EP3059445A1 - Elektromagnetisches regelventil eines verdichters mit variabler verdrängung - Google Patents

Elektromagnetisches regelventil eines verdichters mit variabler verdrängung Download PDF

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Publication number
EP3059445A1
EP3059445A1 EP16154786.4A EP16154786A EP3059445A1 EP 3059445 A1 EP3059445 A1 EP 3059445A1 EP 16154786 A EP16154786 A EP 16154786A EP 3059445 A1 EP3059445 A1 EP 3059445A1
Authority
EP
European Patent Office
Prior art keywords
valve
vibration absorbing
absorbing member
control
shaft
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP16154786.4A
Other languages
English (en)
French (fr)
Other versions
EP3059445B1 (de
Inventor
Yuuki Kaneko
Shinji Saeki
Shigeru Abe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TGK Co Ltd
Original Assignee
TGK Co Ltd
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
Priority claimed from JP2015234949A external-priority patent/JP6609885B2/ja
Application filed by TGK Co Ltd filed Critical TGK Co Ltd
Publication of EP3059445A1 publication Critical patent/EP3059445A1/de
Application granted granted Critical
Publication of EP3059445B1 publication Critical patent/EP3059445B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge 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
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a control valve driven by a solenoid controlled according to pulse width modulation (PWM).
  • PWM pulse width modulation
  • An automotive air conditioner is generally configured by arranging and placing a compressor, an external heat exchanger, an expander, an evaporator and the like in a refrigeration cycle.
  • the compressor is, for example, a variable displacement compressor (also referred to simply as a "compressor") capable of maintaining a constant level of cooling capacity irrespective of the engine speed.
  • This compressor includes a rotational shaft driven by an engine, and a wobble plate mounted to the rotational shaft.
  • a piston for compression is linked to the wobble plate. The angle of the wobble plate is changed to change the stroke of the piston, by which the refrigerant discharging rate is regulated.
  • the angle of the wobble plate is changed continuously by supplying part of the discharged refrigerant into a hermetically-closed control chamber and thus changing the balance of pressures working on both faces of the piston.
  • the pressure in this control chamber (referred to as a "control pressure” below) is controlled by, for example, a control valve provided between a discharge chamber and the control chamber of the compressor.
  • This control valve is usually configured as an electromagnetic valve, and includes in a body thereof a passage through which the discharge chamber and the control chamber communicate with each other.
  • a valve seat is provided in the passage.
  • a valve element is provided in the body and is moved toward and away from the valve seat to adjust the opening degree of a valve section and thus control the flow rate of a refrigerant to be supplied to the control chamber.
  • the valve opening degree is adjusted according to a balance of a force generated by a refrigerant pressure acting on the valve element, a driving force of a solenoid, and a biasing force of a spring disposed to set a control set value.
  • This control set value can be adjusted later by changing the value of current to be supplied to the solenoid.
  • the pulse width modulation is often employed for controlling power supply to the solenoid.
  • capacity control of some control valves is conducted by supplying a pulsed current with a frequency of about 400 Hz set at a predetermined duty ratio (refer to Japanese Unexamined Patent Application Publication No. 2005-171908 , for example).
  • Such a control valve is typically in a state where a valve element is slightly opened during stationary control in which the valve opening degree is controlled.
  • the aforementioned power supply control according to the PWM causes a plunger of the solenoid to generate micro-vibration. This vibration is transmitted to the valve element. Hence, depending on the amplitude of the vibration, the valve element may hit the valve seat and spring back, which changes the valve opening degree and thus lowers the control performance. Hence, such a measure as pressing another member against a movable portion continuous with a valve element to apply a sliding load has been taken.
  • An object of the present invention is to readily suppress vibration of a valve element during stationary control in a control valve where power supply to the control valve is controlled according to a PWM technique.
  • One embodiment of the present invention relates to a control valve driven by a solenoid controlled by pulse width modulation (PWM).
  • the control valve includes: a body having a first port through which a working fluid is introduced, a second port through which the working fluid is delivered, and a valve seat provided in a passage connecting the first port and the second port; a valve element configured to touch and leave the valve seat to close and open a valve section; an actuating member driven in a direction of an axis line to transmit a driving force of the solenoid to the valve element; and a vibration absorbing member having viscoelasticity and being set between the body and the actuating member or between a fixed member fixed to the body and the actuating member.
  • a material and a structure of the vibration absorbing member are set such that, during stationary control of a valve opening degree, the vibration absorbing member having the viscoelasticity, dynamically deforms following vibration of the actuating member accompanying the PWM control, and such that a vibration amplitude of the actuating member is included in a range in which the vibration absorbing member and the actuating member are not caused to slide relative to each other.
  • the viscoelasticity of the vibration absorbing member is used so that the vibration of the actuating member and thus that of the valve element are suppressed.
  • the vibration absorbing member dynamically deforms following the vibration.
  • the viscosity of the vibration absorbing member particularly contributes to a resistance against the vibration of the actuating member, so that the vibration can be suppressed. Since the viscoelasticity of the vibration absorbing member is used in this manner, precise adjustment of the dimensions of the vibration absorbing member and the actuating member is unnecessary unlike a case where a sliding friction between the vibration absorbing member and the actuating member is used. Consequently, the vibration of the valve element during stationary control can be readily suppressed.
  • FIG. 1 is a cross-sectional view showing a structure of a control valve according to a first embodiment
  • FIG. 1 is a cross-sectional view showing a structure of a control valve according to a first embodiment.
  • a control valve 1 is an electromagnetic valve that controls a discharging capacity of a not-shown variable displacement compressor (simply referred to as a "compressor") of an automotive air conditioner.
  • the compressor compresses a refrigerant flowing in a refrigeration cycle into a high-temperature and high-pressure gaseous refrigerant, and discharges the compressed gas refrigerant.
  • the gas refrigerant is cooled by an external heat exchanger (a condenser or a gas cooler) and then adiabatically expanded by an expander into a low-temperature and low-pressure spray of refrigerant.
  • an external heat exchanger a condenser or a gas cooler
  • the low-temperature and low-pressure refrigerant is evaporated by an evaporator, and the evaporative latent heat cools the air inside the vehicle.
  • the refrigerant evaporated by the evaporator is returned to the compressor and circulates in the refrigeration cycle.
  • the compressor includes a rotational shaft rotated by an engine of the vehicle.
  • a piston for compression is linked to a wobble plate mounted on the rotational shaft.
  • the angle of the wobble plate is changed to change the stroke of the piston and to thus regulate the refrigerant discharging rate.
  • the control valve 1 controls the flow rate of refrigerant introduced from the discharge chamber to the control chamber of the compressor to change the angle of the wobble plate and thus the discharging capacity of the compressor.
  • the control chamber of the present embodiment is a crankcase, the control chamber may alternatively be a pressure chamber separately provided in or outside of the crankcase in a modification.
  • the control valve 1 is structured as a so-called (Pd - Ps) differential pressure regulating valve that controls the flow rate of a refrigerant delivered from the discharge chamber into the control chamber such that a differential pressure (Pd - Ps) between a discharge pressure Pd and a suction pressure Ps of the compressor is brought close to a preset differential pressure, which is a control target value.
  • Pd - Ps differential pressure regulating valve that controls the flow rate of a refrigerant delivered from the discharge chamber into the control chamber such that a differential pressure (Pd - Ps) between a discharge pressure Pd and a suction pressure Ps of the compressor is brought close to a preset differential pressure, which is a control target value.
  • the control valve 1 is formed by an integral assembly of a valve unit 2 and a solenoid 3.
  • the valve unit 2 has a body 5 of a stepped cylindrical shape.
  • the body 5 is formed of brass in the present embodiment, it may alternatively be formed of an aluminum alloy.
  • the body 5 has ports 10, 12, and 14 in this order from a top end thereof. Of these ports, the port 10 is provided in an upper end of the body 5, and the ports 12 and 14 are each provided on a lateral side thereof.
  • the port 10 functions as a "discharge chamber communication port" communicating with the discharge chamber.
  • the port 12 functions as a "control chamber communication port” communicating with the control chamber.
  • the port 14 functions as a "suction chamber communication port” communicating with the suction chamber.
  • the port 10 functions as a "first port” through which the refrigerant is introduced from the discharge chamber, and the port 12 functions as a "second port” through which the refrigerant is delivered toward the control chamber.
  • a valve seat forming member 16 of a stepped cylindrical shape is provided in a passage that communicates between the port 10 and the port 12.
  • the valve seat forming member 16 is formed by quenching a stainless steel (e.g., SUS420), and has a hardness higher than that of the body 5.
  • the valve seat forming member 16 is coaxially inserted into an upper part of the body 5 and is secured such that the upper part of the body 5 is swaged inward.
  • the valve seat forming member 16 has a through-hole along an axis line, and a lower half of the through-hole forms a valve hole 18.
  • a valve chamber 20, which communicates with the port 12, is formed below the valve seat forming member 16 in the body 5.
  • the lower half of the valve seat forming member 16 is of a tapered shape such that the outside diameter thereof is gradually reduced from an upper part to a lower part thereof, and extends into the valve chamber 20.
  • a valve seat 22 is formed on a lower end surface of the valve seat forming member 16.
  • a valve element 24 is provided in the valve chamber 20 in such a manner as to face the valve seat 22 from below. The opening degree of a valve section is regulated by moving the valve element 24 toward and away from the valve seat 22.
  • a soft material is used for a material constituting the body 5 and thereby its high processability is kept.
  • a material or a member constituting the valve seat 22 is formed of a material having a higher degree of hardness, so that the wear and deformation of the valve seat 22 are prevented or suppressed. This allows good seating characteristics of the valve element 24 to be maintained.
  • a partition wall 26 is so provided that an internal space of the body 5 is divided into an upper space and a lower space.
  • the valve chamber 20 is formed on an upper side of the partition wall 26, and a working chamber 28 is formed on a lower side thereof.
  • the valve chamber 20 communicates with the control chamber through the port 12.
  • the working chamber 28 communicates with the suction chamber through the port 14.
  • a guide portion 30, which extends in a direction of the axis line, is provided in a center of the partition wall 26.
  • a guiding passage 32 is so formed as to run through the guide portion 30 along the axis line, and an elongated actuating rod 34 is slidably inserted into the guiding passage 32 in the direction of the axis line.
  • the valve element 24 is provided coaxially on an upper end of the actuating rod 34.
  • the valve element 24 and the actuating rod 34 are formed integrally with each other by performing a cutting work on a stainless steel.
  • the guide portion 30 protrudes as a small bump on an upper surface side of the partition wall 26 and protrudes as a large protrusion on a lower surface side thereof.
  • the guide portion 30 is of a tapered shape such that the outside diameter thereof is gradually reduced from an upper part to a lower part thereof, and the guide portion extends into the working chamber 28. With this configuration and arrangement, a sufficient length of the guiding passage 32 is ensured and the actuating rod 34 is stably supported.
  • the valve element 24 and the actuating rod 34 operate and move integrally together with each other, and the valve element 24 touches and leaves the valve seat 22 closes and opens the valve section by touching and leaving the valve seat 22, respectively, at the upper end surface of the valve element 24.
  • the hardness of the valve seat forming member 16 is sufficiently high. Thus, the valve seat 22 is hardly deformed by repeated seating of the valve element 24 on the valve seat 22, thereby ensuring the durability of the valve section.
  • a retaining ring 36 (E-ring) is fitted to a lower part of the actuating rod 34, and a discoidal spring support 38 is provided such that the movement of the lower part thereof in a downward direction is restricted.
  • a spring 40 which biases the actuating rod 34 downward (in a valve closing direction), is set between the spring support 38 and the partition wall 26.
  • the spring 40 is a tapered spring where the diameter thereof is reduced starting from the lower surface of the partition wall 26 toward the spring support 38 located therebelow. Having the guide portion 30 formed in the tapered shape as described above allows the tapered-shape spring 40 to be arranged as described above.
  • a lower part of the body 5 is a small-diameter part 42 and constitutes a coupling portion with the solenoid 3.
  • a filter member 44 which prevents or reduces entry of foreign materials through the port 10, is provided in an upper end opening of the body 5. Since the foreign materials, such as metallic powders, may be contained in the refrigerant discharged from the compressor, the filter member 44 prevents or reduces entry of the foreign material into the control valve 1.
  • the solenoid 3 includes a cylindrical core 50, a bottomed cylindrical sleeve 52 mounted (outserted) around the core 50, a plunger 54, which is contained in the sleeve 52 and which is disposed opposite to the core 50 in the direction of axis line, a cylindrical bobbin 56 mounted (outserted) around the sleeve 52, an electromagnetic coil 58 wound around the bobbin 56, a cylindrical casing 60, which is so provided as to cover the electromagnetic coil 58 from outside, a connecting member 62 of a stepped cylindrical shape, which is mounted between the core 50 and the casing 60 and above the bobbin 56, and an end member 64, which is attached to a lower end opening of the casing 60.
  • the sleeve 52 is formed of a non-magnetic material, and includes a main body 74 of a cylindrical shape mounted (outserted) around the core 50, and an end member 75 of a bottomed cylindrical shape mounted to seal off a lower end opening of the main body 74.
  • the sleeve 52 houses the plunger 54 in a lower half thereof.
  • the valve unit 2 and the solenoid 3 are secured such that the small-diameter part 42 (lower end part) of the body 5 is press-fitted to an upper end opening of the connecting member 62.
  • the body 5, the valve seat forming member 16, the connecting member 62, the casing 60 and the end member 64 constitute a body of the whole control valve 1.
  • An insertion hole 67 is so formed as to run through the center of the core 50 in the direction of the axis line.
  • a shaft 68 is inserted into the insertion hole 67 in such a manner as to extend through the insertion hole 67.
  • the shaft 68 is formed coaxially with the actuating rod 34 and supports the actuating rod 34 from below.
  • the diameter of the shaft 68 is larger than that of the actuating rod 34.
  • the plunger 54 is mounted on a lower half of the shaft 68.
  • the shaft 68 and the actuating rod 34 constitute a "transmitting rod” that transmits a force from the solenoid 3 (hereinafter also referred to as a solenoid force) to the valve element 24.
  • the shaft 68, the actuating rod 34 and the plunger 54 constitute an "actuating member" driven in the direction of the axis line to transmit the solenoid force to the valve element 24.
  • the plunger 54 is coaxially supported by the shaft 68 at an upper portion of the plunger 54.
  • a retaining ring 70 (E-ring) is fitted to a predetermined position in an intermediate part of the shaft 68 in the direction of the axis line, and the retaining ring 70 works to restrict the movement of the plunger 54 in an upward direction.
  • a communicating groove 71 formed in parallel with the axis line is provided on a lateral surface of the plunger 54. The communicating groove 71 forms a communicating path through which the refrigerant is made to pass between the plunger 54 and the sleeve 52.
  • a ring-shaped shaft support member 72 is press-fitted in an upper end of the core 50, and an upper end of the shaft 68 is slidably supported by the shaft support member 72 in the direction of the axis line.
  • An outer periphery of the shaft support member 72 is partially cut out and thereby a communicating path is formed between the core 50 and the shaft support member 72. Through this communicating path, the suction pressure Ps of the working chamber 28 is led into the interior of the solenoid 3, too.
  • a ring-shaped shaft support member 76 (functioning as a "supporting member”) is press-fitted to the lower end of the sleeve 52 (more specifically, the end member 75).
  • the shaft support member 76 slidably supports a lower end part of the shaft 68.
  • the shaft 68 is two-point supported by both the shaft support member 72 at an upper side thereof and the shaft support member 76 at a lower side thereof, so that the plunger 54 can be stably operated in the direction of the axis line.
  • An outer periphery of the shaft support member 76 is partially cut out and thereby a communicating path is formed between the sleeve 52 and the shaft support member 76.
  • the suction pressure Ps introduced into the solenoid 3 fills the interior of the sleeve 52 through the communicating path between the core 50 and the shaft 68, the communicating path between the plunger 54 and the sleeve 52, and the communicating path between the shaft support member 76 and the sleeve 52.
  • a spring 78 that biases the plunger 54 in an upward direction, namely in a valve closing direction, is set between the shaft support member 76 and the plunger 54.
  • the valve element 24 receives the net force of a force exerted by the spring 40 in a valve opening direction and a force exerted by the spring 78 in a valve closing direction.
  • the spring load of the spring 40 is larger than that of the spring 78.
  • the overall spring load of the springs 40 and 78 works in a valve opening direction.
  • a harness 80 leading to the electromagnetic coil 58 extends from the bobbin 56 and is led outside through the end member 64.
  • the end member 64 is attached to support the structure in the solenoid 3 contained in the casing 60 from below.
  • FIG. 2 is a partially enlarged cross-sectional view of an upper half of FIG. 1 .
  • the diameter of a through-hole 90 which is formed in a center of the valve seat forming member 16, is reduced in a lower half thereof.
  • This reduced diameter portion of the through-hole 90 forms the valve hole 18.
  • the upper half of the through-hole 90 is a large-diameter part 92, whereas the lower half thereof is a small-diameter part 94.
  • the small-diameter part 94 forms the valve hole 18.
  • a connection area between the large-diameter part 92 and the small-diameter part 94 has a tapered surface where the inside diameter thereof is gradually reduced downward.
  • the diameter of the through-hole 90 is reduced stepwise from an upstream side to a downstream side.
  • a bleed hole 96 in parallel with the through-hole 90 is formed at a position radially outside of the through-hole 90 in the valve seat forming member 16.
  • the bleed hole 96 is used to ensure the circulation of oil in the compressor by delivering a minimum required amount of refrigerant to the control chamber even when the valve section is closed.
  • the refrigerant contains a lubricating oil in order to ensure a stabilized operation of the compressor, and the bleed hole 96 is to ensure the oil circulation inside and outside the control chamber.
  • the bleed hole 96 is constituted by a leak passage 98 located in an upper part thereof and a communication passage 99 located in a lower part thereof, which are connected together.
  • the inside diameter of the leak passage 98 has such a size that the refrigerant is made to leak therethrough, which is fairly smaller than that of the valve hole 18.
  • the inside diameter of the communication passage 99 is smaller than that of the large-diameter part 92 of the through-hole 90 and larger than that of the small-diameter part 94 thereof.
  • the inside diameter of the communication passage 99 may be greater than or equal to that of the large-diameter part 92 of the through-hole 90 or may be smaller than or equal to that of the small-diameter part 94 thereof.
  • An annular raised portion 150 is formed on a top surface of the valve seat forming member 16 in such a manner as to surround the through-hole 90, and the valve seat forming member 16 is of a stepped shape such that a portion radially inside of and a portion radially outside of the raised portion 150 are one step lower than the raised portion 150.
  • the width of the raised portion 150 is sufficiently small and is less than or equal to that of the valve hole 18 in the present embodiment.
  • the leak passage 98 is opened upward at a position of the raised portion 150.
  • the bleed hole 96 is formed such that an inlet of the refrigerant has a small diameter and is opened on the top surface of the stepped shape. Thus, the entry of foreign materials through the bleed hole 96 is prevented or suppressed.
  • the guide portion 30 protrudes at the middle of the upper surface of the partition wall 26 and thereby an annular groove 152 is formed around this protrusion.
  • the outside diameter of the valve element 24 is slightly larger than that of the actuating rod 34 located immediately beneath the valve element 24.
  • the pressure sensitivity of the valve element 24 is optimally set such that a seal section diameter a (the inside diameter of the valve hole 18) of the valve element 24 in the valve section is slightly (e.g., by a very small amount) larger than a diameter b of the sliding portion of the actuating rod 34 (a > b).
  • a seal section diameter a the inside diameter of the valve hole 18
  • a diameter b of the sliding portion of the actuating rod 34 a > b.
  • a vibration absorbing structure in particular, which suppresses vibration of the actuating member accompanying PWM control, is provided.
  • the vibration absorbing structure includes a vibration absorbing member 100 set between the shaft support member 72 and the shaft 68.
  • the shaft support member 72 corresponds to a "fixed member” fixed to the body 5.
  • An annular groove 102 is formed on an inner face of the shaft support member 72, and the vibration absorbing member 100 is fitted thereto.
  • the vibration absorbing member 100 is a viscoelastic member.
  • the vibration absorbing member 100 is an O-ring made of rubber.
  • an inner peripheral portion of the vibration absorbing member 100 dynamically deforms following vibration of the shaft 68.
  • the vibration amplitude of the shaft 68 and thus that of the valve element 24 are suppressed owing to the viscoelasticity of the vibration absorbing member 100.
  • the vibration absorbing member 100 and the shaft 68 do not slide relative to each other, but a part of the vibration absorbing member 100 in close contact with the shaft 68 deforms.
  • the part of the vibration absorbing member 100 in close contact with the shaft 68 moves, which displaces the shaft 68.
  • the viscoelasticity (viscosity in particular) of the vibration absorbing member 100 works as a resistance against the vibration of the shaft 68, which suppresses the vibration amplitude of the valve element 24.
  • a response delay caused by the viscosity functions to damp the vibration.
  • FIGS. 3A and 3B are partial cross-sectional views of the control valve 1.
  • FIG. 3A is a cross-sectional view along arrows C-C in FIG. 2
  • FIG. 3B is a cross-sectional view along arrows A-A in FIG. 1
  • FIG. 3C is a cross-sectional view along arrows B-B in FIG. 1 .
  • the inner peripheral portion of the vibration absorbing member 100 is in close contact with an outer surface of the shaft 68.
  • An outer periphery of a cylindrical main body of the shaft support member 72 is subjected to so-called D-cut so as to form a flat surface 180.
  • a communicating path 182 is formed between the flat surface 180 and an inner surface of the core 50.
  • one lateral surface of the plunger 54 is subjected to so-called D-cut to form a flat surface 77.
  • a communicating path 183 is formed between the flat surface 77 and the sleeve 52.
  • an outer periphery of a cylindrical main body of the shaft support member 76 is subjected to so-called D-cut to form a pair of flat surfaces 184.
  • a communicating path 186 is formed between these flat surfaces 184 and the sleeve 52 (end member 75).
  • the suction pressure Ps of the working chamber 28 passes through the communicating paths 182, 183 and 186 then fills the inside of the sleeve 52.
  • the plunger 54 is subjected to the D-cut process, and the cross section thereof is thus non-circular (not point-symmetrical with respect to the shaft's center).
  • the flat surface 77 resulting from the D-cut process is made to differ from the opposite lateral surface 79 in radial magnetic gap.
  • the opposite lateral surface 79 which is on a side where the magnetic gap with the sleeve 52 is smaller, is attracted more strongly in a radial direction, when the solenoid 3 is turned on.
  • the plunger 54 can be radially shifted to one side. This can suppress or prevent the rattling movement of the plunger 54 in a radial direction when the plunger 54 operates and moves inside the sleeve 52 while the valve section is opened.
  • the diameter of the actuating rod 34 is approximately equal to the inside diameter of the valve hole 18 although the former is slightly smaller than the latter.
  • the effect of the control pressure Pc acting on the valve element 24 in the valve chamber 20 is almost canceled out.
  • the differential pressure (Pd - Ps) between the discharge pressure Pd and the suction pressure Ps practically acts on the valve element 24 for a pressure-receiving area having approximately the same size as that of the valve hole 18.
  • the valve element 24 operates and moves such that the differential pressure (Pd - Ps) is kept at a preset differential pressure set by a control current supplied to the solenoid 3.
  • the valve element 24 gets separated away from the valve seat 22 by the net force of the springs 40 and 78 in a valve opening direction with the result that the valve section is remained at a fully opened state.
  • a high-pressure refrigerant having the discharge pressure Pd introduced into the port 10 from the discharge chamber of the compressor passes through the fully-opened valve section and then flows into the control chamber through the port 12.
  • the control pressure Pc is raised and the compressor carries out a minimum capacity operation where the discharging capacity is the minimum.
  • the value of current supplied to the solenoid 3 is the maximum and the plunger 54 is attracted by a maximum suction force of the core 50.
  • the valve element 24, the actuating rod 34, the shaft 68 and the plunger 54 operate and move integrally altogether in a valve closing direction, and the valve element 24 is seated on the valve seat 22.
  • the control pressure Pc drops as a result of this valve closing movement and therefore the compressor carries out a maximum capacity operation where the discharging capacity is the maximum.
  • valve element 24 When the value of current supplied to the solenoid 3 is set to a predetermined value while the capacity is being controlled, the valve element 24, the actuating rod 34, the shaft 68 and the plunger 54 operate and move integrally altogether. At this time, the valve element 24 stops at a valve-lift position.
  • This valve-lift position is a position where five loads/forces are all balanced thereamong.
  • the five loads/forces are the spring load of the spring 40 that biases the actuating rod 34 in a valve opening direction, the spring load of the spring 78 that biases the plunger 54 in a valve opening direction, the load of the solenoid 3 that biases the plunger 54 in a valve closing direction, the force by the discharge pressure Pd that the valve element 24 receives in a valve opening direction, and the force by the suction pressure Ps that the valve element 24 receives in a valve closing direction.
  • FIG. 4 is a graph showing load characteristics of the vibration absorbing member 100.
  • the horizontal axis indicates the stroke of the valve element 24, and the vertical axis indicates the load applied to the shaft 68.
  • the stroke of the valve element 24 is equal to that of the shaft 68.
  • a range of the stroke of the valve element 24 from zero to about 0.12 mm is a range (referred to as a 'viscoelastic range" below) in which the viscoelasticity of the vibration absorbing member 100 effectively functions as a resistance.
  • the vibration absorbing member 100 and the shaft 68 do not slide relative to each other, and the vibration absorbing member 100 deforms, which can apply a resistance (elastic resistance and viscous resistance) to the shaft 68.
  • a load caused by this viscoelasticity increases and acts in such a direction as to suppress displacement of the shaft 68.
  • the load becomes substantially constant at its maximum (such a range will be referred to as an "elastic range” below).
  • the vibration absorbing member 100 elastically deforms, the vibration absorbing member 100 and the shaft 68 keep in close contact with each other.
  • the load lowers and becomes substantially constant (such a range will be referred to as a "frictional range” below).
  • the shaft 68 slides relative to the vibration absorbing member 100 and receives a resistance caused by dynamic friction.
  • the vibration amplitude of the shaft 68 (i.e., the vibration amplitude of the valve element 24) during stationary control of the valve opening degree (when the valve section is slightly opened) is to be included in a range corresponding to the viscoelastic range of the vibration absorbing member 100.
  • the resistance (vibration damping function) caused by the viscoelasticity (viscosity in particular) of the vibration absorbing member 100 is used for setting of the material and the structure of the vibration absorbing member 100 such that the vibration amplitude of the shaft 68 and thus that of the valve element 24 are within the viscoelastic range (about 0.07 mm, for example).
  • the vibration absorbing member 100 of a material and a structure where the original vibration amplitude (the vibration amplitude when no resistance is caused by the viscoelasticity) of the valve element 24 under PWM control is included in the viscoelastic range is used.
  • the valve element 24 makes a great stroke.
  • the vibration absorbing member 100 temporarily enters a state in the frictional range.
  • the material and the structure of the vibration absorbing member 100 are set to allow sliding relative to the vibration absorbing member 100 when the valve element 24 makes a stroke in response to switching of the power supply state of the solenoid 3 (between on and off states of power supply).
  • the vibration absorbing member 100 absorbing vibration energy of the shaft 68 due to its viscoelasticity (viscosity in particular), and this is used to suppress vibration of the valve element 24 during stationary control. Since the viscoelasticity is used as described above, it is not necessary to precisely adjust the dimensions of the vibration absorbing member 100 and the shaft 68 unlike a case where sliding friction between the vibration absorbing member 100 and the shaft 68 is used. According to the present embodiment, the vibration of the valve element 24 can be readily suppressed during stationary control.
  • FIG. 5 is a partially enlarged cross-sectional view of an upper half of a control valve according to a second embodiment.
  • FIGS. 6A to 6F are partially enlarged cross-sectional views showing main parts according to modifications. Differences from the first embodiment will be mainly described below. In the figures, substantially the same components as those of the first embodiment will be designated by the same reference numerals.
  • a vibration absorbing member 100 is disposed at a stepped portion 210 formed at an upper end opening of a core 250.
  • a ring-shaped shaft support member 272 is press-fitted to an upper end of the stepped portion 210 to prevent the vibration absorbing member 100 from dropping off.
  • the vibration absorbing member 100 is supported between an inner surface of the core 250 and an outer surface of the shaft 68.
  • the core 250 has a communicating path 220 communicating between the insertion hole 67 and the working chamber 28 bypassing the vibration absorbing member 100.
  • the material and the structure of the vibration absorbing member 100 are set such that the vibration absorbing member 100 dynamically deforms following the vibration of the shaft 68 accompanying the PWM control and that the vibration amplitude of the shaft 68 is within the viscoelastic range owing to the viscoelasticity of the vibration absorbing member 100.
  • the vibration of the vibration absorbing member 100 and thus that of the valve element 24 can be suppressed without causing sliding of the vibration absorbing member 100 and the shaft 68 relative to each other during stationary control of the valve opening degree.
  • a square ring having a polygonal (square) cross section may be adopted as a vibration absorbing member 120.
  • a D-ring having a cross section of a D shape may be adopted as a vibration absorbing member 130.
  • These vibration absorbing members each have an outer surface being in close contact with the inner surface of the core 250, and an inner surface being in close contact with the outer surface of the shaft 68.
  • a vibration absorbing member 140 may be supported in a state in which the vibration absorbing member 140 is sandwiched between a core 250 and a shaft support member 274 in the direction of the axis line.
  • an outer circumferential edge of the vibration absorbing member 140 is sandwiched by the stepped portion 210 and the shaft support member 274.
  • the vibration absorbing member 140 has an inner surface being in close contact with the outer surface of the shaft 68, which applies a resistance against the vibration of the shaft 68 similarly to the above-described embodiment.
  • an annular recess 230 may be formed in an outer surface of a shaft 268 and a vibration absorbing member 100 may be fitted thereto.
  • the vibration absorbing member 100 is supported in such a manner that the vibration absorbing member 100 is fitted to the recess 230, and the outer surface of the vibration absorbing member 100 is in close contact with an inner surface of a core 252.
  • This configuration also allows the viscoelasticity of the vibration absorbing member 100 to effectively function, and can suppress the vibration of the shaft 268 and thus that of the valve element 24.
  • an annular recess 212 and an annular recess 232 may be formed in an inner surface of a core 254 and in an outer surface of a shaft 270, respectively, and a ring-shaped vibration absorbing member 122 may be fitted to these recesses.
  • the vibration absorbing member 122 is supported in such a manner that an outer circumferential edge thereof is fitted to the recess 212 and an inner circumference portion is fitted to the recess 232.
  • This configuration also allows the viscoelasticity of the vibration absorbing member 122 to effectively function, and can suppress the vibration of the shaft 270 and thus that of the valve element 24.
  • the vibration absorbing member 122 is only fitted to the core 254 and the shaft 270 in the example shown in FIG. 6E , the vibration absorbing member 122 may also be fixed by means such as baking or adhesion. Alternatively, when the vibration absorbing member 122 is fixed by baking or the like, the vibration absorbing member 122 may not be fitted.
  • the vibration absorbing member is formed of rubber alone in the above-described embodiment and modifications.
  • a vibration absorbing member 214 may be formed by laminating resin plates 216 made of rubber or the like and metal plates 218. According to this configuration, the viscoelasticity of the resin plates 216 and the elasticity of the metal plates 218 can be used to appropriately adjust the degree of vibration suppression.
  • FIG. 7 is a cross-sectional view showing a structure of a control valve according to a third embodiment.
  • the structures of shaft support members 372 and 376 in a solenoid 303 are different from those of the first embodiment.
  • a vibration absorbing member 100 is mounted on the lower shaft support member 376 instead of the upper shaft support member 372.
  • the shaft support member 376 corresponds to a "fixed member” fixed to the body 5.
  • An annular groove 102 is formed in an inner surface of the shaft support member 376, and the vibration absorbing member 100 is fitted thereto.
  • This configuration also allows the viscoelasticity of the vibration absorbing member 100 to effectively function, and suppress the vibration of the shaft 68 and thus that of the valve element 24.
  • the shape and the support structure of the vibration absorbing member are not limited to those shown in FIG. 7 , but a structure shown in any of FIGS. 6A to 6F , for example, can also be adopted.
  • FIG. 8 is a partially enlarged cross-sectional view showing a structure of a lower half of a control valve according to a fourth embodiment.
  • a vibration absorbing member 100 is mounted on a plunger 454.
  • An annular groove 420 is formed in an outer surface of the plunger 454, and the vibration absorbing member 100 is fitted thereto.
  • a communicating path 430 through which a refrigerant circulates is formed to run therethrough in parallel with the axis line.
  • This configuration also allows the viscoelasticity of the vibration absorbing member 100 to effectively function, and can suppress the vibration of the shaft 68 and thus that of the valve element 24.
  • the shape and the support structure of the vibration absorbing member are not limited to those shown in FIG. 8 , but a structure shown in any of FIGS. 6A to 6F , for example, can also be adopted.
  • the vibration absorbing member is a ring-shaped member in the above-described embodiments, the vibration absorbing member may be constituted by one or a plurality of members of other shapes such as small pieces.
  • the vibration amplitude of the actuating member i.e., the vibration amplitude of the valve element, the shaft, and the plunger
  • the material and the structure of the vibration absorbing member may be set such that the vibration amplitude of the actuating member during stationary control is included in a range corresponding to the viscoelastic range and the elastic range shown in FIG. 4 .
  • the vibration amplitude of the actuating member can be suppressed to a range in which the vibration member and the actuating member are not caused to slide relative to each other.
  • the lower shaft support member not only functions as a spring support for supporting the spring but also functions as a shaft support for supporting the shaft.
  • a spring support for supporting the spring and a shaft support for supporting the shaft may be provided separately.
  • a vibration absorbing member may be set between the spring support and the shaft.
  • a vibration absorbing member may be set between the shaft support and the shaft.
  • actuating rod and the shaft are manufactured as separate units and then coupled together such that the actuating rod and the shaft are coaxially abutted against each other in the direction of the axis line, thereby constituting a transmitting rod for transmitting the solenoid force to the valve element.
  • the actuating rod and the shaft may be integrally formed as a single element to constitute a transmitting rod.
  • control valve 1 is configured as a so-called (Pd - Ps) differential pressure valve.
  • control valve 1 may be configured as a so-called (Pc - Ps) differential pressure valve, for instance.
  • Pc - Ps differential pressure valve
  • a differential pressure (Pc - Ps) between the control pressure Pc and the suction pressure Ps is brought closer to a preset differential pressure, which is a control target value.
  • any of the above-described structures according to the above-described embodiments may be applied to a control valve configured to change the discharging capacity of a variable displacement compressor for compressing the refrigerant led into the suction chamber and then discharging the compressed refrigerant from the discharge chamber by regulating the flow rate of the refrigerant delivered to the suction chamber from the control chamber.
  • the control valve 1 may be applied to a so-called Ps control valve in which the suction pressure Ps is brought closer to a preset pressure, which is a control target value.
  • control valve having each of the above-described structures is used as a control valve for a variable displacement compressor.
  • the use of the control valve is not particularly limited, and each of the above-described structures is applicable to any control valve driven by a solenoid controlled by the PWM.
  • FIGS. 9A and 9B are partially enlarged cross-sectional views showing application examples of the vibration absorbing member shown in FIG. 6F .
  • FIG. 9A shows a first application example
  • FIG. 9B shows a second application example.
  • the vibration absorbing member 214 may be formed in a ring shape by alternately laminating resin plates 216 (e.g., rubber) of a disk shape and metal plates 218 of a disk shape in the direction of the axis line. Insertion holes for allowing insertion of the shaft 68 are formed in the centers of the resin plates 216 and the metal plates 218.
  • the vibration absorbing member 214 has an outer surface, which is formed by outer edges of the laminated plates, in close contact with the inner surface of the core 250, and an inner surface, which is formed by inner edges of the laminated plates, in close contact with the outer surface of the shaft 68.
  • the metal plates 218 preferably have such an appropriate elasticity that the metal plates 218 can deform in such a manner as to warp in the direction of the axis line.
  • the vibration absorbing member 214 may be formed in a ring shape by coaxially and alternately laminating in a radial direction resin plates 216 of cylindrical shapes (cylindrical resin members made of rubber or the like) whose diameters are different from each other, and metal plates 218 of cylindrical shapes (cylindrical metal members).
  • a resin plate 216 is arranged at each of the innermost side and the outermost side of the vibration absorbing member 214.
  • An outer circumferential surface of the resin plate 216 at the outermost side of the vibration absorbing member 214 is in close contact with the inner surface of the core 250, and an inner circumferential surface of the resin plate 216 at the innermost side thereof is in close contact with the outer surface of the shaft 68.
  • the viscoelasticity of the resin plates 216 and the elasticity of the metal plates 218 can be used to adjust the degree of vibration suppression.
  • the viscoelasticity of a plurality of resin plates 216 e.g., rubber
  • the amount of deformation of the vibration absorbing member 214, which occurs following the motion of the shaft 68 in the direction of the axis line, can be increased.
  • the stroke in the viscoelastic range can be made longer than that in the load characteristics shown in FIG. 4 .
  • the vibration absorbing member 214 may be in a form of a D-ring having a cross section of a D shape as shown in FIG. 6B .
  • the lamination structure shown in FIG. 9B is applicable to the structure of the vibration absorbing member 214.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
EP16154786.4A 2015-02-23 2016-02-09 Elektromagnetisches regelventil eines verdichters mit variabler verdrängung Not-in-force EP3059445B1 (de)

Applications Claiming Priority (2)

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JP2015032575 2015-02-23
JP2015234949A JP6609885B2 (ja) 2015-02-23 2015-12-01 制御弁

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111315986A (zh) * 2017-11-07 2020-06-19 株式会社不二工机 可变容量型压缩机用控制阀
EP3748158A4 (de) * 2018-01-29 2021-11-24 Fujikoki Corporation Regelventil für einen verdichter mit variabler verdrängung
WO2022042633A1 (zh) * 2020-08-31 2022-03-03 浙江三花汽车零部件有限公司 电磁阀及电磁阀组件

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JP2005171908A (ja) 2003-12-12 2005-06-30 Tgk Co Ltd 可変容量圧縮機の容量制御弁
JP2006057506A (ja) 2004-08-19 2006-03-02 Tgk Co Ltd 可変容量圧縮機用制御弁
JP2009192198A (ja) * 2008-02-18 2009-08-27 Denso Corp 膨張弁
WO2012008787A2 (ko) * 2010-07-16 2012-01-19 두원공과대학교 용량가변형 압축기의 용량제어밸브
EP2667118A2 (de) * 2012-04-25 2013-11-27 TGK CO., Ltd. Expansionsventil und schwingungsfeste Feder
KR20140111629A (ko) * 2014-04-07 2014-09-19 가부시키가이샤 테지케 가변 용량 압축기용 제어 밸브

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JP2006188961A (ja) * 2004-12-28 2006-07-20 Tgk Co Ltd 可変容量圧縮機用制御弁
JP6281046B2 (ja) * 2012-04-23 2018-02-21 株式会社テージーケー 可変容量圧縮機用制御弁

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Publication number Priority date Publication date Assignee Title
JP2005171908A (ja) 2003-12-12 2005-06-30 Tgk Co Ltd 可変容量圧縮機の容量制御弁
JP2006057506A (ja) 2004-08-19 2006-03-02 Tgk Co Ltd 可変容量圧縮機用制御弁
JP2009192198A (ja) * 2008-02-18 2009-08-27 Denso Corp 膨張弁
WO2012008787A2 (ko) * 2010-07-16 2012-01-19 두원공과대학교 용량가변형 압축기의 용량제어밸브
EP2667118A2 (de) * 2012-04-25 2013-11-27 TGK CO., Ltd. Expansionsventil und schwingungsfeste Feder
KR20140111629A (ko) * 2014-04-07 2014-09-19 가부시키가이샤 테지케 가변 용량 압축기용 제어 밸브

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111315986A (zh) * 2017-11-07 2020-06-19 株式会社不二工机 可变容量型压缩机用控制阀
EP3670908A4 (de) * 2017-11-07 2021-01-20 Fujikoki Corporation Regelventil für einen verdichter mit variabler verdrängung
EP3748158A4 (de) * 2018-01-29 2021-11-24 Fujikoki Corporation Regelventil für einen verdichter mit variabler verdrängung
WO2022042633A1 (zh) * 2020-08-31 2022-03-03 浙江三花汽车零部件有限公司 电磁阀及电磁阀组件

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CN105909490A (zh) 2016-08-31
CN105909490B (zh) 2018-12-28

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