WO2007142021A1 - Vanne à régulation d'ouverture et compresseur à capacité variable l'employant - Google Patents

Vanne à régulation d'ouverture et compresseur à capacité variable l'employant Download PDF

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Publication number
WO2007142021A1
WO2007142021A1 PCT/JP2007/060397 JP2007060397W WO2007142021A1 WO 2007142021 A1 WO2007142021 A1 WO 2007142021A1 JP 2007060397 W JP2007060397 W JP 2007060397W WO 2007142021 A1 WO2007142021 A1 WO 2007142021A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
opening
case member
opening adjustment
valve body
Prior art date
Application number
PCT/JP2007/060397
Other languages
English (en)
Japanese (ja)
Inventor
Yoshihiro Adachi
Tomoyasu Takahashi
Yoshie Sato
Original Assignee
Valeo Thermal Systems Japan Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Thermal Systems Japan Corporation filed Critical Valeo Thermal Systems Japan Corporation
Publication of WO2007142021A1 publication Critical patent/WO2007142021A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1881—Suction pressure

Definitions

  • the present invention provides an opening adjustment valve that is provided in a flow path that communicates a suction port and a suction chamber of a compressor, and that variably controls the opening of the flow path, and a variable capacity that uses the opening adjustment valve.
  • an opening adjustment valve that is provided in a flow path that communicates a suction port and a suction chamber of a compressor, and that variably controls the opening of the flow path, and a variable capacity that uses the opening adjustment valve.
  • the valve body of the opening adjustment valve undergoes minute repeated movement at a minute flow rate, and this minute repeated movement causes pressure pulsation of the refrigerant gas. It has been pointed out that the pressure pulsation of the medium gas propagates from the suction port to the external refrigerant circuit, and this pressure pulsation causes the evaporator to vibrate in the same way, generating noise.
  • Patent Document 2 Japanese Patent Application Laid-Open No. 2000-136776
  • Patent Document 2 Japanese Patent Laid-Open No. 2001-289177
  • a bypass passage is provided so that the refrigerant can flow even at a minute flow rate, and an air damper is formed by using the bypass passage.
  • the force bypass passage is formed by cutting out the case of the pressure regulating valve, and after the passage is closed, the refrigerant flows through the notch.
  • the opening area changes almost linearly in the process of gradually decreasing, the passage area of the refrigerant becomes only a notch cross-sectional area at a minute flow rate, and the passage area changes rapidly, so the suction characteristics change suddenly and the performance decreases. Inconvenience.
  • the present invention has been made in view of the circumstances described above, and at the time of shifting to a minute flow rate, even if the passage cross section is gradually changed, a sudden change in the suction characteristics can be avoided.
  • the main challenge is to provide a possible opening adjustment valve and a variable displacement compressor using this valve.
  • an opening adjusting valve is disposed in a flow path that connects a suction port and a suction chamber of a compressor, and variably controls an opening area of the flow path.
  • a cylindrical case member having a peripheral wall in which a plurality of through holes are formed, and a valve body accommodated in the case member so as to be slidable in the axial direction and biased in a valve closing direction by a return spring.
  • a stopper portion for restricting movement of the valve body in the valve closing direction so as to leave an opening region of the through hole upstream of the valve body (Claim 1). .
  • the valve element moves in the valve closing direction by the return spring and attempts to block the communication between the upstream side of the valve element and the through hole. Movement force of the valve body in the valve closing direction so as to leave the opening area of the hole. Because it is regulated by the S stopper part, the communication between the upstream side of the valve body and the through hole is completely blocked by this stopper part. None will happen. For this reason, the passage cross section between the upstream side and the downstream side of the valve element is prevented from suddenly changing due to the complete closure of the through-hole, and the passage cross section between the upstream side and the downstream side is gradually changed at the time of high flow force and minute flow rate. It is possible to prevent the passage cross section from changing suddenly when the flow rate is small.
  • the stagger portion is formed on the inner side of the column portion formed between adjacent through holes in the peripheral wall of the case member (Claim 2).
  • the stagger portion is formed on the inner side of the column portion formed between adjacent through holes in the peripheral wall of the case member (Claim 2).
  • the return spring and the valve body are also accommodated in the case member for the upstream force, and the stopper portion is formed on, for example, the peripheral edge of the lid member attached to the upstream force case member (claim 3).
  • the lid member is attached to the case member from the upstream side, there is no possibility that the lid member is detached by the fluid pressure sucked.
  • the lid member may be fixed to the case member by locking a claw portion provided on the lid member to the case member (claim 4).
  • the claw portion and the stopper portion may be formed separately, or the claw portion and the stopper portion may be formed integrally (claims 5 and 6).
  • the opening adjustment valve as described above is useful when used as a compressor, particularly in a variable displacement compressor, that is, when a compressor capable of setting the flow rate of the working fluid to a minute flow rate is used. (Claim 7).
  • the opening adjustment valve that is disposed in the flow path that communicates the suction port and the suction chamber of the compressor and variably controls the opening area of the flow path is provided with a through hole.
  • a through hole Comprises a case member formed on the peripheral wall, and a valve body housed in the case member and urged in the valve closing direction by the return panel, and moves the valve body in the valve closing direction. Since the opening area of the through hole remains on the upstream side of the valve body by the strobe portion, the passage cross section between the upstream side of the valve body and the through hole is subjected to a high flow rate force and a minute flow rate. By gradually changing it, it is possible to prevent sudden changes in the passage cross section, and it is possible to avoid sudden changes in inhalation characteristics.
  • FIG. 1 is a cross-sectional view showing a configuration example of a variable capacity compressor according to the present invention.
  • FIG. 2 is an enlarged view of a portion where an opening degree adjusting valve is provided in a flow path communicating the suction port and the suction chamber.
  • FIG. 3 is a view showing the state of the opening adjustment valve at a high flow rate.
  • FIG. 3 (a) is a cross-sectional view taken along line A—A in FIG. ) Is a perspective view. o
  • FIG. 4 A diagram showing the state of the opening adjustment valve at a minute flow rate.
  • Fig. 4 (a) is a cross-sectional view taken along line AOC AO C in Fig. 4 (b), and
  • Fig. 4 (b) is a perspective view. It is.
  • FIG. 5 is an exploded view showing the opening adjustment valve.
  • FIG. 5 (a) is a cross-sectional view taken along line A—A in FIG. 5 (b), and
  • FIG. 5 (b) is a perspective view. is there.
  • Fig. 6 is a view showing another example of the opening adjustment valve.
  • Fig. 6 (a) is a cross-sectional view taken along the line A-A in Fig. 6 (b), and
  • Fig. 5 (b) is a diagram. It is a perspective view.
  • FIG. 1 a variable capacity compressor suitable for a refrigeration cycle using a refrigerant as a working fluid is shown.
  • This compressor is, for example, a clutchless type swash plate type variable capacity compressor, and includes a cylinder block 1, a rear head 3 assembled to the rear side of the cylinder block 1 via a valve plate 2, and a cylinder block 1.
  • the front side of the cylinder block 1 is assembled so as to cover the front side, and the front head 5 that defines the crank chamber 4 is configured.
  • the front head 5, cylinder block 1, nozzle plate 2, and rear head 3 are fastened in the axial direction by fastening bolts 6.
  • a drive shaft 7 disposed in the crank chamber 4 is rotatably held by the front head 5 and the cylinder block 1 via bearings 8 and 9, and this drive shaft 7 is used for traveling (not shown). It is connected to the engine through a belt and pulley, and the power of the traveling engine is transmitted to rotate.
  • the cylinder block 1 is formed with a recess 11 in which the bearing 9 is accommodated, and a plurality of cylinder bores 12 arranged at equal intervals on a circumference centered on the recess 11.
  • a single-head piston 13 is inserted into each cylinder bore 12 so as to be reciprocally slidable.
  • a thrust flange 14 that rotates integrally with the drive shaft 7 is fixed to the drive shaft 7 in the crank chamber 4.
  • the thrust flange 14 is rotatably supported by an inner wall surface of the front head 5 formed substantially perpendicular to the drive shaft 7 via a thrust bearing 15.
  • a swash plate 21 is connected to the thrust flange 15 via a link member 20.
  • the swash plate 21 is held so as to be tiltable via a hinge ball 22 provided on the drive shaft 7, and rotates integrally with the rotation of the thrust flange 14. Then, the engaging portion 13a of the single-headed piston 13 is moored to the peripheral portion of the swash plate 21 through a pair of bushes 23 provided at the front and rear.
  • the valve plate 2 is formed with suction holes 31 and discharge holes 32 corresponding to the respective cylinder bores 12, and the rear head 3 is a suction chamber that stores the working fluid supplied to the compression chamber 25. 33 and a discharge chamber 34 for storing the working fluid discharged from the compression chamber 25 are provided.
  • the suction chamber 33 is formed in the center portion of the rear head 3, and the discharge chamber 34 is formed around the suction chamber 33.
  • the suction chamber 33 communicates with a suction port 35 connected to the low pressure side of the external refrigerant circuit (the outlet side of the evaporator), and the discharge chamber 34 is connected to the high pressure side of the external refrigerant circuit (the inlet side of the radiator) Connected to a discharge port (not shown).
  • the suction chamber 33 is connected to a suction valve (not shown).
  • the discharge chamber 34 can communicate with the compression chamber 25 via the discharge hole 32 that is opened and closed by a discharge valve (not shown). ing.
  • the discharge capacity of this compressor is determined by the stroke of the piston 13, and this stroke is determined by the inclination angle of the swash plate 21 with respect to the plane perpendicular to the drive shaft 7. That is, the difference between the pressure acting on the front surface of the piston 13, that is, the pressure in the compression chamber 25 (pressure in the cylinder bore) and the pressure acting on the back surface of the piston 13, that is, the pressure in the crank chamber 4 (crank chamber pressure).
  • the inclination of the swash plate 21 is determined where the pressure and the urging force of the destroke spring 28 that urges the hinge ball 22 in the direction of decreasing the piston stroke are balanced, thereby determining the piston stroke and the discharge capacity. Is now decided! /
  • the rear head 3 is provided with a pressure control valve (not shown) that variably controls at least one of the communication state between the discharge chamber 34 and the crank chamber 4 and the communication state between the crank chamber 4 and the suction chamber 33.
  • the pressure control valve controls the pressure in the crank chamber 4 to adjust the piston stroke, that is, the discharge capacity.
  • the swash plate 21 rotates with a predetermined inclination, so that the edge portion of the swash plate 21 swings with a predetermined width in the axial direction of the drive shaft 7. .
  • the piston 13 held at the edge of the swash plate 21 reciprocates with a predetermined stroke in the axial direction of the drive shaft 7, changing the volume of the compression chamber 25 defined in the cylinder bore 12, and
  • the refrigerant is sucked into the compression chamber 25 from the suction chamber 33 through the suction hole 31 opened and closed by the suction valve, and during the compression stroke, the refrigerant is drawn through the discharge hole 32 opened and closed by the discharge valve.
  • the compressed refrigerant is discharged from the compression chamber 25 to the discharge chamber 34.
  • an opening degree adjusting valve 40 is disposed on the downstream side of the suction port 35, that is, in the flow path 36 that connects the suction port 35 and the suction chamber 33.
  • the opening adjustment valve 40 has a bottomed cylindrical case member 41, and a valve body 42 is accommodated in the case member 41 so as to be slidable in the axial direction. Yes.
  • the case member 41 has a plurality of through holes (for example, four through holes) 43 formed in the peripheral wall at equal intervals, and the upstream end opening 41b and the bottom 41a of the case member 41 are connected between adjacent through holes.
  • a column portion 44 having a predetermined width is formed.
  • the bottom 41a of the case member 41 has a predetermined diameter in the center.
  • a through hole 45 is formed, and an annular groove 46 is formed around the through hole 45 to serve as a panel receiver for receiving a return spring described later.
  • the upstream end opening 41b is formed with a lid mounting portion 47 having an inner diameter larger than that of the peripheral wall in which the through hole 43 is formed, and the through hole 43 is formed in a substantially rectangular shape.
  • an engagement margin 49 is formed by cutting away toward the upstream end opening 41b.
  • the valve body 42 is formed in a bottomed cylindrical shape having a diameter substantially equal to the inner diameter of the case member 41 so that a predetermined clearance is secured between the valve member 42 and the case member 41, and the downstream side ( The lower part of the figure is accommodated so as to open. Then, one end of the return spring 50 can be accommodated from the downstream side, and the return spring 50 is fitted between the annular groove 46 of the case member 41, and the upstream end opening 41b is closed by the return spring 50. Always energized in the valve closing direction (upstream).
  • a lid member 51 is engaged with the upstream end opening 41b of the case member 41.
  • the lid member 51 is formed in a ring shape, and a locking portion that protrudes outward in the radial direction so as to be held by the lid mounting portion on the side of the ring portion 52.
  • a plurality of protrusions 53 are formed at equal intervals in the circumferential direction.
  • claw portions 54 extending toward the downstream side are formed at the lower end of the ring portion 52 at equal intervals according to the number of through holes.
  • the claw portions 54 are extended from between the adjacent locking projections 53 in the axial direction of the case member 41 (by downward force in the figure), and are formed at four positions at intervals of 90 degrees.
  • a barb 54a projecting outward is formed at the tip, and the barb 54a can be engaged by being accommodated in an engagement margin 49 formed at the upstream end edge of the through hole 43. Therefore, the claw portion 54 is engaged with the engagement margin 49 so that it does not protrude downstream from the upstream end edge of the through hole 43!
  • Stopper part 55 is formed.
  • the stopper portion 55 is formed in accordance with the position of the column portion 44 of the case member 41, and is formed with a width equal to or smaller than the width of the column portion 44.
  • the stopper protrusion 55 is formed. It is arranged below the portion 53 and is formed inside the support portion 44 without facing the through hole 43.
  • the tip of the stagger 55 is downstream of the tip of the claw 54, and It is located downstream of the upstream edge of the through-hole 43 (the amount of extension of the stopper 55 to the downstream side is larger than the amount of extension of the claw 54 to the downstream side, It protrudes below the upstream edge of the through hole 43).
  • valve body 42 When the refrigerant flow rate decreases, the valve body 42 is displaced to a position where the pressure of the refrigerant received from the upstream side and the spring force of the return spring 50 received from the downstream side are balanced, and the refrigerant to be sucked in Depending on the flow rate, the size of the opening region of the through hole 43 formed on the upstream side of the valve element 42 changes.
  • the spring force of the return spring 50 overcomes the force of the refrigerant that pushes the valve element 42 from the upstream side, and displaces the valve element 42 to the most upstream side that can be moved.
  • the valve body 42 since the tip of the stubbing portion 55 formed on the lid member 51 protrudes downstream from the upstream end edge of the through hole 43, the valve body 42 abuts against the stopper portion 55 and moves to the upstream side. The above displacement is prevented, and an opening region of the through hole 43 that is not blocked by the valve body 42 remains on the upstream side of the valve body 42. For this reason, the refrigerant flowing from the suction port 35 is guided to the suction chamber 33 through the opening region force of the through-hole 43 on the upstream side of the valve body 42 to the periphery of the cover member 51.
  • the movement of the valve body 42 in the valve closing direction is left in the stopper portion 55 so as to leave the opening region of the through hole 43 upstream of the valve body 42 even at a minute flow rate. Therefore, the communication between the upstream side of the valve element 42 and the through hole 43 is not completely blocked by the stopper portion 55. For this reason, the cross section of the passage between the upstream side of the valve element 42 and the through hole 43 can be gradually changed from a high flow rate to a micro flow rate, and the passage cross section rapidly changes when the flow rate changes to a micro flow rate. This makes it possible to prevent sudden changes in inhalation characteristics.
  • the stopper portion 55 is a through hole 43 adjacent to the peripheral wall of the case member 41. Since the stopper portion 55 protrudes downstream from the through-hole 43, the opening area of the through-hole 43 is not blocked, and the valve body 42 is disposed. With this displacement, it is possible to ensure a continuous change in the passage cross section.
  • the return spring 50 and the valve element 42 are accommodated in the case member 41 by the upstream force, and the lid member 51 is attached to the upstream opening end of the case member 41 from the upstream side. It is possible to obtain a strong structure with no risk of detachment due to inhaled fluid pressure.
  • FIG. 6 shows a modified example of the opening degree adjustment valve.
  • the stopper portion 55 is disposed between the claw portions 54 and the stopper portion 55 is formed separately from the claw portion 54.
  • the stopper portion 55 and the claw portion are formed.
  • 54 is integrally formed, and the stopper portion 55 is formed so as to extend from the tip of the claw portion 54 to the downstream side. Since the other configuration is the same as the above configuration example, the same reference numerals are assigned to the same portions and the description thereof is omitted.
  • the stopper portion 55 cannot be disposed inside the support portion 44, but the valve body is brought into contact with the stopper portion 55 before the through-hole 43 is completely closed. Therefore, as long as the stopper 55 is made small, it is possible to prevent the passage cross section from changing suddenly when shifting to a minute flow rate. It is possible to avoid a sudden change in characteristics.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne une vanne à régulation d'ouverture dans laquelle un changement soudain dans les caractéristiques d'aspiration peut être évité en faisant varier progressivement la section droite d'un passage même lorsqu'une transition est effectuée vers un débit minime. L'invention concerne également un compresseur à capacité variable l'employant. La vanne à régulation d'ouverture disposée dans un canal permettant la communication entre l'orifice d'aspiration et la chambre d'aspiration d'un compresseur et réalisant une commande variable sur l'aire d'ouverture du canal comporte un élément (41) de boîtier tubulaire présentant une paroi circonférentielle pourvue d'une pluralité de trous débouchants (43), un élément (42) de vanne contenu dans l'élément (41) de boîtier de façon à pouvoir coulisser dans la direction axiale et sollicité par un ressort (50) de rappel dans la direction de fermeture de la vanne, et une partie (55) de butée pour la régulation du mouvement de l'élément (42) de vanne dans la direction de fermeture de la vanne de façon à laisser la région d'ouverture du trou débouchant (43) du côté amont de l'élément (42) de vanne.
PCT/JP2007/060397 2006-06-08 2007-05-22 Vanne à régulation d'ouverture et compresseur à capacité variable l'employant WO2007142021A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006160345A JP2007327446A (ja) 2006-06-08 2006-06-08 開度調整弁及びこれを用いた可変容量型圧縮機
JP2006-160345 2006-06-08

Publications (1)

Publication Number Publication Date
WO2007142021A1 true WO2007142021A1 (fr) 2007-12-13

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PCT/JP2007/060397 WO2007142021A1 (fr) 2006-06-08 2007-05-22 Vanne à régulation d'ouverture et compresseur à capacité variable l'employant

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JP (1) JP2007327446A (fr)
WO (1) WO2007142021A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111219325A (zh) * 2020-01-19 2020-06-02 沈维强 一种流量可调式液压泵

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101693042B1 (ko) * 2010-06-08 2017-01-04 한온시스템 주식회사 가변용량형 사판식 압축기
KR101452568B1 (ko) * 2012-02-13 2014-10-21 한라비스테온공조 주식회사 가변용량형 사판식 압축기
KR101452569B1 (ko) * 2012-02-13 2014-10-21 한라비스테온공조 주식회사 가변용량형 사판식 압축기
KR101883174B1 (ko) * 2012-08-23 2018-07-30 한온시스템 주식회사 가변용량형 사판식 압축기
KR20140035114A (ko) * 2012-09-13 2014-03-21 한라비스테온공조 주식회사 압축기용 체크밸브
JP6192369B2 (ja) * 2013-06-07 2017-09-06 サンデンホールディングス株式会社 往復動式圧縮機
JP6421747B2 (ja) * 2015-12-24 2018-11-14 株式会社豊田自動織機 圧縮機

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001289177A (ja) * 2000-04-04 2001-10-19 Sanden Corp ピストン式可変容量圧縮機
JP2004027846A (ja) * 2002-05-10 2004-01-29 Sanden Corp 圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001289177A (ja) * 2000-04-04 2001-10-19 Sanden Corp ピストン式可変容量圧縮機
JP2004027846A (ja) * 2002-05-10 2004-01-29 Sanden Corp 圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111219325A (zh) * 2020-01-19 2020-06-02 沈维强 一种流量可调式液压泵
CN111219325B (zh) * 2020-01-19 2021-11-05 上海韦航装备科技有限公司 一种流量可调式液压泵

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