WO2019047466A1

WO2019047466A1 - Novel efficient hvac indoor unit

Info

Publication number: WO2019047466A1
Application number: PCT/CN2018/074392
Authority: WO
Inventors: 林炎虎
Original assignee: 中山大洋电机股份有限公司
Priority date: 2017-09-07
Filing date: 2018-01-28
Publication date: 2019-03-14
Also published as: CN107420996A

Abstract

Disclosed is a novel efficient HVAC indoor unit, comprising a housing (1), a heat exchanger (2) and a centrifugal fan (3), wherein the heat exchanger (2) and the centrifugal fan (3) are installed inside a first cavity (10); a first air outlet (131) is provided in a left side plate (13) of the housing (1), and a first air inlet (14) is provided in a right side plate thereof. The heat exchanger (2) is V-shaped. The centrifugal fan (3) comprises a volute (31), a wind wheel (32) and an electric motor (33), wherein the volute (31) comprises a second air inlet (311) and a second air outlet (312), the volute (31) is located between an upper side plate (11) and a lower side plate (12), and the first air outlet (131) is in communication with the second air outlet (312). A volute tongue (313) of the volute (31) is connected to a static pressure return plate (34), and the static pressure return plate (34) is arranged obliquely, one end of the static pressure return plate (34) being connected to the volute tongue (313) of the volute at the air outlet, and the other end of the static pressure return plate (34) extending in a direction towards the first air outlet (131), so that the centrifugal fan (3) directly blows air towards the first air outlet (131), thereby effectively preventing a vortex phenomenon, improving efficiency and being able to reduce the output power from the electric motor where the air outlet volume is the same.

Description

A new type of efficient HVAC internal machine

Technical field:

The invention relates to a new and efficient HVAC internal machine.

Background technique:

The existing HVAC internal machine includes an outer casing, a heat exchanger and a centrifugal fan, and the outer casing is surrounded by an upper side plate, a lower side plate, a front side plate and a rear side plate, and the heat exchanger and the centrifugal fan are installed. In the d cavity, the left side of the cavity is provided with a left side plate, the left side plate is provided with a first air outlet, and the right side of the cavity is provided with a first air inlet, the first air outlet, the first inlet The tuyere and the cavity are connected, the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the centrifugal fan comprises a volute and a wind a wheel and a motor, the volute includes a second air inlet and a second air outlet, the second air inlet includes a second upper air inlet and a second lower air inlet, the volute being located between the upper side plate and the lower side plate There is a distance between the second upper air inlet and the upper side plate, and a distance between the second lower air inlet and the lower side plate is at one end, and the first air outlet is connected to the second air outlet.

The above structure has the following technical problems: 1) Since there is a distance between the second air outlet and the first air outlet, when the second air outlet discharges the wind to the first air outlet, the wind will have a vortex phenomenon, resulting in loss of air volume. Too much, reduce the operating efficiency of the fan, and increase the cost; 2) the second upper air inlet and the second lower air inlet of the volute are narrower than the distance between the upper side plate and the lower side plate, respectively, and the air volume of the volute is small, resulting in The fan exhaust air volume is reduced, and the fan operating efficiency is reduced. 3) The parameter ratio design of the volute and the cavity is unreasonable, affecting the efficiency of the fan and reducing the operating efficiency of the motor.

Summary of the invention:

The object of the present invention is to provide a new and efficient HVAC internal machine, which can reduce the output power of the motor, improve the operating efficiency of the fan, and save energy.

The object of the present invention is achieved by the following technical solutions.

A novel high-efficiency HVAC internal machine comprising a casing, a heat exchanger and a centrifugal fan, the casing being surrounded by an upper side plate, a lower side plate, a front side plate and a rear side plate, the heat exchanger and the centrifugal The fan is installed in the d cavity, the left side of the cavity is provided with a left side plate, the left side plate is provided with a first air outlet, and the right side of the cavity is provided with a first air inlet, the first air outlet, the first An air inlet is connected to the cavity, the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the centrifugal fan includes a volute a wind wheel and a motor, the volute includes a second air inlet and a second air outlet, the second air outlet of the volute is provided with a volute tongue, and the second air inlet includes a second upper air inlet and a second lower air inlet a tuyere, the volute is located between the upper side plate and the lower side plate, a distance between the second upper air inlet and the upper side plate, and a distance between the second lower air inlet and the lower side plate. The first air outlet is connected to the second air outlet, and the volute of the volute is connected to a static pressure recovery plate, and the static pressure recovery plate is Tilting, one end of the static pressure recovery plate is connected with the volute tongue of the volute air outlet, and the other end of the static pressure recovery plate extends toward the first air outlet.

An exhaust passage is disposed between the first air outlet and the second air outlet, and the static pressure returning plate is disposed on the air exhaust passage and extends toward the first air outlet.

The width H1 of the first air outlet and the width H2 of the second air outlet are equal.

The volute top plate corresponding to the volute tongue on the second air outlet is in close contact with the rear side plate.

The second air outlet is located at a middle portion of the upper side plate and the lower side plate.

The first cavity is provided with a water drop tray, the water tray is located below the heat exchanger and the water tray is installed obliquely to the lower side plate.

The first cavity is divided into an A zone cavity and a B zone cavity, the centrifugal fan is located in the A zone cavity, the heat exchanger is located in the B zone cavity, and the A zone cavity zone is in the second air outlet. Between the leftmost end of the heat exchanger, the cavity region of the B region is between the leftmost end of the heat exchanger and the first air inlet.

Based on the static pressure recovery plate described above, the volute parameter setting satisfies the following condition: 0.5 ≤ B1/B ≤ 0.7, B1 is the width of the volute, and B is the width of the outer casing.

The ratio of the effective width of the wind wheel to the outer diameter of the wind wheel: 0.7 ≤ 2b2 / D2 ≤ 1, b2 is the effective width of the wind wheel, and D2 is the outer diameter of the wind wheel.

The ratio of the length of the volute to the length of the cavity of the A zone is 0.7 ≤ L1/L ≤ 0.9, L1 is the length of the volute, and L is the length of the cavity of the A zone.

The volute tongue is a circular arc shape, and the radius r of the volute tongue is 13 mm ≤ r ≤ 15 mm.

The inclination angle a of the static pressure recovery plate is 20° ≤ a ≤ 30°.

The width H3 of the volute is 234 mm ≤ H3 ≤ 242 mm.

The diameter R of the wind wheel is 216 mm ≤ R ≤ 224 mm, and the width of the wind wheel is H4 at 214 mm ≤ H3 ≤ 222 mm.

Compared with the prior art, the invention has the following effects:

1) The present invention includes a casing, a heat exchanger, and a centrifugal fan, the left side plate of the casing is provided with a first air outlet, and the right side panel is provided with a first air inlet, the first air outlet, the first The air inlet is in communication with the first cavity, the heat exchanger is V-shaped, the heat exchanger is located on the left side of the first air inlet, the centrifugal fan is located on the right side of the first air outlet, and the volute is located on the upper side a space between the second upper air inlet and the upper side plate, a distance between the second lower air inlet and the lower side plate, the first air outlet and the second The air outlet is connected, the volute of the volute is connected to a static pressure recovery plate, and the static pressure recovery plate is inclined, and one end of the static pressure recovery plate is connected with the volute tongue of the volute air outlet, and the static pressure is restored. The other end of the plate extends toward the first air outlet, so that the centrifugal fan directly blows to the first air outlet, effectively avoiding the phenomenon of vortex flow and improving efficiency; overall, if the same air volume is output, the output power ratio of the motor is required now. The original is lower, more energy saving, and lower costs;

2) The width H1 of the first air outlet is equal to the width H2 of the second air outlet, which can effectively reduce the loss of air volume and improve the air blowing efficiency of the fan;

3) The first cavity is provided with a water tray, the water tray is located below the heat exchanger and the water tray is inclined to the lower side plate, and the dripping water of the heat exchanger is flowed out through the water tray to prevent water from accumulating inside the shell. .

4) On the basis of the static pressure recovery plate, the inclination angle a of the static pressure recovery plate is 20°≤a≤30°, and the volute parameter setting satisfies the following conditions: 0.5≤B1/B≤0.7, B1 is the width of the volute B is the width of the outer casing, the width H3 of the volute is 234mm ≤ H3 ≤ 242mm, the volute tongue is circular arc shape, and the radius r of the volute tongue is 13mm ≤ r ≤ 15mm. In the output of the same air volume, the output of the motor can be reduced. Power, saving energy;

5) The ratio of the effective width of the wind wheel to the outer diameter of the wind wheel: 0.7 ≤ 2b2 / D2 ≤ 1, b2 is the effective width of the wind wheel, D2 is the outer diameter of the wind wheel, and the diameter R of the wind wheel is 216 mm ≤ R ≤ 224 mm The width of the wind wheel is H4 at 214mm ≤ H3 ≤ 222mm. In the same air volume output, the output power of the motor can be reduced and energy can be saved.

6) The ratio of the length of the volute to the length of the cavity in the A zone: 0.7 ≤ L1/L ≤ 0.9, L1 is the length of the volute, L is the length of the cavity in the A zone, and the output of the same air volume can reduce the motor Output power, saving energy.

BRIEF DESCRIPTION OF THE DRAWINGS:

Figure 1 is a perspective view of the present invention;

Figure 2 is another perspective view of the present invention;

3 is a schematic structural view of a hidden front side panel of the present invention;

Figure 4 is a front elevational view of the hidden front side panel of the present invention;

Figure 5 is a cross-sectional view taken along line A-A of Figure 4;

Figure 6 is a cross-sectional view showing the structure of the present invention;

Figure 7 is a perspective view of the centrifugal fan of the present invention;

Figure 8 is a front elevational view of the centrifugal fan of the present invention;

Figure 9 is a schematic diagram of the parameter design of the centrifugal fan of the present invention;

Figure 10 is another schematic diagram of the parameter design of the centrifugal fan of the present invention;

Figure 11 is an experimental comparison diagram of the present invention.

Detailed ways:

The present invention will now be described in further detail by way of specific embodiments and the accompanying drawings.

Embodiment 1 As shown in FIG. 1 to FIG. 10, this embodiment is a new type of high-efficiency HVAC internal machine, comprising a casing 1, a heat exchanger 2 and a centrifugal fan 3, wherein the casing 1 is composed of an upper side plate 11, The lower side panel 12, the front side panel 15 and the rear side panel 16 enclose a cavity 10, the heat exchanger 2 and the centrifugal fan 3 are mounted in the cavity 10, and the left side panel 13 is provided on the left side of the cavity 10. a first air outlet 131 is disposed on the left side plate 13 , and a first air inlet 14 is disposed on a right side of the cavity 10 , and the first air outlet 131 , the first air inlet 14 , and the cavity 10 are connected to each other. The heat exchanger 2 is V-shaped, the heat exchanger 2 is located on the left side of the first air inlet 14, the centrifugal fan 3 is located on the right side of the first air outlet 131, and the centrifugal fan 3 includes a volute 31, a wind wheel 32, and The volute 31 includes a second air inlet 311 and a second air outlet 312. The second air outlet 312 of the volute 31 is provided with a volute tongue 313, and the second air inlet 311 includes a second upper air inlet 3111. And the second lower air inlet 3112, the volute 31 is located between the upper side plate 11 and the lower side plate 12, and the second upper air inlet 3111 and the upper side plate 11 are spaced apart from each other, and the second lower air inlet 3112 and under There is a space between the plates 12, and the first air outlet 131 is in communication with the second air outlet 312. The volute 313 of the volute 31 is connected to a static pressure recovery plate 34. The return plate 34 is inclined, and one end of the static pressure returning plate 34 is in contact with the volute tongue 313 of the second air outlet 312 of the volute 31, and the other end of the static pressure returning plate 34 extends in the direction of the first air outlet 131.

An exhaust passage 4 is disposed between the first air outlet 131 and the second air outlet 312. The static pressure recovery plate 34 is disposed on the exhaust passage 4 and extends toward the first air outlet 131.

The width H1 of the first air outlet 131 and the width H2 of the second air outlet 312 are equal.

The top plate 314 of the volute 31 corresponding to the volute tongue 313 on the second air outlet 312 abuts against the rear side plate 16.

The second air outlet 312 is located at a middle portion of the upper side plate 11 and the lower side plate 12.

A water tray 5 is disposed in the first cavity 10, and the water tray 5 is located below the heat exchanger 2 and the water tray 5 is obliquely mounted in the direction of the lower side plate 12.

The first cavity 10 is divided into a cavity A of the A zone and a cavity 102 of the B zone, the centrifugal fan 3 is located in the cavity 101 of the A zone, and the heat exchanger 2 is located in the cavity 102 of the zone B, and the cavity 101 of the zone A is Between the second air outlet 312 and the leftmost end of the heat exchanger 2, the area B cavity 102 is between the leftmost end of the heat exchanger 2 and the first air inlet 14.

On the basis of the static pressure recovery plate 34, the parameter setting of the volute 31 satisfies the following condition: 0.5 ≤ B1/B ≤ 0.7, B1 is the width of the volute 31, and B is the width of the outer casing 1.

The ratio of the effective width of the wind wheel 32 to the outer diameter of the wind wheel 32 is 0.7 ≤ 2b2 / D2 ≤ 1, b2 is the effective width of the wind wheel 32, and D2 is the outer diameter of the wind wheel 32.

The ratio of the length of the volute 31 to the length of the cavity 101 of the A region is 0.7 ≤ L1/L ≤ 0.9, L1 is the length of the volute 31, and L is the length of the cavity 101 of the A region.

The volute tongue 313 has a circular arc shape, and the radius r of the volute tongue 313 is 13 mm ≤ r ≤ 15 mm.

The inclination angle a of the static pressure recovery plate 34 is 20° ≤ a ≤ 30°.

The width H3 of the volute 31 is 234 mm ≤ H3 ≤ 242 mm.

The diameter R of the wind wheel 32 is 216 mm ≤ R ≤ 224 mm, and the width of the wind wheel 32 is H4 at 214 mm ≤ H3 ≤ 222 mm.

As shown in Figure 11, the test was carried out according to the above data: experimental verification was carried out under the objective conditions set in Table 1:

The experimental parameters in Table 2 are selected as follows: 2b2/D2=0.936, B1/B=0.591, L1/L=0.786; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A1;

The experimental parameters in Table 3 are selected as follows: 2b2/D2=0.936, B1/B=0.591, L1/L=0.786; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A2;

The experimental parameters in Table 4 are selected as follows: 2b2/D2=0.758, B1/B=0.567, L1/L=0.873; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A3;

The experimental parameters in Table 5 are selected as follows: 2b2/D2=0.87, B1/B=0.591, L1/L=0.837; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A4;

The experimental parameters in Table 6 are selected as follows: 2b2/D2=0.833, B1/B=0.591, L1/L=0.837; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A5;

The experimental parameters in Table 7 are selected as follows: 2b2/D2=0.84, B1/B=0.665, L1/L=0.925; after experiment, the corresponding efficiency values under different air volume conditions are obtained, and are plotted as curves in Fig. 11 A6;

The curve A1, the curve A2, the curve A3, the curve A4, the curve A5, and the curve A6 are respectively shown by the above-mentioned six sets of experimental data, and the curve A5 satisfies the volute. 31 parameter setting conditions: 0.5 ≤ B1/B ≤ 0.7, 0.7 ≤ 2b2 / D2 ≤ 1, 0.7 ≤ L1/L ≤ 0.9, the line C in Fig. 11 refers to the same operation when the air volume at the same operating point is 1780 CFM. Among the point air volume: curve A2, curve A3, and curve A4 are in a critical condition, the motor output power of curve A5 is the lowest, and the motor output power of curve A1 and curve A6 is the highest.

Table 1

Table 2

table 3

Table 4

table 5

Table 6

Table 7

The above embodiments are preferred embodiments of the present invention, but the embodiments of the present invention are not limited thereto, and any other changes, modifications, substitutions, combinations, and simplifications made without departing from the spirit and scope of the present invention are equivalent. The manner of replacement is included in the scope of protection of the present invention.

Claims

A new type of high efficiency HVAC internal machine comprising a casing (1), a heat exchanger (2) and a centrifugal fan (3), the casing (1) being composed of an upper side plate (11), a lower side plate (12), a front The side plate (15) and the rear side plate (16) enclose a cavity (10), and the heat exchanger (2) and the centrifugal fan (3) are installed in the cavity (10), and the left side of the cavity (10) The side is provided with a left side plate (13), the left side plate (13) is provided with a first air outlet (131), and the right side of the cavity (10) is provided with a first air inlet (14), the first out The tuyere (131), the first air inlet (14) and the cavity (10) are in communication, the heat exchanger (2) is V-shaped, and the heat exchanger (2) is located at the first air inlet (14). On the left side, the centrifugal fan (3) is located on the right side of the first air outlet (131), and the centrifugal fan (3) includes a volute (31), a wind wheel (32) and a motor (33), the volute ( 31) comprising a second air inlet (311) and a second air outlet (312), the second air outlet (312) of the volute (31) is provided with a volley tongue (313), and the second air inlet (311) The second upper air inlet (3111) and the second lower air inlet (3112) are located, the volute (31) is located between the upper side plate (11) and the lower side plate (12), and the second upper air inlet (3111) There is a gap between the upper side plate (11) and the space. There is a space between the second lower air inlet (3112) and the lower side plate (12), and the first air outlet (131) is in communication with the second air outlet (312), characterized in that: the volute The volute tongue (313) of (31) is connected to a static pressure recovery plate (34), the static pressure recovery plate (34) is inclined, and one end of the static pressure recovery plate (34) and the volute (31) are second. The volute tongue (313) of the tuyere (312) is in contact with each other, and the other end of the static pressure recovery plate (34) extends in the direction of the first air outlet (131).
A new high-efficiency HVAC internal machine according to claim 1, wherein an exhaust passage (4) is disposed between the first air outlet (131) and the second air outlet (312), The static pressure recovery plate (34) is disposed on the exhaust passage (4) and extends toward the first air outlet (131).
A novel high efficiency HVAC internal machine according to claim 2, wherein the width H1 of the first air outlet (131) and the width H2 of the second air outlet (312) are equal.
A novel high-efficiency HVAC internal machine according to claim 1 or 2 or 3, characterized in that the volute (31) corresponding to the volute (313) on the second air outlet (312) corresponds to the top plate (314) of the volute (31). Adheres to the rear side panel (16).
A novel high efficiency HVAC internal machine according to claim 4, characterized in that said second air outlet (312) is located in the middle of the upper side plate (11) and the lower side plate (12).
A new type of high efficiency HVAC internal machine according to claim 4, characterized in that: the first cavity (10) is provided with a water tray (5), and the water tray (5) is located in the heat exchanger ( 2) below and the water tray (5) is installed obliquely in the direction of the lower side plate (12).
A novel high-efficiency HVAC internal machine according to claim 4, wherein the first cavity (10) is divided into an A-zone cavity (101) and a B-zone cavity (102), the centrifugal fan ( 3) located in the cavity (101) of zone A, the heat exchanger (2) is located in the cavity (102) of zone B, and the cavity (101) of zone A is in the second air outlet (312) and the heat exchanger (2) Between the leftmost ends, the zone B cavity (102) is between the leftmost end of the heat exchanger (2) and the first air inlet (14), the length of the volute (31) and the cavity of the A zone The length ratio of (101): 0.7 ≤ L1/L ≤ 0.9, L1 is the length of the volute (31), and L is the length of the cavity (101) of the A region.
A novel high-efficiency HVAC internal machine according to claim 7, characterized in that: on the basis of the static pressure returning plate (34), the parameter setting of the volute (31) satisfies the following condition: 0.5 ≤ B1/B ≤ 0.7 B1 is the width of the volute (31) and B is the width of the outer casing (1).
A novel high-efficiency HVAC internal machine according to claim 8, characterized in that the ratio of the effective width of the wind wheel (32) to the outer diameter of the wind wheel (32) is 0.7 ≤ 2b2 / D2 ≤ 1, b2 It is the effective width of the wind wheel (32), and D2 is the outer diameter of the wind wheel (32).
A novel high-efficiency HVAC internal machine according to claim 9, wherein the volute tongue (313) has a circular arc shape, and the radius r of the volute tongue (313) is 13 mm ≤ r ≤ 15 mm.
A novel high-efficiency HVAC internal machine according to claim 8, characterized in that the inclination angle a of the static pressure returning plate (34) is 20 ° ≤ a ≤ 30 °.
A novel high efficiency HVAC internal machine according to claim 8, characterized in that the width (H3) of the volute (31) is 234 mm ≤ H3 ≤ 242 mm.
A novel high-efficiency HVAC internal machine according to claim 9, wherein the diameter R of the wind wheel (32) is 216 mm ≤ R ≤ 224 mm, and the width of the wind wheel (32) is H4 at 214 mm ≤ H3. ≤ 222mm.