WO2006112278A1

WO2006112278A1 - Top plate structure of air conditioner for installation at high level

Info

Publication number: WO2006112278A1
Application number: PCT/JP2006/307462
Authority: WO
Inventors: Jihong Liu
Original assignee: Daikin Industries, Ltd.
Priority date: 2005-04-13
Filing date: 2006-04-07
Publication date: 2006-10-26
Also published as: JP2006292312A; CN101147031A; EP1867930A1; US20080159848A1

Abstract

An air conditioner for installation at high level has a body casing (3) for receiving a fan (5), a fan motor (9), and a heat exchanger (4), and has a top plate (32) located at the top side of the body casing (3) and suspendingly supporting the fan (5), the fan motor (9), and the heat exchanger (4). On the top plate (32) are reinforcement ribs radially extending from its central portion, where the fan motor (9) is supported, to its outer periphery, where the heat exchanger (4) is supported. The reinforcement ribs are composed of reinforcement ribs (32a’) projecting from the front side of the top plate (32) and reinforcement ribs (32a) projecting from the back side, and by which rigidity of the top plate (32) is enhanced.

Description

Specification

Top plate structure of an air conditioner installed at high altitude

Technical field

[0001] The present invention relates to a top plate structure of an air conditioner installed at a high place.

Background art

[0002] An indoor unit in a ceiling-mounted or ceiling-suspended high-air installation air conditioner includes, for example, a metal top plate on the top surface of a cassette-type main body casing. Suspend and support heavy objects such as heat exchangers, fans and fan motors on the top plate, and then the main body casing is suspended by suspension bolts and embedded in the ceiling, or on the bottom of the ceiling By suspending it, the indoor unit of the air conditioner is installed.

[0003] An example of a ceiling-embedded air conditioner in such an altitude installation type air conditioner is shown in FIGS. In this air conditioner, as shown in FIGS. 22 to 24, the main body 1 of the air conditioner is disposed above the opening 7 formed in the ceiling C, and covers the opening 7 with respect to the main body 1. A decorative panel 2 is attached. A substantially annular heat exchanger 4 is disposed in a cassette-type main casing 3 of the main body 1. Inside the main casing 3, a fan (impeller) 5 and a fan motor 9 are arranged at the center of the heat exchanger 4 with the air suction side facing downward and the air blowing side to the side of the heat exchanger 4. It is arranged. In the main casing 3, a synthetic resin bell mouth 6 is disposed on the suction side of the fan 5.

[0004] The fan 5 is constituted by a centrifugal fan having a plurality of blades 5b between a hub 5a and a shroud 5c. The drain pan 8 is disposed below the heat exchanger 4, and the air blowing passage 10 is formed on the outer periphery of the heat exchanger 4.

[0005] The main body casing 3 has a substantially hexagonal shape, and includes a side wall 31 that also has a heat insulating material force and a top plate 32 that covers the upper portion of the side wall 31. The heat exchanger 4 has a pair of opposed open ends, and tube plates 11 are respectively provided at both open ends, and both the tube plates 11 are connected by a predetermined partition plate 12.

[0006] Mounted on the bottom surface of the top plate 32, the tube plate 11, the partition plate 12 and the bell mouth 6 of the main casing 3 The switch box 13 to be attached is composed of sheet metal products. The top plate 32 and the switch box 13 are screwed to the upper and lower ends of the partition plate 12 as shown in FIG.

On the other hand, the bell mouth 6 is formed with a recess 14 for accommodating the switch box 13, and a switch box coupling portion 15 formed at the lower end of the partition plate 12 is formed on the top surface 14 a of the recess 14. An opening 16 is formed to face the surface. In addition, a pair of mounting pieces 17 coupled to the top plate 32 are provided on both sides of the upper end portion of the partition plate 12 so as to project from the top plate 32 with screws 18 below the top plate 32. It is fixed from.

Further, a pair of mounting pieces 19 coupled to the lower ends of both tube plates 11 are provided on both sides of the lower end portion of the partition plate 12, and a switch box 13 is provided in the middle portion of the partition plate 12. A mounting piece 15 to be joined to is fixed by welding. Each mounting piece 19 is fixed to the corresponding tube plate 11 from below by screws 20. Each mounting piece 15 includes an L-shaped base portion 15a coupled to the partition plate 12, and a mounting portion 15b integrally extending downward from the tip of the base portion 15a. The mounting portion 15b is opened. In a state where it faces the recess 14 from 16, it is fixed to the top surface 13 a of the switch box 13 from below by screws 21.

[0009] The air conditioner includes a drain pump 22, a float switch 23, a drain pump accommodating portion 24 in which the drain pump 22 is disposed, a partition plate 25 that partitions the drain pump accommodating portion 24, and a lid cover 26 of the switch box 13. ing.

[0010] The top plate 32 is formed in a substantially hexagonal shape corresponding to the shape of the main body casing 3 of the air conditioner 1, and the outer periphery of the top plate 32 is fitted to the outer peripheral side of the upper end portion of the main body casing 3. A shaped edge 32c is provided.

[0011] The top plate 32 has a predetermined width extending radially and recessed downward from a central portion 33 where the fan 5 and the fan motor 9 are supported to an outer peripheral portion where the substantially annular heat exchanger 4 is supported. A plurality of main reinforcing ribs 32a having a predetermined depth are provided. A stepped portion 32b having a downward dent depth is formed on the heat exchanger support portion on the outer periphery of the main reinforcing rib 32a. The basic reinforcing rib 32a sets the basic rigidity, strength, deflection characteristics, and vibration characteristics of the top plate 32 to necessary levels.

[0012] On the other hand, in the outer peripheral portion of the top plate 32, the interval between the main reinforcing ribs 32a is widened, and the rigidity is increased accordingly. There is a risk that strength will be insufficient. Therefore, between the plurality of main reinforcing ribs 32a, as shown in FIG. 24, a plurality of secondary reinforcing ribs 34 having a desired shape and size corresponding to the assumed load are provided adjacent to each other. It has been.

[0013] In addition, at the time of design, the static deflection of the top plate 32 is kept below a certain value, and the primary natural frequency of the top plate 32 is kept above a certain value in order to avoid resonance due to the rotation of the fan motor 9. I was trying to do it.

[0014] In addition, the top plate 32 is provided with reinforcing ribs 33a having a substantially triangular shape on the inner side in the support portions of the fan 5 and the fan motor 9 in the central portion 33. As a result, the rigidity, strength, deflection characteristics, and vibration characteristics of the support portions of the fan 5 and the fan motor 9 were improved (see Patent Document 1).

[0015] In the support portions of the fan 5 and the fan motor 9, a circular concave groove is provided at each corner position of the reinforcing rib 33a, and three fan motor 9 mounting portions a, b, c is formed. The fan motor 9 is suspended and fixed via a mount member 11 and a mounting bracket 9b having a vibration absorbing property with respect to the fan motor mounting portions a, b, and c. As a result, the fan 5 is also rotatably supported via the motor shaft 9a.

Patent Document 1: Japanese Patent Laid-Open No. 11 201496 Recently, from various viewpoints, it has been studied to reduce the cost of an air conditioner, and the top plate 32 is no exception. In the case of the top plate 32, as a cost reduction method, for example, the overall plate thickness is made thinner (for example, about 0.7 to 0.6 mm) than the current one (for example, 0.8 mm), and the material cost is reduced. In addition, it is conceivable to improve the workability for forming ribs and the like. However, the problem in that case is a decrease in rigidity and strength, and furthermore, measures against vibration when driving the fan.

[0016] If the plate thickness is made thinner than the current thickness, the material cost is reduced and deformation is facilitated, so that the pressurizing force during press molding can be reduced, and the workability is improved. However, in view of actual thinning, in the case of the conventional structure described above, that is, in the case of a top plate formed with radial reinforcing ribs, the amount of static deflection increases and the primary natural frequency associated with the rotation of the fan motor 9. As a result, the design standards at the conventional product level could not be met.

Disclosure of the invention

[0017] In view of the circumstances as described above, the present invention has the necessary rigidity and strength even if it is thinned. The object of the present invention is to provide a top plate structure of an air conditioner capable of obtaining a degree and vibration characteristics.

[0018] According to one aspect of the present invention, a main body casing that houses a fan, a fan motor, and a heat exchanger, and a fan, a fan motor, and a heat exchanger that are suspended from and supported on the top surface of the main body casing. An air conditioner provided with a plurality of reinforcing ribs extending radially from a central portion where the fan motor is supported to an outer peripheral portion where heat exchange is supported is provided on the top plate. The plurality of reinforcing ribs are composed of reinforcing ribs protruding from the top surface of the top plate and reinforcing ribs protruding from the back surface.

[0019] According to such a top plate structure, even if the thickness of the top plate is made thinner than before, the number of reinforcing ribs and the cross-sectional shape (drawer shape), depth, width, etc. are optimally adjusted and set. As a result, the rigidity, strength, deflection characteristics, vibration characteristics, etc. can be improved to the required levels. In particular, the reinforcement ribs have a structure that protrudes in both the front and back directions, so that the height of the vertical wall between the front and back surfaces is approximately doubled. Is greatly improved. As a result, it is possible to reduce the product cost by reducing the plate thickness and improving the workability.

[0020] It is desirable that the reinforcing ribs that protrude from the surface force of the top plate and the reinforcing ribs that protrude from the back surface are alternately arranged along the circumferential direction of the top plate. In this case, the support rigidity can be increased in a well-balanced manner over the entire top plate, and the maximum deflection amount can be reduced evenly.

[0021] The plurality of reinforcing ribs are composed of a long main reinforcing rib and a short auxiliary reinforcing rib provided between the main reinforcing ribs, and the main reinforcing rib is one of the front and back surfaces of the top plate. It is desirable that the secondary reinforcing rib protrude and the other force on the top and back surfaces of the top plate also protrude. In this case, the support rigidity can be improved in a well-balanced manner over the entire top plate, and the maximum deflection can be evenly reduced.

[0022] The depth of each reinforcing rib varies along its longitudinal direction, and it is desirable that the depth of both ends of each reinforcing rib be shallower than the depth between both ends. In this case, the maximum deflection can be reduced more effectively, the resonance speed can be further improved, and the cost of the top plate can be further reduced by reducing the material. [0023] The thickness of the top plate 32 is 0.6 mn! It is desirable to set in the range of ~ 0.7mm. The thinner the top 32, the lower the material cost and the easier the press molding. However, on the contrary, the strength and rigidity decrease, and the deflection characteristics and vibration characteristics deteriorate. To supplement this, the above-mentioned reinforcing rib is effective, but a certain plate thickness is still necessary.

[0024] According to one aspect of the present invention, the thickness of the top plate 32 can be reduced to a range of 0.6 mm to 0.7 mm, which is thinner than the conventional 0.8 mm. In addition, sufficient support rigidity can be secured. Therefore, the cost reduction of the effective top plate by material reduction can be expected.

In other words, the thickness level in this range (0.6 mm to 0.7 mm) reduces the material cost and improves the workability in consideration of the relationship between the thickness of the conventional product and the reinforcing effect of the reinforcing ribs. Therefore, it is within the range of an appropriate plate thickness that can ensure the necessary quality performance.

[0026] Depth force of each reinforcing rib is preferably 8. Omm to 10. Omm. Conventionally, it has been required as a design standard to keep the maximum deflection of the top plate to 1.31 mm or less and to keep the resonance speed at 742.Orpm or more. Taking into account such design criteria and maintaining the robustness of the top plate's static and dynamic characteristics with respect to the depth of the reinforcing rib, the depth of the reinforcing rib should be 8. Omm ~ 10. Omm is appropriate.

Brief Description of Drawings

FIG. 1 is a bottom view showing a structure of a top plate portion in a state where a heat exchanger is installed in an altitude installation type air conditioner according to a first embodiment.

FIG. 2 is a bottom view showing the structure of the top plate in a state where heat exchange is installed.

FIG. 3 is a front view of the top panel.

4 is a longitudinal sectional view taken along line 4-4 in FIG.

FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 2 and shows the structure of the reinforcing rib portion that is the main part of the top plate portion.

FIG. 6 is a cross-sectional view of the top plate portion in the longitudinal direction of the ribs.

FIG. 7 is a bottom view showing a basic model top plate structure having six ribs manufactured to confirm the characteristics of the top plate part.

[Fig.8] In the basic model (6 pieces) in Fig.6 It is the perspective view which looked at the diagonally lower side which shows the top plate structure of 1 experimental sample.

FIG. 9 is a bottom view showing a top model structure of a basic model having eight ribs manufactured to confirm the characteristics of the top panel part.

FIG. 10 is a perspective view of the top plate structure of a second experimental sample in which all the reinforcing ribs protrude only in the back surface in the basic model (eight) of FIG.

[11] FIG. 11 is a perspective view showing the top plate structure of the third experimental sample in which the reinforcing ribs are also protruded on both sides of the basic model (eight) in FIG.

FIG. 12 is a bottom view showing the top plate structure of a basic model having ten ribs manufactured to confirm the characteristics of the top plate portion.

FIG. 13 is a perspective view showing the top plate structure of the fourth experimental sample in which all the reinforcing ribs protrude only with the back surface force in the basic model (10 pieces) of FIG. 12, as seen from obliquely below.

[14] FIG. 14 is a perspective view showing the top plate structure of the fifth experimental sample in which the reinforcing ribs are also protruded on both sides in the basic model (10 pieces) of FIG.

FIG. 15 is a bottom view showing the top plate structure of a basic model having 12 ribs manufactured to confirm the characteristics of the top plate portion.

FIG. 16 is a perspective view showing the top plate structure of a sixth experimental sample in which all the reinforcing ribs protrude only with the back surface force in the basic model (12 pieces) of FIG.

[17] This is a graph showing the relationship between the number of ribs on the top plate and the maximum deflection amount of the first, second, fourth, and sixth experimental samples in which the radial ribs are arranged on only one side.

[18] This is a graph showing the relationship between the number of ribs on the top plate of the first, second, fourth, and sixth experimental samples in which the radial ribs are arranged on only one side and the resonance rotational speed.

[19] This is a graph showing the relationship between the rib depth of the top plate and the maximum deflection amount of the third and fifth experimental samples with radial ribs arranged on both sides.

[20] This is a graph showing the relationship between the rib depth of the top plate of the third and fifth experimental samples in which radial ribs are arranged on both surfaces and the resonance rotational speed.

[21] FIG. 21 is a bottom view showing the structure of the top plate portion of the air conditioner of high altitude installation according to the second embodiment.

[Fig.22] A longitudinal sectional view taken along line 22-22 in Fig. 24, showing the overall configuration of a conventional air conditioner It is.

FIG. 23 is a bottom view of the conventional air conditioner as seen from below with the decorative panel and main body casing removed.

FIG. 24 is an exploded perspective view showing a mounting relationship between a top plate portion of a conventional air conditioner and a bell mouth.

BEST MODE FOR CARRYING OUT THE INVENTION

[0028] Figs. 1 to 6 show the structure of the top plate of an altitude installation type air conditioner according to the first embodiment of the present invention.

[0029] The top plate 32 in the first embodiment is a main casing 3 of a ceiling-embedded air conditioner (indoor unit) that is substantially the same as that of the conventional example shown in Figs. It is the best one to apply to.

[0030] As shown in FIG. 4, the thickness D of the top plate 32 is thinner than 0.8 mm of the conventional one.

Four

As shown in Fig. 1 and Fig. 2, the shape of the top plate 32 is formed in a substantially hexagonal shape corresponding to the shape of the force-set main body casing 3 of the air conditioner. A flange-like edge portion 32c for fitting to the outer periphery of the upper end portion of the main casing 3 is provided.

[0031] Similarly to the conventional apparatus shown in Figs. 22 to 24, the fan 5 and the fan motor 9 are supported on the top plate 32 at the central portion 33, and a substantially annular heat exchanger 4 is provided at the outer peripheral portion. Supported. As shown in FIGS. 4 and 5, the top plate 32 extends radially from the central portion 33 to the outer periphery of the top plate 32 and has an inverted trapezoidal cross section with a bottom width of W and an upper end width. W, depth D, slope

1 2 2 Front and back side forces with 0 corners Two types of multiple reinforcing ribs 32a, 32 provided alternately

2

It has been. The heat exchanger support located at the outer end of the reinforcing rib 32a of these reinforcing ribs 32a and 32a 'has a downward dent depth D smaller than D by a predetermined dimension.

3 2

A step 32b is formed.

[0032] Further, the top plate 32 has a depth D at the support portion of the fan 5 and the fan motor 9 at the central portion 33.

One reinforcing rib 33a is provided. Depth D is equal to depth D. The reinforcing rib 33a has three points.

1 2

And 5 fan motor support parts a to e that can support 4 points. As a result, the rigidity and strength of the support part of fan 5 and fan motor 9 are increased. The degree, the deflection characteristic, and the vibration characteristic are effectively improved.

Further, as shown in FIG. 1, heavy objects such as a heat exchanger 4, a fan 5, and a fan motor 9 are attached to the top plate 32 in the same manner as in the prior art.

As described above, in the configuration of the present embodiment, a plurality of auxiliary members extending radially from the central portion 33 where the fan motor 9 of the top plate 32 is supported to the outer peripheral portion where the heat exchanger 4 is supported. Strong ribs 32a 'and 32a are provided, and a plurality of reinforcing ribs 32a' and 32a are composed of a reinforcing rib 32 that projects the surface force of the top plate 32 and a reinforcing rib 32a that projects the back surface force. .

[0035] According to such a top plate structure, even if the thickness of the top plate 32 is made thinner than before, the number of the plurality of reinforcing ribs 32, 32a and the cross-sectional shape (drawing shape), depth, width, etc. By optimally adjusting and setting in a wide range, the rigidity, strength, deflection characteristics, vibration characteristics, etc. can be improved to the required levels. In particular, in the above case, the height of the vertical wall between the front and back surfaces is approximately doubled because the reinforcing ribs protrude from both the front and back surfaces of the top plate 32. The rigidity against stagnation is greatly improved. As a result, the plate thickness itself can be reduced, and the product cost can be reduced by improving the workability.

[0036] Reinforcing ribs 32 that project both the force and the surface force of the top plate 32 and the reinforcing ribs 32a that project the back surface force are alternately arranged along the circumferential direction. According to such a configuration, the support rigidity can be improved with good tolerance over the entire top plate 32, and the maximum deflection amount can be evenly reduced over the whole.

[0037] Then, the depth h of both ends in the longitudinal direction (radial direction) of each of the reinforcing ribs 32, 32a is set so as to become deeper between them as it approaches the both ends as shown in FIG. It is changing. Depth at both ends is represented by h and depth at the middle is represented by h

1 2

H <h.

1 2

[0038] As described above, when the depth of each of the reinforcing ribs 32a and 32 is changed along the longitudinal direction so as to be deeper between them, the maximum deflection is more effectively reduced. In addition, the rotational speed of the resonance can be further improved, and the cost of the top plate 32 can be further reduced by reducing the material.

[0039] In the present embodiment, the thickness of the top plate 32 is set to 0.6 mn! Set to a range of ~ 0.7mm Yes. The thinner the top plate 32, the lower the material cost and the easier the press molding. However, on the contrary, strength and rigidity are lowered, and deflection characteristics and vibration characteristics are deteriorated. In order to compensate for this, the reinforcing ribs 32 and 32a having the above-described configuration require an effective force, and a certain level of plate thickness is still necessary.

[0040] According to the results of various experiments with such viewpoint power, according to the top plate structure employing the above-described reinforcing ribs 32a 'and 32a, the thickness of the top plate 32 is 0.6 mn! The thickness could be reduced to a range of ~ 0.7mm, and even in that case, sufficient support rigidity could be realized and stable vibration characteristics could be secured. Therefore, the cost reduction of the effective top plate 32 by material reduction can be expected.

[0041] In other words, considering the relationship between the plate thickness level force and the conventional product plate thickness and the reinforcing effect of the above-mentioned reinforcing rib, the material cost is reduced, the workability is improved, and the necessary quality performance is ensured. This is an appropriate plate thickness range that can be achieved.

[0042] According to the top plate structure of the air conditioner of the above-described embodiment, the stable support rigidity, support strength, and low noise performance of the top plate can be achieved while reducing the thickness and cost of the top plate. It can be realized.

(Experimental example)

In order to confirm the actual effect of the radial reinforcing ribs 32 and 32a with the structure where both the front and back surface forces of the top plate protruded as described above, the following analysis experiment was conducted.

(1) Experimental sample

First, as an experimental sample, the number of reinforcing ribs related to the projecting direction is different as shown in FIGS. 7 (6), 9 (8), 12 (10), and 15 (12). We assumed the existence of four basic models. For the basic model shown in Fig. 9 (eight) and the basic model shown in Fig. 12 (10), two types are available: one-sided rib 32a and double-sided ribs 32a 'and 32a. 7 (6 pieces) and Fig. 15 (12 pieces) models with single-sided ribs 32a were prepared, and a total of six types of first to sixth experimental top plates 32A to 32F were manufactured. And the thickness is all 0.7mm. See Table 1 for the specifications.

[0043] In Table 1, the root R (mm) represents the radius of an arc connecting the base ends of a pair of adjacent reinforcing ribs.

[0044] [Table 1] Sample number 1 2 3 4 5 6

Number 6 8 8 10 1 0 1 2 ffgw (mm) 60.0

L (mm) 696.0

Root R (mm) 81.0 39.0 39.0 20.0 20.0 9.5 Depth h Single side 9.5 6.0 ― 9.5 ― 9.5

(mm) Both sides ― ― 8.0 ― 9.5 ―

[0045] a) First top plate 32A

In the first top plate 32A, as shown in FIG. 7, six reinforcing ribs 32a are evenly arranged in the circumferential direction at intervals of 60 °, and a pair of reinforcing ribs facing each other with a spacing of 180 ° therebetween. Dimensions (length) between both ends of 32a L is 696. Omm, groove width W is 60. Omm, and the reinforcing rib 32a protrudes only from either the front or back side (see Fig. 8).

[0046] b) Second top plate 32B

In the second top plate 32B, as shown in FIG. 9, eight reinforcing ribs 32a are evenly arranged at intervals of 45 ° in the circumferential direction, and a pair of reinforcing ribs facing each other at an interval of 180 °. Dimension (length) between both ends of 32a L is 696. Omm, groove width W is 60. Omm, and the reinforcing rib 32a protrudes only from either the front or back side (see Fig. 10).

[0047] c) Third top plate 32C

In the third top plate 32C, as shown in FIG. 9, eight reinforcing ribs 32a ', 32a are evenly arranged at intervals of 45 ° in the circumferential direction, and a pair of opposing each other is maintained at an interval of 180 °. Reinforcing ribs 3 2a ', 32a Dimension between both ends (length) L is 696. Omm, groove width W is 60. Omm, and reinforcing ribs 32a', 32a protrude alternately on both the front and back sides ( (See Figure 11).

[0048] d) Fourth top plate 32D

In the fourth top plate 32D, as shown in FIG. 12, ten reinforcing ribs 32a are evenly arranged at intervals of 36 ° in the circumferential direction, and a pair of reinforcing ribs facing each other with an interval of 180 ° therebetween. Dimensions at both ends of 32 and 32a (length) Force 696. Omm, groove width W force S 60. Omm, and the strong rib 32a protrudes from only one of the front and back surfaces (see Fig. 13) .

[0049] e) Fifth top plate 32E

In the fifth top plate 32E, as shown in FIG. 12, ten reinforcing ribs 32a 'and 32a are arranged in the circumferential direction. Dimension (length) between both ends of a pair of reinforcing ribs 32a 'and 32a facing each other at an interval of 180 ° and spaced apart by 180 ° L is 696. Omm, groove width W is 60. At 0 mm, the reinforcing ribs 32a 'and 32a protrude alternately on both the front and back surfaces (see Fig. 14).

[0050] f) 6th top plate 32F

In the sixth top plate 32F, as shown in FIG. 15, twelve reinforcing ribs 32a are evenly arranged at intervals of 30 ° in the circumferential direction, and a pair of reinforcing members facing each other with an interval of 180 ° therebetween. The dimension (length) between both ends of the rib 32a is 696. Omm, the groove width W is 60. Omm, and the reinforcing rib 32a protrudes only from either the front or back side (see Fig. 16).

[0051] 1) Influence of the number of radial ribs arranged on only one side

The effect of the number of ribs on the maximum deflection and the resonance speed of the top plate 32 with the radial reinforcing ribs 32a protruding only from one side is shown in Table 2 and the graphs in Figures 17 and 18. . Here, the width W, the length L, and the depth h of the reinforcing rib 32a are constant.

[0052] [Table 2]

[0053] From the analysis results shown in Table 2 and the graphs of FIGS. 17 and 18, the following knowledge is obtained.

[0054] When the number of reinforcing ribs 32a is 8 and 10, the static and dynamic characteristics of the top plate 32 are generally better than when the number of reinforcing ribs 32a is 6 and 12.

[0055] When the number of reinforcing ribs 32a is ¾ or 10, the maximum deflection of the top 32 (1.35 / 1.32 mm) and the primary resonance speed (907.0 / 914. Orpm) Are almost equivalent to each other. On the other hand, the secondary resonance rotational speed of the 8-rib top plate 32 is 990.Orpm, whereas the 10-rib top plate 32 is 940.Orpm, a decrease of 5.0%. It is clear that . Further, when the number of the reinforcing ribs 32a is 8, it is estimated that the top plate 32 has the best static characteristics and dynamic characteristics.

[0056] 2) Effect of radial rib depth Effect of Z single-sided and double-sided ribs

When eight radial ribs are arranged on one side (32a) and both sides (32, 32a), the change in the maximum deflection of the top plate 32 and the resonance speed due to the difference in the radial rib depth h is shown in Table 3 and Fig. 19

This is shown in the graph of Fig. 20.

[0057] [Table 3]

[0058] From this analysis result, the following knowledge is obtained.

[0059] In either case of the single-sided rib arrangement (32a) and the double-sided rib arrangement (32a ', 32a), the greater the rib depth, the lower the maximum deflection of the top plate 32, and the more the resonance rotational speed. It became clear that it improved. This means that increasing the depth of the ribs leads to an improvement in the static characteristics of the top board 32.

It can be seen from Table 3 and the graphs of FIG. 19 and FIG. 20 that the top plate 32 having the double-sided ribs shows superior static characteristics and dynamic characteristics as compared with the single-sided ribs.

[0061] By the way, in relation to the depth of the rib, the inventor of the present application similarly uses a plurality of ribs in the case where a plurality of ribs are arranged in parallel, in addition to the radial ribs as described above. Measure the maximum deflection amount of the top plate 32 and the change in the number of resonance rotations due to the difference in rib depth when it is placed on one side and both sides.

[0062] According to this, when the depth of the rib is relatively shallow at 2.0 to 6. Omm, the maximum deflection amount of the top plate 32 and the resonance rotational speed are strongly influenced by the depth of the rib. This is because, if the rib depth is relatively shallow, small fluctuations or variations in the rib depth will cause a large change in the maximum deflection of the top plate 32 and the resonance rotational speed. The top plate against the depth of the rib 2 means that the static and dynamic characteristics have low robustness.

[0063] On the other hand, when the rib depth is relatively large, 8.0-12.Omm, the influence of the rib depth on the maximum deflection amount of the top plate 32 and the resonance rotational speed is reduced. This is because when the rib depth is relatively large, there is a tendency for the rib depth to be such that small fluctuations or variations in the rib depth do not significantly change the maximum deflection of the top plate 32 and the resonance rotational speed. This means that the robustness of the static and dynamic characteristics of the plate 32 is relatively high.

[0064] On the other hand, when the rib depth is as great as 14. 0-18. Omm, the effect of the rib depth on the maximum deflection of the top plate 32 and the resonance rotational speed is limited. This is because when the rib depth is large, the variation or variation in the rib depth causes the maximum deflection of the top plate 32 and the change that the resonant rotation speed causes to be small. This means that the static and dynamic characteristics have high robustness.

[0065] These can be said to be substantially the same when the reinforcing ribs are radially arranged.

[0066] On the other hand, conventionally, the maximum deflection of the top plate 32 is 1.31 mm or less, and the resonance rotational speed is 742.

It is required as a design standard to maintain at Orpm or higher.

[0067] Therefore, if comprehensive consideration is given to satisfying such design criteria and maintaining the static characteristic and dynamic characteristic robustness of the top plate 32 with respect to the rib depth, the rib depth 8. Omm ~: LO. Omm is desirable.

[0068] (Second Embodiment)

FIG. 21 shows the structure of the top plate of an altitude installation type air conditioner according to the second embodiment of the present invention.

[0069] The top plate 32 in the second embodiment is also applied to the main body casing 3 of the indoor unit of the ceiling-embedded air conditioner that is substantially the same as the case of the conventional example shown in Figs. It is configured as the best one for you.

[0070] And, the plate thickness is thinner than the conventional 0.8 mm, and is about 0.7 mm, and the shape is the cassette type main body casing of the air conditioner of FIGS. 22 to 24 as shown in the figure. Corresponding to the shape of FIG. 3, it is formed in a substantially hexagonal shape, and on the outer periphery thereof, a bowl-shaped edge portion 32c for being fitted to the outer periphery of the upper end portion of the main body casing 3 is provided.

[0071] Further, in the central portion 33 of the top plate 32, the fan 5 and the configuration similar to those shown in Figs. A fan motor 9 is supported, and a substantially annular heat exchanger 4 is supported on the outer periphery. And, from the central part 33 to the outer peripheral part of the top plate 32, it extends radially like the first embodiment, and the cross-section protruding from the back surface is an inverted trapezoidal shape, the bottom width is W, and the top width is W

1 2

A plurality of main reinforcing ribs 32a having a depth D and an inclination angle Θ are provided. And each lord

twenty two

In the heat exchanger support outside the reinforcing rib 32a, the downward recess D is greater than the depth D.

3 2 is also formed with a stepped portion 32b that is reduced by a predetermined dimension (the dimensions are not shown).

[0072] Further, the top plate 32 has a depth D at the support portion of the fan 5 and the fan motor 9 at the central portion 33.

1 2

And five fan motor support portions a to e that can support four points, and are inscribed.

Thus, the basic rigidity, strength, deflection characteristics, and vibration characteristics of the support portions of the fan 5 and the fan motor 9 are effectively improved. However, as it is, the space between the main reinforcing ribs 32a becomes wider on the outer peripheral side of the top plate 32, and the rigidity, strength, etc. are insufficient accordingly.

[0074] Therefore, a plurality of sub-reinforcing ribs 34 having a desired shape and size are adjacent to each other between the plurality of main reinforcing ribs 32a in accordance with the magnitude of the assumed load as shown in the figure. Is provided. In this embodiment, the main reinforcing rib 32a protrudes from the back surface of the top plate 32, while the auxiliary reinforcing rib 34 also protrudes from the opposite surface force.

[0075] Accordingly, in order to keep the static deflection of the top plate 32 below a certain value and to avoid resonance due to the rotation of the fan motor 9, the primary natural frequency of the top plate 32 is kept above a certain value. Yes.

In such a configuration, like the conventional one, heavy objects such as the heat exchanger 4, the fan 5, and the fan motor 9 are attached.

[0077] As described above, in the second embodiment, the plurality of reinforcing ribs are composed of the long main reinforcing rib 32a and the short auxiliary reinforcing rib 34 provided between the main reinforcing rib 32a. The main reinforcing rib 32a projects either the front surface or the back surface of the top plate 32, and the auxiliary reinforcing rib 34 projects the opposite surface force. [0078] The same effects as those of the first embodiment can be realized in the same manner even in the case of such a configuration having the auxiliary reinforcing ribs 32a. As a result, the support rigidity can be increased with good tolerance, and the maximum deflection can be evenly reduced.

Therefore, even in this case, a thickness of the top plate 32 of 0.6 mm to 0.7 mm is sufficient.

Claims

The scope of the claims

[1] A main casing (3) that houses the fan (5), fan motor (9), and heat exchange ^^ (4), and on the top surface of the main casing (3), the fan (5) and fan A top plate (32) for suspending and supporting the motor (9) and the heat exchanger (4). The top plate (32) has a heat exchanger (4) from the center where the fan motor (9) is supported. ) Is supported by an air conditioner provided with a plurality of reinforcing ribs extending radially.

The top plate structure of an air conditioner, wherein the plurality of reinforcing ribs are composed of a reinforcing rib (32a ') protruding from the surface force of the top plate (32) and a reinforcing rib (32a) protruding from the back surface.

[2] The surface force of the top plate (32) The protruding reinforcing rib (32a ') and the back surface protruding the reinforcing rib (32a) are alternately arranged along the circumferential direction of the top plate (32). The top plate structure of the air conditioner according to claim 1, wherein

[3] The plurality of reinforcing ribs are composed of a plurality of long main reinforcing ribs (32a) and a plurality of short reinforcing ribs (34) provided between the main reinforcing ribs (32a). The main reinforcing rib (32a) protrudes from either the front or back surface of the top plate (32), and the auxiliary reinforcing rib (34) protrudes from the other surface of the top plate (32) or the back surface. The top plate structure of the air conditioner according to claim 1 or 2.

[4] The depth of each reinforcing rib (32), (32a), (34) varies along the longitudinal direction, and the depth of each end of each reinforcing rib is shallower than the depth between both ends. The top plate structure for an air conditioner according to any one of claims 1 to 3, wherein the top structure is an air conditioner.

[5] Thickness of the top plate (32) is 0.6mn! The top plate structure for an air conditioner according to any one of claims 1 to 4, wherein the top plate structure is set in a range of ˜0.7 mm.

[6] The depth force of each reinforcing rib (32a ^), (32a), (34) is 8.0 mm to 10. Omm, according to any one of claims 1 to 5, Air conditioner top plate structure.