CN1788168A

CN1788168A - Centrifugal blower

Info

Publication number: CN1788168A
Application number: CN 200380110333
Authority: CN
Inventors: 村川雅裕; 浅山荣治
Original assignee: Seikow Chemical Engr and Machinery Ltd
Current assignee: Seikow Chemical Engr and Machinery Ltd
Priority date: 2003-06-05
Filing date: 2003-11-26
Publication date: 2006-06-14
Anticipated expiration: 2023-11-26
Also published as: CN100404878C; JP2004360579A; WO2004109120A1; JP4590167B2; TWI253491B; TW200427930A

Abstract

The object of the present invention is to provide a centrifugal blower capable of reducing kinds as compared to the conventional centrifugal blowers without deteriorating performance. The centrifugal blower (100) in accordance with the present invention is a centrifugal blower (100) that comprises an impeller (2) incorporated in a volute casing (1). The casing (1) includes: a delivery passage (1b) formed so that an axial centerline (3) of a delivery port (1c) thereof extends through an axis of the impeller (2) and a speed reduction part (4) formed in the delivery passage (1b) near the delivery port (1c) and the flow passage thereof being outward curved and gradually diverged in the delivery direction of the fluid to efficiently reduce the speed of the fluid flowing therein.

Description

Centrifugal blower

Technical field

The present invention relates to that air-conditioning equipment or air regenerating device etc. use, possess the centrifugal blower of swirl shape shell.

Background technique

Fig. 5 is the sectional arrangement drawing of the structure of the existing centrifugal blower that possesses the swirl shape shell of expression.Centrifugal blower 200 possess shell 10 and in be loaded on impeller 11 in the vortex chamber in this shell 10.The axle direction center line 12 of the exhaust outlet 10a of shell 10 and the axis by impeller 11 keep certain spaced and parallel with center line (hereinafter referred to as " the 1st the center line ") CL1 of the axle direction equidirectional of exhaust outlet 10a.

At the exhaust outlet 10a of the shell 10 of this centrifugal blower 200, flow through its outer circumferential side fluid flow faster than the flowing velocity that flows through the fluid of all sides in it.Therefore be connected under the bending direction of pipe arrangement of the exhaust outlet 10a situation identical with the sense of rotation of impeller 11, fluid flows along the bending of pipe arrangement, therefore the big pressure loss does not take place, but under the bending direction of the pipe arrangement situation opposite with the sense of rotation of impeller 11, the fluid of the fast part that flows exerts an influence, in the bigger pressure loss of curved section generation of pipe arrangement.Therefore the problem of predetermined airflow takes place to obtain.

And shown in Fig. 6 A and Fig. 6 B, even made fluid under the situation that identical direction (top among the figure) flows out in the past, also prepare to make the two kinds of impellers 11 and the shell 10 corresponding of sense of rotation difference (dextrorotation or left-handed) respectively with it corresponding to the bending direction of the pipe arrangement that connects on the exhaust outlet 10a of shell 10.

This shell 10 is provided with simultaneously with the motor 15 of drives impeller 11 on the base station 14 of centrifugal blower 200.The sense of rotation that makes impeller 11 is identical direction, only change under the situation of outflow direction 13 of fluid, respectively shown in Fig. 6 A, Fig. 6 C, Fig. 6 E, identical shell 10 is arranged on the base station 14, so that make the outflow direction 13 (top among the figure, left, right-hand) of axle direction center line 12 with each fluid of exhaust outlet 10a roughly consistent.But the shape that is installed on the part on the base station 14 of shell 10 has nothing in common with each other, and therefore is necessary to prepare 3 kinds of base stations 14 corresponding to the outflow direction 13 of fluid.

Equally, under the sense of rotation of impeller 11 and top described different situation, shown in Fig. 6 B, Fig. 6 D, Fig. 6 F, identical shell 10 is arranged on the base station 14, so that make the outflow direction 13 (top among the figure, left, right-hand) of axle direction center line 12 with each fluid of exhaust outlet 10a roughly consistent.In this case, also, be necessary to prepare respectively 3 kinds of base stations 14 with top described identical.

According to the above, always all need to prepare at least 6 kinds of centrifugal blowers 200 with identical performance.Therefore the manufacturing efficiency of centrifugal blower 200 is low, also has the miscellaneous problem of storehouse management.

Therefore, in order to tackle such problem, for example shown in Fig. 7 A, the shell 10 of the existing centrifugal blower 200 shown in 2 locking wires is disposed on the base station 14, so that make the 1st centre line C L 1 of the axle direction center line 12 of its exhaust outlet 10a near above-mentioned impellers 11.Also have, elbow 16 is installed on the exhaust outlet 10a of this shell 10, and make that the axle direction center line 12 of exhaust outlet 10a of this shell 10 is consistent with the 1st centre line C L 1 of impeller 11.By means of this, make the axle direction center line 12a of the exhaust outlet 16a that newly forms on the end of elbow 16 consistent with the 1st centre line C L 1 of impeller 11.

So just make near the central part of the fast fluid of above-mentioned flowing velocity near above-mentioned new exhaust outlet 16a, even this exhaust outlet 16a is gone up the pipe arrangement of connection to the direction bending identical with the sense of rotation of impeller 11, or crooked round about, in situations such as this curved section also are not easy to take place that fluid is peeled off.Consequently, can prevent the big pressure loss situation.

But in this case, elbow 16 newly is installed on the exhaust outlet 10a of shell 10, therefore compared with the past when existing shell to become Datong District the pressure loss become big problem.

And in Japanese kokai publication hei 11-294393 communique in the disclosed centrifugal blower 201, shell 10 is shown in Fig. 7 B, form the shape that the part nearby 17 of its exhaust outlet 10a is eliminated, so that the axle direction center line 12 that makes its exhaust outlet 10a is near the 1st centre line C L 1 of impellers 11 and towards identical direction.By means of this, elbow 16 is not set as mentioned above at the exhaust outlet 10a of shell 10, the axle direction center line 12a of the new exhaust outlet 10b that forms is near the 1st centre line C L 1 of impeller 11, towards identical direction.

By means of this, centrifugal blower 201 does not become big as mentioned above, but the diffuser portion 18 of centrifugal blower 201 shortens, and therefore the flow velocity of this part 18 is fully reduced, exist the pressure loss of this part 18 to increase the problem of the decreased performance of centrifugal blower 201.

Specifically, as shown in Figure 8, compare with the air volume-static pressure characteristic curve L1 of existing centrifugal blower, the air volume-static pressure characteristic curve L2 of the centrifugal blower shown in Fig. 7 B moves to the little direction of static pressure under identical air quantity.Consequently, exist in the problem that can not obtain predetermined airflow on the static pressure of regulation.

To this, can suppress the increase of the pressure loss by the above-mentioned diffuser portion 18 that extends, but, exist centrifugal blower to become big problem with top described identical.

Summary of the invention

Therefore, the present invention makes for solving above-mentioned existing problems, and its purpose is, provides performance not descend, and can reduce the centrifugal blower of kind than existing centrifugal blower.

Centrifugal blower of the present invention, it is the centrifugal blower that impeller is installed in its swirl shape shell, possess: in described shell, the air-out path that the axis ground of the axle direction center line of its exhaust outlet by described impeller is provided with and near the exhaust outlet of this air-out path, the direction that its stream flows out along fluid is bent to form with enlarging gradually laterally, can make to flow through effectively the slow down reduction part of usefulness of its inboard fluid.

Adopt such structure, at the exhaust outlet of the air-out passage of centrifugal blower, the fast fluid of flow velocity can be near near the central part, and the fluid that flows through simultaneously wherein can effectively slow down.Thereby, even make the pipe arrangement that is connected in the air-out path, or crooked round about, also be not easy to take place situations such as peeling off of fluid in the part of this bending to the direction bending identical with the sense of rotation of impeller, the big pressure loss can not take place.Like this, the performance of centrifugal blower is reduced, and the sense of rotation that makes the centrifugal blower impeller become a kind of from the past two kinds.

Again, above-mentioned reduction part also can be formed at the both sides of the identical direction of the axle direction with impeller nearby of exhaust outlet of air-out path respectively.

Usually, near the exhaust outlet of the air-out path of centrifugal blower, the internal surface of the both sides radially of impeller forms along the vortex shape of shell, therefore the big pressure loss can not take place in this part.And the exhaust outlet of the air-out path of centrifugal blower nearby, the internal surface of the axial both sides of impeller, the exhaust outlet of the air-out path of its centrifugal blower, the width dimensions of the direction identical with the axle direction of impeller is greater than width dimensions shell and axle direction equidirectional impeller, and therefore the span of two internal surfaces forms more and enlarges more to exhaust outlet.So the fluid that sometimes flows through in this air-out path situation such as peels off from the internal surface of air-out path, and the big pressure loss takes place.Therefore in the present invention in order to prevent such situation, reduction part is set in this part.Can prevent that like this pressure loss from increasing, therefore can prevent the decreased performance of centrifugal blower.

Again, preferably above-mentioned reduction part form the radius of curvature of the part of its bending be the air-out path exhaust outlet internal diameter 5～20%.

Adopt such structure, the interior fluid of air-out path that flows through centrifugal blower slows down effectively in reduction part.Therefore can prevent that the pressure loss from increasing, so can prevent the decreased performance of centrifugal blower.Also have, under the radius of curvature of the curved section of reduction part 5% situation less than the internal diameter of the exhaust outlet of air-out path, reduction part is too short, and fluid is slowed down effectively.Again, the radius of curvature of the curved section of reduction part surpasses 20% o'clock of internal diameter of the exhaust outlet of air-out path, and it is big that shell becomes.

Description of drawings

Figure 1A is the sectional arrangement drawing of board structure example of the centrifugal blower of the present invention's one example.

Figure 1B is the planimetric map of basic structure example of the centrifugal blower of the present invention's one example.

Fig. 1 C is the fragmentary cross-sectional view of A-A line of the air-out path of the centrifugal blower shown in Figure 1B.

Fig. 2 A is the fragmentary cross-sectional view of the X1-X1 line of Figure 1B.

Fig. 2 B is the fragmentary cross-sectional view of the X2-X2 line of Figure 1B.

Fig. 2 C is the fragmentary cross-sectional view of the A-A line of Figure 1B.

Fig. 2 D is the fragmentary cross-sectional view of the X3-X3 line of Figure 1B.

Fig. 2 E is the fragmentary cross-sectional view of the X4-X4 line of Figure 1B.

Fig. 3 is the air quantity of expression centrifugal blower and the graph of relation of static pressure.

Fig. 4 A is the front view of finished product of the centrifugal blower of the present invention's one example, and the outflow direction of expression fluid is the structure example under vertically upward the situation.

Fig. 4 B is the front view of finished product of the centrifugal blower of the present invention's one example, and the outflow direction of expression fluid is the structure example under to the right the situation.

Fig. 4 C is the front view of finished product of the centrifugal blower of the present invention's one example, and the outflow direction of expression fluid is the structure example under left the situation.

Fig. 5 is the sectional arrangement drawing of the structure of the existing centrifugal blower that possesses the swirl shape shell of expression.

Fig. 6 A is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is vertically upward, and the sense of rotation of impeller is the structure example under the left-handed situation.

Fig. 6 B is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is vertically upward, and the sense of rotation of impeller is the structure example under the situation of dextrorotation.

Fig. 6 C is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is left, and the sense of rotation of impeller is the structure example under the left-handed situation.

Fig. 6 D is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is left, and the sense of rotation of impeller is the structure example under the situation of dextrorotation.

Fig. 6 E is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is to the right, and the sense of rotation of impeller is the structure example under the left-handed situation.

Fig. 6 F is the sectional arrangement drawing of the finished product of existing centrifugal blower, and the outflow direction of expression fluid is to the right, and the sense of rotation of impeller is the structure example under the situation of dextrorotation.

Fig. 7 A is that the shell with existing centrifugal blower shown in Figure 5 is disposed on the base station, and make the axis of the axle direction center line of exhaust outlet by impeller, near with the center line of the axle direction equidirectional of exhaust outlet, the sectional arrangement drawing of the another kind of centrifugal blower of elbow also is installed on exhaust outlet.

Fig. 7 B is that the shell with existing centrifugal blower shown in Figure 5 is disposed on the base station, and make the axis of the axle direction center line of exhaust outlet by impeller, near with the center line of the axle direction equidirectional of exhaust outlet, the sectional arrangement drawing of the another kind of centrifugal blower of the exhaust outlet of a cancellation shell part nearby.

Fig. 8 is the air quantity of the existing centrifugal blower of expression and the graph of relation of static pressure.

Preferred forms

With reference to the accompanying drawings example of the present invention is described.

Shown in Figure 1A, the interior impeller 2 of vortex chamber 1a that centrifugal blower 100 possesses swirl shape shell 1 and is arranged at this shell 1.Possess from the outlet of vortex chamber 1a at shell 1 and to begin the air-out path 1b that stream more and more enlarges.Shown in Figure 1B, the stream section of vortex chamber 1a is roughly rectangle, and this stream section begins slowly to become circle by air-out path 1b from vortex chamber 1a, forms circle at the exhaust outlet 1c of air-out path 1b.

Again, the axle direction center line of this exhaust outlet 1c 3 is by the axis of impeller 2, and is roughly consistent with center line (hereinafter referred to as " the 1st the center line ") CL1 of the axial equidirectional of exhaust outlet 1c.That is to say that above-mentioned axle direction center line 3 is by the axis of impeller 2.

By means of this, can make velocity ratio faster near the central part of fluid near the exhaust outlet 1c of centrifugal blower 100.Consequently, even it is crooked or crooked round about to the direction identical with the sense of rotation of impeller 2 to be connected in the pipe arrangement (not shown) of exhaust outlet 1c, also be not easy to prevent the big pressure loss in situations such as peeling off of this curved section generation fluid.According to the above, can be a kind of from the past two kinds of unifications with the sense of rotation of impeller 2.

In more detail, this air-out path 1b shown in Fig. 1 C, possess make the reduction part 4 that flows through inboard fluid high-effective rate deceleration usefulness, on the axle direction of air-out path 1b with the width direction (direction identical of shell 1 with the axle direction of impeller 2.Symbol W with reference to Figure 1B.) expanded-angle δ 1 enlarge the inclination position 5 that forms and connect the connection part 6 that the radially inner side of this inclination position 5 and reduction part 4 usefulness is bent to form with radius of curvature 2R.Also have, the expanded-angle δ 1 at inclination position 5 is redefined for the angle of the situation of can not peeling off etc. at inclination position 5 inner fluids.

This reduction part 4 is formed at the both sides (part that the oblique line among Figure 1B marks) of width direction of exhaust outlet 1c shell 1 nearby of the air-out path 1b of this centrifugal blower 100 shown in Figure 1B.This reduction part 4 is shown in Fig. 1 C, and axle direction center line 3 left and right symmetricallies with respect to exhaust outlet 1c on the A-A of Figure 1B line section form diametrically laterally agley with the radius of curvature R of stipulating.

Again, the radius of curvature of crooked reduction part 4 shown in Fig. 2 A～E, is respectively R1, R2, R3, R4 on the section of X1-X1, the X2-X2 of Figure 1B, A-A, X3-X3, X4-X4 line.These radius of curvature have the relation of R1＞R2＞R and R4＞R3＞R.That is to say, the position of observing along with section from the center of exhaust outlet 1c to the left and right direction (Vertical direction of the width direction of shell 1) leave away, the radius of curvature of the reduction part 4 corresponding with this position slowly increases.And this reduction part 4 about end be connected to position 7 near the exhaust outlet 1c of air-out path 1b the reduction part 4.

Here, the radius of curvature R of this reduction part 4 preferably is set at 0.05D～0.2D (D is the internal diameter of the exhaust outlet 1c of air-out path 1b).This is because under the radius of curvature R of reduction part 4 5% the situation less than the inside diameter D of the exhaust outlet 1c of air-out path 1b, reduction part 4 is too short, and fluid is effectively slowed down.Again, the radius of curvature R of reduction part 4 surpasses under 20% the situation of inside diameter D of exhaust outlet 1c, and shell 1 becomes big.Preferably make corresponding to the radius of curvature R of this reduction part 4 the axial height H 2 of reduction part 4 is set at 0.05D～0.2D again.

Also have, the kind of the fluid of the buckling curve of reduction part 4 during in fact corresponding to the air quantity of centrifugal blower, air blast etc. are utilized setting such as experiment grade in advance.

Therefore in above-mentioned reduction part 4, the fluid that flows through wherein can slow down effectively, makes the slow down axial distance of needed air-out path 1b of fluid can set forr a short time than in the past.In other words, above-mentioned distance must be done longlyer under near the situation that reduction part 4 is not set the exhaust outlet 1c.

More particularly, center line (hereinafter referred to as " the 2nd the center line ") CL2 that can be roughly parallel to the axis by impeller 2 exhaust outlet 1c is set at for example below 1.5 times of inside diameter D of exhaust outlet 1c to the height H of exhaust outlet 1c.

By means of this, can do the shell 1 of the centrifugal blower 100 of this example than the shell compactness of existing centrifugal blower.

Can make the inside diameter D of exhaust outlet 1c identical again with the inside diameter D 1 of the suction port 8 of shell 1.So also the kind of the pipe arrangement that connects on these members can be united.

Again, make the axle direction center line 3 of exhaust outlet 1c of air-out path 1b of shell 1 consistent with the 1st centre line C L 1 of impeller 2 here, roughly the 2nd centre line C L 2 with impeller 2 is consistent but also can be set at according to the configuration of the pipe arrangement that connects with this exhaust outlet 1c.

Followingly line concentration of the present invention is described in detail according to embodiment.

Embodiment

Shown in Figure 1A～C, the interior impeller 2 of vortex chamber 1a that centrifugal blower 100 possesses gyrate shell 1 and is arranged at this shell 1.The axle direction center line 3 of the exhaust outlet 1c of the air-out path 1b of shell 1 is roughly consistent with the Vertical direction centre line C L 1 of impeller 2.Nearby possesses reduction part 4 at this exhaust outlet 1c.

And in this centrifugal blower 100, inside diameter D with respect to shell 1 exhaust outlet 1a, the 2nd centre line C L 2 from impeller 2, the height H of exhaust outlet 1c is set to H=0.95D, sets the radius of curvature R=0.07D of reduction part 4, the height H 2 of reduction part 4 is set at H2=0.07D, 1=28 ° of the start point δ of setting air-out path 1b.

Comparative example 1

Comparative example 1 as shown in Figure 5, be with embodiment's difference, the axle direction center line 12 of the exhaust outlet 10a of shell 10, centre line C L 1 with the axle direction equidirectional of axis by impeller 11 and exhaust outlet 10a, keep the span of regulation parallel, do not possess above-mentioned reduction part 4 and with respect to the inside diameter D 2 (being approximately 0.85D) of shell 10 exhaust outlet 10a, the height H 3 that plays exhaust outlet 10a from the 2nd centre line C L 2 of impeller 11 is set to H3=0.92D2.Other are identical with embodiment.

Comparative example 2

Comparative example 2 is shown in Fig. 7 B, and it is different with embodiment not possess above-mentioned reduction part 4 this point.Therefore shown in 2 locking wires of Fig. 1 C, the start point δ 1 of above-mentioned air-out path 1b expands into 28 °～30 °.Other are identical with embodiment.

Evaluating characteristics

Use the centrifugal blower of the foregoing description, comparative example 1 and comparative example 2, the performance of centrifugal blower has been carried out mensuration and it is estimated.It the results are shown in Fig. 3.Symbol L1, L2, L3 are the performance curves that corresponds respectively to comparative example 1, comparative example 2 and embodiment among the figure.

As shown in Figure 3, comparative example 1 (performance curve L1) is compared as can be known with embodiment (performance curve L3), compared with comparative example 1, embodiment's performance is very not low.Therefore we can say that embodiment has the performance equal with comparative example.And the centrifugal blower of present embodiment as mentioned above needn't be as the centrifugal blower of comparative example 1, and correspondence is connected in being provided with of pipe arrangement of exhaust outlet 10a and prepares multiple pipe arrangement.Specifically, the finished product kind of the centrifugal blower of present embodiment can be cut to 3 kinds from the past 6 kinds shown in Fig. 4 A～C.

On the other hand, the same kind that can cut down centrifugal blower of comparative example 2 with embodiment, but as shown in Figure 3, the poor performance of centrifugal blower.Particularly in the big air quantity zone of centrifugal blower, compare with embodiment (performance curve L3), the static pressure of comparative example 2 (performance curve L2) reduces greatly, and the big pressure loss has taken place.This can think owing on above-mentioned air-out path 1b reduction part 4 is not set, therefore the fluid that flows through does not wherein fully slow down, and the expanded-angle δ 1 of air-out path 1b expands to 30 ° from 28 °, so take place easily at the internal surface of air-out path 1b that situations such as peeling off of fluid cause.Hence one can see that, on the air-out path 1b of centrifugal blower 100 reduction part 4 is set and can reduces the pressure loss effectively.

Again, above-mentioned example is an example, and the present invention can have various changes in the scope of not damaging main idea of the present invention, the invention is not restricted to above-mentioned example.

Industrial applicability

Adopt centrifugal blower of the present invention, performance ground does not reduce centrifugal blower than in the past Kind. Consequently, centrifugal blower of the present invention is as production efficiency height, easy in library management Centrifugal blower is useful.

Claims

1. a centrifugal blower is installed impeller in its swirl shape shell, it is characterized in that possessing

In described shell, the air-out path that the axis ground of the axle direction center line of its exhaust outlet by described impeller is provided with and

Near the exhaust outlet of this air-out path, the direction that its stream flows out along fluid is bent to form with enlarging gradually laterally, can make to flow through effectively the slow down reduction part of usefulness of its inboard fluid.

2. centrifugal blower according to claim 1 is characterized in that, described reduction part is formed at the both sides of the identical direction of the axle direction with impeller nearby of exhaust outlet of described air-out path respectively.

3. centrifugal blower according to claim 1 is characterized in that, the radius of curvature that described reduction part forms the part of its bending be described air-out path exhaust outlet internal diameter 5～20%.

4. centrifugal blower according to claim 2 is characterized in that, the radius of curvature that described reduction part forms the part of its bending be described air-out path exhaust outlet internal diameter 5～20%.