CN1317073A - Control valve for variable displacement compressor - Google Patents
Control valve for variable displacement compressor Download PDFInfo
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- CN1317073A CN1317073A CN00801324A CN00801324A CN1317073A CN 1317073 A CN1317073 A CN 1317073A CN 00801324 A CN00801324 A CN 00801324A CN 00801324 A CN00801324 A CN 00801324A CN 1317073 A CN1317073 A CN 1317073A
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- 238000006073 displacement reaction Methods 0.000 title abstract 2
- 230000008676 import Effects 0.000 claims description 29
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 description 15
- 238000007906 compression Methods 0.000 description 15
- 230000001815 facial effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 8
- 230000009467 reduction Effects 0.000 description 5
- 238000010276 construction Methods 0.000 description 4
- 238000003825 pressing Methods 0.000 description 4
- 230000004888 barrier function Effects 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 229910021076 Pd—Pd Inorganic materials 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000006200 vaporizer Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 244000287680 Garcinia dulcis Species 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
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Classifications
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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
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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
- 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
- F04B2027/1831—Valve-controlled fluid connection 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
- 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
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A control valve for variable displacement compressor, comprising a ball valve disc (37) which opens and closes communication passages (32, 34, 33) communicating a suction port with a crank chamber of a compressor and is energized in the valve closing direction by a spring force of a compressive coil spring (44), a bellows device (40) driving the ball valve disc (37) in the valve opening direction by the application of a suction pressure of the compressor, the ball valve disc (37) being connected directly with the bellows device (40) with the ball valve disc (37) used as a self-centering ball, and a delivery pressure leading hollow tube body (49) connected to the ball valve disc (37) at one end and applying a delivery pressure of the compressor directly in the valve opening direction of the ball valve disc (37) which is disposed in a valve housing (31), a compressive coil spring (50) energizing the ball valve disc (37) in the valve opening direction through the delivery pressure leading hollow tube body (49).
Description
Technical field
The present invention relates to a kind of control valve for variable capacity compressors, particularly a kind of capacity control drive that is used at the ramp type capacity variable type compressor of uses such as in-vehicle air conditioner.
Background technique
The capacity control drive that is used for the ramp type capacity variable type compressor is as the fair 3-53474 communique of spy, real fair 6-17010 communique, that the spy opens the disclosed capacity control drive of flat 8-177735 communique is known.
This capacity control drive is to rise and reduce the discharge capacity at the pressure corresponding to the crankshaft room of the compressor of built-in swash plate basically, corresponding to reducing, crankshaft room's pressure increases in the capacity variable type compressor of discharge capacity, open and close the suction port of connection compressor and the access of crankshaft room by valve body, control the control valve of the suction pressure of relative crankshaft room compressed and supplied machine, above-mentioned valve body is driven with the equilibrium relation of closing the spring force of valve spring by moving the valve opening force that should move device in the pressure of the suction pressure of compressor, and, head pressure along valve opening position effect compressor, corresponding to head pressure the on-off action point of above-mentioned valve body is offset, carries out and outer gas load (head pressure) relevant volume controlled.
Though above-mentioned existing capacity control drive all is to have reached its intended purposes substantially, but, quantity, the assembling number in man-hour of part have been increased, and in the capacity control drive that directly is assembled in the compressor housing, be used for passway structure complexity with the each several part of suction pressure or head pressure importing capacity control drive, the degrees of freedom of the allocation position in the compressor housing is limited, because these problems, so above-mentioned capacity control drive can not fully satisfy the expection requirement.
Should move device as pressure has diaphragm apparatus and bellows arrangement etc., and if not these pressure should move the driving force that device produces need, can turn round sled to the mobile generation of valve body as responsive to axial force in valve body, and the infringement valve body opens and closes the slyness that moves.Therefore, in the capacity control drive of prior art, must should move at valve body and pressure spring or automatic centering ball are set between the device, thereby bring number of spare parts, the assembling increase in man-hour.
The general introduction of invention
The present invention is conceived to above-mentioned problem points and makes, its objective is provides a kind of control valve for variable capacity compressors, this control valve for variable capacity compressors does not need special automatic centering ball etc., simple structure, do not increase number of spare parts and assembling number in man-hour, and can not make the passway structure complexity as the structure that the compressor housing group is gone into formula yet, the allocation position degrees of freedom in the compressor housing is good.
In order to achieve the above object, the control valve for variable capacity compressors of first technological scheme of the present invention comprises valve chest, ball valve body, spring, pressure should move device, head pressure imports hollow tube, this valve chest has the suction port of connection compressor and the access of crankshaft room, this ball valve body is located in the above-mentioned valve chest and is used to open and close above-mentioned access, this spring suppresses above-mentioned ball valve body to closing the valve direction, this pressure should move device above-mentioned ball valve body directly is connected with above-mentioned ball valve body as the automatic centering ball, drive above-mentioned ball valve body by the suction pressure that is compressed machine to valve opening position, this head pressure imports hollow tube and is entrenched in slidably in the above-mentioned valve chest, one end engages with above-mentioned ball valve body, the other end has the head pressure introducing port of compressor, by internal path the head pressure of the compressor masterpiece as valve opening position is used on the back side of above-mentioned ball valve body.
The simple declaration of accompanying drawing
Fig. 1 is that expression is organized into an embodiment the sectional drawing of capacity variable type compressor of control valve of the present invention.
Fig. 2 is the sectional drawing of expression capacity variable type compression of the present invention with first embodiment of control valve.
Fig. 3 is the plotted curve of head pressure-suction pressure characteristic of the control valve for variable capacity compressors of the expression first embodiment of the present invention.
Fig. 4 is second embodiment's of an expression control valve for variable capacity compressors of the present invention sectional drawing.
Fig. 5 is the 3rd embodiment's of an expression control valve for variable capacity compressors of the present invention sectional drawing.
Be used to implement most preferred embodiment of the present invention
The capacity variable type compression of the first most preferred embodiment of the present invention concrete structure of control valve
At first, with reference to Fig. 1～Fig. 3 the structure of the control valve for variable capacity compressors of the first embodiment of the present invention is described.
As shown in Figure 1, ramp type capacity variable type compressor a plurality of oil hydraulic cylinders chamber 4 of comprising the crankshaft room 3 that delimit by compressor housing 2, being communicated with crankshaft room 3 with the end of travel of each My World.In each oil hydraulic cylinder chamber 4, be free to slide along axial direction chimeric piston 5, crankshaft room's 3 sides of each piston 5 are connecting an end of piston rod 6.
Compressor housing 2 rotatably mounted live axle 7, live axle 7 is connected with not shown engine-driving by the not shown drive belt that is hung on the belt pulley 8, is driven by engine revolution.
Live axle 7 is connecting swash plate 9 by known bindiny mechanism (omitting among the figure) variable setting angle ground with the transmission of torque relation in crankshaft room 3, engaging piston rod 6 on the plate face of oil hydraulic cylinder chamber 4 sides of swash plate 9 with can transmitting axial force.
Drive by live axle 7 rotations with heeling condition by swash plate 9, the piston 5 of each oil hydraulic cylinder chamber 4 is with the stroke reciprocating corresponding to the angle of inclination of swash plate 9, and its tilt angle is adjusted automatically corresponding to the pressure reduction of suction pressure (compressor suction pressure) Ps of the pressure P c of crankshaft room and each oil hydraulic cylinder chamber 4.
At this moment, compressor 1 is by reduce at the angle of inclination of swash plate 9 accordingly, the stroke of piston 5 reduces to reduce the discharge capacity with the rising of the pressure P c of crankshaft room, by the angle of inclination of swash plate 9 increases accordingly, the stroke of piston 5 increases the discharge capacity with the reduction of the pressure P c of crankshaft room, become the pressure that equates in fact with suction pressure Ps by the pressure P c of crankshaft room and become full load operation.
On each oil hydraulic cylinder chamber 4, forming suction port 14 and exhaust port 15, this suction port 14 and exhaust port 15 have suction valve 12, the expulsion valve 13 that is made of one-way valve respectively, the suction port 14 of each oil hydraulic cylinder 4 is communicated with suction connection mouth 17 by sucking path 16, exhaust port 15 is communicated with discharge connection mouth 19 by drain passageway 18, is being connected the refrigeration cycle circulation loop that comprises vaporizer 20, expansion valve 21, condenser 22 etc. on suction connection mouth 17 and discharge connection mouth 19.
On compressor housing 2, forming by the control valve receiving orifice 23 that has bottom outlet to constitute, inserting in this control valve receiving orifice 23 and fixing control valve 30 of the present invention.
As shown in Figure 2, on valve chest 31, form crankshaft room's side path 32, sucking oral-lateral path 33, valve chamber 34, the intermediate portion ground that above-mentioned crankshaft room side path 32 and suction oral-lateral path 33 radially cross valve chest 31 respectively extends, and above-mentioned valve chamber 34 is crankshaft room's side path 32 in the inside of valve chest 31 and sucks between the oral-lateral path 33.In addition, the peripheral part at valve chest 31 is forming all grooves 35 of the ring-type that is used for crankshaft room's side path 32 and the ring-type week groove 36 that is used to suck oral-lateral path 33.
Disposing ball valve body 37 in valve chamber 34, ball valve body 37 carries out crankshaft room's side path 32 and sucks being communicated with of oral-lateral path 33, partition by being seated in selectively on the seat portion 38.
Bellows case 39 is being riveted in a end (underpart) at valve chest 31.
In bellows case 39, disposing the bellows arrangement 40 that should move the airtight construction of device as pressure.Bellows arrangement 40 is had the bellows body 41 of accordion-like of end plate 43 integratedly by an end and the end plate 42 of shrouded bellow body 41 the other ends constitutes, and inside becomes vacuum pressure condition.
Be provided with compression helical spring 44 (being equivalent to the spring in the claim) between end plate 42 in bellows body 41 and the end plate 43, this compression helical spring 44 is used for bellows arrangement 40 is suppressed to the direction (closing the valve direction) of elongation.In addition, end plate 43 sides in bellows body 41 are provided with platen member 45, by the maximum collapse amount that contacts regulation bellows arrangement 40 of the facial 42a of backstop of facial 45a of the backstop of platen member 45 and end plate 42.
Screw-thread fit adjustment screw component 46 in bellows case 39, adjusts screw component 46 by an end that is being kept bellows arrangement 40 by the ball 47 that is configured in these adjustment screw component 46 axis central parts and the sphere joint construction of the spherical recess 42b formation of the axis central part (bellows core) that is formed on the facial 42a of end plate 42 backstops.That is, bellows arrangement 40 is being connected by sphere joint construction sphere by adjusting screw component 46 with bellows case 39.
Forming the embedding hole 48 that connects the central part of valve chest 31 along axial direction in the other end (upper end portion) of valve chest 31.In embedding hole 48 along axial direction chimeric slidably head pressure import hollow tube 49.Head pressure imports hollow tube 49 one ends (lower end) and is being engaged with ball valve body 37 by welding etc.Another distolateral (upper end side) that head pressure imports hollow tube 49 is in the embedding hole 48, constitutes the introducing port 49c of the head pressure Pd of compressor 4.Head pressure import hollow tube 49 with joining portion (underpart) hole enlargement of ball valve body 37, head pressure imports the outside dimension Da of hollow tube 49 and imports the effective diameter Db that hollow tube 49 acts on the facial 37a of pressurized of the pressure on the ball valve body 37 from head pressure and equates.
Import in head pressure and to be provided with between the wide diameter portion 49a of hollow tube 49 and the valve chest 31 ball valve body 37 to compression helical spring 50 (quite the valve body in the claim is composed the gesture device) that valve opening position suppresses.
The elastic load of above-mentioned compression helical spring 50 is set at when ball valve body 37 is driven valve, and ball valve body 37 and bellows arrangement 40 can not rock such value owing to the vibration in the operation process of compressor 1 produces.
The control valve 30 of above-mentioned structure inserts in the control valve receiving orifice 23 that is fixed on compressor housing 2 as illustrated in fig. 1, crankshaft room's side axis 32, all grooves 35 of ring-type are communicated with crankshaft room 3 by crankshaft room's pressure port 24, suction oral-lateral path 33, all grooves 36 of ring-type are communicated with suction port 14 by suction pressure path 25, and embedding hole 48 is communicated with exhaust port 15 by head pressure path 26.
Crankshaft room's pressure port 24, suction pressure path 25, head pressure path 26 are formed in compressor housing 2 pressure inside paths.
Below the action of the control valve 30 that is made of above-mentioned structure is described.
The suction pressure Ps of compressor arrives ring-type week groove 36, sucks oral-lateral path 33 through suction pressure path 25 from suction port 14, from then on enters in the bellows storage case 39 again, acts on bellows arrangement 40.Thus, bellows arrangement 40 stretches according to the pressure reduction of pressing in the suction pressure Ps of compressor 1 and the ripple, and the elastic force that is accompanied by the increase resistance compression helical spring 44 of suction pressure Ps shrinks.Ball valve body 37 is driven valve owing to be discharged from the elastic force that head pressure Pd that pressure imports the compressor that hollow tube 49 imports acts on the facial 37a of pressurized and be compressed helical spring 50 and push to valve opening position owing to contact the contraction of the bellows arrangement that increase produced 40 of suction pressure Ps.
Press the discharge act on the facial 37a of pressurized to press Pd as revisal is one regularly, and ball valve 37 is applied the equilibrium relation driven for opening and closing of the valve closed force that elastic force produced of valve opening force that suction pressure Ps produced on bellows arrangement 40 and compression helical spring 44.
Therefore, be to set when pressing (benchmark setting pressure Pss) following at suction pressure Ps by the control valve of the assumed load of compression helical spring 44 decision, close valve by the elastic force of compression helical spring 44 and move ball valve body 37, ball valve body 37 is seated in and closes valve on the seat portion 38.Thus, stop the supply to the suction pressure Ps of crankshaft room 3, the pressure P c of crankshaft room rises, and compressor 1 becomes the unloading operating condition.
In contrast, when suction pressure Ps set pressure (benchmark setting pressure Pss) greater than control valve, the elastic force of ball valve body 37 resistance compression helical springs 44 was driven valve and is moved, and leaves out valve from seat portion 38.Thus, crankshaft room 3 is supplied with suction pressure Ps, the pressure P c of crankshaft room becomes the pressure identical with suction pressure Ps, and compressor 1 becomes the running at full capacity state.
As mentioned above, make discharge pressure Pd one timing that acts on the facial 37a of pressurized as the revisal pressure, promptly, when not carrying out the high pressure revisal, compressor 1 is ground as dotting among Fig. 3, becomes suction pressure Ps and be benchmark setting pressure Pss and become certain capacity control running.
On the facial 37a of the pressurized of ball valve body 37, directly acting on the head pressure Pd that presses the compressor 1 that is discharged from 49 importings of pressure importing hollow tube as revisal, when the useful area of pressurized face 37 was set at Ah, the valve opening force that is produced by AhPd was attached on the ball valve body 37.
In addition, also acting on the head pressure Pd of compressor 1 on the end face 49b of the introducing port 49c side of the head pressure importing hollow tube 49 in being entrenched in embedding hole 48 slidably, but equate because head pressure imports the effective diameter Db of the facial 37a of pressurized of the outside dimension Da of hollow tube 49 and ball valve body 37, act on the head pressure Pd that end face 49b that head pressure imports hollow tube 49 goes up compressor 1 and disappear mutually.
Owing on valve sphere 37, acting on by the valve opening force by the AhPd generation relevant with head pressure Pd, therefore when the state of equilibrium of being discharged pressure P ds by benchmark is set benchmark setting pressure Pss, because the reduction of head pressure Pd (head pressure Pd discharges pressure P ds less than benchmark) is opened the needed suction pressure Ps of valve and is uprised, because the needed suction pressure Ps step-down of valve is opened in the rising of head pressure Pd (head pressure Pd discharges pressure P ds greater than benchmark).
That is, when head pressure Pd was reduced to Pd ', valve opening force Ah (Pd-Pd ') diminished to degree, from the ratio of the area A d that effectively is stressed of this valve opening force and bellows arrangement 40 draw out valve press with Ah (Pd-Pd '/ Pressure characteristics that Ad rises accordingly.
This situation is expressed from the next, and the effective diameter that the head pressure of the useful area Ah by the facial 37a of selected decision pressurized imports hollow tube 49 obtains to become the affected by high characteristic of purpose.
Ps=Pss-Ah(Pd-Pds)/Ad
Thus, as among Fig. 3 with shown in the solid line like that, can obtain and the increase of the head pressure Pd control characteristic that reduces of suction pressure Ps pro rata, can be by the control characteristic of the head pressure Pd adjustment volume controlled compressor relevant with the system loading characteristic.
Like this, in refrigerant circuit systems, evaporation load and condensation load become proportionate relationship, and evaporation load and refrigeration agent system circulating load are proportional, vaporizer internal pressure loss and circulating mass of refrigerant are proportional, become to be suitable for the efficient volume controlled of economizing the volume controlled compressor of energy system.
In addition, ball valve body 37 directly is connected with bellows arrangement 40, ball valve body 37 plays a role as the automatic centering ball that valve body one pressure should move the sphere connection between device, therefore do not need special automatic centering ball etc., the driving force of bellows arrangement 40 acts on the ball valve body 37 well as axial force.
The concrete structure of the control valve for variable capacity compressors of second most preferred embodiment of the present invention
Then, with reference to Fig. 4 second embodiment of the present invention capacity variable type compressor control valve is described.
Fig. 4 represents second embodiment of control valve for variable capacity compressors of the present invention.In Fig. 4,, omit its explanation with the corresponding part of Fig. 2 mark and the identical symbol of symbol that Fig. 2 is marked.
In this second embodiment, in the hole 51 of the embedding hole that is equivalent to first embodiment (48), to insert and fixing guiding cylindrical shell 52, head pressure imports hollow tube 49 and is linked in slidably on the peripheral part of guiding cylindrical shell 52.
In this second embodiment, on the pressurized face 37a of ball valve body 37, also directly acting on and be discharged from the head pressure Pd that pressure imports the compressor 1 of hollow tube 49 importings as auxiliary the pressure, obtain and equal effect, the effect of first embodiment, the control valve characteristic in the time of reality can being turned round is as the characteristic that is equivalent to head pressure Pd.
In this second embodiment, because can not acting on head pressure, the head pressure Pd of compressor 1 imports on the end face 49a of hollow tube 49, therefore do not need to make the effective diameter of head pressure importing hollow tube 49 consistent with outside dimension.
In this second embodiment, ball valve body 37 is also directly contacting with bellows arrangement 40, ball valve body 37 also plays the effect that valve body-pressure should move the automatic centering ball of the sphere connection between device, therefore, do not need special automatic centering ball etc., the driving force of bellows arrangement 40 acts on the ball valve body 37 well as axial force.
Even in any one embodiment of above-mentioned first and second, it all is the bellows arrangement of airtight construction that pressure should move device, but pressure should move device and be not limited to bellows arrangement 40, also can be diaphragm apparatus etc., will be applicable to that below the embodiment that pressure should move the control valve for variable capacity compressors that device constitutes with diaphragm apparatus describes as the 3rd embodiment.
The concrete structure of the control valve for variable capacity compressors of the 3rd most preferred embodiment of the present invention
Then, with reference to Fig. 5 third embodiment of the present invention capacity variable type compressor control valve is described.
Fig. 5 represents the 3rd embodiment of capacity control drive of the present invention.In Fig. 5,, omit its explanation with the corresponding part of Fig. 2 mark and the identical symbol of symbol that Fig. 2 is marked.
Be provided with pad 69, ball 70, spring in confined chamber 67 sides of chamber of septum 62 order bear member 71, bear member 71 and adjust between the screw 65 at spring and be provided with compression helical spring 72, this compression helical spring 72 by barrier film 62 with ball valve body 37 to closing valve direction (up) pushing.
Chamber of septum 66 is being communicated with valve chamber 34, is given the suction pressure Ps that is imported by valve chamber 34.
In the 3rd embodiment,, therefore in the 3rd embodiment, also can obtain effect, the effect equal with first embodiment because the structure of head pressure importing hollow tube 49 grades and first embodiment's is equal.
In addition, ball valve body 37 directly is connected with diaphragm apparatus 60 by keeping body 68, in this case, because ball valve body also plays the effect of the automatic centering ball that sphere that valve body-pressure should move device connects, therefore do not need special automatic centering ball etc., the driving force of bellows arrangement 40 acts on the ball valve body 37 well as axial force.
In the various embodiments described above, an end (lower end) that head pressure is imported hollow tube 49 is waited by welding and is combining with ball valve body 37, but, also can the end (lower end) that head pressure imports hollow tube 49 be crimped on the ball valve body 37 by the elastic force pressure of compression helical spring 50.
Utilizability on the industry
First～the 3rd each embodiment from the above description as can be known, according to volume-variable of the present invention The type control valve for compressor, it is straight that the discharge pressure of compressor imports hollow tube by discharge pressure Connect and act on the ball valve body, set corresponding to the compressor relevant with system load characteristic and discharge pressure The affected by high characteristic of power (discharge pressure influencing characterisitic). At this moment, by in the discharge pressure importing The setting of the effective diameter of blank pipe body can obtain arbitrarily affected by high characteristic, this affected by high Characteristic imports the selected setting freedom that can be high of the effective diameter of hollow tube by discharge pressure Degree.
In addition, owing to the discharge pressure of compressor is directly done by discharge pressure importing hollow tube Be used on the ball valve body, can reduce number of spare parts, assembling number in man-hour with comparing of prior art, Enter at direct-assembling in the situation of compressor housing, can not be used in suction pressure or discharge are pressed It is complicated that power imports the passway structure of each one of capacity control drive, can the limit compression engine housing in The free degree of allocation position.
In addition, because ball valve body directly should move device with pressure and be connected, ball valve body plays valve body-pressure should move the automatic centering ball effect that the sphere between device connects, so, do not need special automatic centering ball etc., the driving force that pressure should move device acts on the ball valve body well as responsive to axial force, therefore also can reduce number of spare parts, assembling number in man-hour.
In addition, according to control valve for variable capacity compressors of the present invention, on the end face of the discharge importing oral-lateral that is entrenched in the head pressure importing hollow tube in the embedding hole slidably, also acting on the head pressure of compressor, but, head pressure equates with the effective diameter of the pressurized face of ball valve body because importing the outside dimension of hollow tube, the head pressure that acts on the compressor on the end face that head pressure that head pressure imports hollow tube imports oral-lateral is cancelled, and can obtain needed affected by high characteristic.
In addition, according to control valve for variable capacity compressors of the present invention, import the head pressure that can not act on compressor on the end face of hollow tube in head pressure, can obtain needed affected by high characteristic in that head pressure is imported under the effective diameter of the hollow tube situation consistent with outside dimension.
In addition, according to control valve for variable capacity compressors of the present invention, by import hollow tube by head pressure ball valve body the vibration resistance that ball valve body and pressure should move device can be improved to the pushing force of the valve body pressing device of valve opening position pushing, the stable capacity control drive of solemn silence can be obtained.
Claims (4)
1. control valve for variable capacity compressors is characterized in that, comprises that valve chest, ball valve body, spring, pressure should move device, head pressure imports hollow tube; This valve chest has the suction port of connection compressor and the access of crankshaft room; This ball valve body is located in the above-mentioned valve chest and is used to open and close above-mentioned access, and this spring suppresses above-mentioned ball valve body to closing the valve direction; This pressure should move device above-mentioned ball valve body directly is connected as the automatic centering ball and with above-mentioned ball valve body, drives above-mentioned ball valve body by the suction pressure that is compressed machine to valve opening position; This head pressure imports hollow tube and is entrenched in slidably in the above-mentioned valve chest, one end engages with above-mentioned ball valve body, the other end has the head pressure introducing port of compressor, by internal path the head pressure of the compressor masterpiece as valve opening position is used on the back side of above-mentioned ball valve body.
2. control valve for variable capacity compressors as claimed in claim 1, it is characterized in that, above-mentioned head pressure imports hollow tube and is entrenched in slidably in the embedding hole that is formed on the above-mentioned valve chest, and outside dimension equates with the effective diameter of pressurized face that makes above-mentioned ball valve body be compressed the head pressure of machine.
3. control valve for variable capacity compressors as claimed in claim 1 is characterized in that, above-mentioned head pressure imports hollow tube and is linked in slidably on the peripheral part of the guiding cylindrical shell that is fixed on the above-mentioned valve chest.
4. as any one described control valve for variable capacity compressors of claim 1～3, it is characterized in that also having valve body and compose the gesture device, this valve body is composed the gesture device and by above-mentioned head pressure importing hollow tube above-mentioned ball valve body is composed gesture to valve opening position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP189979/1999 | 1999-07-05 | ||
| JP11189979A JP2001020857A (en) | 1999-07-05 | 1999-07-05 | Control valve for variable displacement type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1317073A true CN1317073A (en) | 2001-10-10 |
Family
ID=16250385
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN00801324A Pending CN1317073A (en) | 1999-07-05 | 2000-06-29 | Control valve for variable displacement compressor |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP1111237A1 (en) |
| JP (1) | JP2001020857A (en) |
| KR (1) | KR20010079737A (en) |
| CN (1) | CN1317073A (en) |
| BR (1) | BR0007004A (en) |
| WO (1) | WO2001002726A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100368685C (en) * | 2002-11-12 | 2008-02-13 | 株式会社不二工机 | Control valve for variable capacity compressor |
| CN101762130A (en) * | 2008-12-24 | 2010-06-30 | 上海三电贝洱汽车空调有限公司 | Control valve |
| CN102639871A (en) * | 2009-12-04 | 2012-08-15 | 三电有限公司 | Control valve and variable capacity swash-plate type compressor provided with same |
| CN113646530A (en) * | 2019-04-03 | 2021-11-12 | 伊格尔工业股份有限公司 | Capacity control valve |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10227817A1 (en) * | 2002-02-28 | 2003-09-11 | Taiheiyo Kogyo Kk | Control valve for compressors and its manufacturing process |
| JP5443444B2 (en) * | 2011-07-06 | 2014-03-19 | 株式会社鷺宮製作所 | Pressure sensitive control valve |
| KR101462418B1 (en) * | 2011-12-02 | 2014-11-19 | 주식회사 퍼시픽콘트롤즈 | A Variable Capacity Control Valve |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06200875A (en) * | 1993-01-08 | 1994-07-19 | Toyota Autom Loom Works Ltd | Rocking swash plate type variable displacement compressor |
-
1999
- 1999-07-05 JP JP11189979A patent/JP2001020857A/en not_active Withdrawn
-
2000
- 2000-06-29 BR BR0007004-1A patent/BR0007004A/en not_active IP Right Cessation
- 2000-06-29 KR KR1020017002813A patent/KR20010079737A/en active IP Right Grant
- 2000-06-29 CN CN00801324A patent/CN1317073A/en active Pending
- 2000-06-29 EP EP00940881A patent/EP1111237A1/en not_active Ceased
- 2000-06-29 WO PCT/JP2000/004300 patent/WO2001002726A1/en not_active Application Discontinuation
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100368685C (en) * | 2002-11-12 | 2008-02-13 | 株式会社不二工机 | Control valve for variable capacity compressor |
| CN101762130A (en) * | 2008-12-24 | 2010-06-30 | 上海三电贝洱汽车空调有限公司 | Control valve |
| CN102639871A (en) * | 2009-12-04 | 2012-08-15 | 三电有限公司 | Control valve and variable capacity swash-plate type compressor provided with same |
| CN102639871B (en) * | 2009-12-04 | 2015-07-29 | 三电有限公司 | Control valve and comprise the ramp type variable displacement compressor of control valve |
| CN113646530A (en) * | 2019-04-03 | 2021-11-12 | 伊格尔工业股份有限公司 | Capacity control valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2001020857A (en) | 2001-01-23 |
| EP1111237A1 (en) | 2001-06-27 |
| WO2001002726A1 (en) | 2001-01-11 |
| BR0007004A (en) | 2001-06-19 |
| KR20010079737A (en) | 2001-08-22 |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
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| AD01 | Patent right deemed abandoned | ||
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