WO2014024221A1

WO2014024221A1 - Heat exchanger and air conditioner provided with said heat exchanger

Info

Publication number: WO2014024221A1
Application number: PCT/JP2012/005041
Authority: WO
Inventors: 亮一池田; 明生村田; 三宅　展明; 宏樹岡澤; 渉鈴木; 拓也松田
Original assignee: 三菱電機株式会社
Priority date: 2012-08-08
Filing date: 2012-08-08
Publication date: 2014-02-13
Also published as: EP2884211A1; CN104321610A; EP2884211A4; US20150107803A1; JPWO2014024221A1

Abstract

This heat exchanger (1) is provided with: a plurality of fins (12) stacked at a predetermined fin pitch; and a plurality of flat-cross-sectioned heat transmission tubes (10) that penetrate the fins (12) along the direction of stacking. In the fins (12), a plurality of notches (13) are formed at the ends in the lengthwise direction thereof and having a shape corresponding to the cross-sectional shape of the heat transmission tubes (10); a collar (14) is formed at the edge of the notches (13); the heat transmission tubes (10) are inserted into the notches (13); the fin pitch between a subset of the plurality of fins (12) is larger than the fin pitch between the remaining fins (12); and at least the larger fin pitch is greater than the height of the collars (14).

Description

Heat exchanger and air conditioner equipped with the heat exchanger

The present invention relates to a heat exchanger and an air conditioner equipped with the heat exchanger.

Conventionally, in a heat exchanger of an air conditioner, a plurality of strip-shaped aluminum fins with circular holes formed are stacked via a predetermined fin pitch, and these stacked fins (hereinafter referred to as fin groups) are stacked. Heat exchange by expanding the inner diameter of the heat transfer tube using a hydraulic or mechanical pipe expander after inserting multiple copper or aluminum heat transfer tubes with a circular cross section along the stacking direction) Many plate fin tube type structures that ensure the adhesion between the fins and the heat transfer tubes necessary for the heat transfer performance of the heat exchanger are used (see, for example, Patent Document 1).

Also, the edge of the circular hole of the fin is subjected to burring processing to form a cylindrical collar in order to increase the area where the fin and the heat transfer tube are in close contact. Some fin flat plate portions between the circular holes are provided with slits to improve the heat exchange performance between the fins and the air flowing between the fins. The processing of circular holes, collars and slits to be formed on the fins is carried out sequentially by placing a progressive die with multiple steps on the press machine and continuously operating the press machine while supplying a strip-shaped aluminum hoop material. (For example, refer to Patent Document 2). And the fin is completed by cut | disconnecting the hoop material by which the circular hole, the color | collar, and the slit were processed by press work to desired strip length.

The fins formed in this manner are stacked in sequence while the collar is in contact with the adjacent fin, and then a plurality of long heat transfer tubes each having a U-shaped part called a hairpin are inserted and expanded. Is called. As described above, since the lamination of the fins and the circular tube insertion are performed on the basis of the collar, the fins are laminated and fixed at equal intervals of the collar height as a result (see, for example, Patent Document 3). Multiple heat transfer tubes are connected to parts such as U-bends and distributors, which are pipe-connecting circular tubes bent at the end, by brazing, so that they are layered in the fin group. A continuous flow path of the folded refrigerant is formed. The fin group with a built-in heat transfer tube connected to the end pipe may be formed in an L shape or a U shape. For example, when the heat exchanger is formed in a U-shape, the entire shape of the fin group and the inner heat transfer tube shape are finally formed by performing an L-shaped bending process on the fin group twice. It becomes a heat exchanger (for example, refer patent document 4). Even in the heat exchanger after the bending, the fins are laminated on the three U-shaped surfaces (straight line portions) at the same interval of the collar height as they are before the molding.

∙ Air conditioners have significant competition for energy savings and cost reductions against the background of rising energy problems. For this reason, in the heat exchanger as described above, further improvement measures are pursued with respect to the shape of the heat transfer tubes and fins, the fin pitch, the heat transfer tubes and the fin materials, and the fins according to the internal structure of the air conditioner. Measures such as changing the pitch have also been proposed (see, for example,

Patent Documents

5, 6, and 7).

Japanese Examined Patent Publication No. 58-13249 (page 3-4, Fig. 1-3) Japanese Examined Patent Publication No. 58-9358 (page 2-3, Fig. 1-5) Japanese Examined Patent Publication No. 3-80571 (page 9, Fig. 1-2) Japanese Patent No. 4417620 (page 15, FIG. 20) JP 63-233296 A (2nd page) JP 2004245553 A (page 3) JP 2008-8541 A (Page 7, FIG. 3)

As described above, the conventional heat exchanger has a step of laminating a plurality of fins with collars formed on the edges of the circular holes, and inserts a heat transfer tube having a circular cross section into the circular holes of the laminated fins. It is completed through the process of expanding the heat pipe. For this reason, the pitch between the fins of the conventional heat exchanger is constant at the burring collar height. Therefore, it has been difficult for the conventional heat exchanger to change the fin pitch in a part of the range according to the internal structure of the air conditioner or the like in order to improve the performance of the air conditioner. For this reason, the air conditioner provided with the conventional heat exchanger had the subject that cost was high with respect to heat exchanger performance.

For example, an outdoor unit of an air conditioner has a housing such as a compressor cover (cover for storing the compressor) or a control panel built in the housing. For this reason, the ventilation resistance in each part of a heat exchanger changes according to the arrangement position of a stored item. However, in the conventional heat exchanger, since the fin pitch is determined by the collar height, it is difficult to change the fin pitch in a part of the heat exchanger according to the ventilation resistance in each part of the heat exchanger. Met.

In addition, the structure which changes the fin pitch of the partial range of a heat exchanger by dividing | segmenting a heat exchanger, using the fin of different color height, etc. is also proposed. However, in order to make the heat exchanger such a structure, it is necessary to prepare a plurality of types of fin progressive molds according to the collar height. Or it is necessary to prepare the metal mold | die provided with the mechanism which can set up burring height. For this reason, when preparing a plurality of types of molds, the mold cost becomes expensive, or the replacement work of the mold becomes complicated, and the fin manufacturing cost becomes expensive. In addition, when using a die having a mechanism capable of setting up the burring height, the die cost and the press cost are increased due to the complexity and size of the die and the accompanying increase in the size of the press machine. End up. Further, in order to assemble a heat exchanger having such a structure, it is necessary to stack fins having different color heights at predetermined positions, and therefore the assembly cost becomes expensive. In practice, it is the limit to prepare two to three types of fins having different color heights due to restrictions on the mold size. For this reason, it is practically difficult to make the heat exchanger such a structure.

Also, in order to avoid such a problem, a method in which the collar is made lower than the fin pitch (stacking interval) and the heat exchanger is manufactured without stacking the fins on the basis of the collar height can be considered. However, when manufacturing a conventional heat exchanger by such a method, in the conventional heat exchanger in which a heat transfer tube having a circular cross section is inserted into the circular hole of the fin, each fin is laminated at a predetermined fin pitch. If it is going to insert a heat exchanger tube in a fin group, each fin will shift | deviate and it cannot make a desired fin pitch between each fin. For this reason, when manufacturing the conventional heat exchanger by such a method, it is necessary to attach a fin one by one to a heat exchanger tube. However, in order to construct a conventional heat exchanger by attaching fins one by one to the heat transfer tube, in each fin, the heat transfer tube is inserted into a circular hole of the fin, and the fin is a tube shaft of the heat transfer tube. A step of moving the long stroke along the direction and arranging it at a desired position is required. For this reason, it is difficult to realize a conventional heat exchanger with a collar lower than the fin pitch (stacking interval) and without stacking the fins on the basis of the collar height.

The present invention has been made to solve the above-described problems. A first object of the present invention is to provide a fin pitch within a certain range without increasing the mold cost, press machine cost and assembly cost of the fin. Is to get a heat exchanger that can be changed. Moreover, the second object of the present invention is to provide an energy-saving and low-cost air conditioner by providing the heat exchanger, thereby reducing the cost for the heat exchanger performance.

The heat exchanger according to the present invention is arranged with a plurality of fins stacked via a predetermined fin pitch and a predetermined interval along a longitudinal direction of the fins, and the fins are arranged along the stacking direction. A plurality of heat transfer tubes penetrating, wherein the plurality of heat transfer tubes are heat transfer tubes having a flat cross-section, and the plurality of fins correspond to the cross-sectional shape of the heat transfer tubes at end portions on the longitudinal direction side. A plurality of cutouts having the above-described shape are formed, collars are formed at the edges of the plurality of cutouts, the heat transfer tubes are inserted into the cutouts, and a fin pitch between a part of the plurality of fins is The fin pitch between the other fins is larger, and at least the larger fin pitch is larger than the height of the collar, which is the amount of projection of the collar from the plate surface of the fin. In .

An air conditioner according to the present invention includes a housing in which an inlet and an outlet are formed, a heat exchanger according to the present invention provided in the housing, a fan provided in the housing, It is equipped with.

In the heat exchanger according to the present invention, a notch into which the heat transfer tube is inserted is formed at the end of the fin in the longitudinal direction. For this reason, since a fin can be attached from the side surface side of a heat exchanger tube, a fin can be attached to a desired position with an end stroke. Therefore, a heat exchanger can be manufactured without inserting a heat transfer tube into a fin group in which fins are previously laminated on a color basis. That is, the fin of the same shape which does not require an expensive metal mold | die and a press machine can be attached to the desired position of a heat exchanger tube, without requiring the effort of an assembly. Therefore, it is possible to obtain a heat exchanger that can change a fin pitch in a certain range without increasing the mold cost, press machine cost, and assembly cost of the fins.

In addition, since the air conditioner according to the present invention includes the heat exchanger according to the present invention as described above, the fin pitch in a partial range of the heat exchanger is changed according to the internal structure of the air conditioner. By doing so (for example, by configuring the fin pitch in a range where the amount of air passing therethrough is smaller than the other range depending on the storage items), the fins can be distributed more effectively than before, so the price From the viewpoint of performance ratio, the heat exchange efficiency can be improved, and an energy-saving and low-cost air conditioner can be obtained. In addition, when the present invention is applied to an air conditioner with specifications that do not have any problem with the conventional performance, the number of fins can be reduced by the surplus performance due to the above performance improvement, so that equivalent performance is ensured. However, it is possible to reduce the size and price of the air conditioner.

It is a perspective view which shows the outdoor unit which concerns on Embodiment 1 of this invention. It is a perspective view which shows the internal structure of the outdoor unit which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the compressor cover adjacent range in the outdoor unit which concerns on Embodiment 1 of this invention. In the outdoor unit according to Embodiment 1 of the present invention, “the air volume Q of the compressor cover adjacent range 5”, “the distance D between the compressor cover adjacent range 5 and the compressor cover 7, the diameter D of the propeller fan 9, It is a characteristic view which shows a correlation with "ratio L / D". It is a characteristic view which shows the correlation with the fin pitch and compressor coefficient of the compressor cover adjacent range in the outdoor unit which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the component shape and manufacturing method of the heat exchanger of the outdoor unit which concerns on Embodiment 1 of this invention. It is the plane sectional view showing the heat exchanger and control panel 8 in the outdoor unit concerning Embodiment 2 of the present invention from the propeller fan side. It is a perspective view which shows the internal structure of the outdoor unit which concerns on Embodiment 2 of this invention. It is the plane sectional view showing the heat exchanger in the outdoor unit concerning Embodiment 3 of the present invention from the propeller fan side. It is the plane sectional view which showed the heat exchanger in the outdoor unit concerning Embodiment 4 of the present invention from the propeller fan side. It is a figure which shows the relationship between temperature efficiency (epsilon) and heat exchanger performance AK. It is a front view which shows the density position of the fin of the heat exchanger in the outdoor unit of the air conditioner in Embodiment 5 of this invention.

Embodiment 1 FIG.
The heat exchanger according to the first embodiment is configured such that the fin pitch in a part of the range is formed larger than the fin pitch of the other range by an assembly method different from the conventional one that can easily change the fin pitch. is there. In addition, the air conditioner according to the first embodiment includes the heat exchanger according to the first embodiment in which the optimum fin density arrangement is performed in consideration of the internal structure in the casing, It enables energy saving, low cost and low price while maintaining equivalent performance.
Hereinafter, the heat exchanger according to the first embodiment, the method for manufacturing the heat exchanger according to the first embodiment, and the details of the air conditioner according to the first embodiment will be described. In the following, the air conditioner according to the first embodiment will be described by taking an outdoor unit equipped with the heat exchanger according to the first embodiment as an example.

FIG. 1 is a perspective view showing an outdoor unit according to Embodiment 1 of the present invention. FIG. 2 is a perspective view showing the internal structure of the outdoor unit. In FIG. 2, in order to facilitate understanding of the structure of the outdoor unit according to the first embodiment, only storage items that occupy the internal space of the housing are illustrated, and refrigerant piping, four-way valves, and valves are illustrated. Illustrations of stored items such as these are omitted.

The outdoor unit 101 according to the first embodiment is an outdoor unit of a commercial air conditioner used in a building or factory. This outdoor unit 101 constitutes a refrigeration cycle together with an indoor unit (not shown), and includes a heat exchanger 1, a propeller fan 9, a compressor cover 7 in which a compressor is stored, a control panel 8, and the like. It contains storage items.

The housing 34 has a shape in which four corners of a substantially square upper surface portion 35a and a bottom surface portion 35b are connected by pillars 36 (columnar members), that is, a substantially rectangular parallelepiped shape in which four side surfaces are opened. Of these four side opening portions, three side opening portions serve as suction ports 34a. In addition, in order to prevent a hand etc. contacting the heat exchanger 1 to the suction inlet 34a, you may provide the member of a grid | lattice-like part. In addition, a substantially cylindrical protruding portion is formed on the upper surface portion of the housing 34. The upper surface portion and the outer peripheral portion of the projecting portion are open, and the opening portion serves as a blowout port 34b. The air outlet 34b is provided with a fan guard 38 that guides the flow of air blown from the air outlet 34b.

As described above, the casing 34 configured as described above accommodates the heat exchanger 1, the propeller fan 9, the compressor cover 7 storing the compressor, the control panel 8, and the like.
The heat exchanger 1 is provided so as to face the suction port 34a opened in the three side portions, and is formed in a U shape in plan view. That is, the outdoor unit 101 has a structure in which the heat exchanger 1 is exposed to the periphery in most of the outdoor unit 101 except for the lattice members provided in the pillar 36 and the suction port 34a. This heat exchanger 1 is divided into three stages of heat exchanger parts in the vertical direction (hereinafter, when it is necessary to distinguish and describe these three stages of heat exchanger parts, one stage from the top in order. Eye heat exchanger 2, second stage heat exchanger 3, and third stage heat exchanger 4). Each of the first-stage heat exchanger 2, the second-stage heat exchanger 3, and the third-stage heat exchanger 4 further includes two rows of heat along the flow direction of air passing through the heat exchanger sections. Divided into exchanger parts.

Here, the configuration of the heat exchanger 1 described above is merely an example. For example, the first-stage heat exchanger 2, the second-stage heat exchanger 3, and the third-stage heat exchanger 4 may be integrated to form the heat exchanger 1. The heat exchanger 1 may be configured as a single row heat exchanger. Moreover, when the suction inlet 34a is formed in two adjacent side parts, you may form the heat exchanger 1 in planar view L shape. Further, it is not always necessary to form a bent portion in the heat exchanger 1, and the heat exchanger 1 may be configured by combining heat exchanger portions that are linear in a plan view. Details of the heat exchanger 1 (detailed configuration of fins and heat transfer tubes and a method for manufacturing the heat exchanger 1) will be described later.

The propeller fan 9 is provided in the convex part of the upper surface part 35a so that the outer peripheral part thereof faces the air outlet 34b. That is, the outdoor unit 101 according to the first embodiment sucks outside air from the suction port 34a formed on the side surface of the casing 34 when the propeller fan 9 is driven to rotate, and exchanges heat with the sucked outside air. Heat is exchanged with the refrigerant in the vessel 1 and the outside air after the heat exchange is blown out from the outlet 34b.

The compressor cover 7 and the control panel 8 are arranged so as to be surrounded by the heat exchanger 1 in plan view. That is, the compressor cover 7 and the control panel 8 are arranged on the air path of the outside air in the housing 34. Specifically, the compressor cover 7 is provided below the housing 34 so as to be surrounded by the heat exchanger 1 in plan view. The control panel 8 is provided above the housing 34 so as to be surrounded by the heat exchanger 1 in plan view. Further, the control panel 8 is provided so as to face the side surface portion of the housing 34 which is not the suction port 34 a, and this side surface portion is covered with a panel 37.

Here, the outdoor unit 101 according to the first embodiment has a configuration in which the compressor cover 7 is adjacent to a part of the third stage heat exchanger 4 of the heat exchanger 1 (hereinafter, this adjacent range). Is referred to as compressor cover adjacent range 5). In other words, the outdoor unit 101 according to Embodiment 1 is configured such that the distance between the compressor cover adjacent range 5 of the third stage heat exchanger 4 and the compressor cover 7 is within a predetermined distance. That is, in the heat exchanger 1, the ventilation resistance of the compressor cover adjacent range 5 is larger than the ventilation resistance of the other range (hereinafter referred to as the compressor non-adjacent range 6). The air volume is smaller than the air volume in the compressor non-adjacent range 6. Therefore, in the first embodiment, the heat exchanger 1 is formed such that the fin pitch in the compressor cover adjacent range 5 is larger than the fin pitch in the compressor non-adjacent range 6.

At this time, the heat exchanger 1 is provided facing the suction port 34a formed in the side surface portion of the housing 34, and the propeller fan 9 is provided facing the air outlet 34b formed in the upper surface portion of the housing 34. In the outdoor unit 101 according to the first embodiment, the compression is performed when the distance between the compressor cover adjacent range 5 of the third stage heat exchanger 4 and the compressor cover 7 is equal to or less than the distance as described later. It is effective to form the heat exchanger 1 so that the fin pitch in the machine cover adjacent range 5 is larger than the fin pitch in the compressor non-adjacent range 6.

FIG. 3 is an explanatory diagram for explaining a compressor cover adjacent range in the outdoor unit according to Embodiment 1 of the present invention. FIG. 3 is a plan sectional view showing the third-stage heat exchanger 4 and the compressor cover 7 from the propeller fan 9 side.
As shown in FIG. 3, when the diameter of the propeller fan 9 is D, and the distance between the compressor cover adjacent range 5 and the compressor cover 7 is L, the air volume in each part of the third stage heat exchanger 4 is shown in FIG. It becomes like this.

FIG. 4 shows “the air volume Q of the compressor cover adjacent range 5”, “the distance L between the compressor cover adjacent range 5 and the compressor cover 7, and the diameter of the propeller fan 9 in the outdoor unit according to Embodiment 1 of the present invention. It is a characteristic view which shows the correlation with "ratio L / D" of D. The rotation speed N of the propeller fan 9 is constant.
As shown in FIG. 4, it can be seen that when L / D is 0.15 or less, the ventilation resistance in the compressor cover adjacent range 5 is large, and the compressor cover adjacent range 5 air volume Q is small. Therefore, the heat exchanger 1 is provided facing the suction port 34 a formed in the side surface portion of the housing 34, and the propeller fan 9 is provided facing the air outlet 34 b formed in the upper surface portion of the housing 34. In the outdoor unit 101 according to the first embodiment, when L / D is 0.15 or less, the fin pitch in the compressor cover adjacent range 5 is set larger than the fin pitch in the compressor non-adjacent range 6. It is effective to form the heat exchanger 1.

Further, when the heat exchanger 1 is formed so that the fin pitch of the compressor cover adjacent range 5 is larger than the fin pitch of the compressor non-adjacent range 6, the fin pitch of the compressor cover adjacent range 5 is, for example, as follows. Is set.

FIG. 5 is a characteristic diagram showing a correlation between the fin pitch in the adjacent range of the compressor cover and the coefficient of performance in the outdoor unit according to Embodiment 1 of the present invention. In FIG. 5, the coefficient of performance (COP) of the air conditioner using the outdoor unit 101 is shown on the vertical axis. Further, the horizontal axis of FIG. 5 indicates k (= fp2 / fp1) which is a ratio of the fin pitch fp2 of the compressor cover adjacent range 5 and the fin pitch fp1 of the compressor non-adjacent range 6.
As can be seen from FIG. 5, when k (= fp2 / fp1) = 1, that is, when the fin pitch fp2 of the compressor cover adjacent range 5 is the same as the fin pitch fp1 of the compressor non-adjacent range 6, The coefficient of performance (COP) of the air conditioner using the outdoor unit 101 is close to the maximum value. Further, the vicinity of k = 1 (region where the fin pitch fp2 is close to the fin pitch fp1) is a region where the coefficient of performance (COP) is small even if the fin pitch fp2 is changed. Further, the outdoor unit 101 was used as k (= fp2 / fp1) increased, that is, as the fin pitch fp2 in the compressor cover adjacent range 5 increased with respect to the fin pitch fp1 in the compressor non-adjacent range 6. The coefficient of performance (COP) of the air conditioner is decreasing. For this reason, in this Embodiment 1, the coefficient of performance (COP) of the air conditioner using the outdoor unit 101 is prevented from excessively decreasing by making the fin pitch fp2 of the compressor cover adjacent range 5 too large. Therefore, for example, the coefficient of performance (COP) of the air conditioner using the outdoor unit 101 is 95% or more when k (= fp2 / fp1) = 1 (1 <k ≦ b in FIG. 5). The coefficient of performance (COP) of the air conditioner using the outdoor unit 101 is set.

<Details of heat exchanger 1>
Next, details of the heat exchanger 1 will be described.
FIG. 6 is an explanatory diagram for explaining a part shape and a manufacturing method of the heat exchanger of the outdoor unit according to Embodiment 1 of the present invention.

First, the detailed structure of the heat exchanger 1 is demonstrated using FIG.
The heat exchanger 1 is arranged with a plurality of fins 12 stacked via a predetermined fin pitch and a predetermined interval along the longitudinal direction of the fins 12, and the fins 12 are arranged along the stacking direction of the fins 12. A finned tube heat exchanger including a plurality of heat transfer tubes 10 penetrating therethrough.

In the heat transfer tube 10, a refrigerant that exchanges heat with air flowing between the fins 12 flows. The heat transfer tube 10 has a flat cross section (for example, a long round shape), and the inside thereof is divided into a plurality of flow paths (holes) by a partition wall. Each heat transfer tube 10 is inserted into a notch 13 of a fin 12 described later along the long axis direction of the cross-sectional shape.

The fins 12 are, for example, thin plates having a substantially rectangular parallelepiped shape. A plurality of cutouts 13 are formed at predetermined ends in the end portion of the fin 12 on the longitudinal direction side. These notches 13 are locations where the heat transfer tubes 10 are inserted as described above, and have a shape corresponding to the cross-sectional shape of the heat transfer tubes 10. In the first embodiment, the notch 13 is formed in a U-shaped groove shape, and the opening width at the end is substantially equal to the width of the heat transfer tube 10 (in other words, the length in the minor axis direction of the cross section). Yes. In addition, the edges of the notches 13 are connected to the plate surfaces of the fins 12 for the purpose of increasing the contact area between the fins 12 and the heat transfer tubes 10 and for securing the bonding strength between the fins 12 and the heat transfer tubes 10. A collar 14 is formed substantially vertically. The height of the collar 14 (the protruding amount of the collar 14 protruding from the plate surface of the fin 12) is at least adjacent to the compressor cover formed larger than the fin pitch in the compressor non-adjacent range 6 of the heat exchanger 1. It is lower than the fin pitch in range 5. In addition, a plurality of cut-and-raised slits (not shown) are formed on the surface of each fin 12 so as to open in the flow direction of the air flowing between the fins 12 (in other words, in the short direction of the fins 12). Yes. By forming the cut-and-raised slit, the temperature boundary layer on the surface of the fin 12 can be divided and updated, and the heat exchange efficiency between the air flowing between the fins 12 and the fins 12 can be improved.

A heat exchanger that combines a heat transfer tube and fins with a flat cross section and an interior divided into a plurality of flow paths is compared to a conventional heat exchanger that combines a heat transfer tube and fins with a circular cross section. Many literatures show that a volume-to-performance ratio equal to or higher than that can be obtained.

Next, the manufacturing method of the heat exchanger 1 is demonstrated.
The fins 12 of the heat exchanger 1 are manufactured by cutting out from a thin plate (plate member) such as an aluminum thin plate wound around a reel in a hoop shape. Specifically, first, a plurality of pilot holes 15 are formed in the vicinity of the end portion of the thin plate along the feeding direction of the thin plate. Then, using these pilot holes 15 (for example, by inserting pins or the like into the pilot holes 15), the thin plate feed mechanism of the high speed press machine intermittently feeds the thin plates in the high speed press machine (FIG. 6 shows a thin plate feed operation). As indicated by arrow 16). Further, the high-speed press machine is provided with a progressive die, and when a thin plate is intermittently fed through the high-speed press machine, the high-speed press machine has an opening hole that becomes a notch 13, a collar 14, a cut-and-raised slit, and the like. Are sequentially press-formed. As a result, on the thin plate fed out from the high-speed press machine, the fin series 17 in which the fins 12 are connected is formed.

The above-mentioned fin series 17 is cut into the fins 12 one by one by a cutting device provided on the downstream side of the high-speed press (see arrow 18 shown as the cutting operation in FIG. 6). And the fin 12 cut | disconnected in this way is attached to the heat exchanger tube 10 as follows.

Specifically, the production line of the heat exchanger 1 according to Embodiment 1 has a table. A plurality of heat transfer tubes 10 are arranged at a predetermined interval on the upper surface of the table. In addition, this table is provided with a conveyance mechanism including, for example, a servo motor, a ball screw, a linear guide, and the like, and a pitch feeding operation is performed along the tube axis direction of the heat transfer tube 10 (in other words, the lamination direction of the fins 12). (See arrow 21 shown as pitch feed operation in FIG. 6). On the other hand, an insertion device including a cam and a servo is provided above the table. The insertion device includes a gripping mechanism that grips the fins 12 that have been cut by the cutting device, and a rotation mechanism that rotates the gripped fins 12 so that the opening side end of the notch 13 faces downward.

For this reason, the fin 12 cut | disconnected with the cutting device with the insertion apparatus is hold | gripped, the fin 12 hold | gripped so that the opening side edge part of the notch 13 may face down, and the fin 12 is lowered | hung on a table Accordingly, the upper portion of the heat transfer tube 10 starts to be inserted into the notch 13 of the fin 12 from the opening side thereof, and the fin 12 is pushed in until the inner portion of the notch 13 comes into contact with the upper portion of the heat transfer tube 10. Fins 12 are attached to the plurality of arranged heat transfer tubes 10 (see arrow 19 shown in FIG. 6 as movement / rotation operation of fins 12). And while an insertion apparatus repeats the attachment process of this fin 12, that is, after a fin 12 is attached to the heat exchanger tube 10, until the next fin 12 is attached to the heat exchanger tube 10, a table is the heat exchanger tube 10. The fins 12 are attached to the heat transfer tube 10 so as to have the desired fin pitch and the tail of the fins already attached to the heat transfer tube 10 by moving by a predetermined pitch in the tube axis direction.

The above-described cutting operation 18, movement / rotation operation 19 of the fin 12, and pitch feed operation 21 of the heat transfer tube 10 follow the hoop feed operation 16 of the high-speed press machine while synchronizing the insertion device and the table transport mechanism. Are performed sequentially. Regarding the out-of-synchronization between the high-speed press and the insertion device, the material is provided in the supply path of the thin plate on the upstream side of the high-speed press to provide a material buffer, and the press stroke is detected while detecting the amount of slack. Absorb by increasing or decreasing.

Also, the pitch movement amount of the above-described pitch feed operation 21 is set by the controller of the transport mechanism. Specifically, a large pitch movement amount is set for the fin group 22 that constitutes the compressor cover adjacent range 5 in the heat exchanger 1 where the air volume is small. About the fin group 23 which comprises the compressor non-adjacent range 6 used as the range with a large airflow among the heat exchangers 1, the pitch moving amount is set to a small moving amount. By laminating the required number of fins 12 with such a pitch movement amount, a fin group assembly portion comprising a fin group 22 laminated with a larger fin pitch and a fin group 23 laminated with a smaller fin pitch. 24 (during assembly in FIG. 6) is completed.

The completed fin group assembly portion 24 and the heat transfer tube 10 are fixed by brazing in a furnace using a brazing material pre-coated on the heat transfer tube 10. Or the completed fin group assembly part 24 and the heat exchanger tube 10 are fixed by making use of the adhesive applied to the gap between the collar 14 of the heat exchanger tube 10 and the fins 12. After that, the fin group assembly unit 24 is connected in a state where two sheets are overlapped, and the U-shape is formed by two L-shaped bends, so that the heat exchanger 1 (first-stage heat exchanger) 2, the assembly of the second stage heat exchanger 3, the third stage heat exchanger 4) is completed.

As described above, in the first embodiment, the heat transfer tubes 10 are arranged at predetermined intervals, the fins 12 are attached to the heat transfer tubes 10 one by one, and the fin pitch of the compressor cover adjacent range 5 is the compressor non-adjacent range. The heat exchanger 1 (first stage heat exchanger 2, second stage heat exchanger 3, third stage heat exchanger 4) formed to be larger than the fin pitch of 6 is manufactured. For this reason, unlike the conventional manufacturing method in which a heat transfer tube having a circular cross section is inserted into a circular hole of a fin group that has been laminated in advance on a color basis, the manufacturing method of the heat exchanger 1 according to the first embodiment is When changing the fin pitch in a part of the range of the exchanger 1, a complicated mold or a large press for changing the color height is not required. Moreover, the manufacturing method of the heat exchanger 1 which concerns on this Embodiment 1 only changes the controller command value of the pitch movement amount of a conveyance mechanism, when changing the fin pitch of the partial range of the heat exchanger 1. FIG. The fin pitch can be immediately changed to various sizes.

Further, the manufacturing method of the heat exchanger 1 according to the first embodiment is a conventional manufacturing method (one sheet) in which the collar is made lower than the fin pitch and the heat exchanger is manufactured without stacking the fins on the basis of the collar height. In each fin, unlike the manufacturing method in which a heat transfer tube is inserted into a circular hole of the fin, the fin is moved by a long stroke along the tube axis direction of the heat transfer tube, and the fin 12 is disposed at a desired position, the fin 12 is connected to the heat transfer tube. 10 can be attached from the side surface side, so that the stroke from when the heat transfer tube 10 is inserted into the notch 13 of the fin 12 until the fin 12 is arranged at a desired position can be shortened. Therefore, the manufacturing method of the heat exchanger 1 according to the first embodiment transmits the fins at various fin pitches at a high speed operation capable of following the punching speed of a high speed press with, for example, several hundred SPM (strokes per minute). It can be attached to a desired position of the heat tube 10.

Moreover, the heat exchanger 1 with which the outdoor unit 101 comprised like this Embodiment 1 is equipped with the fin pitch of the compressor cover adjacent range 5 used as the range with a large ventilation resistance and a small air volume has a compressor cover adjacent range. It is formed larger than the fin pitch of the compressor non-adjacent range 6 where the air volume is larger than 5. That is, the heat exchanger 1 has a large fin pitch in a range where the coefficient of performance (COP) is small even when the air volume is small and the fin pitch is large. For this reason, this heat exchanger 1 is more efficient in terms of price / performance than a heat exchanger in which the total number of fins is the same as that of the heat exchanger 1 and the fin pitch between all fins is uniform. Can be improved. Therefore, the outdoor unit 101 provided with this heat exchanger 1 can be energy-saving and cost-saving compared with the past. In addition, when the configuration of the outdoor unit 101 according to the first embodiment is adopted for an outdoor unit that has no problem in performance as in the past, the number of fins 12 can be reduced by the amount of surplus performance due to the above performance improvement. Therefore, it is possible to reduce the size and price of the outdoor unit while ensuring equivalent performance. Further, the manufacturing time can be shortened by reducing the number of inserted fins.

In the first embodiment, the fin pitch of a partial range (compressor cover adjacent range 5) is enlarged only in the third stage heat exchanger 4, but the compressor cover 7 is large in the height direction. In the second stage heat exchanger 3 and the first stage heat exchanger 2 arranged above the third stage heat exchanger 4, the fin pitch in a part of the range may be enlarged. In the first embodiment, the heat exchanger 1 is divided into three stages of heat exchanger parts (first stage heat exchanger 2, second stage heat exchanger 3, third stage heat exchanger 4). The heat exchanger 1 may be divided into two stages of heat exchanger units, or may be divided into four or more stages of heat exchanger units. It goes without saying that the above effect can be obtained even with such a configuration.

Further, in the first embodiment, the compressor cover 7 is described as an example of the stored item that increases the ventilation resistance (in other words, the stored item disposed in the vicinity of the heat exchanger 1), but this is only an example. is there. When the stored items other than the compressor cover 7 are arranged in the vicinity of the heat exchanger 1, the fin pitch in the range in the vicinity of the stored item in the heat exchanger 1 is formed larger than the fin pitch in the other range. The above effects can be obtained.

Embodiment 2. FIG.
In the first embodiment, as an example of changing the fin pitch in a partial range of the heat exchanger 1, an example of changing the fin pitch in the compressor cover adjacent range 5 adjacent to the compressor cover 7 has been described. However, the range in which the fin pitch is changed is not limited to the compressor cover adjacent range 5. The fin pitch in the following range of the heat exchanger 1 may be changed together with the compressor cover adjacent range 5 or separately from the compressor cover adjacent range 5. Note that a configuration not particularly described in the second embodiment is the same as that of the first embodiment, and the same function and configuration are described using the same reference numerals.

FIG. 7 is a plan sectional view showing the heat exchanger and the control panel 8 in the outdoor unit according to Embodiment 2 of the present invention from the side of the propeller fan.
In the outdoor unit 101 according to the second embodiment, the control panel 8 is provided on one side surface of the housing 34 as in the first embodiment. Since the control panel 8 generates heat when the outdoor unit 101 is operated, it is necessary to cool the control panel 8 during the operation of the outdoor unit 101. For this reason, the outdoor unit 101 according to the second embodiment is configured to cool the control panel 8 using the air flow generated by the action of the propeller fan 9.

In the second embodiment, in order to improve the cooling effect of the control panel 8, the fin pitch at the end of the heat exchanger 1 arranged on the control panel 8 side is set to a fin in another range of the heat exchanger 1. It is formed larger than the pitch. In the second embodiment, the heat exchanger 1 formed in a U-shape is used as in the first embodiment. For this reason, the fin pitch of the both ends 25 of the heat exchanger 1 formed in the U-shape is formed larger than the fin pitch in the other range of the heat exchanger 1.
Hereinafter, the reason why the cooling effect of the control panel 8 is improved by making the fin pitch of the both ends 25 of the heat exchanger 1 larger than the fin pitch of the other range of the heat exchanger 1 will be described.

FIG. 8 is a perspective view showing the internal structure of the outdoor unit 101 according to Embodiment 2 of the present invention. The white arrows shown in FIG. 8 indicate the flow of air inside the outdoor unit 101. In FIG. 8, illustrations of storage items other than the heat exchanger 1 and the propeller fan 9 are omitted to facilitate understanding of the air flow.
Air has the property of flowing along the wall surface. Therefore, as shown in FIG. 8, the heat exchanger 1 is provided so as to face the suction port 34 a formed in the side surface portion of the housing 34, and faces the air outlet 34 b formed in the upper surface portion of the housing 34. In the outdoor unit 101 according to the second embodiment in which the propeller fan 9 is provided, the air that has passed through the heat exchanger 1 gathers at both end portions 25 of the heat exchanger 1 in the vicinity of the panel 37 and performs heat exchange. It flows upward along both ends 25 of the vessel 1, passes through the propeller fan 9 at the top of the housing 34, and is exhausted from the outlet 34 b.

At this time, both ends of the heat exchanger 1 are reduced by reducing the ventilation resistance of the both ends 25 by making the fin pitch of the both ends 25 of the heat exchanger 1 larger than the fin pitch of the other range of the heat exchanger 1. The amount of air flowing in from the portion 25 can be increased, and the amount of air flowing along the both end portions 25 of the heat exchanger 1 can be increased. For this reason, the cooling effect of the control panel 8 can be improved by making the fin pitch of the both ends 25 of the heat exchanger 1 larger than the fin pitch of the other range of the heat exchanger 1.

Furthermore, by making the fin pitch of the both ends 25 of the heat exchanger 1 larger than the fin pitch in the other range of the heat exchanger 1, the air passing through the both ends 25 and the refrigerant flowing inside the heat exchanger 1 The amount of heat exchange becomes smaller. For this reason, at the time of cooling operation, the temperature of the air flowing in from both ends 25 of the heat exchanger 1, that is, the temperature of the air flowing along both ends 25 of the heat exchanger 1 can be reduced. For this reason, at the time of cooling operation, the cooling effect of the control panel 8 can be improved also by the temperature fall of the said air.

As described above, in the outdoor unit 101 configured as in the second embodiment, the control panel 8 is provided on one side surface of the housing 34 and the end of the heat exchanger 1 disposed on the control panel 8 side is provided. The fin pitch is formed larger than the fin pitch in the other range of the heat exchanger 1. For this reason, the cooling air volume of the control panel 8 can be increased, and the cooling effect of the control panel 8 can be improved.

Embodiment 3 FIG.
The example which changes the fin pitch of the partial range of the heat exchanger 1 is not restricted to what was shown in Embodiment 1 and Embodiment 2, Configuration of at least one of Embodiment 1 and Embodiment 2 In addition, or separately from the configurations of the first and second embodiments, the fin pitch in the following range of the heat exchanger 1 may be changed. Note that a structure not particularly described in the third embodiment is the same as that in the first or second embodiment, and the same function or structure is described using the same reference numeral.

FIG. 9 is a plan sectional view showing the heat exchanger in the outdoor unit according to Embodiment 3 of the present invention from the side of the propeller fan. The white arrows shown in FIG. 9 indicate the flow of air inside the outdoor unit 101.
The heat exchanger 1 according to the third embodiment is divided into two rows of heat exchanger sections along the air flow direction passing through the heat exchanger 1 (hereinafter, on the upstream side in the air flow direction). The arranged heat exchanger part is referred to as an outer heat exchanger 1b, and the heat exchanger part arranged on the downstream side is referred to as an inner heat exchanger 1a). Moreover, the fin pitch of the inner side heat exchanger 1a which is a part of the heat exchanger 1 is formed larger than the fin pitch of the outer side heat exchanger 1b.

As shown in FIG. 9, the air passing through the heat exchanger 1 and exhausted by the propeller fan 9 first passes through the outer heat exchanger 1b and then passes through the inner heat exchanger 1a. For this reason, assuming that the temperature of the refrigerant flowing inside the heat exchanger 1 is constant, the temperature of the air exchanged in the outer heat exchanger 1b changes, and the air flowing out of the outer heat exchanger 1b 1 The temperature difference with the refrigerant flowing inside is reduced. That is, since the air passing through the inner heat exchanger 1a has a small temperature difference from the refrigerant flowing through the heat exchanger 1 (that is, the inner heat exchanger 1a), the amount of heat exchange becomes small.
For this reason, in this Embodiment 3, the fin pitch of the inner side heat exchanger 1a with little heat exchange amount with air with respect to the outer side heat exchanger 1b is formed large.

As described above, in the outdoor unit 101 configured as in Embodiment 3, by reducing the number of fins inserted in the inner heat exchanger 1a with a small heat exchange amount and a small contribution to the heat exchange performance, The outdoor unit 101 can be reduced in size and price while maintaining equivalent performance.

In the third embodiment, the heat exchanger 1 is divided into two rows of heat exchanger parts along the air flow direction passing through the heat exchanger 1, but in the air flow direction passing through the heat exchanger 1. Of course, the heat exchanger 1 may be divided into three or more rows of heat exchanger sections. At this time, in at least two of these heat exchanger units, the fin pitch of the heat exchanger unit arranged on the downstream side is formed larger than the fin pitch of the heat exchanger unit arranged on the upstream side. Thus, the effect shown in the third embodiment can be obtained.

Here, in Embodiment 3, the outdoor unit 101 including the heat exchanger 1 in which the fin pitch of the inner heat exchanger 1a is formed larger than that of the outer heat exchanger 1b has been described. However, the inner heat exchanger 1a is described. On the other hand, the heat exchanger 1 in which the fin pitch of the outer heat exchanger 1b is formed larger may be mounted on the outdoor unit 101. Such a configuration is a particularly effective means when the outdoor unit 101 is installed in a low outside air environment where frost formation is likely to occur.

When a conventional outdoor unit where the fin pitch of the outer heat exchanger and the inner heat exchanger is the same is installed in a low outdoor environment where frost formation occurs in the heat exchanger, compared to the inner heat exchanger Therefore, the amount of frost formation on the outer heat exchanger increases, and the frost distribution is biased toward the outer heat exchanger. For this reason, in the outer side heat exchanger, the air path between the fins was closed early, and there was a problem that the heating performance of the air conditioner including the outdoor unit was lowered. This is because air first passes through the outer heat exchanger and then passes through the inner heat exchanger, so that the amount of frost formation on the outer heat exchanger having a large absolute humidity of air increases.

For this reason, in the modification of the third embodiment, the fin pitch of the outer heat exchanger 1b having a large amount of frost formation with respect to the inner heat exchanger 1a is formed larger. By configuring the heat exchanger 1 in this way, the frost formation distribution of the inner heat exchanger 1a and the outer heat exchanger 1b can be made uniform, and the closing of the air passage between the fins can be delayed. It becomes possible to improve the heating performance of the air conditioner provided with.

In the modification of the third embodiment, the heat exchanger 1 is divided into two rows of heat exchanger parts along the flow direction of the air passing through the heat exchanger 1, but the air passing through the heat exchanger 1 is divided. Of course, the heat exchanger 1 may be divided into three or more rows of heat exchanger sections along the flow direction. At this time, in at least two of these heat exchanger parts, the fin pitch of the heat exchanger part arranged on the upstream side is formed larger than the fin pitch of the heat exchanger part arranged on the downstream side. That's fine. By comprising in this way, since the frost distribution to the heat exchanger 1 can be made uniform and obstruction | occlusion of the air path between fins can be delayed, the heating performance of the air conditioner provided with the outdoor unit 101 is improved. It becomes possible to make it.

Embodiment 4 FIG.
Further, the example of changing the fin pitch in a partial range of the heat exchanger 1 is not limited to that shown in the first to third embodiments, and is at least one of the first to third embodiments. The fin pitch in the following range of the heat exchanger 1 may be changed together with the above configuration or separately from the configuration of the first to third embodiments. Note that configurations not particularly described in the fourth embodiment are the same as those in the first to third embodiments, and the same functions and configurations are described using the same reference numerals.

FIG. 10 is a plan cross-sectional view showing the heat exchanger in the outdoor unit according to Embodiment 4 of the present invention from the side of the propeller fan.
The heat exchanger 1 according to Embodiment 4 is formed in a U shape in plan view. That is, the heat exchanger 1 includes two bent portions 29 and three straight portions 30 (heat exchanger portions that appear linear in a plan view). And the heat exchanger 1 which concerns on this Embodiment 4 makes the fin pitch of the bending part 29 and the fin pitch of the linear part 30 differ.

In the bending process of the heat exchanger 1, the fins 12 of the bent portion 29 may fall or buckle. In such a case, for example, when the fin pitch of the bent portion 29 of the heat exchanger 1 is made larger than the fin pitch of the linear portion 30, the end of the fin 12 falls or the fin 12 buckles during bending. However, the amount of ventilation of the bent portion 29 can be secured. Further, for example, by making the fin pitch of the bent portion 29 of the heat exchanger 1 smaller than the fin pitch of the straight portion 30, that is, by increasing the number of fins laminated in the bent portion 29, the number of fins 12 per one at the time of bending molding. Can be reduced, the fin 12 can be prevented from falling over and buckling, and the amount of ventilation of the bent portion 29 can be secured.

As described above, by configuring the heat exchanger 1 as in the fourth embodiment, it is possible to secure the air flow rate of the bent portion 29, so that the bent portion 29 can effectively perform heat exchange. For this reason, the heat exchange efficiency of the heat exchanger 1 can be improved, and the energy saving and small outdoor unit 101 can be obtained.

In addition, the following effects can also be acquired by making the fin pitch of the bending part 29 of the heat exchanger 1 larger than the fin pitch of the linear part 30. FIG.

When the heat exchanger 1 is bent into a U-shape in plan view, the fin pitch inside the bent portion 29 is smaller than the outer fin pitch between the fins 12 arranged in the bent portion 29. Moreover, the pillar 36 is installed in the outer peripheral side of the bending part 29 (refer FIG. 1). As a result, the air flow rate of the bent portion 29 is smaller than that of the straight portion 30, and the temperature efficiency distribution is generated between the bent portion 29 and the straight portion 30 (the temperature efficiency is different between the bent portion 29 and the straight portion 30). . In particular, in the case of a conventional heat exchanger in which a heat exchanger having a uniform fin pitch is bent into a U-shape in plan view, the difference in temperature efficiency between the bent portion and the straight portion is the bending of the heat exchanger 1. It becomes larger than the heat exchanger 1 which concerns on this Embodiment 4 which made the fin pitch of the part 29 larger than the fin pitch of the linear part 30. FIG.

Here, the temperature efficiency ε and the heat exchanger performance AK will be described with reference to FIG.
FIG. 11 is a diagram showing the relationship between the temperature efficiency ε and the heat exchanger performance AK. In FIG. 11, the temperature efficiency ε of the heat exchanger 1 according to the fourth embodiment (the heat exchanger 1 in which the fin pitch of the bent portion 29 of the heat exchanger 1 is larger than the fin pitch of the straight portion 30) is black. This is indicated by a filled circle. In addition, the temperature efficiency ε of a conventional heat exchanger (a heat exchanger in which a fin pitch is uniformly formed and bent into a U-shape in plan view) is indicated by a white circle. The heat exchanger 1 according to the fourth embodiment and the conventional heat exchanger have the same total number of fins.

The temperature efficiency ε (= heat exchanger outlet air temperature−heat exchanger inlet air temperature) / (refrigerant saturation temperature−heat exchanger inlet air temperature) is characterized by decreasing as the amount of ventilation increases (when the wind speed increases). . For this reason, in both the heat exchanger 1 according to the fourth embodiment and the conventional heat exchanger, the temperature efficiency (ε2, ε2 ′) of the bent portion is higher than the temperature efficiency (ε1, ε1 ′) of the straight portion. Yes. When attention is paid to the temperature efficiency of the straight portion, when the heat exchanger 1 according to the fourth embodiment and the conventional heat exchanger are manufactured with the same number of fins, the fin pitch of the bent portion 29 is set to the fin of the straight portion 30. The temperature efficiency ε1 ′ of the heat exchanger 1 according to the fourth embodiment that is larger than the pitch is larger than the temperature efficiency ε1 of the linear portion of the conventional heat exchanger. When attention is paid to the temperature efficiency of the bent portion, when the heat exchanger 1 according to the fourth embodiment and the conventional heat exchanger are manufactured with the same number of fins, the fin pitch of the bent portion 29 is set to the fin of the straight portion 30. The temperature efficiency ε2 of the heat exchanger 1 according to the fourth embodiment that is larger than the pitch is smaller than the temperature efficiency ε2 ′ of the linear portion of the conventional heat exchanger.

Here, as shown in FIG. 11, the heat exchanger performance AK (heat transfer performance) and the temperature efficiency ε are characterized in that the temperature efficiency ε gradually approaches 1 as the heat exchanger performance AK increases. For this reason, in the straight portion where the air flow rate is large, the heat exchanger 1 according to the fourth embodiment is improved in temperature efficiency by ε1′−ε1 because the fin pitch is smaller than that of the conventional heat exchanger. To do. Further, in a bent portion with a small air flow rate, the heat exchanger 1 according to the fourth embodiment has a fin pitch larger than that of the conventional heat exchanger, so that the temperature efficiency is reduced by ε2′−ε2. .

However, the temperature efficiency (ε1, ε1 ′) of the straight portion is smaller than the temperature efficiency (ε2, ε2 ′) of the bent portion, and the temperature efficiency ε gradually approaches 1 as the heat exchanger performance AK increases. It has characteristics. For this reason, the improvement (ε1′−ε1) of the temperature efficiency due to the configuration of the heat exchanger as in the fourth embodiment is increased, and the heat exchanger is configured as in the fourth embodiment. The decrease in temperature efficiency (ε2′−ε2) is very small.
That is, (ε1′−ε1)> (ε2′−ε2).

Therefore, as in the fourth embodiment, the average pitch of the heat exchanger 1 is increased by increasing the fin pitch of the bent portion 29 having a high temperature efficiency ε and decreasing the fin pitch of the straight portion 30 having a low temperature efficiency ε. Temperature efficiency, that is, the heat exchange efficiency of the entire heat exchanger 1 is greatly improved.

Embodiment 5 FIG.
Further, the example of changing the fin pitch in a partial range of the heat exchanger 1 is not limited to that shown in the first to fourth embodiments, and is at least one of the first to fourth embodiments. The fin pitch in the following range of the heat exchanger 1 may be changed together with the above configuration or separately from the configuration of the first to fourth embodiments. Note that configurations not particularly described in the fifth embodiment are the same as those in the first to third embodiments, and the same functions and configurations are described using the same reference numerals.

FIG. 12 is a front view showing the internal structure of the outdoor unit according to Embodiment 5 of the present invention. In addition, in FIG. 12, illustration of things other than the heat exchanger 1 and the propeller fan 9 is abbreviate | omitted.
The heat exchanger 1 according to the fifth embodiment is arranged in a three-stage heat exchanger section (first-stage heat exchanger 2, second-stage heat exchanger 3, third-stage heat exchanger 4) in the vertical direction. It is divided. The fin pitch 33 of the third stage heat exchanger 4 is formed larger than the fin pitch 32 of the second stage heat exchanger 3, and the fin pitch 32 of the second stage heat exchanger 3 is the first stage heat exchange. It is formed with a fin pitch 31 or more of the vessel 2.

A book in which the heat exchanger 1 is provided facing the suction port 34a formed in the side surface portion of the housing 34 and the propeller fan 9 is provided facing the air outlet 34b formed in the upper surface portion of the housing 34. In the outdoor unit 101 according to Embodiment 1, the air volume passing through each part of the heat exchanger 1 varies depending on the distance from the propeller fan 9. Specifically, the air volume passing through the third stage heat exchanger 4 is smaller than the air volume passing through the first stage heat exchanger 2. For this reason, in this Embodiment 5, the fin pitch of the 3rd-stage heat exchanger 4 with little heat exchange amount with air with respect to the 1st-stage heat exchanger 2 is formed large.

As described above, by reducing the number of fins inserted in the third stage heat exchanger 4 with a small air volume and a small contribution to the heat exchange performance, the air conditioner can be reduced in size while maintaining the same performance as before. Lower prices are possible.

In Embodiment 5, the heat exchanger 1 is divided into three stages of heat exchanger parts in the upper limit direction, but the heat exchanger 1 may be divided into two stages of heat exchanger parts, Of course, the exchanger 1 may be divided into four or more heat exchanger sections. At this time, in at least two of these heat exchanger parts, if the fin pitch of the heat exchanger part disposed below is formed smaller than the fin pitch of the heat exchanger part disposed above, The effects shown in the fifth embodiment can be obtained.

In the first to fifth embodiments described above, the present invention has been described by taking the outdoor unit 101 in which the air outlet 34b is formed on the upper surface of the housing 34 as an example. However, the air outlet is provided on the side surface of the housing. Even if the present invention is applied to the formed outdoor unit, the effects described in the first to fifth embodiments can be obtained.

In the first to fifth embodiments described above, the present invention has been described by taking the U-shaped heat exchanger 1 in plan view as an example, but the shape of the heat exchanger is arbitrary, and the heat exchanger The effects shown in the first to fifth embodiments can be obtained regardless of the shape.

In the first to fifth embodiments described above, the present invention has been described by taking the outdoor unit 101 including one heat exchanger 1 (consisting of a plurality of heat exchanger units) as an example. Even in an outdoor unit including a plurality of heat exchangers 1, the effects described in the first to fifth embodiments can be obtained.

In the first to fifth embodiments described above, the present invention has been described by taking the outdoor unit 101 including the propeller fan 9 as an example. However, the present invention is also implemented in an outdoor unit including a fan other than the propeller fan 9. The effects described in the first to fifth embodiments can be obtained.

In Embodiments 1 to 5 described above, the present invention has been described by taking the outdoor unit 101 as an example, but it is of course possible to implement the present invention in an indoor unit.

1 heat exchanger, 1a inner heat exchanger, 1b outer heat exchanger, 2nd stage heat exchanger, 3rd stage heat exchanger, 4th stage heat exchanger, 5 compressor cover adjacent range, 6 compression Machine non-adjacent range, 7 compressor cover, 8 control panel, 9 propeller fan, 10 heat transfer tube, 12 fin, 13 notch, 14 collar, 15 pilot hole, 16 thin plate feed operation, 17 fin series, 18 cutting operation, 19 Movement / rotation operation, 21 pitch feed operation, 22 fin group, 23 fin group, 24 fin group assembly part, 25 end part, 29 bending part, 30 straight part, 31 fin pitch of first

stage heat exchanger

2, 32 Fin pitch of the second

stage heat exchanger

3, 33, fin pitch of the third

stage heat exchanger

4, 34 housing, 34a suction port, 34b outlet, 35a upper surface portion, 35b bottom Parts, 36 pillars, 37 panel, 38 fan guard, 101 outdoor unit.

Claims

A plurality of fins stacked via a predetermined fin pitch;
A plurality of heat transfer tubes disposed along a longitudinal direction of the fins at a predetermined interval and penetrating the fins along the laminating direction;
With
The plurality of heat transfer tubes are heat transfer tubes having a flat cross section,
The plurality of fins are formed with a plurality of cutouts in a shape corresponding to the cross-sectional shape of the heat transfer tube at an end on the longitudinal direction side,
A collar is formed on the edges of the plurality of notches,
The heat transfer tubes are inserted into the notches,
The fin pitch between some of the plurality of fins is larger than the fin pitch between the other fins,
The heat exchanger according to claim 1, wherein at least the large fin pitch is larger than a height of the collar which is an amount of protrusion of the collar from a plate surface of the fin.
A housing in which an inlet and an outlet are formed;
The heat exchanger according to claim 1 provided in the housing,
An air conditioner comprising: a fan provided in the housing.
In the case, a stored item is accommodated in an air path between the heat exchanger and the fan,
The heat exchanger is
The air conditioner according to claim 2, wherein a fin pitch in a range in which a distance from the housing portion is within a predetermined distance is the large fin pitch.
The housing has the suction port formed in at least one side surface portion, and a blowout port formed in an upper surface portion.
The heat exchanger is provided to face the suction port,
The fan is a propeller fan, and is provided to face the outlet.
When the diameter of the propeller fan is D and the distance between the heat exchanger and the accommodation is L,
The heat exchanger is
The air conditioner according to claim 3, wherein a fin pitch in a range satisfying L / D ≦ 0.15 is the large fin pitch.
When the large fin pitch is fp2 and the fin pitch between the other fins is fp1,
In the heat exchanger, fp2 is set so that the coefficient of performance is 95% or more with respect to the heat exchanger in which the fin pitch of the fin in the range where the fin pitch in the heat exchanger is fp2 is formed at fp1. The air conditioner according to claim 3 or 4, wherein the air conditioner is provided.
The container is a control panel, and the control panel is provided on one side surface of the casing.
The suction port is formed at least in a side surface portion adjacent to a side surface portion of the housing in which the control panel is disposed,
The heat exchanger is provided to face the suction port,
The air conditioner according to any one of claims 2 to 5, wherein a fin pitch at an end portion on the control panel side of the heat exchanger is the large fin pitch.
The heat exchanger is divided into a plurality of heat exchanger sections along the direction of air flow through the heat exchanger,
At least one of the plurality of the divided heat exchanger units is configured such that the fin pitch of the heat exchanger unit arranged on the downstream side is larger than the fin pitch of the heat exchanger unit arranged on the upstream side. The air conditioner according to claim 2, wherein the air conditioner is large.
The heat exchanger is divided into a plurality of heat exchanger sections along the direction of air flow through the heat exchanger,
At least one of the plurality of the divided heat exchanger parts has a fin pitch of the heat exchanger part arranged on the upstream side than a fin pitch of the heat exchanger part arranged on the downstream side. The air conditioner according to claim 2, wherein the air conditioner is large.
A bent portion is formed in the heat exchanger,
The air conditioner according to claim 2, wherein a fin pitch between the fins arranged in the bent part is larger than a fin pitch between the fins arranged in the straight part.
A bent portion is formed in the heat exchanger,
The air conditioner according to claim 2, wherein a fin pitch between the fins arranged in the straight portion is larger than a fin pitch between the fins arranged in the bent portion.
The housing has the suction port formed in at least one side surface portion, and a blowout port formed in an upper surface portion.
The fan is a propeller fan, and is provided to face the outlet.
The heat exchanger is provided to face the suction port, and is divided into a plurality of heat exchanger parts in the vertical direction,
At least one of the plurality of the divided heat exchanger sections has a fin pitch of the heat exchanger section disposed below that larger than a fin pitch of the heat exchanger section disposed above. The air conditioner according to claim 2, wherein the air conditioner is provided.
The heat exchanger according to claim 1, wherein the fin and the heat transfer tube are fixed by brazing or bonding.