JP6795193B2 - Control valve - Google Patents

Description

The present invention relates to a control valve and relates to a structure capable of suppressing clogging of a valve portion with foreign matter.

An automobile air conditioner is generally configured by arranging a compressor, a condenser, an evaporator, and the like in a refrigerant circulation passage. Various control valves are provided for switching the refrigerant circulation passage, adjusting the flow rate of the refrigerant, and the like (see, for example, Patent Document 1). Such control valves are generally required to have so-called contamination countermeasures. That is, measures have been taken such as providing a filter member at the upstream port of the control valve so that foreign matter generated in the sliding portion of the compressor or the like circulates together with the refrigerant and does not cause clogging of the valve portion.

JP-A-2010-150967

However, especially in a control valve with a small valve stroke, even a small foreign object that has passed through the filter member may cause clogging of the valve portion. As a result, the opening area of the valve portion becomes smaller than the design value, and there is a concern that the controllability is lowered.

The present invention has been made in view of such a problem, and one of the objects thereof is to provide a control valve structure capable of suppressing clogging of a valve portion due to contamination.

The control valve of a certain aspect of the present invention is formed so that the upstream chamber and the downstream chamber communicate with each other in the axial direction via the valve hole, and a lateral hole for communicating the inside and outside of the upstream chamber is provided as a fluid introduction port. It includes a cylindrical body, a valve body that opens and closes the valve portion in contact with the valve hole, and a drive unit that drives the valve body in the opening and closing direction of the valve portion. The lateral hole is provided so that its central axis is offset with respect to the axis of the body. A spiral guide groove extending in the axial direction from the periphery of the lateral hole is provided on the inner peripheral surface of the body that defines the upstream chamber. The guide groove is set in a spiral direction so as to guide the fluid guided from the lateral hole in the direction away from the valve hole.

According to this aspect, since the central axis of the lateral hole is offset with respect to the axis of the body, the fluid passing through the introduction port is guided to the valve hole while swirling substantially along the inner peripheral surface of the body. On the other hand, since the foreign matter contained in the fluid has a relatively large specific gravity, it easily moves along the spiral of the guide groove due to centrifugal force. That is, the fluid as a whole is guided to the valve hole, but the foreign matter tends to stay in a mode of swirling at a position away from the valve hole. As a result, clogging of the valve portion due to foreign matter can be suppressed.

According to the control valve of the present invention, it is possible to provide a control valve structure capable of suppressing clogging of the valve portion due to contamination.

It is a front view which shows the appearance of a control valve. FIG. 1 is a cross-sectional view taken along the line AA of FIG. It is explanatory drawing which shows the foreign matter countermeasure structure. It is a figure which shows the result of having analyzed the flow when the foreign matter invades into a port about an embodiment. It is a figure which shows the result of having analyzed the flow when the foreign matter invades into a port about 1st comparative example. It is a figure which shows the result of having analyzed the flow when the foreign matter invades into a port about the 2nd comparative example.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for convenience, the positional relationship of each structure may be expressed with reference to the illustrated state.

The control valve of the present embodiment is configured as a back pressure control valve that controls the back pressure of a scroll type compressor (hereinafter, simply referred to as “compressor”). This compressor is installed in the refrigeration cycle of an automobile air conditioner, and compresses the refrigerant flowing through the refrigeration cycle into a high-temperature, high-pressure gas refrigerant and discharges the compressor. This refrigerant is condensed by a condenser and further adiabatically expanded by an expansion device to become a low-temperature, low-pressure mist-like refrigerant. The refrigerant is guided to the evaporator, and the latent heat of vaporization cools the vehicle interior air. The refrigerant that has passed through the evaporator is returned to the compressor and circulates in the refrigeration cycle.

The compressor has a fixed scroll and a movable scroll, which are pressed against each other by the pressure in the back pressure chamber (back pressure Pm). The compressor guides the refrigerant having the suction pressure Ps introduced into the suction chamber from the evaporator side to the compression chamber. The swivel motion of the movable scroll causes the compression chamber to move from the outer peripheral side to the center while reducing the volume. In the process, the refrigerant in the compression chamber is gradually compressed, resulting in high temperature and high pressure. This refrigerant is discharged into the discharge chamber as a refrigerant having a discharge pressure of Pd, and is led out toward the condenser. A part of the discharged refrigerant is introduced into the back pressure chamber via a control valve and is used for back pressure control.

FIG. 1 is a front view showing the appearance of the control valve. FIG. 2 is a cross-sectional view taken along the line AA of FIG.
As shown in FIG. 1, the control valve 1 has a stepped cylindrical body 2. A mounting hole is provided in the housing of a compressor (not shown), and the control valve 1 is inserted into the mounting hole and fixed. A filter member 3 for suppressing the intrusion of foreign matter into the introduction port (“port 10” described later) is fitted to the lower end portion of the body 2. A plurality of O-rings 90 to 94 that exert a sealing function when the control valve 1 is assembled into the mounting hole are fitted on the outer peripheral surface of the body 2.

As shown in FIG. 2, the body 2 is configured by coaxially connecting the first body 4 and the second body 6. A male screw portion is formed on the upper portion of the first body 4, and a female screw portion is formed on the lower half portion of the second body 6. By screwing the upper part of the first body 4 into the second body 6, the two are coaxially connected. A power element 8 (functioning as a "pressure sensitive portion" and a "drive portion") is assembled so as to close the upper end opening of the second body 6.

Ports 10, 12, and 14 are provided on the side of the first body 4 from below. The port 10 functions as a “discharge chamber communication port” and communicates with the discharge chamber of the compressor. The port 12 functions as a “back pressure chamber communication port” and communicates with the back pressure chamber of the compressor. The port 14 functions as a “suction chamber communication port” and communicates with the suction chamber of the compressor. The port 10 also functions as an "introduction port" for introducing a refrigerant having a discharge pressure of Pd.

The inner diameter of the lower half of the first body 4 is gradually increased downward. A valve seat forming member 16 is press-fitted in the vicinity of the port 12 in the passage connecting the port 10 and the port 12. The valve seat forming member 16 has a cylindrical shape in which the inner diameter is gradually reduced upward, and a valve hole 18 is provided above the cylindrical shape. A valve seat 20 is formed at the upper end opening of the valve hole 18. The upper end of the cylindrical passage forming member 22 is press-fitted into the lower half of the valve seat forming member 16. The passage forming member 22 extends in the axial direction toward the lower side of the first body 4 and has an internal passage 23 coaxial with the valve hole 18.

A screw hole 24 (female screw) is formed in the lower portion of the first body 4, and a passage forming member 26 is assembled. The screw hole 24 functions as a “guide groove” spirally formed on the inner peripheral surface of the first body 4, and extends above the port 10. The passage forming member 26 has a bottomed stepped cylindrical shape, and the bottom portion 28 thereof is screwed into the screw hole 24. The screwing position of the bottom 28 is set below the port 10. A cylindrical main body 30 extends upward from the bottom 28, and its tip is in contact with the lower surface of the valve seat forming member 16. The main body 30 forms a double pipe structure by arranging the passage forming member 22 inward. A communication hole 32 for communicating inside and outside is provided in the upper part of the main body 30.

A filter member 3 is fitted to the lower portion of the first body 4 so as to cover the port 10 from the outside. The filter member 3 includes a mesh that suppresses the intrusion of foreign matter into the first body 4. A discharge pressure chamber 34 is formed between the valve seat forming member 16 and the passage forming member 26, and communicates with the port 10. The port 10 functions as a "lateral hole" and the discharge pressure chamber 34 functions as an "upstream chamber".

The passage forming member 26 functions as a “cylindrical member”, and the main body 30 forms an annular passage 36 with the inner peripheral surface of the first body 4. The communication hole 32 is formed at a position sufficiently separated from the port 10 in the axial direction, and functions as a “communication passage” for communicating the port 10 and the valve hole 18. The passage forming member 22 functions as an “inner cylinder member”, separates the communication hole 32 and the valve hole 18, and forms an annular passage 38 between the passage forming member 26. That is, the annular passage 36, the communication hole 32, the annular passage 38, and the internal passage 23 form an upstream passage that communicates the port 10 and the valve hole 18.

A partition wall 40 is provided so as to partition the inside of the first body 4 in the axial direction. The suction pressure chamber 42 is formed above the partition wall 40, and the first pressure chamber 44 is formed below. A guide hole 46 is provided so as to penetrate the center of the partition wall 40 in the axial direction. A long valve body 48 is slidably inserted into the guide hole 46. The lower end of the valve body 48 has a tapered shape, and the tapered surface is attached to and detached from the valve seat 20 to open and close the valve portion. The first pressure chamber 44 forms a pressure space between the valve hole 18 and the port 12 and functions as a “downstream chamber”. The first pressure chamber 44 and the discharge pressure chamber 34 communicate with each other in the axial direction via the valve hole 18. When the valve body 48 is brought into contact with and separated from the valve hole 18 from the first pressure chamber 44 side, the opening degree of the valve portion is adjusted.

The connecting member 50 is arranged so as to partition the pressure space surrounded by the first body 4, the second body 6, and the power element 8 in the axial direction. The connecting member 50 divides the pressure space into an upper second pressure chamber 45 and a lower suction pressure chamber 42. The suction pressure chamber 42 communicates with the port 14 to satisfy the suction pressure Ps. A communication passage 47 parallel to the axis is provided in the vicinity of the peripheral edge of the first body 4. The communication passage 47 communicates the second pressure chamber 45 with the port 12. With such a configuration, the back pressure Pm of the first pressure chamber 44 is also introduced into the second pressure chamber 45 via the communication passage 47.

The connecting member 50 is assembled so as to close the upper end opening of the first body 4, and is slidably supported by a guide hole 49 formed in the upper part of the first body 4. The upper half of the valve body 48 extends to the suction pressure chamber 42, and the upper end surface thereof is in contact with the bottom portion of the connecting member 50. A stop ring 52 (E-ring) is fitted to the upper portion of the valve body 48, and a disk-shaped spring receiver 54 is provided so that the stop ring 52 restricts upward movement. A spring 56 is interposed between the spring receiver 54 and the partition wall 40. The spring 56 functions as a "first urging member" that urges the valve body 48 upward (in the valve opening direction).

The power element 8 is assembled so as to close the upper end opening of the second body 6. The power element 8 includes a housing 60 fixed to the upper end of the second body 6, a diaphragm 62 as a “pressure sensitive member”, and an operating member 64 that supports the center of the diaphragm 62 in the axial direction.

The housing 60 includes a bottomed cylindrical upper housing 66 and a stepped disk-shaped lower housing 68. The power element 8 is obtained by assembling the diaphragm 62 between the upper housing 66 and the lower housing 68 so as to sandwich the diaphragm 62. An O-ring 70 for sealing is interposed between the lower housing 68 and the second body 6. An annular plate 72 is crimp-joined to the upper end of the second body 6 to support the flange of the upper housing 66 so as to be pressed from above. When the plate 72 presses the flange portion over a wide range, the power element 8 is stably fixed to the second body 6. In the modified example, the plate 72 may be press-fitted into the upper end portion of the second body 6.

The inside of the power element 8 is divided into a closed space S1 and an open space S2 by a diaphragm 62, and the closed space S1 is filled with the atmosphere. On the other hand, the open space S2 is open to the second pressure chamber 45.

A disc-shaped partition member 74 is press-fitted into the lower end of the upper housing 66. A recess 76 is formed in the center of the lower surface of the partition member 74. The partition member 74 separates the closed space S1 into the reference pressure chamber 80 and the operating chamber 82 defined by the recess 76. An insertion hole 84 is provided so as to penetrate the partition member 74 in the axial direction. The actuating member 64 slidably penetrates the insertion hole 84, and the lower end portion thereof is slightly enlarged in diameter to form the actuating connecting portion 86. The actuating connecting portion 86 is actuatingly connected to the connecting member 50 and thus to the valve body 48 with the central portion of the diaphragm 62 interposed therebetween. At the center of the upper end surface of the connecting member 50, an operating connecting portion 88 having substantially the same diameter as the operating connecting portion 86 is projected, and these operating connecting portions are connected with the diaphragm 62 interposed therebetween.

The upper half of the operating member 64 is supported from above by the support member 78. An adjusting member 90 is screwed onto the upper portion (bottom) of the upper housing 66. A spring 92 is interposed between the adjusting member 90 and the supporting member 78. The spring 92 functions as a "second urging member" that urges the valve body 48 in the valve closing direction via the operating member 64 and the connecting member 50. The load (urging force) of the spring 92 can be adjusted by pressing and deforming the center of the upper surface (bottom surface) of the upper housing 66 in the axial direction and adjusting the fixed position of the adjusting member 90.

Since the working connecting portion 86 has a diameter slightly larger than that of the insertion hole 84, it functions as a stopper. That is, even if the operating member 64 is displaced upward, the operating connecting portion 86 is locked to the partition member 74, so that the actuating member 64 is prevented from falling off. Further, the opening degree of the valve portion when the partition member 74 is locked becomes the maximum opening degree.

The inside of the operating chamber 82 becomes the atmospheric pressure as the reference pressure Po. The reference pressure Po is also filled in the reference pressure chamber 80 through the gap between the operating member 64 and the insertion hole 84. The reference pressure chamber 80 of the present embodiment is maintained at a lower pressure than the second pressure chamber 45.

The diaphragm 62 partitions the second pressure chamber 45 and the reference pressure chamber 80, and supports the valve body 48 in the axial direction via the connecting member 50. The diaphragm 62 operates in the opening / closing direction of the valve portion by sensing the differential pressure between the back pressure Pm of the second pressure chamber 45 and the reference pressure Po of the reference pressure chamber 80.

With the above configuration, the suction pressure Ps and the discharge pressure Pd act on the valve body 48 in the valve opening direction, while the back pressure Pm acts in the valve closing direction. That is, as shown in the figure, the effective pressure receiving area A of the diaphragm 62, the cross-sectional area B of the guide hole 49, the cross-sectional area C of the guide hole 46, and the cross-sectional area D of the valve hole 18. At this time, regarding the effective pressure receiving area (pressure receiving area after offsetting) of the valve body 48, the effective pressure receiving area Ad = D (valve opening direction) on which the discharge pressure Pd acts and the effective pressure receiving area As = B- on which the suction pressure Ps acts. The effective pressure receiving area Am = (BA)-(CD) (valve closing direction) on which C (valve opening direction) and back pressure Pm act, and the relationship of As> Am> Ad is established. However, the back pressure Pm acts on the diaphragm 62 in the valve opening direction.

Next, the control operation of the control valve 1 will be described.
When a compressor (not shown) is driven, the movable scroll turns (revolves) around the axis of the fixed scroll. Due to the revolution of the movable scroll, the compression chamber formed between the two scrolls is moved from the outer peripheral side toward the center while reducing the volume. In this process, the refrigerant pressure is boosted from the suction pressure Ps to the discharge pressure Pd. The discharged refrigerant circulates in the refrigeration cycle to air-condition the vehicle air conditioner. At this time, a part of the discharged refrigerant is supplied to the port 10 of the control valve 1.

At this time, the back pressure Pm of the compressor is controlled by the control valve 1. The valve body 48 has a valve opening direction force due to the discharge pressure Pd, a valve opening direction force due to the suction pressure Ps, a valve closing direction force due to the back pressure Pm, a valve opening direction driving force due to the diaphragm 62, and a valve opening direction due to the spring 56. The directional force and the valve closing force by the spring 92 are kept in a balanced valve lift position.

When either the discharge pressure Pd or the suction pressure Ps rises in the process of controlling the back pressure, the force acting on the valve body 48 in the valve opening direction becomes large. Therefore, the back pressure Pm also increases so as to increase the force in the valve closing direction that balances the load. According to this embodiment, a control characteristic is obtained in which the back pressure Pm increases as the discharge pressure Pd and the suction pressure Ps increase.

Next, the foreign matter countermeasure structure, which is the main part of the present embodiment, will be described in detail.
FIG. 3 is an explanatory diagram showing a foreign matter countermeasure structure. (A) corresponds to the lower part of FIG. 1 and shows a state in which the filter member 3 is removed. (B) is a cross-sectional view taken along the line AA of (A).

As shown in FIG. 3A, the port 10 is provided so that its central axis L1 is offset to the right with respect to the axis L2 of the body 2. On the other hand, as shown in FIG. 3B, screw holes 24 are spirally formed on the lower inner peripheral surface of the body 2. The spiral direction (spiral winding direction) is a direction in which the medium (refrigerant) guided from the port 10 is swirled and guided downward. That is, by offsetting the central axis L1 of the port 10 to the right with respect to the axis L2 of the body 2, the refrigerant turns clockwise (clockwise) when viewed from the bottom, while the screw hole 24 is left-handed (turned clockwise). Counterclockwise is the screw fastening direction). Therefore, the screw hole 24 has a spiral shape that guides the medium (refrigerant) guided from the port 10 in the direction away from the communication hole 32 (that is, the direction away from the valve hole 18).

Since there is a differential pressure between the discharge pressure chamber 34 and the first pressure chamber 44, the refrigerant introduced from the port 10 is guided to the valve hole 18 as a whole along the annular passages 36, 38, etc. (thick solid line arrow). reference). However, the foreign matter contained in the refrigerant easily moves along the spiral shape of the screw hole 24 due to the centrifugal force. That is, the foreign matter easily turns away from the mainstream of the refrigerant (so that it is separated) along the screw hole 24 and stays at a lower position away from the valve hole 18 (see the alternate long and short dash arrow). As a result, clogging of the valve portion due to foreign matter can be suppressed.

4 to 6 are diagrams showing the results of analyzing the flow when a foreign substance invades the port 10. FIG. 4 shows the analysis result of the present embodiment, FIG. 5 shows the analysis result of the first comparative example, and FIG. 6 shows the analysis result of the second comparative example. In the first comparative example, the spiral direction of the screw hole is opposite to that of the present embodiment. In the second comparative example, the screw hole itself is not formed. The numerical values in the figure indicate the relative size of the particle size of the foreign matter. (A) to (E) of each figure show the flow of the refrigerant containing foreign matter in time series.

As shown in FIG. 4, according to the present embodiment, the foreign matter tends to stay in the lower part of the discharge pressure chamber 34 so as to continue to rotate. On the other hand, as in the first comparative example shown in FIG. 5, if the spiral direction is the direction in which the swirling flow is moved upward, the foreign matter is positively guided upward while swirling with the refrigerant, and the upstream passage. It is easy to be guided to the valve hole 18 through the valve hole 18. When there is no spiral guide groove itself as in the second comparative example shown in FIG. 6, the foreign matter is guided upward more quickly and is easily guided to the valve hole 18 through the upstream passage. Therefore, if the valve opening degree is small in the first and second modified examples, the valve portion may be clogged. On the other hand, according to the present embodiment, since the foreign matter is easily separated from the refrigerant and fastened to the lower part, the valve portion is less likely to be clogged by the foreign matter.

Although the preferred embodiment of the present invention has been described above, the present invention is not limited to the specific embodiment, and it goes without saying that various modifications can be made within the scope of the technical idea of the present invention. Absent.

In the above embodiment, as shown in FIG. 3, an example is shown in which the central axis L1 of the port 10 is offset to the right with respect to the axis L2 of the body 2 and the screw hole 24 is a left-handed screw. In the modified example, the central axis L1 of the port 10 may be offset to the left with respect to the axis L2 of the body 2, and the screw hole 24 may be a right-hand thread. In that case, the refrigerant turns counterclockwise (counterclockwise) when viewed from the bottom, but the screw hole 24 is in a direction that keeps the refrigerant guided from the port 10 away from the communication hole 32 (that is, a direction away from the valve hole 18). Has a spiral shape that guides to. Therefore, the same effect as that of the above-described embodiment can be obtained with respect to the prevention of clogging of foreign matter.

In the above embodiment, an example is shown in which the extension portion of the screw hole 24 for fastening the passage forming member 26 is a “guide groove”. In the modified example, a screw hole for fixing the passage forming member 26 and a screw hole as a "guide groove" may be provided individually. That is, the dimensions of the screw hole (first female screw) at the back (upper side) and the screw hole (second female screw) at the front (lower side) of the hand when viewed from the lower end opening of the body 2 may be different. For example, the diameter of the valley of the first female screw may be equal to or less than the inner diameter of the second female screw. With such a configuration, the degree of freedom in designing the screw hole as the "guide groove" is increased. That is, it becomes easy to select the optimum screw size aiming at the action effect of turning the foreign matter at the lower part of the body 2 so as not to go toward the valve hole 18.

In the above embodiment, the "guide groove" is a screw hole, but it may be a spiral groove that is not necessarily included in the concept of "screw" (the function as a screw is not planned at all).

In the above embodiment, the double pipe structure by the passage forming members 26 and 22 is illustrated, but for example, the inner passage forming member 22 may be omitted. Even with such a configuration, since the port 10 and the communication hole 32 are separated from each other in the axial direction, the effect of turning the foreign matter at the lower part of the body 2 so as to make it difficult to move toward the valve hole 18 can be obtained.

In the above embodiment, a communication hole 32 is provided in the upper part of the passage forming member 26 to form a “communication passage” for communicating the port 10 and the valve hole 18. In the modified example, a slit may be provided at the upper end of the passage forming member 26 to form a “continuous passage”. Alternatively, a gap may be provided between the passage forming member 26 and the valve seat forming member 16 to form a “continuous passage”.

In the above embodiment, the reference pressure chamber 80 is filled with the atmosphere, but a vacuum state may be used. Further, in the above embodiment, the diaphragm is exemplified as the pressure-sensitive member of the control valve 1, but a bellows or other pressure-sensitive member may be used.

Although not described in the above embodiment, from the viewpoint of retaining foreign matter at a position away from the valve portion, it is preferable to mount the control valve 1 on the compressor (mounting target) in the vertical positional relationship shown in FIG. By setting the stagnant position of the foreign matter in the body in the direction of gravity, it is possible to prevent or suppress the stagnant foreign matter from heading toward the valve portion when the compressor is stopped. Further, a discharge passage for discharging the accumulated foreign matter to the outside at a position different from that of the valve portion may be provided. For example, the passage forming member 26 may be provided with a discharge hole that functions as a “discharge passage”.

In the above embodiment, the mechanical structure that operates by the differential pressure is illustrated as the “driving unit”, but a solenoid or other electromagnetic / electrical structure may be adopted.

In the above embodiment, as a scroll type compressor to which the control valve 1 is applied, a compressor mounted on an automobile air conditioner is exemplified. In the modified example, the control valve 1 may be applied to a scroll type compressor mounted on a general-purpose (household or commercial) air conditioner. Further, the control valve 1 may be applied to a scroll type compressor using a working fluid other than the refrigerant.

In the above embodiment, an example in which the foreign matter countermeasure structure is applied to the back pressure control valve of the scroll type compressor is shown. In the modified example, the same foreign matter countermeasure structure may be applied to other control valves that require contamination countermeasures. For example, in the control valve of a variable displacement compressor, the guide groove (spiral shape) may be applied to the upstream chamber side where the high-pressure refrigerant is introduced in the body.

The present invention is not limited to the above-described embodiment or modification, and the components can be modified and embodied without departing from the gist. Various inventions may be formed by appropriately combining a plurality of components disclosed in the above embodiments and modifications. In addition, some components may be deleted from all the components shown in the above embodiments and modifications.

1 control valve, 2 body, 3 filter member, 8 power element, 10 port, 12 port, 14 port, 18 valve hole, 20 valve seat, 22 passage forming member, 23 internal passage, 24 screw hole, 26 passage forming member, 32 communication hole, 34 discharge pressure chamber, 36 annular passage, 38 annular passage, 40 partition wall, 42 suction pressure chamber, 44 first pressure chamber, 45 second pressure chamber, 46 guide hole, 47 communication passage, 48 valve body, 49 Guide hole, 50 connecting member, 56 spring, 60 housing, 62 diaphragm, 64 operating member, 74 partition member, 78 support member, 80 reference pressure chamber, 90 adjust member, 92 spring, L1 central axis, L2 axis, S1 sealed space , S2 Open space.

Claims (6)

A body in which the upstream chamber and the downstream chamber are formed so as to communicate with each other in the axial direction via a valve hole, and a lateral hole for communicating the inside and outside of the upstream chamber is provided as a fluid introduction port.
A valve body that opens and closes the valve portion in contact with the valve hole,
A drive unit that drives the valve body in the opening / closing direction of the valve unit,
With
The lateral hole is provided so that its central axis is offset with respect to the axis of the body.
A spiral guide groove extending in the axial direction from the periphery of the lateral hole is provided on the inner peripheral surface of the body that defines the upstream chamber.
The guide groove is a control valve whose spiral direction is set so as to guide the fluid guided from the lateral hole in a direction away from the valve hole. The control valve according to claim 1, wherein the guide groove is formed of a screw hole. A cylindrical member extending in the axial direction inside the upstream chamber is further provided.
The control valve according to claim 1 or 2, wherein the cylindrical member forms an annular passage for swirling the fluid with the inner peripheral surface of the body. The control valve according to claim 3, wherein the cylindrical member has a communication passage for communicating the horizontal hole and the valve hole at a position separated from the horizontal hole in the axial direction. An inner cylinder member concentrically arranged inside the cylindrical member is further provided.
The control valve according to claim 4, wherein the inner cylinder member separates the communication passage from the valve hole and forms another annular passage between the inner cylinder member and the cylindrical member. The fixed scroll and the movable scroll are pressed against each other by the pressure of the back pressure chamber, and the fluid introduced into the suction chamber is compressed in the compression chamber formed between the two scrolls and applied to the scroll type compressor that discharges from the discharge chamber. It is configured as a control valve that controls the pressure in the back pressure chamber.
A discharge pressure chamber communicating with the discharge chamber, a first pressure chamber communicating with the back pressure chamber, an suction pressure chamber communicating with the suction chamber, a second pressure chamber communicating with the back pressure chamber, and a reference pressure. With the body having a reference pressure chamber in series with which
A valve body extending from the first pressure chamber to the second pressure chamber and contacting and separating from the valve hole from the side of the first pressure chamber to adjust the opening degree of the valve portion.
It separates the second pressure chamber from the reference pressure chamber, supports the valve body in the axial direction, senses the differential pressure between the second pressure chamber and the reference pressure chamber, and operates in the opening / closing direction of the valve portion. With pressure-sensitive members
The control valve according to any one of claims 1 to 5, wherein the control valve comprises.