CN1508426A - Control valve for volume-variable compressor - Google Patents
Control valve for volume-variable compressor Download PDFInfo
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- CN1508426A CN1508426A CNA200310120943XA CN200310120943A CN1508426A CN 1508426 A CN1508426 A CN 1508426A CN A200310120943X A CNA200310120943X A CN A200310120943XA CN 200310120943 A CN200310120943 A CN 200310120943A CN 1508426 A CN1508426 A CN 1508426A
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- 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
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- 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
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- 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
- F04B39/16—Filtration; Moisture separation
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- 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
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- 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
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- 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
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- 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
- F04B2027/1886—Open (not controlling) fluid passage
- F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber
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- 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
- F04B2205/00—Fluid parameters
- F04B2205/05—Pressure after the pump outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0403—Refractory metals, e.g. V, W
- F05C2201/0406—Chromium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
- F05C2201/0466—Nickel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0469—Other heavy metals
- F05C2201/0475—Copper or alloys thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/12—Coating
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A variable displacement compressor optionally varies displacement based upon pressure in a crank chamber for adjusting the pressure in the crank chamber by varying an opening degree of a passage that interconnects the crank chamber and one of relatively high and low pressure regions of the refrigeration cycle. A control valve of the variable displacement compressor has a valve seat and a valve. The valve seat has a seat surface for adjusting the opening degree of the passage. The valve has a valve surface for adjusting the opening degree of the passage. At least one of the seat surface and the valve surface is made of a material with relatively high hardness.
Description
Technical field
The present invention relates to a kind of control valve that is used to control variable displacement compressor capacity in the refrigeration cycle.
Background technique
Disclosed as the 15th to 16 page of unexamined Japanese patent application 2001-173556 and Figure 12, the variable capacity oblique tray type compressor that is used for refrigeration cycle, by regulating the crank chamber or holding pressure in the chamber of swash plate, at random change the inclination angle of swash plate or the capacity of compressor.
That is to say that compressor provides a kind of control valve of regulating the crank cavity pressure.Control valve for example changes the opening degree of air supply channel, and wherein air supply channel interconnects the elevated pressures district of refrigeration cycle and crank chamber.The lower pressure district and the crank chamber of one refrigeration cycle interconnect by a bleed passage.
The opening degree of adjusting control valve, import by air supply channel from the elevated pressures district with control the crank chamber the ratio elevated pressures the refrigerant gas total amount and be discharged to equilibrium relation between the total amount of refrigerant gas in lower pressure district by bleed passage from the crank chamber.Thereby, determine the pressure in the crank chamber.The inclination angle of swash plate changes according to the variation of crank cavity pressure.Consequently: the stroke of having regulated piston is the capacity of compressor.
Recently, carbon dioxide as the refrigeration agent of refrigeration cycle, has replaced traditional fluorine-containing chlorine carbide usually.When carbon dioxide when the refrigeration agent, in the refrigeration cycle higher and than the pressure difference between the low pressure area than big a lot (for example 10Mpa) with CFCs.Therefore, utilize the pressure difference in the refrigeration cycle to regulate in the structure of compressor capacity above-mentioned, refrigerant gas is with the inside of the control valve of flowing through based on the fair speed of the pressure difference that produces in refrigeration cycle.
When refrigerant gas is flowed through control valve inside at a relatively high speed, be included in the refrigerant gas, can not can corrode inner generation of control valve by the trickle foreign particle (for example 10 to 20 microns solid particle) that filter filters out fully.In view of the structure of control valve, corrode trend and appear at around that part of adjusting control valve opening degree, very big and air-flow is intricate at the flow of this part refrigerant gas.Particularly, be used for the seating face of valve seat of opening and closing control valve and the valve surface of valve body, constitute the part of adjusting control valve opening degree.When seating face and valve surface generation crack, to close fully at control valve under the state of (being that seating face contacts with valve surface), refrigerant gas can leak out by the crack.Consequently, can not remain on the capacity of the compressor under the control valve buttoned-up status.Therefore, need be a kind of when the control valve that is used for variable displacement compressor is in buttoned-up status, can reduce the control valve of refrigerant gas leakage rate.
Summary of the invention
According to the present invention, variable displacement compressor can change the capacity based on the crank cavity pressure arbitrarily, by changing the opening degree of the passage that one of higher and lower pressure region with crank chamber and refrigeration cycle couples together, the pressure in the adjusting crank chamber.The control valve of variable displacement compressor has a valve seat and a valve.Valve seat has the seating face of regulating the access portal degree.Valve has the valve surface of regulating the access portal degree.At least one of seating face and valve surface are made by the material of higher hardness.
Other aspects and advantages of the present invention by the following describes book, in conjunction with the accompanying drawings, by the explanation to example of the present invention, can clearly show.
Description of drawings
Think and in the claim of enclosing, at length show the characteristics that have novelty among the present invention.The present invention and purpose thereof and advantage, the following explanation that preferred embodiment is carried out in conjunction with the drawings can be carried out best understanding, wherein:
Figure 1A represents the schematic representation of transfiguration oblique tray type compressor and vertical cross-section profile of control valve according to the preferred embodiment of the invention; And
Figure 1B represents the cross-section profile according to the part amplification of the adjacent portion that is used for the adjusting control valve opening degree in the preferred embodiment of the present invention.
Embodiment
Below, with reference to Figure 1A and 1B, the preferred embodiments of the present invention are described.
Figure 1A represents to be used for the schematic representation of automobile air-conditioning refrigeration circuit transfiguration oblique tray type compressor 1 (hereinafter referred to as compressor 1).Compressor 1 imports compression chamber 1a with refrigerant gas from air aspiration cavity 2, then, when the rotation by the swash plate (not shown) of the capacity of compression chamber 1a changes, the refrigerant gas that compression imports and compressed refrigerant gas entered exhaust cavity 3.One oil separator 4 is used to make the mist lubrication oil that is contained in the refrigerant gas to separate with refrigerant gas near the outlet of exhaust cavity 3.By the way, carbon dioxide is as the refrigeration agent of refrigeration cycle.
In compressor 1, the crank chamber 5 that holds swash plate is communicated with the air aspiration cavity 2 in lower pressure district in refrigeration cycle by bleed passage 6.Oil separator 4 in refrigeration cycle in the elevated pressures district is communicated with crank chamber 5 by air supply channel 7.In oil separator 4, the lubricant oil of separating from refrigerant gas and a part of refrigerant gas are transported in the crank chamber 5 and the sliding parts in the lubricated crank chamber 5 by air supply channel 7 together.That is, air supply channel 7 will be delivered to crank chamber 5 from the lubricant oil that oil separator 4 is separated as dual transfer passage.
By the way, a filter 8 is installed in the upstream side (side of oil separator 4) of air supply channel 7, to get rid of the foreign particle in the refrigerant gas.The mesh size of filter 8 is only for getting rid of 20 to 30 microns foreign particle or being the above-mentioned interference to the refrigerant gas flow of release.
One control valve CV is installed in the air supply channel 7 and can at random regulates the opening degree of air supply channel 7.The adjusting of control valve CV opening degree, may command import by air supply channel 7 from exhaust cavity 3 crank chambeies 5 the higher pressure refrigerant gas total amount and be transported to equilibrium relation between the total amount of refrigerant gas of air aspiration cavity 2 by bleed passage 6 from crank chamber 5.Thereby the pressure in definite crank chamber 5.The inclination angle of swash plate changes according to the variation of crank chamber 5 internal pressures, thereby the capacity of compressor 1 is regulated.
For example, when the pressure in the crank chamber 5 reduced to descend owing to the opening degree of control valve CV, the inclination angle of swash plate increased, thereby the capacity of compressor 1 increases.On the contrary, when the pressure in the crank chamber 5 rose owing to the opening degree increase of control valve CV, the inclination angle of swash plate reduced, thereby the capacity of compressor 1 reduces.
Now, control valve is described.
Shown in Figure 1A, the valve casing 10 of control valve CV comprises the valve body 11 of upside and the actuating housing 12 of downside in the drawings.Downside begins from figure, and valve pocket 22, communication passage 23 and pressure sensing chamber 24 are each defined in the valve body 11.Valve rod 25 is installed movingly and is passed valve pocket 22 and communication passage 23, along the axial direction extension of valve casing 10 (Vertical direction among the figure).Valve rod 25 upper ends of interting communication passage 23 are separated communication passage 23 and pressure sensing chamber 24.
Shown in Figure 1A and 1B, the valve portion 31 that forms at valve rod 25 intermediate portions is arranged in the valve pocket 22.In valve body 11, the step between valve pocket 22 and the communication passage 23 forms valve seat 32, so communication passage 23 forms valve opening.When valve rod 25 moves upward to the state of valve portion 31 arrival valve seats 32 under the state that the communication passage shown in Figure 1A 23 (air supply channel 7) is opened, the flat valve surface 31a of valve portion 31 contacts with the flat seating face 32a of valve seat 32, thereby communication passage 23 (air supply channel 7) is closed.The helical spring 60 that is used to promote valve rod 25 is installed in the valve pocket 22.Helical spring 60 promotes valve rod 25 along the direction that makes valve portion 31 away from valve seat 32.
One cylindrical bellows 33 is contained in the pressure sensing chamber 24.The upper end of bellows 33 is fixed to valve casing 10.The upper end of valve rod 25 is fixed to the lower end of bellows 33.Bellows 33 1 ends have a bottom and pressure sensing chamber 24 are separated into first pressure chamber 49 and second pressure chamber 50.
Fixed restrictive valve 41 is arranged in the exhaust passage 40, and this exhaust passage couples together exhaust cavity 3 and external refrigeration cycle loop (not shown).First pressure chamber 49 is communicated with exhaust passage 40 by the first pressure guiding channel 42, and is connected with upstream side (side of exhaust cavity 3) with respect to fixed restrictive valve 41.Second pressure chamber 50 is communicated with exhaust passage 40 by the second pressure guiding channel 43, and connects in the downstream side with respect to fixed restrictive valve 41.Therefore, because the end portion of bellows 33 moves according to pressure difference, thus the variation of pressure difference between the upstream side of bellows 33 reflection fixed restrictive valves 41 and the downstream side, to determine the position of valve rod 25 (valve portion 31).By the way, bellows 33 makes valve portion 31 motion in the following manner, and compressor 1 volume change is with the variation of pressure difference between the upstream side of eliminating fixed restrictive valve 41 and the downstream side.
Downside at valve casing 10 is provided with an electromagnetic actuators 51.Electromagnetic actuators 51 provides a cylindrical cylindrical body 52 that holds, and the bottom of this cylindrical body one end is in the centre of actuator casing 12.One newel 53 that is tubular fixedly is fitted on the opening that holds cylindrical body 52 that is positioned at upside.The equipped structure of this newel 53 forms a piston cavity 54 in the bottom part of holding cylindrical body 52.
It is interior and removable along axial direction (Vertical direction among Figure 1A) that piston 56 is contained in piston cavity 54.Pilot hole 57 passes the center of newel 53 along extending axially of newel 53.The downside of valve rod 25 is installed in the pilot hole 57 movingly.The lower end of valve rod 25 fixedly is fitted into the piston 56 in the piston cavity 54.Therefore, at any time piston 56 and valve rod 25 all move up and down in overall.
Coil 61 twines and partly is covered with the zone of newel 53 to piston 56 around the excircle that holds cylindrical body 52.Order according to the air-conditioner ECU (not shown) transmits electric power to coil 61.Therefore, between piston and newel 53, produce size and the corresponding electromagnetic force of electric power (electromagnetic attraction) that is transported to coil 61.Electromagnetic force is delivered to valve rod 25 (valve portion 31) by piston 56.
In above-mentioned control valve CV, electromagnetic actuators 51 changes the electromagnetic force that is applied on the valve portion 31 according to the electric power of outside supply, thereby, can at random change the upstream side of fixed restrictive valve 41 and the control target of the pressure difference between the downstream side (set pressure differential), wherein throttle valve is to be used to utilize bellows 33 to carry out the benchmark of the positioning action of valve portion 31.That is, control valve CV is according to the variation of pressure difference, and is whole also independently with valve rod 25 (valve portion 31) location, so that keep the set pressure differential by the electric power decision that is transported to coil 61.In addition, this set pressure differential is carried out External Change by the electric power that adjusting is transported to coil 61.
Described in prior art, the capacity of compressor 1 is regulated by the pressure difference in the refrigeration cycle in a preferred embodiment, and refrigerant gas can be crossed air supply channel 7 with high relatively velocity flow.Then, in the control valve CV of opening and closing air supply channel 7,, all make by the material of the anti-higher hardness that corrodes as the seating face 32a of adjusting control valve CV opening degree valve seat 32 partly and the valve surface 31a of valve portion 31.
By the way, " material with higher hardness " speech means that material has 500 or above Vickers hardness in a preferred embodiment, this is once in a while can be near 10Mpa because of the pressure difference between the pressure high and low relatively in the refrigeration cycle, and the particle that causes erosion is arranged, and the silica that is for example had higher hardness by trickle solid particle (10 to 20 microns) constitutes.The material of valve seat 32 is that brass and its have the Vickers hardness near 200.Therefore, for the material of the seating face 32a of the valve seat 32 that obtains having higher hardness, utilize the method for nickel plating phosphorus to apply a high hardness layer 32b at the material surface of valve seat 32.Therefore, the seating face 32a of valve seat 32 is made of the material of the higher hardness with 500 to 800 Vickers hardnesses.
In addition, the material of valve rod 25 (valve portion 31) is stainless steel (SUS) and has Vickers hardness near 00.Therefore, the material for the valve surface 31a of the valve portion 31 that obtains having higher hardness utilizes the salt bath nitriding method to apply a high hardness layer 31b on the surface of valve portion 31 materials.Therefore, the valve surface 31a of valve portion 31 is made of the higher hardness material with 900 to 1100 Vickers hardnesses.
By the way, the thickness range of above-mentioned high hardness spray coating 31b, 32b approximately from several micron to 1 millimeter.The thickness of the layer of high hardness shown in Figure 1B 31b, 32b is to exaggerate for ease of understanding.And, not shown spiral winding 60 in Figure 1B.
According to above preferred embodiment, can obtain following beneficial effect.
(1) in control valve CV, the seating face 32a of valve seat 32 and the valve surface 31a of valve portion 31 are made by the material of higher hardness.Therefore, even be included in the valve surface 31a collision of the seating face 32a and the valve portion 31 of foreign particle in the refrigerant gas and valve seat 32, also be difficult to produce the crack.Therefore, being in the refrigerant gas leakage rate that is caused by the crack under the buttoned-up status at control valve CV can descend.Consequently, the capacity (maximum capacity in the preferred embodiment) with the compressor 1 of corresponding control valve CV buttoned-up status maintains.
(2) the high hardness layer 32b of valve seat 32 made by the material different with the high hardness layer 31b of valve portion 31.Thereby, can prevent from the same metal phenomenon to occur between the valve surface 31a of the seating face 32a of valve seat 32 and valve portion 31.The same metal phenomenon means that mutually the same metal can cause for example disadvantage of friction factor increase.
(3) double action of air supply channel 7 is to can be used as a transfer passage, and this transfer passage is carried by oil separator 4 isolated lubricant oil to crank chamber 5.In oil separator 4, foreign particle also is separated when lubricant oil is separated from refrigerant gas.Therefore, for example compare, more foreign particle is arranged by control valve CV inside with the air supply channel 7 that does not have the transfer passage double action.In control valve CV, the seating face 32a of valve seat 32 and the valve surface 31a of valve portion 31 are made by the material with higher hardness.Even under above-mentioned stiffness conditions, the leakage rate of refrigerant gas also can descend reliably under the complete closing state of control valve CV.Yet concrete structure of the present invention is: air supply channel 7 has the double action as transfer passage, be used for carrying lubricant oil from oil separator 4 to crank chamber 5, thereby the leakage rate of refrigerant gas also can more effectively descend under the complete closing state of control valve CV.
(4) compressor 1 is a refrigeration compressor that is used in the refrigeration cycle, and with the refrigeration agent of carbon dioxide as refrigeration cycle.Therefore, compare with using the Chlorofluorocarbons refrigeration agent, the pressure difference between the higher and low pressure of the refrigeration agent in control valve CV can become very big, and it is very fast that the flow velocity of refrigeration agent becomes.As a result, the valve surface 31a of the seating face 32a of valve seat 32 and valve portion 31 is easy to be subjected to the damage that foreign particle causes.That is, the present invention implements in the mode of the control valve of carbon dioxide coolant compressor, and like this, the leakage rate of refrigerant gas can descend under the complete closing state of control valve CV effectively.
The present invention is not limited to the foregoing description, but can be revised as following interchangeable embodiment.
In the alternative embodiment of above preferred embodiment, the seating face 32a of valve seat 32 and the valve surface 31a of valve portion 31 are made by the material of higher hardness.In this state, can obtain and the identical beneficial effect of paragraph (1).That is to say, when control valve CV is in complete closing state, the leakage rate of refrigerant gas is descended.But obviously, the seating face 32a of the valve seat of being made by the higher hardness material 32 and the valve surface 31a of valve portion 31 realize above-mentioned beneficial effect more reliably respectively.
In a preferred embodiment, the seating face 32a of valve seat 32 constituting by the material with higher hardness by this way: the method for the material use nickel plating phosphorus of valve seat 32 is carried out surface hardening and is handled.In the alternative embodiment of above preferred embodiment, the surface-hardening treatment method of valve seat 32 materials can be selected from the method group of being made up of nickel plating, nickel plating phosphorus boron, nickel plating boron, nickel plating boron tungsten, chromium plating and copper facing.Therefore, seating face 32a is made of the material with higher hardness.
And the seating face 32a of valve seat 32 is not limited to electro-plating method and carries out the surface hardening processing, but can utilize one of ion nitriding, gas nitrocarburizing, salt bath nitriding method to carry out cure process.Therefore, valve surface 31a is made of the material of higher hardness.
Moreover the valve surface 31a of valve portion 31 is not limited to utilize nitriding to carry out surface hardening and handles.The valve surface 31a of valve portion 31 can utilize one of nickel plating, nickel plating phosphorus, nickel plating phosphorus boron, nickel plating boron, nickel plating boron tungsten, chromium plating and copper electroplating method, to the surface hardening of valve portion 31 materials.
Selectable, the material of valve portion 31 (valve rod 25) is a steel for carburizing, and material surface utilizes method for carburizing to carry out cure process, has the valve surface 31a of higher hardness with formation.
In the selected embodiment of above preferred embodiment, the material of valve seat 32 is not limited to brass, and can be other copper series material, aluminium series material or stainless steel material (SUS).
In a preferred embodiment, control valve CV changes the opening degree of the air supply channel 7 that connects refrigeration cycle (oil separator 4) elevated pressures district and crank chamber 5, thereby regulates the pressure in the crank chamber 5.That is, the present invention is specially the so-called side control valve of supplying gas, and this control valve is installed in the air supply channel 7.In the selected embodiment of above preferred embodiment, control valve changes the opening degree of the bleed passage 6 of connecting crank chamber 5 and refrigeration cycle lower pressure district (for example air aspiration cavity 2), thereby regulates the pressure in the crank chamber 5.Therefore, the present invention is specially so-called venting side control valve, and this control valve is installed in the bleed passage 6.
In a preferred embodiment, control valve CV is according to the variation of pressure difference, and is whole also independently with valve portion 31 location, so that keep the set pressure differential by the electric power decision of outside supply.That is, the present invention is specially so-called external control valve.But the present invention does not limit in the mode of external control valve and implements, can internally piloted valve or singly implement in the mode of solenoid valve yet.
Therefore, example of the present invention and embodiment only for purpose of explanation but not limit, and the present invention is not limited to details given herein, but can improve in the scope of dependent claims.
Claims (10)
1. the control valve of a variable displacement compressor, this control valve can at random change capacity according to the pressure in the crank chamber, with the pressure in the opening degree adjusting crank chamber of the passage of one of higher and lower pressure region by changing connecting crank chamber and refrigeration cycle, control valve comprises:
One valve seat has the seating face that is used to regulate the access portal degree; And
One valve has the valve surface that is used to regulate the access portal degree, and one of seating face and valve surface are made by the material of higher hardness at least.
2. control valve according to claim 1 is characterized in that: the seating face of valve seat and the valve surface of valve are all made by the material with higher hardness.
3. control valve according to claim 1 is characterized in that: seating face and valve surface are made by the material that differs from one another.
4. control valve according to claim 1, it is characterized in that: the material with higher hardness is handled formation by surface hardening, and surface treatment is selected from the method group that nickel plating, nickel plating phosphorus, nickel plating boron, nickel plating phosphorus boron, nickel plating boron tungsten, chromium plating, copper facing, salt bath nitriding, ion nitriding, gas nitrocarburizing and Carburization Treatment are formed.
5. control valve according to claim 1, it is characterized in that: oil separator is installed in the elevated pressures district of refrigeration cycle, be used for isolating lubricant oil from the refrigerant gas that flows into the elevated pressures district, the passage that connects oil separator and crank chamber can have the double action of carrying isolated lubricant oil from oil separator to the crank chamber.
6. control valve according to claim 1 is characterized in that: with the refrigeration agent of carbon dioxide as refrigeration cycle.
7. control valve according to claim 1 is characterized in that: the material of higher hardness has 500 or above Vickers hardness.
8. control valve according to claim 7 is characterized in that: the material of seating face has 500 to 800 Vickers hardness.
9. control valve according to claim 7 is characterized in that: the material of valve surface has 900 to 1100 Vickers hardness.
10. control valve according to claim 1 is characterized in that: the maximum pressure differential between the higher and low pressure zone surpasses 10Mpa.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002330720A JP2004162640A (en) | 2002-11-14 | 2002-11-14 | Control valve for variable displacement compressor |
| JP330720/2002 | 2002-11-14 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1508426A true CN1508426A (en) | 2004-06-30 |
Family
ID=32171396
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200310120943XA Pending CN1508426A (en) | 2002-11-14 | 2003-11-13 | Control valve for volume-variable compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20040118140A1 (en) |
| EP (1) | EP1420162A3 (en) |
| JP (1) | JP2004162640A (en) |
| KR (1) | KR20040042801A (en) |
| CN (1) | CN1508426A (en) |
| BR (1) | BR0305196A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597587A (en) * | 2009-11-09 | 2012-07-18 | 株式会社富士金 | Control valve device |
| CN103547804A (en) * | 2011-05-23 | 2014-01-29 | 学校法人斗源学院 | Control valve for a variable capacity compressor and method for manufacturing same |
| CN104373650A (en) * | 2014-11-18 | 2015-02-25 | 温州仁谦汽车油泵有限公司 | Leaf spring type constant pressure valve |
| CN104697505A (en) * | 2015-03-20 | 2015-06-10 | 张家港海纳德智能科技有限公司 | Rotating component for surveying and mapping instrument and manufacturing method thereof |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006029144A (en) * | 2004-07-13 | 2006-02-02 | Sanden Corp | Displacement control valve of variable displacement swash plate type compressor |
| JP2007177627A (en) * | 2005-12-27 | 2007-07-12 | Sanden Corp | Discharge capacity control valve of variable displacement compressor |
| JP4607047B2 (en) * | 2006-04-28 | 2011-01-05 | サンデン株式会社 | Variable displacement compressor discharge capacity control valve |
| JP4599327B2 (en) * | 2006-05-23 | 2010-12-15 | サンデン株式会社 | Variable capacity compressor |
| DE102012202859A1 (en) * | 2012-02-24 | 2013-08-29 | Mahle International Gmbh | Valve system for charge exchange control |
| JP2016020682A (en) * | 2014-06-19 | 2016-02-04 | 株式会社テージーケー | Control valve for variable capacity type compressor |
| US11060493B2 (en) * | 2019-03-29 | 2021-07-13 | Delphi Technologies Ip Limited | Fuel pump for gasoline direct injection |
| EP4141302A4 (en) * | 2020-04-22 | 2024-03-20 | Eagle Industry Co., Ltd. | Capacity control valve |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4683804A (en) * | 1985-01-18 | 1987-08-04 | Taiho Kogyo Kabushiki Kaisha | Swash plate type compressor shoe |
| KR880005354A (en) * | 1986-10-08 | 1988-06-28 | 나까무라 겐조 | Electronic actuator |
| US5080131A (en) * | 1989-09-26 | 1992-01-14 | Lintec Co., Ltd. | Mass flow controller |
| US5676309A (en) * | 1994-12-06 | 1997-10-14 | The Lee Company | Thermally responsive flow control valve |
| JPH10281060A (en) * | 1996-12-10 | 1998-10-20 | Toyota Autom Loom Works Ltd | Variable displacement compressor |
| JP3585150B2 (en) * | 1997-01-21 | 2004-11-04 | 株式会社豊田自動織機 | Control valve for variable displacement compressor |
| JP3469435B2 (en) * | 1997-06-27 | 2003-11-25 | 日本ピストンリング株式会社 | Valve seat for internal combustion engine |
| JP4000694B2 (en) * | 1997-12-26 | 2007-10-31 | 株式会社豊田自動織機 | Capacity control valve in variable capacity compressor |
| JP3728387B2 (en) * | 1998-04-27 | 2005-12-21 | 株式会社豊田自動織機 | Control valve |
| JPH11336660A (en) * | 1998-05-27 | 1999-12-07 | Toyota Autom Loom Works Ltd | Variable displacement compressor and assembling method therefor |
| US6321564B1 (en) * | 1999-03-15 | 2001-11-27 | Denso Corporation | Refrigerant cycle system with expansion energy recovery |
| EP1061257B1 (en) * | 1999-06-15 | 2005-01-26 | Fujikoki Corporation | Regulating valve for variable displacement swash plate compressor and its assembly method |
| JP4418571B2 (en) * | 2000-04-11 | 2010-02-17 | シーケーディ株式会社 | High temperature gas control valve |
| EP1172556A3 (en) * | 2000-07-14 | 2004-05-12 | Kabushiki Kaisha Toyota Jidoshokki | Swash plate compressor piston shoes |
| JP3918516B2 (en) * | 2001-11-07 | 2007-05-23 | 株式会社豊田自動織機 | Swash plate compressor |
| US6840054B2 (en) * | 2001-12-21 | 2005-01-11 | Visteon Global Technologies, Inc. | Control strategy of a variable displacement compressor operating at super critical pressures |
| US6715995B2 (en) * | 2002-01-31 | 2004-04-06 | Visteon Global Technologies, Inc. | Hybrid compressor control method |
-
2002
- 2002-11-14 JP JP2002330720A patent/JP2004162640A/en active Pending
-
2003
- 2003-09-08 KR KR1020030062498A patent/KR20040042801A/en not_active Application Discontinuation
- 2003-11-12 US US10/712,910 patent/US20040118140A1/en not_active Abandoned
- 2003-11-12 EP EP03025917A patent/EP1420162A3/en not_active Withdrawn
- 2003-11-13 CN CNA200310120943XA patent/CN1508426A/en active Pending
- 2003-11-13 BR BR0305196-0A patent/BR0305196A/en not_active IP Right Cessation
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597587A (en) * | 2009-11-09 | 2012-07-18 | 株式会社富士金 | Control valve device |
| TWI451030B (en) * | 2009-11-09 | 2014-09-01 | Fujikin Kk | Adjust the valve device |
| CN103547804A (en) * | 2011-05-23 | 2014-01-29 | 学校法人斗源学院 | Control valve for a variable capacity compressor and method for manufacturing same |
| CN103547804B (en) * | 2011-05-23 | 2016-03-09 | 学校法人斗源学院 | Control valve for variable displacement compressor and the method for the manufacture of this control valve |
| CN104373650A (en) * | 2014-11-18 | 2015-02-25 | 温州仁谦汽车油泵有限公司 | Leaf spring type constant pressure valve |
| CN104697505A (en) * | 2015-03-20 | 2015-06-10 | 张家港海纳德智能科技有限公司 | Rotating component for surveying and mapping instrument and manufacturing method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1420162A2 (en) | 2004-05-19 |
| JP2004162640A (en) | 2004-06-10 |
| KR20040042801A (en) | 2004-05-20 |
| US20040118140A1 (en) | 2004-06-24 |
| EP1420162A3 (en) | 2004-09-15 |
| BR0305196A (en) | 2004-08-31 |
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| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |