U.S. patent application number 14/410796 was filed with the patent office on 2015-07-09 for centrifugal multi-blade blower.
The applicant listed for this patent is DENSO CORPORATION. Invention is credited to Shouichi Imahigashi, Masaharu Sakai.
Application Number | 20150192143 14/410796 |
Document ID | / |
Family ID | 49782594 |
Filed Date | 2015-07-09 |
United States Patent
Application |
20150192143 |
Kind Code |
A1 |
Sakai; Masaharu ; et
al. |
July 9, 2015 |
CENTRIFUGAL MULTI-BLADE BLOWER
Abstract
A centrifugal multi-blade blower includes an impeller, and a
casing that accommodates the impeller, and draws in air at least
from an inlet port of the casing which opens on one end side of a
rotation shaft and blows out the air radially outward of the
rotation shaft. The impeller includes a main plate that is joined
to the rotation shaft, vanes which are arranged around the axis of
the rotation shaft and the other end sides of which in the rotation
axis direction are connected to the main plate, and a side plate
that connects together the vanes on their one end sides in the
rotation axis direction. The vanes are characterized in that an
inlet angle on a cross-sectional surface crossing each inner
peripheral edge part of the vanes on a meridian plane of the
impeller in a predetermined direction is evenly made in the entire
region from the side plate-side through the main plate-side, and
that outer peripheral edge parts of the vanes are configured to be
away from the axis of the rotation shaft from the main plate-side
toward the side plate-side.
Inventors: |
Sakai; Masaharu; (Obu-city,
JP) ; Imahigashi; Shouichi; (Kariya-city,
JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
DENSO CORPORATION |
Kariya-city, Aichi-pref. |
|
JP |
|
|
Family ID: |
49782594 |
Appl. No.: |
14/410796 |
Filed: |
June 6, 2013 |
PCT Filed: |
June 6, 2013 |
PCT NO: |
PCT/JP2013/003549 |
371 Date: |
December 23, 2014 |
Current U.S.
Class: |
415/203 |
Current CPC
Class: |
F04D 29/282 20130101;
F04D 29/30 20130101; F04D 17/162 20130101; F04D 29/281 20130101;
F04D 17/10 20130101 |
International
Class: |
F04D 29/28 20060101
F04D029/28; F04D 29/30 20060101 F04D029/30; F04D 17/10 20060101
F04D017/10 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 26, 2012 |
JP |
2012-142803 |
May 10, 2013 |
JP |
2013-100170 |
Claims
1. A centrifugal multi-blade blower comprising: a rotation shaft;
an impeller that rotates with the rotation shaft as a center of the
rotation and includes: a main plate that is coupled with the
rotation shaft; a plurality of vanes that are arranged around an
axis of the rotation shaft; and a side plate that connects together
the plurality of vanes on one end side of the rotation shaft; and a
casing that accommodates the impeller and includes an inlet port
which opens at least on the one end side of the rotation shaft,
wherein: the blower draws in air through the inlet port and blows
out the air radially outward of the rotation shaft; the plurality
of vanes on the other end side of the rotation shaft are connected
to the main plate; the plurality of vanes are configured such that
an inlet angle on a cross-sectional surface crossing each inner
peripheral edge part of the plurality of vanes on a meridian plane
of the impeller in a predetermined direction is evenly made in an
entire region from the side plate through the main plate; outer
peripheral edge parts of the plurality of vanes are configured to
separate from the axis of the rotation shaft from the main plate
toward the side plate; a ratio of an outer peripheral diameter to
an inner peripheral diameter of the impeller on the side plate-side
is a side-plate side inner-outer diameter ratio; a ratio of an
outer peripheral diameter to an inner peripheral diameter of the
impeller on the main plate-side is a main-plate side inner-outer
diameter ratio; and the impeller is configured such that the
side-plate side inner-outer diameter ratio is smaller than the
main-plate side inner-outer diameter ratio.
2. The centrifugal multi-blade blower according to claim 1, wherein
each of the plurality of vanes is configured such that a part of
the inner peripheral edge part on the one end side of the rotation
shaft is located on a front side of a part of the inner peripheral
edge part on the other end side of the rotation shaft in a rotation
direction of the impeller.
3. (canceled)
4. (canceled)
5. (canceled)
6. The centrifugal multi-blade blower according to claim 1, wherein
the inlet angle of each of the plurality of vanes on each
cross-section perpendicular to a direction of the rotation shaft is
made evenly in the entire region from the side plate through the
main plate.
7. The centrifugal multi-blade blower according to claim 1,
wherein: the each inner peripheral edge part of the plurality of
vanes is divided into a predetermined number of portions whose
lengths along the inner peripheral edge part are the same; each of
the outer peripheral edge parts of the plurality of vanes is
divided into the predetermined number of portions whose lengths
along the each of the outer peripheral edge parts are the same; a
line that connects together an inner division point at the each
inner peripheral edge part and an outer division point at the each
of the outer peripheral edge parts is an imaginary flow line, the
inner division point and the outer division point being located in
the same order; and each of the plurality of vanes is configured
such that the inlet angle on a cross-section along each imaginary
flow line is made evenly in the entire region from the side plate
through the main plate.
8. (canceled)
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This application is based on Japanese Patent Application No.
2012-142803 filed on Jun. 26, 2012 and Japanese Patent Application
No. 2013-100170 filed on May 10, 2013, the disclosures of which are
incorporated herein by reference.
TECHNICAL FIELD
[0002] The present disclosure relates to a centrifugal multi-blade
blower that draws air from a direction of a rotation axis and blows
out the air radially outward of the rotation axis.
BACKGROUND ART
[0003] An impeller of a conventional centrifugal multi-blade blower
includes vanes arranged around the rotation axis, and blows out
radially outward the air, which is drawn from the direction of the
rotation axis.
[0004] In this impeller, a wind direction rapidly changes from the
rotation axis direction to the radial direction at spaces between
adjacent vanes (hereinafter referred to as an inter-vane space)
near an air inlet. Accordingly, the air does not flow easily
compared to on an opposite side from the inlet in the rotation axis
direction.
[0005] In a case of a large difference (incidence angle) between an
inlet angle (inlet condition) of an inner peripheral edge of the
vane and an inflow angle (inflow condition) of the air flowing into
the vane, there is a tendency that the air flow exfoliates in the
inter-vane space, and the impeller of the centrifugal multi-blade
blower loses speed. As the incidence angle becomes smaller, the
impeller comes closer to its ideal state.
[0006] However, in a normal impeller, the inlet angle of the inner
peripheral edge of the vane on the inlet side, on which the flow of
air flowing into the vane rapidly changes, becomes significantly
different from the inlet angle on the opposite side from the inlet
on which the flow of air flowing into the vane gradually changes.
For this reason, on the inlet side of the impeller, a difference
easily becomes large between the inflow condition of the air
flowing into the inner peripheral edge and the inflow condition of
the air flowing into the vane. Accordingly, the exfoliation of an
air flow is easily caused in the inter-vane space on the inlet
side.
[0007] As measures against these issues, in, for example, Patent
Document 1, as illustrated in FIG. 21, an inner peripheral edge
part 111 of a vane 110 on a side plate 130-side is formed in a
tapered shape so that an inner diameter of an impeller 100 on the
side plate 130-side (inlet side) is larger than on a main plate
120-side (opposite side from the inlet). Accordingly, draft
resistance on the inlet side of the impeller 100 is reduced to
facilitate a flow of the air flowing from the rotation axis
direction through the inter-vane space near the inlet.
[0008] Furthermore, in Patent Document 1, with a substantial inflow
angle of air flowing into the vane 110 considered to be constant
regardless of the position in the rotation axis direction, an inlet
angle on each section crossing the inner peripheral edge part 111
of the vane 110 in a predetermined direction (e.g., perpendicular
direction) is set within .+-.5 degrees. Accordingly, a difference
between the inlet angle and the inflow angle at the inner
peripheral edge part 111 on the side plate 130-side is reduced to
limit the exfoliation of an air flow on the side plate 130-side. In
addition, FIG. 21 is a meridian plane diagram corresponding to the
impeller 100 illustrated in FIG. 20 of Patent Document 1. The
meridian plane is a surface of section including the rotation axis
of the impeller, onto which a shape of the vane is rotationally
projected.
PRIOR ART DOCUMENT
Patent Document
[0009] Patent Document 1: JP-A-2006-200525
[0010] In the impeller 100 of the above-described conventional
technology, although the air flows easily through the inter-vane
space near the side plate 130, it is still difficult to
sufficiently curb the exfoliation of the air flow on the side plate
130-side. As a consequence of this, there is an issue that a flow
speed distribution is caused on an air outlet side of the impeller
100.
[0011] An explanation as to this regard will be given below with
reference to the drawings. FIGS. 22 and 23 are diagrams
illustrating the issue of the above conventional technology. FIG.
22 is a cross-sectional view taken along a line XXII-XXII in FIG.
21 (sectional view of the vane 110 on the main plate 120-side).
FIG. 23 is a cross-sectional view taken along a line XXIII-XXIII in
FIG. 21 (sectional view of the vane 110 on the side plate
130-side). In FIGS. 22 and 23, an inlet angle .alpha. of each vane
110 is an angle made between a tangent of an inscribed circle
passing through the inner peripheral edge part 111 of each vane
(alternate long and short dash line in FIGS. 22 and 23), and a
tangent at an inner end part of the inner peripheral edge part 111
on a positive pressure surface 110a-side (alternate long and two
short dashes line in FIGS. 22 and 23).
[0012] In the impeller 100 of the conventional technology, because
the inner diameter of the impeller 100 on the side plate 130-side
is larger than on the main plate 120-side, a circumferential speed
Us' on the side plate 130-side is faster than a circumferential
speed Um' on the main plate 120-side (Us'>Um').
[0013] In the impeller 100, as indicated by short dashes arrows in
FIG. 21, a change of the flow direction of air flowing into the
inter-vane space on the side plate 130-side is greater than on the
main plate 120-side. Accordingly, as illustrated in FIGS. 22 and
23, an absolute inflow speed Cs' of the air flowing into the inner
peripheral edge part 111 of the vane 110 on the side plate 130-side
is slower than an absolute inflow speed Cm' of the air flowing into
the inner peripheral edge part 111 of the vane 110 on the main
plate 120-side (Cs'<Cm').
[0014] When an angle made between a resultant relative inflow speed
V of air between a circumferential speed component and an absolute
inflow speed component, and the circumferential speed component is
defined as an inflow angle .beta., as illustrated in FIGS. 22 and
23, an inflow angle .beta.s' on the side plate 130-side is smaller
than an inflow angle .beta.m' on the main plate 120-side.
[0015] Accordingly, if an inlet angle .alpha.s' on the side plate
130-side is made the same as an inlet angle .alpha.m' on the main
plate 120-side as in the impeller 100 of the above conventional
technology, a difference (incidence angle .gamma.s') between the
inlet angle .alpha.s' and the inflow angle .beta.s' on the side
plate 130-side is larger than an incidence angle .gamma.m' on the
main plate 120-side.
[0016] As described above, even in the impeller 100 of the above
conventional technology, the incidence angle .gamma.s' on the side
plate 130-side is still larger than the incidence angle .gamma.m'
on the main plate 120-side, and it is difficult to sufficiently
restrain the exfoliation of the air flow on the side plate
130-side. A flow speed on the side plate 130-side of the impeller
100 on the air outlet side is reduced due to the exfoliation of the
air flow on the side plate 130-side.
[0017] As a result, for example, as in a flow speed distribution
indicated on a right side of the impeller 100 in FIG. 21, on the
air outlet side of the impeller 100, there is made such a flow
speed distribution that a flow speed on the side plate 130-side is
slower than on the main plate 120-side.
[0018] Such an issue arises similarly in the impeller 100 in which
the inner diameter on the side plate 130-side is the same as on the
main plate 120-side, i.e., the impeller 100 in which the inner
peripheral edge part 111 does not have a tapered shape. This is
because in the impeller 100 in which the inner peripheral edge part
111 does not have a tapered shape, the absolute inflow speed Cs' on
the side plate 130-side is slower than on the main plate 120-side,
so that the inflow angle .beta.s' on the side plate 130-side is
smaller than the inflow angle .beta.m' on the main plate
120-side.
SUMMARY OF INVENTION
[0019] The present disclosure addresses the above issues. Thus, it
is an objective of the present disclosure to provide a centrifugal
multi-blade blower that can sufficiently evenly make a flow speed
distribution in a rotation axis direction on an air outlet side of
an impeller.
[0020] To achieve the above-described objective, the present
inventors have earnestly given a great deal of consideration. As a
result, with their attention turned to the fact that in a
centrifugal multi-blade blower, a flow rate of an impeller on its
air outlet side increases in proportion to the second power of an
outer peripheral diameter of the impeller under conditions where
rotating speed and draft resistance are constant, they have worked
out a centrifugal multi-blade blower that can evenly make a flow
speed distribution on the air outlet side of the impeller.
[0021] In one aspect of the present disclosure, the impeller
includes a main plate that is joined to a rotation shaft, vanes
which are arranged around the axis of the rotation shaft and the
other end sides of which in the rotation axis direction are
connected to the main plate, and a side plate that connects
together the vanes on their one end sides in the rotation axis
direction. The vanes are characterized in that the inlet angle on a
cross-sectional surface crossing each inner peripheral edge part of
the vanes on a meridian plane of the impeller in a predetermined
direction is evenly made in the entire region from the side
plate-side through the main plate-side, and that outer peripheral
edge parts of the vanes are configured to be away from the axis of
the rotation shaft from the main plate-side toward the side
plate-side.
[0022] As described above, in such a configuration that the inlet
angle is evenly made in the entire region from the side plate side
through the main plate side, the outer peripheral diameter of the
impeller is larger on the side plate side than on the main plate
side. Accordingly, a flow rate on the air outlet side on the side
plate side of the impeller can be increased. As a consequence, a
flow speed on the air outlet side on the side plate side of the
impeller can be increased compared to the impeller of the
conventional technology.
[0023] Moreover, in accordance with the increase of the flow rate
on the air outlet side on the side plate side of the impeller, a
flow rate of air flowing into the inner peripheral edge part on the
side plate side increases. This increase of the flow rate of air
flowing into the inner peripheral edge part on the side plate side
makes faster a flow speed (absolute inflow speed) on the side plate
side. Accordingly, an inflow angle on the side plate side can be
brought close to the inlet angle.
[0024] As a result, the exfoliation of the air flow on the side
plate side can be restricted as compared with the impeller of the
conventional technology, and there can be mitigated a reduction of
the flow speed on the air outlet side on the side plate side in
association with the exfoliation of the air flow on the side plate
side.
[0025] For the above reason, the centrifugal multi-blade blower of
the present disclosure can sufficiently evenly make a flow speed
distribution in the rotation axis direction on an air outlet side
of the impeller, which becomes an issue in the impeller of the
conventional technology.
[0026] In the above description, "evenly" means a state where the
inlet angle is not shifted or a state where there is only a minute
difference within .+-.5 degrees in the entire region from the side
plate side through the main plate side. The "meridian plane" is a
surface of section including the rotation axis of the impeller,
onto which a shape of the vane is rotationally projected In
addition, the "inlet angle" is an intersecting angle between a
tangent of a circle (inscribed circle) passing through each inner
peripheral edge part of the vanes in a radial direction of the
rotation axis, and the inner peripheral edge part of the vane.
BRIEF DESCRIPTION OF DRAWINGS
[0027] The above and other objects, features and advantages of the
present disclosure will become more apparent from the following
detailed description made with reference to the accompanying
drawings. In the drawings:
[0028] FIG. 1 is a schematic view illustrating an air-conditioning
system for a vehicle including a blower in accordance with a first
embodiment;
[0029] FIG. 2 is a perspective view illustrating an impeller of the
blower of the first embodiment;
[0030] FIG. 3 is a half sectional view illustrating the impeller of
the blower of the first embodiment;
[0031] FIG. 4 is a diagram illustrating a vane part viewed from an
arrowed line IV in FIG. 3;
[0032] FIG. 5 is a diagram illustrating the vane part viewed from
an arrowed line V in FIG. 3;
[0033] FIG. 6 is a diagram illustrating the vane part viewed from
an arrowed line VI in FIG. 3;
[0034] FIG. 7 is a meridian plane diagram illustrating the entire
impeller of the first embodiment;
[0035] FIG. 8 is a meridian plane diagram illustrating an essential
part of the impeller of the first embodiment;
[0036] FIG. 9 is a cross-sectional view taken along a line IX-IX in
FIG. 8;
[0037] FIG. 10 is a cross-sectional view taken along a line X-X in
FIG. 8;
[0038] FIG. 11 is a perspective view illustrating an impeller of a
blower in accordance with a second embodiment;
[0039] FIG. 12 is a half sectional view illustrating the impeller
of the blower of the second embodiment;
[0040] FIG. 13 is a top view illustrating the impeller of the
blower of the second embodiment;
[0041] FIG. 14 is a meridian plane diagram illustrating the
impeller of the blower of the second embodiment;
[0042] FIG. 15 is a meridian plane diagram illustrating an impeller
of a blower in accordance with a third embodiment;
[0043] FIG. 16 is a meridian plane diagram illustrating an
essential part of an impeller of a blower in accordance with a
fourth embodiment;
[0044] FIG. 17 is a meridian plane diagram illustrating an impeller
of a blower in accordance with a modification;
[0045] FIG. 18 is a meridian plane diagram illustrating an impeller
of a blower in accordance with another modification;
[0046] FIG. 19 is a perspective view illustrating an impeller of a
blower in accordance with yet another modification;
[0047] FIG. 20 is a half sectional view illustrating the impeller
of the blower of the yet another modification;
[0048] FIG. 21 is a meridian plane diagram illustrating an
essential part of an impeller in accordance with a conventional
technology;
[0049] FIG. 22 is a cross-sectional view taken along a line
XXII-XXII in FIG. 21; and
[0050] FIG. 23 is a cross-sectional view taken along a line
XXIII-XXIII in FIG. 21.
EMBODIMENTS FOR CARRYING OUT INVENTION
[0051] Embodiments of the present disclosure will be described
below in reference to the drawings. For the same or equivalent
component in the following embodiments, description may be omitted
using its same corresponding reference numeral.
First Embodiment
[0052] A first embodiment will be described below. In the present
embodiment, a centrifugal multi-blade blower of the present
disclosure is applied to an air-conditioning system 1 for a vehicle
including a water-cooled engine.
[0053] As illustrated in FIG. 1, the air-conditioning system 1
includes an air-conditioning casing 2 that defines an air passage
for blown air which is blown into a vehicle interior. At an
uppermost stream side part of the air-conditioning casing 2 in an
air flow direction, there are formed an inside air introduction
port 3 for introducing inside air (vehicle interior air), and an
outside air introduction port 4 for introducing outside air
(vehicle exterior air), and there is provided an inside-outside air
switch door 5 for selectively opening or closing these introduction
ports 3, 4.
[0054] A blower 7 is disposed on a downstream side of the
inside-outside air switch door 5 in an air flow direction, and the
air introduced through the introduction ports 3, 4 is blown by this
blower 7 toward air outlets 14, 15, 17 which will be described
later.
[0055] The blower 7 is a centrifugal multi-blade blower that blows
out radially outward the air which is drawn from the direction of
the rotation axis. In the present embodiment, for the blower 7,
there is employed a single-suction type blower that suctions air
from its one end side in the rotation axis direction and blows out
the air outward in the radial direction.
[0056] The blower 7 includes an impeller 7a, a scroll casing
(casing) 7b, and an electric motor 7c that drives the impeller 7a.
The impeller 7a rotates with a rotation shaft 70 as the center to
blow out the air outward in the radial direction, and is configured
from resin. The scroll casing 7b accommodates the impeller 7a, and
includes a vortical passage through which the air blown out of the
impeller 7a merges together. The scroll casing 7b includes an inlet
port 74 that opens on one end side of the rotation shaft 70.
Details of the impeller 7a of the blower 7 of the present
embodiment will be described later.
[0057] An evaporator 9 is disposed on a downstream side of the
blower 7 in the air flow direction, and all the air blown by the
blower 7 passes through this evaporator 9. The evaporator 9 of the
present embodiment is an air cooling means for exchanging heat
between refrigerant flowing in the evaporator 9 and blown air which
is blown by the blower 7 to cool the blown air. Together with a
compressor, a condenser, a gas-liquid separation device, an
expansion valve, and so forth which are not shown, this evaporator
9 constitutes a vapor-compression type refrigeration cycle.
[0058] A heater core 10 is disposed on a downstream side of the
evaporator 9 in the air flow direction. The heater core 10 is an
air heating means for exchanging heat between engine coolant for
cooling an engine 11 and air after having passed through the
evaporator 9 to heat the air after having passed through the
evaporator 9.
[0059] The air-conditioning casing 2 includes a bypass passage 12
through which the air after having passed through the evaporator 9
flows to bypass the heater core 10. On an upstream side of the
heater core 10 in the air flow direction, there is disposed an air
mixing door 13 that adjusts an air volume ratio between the volume
of air passing through the heater core 10 and the volume of air
passing through the bypass passage 12 to adjust the temperature of
air blown out into the vehicle interior.
[0060] At a downmost stream part of the air-conditioning casing 2
in the air flow direction, there are provided the face air outlet
14 for blowing out the air toward an upper half of a body of an
occupant of the vehicle, the foot air outlet 15 for blowing out the
air toward a foot of the occupant, and the defroster air outlet 17
for blowing out the air toward an inner surface of a window pane
16.
[0061] Blowing-out mode switch doors 18, 19, and 20 are arranged
respectively on an upstream side of these air outlets 14, 15, 17 in
the air flow direction. These blowing-out mode switch doors 18 to
20 are switchingly opened or closed to switch between a face mode
in which to blow out the air toward an upper body of the occupant,
a foot mode in which to blow out the air toward a lower body of the
occupant, and a defroster mode in which to blow out the air toward
an inner surface of the window pane of the vehicle.
[0062] The impeller 7a of the blower 7 of the present embodiment
will be described below. As illustrated in a perspective view of
FIG. 2 and a half sectional view of FIG. 3, the impeller 7a of the
blower 7 includes vanes 71, a side plate 72, and a main plate
73.
[0063] The main plate 73 is configured by a disc-like member that
is joined to the rotation shaft 70. The main plate 73 of the
present embodiment is connected to a part 71b of each vane 71 on
the other end side (lower side on a plane of paper) in the rotation
axis direction, and is configured to overlap with the vanes 71 when
viewed from the rotation axis direction.
[0064] The side plate 72 is connected to a part of each vane 71
radially outward of the rotation shaft 70 on one end side (upper
side on a plane of paper) in the rotation axis direction. The side
plate 72 of the present embodiment is connected to cover an outer
peripheral edge part (vane rear edge) 712 of each vane 71 on the
one end side in the rotation axis direction, from a radially
outward side of the rotation shaft 70. More specifically, the side
plate 72 of the present embodiment has an annular shape (shroud
shape) which is bent such that its part on the one end side in the
rotation axis direction is located inward of the part on the other
end side in the radial direction of the rotation shaft 70. The side
plate 72 of the present embodiment is configured such that its
inner peripheral diameter Ds is larger than an outer peripheral
diameter Dm of the main plate 73, and has a shape that does not
overlap with the main plate 73 when viewed from the rotation axis
direction.
[0065] The vanes 71 are arranged around the axis Z of the rotation
shaft 70. The vanes 71, the side plate 72, and the main plate 73,
which constitute the impeller 7a, are integrally molded by resin
molding or the like.
[0066] As a result of the rotation of the rotation shaft 70, the
impeller 7a configured in this manner blows out by centrifugal
force radially outward of the impeller 7a the air, which has flowed
from the inlet port 74 on the one end side in the rotation axis
direction into inter-vane spaces (spaces between the vanes 71) in
the impeller 7a.
[0067] A shape of the vane 71 of the present embodiment will be
described below. FIGS. 4 to 6 are diagrams viewed respectively from
arrowed lines in FIG. 3 and illustrate the shape of the vane 71 of
the present embodiment. For convenience of explanation, in FIGS. 4
to 6, illustrations of the side plate 72 and the main plate 73 are
omitted, and typical three vanes 71 in directions of the arrowed
lines A to C in FIG. 3 are illustrated.
[0068] As illustrated in FIG. 4, an inner peripheral edge part
(vane front edge) 711 is provided for each vane 71 between parts
71a, 71b on both end sides of the vane 71 on an inner peripheral
side of the impeller 7a. As illustrated in FIG. 5, an outer
peripheral edge part (vane rear edge) 712 is provided for each vane
71 between the parts 71a, 71b on both end sides of the vane 71 on
an outer peripheral side of the impeller 7a.
[0069] In each vane 71 of the present embodiment, as illustrated in
FIG. 6, when viewed from the rotation axis direction, a part 711a
of the inner peripheral edge part 711 on the one end side in the
rotation axis direction is located further on a front side than a
part 711b of the inner peripheral edge part 711 on the other end
side in the rotation axis direction, in a rotation direction R of
the impeller 7a.
[0070] As described above, the impeller 7a of the present
embodiment is configured to blow out radially outward the air which
is drawn from the rotation axis direction. Accordingly, the part
711a of the inner peripheral edge part 711 on the one end side in
the rotation axis direction is located on a front side of the part
711b of the inner peripheral edge part 711 on the other end side in
the rotation axis direction, in the rotation direction R, so that
the air is suctioned easily into the inter-vane spaces from the
rotation axis direction on the side plate 72-side. As a result, the
flow rate of air flowing into the inter-vane spaces on the side
plate 72-side can be increased. The part 711a of the inner
peripheral edge part 711 on the one end side in the rotation axis
direction may be hereinafter referred to as a forward part 711a,
and the part 711b of the inner peripheral edge part 711 on the
other end side in the rotation axis direction may be hereinafter
referred to as a backward part 711b.
[0071] The specific shapes of the inner peripheral edge part 711
and the outer peripheral edge part 712 of each vane 71 will be
described with reference to the meridian plane diagrams in FIGS. 7
and 8. The "meridian plane" is a surface of section including the
rotation shaft 70 of the impeller 7a, onto which a shape of the
vane 71 is rotationally projected.
[0072] As illustrated in FIGS. 7 and 8, the inner peripheral edge
part 711 of the vane 71 of the present embodiment is configured to
separate from the axis Z of the rotation shaft 70 from the main
plate 73-side toward the side plate 72-side such that the inner
peripheral diameter of the impeller 7a on the side plate 72-side is
larger than the inner peripheral diameter on the main plate
73-side. The inner peripheral diameter of the impeller 7a is a
diameter of an inscribed circle passing through the inner
peripheral edge parts 711 of the vanes 71 in the radial direction
of the rotation shaft 70.
[0073] In the case of a large difference (incidence angle .gamma.)
between an inlet angle .alpha. at the inner peripheral edge part
711 of the vane 71, and an inflow angle .beta. of air flowing into
the inner peripheral edge part 711, an exfoliation region is formed
in the inter-vane space, so that the centrifugal multi-blade blower
loses its speed. Accordingly, the centrifugal multi-blade blower is
put into its ideal state when the incidence angle .gamma. is
small.
[0074] However, in a normal centrifugal multi-blade blower, there
is a tendency that a difference between an inlet angle .alpha. and
an inflow angle .beta. at the inner peripheral edge part 711 on the
side plate 72-side easily becomes large in comparison to on the
main plate 73-side, and the exfoliation of the air flow is thereby
easily produced in the inter-vane space on the side plate
72-side.
[0075] Accordingly, in the present embodiment, the inlet angle
.alpha. on each cross-sectional surface crossing the inner
peripheral edge part 711 of the vane 71 that appears on the
meridian plane of the impeller 7a in a predetermined direction is
set to be evenly made in the entire region from the side plate
72-side through the main plate 73-side. "Evenly" means a state
where the inlet angle .alpha. is not shifted or a state where there
is only a minute difference within .+-.5 degrees in the entire
region from the side plate 72-side through the main plate
73-side.
[0076] FIG. 9 is a cross-sectional view taken along a line IX-IX in
FIG. 8, and FIG. 10 is a cross-sectional view taken along a line
X-X in FIG. 8. The cross-section surface along the line IX-IX is a
surface of section obtained by cutting a part of the vane 71 on the
main plate 73-side in a direction perpendicular to the rotation
axis direction. The cross-section surface along the line X-X is a
surface of section obtained by cutting a part of the vane 71 on the
side plate 72-side in a direction perpendicular to the rotation
axis direction.
[0077] Specifically, in the present embodiment, as illustrated in
FIGS. 9 and 10, an inlet angle .alpha.m, as at the inner peripheral
edge part 711 of each vane 71 on each cross-section perpendicular
to the rotation axis direction is set at an angle (e.g., angle
ranging from 55 degrees to 76 degrees) that is even in the entire
region from the side plate 72-side through the main plate
73-side.
[0078] In the present embodiment, the inlet angle .alpha.m, as is
an angle made between a tangent line (alternate long and short dash
line in FIGS. 9 and 10) of the inscribed circle passing through the
inner peripheral edge parts 711 of the vanes 71, and a tangent line
(alternate long and two short dashes line in FIGS. 9 and 10) at an
inner end part 713a of the vane 71 on a positive pressure surface
713-side.
[0079] As described for the above issue, it is difficult to
sufficiently inhibit the exfoliation of the air flow on the side
plate 72-side only by evenly making the inlet angle .alpha.m, as at
the inner peripheral edge part 711 of each vane 71 in the entire
region from the side plate 72-side through the main plate
73-side.
[0080] Accordingly, in the present embodiment, as illustrated in
FIG. 7, the outer peripheral edge parts 712 of the vanes 71 are
shaped to be away from the axis Z of the rotation shaft 70 from the
main plate 73-side toward the side plate 72-side such that the
outer peripheral diameter of the impeller 7a on the side plate
72-side is larger than the outer peripheral diameter of the
impeller 7a on the main plate 73-side. The outer peripheral
diameter of the impeller 7a is a diameter of a circumscribed circle
passing through the outer peripheral edge parts 712 of the vanes 71
in the radial direction of the rotation shaft 70.
[0081] Specifically, the vanes 71 of the present embodiment are
configured to have the inner peripheral diameter increased from the
main plate 73-side toward the side plate 72-side, and to have the
outer peripheral diameter increased from the main plate 73-side
toward the side plate 72-side (d1>d2, D1>D2). For this
reason, an outer configuration of the impeller 7a of the present
embodiment has a shape of an inverted trapezoid.
[0082] In the present embodiment, a side-plate side inner-outer
diameter ratio is smaller than a main-plate side inner-outer
diameter ratio. The side-plate side inner-outer diameter ratio is a
ratio of an outer peripheral diameter D1 to an inner peripheral
diameter d1 (=D1/d1) of the impeller 7a on the side plate 72-side,
and the main-plate side inner-outer diameter ratio is a ratio of an
outer peripheral diameter D2 to an inner peripheral diameter d2
(D2/d2) of the impeller 7a on the main plate 73-side.
[0083] Operation of the air-conditioning system 1 of the present
embodiment will be described below. When the operation of the
air-conditioning system 1 is started by operation by the occupant,
for example, the air introduced into the air-conditioning casing 2
through the introduction ports 3, 4 is blown toward the air outlets
14, 15, 17 by the blower 7. The blown air which is blown by the
blower 7 is adjusted to have a desired temperature by the
evaporator 9, the heater core 10, and the air mixing door 13, and
is blown out into the vehicle interior through any air outlet of
the air outlets 14, 15, 17.
[0084] In the blower 7 of the present embodiment, the inner
peripheral edge parts 711 of the vanes 71 are shaped to separate
from the axis Z of the rotation shaft 70 from the main plate
73-side toward the side plate 72-side such that the inner
peripheral diameter of the impeller 7a becomes large from the main
plate 73-side toward the side plate 72-side. Accordingly, draft
resistance on the side plate 72-side of the impeller 7a can be
reduced to make the air flowing from the rotation axis direction
flow easily into the inter-vane spaces on the side plate
72-side.
[0085] In the blower 7 of the present embodiment, the inlet angle
.alpha.m, as at the inner peripheral edge part 711 of each vane 71
on each cross-section perpendicular to the axis of the rotation
shaft 70 is made evenly in the entire region from the side plate
72-side through the main plate 73-side. Accordingly, as compared to
a normal centrifugal multi-blade blower, the exfoliation of the air
flow on the side plate 72-side can be limited to make the air
flowing from the rotation axis direction flow easily into the
inter-vane spaces near the inlet port 74.
[0086] In the blower 7 of the present embodiment, the outer
peripheral edge parts 712 of the vanes 71 are shaped to be away
from the axis Z of the rotation shaft 70 from the main plate
73-side toward the side plate 72-side. Accordingly, there is evenly
made a flow speed distribution in the rotation axis direction on an
air outlet side of the impeller 7a, which comes to an issue when
the inlet angle .alpha.m, as at the inner peripheral edge part 711
of each vane 71 is made evenly in the entire region from the side
plate 72-side through the main plate 73-side.
[0087] To explain this regard, in the centrifugal multi-blade
blower, the flow rate of the impeller 7a on its air outlet side
increases in proportion to the second power of the outer peripheral
diameter of the impeller 7a under conditions where rotating speed
and draft resistance are constant. Accordingly, by increasing the
outer peripheral diameter of the impeller 7a on the side plate
72-side compared with on the main plate 73-side, the flow rate on
the air outlet side of the impeller 7a on its side plate 72-side
increases, whereupon the flow speed on the air outlet side of the
impeller 7a on its side plate 72-side becomes fast. Thus, the flow
speed on the side plate 72-side of the impeller 7a on its air
outlet side can be brought close to the flow speed on the main
plate 73-side.
[0088] Moreover, the flow rate of air flowing into the inner
peripheral edge parts 711 on the side plate 72-side increases in
accordance with the increase of the flow rate on the air outlet
side of the impeller 7a on its side plate 72-side. This increase of
the flow rate of air flowing into the inner peripheral edge parts
711 on the side plate 72-side makes faster the flow speed on the
side plate 72-side. Accordingly, a difference between the inlet
angle and the inflow angle on the side plate 72-side can be
reduced.
[0089] In the present embodiment, because the inner diameter of the
impeller 7a on its side plate 72-side is larger than on the main
plate 73-side, a circumferential speed Us on the side plate 72-side
is faster than a circumferential speed Um on the main plate 73-side
(Us>Um) as illustrated in FIGS. 9 and 10.
[0090] On the other hand, an absolute inflow speed of the air
flowing into the inner peripheral edge parts 711 of the vanes 71 on
the side plate 72-side is faster by an increase Cp of the flow
speed (=Cs+Cp) due to the increase of the flow rate of air flowing
into the inner peripheral edge parts 711.
[0091] When an angle made between a resultant relative inflow speed
V of air between a circumferential speed component and an inflow
speed component, and the circumferential speed component is defined
as an inflow angle .beta., an inflow angle .beta.s on the side
plate 72-side is an angle that is close to an inflow angle .beta.m
on the main plate 73-side.
[0092] In the impeller 7a of the present embodiment, the inlet
angle .alpha.s on the side plate 72-side is made (almost) the same
as the inlet angle .alpha.m on the main plate 73-side. Accordingly,
a difference (incidence angle .gamma.s) between the inlet angle
.alpha.s and the inflow angle .beta.s on the side plate 72-side is
reduced.
[0093] As a result, the exfoliation of the air flow on the side
plate 72-side is sufficiently curbed, so that there can be
alleviated a reduction of the flow speed on the air outlet side on
the side plate 72-side associated with the exfoliation of the air
flow on the side plate 72-side. Consequently, the flow speed on the
side plate 72-side of the impeller 7a on its air outlet side can be
brought even closer to the flow speed on the main plate
73-side.
[0094] As a consequence, as in a flow speed distribution indicated
on a right side of the impeller 7a in FIG. 8, for example, the flow
speed distribution in the rotation axis direction on the air outlet
side of the impeller 7a can be sufficiently evenly made.
Improvement in efficiency of the blower 7 and restraint of noise of
the blower 7 can be promoted.
[0095] Particularly, in the present embodiment, the part 711a of
the inner peripheral edge part 711 on the one end side in the
rotation axis direction is positioned further on a front side in
the rotation direction R than the part 711b of the inner peripheral
edge part 711 on the other end side in the rotation axis
direction.
[0096] Accordingly, because of the increase of the flow rate of air
flowing into the inter-vane spaces on the side plate 72-side, there
can be increased the flow speed (absolute inflow speed) of air
flowing into the inner peripheral edge parts 711 on the side plate
72-side. As a consequence, the incidence angle .gamma.s on the side
plate 72-side can be further reduced. Consequently, the exfoliation
of the air flow on the side plate 72-side can be restricted more
effectively.
Second Embodiment
[0097] A second embodiment will be described below. In the present
embodiment, an example of modification of the shape of the main
plate 73 to the first embodiment will be described. In the present
embodiment, explanation will be given with the description of a
part similar or equivalent to the first embodiment omitted or
simplified.
[0098] In an impeller 7a of the present embodiment, an outer
peripheral diameter of a main plate 73 is made smaller than in the
first embodiment as illustrated in a perspective view in FIG. 11, a
half sectional view in FIG. 12, and a top view in FIG. 13.
Specifically, in the present embodiment, as illustrated in FIG. 13,
the outer peripheral diameter of the main plate 73 is made small
such that the main plate 73 and a forward part 711a of an inner
peripheral edge part 711 do not overlap with each other when the
impeller 7a is viewed from the rotation axis direction.
[0099] More specifically, as illustrated in a meridian plane
diagram in FIG. 14, a distance L1 from an axis Z of a rotation
shaft 70 to an outer peripheral end of the main plate 73 is smaller
than a distance L2 from the axis Z of the rotation shaft 70 to the
forward part 711a of the inner peripheral edge part 711.
[0100] The other configurations are similar to the first
embodiment. Thus, a blower 7 of the present embodiment produces
effects similar to the first embodiment.
[0101] In the case of such a configuration (three-dimensional vane)
that the forward part 711a of the inner peripheral edge part 711 is
located on a front side of a backward part 711b of the inner
peripheral edge part 711 in the rotation direction R, when
integrally molding vanes 71, a side plate 72, and the main plate
73, the forward part 711a may be undercut.
[0102] As measures against this, in the present embodiment, the
impeller 7a is shaped such that the main plate 73 and a forward
part 711a of an inner peripheral edge part 711 do not overlap with
each other in the rotation axis direction by making small the outer
peripheral diameter of the main plate 73. Accordingly, when
integrally-shaping at least the main plate 73 and the vanes 71 by
molding, a molded article can be taken out from a mold by sliding
the mold in the rotation axis direction. As a consequence, the
impeller 7a can easily be produced to reduce the costs.
Third Embodiment
[0103] A third embodiment will be described below. In the present
embodiment, an example of modification of the shape of the impeller
7a to the first and second embodiments will be described. In the
present embodiment, explanation will be given with the description
of a part similar or equivalent to the first and second embodiments
omitted or simplified.
[0104] In the present embodiment, as illustrated in FIG. 15, a
ratio of an outer peripheral diameter D1 to an inner peripheral
diameter d1 of an impeller 7a on a side plate 72-side (side-plate
side inner-outer diameter ratio) is larger than a ratio of an outer
peripheral diameter D2 to an inner peripheral diameter d2 of the
impeller 7a on a main plate 73-side (main-plate side inner-outer
diameter ratio) (D1/d1>D2/d2).
[0105] Specifically, in the present embodiment, outer peripheral
edge parts 712 of vanes 71 are configured to be away from an axis Z
of a rotation shaft 70 from the main plate 73-side toward the side
plate 72-side, and inner peripheral edge parts 711 of the vanes 71
are configured to extend along the rotation axis direction. More
specifically, in the impeller 7a of the present embodiment, the
outer peripheral diameter of the impeller 7a on the side plate
72-side is larger than the outer peripheral diameter of the
impeller 7a on the main plate 73-side, and the inner peripheral
diameter of the impeller 7a on the side plate 72-side and the inner
peripheral diameter of the impeller 7a on the main plate 73-side
are equal to each other.
[0106] The other configurations are similar to the first
embodiment, and the blower 7 of the present embodiment produces
effects similar to the effects of the first embodiment.
[0107] In the case of the side-plate side inner-outer diameter
ratio (=D1/d1) being smaller than the main-plate side inner-outer
diameter ratio (D2/d2) as in the first embodiment, if the inner
peripheral diameter of the impeller 7a on the side plate 72-side is
too large, the circumferential speed Us at the inner peripheral
edge part 711 on the side plate 72-side increases. As a result, the
inflow angle .beta.s at the inner peripheral edge part 711 on the
side plate 72-side becomes small, and the difference between the
inlet angle .alpha.s and the inflow angle .beta.s at the inner
peripheral edge part 711 on the side plate 72-side may thereby be
increased.
[0108] On the other hand, in the present embodiment, since the
side-plate side inner-outer diameter ratio of the impeller 7a is
larger than the main-plate side inner-outer diameter ratio, the
inner peripheral diameter of the impeller 7a on the side plate
72-side is not too large, so that there can be limited the increase
of the circumferential speed Us at the inner peripheral edge part
711 on the side plate 72-side. Therefore, as a result of the
configuration of the present embodiment, there can be restrained a
the increase of the circumferential speed at the inner peripheral
edge part 711 on the side plate 72-side which influences the inflow
angle at the inner peripheral edge part 711 on the side plate
72-side in addition to the flow rate increase on the side plate
72-side.
[0109] Accordingly, the inflow angle .beta.s at the inner
peripheral edge part 711 on the side plate 72-side becomes large,
so that the difference between the inlet angle .alpha.s and the
inflow angle .beta.s at the inner peripheral edge part 711 on the
side plate 72-side is reduced. As a result, the exfoliation on the
side plate 72-side can be effectively inhibited.
Fourth Embodiment
[0110] A fourth embodiment will be described below. In the present
embodiment, explanation will be given with the description of a
part similar or equivalent to the first to third embodiments
omitted or simplified.
[0111] In the present embodiment, imaginary flow lines, whereby
flow directions of air flowing into inner peripheral edge parts 711
of vanes 71 are assumed, are set, and the inlet angles .alpha. on
cross-sections on the imaginary flow lines are made evenly in the
entire region from a side plate 72-side through a main plate
73-side (e.g., angle ranging from 55 degrees to 76 degrees).
[0112] Specifically, in the present embodiment, as illustrated in
FIG. 16, first to sixth division lines Yd1 to Yd6 are set as the
imaginary flow lines, and the inlet angles .alpha. on
cross-sections on the imaginary flow lines Yd1 to Yd6 are made
evenly over the entire range of the inner peripheral edge part 711
of the vane 71
[0113] To explain the setting of the imaginary flow lines, the
inner peripheral edge part 711 of the vane 71 is divided into a
predetermined number of portions whose lengths along the inner
peripheral edge part 711 are equal to set a division point Yin at
the inner peripheral edge part 711. In the present embodiment, the
division point Yin at the inner peripheral edge part 711 is set as
a first inner peripheral division point Yi1, a second inner
peripheral division point Yi2, . . . , and a sixth inner peripheral
division point Yi6 in order from one end side of the vane 71 in the
rotation axis direction.
[0114] Similarly, an outer peripheral edge part 712 of the vane 71
is divided into a predetermined number of portions whose lengths
along the outer peripheral edge part 712 are equal to set a
division point Yon at the outer peripheral edge part 712. In the
present embodiment, the division point Yon at the outer peripheral
edge part 712 is set as a first outer peripheral division point
Yo1, a second outer peripheral division point Yo2, . . . , and a
sixth outer peripheral division point Yo6 in order from one end
side of the vane 71 in the rotation axis direction.
[0115] Then, a line (first to sixth division points Yd1 to Yd6)
that connects together the division points having the same number
out of the inner peripheral division point Yin and the outer
peripheral division point Yon when counted in order from one end
side of the vane 71 in the rotation axis direction is set as the
imaginary flow line.
[0116] The other configurations are similar to the first
embodiment, and a blower 7 of the present embodiment produces
effects similar to the effects of the first embodiment.
Furthermore, the blower 7 of the present embodiment has the
advantage that design surfaces of the vanes 71 do not intersect
with each other and the vanes 71 of an impeller 7a are thereby
easily designed.
[0117] In the present embodiment, there has been described an
example of setting the six imaginary flow lines by dividing the
inner peripheral edge part 711 and the outer peripheral edge part
712 of the vane 71 into six portions. However, the present
disclosure is not limited to this example, and the set number of
imaginary flow lines may be specified at an arbitrary number (e.g.,
ten).
[0118] The embodiments of the present disclosure have been
described above. However, the present disclosure is not limited to
these embodiments, and can be variously modified, for example, as
below without departing from the scope of claims.
[0119] (1) In the above-described embodiments, it is illustrated
for the shape of the vane 71 that the part 711a of the inner
peripheral edge part 711 on the one end side in the rotation axis
direction is positioned further on a front side in the rotation
direction R of the impeller 7a than the part 711b of the inner
peripheral edge part 711 on the other end side in the rotation axis
direction. However, the present disclosure is not limited to this
example. For example, there may be employed such a vane 71 that the
position of the inner peripheral edge part 711 is located further
on a rear side in the rotation direction R of the impeller 7a from
the main plate 73-side toward the side plate 72-side.
[0120] (2) In the above embodiments, it is illustrated that the
side plate 72 has an annular shape which is bent such that its part
on the one end side in the rotation axis direction is located
inward of the part on the other end side in the radial direction of
the rotation shaft 70. However, the present disclosure is not
limited to this example. For example, as illustrated in FIG. 17,
the side plate 72 is formed in a circular ring shape extending
along the rotation axis direction, and may be connected to the
outer peripheral edge parts 712 of the vanes 71 located radially
outward on the one end side in the rotation axis direction.
[0121] In the above embodiments, it is illustrated that the side
plate 72 is connected to cover the outer peripheral edge parts 712
of the vanes 71 from a radially outward side of the rotation shaft
70. However, the present disclosure is not limited to this example.
For example, as illustrated in FIG. 18, the side plate 72 may be
connected to the parts 71a of the vanes 71 on the one end side in
the rotation axis direction.
[0122] In a case of employment of any shape, the main plate 73 and
the side plate 72 do not overlap with each other as far as possible
when viewed from the rotation axis direction so that undercutting
is not caused when integrally molding the impeller 7a. As a matter
of course, as long as the impeller 7a can be integrally molded, the
main plate 73 and the side plate 72 may overlap with each other
when viewed from the rotation axis direction.
[0123] (3) In the above-described third embodiment, it is
illustrated that the inner peripheral edge parts 711 of the vanes
71 extend along the rotation axis direction. However, as long as
the side-plate side inner-outer diameter ratio of the impeller 7a
is larger than the main-plate side inner-outer diameter ratio, the
inner peripheral edge parts 711 of the vanes 71 may separate from
the axis Z of the rotation shaft 70 from the main plate 73-side
toward the side plate 72-side.
[0124] (4) In the above embodiments, an example of employment of a
single-suction type blower for the blower 7 has been described.
However, the present disclosure is not limited to this example.
There may be used a double-suction type blower that suctions air
from both sides in the rotation axis direction.
[0125] In this case, for example, as illustrated in FIGS. 19 and
20, first and second impeller parts 7aa, 7ab that are configured
similar to the impeller 7a described in the above embodiments may
be provided. Main plates 73a, 73b of the impeller parts 7aa, 7ab
may be connected together by a connecting member 75.
[0126] Each vane 71 of the impeller parts 7aa, 7ab is configured
such that the inlet angle .alpha. on each cross-sectional surface
crossing the inner peripheral edge part 711 on the meridian plane
of the impeller 7a in a predetermined direction is made evenly in
the entire region from a side plate 72a, 72b-side through a main
plate 73a, 73b-side. Moreover, the outer peripheral edge parts 712
of the vanes 71 in the impeller parts 7aa, 7ab are configured to be
away from the axis Z of the rotation shaft 70 from the main plates
73a, 73b-side toward the side plates 72a, 72b-side.
[0127] (5) In the above first embodiment, it is illustrated that
the inlet angle .alpha. on each cross-section perpendicular to the
rotation axis direction on the meridian plane of the impeller 7a is
made evenly in the entire region from the side plate 72-side
through the main plate 73-side. However, the present disclosure is
not limited to this example. For example, the inlet angle .alpha.
on each cross-section perpendicular to the inner peripheral edge
part 711 on the meridian plane of the impeller 7a may be made
evenly in the entire region from the side plate 72-side through the
main plate 73-side.
[0128] (6) In the above embodiments, an example of application of
the blower 7 to the air-conditioning system 1 for a vehicle has
been described. However, the blower 7 may be applied to another
air-conditioning system as well as to the air-conditioning system 1
for a vehicle.
[0129] (7) The above embodiments can be appropriately combined
together if they are not unrelated and unless the combination is
obviously impossible. In the above embodiments, it goes without
saying that the elements which constitute the embodiment are not
necessarily essential except, for example, when clearly shown to be
particularly necessary and when considered to be obviously
essential in principle.
[0130] In the above embodiments, the present disclosure is not
limited to a particular numeral for the component of the embodiment
except, for example, when the numerical value of the component such
as the number, value, amount, or range is referred to, when it is
clearly shown to be particularly necessary, or when the component
is obviously limited to its particular numeral in principle.
[0131] In addition, in the above embodiments, when the shape or
positional relationship of the component or the like is referred
to, the component is not limited to this shape or positional
relationship except, for example, in the case of its particularly
explicit indication or in the case of the component limited to its
particular shape, positional relationship or the like in
principle.
[0132] While the present disclosure has been described with
reference to embodiments thereof, it is to be understood that the
disclosure is not limited to the embodiments and constructions. The
present disclosure is intended to cover various modification and
equivalent arrangements. In addition, while the various
combinations and configurations, other combinations and
configurations, including more, less or only a single element, are
also within the spirit and scope of the present disclosure.
* * * * *