JP2002005545A - Accumulator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an accumulator in which a pressure loss of a refrigerant flowing in the inside can be reduced, while the function of the accumulator is fully developed by carrying out completely the gas-liquid separation. SOLUTION: A refrigerant intake port 10 and a refrigerant outlet port 11 are provided in a header 3 above a tank 2. A discharge port 13 at one end of a suction pipe 4 placed in the intake 2 is connected in communication with the outlet port 11, a suction port 12 at the other end of the pipe 4 is opened at the upper part in the tank 2. A defroster 5 is provided between the suction port 12 and the refrigerant intake port 10. A shielding wall 5a of the defroster is made visible from the outside partly in the opening face of the port 10, when the inside of the tank 2 is observed through the intake port 10.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a car air conditioner,
The present invention relates to an accumulator used for a refrigeration cycle of a room air conditioner or the like.

[0002]

2. Description of the Related Art A conventional accumulator is, for example, shown in FIG.
As shown in FIG. 1, a suction pipe (104) bent in a U-shape is provided in a tank (101) for gas-liquid separation of the refrigerant evaporated in the evaporator.
4) The upper end discharge port is connected to the refrigerant outlet port (108), and the upper end suction port is opened at the upper part in the tank. Also, an umbrella-shaped defroster (120)
Is disposed in the upper portion of the tank (101) so as to cover the upper end suction port of the pipe (104), and the gas-liquid mixed refrigerant containing the lubricating oil flowing from the refrigerant inlet port (107) is supplied to the pipe (104). The defroster (120) is sprayed.

[0003] Among the refrigerant blown to the defroster (120), the lubricating oil and the liquid refrigerant having a large specific gravity among them flow down along the defroster (120) and are stored in the tank bottom. On the other hand, the gaseous refrigerant is drawn from the upper end suction port of the U-shaped suction pipe (104), discharged from the refrigerant outlet port (108), and drawn into the compressor.

[0004]

In the above-described conventional accumulator, as shown in FIG.
20) obstructs the flow of the refrigerant sucked from the refrigerant inlet port (107), so that there is a problem that the flow resistance of the refrigerant is large and the pressure loss of the refrigerant flowing inside becomes large.

On the other hand, if the defroster (120) is arranged in such a manner as not to block the flow of the refrigerant sucked from the refrigerant inlet port (107) in order to reduce the flow resistance of the refrigerant, the defroster (120) has the same structure as that of the defroster (120). Since the original function is not exhibited, that is, the gas-liquid separation is not effectively performed, it is necessary to sufficiently perform the gas-liquid separation to fully exert the accumulator function, and the pressure loss of the refrigerant flowing through the inside It has been difficult to reduce the size and to achieve both.

The present invention has been made in view of the above technical background, and reduces the pressure loss of the refrigerant flowing inside while sufficiently performing the gas-liquid separation and fully exerting the accumulator function. It is an object of the present invention to provide an accumulator that can be used.

[0007]

Means for Solving the Problems In order to achieve the above object, the present inventors have made intensive studies and determined that the relative arrangement relationship between the refrigerant inlet port and the defroster is specified, that is, from the refrigerant inlet port to the tank. When looking inside, it has been found that the desired accumulator can be formed by arranging the both so that the shielding wall of the defroster appears in part, but not all, of the opening surface of the refrigerant inlet port, The present invention has been completed.

That is, in the accumulator of the present invention, a refrigerant inlet port and a refrigerant outlet port are provided in a header provided at an upper end portion of a tank, a suction pipe is disposed in the tank, and a discharge pipe at one end of the suction pipe is provided. While the outlet is connected to the refrigerant outlet port, the suction port at the other end of the suction pipe is opened at the upper part in the tank, and a defroster is arranged between the suction port and the refrigerant inlet port, and the refrigerant inlet port is The shield wall of the defroster is made to appear at a part of the opening surface of the refrigerant inlet port when the inside of the tank is viewed through the tank.

A shield wall of the defroster is arranged so as to be visible at a part of the opening surface of the refrigerant inlet port, and the flow of the refrigerant from the refrigerant inlet port extends in a direction extending inward from the remainder of the opening surface into the tank. Since there is no shielding wall that largely blocks the flow, the flow resistance of the refrigerant is reduced, and the pressure loss of the refrigerant flowing inside can be reduced. In addition, since the defroster shielding wall is arranged so as to be visible in a part of the opening surface, the refrigerant is sprayed on the shielding wall, thereby sufficiently performing gas-liquid separation, and without any effect of the accumulator function. Can be demonstrated.

The opening area of the refrigerant inlet port is 40 to 8
It is preferable that the shielding wall of the defroster be configured to have an external appearance at 5%. With such an arrangement, the pressure loss of the refrigerant flowing through the inside can be reduced while performing gas-liquid separation more sufficiently. It can be further reduced.

Preferably, the shape of the defroster is a cup-like shape, and the shielding wall is arranged in a manner substantially perpendicular or perpendicular to the direction of flow of the refrigerant from the refrigerant inlet port. Since the arrangement is such that the flow of the refrigerant is largely blocked, gas-liquid separation can be performed more reliably.

Further, a part of the peripheral side wall of the defroster is arranged along the outer half of the peripheral wall on the suction end side of the suction pipe so as to be closer to the outer half. This is preferable in that a refrigerant having a high flow rate can be sucked and suction at a high flow rate can be performed.

Preferably, a pressure balance hole is provided on the discharge port side of the suction pipe, and a distance from a center position of the pressure balance hole to a top surface position of the header is set to 50 mm or less. By providing the pressure balance hole at such a position, when the compressor is stopped, it is possible to reliably prevent the liquid from flowing into the compressor due to the siphon phenomenon, and to reduce the liquid refrigerant present in the pipe connecting the accumulator and the compressor to the accumulator tank. Can be returned inside. Further, even when the refrigerant is overfilled in the tank, the vaporized refrigerant sucked into the pipe from the pressure balance hole and the low-dryness refrigerant sucked into the pipe from the oil return hole are mixed well. Since the mixed refrigerant can be discharged to the compressor, it is possible to avoid discharging only the liquid refrigerant to the compressor.
As described above, in any state during the stop of the compressor and during the operation, it is possible to avoid adverse effects (such as failure) on the compressor due to the suction of the liquid refrigerant. Further, when the amount of the liquid refrigerant in the tank increases, it is possible to prevent the liquid refrigerant from flowing into the pipe through the pressure balance hole.

Further, the distance La from the upper surface of the bottom wall of the tank to the suction port of the suction pipe and the distance Lb from the upper surface of the bottom wall of the tank to the center of the pressure balance hole.
And the distance Lc from the upper surface position of the tank bottom wall to the lower surface position of the suction pipe discharge port fixing portion in the header, the relationship of La ≦ Lb ≦ Lc is established from the pressure balance hole. In that the vaporized refrigerant sucked into the pipe and the low-dryness refrigerant sucked into the pipe from the oil return hole can be mixed more favorably,
More preferred.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the accumulator according to the present invention will be described below with reference to the drawings. Figure 1
And an aluminum accumulator (1) shown in FIG. 2 is used for a refrigeration cycle for a car cooler, (2) is a tank, (3) is a header,
(4) is a suction pipe, and (5) is a defroster.

The tank (2) is, as shown in FIG.
It is a cylindrical shape with a bottom having a predetermined height, and its upper end opening is closed by a header (3). The header (3) is provided with a refrigerant inlet port (10) and a refrigerant outlet port (11), and the flow direction of the refrigerant in each port (10) (11) is up and down (axial direction of the tank).
It is arranged so that it becomes.

A suction pipe (4) bent in a substantially U-shape is disposed in the tank (2).
The discharge port side end of the suction pipe (4) is connected to the refrigerant outlet port (11) by being caulked and fixed to the inner wall of the refrigerant outlet port (11). On the other hand, the suction port (12) at the other end of the suction pipe (4) is open at the upper part in the tank (2).

An oil return hole (52) is formed at the bottom of the bottom of the suction pipe (4) (see FIG. 5), so that the lubricating oil accumulated in the accumulator is returned to the oil return hole. (52) It is possible to return to the compressor.

Further, at the bottom of the suction pipe (4),
A substantially cylindrical strainer (14) is externally fitted and fixed. The strainer (14) has a mesh body (18) such as a nylon mesh attached to a plurality of openings provided on the outer peripheral wall thereof, and flows down from the oil return hole (52). It is provided to remove foreign substances and the like in the lubricating oil.

Further, as shown in FIGS. 2 (b) and 3, a pressure balance hole (53) which opens inward is formed in a part of the peripheral wall at the distal end of the suction pipe (4) on the discharge port side. Has been drilled. This pressure balance hole (53) makes the pressure of the entire accumulator always uniform when the compressor is stopped,
This is to prevent the liquid from flowing to the compressor due to the siphon phenomenon.

A desiccant unit (20) is provided in a central space surrounded by the left and right tubular portions of the suction pipe (4). A desiccant (21) is held inside the desiccant unit (20) (see FIG. 2B), and a large number of small holes (20a) are formed on the outer wall of the unit (20) over substantially the entire surface. Are formed in a dispersed state (FIG. 1).
), So that the refrigerant can flow inside the desiccant unit (20).

An inverted cup-shaped defroster (5) is disposed between the suction port (12) of the suction pipe (4) and the refrigerant inlet port (10) so as to cover the suction port (12). I have. As shown in FIG. 6 (a), the defroster (5) has a curved side wall on the right side extending vertically downward with respect to the shielding wall (5a) as the bottom wall, as viewed from the front, while the left side on the left side. The curved plate-like side wall has a shape extending in a direction slightly opened outward from the vertically lower portion. A pipe fitting hole (30) is formed in a substantially right half of the shielding wall (5a), and a tip of the suction pipe (4) on the discharge port (13) side is formed in the fitting hole (30). It is fitted in a compatible inner fitting state (see FIG. 2B).

As shown in FIG. 6B, a left curved side wall (5b) on the peripheral side wall of the defroster (5).
The first locking projection (31) is formed to protrude inward from the boundary between the first flattened side wall and the front flat side wall, while the left curved side wall (5b) and the rear flat side wall of the same circumferential side wall are formed. A second locking projection (32) is formed so as to protrude inward from a boundary portion of the left side, and a third locking projection (32) is formed inwardly from a central portion of the left curved plate-like side wall (5b). The projection is formed.

As shown in FIG. 6C, each of the first locking projections (31) and the second locking projections (32) is provided with a step (31a) (32a) at the center in the longitudinal direction. ) Is formed, and has flat end portions (31b) and (32b) whose protruding heights are reduced in the end direction, respectively, and the interval between these two end portions (31b) and (32b) is The outer diameter of the front end of the suction pipe (4) on the side of the suction port (12) substantially matches the outer diameter of the front end of the suction pipe (4).
b) and the central portion of the left curved side wall (5b).
The distal end of the suction pipe (4) on the side of the suction port (12) is fitted and fixed between the locations so as to be in a properly fitted state (see FIGS. 3 and 4). Further, the leading edge of the suction pipe (4) on the side of the suction port (12) abuts on the step portions (31a) and (32a) and is locked, and is fixed in an expected positioning state. Note that (31c) and (32c) are provided at the tip (31) of the suction pipe (4) in order to facilitate the fitting operation.
b) A tapered portion provided at the tip of (32b). Further, as shown in FIGS. 6 (b) and 6 (c), the contact surfaces of the tips (31b) and (32b) with the pipe (4) can easily perform the fitting operation of the suction pipe (4). In order to make it so, it is formed on an inclined surface.

The third locking projection (33) is formed such that its leading edge on the suction port (12) side of the suction pipe (4) has the projection (3).
This is provided so that the suction pipe (4) can be fixed in a predetermined positioning state in the same manner as described above by being brought into contact with the leading edge (33a) of (3) and locked (FIG. 2).
(B)).

As described above, the defroster (5) is fitted and fixed to the tip of the suction pipe (4) on the side of the discharge port (13), and is located on the side of the suction port (12) of the pipe (4). Since it is fixed in an expected positioning state, the fixing is reliably performed. In the case of the conventional product, only one end of the suction pipe is inserted into the defroster, so that the defroster is not securely fixed and the fixing position is not stable. Thus, the defroster can be securely fixed.

The relative arrangement relationship between the defroster (5) and the refrigerant inlet port (10) is configured to have the following specific arrangement relationship. That is, when the inside of the tank (2) is viewed through the refrigerant inlet port (10), the shielding wall (5a) of the defroster (5) is made to appear at a part of the opening surface of the refrigerant inlet port (10). (See FIG. 2A). Since the shielding wall (5a) of the defroster is arranged so as to appear only at a part of the opening surface of the refrigerant inlet port (10), the direction extending from the remaining portion (Z) of the opening surface toward the inside of the tank. There is a shielding wall (5) which largely blocks the flow of the refrigerant from the refrigerant inlet port (10).
a) does not exist, that is, in the present embodiment, in the direction extending from the remaining portion (Z) of the opening surface to the inside of the tank, there is a left curved plate-like side wall (5b) extending substantially along the extension direction. Therefore, the flow resistance of the refrigerant is reduced, and the pressure loss of the refrigerant flowing inside can be reduced.

On the other hand, since the shielding wall (5a) of the defroster (5) is arranged so as to be visible at a part of the opening surface of the refrigerant inlet port (10), the gas-liquid separation can be sufficiently performed. Thus, the accumulator function can be fully exhibited. In particular, in the present embodiment, since the shielding wall (5a) is arranged in a mode orthogonal to the direction of flow of the refrigerant from the refrigerant inlet port (10), the flow of the refrigerant at the shielding wall (5a) portion is increased. It is possible to block, and the gas-liquid separation can be performed more reliably.

It should be noted that the description that "the defroster shielding wall appears on a part of the opening surface of the refrigerant inlet port when the inside of the tank is viewed through the refrigerant inlet port" is described in FIG.
As shown by the two-dot chain line in (b), the refrigerant inlet port (1
0) means that the outer edge of the opening surface is exposed as it is in a part of a region extending inward in parallel with the axial direction of the inlet port (10) (the flow direction of the refrigerant from the refrigerant inlet port) as it is. It is.

It is preferable that the shield wall (5a) of the defroster is formed so as to have an appearance at 40 to 85% of the opening area of the refrigerant inlet port (10). 40%
If it is less than 85%, it becomes difficult to sufficiently perform gas-liquid separation, and if it exceeds 85%, the relaxation of the flow resistance of the refrigerant becomes insufficient and the pressure loss of the refrigerant flowing inside increases, which is not preferable. . In addition, in this embodiment, it is comprised so that the shielding wall (5a) of a defroster may be shown in 78% of the opening area of a refrigerant inlet port (10).

In this embodiment, as shown in FIG. 4, the left side wall (5) of the defroster (5)
b) is disposed along and close to the outer half portion (40) of the peripheral wall on the suction port (12) side of the suction pipe (4) (the two (5b) and (40)). (Except for the parts that are in linear contact in the vertical direction at the center). By arranging in such a close state, gas-liquid separation can be reliably performed, so that a refrigerant having a high degree of dryness can be sucked from the suction port, and there is an advantage that suction at a high flow rate can be performed.

In the above embodiment, the shielding wall (5a) is formed in a flat plate shape. However, the present invention is not limited to this, and may be, for example, a curved plate shape. Further, in the above embodiment, the shielding wall (5a) is configured by the bottom wall of the defroster, but is not particularly limited to such a configuration, and the shielding wall is configured by the side wall of the defroster. It may be made to be. However, from the viewpoint of sufficiently performing the gas-liquid separation, it is desirable that the shielding wall (5a) is constituted by the bottom wall of the defroster (5) as in the above embodiment.

The angle θ between the shielding wall (5a) and the flow direction of the refrigerant from the refrigerant inlet port is 60 ° ≦ θ ≦ 9.
It is preferable that the angle is set in the range of 0 °. The angle α between the side wall (5b) and the flow direction of the refrigerant from the refrigerant inlet port is preferably set to 30 ° or less.

The tank (2) and the header (3)
Can be made of a metal material having good formability, such as aluminum or an aluminum alloy. Further, the defroster (5) can be suitably manufactured from a synthetic resin material such as a polyamide resin. Further, the desiccant unit (20) can be suitably manufactured by a cloth pack or the like.

In the accumulator (1), the liquid / gas mixed refrigerant evaporated in the evaporator flows into the tank (2) through the refrigerant inlet port (10) of the header (3). And the refrigerant inlet port (1
Part of the refrigerant flowing in from 0) is blown against the shielding wall (5a) of the defroster, whereby the gas-liquid separation is sufficiently performed, while the remaining refrigerant flowing in the defroster becomes an obstacle in the flow direction. (Although the left curved plate-like side wall (5b) is visible, but extends substantially in the direction along which the refrigerant flows, it cannot substantially become an obstacle). Since the refrigerant flows, the flow resistance of the refrigerant is reduced, and the pressure loss of the refrigerant flowing inside can be reduced.

The gaseous refrigerant passes through the desiccant unit (20), is introduced into the suction pipe (4) through the suction port (12), and flows through the pipe (4). It flows out of the outlet port (11) and is sucked into the compressor. At this time, the moisture contained in the refrigerant is removed by the desiccant (21). On the other hand, the liquid refrigerant and the lubricating oil are sprayed on the defroster (5), then fall down in the tank (2), and are stored at the bottom of the tank (2). The gas-liquid separation is sufficiently performed by such a mechanism, and only the gas refrigerant can be sent to the compressor.

In the present invention, the pressure balance holes (5
3) is provided on the discharge port (13) side of the suction pipe (4), and the distance (X) from the center position of the pressure balance hole (53) to the upper surface position of the header (3) is set to 50 mm or less. It is preferred that Pressure balance hole (5
By providing 3) at such a position, when the compressor is stopped, it is possible to reliably prevent the liquid from flowing into the compressor due to the siphon phenomenon, and to reduce the liquid refrigerant present in the pipe connecting the accumulator and the compressor to the inside of the accumulator tank. Even when the refrigerant is overfilled in the tank, the vaporized refrigerant sucked into the pipe (4) from the pressure balance hole (53) and the pipe (from the oil return hole (52)) 4) It is possible to mix the refrigerant with a low-dryness refrigerant sucked in well and discharge this mixed refrigerant to the compressor, so that it is possible to avoid that only the liquid refrigerant is discharged to the compressor. The adverse effect on the compressor due to the suction of liquid refrigerant (failure, etc.) can be prevented both when the compressor is stopped and when the compressor is operating. It can be. In addition, since the pressure balance hole (53) exists at a position 50 mm or less from the upper surface position of the header (3), even when the amount of the liquid refrigerant in the tank (2) increases, the pressure balance hole (5) is formed.
The liquid refrigerant can be prevented from flowing into the pipe (4) from 3). In particular, the distance (X) from the center position of the pressure balance hole (53) to the upper surface position of the header (3) is:
More preferably, it is set to 28 to 38 mm.

Further, a distance La from the upper surface position of the bottom wall of the tank (2) to the suction port (12) of the suction pipe (4).
And the distance Lb from the upper surface position of the bottom wall of the tank (2) to the center position of the pressure balance hole (53), and the fixing portion (37) of the suction pipe discharge port in the header (3) from the upper surface position of the bottom wall of the tank (2). It is more preferable that the relationship of La ≦ Lb ≦ Lc be established between the distance Lc and the distance Lc to the lower surface position. When the above relationship is satisfied, even when the refrigerant is overfilled in the tank (2), the vaporized refrigerant sucked into the pipe (4) from the pressure balance hole (53) and the oil return hole (52) The refrigerant with a lower dryness sucked into the pipe (4) can be mixed more favorably and the mixed refrigerant can be discharged to the compressor. Therefore, it is ensured that only the liquid refrigerant is discharged to the compressor. Can be avoided.

When the suction port (12) of the suction pipe is inclined, the above-mentioned “La” is changed from the upper surface position of the bottom wall of the tank (2) to the suction port (12) of the suction pipe (4).
, The distance to the center position.

FIG. 7 (b) shows a refrigerant outlet port (11) of an accumulator according to another embodiment of the present invention and its vicinity, and shows a discharge port side of a suction pipe (4) and a refrigerant outlet port. The mode of communication connection with (11) is different from that of the above-described embodiment, and other configurations are the same as those of the above-described embodiment. That is, in this embodiment, the discharge port side of the suction pipe (4) and the refrigerant outlet port (1)
The communication connection with 1) is performed as follows. First, the tip of the suction pipe (4) on the discharge port side is connected to the refrigerant outlet port (1).
Insert in 1). At this time, a ridge (50) formed by beading on the peripheral wall of the suction port (4) on the discharge port side has an inwardly protruding portion (11a) of the outlet port (11).
, So that positioning at the time of insertion and placement can be reliably performed (see FIG. 7A). Next, a pipe expanding punch (70) is inserted from the outside into the refrigerant outlet port (11) to expand the discharge port side tip of the suction pipe (4) to form a tip expanding section (51).
The inwardly protruding portion (11a) is clamped and fixed between the distal end expanding portion (51) and the protruding ridge (50) (FIG. 7 (b)).
reference). Since the communication port is connected and connected in such a sandwiched fixed state, the discharge port side of the suction pipe (4) does not come out of the refrigerant outlet port (11), so that an accumulator that is more excellent in pipe-preventing property can be configured. Can be done.

FIG. 8 is a view showing a header in an accumulator according to still another embodiment. The configuration of this header is different from that of the first embodiment, and other configurations are the same as those of the first embodiment. Same as the form.
That is, the header (3B) is a forged product, and the shape and arrangement of the ports (10) and (11) in the header (3B) are as shown in FIGS. 10) They are arranged so that the cross-sectional shapes of (11) are the same and they are symmetrical in plan view.
By designing the two ports (10) and (11) in such a shape and arrangement, the flow of the material at the time of forging becomes smooth, and the occurrence of sink marks in the header (3B) can be surely prevented. The generation can be sufficiently prevented.

FIG. 9 is a sectional view showing a strainer and its vicinity in an accumulator according to still another embodiment. The structure of the strainer is different from that of the first embodiment. This is the same as the first embodiment. That is, in this embodiment, the strainer (14B) is a pair of strainer halves (1) having a form divided into two by a plane including the axis of the insertion hole (14a).
5) (15) is integrated in a facing state. That is, as shown in FIG. 10, this strainer half (1)
5) One of the divided surfaces (15a) is provided with a fitting projection (16).
On the other hand, a fitting hole (17) is formed in the other divided surface (15b), and a pair of strainer halves (1) are formed.
5) and (15) are arranged with the divided surfaces facing each other with the bottom of the suction pipe (4) interposed therebetween.
6) are fitted into the other fitting holes (17), respectively, so that the cylindrical bottom of the suction pipe (4) is inserted and arranged in the insertion hole (14a). (15) is an integrated one (see FIG. 9).

With this configuration, it is not necessary to push the pipe from the tip end thereof into the insertion hole of the strainer, so that the setting work becomes very simple and easy, and the pushing work is eliminated. This has the advantage that cracks and the like due to friction between the pipe and the strainer can be effectively prevented, and an even higher quality accumulator can be provided. Further, in the case of the strainer composed of the strainer body and the lid, two molds are required for manufacturing the strainer. In the strainer (14B) of this embodiment, the strainer half (1) is used.
Only one mold corresponding to 5) is required, and there is an advantage that the manufacturing cost can be greatly reduced. Furthermore, in the strainer composed of the strainer main body and the lid, a step of welding the main body and the lid is required. In the strainer (14B) of this embodiment, the fitting projection (16) is fitted. Since the pair of strainer halves (15) and (15) can be integrated simply by being fitted into the joint hole (17), the productivity is also excellent.

In each of the above embodiments, the refrigerant inlet port (10) and the refrigerant outlet port (11) are formed along the vertical direction of the tank (2), respectively. It is not limited to this.

[0045]

As described above, the accumulator according to the present invention is arranged so that the defroster shielding wall can be seen at a part of the opening surface of the refrigerant inlet port, and from the remaining portion of the opening surface to the inside of the tank. Since there is no shielding wall in the extended direction that largely blocks the flow of the refrigerant from the refrigerant inlet port, the flow resistance of the refrigerant is reduced, and the pressure loss of the refrigerant flowing inside can be reduced. on the other hand,
Since the shielding wall of the defroster is arranged so as to be visible in a part of the opening surface, the refrigerant is sprayed on the shielding wall, thereby sufficiently performing gas-liquid separation and fully exerting the accumulator function. Can be. As described above, the present invention makes it possible to sufficiently perform gas-liquid separation and reduce the pressure loss of the refrigerant, but without providing a new special mechanism for that purpose, Since the relative arrangement between the refrigerant inlet port and the defroster only needs to be the specific one described above, there is an advantage that the configuration can be made at low cost.

40 to 85% of the opening area of the refrigerant inlet port
In this case, when the shielding wall of the defroster is configured to be visible, the pressure loss of the refrigerant can be further reduced while performing gas-liquid separation more sufficiently.

When the shape of the defroster is cup-shaped and the shielding wall is arranged in a manner substantially orthogonal or orthogonal to the direction of flow of the refrigerant from the refrigerant inlet port, the gas-liquid separation is improved. It can be performed reliably.

When a part of the peripheral side wall of the defroster is disposed along and close to the outer half of the peripheral wall on the suction end side of the suction pipe, the degree of dryness is lower than that of the suction port. There is an advantage that a high refrigerant can be sucked and suction at a high flow rate can be performed.

When a pressure balance hole is provided on the discharge port side of the suction pipe, and the distance from the center position of the pressure balance hole to the upper surface position of the header is set to 50 mm or less, when the compressor is stopped, the Can be reliably prevented from flowing into the compressor, and the liquid refrigerant present in the pipe connecting the accumulator and the compressor can be returned into the tank. Since the vaporized refrigerant to be sucked and the low-dryness refrigerant sucked up from the oil return hole can be mixed well and the mixed refrigerant can be discharged to the compressor, only the liquid refrigerant is discharged to the compressor. With these actions, the liquid refrigerant can be sucked regardless of whether the compressor is stopped or operating. That adverse effects to the compressor (failure or the like) can be avoided. Further, even when the amount of the liquid refrigerant in the tank increases, it is possible to prevent the liquid refrigerant from flowing into the pipe from the pressure balance hole.

Further, a distance La from the upper surface position of the bottom wall of the tank to the suction port of the suction pipe and a distance Lb from the upper surface position of the bottom wall of the tank to the center position of the pressure balance hole.
And a distance Lc from the upper surface position of the tank bottom wall to the lower surface position of the suction pipe discharge port fixing portion in the header, when the relationship of La ≦ Lb ≦ Lc holds, only the liquid refrigerant is discharged to the compressor. Can be reliably avoided.

[Brief description of the drawings]

FIG. 1 is a front view of an accumulator according to an embodiment of the present invention, in which a part of an outer wall is cut away.

FIG. 2A is a plan view of the accumulator,
(B) is a sectional view taken along the line II-II in (A).

FIG. 3 is a sectional view taken along line III-III in FIG. 1;

FIG. 4 is a sectional view taken along line IV-IV in FIG. 1;

FIG. 5 is a view taken along line VV in FIG. 1;

6A and 6B are views showing a defroster, wherein FIG. 6A is a front view, FIG. 6B is a bottom view, and FIG. 6C is a cross-sectional view taken along line VI-VI in FIG.

FIG. 7 is a process diagram for forming a communication connection structure between a suction pipe and a refrigerant outlet port in an accumulator according to another embodiment, in which (a) shows a state in which a pipe tip is inserted and arranged in an outlet port; (B) is a cross-sectional view showing a communication connection state after pipe expansion by the pipe expansion punch.

FIG. 8 is a view showing a header in an accumulator according to still another embodiment, wherein (A) is a plan view,
(B) is a sectional view taken along line VII-VII in (A).

FIG. 9 is a side sectional view showing a strainer and its vicinity in an accumulator according to still another embodiment.

FIGS. 10A and 10B are diagrams illustrating a strainer half, wherein FIG. 10A is a front view, FIG. 10B is a right side view, and FIG.

FIG. 11 is a longitudinal sectional view showing a conventional accumulator.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Accumulator 2 ... Tank 3 ... Header 4 ... Suction pipe 5 ... Defroster 5a ... Shielding wall 10 ... Refrigerant inlet port 11 ... Refrigerant outlet port 12 ... Suction port 13 ... Discharge port

Claims (6)

[Claims] A refrigerant inlet port and a refrigerant outlet port are provided in a header provided at an upper end of a tank, a suction pipe is disposed in the tank, and a discharge port at one end of the suction pipe is connected to the refrigerant outlet port. And a suction port at the other end of the suction pipe is opened in the upper part of the tank, and a defroster is disposed between the suction port and the refrigerant inlet port, and the inside of the tank is viewed through the refrigerant inlet port. An accumulator characterized in that a defroster shielding wall is made to appear on a part of the opening surface of the refrigerant inlet port when the refrigerant is discharged. 2. An opening area of the refrigerant inlet port of 40 to
The accumulator according to claim 1, wherein the defroster shield wall is configured to be visible at 85%. 3. The defroster according to claim 1, wherein the shape of the defroster is a cup-like shape, and a shielding wall thereof is disposed substantially orthogonally or orthogonally to a flow direction of the refrigerant from the refrigerant inlet port. Accumulator as described. 4. A part of a peripheral side wall of the defroster is disposed along and close to an outer half portion of a peripheral wall on a suction end side of a suction port of the suction pipe. An accumulator according to any one of the preceding claims. 5. A pressure balance hole is provided on the discharge port side of the suction pipe, and a distance from a center position of the pressure balance hole to a top surface position of the header is set to 50 mm or less. An accumulator according to any one of the preceding claims. 6. A distance La from an upper surface position of a bottom wall of the tank to an inlet of a suction pipe, a distance Lb from an upper surface position of the tank bottom wall to a center position of the pressure balance hole, and a tank bottom wall. Lc from the upper surface position of the head to the lower surface position of the suction pipe discharge port fixing portion in the header
6. The relationship of La ≦ Lb ≦ Lc is established between
The accumulator according to 1.