CN101328872B - Picking pump of water jet loom - Google Patents
Picking pump of water jet loom Download PDFInfo
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- CN101328872B CN101328872B CN2008101253702A CN200810125370A CN101328872B CN 101328872 B CN101328872 B CN 101328872B CN 2008101253702 A CN2008101253702 A CN 2008101253702A CN 200810125370 A CN200810125370 A CN 200810125370A CN 101328872 B CN101328872 B CN 101328872B
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Abstract
The present invention discloses a jet pump which is suitable to be used in a water spraying loom that picks the abb through the water injected from the picking nozzle, and the jet pump activates the plunger piston with the spring force of the spiral spring and pumps the water to the picking nozzle. The picking pump is provided with a base spring base, a movable spring base, a supplementary spring and a deamplification force generating part. The movable spring base is jointed to one end of the spiral spring. The supplementary spring is provided between the base spring base and the movable spring base. The deamplification force generating part generates deamplification force relative to the moving of the movable spring base.
Description
Technical field
The present invention relates to utilize helical spring spring force to make plunger action and with the picking pump of water to the water jet loom of Weft insertion nozzle force feed.
Background technique
As the picking pump of hydraulic pressure being delivered to the water jet loom in the Weft insertion nozzle, the general for example disclosed plunger pump in real fair 7-26381 communique that uses.In this picking pump,, make plunger to-and-fro motion in cylinder by possessing the cam mechanism and the helical spring synergy of the cam that rotates synchronously with loom.In the rotation by cam plunger being overcome under the situation that helical spring spring force moves in cylinder is drawn into water in the picking pump, under the situation that plunger is moved in cylinder, the water in the picking pump is spued and spray water spray from Weft insertion nozzle.By this water spray weft yarn is carried in the opening of warp thread.
For the preferred water jet pressure of the running of water jet loom waveform is the waveform that the waveform Go shown in the solid line of Fig. 4 C descends behind the water injection beginning like that at once smoothly.But, in using helical spring picking pump, when the water injection beginning or water spray excessive helical spring elastic vibration take place when finishing.And then if make loom with specific rotational speed action, then helical spring natural vibration synchronously, produces violent helical spring vibration with the action (action that plunger is moved to the direction that sucks water) of cam intermittently.Helical spring vibration transfer is like this given plunger, thereby produces pressure oscillation (pressure pulsation) in the high pressure water that spues.The waveform Ge that dot and dash line is represented among Fig. 4 C results from the example of change of pressure waveform of helical spring vibration.Such pressure pulsation makes the speed fluctuation of water spray, and the speed fluctuation of water spray brings obstacle for the picking of weft yarn.
In above-mentioned communique,, disclose or between helical spring end and spring carrier, be provided with the vibration damping sheet of thin sheet form or helical spring has been implemented resin-coated structure as the structure that is used for suppressing helical spring vibration.Change by the elasticity of utilizing above-mentioned vibration damping sheet or resin-coated thickness and to absorb helical spring vibration.
But the elasticity variable quantity of above-mentioned vibration damping sheet or resin-coated thickness is very little.Therefore, enough vibration suppressioning effects can not be obtained, the pressure pulsation of high pressure water can not be fully suppressed.
Summary of the invention
The objective of the invention is to suppress effectively the pressure pulsation of the high pressure water that spues from the picking pump that uses helical spring water jet loom.
In order to achieve the above object, in a technological scheme of the present invention, provide a kind of be adapted at by the water that sprays from Weft insertion nozzle with use the water jet loom of weft yarn picking, by utilize helical spring spring force make plunger action, with the picking pump of water to the Weft insertion nozzle force feed.Picking pump possesses basic spring seat, fluid spring seat, auxiliary spring and deamplification force generating part.The fluid spring seated connection is combined on the above-mentioned helical spring end.Above-mentioned auxiliary spring is located between above-mentioned basic spring seat and the above-mentioned fluid spring seat.Above-mentioned deamplification force generating part is with respect to the mobile generation damping force of above-mentioned fluid spring seat.
Description of drawings
Figure 1A is the figure that expression comprises the picking pump structure of relevant the 1st mode of execution of the present invention.
Figure 1B is the sectional view of the pump of Figure 1A.
Fig. 1 C is the partial enlarged drawing of the pump of Figure 1B.
Fig. 2 is the schematic representation of mechanical model of the pump of expression Figure 1B.
Fig. 3 is the plotted curve of frequency characteristic of spring system of the pump of expression Figure 1B.
Fig. 4 A is the plotted curve of variation of water jet pressure of the pump of expression Figure 1B.
Fig. 4 B is the plotted curve of variation of representing the water jet pressure of pump in the past.
Fig. 4 C is the plotted curve of the variation of the desirable water jet pressure of expression.
Fig. 5 is the plotted curve that the pump of expression Figure 1B reaches the variation of pump pulsation rate separately in the past.
Fig. 6 is the sectional view of the pump of relevant the 2nd mode of execution of the present invention of expression.
Fig. 7 is the local Zoom Side sectional view of the pump of relevant the 3rd mode of execution of the present invention of expression.
Fig. 8 A is the sectional view of the pump of relevant the 4th mode of execution of the present invention of expression.
Fig. 8 B is the sectional view along the 8B-8B line of Fig. 8 A.
Fig. 9 A is the sectional view of the pump of relevant the 5th mode of execution of the present invention of expression.
Fig. 9 B is the sectional view along the 9B-9B line of Fig. 9 A.
Figure 10 A is the sectional view of the pump of relevant the 6th mode of execution of the present invention of expression.
Figure 10 B is the sectional view along the 10B-10B line of Figure 10 A.
Figure 10 C is the partial enlarged drawing of Figure 10 A.
Embodiment
Below, based on the 1st mode of execution that Fig. 1～the present invention is specialized in Fig. 5 explanation.
Shown in Figure 1A, on Weft insertion nozzle 11, be connected with picking pump 12 via discharge pipe 13.Picking pump 12 will float water in the box 14 and pick up via suction pipe 15 and spue to discharge pipe 13.
Shown in Figure 1B, at pump case 16 internal fixation of the barrel shape of pump 12 cylinder 17 that forms water chamber is arranged, in cylinder 17, contain plunger 18 slidably.Plunger 18 moves to suction action direction (toward moving direction) for water is sucked in pump case 16, for the water in the pump case 16 being spued and moving to disgorging motion direction (direction of reversing).In Figure 1B, the suction action direction is the direction in left side, and the disgorging motion direction is the direction on right side.
On plunger 18, be mounted with spring seat device (ス プ リ Application グ シ one ト) 19, on the inner peripheral surface of pump case 16, twist and closed spring compressor 20.Spring compressor 20 comprises the tube portion 201 and the spring seat 202 of twisting on the inner peripheral surface that is combined in pump case 16.Spring compressor 20 is fixed on the pump case 16 by the fastening of lock-nut 21.Spring seat device 19 comprises a portion 191 and spring seat 192.Between the spring seat 202 of the spring seat 192 of spring seat device 19 and spring compressor 20, dispose helical spring 22, fluid spring carrier 23 and a plurality of disc spring 24.Helical spring 22 has as the 1st end 221 of the end of the suction action direction side of plunger 18 with as the 2nd end 222 of the end of the disgorging motion direction side of plunger 18.Fluid spring carrier 23 is bonded on the 1st end 221 of helical spring 22.Fluid spring carrier 23 and spring seat 202 are configured near the 1st end 221 of helical spring 22.
A plurality of disc springs 24 constitute and are located at fluid spring carrier 23 and as the auxiliary spring 25 between the spring seat 202 of basic spring seat.The spring constant of auxiliary spring 25 is bigger than the spring constant of helical spring 22.
If change spring compressor 20 is with respect to the position that is screwed into of pump case 16, then the spring force of helical spring 22 is changed.If spring compressor 20 is deepened, then the spring force grow of helical spring 22 with respect to the position that is screwed into of pump case 16.If spring compressor 20 is shoaled with respect to the position that is screwed into of pump case 16, then the spring force of helical spring 22 dies down.
On pump case 16, be formed with suction port 161 and discharge opening 162, between suction port 161 and discharge opening 162, be formed with water chamber 163.Between water chamber 163 and suction port 161, be provided with safety check 31, between water chamber 163 and discharge opening 162, be provided with safety check 32.On suction port 161, connect suction pipe 15, on discharge opening 162, connecting discharge pipe 13.
Shown in Figure 1A, cam 27 is installed at the live axle 26 that obtains rotary driving force from loom drive motor (diagram slightly).Rotatably mounted cam lever 28 on the fulcrum 281 that sets abreast with live axle 26.Cam lever 28 can be via cam follower 282 and cam 27 contact separations.By with certain angular velocity to the cam 27 of the direction of the arrow R of Figure 1A rotation, with helical spring 22 synergies of pump 12, make cam lever 28 swings.
On cam lever 28, link via the plunger 18 of joint 29 with pump 12.By the swing of cam lever 28, make plunger 18 and spring seat device 19 to-and-fro motion integratedly.
In Figure 1A, be that the center is curled up direction left and rotated if the rotating force by cam 27 makes cam lever 28 with fulcrum 281, then the plunger 18 of pump 12 and spring seat device 19 overcome helical spring 22 spring force and toward moving, promptly mobile from right to left in Figure 1B.Spring seat device 19 toward moving action with helical spring 22 compressions, a certain amount of water being drawn in the water chamber 163 via suction pipe 15 from floating box 14 of plunger 18 toward action.In that safety check 31 is opened water is drawn in the water chamber 163 during in, safety check 32 cuts out.Thereby the water in the discharge pipe 13 can not flow backwards to water chamber 163.
If cam follower 282 is crossed the maximum diameter position N of the camming surface 271 of cam 27, then cam follower 282 leaves from camming surface 271.As a result, plunger 18 is subjected to the recuperability of helical spring 22, with the pressurization of the water in the water chamber 163.If the water in the water chamber 163 is pressurized, then safety check 31 cuts out, and safety check 32 is opened.The water of the pressurization in the water chamber 163 via discharge pipe 13 by to nozzle 11 force feeds.Sprayed from nozzle 11 by the water of force feed, weft yarn Y is inserted in the opening of warp thread (diagram slightly).If the cam follower 282 that leaves from the camming surface 271 of cam 27 is connected on the camming surface 271 or cam lever 28 is connected on the retainer 30 of the water yield restriction usefulness that spues of other setting, the water of then 1 circulation (weft yarn Y by picking during) sprays end.
Shown in Fig. 1 C, fluid spring carrier 23 comprises the fluid spring seat 231 of ring flat-plate shape and is positioned at tube portion 33 on the periphery of fluid spring seat 231.Fluid spring seat 231 forms with tube portion 33.Tube portion 33 as cartridge unit is embedded in the portion 201 slidably.On the inner peripheral surface 203 of the tube portion 201 of spring compressor 20, be formed with groove 34.Groove 34 extends around a week along above-mentioned inner peripheral surface 203.On spring compressor 20, be formed with inlet 35, so that it is communicated with groove 34.Inlet 35 is closed by threaded cap 36, is filled with viscous fluid Q in groove 34.Viscous fluid Q is injected in groove 34 from inlet 35.Between the inner peripheral surface of the outer circumferential face 331 of tube portion 33 and spring compressor 20, be provided with pair of seal rings 37,38. Seal ring 37,38 prevents that viscous fluid Q is from the outflow between the inner peripheral surface 203 of the outer circumferential face 331 of tube portion 33 and tube portion 201.As viscous fluid Q, use aqueous seal ring of for example non-dryness or viscous silicone fluid.
If fluid spring seat 231 (fluid spring carrier 23) moves, then between viscous fluid Q and tube portion 33, produce friction, effect has frictional force on fluid spring carrier 23.Tube portion 201, tube portion 33 and viscous fluid Q constitute the deamplification force generating part that produces damping force that moves by fluid spring seat 231.Below, will make frictional attenuation power by fricative damping force note, will make frictional attenuation power generating unit by the deamplification force generating part note of friction-produced damping force.
The tube portion 201 of auxiliary spring 25, spring compressor 20, tube portion 33 and viscous fluid Q constitute the attenuating device 39 of the vibration amplitude decay that makes helical spring 22.
Fig. 2 represents the mechanical model of the basic structure of pump 12.This mechanical model is about comprising the structure of helical spring 22 and attenuating device 39.Mechanical model shown in Figure 2 is with the elastomeric characteristic of conduct of the approximate helical spring 22 of two serial spring K1, K2 not having quality and is similar to the 1 degrees of freedom-particle model as the characteristic of quality of helical spring 22 with the particle M that concentrates on central authorities.In addition, if consider closely, then helical spring 22 has the vibration characteristics of infinite degrees of freedom, but in the action of loom, show 1 pattern of two ends constraint of low order significantly, even the higher modes more than 2 times occur, because the amplitude of helical spring 22 is less, so also can not become the level that becomes problem in picking.So, the higher modes more than 2 times are ignored.
The damper D1 that is connected with particle M represents the damper corresponding to the friction at the assembly department place of the friction of helical spring 22 and its ambient air and helical spring 22.The damping coefficient of damper D1 is very little, but is not zero.
Left end Z represents to import the input part (being spring compressor 20) by the periodic displacement of the cam profile of cam 27 and the decision of water injection conditions in mode of execution.Ti Shi attenuating device 39 can be represented with auxiliary spring 25 and damper D2 in the present invention, and damper D2 is illustrated in the frictional force that produces between viscous fluid Q and the tube portion 33.
If the damping coefficient that the spring constant of auxiliary spring 25 is Kd, establish damper D2 is Cd.For about which of Kd, Cd all be ∞ situation, promptly about not in the present invention the generation principle of the resonance of the pump in the past of the attenuating device 39 of prompting describe.
If establishing the natural frequency of spring system (comprising helical spring 22) is f, then under situation about the cam displacement being input among the input part Z, motivate the natural vibration of spring system.If natural frequency f is not consistent with n times (n is an integer) of loom rotational speed, then the natural vibration of spring system can not be exaggerated, and spring system moves corresponding to the cam deflection curve.But under n times of natural frequency f and loom rotational speed consistent situation, the motion of helical spring 22 and cam deflection curve are synchronous, and spring vibration is exaggerated, and the violent vibrational state of helical spring 22 is continued.Because only act on the very little damping force that has damper D1 to produce on spring system, so helical spring 22 vibrates tempestuously, this vibration transfer causes pressure pulsation to plunger 18.
All be limited pump 12, promptly possess in the pump 12 of the attenuating device 39 of prompting in the present invention the action amplitude of auxiliary spring 25 restriction fluid spring seats 231 which of Kd, Cd.The spring constant Kd of auxiliary spring 25 is bigger than the spring constant K of helical spring 22.If establishing the coefficient of viscosity of viscous fluid Q and be μ, tube portion 33 is that the gap (degree of depth of groove 34) at the end of the outer circumferential face of A, tube portion 33 and groove 34 is ε (illustrated in Fig. 1 C) with respect to the area of contact of viscous fluid Q, then damping coefficient Cd is provided by following formula (1).
Cd＝μ×A/ε…(1)
Damping coefficient Cd can regulate on a large scale by change μ, A, ε.
The fit value of the damping coefficient Cd of damper D2 is considered the frequency characteristic decision by the spring system of the graphical representation of Fig. 3.Transverse axis in the plotted curve of Fig. 3 is represented frequency, and the longitudinal axis is represented the vibration amplitude ratio of helical spring 22.The plotted curve of Fig. 3 is represented frequency characteristic with the displacement of the central part of the helical spring 22 of cam displacement under the situation of input part Z input respectively for different damping coefficient Cd in mechanical model shown in Figure 2.Under the situation of damping coefficient Cd very big (for example ∞), it is such that frequency characteristic becomes curve E1, and attenuating device 39 produces resonance as the rigid body action.Under the situation of damping coefficient Cd very little (for example zero), it is such that frequency characteristic becomes curve E2, and attenuating device 39 only as simple spring performance function, produces resonance.
It is minimum that frequency characteristic when curve Eo represents that damping coefficient Cd is fit value, the peak value of resonance become.The fit value of damping coefficient Cd exists with ... spring constant than Kd/K, and spring constant is more littler than Kd/K, and the fit value of damping coefficient Cd is also more little.The fit value of damping coefficient Cd can be according to the plotted curve prediction of Fig. 3.But, in practicality, have the modelling error.Therefore, the viscosity of preferably finally regulating the shape (gap ε, area of contact A) of damper D2 and viscous fluid Q is by experiment selected the fit value of damping coefficient Cd.
The waveform G1 that represents with solid line in the plotted curve of Fig. 4 A represents to use the example of water jet pressure change of the pump 12 of attenuating device 39.The waveform H1 that represents with dot and dash line represents the example that the strain of helical spring 22 changes.In the case, the spring constant Kd of auxiliary spring 25 is set at 5 times of spring constant K of helical spring 22, at gap ε=0.5mm, area of contact A=100cm
2 Groove 34 in enclose the viscous fluid Q of coefficient of viscosity 10000 pools.The strain of helical spring 22 is measured by paste strainometer on helical spring 22.
The waveform G2 that represents with solid line in the plotted curve of Fig. 4 B represents not use the example of water jet pressure change of the pump in the past of attenuating device 39.The waveform H2 that is represented by dot and dash line represents the example that the strain of helical spring 22 changes.Spring constant K is identical with the situation of Fig. 4 A.
By the plotted curve of Fig. 4 A and Fig. 4 B as can be known, in the pump 12 that uses attenuating device 39, the pulsation of water jet pressure is less.
Waveform J1 in the plotted curve of Fig. 5 represents to measure the result of the pulsation rate X of the water jet pressure waveform under the situation of using the pump 12 that possesses attenuating device 39 to make the variation of loom rotational speed.Waveform J2 represents to measure the result that pump in the past that use do not possess attenuating device 39 makes the pulsation rate X of the water jet pressure waveform under the situation that the loom rotational speed changes.Pulsation rate X is represented with following formula (2) by pressure variance A P shown in Fig. 4 C and initiation pressure Pa.
X＝0.5×A?P/Pa …(2)
As by shown in the waveform J2, in pump in the past, every about 50rpm carries out the increase and decrease of pulsation rate X repeatedly.On the other hand, shown in waveform J1, in the pump 12 that possesses attenuating device 39, in pulsation rate X is included in about the pulsation rate of the minimum under the situation of pump in the past in the whole zone of loom rotational speed.By the result as can be known, pump in accordance with the present invention 12 is no matter loom is with what kind of rotational speed action, even perhaps under the situation that has changed helical spring 22, always also can keep the less water jet pressure waveform of pressure stable pulsation.
If the spring constant Kd of auxiliary spring 25 is diminished, then the amplitude of fluid spring seat 231 increases, and the active force of damper D2 (frictional force of viscous fluid Q) increases, and it is big that the vibration suppressioning effect of helical spring 22 becomes.But if spring constant Kd is diminished, then the size of auxiliary spring 25 increases.Therefore, making spring constant Kd too small is bad for the aspect of taking in of auxiliary spring 25 in pump 12.In addition, if spring constant Kd is diminished, then the amplitude of fluid spring seat 231 increases.Therefore, make spring constant Kd too small not preferred aspect durability, reliability.Otherwise if make spring constant Kd excessive, then the size of auxiliary spring 25 becomes compact, but the amplitude of fluid spring seat 231 diminishes.Thereby the active force of damper D2 reduces, and the vibration suppressioning effect of helical spring 22 diminishes.
If consider these situations, then preferably spring constant Kd is set at and makes it satisfy following formula (3).
3×K≤Kd≤20×K …(3)
In the 1st mode of execution, can access following advantage.
(1) has the shock absorption that helps very much helical spring 22 than the big elasticity variable quantity (variable quantity of the vibration-direction of plunger 18) of the vibration damping sheet of in the past decay usefulness and auxiliary spring 25 with spring constant Kd bigger than the spring constant K of helical spring 22.In addition, the frictional force that between viscous fluid Q and tube portion 33, produces make fluid spring seat 231 double vibrations, be the vibration attenuation of helical spring 22.As a result, can suppress the pressure pulsation of the high pressure water that spues from the pump 12 that uses helical spring 22.
(2) by the fricative frictional attenuation power between viscous fluid Q and the tube portion 33 damping force of the vibration that is synchronized with helical spring 22 is acted on the helical spring 22, make the vibration attenuation of helical spring 22.This frictional attenuation power is used as the adjusting key element of the shock absorption that is used for improving helical spring 22 and uses.
(3) viscous fluid Q is fit to as the key element of the frictional attenuation power generating unit that is configured to produce frictional force steady in a long-term.
(4) containing room (groove 34) that is formed on the ring-type between the tube portion 201 of a portion 33 and spring compressor 20 complete cycle that spreads all over a portion 33 contacts in tube portion 33.Therefore, the complete cycle that the frictional force that produces spreads all over a portion 33 that moves between viscous fluid Q and tube portion 33 by fluid spring seat 231 acts on equably, and frictional force can not become inclined to one side load and act in the portion 33.As a result, can relax the vibration of helical spring 22 well.Chimeric mutually tube portion 33 and tube portion 201 have the shape that is suitable for forming the containing room of enclosing viscous fluid Q.
(5) tube portion 201 is parts of spring compressor 20.Thereby the spring compressor in the past 20 that stubborn merging is attached on the pump case 16 uses as the guiding tube of guiding tube portion 33.Therefore, do not need to be used for the guiding tube of special use of guiding tube portion 33.
(6) disc spring 24 is owing to have than the big spring constant of the spring constant of helical spring 22 and compact, so be fit to as auxiliary spring.
Follow the 2nd mode of execution of explanatory drawing 6.Use identical reference character for the structural portion identical with the 1st mode of execution.
Between the 1st end 221 of the spring seat 202 of spring compressor 20 and helical spring 22, be provided with fluid spring seat 40 and a plurality of disc spring 24 of ring flat-plate shape, on fluid spring seat 40, link and be fixed with tube 41.The external diameter of tube 41 is slightly littler than the external diameter of fluid spring seat 40.Thereby, between the inner peripheral surface of the tube portion 201 of the outer circumferential face of tube 41 and spring compressor 20, form the gap.In this gap, be incorporated with the viscous fluid Q of the paste that can not drop from the gap.If fluid spring seat 40 moves, then between viscous fluid Q and tube 41, produce friction, frictional force action is on fluid spring seat 40 and helical spring 22.The tube portion 201 of spring compressor 20 is with the flexible direction guiding of tube 41 to the helical spring 22 shown in the arrow W.Tube 41 and tube portion 201 between form the containing room (above-mentioned gap) be used for accommodating viscous fluid Q.
Between the 2nd end 222 of the spring seat 192 of spring seat device 19 and helical spring 22, be provided with fluid spring seat 42 and a plurality of disc spring 43.On fluid spring seat 42, link and be fixed with tube 44.Fluid spring seat 42 is bonded on the 2nd end 222 of helical spring 22.The internal diameter of tube 44 is bigger slightly than the external diameter of spring seat device 19.Thereby, between the outer circumferential face of the tube portion 191 of the inner peripheral surface of tube 44 and spring seat device 19, form the gap.In this gap, be incorporated with viscous fluid Q.If fluid spring seat 42 relatively moves with respect to the tube portion 191 of spring seat device 19, then between viscous fluid Q and tube 44, produce friction, frictional force action is on fluid spring seat 42 and helical spring 22.The tube portion 191 of spring seat device 19 is the flexible direction guiding of tube 44 along the helical spring 22 shown in the arrow W, tube 44 and tube portion 191 between form the containing room (above-mentioned gap) that is used for accommodating viscous fluid Q.
In the 2nd mode of execution, except with the same advantage of the advantage of (1)～(4) of the 1st mode of execution and (6), can also obtain following advantage.
(7) being formed on tube 44 and gap (containing room of ring-type) between the tube portion 191 of spring seat device 19 spreads all over the complete cycle that is located at tins 44 on the fluid spring seat 42 and contacts on tube 44.Therefore, the complete cycle that the frictional force that produces between viscous fluid Q and tube 44 spreads all over tube 44 that moves by fluid spring seat 42 acts on equably, and frictional force can not become inclined to one side load and act on the tube 44.As a result, can relax the vibration of helical spring 22 well.Mutually chimeric tube 44 and tube portion 191 are the containing room formation parts that are suitable for forming the shape of the containing room of enclosing viscous fluid Q.
(8) tube portion 191 is parts of spring seat device 19, links the spring seat device 19 in the past be fixed on the plunger 18 and uses as the guiding tube of guiding tube 44.Therefore, do not need to be used for the guiding tube of special use of guiding tube 44.
(9) in the 1st end of helical spring 22 221 sides attenuating device 39A is set, and is provided with attenuating device 39B in the 2nd end 222 sides.In this structure, compare component number increases with the 1st mode of execution.But, compare the elastic deformation amount that can reduce auxiliary spring 25 and auxiliary spring 45 with the auxiliary spring 25 of the 1st mode of execution, and the energy of the vibration attenuation that is used for making helical spring 22 is distributed on attenuating device 39A and the attenuating device 39B.Therefore, can reduce the strain of auxiliary spring 25,45.The structure that attenuating device is set respectively in the both end sides of helical spring 22 is being preferred aspect the fatigue strength of auxiliary spring 25,45.
In addition, both end sides at helical spring 22 is provided with respectively in the structure of attenuating device, compare with the structure that only at the either side of the both end sides of helical spring 22 attenuating device is set, the speed of cutting off of viscous fluid Q and be accompanied by the heating of cutting off and reduce is so the life-span of viscous fluid Q increases.
Then, the 3rd mode of execution of explanatory drawing 7.Use identical reference character for the structural portion identical with the 1st mode of execution.
Spring compressor 20A possesses a portion 201 and links the spring be fixed in the portion 201 and accepts parts 46.Spring is accepted parts 46 and is possessed spring seat 461 and tube portion 462 as basic spring seat.In tube portion 462, contain fluid spring carrier 47.Fluid spring carrier 47 possess the ring flat-plate shape fluid spring seat 471, be positioned at fluid spring seat 471 all sides tube portion 472 and be positioned at the tube portion 473 of the outer circumferential side of fluid spring seat 471.Fluid spring seat 471, tube portion 472 and tube portion 473 are integrally formed.Tube portion 472 connects spring seat 461, is provided with seal ring 49 between tube portion 472 and spring seat 461.Accept the seal ring 50 that is provided with between the tube portion 462 of parts 46 as elastomeric rubber system at tube portion 473 and spring.Seal ring 49,50 will be filled with viscous fluid by spring seat 461 and the sealing of fluid spring carrier 47 area surrounded in the sealing zone.
Accept at spring be provided with between the fluid spring seat 471 of the spring seat 461 of parts 46 and fluid spring carrier 47 many to disc spring 48A, 48B.Disc spring 48A and 48B are close to mutually and are overlapping.Disc spring 48A, 48B formation is located at as the auxiliary spring 51 between the fluid spring seat 471 of the spring seat 461 of basic spring seat and fluid spring carrier 47.The spring constant of auxiliary spring 51 is bigger than the spring constant of helical spring 22.
Along with the flexible direction of fluid spring carrier 47 to helical spring 22 moves, accept in the tube portion 462 of parts 46 at spring as elastomeric seal ring 50 sliding contacts.By this sliding contact effect, frictional force action makes the vibration attenuation of helical spring 22 on fluid spring carrier 47.In addition, if helical spring 22 vibrations, then each by producing squeezing effect when they be close on the part because of the resiliently deformable relative movement, produce because of the viscous effect of viscous fluid that viscous fluid around fluid friction, disc spring 48A, the 48B is stirred, the increase and decrease of axial clearance between disc spring 48A, 48B, can access damping to disc spring 48A, 48B.
As a result, can suppress the pressure pulsation of the high pressure water that spues from the pump 12 that uses helical spring 22.
Then, the 4th mode of execution of explanatory drawing 8A and Fig. 8 B.Use identical reference character for the structural portion identical with the 2nd mode of execution.
Shown in Fig. 8 A, in spring compressor 20, in series contain helical spring 22A and, between helical spring 22A and secondary helical spring 22B, be provided with fluid spring carrier 52 as the secondary helical spring 22B of auxiliary spring.Helical spring 22A is with the suction action direction application of force of fluid spring carrier 52 to plunger 18, and secondary helical spring 22B is with the disgorging motion direction application of force of fluid spring carrier 52 to plunger 18.That is, the spring force of helical spring 22A resists via fluid spring carrier 52 mutually with the spring force of secondary helical spring 22B.
Freely growing with freely growing of helical spring 22A of secondary helical spring 22B is same, and the spring constant of the spring constant of secondary helical spring 22B and helical spring 22A is same.The free length of helical spring 22A and secondary helical spring 22B be the 2nd mode of execution helical spring 22 freely grow half, the line of helical spring 22A and secondary helical spring 22B footpath is same with the line footpath of the helical spring 22 of the 2nd mode of execution.That is, helical spring 22A and secondary helical spring 22B are equivalent to the helical spring 22 binary a pair of helical springs with the 2nd mode of execution.
Shown in Fig. 8 B, fluid spring carrier 52 possesses the fluid spring seat 521 of ring flat-plate shape and is positioned at the tube portion 522 of the periphery of fluid spring seat 521.Fluid spring seat 521 is integrally formed with tube portion 522.Tube portion 522 is embedded in the tube portion 201 of spring compressor 20 slidably.
The external diameter of tube portion 522 is slightly littler than the internal diameter of tube portion 201.Therefore, between the inner peripheral surface of the tube portion 201 of the outer circumferential face of tube portion 522 and spring compressor 20, form the gap.The viscous fluid Q of the paste that can not drop from the gap packs in this gap.If fluid spring carrier 52 (fluid spring seat 521) moves, then between viscous fluid Q and tube portion 522, produce friction, frictional force action is on fluid spring seat 521, helical spring 22A and secondary helical spring 22B.The tube portion 201 of spring compressor 20 is along the flexible direction guiding fluid spring carrier 52 (fluid spring seat 521) of helical spring 22A shown in the arrow W and secondary helical spring 22B.Tube portion 522 and tube portion 201 between form the containing room (above-mentioned gap) be used for accommodating viscous fluid Q.
If fluid spring carrier 52 (fluid spring seat 521) moves, then between viscous fluid Q and tube portion 201, produce friction, make the vibration attenuation of helical spring 22A and secondary helical spring 22B.Tube portion 201, tube portion 522 and viscous fluid Q constitute the frictional attenuation power generating unit by the mobile generation frictional attenuation power of fluid spring carrier 52 (fluid spring seat 521).
In the 4th mode of execution, except with the same advantage of the advantage of (2)～(5) of the 1st mode of execution, can also obtain following advantage.
(10) since fluid spring seat 521 be located at and freely grow between same helical spring 22A and the secondary helical spring 22B, so fluid spring seat 521 is half of stroke of plunger 18 with respect to the addendum modification (maximum addendum modification) of the displacement of 1 stroke of plunger 18.The maximum addendum modification of fluid spring seat 521 is big more, and the vibration-damping effect of helical spring 22A and secondary helical spring 22B is high more.The maximum addendum modification of fluid spring seat 521 is bigger than the maximum addendum modification of the fluid spring seat 231 of the 1st mode of execution.Therefore, the vibration-damping effect of the helical spring of present embodiment (helical spring 22A and secondary helical spring 22B) is compared with the situation of the 1st mode of execution significantly and is improved.
(11) also can access vibration-damping effect even a pair of helical spring that resonant frequency is different is housed in the spring compressor 20 side by side, but need make a pair of helical spring line directly little than single helical spring line footpath in the past for fear of the hole enlargementization of spring compressor 20.But if like this, it is littler than in the past single helical spring spring constant that a pair of helical spring synthetic spring constant that then is set up in parallel becomes.The characteristic that spues that this has changed pump can access the water jet pressure waveform of the water jet pressure waveform that approaches hope such shown in Fig. 4 C.
Be provided with in the present embodiment of freely growing same and helical spring 22A that spring constant is same and secondary helical spring 22B in series connection, the synthetic spring constant of helical spring 22A and secondary helical spring 22B and the spring constant of the helical spring 22 in the 1st mode of execution are same.Therefore, in the present embodiment, can access the water jet pressure waveform of the water jet pressure waveform that approaches hope such shown in Fig. 4 C.
Follow the 5th mode of execution of explanatory drawing 9A and Fig. 9 B.Use identical reference character for the structural portion identical with the 4th mode of execution.
Shown in Fig. 9 A, between helical spring 22A and secondary helical spring 22B, be provided with fluid spring carrier 53.Fluid spring carrier 53 have the tube portion 191 that surrounds spring seat device 19 cylinder base 54, be arranged on the periphery of cylinder base 54 and and a pair of fluid spring seat 55,56 of the integrally formed ring flat-plate shape of cylinder base 54 and mark the cylindrical portion 57 (Fig. 9 B illustrates) that supports chamber 571 55,56 of fluid spring seats.Helical spring 22A contact is on fluid spring seat 55, and with the suction action direction application of force of fluid spring carrier 53 to plunger 18, secondary helical spring 22B contact is on fluid spring seat 56, with the disgorging motion direction application of force of fluid spring carrier 53 to plunger 18.That is, the spring force of the spring force of helical spring 22A and secondary helical spring 22B is via 53 antagonism of fluid spring carrier.
Shown in Fig. 9 B, a plurality of (being 4 in the present embodiment) supporting chamber 571 equally spaced is provided with around plunger 18.In each supporting chamber 571, contain pressure spring 58 and slide member 59.Pressure spring 58 is crimped on slide member 59 on the inner peripheral surface 203 of tube portion 201 of spring compressor 20.Slide member 59 can slide with respect to the inner peripheral surface 203 of tube portion 201.Tube portion 201 is the slip guide portions that can guide slide member 59 along the flexible direction of helical spring 22A and secondary helical spring 22B slidably.Pressure spring 58 is by elastic force slide member 59 to be crimped on pressure contact portion in the portion 201.
If fluid spring carrier 53 (fluid spring seat 55,56) moves, then between slide member 59 and tube portion 201, produce friction, make the vibration attenuation of helical spring 22A and secondary helical spring 22B.The frictional attenuation power generating unit that tube portion 201, slide member 59 and pressure spring 58 constitute by the mobile generation frictional attenuation power of fluid spring carrier 53 (fluid spring seat 55,56).
In the 5th mode of execution, can access the same advantage of advantage that reaches (11) with (10) of the 4th mode of execution.
Then, the 6th mode of execution of explanatory drawing 10A, Figure 10 B and Figure 10 C.Use identical reference character for the structural portion identical with the 5th mode of execution.
Shown in Figure 10 A, between helical spring 22A and secondary helical spring 22B, be provided with fluid spring carrier 60.Fluid spring carrier 60 possess the tube portion 191 that surrounds spring seat device 19 a pair of cylinder base 61,62, be attached at a pair of fluid spring seat 63,64 of the ring flat-plate shape on the periphery of cylinder base 61,62 and be positioned on the outer periphery of fluid spring seat 63,64 and the cylindrical portion 65,66 integrally formed with fluid spring seat 63,64.A pair of cylinder base 61,62 engages with concentric mutually.A pair of cylindrical portion 65,66 engages with concentric mutually.In fluid spring carrier 60, form Packed chamber 601.
But in chamber 601, can contain the rotating ring 67 of ring-type movably to the movement direction of plunger 18.
Shown in Figure 10 C, but on the 1st end face of rotating ring 67, be formed with a plurality of recesses 671, but on the 2nd end face of rotating ring 67, be formed with a plurality of recesses 672.Recess 671 and recess 672 be opening round about mutually.Shown in Figure 10 B, a plurality of (4 in the present embodiment) recess 671 equally spaced is located at around the plunger 18, and a plurality of (4 in the present embodiment) recess 672 equally spaced is located at around the plunger 18.
Shown in Figure 10 C, between the end of recess 671 and fluid spring seat 63, be provided with pressure spring 68, be provided with pressure spring 69 between recess 672 and the fluid spring seat 64.But the spring force of the spring force of pressure spring 68 and pressure spring 69 resists on the movement direction of plunger 18 via rotating ring 67, but rotating ring 67 can be gone up vibration at the movement direction (direction of vibration of helical spring 22A and secondary helical spring 22B) of plunger 18.
In chamber 601, enclose liquid S is arranged.But on rotating ring 67, be formed with circulation path 673, but so that its 1st end face from rotating ring 67 connect to the 2nd end face.If but rotating ring 67 moves to another from fluid spring seat 64 one of fluid spring seat 63, then liquid S circulates circulation path 673 in towards above-mentioned one from above-mentioned another.
But the inertia effect of the rotating ring 67 that moves by being accompanied by fluid spring carrier 60 makes the vibration attenuation of helical spring 22A and secondary helical spring 22B.But rotating ring 67, pressure spring 68,69, liquid S and circulation path 673 constitute the moving bump leveller 70 (deamplification force generating part) that produces damping force that moves by fluid spring carrier 60 (fluid spring seat 63,64).
In the 6th mode of execution, can access the same advantage of advantage that reaches (11) with (10) of the 4th mode of execution.
The present invention also can be following such mode of execution.
Also can use rubber as auxiliary spring.In the case, also can when moving, the fluid spring carrier produce frictional force by this rubber and miscellaneous part sliding contact.
Also can using gases spring (for example pneumatic spring) as auxiliary spring.
In the 2nd mode of execution, also can attenuating device 39A be set and attenuating device 39B only is set.
In the 5th mode of execution, also two, slide member 59 more than 3 or 5 equally spaced can be located at spring seat device 19 tube portion 191 around.
In the 6th mode of execution, in the tube portion 191 that also viscous fluid Q can be filled into spring seat device 19 and the gap of cylinder base 61,62.
In the 4th～the 6th mode of execution, freely growing of secondary helical spring 22B also can be than the free length of helical spring 22A.
In the 4th～the 6th mode of execution, freely growing of secondary helical spring 22B also can be than the freely length of helical spring 22A.
Claims (10)
1. picking pump, be adapted at by the water that sprays from Weft insertion nozzle with use the water jet loom of weft yarn picking, by utilize helical spring spring force make plunger action, with the picking pump of water to above-mentioned Weft insertion nozzle force feed, it is characterized in that possessing:
The basis spring seat is arranged on the spring compressor that is fixed in pump case or is fixed on the spring seat device of above-mentioned plunger;
The fluid spring seat is bonded on the end that is clipped in the above-mentioned helical spring above-mentioned basic spring seat side between above-mentioned spring compressor and the above-mentioned spring seat device;
Auxiliary spring, an end engage with above-mentioned basic spring seat and the other end and above-mentioned fluid spring seated connection close;
Deamplification force generating part makes the damping force of helical spring vibration attenuation with respect to the mobile generation of above-mentioned fluid spring seat.
2. picking pump as claimed in claim 1 is characterized in that, above-mentioned deamplification force generating part is the frictional attenuation power generating unit with respect to the mobile generation frictional attenuation power of above-mentioned fluid spring seat.
3. picking pump as claimed in claim 2, it is characterized in that above-mentioned frictional attenuation power generating unit possesses the 2nd containing room that the 1st containing room that is located on the above-mentioned fluid spring seat forms parts, forms the parts concerted action with above-mentioned the 1st containing room and form containing room and forms parts and be enclosed in viscous fluid in the above-mentioned containing room.
4. picking pump as claimed in claim 3, it is characterized in that, it is the cartridge units that are attached on the above-mentioned fluid spring seat that above-mentioned the 1st containing room forms parts, it is to be entrenched on the above-mentioned cartridge unit so that can guide the guiding tube of above-mentioned cartridge unit along above-mentioned helical spring flexible direction movably that above-mentioned the 2nd containing room forms parts, and above-mentioned containing room is formed between the outer circumferential face of the inner peripheral surface of above-mentioned guiding tube and above-mentioned cartridge unit.
5. picking pump as claimed in claim 2, it is characterized in that above-mentioned frictional attenuation power generating unit possesses the slide member that is bearing on the above-mentioned fluid spring seat, can guide the slip guide portion of above-mentioned slide member slidably and by elastic force above-mentioned slide member is crimped on pressure contact portion on the above-mentioned slip guide portion along above-mentioned helical spring flexible direction.
6. picking pump as claimed in claim 1 is characterized in that, above-mentioned deamplification force generating part is provided in a side of the moving bump leveller on the above-mentioned fluid spring seat.
7. picking pump as claimed in claim 1 is characterized in that, above-mentioned auxiliary spring is secondary helical spring, and above-mentioned pair is helical spring freely to be grown and above-mentioned helical spring freely length equally, and the spring constant of above-mentioned auxiliary spring and above-mentioned helical spring spring constant are same.
8. as each described picking pump in the claim 1～6, it is characterized in that the spring constant of above-mentioned auxiliary spring is bigger than above-mentioned helical spring spring constant.
9. picking pump as claimed in claim 8 is characterized in that above-mentioned auxiliary spring is made of disc spring.
10. picking pump as claimed in claim 2, it is characterized in that, above-mentioned frictional attenuation power generating unit is an elastomer, above-mentioned elastomer along with moving of above-mentioned fluid spring seat sliding contact at least one of the tube portion of the tube portion of above-mentioned spring compressor and above-mentioned spring seat device.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007163737 | 2007-06-21 | ||
| JP2007163737 | 2007-06-21 | ||
| JP2007-163737 | 2007-06-21 | ||
| JP2008151968A JP2009024319A (en) | 2007-06-21 | 2008-06-10 | Weft inserting pump of water jet loom |
| JP2008-151968 | 2008-06-10 | ||
| JP2008151968 | 2008-06-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101328872A CN101328872A (en) | 2008-12-24 |
| CN101328872B true CN101328872B (en) | 2010-12-15 |
Family
ID=40204843
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101253702A Expired - Fee Related CN101328872B (en) | 2007-06-21 | 2008-06-20 | Picking pump of water jet loom |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2009024319A (en) |
| CN (1) | CN101328872B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5521588B2 (en) * | 2010-02-01 | 2014-06-18 | 株式会社豊田自動織機 | Water injection device for water jet loom |
| JP2014214402A (en) * | 2013-04-26 | 2014-11-17 | 株式会社豊田自動織機 | Weft inserting pump of water jet loom |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1162029A (en) * | 1996-03-21 | 1997-10-15 | 日产得克西斯株式会社 | Pump for water-jetting type textile machine |
| JP2002235261A (en) * | 2001-02-06 | 2002-08-23 | Tsudakoma Corp | Weft-insertion pump for water-jet loom |
| CN2753755Y (en) * | 2004-09-25 | 2006-01-25 | 绍兴越剑机械制造有限公司 | Jet loom weft-jet device |
-
2008
- 2008-06-10 JP JP2008151968A patent/JP2009024319A/en active Pending
- 2008-06-20 CN CN2008101253702A patent/CN101328872B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1162029A (en) * | 1996-03-21 | 1997-10-15 | 日产得克西斯株式会社 | Pump for water-jetting type textile machine |
| JP2002235261A (en) * | 2001-02-06 | 2002-08-23 | Tsudakoma Corp | Weft-insertion pump for water-jet loom |
| CN2753755Y (en) * | 2004-09-25 | 2006-01-25 | 绍兴越剑机械制造有限公司 | Jet loom weft-jet device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2009024319A (en) | 2009-02-05 |
| CN101328872A (en) | 2008-12-24 |
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