CN109306600B - Washing machine anti-collision barrel device and washing machine - Google Patents
Washing machine anti-collision barrel device and washing machine Download PDFInfo
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- CN109306600B CN109306600B CN201710632488.3A CN201710632488A CN109306600B CN 109306600 B CN109306600 B CN 109306600B CN 201710632488 A CN201710632488 A CN 201710632488A CN 109306600 B CN109306600 B CN 109306600B
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/20—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/26—Casings; Tubs
- D06F37/265—Counterweights mounted to the tub; Mountings therefor
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Abstract
The invention provides a washing machine anti-collision barrel device and a washing machine, wherein the anti-collision barrel device comprises a guide sleeve and a guide rod, one end of the guide rod extends into the guide sleeve, a damping sheet matched with the guide rod to generate damping force is arranged on the inner side of the guide sleeve, the guide rod is provided with a no-load section in the middle and working sections positioned at two ends of the no-load section, the diameter of the no-load section is smaller than the inner diameter of the damping sheet, and the diameter of the working section is larger than the inner diameter of the damping sheet; the anti-collision barrel device is provided with the no-load section and the working section, so that variable damping force is provided, and when the outer barrel vibrates greatly, the anti-collision barrel device provides enough damping force to prevent the outer barrel from colliding a box; and in the safe amplitude of the stable operation of the outer drum of the washing machine, the anti-collision drum device gives smaller damping force or does not give damping force; therefore, the problem that the washing machine collides the box during low-speed dehydration can be prevented, and the noise of the whole machine cannot be increased due to the increase of vibration transmitted to the box during high-speed dehydration.
Description
Technical Field
The invention belongs to the technical field of washing machines, and particularly relates to an anti-collision barrel device of a washing machine and the washing machine with the anti-collision barrel device.
Background
At present, the vibration of the washing machine is mainly used for hanging the inner barrel and the outer barrel of the washing machine through the hanging rods hung at the four corners of the washing machine, the vibration of the inner barrel and the outer barrel is reduced by compressing the hanging rods in the washing and dewatering processes, and the vibration of the inner barrel and the outer barrel is consumed by the hanging rods through self damping. However, the hanger rod can only buffer the vibration in the vertical direction, and cannot reduce the transverse vibration, so that the box is collided under large eccentricity, and the volume ratio and the starting capability of the washing machine are influenced.
In the dehydration process of the pulsator washing machine, the rotating speed is increased from zero to 700 revolutions or even higher. The eccentric load caused by the unbalanced clothes is gradually increased along with the increase of the rotating speed, and the fundamental frequency of the exciting force corresponding to the eccentric load is increased from zero to dozens of hertz. The pulsator washing machine generally has an obvious inherent mode near 1-3 Hz, and when the rotating speed of the washing machine passes through the mode frequency, the washing machine is caused to generate a resonance phenomenon. If the resonance phenomenon of the washing machine cannot be well controlled, the washing machine can be collided and even damaged.
In order to solve the problem of the box collision of the washing machine, a spring is fixed between the outer cylinder and the box body in patent CN201020229971.0 to provide restoring force. When resonance occurs, the outer cylinder and the box body are greatly displaced, so that a spring connected between the outer cylinder and the box body is stretched or compressed to generate restoring force, the displacement between the outer cylinder and the box body is reduced, and the problem of box collision caused by overlarge vibration of the washing machine is solved. However, when the rotating speed of the washing machine exceeds the corresponding modal frequency to reach the stable rotating speed and the washing machine is in normal dehydration work, the spring can transmit the vibration on the outer cylinder to the box body, so that the box body of the washing machine vibrates and produces sound, and the noise of the whole machine is increased.
Disclosure of Invention
The invention aims at the problems in the prior art and provides an anti-collision barrel device of a washing machine, which can prevent the problem of box collision of the washing machine during low-speed dehydration and ensure that the noise of the whole machine is not increased due to the increase of vibration transmitted to a box body during high-speed dehydration.
In order to achieve the technical purpose, the invention adopts the following technical scheme:
an anti-collision barrel device of a washing machine comprises a guide sleeve and a guide rod, wherein one end of the guide rod extends into the guide sleeve, a damping fin matched with the guide rod to generate damping force is arranged on the inner side of the guide sleeve, the guide rod is provided with an idle load section in the middle and working sections positioned at two ends of the idle load section, the diameter of the idle load section is smaller than the inner diameter of the damping fin, and the diameter of the working section is larger than the inner diameter of the damping fin; when the washing machine is in stable operation, the no-load section is positioned at the damping sheet; when the vibration of the outer drum of the washing machine is large, the working section is located at the damping sheet.
Furthermore, the working section is provided with a cylindrical main working section and a reducing section arranged between the idle loading section and the main working section, and the diameter of any section of the reducing section is positioned between the diameter of the idle loading section and the diameter of the working section.
Further, the guide rod is also provided with a stopping section which extends towards the end along the working section, the guide rod moves telescopically relative to the guide sleeve, and when the stopping section of the guide rod moves to the vicinity of the damping sheet, the relative movement of the stopping section of the guide rod and the damping sheet is stopped.
Furthermore, the guide sleeve is of a cylindrical structure with one open end, the damping fin is arranged on the inner side of the open end of the guide sleeve, and a first hinge portion is arranged at the other end of the guide sleeve.
Furthermore, the guide rod is a hollow rod with an opening at one end, the opening end of the hollow rod is positioned in the guide sleeve, and the other end of the guide rod is provided with a second hinge part.
Furthermore, a clamping sleeve is arranged between the damping fin and the guide sleeve, an annular first notch is formed in the inner side of the opening end of the guide sleeve, and the clamping sleeve is positioned at the first notch; and a second notch is formed in the inner side of the clamping sleeve, and the damping sheet is positioned at the second notch and is in contact with the radial edge of the first notch.
Furthermore, the end part of the clamping sleeve is also provided with a blocking edge extending outwards along the radial direction, and the blocking edge is positioned at the end part of the opening end of the guide sleeve.
Furthermore, at least two buckles are circumferentially distributed on the outer side of the clamping sleeve, a clamping groove matched with the buckle is formed in the first notch, and the buckle is clamped and fixed in the clamping groove.
Furthermore, a vent hole is formed in the sleeve wall at the end opposite to the opening end of the guide sleeve.
Based on the anti-collision barrel device of the washing machine, the invention also provides a design method of the anti-collision barrel device, which comprises the following steps:
A. determining the maximum eccentric force Fe of the washing machine during dehydration according to the parameters of the washing machine; further determining the damping force F of the crash can deviceDFinally determining the interference distance d between the working section of the guide rod and the damping finc；
B. According to the interference spacing dcAt the maximum diameter phi of the working section of the guide rodwAnd inner diameter phi of damping fincIn accordance with phiw=φc+2dcAfter one of the sizes is selected, the other size can be calculated;
C. according to the inner diameter phi of the damping finc，Determining the diameter phi of the no-load section of the guide rodz；
D. According to the displacement amplitude d of the outer cylinder in the dehydration stable operation stage of the washing machineODetermining the length L of the idle section of the guide barz；
E. According to the length L of the idle section of the guide rodzAnd a minimum distance L between the outer cylinder and the caseMaxDetermining the length L of the working section of the guide rodw；
F. And obtaining the anti-collision barrel device designed for the washing machine according to the main parameters of the anti-collision barrel device in the steps.
Further, in step A, the eccentric mass m is started according to the dehydration of the washing machineeInner barrel diameter r of washing machine1And the highest resonance frequency f of the low-frequency rigid body modePMaxCalculating the eccentric force Fe = m when the washing machine dehydratese*(2πfPMax)2rI。
Furthermore, step A1 is provided in step A, and a crash box balance force F is determined according to the eccentric force FeC=s1Fe(ii) a Wherein s is1The safety factor is.
Preferably, 0.1<s1<3。
Further, step A2 is provided after step A1, and the step A is based on the crash box balancing force FCAnd the number N of the anti-collision barrel devices planned to be arranged on the washing machine, and calculating the damping force of each anti-collision barrel device to be FD(ii) a Damping force FD=2FC/N。
Further, there is a step A3 after the step a2 in the step a, where the damping force according to the crash-proof tub device is FDAnd the friction coefficient c of the selected damping sheet, and determining the positive pressure F between the working section of the guide rod and the damping sheetN=FD/c。
Further, step A4 is provided after step A3 in step A according to positive pressure FNAnd the equivalent stiffness k of the damping fincDetermining the interference distance d between the working section of the guide rod and the damping sheetc=FN/kc。
Further, in step C, the diameter phi of the idle section of the guide rodz=s3φcWherein s is3For safety factor, 0.3<s3≤1。
Further, in step D, the length L of the idle section of the guide rodz=2s4dOWherein s is4To a safety factor, s4>1。
Preferably, 1<s4<3。
Further, in step E, the length L of the working section of the guide rodw=s5LMax-Lz/2 wherein s5For safety factor, 0.2<s5<1。
Further, the maximum diameter phi of the working section of the guide rodwDiameter phi of the no-load sectionzA frustum-shaped transition section is arranged between the two parts.
Further, the maximum diameter phi of the working section of the guide rodwDiameter phi of the no-load sectionzA cambered surface-shaped transition section is arranged between the two guide bars, and the diameter of any cross section of the cambered surface-shaped transition section is positioned at the maximum diameter phi of the working section of the guide barwDiameter phi of no-load sectionzIn the meantime.
Further, the maximum diameter phi of the working section of the guide rodwDiameter phi of the no-load sectionzAt least one section of cylindrical transition section is arranged between the guide rod and the guide rod, and the diameter of the cylindrical transition section is positioned at the maximum diameter phi of the working section of the guide rodwDiameter phi of no-load sectionzIn the meantime.
Based on the anti-collision barrel device of the washing machine, the invention also provides the washing machine with the anti-collision barrel device, which can prevent the washing machine from colliding a box during low-speed dehydration and ensure that the noise of the whole machine is not increased due to the increase of vibration transmitted to the box during high-speed dehydration.
A washing machine comprises a box body, an outer barrel and an inner barrel, wherein the outer barrel and the inner barrel are arranged in the box body in a sleeved mode, the outer barrel is hung on the box body through a hanging rod, and the anti-collision barrel device is arranged between any two of the outer barrel, the box body and the hanging rod.
The anti-collision barrel device is used for providing damping force in the horizontal direction, variable damping force is provided by arranging the guide rod with the no-load section in the middle and the working sections at two ends of the no-load section, and when the outer barrel vibrates greatly, the anti-collision barrel device provides enough damping force to prevent the outer barrel from colliding with a box; and in the safe amplitude of the stable operation of the outer drum of the washing machine, the anti-collision drum device gives smaller damping force or does not give damping force; thus, when the washing machine is in stable operation, the no-load section is positioned at the damping sheet; when the vibration of the outer drum of the washing machine is large, the working section is positioned at the damping sheet; therefore, the problem that the washing machine collides the box during low-speed dehydration can be prevented, and the noise of the whole machine cannot be increased due to the increase of vibration transmitted to the box during high-speed dehydration.
Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when taken in conjunction with the accompanying drawings.
Drawings
Fig. 1 is a schematic structural view of an embodiment of a crash-proof bucket apparatus according to the present invention;
FIG. 2 is a schematic cross-sectional view of FIG. 1;
FIG. 3 is an enlarged exploded view of the damper of FIG. 2;
FIG. 4 is a schematic view of the damper rod of FIG. 2;
fig. 5 is a washing machine provided with the crash-proof tub device of fig. 1;
FIG. 6 is a flow chart of a design method of the crash bucket apparatus;
fig. 7 is a schematic view showing a specific structure of the guide bar.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention.
In the description of the present invention, it should be noted that the terms "inside", "upper", "lower", "left", "right", etc. indicate the positional relationship based on the positional relationship shown in the drawings, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Referring to fig. 1 to 7, which are views showing an embodiment of the anti-collision tub device according to the present invention, the washing machine includes a cabinet 10, an outer tub 20 and an inner tub 30 disposed in the cabinet 10, the outer tub 20 being hung on corner plates at four corners of the cabinet 10 by four hanger rods 40; the collision of the washing machine mainly occurs in the dehydration starting stage, when the fundamental frequency of the exciting force corresponding to the rotating speed of the washing machine is close to the common frequency of the inner barrel machine hanger rod and the outer barrel machine hanger rod component system, the inner barrel and the outer barrel resonate, the amplitude of the outer barrel 20 is obviously increased, and the outer barrel 20 collides with a box body, so that the collision occurs. In order to prevent the tub from colliding, at least two anti-collision tub devices 50 are oppositely arranged on the washing machine for providing a damping force in the horizontal direction; the anti-collision tub device 50 is disposed between two of the box body 10, the tub 20, and the hanger bar 40, preferably between the box body 10 and the tub 20, and provides a more effective damping force to prevent collision of the tub due to the relative stillness of the box body 10.
In this embodiment, the anti-collision barrel device 50 includes a guide rod 1 and a guide sleeve 3 sleeved outside the guide rod 1, a damping fin 2 matched with the guide rod 1 to generate a damping force is disposed inside the guide sleeve 3, the guide rod 1 has an idle load section 12 at the middle portion and working sections 11 located at two ends of the idle load section 12, wherein the diameter of the idle load section 12 is smaller than the inner diameter of the damping fin 2, and the diameter of the working sections 11 is larger than the inner diameter of the damping fin 2.
In the embodiment, the barrel collision is avoided by generating damping force between the guide rod 1 and the damping fin 2; by the guide rod 1 having the no-load section 12 and the working section 11, when the washing machine is in stable operation, the no-load section 12 is located at the damping fin 2, that is, the outer drum 20 of the washing machine is within the safe amplitude of the stable operation, the anti-collision drum device gives a small damping force or no damping force, so that the vibration on the outer drum 20 cannot be transmitted to the box body 10 through the anti-collision drum device 50, and the increase of noise is avoided; when the outer cylinder of the washing machine vibrates greatly, the risk of collision of the cylinder is existed, the extension amplitude of the guide rod 1 is large at the moment, the working section 12 is positioned at the damping fin 2, and the damping force for stopping the vibration of the outer cylinder 20 is generated at the moment, so that the vibration amplitude of the outer cylinder 20 is reduced, and the collision of the cylinder is avoided; that is, the anti-collision tub device 50 provides a variable damping force, and the anti-collision tub device 50 needs to prevent the washing machine from colliding with the cabinet during low-speed dehydration and ensure that the noise of the whole machine is not increased due to the increase of vibration transmitted to the cabinet during high-speed dehydration.
In the present embodiment, referring to fig. 4, the idle load section 12 is cylindrical, the working section 11 has a main working section 111 which is cylindrical and a reducing section 112 which is arranged between the idle load section 12 and the main working section 111, and of course, the parts of the reducing section 112 with a diameter larger than the inner diameter of the damping fin 2 are all contacted with the damping fin 2 to generate damping force; the reducing section 112 is in a frustum shape, that is, a generatrix of the reducing section 112 is a straight line connecting one end of the idling section 12 and the main working section 111, and the diameter of any section of the reducing section 112 is located between the diameter of the idling section 12 and the diameter of the main working section 111. The variable diameter section 112 is arranged to enable the guide rod 1 to smoothly transit between the idle section 12 and the working section 11 during telescopic motion, and when the variable diameter section 112 passes through the damping fin 2, the damping force between the variable diameter section 112 and the damping fin 2 is gradually changed.
In this embodiment, the guide rod 1 further has a stopping section 13 extending along the working section 11 towards the end, the diameter of the stopping section 13 is certainly larger than that of the working section 11, the guide rod 1 moves telescopically relative to the guide sleeve 3, and the relative movement of the stopping section 14 of the guide rod 1 stops when the stopping section moves to the vicinity of the damping fin 2. The guide rod 1 can be prevented from being separated from the guide sleeve 3 by arranging the cut-off section 13, and meanwhile, the cut-off section 13 can also move to the position near the damping sheet 2 only when the amplitude of the outer cylinder 20 is large, so that the guide rod 1 and the guide sleeve 3 are relatively static at the moment, namely the guide rod 1 and the guide sleeve 3 form a rigid whole, and the rigid stopping force can be given to the outer cylinder 20 to prevent the box body of the outer cylinder 20 from colliding.
In the present embodiment, as shown in fig. 2, the guide sleeve 3 is a tubular structure with one end open, the damping fin 2 is disposed inside the open end of the guide sleeve 3, and the other end of the guide sleeve 3 is provided with the first hinge portion 31. The vibration of the outer cylinder 20 drives the guide rod 1 to move relative to the guide sleeve 3, so as to provide variable damping force; the vent hole 32 is formed in the sleeve wall at the end opposite to the opening end of the guide sleeve 3, when the guide rod 1 moves in the guide sleeve 3 in a telescopic mode, gas can flow out or enter the guide sleeve 3 through the vent hole 32, the fact that one section of gas is sealed in the guide sleeve 3 by the free end of the guide rod 1 is avoided, therefore, when the guide rod 1 moves, the gas in the guide sleeve 3 can flow out or be supplemented, and therefore when vibration of the outer cylinder 20 is slow, gas damping cannot be formed.
In the embodiment, the guide rod 1 is a hollow rod with an opening at one end, the opening end of the hollow rod is positioned in the guide sleeve 3, and the cavity of the guide rod 1 is communicated with the cavity of the guide sleeve 3 by arranging the hollow rod of the guide rod 1, so that a larger accommodating space is formed, and when the guide rod 1 moves in the guide sleeve 3 in a telescopic manner, the influence of the airflow flowing through the through hole 32 on the guide rod 1 is reduced; the other end of the guide bar 1 is provided with a second hinge 14.
Referring to fig. 3, in order to fix the damper 2, a cutting sleeve 5 is arranged between the damper 2 and the guide sleeve 3, an annular first notch 33 is formed in the inner side of the opening end of the guide sleeve 3, and the cutting sleeve 5 is located at the first notch 33; a second notch 51 is formed in the inner side of the ferrule 5, and the damping fin 2 is located at the second notch 51 and contacts with the radial edge of the first notch 33. The damping fin 2 is limited and fixed by the clamping sleeve 5 and the first notch 33, the thickness of the clamping sleeve 5 is equal to that of the first notch 33, and therefore the connecting and fixing structures at the two ends of the damping fin 2 are flush; the thickness of the damping fin 2 is greater than that of the second notch 51, that is, a part of the damping fin 2 protrudes inward, and the working section of the guide rod 1 moves relative to the protruding part of the damping fin 2 to generate a frictional damping force.
In order to firmly fix the cutting sleeve 5, at least two buckles 52 are circumferentially arranged on the outer side of the cutting sleeve 5, a clamping groove 331 matched with the buckles 52 is formed in the first notch 33, the buckles 52 are clamped and fixed in the clamping groove 331, and four buckles 52 are uniformly distributed in the axial direction of the cutting sleeve 5; thus, the fastener 52 and the clamping groove 331 are arranged, so that the firmness of fixation between the cutting sleeve 5 and the guide sleeve 3 is increased, and meanwhile, the assembly operation of the cutting sleeve 5 is simple.
In order to further increase the stability and the aesthetic appearance of the fixed ferrule 5, a stop edge 53 extending radially outward is further provided at the end of the ferrule 5, and the stop edge 53 is located at the end of the opening end of the guide sleeve 3. The force-bearing performance of the cutting sleeve 5 is improved by arranging the blocking edge 53, the stability of the cutting sleeve 5 is improved, and the attractiveness of the cutting sleeve 5 and the guide sleeve 3 after assembly is improved.
In this embodiment, in order to make the anti-collision tub device 50 provide the required variable damping force, the anti-collision tub device 50 needs to be designed for a specific model of the washing machine, and the main parameters of the anti-collision tub device 50 designed for the washing machine are derived according to the known conditions of the washing machine, so as to ensure that the anti-collision tub device 50 has the above-mentioned effects.
Referring to fig. 6, a method for designing the anti-collision barrel device 50 in the present embodiment includes the following steps:
A. determining the maximum eccentric force Fe of the washing machine during dehydration according to the parameters of the washing machine; further determining the damping force F of the crash can deviceDFinally determining the interference distance d between the working section of the guide rod and the damping finc。
In particular, the eccentric mass m is activated according to the dehydration of the washing machineeInner barrel diameter r of washing machine1And the highest resonance frequency f of the low-frequency rigid body modePMaxCalculating the eccentric force Fe = m when the washing machine dehydratese*(2πfPMax)2rI. Wherein the dewatering starting eccentric mass m of the washing machine is determined according to the eccentricity resistance determined during the design of the washing machine of the modele(ii) a Highest resonance frequency f of low frequency rigid body mode of washing machinePMaxIs a value obtained by simulation under ideal conditions; and calculating to obtain the eccentric force Fe which is the maximum eccentric force when the washing machine dehydrates.
Step A1, determining the balance force F of the anti-collision box according to the eccentric force Fe of the washing machine during dehydrationC=s1Fe(ii) a Wherein s is1For safety reasons, preferably, 0.1<s1<3。
Specifically, in order to overcome the eccentric force during the dehydration of the washing machine and prevent the washing machine outer cylinder 20 from colliding with the tank, the crash box device 50 needs to provide a crash box balance force FCWherein F is required to be satisfiedC>Fe-Fh-FaIn which F ishHorizontal balance force, F, provided for the boom 40aAnd the elastic restoring force is provided for the motor spindle. FhDependent on the amount of spring deflection of the suspension bar 40 and the angle of the suspension bar 40 to the vertical, FaRelated to the motor spindle slip angle. Since in the usual case FhSmaller and FaRelated to main shaft deflection angleThus, these two forces are replaced by a safety factor s 1.
Step A2, balancing force F according to the crash-proof boxCAnd the number N of the crash-proof tub devices 50 planned to be set on the washing machine, and calculating the damping force of each crash-proof tub device 50 as FD(ii) a Damping force FD=2FC/N。
Specifically, each washing machine is at least guaranteed to have two or more crash box devices 50, and each washing machine is at least guaranteed to have two crash box devices placed in different directions, so as to guarantee that when the outer tub 20 vibrates in the horizontal direction, the two crash box devices 50 damp the vibration of the outer tub 20 from two directions. The number of crash box arrangements 50 is preferably an integer multiple of 2, preferably 2, 4, 6, 8. The included angle of two adjacent crash box devices 50 on the horizontal plane is 30 ° to 150 °, preferably, four crash box devices 50 are adopted, and two adjacent crash box devices 50 are perpendicular to each other, that is, the included angle of two adjacent crash box devices 50 on the horizontal plane is 90 °.
Step A3, the damping force according to the crash-proof barrel device 50 is FDAnd the selected coefficient of friction c of the damping plate 2, determining the positive pressure F between the working section 11 of the guide rod 1 and the damping plate 2N=FDAnd c, the ratio of the total weight to the total weight of the product. Wherein, FNIs proportional to the contact area and the contact normal stress of the damping fin 2 and the guide rod 1.
Step A4 according to positive pressure FNAnd the equivalent stiffness k of the damper 2cDetermining the interference distance d between the working section 11 of the guide rod 1 and the damping fin 2c=FN/kc。
B. According to the interference spacing dcThe maximum diameter phi of the working section 11 of the guide rod 1wAnd the inner diameter phi of the damping fin 2cIn accordance with phiw=φc+2dcAfter one of the dimensions is selected, the other dimension can be calculated.
Specifically, the damping fin 2 is circular, phic isThe diameter of the inner circle of the damping sheet 2 and the maximum diameter phi of the working section 11 of the guide rod 1wAnd the inner diameter phi of the damping fin 2cOne value is selected and the other is calculated.
C. According to the inner diameter phi of the damping fin 2c，Determining the diameter phi of the idle section 12 of the guide rod 1z。
In particular, the diameter φ of the idle section 11 of the guide rod 1zMust be smaller than the inner diameter phi of the damping fin 2cSo as to ensure that no damping force exists between the no-load section 12 and the damping fin 2; is preferably phiz=s3φcWherein s is3For safety factor, 0.3<s3≤1。
D. According to the displacement amplitude d of the outer cylinder 20 in the dehydration stable operation stage of the washing machineODetermining the length L of the free section 12 of the guide rod 1z。
In particular, the displacement amplitude dOFor a displacement amplitude in the horizontal direction, the length L of the free-load section 12 of the guide rod 1z=2s4dOWherein s is4To a safety factor, s4>1 to ensure that the no-load section 12 is positioned at the damping fin 2 when the outer cylinder 40 operates stably, and the anti-collision barrel device 50 does not provide damping force; wherein 1 is<s4<3, but s4Cannot be too large, so as to avoid that the working section of the guide rod 1 is not positioned at the damping fin 2, preferably 1, when the vibration amplitude of the outer drum 20 of the washing machine is large<s4<1.5。
E. According to the length L of the idle section of the guide rod 1zAnd a minimum distance L between the outer cylinder 20 and the casing 10MaxDetermining the length L of the working section 11 of the guide rod 1w。
Particularly, in order to ensure that the outer cylinder does not collide the box, the length L of the working section of the guide rodw<LMax-Lz/2 wherein LMaxIs the minimum distance between the outer cylinder and the box body. The guide rod 1 is also provided with a stop section 13 extending along the working section 11 towards the end, when the stop section 13 of the guide rod 1 moves to the vicinity of the damping sheet 2, the relative movement of the stop section and the damping sheet is stopped, namely, the barrel collision preventing device 50 gives rigid resistance to the outer barrel 20 at the moment, the barrel collision of the outer barrel 20 is avoided, and therefore, the working section length L of the guide rod is setw<LMax-Lz/2. To further ensure safety, L is preferredw=s5LMax-Lz/2,s5For safety factor, 0.2 is preferred<s5<1。
F. According to the main parameters of the anti-collision barrel device 50 in the above steps, the anti-collision barrel device designed for the washing machine is obtained.
Specifically, the barrel crash prevention device 50 obtained in the above steps has several main parameters: the maximum diameter phi of the working section 11 of the guide rod 1wLength L of working sectionwDiameter phi of the no-load section 12zLength L of the idle section 12zInner diameter phi of the damping fin 2c。
Referring to fig. 7, a concrete structure form of the guide rod 1 is shown, and the no-load section 12 is of a diameter phiz、Length LzOf equal diameter, the working section 11 having a diameter phiwThe equal diameter cylindrical section 111 and the frustum-shaped transition section 112, the diameter of any cross section of the frustum-shaped transition section is positioned at the maximum diameter phi of the working section 11 of the guide rod 1wDiameter phi of the idle section 13zIn the meantime. The frustum-shaped transition section 112 is a frustum between the equal-diameter cylindrical section 111 and the idle section 12, the cut-off sections 13 are located at two ends of the guide rod 1, and the cut-off sections 13 are also equal-diameter cylindrical sections.
In order to further explain the design method of the anti-collision barrel device, the design process is illustrated by taking an 8kg platform pulsator washing machine as an example, and the design method is as follows:
A. determining the maximum eccentric force Fe of the washing machine during dehydration according to the parameters of the washing machine; further determining the damping force F of the crash can deviceDFinally determining the interference distance d between the working section of the guide rod and the damping finc。
In particular, the eccentric mass m is activated according to the dehydration of the washing machinee=1kg, washing machine inner barrel diameter r1=0.25m and the highest resonance frequency f of the low-frequency rigid body modePMax=3.5Hz, and the eccentricity force Fe = m when the washing machine is dehydrating is calculatede*(2πfPMax)2rI=121N。
Step A1, calculating the balance force F of the anti-collision box according to the eccentric force Fe of the washing machine during dehydrationC=s1Fe(ii) a Wherein s is1To a safety factorPreferably s1=0.2, thus FC=24N。
Step A2, balancing force F according to the crash-proof boxCAnd the number N of the crash-proof tub devices 50 planned to be set on the washing machine, and calculating the damping force of each crash-proof tub device 50 as FD(ii) a Damping force FD=2FCand/N. With four anti-collision tub arrangements 50 on the washing machine, i.e. N =4, the damping force FD=24N。
Step A3, the damping force according to the crash-proof barrel device 50 is FDAnd the friction coefficient c =0.3 of the selected damping fin 2, and the positive pressure F between the working section 11 of the guide rod 1 and the damping fin 2 is calculatedN=FD/c=40N。
Step A4 according to positive pressure FNAnd the equivalent stiffness k of the damper 2cWherein k isc=5×104N/m, calculating the interference distance d between the working section 11 of the guide rod 1 and the damping sheet 2c=FN/kcc=0.8×10-3m。
B. According to the interference spacing dcSelecting the inner diameter phi of the damping fin 2c=1.5×10-2m, and according to phiw=φc+2dcThe maximum diameter phi of the working section 11 of the guide rod 1 is calculatedw=1.66×10-2m。
C. According to the inner diameter phi of the damping fin 2c，Wherein phiz=s3φc，s3=0.9, the diameter phi of the idle section 12 of the guide rod 1 is calculatedz= 1.35×10-2m。
D. According to the displacement amplitude d of the outer cylinder 20 in the dehydration stable operation stage of the washing machineOWherein d isO=3×10-3m，s4=1.2, the length L of the free segment 12 of the guide bar 1 is calculatedz=7.2×10-3m。
E. According to the length L of the idle section 12 of the guide rod 1zAnd a minimum distance L between the outer cylinder 20 and the casing 10MaxDetermining the length L of the working section 11 of the guide rod 1w=s5LMax-Lz/2 wherein LMax=1.8×10-2m，s5If =0.9, then the working segmentLength L of 11w=9×10-3m。
The tub crash prevention device designed for the washing machine is obtained according to the main parameters of the tub crash prevention device 50 in the above steps.
The foregoing is directed to preferred embodiments of the present invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow. However, any simple modification, equivalent change and modification of the above embodiments according to the technical essence of the present invention are within the protection scope of the technical solution of the present invention.
Claims (10)
1. A washing machine anti-collision barrel device comprises a guide sleeve and a guide rod, wherein one end of the guide rod extends into the guide sleeve, and a damping fin matched with the guide rod to generate damping force is arranged on the inner side of the guide sleeve; when the washing machine is in stable operation, the no-load section is positioned at the damping sheet; when the vibration of the outer drum of the washing machine is large, the working section is positioned at the damping sheet;
the design method of the anti-collision barrel device comprises the following steps:
A. determining the maximum eccentric force Fe of the washing machine during dehydration according to the parameters of the washing machine; further determining the damping force F of the crash can deviceDFinally determining the interference distance d between the working section of the guide rod and the damping finc(ii) a The method specifically comprises the following steps:
a1, determining the balance force F of anti-collision box according to the maximum eccentric force Fe of washing machine during dewateringC=s1Fe(ii) a Wherein s is1A safety factor is set;
a2, based on crash box balancing force FCAnd the number N of the anti-collision barrel devices planned to be arranged on the washing machine, and calculating the damping force of each anti-collision barrel deviceIs FD(ii) a Damping force FD=2FC/N；
A3, according to the damping force of the anti-collision barrel device being FDAnd the friction coefficient c of the selected damping sheet, and determining the positive pressure F between the working section of the guide rod and the damping sheetN=FD/c；
A4, according to positive pressure FNAnd the equivalent stiffness k of the damping fincDetermining the interference distance d between the working section of the guide rod and the damping sheetc=FN/kc；
B. According to the interference spacing dcAt the maximum diameter phi of the working section of the guide rodwAnd inner diameter phi of damping fincIn accordance with phiw=φc+2dcAfter one of the sizes is selected, the other size can be calculated;
C. according to the inner diameter phi of the damping finc，Determining the diameter phi of the no-load section of the guide rodz；
D. According to the displacement amplitude d of the outer cylinder in the dehydration stable operation stage of the washing machineODetermining the length L of the idle section of the guide barz；
E. According to the length L of the idle section of the guide rodzAnd a minimum distance L between the outer cylinder and the caseMaxDetermining the length L of the working section of the guide rodw；
F. And obtaining the anti-collision barrel device designed for the washing machine according to the main parameters of the anti-collision barrel device in the steps.
2. The barrel crash barrier apparatus as recited in claim 1, wherein said working section has a main working section of a cylindrical shape, and a reducing section disposed between said idle section and said main working section, wherein a diameter of any section of said reducing section is located between a diameter of said idle section and a diameter of said working section.
3. The barrel crash barrier of claim 1 wherein said guide bar further comprises a stop section extending distally along said working section, said guide bar telescopically movable relative to said guide sleeve, relative movement of said guide bar and said stop section being stopped when said guide bar is moved adjacent said damping tab.
4. The barrel crash prevention device as claimed in claim 1, wherein the guide sleeve is a cylindrical structure having an open end, the damper is provided inside the open end of the guide sleeve, and the other end of the guide sleeve is provided with a first hinge portion.
5. The barrel crash prevention device as claimed in claim 1 wherein said guide bar is a hollow bar with one open end, the open end of said bar being located within said guide sleeve, the other end of said bar being provided with a second hinge.
6. The barrel collision prevention device according to any one of claims 1 to 5, wherein a ferrule is disposed between the damping fin and the guide sleeve, an annular first notch is disposed inside the open end of the guide sleeve, and the ferrule is located at the first notch; and a second notch is formed in the inner side of the clamping sleeve, and the damping sheet is positioned at the second notch and is in contact with the radial edge of the first notch.
7. The barrel crash prevention device as recited in claim 6 wherein the end of the ferrule is further provided with a radially outwardly extending ledge at the end of the open end of the guide sleeve.
8. The barrel collision prevention device according to claim 6, wherein at least two buckles are circumferentially arranged on the outer side of the cutting sleeve, a clamping groove matched with the buckles is formed in the first notch, and the buckles are clamped and fixed in the clamping groove.
9. The apparatus according to claim 4, wherein a vent hole is formed in the wall of the guide sleeve at an end opposite to the open end of the guide sleeve.
10. A washing machine, including the container body, and outer cylinder and inner cylinder that the suit sets up located in container body, the said outer cylinder hoists on the said container body through the hanger rod, characterized by that, there is the anti-collision barrel device of any one of claims 1 to 9 between any two of the said outer cylinder, container body, hanger rod.
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| CN201710632488.3A CN109306600B (en) | 2017-07-28 | 2017-07-28 | Washing machine anti-collision barrel device and washing machine |
| PCT/CN2017/119726 WO2019019553A1 (en) | 2017-07-28 | 2017-12-29 | Washing machine damping structure, design method, transverse shock-absorbing apparatus, and washing machine |
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| CN201710632488.3A CN109306600B (en) | 2017-07-28 | 2017-07-28 | Washing machine anti-collision barrel device and washing machine |
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| CN109306600B true CN109306600B (en) | 2022-04-12 |
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