CN101503994A - Swash plate compressor - Google Patents
Swash plate compressor Download PDFInfo
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- CN101503994A CN101503994A CNA2009100065236A CN200910006523A CN101503994A CN 101503994 A CN101503994 A CN 101503994A CN A2009100065236 A CNA2009100065236 A CN A2009100065236A CN 200910006523 A CN200910006523 A CN 200910006523A CN 101503994 A CN101503994 A CN 101503994A
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Abstract
The present invention provides a swash plate compressor which can realize excellent sliding characteristic when a driving shaft rotates with a high speed and can realize higher refrigerating effect when the driving shaft rotates with a low speed. In the swash plate compressor of the invention, an oil guiding groove (3b), an oil guiding hole (3c), a first hole (37), a tapping hole (39), a valve hole (41), a communicating hole (49b), a receiving chamber (1c), an orifice (9a) and a second hole (55) form a releasing channel. The oil guiding groove (3b), the oil guiding hole (3c), the first hole (37), the tapping hole (39), the valve hole (41), the communicating hole (49b), the receiving chamber (1c) and the orifice (9a) form a first channel. Furthermore, the second hole (55) forms a second channel. A valve mechanism (45) can increase the rate of the first channel in the releasing channel along with the increase of driving shaft (7).
Description
Technical field
The present invention relates to a kind of swash-plate-type compressor.
Background technique
JP-A-8-284816 discloses a kind of traditional swash-plate-type compressor.This swash-plate-type compressor comprises the housing of being made up of front case, cylinder body and rear case, and defines a plurality of cylinder thoraxes, suction chamber, drain chamber and crank chamber in this housing.Front case is supporting driving shaft rotatably, and an end of live axle exposes from front case.Wobbler is supported by live axle in crank chamber, thereby can change its inclination angle.Piston is received in the corresponding cylinder thorax in reciprocating mode.Between wobbler and corresponding piston, be provided with severally, be used for the oscillating motion of wobbler is converted to the to-and-fro motion of respective pistons front side sliding shoes and rear side sliding shoes.Service duct provides connection between drain chamber and crank chamber, and this service duct is provided with displacement control valve in order to regulate the pressure in the crank chamber.
And swash-plate-type compressor has release channel, and it is used for crank chamber is communicated to suction chamber.In the open text of aforementioned patent applications in the disclosed swash-plate-type compressor, release channel comprises and forms first radial hole that radially extends along live axle and the tap hole that first radial hole is communicated to suction chamber.The lug plate to be can being fixed to this live axle with the mode that live axle rotates, and is formed with oil supply gallery on this lug plate, and this oil supply gallery extends to the center from the outer regions of crank chamber.And, also be provided with and be used for the shaft sealer that between front case and live axle, seals, and on front case, be formed with lubrication channel, in order to oil supply gallery is communicated to first radial hole in the position that is provided with shaft sealer.
Swash-plate-type compressor has constituted refrigerating circuit with condenser, expansion valve and vaporizer, and this refrigerating circuit is used for car air-conditioner equipment.In this swash-plate-type compressor, displacement control valve is regulated pressure in the crank chamber based on the flow of pressure in the suction chamber or refrigerant gas, so that change the angle of wobbler with respect to live axle, thereby changes its discharge capacity.
And, in this swash-plate-type compressor, in the outer regions of crank chamber, there is a large amount of lubricant oil in the crank chamber, and be communicated to the zone of a large amount of lubricant oil of described existence by the release channel that oil supply gallery, lubrication channel, first radial hole and tap hole constitute, like this, the lubricant oil in the crank chamber might be fed to shaft sealer, so improved the durability of the rubber material that is used for shaft sealer.
Summary of the invention
The technical problem to be solved in the present invention
In this swash-plate-type compressor,, need improve sliding properties between cylinder thorax and the piston and between wobbler and corresponding sliding shoes etc. when live axle during with high speed rotating.And when live axle during with low speed rotation, the lubricants capacity that is discharged in the refrigerant gas in the external refrigeration loop of swash-plate-type compressor outside need reduce to represent high refrigerating capacity.
At this on the one hand, in the open text of aforementioned patent applications in the disclosed swash-plate-type compressor, release channel makes the rich oil zone that has a large amount of lubricant oil in the crank chamber be communicated with suction chamber with predetermined cross-section area always, like this, no matter the rotating speed of live axle how, the lubricants capacity in the crank chamber may be very few or too much.When drive shaft speed of excessive while of the lubricants capacity in the crank chamber increases, wobbler will excessively stir lubricant oil, and like this, lubricant oil will be easy to produce heat and viscosity reduction owing to shearing.In this case, the lubricated existence of sliding parts is worried.And when the very few while of the lubricants capacity in the crank chamber, drive shaft speed reduced, the lubricants capacity that is discharged in the refrigerant gas in the refrigerating circuit of swash-plate-type compressor outside increased, and like this, it is not enough that refrigerating capacity becomes.
An object of the present invention is to provide a kind of swash-plate-type compressor, it can realize fabulous sliding properties during with high speed rotating at live axle, and realizes high refrigerating capacity during with low speed rotation at live axle.
The means of technical solution problem
In swash-plate-type compressor, adopt the refrigerant gas that mixes with lubricant oil.According to the experiment of implementing by the present inventor, there are lubricants capacity bigger rich oil zone and the less oil-poor zone of lubricants capacity in the crank chamber in swash-plate-type compressor.For example, the rich oil zone is present in the outer regions of crank chamber, and oil-poor zone is present in the zone of interior week of crank chamber, that is, and and away from the zone of crank chamber wall.This is because the live axle of wobbler in crank chamber rotates, and lubricant oil is forced to flow to the outer regions of crank chamber owing to centrifugal force.And, lubricant oil abundance on the side face of cylinder thorax.Made the present invention based on these discoveries.
The invention provides a kind of swash-plate-type compressor, comprising: housing, it has cylinder thorax, suction chamber, drain chamber and crank chamber; Live axle, it is rotatably supported by described housing; Wobbler, it is supported on the described live axle in described crank chamber; Piston, it is contained in the described cylinder thorax in reciprocating mode; Movement conversion mechanism, it is arranged on the to-and-fro motion that is used for the oscillating motion of described wobbler is converted to described piston between described wobbler and the described piston; And release channel, it is used for described crank chamber is communicated to described suction chamber, described compressor is characterised in that, described release channel comprises the first passage that is communicated to the bigger rich oil zone of the interior lubricants capacity of described crank chamber, also be provided with valve system, described valve system increases the aperture of described first passage along with the raising of described drive shaft speed, and described valve system is arranged on the described first passage and moves by centrifugal force.
In swash-plate-type compressor of the present invention, when live axle during with high speed rotating, valve system can improve the aperture of first passage.Therefore, the refrigerant gas that comprises a large amount of lubricant oil in the crank chamber moves to suction chamber through the first passage that aperture increases.Therefore, the lubricants capacity in the crank chamber becomes moderate, and wobbler can not stir too many lubricant oil, and like this, lubricant oil hardly can be owing to shearing produces heat, and its viscosity can reduce hardly.Therefore, sliding parts is successfully lubricated.And the refrigerant gas that sucks from suction chamber comprises a large amount of lubricant oil, and the sliding parts between cylinder thorax and the piston is successfully lubricated.In addition, although the lubricants capacity that refrigerant gas comprised that is discharged in the refrigerating circuit of swash-plate-type compressor outside increases, owing to the to-and-fro motion of piston high speed, so refrigerating capacity can not have problems.
In addition, in this swash-plate-type compressor, although when live axle during with low speed rotation the lubricants capacity in the crank chamber increase, but wobbler etc. only stir lubricant oil with low speed, like this, oil body can not reduce too much, and the temperature of lubricant oil rises slightly.Therefore, sliding parts still can successfully be lubricated.
Described valve system is arranged on the first passage and by centrifugal force and moves.Adopted mechanical valve mechanism, wherein mass moves by centrifugal force, and activates valve body.Therefore, the increase of centrifugal force will cause moving along the direction that the aperture of first passage increases, and centrifugal force reduce will cause direction to move along the aperture of first passage reduces.
Therefore, in swash-plate-type compressor of the present invention, might realize fabulous sliding properties during with high speed rotating and realize high refrigerating capacity during with low speed rotation at live axle at live axle.
Swash-plate-type compressor of the present invention can be the variable-displacement compressor of the variable pitch of constant fixed displacement type compressor in the inclination angle of wobbler or wobbler.
And, in swash-plate-type compressor of the present invention, release channel is enough to make crank chamber to be communicated with suction chamber, and release channel can be the release channel that crank chamber and suction chamber directly are communicated with, or makes crank chamber and the suction chamber release channel by indirect communication such as suction passages.Release channel can comprise first passage, perhaps can comprise other passage.
First passage is communicated to any one in the zone of lubricant oil abundance.The zone of lubricant oil abundance is by relatively coming mutually to determine with other zone.
Release channel can comprise with crank chamber in the second channel of the less regional connectivity of lubricants capacity.Valve system can increase the ratio that first passage accounts for release channel along with the raising of drive shaft speed, and reduces the ratio that second channel accounts for release channel along with the reduction of drive shaft speed.
In this case, release channel comprises first passage and second channel, and the refrigerant gas that does not comprise too much lubricant oil in the crank chamber can move in the suction chamber by second channel.Therefore, valve system can change the ratio that first passage accounts for release channel, like this, can improve the responsiveness with respect to rotating speed.
And in this swash-plate-type compressor, when live axle during with low speed rotation, valve system reduces the ratio that first passage accounts for release channel.Therefore, the first passage that the refrigerant gas that comprises a large amount of lubricant oil in the crank chamber can be not too much reduced via the ratio that accounts for release channel moves to suction chamber, but the refrigerant gas that does not comprise a large amount of lubricant oil in the crank chamber moves to suction chamber by second channel.Therefore, be discharged into the lubricants capacity that is comprised in the refrigerant gas in the refrigerating circuit of swash-plate-type compressor outside and reduce, like this, can show high refrigerating capacity.
And, in this swash-plate-type compressor, when live axle during with low speed rotation, the summation of the unlatching cross-section area of release channel reduces, and like this, the discharge that moves to the refrigerant gas of suction chamber from crank chamber reduces, and circuit refrigerant gas amount reduces in compressor, like this, the refrigerant gas amount that is used for suitable purpose increases, and the performance of compressor is improved.Especially, in no-clutch type swash-plate-type compressor, wherein, power is delivered to the live axle of swash-plate-type compressor always when driving source turns round, when not needing to freeze, refrigerant gas only circulates in compressor, but when live axle during with low speed rotation, circuit refrigerant gas amount can minimize, like this, during with high speed rotating, might realize fabulous sliding properties at live axle, and during with low speed rotation, can reduce the power of compressor at live axle.
Second channel preferably is formed with throttle valve.
In this case, the refrigerant gas that does not comprise a large amount of lubricant oil in the crank chamber is difficult to move in the suction chamber, and like this, the effect of the present invention that is produced by lubricant oil will become more obvious.
In swash-plate-type compressor of the present invention, wobbler can be supported for and make its variable pitch.And the lug plate that receives compression reaction force can be fixed to live axle rotating with the live axle one.And, can on housing, form the Oil Guide path, described Oil Guide path outer regions from crank chamber between housing and lug plate is extended.First passage preferably is communicated to the Oil Guide path.
According to the experiment that inventor of the present invention implements, the outer regions in the crank chamber of described swash-plate-type compressor is the zone of lubricant oil abundance, like this, might lubricant oil easily be directed to first passage by the Oil Guide path.
Can between housing and live axle, shaft sealer be set, so that the live axle that sealing is exposed from housing.First passage preferably is communicated to the Oil Guide path via described shaft sealer.
In this case, by supply with a large amount of lubricant oil to shaft sealer, might improve the durability of the rubber material that is used for shaft sealer.
In swash-plate-type compressor of the present invention, wobbler can support to and make its variable pitch.And the lug plate that receives compression reaction force can be fixed to live axle so that can rotate with the live axle one.And first passage can comprise and being formed on the lug plate and to the guide hole of the outer regions opening of crank chamber.
According to the result of test that inventor of the present invention does, the outer regions of the crank chamber of swash-plate-type compressor is the zone of lubricant oil abundance, like this, might lubricant oil easily be directed to first passage by oil guiding hole.
In swash-plate-type compressor of the present invention, can between housing and live axle, shaft sealer be set so that the live axle that sealing is exposed from housing.And, second channel preferably near shaft sealer to the crank chamber opening.
Under the manufacturing situation, lubricant oil can supply to shaft sealer always, and like this, the durability of shaft sealer can improve.
Description of drawings
Fig. 1 is the sectional view that illustrates according to the swash-plate-type compressor of mode of execution 1.
Fig. 2 relates to the swash-plate-type compressor according to mode of execution 1, and is the sectional view that the compressor critical piece is shown.
Fig. 3 relates to the swash-plate-type compressor according to mode of execution 1, and is the sectional view of compressor critical piece when with magnification ratio live axle being shown with low speed rotation.
Fig. 4 relates to the swash-plate-type compressor according to mode of execution 1, and is the sectional view of compressor critical piece when with magnification ratio live axle being shown with high speed rotating.
Fig. 5 relates to the swash-plate-type compressor according to mode of execution 1, and shows the chart that concerns between the rotating speed of live axle and the orifice size.
Fig. 6 is the sectional view that illustrates according to the swash-plate-type compressor of mode of execution 2.
Fig. 7 is the sectional view that illustrates according to the swash-plate-type compressor that improves example.
Fig. 8 illustrates the sectional view that improves the swash-plate-type compressor of example according to another.
Embodiment
Be described embodying embodiments of the present invention 1 and 2 below with reference to accompanying drawings.
Mode of execution 1
Swash-plate-type compressor according to mode of execution 1 is the variable-displacement compressor that is used for vehicle air conditioning.As shown in Figure 1, this compressor comprises the housing that is made of cylinder body 1, front case 3 and rear case 5, and cylinder body 1 is provided with a plurality of cylinder thorax 1a that the axis that is parallel to live axle 7 extends through cylinder body.In addition, the left side of Fig. 1 represents that the front portion of compressor, right side represent the rear portion of compressor.
Be formed with suction chamber 11 and drain chamber 13 on rear case 5, they are communicated to corresponding cylinder thorax 1a by valve cell 9.And front case 3 and cylinder body 1 define crank chamber 15, and axial bore 3a, and 1b is formed on front case 3 and the cylinder body 1.In axial bore 3a, be provided with shaft sealer 17.Can use rubber material as shaft sealer 17.And, in axial bore 1b, be provided with sliding bearing 19.The receiving chamber 1c that is communicated to axial bore 1b is formed on the center of cylinder body 1 rear end, and receiving chamber 1c is relative with valve cell 9.
An end of live axle 7 from front case 3 expose and its central part under the state of crank chamber 15, live axle 7 is supported for and can rotates by shaft sealer 17 grades.Known belt pulley and magnetic clutch are connected to live axle 7, and live axle 7 can pass through driving source, and for example motor etc. rotatably drives by the belt that is stretched on belt pulley and the magnetic clutch.And, thereby be received in respectively among the corresponding cylinder thorax 1a can to-and-fro motion for piston 21, and each piston 21 defines pressing chamber respectively in cylinder thorax 1a.
The lug plate 23 that receives compression reaction force is fixed to live axle 7 in crank chamber 15, and is provided with thrust-bearing 25 and sliding bearing 27 between lug plate 23 and front case 3.And live axle 7 inserts and passes wobbler 29, and wobbler 29 is variable with respect to the inclination angle perpendicular to the imaginary plane of live axle 7.Be formed with the articulated section 23a that points to wobbler 29 on lug plate 23, wobbler 29 is provided with the articulated section 29a that points to lug plate 23, and articulated section 23a and 29a have constituted linkage 31.And, between lug plate 23 and wobbler 29, be provided with pushing spring 33, so as the direction bias voltage that is separated from each other along lug plate 23 and wobbler 29 the two.
And, between wobbler 29 and each piston 21, be provided with several to front side sliding shoes and rear side sliding shoes 35.Front side sliding shoes 35 is located between the preceding seat surface of the front surface of wobbler 29 and piston 21, and rear side sliding shoes 35 is located between the back seat surface of the rear surface of wobbler 29 and piston 21.Each sliding shoes 35 is hemisphere substantially.Each sliding shoes 35 is as movement conversion mechanism.
On live axle 7, be formed with first hole 37, tap hole 39 and valve opening 41, wherein radially extend in first hole 37, thereby tap hole 39 is communicated to first hole 37 so that extend to the rear end of live axle 7 vertically with axis coaxle, and valve opening 41 is communicated to tap hole 39 so that radially extend.
As described in Figure 2, first hole 37 is arranged between lug plate 23 and the front case 3, and is formed on axis from live axle 7 to the radius of the live axle 7 of its periphery.Be formed with oil guide slot 3b on front case 3, it extends to face thrust bearing 25 from the outer regions of crank chamber 15 between front case 3 and lug plate 23.And, on front case 3, being formed with oil guiding hole 3c, it is communicated to oil guide slot 3b to face sliding bearing 27 and shaft sealer 17.Oil guiding hole 3c in the face of the shaft sealer 17 among the axial bore 3a so that be communicated to first hole 37.Oil guide slot 3b and oil guiding hole 3c are as the Oil Guide path.
As shown in Figure 1, the rear end of live axle 7 protrudes in the receiving chamber 1c, and the rear end of tap hole 39 is by plug 43 sealings.Valve opening 41 is a bit located before being formed on plug 43.Shown in Fig. 3 and 4, valve opening 41 runs through live axle 7 and is provided with, so that tap hole 39 is communicated to receiving chamber 1c.
Around valve opening 41, be provided with valve system 45.Valve system 45 comprises can sit spherical valve body of putting on an opening 41a of valve opening 41 47 and the shell 49 that is fixed to live axle 7 around valve opening 41.Valve body 47 also can be used as mass.Shell 49 comprises valve chamber 49a at it on the side of opening 41a.In valve chamber 49a, be provided with first spring 51 and second spring 53, wherein first spring 51 along away from direction bias voltage valve body 47, the second springs 53 of opening 41a along direction bias voltage valve body 47 towards opening 41a.Valve chamber 49a is communicated to receiving chamber 1c by the connecting port 49b that is formed on the shell 49.
As shown in Figure 1, on valve cell 9, be provided with the throttle orifice 9a that extends through it and be used to make receiving chamber 1c to be communicated with suction chamber 11.And, on cylinder body 1 and valve cell 9, be formed with second hole 55, be used for zone of interior week in suction chamber 11 and crank chamber 15, that is, provide connection near between the zone of live axle 7.On second hole 55 of valve cell 9, be formed with throttle valve 55a.Oil guide slot 3b, oil guiding hole 3c, first hole 37, tap hole 39, valve opening 41, connecting port 49b, receiving chamber 1c, throttle orifice 9a and second hole 55 have constituted release channel.Oil guide slot 3b, oil guiding hole 3c, first hole 37, tap hole 39, valve opening 41, connecting port 49b, receiving chamber 1c and throttle orifice 9a have constituted first passage.And second hole 55 has constituted second channel.In addition, connecting port 49b and throttle orifice 9a are set at and make it open the cross-section area that cross-section area is equal to or greater than the opening 41a of valve opening 41.
And receiving in rear case 5 has displacement control valve 57.Displacement control valve 57 is communicated to suction chamber 11 by sense channel 59, and provides connection by this sense channel 59 between drain chamber 13 and crank chamber 15.Pressure in the displacement control valve 57 detection suction chambers 11 is with the aperture of change service duct 61, thus the discharge capacity of change compressor.
In the compressor of like this structure, displacement control valve 57 can be regulated pressure in the crank chamber 15 based on the flow of pressure in the suction chamber 11 and refrigerant gas, changing the angle of wobbler 29 with respect to live axle 7, thereby changes its discharge capacity.
And, in this compressor, when vehicle when running at high speed, live axle 7 is with high speed rotating, the valve body 47 of valve system 45 overcomes second spring 53 owing to the bias voltage of the big centrifugal force and first spring 51 bias voltage moves away from the axis of live axle 7, like this, as shown in Figure 4, valve body 47 has increased the aperture of opening 41a.
Therefore, the aperture that valve opening 41 is communicated with connecting port 49b increases, and first hole 37 shown in Figure 2 also increases with the aperture that connecting port 49b is communicated with.At this moment, second hole 55 provides connection with predetermined cross-section area between crank chamber 15 and suction chamber 11.Therefore, as shown in Figure 5, it is big that the orifice size that crank chamber 15 and suction chamber 11 are interconnected becomes.That is, single valve system 45 has improved the ratio that first hole 37 accounts for release channel, has reduced the ratio that second hole 55 accounts for release channel simultaneously.
In the outer regions of crank chamber shown in Figure 2 15, lubricant oil very abundance and lubricant oil is guided first hole 37 into by oil guide slot 3b and oil guiding hole 3c.At this moment, lubricant oil is guided first hole 37 into by shaft sealer 17, and like this, a large amount of lubricant oil supply to shaft sealer 17, thereby have increased the durability of shaft sealer 17.
Because first hole 37 has been improved it and has been accounted for the ratio of release channel, so the refrigerant gas that is positioned at crank chamber 15 and comprises a large amount of lubricant oil is guided receiving chamber 1c into by tap hole 39, valve opening 41 and connecting port 49b, and further moves to suction chamber 11 by throttle orifice 9a.Therefore, the lubricants capacities in the crank chamber 15 become moderate, and wobbler 29 can not stir too many lubricant oil, and like this, lubricant oil hardly can be owing to shearing produces heat, and its viscosity can reduce hardly.Therefore, the sliding parts between wobbler 29 and the corresponding sliding shoes 35 is successfully lubricated.And the refrigerant gas that sucks from suction chamber 11 comprises a large amount of lubricant oil, and the sliding parts between cylinder thorax 1a and the piston 21 is successfully lubricated.Thereby itself can show fabulous durability under high speed.
In addition, although the lubricants capacity that refrigerant gas comprised that is discharged into this moment in the refrigerating circuit of compressor outside increases, because piston 21 high speed to-and-fro motion, so refrigerating capacity can not have problems.
When vehicle during with low speed driving, live axle 7 is with low speed rotation, and the valve body 47 of valve system 45 is owing to less centrifugal force is resisted the bias voltage of first spring 51, and yield to second spring 53 bias voltage and as shown in Figure 3 near the axis of live axle 7, like this, valve body 47 has reduced the aperture of opening 41a.When live axle 7 rotated with lower speed, valve body 47 was sat and is put on opening 41a so that sealing valve opening 41.
Therefore, valve opening 41 reduces with the aperture that connecting port 49b is communicated with, and first hole 37 as shown in Figure 2 reduces with the aperture that connecting port 49b is communicated with.And at this moment, second hole 55 provides connection with predetermined cross-section area between crank chamber 15 and suction chamber 11.Therefore, as shown in Figure 5, the orifice size that crank chamber 15 and suction chamber 11 are interconnected diminishes.That is, single valve system 45 has reduced the ratio that first hole 37 accounts for release channel, has increased the ratio that second hole 55 accounts for release channel simultaneously.
In the zone of interior week of crank chamber shown in Figure 2 15, that is, near in the zone of live axle 7, lubricants capacity is less, and does not comprise that the refrigerant gas of a large amount of lubricant oil is incorporated into second hole 55 from here.
Because second hole 55 has been improved it and has been accounted for the ratio of release channel, so the refrigerant gas that does not comprise a large amount of lubricant oil in the crank chamber 15 moves to suction chamber 11 by throttle valve 55a.Therefore, the lubricants capacity that refrigerant gas comprised that is discharged in the refrigerating circuit of compressor outside reduces, and like this, itself can show high refrigerating capacity.
And in this swash-plate-type compressor, first hole 37 is in closed condition during with low speed rotation at live axle 7.Therefore, the summation of the cross-section area that release channel is opened reduces, thus, the refrigerant gas amount that moves to suction chamber 11 from crank chamber 15 reduces, and circuit refrigerant gas amount also reduces in swash-plate-type compressor, thereby make the refrigerant gas amount that is used for proper purpose increase, and the performance of swash-plate-type compressor is improved.
In addition, when the lubricants capacity in the crank chamber 15 increased, wobbler 29 only stirred lubricant oil with low speed, and like this, the temperature of lubricant oil raises slightly, and oil body can not reduce too much.Therefore, sliding parts still can lubricate smoothly.
Therefore, compressor can show fabulous sliding properties during with high speed rotating at live axle 7, and shows higher refrigerating capacity during with low speed rotation at live axle 7.
Mode of execution 2
As shown in Figure 6, in the swash-plate-type compressor according to mode of execution 2, cylinder body 2 is provided with a plurality of cylinder thorax 2a that extend along the axis that is parallel to live axle 8, and cylinder thorax 2a runs through the cylinder body extension.Be formed with suction chamber 12 and drain chamber 14 on rear case 6, they are communicated with corresponding cylinder thorax 2a by valve cell 10.And front case 4 and cylinder body 2 define crank chamber 16, and are formed with axial bore 4a, 2b on front case 4 and cylinder body 2.Shaft sealer 18 and sliding bearing 20 are arranged among the axial bore 4a.Can use rubber material as shaft sealer 18.And, in axial bore 2b, be provided with sliding bearing 22.The receiving chamber 2c that is communicated to axial bore 2b is formed on the center of cylinder body 2 rear ends, and receiving chamber 2c is relative with valve cell 10.
By shaft sealer 18 supports such as grade, an end of live axle 8 exposes from front case 4 live axle 8, and its central part is towards crank chamber 16 with the state that can rotate.And piston 24 is received in respectively among the corresponding cylinder thorax 2a so that can to-and-fro motion, and each piston 24 defines pressing chamber in cylinder thorax 2a.
The lug plate 26 that receives compression reaction force is fixed to live axle 8 in crank chamber 16, and is provided with thrust-bearing 28 between lug plate 26 and front case 4.And live axle 8 inserts and passes wobbler 30 so that the variable pitch of wobbler 30.Between lug plate 26 and wobbler 30, be formed with linkage 32.And, be provided with pushing spring 34,36 between lug plate 26 and the wobbler 30 and between wobbler 30 and live axle 8.And, between wobbler 30 and each piston 24, be provided with several to front side sliding shoes and rear side sliding shoes 38.
Thereby on the body 8a of live axle 8, be formed with radially second hole 44 of extending and be communicated with vertically intercommunicating pore 46 with the axis coaxle extension with second hole 44.Thereby on tube body 8b, be formed with and be communicated with the tap hole 48 that extends to live axle 8 rear ends with intercommunicating pore 46.Second hole 44 is arranged between shaft sealer 18 and the sliding bearing 20, and second hole 44 is formed on axis from live axle 8 to the radius of the live axle 8 of its periphery.On front case 4, be formed with oil guiding hole 4b, the regional opening of interior week of its crank chamber 16 between front case 4 and lug plate 26.The shaft sealer 18 of oil guiding hole 4b in the axial bore 4a is so that be communicated to second hole 44.The rear end of live axle 8 protrudes in the receiving chamber 2c.
On valve cell 10, be provided with the throttle orifice 10a that extends through it and be used to make receiving chamber 2c to be communicated with suction chamber 12.Guide hole 26a, valve chamber 26b, first hole 40, oil guiding hole 4b, second hole 44, intercommunicating pore 46, tap hole 48, receiving chamber 2c and throttle orifice 10a have constituted release channel.Guide hole 26a, valve chamber 26b, first hole 40, receiving chamber 2c and throttle orifice 10a have constituted first passage.And oil guiding hole 4b, second hole 44, intercommunicating pore 46, tap hole 48, receiving chamber 2c and throttle orifice 10a have constituted second channel.Remaining structure is identical with mode of execution 1.
In this compressor, when vehicle when running at high speed etc., live axle 8 is with high speed rotating, the valve body 42a of valve system 42 overcomes spring 42b owing to big centrifugal force bias voltage moves away from the axis of live axle 8, like this, valve body 42a has increased the aperture of guide hole 26a.At this moment, second hole 44 provides connection with predetermined cross-section area between crank chamber 16 and suction chamber 12.Therefore, the orifice size that is interconnected of crank chamber 16 and suction chamber 12 becomes big.Therefore, single valve system 42 has improved the ratio that first hole 40 accounts for release channel, has reduced the ratio that second hole 44 accounts for release channel simultaneously.
And when vehicle during with low speed driving etc., live axle 8 is with low speed rotation, and near the axis of live axle 8, and therefore, valve body 42a has reduced the aperture of guide hole 26a to the valve body 42a of valve system 42 because the bias voltage of spring 42b overcomes less centrifugal force.When live axle 8 rotated with lower speed, valve body 42a sat and puts on guide hole 26a.At this moment, second hole 44 provides connection with predetermined cross-section area between crank chamber 16 and suction chamber 12.Therefore, the orifice size that is interconnected of crank chamber 16 and suction chamber 12 diminishes.Therefore, single valve system 42 has reduced the ratio that first hole 40 accounts for release channel, has increased the ratio that second hole 44 accounts for release channel simultaneously.
Therefore, in this compressor, can realize and mode of execution 1 identical functions and effect.In this compressor, because interior all regional connectivities of oil guiding hole 4b and crank chamber 16, and when compressor has only less amount of lubrication oil to supply to oil guiding hole 4b during with high speed rotating, therefore at compressor during with high speed rotating, the compressor of mode of execution 2 is very outstanding aspect the durability of the rubber material of axial brake device 18.But lubricant oil can supply to shaft sealer 18 always.
Although with reference to mode of execution 1 with 2 invention has been described, this is not that the present invention just is limited to mode of execution 1 and 2, but can carry out suitable change and application in the scope that does not depart from its main points.
For example, as shown in Figure 7, can in the compressor of mode of execution 1, remove throttle valve 55 as second channel, and on live axle 7, form throttle valve 55b as second channel, this throttle valve 55b between tap hole 39 and receiving chamber 1c, provide be communicated with and its diameter identical with the diameter of throttle valve 55a.
In this structure, can easily form second channel; Lubricant oil can supply to shaft sealer 18 always, and can realize the effect same with mode of execution 2.In addition, in this case, throttle orifice 9b is set at and makes it open the summation that cross-section area is equal to or greater than the air cross-section area of the opening 41a of valve opening 41 and throttle valve 55b.
And, as shown in Figure 8, can remove throttle valve 55, and the bypass that is provided as second channel on the opening 41a of valve opening 41 is crossed the groove 55c of valve body 47 as second channel.In this structure, can realize same effect.
And in the compressor of mode of execution 2, preferably, the outer distolateral opening of guide hole 26a like this, helps the lubricant oil in the crank chamber 16 is drawn into guide hole 26a along the sense of rotation of lug plate 26 in advance.
And, under the situation of the sliding bearing 19,22 in the compressor that replaces mode of execution 1 and 2 with the radial bearing that uses roller, can between each roller, release channel be set, and the ratio that first passage and second channel account for release channel can change.And linkage 31,32 is not limited to those in the mode of execution, but can adopt various configurations.
Industrial applicibility
The present invention can use in car air-conditioner equipment.
Claims (7)
1. swash-plate-type compressor comprises:
Housing, it has cylinder thorax, suction chamber, drain chamber and crank chamber,
Live axle, it is rotatably supported by described housing,
Wobbler, it is supported in described crank chamber on the described live axle,
Piston, it is contained in the described cylinder thorax in reciprocating mode,
Movement conversion mechanism, its be arranged on the oscillating motion that is used between described wobbler and the described piston described wobbler convert to described piston to-and-fro motion and
Release channel, it is used for described crank chamber is communicated to described suction chamber,
Described compressor is characterised in that described release channel comprises the first passage that is communicated to the rich oil zone that lubricants capacity is bigger in the described crank chamber,
Also be provided with valve system, described valve system increases the aperture of described first passage along with the raising of described drive shaft speed, and
Described valve system is arranged on the described first passage and moves by centrifugal force.
2. swash-plate-type compressor as claimed in claim 1, wherein, described release channel comprises the second channel that is communicated to the less oil-poor zone of the interior lubricants capacity of described crank chamber, and
Described valve system increases the ratio that described first passage accounts for described release channel along with the raising of described drive shaft speed, and reduces the ratio that described second channel accounts for described release channel along with the reduction of described drive shaft speed.
3. swash-plate-type compressor as claimed in claim 2, wherein, described second channel is formed with throttle valve.
4. swash-plate-type compressor as claimed in claim 2, wherein, described wobbler is supported for and makes its variable pitch,
The lug plate of reception compression reaction force is fixed to described live axle and rotates with described live axle one,
Be formed with the Oil Guide path on described housing, described Oil Guide path outer regions from described crank chamber between described housing and described lug plate is extended, and
Described first passage is communicated to described Oil Guide path.
5. swash-plate-type compressor as claimed in claim 4 wherein, is provided with shaft sealer, and it is used for providing sealing between described housing and described live axle, and
Described first passage is communicated to described Oil Guide path in the position near described shaft sealer.
6. swash-plate-type compressor as claimed in claim 2, wherein, described wobbler is supported for and makes its variable pitch,
The lug plate of reception compression reaction force is fixed to described live axle and rotates with described live axle one, and
Described first passage comprises and being formed on the described lug plate and to the guide hole of the outer regions opening of described crank chamber.
7. swash-plate-type compressor as claimed in claim 6 wherein, is provided with shaft sealer, and it is used for providing sealing between described housing and described live axle, and
Described second channel near described shaft sealer to described crank chamber opening.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008025757 | 2008-02-05 | ||
| JP2008025757 | 2008-02-05 | ||
| JP2008038686 | 2008-02-20 | ||
| JP2008052548 | 2008-03-03 |
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| Publication Number | Publication Date |
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| CN101503994A true CN101503994A (en) | 2009-08-12 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100065221A Active CN101503993B (en) | 2008-02-05 | 2009-02-04 | Swash plate compressor |
| CNA2009100065236A Pending CN101503994A (en) | 2008-02-05 | 2009-02-04 | Swash plate compressor |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100065221A Active CN101503993B (en) | 2008-02-05 | 2009-02-04 | Swash plate compressor |
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| Country | Link |
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| CN (2) | CN101503993B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106460816B (en) * | 2014-06-27 | 2018-12-07 | 法雷奥日本株式会社 | Variable displacement swash plate compressor |
| CN109899268A (en) * | 2017-12-08 | 2019-06-18 | 长城汽车股份有限公司 | Compressor, air-conditioning system and vehicle |
| CN108547765B (en) * | 2018-04-08 | 2019-11-26 | 杭州绿聚科技有限公司 | A kind of novel axial plunger pump |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4685866A (en) * | 1985-03-20 | 1987-08-11 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement wobble plate type compressor with wobble angle control unit |
| DE4481042C2 (en) * | 1994-07-13 | 1999-02-11 | Toyoda Automatic Loom Works | Swash plate compressor with variable displacement |
| JP4399994B2 (en) * | 2000-11-17 | 2010-01-20 | 株式会社豊田自動織機 | Variable capacity compressor |
| JP3896822B2 (en) * | 2001-11-12 | 2007-03-22 | 株式会社豊田自動織機 | Swash plate compressor |
| JP3891099B2 (en) * | 2001-11-12 | 2007-03-07 | 株式会社豊田自動織機 | Piston compressor |
| JP2006022785A (en) * | 2004-07-09 | 2006-01-26 | Toyota Industries Corp | Variable displacement compressor |
| JP2006307700A (en) * | 2005-04-27 | 2006-11-09 | Toyota Industries Corp | Compressor |
-
2009
- 2009-02-04 CN CN2009100065221A patent/CN101503993B/en active Active
- 2009-02-04 CN CNA2009100065236A patent/CN101503994A/en active Pending
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| Publication number | Publication date |
|---|---|
| CN101503993B (en) | 2012-08-22 |
| CN101503993A (en) | 2009-08-12 |
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Open date: 20090812 |