CN1078675C

CN1078675C - Variable displacement compressor

Info

Publication number: CN1078675C
Application number: CN97110049A
Authority: CN
Inventors: 川口真广; 园部正法; 水藤健; 深昭哲彦; 永井宏幸; 牧野善洋; 三浦慎太郎
Original assignee: Toyoda Automatic Loom Works Ltd
Current assignee: Toyota Industries Corp
Priority date: 1996-03-12
Filing date: 1997-03-11
Publication date: 2002-01-30
Anticipated expiration: 2017-03-11
Also published as: DE19709935C2; FR2746146B1; KR970066085A; KR100212769B1; DE19709935A1; TW400919U; CN1168448A; FR2746146A1

Abstract

A variable displacement type compressor having a piston accommodated in a cylinder bore, a swash plate accommodated in a crank chamber for reciprocating the piston and a drive shaft for tiltably and rotatably supporting the swash plate. The swash plate includes projections that extend toward a thrust bearing and have outer surfaces that contact the thrust bearing. A shaft hole within which the drive shaft is located between the projections. The shaft hole has an opening that opens adjacent to the projections. A recess is formed at the end of the shaft hole adjacent to the projections. A hardening method is performed on the wall of the through hole and on the outer surfaces of the projections to improve wear resistance. The hardening method prevents overheating of localized areas of the swash plate.

Description

Variable displacement compressor

The present invention relates to a kind of variable displacement compressor that in vehicle air conditioning, uses.Particularly relate to a kind of variable displacement compressor that changes its capacity by the inclination angle of adjusting a cam disk.

Variable displacement compressor generally has a cam disk, and this cam disk tiltably is supported on the live axle.The cam disk inclination angle is controlled according to the pressure reduction between pressure in the crank chamber and the cylinder-bore internal pressure.The stroke of each piston is changed by the inclination angle of cam disk.

Variable displacement compressor has a live axle usually, and this live axle directly links to each other as a motor with an external drive source, and between does not have clutch.In this no-clutch system, when not needing refrigerating function or just having frost to form in vaporizer, compressor also still continues operation.Disclosed variable displacement compressor among Japanese unexamined patent publication No.3-37378 and the 7-127566, when need not freeze or vaporizer in when just having frost to form, stop the circulation of refrigerant gas.

Compressor described in the Japanese unexamined patent publication No.3-37378 stops refrigerant gas from the importing of external refrigeration loop to suction chamber, to stop gas circulation by a solenoid valve.It is too fast that yet solenoid valve opens or closes the speed of the passage between external refrigeration loop and suction chamber, can suddenly increase or reduce the gas flow that enters into cylinder-bore from suction chamber.The unexpected variation that flows into the gas flow of cylinder-bore can cause the rapid fluctuation of compressor capacity, so the head pressure of compressor also fluctuates.This has clearly changed the load torque of compressor, i.e. the necessary moment of torsion of operate compressor in the short time.

The described compressor of Japanese unexamined patent publication No.7-127566 has a valve in connecting the discharge route of discharging chamber and external refrigeration loop.When discharging indoor pressure (head pressure) and the difference between the pressure (suction pressure) in the suction pressure district when being equal to or less than predeterminated level, valve cuts out discharge route, and refrigerant gas is stopped to the mobile of external circuit by compressor.Pressure reduction between head pressure and the suction pressure changes slowly.Therefore, valve changes the cross sectional area of passage overcurrent lentamente according to the pressure reduction between head pressure and the suction pressure, and refrigerant gas this flow section of flowing through is discharged to the external refrigeration loop from discharging the chamber.This makes the fluctuation from the discharge chamber to the gas flow of external circuit become slowly, has therefore avoided the sudden change of compressor load moment of torsion.

Valve described above comprises a cylinder shape valve.Valve body has a face that bears head pressure to bear the face of suction pressure with another.The suction pressure bearing surface is relative with the position of head pressure bearing surface.Valve body moves vertically according to the pressure reduction that acts between its lip-deep pressure.Big pressure reduction can cause discharges indoor higher pressure refrigerant gas by the valve body periphery with hold clearance leakage between the wall of chamber of valve body to the suction pressure zone, and the leakage of gas makes the refrigerating efficiency reduction of external refrigeration cycle.

Therefore, an object of the present invention is to provide a kind of compressor, it can avoid the sudden change of compressor load moment of torsion, and does not reduce refrigerating efficiency, and can avoid the formation of frost.

For achieving the above object, according to the invention provides a kind of compressor, comprise: be positioned at crank chamber and be installed in cam disk on the live axle, the piston that is positioned at cylinder-bore and matches with cam disk, described cam disk is converted into the to-and-fro motion of piston in cylinder-bore with the rotation of live axle, described piston is to compressing from the gas that independent external circuit is conducted to cylinder-bore by means of suction chamber, and pressurized gas is drained in the external circuit by means of discharging the chamber, described cam disk, according to pressure in the crank chamber and the pressure reduction between the pressure in the cylinder-bore, with respect to becoming the position of inclination maximum with the perpendicular plane of the axis of live axle and becoming between the minimum angle-of-incidence position, and described piston moves according to the stroke based on the inclination angle gained of cam disk, control the capacity of compressor, it is characterized in that, also comprise: a discharge route, will discharge chamber and external circuit and be communicated with; A valve that is positioned at discharge route, described valve is according to acting on the pressure of valve upstream extremity and acting on that pressure reduction between the pressure of valve downstream will be discharged the chamber selectively and the external circuit is switched on or switched off; And a discharge silencing apparatus, this discharge silencing apparatus prevents that gas is discharged to caused vibration when discharging the chamber from the cylinder orifice flow, described discharge route is arranged on the inside of discharging silencing apparatus.

Novel feature of the present invention proposes in claims in detail.And its purpose of the present invention and advantage are by hereinafter following the described most preferred embodiment of accompanying drawing can be more cheer and bright.Wherein:

Fig. 1 is the cross-section profile of the variable displacement compressor of first embodiment of the invention;

Fig. 2 is the sectional view of doing to analyse and observe along Fig. 1 center line 2-2;

Fig. 3 is the sectional view of doing to analyse and observe along Fig. 1 center line 3-3;

Fig. 4 is that the inclination angle of wobbler is the cross-section profile of hour variable displacement compressor;

Fig. 5 is the local enlarged cross sectional view of solenoid compressor during by excitation and one-way valve opens;

Fig. 6 is the local enlarged cross sectional view of solenoid compressor during by excitation and closed check valve;

Fig. 7 is that solenoid is demagnetized and the local enlarged cross sectional view of compressor during closed check valve;

Fig. 8 is the cross-section profile of second embodiment's of the present invention variable displacement compressor;

The local enlarged cross sectional view of compressor when Fig. 9 is closed check valve;

Figure 10 is the perspective view of an one-way valve;

Figure 11 (a) is the 3rd embodiment's the local enlarged cross sectional view of compressor when closed check valve; And

Figure 11 (b) is the 3rd embodiment's the local enlarged cross sectional view of compressor when one-way valve opens.

With reference to Fig. 1 to Fig. 7, first embodiment of variable displacement compressor of the present invention is described below.

As shown in Figure 1, front case 12 is fixed together with the front-end face of cylinder block 11.Rear case 13 is fixed together with the ear end face of cylinder block 11, and between is provided with first plate 14, second plate 15, the 3rd plate 16 the 4th plate 17.Crank chamber 121 is surrounded by the inwall of front case 12 and the front-end face of cylinder block 11.

Rotatable live axle 18 is supported in front case 12 and the cylinder block 11.The front end of live axle 18 stretches out from crank chamber 121, and is connected with a belt pulley 19.Belt pulley 19 by one be with 20 directly with an external drive source (being motor car engine E among this embodiment) mutually coupling join.The compressor of Fig. 1 is a no-clutch type variable displacement compressor, does not have clutch between live axle 18 and external drive source.Belt pulley 19 is supported by means of a radial bearing 21 that is positioned between the two by front case 12.Front case 12 bears thrust and the radial load that acts on the belt pulley 19 by radial bearing 21.

A wobbler 23 that is close to dish type is substantially supported by the live axle in the crank chamber 121 18, so that can be along the axis slip of axle 18 with respect to this axis tilt.As depicted in figs. 1 and 2, wobbler 23 is equipped with a pair of

guide finger

26,27, and each guide finger all has a SDeflector 261,271.

Guide finger

26,27 is fixed on the wobbler 23 by supporting 24,25 respectively.Rotor 22 is installed on the live axle 18 in the crank chamber 121, and with live axle 18 unitary rotation.Rotor 22 has a support arm 221 that stretches out to the direction of wobbler 23.A pair of pilot hole 222,223 forms on support arm 221.Each SDeflector 261,271 is packed in the corresponding pilot hole 222,223 slidably.The acting in conjunction of arm 221 and

guide finger

26,27 make wobbler 23 can with live axle 18 unitary rotation.This acting in conjunction is also led along moving of live axle 18 axis for the banking motion of wobbler 23 and wobbler 23.Because wobbler 23 is to slide to the direction of cylinder block 11 or opposite direction, so reduce at the inclination angle of wobbler 23.

A helical spring 28 is arranged between rotor 22 and wobbler 23.Spring 28 promotes wobbler 23 backward or to the direction at the inclination angle that can reduce wobbler 23.

As shown in figures 1 and 3, a plurality of cylinder-bore 111 are set at and pass that cylinder block 11 is extended and on the position of live axle 18.Each hole 111 all is positioned at the position that parallels with the axis of live axle 18, leaves a predetermined gap between per two adjacent holes 111.A single head pison 37 all is housed in each hole 111.A pair of hemispheric piston shoes 38 all are housed between each piston 37 and wobbler 23, and each piston shoes 38 all has a hemisphere portion and a planar section.Hemispherical portion is joined with piston 37 slidably, and planar section then joins with wobbler 23 slidably.Wobbler 23 and live axle 18 unitary rotation.The rotation of wobbler 23 is delivered to each piston 37 by piston shoes 38, and is converted into the straight reciprocating motion of each piston 37 in the cylinder-bore 111 that is associated.

As shown in figs. 1 and 3, an annular suction chamber 131 is arranged in rear case 13.In rear case 13, be provided with an annular and discharge chamber 132 around suction chamber 131.Suction port 141 and exhaust port 142 on first plate 14, have been formed.Each suction port 141 and each exhaust port 142 are all corresponding to a cylinder-bore 111.On second plate 15, form suction valve 151.Each suction valve 151 is all corresponding to a suction port 141.On the 3rd plate 16, expulsion valve 161 is arranged.Each expulsion valve 161 is corresponding to an exhaust port 142.

When each piston 37 in corresponding cylinder-bore 111 from upper dead center when lower dead centre moves, suction chamber 131 interior refrigerant gas are inhaled in the cylinder-bore 111 by corresponding suction port 141 and suction valve 151.When each piston 37 in corresponding cylinder-bore 111 from lower dead centre when upper dead center moves, refrigerant gas is compressed in cylinder-bore 111, and is discharged to discharge chamber 132 by corresponding exhaust port 142 and corresponding expulsion valve 161.On the 4th plate 17, form plate washer 171.Each plate washer 171 is corresponding with an expulsion valve 161.The contact of valve 161 and corresponding plate washer 171 has limited opening of each expulsion valve 161.

A thrust-bearing 39 is housed between front case 12 and rotor 22.Thrust-bearing 39 bears from piston 37 and wobbler 23 and acts on compression force on the rotor 22.

As shown in figs. 1 and 4, the axis along live axle 18 extends to form a valve chamber 29 at the middle part of cylinder block 11.Valve chamber 29 communicates with suction chamber 131 by a port 143.The cylinder valve 30 of a hollow is housed in the valve chamber 29, and it can slide along the axial direction of live axle 18.Between the wall of valve chamber 29 and valve 30 helical spring 31 is arranged, helical spring 31 promotes valve 30 to the direction of wobbler 23.

Insert in the valve 30 rear end of live axle 18.Radial bearing 32 is fixed on the inwall of valve 30 with a split circlip 33.Therefore, radial bearing 32 together moves along the axis of live axle 18 with valve 30.Live axle 18 rear ends are supported by the inwall of valve chamber 29 and therebetween radial bearing 32 and valve 30.

There is a suction passage 34 middle part and first plate, 14 to the 4th plates, 17 intermediate portions at rear case 13.Passage 34 extends along the axis of live axle 18, and communicates with valve chamber 29.Around the internal end surface of suction passage 34, on second plate 15, form a locating face 35.The ear end face of valve 30 can engage with locating face 35.Valve 30 prevents that with engaging of locating face 35 valve from moving to the rear further from wobbler, and suction passage 34 and valve chamber 29 are disconnected.

A thrust-bearing 36 supporting driving shafts 18 are arranged between wobbler 23 and valve 30.Thrust-bearing 36 slides along the axis of live axle 18.The power of helical spring 31 is clamped in thrust-bearing 36 between wobbler 23 and the valve 30 all the time.Thrust-bearing 36 prevents that the rotation of wobbler 23 is transferred to valve 30.

When reduced at the inclination angle of wobbler 23, wobbler moved backward.During along with backward mobile of wobbler, promote valve 30 backward by thrust-bearing 36.Correspondingly, valve 30 power that overcomes helical spring 31 moves to locating face 35.As shown in Figure 4, when wobbler 23 reached the incident angle of minimum, valve 30 ear end faces contacted with locating face 35.This makes valve 30 be in the closed position that valve chamber 29 and suction passage are disconnected.

A pressure relief channels 40 is arranged in the center portion of live axle 18.Pressure relief channels 40 communicates the inside of crank chamber 121 and valve 30.Near the rear end of valve 30, a pressure relief opening 301 is arranged on its circumference wall.Hole 301 makes the inside of valve 30 communicate with valve chamber 29.

A discharge route 133 is arranged in rear case 13, and it is connected with discharge chamber 132.External refrigeration loop 45 will discharge chamber 133 and suction passage 34 couples together.External refrigeration loop 45 comprises a condenser 46, an expansion valve 47 and a vaporizer 48.Expansion valve 47 is controlled the flow of refrigeration agent according to the fluctuation of the gas temperature in vaporizer 48 outlet ports.

Shown in Fig. 1 and 5, an one-way valve 52 is arranged in the discharge route 133.One-way valve 52 comprises 521, one circlips 53 of cylinder shape valve and spring 54 of a hollow.Circlip 53 is fixed in the groove on discharge route 133 inwalls, and spring 54 is positioned at the centre of valve body 521 and circlip 53.Valve body 521 slides along the axis of passage 133.A valve opening 134 makes discharge chamber 132 communicate with discharge route 133, and spring 54 is the closing direction promotion valve body 521 of valve opening 134 to the inner of discharge route 133.On the inwall of discharge route 133, a circuitous groove 135 is arranged between valve body 134 and circlip 53.Circuitous groove 135 constitutes the part of discharge route 133.A through hole 522 is arranged on the perisporium of valve body 521.As Fig. 1 and shown in Figure 5, when valve body 521 was in the position of opening valve opening 134, the refrigerant gas in the discharge chamber 132 was discharged to external refrigeration loop 45 by the inside of valve opening 134, circuitous groove 135, through hole 522 and valve body 521.As shown in Figure 6 and Figure 7, when valve body 521 was in the position of close valve orifice 134, valve body 521 prevented that the refrigerant gas of discharging in the chamber 132 is discharged to external refrigeration loop 45.

As Fig. 1 and shown in Figure 5, a supply passage 41 is arranged in rear case 13, pass first plate, 14 to the 4th plates 17 and cylinder block 11.Supply passage 41 is connected and is discharged chamber 132 and crank chamber 121.The capacity control drive of installing in the rear case 13 42 is in the intermediate portion of supply passage 41.Control valve 42 includes a valve body 44, a bellows 51 and a solenoid 43.Valve body 44 opens or closes valve opening 421 selectively.Control by bellows 51 by the opening that valve body 44 and valve opening 421 limit.

When solenoid 43 was demagnetized, valve body 44 was opened valve opening 421, entered crank chamber 121 with the refrigerant gas that allow to discharge in the chamber 132 by supply passage 41.The pressure of suction passage 34 (suction pressure) acts on the bellows 51 by a passage 136.The suction pressure reflection cooling load of suction passage 34.When solenoid 43 during by excitation, the opening between valve body 44 and the valve opening 421 is according to the suction pressure control that acts on the bellows 51.In other words, from discharging the flow of chamber 132, control according to cooling load to the refrigerant gas of crank chamber 121.Pressure in the crank chamber 121 is therefore controlled.

Starting the switch 50 of air-conditioning is received on the computer C.When switch opens, computer C excitation solenoid 43.When switch cut out, computer C made solenoid 43 demagnetizations.

The operation of above-described variable displacement compressor will be described below.

In Fig. 5 and Fig. 6, the solenoid 43 in the control valve 42 is by excitation.Under this state, when the gas pressure in the suction passage 34 increased with the increase of cooling load, as shown in Figure 5, bellows 51 shrank, and makes the opening that is limited by valve body 44 and valve opening 421 become narrow.This has reduced by supply passage 41 from discharging the gas flow of chamber 132 to crank chamber 121.On the other hand, the refrigerant gas in the crank chamber enters suction chamber 131 by inside, pressure relief opening 301, valve chamber 29 and the port 143 of pressure relief opening 40, valve 30.Pressure in the crank chamber 121 correspondingly descends.This has reduced the pressure reduction between crank chamber 121 and the cylinder-bore 111, so the inclination angle of wobbler 23 increases.Therefore capacity increases.

When a great cooling load promptly, when a high gas pressure in the suction passage 34 causes valve body 44 close valve orifice 421, this has just closed supply passage 41.The higher pressure refrigerant gas of discharging in the chamber 132 does not enter in the crank chamber 121.This makes the inclination angle of wobbler 23 as shown in Figure 1 reach maximum.Correspondingly, compressor brings into operation at the maximum capacity place.Boss on the wobbler 23 leans against on the boss 224 that stretches out from rotor 22 ear end faces, can avoid the inclination angle of wobbler 23 to exceed predetermined inclination maximum like this.

Under the situation of solenoid 43 excitations, as shown in Figure 6, when the gas pressure in the suction passage 34 reduced with the minimizing of cooling load, bellows 51 elongations made the opening increase that is limited by valve body 44 and valve opening 421.This has increased by supply passage 41 from discharging the gas flow of chamber 132 to crank chamber 121, so increased the pressure in the crank chamber 121.Thereby increased the pressure reduction between crank chamber 121 and the cylinder-bore 111, therefore reduced the inclination angle of wobbler 23, capacity also reduces thereupon.

When a minimum cooling load promptly, when suction passage 34 in one extremely hangs down gas pressure and has increased the opening that is limited by valve body 44 and valve opening 421, just increased the refrigerant gas amount that enters crank chamber 121 from discharge chamber 132, therefore made the inclination angle of wobbler 23 reach minimum.Correspondingly, compressor brings into operation under minimum capacity.Further, as shown in Figure 7, the solenoid 43 of demagnetization makes the opening that is limited by valve body 44 and valve opening 421 reach maximum in control valve 42, and this makes the inclination angle of wobbler 23 become minimum, causes compressor to move under its minimum capacity.

When the inclination angle of wobbler 23 for hour, valve 30 contacts with locating face 35.Boss on the valve 30 leans against on the locating face 35, makes suction passage 34 and suction chamber 131 disconnect.Valve 30 slides with the variation at the inclination angle of wobbler 23.Therefore, when the inclination angle of wobbler 23 reduced, valve 30 made from suction passage 34 to suction chamber the cross sectional area of 131 air-flow path reduce gradually.This reduces the refrigerant gas amount that enters suction chamber 131 from suction passage 34 gradually.Therefore the refrigerant gas amount that sucks in the cylinder-bore 111 from suction chamber 131 also reduces gradually.The capacity of compressor reduces gradually as a result.Get rid of pressure reduces thereupon gradually.Thereby reduced the load torque of compressor gradually.In this manner, notable change does not take place in the load torque of compressor at short notice.Therefore the vibration of following the load torque fluctuation and producing also reduces.

Shown in Fig. 6 and 7, the boss that heads on the valve 30 of locating face 35 prevents that the inclination angle of wobbler 23 from becoming littler than predetermined minimum angle-of-incidence.This boss also makes suction passage 34 and suction chamber 131 disconnect.This makes from external refrigeration loop 45 to suction chamber 131 air-flow stop, thereby has stopped the circulation of the refrigerant gas between loop 45 and the compressor.Extremely low gas pressure can cause that the temperature of vaporizer 48 drops to the temperature that frost can form in the suction passage 34.Yet in this case, compressor moves under the minimum capacity state, and the gas circulation of external refrigeration loop 45 and compressor chamber stops.This prevents frosting in vaporizer 48.

The minimum angle-of-incidence of wobbler 23 is bigger slightly than zero degree.Zero degree is meant when the wobbler 23 and the axis of live axle 18 are perpendicular, the angle of inclination of wobbler.Therefore, even under the inclination angle of wobbler 23 is minimum situation, refrigerant gas also can drain into from cylinder-bore 111 and discharge chamber 132, and compressor is moved under the minimum capacity state.Be discharged to the refrigerant gas of discharging chamber 132 from cylinder-bore 111 and suck crank chamber 121 by supply passage 41.Refrigerant gas in the crank chamber 121 is sucked back in cylinder-bore 111 by pressure relief channels 40, pressure relief opening 301 and suction chamber 131.Just, when the inclination angle of wobbler 23 for hour, refrigerant gas is through discharging chamber 132, supply passage 41, crank chamber 121, pressure relief channels 40, pressure relief opening 301, suction chamber 131 and cylinder-bore 111 and circulating in compressor.The circulation of this refrigerant gas makes the lubricant oil that is included in the gas be able to each interior sliding parts of lubricate compressors.

When compressor moves under the minimum capacity state, in other words, when the inclination angle of wobbler 23 for hour, capacity pressure descends.Spring 54 has a ratio to be scheduled to straight bigger power.Just, determine the amplitude of spring force in the following manner, promptly when compressor moved under the minimum capacity state, the pressure in the power of spring 54 and one-way valve 52 downstreams (pressure in the zone that is connected with external refrigeration loop 45) sum was greater than the pressure (pressure in the zone that communicates with discharge chamber 132) of one-way valve 52 upstreams.Therefore, be under the situation of minimum at the inclination angle of wobbler 23, valve body 521 close valve orifice 134 thus, make and

discharge chamber

132 and 45 disconnections of external refrigeration loop.

When the inclination angle of wobbler when Fig. 6 and state shown in Figure 7 begin to increase, the power of spring 31 promotes valve 30 gradually, makes it away from locating face 35.This has strengthened gradually from suction passage 34 to suction chamber the cross sectional area of 131 gas flow.So the refrigerant gas amount that enters suction chamber 131 from suction passage 34 just increases gradually.Therefore, suck the also increase gradually of refrigerant gas amount of cylinder-bore 111 from suction chamber 131.Correspondingly, the capacity of compressor also increases gradually.The head pressure of compressor improves gradually, and the load torque of compressor also increases gradually.In the case, the load torque of compressor notable change can not occur at short notice.Thereby follow load torque fluctuation and the vibration that occurs has also just reduced.

When the head pressure of compressor increased with the increase at wobbler 23 inclination angles, the upstream pressure of one-way valve 52 became greater than the summation of the power of one-way valve 52 downstream pressures and spring 54.Therefore, when the inclination angle of wobbler 23 during greater than minimum angle-of-incidence, valve body 521 is opened valve opening 134, so that the refrigerant gas that allows to discharge chamber 132 is discharged to external refrigeration loop 45 by discharge route 133.

If shutting engine down E, compressor are also with regard to quit work (rotation that is wobbler 23 stops), and 43 demagnetizations of the solenoid in the control valve 42.Under this state, the inclination angle of wobbler 23 is minimum as shown in Figure 7.If compressor continues this not operating state, the pressure in the compressor will become evenly, and wobbler 23 remains under the minimum angle-of-incidence by the elastic force of spring 28.Therefore, when motor E started again, compressor was at wobbler under the situation of minimum angle-of-incidence, moment of torsion minimum and brings into operation.Thereby make the vibration that causes by compressor start become minimum.

According to the compressor valve among the above-mentioned Japanese unexamined patent publication No.7-127566, according to the head pressure that acts on valve body one end and act on pressure reduction between the suction pressure of the valve body the other end, open or close selectively and connect the discharge route of discharging chamber and external refrigeration loop.Therefore, when the pressure reduction between head pressure and the suction pressure is big, discharge indoor pressurized gas by the clearance leakage between the chamber inner wall of valve body periphery and containing valve body to the suction pressure zone.

In aforementioned compressor, with different at the described compressor of the prior art of background parts, discharge route 133 will discharge chamber 132 simply and external refrigeration loop 45 couples together.One-way valve 52 in discharge route 133 is according to the pressure of the upstream extremity that acts on one-way valve 52 and act on pressure reduction between the pressure of downstream of one-way valve 52, opens or closes discharge route 133 selectively.That is to say that the compressor among Fig. 1 is design like this: suction pressure does not act on the one-way valve 52.Prevented that the refrigerant gas of discharging in the chamber 132 from leaking into the suction pressure zone.Therefore, the refrigerating efficiency in external refrigeration loop 45 is improved.

Compressor among the Japanese unexamined patent publication No.7-127566 has a passage that is designed to the pressure pilot valve in suction pressure district.This passage makes the structure of compressor and manufacturing become complicated.In the present invention, unlike the prior art, only one-way valve 52 is arranged in the discharge route 133 that connects discharge chamber 132 and external refrigeration loop 45.Therefore, need not form one again with the lead passage of one-way valve 52 of suction pressure.Like this, just simplified the structure of compressor, and be easy to make.

Compare with vaporizer 48 with the condenser 46 as heat exchanger in the loop 45, when compressor was out of service, its temperature descended rapidly.Therefore, when compressor did not move, refrigeration agent was easy to be inhaled into compressor from external refrigeration loop 45.If refrigeration agent is inhaled into compressor, then its liquefies and is trapped in the there.The refrigeration agent of liquefaction has diluted the oiling agent in the compressor, and has washed the part that need lubricate.

Yet in the present invention, the inclination angle of wobbler 23 is for hour, and one-way valve 52 prevents that the refrigeration agent in the external refrigeration loop 45 from bleeding and discharges chamber 132.And valve 30 prevents the suction chamber 131 that bleeds of the refrigeration agent in the loop 45.Therefore, the oiling agent that has diluted can not be trapped in the compressor.

When the inclination angle of wobbler 23 for hour, the valve body 44 in the control valve 42 is opened valve opening 421.Under this state, refrigerant gas circulates in compressor through discharging chamber 132, supply passage 41, crank chamber 121, pressure relief channels 40, suction chamber 131 and cylinder-bore 111.When the inclination angle of wobbler for hour, refrigerant gas has increased pressure in the crank chamber 121 from external refrigeration loop 45 to the backflow of discharging chamber 132.When the inclination angle of wobbler 23 when minimum angle-of-incidence begins to increase, promptly the capacity of compressor is when minimum capacity begins to increase, the pressure in the crank chamber 121 is low more, the increase of compressor capacity is just fast more.In the above embodiment, when the inclination angle of wobbler 23 for hour, one-way valve 52 prevents refrigerant gas 45 backflows to suction chamber 131 from the loop.This has kept pressure in the crank chamber 121 a low level, increases its capacity fast to allow compressor.

With reference to Fig. 8 to Figure 10 second embodiment of the present invention described below.The parts similar or identical with first embodiment are with similar or identical symbolic representation.

A solenoid valve 62 is arranged in rear case 13.Valve 62 is positioned at the intermediate portion of supply passage 41.As shown in Figure 8, be arranged in the excitation of the solenoid 63 of solenoid valve 62, cause valve body 64 close valve orifice 621.As shown in Figure 9, solenoid 63 demagnetization causes that valve body 64 opens valve opening 621.Solenoid valve 62 opens or closes selectively and will discharge the supply passage 41 that chamber 132 and crank chamber 121 are connected.

A temperature transducer 49 is arranged near vaporizer 48.Temperature transducer 49 detects the temperature of vaporizer 48, and the temperature data that is detected is sent to computer C.Computer C basis is from the solenoid 63 in the numerical control solenoid valve 62 of sensor 49.Specifically, when switch 50 was opened, if the temperature that is detected by temperature transducer 49 is equal to or less than predetermined temperature, computer C made solenoid 63 demagnetizations, opens valve opening 621, to prevent frosting in vaporizer 48.When switch 50 cut out, computer C made solenoid 63 demagnetizations, to open valve opening 621.

Fig. 8 shows such state: the solenoid 63 in the valve 62 is by excitation, with by valve body 64 close valve orifice 621, thereby closes supply passage 41.The higher pressure refrigerant gas of discharging in the chamber 132 is not fed to crank chamber 121.Refrigerant gas in the crank chamber 121 enters suction chamber 131 by pressure relief channels 40 and pressure relief opening 301.Pressure in the crank chamber 121 is suction pressure near the low-pressure in the suction chamber.This has reduced pressure in the crank chamber 121 and pressure reduction between cylinder-bore 111 internal pressures.The inclination angle of wobbler 23 thereby become maximum, compressor moves under maximum capacity.

When compressor moved under the state of the inclination angle of wobbler for maximum, the reduction of cooling load caused that the temperature of the vaporizer 48 in the external refrigeration loop 45 descends gradually.When the temperature of vaporizer was equal to or less than the formation temperature of frost, computer C made solenoid 63 demagnetizations according to the testing signal from temperature transducer 49.As shown in Figure 9, the demagnetization of solenoid 63 causes that valve body 64 opens valve opening 621.The higher pressure refrigerant gas that to discharge in the chamber 132 by supply passage 41 supplies to crank chamber 121 like this, thereby increases the pressure in the crank chamber 121.Pressure reduction between the interior pressure of pressure in the crank chamber 121 and cylinder-bore 111 thereby be increased.This makes wobbler 23 move to minimum angle-of-incidence from inclination maximum.So compressor brings into operation under minimum capacity.Off switch 50 also make solenoid 63 demagnetizations, thereby mobile wobbler 23 is to minimum angle-of-incidence.

Be formed with a discharge silencing apparatus 551 on the top of cylinder block 11 and front case 12.Discharge silencing apparatus 551 and comprise first housing 113 and second housing 122.First housing 113 is made integral body with cylinder block 11, is positioned on the periphery of cylinder block.Second housing 122 is made integral body with front case 12, is positioned on the periphery of front case 12.Silencing apparatus chamber 55 forms in first housing 113 and second housing 122.The cylindrical oil separator 56 and first housing 113 are integral, and are positioned at silencing apparatus chamber 55.Communication passage 57 makes silencing apparatus chamber 55 communicate with discharge chamber 132.A narrow oily passage 123 makes silencing apparatus chamber 55 communicate with crank chamber 121.

A formed passage and external refrigeration loop 45 join in oil separator 56.The part of this passage that links to each other with loop 45 has constituted a discharge route 561.One-way valve 58 is housed in the discharge route 561.One-way valve 58 comprises hollow cylindrical valve body 59, circlip 60 and spring 61.Circlip 60 is fixed in the groove on the inwall of discharge route 561, and spring 61 is between valve body 59 and circlip 60.Valve body 59 axis along passage 561 in discharge route 561 slides.The inner of discharge route 561 constitutes a valve opening 562.Spring 61 is that the direction that valve opening 562 is closed promotes valve body 59 to the direction of the inner of discharge route 561.As shown in figure 10, on the periphery of valve body 59, form a plurality of through holes 591.One-way valve 52 among the one-way valve 58 and first embodiment has identical functions.

Be discharged to the refrigerant gas of discharging chamber 132 from cylinder-bore 111 and enter silencing apparatus chamber 55 by communication passage 57.Caused vibration and noise when this has prevented gas from cylinder-bore inflow discharge chambers 132 111.Be sucked into the refrigerant gas of silencing apparatus chamber 55, shown in arrow P among Fig. 8, before the inner passage that enters separator 56, flow around oil separator 56 earlier.Refrigerant gas promotes valve body 59, and flows in the external refrigeration loop 45 through the inside of through hole 591 and valve body 59.

Produced a centrifugal effect around the refrigerant gas of oil separator 56 around operation.This effect is separated the oiling agent of mist from refrigerant gas.The oiling agent that is separated is fallen the bottom of silencing apparatus chamber 55.Therefore oiling agent is successfully separated from refrigerant gas.Prevented that oiling agent from discharging from compressor with refrigerant gas.The oiling agent of 55 bottoms, silencing apparatus chamber is fed to crank chamber 121 by oily passage 123.As a result, oiling agent just can lubricate the corresponding site in the crank chamber 121.

Second embodiment also has following advantage except the advantage with first embodiment.

One-way valve 58 is installed in the discharge route 561 that forms in the oil separator 56, and this has simplified the structure of the discharge route that holds one-way valve 58.

According to second embodiment, use one-way valve 58 to eliminate needed circuitous groove 135.Compare with first embodiment, simplified the structure of discharge route.

Below with reference to Figure 11 (a) and 11 (b) third embodiment of the present invention is described.For the parts similar or identical with first and second embodiments with similar or identical symbolic representation.

Be formed with discharge silencing apparatus 66 on the top of cylinder block 11 and front case 12.Discharge silencing apparatus 66 and comprise first housing 113 and second housing 122.First housing 113 is made integral body with cylinder block 11, is positioned on the periphery of cylinder block 11, and second housing 122 is integral with front case 12, is positioned on its periphery.Silencing apparatus chamber 65 is limited in first housing 113.Communication passage 114 is connected silencing apparatus chamber 65 and discharge chamber 132.In first housing 113, be formed with a discharge route 67.Discharge route 67 comprises valve chamber 671 and exhaust port 672.One-way valve 68 is arranged in the valve chamber 671.Exhaust port 672 communicates with external refrigeration passage 45.Valve chamber 671 extends in the horizontal direction, and its opening is relative with second housing 122.Exhaust port 672 vertically extends, and its opening is on the top surface of first housing 113.The passage 69 that forms in second housing makes silencing apparatus chamber 65 communicate with valve chamber 671.

One-way valve 68 is the whole assemblys that are made of housing 70, valve body 71, spring 72 and lining 73.Housing 70 is hollow cylindrical of end sealing.Valve body 71 also is the hollow cylindrical of end sealing and is comprised in the housing 70.Valve body 71 slides along the axis of housing 70.Spring 72 promotes valve body 71 to the opening end of housing 70.Lining 73 is installed in the opening end of housing 70.The end of inserting the lining 73 of housing 70 engages with valve body 71.The other end at lining 73 is formed with flange 73a.Opening end at valve chamber 671 has step 67a.Flange 73a cooperates with step 67a.

One-way valve 68 embeds in the valve chamber 671, and flange 73a matches with step 67a simultaneously.Flange 73a then is clamped between first housing 113 and second housing 122.This makes one-way valve 68 fixing with respect to valve chamber 671.Valve opening 73b in the lining 73 makes passage 69 communicate with the inside of housing 70.On the periphery of housing 70, form a plurality of through hole 70a.

One-way valve 68 among the 3rd embodiment has identical advantage with one-way valve 52 and 58 among first, second embodiment.When compressor moves under the minimum capacity state, shown in Figure 11 (a), valve body 71 close valve orifice 73b.When compressor moved under the capacity status greater than minimum capacity, the pressure of silencing apparatus chamber 65 made valve body 71 open valve opening 73b.Thereby the refrigerant gas in the silencing apparatus chamber 65 flow in the external refrigeration loop 45 by passage 69, valve opening 73b, through hole 70a and exhaust port 672, shown in the arrow among Figure 11 (b).

The 3rd embodiment's one-way valve 68 is the one-piece element that is made of a plurality of parts.Therefore, when compressor is installed, insert chamber 671, just one-way valve 68 can be installed in the valve chamber by the valve 68 that will form one simply in advance.This has simplified the installation of one-way valve in valve chamber.And be that the structure that forms on the housing of compressor is compared with the part of one-way valve among first, second embodiment, each part that constitutes one-way valve 68 is easy to accurately manufacture.Therefore, such as when valve opening 73b closes, the inner of the lining 73 that cooperates with valve body 71 can simply accurately process.Like this, improved the sealing of lining 73 and valve body 71 when valve opening 73b closes.

The present invention goes for the variable displacement compressor that for example discloses in Japanese unexamined patent publication No.7-310654, this variable displacement compressor is equipped with solenoid valve in the passage that crank chamber and suction chamber are coupled together.

Therefore, above-mentioned example and embodiment only are used to illustrate the present invention, do not constitute limitation of the invention.The present invention also is not limited to example cited herein, within the scope of the appended claims, can carry out various changes.

Claims

1, a kind of compressor, comprise: be positioned at crank chamber (121) and be installed in cam disk (23) on the live axle (18), the piston (37) that is positioned at cylinder-bore (111) and matches with cam disk (23), described cam disk (23) is converted into the to-and-fro motion of piston (37) in cylinder-bore (111) with the rotation of live axle (18), described piston (37) is to compressing from the gas that independent external circuit (45) are conducted to cylinder-bore (111) by means of suction chamber (131), and pressurized gas is drained in the external circuit (45) by means of discharging chamber (132), described cam disk (23), according to pressure in the crank chamber (121) and the pressure reduction between the pressure in the cylinder-bore (111), with respect to becoming the position of inclination maximum with the perpendicular plane of the axis of live axle (18) and becoming between the minimum angle-of-incidence position, and described piston (37) moves according to the stroke based on the inclination angle gained of cam disk (23), control the capacity of compressor, it is characterized in that, also comprise:

A discharge route (133; 561; 67), will discharge chamber (132) and external circuit (45) is communicated with;

One is positioned at discharge route (133; 561; 67) Nei valve (52; 58; 68), described valve (52; 58; 68) according to acting on valve (52; 58; 68) pressure of upstream extremity with act on valve (52; 58; 68) pressure reduction between the pressure of downstream will be discharged chamber (132) and external circuit (45) selectively and will be switched on or switched off; And

A discharge silencing apparatus (551; 66), this discharges silencing apparatus (551; 66) prevent that gas is discharged to caused vibration when discharging chamber (132), described discharge route (561 from cylinder-bore (111) stream; 67) be arranged on discharge silencing apparatus (551; 66) inside.

2, compressor according to claim 1 is characterized in that, when cam disk (23) is in position, minimal tilt angle, and described valve (52; 58; 68) will discharge chamber (132) disconnects with external circuit (45).

3, compressor according to claim 2 is characterized in that, when cam disk (23) is in its inclination angle greater than the position at minimal tilt angle, and described valve (52; 58; 68) will discharge chamber (132) is communicated with external circuit (45).

4, compressor according to claim 1 is characterized in that, described valve comprises the one-way valve (52 that only allows pressurized gas to be discharged to external circuit (45) from discharge chamber (132); 58; 68).

5, compressor according to claim 4 is characterized in that, described valve (52; 58; 68) comprising:

A valve body (521; 59; 71), it can move between the primary importance and the second place, wherein said valve body (521; 59; 71) will discharge chamber (132) at the primary importance place and link to each other described valve body (521 with external circuit (45); 59; 71) (45) disconnect from the external circuit will to discharge chamber (132) at second place place; And

With valve body (521; 59; 71) push the device (54 of the second place to; 61; 72).

6, compressor according to claim 5 is characterized in that, described valve (68) comprises an element (70 that is used to install described valve body (71) and described pushing device (72); 73), described valve (68) is to have installation elements (70; 73), the one-piece element of valve body (71) and pushing device (72).

7, compressor according to claim 6 is characterized in that, described compressor also comprises: the pair of shells (113 together that is connected to each other of end face separately; 122); With

Described valve (68) has one by the flange of end face clamping (73a), makes valve (68) be fixed on housing (113; 122) on.

8, according to claim 6 or 7 described compressors, it is characterized in that described installation elements (70; 73) comprise a housing (70), housing (70) is a hollow cylindrical, the lining (73) that has an opening end and cooperate with the opening end of housing (70), described housing (70) has one with the inner through hole (70a) that is communicated with external circuit (45) of housing (70), described lining (73) have one with the inside of housing (70) with discharge a valve opening (73b) that chamber (132) is communicated with and an insertion housing (70) in case with the relative internal end surface of valve body (71), described valve body (71) is when it is positioned at the second place, abut against on the internal end surface, (73b) closes with valve opening, and blocking-up valve opening (73b) and through hole (71a) are connected by housing (70) inside.

9, compressor according to claim 1 is characterized in that, also comprises:

A supply passage (41) will be discharged chamber (132) and will be connected with crank chamber (121), make gas be transferred to crank chamber (121) from discharging chamber (132);

A release channel (40; 301), crank chamber (121) is connected with suction chamber (131), makes gas be transferred to suction chamber (131) and reach from crank chamber (121)

Control gear (42; 62), be positioned at the intermediate portion of supply passage (41), be used for adjusting the gas flow that imports crank chamber (121) from discharge chamber (132) through supply passage (41), thus the pressure in the control crank chamber (121).

10, compressor according to claim 9, it is characterized in that, one valve element (30), can between the primary importance and the second place, move according to the inclination angle of cam disk (23), and under the primary importance state, external circuit (45) are communicated with suction chamber (131), and under second place state, external circuit (45) and suction chamber (131) are disconnected, when described cam disk (23) is in position, minimal tilt angle valve element (30) is moved to the second place, thereby make the capacity minimum of compressor.

11, compressor according to claim 10 is characterized in that, also comprises:

Locating face (35) in the face of valve element (30);

Described valve element (30) has an end face, and this end face abuts against on the locating face (35) when this valve element (30) is positioned at second position; And

When described valve element (30) when being positioned at the second place, described cam disk (23) remains on the position at minimal tilt angle.

12, according to claim 10 or 11 described compressors, it is characterized in that, a gas circulation channel, it comprises described release channel (40; 301) and supply passage (41), described circulation canal forms according to external circuit (45) is disconnected with suction chamber (131).

13, compressor according to claim 1 is characterized in that, an external drive source (E) directly links to each other with live axle (18), is used for Driven Compressor.