CN1222646A - Torsional vibration attenuating structure in compressor - Google Patents
Torsional vibration attenuating structure in compressor Download PDFInfo
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- CN1222646A CN1222646A CN 98122938 CN98122938A CN1222646A CN 1222646 A CN1222646 A CN 1222646A CN 98122938 CN98122938 CN 98122938 CN 98122938 A CN98122938 A CN 98122938A CN 1222646 A CN1222646 A CN 1222646A
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Abstract
A mechanism for attenuating torsional vibration in a compressor is described. The compressor includes a swash plate secured to a drive shaft and pistons coupled to the swash plate. Compression of refrigerant gas by the pistons generates torsional vibrations of the drive shaft. The rear end of the drive shaft is coupled to a damper for attenuating torsional vibrations. The damper includes a frictional plate secured to the rear end of the drive shaft, a weight rotatably fitted about the drive shaft, and a coil spring. The coil spring elastically presses the weight against the frictional plate and elastically couples the weight with the drive shaft. When the drive shaft torsionally vibrates, the weight contacts the frictional plate and is vibrated about the axis of the drive shaft by the coil spring. As a result, energy of the torsional vibrations is consumed and the vibrations are attenuated.
Description
The present invention relates to be used for decaying for example structure of the torsional vibration of the used compressor of auto air-con.
Typical compressor for example swash-plate-type compressor comprises the shell that wherein forms crankshaft room.Compressor also has transmission shaft, and this shaft extension is crossed this crankshaft room also rotationally by outer casing supporting.Wobbler is fixed on the transmission shaft, rotates simultaneously with axle.The cylinder block that constitutes a shell part has cylinder chamber.But be contained in each cylinder chamber to the piston to-and-fro motion.Be connected in wobbler on this piston operation, and move back and forth by the rotation of wobbler.
Transmission shaft is connected in external drive source for example on the motor of car by magnetic clutch and belt.Clutch be linked optionally with on external drive source and the transmission shaft and with its disengagement.Clutch comprises rotationally by the belt pulley of compressor case supporting, is fixed in the inner sleeve of transmission shaft far-end, towards the armature and the electromagnetic coil of belt pulley.Armature is connected in inner sleeve by the leaf spring and is driven by electromagnetic coil.Electromagnetic coil is pressed on the belt pulley armature.In this state, the power of driving source can be sent on the transmission shaft by belt, belt pulley, armature, leaf spring and inner sleeve.
During compressor operation, the compression of each piston causes acting on compression reaction force on the transmission shaft by piston and wobbler.The rotation of compression reaction force resistance transmission shaft.This counteractive big or small cyclic fluctuation.This makes transmission shaft produce torsional vibration again.When torsional vibration was sent to armature by inner sleeve and leaf spring, this torsional vibration was weakened a little by rubber-like leaf spring.Yet because the original design of this leaf spring is to play parts of magnetic clutch as soon as possible, so leaf spring damping rotary oscillations satisfactorily.
Transmission shaft and the wobbler that rotates simultaneously and magnetic clutch constitute the rotor with natural frequency.Torsional vibration occurs on the rotor.If frequencies of torsional vibration equals the free frequency of rotor, then on rotor, resonate.Resonance has increased torsional vibration widely.Torsional vibration also makes the torque that acts on the transmission shaft and the fluctuation of speed of belt pulley.In addition, the fluctuation of torsional vibration will make other engine components vibration that is connected in compressor by belt at last.Therefore increased the noise in the passenger compartment.
Very strong torsional vibration can make armature and belt pulley slide relative to one another, and this causes the power transmission between power source and transmission shaft to degenerate.Transmit in order to improve power, must increase the friction between armature and the belt pulley.Promptly need to use bigger electromagnetic coil.Bigger electromagnetic coil has increased the size and the manufacture cost of compressor.
Uncensored Japanese patent laid-open publication gazette No.55-20908 discloses a kind of compressor with vibration attenuation mechanism.This mechanism is contained in the magnetic clutch, comprises vibration damper and connecting plate.This vibration damper and connecting plate make armature be connected in inner sleeve.This inner sleeve and connecting plate are interconnected by the spring that is positioned at its circumferential section.Inner sleeve and connecting plate have serrated surface respect to one another respectively.This vibration damper is between serrate surface.
Comprising that the torsional vibration on the rotor of transmission shaft changes the torque that is added on the transmission shaft, and inner sleeve is slided with respect to connecting plate a little.Vibration damper between inner sleeve and connecting plate reduces vibration.
Vibration attenuation mechanism is arranged in clutch, specifically between the inner sleeve of armature and transmission power.Yet it is very difficult to design this clutch, and the original function that make selectivity transmit the clutch of power is not subjected to the obstruction of damping mechanism.In addition, the facing surfaces of inner sleeve and connecting plate is zigzag, and applied spring makes inner sleeve be connected with connecting plate.Zigzag surface and spring make the structure complicated of clutch, have increased part count, and it is very bothersome therefore to make clutch, and the cost height.
Therefore the purpose of this invention is to provide a kind of simple mechanism and come torsional vibration in the attenuate compressor effectively.
For reaching above-mentioned and other purpose,, provide a kind of compressor with the vibration damper that is used for damping rotary oscillations according to the present invention.This compressor has rotor, and this rotor comprises the transmission shaft of unitary rotation and driven so that the compression member of compressed fluid by rotor.The compression of fluid makes the rotor vibration that twists.The vibration damper of decay rotor torsional vibration comprises friction means, weight and link.Friction means is contained on the rotor and rotates and have a friction surface with rotor.This weight has friction surface, and this surface contacts with the friction surface of friction means, thereby produces predetermined friction torque resistance between weight and friction means.Link flexibly is connected in rotor and the friction means one, so that the rotation of rotor and torsional vibration are sent on the weight weight.Link has elasticity in the direction of torsional vibration.Weight contact friction parts, and the shaft vibration of the kinetoplast that rotates, thereby the torsional vibration of counteracting rotor.
Describe below in conjunction with accompanying drawing, can obviously find out other aspects and advantages of the present invention thus, this accompanying drawing is illustration principle of the present invention as an example.
The following describes current preferred embodiment and related accompanying drawing, with reference to these explanations the present invention may be better understood with and purpose and advantage.
Fig. 1 is a cross-sectional view, and the compressor of first embodiment of the invention is shown;
Fig. 2 is the partial cross section view of amplifying, and the dynamic shock-absorber of Fig. 1 is shown;
Fig. 3 is a schematic representation, and being connected of transmission shaft, wobbler, clutch and vibration damper of Fig. 1 is shown;
Fig. 4 is a plotted curve, and the relation between torsional frequency and Fig. 1 transmission shaft torque ripple is shown;
Fig. 5 is a plotted curve, and the transmission shaft rotating speed of Fig. 1 and the relation between its torque ripple are shown;
Fig. 6 is the partial cross section view of amplifying, and second embodiment's dynamic shock-absorber is shown;
Fig. 7 is the front elevation of dynamic shock-absorber among Fig. 6;
Fig. 8 is the partial cross section view of amplifying, and the 3rd embodiment's dynamic shock-absorber is shown;
Fig. 9 is a front elevation, and the dynamic shock-absorber among Fig. 8 is shown;
Figure 10 is a front elevation, and the 4th embodiment's dynamic shock-absorber is shown;
Figure 11 is the partial cross section view of amplifying, and the 5th embodiment's dynamic shock-absorber is shown;
Figure 12 is the partial cross section view of amplifying, and the 6th embodiment's dynamic shock-absorber is shown;
Figure 13 is a schematic representation, and the vibration damper of Figure 12 is shown;
Figure 14 is the cross-sectional view along the 14-14 line intercepting of Figure 15, and the 7th embodiment's dynamic shock-absorber is shown;
Figure 15 is a front elevation, and dynamic shock-absorber shown in Figure 14 is shown;
Figure 16 is a front elevation, and the 8th embodiment's dynamic shock-absorber is shown;
Figure 17 is a front elevation, and the 9th embodiment's dynamic shock-absorber is shown;
Figure 18 is the cross-sectional view along the 18-18 line intercepting of Figure 19, and the tenth embodiment's dynamic shock-absorber is shown;
Figure 19 is a front elevation, and the dynamic shock-absorber of Figure 18 is shown;
Figure 20 is the cross-sectional view along the 20-20 line intercepting of Figure 21, and the 11 embodiment's dynamic shock-absorber is shown;
Figure 21 is a front elevation, and the dynamic shock-absorber of Figure 20 is shown;
Figure 22 is the cross-sectional view along the 22-22 line intercepting of Figure 23, and the 12 embodiment's dynamic shock-absorber is shown;
Figure 23 is a front elevation, and the dynamic shock-absorber of Figure 22 is shown;
Figure 24 is a partial section, and the 13 embodiment's dynamic shock-absorber is shown;
Figure 25 is the cross-sectional view along the 25 25 lines intercepting of Figure 24;
Figure 26 is a fragmentary, perspective view, and the dynamic shock-absorber of Figure 24 and 25 is shown.
Swash-plate-type compressor below with reference to Fig. 1-5 explanation first embodiment of the invention with double-head piston.
As shown in Figure 1, front air cylinder seat 21 and rear cylinder seat 22 are connected to each other in the middle part of compressor.Front air cylinder seat 21 has front end, and this front end is connected in front casing 25 by valve block 23.Rear cylinder seat 22 has the rear end, and this rear end is connected in rear casing 26 by valve block 24.Cylinder block 21,22, valve block 23,24, front casing 25 and rear casing 26 are tightened together by bolt 27, form the shell of compressor.
Clutch 31 comprises belt pulley 33, inner sleeve 34, armature 35 and electromagnetic coil 36.On the forward part of front casing 25, form support column.Pair of bearings 37 is housed, with the wheel of back(-)up belt rotationally 33 on this support column.Belt 32 is on belt pulley 33.Inner sleeve 34 is fixed in the front end 28a of transmission shaft 28.Armature is fixed on the inner sleeve 34 by leaf spring 38.Electromagnetic coil 36 is fixed in front casing 25 and is configured in the belt pulley 33, is positioned at the position facing to armature 35.Armature selectively is pressed against on the front surface of belt pulley and is separated.
21a passes front air cylinder seat 21 in the front air cylinder chamber of uniform distances, and has the rear cylinder chamber 22a of uniform distances to pass rear cylinder seat 22, and each rear cylinder chamber is aimed at a chamber among the 21a of front air cylinder chamber.Cylinder chamber 21a, the 22a that each group is aimed at is parallel to the axis of transmission shaft 28, and the axis of chamber 21a, 22a forms a circle, and the center of this circle overlaps with drive shaft axis.Compression member or have fore head and occipital double-head piston 39 is received within and respectively organizes among cylinder chamber 21a, the 22a.Pressing chamber 40 shapes are between the fore head of piston 39 and the valve block 23 and between the occiput and valve block 34 at piston 39.
Crankshaft room 41 limits between cylinder block 21,22.Wobbler 42 is fixed in the transmission shaft 28 in the crankshaft room 41.Wobbler 42 is connected in each piston 39 by a pair of hemispheric watt.The rotation of transmission shaft makes wobbler 42 cause each piston to move back and forth.Thrust bearing 44 is configured between the end, interior center of each side of wobbler 42 and relevant cylinder block 21,22.In other words, thrust bearing 44 is fixed on wobbler 42 between the cylinder block 21,22.
The discharge chamber 47 of suction chamber 45 and encirclement suction chamber 45 is formed on the front portion of front casing 25.Equally, the discharge chamber 48 of suction chamber 46 and encirclement suction chamber 46 is formed in the rear casing 26.Suction chamber 45,46 is connected in crankshaft room 41 by sucking path 49 respectively, and this passage extends through relevant cylinder block 21,22 and valve block 23,24.Crankshaft room's 41 compressed machine inlet (not shown) are connected in external refrigerant pipeline (not shown).Discharge chamber 47,48 compressed respectively machine outlet (not shown) and discharge route 61 and be connected in the external refrigerant pipeline, this passage 61 extends through relevant cylinder block 21,22 and valve block 23,24.
As illustrated in fig. 1 and 2, vibration damper 55 is contained on the rearward end 28b of the transmission shaft 28 in the suction chamber 46 of back, with the torsional vibration of decay rotor 63.Vibration damper 55 comprises discoidal friction plate 56, annular weight 57 and disc spring 58.Friction plate 56 is fixed in the rearward end of transmission shaft 28 by the bolt (not shown).The circumferential surface 28c that weight 57 is enclosed within transmission shaft rear section 28b goes up and can rotate with respect to transmission shaft 28.The surface of the friction plate 56 of contact weight 57 forms rubbing surface 56a, and the surface of the weight 57 of contact friction face 56a also forms friction surface 57a.Disc spring 58 is pressed on the friction surface 56a of friction plate 56 the friction surface 57a of weight 57.Friction surface 56a is positioned at a plane perpendicular to the axes O of transmission shaft 28.
With metal for example the weight 57 done of iron or steel therein the heart partly have hole 57b.Between the surface of hole 57b and transmission shaft rear section 28b, there is very little slit.This slit can make weight 57 rotate and move axially along transmission shaft 28 around transmission shaft 28.Yet this slit can not make weight 57 measure significantly with respect to the plane inclination perpendicular to axes O.
One end of disc spring 58 is fixed in transmission shaft 28 by pin 59, and its other end is fixed in the front surface of weight 57 by pin 60.Disc spring 58 not only makes weight 57 be pressed against on the friction plate 56, but also makes weight 57 flexibly be connected in transmission shaft 28.In other words, disc spring 58 not only has elasticity at axial direction, and also has elasticity at rotor 63 torsional directions.The torsional vibration of rotor 63 is sent to weight 57 by spring 58, and makes the axes O vibration of weight 57 around transmission shaft 28.
The free frequency of vibration damper 55 is determined by the quality of weight 57 and the Young's modulus of spring 58.In the embodiment shown in Fig. 1～5, the Young's modulus of the quality of weight 57 and spring 58 is confirmed as making the free frequency of vibration damper 55 to be substantially equal to the free frequency of rotor 63.
Fig. 3 schematically shows transmission shaft 28, wobbler 42, clutch 31 and is connected with vibration damper 55.If motor E is a fixed support, then belt pulley 33 and armature 35 are connected in this fixed support by the belt 32 that plays the elastic component effect.Armature 35 is connected in inner sleeve 34 by the leaf spring 38 that plays the elastic component effect.This inner sleeve 34 is connected in the front end 28a of transmission shaft 28.The part of transmission shaft 28 between inner sleeve 34 and wobbler 42 is quite long.This long part is because the fluctuation of compression reaction force and in torsional direction generation elastic strain.Therefore the front end 28a of transmission shaft 28 plays elastomeric effect.Wobbler 42 is fixed on the intermediate portion of transmission shaft 28.The rear end 28b of transmission shaft 28 is fixed in friction plate 56 and rotatably support weight 57.Weight 57 is connected in the rear end 28b of transmission shaft 28 by spring 58.
The operation of explanation compressor now.
Constantly be transported to the belt pulley 33 of clutch 31 by belt 32 by the power of motor E generation.Therefore when motor E operated, belt pulley 23 just rotated consistently.When cooling load was added on the external refrigerant pipeline, electromagnetic coil 36 just excited, and made the thrust of armature 35 resistance leaf springs 38 and attracted on the front surface of belt pulley 33.So just, make transmission shaft 28 be connected in motor E.When the cooling load on being added in the external coolant pipeline is zero, the electromagnetic coil deexcitation, thus make the thrust of leaf spring 38 that armature 35 and belt pulley 33 are separated.So just, disconnect being connected of transmission shaft 28 and motor E.
When motor E rotating drive shaft 28, wobbler 42 rotates in crankshaft room 41, and by watts 43 each piston among cylinder chamber 21a, the 22a of relevant group is moved back and forth.The to-and-fro motion of piston 39 makes refrigerant gas be pumped into the crankshaft room 41 from the compressed machine inlet of external refrigerant pipeline.Refrigerant gas in the crankshaft room 41 is pumped in the relevant suction chamber 45,46 through suction passage 49 then.When any one head of each piston 39 enters induction stroke, the pressure that this moves to lower dead centre and reduce relevant pressing chamber 40 from upper dead center.So just, open relevant suction valve 52 and refrigerant gas is extracted in the pressing chamber 40 through relevant suction port 50.
When each piston head enters compression/discharge stroke and when lower dead centre moved on to upper dead center, the refrigerant gas in pressing chamber 40 just was compressed to predetermined pressure.The refrigerant gas of compression is the relevant expulsion valve 53 of breakdown then.So just, make refrigerant gas be drained into relevant discharge chamber 47,48 through corresponding exhaust port 51.Refrigerant compressed gas is discharged chamber 47,48 through discharge route 61 and compressor outlet then.Outside refrigerant line comprises condenser, expansion valve and vaporizer (all not shown), and this exterior line utilization comes air-conditioning passenger railway carriage by the refrigeration agent of compressor compresses.
During compressor operation, the compression of piston 39 produces compression reaction force.Compression reaction force fluctuates, the torsional vibration of the body 63 that therefore rotates, and rotor 63 comprises transmission shaft 28, wobbler 42 and clutch 31.Particularly, because the fluctuation of compression reaction force will make the quite long transmission shaft between inner sleeve 34 and the wobbler 42 partly produce elastic strain, this deformation just causes the torsional vibration of rotor 63.This torsional vibration makes and to act on torque on the transmission shaft 28 and the rotating speed of belt pulley 33 fluctuates.Shown in the solid line of Fig. 4 plotted curve, it is maximum that the torsional vibration of rotor 63 reaches at frequency F1 place, and this frequency equals the free frequency of rotor 63.In plotted curve, the torque ripple of transmission shaft 28 is represented the size of torsional vibration.When torsional vibration was sent on the armature 35 by inner sleeve 34 and leaf spring 38, torsional vibration can be attenuated a little by spring 38.But this decay can't be satisfactory.
When rotor 63 twisted vibration, the vibration damper 55 that is connected in transmission shaft 28 just vibrated, thereby suppressed the torsional vibration of rotor 63.In the embodiment shown in Fig. 1～5, the Young's modulus of the quality of weight 57 and spring 58 is confirmed as making free frequency consistent with rotor 63 basically of vibration damper 55.The torsional frequency of vibration damper 55 reaches maximum (with reference to Fig. 4) at frequency F1, and the torsional vibration of rotor 63 also reaches maximum under this frequency.Specifically be, the vibration of rotor 63 is sent to weight 57 by spring 58, and makes the axes O vibration of weight 57 around transmission shaft.The friction surface 57a of weight 57 is pressed against on the friction surface 56a of friction plate 56 by spring 58.Therefore, the vibration of weight 57 just produces friction between friction surface 57a, 56a.The vibration of weight 57 and friction have consumed the energy by the torsional vibration generation of rotor 63.In brief, vibration takes place and reacts on the torsional vibration of rotor 63 and offset this vibration in weight 57.As a result, the torsional vibration of weight 57 has reduced the torsional vibration peak value of rotor 63, shown in the dotted line in Fig. 4 curve.Thereby the rotation that can reduce belt pulley 33 is fluctuateed.
Shown in the solid line in Fig. 5 curve, the torque ripple of transmission shaft 28 is issued to peak value at certain revolution of transmission shaft 28.Yet the vibration damper 55 among Fig. 1 and Fig. 2 has reduced the peak value of torque ripple, shown in the dotted line in Fig. 5 curve.
Thereby reduced the torsional vibration of the rotor 63 that comprises transmission shaft 28 with optimal way.So just reduce vibration reliably, suppressed noise.The torsional vibration that reduces can not make armature 35 and belt pulley 33 slide relative to one another when it meshes.Therefore the power of motor can be sent on the transmission shaft 28 reliably.Therefore the size that does not need to increase electromagnetic coil increases the frictional force between armature and the belt pulley 33.Promptly can reduce the size of electromagnetic coil.
The friction surface 56a of friction plate 56 is positioned at a plane perpendicular to the axes O of drive shaft 28.In addition, weight 57 can rotate with respect to transmission shaft 28, and can not tilt with respect to transmission shaft 28.This structure makes that weight 57 can only be around the axle O of transmission shaft 28 vibration, damping rotary oscillations thus on sense of rotation.If weight 57 can vibrate in other direction, not the axes O vibration of sense of rotation around transmission shaft 28, then can not suppress torsional vibration effectively.
For improving the decay of vibration, the diameter of weight 57 is preferably bigger.In the embodiment shown in Fig. 1～5, weight 57 is in the quite well-to-do suction chamber 46.This can increase the diameter of weight 57 and reduces the quality of weight 57 simultaneously with regard to making.In other words, can utilize the as far as possible little weight of quality 57 to come damping rotary oscillations fully, because diameter can be done quite greatly.In addition, the weight that reduces and reduced compressor of the quality of weight 57.
Other embodiments of the invention are described now.Below main explanation and first embodiment's difference.
Fig. 6 and 7 illustrates second embodiment's vibration damper 55.Vibration damper 55 among Fig. 6 and 7 has a pair of leaf spring 62, and without the disc spring 58 of the vibration damper 55 of Fig. 1.Vibration damper 55 its advantages with leaf spring 62 are identical with the advantage of the vibration damper of Fig. 1.
Fig. 8 and 9 illustrates the 3rd embodiment's vibration damper 55.Fig. 8 and 9 vibration damper 55 comprise the chest 65 of the weight 57 of packing into.This chest 65 is contained in the rear end 28b of transmission shaft 28.Weight 57 has two friction surface 57a, and one in its front portion, and one at its rear portion.This friction surface 57a is with the inner side surface of predetermined frictional force contact chest 65.Therefore the effect of the friction plate 56 of vibration damper 55 is identical among the effect of chest 65 and Fig. 1.The inner side surface of the chest 65 of contact weight 57 plays a part friction surface 65a.As shown in Figure 9, leaf spring 66 makes the outer circumferential face of weight 57 flexibly be connected in the opposite inner face of chest 65.Leaf spring 66 can be more than one.Fig. 8 has identical advantage with 9 vibration damper 55 with the vibration damper 55 of Fig. 1.In addition, chest 65 encases weight 57.This structure can prevent the refrigerant gas in the vibration damper disturbance suction chamber 46, thereby has improved the gas suction performance of compressor.
What Figure 10 illustrated the 4th embodiment subtracts vibrator 55.The vibration damper 55 of Figure 10 comprises having the radially impeller shape weight 57 of extended blade 57c.When rotating, this weight 57 is subjected to the resistance of cooling gas in the suction chamber.This air resistance can suppress the vibration of weight 57, and this vibration originates from the torsional vibration of rotor 63.As a result, the decayed torsional vibration of rotor 63.The blade of other shape has same advantage.That is, each blade 57c can be rectangle or L shaped cross section.In addition, the leading flank of each blade 57 can have recess.
Figure 11 illustrates the 5th embodiment's vibration damper.The vibration damper 55 of Figure 11 is not contained in the compressor.Vibration damper 55 replaces the front end 28a that is fixed in transmission shaft 28, is positioned at the outside of compressor.The vibration damper 55 of Figure 11 is identical with the structure of the vibration damper 55 of Fig. 6.Therefore the vibration damper of Figure 11 is contained on the compressor that does not have inner vibration damper easily.
Figure 12～16 illustrate the vibration damper that is contained on the clutch 31 and is positioned at the compressor outside.Figure 12 and 13 illustrates the 6th embodiment's vibration damper 55.Figure 12 and 13 vibration damper have the annular weight 57 of close armature 35.Weight 57 has the friction surface 57a of contact armature 35 front surfaces.In the vibration damper 55 of Figure 12 and 13, the effect of armature 35 is just as the effect of the friction plate 56 of vibration damper 55 among Fig. 1 and Fig. 2.That is, the front surface of armature 35 forms friction surface 35a.Ring part 67 is fixed in the outer surface of armature 35, so that surround weight 57.Ring part 67 prevents that weight 57 from moving vertically and prevent with respect to the plane inclination perpendicular to transmission shaft 28 axis.Leaf spring 62 makes ring part 67 be connected in weight 57.Leaf spring 62 makes annular weight flexibly be connected in ring 67, and weight 57 is pressed against on the friction surface 35a of armature 35.Leaf spring 62 is spaced apart and form a circle, the center and the armature dead in line of this circle with the angular distance that equates around the axis of armature 35.Figure 13 schematically illustrates the vibration damper 55 of Figure 12.
Figure 12 and 13 vibration damper be not in the centre of the power transmission of clutch 31.That is, vibration damper 55 does not make inner sleeve 34 be connected in armature 35, but is fixed on the armature 35.Therefore Figure 12 and 13 vibration damper are contained on the clutch easily, do not change the linkage structure of leaf spring 38, and this leaf spring makes inner sleeve 34 be connected in armature 35.So function of the not anti-evil clutch 31 of the vibration damper 55 of Figure 12 and 13.In addition, Figure 12 and 13 damper structure make the diameter of weight 57 can be increased to maximum.Maximum diameter can make vibration damper reach vibration suppression characteristic to greatest extent, also can make the quality of weight 57 reduce to minimum simultaneously.
Figure 14 and 15 illustrates the 7th embodiment's vibration damper 55.This vibration damper 55 comprises armature 35 and annular weight 71, and the effect of the friction plate 56 of the vibration damper 55 among the former effect and Fig. 1,2 is the same.The friction surface 35a of the friction surface 71a contact armature 35 of weight 71.Weight 71 comprises equally spaced hole 71b.The axis of this hole 71b forms a circle, the dead in line of its center of circle and weight 71.Pin 72 with head 72a is contained in each hole 71b from the loose loose ground in the front side of vibration damper 55.The rear end of each pin is screwed on the armature 35.Disc spring 73 is contained between the head 72a and weight 71 of each pin 72.Disc spring 73 is pressed on the friction surface 35a of armature 35 the friction surface 71a of weight 71.As shown in figure 15, leaf spring 74 is between weight 71 and armature 35.Each leaf spring 74 has two ends, and an end is connected in the front surface of weight 71 by pin 75, and the other end has the pin 77 of liner 76 to be connected in the front surface of armature 35 by the centre.Leaf spring 74 makes weight 71 flexibly be connected in armature 35.Leaf spring 74 separates with the angular spacing that equates around the axis of armature 35.
Shown in Figure 14 and 15, inner sleeve 34 comprises the cylindrical wall 34a that protracts from mind-set wherein.Connecting plate 70 is fixed in this cylindrical wall 34a.One end of each leaf spring 78 is connected in plate 70 by pin 79.The other end of each leaf spring 78 is connected in the front surface of armature 35 by pin 80.Leaf spring 78 is sent to inner sleeve 34 with the rotation of armature 35.
Like the same in the vibration damper of Fig. 1～13, can the decay torsional vibration of rotor 63 of the vibration of the weight 71 in Figure 14 and 15 the vibration damper 55.Can prevent the inclination of weight 71 by the friction surface 35a that weight 71 is pressed against armature 35.Yet also can prevent the inclination of weight 71 by the engagement of pin 72 and hole 71b.
In the vibration damper 55 of Figure 14 and 15, the spring 73 that weight 71 is pressed against on the friction surface 35a is independent of the spring 74 that weight 71 is connected in armature 35.Therefore the characteristic that can determine spring 73,74 independently is spring modulus for example.
Image pattern 12 and 13 vibration damper 55 are such, and Figure 14 and 15 vibration damper 55 do not make inner sleeve 34 be connected in armature 35.Therefore Figure 14 and 15 vibration damper 55 make and easily clutches 31 are installed and can not be hindered the effect of clutch 31.
Can adopt and not be that magnetic material for example is not the material that the material of iron is made weight 71.That is, weight 71 usefulness nonmagnetic substances are made.The original effect of electromagnetic coil 36 is that armature is attracted on the belt pulley 33.If yet weight make of magnetic material, exciting of electromagnetic coil 36 will cause making weight 71 to attracted on the armature 35, this will damage the combination of armature 35 and belt pulley 33.Therefore the suction between needs consideration weight 71 and the electromagnetic coil 36 is determined the electromagnetic force of electromagnetic coil 36.
In addition, the change of the electric current [strength by electromagnetic coil 36, the error that the size error of the parts of clutch 31 and assembling clutch produce all can make the frictional force between weight 71 and the armature 35 change.Therefore the frictional force between weight 71 and the armature 35 will influence the vibration dampening characteristic of vibration damper 55 greatly.In other words, the change of frictional force will cause not satisfied vibration attenuation.Therefore weight 71 the most handy nonmagnetic substances are made, because it does not disturb the effect of clutch 31, and help obtaining satisfied vibration attenuation.
Figure 16 illustrates the 8th embodiment's vibration damper 55.The vibration damper 55 of Figure 16 is modified models of the vibration damper 55 of Figure 14 and 15.The vibration damper 55 of Figure 16 lacks the spring 73 that the vibration damper 55 in Figure 14 and 15 has.Replace is that each leaf spring 74 has the pressures partially 74a of close pin 77.This pressures partially 74a is pressed in weight 71 on the friction surface 35a of armature 35.Compare with 15 vibration damper with Figure 14, the vibration damper of Figure 16 has less parts.
Figure 17 illustrates the 9th embodiment's vibration damper.The vibration damper of Figure 17 is identical with the vibration damper of Figure 14 and 15, has just saved pin 72 and disc spring 73.And the vibration damper of Figure 17 has leaf spring 81.The near-end of leaf spring 81 is welded in the outer surface of weight 71 or fixed thereon.The internal surface of each spring 81 distal portions forms friction surface 81a.Friction surface 81a is crushed on the periphery friction surface 35c of armature 35.The number of spring 81 is preferably three or more.In addition, its structure of the vibration damper of Figure 17 is identical with the structure of the vibration damper 55 of Figure 14 and 15.
Figure 18 and 19 illustrates the tenth embodiment's vibration damper 55.Figure 18 and 19 vibration damper 55 are to have saved pin 72 and spring 73 with vibration damper 55 differences of Figure 14 and 15.Weight 71 replaces with magnetic material to be made.When electromagnetic coil 36 swashs when strict, the friction surface 71a of weight 71 attracted on the friction surface 35a of armature 35.This structure decrease the part count in the vibration damper 55.
Figure 20 and 21 illustrates the dynamic shock-absorber 85 of the 11 embodiment's integral body.Dynamic shock-absorber 85 is fixed in armature 35.Vibration damper 85 is made by crooked metal sheet.Vibration damper 85 comprises annular weight 86 and leaf spring 87, and this spring and weight 86 form whole and extend internally.The number of spring 87 for example is 4.Leaf spring 87 is fixed in the front surface of armature 35, so that make weight 86 elasticity be connected in armature 35.Vibration damper 85 also has pressures partially 88.Each pressures partially 88 has the friction surface 88a on the friction surface 35a that is pressed in armature 35.Like this, vibration damper 85 can form with single piece plate.Therefore the simple in structure and easy manufacturing of vibration damper 85.
Figure 22 and 23 illustrates the 12 embodiment's vibration damper 85.Figure 22 and 23 vibration damper are different from the vibration damper of Figure 20 and 21, and difference is, its number for example is that 4 the weight that separates 89 is fixed on the front surface of weight 86.Compare with 21 vibration damper with Figure 20, Figure 22 and 23 vibration damper be damping rotary oscillations more effectively.
Figure 24～26 illustrate the 13 embodiment's annular dynamic vibration damper 91.Vibration damper 91 is fixed in belt pulley 33.Belt pulley 33 has the cylindrical wall 33a that extends back.Vibration damper 91 is installed around this cylindrical wall 33a.Just can make vibration damper 91 by crooked single piece of sheet metal.Vibration damper 91 comprises tubular weight 92, and its number is 4 in the embodiment shown in Figure 24～26.Each weight 92 has the cross section of general rectangular.Each is connected by leaf spring 93 adjacent weight 92.This leaf spring 93 makes weight 92 flexibly be connected in belt pulley 33.The inwall of each weight 92 forms arc pressures partially 94, and the effect of this part is the same with the effect of spring.Each pressures partially 94 comprises friction surface 94a, makes this surface pressure on the periphery friction surface 33b of circle wall tube 33a.Like this, vibration damper 91 can be made of single piece plate.Therefore the simple in structure and easy manufacturing of vibration damper 91.
Illustrative embodiment can retrofit as follows.
The present invention can implement on the compressor except that compressor shown in Figure 1.For example, the present invention can implement on single-head piston type compressor, compressor with variable displacement, the recessed wheel-plate type compressor of waveform, vane compressor or turbocompressor.
Therefore, the example of this paper and embodiment should see as exemplary with unrestricted.The invention is not restricted to details as herein described, but can be within the scope of the appended claims with the scope of equivalence in change.
Claims (23)
1. vibration damper (55 that has in order to damping rotary oscillations; 85; 91) compressor, this compressor has rotor (63) and compression member (39), this rotor comprises the transmission shaft (28) that rotates simultaneously, this compression member is driven with compressed fluid by rotor, this causes the torsional vibration of rotor, the wherein torsional vibration of vibration damper decay rotor, this vibration damper is characterised in that:
Friction means (56; 65; 35; 33), be contained on the rotor so that rotate with rotor, wherein friction means has friction surface (56a; 65a; 35a; 33b);
Has friction surface (57a; 71a; 88a; Weight (57 94a); 71; 86; 92), the friction surface of the friction surface contact friction parts of weight wherein, thus between weight and friction means, produce predetermined friction torque resistance;
Link (58; 62; 66; 74; 87; 93), weight flexibly is connected in rotor and the friction means one, so that the rotation and the torsional vibration of rotor are sent on the weight, wherein link has elasticity on the direction of torsional vibration, and weight contact friction parts wherein, and around the vibration of the axis of rotor, thereby offset the torsional vibration of rotor.
2. compressor as claimed in claim 1 is characterized in that, weight (57; 71; 86; 92) be supported, in case with respect to a plane inclination, this plane is perpendicular to the axis of rotor (63).
3. compressor as claimed in claim 2 is characterized in that, friction means (56; 65; 35) friction surface (56a; 65a; 35a) be positioned at a plane perpendicular to rotor (63) axis.
4. compressor as claimed in claim 1 is characterized in that, vibration damper (55) also comprises pressure-producing part (58; 62; 73; 74a), these parts are used to make weight (57; 71) flexibly be pressed in friction means (56; 35) on.
5. compressor as claimed in claim 4 is characterized in that, link comprises disc spring (58) or leaf spring (62; 74), this leaf spring also plays pressure-producing part.
6. compressor as claimed in claim 1 is characterized in that, transmission shaft (28) comprises first end (28b) that is positioned at compressor and be positioned at the second outer end 28a of compressor that wherein vibration damper (55) is contained on the end of these two ends.
7. compressor as claimed in claim 6 is characterized in that, friction means (56; 65) be fixed on the transmission shaft (28), wherein, weight (57) can be rotated with respect to this transmission shaft by cardan-shaft suspension; Wherein link comprises spring (58; 62), this spring is connected on transmission shaft and friction member one weight; This spring (58; 62) weight (57) flexibly is pressed against in the friction means on (56).
8. compressor as claimed in claim 1 is characterized in that being used for the shell (21,22,25,26) of rotating support transmission shaft (28), and wherein, shell defines suction chamber (45,46), pressing chamber (40) and discharges chamber (47,48); And wherein compression member (39) is drawn into pressing chamber with fluid from absorption chamber, and the fluid that compresses in the pressing chamber is discharged to drain chamber, and wherein vibration damper (55) is arranged in absorption chamber (46).
9. compressor as claimed in claim 6 is characterized in that, vibration damper (55) comprises the chest (65) of the weight of packing into (57), and wherein, chest (65) plays a part friction means; Link is to make weight (57) be connected in the spring (66) of chest (65).
10. compressor as claimed in claim 1 is characterized in that, the shape of weight (57) resembles turbine.
11. compressor as claimed in claim 1, it is characterized in that, rotor (63) comprises the clutch (31) that is positioned between external drive source (E) and the transmission shaft (28), and wherein, clutch (31) makes external drive source (E) be connected in transmission shaft (28) selectively; And wherein vibration damper (55; 85; 91) be contained on the clutch.
12. compressor as claimed in claim 11 is characterized in that, clutch (31) has comprised the part (35,33) of friction means effect, wherein, and link (74; 87; 93) make weight (71; 86; 92) be connected in above-mentioned part (35; 33).
13. compressor as claimed in claim 11, it is characterized in that, clutch (31) comprises the belt pulley (33) that is connected in external drive source (E), be fixed on the transmission shaft (28) inner sleeve (34) thereby, towards belt pulley and the armature (35) that rotates simultaneously by inner sleeve supporting and inner sleeve, and make armature contact belt pulley and separated electromagnetic coil (36) based on electromagnetic force, wherein, vibration damper (55; 85; 91) be contained on the belt pulley or be contained on the armature.
14., it is characterized in that link (62 as compressor as described in the claim 13; 74; 87; 93) make weight (57; 71; 86; 92) be connected in friction means, this friction means comprises belt pulley (33) or armature (35).
15. compressor as claimed in claim 14 is characterized in that, armature (35) plays friction means, and wherein, vibration damper (55) comprises pressure-producing part (62; 73; 74a), this pressure-producing part is used for weight (57; 71) flexibly be pressed on the armature.
16. compressor as claimed in claim 15 is characterized in that, link (62; 74) comprise the leaf spring that also plays the pressing means effect.
17. compressor as claimed in claim 15 is characterized in that, link (74) comprises the leaf spring, and wherein pressing means (73) comprises disc spring.
18. compressor as claimed in claim 15 is characterized in that, weight (71) is made of nonmagnetic substance.
19. compressor as claimed in claim 14 is characterized in that, armature (35) plays friction means, and wherein, weight (71) is made of magnetic material; And wherein swash when strict when electromagnetic coil, this weight is attracted to armature.
20. compressor as claimed in claim 14 is characterized in that, armature (35) plays friction means, and wherein, armature and weight (71) have peripheral surface respectively; And wherein vibration damper (55) comprises friction means (81), and these parts are contained on the surface in this peripheral surface, so that flexibly pressing another surface in this peripheral surface.
21. compressor as claimed in claim 14 is characterized in that, link (87; 93) with weight (86; 92) whole formation.
22. compressor as claimed in claim 21 is characterized in that, weight (86; 92) comprise integrally formed pressure-producing part (88; 94), this pressure-producing part is used to make the friction surface (88a of weight; 94a) be pressed against flexibly that belt pulley (33) is gone up or armature (35) on.
23. compressor as claimed in claim 22 is characterized in that, vibration damper (85; 91) comprise ring part, can form this ring part by curved plate member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98122938 CN1222646A (en) | 1997-11-28 | 1998-11-27 | Torsional vibration attenuating structure in compressor |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP329060/97 | 1997-11-28 | ||
| CN 98122938 CN1222646A (en) | 1997-11-28 | 1998-11-27 | Torsional vibration attenuating structure in compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1222646A true CN1222646A (en) | 1999-07-14 |
Family
ID=5227975
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 98122938 Pending CN1222646A (en) | 1997-11-28 | 1998-11-27 | Torsional vibration attenuating structure in compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1222646A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105917140A (en) * | 2013-12-20 | 2016-08-31 | 株式会社丰田中央研究所 | Drive power transmission device and control program therefor |
-
1998
- 1998-11-27 CN CN 98122938 patent/CN1222646A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105917140A (en) * | 2013-12-20 | 2016-08-31 | 株式会社丰田中央研究所 | Drive power transmission device and control program therefor |
| CN105917140B (en) * | 2013-12-20 | 2018-04-03 | 株式会社丰田中央研究所 | Drive power transmission apparatus and its control program |
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