequence of conveying elements of one crown may be
diametrically opposite to an arrangement sequence of the other crown.
The impeller wheel may be positioned in a pump chamber of a fuel conveying
aggregate.
The novel features which are considered as characteristic for the invention
are set forth in particular in the appended claims. The invention itself,
however, both as to its construction and its method of operation, together
with additional objects and advantages thereof, will be best understood
from the following description of specific embodiments when read in
connection with the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWING
FIGS. 1a and 1b and 1c are graphs showing different ideal output spectra of
conveyor noise;
FIG. 2 is a schematic side view of the combination of the fuel feeding
aggregate, fuel supply tank and internal combustion engine;
FIG. 3 is a side partially sectional, view taken along lines III--III of
FIG. 4 of the fuel feeding aggregate in the chamber of which an impeller
is positioned; and
FIG. 4 is a front view of the impeller wheel.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawings in detail, and firstly to FIG. 2 thereof, it
will be seen that a fuel supply tank 10 is connected via a suction line 12
with the suction side of a fuel feeding aggregate 14. A pressure conduit
16 is connected to the pressure side of the fuel feeding aggregate.
Conduit 16 leads to an internal combustion engine 18. In operation of the
internal combustion engine the fuel feeding aggregate delivers fuel from
the supply tank 10 to the internal combustion engine 18.
With reference to FIGS. 3 and 4 it will be seen that a flow pump 20 of the
fuel feeding aggregate has an impeller wheel 22 which is arranged in a
pump chamber 24 of the fuel feeding aggregate 14. Impeller 22 is connected
with a drive shaft 26 which is formed by an armature shaft of an electric
motor 28 which is the part of the fuel feeding aggregate. In the proposed
aggregate a two-stage flow pump is formed as a so-called WESTCO pump. It
has a first inner crown 30 of conveying elements or vanes 34 and a second
double crown 32 which consists of two outer crowns 38 and 39 of conveying
elements or vanes 40. Each crown 30 and 32 of the conveying elements
corresponds to one stage of the pump.
Conveying elements 34 of the inner crown 30 are spaced from each other by
cut-outs 36 which extend parallel to the axis rotation of shaft 26.
Cut-outs 36 are spaced from each other as shown in FIG. 4. As specifically
seen from FIG. 3 the double crown 32 consists of two outer crowns 38 and
39 of conveying elements or vanes 40 which are provided at two opposing
sides of a middle rotation plane of impeller 22. The middle rotation plane
when the imaginary rotation plane which is viewed in the direction of the
axis of rotation of shaft 26 is, in the middle region between two opposite
end faces 23 and 25 of impeller 22.
The front view of the impeller 22 is shown in FIG. 4. Individual conveying
elements or vanes 40 of outer crowns 38 and 39 are separated by cut-outs
or recesses 42 at the two sides of the aforementioned middle rotation
plane so that these vanes 40 are spaced at intervals 41 from respective
neighboring vanes. Recesses 42 extend respectively from outer portions of
either end face 23, 25 of the impeller 22 to its peripheral surface 27. As
indicated in FIG. 4, each other vane crown 38 and 39 has 63 outer vanes 40
which are spaced from each other in the peripheral direction of impeller
22 by unequal distances 41. These distances 41 between individual vanes of
crown 38 or 39 are dimensional in accordance with mathematical
interrelations of a pseudo sound noise sequence. In the following table I,
an example of the maximum length sequence Q.sub.k of the length 31 is set
forth. The individual fuel conveying elements or vanes 40 are numbered
from 1 to 31 in column k. The second column a.sub.k shows the binary
maximal length sequence from which the position of each vane in accordance
with the equation (3) is calculated. The transition from 0 to 1
corresponds to the step of 5.81 degrees whereas the transition from 1 to 0
corresponds to the step of 17.42 degrees. .phi..sub.k in the third column
of the table I identifies the positions of the individual conveying
elements in the range defined from the middle between the conveying
element 1 and the conveying element 31.
An impeller with 31 vanes is subdivided according to the binary maximal
length sequence (3), i.e.
TABLE I
______________________________________
##STR1##
k a.sub.k .phi..sub.k
k a.sub.k
.phi..sub.k
______________________________________
1 1 5.81 16 1 180.00
2 0 23.23 17 1 191.61
3 0 34.84 18 1 203.23
4 0 46.45 19 0 220.65
5 0 58.06 20 1 226.45
6 1 63.87 21 0 243.87
7 1 75.48 22 0 255.48
8 1 87.10 23 0 267.10
9 0 104.52 24 1 272.90
10 0 116.13 25 0 290.32
11 1 121.94 26 0 301.94
12 1 133.55 27 1 307.74
13 0 150.97 28 0 325.16
14 1 156.77 29 1 330.97
15 1 168.39 30 1 348.39
31 1 354.19
______________________________________
The binary maximal length sequence ensures reduction of pump noises
originating from the impeller 22 to an unavoidable minimum. The crown of
conveying elements or vanes 39 on the other side of the middle plane fully
corresponds to the arrangement clarified by the table above. The
arrangement sequences of the crown of vanes 38 are provided diametrically
opposite the corresponding arrangement sequences of the other crown vanes
39. It is evident that the vane distribution is exempt from an arbitrary
distribution, according to the principle that the sound intensity should
be uniformly distributed in the frequency range. These spectral properties
include pseudo sound noise sequences, particularly binary maximal length
sequences. The advantage of the vane distribution in accordance with the
binary maximal sequence is the limiting to three different intervals or
distances between the vanes.
A further example is the impeller with 18 vanes in which the intervals
between the vanes are distributed according to a primitive root sequence.
The sequence depends on the prime number p=19 and their primitive root g=2
and is formed according to the principle:
a.sub.k =g.sup.k (mod 19); (k=1, 2, . . . , 18) (4)
The table II, that is set forth below, has three columns, of which the
first column indicates the ordinal number k of the vanes, the second
column identifies the primitive root sequence {a.sub.k } and the third
column shows the angle of the position of the respective vanes. The first
vane is positioned at angle 0.degree.. The position of the vane results
from the predecessor position according to the recurrence equation:
.phi.k=.phi.k-1+10.5.degree.+1.degree.a.sub.k-1 ; (k=2, . . . , 18) (5)
Since .phi..sub.1 =0.degree. and a.sub.1 =2,
.phi..sub.2 =0.degree.+10.5.degree.+2.degree.=12.5.degree. and so forth.
The constant addition of 10.5.degree. to the sequence dependent value in
the equation (5) is necessary in order not to allow the difference between
the greatest and the smallest interval to be too large to offset the
efficiency of the pump.
TABLE II
______________________________________
k a.sub.k .phi.k
______________________________________
1 2 0.degree.
2 4 12.5.degree.
3 8 27.degree.
4 16 45.5.degree.
5 13 72.degree.
6 7 95.5.degree.
7 14 113.degree.
8 9 137.5.degree.
9 18 157.degree.
10 17 185.5.degree.
11 15 213.degree.
12 11 238.5.degree.
13 3 260.degree.
14 6 273.5.degree.
15 12 290.degree.
16 5 312.5.degree.
17 10 328.degree.
18 1 348.5.degree.
______________________________________
A further possibility for the impeller is that the intervals between the
vanes can be distributed in accordance with the quadratic residual
sequence. The exemplified sequence depends on the prime number p=17. The
quadratic residuals {a.sub.k } are determined according to the following
equation:
a.sub.k=k.sup.2 (mod p); (k=1, . . . , 16) (6)
The impeller 22 has 16 vanes. The table III which is shown below has three
columns the first of which indicates the ordinal number k of the vanes,
the second column shows the sequence {a.sub.k } of quadratic residuals and
the third column shows the angular position of the corresponding vanes.
The first vane is positioned at angle 0.degree.. The position of the vane
can be defined from the predecessor position according to the following
recurrent equation:
.phi..sub.k =.phi..sub.k-1 +14.degree.+1.degree.a.sub.k-1 ;(k=2 , . . . ,
16) (7)
Since .phi..sub.1 =0.degree. and a.sub.1 =1, .phi..sub.2
=0.degree.+14.degree.+1.degree.=15.degree.. The constant addition of
14.degree. to the sequence-dependent value in equation (7) is necessary in
order not to allow the difference between the greatest interval and the
smallest interval to be too large to affect the efficiency of the
impeller.
TABLE III
______________________________________
k a.sub.k .phi.k
______________________________________
1 1 0.degree.
2 4 15.degree.
3 9 33.degree.
4 16 56.degree.
5 8 86.degree.
6 2 108.degree.
7 15 124.degree.
8 13 153.degree.
9 13 180.degree.
10 15 207.degree.
11 2 236.degree.
12 8 252.degree.
13 16 274.degree.
14 9 304.degree.
15 4 327.degree.
16 1 345.degree.
______________________________________
It will be understood that each of the elements described above, or two or
more together, may also find a useful application in other types of
differing from the impellers for conveying a medium types described above.
While the invention has been illustrated and described as embodied in an
impeller for conveying a medium, it is not intended to be limited to the
details shown, since various modifications and structural changes may be
made without departing in any way from the spirit of the present
invention.
Without further analysis, the foregoing will so fully reveal the gist of
the present invention that others can, by applying current knowledge,
readily adapt it for various applications without omitting features that,
from the standpoint of prior art, fairly constitute essential
characteristics of the generic or specific aspects of this invention.
What is claimed as new and desired to be protected by Letters Patent is set
forth in the appended claims.
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