JP2017015366A - accumulator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an accumulator which can surely inhibit a bumping phenomenon and an impulsive sound associated therewith without causing complication, cost increase, increase in size, etc.SOLUTION: An accumulator has a bottomed cylindrical tank 10 with an upper surface opening closed by a lid member 12 which is provided with an inflow port 15 and an outflow port 16. A refrigerant introduced into the inflow port 15 is led out, through an inflow pipe 20 connected to the inflow port 15, into a liquid state portion which is accumulated in the tank 10 and formed of oil and the liquid phase refrigerant, to generate a swirl flow or a vortex flow in the liquid state portion along the inner peripheral surface of the tank 10 and stir the liquid state portion.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an accumulator (gas-liquid separator) used in a heat pump refrigeration cycle (hereinafter referred to as a heat pump system) such as a car air conditioner, a room air conditioner, and a refrigerator.

  In general, a heat pump system 200 that constitutes a car air conditioner or the like includes a compressor 210, an outdoor heat exchanger 220, an indoor heat exchanger 230, an expansion valve 260, a four-way switching valve 240, and the like as illustrated in FIG. The accumulator 250 is provided.

  In such a system 200, switching between the cooling operation and the heating operation (flow path switching) is performed by the four-way switching valve 240. During the cooling operation, the refrigerant is circulated in a cycle as shown in FIG. At this time, the outdoor heat exchanger 220 functions as a condenser, and the indoor heat exchanger 230 functions as an evaporator. On the other hand, during the heating operation, the refrigerant is circulated in a cycle as shown in FIG. 11B. At this time, the outdoor heat exchanger 220 functions as an evaporator, and the indoor heat exchanger 230 functions as a condenser. In either operation, low-temperature and low-pressure gas-liquid mixed refrigerant is introduced into the accumulator 250 from the evaporator (the indoor heat exchanger 230 or the outdoor heat exchanger 220) via the four-way switching valve 240.

  The accumulator 250 is, for example, a bottomed cylindrical tank whose top opening is hermetically closed by a lid member provided with an inflow port and an outflow port, a cap shape or an inverted thin bowl shape whose diameter is smaller than the inner diameter of the tank. A gas-liquid separator, one end of which is connected to the outlet, and the other end-side opening is positioned near the lower surface of the gas-liquid separator, for example, a U-shaped outflow pipe or the like, and a refrigerant introduced into the accumulator 250 Collides with the gas-liquid separator and is diffused radially to be separated into a liquid-phase refrigerant and a gas-phase refrigerant. The liquid-phase refrigerant flows down along the inner peripheral surface of the tank and accumulates in the lower part of the tank. The phase refrigerant is sucked into the suction side of the compressor 210 through the U-shaped outflow pipe.

  The refrigerant used in such a system 200 is mixed with oil (refrigeration oil) used for lubrication of the sliding portion of the compressor 210, and the oil is also mixed with the gas-phase refrigerant. Is circulated through the suction side (see Patent Documents 1, 2, etc.).

  On the other hand, when the system (compressor) is shut down, liquid-phase refrigerant containing oil accumulates in the lower part of the accumulator tank, but the oil is not compatible with the refrigerant and has a lower specific gravity than the refrigerant. Is separated into two layers, that is, an oil layer is formed on the upper side and a liquid phase refrigerant layer is formed on the lower side due to the difference in specific gravity and viscosity between the liquid phase refrigerant and the oil.

  In such a two-layer separation state, when the system (compressor) is started, the pressure in the tank rapidly decreases, so the liquid-phase refrigerant suddenly and rapidly boils (hereinafter referred to as bumping) and generates a large impact sound. There was a problem that occurred.

  The cause of this bumping phenomenon and the accompanying impact noise is that, even if the pressure in the tank (compressor suction side) drops when the compressor is started, the oil layer becomes a cover of the refrigerant layer until a certain point. (There is no bumping phenomenon in the oil layer), the occurrence of the bumping phenomenon is suppressed, but there is a pressure difference between the upper side (gas phase refrigerant) and the lower side (liquid phase refrigerant). When the pressure exceeds a predetermined pressure, it is assumed that the liquid-phase refrigerant is generated because it explosively boils at a stroke (see also Patent Document 1 describing an explanation of a bumping phenomenon in a compressor).

  Further, when the oil and the liquid refrigerant are not in the two-layer separation state as described above when the compressor is stopped, that is, when the oil and the liquid refrigerant remain in the mixed state even when the compressor is stopped, or Even if the oil is not compatible with the refrigerant and has a higher specific gravity than the refrigerant, the liquid phase refrigerant layer is formed on the upper side and the oil layer is formed on the lower side. Depending on the situation, the bumping phenomenon in which the liquid-phase refrigerant boils explosively and the impact noise accompanying it may occur.

  As one measure for suppressing the occurrence of such a bumping phenomenon and the accompanying impact noise, Patent Document 1 provides a stirring blade on a rotating shaft (crankshaft) of a compressor having a reciprocating engine as a drive source, It has been proposed that when the compressor is started, the agitation blade is rotated to agitate the oil layer portion, and the liquid phase refrigerant is discharged to the oil upper portion.

  Further, Patent Document 2 discloses a gas phase discharged from a compressor mainly for the purpose of reliably mixing oil and liquid refrigerant when they are in a two-layer separated state in an accumulator (tank). It has been proposed to stir a part of the refrigerant by blowing it into the liquid phase refrigerant from the bottom of the tank via a bypass channel with an on-off valve.

JP 2001-248923 A JP 2004-26395 A

  As described above, the present inventors have also confirmed that by stirring the liquid portion consisting of oil and liquid refrigerant in the tank at the time of starting the compressor, it is possible to suppress the occurrence of bumping phenomenon and the accompanying impact sound. However, the above-mentioned conventional proposed technique requires additional means for stirring (agitating blades, a drive source for rotating the stirring blades, a bypass flow path with an on-off valve, etc.), and an accumulator (and the same). Heat pump system) is complicated, costs are increased, and the size is increased.

  The present invention has been made in view of the above circumstances, and the object of the present invention is to reliably suppress the occurrence of bumping phenomenon and the accompanying impact sound without incurring complexity, cost increase, size increase, etc. It is to provide an accumulator that can be used.

  In order to achieve the above object, an accumulator according to the present invention has a tank provided with an inflow port and an outflow port, and allows refrigerant introduced into the inflow port to pass through an inflow pipe connected to the inflow port. Thus, the liquid part is led out to a liquid part composed of oil and liquid phase refrigerant accumulated in the tank, and the liquid part is stirred.

  More specifically, a swirl flow or vortex flow along the inner peripheral surface of the tank is generated in the liquid portion, and the liquid portion is stirred.

  In a preferred aspect, the position where the refrigerant is led out from the inflow pipe is set at the lowermost part of the tank.

  In another preferred aspect, the position where the refrigerant is led out from the inflow pipe is set at a boundary portion between the upper oil and the lower liquid refrigerant when the compressor is stopped.

  Moreover, the lead-out position of the refrigerant from the inflow pipe is preferably set at the outermost periphery in the tank.

  The inflow pipe is preferably composed of a refrigerant introduction portion connected to the inflow port, a refrigerant outlet portion having a circular arc shape in plan view, and an intermediate curved portion that gently connects the refrigerant introduction portion and the refrigerant outlet portion. .

  In a preferred aspect, the refrigerant outlet part is brought into contact with the inner peripheral surface of the tank.

  In a further preferred aspect, at least a portion connected to the intermediate curved portion of the refrigerant lead-out portion is brought into contact with the bottom surface of the tank, and at least a part of the intermediate curved portion is brought into contact with an inner peripheral surface of the tank. To be harassed.

  The lowermost part of the inflow pipe is preferably brought into contact with the bottom of the tank.

  In the accumulator according to the present invention, when the compressor is started, the refrigerant from the evaporator is led out into the liquid part (liquid phase refrigerant and oil) via the inflow pipe, and the liquid part follows, for example, the inner peripheral surface of the tank. Since the swirl flow or vortex flow is generated, the liquid part can be sufficiently stirred even when the compressor with a low refrigerant flow rate is started. Can be reliably suppressed.

  In this case, as the stirring means, basically, only an inflow pipe having a specific shape that can be manufactured at low cost by bending or the like needs to be prepared. Therefore, as in the conventional case, the stirring blade and the rotating blade are rotated. Compared to the case of using a drive source, a bypass flow path with an on-off valve, etc., the configuration of the accumulator can be simplified, and cost reduction, size reduction, and the like can be achieved.

  In addition, since the liquid portion can be sufficiently stirred even when the compressor is started with a low refrigerant flow rate, regardless of the properties of the refrigerant and oil used in the heat pump system, in other words, in the tank when the compressor is stopped, Any system that has an oil layer, a two-phase separated state of a liquid-phase refrigerant layer on the lower side, a mixed state of oil and liquid-phase refrigerant, and a two-phase separated state of a liquid-phase refrigerant layer on the upper side and an oil layer on the lower side In addition, there is an advantage that the accumulator according to the present invention can be employed.

  In addition, during normal operation after starting the compressor, the flow velocity and flow rate of the refrigerant led to the liquid part increases, so that the swirling flow or vortex flow is strengthened, and the stirring action thereby promotes gas-liquid separation. The liquid phase refrigerant having a large specific gravity is separated upward by the centrifugal force, and the oil having a small specific gravity is separated to the lower side of the center. Therefore, the oil has no compatibility with the liquid phase refrigerant and has a lower specific gravity than the liquid phase refrigerant. Even when the product is used (when the compressor is stopped, the oil layer is on the upper side and the liquid phase refrigerant layer is on the lower side in the tank), only the oil can be provided near the bottom of the tank. In addition, it is possible to return to the compressor via the oil strainer.

The partial notch front view which shows 1st Embodiment of the accumulator which concerns on this invention. The partial notch side view which shows 1st Embodiment of the accumulator which concerns on this invention. FIG. 3 is an enlarged cross-sectional view taken along the line U-U in FIG. 1. The perspective view of the inflow tube used for the accumulator of 1st Embodiment. It is a figure with which it uses for description of the oil strainer mainly used for the accumulator of 1st Embodiment, (A) is a partially notched front view, (B) is a principal part expanded half sectional view of (A), (C). These are sectional drawings which follow the VV arrow line of (B). The partial notch front view with which operation | movement of the accumulator of 1st Embodiment and description of an effect are provided. The expanded sectional view which follows the XX arrow line of FIG. It is a figure which shows 2nd Embodiment of the accumulator which concerns on this invention, (A) is a partially notched front view, (B) is a partially notched side view. It is a figure which shows 3rd Embodiment of the accumulator which concerns on this invention, (A) is a partially notched front view, (B) is a partially notched side view, (C) is sectional drawing which follows the YY arrow line of (A). . It is a figure which shows 4th Embodiment of the accumulator which concerns on this invention, (A) is a partially notched front view, (B) is a partially notched side view, (C) is sectional drawing which follows the ZZ arrow line of (A). . An example of a heat pump system is shown, (A) is a schematic block diagram which shows the refrigerant | coolant flow (cycle) at the time of cooling operation, (B) is a schematic block diagram which shows the refrigerant | coolant flow (cycle) at the time of heating operation.

  Embodiments of the present invention will be described below with reference to the drawings.

[First Embodiment]
1 and 2 are a partially cutaway front view and a partially cutaway side view showing a first embodiment of an accumulator according to the present invention, respectively.

  The accumulator 1 of the illustrated first embodiment is used as an accumulator 250 in, for example, a heat pump system 200 constituting a car air conditioner for an electric vehicle as shown in FIG. 11 described above, and is made of a metal such as stainless steel or aluminum alloy. A bottomed cylindrical tank 10 is provided, and the upper surface opening of the tank 10 is hermetically closed by the same metal lid member 12. The accumulator 1 of the present embodiment is installed vertically, for example, as illustrated, that is, with the lid member 12 on the upper (top) side and the bottom of the tank 10 on the lower (ground) side.

  In the heat pump system employing the accumulator 1 of the present embodiment, oil that is not compatible with the refrigerant and has a smaller specific gravity than the refrigerant is used. When the system (compressor) is shut down, the oil is used. The liquid phase refrigerant contained in the tank 10 is accumulated in the lower part of the tank 10, but due to the difference in specific gravity and viscosity between the liquid phase refrigerant and the oil, as shown in FIGS. A liquid phase refrigerant layer is formed on the lower side.

  The lid member 12 has an inflow port 15 and an outflow port 16 arranged in parallel, and one end side (upper end portion) of the inflow pipe 20 is connected to the lower portion of the inflow port 15 by caulking, press fitting, or the like. One end side (upper end portion) of the outflow pipe 30 is connected to the lower portion of 16 by caulking, press fitting, or the like.

  The inflow pipe 20 is manufactured by bending a metal pipe, and one end side (upper part) can be understood by referring to FIGS. 3 and 4 in addition to FIGS. The refrigerant introduction part 21 that has a letter-like shape in a side view that forms a side surface, the refrigerant lead-out part 23 that has an arc shape in plan view that forms the other end side (lower end part), and the refrigerant introduction part 21 and the refrigerant lead-out part 23 are gently connected. An intermediate bending portion 22 is included. The refrigerant introduction part 21 is bent after extending downward from the inflow port (toward the back side in FIG. 1 or toward the left side in FIG. 2) in order to secure a bending radius of the pipe, A portion of the lower end portion or the intermediate curved portion 22 that is close to the lower end portion of the refrigerant introduction portion 21 is brought into contact with the inner peripheral surface of the tank 10 at a position away from the bottom surface of the tank 10. 22 is bent toward the opposite side (the front side in FIG. 1 or the right side in FIG. 2) and connected to the refrigerant outlet 23. The refrigerant outlet 23 having a circular arc shape in plan view is brought into contact with the bottom surface and the inner peripheral surface of the tank 10 (particularly, the near side in FIG. 1 or the right bottom surface and the inner peripheral surface in FIG. 2) over substantially the entire length. Being fixed. The opening on the other end side (refrigerant outlet 23) of the inflow pipe 20 is positioned at the lowermost part and the outermost periphery of the tank 10, and the opening surface is the center of the upper end part of the inflow pipe 20 and the outflow pipe 30. It has an elliptical shape parallel to a vertical plane passing through the center of the upper end of the.

  With the above configuration, the refrigerant introduced into one end side (refrigerant introduction portion 21) of the inflow pipe 20 passes through the opening of the other end side (refrigerant lead-out section 23) of the inflow pipe 20 to the inside of the oil strainer 40 and the tank 10 described later. It is led out along the inner peripheral surface of the tank 10 and directed to the narrowed portion formed between the peripheral surface and the peripheral surface.

  On the other hand, as shown in FIG. 5, the outflow pipe 30 has a metal inner pipe 31 whose upper end portion is connected to the lower part of the outlet 16 by caulking or press-fitting and the like, and the inner pipe 31. The outer pipe 32 has a double pipe structure composed of a synthetic resin bottomed outer pipe 32 arranged on the outer periphery, and the lower end of the outer pipe 32 is press-fitted into the upper part 42 a with an inner peripheral step in the case 42 of the oil strainer 40. It is fixed by internal fitting. The lower end of the inner pipe 31 is positioned slightly above the bottom 32 b of the outer pipe 32, and the upper end of the outer pipe 32 is positioned slightly below the lid member 12. An oil return hole 35 is formed at the center of the bottom 32 b of the outer pipe 32. The hole diameter of the oil return hole 35 is set to about 1 mm, for example.

  In order to stably arrange the outer pipe 32 around the inner pipe 31, one or two or more for maintaining or connecting the gap between the inner pipe 31 and the outer pipe 32. Ribs may be provided. This rib can be provided on one or both of the pipes 31, 32.

  Further, the inner pipe 31 and the outer pipe 32 and the connecting ribs may be integrally formed by extrusion molding or the like.

  The oil strainer 40 is placed and fixed on the bottom of the tank 10 in a pressure-contact manner, and as can be understood with reference to FIGS. 5B and 5C, a bottomed cylindrical shape made of synthetic resin. It comprises a case 42 and a filter 45 made of a cylindrical mesh member integrated with the case 42 by insert molding. The case 42 includes an inner peripheral stepped upper portion 42a in which the lower end portion of the outer pipe 32 is fitted and fixed, a bottom plate portion 42c, and four columnar portions erected on the outer periphery of the bottom plate portion 42c at equal angular intervals. 42b, and annular band-shaped embedded portions 42d and 42d having a predetermined thickness and band width, including the upper end portion and the lower end portion of the columnar portion 42b. The upper and lower embedded portions 42d and 42d are sealed by integrating the upper and lower ends of the filter 45 during insert molding, and the columnar portion 42b of the filter 45 is also integrated with the columnar portion 42b during insert molding. Has been sealed. In other words, four windows 44 having a rectangular shape in a side view are defined by the four columnar portions 42b and the upper and lower embedded portions 42d and 42d, and a filter 45 is stretched on each window 44 portion. Although the four columnar portions 42b are provided with a gradient for punching, the radial widths of the four columnar portions 42b and the upper and lower embedded portions 42d and 42d are substantially equal.

  Next, operations and effects of the accumulator 1 according to the first embodiment having the configuration as described above will be described.

  As described above, when the compressor is stopped, the liquid-phase refrigerant containing oil accumulates in the lower part of the tank 10, but as shown in FIGS. 1 and 2 due to the difference in specific gravity and viscosity between the liquid-phase refrigerant and oil. The two layers are separated, that is, the oil layer is formed on the upper side and the liquid refrigerant layer is formed on the lower side.

  When the compressor is started in this two-layer separation state, the gas-phase refrigerant staying in the upper part of the tank 10 is sucked into the suction side of the compressor through the outflow pipe 30 and the outflow port 16, and the pressure in the upper space in the tank 10 Begins to fall, and the refrigerant discharged from the compressor is circulated in a cycle as shown in FIG.

  In this case, the frequency (the number of revolutions) does not increase so much immediately after the start of the compressor, but a small amount of refrigerant still flows from the evaporator (indoor heat exchanger or outdoor heat exchanger) through the inlet 15 through the inlet 15. From the opening of the refrigerant outlet portion 23 through the intermediate curved portion 22 to the narrowed portion formed between the oil strainer 40 and the inner peripheral surface of the tank 10. It is derived | led-out along the inner peripheral surface. In this way, the refrigerant derived into the liquid phase refrigerant in the liquid portion generates a swirling flow, and the swirling flow causes the liquid phase refrigerant accumulated in the tank 10 to flow from the vicinity of the bottom of the tank 10 and stir. Begin to be.

  The flow rate of the refrigerant derived from the opening of the refrigerant deriving unit 23 increases with time, and accordingly, as shown in FIG. 6, the counterclockwise swirling flow spirals from the bottom to the top as seen from above. In addition, as shown in FIG. 7, a counterclockwise vortex is similarly generated. In this case, due to the action of the spiral swirling flow and vortex flow, the liquid refrigerant having a large specific gravity moves upward on the outer peripheral side by centrifugal force, the oil having a small specific gravity moves to the lower side on the center side, and the swirling flow and the vortex flow are also introduced into the inflow pipe. 20 and the outflow pipe 30 may collide with each other, and the pressure difference between the upper side (gas phase refrigerant) and the lower side (liquid phase refrigerant) of the oil layer is reduced in a short time. Before reaching the predetermined pressure at which the phenomenon occurs, the liquid phase refrigerant is sufficiently agitated.

  As described above, in the accumulator 1 of the present embodiment, when the compressor is started, the refrigerant from the evaporator is led out into the liquid phase refrigerant through the inflow pipe 20, and the liquid phase refrigerant is transferred to the inner peripheral surface of the tank 10. A spiral swirling flow or vortex flow is generated, so that the liquid phase refrigerant can be sufficiently stirred even when the compressor starts with a small refrigerant flow rate. In addition, it is possible to reliably suppress the generation of the impact sound associated therewith.

  Further, in the accumulator 1 of the present embodiment, basically only the inflow pipe 20 having a specific shape needs to be prepared as the stirring means, so that the stirring blade and the drive for rotating the stirring blade as the stirring means as in the prior art. Compared with the case where a source, a bypass flow path with an on-off valve, or the like is used, the configuration of the accumulator 1 can be simplified, and cost reduction, size reduction, and the like can be achieved.

  On the other hand, during normal operation after starting the compressor, the flow rate and flow rate of the refrigerant led out to the liquid portion composed of the liquid refrigerant and oil through the inflow pipe 20 increases, so that the spiral swirl flow or vortex flow is increased. The gas-liquid separation is promoted by the stirring action of the spiral swirl flow and vortex flow, and as shown by the arrow line in FIG. The oil having a small specific gravity is separated to the lower side on the outer peripheral side, and the oil is sucked into the compressor suction side through the filter 45 → the oil return hole 35 → the outflow pipe 30 of the oil strainer 40. The refrigerant is sucked in and returned to the compressor suction side together with the gas-phase refrigerant. When passing through the filter 45, foreign matters such as sludge mixed with oil are removed.

  As described above, the accumulator 1 according to the present embodiment can effectively perform gas-liquid separation during normal operation, and has an oil that is not compatible with the liquid phase refrigerant and has a smaller specific gravity than the liquid phase refrigerant. Even when used, only the oil can be returned to the compressor via the oil strainer 40 provided at the bottom of the tank 10.

[Second Embodiment]
FIG. 8 is a view showing a second embodiment of the accumulator according to the present invention, FIG. 8 (A) is a partially cutaway front view, and FIG. 8 (B) is a partially cutaway side view.

  The accumulator 2 of the illustrated second embodiment is different from the accumulator 1 of the first embodiment only in the configuration of the inflow pipe, and the other portions have the same configuration. That is, in the accumulator 1 of the first embodiment, the refrigerant outlet position from the inflow pipe 20 is set at the lowermost part of the tank 10, but in the accumulator 2 of the second embodiment, the refrigerant from the inflow pipe 20A. Is set at the boundary portion K so as to straddle the upper oil and the lower liquid refrigerant when the compressor is stopped.

  Similarly to the first embodiment, the inflow pipe 20A of the present embodiment also has a refrigerant introduction portion 21A that is horizontally folded in a side view, a refrigerant outlet portion 23A that is arcuate in a plan view, and a refrigerant introduction portion 21A and a refrigerant outlet portion. 23A, and the lowermost part of the inflow pipe 20A is in contact with the bottom of the tank 10, but the refrigerant outlet 23A having a circular arc shape in plan view is 10 extends from the bottom of the tank 10 along the inner peripheral surface of the tank 10 and is positioned at the boundary K between the oil layer and the liquid refrigerant layer. In the illustrated example, the refrigerant outlet portion 23A extends upward immediately after the portion connected to the intermediate curved portion 22A. However, the refrigerant outlet portion 23A moves upward after being brought into contact with the bottom surface and the inner peripheral surface of the tank 10 by a predetermined length. You may make it extend.

  In the accumulator 2 according to the second embodiment configured as described above, when the compressor is started, the refrigerant flows from the opening of the refrigerant outlet 23A to the boundary portion K between the oil layer and the liquid-phase refrigerant layer. 30 is directed to a narrowed portion formed between the inner peripheral surface of the tank 10 and along the inner peripheral surface of the tank 10. The refrigerant thus led into the liquid portion generates a swirling flow, and the swirling flow starts to flow and stir from the oil and the liquid refrigerant above the tank 10. Thereafter, a counterclockwise swirling flow is generated from the top to the bottom so as to draw a spiral when viewed from above, and a counterclockwise vortex flow is generated in the same manner as in the first embodiment. In addition, even when the compressor having a small refrigerant flow rate is started, the liquid-phase refrigerant can be sufficiently agitated, so that it is possible to reliably suppress the occurrence of a bumping phenomenon and the accompanying impact sound when the compressor is started. Other functions and effects can be obtained in substantially the same manner as in the first embodiment.

[Third Embodiment]
FIG. 9 is a view showing a third embodiment of the accumulator according to the present invention, FIG. 9 (A) is a partially cutaway front view, FIG. 9 (B) is a partially cutaway side view, and FIG. 9 (C) is FIG. It is sectional drawing which follows the YY arrow line of (A).

  The accumulator 3 of the third embodiment shown in the figure is different from the accumulator 1 of the first embodiment only in the configuration of the inflow pipe, and the other portions have the same configuration. That is, in the accumulator 1 of the first embodiment, the intermediate curved portion 22 of the inflow pipe 20 moves from the back side to the near side in FIG. 1 or from the left side to the right side in FIG. In the accumulator 3 according to the third embodiment, the intermediate curved portion 22B that connects the refrigerant introducing portion 21B and the refrigerant leading portion 23B of the inflow pipe 20B is curved and connected to the refrigerant leading portion 23 (away from the inner peripheral surface). However, it is curved while being in contact with the inner peripheral surface of the tank 10 (along with it) and connected to the refrigerant outlet portion 23B. In other words, in the accumulator 1 of the first embodiment, the inner peripheral surface of the tank 10 from the position where the inflow pipe 20 extending downward reaches the bottom surface of the tank 10 (the position where the intermediate curved portion 22 and the refrigerant outlet portion 23 are connected). In the accumulator 3 according to the third embodiment, the accumulator 3 according to the third embodiment extends from the front of the position where the inflow pipe 20B reaches the bottom surface of the tank 10 to the inner peripheral surface of the tank 10. It is arranged along.

  In the accumulator 3 of the third embodiment having such a configuration, the length of the portion of the inflow pipe 20B along the inner peripheral surface of the tank 10 is made longer than the accumulator 1 of the first embodiment (see FIG. In the example shown, the length of the portion along the bottom surface of the tank 10 is also increased), so that the spiral swirl or vortex generated in the liquid-phase refrigerant in the tank 10 is strengthened and the compressor flow rate is low. In this case, the liquid-phase refrigerant can be more sufficiently stirred, and therefore, the bumping phenomenon at the time of starting the compressor and the generation of the impact sound accompanying it can be suppressed more reliably. Other functions and effects can be obtained in substantially the same manner as in the first embodiment.

[Fourth Embodiment]
FIG. 10 is a view showing a fourth embodiment of an accumulator according to the present invention, FIG. 10 (A) is a partially cutaway front view, FIG. 10 (B) is a partially cutaway side view, and FIG. 10 (C) is FIG. It is sectional drawing which follows the ZZ arrow line of (A).

  The accumulator 4 in the illustrated fourth embodiment is different from the accumulator 2 in the second embodiment only in the configuration of the inflow pipe, and the other portions have the same configuration. That is, in the accumulator 4 of the fourth embodiment, as in the accumulator 3 of the third embodiment, the intermediate curved portion 22C that connects the refrigerant introduction portion 21C and the refrigerant outlet portion 23C of the inflow pipe 20C has the tank 10 Is curved and connected to the refrigerant outlet 23C while being in contact with (in line with) the inner peripheral surface of the tank 10, in other words, along the inner peripheral surface of the tank 10 from the position before the position where the inflow pipe 20C reaches the bottom surface of the tank 10. Are arranged.

  Also in the accumulator 4 of the fourth embodiment configured as described above, the length of the portion along the inner peripheral surface of the tank 10 of the inflow pipe 20C is increased compared to the accumulator 2 of the second embodiment. The helical swirling flow or vortex generated in the liquid phase refrigerant in the tank 10 is strengthened, and the liquid phase refrigerant can be more sufficiently stirred even when the compressor has a low refrigerant flow rate. It is possible to more reliably suppress the occurrence of bumping phenomenon and the accompanying impact sound at the start-up time. Other functions and effects can be obtained in substantially the same manner as in the second embodiment.

  In the above embodiment, the case where the present invention is applied to an accumulator of a system in which the oil layer on the upper side and the liquid phase refrigerant layer on the lower side are separated in the tank when the compressor is stopped is illustrated. The present invention is also applied to a case where the oil and the liquid refrigerant remain in a mixed state even when the compressor is stopped, or a case where the liquid phase refrigerant layer is on the upper side and the oil layer is on the lower side. It is possible to obtain the same effects as the above embodiment.

1 Accumulator (first embodiment)
2 Accumulator (second embodiment)
3 Accumulator (Third embodiment)
4 accumulator (fourth embodiment)
DESCRIPTION OF SYMBOLS 10 Tank 12 Cover member 15 Inlet 16 Outlet 20 Inflow pipe 21 Refrigerant introduction part 22 Intermediate bending part 23 Refrigerant outlet part 30 Outlet pipe 31 Inner pipe 32 Outer pipe 35 Oil return hole 40 Oil strainer 42 Case 45 Filter

Claims (9)

  It has a tank provided with an inflow port and an outflow port, and the refrigerant introduced into the inflow port is made up of oil and liquid phase refrigerant accumulated in the tank via an inflow pipe connected to the inflow port. An accumulator characterized by being led to a liquid part and stirring the liquid part.   The accumulator according to claim 1, wherein a swirl flow or a vortex flow along the inner peripheral surface of the tank is generated in the liquid portion to stir the liquid portion.   The accumulator according to claim 1 or 2, wherein a position where the refrigerant is led out from the inflow pipe is set at a lowermost part of the tank.   The accumulator according to claim 1 or 2, wherein the refrigerant outlet position from the inflow pipe is set at a boundary portion between the upper oil and the lower liquid refrigerant when the compressor is stopped. .   The accumulator according to any one of claims 1 to 4, wherein a lead-out position of the refrigerant from the inflow pipe is set at an outermost periphery in the tank.   The inflow pipe is composed of a refrigerant introduction part connected to the inflow port, a refrigerant outlet part having a circular arc shape in plan view, and an intermediate curved part that gently connects the refrigerant introduction part and the refrigerant outlet part. The accumulator according to claim 1, wherein the accumulator is characterized in that   The accumulator according to claim 6, wherein the refrigerant lead-out portion is brought into contact with an inner peripheral surface of the tank.   The refrigerant outlet portion has at least a portion connected to the intermediate curved portion abutted against the bottom surface of the tank, and at least a portion of the intermediate curved portion abutted against the inner peripheral surface of the tank. The accumulator according to claim 6 or 7, characterized in that.   The accumulator according to any one of claims 1 to 8, wherein a lowermost portion of the inflow pipe is brought into contact with a bottom portion of the tank.

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