JP2018193884A - Control valve - Google Patents

Abstract

To provide a control valve structure capable of suppressing the clogging of a valve portion due to contamination.SOLUTION: A control valve 1 is equipped with a cylindrical body which is formed so that an upstream chamber and a downstream chamber communicate through a valve hole in an axial direction, and is provided with a lateral hole communicating the inside and outside of the upstream chamber as an introduction port of a fluid; a valve body which opens/closes the valve portion contacting/separating to/from the valve hole; and a drive portion which drives the valve body in an opening/closing direction of the valve portion. The lateral hole is provided so as to offset a center axis thereof with respect to an axis of the body. On an inner peripheral surface of the body defining the upstream chamber, a spiral guide groove extending in the axial direction from a periphery of the lateral hole is provided. The guide groove is set in a spiral direction so as to guide the fluid led from the lateral hole in a direction separating from the valve hole.SELECTED DRAWING: Figure 2

Description

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

  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 refrigerant flow rate, and the like (see, for example, Patent Document 1). Such a control valve generally requires a so-called contamination countermeasure. That is, measures are 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 circulates together with the refrigerant and does not cause clogging of the valve portion.

JP 2010-150967 A

  However, particularly in a control valve having a small valve stroke, even a small foreign matter that has passed through the filter member may cause clogging of the valve portion. Thereby, 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 problems, and one of its purposes is to provide a control valve structure capable of suppressing clogging of the valve portion due to contamination.

  The control valve according to an aspect of the present invention is formed such that the upstream chamber and the downstream chamber communicate with each other in the axial direction through the valve hole, and a lateral hole that communicates the inside and outside of the upstream chamber is provided as a fluid introduction port. A cylindrical body, a valve body that opens and closes the valve portion by contacting and separating from the valve hole, and a drive unit that drives the valve body in the opening and closing direction of the valve portion are provided. The lateral hole is provided such 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 spiral direction of the guide groove is set so as to guide the fluid guided from the lateral hole in a direction away from the valve hole.

  According to this aspect, since the central axis of the horizontal hole is offset with respect to the axis of the body, the fluid that has passed 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 by centrifugal force. That is, the entire fluid is guided to the valve hole, but the foreign matter tends to stay in a state of turning at a position away from the valve hole. As a result, the clogging of the valve portion due to foreign matters can be suppressed.

  According to the control valve of the present invention, a control valve structure capable of suppressing clogging of the valve portion due to contamination can be provided.

It is a front view showing the external appearance of a control valve. It is AA arrow sectional drawing of FIG. It is explanatory drawing showing a foreign material countermeasure structure. It is a figure showing the result of having analyzed the flow when a foreign material penetrate | invaded a port about embodiment. It is a figure showing the result of having analyzed the flow when a foreign material penetrate | invades into a port about the 1st comparative example. It is a figure showing the result of having analyzed the flow when a foreign material penetrate | 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 the sake of convenience, the positional relationship between the structures may be expressed based on 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 compressor (hereinafter simply referred to as “compressor”). This compressor is installed in a refrigeration cycle of an automotive air conditioner, compresses the refrigerant flowing through the refrigeration cycle, and discharges it as a high-temperature and high-pressure gas refrigerant. This refrigerant is condensed in a condenser and further adiabatically expanded by an expansion device to become a low temperature / low pressure mist refrigerant. The refrigerant is guided to the evaporator, and the passenger compartment air is cooled by the latent heat of vaporization. The refrigerant that has passed through the evaporator is returned again to the compressor and circulates in the refrigeration cycle.

  The compressor has a fixed scroll and a movable scroll, and they 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 orbiting scroll makes a revolving motion, and the compression chamber moves from the outer peripheral side toward the center while reducing the volume. In the process, the refrigerant in the compression chamber is gradually compressed to high temperature and high pressure. This refrigerant is discharged into the discharge chamber as a refrigerant having a discharge pressure Pd, and is led out toward the condenser. Part of the discharged refrigerant is introduced into the back pressure chamber via the 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 housing of the compressor (not shown) is provided with a mounting hole, and the control valve 1 is inserted into the mounting hole and fixed. A filter member 3 that suppresses entry 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 exhibit a sealing function when the control valve 1 is assembled in the mounting hole are fitted to the outer peripheral surface of the body 2.

  As shown in FIG. 2, the body 2 is configured by connecting a first body 4 and a second body 6 coaxially. 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, both are connected coaxially. A power element 8 (functioning as a “pressure sensitive part” and a “driving part”) 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 the refrigerant having the discharge pressure Pd.

  As for the 1st body 4, the internal diameter of the lower half part is gradually expanded toward the downward direction. A valve seat forming member 16 is press-fitted in the vicinity of the port 12 in a passage communicating the port 10 and the port 12. The valve seat forming member 16 has a cylindrical shape whose inner diameter gradually decreases toward the upper side, and a valve hole 18 is provided in the upper part thereof. A valve seat 20 is formed at the upper end opening of the valve hole 18. An upper end portion of a cylindrical passage forming member 22 is press-fitted into the lower half portion of the valve seat forming member 16. The passage forming member 22 has an internal passage 23 that extends in the axial direction toward the lower side of the first body 4 and is 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” formed in a spiral shape on the inner peripheral surface of the first body 4, and extends to above the port 10. The passage forming member 26 has a bottomed stepped cylindrical shape, and the bottom portion 28 is screwed into the screw hole 24. The screwing position of the bottom portion 28 is set below the port 10. A cylindrical main body 30 extends upward from the bottom portion 28, and its tip abuts against the lower surface of the valve seat forming member 16. The main body 30 forms a double tube structure by disposing the passage forming member 22 inward. A communication hole 32 is provided in the upper part of the main body 30 to communicate the inside and outside.

  The 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 entry 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 between 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 path” 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 with 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. A suction pressure chamber 42 is formed above the partition wall 40, and a first pressure chamber 44 is formed below the partition wall 40. 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 valve body 48 has a tapered lower end portion, and is attached to and detached from the valve seat 20 at its tapered surface 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 through the valve hole 18. When the valve body 48 contacts and separates from the valve hole 18 from the first pressure chamber 44 side, the opening degree of the valve portion is adjusted.

  A connecting member 50 is disposed 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 and is filled with 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 allows the second pressure chamber 45 and the port 12 to communicate with each other. 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 path 47.

  The connecting member 50 is assembled so as to close the upper end opening of the first body 4, and is slidably supported in a guide hole 49 formed in the upper portion 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 of the connecting member 50. A retaining ring 52 (E-ring) is fitted to the upper portion of the valve body 48, and a disc-shaped spring receiver 54 is provided so that upward movement is restricted by the retaining ring 52. A spring 56 is interposed between the spring receiver 54 and the partition wall 40. The spring 56 functions as a “first biasing member” that biases 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 portion 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-like lower housing 68. The power element 8 is obtained by assembling so that the diaphragm 62 is sandwiched between the upper housing 66 and the lower housing 68. An O-ring 70 for sealing is interposed between the lower housing 68 and the second body 6. An annular plate 72 is caulked and joined to the upper end portion of the second body 6 to support the upper housing 66 so as to press the flange portion from above. The power element 8 is stably fixed to the second body 6 by the plate 72 pressing the flange portion over a wide range. In the modification, 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 partitioned into a sealed space S1 and an open space S2 by a diaphragm 62, and the sealed space S1 is filled with air. On the other hand, the open space S <b> 2 is opened to the second pressure chamber 45.

  A disc-shaped partition member 74 is press-fitted into the lower end portion 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 sealed space S <b> 1 into the reference pressure chamber 80 and the working 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 operating member 64 penetrates the insertion hole 84 so as to be slidable, and a lower end portion thereof is slightly expanded in diameter to form an operating connection portion 86. The operation connecting portion 86 is operatively 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 connection member 50, an operation connection portion 88 having substantially the same diameter as the operation connection portion 86 is projected, and these operation connection portions are connected with the diaphragm 62 interposed therebetween.

  The upper half of the operating member 64 is supported from above by a support member 78. An adjustment member 90 is screwed into the upper portion (bottom portion) of the upper housing 66. A spring 92 is interposed between the adjustment member 90 and the support 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 fixing position of the adjustment member 90.

  Since the operation connecting portion 86 has a slightly larger diameter than the insertion hole 84, it functions as a stopper. That is, even if the operation member 64 is displaced upward, the operation connecting portion 86 is locked to the partition member 74, so that the drop-off is prevented. Moreover, the opening degree of the valve part when the partition member 74 is locked becomes the maximum opening degree.

  The working chamber 82 has an 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 in this 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 senses a differential pressure between the back pressure Pm of the second pressure chamber 45 and the reference pressure Po of the reference pressure chamber 80, and operates in the valve opening / closing direction.

  With the above configuration, the suction pressure Ps and the discharge pressure Pd substantially 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 are used. At this time, with respect to the effective pressure receiving area (the pressure receiving area after cancellation) 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. C (valve opening direction), effective pressure receiving area Am applied by the back pressure Pm = (B−A) − (C−D) (valve closing direction), and the relationship 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 line of the fixed scroll. By 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 increased from the suction pressure Ps to the discharge pressure Pd. The discharged refrigerant circulates in the refrigeration cycle, whereby air conditioning of the vehicle air conditioner is performed. At this time, part of the discharged refrigerant is supplied to the port 10 of the control valve 1.

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

  When one of the discharge pressure Pd and the suction pressure Ps increases during the back pressure control process, the force in the valve opening direction acting on the valve body 48 increases. For this reason, the back pressure Pm also increases so as to increase the force in the valve closing direction that balances the load. According to the present embodiment, it is possible to obtain a control characteristic in which the back pressure Pm increases as the discharge pressure Pd and the suction pressure Ps increase.

Next, the foreign matter countermeasure structure that 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 AA arrow sectional drawing of (A).

  As shown in FIG. 3A, the port 10 is provided such that the center 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, a screw hole 24 is formed in a spiral shape 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 guided downward while turning. That is, when the center axis L1 of the port 10 is offset to the right with respect to the axis L2 of the body 2, the refrigerant turns rightward (turns clockwise) when viewed from the bottom, whereas the screw hole 24 has a left-hand thread ( The counterclockwise direction is the screw fastening direction). For this reason, the screw hole 24 has a spiral shape that guides the medium (refrigerant) guided from the port 10 in a direction away from the communication hole 32 (that is, a 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 along the annular passages 36, 38 and the like as a whole (thick solid arrow) reference). However, the foreign matter contained in the refrigerant easily moves along the spiral shape of the screw hole 24 by centrifugal force. In other words, the foreign matter is easily removed from the main flow of the refrigerant (so as to be separated), swirls along the screw hole 24, and stays at a lower position away from the valve hole 18 (see a two-dot chain line arrow). As a result, the clogging of the valve portion due to foreign matters can be suppressed.

  4 to 6 are diagrams showing the results of analyzing the flow when a foreign object has entered the port 10. FIG. 4 shows the analysis result of this 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 value in the figure relatively indicates the particle size of the foreign matter. (A)-(E) of each figure has shown the flow of the refrigerant | coolant containing a foreign material in time series.

  As shown in FIG. 4, according to the present embodiment, the foreign matter is likely to stay in a state where it continues to swivel below the discharge pressure chamber 34. On the other hand, as in the first comparative example shown in FIG. 5, if the spiral direction is a direction in which the swirl flow is moved upward, the foreign matter is actively guided upward while swirling with the refrigerant, and the upstream side passage It is easy to be guided to the valve hole 18 through. As in the second comparative example shown in FIG. 6, when there is no spiral guide groove itself, the foreign matter is more quickly guided upward and easily guided to the valve hole 18 through the upstream passage. For this reason, when the valve opening degree is small in the first and second modified examples, there is a possibility that the valve portion is clogged. On the other hand, according to the present embodiment, the foreign matter is easily separated from the refrigerant and kept at the lower portion, and therefore, the valve portion is hardly clogged with the foreign matter.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the specific embodiments, and 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, the center axis L1 of the port 10 is offset to the right side with respect to the axis L2 of the body 2, and the screw hole 24 is a left-hand thread. In a modification, the center 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 this case, the refrigerant turns leftward (turns counterclockwise) when viewed from the bottom, but the screw hole 24 is a direction in which the refrigerant guided from the port 10 is away from the communication hole 32 (ie, away from the valve hole 18). It has a spiral shape that guides it. For this reason, the effect similar to the said embodiment can be acquired regarding prevention of clogging of a foreign material.

  In the above-described embodiment, an example in which the extended portion of the screw hole 24 for fastening the passage forming member 26 is a “guide groove” has been described. In a 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, as viewed from the lower end opening of the body 2, the rear (upper) screw hole (first female screw) and the front (lower) screw hole (second female screw) may have different dimensions. For example, the valley diameter of the first female screw may be equal to or smaller than the inner diameter of the second female screw. With this configuration, the degree of freedom in designing the screw hole as the “guide groove” is increased. That is, it becomes easy to select an optimal screw size aiming at the effect of turning the foreign matter under the body 2 so as not to go to 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” (no function as a screw is planned at all).

  In the said embodiment, although the double pipe structure by the channel | path formation members 26 and 22 was illustrated, you may abbreviate | omit the inner channel | path formation member 22, for example. Even in such a configuration, since the port 10 and the communication hole 32 are separated from each other in the axial direction, it is possible to obtain an operational effect that the foreign matter is swung at the lower portion of the body 2 so as not to go to the valve hole 18.

  In the above embodiment, the 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 a modification, a slit may be provided at the upper end of the passage forming member 26 to form a “communication passage”. Alternatively, a “communication path” may be formed by providing a gap between the passage forming member 26 and the valve seat forming member 16.

  In the above embodiment, an example in which the reference pressure chamber 80 is filled with air has been described, but a vacuum state may be used. Moreover, in the said embodiment, although the diaphragm was illustrated as a pressure-sensitive member of the control valve 1, it is good also as a bellows other pressure-sensitive member.

  Although not described in the above embodiment, it is preferable to attach the control valve 1 to the compressor (attachment target) in the vertical position relationship shown in FIG. 2 from the viewpoint of retaining foreign matter at a position away from the valve portion. By setting the foreign matter staying position below the gravitational direction in the body, the staying foreign matter can be prevented or suppressed from moving toward the valve portion when the compressor is stopped. Moreover, you may provide the discharge channel | path for discharging the staying foreign material to the exterior in the position different from a valve part. For example, the passage forming member 26 may be provided with a discharge hole that functions as a “discharge passage”.

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

  In the said embodiment, the compressor mounted in the air conditioner for motor vehicles was illustrated as a scroll type compressor to which the control valve 1 is applied. In a modification, the control valve 1 may be applied to a scroll compressor mounted on a general-purpose (home use, business use) air conditioner. Further, the control valve 1 may be applied to a scroll compressor that uses a working fluid other than the refrigerant.

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

  In addition, this invention is not limited to the said embodiment and modification, A component can be deform | transformed and embodied in the range which does not deviate from a summary. Various inventions may be formed by appropriately combining a plurality of constituent elements disclosed in the above embodiments and modifications. Moreover, you may delete some components from all the components shown by the said embodiment and modification.

  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, 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 actuating member, 74 partition member, 78 support member, 80 reference pressure chamber, 90 adjusting member, 92 spring, L1 central axis, L2 axis, S1 sealed space , S2 Open space.

Claims (6)

A body in which an upstream chamber and a downstream chamber are formed so as to communicate in an axial direction via a valve hole, and a lateral hole that communicates 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 and away from the valve hole;
A drive unit for driving the valve body in the opening and closing direction of the valve unit;
With
The lateral hole is provided such 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 control valve is characterized in that a spiral direction is set 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 a screw hole. A cylindrical member extending in the axial direction inside the upstream chamber;
The control valve according to claim 1, wherein the cylindrical member forms an annular passage for allowing fluid to swirl with the inner peripheral surface of the body.   4. The control valve according to claim 3, wherein the cylindrical member has a communication passage for communicating the lateral hole and the valve hole at a position spaced apart from the lateral hole in the axial direction. 5. An inner cylinder member disposed concentrically on the inner side of the cylindrical member;
The control valve according to claim 4, wherein the inner cylinder member separates the communication path and the valve hole and forms another annular path between the inner cylinder member and the cylindrical member. Applied to a scroll compressor where the fixed scroll and the movable scroll are pressed against each other by the pressure in the back pressure chamber, the fluid introduced into the suction chamber is compressed in the compression chamber formed between the two scrolls, and discharged from the discharge chamber Is configured as a control valve for controlling the pressure of the back pressure chamber,
A discharge pressure chamber communicating with the discharge chamber, a first pressure chamber communicating with the back pressure chamber, a suction pressure chamber communicating with the suction chamber, a second pressure chamber communicating with the back pressure chamber, and a reference pressure The body having in series with a reference pressure chamber into which is introduced,
The valve body extending from the first pressure chamber to the second pressure chamber, and adjusting the opening of the valve portion by contacting and separating from the valve hole from the first pressure chamber side;
The second pressure chamber and the reference pressure chamber are partitioned and the valve body is supported in the axial direction, and the differential pressure between the second pressure chamber and the reference pressure chamber is sensed to operate in the opening / closing direction of the valve portion. A pressure sensitive member,
The control valve according to claim 1, comprising: