CN1204741A - Torque limiting mechanism - Google Patents
Torque limiting mechanism Download PDFInfo
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- CN1204741A CN1204741A CN 98109761 CN98109761A CN1204741A CN 1204741 A CN1204741 A CN 1204741A CN 98109761 CN98109761 CN 98109761 CN 98109761 A CN98109761 A CN 98109761A CN 1204741 A CN1204741 A CN 1204741A
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Abstract
A torque limiting device for a compressor. An input shaft of the compressor is connected to the torque limiting device so that the power source driving the compressor will not be affected if abnormal conditions cause the compressor to generate an excessive load. A flexible connector is located between the power source and the compressor. The flexible connector is deformed when torque is applied to the compressor input shaft. When the applied torque exceeds a predetermined value, a spring is permitted to expand axially, which uncouples the compressor from the power source. The torque at which the device uncouples is stable and predictable.
Description
The present invention relates to a kind of torque limiting apparatus, this torque limiting apparatus is connected with a slave equipment.Thereby in particular, the present invention relates to a kind ofly can work as load when overload of breaking down in the slave equipment and causing slave equipment the device that can separate slave equipment from power source.
The open NO.8-159028 of Japanese unexamined patent has described such torque limiting apparatus, and this torque limiting apparatus is connected with a slave equipment.This device comprises a power reception unit and a belt pulley, this belt pulley and the coaxial setting of the rotating shaft of slave equipment.This belt pulley rotatably is supported on the slave equipment by a radial bearing, and is connected with power source by a belt.The power reception unit is fixed in the rotating shaft and by ball and is connected with belt pulley.Particularly, the power reception unit has some grooves, and belt pulley also has some grooves, and the quantity of the groove on its quantity and the power reception unit is corresponding.Each ball and is fixed in the corresponding a pair of groove between power reception unit and belt pulley.Belt pulley and radial bearing are by a disc spring extruding power reception unit.The rotation of belt pulley is delivered to rotating shaft by ball and power reception unit.When the load torque of slave equipment surpassed a predetermined value, ball broke from the groove of belt pulley.Therefore, belt pulley is thrown off from the power reception unit, has stoped the transmission of power.
Ball is positioned near the edge of power reception unit.Therefore, the rotation of belt pulley imposes on centrifugal force of ball.When the rotating speed of belt pulley was very high, bigger centrifugal force may make ball throw off from the groove of power reception unit and belt pulley.When even the load torque of slave equipment is lower than a predetermined value, this also can make power source throw off from slave equipment.
When power source was thrown off, the load torque value of slave equipment was by the elastic force decision of frictional force between the groove of ball and belt pulley and disc spring to torque limiting apparatus with slave equipment.In other words, when determining slave equipment, must consider friction factor between the groove of ball and belt pulley from load torque that power source is thrown off.Therefore, be difficult to make the disengagement characteristic of torque limiting apparatus to become stable.In other words, when the load torque that applies less or during greater than a predetermined value torque limiting apparatus all slave equipment is thrown off from power source.
Therefore, the purpose of this invention is to provide a kind of torque limiting apparatus, this device can be worked as the speed of slave equipment and prevent that slave equipment from throwing off suddenly when very high from power source, and has predictable.
In order to realize aforementioned and other purpose, provide a torque limiting apparatus according to purpose of the present invention, this device is given slave equipment the transmission of power from power source.This torque limiting apparatus comprises a power rotor, a driven rotor and a flexible connecting member.Power rotor provides power by power source.Driven rotor is driven by power rotor under normal state.Driven rotor is connected with slave equipment, makes driven rotor give the slave equipment transferring power, and bears the load torque from slave equipment.Flexible connecting member is connected with power rotor with driven rotor between power rotor and driven rotor, with power rotor and driven rotor links together and from power rotor to the driven rotor transmitting torque.This moment of torsion will make flexible connecting member be out of shape.The disconnection of flexible connecting member from power rotor and driven rotor when the load torque on being applied to flexible connecting member surpasses some predetermined values, thus limit the moment of torsion that is applied between power rotor and the driven rotor.
With objects and advantages of the present invention, with reference to the description of following most preferred embodiment and accompanying drawing, the present invention will be more readily understood.
Fig. 1 is a sectional drawing, and a no-clutch type variable compressor is described, this compressor has the torque limiting apparatus of a first embodiment according to the invention.
Fig. 2 is the sectional drawing of an amplification, in the explanatory drawing 1 in conjunction with the time torque limiting apparatus.
Fig. 3 is the sectional drawing of an amplification, the torque limiting apparatus when throwing off in the explanatory drawing 1.
Fig. 4 (a) is the sectional drawing of the 4a-4a line in Fig. 2.
Fig. 4 (b) is the sectional drawing of the 4b-4b line in Fig. 2.
Fig. 5 (a) is the sectional drawing of the 5a-5a line in Fig. 3.
Fig. 5 (b) is the sectional drawing of the 5b-5b line in Fig. 3.
Fig. 6 is the part sectioned view of an amplification, and a torque limiting apparatus that is in bonding state according to second embodiment of the present invention is described.
Fig. 7 is the fragmentary cross-sectional view of an amplification, the torque limiting apparatus that is in disengaged condition in the explanatory drawing 6.
Fig. 8 is the sectional drawing of the 8-8 line in Fig. 6.
Fig. 9 is the part sectioned view of an amplification, and a torque limiting apparatus that is in bonding state according to the 3rd embodiment of the present invention is described.
Figure 10 is the part sectioned view of an amplification, the torque limiting apparatus that is in disengaged condition in the explanatory drawing 9.
Figure 11 is the sectional drawing of the 11-11 line in Fig. 9.
Figure 12 is the part sectioned view of an amplification, and a torque limiting apparatus that is in bonding state according to the 4th embodiment of the present invention is described.
Figure 13 is the part sectioned view of an amplification, and the torque limiting apparatus that is in the branch disengaged condition among Figure 12 is described.
Figure 14 (a) is the sectional drawing of the 14a-14a line in Figure 12.
Figure 14 (b) is the sectional drawing of the 14b-14b line in Figure 13.
Figure 15 is the sectional drawing of an amplification, and a torque limiting apparatus that is in bonding state according to the 5th embodiment of the present invention is described.
Figure 16 is the sectional drawing of the 16-16 line in Figure 15.
Figure 17 is the sectional drawing of an amplification, and the torque limiting apparatus that is in disengaged condition among Figure 15 is described.
Figure 18 is the sectional drawing of the 18-18 line in Figure 17.
With reference to Fig. 1～5, the torque limiting apparatus of first embodiment according to the invention is described.This device uses with the variable compressor of a no-clutch type.
At first, no-clutch type variable compressor is described.
Fig. 1 has represented a no-clutch type variable compressor 21 as slave equipment.Compressor 21 comprises a cylinder body 22, a protecgulum 23 and a bonnet 25.Protecgulum 23 is fixed on the front-end face of cylinder body 22, and bonnet 25 is fixed on the ear end face of cylinder body 22 by a valve plate 24, and wherein valve plate 24 is between cylinder body 22 and bonnet 25.
A center that rotatably is supported on cylinder body 22 and protecgulum 23 as the input shaft 26 of driven rotor by a pair of radial bearing.A lip packing 28 is between input shaft 26 and protecgulum 23.
The swash plate 36 of a plate-like is supported on the input shaft 26 obliquely.Swash plate 36 has a pair of SDeflector 37, and this SDeflector is outstanding towards lug 32.SDeflector 37 is rotatable and be placed in slidably in the pilot hole 35 of support arm 34.In other words, swash plate 36 is connected on the lug 32 with a similar hinged form.SDeflector 37 allows swash plate 36 to tilt with respect to lug 32.
Each piston 30 is connected on the swash plate 36 by a pair of hemispherical piston shoes 38.When input shaft 26 rotations, swash plate 36 and input shaft 26 whole rotations.At this moment, shoe-shaped thing 38 is converted to rotatablely moving of swash plate 36 linear motion of cylinder hole 29 inner carriers 30.
Be formed centrally a valve chamber 39 in cylinder body 22, this valve chamber 39 extends along the axis of input shaft 26.Middle body at bonnet 25 and valve plate 24 forms a suction passage 40.Suction passage 40 also extends along the axis of input shaft 26.The front end of suction passage 40 is connected with valve chamber 39, and its rear end is connected to the refrigeration pipeline 41 of an outside.Refrigeration pipeline 41 comprises a condenser 42, a safety valve 43 and a vaporizer 44.
In bonnet 25, form an annular suction chamber 45.This annular suction chamber 45 is connected with valve chamber 39 by a through hole 46.Form an annular discharge side 47 around the suction chamber 45 in bonnet 25.This annular discharge side 47 is connected by the refrigeration pipeline 41 of an outlet passage 48 with the outside.
On valve plate 24 respectively with each cylinder hole 29 corresponding formation inhalation valve 49 and injection valve device 50.When lower dead centre moved, the refrigeration gas in suction chamber 45 entered cylinder hole 29 by the inhalation valve 49 of correspondence to piston 30 in corresponding cylinder hole 29 from upper dead center.When upper dead center moved, the injection valve device 50 by correspondence after the refrigeration gas in cylinder hole 29 is compressed to certain pressure was ejected into spray chamber 47 to piston in each cylinder hole 29 from lower dead centre.
When swash plate was moved to the minimum angle-of-incidence position, swash plate 36 overcame 51 to closed positions of elastic force mobile valve of spring 52.At this closing position, the opening UNICOM of valve 51 and suction passage 40.This has sealed suction passage 40, has stoped from the refrigeration pipeline 41 of outside to supply the refrigeration gas to suction chamber 45.This minimum angle-of-incidence of swash plate 36 is a bit larger tham zero degree, and limits by location valve 51 when the minimum angle-of-incidence position.
Swash plate was in the minimum angle-of-incidence position when this made even without refrigeration load, and compressor 21 still can be worked.Since compressor 21 opens and closes without clutch, so compressor 21 is a kind of no-clutch type compressors.
When swash plate 36 was positioned at an inclination maximum position, the elastic force valve 51 by spring 52 moved to the enable possition.In other words, valve 51 is removed from the opening of suction passage 40.By valve chamber 39 and intercommunicating pore 46 suction passages 40 external refrigeration pipeline 41 is communicated with suction chamber 45.This just introduces suction chamber 45 to refrigeration gas.A stopper 54 that forms on the front-end face of swash plate 36, thus this stopper 54 is supported on the inclination maximum that has limited swash plate 36 on the ear end face of lug 32.In this position of swash plate 36, compressor 21 is operated under the maximum pump discharge state.
Middle body at input shaft 26 forms a relief passage 56.This relief passage 56 has two inlets and an outlet, and wherein two inlets are opened on crank chamber 31, and exit opening is in the inside of valve 51.The inside of valve 51 is communicated with valve chamber 39 by release of pressure hole 57, and this release of pressure hole 57 forms near the wall of the valve the rearward end of valve 51.Therefore pressure in crank chamber 31 be communicated with suction chamber 45 by inside, release of pressure hole 57, valve chamber 36 and the through hole 46 of relief passage 56, valve 51.
In bonnet 25, valve plate 24 and cylinder body 22, form a supply passage 58 that is used for UNICOM's spray chamber 47 and crank chamber 31.The middle part of supply passage 58 accommodates a solenoid valve 59 in bonnet.This control valve 59 comprises a coil 60.Control valve 59 is opened passage 58 when coil 60 is energized, and the pressure in the spray chamber 47 is communicated with crank chamber 31.In this manner, controlled at the pressure in crank chamber 31.
Torque limiting apparatus will be described below.
Shown in Fig. 1,2 and 4, the outer support ring 68 of an annular is by the front end of bolt to belt pulley 65.Outer support ring 68 has the cross section of a L shaped shape.The rubber buffer 69 of an annular is bonded to the inwall of outer support ring 68.The inside support ring 70 of an annular is bonded to the inwall of rubber buffer 69.Inside support ring 70 also has the cross section of a L shaped shape.Inside support ring 70 has a boss 71, and this boss 71 stretches out towards input shaft 26.Boss 71 comprises two openings 72, these two openings be separated by 180 the degree.Outer support ring 68, rubber buffer 69 and inside support ring 70 are with belt pulley 65 rotations.
Near the front end of input shaft 26, form a step 73.A positioning work piece 74 is installed on this step 73.Positioning work piece 74 is fixed on the input shaft 26 by bolt 75.Positioning work piece 74 is therefore with input shaft 26 rotations.This positioning work piece 74 comprises a cylindrical shape part 80 and a boss 77.
Positioning work piece 74 has a pair of engagement groove 76 or rotation limiter in its back-end.Two engagement groove 76 intervals 180 degree.The boss 77 of positioning work piece 74 has a flange 78.This flange 78 is outstanding backward from the outer periphery of boss 77.This flange 78 extends towards the boss 7 of inside support ring 70.Flange 78 has a pair of release groove 79.Release groove 79 and the engagement groove 76 predetermined angle of being separated by on the direction opposite with input shaft 26 rotations.Front end at positioning work piece 74 forms a neck 81.
A restraining spring 82 or a connection set are wound on the positioning work piece 74.Spring 82 is double torsion springs, is intertwined by two parallel spring threads.Each spring thread has one first end and one second end.First end of spring thread comprises permanent locking spare 83, and this latch 83 is outstanding relatively inwards.Second end of spring thread forms a releasably locking spare 84, and is protruding along direction away from each other.The winding of spring thread makes that spring 92 shrinks when spring 82 bears load torque by input shaft 26 and positioning work piece.In other words, spring 82 is screwing springs, and under normal load condition, this spring reverses along the direction of shrinking.
When spring 82 and positioning work piece 74 are assembled on the input shaft 26, spring 82 be positioned in positioning work piece 74 around.Then, this positioning work piece 74 is fixed on the input shaft 26 by bolt 75, this positioning work piece 74 by bolt 75 along axially with a predetermined value pressure spring 82.
Permanent locking spare 83 combines with the engagement groove 76 of positioning work piece 74.This has limited the rotation of permanent locking spare 83 with respect to input shaft 26.Releasably locking spare 84 combines with the opening 72 of inside support ring 70, and with positioning work piece 74 ear end face contact.The ear end face that comprises the spring 82 of permanent locking spare 83 contacts with positioning work piece 74, and comprises that the front-end face and the neck 81 of the spring 82 of a releasably locking spare 84 separate.Spring 82 is towards the direction extruding releasably locking spare 84 of the boss 77 of positioning work piece 74.
The power of motor 67 is delivered on the input shaft 26 of compressor 21 by belt 66, belt pulley 65, outer support ring 68, rubber buffer 69, inside support ring 70, spring 82 and positioning work piece 74 in normal operation.
The operation of compressor 21 will be described below.
In state as shown in Figure 1, the coil 60 of solenoid valve 59 is energized, and supply passage 58 is closed.Therefore, supply passage 58 stops pressurized gas flowing from discharge side 47 to crank chamber 31.On the other hand, the refrigeration gas in crank chamber 31 enters suction chamber 45 by inside, release of pressure hole 57, valve chamber 39 and the intercommunicating pore 46 of relief passage 56, valve chamber 51.Pressure in the crank chamber 39 is pressed near low suction of suction chamber 45.In this state, swash plate 36 is maintained at an inclination maximum position.Therefore compressor 21 works under maximum pump discharge.
If refrigeration load reduces in this state, the temperature of the vaporizer 44 in the refrigeration pipeline 41 reduces gradually outside.When the temperature of vaporizer 44 was equal to or less than freezing temperature, coil 60 was not energized, thereby opened solenoid valve 59.Supply passage 58 offers crank chamber 31 to the pressurized gas in the discharge side 47 then.Therefore increase in crank chamber 31 internal pressures.This causes swash plate 36 to move to the minimum angle-of-incidence position from the inclination maximum position.
When in the minimum angle-of-incidence position, swash plate 36 passes through thrust bearing 53 mobile valve 51 backward.Therefore, valve 51 elastic force that overcomes spring 52 moves towards closed position from open position.When swash plate 36 during in the minimum angle-of-incidence position, valve 51 is positioned at closed position, and links with the opening of suction passage 40.Thereby valve 51 is closed suction passage 40 and has been stoped gas to flow to suction chamber 45 from external refrigeration pipeline 41.
The minimum angle-of-incidence of swash plate 36 is a bit larger tham zero degree.Therefore, though when the inclination angle of swash plate 36 for hour, the refrigeration gas in cylinder hole 29 can be injected into spray chamber 47, thus compressor 21 is worked under minimum injection rate.The refrigeration gas that is ejected into spray chamber 47 sucks crank chamber 31 by supply passage 58.Refrigeration gas in crank chamber 31 is sucked back to suction chamber 45 by relief passage 56, release of pressure hole 57, valve chamber 39 and through hole 46.Gas is inhaled into cylinder hole 29 then.In other words, when the inclination angle of swash plate 32 hour refrigeration gas still compressor 21 in, circulate.
If when swash plate 36 during in the minimum angle-of-incidence position refrigeration load increase, then the temperature in the vaporizer 44 increase gradually.When the temperature of vaporizer 44 surpassed a predetermined temperature, coil 60 was energized, thereby closes solenoid valve 59.Therefore, supply passage 58 has stoped high pressure refrigeration gas to flow to crank chamber 31 from discharge side 47.Pressure in crank chamber 31 discharges by inside, release of pressure hole 57, valve 39 and the intercommunicating pore 46 of relief passage 56, valve 51.The pressure that this has just reduced in the crank chamber 31 gradually moves to the inclination maximum position to swash plate 36 from the minimum angle-of-incidence position.
When swash plate 36 when move the inclination maximum position, spring 52 moves to open position to valve 51 from closing position.In other words, valve 51 is thrown off from the opening of suction passage 40, as shown in Figure 1.This just allows refrigeration gas to enter suction chamber 45 from the refrigeration pipeline 41 of outside.Swash plate 36 is positioned at the inclination maximum position then, and compressor 21 is worked under maximum pump discharge.
When motor 67 stopped, compressor 21 also stopped.In this state, solenoid valve 59 is opened, and swash plate 36 is worked on the minimum angle-of-incidence position.
The operation of torque limiting apparatus will be described below.
Under normal operation condition, the power of motor 67 is passed to the input shaft 26 of compressor 21 by belt 66, belt pulley 65, outer support ring 68, rubber buffer 69, inside support ring 70, spring 82 and positioning work piece 74.
If load torque does not surpass a prespecified range, and is therefore very little to the influence of motor 67 and belt pulley 66, inside support ring 70 can not make opening 72 and release groove 79 conllinear with respect to the rotation of positioning work piece 74.Under this state, load torque is owing to the torsional deflection of spring 82 reduces, and the power of motor 67 is passed to input shaft 26 continuously.
Even work under normal state when compressor, the variation of the load torque of the fluctuation generation that the differing of the variation in pressure cylinder hole 29 in, compressive load and other factors cause can not surpass the predetermined torque scope.Yet these torque ripples are owing to the torsional deflection of spring 82 reduces.
If an overload moment of torsion imposes on compressor 21, spring 82 is greatly reversed, as Fig. 3 and shown in Figure 5.Inside support ring 70 rotates with respect to positioning work piece 74, therefore, and at opening on the inside support ring 70 70 and release groove 79 conllinear on positioning work piece 74.The elastic force of spring 82 makes releasably locking spare 84 move in the release groove 79 of positioning work piece 74 from the opening 72 on the inside support ring 70 then.Thereby the transmission of power between belt pulley 65 and the input shaft 26 is interrupted.In this state, releasably locking spare 84 is maintained in the release groove 79 of positioning work piece 74 by the elastic force of spring 82, can not disturb inside support ring 70.
First embodiment has following advantage.
The load torque value of motor when compressor 21 cuts off is not to be determined by the frictional force between belt pulley 65 and the input shaft 26, but by the torsional stiffness of spring 82 and opening 72 to the angular distance the release groove 79.Load torque value when therefore, transmission of power is interrupted can be predicted.And spring 82 can not be subjected to the influence of centrifugal force.Therefore, even belt pulley 65 high speed rotating, transmission of power can not interrupted suddenly yet.
If be no more than a predetermined value by what the load torque of compressor 21 applied, the fluctuation of load torque is owing to the torsional deflection of restraining spring reduces.
Releasably locking spare 84 is made one with spring 82.This structure decrease the number of parts, therefore simple in structure.
When the transmission of power of motor 67 arrives compressor 21, spring 82 chucking positioning work pieces 74.The rear portion that comprises the spring 82 of permanent locking spare 83 contacts with positioning work piece 74.Therefore spring 82 fixedly remains on the rearward end of positioning work piece 74.On the other hand, the front end that comprises the spring 82 of releasably locking spare 84 separates with positioning work piece 74.Therefore, the load torque that is applied by compressor 21 makes spring 82 take place just to reverse.As a result, spring 74 can not be offset by relative positioning device 74, and the twisting characteristic of spring 82 is stable.Therefore the cut-out characteristic of torque limiting apparatus is stable with predictable.Therefore, the disengagement characteristic of torque limiting apparatus is stable, and measurable.In other words, torque limiting apparatus load torque value that motor 67 is cut off from compressor 21 is stable with predictable.
On positioning work piece 74, form neck 81, separate thereby handle comprises the front portion and the positioning work piece 74 of the spring 82 of releasably locking spare 84.Therefore, only need a very simple machine-tooled method just can separate the front end of spring 82 and positioning work piece 74.
Above-mentioned torque limiting apparatus is connected with the compressor 21 of the no-clutch type that has motor 67.In other words, input shaft 26 be connected with motor 67 all the time (under normal state).In a compressor with clutch, if an overload moment of torsion imposes on compressor, clutch will cut off motor from compressor.This compressor (compressor of the present invention-translator annotates) 21 does not cut off motor 67 from compressor 21 clutch.Yet when the load torque of compressor surpassed a predetermined value, above-mentioned releasing device simple in structure was thrown off motor 67 energetically from compressor 21.
Second embodiment's of the present invention description is with reference to Fig. 6～8.Below main explanation and first embodiment's difference.
Second embodiment's torque limiting apparatus has been showed in Fig. 6～8.Different with first embodiment's positioning work piece 74, second embodiment's positioning work piece does not have neck 81.Cylindrical body 80 has a constant diameter.A spring 82 is wrapped in around the positioning work piece 74.Spring 82 is the holddown springs with single spring thread.There is a constant diameter at the rear portion that comprises the spring 82 of a permanent locking spare 83, and increases gradually towards releasably locking spare 84 at the diameter of the front portion that comprises a releasably locking spare 84.In other words, spring 82 has the cross section of a taper.Therefore, the rear portion of spring 82 contacts with positioning work piece 74, and separate with positioning work piece 74 front portion.As shown in Figure 8, permanent locking spare 83 is inserted in the L shaped engagement groove 76 that forms on positioning work piece 74.Engagement groove 76 is as the rotation limiter of spring 82.
Torque limiting apparatus from Fig. 6 to Fig. 8 have almost with Fig. 1 to the same advantage of the torque limiting apparatus among Fig. 5.Fig. 6 also has following advantage to the device of Fig. 8.
The rear portion that comprises the restraining spring 82 of permanent locking spare 83 has a constant diameter, and contacts with positioning work piece 74.Therefore, when the load torque of compressor was applied on the spring 82, spring 82 was reversed opposing positioning work piece 74 and is shunk.This has guaranteed that spring 82 combines with rigidity between the positioning work piece 74.On the other hand, comprise that the front portion of the spring 84 of releasably locking spare 84 has the diameter that increases gradually towards releasably locking spare 84, thereby separate with positioning work piece 74.This reverses for spring 82 according to the load torque generation of compressor freedom, if necessary, spring can move axially.As the device in first embodiment, spring can not be with respect to positioning work piece 74 skew, and the twisting characteristic of restraining spring 82 is stable with predictable.In other words, torque limiting apparatus load torque value that motor 67 is cut off from compressor is stable with predictable.
Engagement groove 76 L shaped on the permanent locking spare on the spring 82 83 and positioning work piece 74 combines.Spring 82 is easy to compress certain amount during installation.In other words, releasably locking spare 84 combines with the opening 72 of inside support ring 70.Then, permanent locking spare 83 combines simply with the engagement groove 76 of L shaped shape, thus the certain amount of pressure spring 82.
The 3rd embodiment's of the present invention description is with reference to Fig. 9～11.Below the main difference of describing with first and second embodiment.
The 3rd embodiment's torque limiting apparatus has spring 82 and positioning work piece 74 of a single spring thread.As shown in FIGS. 9 to 11, positioning work piece 74 has an engagement groove 76 as the spring rotational limit stop.An elastic component 87 is installed in the engagement groove 76.Elastic component 87 is for example made with rubber.Elastic component 87 is between the step 73 of the permanent locking spare 83 of spring 82 and input shaft 26.Step 73 forms the inwall of rotational limit stop.When positioning work piece 74 is extruded when being installed on the input shaft 26, the amount that the permanent locking spare 83 of spring 82 and step 73 compression elastic pieces 87 are certain.
As in first embodiment, if when for example resembling the load torque overload that compressor 21 applies by slave equipment, spring 82 is greatly reversed, as shown in figure 10.This has caused release groove 79 conllinear on opening 72 and the positioning work piece 74 on the inside support ring 70.The elastic force of elastic component 87 helps releasably locking spare 84 is separated from opening 72, thereby releasably locking spare 84 is combined with release groove 79.
The 3rd embodiment has following advantage.
Torque limiting apparatus from Fig. 9 to Figure 11 have almost with first and second embodiment in the same advantage of torque limiting apparatus.Fig. 9 also has following advantage to the device of Figure 11.
When load torque transships, thereby elastic component 87 is released the axial direction extrusion spring 82 along input shaft 26.Therefore, if the axial rigidity of spring 82 is enough big, can not be compressed to required amount, elastic component 87 has guaranteed correct disconnection action so.
The 4th embodiment's of the present invention description is with reference to Figure 12～14.Below the main difference of describing with first to the 3rd embodiment.
The 4th embodiment's torque limiting apparatus has spring 82 and positioning work piece 74 of a single spring thread.Shown in Figure 12 and 14 (a), positioning work piece 74 has an engagement groove 76 as the rotational limit stop of spring 82.This engagement groove 76 is spiral-shaped with respect to input shaft 26 one of formation.The permanent locking spare 83 of spring 82 combines with the front end of engagement groove 76.When for example resembling compressor 21 for slave equipment from the transmission of power of power source, the load torque that slave equipment applies is divided into component and component along input shaft 26 directed forward of sensing direction opposite with the sense of rotation of input shaft 26 by oblique engagement groove 76.The component that points to the direction opposite with the sense of rotation of input shaft 26 makes spring 82 reverse, and along the component of input shaft 26 directed forward forward extrusion spring 82 the rear end or towards the far-end extruding of positioning work piece 74.
As in first embodiment, if the load torque of an overload imposes on compressor 21, spring 82 is greatly reversed, shown in Figure 13 and 14 (b).This causes release groove 79 conllinear on opening 72 and the positioning work piece 74 on the inside support ring 70.The axial thrust load that acts on the spring 82 is removed releasably locking spare 84 from opening 72, thereby makes releasably locking spare 84 combine with release groove 79.At this moment, the load torque of overload is released.Therefore, the rearward end that comprises the spring 82 of permanent locking spare 83 expands from positioning work piece 74 radially outwards.This has caused permanent locking spare 83 to move forward (towards the left direction of Figure 14 (b)) along oblique engagement groove 76.As a result, whole spring 82 moves forward.Therefore spring 82 can not disturb inside support ring 70.
Figure 12 to the torque limiting apparatus of Figure 14 have almost with first to the 3rd embodiment in the same advantage of torque limiting apparatus.Figure 12 also has following advantage to the device of Figure 14.
When load torque transshipped, combining between spiral-shaped engagement groove 76 and the spring 82 produced one along the input shaft 26 axial directions power of goring push spring 82 forward.Therefore, can not make length of spring compressed arrive required amount if the axial rigidity of spring 82 is enough big, the device that is used to move axially spring 82 can be realized by a simple structure.And, do not need extra parts to come mobile spring 82.This has reduced the part count of torque limiting apparatus.
The 5th embodiment's of the present invention description is with reference to Figure 15～18.Below the main difference of describing with first to the 4th embodiment.
Shown in Figure 15 and 16, this embodiment's input shaft 26 comprises a small diameter portion 90.The function of this small diameter portion 90 is the connection sets as a common transmitting torque.Form a pair of splined section 91,92 respectively in the front-end and back-end of this small diameter portion 90.This small diameter portion 90 and splined section 91,92 are covered by a cylindrical shape cap 93.This cylindrical shape cap 93 has a boss 94, and this boss 94 inwardly stretches out from the rear end of cylindrical shape cap 93.This boss 94 is fixed on the splined section 91 of back.Cylindrical shape cap 93 is therefore with input shaft 26 rotations.The claw 93 of L shaped shape (having four in this embodiment) extends from the front end of cylindrical shape cap 93, thereby can open along this claw on the sense of rotation of driving shaft 26.
A plate-like connecting plate 96 is fixed on the preceding splined section 92 of input shaft 26.This connecting plate 96 can endwisely slip with respect to input shaft 26.A pad 98 is fixed on the input shaft 26 by a bolt 97, separates from input shaft 26 to prevent connecting plate 96.A spring 99 extends between the boss 94 of connecting plate 9 and cylindrical shape cap 93.This spring 99 is compressed certain amount along the axial direction of input shaft 26.
Connecting plate 96 has arcuate socket 100 (having four in this embodiment).Each arcuate socket 100 is corresponding with the claw 95 of cylindrical shape cap 93.This connecting plate 96 also has double wedge (having seven in this embodiment).Double wedge 101 stretches out from the peripheral radial of connecting plate 96, the angle that each interval is certain.
A support cylinder body 102 is fixed on the inwall of rubber buffer 69, and this support cylinder body 102 comprises double wedge 103 (having seven in this embodiment), and this double wedge 103 stretches out forward.Each double wedge 103 is corresponding with a double wedge 101 of connecting plate 96.
Under normal operation, the claw 95 of cylindrical shape cap 93 is inserted in the arcuate socket 100, and combines with arcuate socket 100, shown in Figure 15 and 16.The double wedge 101 of connecting plate 96 combines with the double wedge 103 that supports cylinder body 102.Therefore, the moment of torsion of power source is delivered on the input shaft 26 by belt 66, belt pulley 65, outer shroud 68, rubber buffer 69, support cylinder body 102, connecting plate 96 and cylindrical shape cap 93.
If slave equipment for example resembles compressor 21 and applies an overload moment of torsion, the small diameter portion 90 of input shaft 26 is reversed.This makes rear portion splined section 91 with respect to preceding splined section 92 rotations, shown in Figure 17,18.Therefore, the claw 95 of cylindrical shape cap 93 produces displacement with respect to arcuate socket 100 along the direction with the switched in opposite of input shaft 26.Therefore claw 95 is separated in arcuate socket 100.Then, the elastic force of spring 99 axially moves forward connecting plate 96 along input shaft 26.Therefore, the double wedge 101 of connecting plate 96 is separated from the double wedge 103 that supports cylinder body 102, and therefore 26 transmission of power is interrupted from belt pulley 65 to input shaft.In this case, connecting plate 96 is close to pad 98 by the extruding by the elastic force of spring 99.Therefore, connecting plate 96 can not interfere with each other with cylindrical shape cap 93 and supporting post 92.
The 5th embodiment has following advantage.
When the load torque of compressor was increased to the level that may destroy motor 67, the small diameter portion 90 of input shaft 26 was reversed.This just connecting plate 96 from cylindrical shape cap 93 separately.In this state, the elastic force of spring 99 moves axially connecting plate 96 along input shaft 26, therefore connecting plate 96 is separated from supporting post 102.Therefore, 21 transmission of power is interrupted from motor 67 to compressor.The overload moment of torsion of compressor 21 can not be delivered to motor 67.
Therefore, the load torque value during from motor 67 cut-out compressors 21 is not the frictional force that is decided by between belt pulley and the input shaft, but is decided by the torsional stiffness of small diameter portion 90 or the binding capacity of claw 95 and arcuate socket 100.Therefore, the cut-out characteristic of this device is stable with predictable.And small diameter portion 90 can not be subjected to the influence of centrifugal force.Therefore, even belt pulley 65 high speed rotating, transmission of power can not interrupted suddenly yet.
The fluctuation of load torque that surpasses the compressor 21 of predetermined load torque value reduces owing to the torsional deflection of small diameter portion 90.
The present invention can also realize with following form.
Number at the spring thread of first embodiment's medi-spring 82 can change.The number of spring thread for example can be 1,3,4,5 or 6.
The decreased number to 1 of spring thread can be simplified the structure of this device.Increase the number to 3 of spring thread or can prevent further when transmitting the power of belt pulley 65 that more at most positioning work piece 74 from tilting, therefore the slow-roll stabilization of feasible axle 26.
Number at the spring thread of second to four embodiment's medi-spring 82 can change.The number of spring thread for example can be 2,3,4,5 or 6.
The number that increases spring thread can prevent that when transmitting the power of belt pulley 65 positioning work piece 74 from tilting, and therefore makes the slow-roll stabilization of belt pulley.
Can twine along such direction at each spring thread of first to the 4th embodiment's medi-spring 82: relaxing of spring when the load torque that is subjected to from slave equipment.
In first and second embodiments, the permanent locking spare 83 of spring 82 can omit.
In the 3rd embodiment, elastic component 87 can replace with the spring of a helical spring or other type.
In third and fourth embodiment, spring 82 axially can have a constant diameter along it, and forms a neck 81 on positioning work piece 74, and its position is corresponding with the front end of spring 82.
In the 5th embodiment, the number of the number of claw 95 and arcuate socket 100 for example can change into 2,3,6,7 or 8.
In the 5th embodiment, the number of double wedge 101,103 for example can change into 2,3,4,5,6,8,9 or 10.
The aforesaid structure of the structure that these are alternative and the present invention has same advantage.
Therefore, example of the present invention and embodiment should be considered to illustrative and not restrictive.The details that the invention is not restricted to provide can be made amendment in the scope of additional claims.
Claims (28)
- Claims1. one kind from the torque limiting apparatus of power source to the slave equipment transferring power, and comprising: a power rotor (65) provides power by power source; A driven rotor (26) is driven by power rotor (65) under normal state, and driven rotor (26) is connected with slave equipment, makes driven rotor give the slave equipment transferring power, and bears the load torque from slave equipment; A flexible connecting member (82), this flexible connecting member is positioned between power rotor (65) and the driven rotor (26), and be connected with power rotor with driven rotor, so that thereby power rotor and driven rotor are linked together from power rotor to the driven rotor transmitting torque, wherein, this moment of torsion will make flexible connecting member (82) be out of shape, and the disconnection of flexible connecting member from power rotor and driven rotor when the moment of torsion on being applied to flexible connecting member surpasses some predetermined torque value, thereby limit the moment of torsion that is applied between power rotor and the driven rotor.
- 2. according to the torque limiting apparatus of claim 1, wherein, flexible connecting member is a torsion spring (82), this torsion spring is wrapped in driven rotor (26) on every side, this spring has a releasably locking spare (84) and a permanent locking spare (83), this releasably locking spare is used for separably in conjunction with power rotor and driven rotor, and this permanent locking spare is used for forever connecting another of power rotor and driven rotor.
- 3. according to the torque limiting apparatus of claim 2, wherein, driven rotor has an engagement groove (76), is used to hold permanent locking spare.
- 4. according to the torque limiting apparatus of claim 3, wherein, power rotor and driven rotor are coaxial, power rotor can rotate with respect to driven rotor, power rotor has an opening (72), be used to hold releasably locking spare (84), wherein, the wall of opening (72) combines with releasably locking spare, wherein opening allows releasably locking spare (84) to throw off from opening (72) when the moment of torsion that imposes on flexible connecting member surpasses certain value, wherein driven rotor has a release groove (79), when throwing off, releasably locking spare is used to hold the releasably locking spare (84) of throwing off from opening from opening, release groove and opening are at a distance of a predetermined angle, and this angle under normal circumstances records around the axle of driven rotor.
- 5. according to the torque limiting apparatus of claim 4, wherein, driven rotor has a pair of coaxial ring (68,70), they are all coaxial with input shaft 26, and wherein, these rings flexibly are connected to each other by an elastic material (69), wherein, opening (72) is positioned in the inner part one of ring (68,70).
- 6. according to the torque limiting apparatus of claim 2, wherein, helical spring (82) reacts to the load torque from slave equipment, extruding driven rotor and shrinking.
- 7. according to the torque limiting apparatus of claim 2, wherein, helical spring (82) has one and is positioned near the releasably locking spare (84) first portion and one and is positioned near the permanent locking spare (83) second portion, this first end separates with driven rotor, and the spring of this second end is connected with driven rotor (26).
- 8. according to the torque limiting apparatus of claim 7, wherein, driven rotor (26) has a neck, and the diameter of this neck is less, and wherein, this neck is corresponding with the axial position of helical spring first portion.
- 9. according to the torque limiting apparatus of claim 2, wherein, helical spring (82) has a plurality of independently spring threads, and each spring thread is wrapped on the driven rotor (26).
- 10. according to the torque limiting apparatus of claim 4, wherein, driven rotor comprises a rotating shaft (26) with first end, a positioning work piece (74) is fixed on this first end, positioning work piece (74) has a boss (77), and the diameter of this boss is greater than the diameter of rotating shaft (26), wherein, go up formation engagement groove (76) in rotating shaft (26), go up at boss (77) and form release groove (72).
- 11. torque limiting apparatus according to claim 10, wherein, helical spring (82) is compressed between boss (77) and the engagement groove (76) usually, and when load torque surpasses certain value, rotating shaft makes the axial conllinear of release groove (79) of opening (72) and boss of power rotor with respect to the rotation of power rotor, and this causes releasably locking spare (84) to throw off and enter in the release groove from opening under the effect of helical spring axial expansion power.
- 12. according to the said torque limiting apparatus of claim 11, also comprise an elastic component (87), this elastic component (87) is positioned at engagement groove (76), is used for auxiliary ground towards boss extrusion spiral spring (82).
- 13. torque limiting apparatus according to claim 1, wherein, power rotor (65) and driven rotor (26) are coaxial, the torsional deflection of flexible connecting member when power rotor is applied to flexible connecting member according to moment of torsion (90) and rotating with respect to driven rotor, wherein in this torque limiting apparatus, comprise a spring (99), this spring (99) is coaxial with power rotor and driven rotor, at normal operation situation lower spring by axial compression, wherein spring (99) is released and axial expansion when the moment of torsion that imposes on flexible connecting member surpasses certain torque value, and the axial expansion of its medi-spring (99) makes power rotor and driven rotor throw off.
- 14. torque limiting apparatus according to claim 1, wherein, flexible connecting member (82) is a torsion spring that is wrapped on the driven rotor (26), this spring has a releasably locking spare (84) and at an other end one permanent locking spare (83) is arranged at the one end, and this permanent locking spare is used for combining with driven rotor (26).
- 15. compressor, comprise a housing (22,23,25), one by housing (22,23,25) input shaft (26) that rotatably supports, a swash plate (36) that is mounted obliquely within on the input shaft (26), one is connected to articulated mounting (34 on the swash plate (36) to input shaft (26), 35,37) and one at housing (22,23,25) piston (30) that can be reciprocating in the cylinder hole (29) that forms in, wherein, freeze according to the to-and-fro motion of the piston suction of gas of compressor, compression and discharge, wherein, by swash plate rotatablely moving of input shaft (26) is converted into the to-and-fro motion of piston (30), this compressor comprises: a power rotor (65), provide power by power source, wherein power rotor (65) rotatably is supported on housing (22,23,25) on, wherein input shaft (26) is under normal circumstances driven by a power rotor (65); AndA flexible connecting member (82), this flexible connecting member is positioned between power rotor (65) and the input shaft (26), and be connected with power rotor with input shaft, so that thereby power rotor and input shaft are linked together from power rotor to the input shaft transmitting torque, wherein, this moment of torsion makes flexible connecting member (82) distortion, and the disengagement of flexible connecting member (82) from power rotor (65) and input shaft (26) when the moment of torsion on being applied to flexible connecting member (82) surpasses some predetermined torque value, thereby restriction is applied to the moment of torsion between power rotor (65) and the input shaft (26).
- 16. according to the said compressor of claim 15, wherein, flexible connecting member is a torsion spring (82), this torsion spring is wrapped in input shaft (26) on every side, this spring has a releasably locking spare (84) and a permanent locking spare (83), this releasably locking spare is used for being connected to separably power rotor and input shaft one, and this permanent locking spare is used for power rotor and input shaft are forever linked together.
- 17. according to the compressor of claim 16, wherein, input shaft comprises an engagement groove (76), is used to hold permanent locking spare.
- 18. compressor according to claim 17, wherein, power rotor (65) and input shaft (26) are coaxial, power rotor can rotate with respect to input shaft, power rotor has an opening (72) that is used to hold releasably locking spare (84), wherein, the wall of opening (72) combines with releasably locking spare (84), wherein this opening allows releasably locking spare to throw off from opening when the moment of torsion that imposes on flexible connecting member surpasses certain value, wherein input shaft (26) has a release groove (79), after throwing off, releasably locking spare is used to hold releasably locking spare (84) from opening (72), release groove and opening be a predetermined angle at interval, and this angle under normal circumstances records around the driven rotor axle.
- 19. compressor according to claim 18, wherein, power rotor (65) has a pair of coaxial ring (68,70), they are all coaxial with driven rotor (26), wherein, these rings flexibly are connected to each other by an elastic material (69), wherein, opening (72) is positioned in the inner part one of ring (68,70).
- 20. according to the compressor of claim 16, wherein, helical spring (82) reacts to the load torque from compressor, extruding driven rotor and shrinking.
- 21. compressor according to claim 16, wherein, helical spring (82) has one and is positioned near the releasably locking spare (84) first portion and one and is positioned near the permanent locking spare (83) second portion, this first portion separates with input shaft, and the spring of this second portion is connected with input shaft (26).
- 22. according to the compressor of claim 21, wherein, input shaft (26) has a neck, this neck has a less diameter, and wherein, this neck is corresponding with the axial position of helical spring first portion.
- 23. according to the compressor of claim 16, wherein, helical spring (82) has a plurality of independently spring threads, each spring thread is wrapped on the input shaft (26).
- 24. compressor according to claim 18, wherein, input shaft (26) comprises one first end, a positioning work piece (74) is fixed on this first end, positioning work piece (74) has a boss (77), the diameter of this boss wherein, is gone up formation release groove (72) at boss (77) greater than the diameter of input shaft (26).
- 25. compressor according to claim 24, wherein, helical spring (82) is compressed between boss (77) and the engagement groove (76) usually, and when moment of torsion surpasses certain value, relatively rotating between input shaft and power rotor makes the axial conllinear of release groove (79) of opening (72) and boss of power rotor, and this causes releasably locking spare (84) to throw off and enter in the release groove from opening under the axial expansion power effect of torsion spring.
- 26. according to the compressor of claim 25, also comprise an elastic component (87), this elastic component (87) is positioned at engagement groove (76), is used for auxiliaryly towards boss extruding torsion spring (82).
- 27. according to the said compressor of claim 14, wherein, power rotor (65) and input shaft (26) are coaxial, the torsional deflection of flexible connecting member (90) when power rotor imposes on flexible connecting member (90) according to moment of torsion and rotating with respect to input shaft, wherein in this torque limiting apparatus, comprise a spring (99), this spring (99) is coaxial with power rotor (65) and input shaft (26), at normal operation situation lower spring (99) by axial compression, wherein spring (99) is released and axial expansion when the moment of torsion that imposes on flexible connecting member surpasses certain torque value, and the axial expansion of its medi-spring (99) makes power rotor throw off from input shaft.
- 28. according to the said compressor of claim 14, wherein, flexible connecting member (82) is a torsion spring that is wrapped on the input shaft (26), this spring has a releasably locking spare (84) and has permanent locking spare (83) at an other end at the one end, and this releasably locking spare is used to engage this permanent locking spare of power rotor (65) and is used for combining with input shaft is permanent.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98109761 CN1204741A (en) | 1997-03-24 | 1998-03-23 | Torque limiting mechanism |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP69797/97 | 1997-03-24 | ||
| CN 98109761 CN1204741A (en) | 1997-03-24 | 1998-03-23 | Torque limiting mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1204741A true CN1204741A (en) | 1999-01-13 |
Family
ID=5220059
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 98109761 Pending CN1204741A (en) | 1997-03-24 | 1998-03-23 | Torque limiting mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1204741A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102144108A (en) * | 2008-05-30 | 2011-08-03 | 马伊纳输电机构有限公司 | Safety coupling for the transmission of rotary motion |
| CN103557139A (en) * | 2013-10-15 | 2014-02-05 | 浙江鸿友压缩机制造有限公司 | Oilless compressor with capacity difference type rotation limiting mechanism |
| CN107191589A (en) * | 2017-07-25 | 2017-09-22 | 金陵科技学院 | A kind of machine driving is with blind multi-turn helical flute resiliency compressible torque damper |
| CN107314055A (en) * | 2017-08-31 | 2017-11-03 | 芜湖禾丰离合器有限公司 | A kind of Spring-type one-way clutch |
| CN112005026A (en) * | 2018-06-13 | 2020-11-27 | 舍弗勒技术股份两合公司 | Belt pulley decoupler |
| CN112334351A (en) * | 2018-07-24 | 2021-02-05 | 博格华纳公司 | Torque limiting coupling for motor shaft |
-
1998
- 1998-03-23 CN CN 98109761 patent/CN1204741A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102144108A (en) * | 2008-05-30 | 2011-08-03 | 马伊纳输电机构有限公司 | Safety coupling for the transmission of rotary motion |
| CN102144108B (en) * | 2008-05-30 | 2014-10-29 | 马伊纳输电机构有限公司 | Safety coupling for the transmission of rotary motion |
| CN103557139A (en) * | 2013-10-15 | 2014-02-05 | 浙江鸿友压缩机制造有限公司 | Oilless compressor with capacity difference type rotation limiting mechanism |
| CN103557139B (en) * | 2013-10-15 | 2016-05-04 | 浙江鸿友压缩机制造有限公司 | A kind of oilless (oil free) compressor with tolerance formula limit rotation mechanism |
| CN107191589A (en) * | 2017-07-25 | 2017-09-22 | 金陵科技学院 | A kind of machine driving is with blind multi-turn helical flute resiliency compressible torque damper |
| CN107314055A (en) * | 2017-08-31 | 2017-11-03 | 芜湖禾丰离合器有限公司 | A kind of Spring-type one-way clutch |
| CN112005026A (en) * | 2018-06-13 | 2020-11-27 | 舍弗勒技术股份两合公司 | Belt pulley decoupler |
| CN112334351A (en) * | 2018-07-24 | 2021-02-05 | 博格华纳公司 | Torque limiting coupling for motor shaft |
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