WO2001002726A1 - Valve de commande pour compresseur a cylindree variable - Google Patents

Valve de commande pour compresseur a cylindree variable Download PDF

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Publication number
WO2001002726A1
WO2001002726A1 PCT/JP2000/004300 JP0004300W WO0102726A1 WO 2001002726 A1 WO2001002726 A1 WO 2001002726A1 JP 0004300 W JP0004300 W JP 0004300W WO 0102726 A1 WO0102726 A1 WO 0102726A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
compressor
ball
discharge pressure
Prior art date
Application number
PCT/JP2000/004300
Other languages
English (en)
Japanese (ja)
Inventor
Ken Suitou
Kenta Nishimura
Satoshi Inaji
Ryo Matsubara
Morio Kaneko
Ichiro Ohkawara
Original Assignee
Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Kabushiki Kaisha Saginomiya Seisakusho
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 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho, Kabushiki Kaisha Saginomiya Seisakusho filed Critical Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority to BR0007004-1A priority Critical patent/BR0007004A/pt
Priority to KR1020017002813A priority patent/KR20010079737A/ko
Priority to EP00940881A priority patent/EP1111237A1/fr
Publication of WO2001002726A1 publication Critical patent/WO2001002726A1/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
    • 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
    • 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
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—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
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge 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
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a control valve for a variable displacement compressor, and more particularly to a displacement control valve for a swash plate type variable displacement compressor used in an in-vehicle air conditioner or the like.
  • this displacement control valve reduces the displacement in response to a rise in the pressure in the crankcase of a compressor with a built-in swash plate, and increases the displacement in response to a decrease in the pressure in the crankcase.
  • the communication passage connecting the suction port of the compressor and the crank chamber is provided with a valve opening force of a pressure responsive device that responds to the suction pressure of the compressor and a spring force of a valve closing spring.
  • a control valve that opens and closes with a valve body driven by an equilibrium relationship, and controls a suction pressure of a compressor supplied to a crank chamber, and further exerts a discharge pressure of the compressor in a valve-opening direction. The opening and closing operation point is shifted according to the discharge pressure, and the capacity is controlled in accordance with the external air load (discharge pressure).
  • Diaphragm devices and bellows devices are available as pressure response devices, and the driving force of these pressure response devices must act as an axial force on the valve element. This causes the smoothness of the opening and closing movement of the valve body to be impaired. For this reason, in the conventional displacement control valve, a spring or an automatic A centripetal ball must be provided, which leads to an increase in the number of parts and assembly man-hours. Disclosure of the invention
  • the present invention has been made in view of the above-mentioned problems, and does not require a special automatic centering ball or the like, simplifies the structure, and increases the number of parts and the number of assembling steps.
  • To provide a control valve for a variable displacement compressor which has no complicated passage structure and has a high degree of freedom in the arrangement position in the compressor housing as a compressor housing built-in type. It is an object.
  • a control valve for a variable displacement compressor includes: a valve housing having a communication passage communicating a suction port of a compressor with a crank chamber; and the valve housing.
  • a ball valve body provided in the housing for opening and closing the communication passage; a spring for urging the ball valve body in a valve closing direction; and directly connecting the ball valve body as an automatic centripetal ball to the ball valve body.
  • a pressure responsive device that is driven by the suction pressure of the compressor to drive the ball valve body in the valve opening direction, slidably fitted to the valve housing, and joined at one end to the ball valve body;
  • the other end has a discharge pressure introduction port for the compressor, and has a discharge pressure introduction hollow pipe body for applying the discharge pressure of the compressor to the back surface of the ball valve as a force in the valve opening direction through an internal passage.
  • FIG. 1 is a sectional view showing an embodiment of a variable displacement compressor incorporating a control valve according to the present invention.
  • FIG. 2 is a sectional view showing a first embodiment of a control valve for a variable displacement compressor according to the present invention.
  • FIG. 3 is a graph showing a discharge pressure-suction pressure characteristic of the control valve for a variable displacement compressor according to the first embodiment.
  • FIG. 4 is a sectional view showing a second embodiment of the control valve for a variable displacement compressor according to the present invention.
  • FIG. 5 is a sectional view showing a third embodiment of the control valve for a variable displacement compressor according to the present invention. It is. BEST MODE FOR CARRYING OUT THE INVENTION Specific Configuration of Control Valve for Variable Displacement Compressor According to First Preferred Embodiment of the Invention
  • the swash plate type variable displacement compressor 1 includes a crank chamber 3 defined by a compressor housing 2 and a crank chamber 3 at one of the stroke ends. And a plurality of cylinder chambers 4 communicating with each other. A piston 5 is slidably fitted in each of the cylinder chambers 4 in the axial direction, and one end of a piston rod 6 is connected to the crank chamber 3 side of each piston 5.
  • the compressor housing 2 rotatably supports a drive shaft 7, and the drive shaft 7 is drivingly connected to an engine (not shown) by a drive belt (not shown) stretched over a pulley 8. Is driven to rotate.
  • the drive shaft 7 is connected to a wobbled plate (swash plate) 9 in the crankcase 3 by a known linking mechanism (not shown) in a torque transmitting relationship so that the mounting angle can be changed.
  • a piston hole 6 is engaged with the side plate surface so that axial force can be transmitted.
  • the pivot 9 is rotated by the drive shaft 7 in an inclined state, so that the piston 5 of each cylinder chamber 4 moves forward and backward with a stroke corresponding to the inclination angle of the movable plate 9, and the inclination angle is reduced.
  • the pressure is automatically adjusted according to the pressure difference between the crankcase pressure Pc and the suction pressure (compressor suction pressure) Ps of each cylinder chamber 4.
  • the compressor 1 reduces the discharge capacity by reducing the inclination angle of the wobble plate 9 and the stroke of the piston 5 in accordance with the rise of the crankcase pressure Pc, thereby reducing the discharge capacity.
  • the tilt angle of the wobble plate 9 increases in accordance with the decrease and the stroke of the piston 5 increases, the discharge capacity increases, and the crank chamber pressure P increases.
  • the pressure becomes substantially equal to the suction pressure Ps, a full load operation state is established.
  • Each cylinder chamber 4 is formed with a suction port 14 having a one-way valve and a discharge port 15 having a discharge valve 13 and a discharge port 15 .
  • the suction port 14 of each cylinder chamber 4 is The suction passage 16 communicates with the suction connection port 17, the discharge port 15 communicates with the discharge connection port 19 via the discharge passage 18, and the suction connection port 17 and the discharge connection port 19 communicate with each other.
  • a circulation line for a refrigeration cycle including an evaporator 20, an expansion valve 21, a condenser 22 and the like is connected.
  • a control valve receiving hole 23 having a bottomed hole is formed in the compressor housing 2, and the control valve 30 according to the present invention is inserted and fixed in the control valve receiving hole 23.
  • the control valve 30 has a cylindrical valve housing 31 inserted into the control valve receiving hole 23.
  • the valve housing 31 includes a crank chamber-side passage 32 and a suction port-side passage 33 extending radially across the middle of the valve housing 31. And a valve chamber 34 existing inside the valve housing 31 and between the crank chamber side passage 32 and the suction port side passage 33.
  • An annular peripheral groove 35 for the crank chamber side passage 32 and an annular peripheral groove 36 for the suction port side passage 33 are formed on the outer peripheral portion of the valve housing 31.
  • a ball valve element 37 is disposed in the valve chamber 34, and the ball valve element 37 is selectively seated on the valve seat portion 38, whereby the crank chamber side passage 32 and the suction port side passage 3 are provided. Communication with 3 is cut off.
  • a bellows housing case 39 is caulked to one end (lower end) of the valve housing 31.
  • a bellows device 40 having a closed structure which is a pressure responsive device, is disposed inside the bellows storage case 39.
  • the bellows device 40 is constituted by a bellows-shaped bellows body 41 having an end plate 43 integrally at one end, and an end plate 42 closing the other end of the bellows body 41. Is at vacuum pressure.
  • a compression coil spring 4 4 for urging the bellows device 40 in the extension direction (valve closing direction) is provided between the end plate 42 and the end plate 43 in the bellows body 41. (Corresponding to a spring).
  • a stopper member 45 is provided on the end plate 43 side of the bellows body 41, and a stopper surface portion 45a of the stopper member 45 and a stopper surface portion 42 of the end plate 42 are provided. By contact with a, the bellows device 40 A large amount of shrinkage is specified.
  • An adjusting screw member 46 is screw-engaged with the bellows housing case 39.
  • the adjusting screw member 46 is formed by a ball 47 and an end plate 4 arranged at the axis of the adjusting screw member 46.
  • One end of the bellows device 40 is held by a spherical joint structure formed by a spherical recess 42b formed in the axial center portion (bellows center) of the stopper surface portion 42a. That is, the bellows device 40 and the bellows housing case 39 are spherically connected by the spherical joint structure via the adjusting screw member 46.
  • the bellows device 40 is directly connected to the ball valve body 37 in a spherical joint manner at a spherical recess 43 a formed in the axial center portion (bellows center) of the end plate 43.
  • the expansion and contraction of the closing device 40 is transmitted to the ball valve element 37 as an axial force.
  • the bellows storage case 39 communicates with the suction port side passageway 33, and the bellows device 40 is connected to the suction pressure introduced into the bellows storage case 39 from the suction port side passageway 33 by the bellows. Expands and contracts according to the pressure difference from the internal pressure.
  • the other end (upper end) of the valve housing 31 is formed with a fitting hole 48 that passes through the center of the valve housing 31 in the axial direction.
  • a discharge pressure introducing hollow tube 49 is fitted in the fitting hole 48 so as to be slidable in the axial direction.
  • One end (lower end) of the discharge pressure introducing hollow tubular body 49 is joined to the ball valve body 37 by welding or the like.
  • the other end (upper end) of the discharge pressure introducing hollow tube 49 is located in the fitting hole 48 and forms an inlet 49 c for the discharge pressure Pd of the compressor 1.
  • the discharge pressure introducing hollow tube 49 is expanded at the joint (lower end) with the ball valve body 37, and the outer diameter D a of the discharge pressure introducing hollow tube 49 and the discharge pressure is being introduced.
  • the effective diameter Db of the pressure receiving surface portion 37a of the pressure exerted on the ball valve body 37 from the hollow tube body 49 is equal to each other.
  • a compression coil spring 50 that urges the ball valve body 37 in the valve opening direction is provided between the enlarged diameter portion 49 a of the discharge pressure introduction hollow tubular body 49 and the valve housing 31 (in the claims). (Corresponding to the valve urging means).
  • the spring load of the compression coil spring 50 is such that when the ball valve element 37 is opened, the ball valve element 37 and the bellows device 40 rattle due to vibration during operation of the compressor 1. It is set to a value that does not exist.
  • control valve 30 having the above-described configuration includes a compressor housing Crankcase side passageway 3 and annular groove 35 communicate with crankcase 3 via crankcase pressure passageway 2, and suction port side passageway 33 and annular shape.
  • the circumferential groove 36 communicates with the suction port 14 through the suction pressure passage 25, and the fitting hole 48 communicates with the discharge port 15 through the discharge pressure passage 26.
  • crank chamber pressure passage 24, the suction pressure passage 25, and the discharge pressure passage 26 are pressure passages formed inside the compressor housing 2.
  • the suction pressure P s of the compressor 1 passes from the suction port 14 through the suction pressure passage 25 to the annular circumferential groove 36, the suction port side passage 33, and furthermore, the bellows storage case 3 9 Inside, acting on the bellows device 40. Accordingly, the bellows device 40 expands and contracts according to the differential pressure between the suction pressure P s of the compressor 1 and the bellows internal pressure, and piles on the spring force of the compression coil spring 44 as the suction pressure P s increases. Shrink.
  • the ball valve element 37 is opened by the discharge pressure Pd introduced by the discharge pressure introduction hollow pipe 49 acting on the pressure receiving surface 37 a and the spring force of the compression coil spring 50. Since the valve is biased in the valve direction, the valve is opened by contraction of the bellows device 40 due to an increase in the suction pressure Ps.
  • the ball valve element 37 has a valve opening force due to the suction pressure Ps acting on the bellows device 40 and the compression coil spring 44 spring. Opening / closing is driven by an equilibrium relationship with the valve closing force due to the force.
  • the discharge pressure P d of the compressor 1 introduced into the discharge pressure introducing hollow pipe 49 directly acts as a correction pressure on the pressure receiving surface 37 a of the ball valve element 37, and the effective area of the pressure receiving surface 37 a
  • a h be the valve opening force of A h ⁇ P d applied to the ball valve element 37.
  • the discharge pressure Pd of the compressor 1 also acts on the inlet port 49 b of the discharge pressure introducing hollow pipe 49 slidably fitted in the fitting hole 48.
  • the outer diameter D a of the discharge pressure introducing hollow tube 49 is equal to the effective diameter D b of the pressure receiving surface portion 37 a of the ball valve body 37, the discharge pressure introducing hollow tube 49 is used.
  • the discharge pressure Pd of the compressor 1 acting on the end face 49b of the compressor 1 is canceled.
  • the reference set pressure Pss is set in a balanced state at the reference discharge pressure Pds.
  • discharge pressure P d decreases (discharge pressure P d ⁇ reference discharge pressure P ds)
  • the suction pressure P s required to open the valve increases, and the discharge pressure P d increases (discharge pressure P d).
  • the pressure P ds reduces the suction pressure P s required to open the valve.
  • the evaporation load and the condensation load are in a proportional relationship.
  • the evaporation load is proportional to the amount of circulating refrigerant
  • the pressure loss in the evaporator is proportional to the amount of circulating refrigerant.
  • control valve for variable displacement compressor since the ball valve element 37 is directly connected to the bellows device 40 and the ball valve element 37 acts as an automatic centripetal ball of a spherical joint between the valve element and the pressure response device, a special automatic centripetal ball or the like is used.
  • the driving force of the bellows device 40 acts on the ball valve element 37 as an axial force without any need.
  • FIG. 4 shows a second embodiment of the control valve for a variable displacement compressor according to the present invention.
  • parts corresponding to those in FIG. 2 are denoted by the same reference numerals as those in FIG. 2, and description thereof will be omitted.
  • a guide cylinder 52 is inserted and fixed in a hole 51 corresponding to the fitting hole (48) of the first embodiment, and discharge is performed on an outer peripheral portion of the guide cylinder 52.
  • the pressure introducing hollow tube 49 is movably fitted.
  • the discharge pressure Pd of the compressor 1 introduced into the discharge pressure introducing hollow pipe body 49 acts directly as a correction pressure on the pressure receiving surface 37a of the ball valve body 37, The same operation and effect as those of the first embodiment can be obtained, and the control valve characteristics at the time of actual operation can be made the characteristics related to the discharge pressure Pd.
  • the ball valve element 37 is directly connected to the bellows device 40, and the ball valve element 37 acts as an automatic centripetal ball of the spherical joint between the valve element and the pressure response device.
  • the driving force of the bellows device 40 acts on the pawl valve 37 as an axial force without requiring a special automatic centripetal ball or the like.
  • the pressure responsive device has a closed structure.
  • the pressure responsive device is not limited to the bellows device 40 but may be a diaphragm device, etc., for a variable displacement compressor in which the pressure responsive device is constituted by a diaphragm device.
  • An embodiment applied to a control valve will be described below as a third embodiment. Specific Configuration of Control Valve for Variable Displacement Compressor According to Third Preferred Embodiment of the Invention Next, a control valve for a variable displacement compressor according to the third embodiment of the present invention will be described with reference to FIG. Will be explained.
  • FIG. 5 shows a third embodiment of the capacity control valve according to the present invention.
  • parts corresponding to those in FIG. 2 are given the same reference numerals as those in FIG. 2, and description thereof is omitted.
  • the diaphragm device 60 includes a dish-shaped upper lid 61 crimped to the lower end of the valve housing 31, a dish-shaped lower lid 6 3 joined to the upper lid 61 with the diaphragm 62 interposed therebetween, and a lower lid.
  • the spring box 64 includes a cylindrical spring box 64 that is swaged to the spring box 63, and an adjusting screw 65 that is threadedly engaged with the spring box 64.
  • the diaphragm 62 defines a diaphragm chamber 66 on the valve housing 31 side and a sealed chamber 67 on the spring box 64 side, and the holder 6 for the ball valve element 37 on the diaphragm chamber 66 side. Connected to 8.
  • a contact 69, a ball 70, and a spring receiving member 71 are sequentially provided on the closed chamber 67 side of the diaphragm 62, and a diaphragm is provided between the spring receiving member 71 and the adjusting screw 65.
  • a compression coil spring 72 is provided to urge the ball valve element 37 in the valve closing direction (upward) via the element 62.
  • the diaphragm chamber 66 communicates with the valve chamber 34, and is provided with a suction pressure Ps guided to the valve chamber 34.
  • the configuration of the discharge pressure introducing hollow tubular body 49 and the like is the same as that of the first embodiment, so that the third embodiment has the same operation and effect as the first embodiment. can get.
  • the ball valve element 37 is directly connected to the diaphragm device 60 via the holding body 68, and in this case also, the ball valve element 37 is connected to the spherical joint between the valve element and the pressure response device. Since it acts as a dynamic centripetal ball, the driving force of the bellows device 40 acts favorably on the ball valve element 37 as an axial force without requiring a special automatic centripetal ball or the like.
  • one end (lower end) of the discharge pressure introducing hollow tube 49 is joined to the ball valve body 37 by welding or the like, but the urging force of the compression coil spring 50 is used. Accordingly, one end (lower end) of the discharge pressure introducing hollow tubular body 49 may be pressed against the ball valve body 37.
  • the discharge pressure of the compressor is controlled by the discharge pressure introducing hollow tube.
  • the high pressure influence characteristic discharge pressure influence characteristic corresponding to the compressor discharge pressure is set, which acts directly on the ball valve body and correlates with the system load characteristic.
  • an arbitrary high pressure influence characteristic can be obtained by setting the effective diameter of the discharge pressure introducing hollow tube, and the high pressure influence characteristic can be set with a high degree of freedom by selecting the effective diameter of the discharge pressure introducing hollow tube.
  • the discharge pressure of the compressor is directly applied to the ball valve by the discharge pressure introducing hollow tube, the number of parts and assembly man-hours can be reduced compared to the conventional one, and it is directly incorporated into the compressor housing.
  • the structure of the passage for guiding the suction pressure and the discharge pressure to each part of the displacement control valve is not complicated, and the degree of freedom of the arrangement position in the compressor housing is not limited.
  • the ball valve element is directly connected to the pressure response device and the ball valve element acts as an automatic centripetal ball of the spherical joint between the valve element and pressure response device, a special automatic centripetal ball is required. Without this, the driving force of the pressure responsive device acts satisfactorily as an axial force on the ball valve body, so that the number of parts and the number of assembly steps can be reduced.
  • the end face of the discharge pressure introduction hollow tube body slidably fitted in the fitting hole is also provided on the end face on the discharge pressure introduction port side.
  • the outer diameter of the discharge pressure introduction hollow tube is equal to the effective diameter of the pressure receiving surface of the ball valve, so it acts on the end face of the discharge pressure introduction hollow tube at the discharge pressure introduction port side. Yes The discharge pressure of the compressor is canceled, and the required high pressure influence characteristics can be obtained.
  • the discharge pressure introducing hollow tubular body is provided.
  • the discharge pressure of the compressor does not act on the end face of the hollow pipe, and the required high pressure influence characteristics can be obtained without matching the effective diameter and the outer diameter of the discharge pressure introducing hollow tube.
  • the ball valve is biased by the urging force of the valve urging means for urging the ball valve in the valve opening direction via the discharge pressure introducing hollow pipe.
  • the vibration resistance of the body and pressure response device is improved, and a quiet and stable capacity control operation can be obtained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Cette invention se rapporte à une valve de commande pour compresseur à cylindrée variable, qui comprend un disque à valve sphérique (37) qui ouvre et ferme des passages de communication (32, 34, 33) faisant communiquer un orifice d'aspiration avec une chambre à manivelle d'un compresseur et qui est sollicité dans la direction de fermeture de la valve par la force élastique d'un ressort hélicoïdal de compression (44), un dispositif en accordéon (40) entraînant le disque à valve sphérique (37) dans la direction d'ouverture de la valve grâce à l'application d'une pression d'aspiration du compresseur, le disque à valve sphérique (37) étant relié directement au dispositif en accordéon (40) tout en servant de sphère de centrage automatique, ainsi qu'un corps de tube creux conducteur de pression d'amenée (39) relié au disque à valve sphérique (37) à une extrémité et appliquant une pression d'amenée du compresseur directement dans la direction d'ouverture de la valve du disque à valve sphérique (37), qui est disposé dans un logement de valve (31), un ressort hélicoïdal de compression (50) sollicitant le disque à valve sphérique (37) dans la direction d'ouverture de la valve par l'intermédiaire du corps de tube creux conducteur de pression d'amenée (49).
PCT/JP2000/004300 1999-07-05 2000-06-29 Valve de commande pour compresseur a cylindree variable WO2001002726A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
BR0007004-1A BR0007004A (pt) 1999-07-05 2000-06-29 Válvula de controle para compressor de capacidade variável
KR1020017002813A KR20010079737A (ko) 1999-07-05 2000-06-29 용량가변형 압축기용 제어밸브
EP00940881A EP1111237A1 (fr) 1999-07-05 2000-06-29 Valve de commande pour compresseur a cylindree variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11/189979 1999-07-05
JP11189979A JP2001020857A (ja) 1999-07-05 1999-07-05 容量可変型圧縮機用制御弁

Publications (1)

Publication Number Publication Date
WO2001002726A1 true WO2001002726A1 (fr) 2001-01-11

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Application Number Title Priority Date Filing Date
PCT/JP2000/004300 WO2001002726A1 (fr) 1999-07-05 2000-06-29 Valve de commande pour compresseur a cylindree variable

Country Status (6)

Country Link
EP (1) EP1111237A1 (fr)
JP (1) JP2001020857A (fr)
KR (1) KR20010079737A (fr)
CN (1) CN1317073A (fr)
BR (1) BR0007004A (fr)
WO (1) WO2001002726A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10227817A1 (de) * 2002-02-28 2003-09-11 Taiheiyo Kogyo Kk Regelventil für Kompressoren und dessen Herstellungsverfahren
JP2004162567A (ja) * 2002-11-12 2004-06-10 Fuji Koki Corp 可変容量型圧縮機用の制御弁
CN101762130B (zh) * 2008-12-24 2013-12-18 上海三电贝洱汽车空调有限公司 一种控制阀
JP5424397B2 (ja) * 2009-12-04 2014-02-26 サンデン株式会社 制御弁及び制御弁を備えた斜板式可変容量圧縮機
JP5443444B2 (ja) * 2011-07-06 2014-03-19 株式会社鷺宮製作所 感圧制御弁
KR101462418B1 (ko) * 2011-12-02 2014-11-19 주식회사 퍼시픽콘트롤즈 가변용량형 제어밸브
CN113646530A (zh) * 2019-04-03 2021-11-12 伊格尔工业股份有限公司 容量控制阀

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06200875A (ja) * 1993-01-08 1994-07-19 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06200875A (ja) * 1993-01-08 1994-07-19 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機

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KR20010079737A (ko) 2001-08-22
JP2001020857A (ja) 2001-01-23
CN1317073A (zh) 2001-10-10
EP1111237A1 (fr) 2001-06-27
BR0007004A (pt) 2001-06-19

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