WO2014006651A1 - 絞り装置、および空気調和装置 - Google Patents
絞り装置、および空気調和装置 Download PDFInfo
- Publication number
- WO2014006651A1 WO2014006651A1 PCT/JP2012/004297 JP2012004297W WO2014006651A1 WO 2014006651 A1 WO2014006651 A1 WO 2014006651A1 JP 2012004297 W JP2012004297 W JP 2012004297W WO 2014006651 A1 WO2014006651 A1 WO 2014006651A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- valve body
- opening
- flow path
- main body
- Prior art date
Links
- 238000004378 air conditioning Methods 0.000 title description 6
- 239000003507 refrigerant Substances 0.000 claims abstract description 65
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 238000001704 evaporation Methods 0.000 claims description 2
- 238000010586 diagram Methods 0.000 description 10
- 239000000463 material Substances 0.000 description 8
- 239000002826 coolant Substances 0.000 description 6
- 230000007547 defect Effects 0.000 description 4
- 229910001369 Brass Inorganic materials 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 239000010951 brass Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
- F16K1/38—Valve members of conical shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/42—Valve seats
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/06—Damage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
- F25B2500/221—Preventing leaks from developing
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present invention relates to a throttle device that adjusts the flow rate of a fluid, and an air conditioner including the throttle device.
- an air conditioner such as a multi air conditioning system for buildings
- a cooling operation or a heating operation is performed by circulating a refrigerant between an outdoor unit that is a heat source unit arranged outdoors and an indoor unit arranged indoors. It is supposed to be.
- the air-conditioning target space is cooled or heated by air that has been cooled by absorbing heat from the refrigerant, or air that has been heated by releasing heat from the refrigerant.
- a throttling device is used to control the refrigerant flow rate of such an air conditioner.
- a throttle device used in a conventional air conditioner brass having good workability is used as the material of the throttle device body. Further, the same material as that of the throttle device main body is used for the material of the valve seat. On the other hand, the valve body is independent of the throttle device body, and generally stainless steel having high hardness is used as the material.
- valve body is made of brass metal, a separate seat member is provided on the valve seat, and stainless steel having high hardness is used as the material (see, for example, Patent Document 1).
- the valve body is supported at a position far from the valve seat. That is, the valve body is disposed so as to be movable back and forth so as to face the valve seat, and the end opposite to the valve seat is supported by a valve holder or the like connected to the stepping motor.
- the valve body and the valve can be changed by increasing the number of times the throttle device is opened and closed, or by changing the flow direction of the refrigerant in the reverse direction. There is a problem that the amount of wear at the contact portion of the seat increases, causing a quality defect due to valve leakage of the throttle device, and the reliability is lowered.
- the wear amount of the valve seat can be reduced by providing a separate seat member in the valve seat.
- the support of the valve body is supported at a position far from the valve seat, there is a possibility that the tip of the valve body will shake when the valve body opens and closes due to the clearance of the support part.
- excessive deformation or wear occurs in the valve body itself of a low hardness material.
- the amount of valve leakage of the throttle device increases more than before due to such deformation and increased wear.
- the present invention has been made to solve the above-described problems, and provides a throttle device that can suppress an increase in the amount of valve leakage caused by deformation or wear of a valve body or a valve seat. . Moreover, the quality defect resulting from the valve leakage of a throttle device is reduced, and a highly reliable air conditioning apparatus is obtained.
- a throttling device includes a main body to which a first flow path and a second flow path are connected, a valve chamber formed inside the main body and communicating with the first flow path, and formed in the valve chamber.
- a valve seat having an opening communicating with the second flow path; and a valve body penetrating through the valve chamber and provided so as to be movable forward and backward toward the opening of the valve seat, and adjusting the opening of the opening,
- the valve body includes a valve body body portion that penetrates the valve chamber, a valve body front end column portion that is formed to have a smaller diameter than an opening of the valve seat, the valve body body portion, and the valve body front end column portion.
- a first support portion that is formed by a through-hole through which the valve body body portion penetrates the valve chamber, and that is in sliding contact with the valve body body portion to support the valve body. And a main body channel that communicates the second channel and the opening of the valve seat, and a valve body support hole into which the valve body tip column portion is inserted. And it has a second supporting portion to which the valve body supporting hole for supporting the valve body in contact said valve tip pillar portion sliding.
- the present invention can suppress an increase in the amount of valve leakage caused by deformation or wear of the valve body or the valve seat.
- FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. It is a figure which shows the position of the valve body at the time of flow volume adjustment. It is a figure which shows the structure of the air conditioning apparatus in Embodiment 1 of this invention. It is sectional drawing of the principal part of the aperture_diaphragm
- FIG. 7 is a cross-sectional view taken along the line BB in FIG. 6.
- valve body tip deflection E computed from the specification of each valve body support structure. It is a figure which shows a valve body tip deflection
- a case where the present invention is applied to a throttle device that adjusts the flow rate of a refrigerant in a refrigeration cycle of an air conditioner will be described as an example.
- the throttling device of the present invention is not limited to adjusting the flow rate of the refrigerant, and can be applied to any fluid.
- FIG. 1 is a diagram showing a configuration of a diaphragm device according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 1 of the present invention.
- 3 is a cross-sectional view taken along the line AA in FIG.
- FIG. 4 is a diagram illustrating the position of the valve body during flow rate adjustment.
- the expansion device 100 includes a main body 1 to which the first flow path 2 and the second flow path 3 are connected, a valve chamber 14 that is formed inside the main body 1 and communicates with the first flow path 2, A valve seat 10 having an orifice 11 formed in the valve chamber 14 and communicating with the second flow path 3, and is provided so as to be able to advance and retreat toward the orifice 11 of the valve seat 10 through the valve chamber 14. And a valve body 4 for adjusting the degree.
- a stepping motor 20 including a rotor connected to the valve body 4 via a moving mechanism (not shown) and a stator is provided on the valve body 4. The rotation of the stepping motor 20 is converted into a translation distance by the moving mechanism, and the valve body 4 moves in the axial direction (vertical direction) to control the opening degree of the valve seat 10.
- the valve body 4 includes a valve body body portion 5 that penetrates the valve chamber 14, a valve body front end cylindrical portion 7 that has a smaller diameter than the opening of the orifice 11 of the valve seat 10, and the valve body body portion 5 and the valve body front end.
- a tapered portion 6 that connects the column portion 7 is provided.
- a cylindrical valve body tip column portion 7 is formed on a substantially central axis of the valve body body portion 5, for example.
- tip cylinder part 7 is not limited to a cylinder.
- valve body front end cylindrical part 7 corresponds to the “valve body front end column part” in the present invention.
- the orifice 11 corresponds to the “opening of the valve seat” in the present invention.
- the main body 1 is integrally formed with a first support portion 8 and a second support portion 9 that support the valve body 4.
- the first support portion 8 is formed by a through-hole through which the valve body portion 5 of the valve body 4 penetrates the valve chamber 14. When the valve body 4 is slidably inserted into the first support portion 8, the first support portion 8 is in sliding contact with the valve body body portion 5 to support the valve body 4.
- the second support portion 9 includes a coolant passage 13 through which the coolant (fluid) flows through the second passage 3 and the orifice 11, and a valve body support hole 12 into which the valve body tip cylindrical portion 7 is fitted. Is formed.
- the valve body support hole 12 is formed by an insertion hole having an inner diameter slightly larger than the outer diameter of the valve body tip cylinder portion 7 of the valve body 4, and the valve body tip cylinder portion 7 of the valve body 4 slides. By being inserted movably, the valve body 4 is supported in sliding contact with the valve body tip cylindrical portion 7.
- a plurality of refrigerant flow paths 13 are formed around the valve body tip cylindrical portion 7.
- the plurality of refrigerant flow paths 13 are each formed in a circular shape, and are arranged at substantially equal intervals on a circumference concentric with the orifice 11, for example, as shown in FIG.
- the refrigerant flow path 13 is formed such that the refrigerant flow direction forms an angle with the axial direction of the valve body support hole 12, that is, the central axis direction of the valve body body 5 of the valve body 4.
- coolant flow path 13 comprises the flow path which inclines toward the outer peripheral direction of the 2nd flow path from the orifice 11.
- the second support portion 9 is disposed with a space from the orifice 11, and the plurality of refrigerant flow paths 13 communicate with each other between the orifice 11 and the second support portion 9 by this space.
- the refrigerant channel 13 corresponds to the “main body channel” in the present invention.
- the refrigerant traveling from the first flow path 2 to the second flow path 3 is diverted from the outlet side of the orifice 11 to each refrigerant flow path 13 and reaches the second flow path 3.
- the refrigerant from the second flow path 3 to the first flow path 2 is divided into a plurality of refrigerant flow paths 13, and then merges again between the second support portion 9 and the orifice 11, and then to the orifice 11. It reaches.
- the valve body 4 is further moved upward and the flow passage area between the tapered portion 6 of the valve body 4 and the valve seat 10 is maximized (full opening degree), the flow rate is restricted by the orifice 11. (Second stage aperture).
- valve body 4 When the valve body 4 is moved downward by the rotation of the stepping motor 20, the valve body 4 slides downward while being supported by the first support portion 8 and the valve body support hole 12. . And the taper part 6 of the valve body 4 and the valve seat 10 contact
- valve body 4 and the valve seat 10 main body 1
- the contact portion between the valve body 4 and the valve seat 10 is given reproducibility.
- the degree of adhesion using a small amount of deformation generated in the valve body 4 or the valve seat 10 can be ensured.
- the refrigerant flow path 13 can be used as a restriction
- the opening area of the refrigerant flow path 13 is formed to be equal to or larger than the opening area of the orifice 11 of the valve seat 10 so that the refrigerant flow path 13 does not affect the first stage throttle and the second stage throttle. You may do it.
- FIG. 5 is a diagram showing a configuration of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the air conditioner includes a compressor 110, a condenser 120, an expansion device 100, and an evaporator 130, which are sequentially connected via a refrigerant pipe to constitute a refrigeration cycle.
- Compressor 110 compresses the refrigerant and flows it into condenser 120.
- the condenser 120 condenses the refrigerant compressed by the compressor 110.
- the expansion device 100 is connected to the condenser 120 through a refrigerant pipe constituting the first flow path 2, and expands the refrigerant condensed by the condenser 120. Further, the expansion device 100 is connected to the evaporator 130 by a refrigerant pipe constituting the second flow path 3. The evaporator 130 evaporates the refrigerant expanded by the expansion device 100.
- the low-pressure gas refrigerant when the compressor 110 is started, the low-pressure gas refrigerant is sucked into the compressor 110 and compressed to become a high-pressure gas refrigerant.
- the high-pressure gas refrigerant is condensed by the condenser 120 to become a high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant is decompressed by the expansion device 100 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and is evaporated by the evaporator 130 to become a low-pressure gas refrigerant.
- This low-pressure gas refrigerant is sucked into the compressor 110 again.
- the air conditioner performs heating using heat generated by the condenser 120.
- cooling is performed using the heat absorption of the evaporator 130.
- the evaporator 130 may be connected to the refrigerant pipe constituting the first flow path 2 of the expansion device 100, and the condenser 120 may be connected to the refrigerant pipe constituting the second flow path 3.
- a cooling / heating operation may be switched by providing a four-way valve to change the circulation direction of the refrigerant.
- the main body 1 is in sliding contact with the valve body body portion 5 to support the valve body 4 and the valve body tip column portion 7 is in sliding contact with the valve body 4.
- the valve body 4 is supported by the first support portion 8 and the second support portion 9. For this reason, compared with the case where the valve body 4 is supported only on one side, or when the support portion is disposed at a position farther than the valve seat even if supported by the first support portion and the second support portion, the valve body. It is possible to reduce the inclination of the valve body 4 with respect to the axial direction during opening and closing, and to suppress the change of the position of the contact portion between the valve body 4 and the valve seat 10.
- valve seat 10 it is possible to suppress the deformation or wear of the valve seat 10 from being biased by reproducible contact, and to improve the degree of adhesion between the valve body 4 and the valve seat 10. Therefore, an increase in the amount of valve leakage due to deformation or wear of the valve body or the valve seat can be suppressed. Moreover, the quality defect resulting from the valve leak of the expansion device 100 can be reduced, and a highly reliable air conditioner can be obtained.
- the flow direction of the refrigerant flow path 13 is formed at an angle with the axial direction of the support valve hole. For this reason, the flow channel area of the refrigerant flow channel 13 can be increased without increasing the size of the main body 1 (the size between the orifice 11 and the connection portion of the second flow channel 3).
- valve body tip column part 7 is formed on the central axis of the valve body body part 5, and the refrigerant flow path 13 of the second support part 9 is formed around the valve body support hole 12. A plurality are formed. For this reason, the circulation amount of the refrigerant between the orifice 11 and the second flow path 3 can be dispersed, and an increase in flow resistance can be suppressed. Moreover, it can reduce that the flow of a refrigerant
- Embodiment 2 FIG.
- the second support portion 9 is formed separately from the main body 1.
- the difference from the first embodiment will be mainly described.
- FIG. 6 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 2 of the present invention.
- 7 is a cross-sectional view taken along the line BB in FIG.
- the second support portion 9 in the present embodiment is configured by a disk-shaped member.
- the valve body support hole 12 is formed by a through hole provided in the center of the disk-shaped member, and is slightly smaller than the outer diameter of the valve body tip cylindrical portion 7 of the valve body 4 as in the first embodiment. Has a large inner diameter.
- the refrigerant flow path 13 is formed by a plurality of through holes provided in the disk-shaped member.
- the plurality of refrigerant flow paths 13 are each formed in a circular shape, and are arranged at substantially equal intervals on a circumference concentric with the orifice 11, for example, as shown in FIG.
- the refrigerant flow path 13 is formed so that the refrigerant flow direction is parallel to the axial direction of the valve body support hole 12, that is, the central axis direction of the valve body body 5 of the valve body 4.
- the disk-shaped member constituting the second support portion 9 is arranged with a gap from the orifice 11, and the plurality of refrigerant flow paths 13 are communicated with each other by this gap. Further, between the orifice 11 of the main body 1 and the disk-like member constituting the second support portion 9, a taper shape whose diameter is expanded from the opening end portion of the orifice 11 toward the connection end of the second flow path 3. have.
- Other configurations are the same as those of the first embodiment, and the same parts are denoted by the same reference numerals and description thereof is omitted.
- the second support portion 9 is formed separately from the main body 1. For this reason, the valve body support hole 12 and the coolant channel 13 formed in the second support portion 9 can be easily processed, and the manufacturing cost of the expansion device 100 can be reduced.
- the flow direction of the refrigerant flow path 13 is formed in parallel to the axial direction of the support valve hole. For this reason, processing of the refrigerant flow path 13 formed in the second support portion 9 is facilitated, and the manufacturing cost of the expansion device 100 can be reduced.
- Embodiment 3 FIG.
- the first support portion 8 is formed by a contact portion between the valve body 4 and the moving mechanism.
- the difference from the first and second embodiments will be mainly described.
- FIG. 8 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 3 of the present invention.
- an upper portion of the valve body 4 is provided with a female screw member 15 fixed to the main body 1 and a male screw 16 screwed into the female screw member 15.
- the female screw member 15 and the male screw 16 constitute a moving mechanism.
- the valve body 4 is biased toward the moving mechanism by a coil spring 17, and a recess 4 a formed at the upper end of the valve body 4 abuts against the end of the male screw 16.
- the male screw 16 is driven to rotate along with the rotation of the stepping motor 20, thereby moving in the axial direction (vertical direction) of the valve body 4 and moving the valve body 4 forward and backward toward the valve seat 10.
- the first support portion 8 in the present embodiment is formed by a contact portion between the valve body 4 and the moving mechanism, and the recess 4a at the upper end of the valve body 4 and the end portion of the male screw 16 come into contact with each other. The upper end side of the body 4 is supported.
- Other configurations are the same as those of the first embodiment, and the same parts are denoted by the same reference numerals and description thereof is omitted. Note that the configuration of the first support portion 8 in the third embodiment may be applied to the configuration of the second embodiment.
- the clearance between the through hole through which the valve body 5 of the valve body 4 penetrates the valve chamber 14 and the valve body 5 is made larger so that the through hole and the valve body 5 And may not be in sliding contact with each other.
- the configuration in which the recess 4a at the upper end of the valve body 4 and the end of the male screw 16 are in contact with each other has been described.
- the present invention is not limited to this, and the first support 8 Any configuration may be used as long as the end of the valve body 4 on the moving mechanism side and the moving mechanism are in contact with each other to support the valve body 4.
- it can reduce that the valve body 4 inclines with respect to an axial direction at the time of valve body opening and closing, and can suppress that the position of the contact part of the valve body 4 and the valve seat 10 changes. Therefore, it is possible to suppress the deformation or wear of the valve seat 10 from being biased by reproducible contact, and to improve the degree of adhesion between the valve body 4 and the valve seat 10. Therefore, an increase in the amount of valve leakage due to deformation or wear of the valve body or the valve seat can be suppressed. Moreover, the quality defect resulting from the valve leak of the expansion device 100 can be reduced, and a highly reliable air conditioner can be obtained.
- each of the six refrigerant flow paths 13 has a circular shape and is arranged at substantially equal intervals on the circumference.
- the present invention is not limited to this.
- any number and size of the refrigerant flow paths 13 may be formed.
- a circular shape that is easy to process can be manufactured at a lower cost.
- the flow path area can be increased by using a fan shape or an ellipse.
- valve body tip deflection the amount of change in the position of the contact portion between the valve body and the valve seat in the throttle device according to the embodiment of the present invention
- FIG. 10 is a diagram schematically showing a configuration of a conventional diaphragm device.
- the valve body in the conventional throttle device, the valve body is supported by a support portion at a position far from the valve seat.
- the valve element is supported at two points: a fulcrum and a valve guide (a through hole through which the valve element penetrates the valve chamber) serving as a support part. And the tip of the valve body swings within the clearance range of the support portion).
- valve tip deflection The parameters that affect the valve tip deflection are defined as follows: [length] Support point to support length: m Support section to valve seat length: n [clearance] Displacement of fulcrum (deviation generated between valve body shaft and body shaft): e Clearance of support part (clearance between valve body and valve guide): c [Valve tip deflection] Valve body tip deflection (deviation between valve body and body shaft in valve seat): E
- FIG. 11 is a diagram illustrating a calculation formula for the valve element tip deflection of the conventional throttling device.
- the valve body is brought into contact with the valve guide to simulate a state in which the valve body sag is maximized.
- the valve element tip end deflection E can be obtained by the equations (1) and (2) in FIG.
- FIG. 12 is a diagram schematically illustrating the configuration of the diaphragm device according to the embodiment of the present invention.
- FIG. 13 is a diagram illustrating a calculation formula for the valve element tip deflection of the throttling device according to the embodiment of the present invention.
- parameters that affect the valve tip deflection are defined as follows.
- Support point to length of support part (length of first support part to second support part): m Support section to valve seat length (second support section to valve seat length): n [clearance] Displacement of fulcrum (deviation generated between valve body shaft and body shaft): e Support part clearance (clearance between valve body and second support part): c [Valve tip deflection] Valve body tip deflection (deviation between valve body and body shaft in valve seat): E
- valve element tip deflection E can be obtained by the equations (3) and (4) in FIG.
- FIG. 14 is a diagram showing the result of the valve element tip deflection E calculated from the specifications of each valve element support structure.
- FIG. 14 shows the result of calculating the valve body tip deflection E by assuming the parameters (e, m, n, c) that affect the valve tip deflection from the type and outline specifications of the throttle device. As shown in the drawing, it can be seen that the valve body tip deflection E is smaller in the throttling device of the embodiment of the present invention than in the conventional throttling device.
- FIG. 15 is a diagram showing the valve element tip deflection calculation formula separately for shaft misalignment and guide clearance.
- FIG. 16 is a diagram in which numerical values are extracted from the case where the deviation between the valve body axis and the main body axis is 0.15 mm. The following can be said from the calculation formula of FIG. 15 and the calculation result of FIG. (1) With regard to the length of the support portion, the larger the ratio of the fulcrum to the length m of the support portion and the length n of the support portion to the valve seat, the smaller the valve body tip deflection E becomes. (2) In the conventional throttling device, the valve element tip deflection E is obtained by adding the influence of the guide clearance to the influence of the shaft misalignment. On the other hand, the diaphragm device according to the embodiment of the present invention has a feature that cancels the influence of the shaft deviation by the influence of the guide clearance.
- the amount of change in the position of the contact portion between the valve body and the valve seat is greatly influenced by the clearance c between the valve body and the valve guide.
- the amount of change in the position of the contact portion between the valve body and the valve seat is affected by the clearance c between the valve body and the second support portion. small. It should be noted that the effect of reducing the tip E of the valve element is further increased by reducing the shift e of the fulcrum and increasing the length m of the fulcrum to the second support part.
Abstract
Description
空気調和装置に使用される絞り装置では、空気調和装置が運用される中で、絞り装置の開閉回数の増加や、冷媒の流れ方向が正方向と逆方向で変化することで、弁体と弁座の接触部の磨耗量が増加して絞り装置の弁漏れに起因する品質不具合が発生し、信頼性が低下する、という問題点があった。
また、絞り装置の弁漏れに起因する品質不具合を低減し、信頼性の高い空気調和装置を得るものである。
(絞り装置)
図1は、本発明の実施の形態1における絞り装置の構成を示す図である。
図2は、本発明の実施の形態1における絞り装置の要部の断面図である。
図3は、図2におけるA-A矢視断面図である。
図4は、流量調整時における弁体の位置を示す図である。
図に示すように、絞り装置100は、第1流路2と第2流路3とが接続される本体1と、本体1内部に形成され第1流路2と連通する弁室14と、弁室14に形成され第2流路3と連通するオリフィス11を有する弁座10と、弁室14を貫通して、弁座10のオリフィス11に向かって進退自在に設けられ、オリフィス11の開度を調節する弁体4とを備えている。
また、弁体4の上部には、弁体4と図示しない移動機構を介して連結されたロータと、ステータとにより構成されるステッピングモータ20を備えている。このステッピングモータ20の回転が移動機構によって並進距離に変換され、弁体4が軸方向(上下方向)に移動して弁座10の開口の開度を制御する。
次に、絞り装置100における冷媒の流れについて説明する。
図2に示すように、全閉時には弁体4のテーパ部6と弁座10とが当接して密着状態で保持される。このとき、弁体4は、弁体胴体部5が第1支持部8により支持され、弁体先端円柱部7が弁体支持用孔12により支持されている。
図4に示すように、ステッピングモータ20の回転により弁体4が上方に移動されると、弁体4は、第1支持部8と弁体支持用孔12により支持されたままの状態で上方へ摺動移動する。これにより弁体4のテーパ部6と弁座10との間の流路面積が変化し、流量が調節される(1段目絞り)。このとき、第1流路2から第2流路3へ向かう冷媒は、オリフィス11の出口側から各冷媒流路13に分流して第2流路3へと至る。また、第2流路3から第1流路2へ向かう冷媒は、複数の冷媒流路13に分流されたあと、第2支持部9とオリフィス11との間で再び合流し、オリフィス11へと至る。
そして、さらに弁体4を上方に移動させ、弁体4のテーパ部6と弁座10との間の流路面積が最大とした場合(全開開度)においては、オリフィス11によって流量が制限される(2段目絞り)。
また、ステッピングモータ20の回転により弁体4が下方に移動されると、弁体4は、第1支持部8と弁体支持用孔12により支持されたままの状態で下方へ摺動移動する。そして、弁体4のテーパ部6と弁座10とが当接して密着状態で保持することで全閉状態となる。
このように、弁体4は、第1支持部8と弁体支持用孔12により支持されたままの状態で移動するため、弁体開閉時での弁体先端の振れを軽減して、弁体4のテーパ部6と弁座10との接触部分の位置が変化することを抑制して再現性のある接触を実現できる。また、弁体4及び弁座10(本体1)の少なくとも一方に真鍮などの硬度の低い材料を用いた場合には、弁体4と弁座10との接触部に再現性を持たせることで、弁体4または弁座10に生じる少量の変形を利用した密着度の確保することができる。
次に、上記絞り装置100を備えた空気調和装置について説明する。
図5は、本発明の実施の形態1における空気調和装置の構成を示す図である。
図5に示すように、空気調和装置は、圧縮機110、凝縮器120、絞り装置100、および蒸発器130を備え、順次、冷媒配管で接続されて冷凍サイクルを構成している。
この冷凍サイクルにより、空気調和装置は、凝縮器120での発熱を利用して暖房を行う。また、蒸発器130の吸熱を利用して冷房を行う。
なお、絞り装置100の第1流路2を構成する冷媒配管に蒸発器130を接続し、第2流路3を構成する冷媒配管に凝縮器120を接続するようにしても良い。また、四方弁を設けて冷媒の循環方向を変えることにより、冷房・暖房運転の切り替えを行うようにしても良い。
このため、弁体4を片側のみで支持する場合や、第1支持部と第2支持部とにより支持しても支持部が弁座よりも遠い位置に配置する場合と比較して、弁体開閉時に弁体4が軸方向に対して傾くことを軽減し、弁体4と弁座10との接触部分の位置が変化することを抑制することができる。よって、再現性のある接触により、弁座10の変形または磨耗に偏りが生じることを抑制し、弁体4と弁座10との密着度を向上させることができる。したがって、弁体または弁座の変形や磨耗を要因とする弁漏れ量の増加を抑制することができる。
また、絞り装置100の弁漏れに起因する品質不具合を低減し、信頼性の高い空気調和装置を得ることができる。
このため、本体1の寸法(オリフィス11と第2流路3の接続部との間の寸法)を大きくすることなく、冷媒流路13の流路面積を大きくすることができる。
このため、オリフィス11と第2流路3との間の冷媒の流通量を分散し、流動抵抗の増加を抑制することができる。また、複数の冷媒流路13を等間隔に配置することで冷媒の流れに偏りが生じることを軽減することができる。
本実施の形態2における絞り装置100は、第2支持部9を、本体1とは別体で形成している。以下、上記実施の形態1との相違点を中心に説明する。
図7は、図6におけるB-B矢視断面図である。
図に示すように、本実施の形態における第2支持部9は、円盤状の部材により構成されている。弁体支持用孔12は、円盤状部材の中心部に設けられた貫通孔により形成され、上記実施の形態1と同様に、弁体4の弁体先端円柱部7の外径よりも、僅かに大きい内径を有する。
なお、その他の構成は上記実施の形態1と同様であり、同一部分には同一の符号を付し、説明を省略する。
本実施の形態3における絞り装置100は、第1支持部8を、弁体4と移動機構との接触部により形成している。以下、上記実施の形態1、2との相違点を中心に説明する。
図に示すように、弁体4の上部には、本体1に固定された雌ねじ部材15とこの雌ねじ部材15に螺合する雄ねじ16とが設けられている。雌ねじ部材15および雄ねじ16は移動機構を構成する。
弁体4は、コイルスプリング17によって移動機構側に付勢されており、弁体4の上端に形成された窪み4aが雄ねじ16の端部と当接する。雄ねじ16は、ステッピングモータ20の回転に伴い回転駆動されることで弁体4の軸方向(上下方向)に移動して、弁体4を弁座10に向かって進退させる。
本実施の形態における第1支持部8は、弁体4と移動機構との接触部により形成されており、弁体4の上端の窪み4aと雄ねじ16の端部とが接触することで、弁体4の上端側を支持する。
なお、その他の構成は上記実施の形態1と同様であり、同一部分には同一の符号を付し、説明を省略する。なお、本実施の形態3における第1支持部8の構成を、上記実施の形態2の構成に適用しても良い。
なお、本実施の形態3においては、弁体4の上端の窪み4aと雄ねじ16の端部とが接触する構成を説明したが、本発明はこれに限られるものではなく、第1支持部8は、弁体4の移動機構側の端部と移動機構とが接触して弁体4を支持する構成であれば良い。
また、絞り装置100の弁漏れに起因する品質不具合を低減し、信頼性の高い空気調和装置を得ることができる。
例えば図9の<a>~<i>に示すように、任意の数および大きさの冷媒流路13を形成しても良い。図9の<a>~<f>に示すように、加工の容易な円形とした方が低コストで製作できる。また、図9の<g>~<i>に示すように、扇型または楕円形とすることで、流路面積を大きくすることができる。
図10に示すように、従来の絞り装置は、弁体の支持を、弁座から遠い位置の支持部で実施している。
このような従来の絞り装置において、弁体は、支点と支持部となる弁ガイド(弁体が弁室に貫通する貫通孔)の2点で支持されており、弁座で各支持部(支点及び支持部)のクリアランスの範囲で弁体先端が振れることとなる。
弁先端振れに影響するパラメータを以下のように定義する。
[長さ]
支点~支持部の長さ:m
支持部~弁座の長さ:n
[クリアランス]
支点のズレ(弁体の軸と本体軸との間に発生するズレ):e
支持部のクリアランス(弁体と弁ガイドとのクリアランス):c
[弁体先端振れ]
弁体先端振れ(弁座において弁体と本体軸の間に発生するズレ):E
図11では、弁体を弁ガイドに接触させ、弁体のたおれを最大にした状態を模擬している。また、弁体先端振れEは、図11の式(1)、式(2)により求めることができる。
図13は、本発明の実施例に係る絞り装置の弁体先端振れの算出式を示す図である。
本発明の実施例の絞り装置においては、図12に示すように、弁先端振れに影響するパラメータを以下のように定義する。
[長さ]
支点~支持部の長さ(第1支持部~第2支持部の長さ):m
支持部~弁座の長さ(第2支持部~弁座の長さ):n
[クリアランス]
支点のズレ(弁体の軸と本体軸との間に発生するズレ):e
支持部のクリアランス(弁体と第2支持部とのクリアランス):c
[弁体先端振れ]
弁体先端振れ(弁座において弁体と本体軸の間に発生するズレ):E
図14においては、弁先端振れに影響するパラメータ(e、m、n、c)を、絞り装置の種類・概略仕様から想定し、弁体先端振れEを算出した結果を示している。
図に示すように、従来の絞り装置と比較して、本発明の実施例の絞り装置は、弁体先端振れEが小さくなることが分かる。
図16は、弁体軸と本体軸とのズレが0.15mmの場合から数値を抜粋した図である。
図15の計算式、図16の算出結果より以下のことが言える。
(1)支持部の長さにおいて、支点~支持部の長さmと、支持部~弁座の長さnの比が大きい方が弁体先端振れEが小さくなる。
(2)従来の絞り装置では、軸ズレの影響にガイドクリアランスの影響を加算したものが弁体先端振れEとなる。
それに対して、本発明の実施例の絞り装置では、軸ズレの影響をガイドクリアランスの影響でキャンセルする特徴を有する。
一方、本発明の実施例の絞り装置においては、弁体と弁座との接触部分の位置の変化量(弁体先端振れE)は、弁体と第2支持部とのクリアランスcによる影響が小さい。なお、支点のズレeを小さくし、支点~第2支持部の長さmを長くすることで、より弁体先端振れEを軽減する効果が大きくなる。
Claims (10)
- 第1流路と第2流路とが接続される本体と、
前記本体内部に形成され前記第1流路と連通する弁室と、
前記弁室に形成され前記第2流路と連通する開口を有する弁座と、
前記弁室を貫通して、前記弁座の開口に向かって進退自在に設けられ、前記開口の開度を調節する弁体と
を備え、
前記弁体は、
前記弁室を貫通する弁体胴体部と、
前記弁座の開口よりも小径に形成された弁体先端柱部と、
前記弁体胴体部と前記弁体先端柱部とを接続するテーパ部とを有し、
前記本体は、
前記弁体胴体部が前記弁室に貫通する貫通孔により形成され、前記弁体胴体部と摺接して前記弁体を支持する第1支持部と、
前記第2流路と前記弁座の開口とを連通する本体流路と、前記弁体先端柱部が嵌入される弁体支持用孔とが形成され、前記弁体支持用孔が前記弁体先端柱部と摺接して前記弁体を支持する第2支持部とを有する
ことを特徴とする絞り装置。 - 第1流路と第2流路とが接続される本体と、
前記本体内部に形成され前記第1流路と連通する弁室と、
前記弁室に形成され前記第2流路と連通する開口を有する弁座と、
前記弁室を貫通して、前記弁座の開口に向かって進退自在に設けられ、前記開口の開度を調節する弁体と、
前記弁体を前記弁座の開口に向かって進退させる移動機構と
を備え、
前記弁体は、
前記弁室を貫通する弁体胴体部と、
前記弁座の開口よりも小径に形成された弁体先端柱部と、
前記弁体胴体部と前記弁体先端柱部とを接続するテーパ部と、
前記弁体の前記移動機構側の端部に形成され、前記移動機構と接触して当該弁体を支持する第1支持部とを有し、
前記本体は、
前記第2流路と前記弁座の開口とを連通する本体流路と、前記弁体先端柱部が嵌入される弁体支持用孔とが形成され、前記弁体支持用孔が前記弁体先端柱部と摺接して前記弁体を支持する第2支持部を有する
ことを特徴とする絞り装置。 - 前記本体流路の流通方向が、前記弁体支持用弁孔の軸方向と角度をなして形成された
ことを特徴とする請求項1または2記載の絞り装置。 - 前記本体流路の流通方向が、前記弁体支持用弁孔の軸方向と平行に形成された
ことを特徴とする請求項1または2記載の絞り装置。 - 前記弁体先端柱部は、前記弁体胴体部の中心軸上に形成され、
前記第2支持部の前記本体流路は、前記弁体支持用孔の周囲に複数形成された
ことを特徴とする請求項1~4の何れか一項に記載の絞り装置。 - 前記本体流路の開口面積が、前記弁座の開口の開口面積よりも小さくなるように形成された
ことを特徴とする請求項1~5の何れか一項に記載の絞り装置。 - 前記本体流路の開口面積が、前記弁座の開口の開口面積以上となるように形成された
ことを特徴とする請求項1~5の何れか一項に記載の絞り装置。 - 前記第2支持部は、前記本体と一体に形成された
ことを特徴とする請求項1~7の何れか一項に記載の絞り装置。 - 前記第2支持部は、前記本体とは別体で形成された
ことを特徴とする請求項1~7の何れか一項に記載の絞り装置。 - 冷媒を圧縮する圧縮機と、
前記圧縮機によって圧縮された冷媒を凝縮する凝縮器と、
前記凝縮器によって凝縮された冷媒を膨張する、請求項1~9の何れか一項に記載の絞り装置と、
前記絞り装置によって膨張された冷媒を蒸発する蒸発器とを備えた
ことを特徴とする空気調和装置。
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WO2016075872A1 (ja) * | 2014-11-12 | 2016-05-19 | 株式会社鷺宮製作所 | 絞り装置、および、それを備える冷凍サイクルシステム |
EP3075459A1 (en) * | 2015-03-30 | 2016-10-05 | Alfa Laval Corporate AB | Fluid ejection apparatus |
JP2019158154A (ja) * | 2019-07-01 | 2019-09-19 | 株式会社鷺宮製作所 | 電動弁 |
EP3822265A1 (en) | 2019-11-15 | 2021-05-19 | Bayer AG | Substituted hydantoinamides as adamts7 antagonists |
EP3822268A1 (en) | 2019-11-15 | 2021-05-19 | Bayer Aktiengesellschaft | Substituted hydantoinamides as adamts7 antagonists |
US11313601B2 (en) | 2017-08-29 | 2022-04-26 | Hangzhou Sanhua Research Institute Co., Ltd. | System and method for controlling an expansion valve |
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WO2016075872A1 (ja) * | 2014-11-12 | 2016-05-19 | 株式会社鷺宮製作所 | 絞り装置、および、それを備える冷凍サイクルシステム |
JP2016095049A (ja) * | 2014-11-12 | 2016-05-26 | 株式会社鷺宮製作所 | 絞り装置、および、それを備える冷凍サイクルシステム |
EP3075459A1 (en) * | 2015-03-30 | 2016-10-05 | Alfa Laval Corporate AB | Fluid ejection apparatus |
EP3075460A1 (en) * | 2015-03-30 | 2016-10-05 | Alfa Laval Corporate AB | Fluid ejection apparatus |
US11313601B2 (en) | 2017-08-29 | 2022-04-26 | Hangzhou Sanhua Research Institute Co., Ltd. | System and method for controlling an expansion valve |
JP2019158154A (ja) * | 2019-07-01 | 2019-09-19 | 株式会社鷺宮製作所 | 電動弁 |
EP3822265A1 (en) | 2019-11-15 | 2021-05-19 | Bayer AG | Substituted hydantoinamides as adamts7 antagonists |
EP3822268A1 (en) | 2019-11-15 | 2021-05-19 | Bayer Aktiengesellschaft | Substituted hydantoinamides as adamts7 antagonists |
WO2021094436A1 (en) | 2019-11-15 | 2021-05-20 | Bayer Aktiengesellschaft | Substituted hydantoinamides as adamts7 antagonists |
WO2021094434A1 (en) | 2019-11-15 | 2021-05-20 | Bayer Aktiengesellschaft | Substituted hydantoinamides as adamts7 antagonists |
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